 A method for controlling the outlet temperature of an oil-injected compressor or vacuum pump and an
专利摘要:
The present invention is directed to a method for controlling the outlet temperature of an oil-injected compressor or vacuum pump (1) comprising a compressor or vacuum element (4) with a gas inlet (5), an element outlet (6), and an oil inlet (12), the method comprising the steps of: measuring the outlet temperature (Tout) at the element outlet (6); - controlling the position of a control valve (15) to control the flow of oil flowing through a cooling (13) connected to the oil inlet (12); wherein the step of controlling the position of the control valve means that a fuzzy logic algorithm is applied to the measured outlet temperature (Tout); and characterized in that the method further comprises the step of controlling the speed of a fan (21) cooling the oil flowing through the cooling (13) by applying the fuzzy logic algorithm and further based on the state of the control valve (15). 公开号:BE1024497B1 申请号:E2017/5069 申请日:2017-02-03 公开日:2018-03-19 发明作者:Joeri COECKELBERGS；Yun Shi 申请人:Atlas Copco Airpower Naamloze Vennootschap； IPC主号:
专利说明:
(30) Priority data: 18/08/2016 US 62376550 25/10/2016 US 62412567 (73) Holder (s): ATLAS COPCO AIRPOWER public limited company 2610, WILRIJK Belgium (72) Inventor (s): COECKELBERGS Joeri 2610 WILRIJK Belgium SHI Yun 2610 WILRIJK Belgium (54) A method of controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump employing such a method. (57) The present invention is directed to a method of controlling the outlet temperature of an oil-injected compressor or vacuum pump (1) comprising a compressor or vacuum element (4) with a gas inlet (5), an element outlet (6), and a oil inlet (12), the method comprising the steps of: measuring the outlet temperature (Spout) at the element outlet (6); controlling the position of a control valve (15) to control the flow of oil flowing through a refrigeration (13) connected to the oil inlet (12); wherein the step of controlling the position of the control valve involves applying a fuzzy logic algorithm to the measured exhaust temperature (Tuit); and characterized in that the method further comprises the step of controlling the speed of a fan (21) cooling the oil flowing through the cooling (13) by applying the fuzzy logic algorithm and further based on the state of the control valve (15). ï Figure 1 BELGIAN INVENTION PATENT FPS Economy, K.M.O., Self-employed & Energy Publication number: 1024497 Filing number: BE2017 / 5069 Intellectual Property Office International Classification: F04C 28/00 F04B 49/06 Date of Issue: 19/03/2018 The Minister of Economy, Having regard to the Paris Convention of 20 March 1883 for the Protection of Industrial Property; Having regard to the Law of March 28, 1984 on inventive patents, Article 22, for patent applications filed before September 22, 2014; Having regard to Title 1 Invention Patents of Book XI of the Economic Law Code, Article XI.24, for patent applications filed from September 22, 2014; Having regard to the Royal Decree of 2 December 1986 on the filing, granting and maintenance of inventive patents, Article 28; Having regard to the application for an invention patent received by the Intellectual Property Office on 03/02/2017. Whereas for patent applications that fall within the scope of Title 1, Book XI, of the Code of Economic Law (hereinafter WER), in accordance with Article XI.19, § 4, second paragraph, of the WER, the granted patent will be limited. to the patent claims for which the novelty search report was prepared, when the patent application is the subject of a novelty search report indicating a lack of unity of invention as referred to in paragraph 1, and when the applicant does not limit his filing and does not file a divisional application in accordance with the search report. Decision: Article 1 ATLAS COPCO AIRPOWER public limited company, Boomsesteenweg 957, 2610 WILRIJK Belgium; represented by VAN VARENBERG Patrick, Arenbergstraat 13, 2000, ANTWERP; a Belgian invention patent with a term of 20 years, subject to payment of the annual taxes as referred to in Article XI.48, § 1 of the Code of Economic Law, for: A method for controlling the outlet temperature of an oil-injected compressor or vacuum pump and oil-injected compressor or vacuum pump applying such a method. INVENTOR (S): COECKELBERGS Joeri, c / o ATLAS COPCO AIRPOWER, limited liability company Boomsesteenweg 957, 2610, WILRIJK; SHI Yun, c / o ATLAS COPCO AIRPOWER, limited liability company Boomsesteenweg 957, 2610, WILRIJK; PRIORITY: 08/18/2016 US 62376550; 10/25/2016 US 62412567; BREAKDOWN: Split from basic application: Filing date of the basic application: Article 2. - This patent is granted without prior investigation into the patentability of the invention, without warranty of the Merit of the invention, nor of the accuracy of its description and at the risk of the applicant (s). Brussels, 19/03/2018, With special authorization: BE2017 / 5069 A method of controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump employing such a method. This invention relates to a method of controlling the outlet temperature of an oil-injected compressor or vacuum pump comprising a compressor or vacuum element with a gas inlet, an element outlet, and an oil inlet, the method comprising the steps of: measuring the outlet temperature at the element outlet; and controlling the position of a regulating valve to control the flow of oil flowing through a refrigeration connected to the oil inlet. It is known that the temperature at the outlet of an oil-injected compressor or vacuum pump must be kept above a minimum limit. Existing Systems typically use a fixed temperature thermostat and a fixed speed fan as part of a cooling system so that when the exhaust temperature reaches the minimum limit, the system will stop the fan until the exhaust temperature rises. If these Systems allowed the exhaust temperature to drop below such a limit, condensate would form inside the system, which would negatively affect the cooling or BE2017 / 5069 lubricity of the oil and also would have a corrosive effect, which would shorten the life of the system. At the same time, the exhaust temperature should not exceed a maximum limit as this can cause damage to the system, such as potentially reduced oil quality or even possible deformation of various components of the system. Tests have shown that when a fixed temperature thermostat and a fixed speed fan are used, the implemented solution is not always energy efficient. Even if the exhaust temperature were not significantly higher than the maximum limit, the fan would still start at the fixed and maximum speed, causing the temperature to drop rapidly, usually below the minimum limit, putting the system in a situation where the risk of condensate formation increases. In addition, since the fan should not run for long, the fan would turn on and off quickly, affecting the motor driving the fan. Other existing Systems use a PID controller and a variable speed fan. Where such Systems use separate control circuits to control the thermostat and fan. BE2017 / 5069 Tests have shown that such Systems exhibit irregular and fluctuating behavior since the two control circuits interfere with each other. The consequences of such behavior are emergency stops, damage to the mechanical components and premature wear of various system components. Another drawback of Systems using a PID controller is the fact that such a solution is suitable for single input single output analysis, while tests have shown that the analysis of such Systems can be more complex. Taking into account the above-mentioned drawbacks, it is an object of the present invention to provide a method for controlling the outlet temperature of an oil-injected compressor or vacuum pump and for avoiding condensation and at the same time of irregular and fluctuating behavior. The method of the present invention aims to provide an energy efficient and easy to implement solution, also for existing oil injected compressors or vacuum pumps. In addition, the proposed solution is suitable to be implemented for multi-input - multi-output type analyzes. The present invention aims to provide a solution that continuously adapts to the changing BE2017 / 5069 environmental conditions and at the same time applies to compressors or vacuum pumps all over the world. The present invention further aims to provide a compressor or vacuum pump components, and lines that have a minimum number of minimum number of fittings and such that the maintenance process can be performed much more easily. The present invention provides a solution to at least one of the above and / or other Problems by providing a method of controlling the outlet temperature of an oil-injected compressor or vacuum pump comprising a compressor or vacuum element including a gas inlet, an element outlet, and an oil inlet, the method comprising the steps of: - measuring the outlet temperature at the element outlet; - controlling the position of a control valve to control the flow of oil flowing through a refrigeration connected to the oil inlet; wherein in the step of controlling the position of the control valve, a faint logic algorithm is applied to the measured exhaust temperature; and characterized in that the method further comprises the step of controlling the speed of a fan cooling the oil flowing through the cooling using the fuzzy logic BE2017 / 5069 algorithm and further based on the position of the control valve. By controlling the position of the control valve based on a fuzzy logic algorithm, the method continuously adjusts the path of the oil within the compressor or vacuum pump so that the cooling power is actively adjusted to avoid condensation. In addition, the risk of condensation from the application of such a fuzzy logic algorithm taking into account the measured exhaust temperature is minimized, if not even eliminated. Since the speed of the fan cooling the oil flowing through the cooling is also controlled by the application of the fuzzy logic algorithm and based on the position of the control valve, such a fan is not started until oil reaches the cooling and the speed controlled in such a way that the compressor or vacuum pump operates at maximum efficiency, optimizing power consumption while continuously adapting to the current state of the compressor or vacuum pump. Since the method uses a fuzzy logic algorithm input with the measured exhaust temperature to control the position of the control valve and the speed of the fan cooling the oil flowing through the cooling, the method according to the present invention can easily be implemented on existing systems without it BE2017 / 5069 requires substantial intervention for this and without a major impact on the user of such a compressor or vacuum pump. Where such inlet and / or outlet temperature and / or pressure sensors are usually mounted within a compressor or vacuum pump. In addition, since the method uses measured outlet temperature, the method of the present invention continuously adapts to changing environmental conditions, thereby eliminating the risk of condensation inside the compressor or vacuum pump and extending the life of the oil used therein. In addition, if the compressor or vacuum pump user were to move the device from one geographic location to another, they could use the device immediately, without the need for intervention by a specialist engineer or manual input of certain parameters, as would immediately and automatically adjust the compressor or vacuum pump to the specificity of the new site. Another advantage of the current method is the fact that it uses a simple algorithm with multiple inputs and outputs that does not require large computing power or specialized components. In addition, since the fan speed is controlled based on the position of the control valve and the Ί /2017 / 5069 measured exhaust temperature, the risk of interference between the control valve position control and the fan speed control is eliminated. Preferably, the step of controlling the position of the control valve comprises controlling the flow of oil flowing through the cooling and through a bypass fluidly connected to the oil inlet to bypass the cooling. Since the path of the oil is selected between a bypass and the cooling, such cooling is not used until the temperature rises to a value that creates a risk of the oil or the components of the compressor or vacuum pump degrading. Consequently, the method of the present invention allows for a longer life of the components and keeps the frequency of maintenance interventions and the associated costs very low. In addition, since the path of the oil is chosen between a bypass line and a refrigeration before the oil reaches the oil inlet, approximately the same volume of oil is reinjected into the compressor or vacuum element at all times, keeping the lubricating and sealing properties constant. The present invention is further directed to an oil injected compressor or vacuum pump comprising: BE2017 / 5069 - a compressor or vacuum element with a gas inlet, an element outlet and an oil inlet; - an oil separator with a separator inlet in fluid communication with the element outlet, a separator outlet and an oil outlet in fluid connection with an oil inlet of the compressor or vacuum element by means of an oil pipe; - a cooling connected to the oil outlet of the oil separator and the oil inlet of the compressor or vacuum element; - a bypass that is in fluid communication with the oil outlet and the oil inlet to bypass the cooling; - a control valve provided on the oil outlet configured to allow oil to flow from the oil separator through the cooling and / or through the by-pass; - an exhaust temperature sensor positioned at the element outlet; - a controller that regulates the position of the control valve; the cooling being provided with a fan, and characterized in that the controller further comprises a fuzzy logic algorithm for controlling the speed of the fan based on the position of the control valve and the measured exhaust temperature, in order to BE2017 / 5069 maintain the exhaust temperature at approximately a predetermined target value. Since the oil-injected compressor or vacuum pump has such a structure, a minimum number of components, pipes and fittings are used to achieve an efficient overall system. The present invention is also directed to a controller for controlling the outlet temperature of an oil-injected compressor or vacuum pump comprising a compressor or vacuum element including a gas inlet, an element outlet, and an oil inlet, the controller comprising: a measuring element comprising a data input configured to receive outlet temperature data; - a communication element comprising a first data link for controlling the position of a control valve; at which the communication element for controlling the fan which flows the oil; and wherein further a second of the speed cools by the data link of a cooling the controller further comprises a processor having a fuzzy logic algorithm that controls the speed of the BE2017 / 5069 Fan determines based on the position of the control valve and the measured exhaust temperature. In the context of the present invention, it should be considered that the proposed advantages with regard to the method of maintaining the temperature at an outlet of the compressor or vacuum pump above a predetermined target value also apply to the oil-injected compressor or vacuum pump and to the controller. In addition, it should be assumed that the proposed advantage with regard to the oil-injected compressor or vacuum pump also applies to the controller. With the insight to better demonstrate the features of the invention, some preferred embodiments are described below, by way of example without any limitation, with reference to the accompanying drawings, in which: Figure 1 schematically depicts a compressor or vacuum pump according to an embodiment of the present invention; Figure 2 schematically depicts a compressor or vacuum pump according to another embodiment of the present invention; Figure 3 schematically shows a control valve according to an embodiment of the present invention; BE2017 / 5069 Figure 4 schematically shows a control valve according to an embodiment of the present invention; Figure 5 schematically depicts the graphical representation of the membership functions associated with the error according to an embodiment of the present invention; Figure 6 schematically depicts the graphical representation of the membership functions associated with the error evolution according to an embodiment of the present invention; Figure 7 schematically depicts the graphical representation of the membership functions associated with the change of the angle of the control valve (Delta_RV) according to an embodiment of the present invention; Figure 8 schematically shows the graphical representation of the membership functions associated with the position of the control valve (RV) according to an embodiment of the present invention; Figure 9 schematically shows the graphical representation of the membership functions associated with the position of the control valve (RV) according to another embodiment of the present invention; Figure 10 schematically the graphical representation of the membership functions associated with the change of the fan speed (Delta_VENTILATOR) BE2017 / 5069 according to an embodiment of the present invention; and Figure 11 schematically depicts a control circuit of the fuzzy logic algorithm according to an embodiment of the present invention. Figure 1 illustrates an oil-injected compressor or vacuum pump 1 comprising a process gas inlet 2 and an outlet 3. The compressor or vacuum pump 1 comprises a compressor or vacuum element 4 with a gas inlet 5 in fluid connection with the process gas inlet 2 and an element outlet 6 in fluid connection with the outlet 3. For the purposes of the present invention, oil-injected compressor or vacuum pump 1 is to be understood to mean the entire compressor or vacuum pump installation, including the compressor or vacuum element 4, all common connection lines and valves, the housing of the compressor or vacuum pump 1, and optionally the engine. 7 driving the compressor or vacuum element 4. In the context of the present invention, compressor or vacuum element 4 is to be understood to mean the housing of the compressor or vacuum element in which the compression or vacuum process takes place by means of a rotor or by a reciprocating movement. BE2017 / 5069 In the context of the present invention, the compressor or vacuum element 4 can be selected from a group comprising: screw, stepped, baffles, piston, etc. If the system includes a compressor element, the process gas inlet 2 is usually connected to the atmosphere and the outlet 3 is in fluid communication with a user's network (not shown) through which clean pressurized gas is supplied. If the system includes a vacuum pump, the process gas inlet 2 is usually connected to a user's network (not shown) and the outlet 3 is usually connected to the atmosphere or to an external network (not shown), through which clean gas is vented and possibly reused. The compressor or vacuum element 4 is driven by a motor 7 which can be a fixed speed motor or a variable speed motor. The gas coming out of the compressor or vacuum element 4 is passed through an oil separator 8 which has a separator inlet 9 which is in fluid communication with the element outlet 6 and in which the oil previously contained within the compressor or vacuum element 4 injected, separated from gas, for clean gas is passed through a separator outlet 10 which is in fluid communication with the outlet 3 of the compressor or vacuum pump 1. BE2017 / 5069 After the oil has been separated and collected in the oil separator 8, it can preferably flow through an oil outlet 11 which is in fluid communication with an oil inlet 12 of the compressor or vacuum element 4 through an oil line, through which the oil is redistributed injected into the compressor or vacuum element 4. Typically, the compression or vacuum process generates heat, which increases the temperature of the oil used for injection. Consequently, in order to cool the oil when such a temperature reaches or exceeds a predetermined target value, T target, the compressor or vacuum pump 1 further comprises a cooling 13 connected to the oil outlet 11 of the oil separator 8 and the oil inlet 12 of the oil separator 8. compressor or vacuum element 4. Since the oil only reaches the predetermined target value, T target, after a period of time in which the compressor or vacuum element 4 operates, a bypass line 14 is also provided. Where the by-pass 14 is in fluid communication with the oil outlet 11 and the oil inlet 12 of the compressor or vacuum element 4 and wherein the flow of oil can bypass the cooling 13 and be immediately injected again into the oil inlet 12. In the context of the present invention, it is to be assumed that the bypass line 14 and the fluid line along where the oil reaches the cooling 13 are two comparable lines, which BE2017 / 5069 are fluidly connected to the oil outlet 11 via, for example, a T-shaped connector, or that the oil outlet 11 may comprise two separate lines, one of which is the bypass line 14 and the other is the fluid line along where oil reaches the cooling 13 . Nor should it be excluded that the oil inlet 12 may comprise two fluid lines (not shown) or two injection points for the oil flowing through the oil outlet 12 with one injection point allowing the oil to flow through the cooling 13 to be reinjected into the compressor or vacuum element 4, and wherein an additional injection point allows the oil to flow through the bypass 14 to be reinjected into the compressor or vacuum element 4. The compressor or vacuum pump 1 is further provided with a control valve 15 provided on the oil outlet 11 configured to flow oil through the cooling 13. Depending on how the control valve 15 is mounted in the compressor or vacuum pump 1, it can further be configured so that oil can flow through the bypass 14. In another embodiment according to the present invention, and since the volume of oil flowing through the oil outlet 11 should preferably be kept constant, the volume of oil passing through the bypass BE2017 / 5069 flows automatically regulated! based on the volume of oil that can flow through the cooling 13. Preferably, the control valve 15 is configured to control the path that such oil follows before it reaches the oil inlet 12. Accordingly, the control valve 15 may be a three-way valve allowing fluid communication between the oil inlet 12 and the bypass 14 and / or between the oil inlet 12 and the fluid line along which the oil reaches the cooling 13. Consequently, the control valve 15 allows oil from the oil separator 8 to flow either through the cooling 13 or through the bypass 14, or to simultaneously split the oil flow: partly through the cooling 13 and partly through the bypass 14. To precisely control the path of the oil, the compressor or vacuum pump 1 further includes an outlet temperature sensor 19 positioned at the element outlet 6 to measure the outlet temperature, T U it. Preferably, but without any limitation, the compressor or vacuum pump 1 further includes an inlet temperature sensor 16 and an inlet pressure sensor 17 positioned at the gas inlet 5 to measure the inlet temperature and inlet pressure of the gas, and an outlet pressure sensor 19 positioned at the element outlet 6 of the flow line to measure the outlet pressure of the gas. BE2017 / 5069 A regulator 20 is usually provided for controlling the position of the regulating valve 15. Where such a controller 20 is preferably part of the compressor or vacuum pump 1. However, it cannot be excluded that such a controller 20 is located at a distance from the compressor or vacuum pump 1 and communicates with a local control unit that is part of the compressor or vacuum pump 1 via a wired or wireless connection. In the context of the present invention, the position of the regulating valve 15 is to be understood to mean the real physical position through which the oil can flow through the bypass line 14 and / or through the cooling 13. Depending on the type of control valve 15 used, such a position may be changed via a rotary movement, a blocking or activating type of operation, or through any other type of operation allowing to control a flow as explained above. In order to efficiently cool the oil flowing through the cooling 13, a fan 21 is preferably provided in the vicinity of the cooling 13. In addition, in order to maintain the energy efficiency of the compressor or vacuum pump 1 and to maintain the outlet temperature, T u it, at approximately a predetermined target value, T target, so that the risk of condensate formation is minimized or even eliminated. the BE2017 / 5069 controller 20 further includes a fuzzy logic algorithm to control the speed of the fan 21 based on the position of the control valve 15 and the measured exhaust temperature, T u it. In a preferred embodiment of the present invention, controller 20 further includes a data link 22 to receive measurements from each of: inlet temperature sensor 16, inlet pressure sensor 17, outlet temperature sensor 18 and outlet pressure sensor 19, the controller 20 further including an algorithm for calculating the predetermined target value, T target, taking into account a calculated atmospheric dew point, ADP, based on the measurements received. In the context of the present invention, data link 22 is to be understood to mean a wired or wireless data link between controller 20 and each of: inlet temperature sensor 16, inlet pressure sensor 17, outlet temperature sensor 18 and outlet pressure sensor 19. In an embodiment according to the present invention, for an even more precise calculation of the conditions of the compressor or vacuum pump 1, a relative humidity sensor 23 is placed at the gas inlet 5, the measurements of which are preferably sent to the controller 20 via a data link 22. Alternatively, the controller 20 may include means to estimate approximately the relative humidity, RH, of the gas flowing through the gas inlet 5 or the BE2017 / 5069 data input from the controller 20 can further be configured to receive a relative humidity measurement, RH, from an external relative humidity sensor not integrated in the compressor or vacuum pump 1 or from an external network. In a preferred embodiment according to the present invention, but without any limiting character, the controller 20 comprises means for controlling the speed of the fan 21 on the basis of the position of the control valve 15 and a first error, e1, calculated by the predetermined street value, T st reef, to be deducted from a first measured exhaust temperature, from: ex = Spout, i - T target (comparison 1). For the purposes of the present invention, means for controlling the speed of the fan 21 is to be understood to mean an electrical signal generated by the controller 20 through a wired or wireless connection between the controller 20 and the fan 21. The electrical signal allows to increase or decrease the fan speed. For easier and more precise control of the speed of the fan 21, the fan 21 is provided with a variable speed motor 24. In another embodiment according to the present invention and as illustrated in Figure 2, the compressor or vacuum pump 1 further comprises an energy recovery 20 BE2017 / 5069 element 25 connected to the oil outlet 11 and the oil inlet 12, in order to reuse the heat generated by the compression or vacuum process. Where such an energy recovery element 25 can transfer the heat collected by the oil to another medium such as, for example: a gaseous or liquid medium or to a material that changes phase and can use the transferred heat or generated energy to heat an object or heat water, within the heating system of a room, or to generate electrical energy, or the like. By integrating the energy recovery element 25, the energy footprint of the compressor or vacuum pump 1 is further reduced since instead of immediately starting a fan, the heat transfer between two media is emitted and further used, which the compressor or vacuum pump according to the current makes the invention environmentally friendly. For illustrative purposes only, without any limiting nature, the control valve 15 of the present invention is a rotary valve, as illustrated in Figure 3. Where such control valve 15 has four channels and a central rotating element 26 allowing two or more channels blocked or partially blocked, so that fluid cannot flow or partially flow through it. BE2017 / 5069 However, such a layout for a control valve 15 should not be considered as limiting and it should be assumed that any other type of valve capable of completely or partially blocking two or more fluid channels could also be used herein. If the compressor or vacuum pump 1 includes an energy recovery element 25, the control valve 15 may have the layout as illustrated in Figure 3. If the compressor or vacuum pump 1 does not include an energy recovery element 25, the control valve 15 may have the layout as illustrated in Figure 4, wherein one of the four channels is preferably blocked by a plug 27. Returning now to Figure 3, a first channel 28 is in fluid communication with the oil inlet 12, a second channel 29 is in fluid communication with the bypass 14, a third channel 30 is in fluid communication with the cooling 13 and a fourth channel 31 is in fluid communication with the energy recovery element 25. In another embodiment of the present invention, for more precise control of the position of the control valve 15, the controller 20 is further provided with means for calculating an error evolution, d (error) / dt. Where such error evolution, d (error) / dt, determines whether the error decreases or increases within a predetermined time interval. In the context of the present invention, among the means for calculating the error evolution, -, -. Ττ — ijïiT 'I ..... τη BE2017 / 5069 d (error) / dt, an algorithm to be understood which the controller 20 is provided with. Accordingly, to calculate the error evolution, d (error) / dt, the controller 20 preferably receives two consecutive exhaust temperature measurements, T U it, i θη T U it, 2, determines two consecutive errors: a first error, ei, and a second error, e2, by subtracting the predetermined target value, T target, from the first measured exhaust temperature, T U i t , i, (ei) and by subtracting the predetermined target value, T target from the measured measured exhaust temperature, (Θ2 ). Furthermore, the controller 20 subtracts the calculated first error, e1, from a subsequently calculated second error, e2 and divides it over the time interval, Δt, determined between the time, ti, at which the first exhaust temperature, T u it, i, became measured and the time, t2, at which the resulting exhaust temperature, T u it r 2, was measured: to finish Spout, 2, T2 Spout, 2 T target (Equation 2); d (error) / dt e 2 ~ ei At (equation 3); At = t 2 -t] (equation 4). Accordingly, the controller 20, on the basis of the measured outlet temperature, T ui t, and an error evolution, d (error) / dt, means for the position of the control valve 15 in such a way to change the oil by the energy-recovery element 25 can flow. BE2017 / 5069 For the purposes of the present invention, it should be assumed that the controller 20 is able to receive measurements, perform calculations, optionally forward calculated parameters to other components of the compressor or vacuum pump 1 or to an external computer, and generate electrical Signals to affect the working conditions of other components of the compressor or vacuum pump 1. Accordingly, the controller 20 may include a measuring element that includes a data input configured to receive: inlet temperature data, inlet pressure data, and outlet pressure data from, respectively: the inlet temperature sensor 16, inlet pressure sensor 17 and outlet pressure sensor 19. The controller 20 may further comprise a communication element with a first data link 32 to control the position of a control valve 15 such that oil can flow through the oil cooling 13 and / or a bypass 14 and / or through the energy recovery element 25. The controller further includes a second data link 33 for controlling the speed of a fan 21 which cools the oil flowing through the cooling 13. In the context of the present invention, it is to be assumed that the second data link 33 can communicate with an electronic module (not shown) positioned at the level of the fan 21 or communicate directly with the motor 24 or with BE2017 / 5069 an electronic module (not shown) at the motor 24 driving such fan 21. Preferably, the controller 20 is further provided with a processor of a fuzzy logic algorithm to determine the speed of the fan 21 on the basis of the position of the control valve 15, and the measured inlet and / or outlet temperature (Tin, T u it), and / or pressure (Pin, Puit). Furthermore, the processor may be provided with an algorithm to calculate the predetermined target value, T s target, from a calculated atmospheric dew point, ADP, based on the measurements received from the meter. In another embodiment of the present invention, the processor further includes an algorithm to determine the first error, e1, by using equation 1. Furthermore, to reduce the atmospheric dew point, Use ADP, humidity value to be determined, humidity, RH, a predetermined relative RH, or a measurement of the relative provided by the relative humidity sensor 23 at the gas inlet 5. In another embodiment of the present invention, the controller 20 can apply a predetermined time interval, Δt, also known as sampling frequency, between two successive measurements of temperature, pressure and / or relative humidity. from BE2017 / 5069 For the purposes of the present invention, it is to be assumed that the sampling frequency, At, may be the same for all parameters, or may be different for one or more of the measured parameters, depending on the requirements of the user's network and the required reaction speed for the compressor or vacuum pump 1. Depending on the capacities of the controller 20, such a sampling frequency, At, may be any value selected between 1 millisecond and 1 second. Preferably, for the sampling frequency, At, a value of less than 60 milliseconds is selected, more preferably less than 50 milliseconds. Even more preferably, the measurement element applies a sampling frequency of about 40 milliseconds between two consecutive measurements. Tests have shown that if the measured outlet temperature, T U it, is kept at approximately the determined atmospheric dew point, ADP, or if such a value is exceeded by a relatively small value, the oil-injected compressor or vacuum pump 1 will still operate efficiently and the the quality and service life of the oil or its components are not affected. Accordingly, the controller 20 preferably selects the predetermined target value, T target, by a predetermined one BE2017 / 5069 tolerance, T o ffset, to be raised at the determined atmospheric dew point, ADP. Such pre-determined tolerance, T is O ffset, can be chosen in fnnctie on the requirements of the oil-injected compressor or vacuum pump 1 and may be further manually inserted into the controller via, for example, a user interface (not shown), or may be via a wired or wireless connection from the a local or remote computer is sent to the controller 20. It should further be assumed that the value of the predetermined tolerance, T O ff S et, θη implicit in the predetermined target value, T target, can be changed over the life of the compressor or vacuum pump 1, depending on the requirements of the user's network. The method of controlling the outlet temperature, Tuit, of the oil-injected compressor or vacuum pump 1 is very simple and as follows. The predetermined target value, T target, can be either a pre-calculated value that can be input or sent to the oil-injected compressor or vacuum pump 1, or a system-determined value. In another embodiment of the present invention, the predetermined target value, T stree f, can be determined by the inlet temperature, Ti n , and the BE2017 / 5069 inlet pressure, Pin, to be measured via an inlet temperature sensor 16 and an inlet pressure sensor 17 and the outlet temperature, Tuit, and the outlet pressure, Puit, to be measured at the element outlet 6 via an outlet temperature sensor 18 and an outlet pressure sensor 19. The method of the present invention aims to keep the temperature at an outlet 3 of the oil-injected compressor or vacuum pump 1 at approximately the predetermined target value, T target, by adjusting the position of the control valve 15 to control the flow of oil flowing through the cooling 13 to control flow. Where the step of controlling the position of the control valve 15 means that a vague logic algorithm is applied to the measured exhaust temperature, T U it, and possibly to one or more of the following parameters: measured inlet temperature, Tin, measured inlet pressure, P outlet pressure measured in f,, Puit. In one embodiment of the present invention, without any limiting character, the predetermined target value, T target, can be determined by calculating the atmospheric dew point, ADP. One method of calculating atmospheric dew point, ADP, is to use the following formula: ADP TV m logi0 ( s ^ y (equation 5). BE2017 / 5069 Where, A, m and T n are empirically determined constants and can be selected from Table 1 according to the specific temperature range in which the compressor or vacuum pump 1 operates. a M T n maxwrong Temperature range 6,116441 7.591386 240.7263 0.083% (-20 ° C to + 50 ° C) 6.004918 7,337936 229.3975 0.017% (+ 50 ° C to + 100 ° C) 5.856548 7.27731 225.1033 0.003% (+ 100 ° C to + 150 ° C) water 6.002859 7,290361 227.1704 0.007% (+ 150 ° C to + 200 ° C) 9,980622 7.388931 263.1239 0.395% (+ 200 ° C to + 350 ° C) 6.089613 7.33502 230.3921 0.368% (0 ° C to + 200 ° C) ice 6.114742 9, 778707 273.1466 0.052% (-70 ° C to 0 ° C) Where such empirically determined constants have the following units of measurement: A, for example, stands for the water vapor pressure at 0 ° C and has the unit of measurement in Table 1: hectopascal (hPa), m is an adjustment constant without a unit of measurement, while T n is also an adjustment constant with degrees Celsius (° C) as a unit of measurement. Pwpres from Equation 5 Represents the water vapor pressure converted to atmospheric conditions and can be calculated using the following formula: pwpres P out Pin RV (equation 6}; where P is the inlet pressure to it, RV is measured outlet pressure, Pi n is the measured either the relative humidity at BE2017 / 5069 approximation either measured (if the system is a relative humidity sensor 23 includes) and pws in front of the water vapor saturation pressure state. As the system no relative humidity sensor 23 the Bee approach estimated relative humidity, RH, are selected as about 100% or less. The compressor or vacuum pump 1 may also receive a measurement of the relative humidity, RH, from a sensor positioned near the compressor or vacuum pump, or may receive such a measurement from an external network. Preferably, the relative humidity, RV, if the system includes a compressor, is the relative humidity of the ambient air when the gas inlet 2 is connected to the atmosphere or the relative humidity is characteristic of an external network if the gas inlet 2 is connected to such external network. Still preferably, if the system includes a vacuum pump, the relative humidity, RH, is the relative humidity of the process to which the gas inlet 2 is connected, the process being the user's network. The water vapor saturation pressure, p ws , can be calculated using the following formula: m ' T in p' s = A10 7 hi +7 '(equation 7); BE2017 / 5069 where Tin is the measured inlet temperature and A, m and T are the empirically determined constants from 'label 1. For the purposes of the present invention, the above-identified atmospheric dew point calculation method, ADP, should not be considered as limiting and it should be assumed that another method of calculation may be used without departing from the present invention. In another embodiment according to the present invention, the predetermined target value, T target, is determined from a maximum temperature at which various components of the oil-injected compressor or vacuum pump 1 can operate in normal parameters, such maximum temperature being dependent on the material used for the production or of their properties and how such properties change as the temperature increases. Such a maximum temperature can be, for example, the maximum temperature of the oil at which the viscosity, oil stability and degradation are kept within desired values over time, or the maximum temperature at which the control valve can function without the risk of deformation due to the material used for the production, or the maximum temperature at which the housing of the compressor or vacuum element 4 or the compressor or BE2017 / 5069 vacuum element 4 itself is resistant without the risks of material deformation, or the maximum temperature with which the bearings or seals mounted inside the compressor or vacuum pump can withstand, or the maximum temperature at which the temperature and / or pressure sensors can function without the risk of degradation, or a maximum temperature indicative of normal operation of the lines and fittings of the compressor or vacuum pump 1, or the like. In yet another embodiment of the present invention, without any limitation, the method further comprises the step of comparing the calculated predetermined target value, T target, with the lowest of the maximum temperatures characteristic of the various components, as defined above, and if the calculated predetermined target value, T st reef, is higher than the lowest maximum temperature, the method will consider the lowest maximum temperature as the calculated predetermined target value, T target. Alternatively, for further comparisons and calculations, the method will use the calculated predetermined target value, T target. Depending on the compressor or vacuum pump 1 requirements, determined target value, T target, and reaction rate of the calculated pre-selected may be selected as equal to the calculated atmospheric dew point, ADP, or the method of the present invention further comprises the BE2017 / 5069 step in which a tolerance, Toffset, is added to the calculated atmospheric dew point, ADP. Such a tolerance, Toffset, can be any value selected between 1 ° C and 10 ° C, more preferably between 1 ° C and 7 ° C, even more preferably, between 2 ° C and 5 ° C. Tests have shown that if the tolerance does not exceed the above values, the efficiency of the compressor or vacuum pump 1 is maintained, and the oil quality and stability of the overall system are ensured. Preferably, without any limitation, the predetermined target value, T target, preferably is kept between a minimum limit, T st reef, min, and a maximum limit, T target, max to avoid further condensation and the energy efficiency of the compressor or vacuum pump 1. Consequently, the predetermined target value, T target, is compared to the minimum limit, T target, min, and if the predetermined target value, T target, is less than the minimum limit, T target, min, the predetermined target value, T target, is selected as equal at the minimum limit, T target, min. Likewise, if the predetermined target value, T s target, is higher than the maximum limit, T target, max, the predetermined target value, T target, is selected to be equal to the maximum limit, T target, max BE2017 / 5069 For example, if the system includes a vacuum element, the minimum limit, T target, min, can be selected if any value is comprised between 60 ° C and 80 ° C, preferably between 70 ° C and 80 ° C, still more preferably, the minimum limit can be selected at about 75 ° C or less, and the maximum limit, T target, max, can be selected at about 100 ° C or less. Furthermore, if the system includes a vacuum element, the minimum limit, T target, min, can be selected as any value contained between 50 ° C and 70 ° C, preferably between 55 ° C and 65 ° C, even more preferably , the minimum limit can be selected at about 60 ° C or less, and the maximum limit, T target, max, can be selected at about 110 ° C or less. Furthermore, the fuzzy logic algorithm implemented by the method of the present invention includes the step of determining a first error, e1, by subtracting the predetermined target value, T target, from a first measured exhaust temperature, T U it., i. Further, the fuzzy logic algorithm, the step of determining a second error, e2, by the predetermined set point, T s treef, to pull a next measured outlet temperature, T u .it.2 off. To precisely determine the state of the overall system, the fuzzy logic algorithm further includes the step of calculating the error evolution, d (error) / dt, over the sampling frequency, by the derivative of the error BE2017 / 5069 over time. Consequently, the second error, e2, is subtracted from the first error, el, and the result is divided over the sampling frequency, At. The sampling frequency, At, is to be understood as a time interval, At, calculated between the moment, ti, at which the first outlet temperature, T U it, i, is measured and the moment, t2, at which the next outlet temperature, T U it, 2, is measured. Preferably, but without any limitation, the sampling frequency is selected at 40 milliseconds. Preferably, the fuzzy logic algorithm further comprises the step of determining the direction in which the position of the control valve 15 would change according to the first error, e1, or the second error, e2, and the error evolution, d (error) / dt. Still preferably, the fuzzy logic algorithm further comprises the step of determining of the speed with which the score from it would become a regulator valve modified on base from the first mistake (el) or the second mistake (e2), and the error evolution (d (error) / dt) In another invention, embodiment according to the fuzzy logic algorithm, current to obtain a more stable compressor or vacuum pump further comprises at least one filter, a low-pass filter (LPF), such as, for example, to filter transient temperature fluctuations. BE2017 / 5069 Where such an LPF is designed to disregard temperature fluctuations lasting for example less than one second or less than about five seconds, more preferably the LPF is designed to disregard temperature fluctuations lasting less than two seconds, even more preferably the LPF is designed to disregard temperature fluctuations lasting less than about three seconds. In yet another embodiment of the present invention, the fuzzy logic algorithm assigns membership functions to determine the logic output and further to calculate the calculated first error, e1, or second error, Θ2, and the error evolution, d {error) / dt. use. A example of a graphical representation of such membership functions is illustrated in Figure 5, for the error and in Figure 6, for the error evolution, d (error) / dt. Where the error is represented as a corresponding fuzzy value as a function of temperature, T, with degrees Celsius (° C) as the unit of measurement. While the error evolution, d (error) / dt, is represented as a corresponding fuzzy value as a function of temperature, T, over seconds, s, with degrees Celsius over seconds (° C / s) as the unit of measure. Where such membership functions are identified as N, Z and P for the graphs illustrated in Figure 5, where N stands for Negative, Z for Zero, for which the measured exhaust temperature, T U it, is equal or approximately equal BE2017 / 5069 is at the predetermined target value, T street ΘΠ P stands for Positive. Likewise, the membership functions are identified as N and P for the graphs illustrated in Figure 6, where N stands for negative and P for positive. The temperature interval [-ΔΤ; + ΔΤ] is selected according to the specificity of the compressor or vacuum pump 1 and such a parameter can be changed. For example, without any limitation, -ΔΤ may be any value selected between -10 ° C and -1 ° C, more preferably, -ΔΤ may be any value selected between -8 ° C and -5 ° C, even more preferably, -ΔΤ can be selected as about -8 ° C. Likewise, + ΔΤ can be any value selected between + 1 ° C and + 10 ° C, more preferably, + ΔΤ can be any value selected between + 5 ° C and + 8 ° C , even more preferably, + ΔΤ can be selected as approximately + 5 ° C. For the purposes of the present invention, the values selected for -ΔΤ and + ΔΤ should only be considered as an example and the present invention should not be limited to these specific values, any other values may be selected without the logic of influence the method of the present invention. BE2017 / 5069 Therefore, if the calculated error has a negative value, such a value should be displayed in the N graph of Figure 5 at the corresponding outlet temperature. If the calculated error is approximately zero and the measured exhaust temperature, Tuit, is approximately equal to the predetermined target value, T s tree £, such a value should be displayed in the Z graph at the corresponding temperature. Conversely, if the calculated error is positive, such a value should be displayed in the P Graph at the corresponding temperature. Likewise, if the error evolution is negative, such a value should be displayed in the N graph of Figure 6, while if the error evolution is positive, such a value should be displayed in the P graph. Where such values are displayed at a corresponding temperature T u .it, 2 Tuit, 1 over the time difference At. Accordingly, the determined fuzzy values related to the error and the error evolution, d (error) / dt, are further used by the fuzzy logic algorithm to determine the direction in which the control valve 15 is to be changed. Where such fuzzy values are any real number selected within the interval [0; 1] and according to the calculated error or error evolution, d (error) / dt. BE2017 / 5069 Consequently, if the second error, e2, is negative, N, or if the second error, e2, is approximately equal to zero, shown on the Z graph as explained above, and the error evolution, d (error) / dt, negative is, N, which means that the temperature of the oil decreases, so that it can be re-injected within the compressor or vacuum element, then the direction in which the position of the control valve 15 must be changed is such that more oil flows through the bypass line 14 can curdle. Conversely, if the second error, e2, is positive, P, or if the second error, es, is approximately zero, shown on the Z-graph, and the error evolution, d (error) / dt, positive is, P, which means that the temperature of the oil shows an increase between two consecutive exhaust temperature measurements, T U it, i and T U it, 2, is the direction in which the position of the control valve 15 is to be changed so that more oil flows through the cooling 13. In another embodiment of the present invention, the fuzzy logic algorithm determines the speed at which the position of the control valve 15 is to be changed. Depending on the tout and the error evolution and depending on the required response speed of the overall system, the fuzzy logic algorithm could take into account different speeds for changing the position of the control valve 15. However, equal speeds should not be excluded. BE2017 / 5069 Consequently, if the second error, 02, is negative, N, and the error evolution, d (error) / dt, is negative, N, the position of the control valve 15 can be changed at a first predetermined speed, -L; or if the second error, e2, is negative, N, and the error evolution, d (error) / dt, is positive, P, the position of the control valve 15 can be changed at a second predetermined speed, -M; or if the second error, e2, is approximately equal to zero, Z, and the error evolution, d (error) / dt, is negative, N, the position of the control valve 15 can be changed at a third predetermined speed, -S ; or if the second error, <52, is approximately equal to zero, Z, and the error evolution, ci (error) / dt, is positive, P, the position of the control valve 15 can be changed by a fourth predetermined speed, + S; or if the second error, & 2, is positive, P, and the error evolution, d (error) / dt, is negative, N, the position of the control valve 15 can be changed at a fifth predetermined speed, + M; or if the second error, e2, is positive, P, and the error evolution, d (error) / dt, is positive, P, the position of the control valve 15 can be changed at a sixth predetermined speed, + L. By way of example and without any limitation, the direction in which the control valve 15 is to be changed and the speed at which such a change is to be made can be determined by Table 2, where P1 to P6 are the membership functions as illustrated in Figure 7. Where such membership features are shown in Figure 7 as the BE2017 / 5069 corresponding vague values and as a function of the rate at which the change is to be made are shown in percentage per second,% / s, where the percentage represents the angle of rotation. Table 2: Delta RV Wrong N Z. R d (error) / dt N Pl (-L) P3 (-S) P5 (+ M) P P2 (-M) P4 (+ S) P6 (+ L) In an embodiment of the present invention, the membership functions P1 to P6 can be selected so that, for example, P1 to P3 can be assigned for the situation where the temperature of the oil is not high enough to allow additional volume of oil to flow through the cooling 13 while P4 to P6 can be assigned for the situation where the temperature of the oil is high enough to warrant an extra volume of oil through the cooling 13. Consequently, the membership functions P1 to P3 can be associated with a change in the position of the control valve 15 so that oil can flow through the bypass 14, while the membership functions P4 to P6 can be associated with a change in the position of the control valve 15 so that oil can flow through the cooling 13 can steam. In the specific example illustrated in Figure 4, the change of the position of the control valve 15 is understood to mean that the central rotating element BE2017 / 5069 is being run, but such an example should not be considered limiting. In yet another embodiment of the present invention, the absolute value of the first predetermined speed, -L, is equal to the absolute value of the sixth predetermined speed, + L, the absolute value of the second predetermined speed, -M , equal to the absolute value of the fifth predetermined speed, + M, the absolute value of the third predetermined speed, ~ S equal to the absolute value of the fourth predetermined speed, + S. In yet another embodiment, the absolute value of the first predetermined speed, -L, may be less than the absolute value of the sixth predetermined speed, + L, and / or the absolute value of the second predetermined speed, - M, less than the absolute value of the fifth predetermined speed, + M, and / or the absolute value of the third predetermined speed, -S, may be less than the absolute value of the absolute value of the fourth predetermined speed, + S. By way of example, without any limitation, the absolute value of the first predetermined speed, -L, and / or the absolute value of the sixth predetermined speed, + L, can be selected as any value within the interval [0.5; 1.5% / s, such as, for example, about 0.8% / s, or about 0.9% / s, or even about 1.4% / s. Similarly, the absolute value of BE2017 / 5069 the second predetermined rate, -M, and / or the absolute value of the fifth predetermined rate, + M, are selected as any value within the interval (0; 1]% / s, such as for example about 0.2% / s, or about 0.3% / s, or even about 0.8% / s. Likewise, the absolute value of the third predetermined rate, -S, and / or of the fourth predetermined certain rate, + S, are selected as any value within the interval (0; 0.53% / s, such as, for example, about 0.1% / s, or about 0.2% / s, or even about 0 .4% / s. In the context of the present invention, such examples should in no way be considered limiting and it should be assumed that other values for the respective rates can be selected without departing from the scope of the present invention. To determine how much to change the opening degree of such a control valve 15, to bypass 14 or cooling 13, or for the specific example of Figure 4, to determine the angle by which the position of the control valve 15 is to be changed, the fuzzy logic algorithm applies a first control function, CTR valve, and determines the minimum between the value 1 and the result of the sum of the fuzzy value associated with the second error, β2, multiplied by a first coefficient, fl, and the fuzzy value associated with the error evolution, d (error) / dt, multiplied by a second coefficient, f2: BE2017 / 5069 CTR_valve = MIN [f 1 · FV (e 2 ) + f2 · FV (d (error) / dt); 1] (equation 8), where FV (e2) represents the fuzzy value associated with the second error, e2, and FV (d (error) / dt} represents the faint value associated with the error evolution, d (error) / dt. The first coefficient, f1, and the second coefficient, f2 can be selected such that the controller 20 can respond faster or less quickly to changes in the error and / or in the error evolution, d (error) / dt. Consequently, if the second coefficient, f2, is selected as a relatively larger value than the first coefficient, f1, the fuzzy logic algorithm will instruct the controller 20 to change the position of the control valve 15 whenever a relatively small change in the outlet temperature, T U it, is detected. A compressor or vacuum pump 1 implementing such a method would respond very quickly to small changes in the outlet temperature, T u it, but would also be less stable. On the other hand, if the second coefficient, f2, is selected as a relatively smaller value than the first coefficient, f1, the fuzzy logic algorithm will instruct the controller 20 to change the position of the control valve 15 whenever a more significant change in the exhaust temperature, T u it, is detected. A compressor or vacuum pump 1 implementing such a method would be less likely BE2017 / 5069 respond to minor changes in exhaust temperature, Tuit, but would be more stable. In another embodiment of the present invention, the first coefficient, f1, and the second coefficient, f2, may be any real number selected between the interval (0; 1]. Preferably, but without any limitation, the first coefficient, f1, can be any real number selected between [0.5; 1], and the second coefficient, f2, can be any real number selected between (0; 0.5], By way of example, but without any limitation, the first coefficient f1 to achieve a very efficient and stable compressor or vacuum pump 1 may be selected to be equal to value one, and the second coefficient, f2, may be selected as equal to the value zero decimal two ¢ 0.2). Consequently, equation 8 becomes: CTR_valve = MIN [l'FV {e 2 ) + 0.2 · FV (d (error) / dt); 1] (comparison 9). In another embodiment of the present invention, the fuzzy logic algorithm, to determine the angle by which the position of the control valve 15 is to be changed, determines the maximum between the result of the product of the faint value associated with the second error, e 2 , and a first coefficient, fl, and the result BE2017 / 5069 of the product of the fuzzy value associated with the error evolution, d (error) / dt, and a second coefficient, f2: CTR_valve = MAX [f1 · FV (ez); f2 · FV (d (error) / dt)] (equation 10). In the context of the present invention, if the control valve comprises a central rotating element 26, while determining the angle by which the position of the control valve 15 is to be changed, determining the angle at which the central rotating element 26 is to be rotated to be understood. In yet another embodiment of the present invention, the fuzzy logic algorithm determines the angle by which the position of the control valve 15 is to be changed, by either determining the minimum between the fuzzy value associated with the second error, Θ2, and the fuzzy value associated with the error evolution, d (error) / dt, or by determining the maximum between the fuzzy value associated with the second error, e2, and the fuzzy value associated with the error evolution, d (error) / dt. Tests have shown that such an approach would result in either a less responsive but more stable compressor or vacuum pump 1, or a very responsive and less stable compressor or vacuum pump 1, respectively. Returning now to Figure 7, it would be preferable that each membership function P1 to P6 be assigned for one combination between the error and the error evolution, d (error) / dt. BE2017 / 5069 Therefore, if the second error, Θ2, is negative, N, and the error evolution, d (error) / dt, is negative, N, the result of the first control function, CTR_valve, should be shown in the Pl graph; while if the second error, e2, is negative, N, and the error evolution, d (error) / dt, is positive, P, the result of the first control function, CTR_valve, should be shown in the P2 graph; while if the second error, ez, is approximately equal to zero, Z, and the error evolution, d (error) / dt, is negative, N, the result of the first control function, CTR_valve, should be displayed in the P3- chart; while if the second error, ea, is approximately equal to zero, Z, and the error evolution, d (error) / dt, is positive, P, the result of the first control function, CTR_valve, should be reflected in the P4- chart; while, if the second error, e2, is positive, P, and the error evolution, d (error) / dt, is negative, N, the result of the first control function, CTR_valve, should be shown in the P5 graph; while if the second error, ej, is positive, P, and the error evolution, d (error) / dt, is positive, P, the result of the first control function, CTR_valve, should be shown in the P6 graph. Furthermore, the fuzzy logic algorithm, to determine one angle by which the control valve 15 is to be changed, preferably includes the step of determining the center of gravity of the graph determined after the result of the first control function, CTR_valve, has been incorporated into the respective membership functions of Figure 7, wherein a BE2017 / 5069 such center of gravity is further projected on the% / s axis. Where the% / s axis represents the angle at which the control valve 15 is to be changed in one second. If the center of gravity projected on the% / s axis falls in the range between (0; + x] or higher, the angle of the control valve 15 must be changed so that a larger volume of oil can flow through the cooling 13 with a speed in accordance with the respective membership function. If the center of gravity projected on the% / s axis is in the range between [-x; x] or lower, the angle of the control valve 15 must be changed so that a larger volume of oil can flow through the bypass 14 at a rate according to the respective membership function. In an embodiment of the present invention, depending on the required response speed of the overall system, the values of -x and + x can be any value selected from, for example, [-0.5; -20] and [+ 0.5; +20] respectively, more preferably, the values of -x and + x may be any value selected between [-1; -10] and [+ 1; +10] respectively; even more preferably, -x can be selected to be about -5, while + x can be selected to be about +5. BE2017 / 5069 Furthermore, depending on the designer's specifications, the intermediate values -xl, -x2 can be defined within the interval [-x; 0) and + x1, + x2 can be defined within the interval {0; + x]. For example, without any limitation, -x1 can be selected as about -1, while -x2 can be selected as about -2. Likewise, + xl can be selected as approximately +1, while + x2 can be selected as approximately +2. It is to be understood that such values can be determined experimentally, and that the present invention should not be limited to the specific examples described above. In another embodiment of the present invention, the fuzzy logic algorithm further comprises the step of determining a position of the control valve 15 by applying the calculated angle, or center of gravity projected on the% / s axis, to a current position of the control valve 15 preferably at a speed corresponding to the respective membership function. Accordingly, Figure 8 illustrates the current position of the control valve 15 to which the result previously determined with respect to Figure 7 is applied. Where the membership functions of Figure 8 are shown as the corresponding fuzzy values and as a function of the rotation angle, shown as percentage,%. BE2017 / 5069 Preferably, but without any limitation, if the control valve 15, by applying the result determined with respect to Figure bereikt, reaches a position in which the oil mainly flows through the bypass 14, the result should be shown in graph Q1. Furthermore, if by application of the result determined with respect to Figure 7, the control valve 15 reaches a position where the oil flows partly through the bypass 14 and partly through the cooling 13, the result should be shown in graph Q2. While, when the control valve 15, by applying the result determined with respect to Figure 7, reaches a position where the oil mainly flows through the cooling 13, the result should be shown in graph Q3. In another embodiment of the present invention, the response speed of the system can be affected by controlling when the fan 21 is started. Consequently, for a more responsive system, if any or all of the graphs Q1 to Q3 are shifted to the left, on the% axis in Figure 8, the fan 21 will start earlier, while if any or all of the graphs Q1 to Q3 shifted to the right on the% axis in Figure 8, the fan 21 is started later. If the compressor or vacuum pump includes an energy recovery element 25, the current position of the control valve 15 on which the result previously determined is determined by BE2017 / 5069 regarding Figure 7 is applied, shown in Figure 9. Where the membership functions of Figure 9 are shown as the corresponding fuzzy values and as a function of the rotation angle, shown as percentage,%. Accordingly, when the control valve 15, by applying the result determined with respect to Figure 7, reaches a position where the oil mainly flows through the bypass 14, the result should be shown in the graph Q1 '. Furthermore, if by applying the result determined with respect to Figure 7, the control valve 15 reaches a position in which the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the result should be shown in graph Q2 '. Likewise, if by applying the result determined with respect to Figure 7, the control valve 15 reaches a position where the oil flows mainly through the energy recovery element 25, the result should be shown in graph Q3 '. If by application refer to Figure wherein the of the result determined by 7, the control valve 15 reaches a position oil partly through the energy recovery element 25 and partly through the BE2017 / 5069 cooling 13 flows, client the result to be shown in graph Q4 '. While, when the control valve 15, by applying the result determined with respect to Figure 7, reaches a position where the oil mainly flows through the cooling 13, the result should be shown in the graph Q5 '. Preferably, when the compressor or vacuum pump 1 is started, the control valve 15 is preferably in a standard position characterized by a rotation angle of zero, as illustrated in Figure 3 and in Figure 4, in which case the oil is preferably predominantly by the by-pass 14 flows. As the temperature of the oil gradually increases, the rotation angle is adjusted, gradually allowing a partial flow of oil to flow through the bypass 14 and a partial flow of oil through the cooling 13, until a maximum rotation angle of one hundred percent is reached, in which case oil flows mainly through cooling 13. If the compressor or vacuum pump 1 does not include an energy recovery element 25, the hundred percent rotation angle preferably corresponds to a 90 ° physical rotation of the control valve 15. As illustrated in Figure 4, the 90 ° physical rotation of the control valve 15 would correspond with a rotation of the central rotating element 26 according to arrow AA r , by bringing shaft I over shaft II. Consequently, the central rotating element 26, BE2017 / 5069 to return to the starting position of zero turning angle, must rotate according to arrow AA 'but in the opposite direction, by passing shaft II over shaft I. In other words, in order to flow oil partly through the bypass 14 and partly through the cooling 13 or mainly flow through the cooling 13, the central rotating element 26 must be rotated according to arrow AA 'counterclockwise, whereas if from such a position the central rotating element 26 is to be brought into an intermediate position or to the initial angle of rotation of zero, the central rotating element 26 should be rotated according to arrow AA 'clockwise. If the compressor or vacuum pump 1 includes an energy recovery element 25, the hundred percent rotation angle preferably corresponds to a 180 ° physical rotation angle of the control valve 15. As illustrated in Figure 3, the 180 ° physical rotation angle of the control valve 15 would correspond with a rotation of the central rotating element 26 according to arrow BB ', by bringing shaft I over shaft III. Accordingly, in order to return to the starting position of a zero turning angle, the central rotating element 26 should rotate according to arrow BB 'but in the opposite direction, by passing shaft III over shaft I. BE2017 / 5069 In other words, to allow oil to flow partly through the bypass 14 and partly through the energy recovery element 25 or primarily through the energy recovery element 25, or partly through the cooling 13 and partly through the energy recovery element 25 steaming, or mainly by cooling, the central rotating element 26 must be rotated according to arrow BB 'counterclockwise, while from such a position the central rotating element 26 must be rotated in an intermediate position or in the initial angle of rotation should be brought from zero, the central rotating element 26 should be rotated according to arrow BB 'clockwise. It should further be assumed that when the position of the control valve 15 is changed, the calculated angle is applied to the current angle of the control valve 15, according to arrow AA 'or BB' and where the direction of rotation of the central rotating element 26 is either is changed to clockwise or to clockwise. In another embodiment of the present invention, the fuzzy logic algorithm determines whether to increase or decrease the speed of the fan 21 based on the determined position of the control valve 15, the second error, e2, and the error evolution, d (error) / dt. BE2017 / 5069 Since the fuzzy logic algorithm as input parameter has the position of the control valve 15, the speed of the fan 21 is adjusted according to the volume of fluid reaching the cooling 13, which increases the energy efficiency of the compressor or vacuum pump 1 and the service life of the fan 21 and motor 24 extend. Depending on the second error, & 2, and the error evolution, d (error) / dt, the speed of the fan 21 may need to be changed faster or slower. Consequently determines in a embodiment according to the present invention it vague logic algorithm further how quickly the speed from the fan 21 must be modified by a or Lake of the following to step and controls applying: as the error is negative is, N, and the error evolution, d (error} / dt, is negative, N, then: if the the position of the control valve 15 is such that oil mainly flows through the bypass line 14, the speed of the fan must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the by-pass and partly through the cooling 13, the speed of the fan 21 must be reduced at a second speed, MS; or if the position of the control valve is such that the oil flows mainly through the cooling 13, the speed of the fan 21 must be reduced at a second speed, MS. BE2017 / 5069 Furthermore, if the error is negative, N, and the error evolution, d (error) / dt, is positive, P, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, the speed of the fan are reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the cooling 13, the speed of the fan 21 must be changed to a third speed, M; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be changed to a third speed, M. Further, if the error is approximately equal to zero, Z, and the error evolution, d (error) / dt, is negative, N, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass line 14 and partly through the cooling 13, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that it allows the oil to flow mainly through the cooling 13, the speed of the fan 21 must be reduced at a first speed, S. BE2017 / 5069 Furthermore, if the error is approximately equal to zero, Z, and the error evolution, d (error) / dt, is positive, P, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the cooling 13, the speed of the fan 21 must be increased at a fourth speed, F; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be increased at a fourth speed, F. Furthermore, if the error is positive, P, and the error evolution, d (error) / dt, is negative, N, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, the speed of the fan 21 is reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the cooling 13, the speed of the fan 21 must be changed to a third speed, M; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be changed to a third speed, M. Furthermore, if the error is positive, P, and the error evolution, d (error) / dt, is positive, P, then: if the position of the BE2017 / 5069 control valve 15 is such that the oil mainly flows through the by-pass 14, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the cooling 13, the speed of the fan 21 must be increased at a fourth speed, F; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be increased at a fifth speed, MF. By way of example without any limitation, the speed at which the speed of the fan 21 must be changed is determined by Table 3, where RV stands for the position of the control valve and F1 to F5 are the membership functions as illustrated in Figure 10. Table 3: delta FAN [error; d (error) / dt] [N; N IN P] [z; N] [Z; F>] EP; N] [P; P] RV Q1 (Z) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) Q2 (M) Fl (MS) F3 (M) F2 (S) F4 (F) F3 (M) F4 (F) Q3 (L) Fl (MS) F3 (M) F2 (S) F4 (F) F3 (M) F5 (MF) In another embodiment of the present invention, if the compressor or vacuum pump 1 includes an energy recovery element 25, the fuzzy logic algorithm further determines the speed at which the speed of the fan 21 is to be changed by one or more of BE2017 / 5069 apply the following steps and checks: if the error is negative, N, and the error evolution, d (error) / dt, is negative, N, then: if the position of the control valve 15 is such that the oil flows mainly through the by-pass, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve is such that the oil flows mainly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the energy recovery element 25 and partly through the cooling 13, the speed of the fan 21 must be reduced at a second speed, MS; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be reduced at a second speed, MS. Furthermore, if the error is negative, N, and the error evolution, d (error) / dt, is positive, P, and if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, the speed must of the fan 21 are decreased at a first speed, S; BE2017 / 5069 or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows mainly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the energy recovery element 25 and partly through the cooling 13, the speed of the fan 21 must be changed to a third speed, M; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be changed to a third speed, M. Further, if the error is approximately equal to zero, Z, and the error evolution, d (error) / dt, is negative, N, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or as the position of the control valve BE2017 / 5069 15 such is that the oil especially through it energy recovery element 25 flows, then must the speed of the ventilator 21 be lowered On a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the energy recovery element 25 and partly through the cooling 13, the speed of the fan 21 must be reduced at a first speed, S; if the position of the control valve 15 is such that the oil flows mainly through the cooling 13, the speed of the fan 21 must be reduced at a first speed. Furthermore, if the error is approximately equal to zero, Z, and the error evolution, d (error) / dt, is positive, P, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, then the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows mainly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil partly passes through it BE2017 / 5069 energy recovery element 25 and flowing partly through the cooling 13, then the speed of the fan 21 must be reduced at a fourth speed, F; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be increased at a fourth speed, F. Furthermore, if the error is positive, P, and the error evolution, d (error) / dt, is negative, N, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, the speed of the fan 21 is reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows mainly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the energy recovery element 25 and partly through the cooling 13, the speed of the fan 21 must be changed! at a third speed, M; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the BE2017 / 5069 speed of fan 21 be changed! at a third speed, M. Furthermore, if the error is positive, P, and the error evolution, d (error) / dt, is positive, P, then: if the position of the control valve 15 is such that the oil mainly flows through the bypass line 14, the speed of the fan 21 is reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the bypass 14 and partly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows mainly through the energy recovery element 25, the speed of the fan 21 must be reduced at a first speed, S; or if the position of the control valve 15 is such that the oil flows partly through the energy recovery element 25 and partly through the cooling 13, the speed of the fan 21 must be reduced at a fourth speed, F; or if the position of the control valve 15 is such that the oil mainly flows through the cooling 13, the speed of the fan 21 must be increased at a fifth speed, MF. For example, without any limitation, if the compressor or vacuum pump includes an energy recovery element 25, the speed at which the speed of the fan 25 is to be changed is determined by BE2017 / 5069 Table 4, where RV stands for the position of the control valve and FI to F5 are the membership functions as illustrated in Figure 10. Table 4: delta FAN(ER) [error; d (error) / dt] [N; N] [N; Ê] [Z; Ù] [Z; p] tP; N] (P; P] Ql '(VZ) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) Q2 '(Z) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) RV Q3 '(Μ) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) F2 (S) Q4 '(L) FI (MS) F3 (M) F2 (S) F4 (F) F3 (M) F4 (F) Q5 '(VL) FI (MS) F3 (M) F2 (S) F4 (F) F3 (M) F5 (MF) In another embodiment according to the present invention, but without any limiting character, the absolute value of the second section, MS, is less than or equal to the absolute value of the first section, S, is the absolute value of the first section, S, less than or equal to the absolute value of the third speed, M, is the absolute value of the third speed, M, less than or equal to the absolute value of the fourth speed, F, is the absolute value of the fourth speed, F, less than or equal to the absolute value of the fifth speed, MF. In the context of the present invention, it is to be assumed that there may be other relationships between the first section, S, the second section, MS, the third section, M, the fourth section, F, and the fifth section, MF. without departing from the scope of the present invention. BE2017 / 5069 Furthermore, in another embodiment of the present invention, such speeds may be the same. Consequently, MS = S = M = F = MF. In yet another embodiment of the present invention, the absolute value of the second speed, MS, may be equal to the absolute value of the fifth speed, MF, and / or the absolute value of the first speed, S, may be equal to the absolute value of the fourth speed, F. In a further embodiment of the present invention, the second speed, MS, may be equal in modulus to the fifth speed, MF, and / or the first speed, S, may be equal in modulus to the fourth speed, F. Preferably, but without any limiting character: | -MS | = | MF | and / or | -S | = | F |. In yet another embodiment of the present invention, the third speed, M, can be very low or even negligible. More preferably, the third speed, M, is about zero. Preferably, but without any limitation, the second speed, MS, and / or the first speed, S, is negative, which would mean that the actual speed of the fan 21 would be reduced; while the fourth speed, F, and / or the fifth speed, MF, is positive BE2017 / 5069 is, which would mean that the actual speed of fan 21 would be increased. By way of example, but without any limitation, whereas the speed of the fan 21 can vary between zero and one hundred revolutions per minute over one second (RPM / s), the first speed, S, and the second speed, MS are chosen as any value comprised between -1 and -100 RPM / s; while the fourth speed, F, and the fifth speed, MF, can be selected as any value comprised between +1 and +100 RPM / s. More preferably, the first speed, S, and the second speed, MS, can be selected as any value comprised between -5 and ~ 50 RPM / s; while the fourth speed, F, and the fifth speed, MF, can be selected as any value comprised between +5 and +50 RPM / s, or more preferably between +5 and +40 RPM / s. Even more preferably, the first speed, S, and the second speed, MS, can be selected as any value comprised between -10 and -30 RPM / s; while the fourth speed, F, and the fifth speed, MF, can be selected as any value comprised between +10 and +30 RPM / s. By way of example, but without any limitation, the first speed, S, may be selected to be about -15 RPM / s, the second speed, MS, may be selected to be about -40 RPM / s, the BE2017 / 5069 fourth speed, F, is selected to be about +5 RPM / s, and the fifth speed, MF, can be selected to be about +15 RPM / s. In another embodiment of the present invention, the fuzzy logic algorithm includes the step of determining the second fan to actually change the fan speed by applying control function, CTR_ventilator, and determining the value of: the fuzzy value associated with the real angle of the position of the control valve 15 multiplied by the result of: the fuzzy value associated with the error multiplied by a third coefficient, f3, where the fuzzy value associated with the error evolution, d (error) / dt, multiplied by a fourth coefficient, f4, is added to: CTR_ventilator = FV (RV) · [f3 · FV (error) + f4 · FV (d (error) / dt)] (Equation 11). Where the third coefficient, f3, and the fourth coefficient, f4 are selected in the same way as the first coefficient, fl, and the second coefficient, f2, of equation 7, and depending on whether the controller 20 is to respond faster or less quickly to changes in the error and / or the error evolution, d (error) / dt. Accordingly, the third coefficient, f3, and the fourth coefficient, f4, can be selected as any real number contained within the interval (0; 1]. BE2017 / 5069 Preferably, but without any limitation, the third coefficient, f3, can be selected as any real value contained within the interval [0.5; 1], while the fourth coefficient, f4, can be selected as any real value included within the interval (0; 0.5j. By way of example, without any limitation, the third coefficient, f3, can be selected as about zero point seven (0.7) and the fourth coefficient, f4, can be selected as about zero point three (0.3). Accordingly, Equation 11 becomes: CTR_ventilator = FV (RV) · [0.7FV (error) + 0.3 · FV (d (error) / dt)] (Equation 12). The result of such comparison is preferably further incorporated into the graph of Figure 10, wherein the membership functions F1 to F5 are preferably assigned for one combination between the error and the error evolution, d (error) / dt, and further taking into account with the current position of the control valve 15. Consequently, if the error is negative, N, the error evolution, d (error) / dt, is negative, N, and if the control valve 15 allows the oil to flow primarily through the bypass 14, then the result of the second control function, ClR fan, to be shown in the F2 graph; while, if the control valve 15 allows oil to flow either partly through the bypass 14 and partly through the cooling 13 or mainly through the cooling 13, then BE2017 / 5069 the result of the second control function, CTR_ventilator, must be shown in the Fl graph. If the error is negative, N, the error evolution, d (error) / dt, is positive, P, and if the control valve 15 allows the oil to flow mainly through the bypass 14, the result of the second control function, CTR fan, must be are shown in the F2 graph; whereas, if the control valve 15 allows oil to flow either partly through the bypass 14 and partly through the cooling or mainly through the cooling 13, then the result of the second control function, CTR_ fan, should be shown in the F3 graph. If the error is approximately equal to zero, Z, the error evolution, d (error) / dt, is negative, N, and the control valve 15 leaves oil either mainly through the by-pass 14, or partly through the by-pass and partly through the cooling 13 steaming, or mainly steaming through cooling 13, the result of the second control function, CTR fan, must be shown in the F2 graph. If the error is approximately equal to zero, Z, the error evolution, d (error) / dt, is positive, P, and if the control valve 15 allows the oil to flow mainly through the bypass 14, then the result of the second control function, CTR_ventilator, to be shown in the F2 graph; while, as the control valve 15, the oil is either partly through the bypass line 14 and partly through säüaauüBi » BE2017 / 5069 allows the cooling 13 to flow either mainly through the cooling 13, then the result of the second control function, CTR_ventilator, must be shown in the F4 graph. If the error is positive, P, the error evolution, d (error} / dt, is negative, N, and the control valve 15 allows the oil to flow mainly through the bypass 14, then the result of the second control function, CTR_ventilator, must be shown in the F2 graph; while, if the control valve 15 allows oil to flow either partly through the bypass 14 and partly through the cooling 13 or completely through the cooling 13, then the result of the second control function, CTR_ventilator, should be shown in the F3 chart. If the error is positive, P, the error evolution, d (error) / dt, is positive, P, and the control valve 15 allows the oil to flow mainly through the bypass 14, then the result of the second control function, CTR_ventilator, must be shown in the F2 graph; whereas, if the control valve 15 allows oil to flow partly through the bypass 14 and partly through the cooling 13, then the result of the second control function, CTR fan, should be shown in the F4 graph; whereas, if the control valve 15 allows oil to flow primarily through the cooling 13, then the result of the second control function, ClR fan, should be shown in the Fb graph. 0 BE2017 / 5069 In another embodiment of the present invention, if the oil-injected compressor or vacuum pump 1 includes an energy recovery element 25, then the result of the second control function, CTR_ventilator, is preferably further incorporated into the graph of Figure 10, wherein the membership functions FI to F5 is preferably assigned for a combination between the error and the error evolution, d (error) / dt, as will be explained below. If the error is negative, N, the error evolution, d (error) / dt, is negative, N, and the control valve 15 lets oil either mainly through the bypass 14, or partly through the bypass 14 and partly through the energy recovery element 25 steaming, or mainly steaming through the energy recovery element 25, the result of the second control function, CIR fan, should be shown in the F2 graph; whereas, if the control valve 15 allows oil to flow either partly through the energy recovery element 25 and partly through the cooling 13, or mainly through the cooling, then the result of the second control function, CIR fan, should be shown in the F1 graph. If the error is negative, R, the error evolution, is positive, P, and the control valve 15 mainly through the bypass line 14, either through the bypass line 14 and partially energy recovery element, let d (error) / dt, oil or partially through the or curd, BE2017 / 5069 is mainly streamed by the energy recovery element 25, then the result of the second control function, CTR_ventilator, must be shown in the F2 graph; while if the control valve 15 allows oil to flow either partly through the energy recovery element 25 and partly through the cooling 13 or mainly through the cooling 13, then the result of the second control function, CTR fan, should be displayed in the F3 ~ chart. If the error is approximately equal to zero, Z, the error evolution, d (error) / dt, is negative, N, and the control valve 15 is oil either or mainly through the bypass 14, or partly through the bypass 14 and partly through the energy recovery element 25, either mainly by the energy recovery element 25, or partly by the energy recovery element 25 and partly by the cooling 13, or by being mainly steamed by the cooling 13, the result of the second control function, CTR fan, must be displayed in the F2 chart. If the error is approximately equal to zero, Z, the error evolution, d {error) / dt, is positive, P, and the control valve 15 is oil either or mainly through the bypass 14, or partly through the bypass 14 and partly through the energy recovery if element 25 is steaming, or mainly steamed by the energy recovery element 25, the result of the second control function, CTR fan, must be displayed 2 BE2017 / 5069 in the F2 graph; whereas, if the control valve 15 allows oil to flow either partly through the energy recovery element 25 and partly through the cooling 13 or mainly through the cooling 13, then the result of the second control function, CTR fan, should be shown in the F4 graph. If the error is positive, P, the error evolution, d (error) / dt, is negative, N, and the control valve 15 allows oil either mainly through the bypass 14, or partly through the bypass 14 and partly through the energy recovery element 25 steaming, or primarily steaming through the energy recovery element 25, the result of the second control function, CTR_ventilator, should be shown in the F2 graph; whereas, if the control valve 15 allows oil to flow either partly through the energy recovery element 25 and partly through the cooling 13 or mainly through the cooling 13, then the result of the second control function, CTR fan, should be shown in the F3 graph. If the error is positive, P, the error evolution, d (error) / dt, is positive, P, and the control valve 15 lets oil either mainly through the bypass 14, or partly through the bypass 14 and partly through the energy recovery element 25 steaming, or mainly steaming through the energy recovery element 25, the result of the second control function, CTR fan, must be displayed in the BE2017 / 5069 F2 chart; whereas, if the control valve 15 allows oil to flow either partly through the energy recovery element 25 and partly through the cooling 13, then the result of the second control function, CTRL fan, should be shown in the F4 graph; while, if the control valve 15 allows oil to flow primarily through the cooling 13, then the result of the second control function, CTR_ventilator, should be shown in the F5 graph. In a further embodiment of the present invention, after the second control function, CTR_ventilator, is interposed into the graph of Figure 10, the fuzzy logic algorithm preferably calculates the center of gravity of the resulting graph and projects it at RPM / s (revolution per minute) / second) axis. Consequently, the fuzzy logic algorithm determines the real speed at which the speed of the fan 21 is to be changed. If such a speed were to be decreased, the center of gravity projected on the RPM / s axis would have a value comprised between zero and a minimum value, Min. Preferably such a value is contained within the interval [-100; 0} RPM / s. If such a speed were to be increased, the center of gravity projected on the RPM / s axis would have a value comprised between zero and a maximum value, Max. BE2017 / 5069 Preferably such a value is contained within the interval [0; 100} RPM / s. Accordingly, the controller 20 increases or decreases the speed of the fan 21 according to the result of the determined real speed according to the speed associated with the respective membership function according to the second control function, CTR fan, after interposition in the graph of Figure 10. In the context of the present invention, the center of gravity of a graph is to be understood to mean the average position of all points that are part of the graph and in all coordinate directions. In other words, the center of gravity of a graph represents the equilibrium point of such a graph, or the point at which an infinitely thin cutout of the shape could be in perfect balance on a tip of a pen, assuming a uniform density of the cutout , within a uniform gravitational field. Furthermore, it should be considered that the fuzzy logic algorithm can apply any method to determine such a center of gravity, and that the present invention should not be limited to such a specific method. By way of example, but without any limiting character, the center of gravity can be calculated by the possible peaks of the display of the first control function, CTR valve, or the second control function, BE2017 / 5069 which represents the stand by the following ZUiCTRjtentielpGj CTR_ventieli with Gi CTR_ventiiator, respectively, to be integrated in the respective graphs. Where such peaks are characterized by two coordinates (A; B), where A is part of the% / s axis of Figure 7, or the RPM / s axis of Figure 10; and B is part of the value axis and is contained between [0; 1] of Figure 7 or Figure 10 respectively. Taking into account such coordinates for each of the peaks within the respective membership functions, the center of gravity can be calculated as having the coordinates: mean A and mean B, where mean A is the mean of all A coordinates of all peaks, and mean B is the mean is of all B coordinates of all peaks. In another embodiment of the present invention, the fuzzy logic algorithm can calculate the center of gravity of any graph according to any membership function: either for P1 to P6 or for F1 to F5. Where the result is five or six centers of gravity. Furthermore, the fuzzy logic algorithm can determine the real angle of the control valve 15 to change the formula to be applied: (equation 13), represents center of gravity, and where CTR valve.,. displays the first control function that is BE2017 / 5069 applied for the respective membership functions, Pl to P6. Likewise, the fuzzy logic algorithm can determine the real angle at which the speed of the fan 21 should change by applying the following formula: Σ ( = 1 CTR ~ ventilatori * Gi Σί-t CT R _ventilator L (equation 14), where Gi represents the respective center of gravity, and where CTR_ventilatori represents the second control function applied for the respective membership functions, Fl to F5. For the purposes of the present invention, "partial" is understood to mean a volume of oil selected between a minimum volume of approximately equal to zero and a maximum volume of approximately equal to one hundred percent, such as, for example, without any limitation: approximately thirty percent, or about forty percent or even about sixty percent. More preferably, "partial" is to be understood to mean a volume of oil representing about half, or fifty percent, of the oil volume flowing through the oil outlet 11 and eventually reaching the oil inlet 12. It should be assumed that such a volume may vary according to the requirements of the compressor or vacuum pump 1, such as, for example, between twenty five percent and seventy five percent. BE2017 / 5069 Further, by "primarily" is meant about the full volume, or about one hundred percent of the volume of oil flowing through the oil outlet 11 and finally reaching the oil inlet 12. By way of example, without any limitation, Figure 11 illustrates a control loop applied by the fuzzy logic algorithm. Accordingly, the measured exhaust temperature, T u ± t, provided by the exhaust temperature sensor 18, is received in block 100, comparing such received exhaust temperature, Tuit, with the calculated predetermined target value, T target, of block 101. The error is determined using from block 102. Furthermore, the fuzzy logic algorithm calculates the error evolution, d (error) / dt, in block 103, and before the fuzzy logic block 104 is reached, the transient temperature variations are filtered by LPFs 105 and 106. Consequently, the fuzzy logic block 104 receives as input: on the one hand, filtered values of the error, and on the other hand, filtered values of the evolution of such errors, d (error) / dt. Furthermore, the fuzzy logic block 104 represents such values within the graphs illustrated in Figure 5 and Figure 6, according to the respective membership functions and as explained above. For increased stability of the overall system, the control loop further filters the resulting values with BE2017 / 5069 using the filters in blocks 107 and 108 respectively, ignoring very small fluctuations. In a next step, the fuzzy logic block 104 determines the direction in which the control valve 15 is to be changed and the speed at which such a control valve 15 is to be changed using the graph of Figure 7 and the first control function, CTR_valve. According to the method described herein, the result of the first control function, CTR__valve, is preferably expressed in the respective membership functions of Figure 7, and the center of gravity of the resulting graph is calculated and projected on the% / s axis. Where such center of gravity is projected on the% / s axis, it is shown in block 109 as an output of the fuzzy logic block 104. Furthermore, the fuzzy logic algorithm adds the determined center of gravity projected on the% / s axis to the current position of the control valve 15 using block 110 and control circuit 111, and determines the new current position of the control valve 15 in block 112. Preferably, but without any limitative character, with an even more stable overall system, the regeikring block comprise 113 and 114, which via block 113, the measured outlet temperature, T u it, is taken into account. Block 114 determines a minimum position of the control valve 15 according to the outlet temperature, Tuit. Preferably, in 9 BE2017 / 5069 blök 114, an experimentally determined graph uploaded showing a minimum valve position at respective exhaust temperatures, T U it. Consequently, if after the determined center of gravity projected on the% / s axis has been added to the current position of the control valve 15 using block 110 and control circuit 111, a new determined position would have a smaller angle than the angle determined on the graph from block 114 for the respective outlet temperature, T u .it, the fuzzy logic algorithm will select the value of such a graph has been met and to determine the new current state of the control valve 15 in block 112. Otherwise, the fuzzy logic algorithm would work as explained above. By applying these controls, the fuzzy logic algorithm helps to avoid temperature outliers in the compressor or vacuum pump 1, which may prove harmful. Accordingly, help block 113 and 114 in order to avoid the situation in which the compressor or vacuum pump 1 would be run at a very low speed of the motor 7 and the temperature at the outlet, T U f it would be very high. In addition, if the temperature at the outlet, T U jt, would rise to very high values, the controller 20 would not allow oil to flow through the bypass 14, or allow only a very small amount of oil to flow through it. BE2017 / 5069 Where the new current position of the control valve 15 is an input of the fuzzy logic block 104, using control circuit 115. Using such a new current state, the fuzzy logic block 104 further determines how the speed of the fan 21 is to be changed and the speed at which such a speed is to be changed, using the graph of Figure 10 and the second control function, CTR_ventilator. Consequently, the result of the second control function, CTR_ventilator, is preferably interposed into the respective membership functions of Figure 10, and the center of gravity of the resulting graph is calculated and projected on the RPM / s axis. Where such a center of gravity projected on the RPM / s axis is shown in block 116 as another output of the fuzzy logic block 104. Furthermore, the fuzzy logic algorithm applies the sum between the current value of the speed of the fan 21 and the center of gravity projected on the RPM / s axis, using block 117 and control circuit 118, and determines the new current speed of the fan 21 in block 119. Wherein the new current position of the control valve 15 of block 110 and the new current speed of the fan 21 of block 115 are further used by the controller 20 as set values influencing the position of the control valve 15 via the first data link BE2017 / 5069 and with which the speed of the fan 21 is influenced via the second data link 33. The present invention is by no means limited to the exemplary embodiments described in the figures, but such an oil-injected compressor or vacuum pump can be realized with all kinds of Variants without departing from the scope of the invention. Nor is the invention limited to the exemplary method of keeping the temperature at an outlet of an oil-injected compressor or vacuum pump below a predetermined target value, but the method can be accomplished in various ways without departing from the scope of the invention to act. in the BE2017 / 5069
权利要求:
Claims (7) [1] Conclusions. A method for controlling the outlet temperature of an oil-injected compressor or vacuum pump (1) comprising a compressor or vacuum element (4) with a gas inlet (5), an element outlet (6), and an oil inlet (12), the method comprises the steps of: - measuring the outlet temperature (T u i t ) at the element outlet (6); - controlling the position of a control valve (15) to control the flow of oil flowing through a cooling (13) connected to the oil inlet (12); characterized in that the step of controlling the position of the control valve (15) implies that a vague logic algorithm is applied to the measured exhaust temperature (T u jt)! and characterized in that the method further comprises the step of controlling the speed of a fan (21) cooling the oil flowing through the cooling (13) by applying the fuzzy logic algorithm and further based on the state of the control valve (15). [2] Method according to claim 1, characterized in that it further comprises the step of measuring the BE2017 / 5069 inlet temperature (Tin), inlet pressure (Pin) at the gas inlet (5) and outlet pressure (Puit) at the element outlet (6). [3] Method according to claim 2, characterized in that controlling the position of the control valve means that the vague logic algorithm is further applied to the measured inlet temperature (Tin), inlet pressure (Pin) and the outlet pressure (Puit). 4. Method according to one of the conclusions 1 to 3, characterized in that the step of controlling from the state of the control valve (15) implies that the flow of oil prepared that by cooling ( : i3) flows and through a bypass (14) That in fluid connection Stands with the oil inlet (12), to the cooling (13) bypass. 5. Method according to conclusion 2 or 3, therefore characterized that the method further the step includes from the loving of the outlet temperature (Spout) on about a predetermined one target value (Target), whereby those predetermined target value (T target) is calculated by determining the atmospheric dew point (ADP) based on the measured: inlet temperature (Tin), inlet pressure (Pin) and outlet pressure (Puit) and an estimated or measured relative humidity (RH) of the gas passing through the gas inlet (5 ) flows. Method according to claim 5, characterized in that the fuzzy logic algorithm comprises the step of BE2017 / 5069 determining a first error (ei) by subtracting the predetermined target value (T target) from a first measured exhaust temperature (T U it, i) and determining a second error (β2) by the predetermined target value (T target) ) from a following measured exhaust temperature (T u it, 2) Method according to claim 6, characterized in that the fuzzy logic algorithm further comprises the step of calculating an error evolution (d (error) / dt), by calculating the derivative of the error over time, by the second error (e2) subtract from the first error (ei), and divide it over a time interval (At), calculated between the moment the first exhaust temperature (T u i t , i) is measured and the times when the next ( T U it, 2) is measured. The method according to claim 7, characterized in that the fuzzy logic algorithm further comprises the step of determining the direction in which the position of the regulating valve 7 would change based on the first error (ei) or the second error (β2) and the error evolution (d (error) / dt). Method according to claim 7 or 8, characterized in that the fuzzy logic algorithm further comprises the step of determining the rate at which the position of the control valve 2 would change based on the first error, (ei) or the second error ( 02) and the error evolution, (d (error) / dt). BE2017 / 5069 Method according to claim 7, characterized in that the vague logic algorithm determines the direction in which the control valve (15) is to be changed by using: - if the second error (02) is negative (N) or if the second error (e2> is approximately equal to zero (Z), and the error evolution (d (error) / dt) is negative (N), the direction in which the position of the control valve (15) must be changed so that more oil flows through the bypass line (14); or - if the second error (ea) is positive (P) or if the second error (ea) is approximately zero (Z), and the error evolution (d (error) / dt) is positive (P), the direction in which the position of the control valve (15) must be changed so that more oil flows through the cooling (13). Method according to claim 9, characterized in that the vague logic algorithm determines the speed at which the position of the control valve (15) is to be changed according to one or more of the following steps: - if the second error (ea) is negative (N) and the error evolution (d (error) / dt) is negative (N), the position of the control valve (15) must be changed at a first predetermined speed (-L ); BE2017 / 5069 - if the second error (e2) is negative (N) and the error evolution (d (error) / dt) is positive (P), the position of the control valve (15) must be changed at a second predetermined speed (-M ); - if the second error (ez) is approximately zero (Z) and the error evolution, (d (error) / dt) is negative (N), the position of the control valve (15) must be changed to a third predetermined speed (S); - if the second error (β2) is approximately equal to zero (Z) and the error evolution (d (error) / dt) is positive (P), the position of the control valve (15) must be changed at a fourth predetermined speed (+ S); - if the second error (β2> is positive (P), and the error evolution (d (error) / dt) is negative (N), the position of the control valve (15) must be changed to a fifth predetermined speed (+ M); - if the second error (e2> is positive (P) and the error evolution (d (error) / dt) is positive (P), the position of the control valve (15) must be changed to a sixth predetermined speed (+ L ). Method according to claim 11, characterized in that the first predetermined speed (L) is lower than the sixth predetermined speed (+ L); and / or that the second predetermined speed (87 BE2017 / 5069 M) is less than the fifth predetermined speed (+ M); and / or that the third predetermined speed (S) is less than the fourth predetermined speed (+ S). Method according to claim 7, characterized in that if the control valve (15) comprises a central rotating element (26), the fuzzy logic algorithm determines the angle by which the position of the control valve (15) is to be changed, by a first control function ( CTR_valve) and determine the minimum between one and the sum of a fuzzy value associated with the second error, {e2) multiplied by a first coefficient (fl) and a fuzzy value associated with the error evolution (d (error) / dt) multiplied by a second coefficient (f2). Method according to claim 13, characterized in that the fuzzy logic algorithm further comprises the step of determining the position of the control valve (15) by applying the calculated angle to a current position of the control valve (15). Method according to claim 14, characterized in that the fuzzy logic algorithm determines whether the speed of the fan (21) is to be increased or decreased based on the determined position BE2017 / 5069 of the control valve (15), the second error (θ2) and the error evolution (d (error) / dt). The method according to claim 14, characterized in that the fuzzy logic algorithm comprises the step of determining the real speed with which the speed of the fan (21) is to fit a second control function and determine the value of: a faint value associated with the real angle of the position of the control valve ¢ 15) multiplied by the result of: a faint value associated with the second error (θ2) multiplied by a third coefficient (f3) where the faint value associated with the error evolution changed by ( CTR fan) (d (error) / dt) multiplied by coefficient (f [4] 4) is added to. a quarter An oil-injected compressor or vacuum pump comprising: a compressor or vacuum element gas inlet ¢ 5), an element outlet (inlet (12); (4) with a 6) and an oil and oil separator (8) with a separator inlet with (9) which is in fluid connection element outlet (6), a separator outlet (10) and an oil outlet (11) in fluid connection with an oil inlet (12) of the compressor or vacuum element (4) through an oil pipe; the BE2017 / 5069 - a cooling (13) connected to the oil outlet (11) of the oil separator (8) and the oil inlet (12) of the compressor or vacuum element (4); - a bypass pipe (14) in fluid communication with the oil outlet (11) and the oil inlet (12) to bypass the cooling (13); - a control valve (15) provided on the oil outlet (11) configured to flow oil from the oil separator (8) through the cooling (13) and / or through the bypass line (14); - an exhaust temperature sensor (18) positioned at the element outlet (6); - a controller (20) that controls the position of the control valve (15); characterized in that the cooling (13) includes a fan (21) and the controller (20) further includes a fuzzy logic algorithm to control the speed of the fan (21) based on the position of the control valve (15) and the measured exhaust temperature, to maintain the exhaust temperature (Tuit) at approximately a predetermined target value (T target). An oil injected compressor or vacuum pump according to claim 17, further comprising an inlet temperature sensor (16) and an inlet pressure sensor (17) positioned at the gas inlet (5) and further BE2017 / 5069 comprising an outlet pressure sensor (19) positioned at the element outlet (6). Oil-injected compressor or vacuum pump according to claim 18, characterized in that the controller (20) comprises a data link (22 receiving measurements from for each of the: inlet temperature sensor (16), inlet pressure sensor (17), outlet temperature sensor (18) and outlet pressure sensor (19), the controller (20) further comprising an algorithm for calculating the predetermined target value (T target) from a calculated atmospheric dew point ( ADP) based on the measurements received. Oil-injected compressor or vacuum pump according to any one of claims 17 to 19, characterized in that the compressor or vacuum pump (1) comprises a relative humidity sensor (23) and the controller (20) further comprises a data link (22) for receiving measurements of a relative humidity sensor (23) positioned at the gas inlet (5) or comprising means to estimate the approximate relative humidity (RH) of the gas at the gas inlet (5). Oil-injected compressor or vacuum pump according to any one of claims 17 to 20, characterized in that the controller (20) comprises means for controlling the speed of the fan (21) at BE2017 / 5069 based on the position of the control valve (15) and an error, calculated by subtracting the predetermined target value (T target) from the measured exhaust temperature (T U it). Oil-injected compressor or vacuum pump according to any one of claims 17 to 21, characterized in that the fan (21) is provided with a variable speed motor (24). Oil-injected compressor or vacuum pump according to any one of claims 17 to 22, characterized in that the compressor or vacuum pump (1) further comprises an energy recovery element (25) connected to the oil outlet (11) and the oil inlet (12 ). for controlling a Spout) of an oil injected (1) comprising a) 4) provided with a 6), and an oil 24. A controller outlet temperature compressor or vacuum pump compressor or vacuum element gas inlet (5), an element outlet inlet (12) where controller (20) includes: a measuring element comprising a data input configured to receive outlet temperature data; - a communication element comprising a first data link (32) for controlling the position of a control valve (15); characterized by that BE2017 / 5069 - the communication element further comprises a second data link (33) for controlling the speed of a fan (21) cooling the oil flowing through the cooling (13); and in which - the controller (20) further comprises a processor equipped with a fuzzy logic algorithm that determines the speed of the fan (21) based on the position of the control valve (15) and the measured exhaust temperature (T u it) Controller according to claim 24, characterized in that the measuring element further comprises a data input configured to receive: inlet temperature data, inlet pressure data and outlet pressure data. Controller according to claim 25, characterized in that the processor is provided with an algorithm for calculating a predetermined target value (T target) by taking into account a calculated atmospheric dew point (ADP) based on the measurements received from the measuring element. Controller according to claim 26, characterized in that the processor further comprises an algorithm for determining a first error (ei) by subtracting the calculated predetermined target value (T target) from the measured outlet temperature (T U it, i). BE2017 / 5069 Regulator according to any one of claims 24 to 27, characterized in that the processor uses a predetermined relative humidity (RH) value of the gas flowing through the gas inlet (5) or that [5] 5, the controller further comprises a relative humidity sensor (23) positioned at the gas inlet (5) for determining the atmospheric dew point (ADP). Controller according to claim 27, characterized in that the processor is configured to [6] 10 further determining an error evolution (d (error) / dt), by subtracting the calculated first error (ei) from a next calculated second error (es), determines a next measurement of the outlet temperature (T U it, 2) in take it into account, and distribute it over it [7] 15 time interval (At) determined between the moment when the first exhaust temperature (T U it, i) is measured and the times when the next exhaust temperature (Tu.it, 2) is measured. BE2017 / 5069 BE2017 / 5069
类似技术:
公开号 | 公开日 | 专利标题 BE1024497B1|2018-03-19|A method for controlling the outlet temperature of an oil-injected compressor or vacuum pump and an oil-injected compressor or vacuum pump applying such a method. BE1016814A3|2007-07-03|DEVICE FOR PREVENTING THE FORMATION OF CONDENSATE IN COMPRESSED GAS AND COMPRESSOR INSTALLATION EQUIPPED WITH SUCH DEVICE. US9145783B2|2015-09-29|Seal gas monitoring and control system US20120261092A1|2012-10-18|Compressor inter-stage temperature control US20040244393A1|2004-12-09|Variable speed compressor cooling system RU2580574C1|2016-04-10|Compressor device and method for control thereof EP2058522B1|2012-06-27|Compressor with flow control sensor JP4418321B2|2010-02-17|Compressor and operation method thereof WO2018033827A1|2018-02-22|A method for controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump implementing such method US20160251946A1|2016-09-01|Method and system for optimizing well production US10294825B2|2019-05-21|Waste-heat utilization assembly of an internal combustion engine and method for operating a waste-heat utilization assembly JP2017008934A|2017-01-12|Screw machine and operation method of screw machine KR101849821B1|2018-04-17|Method for temperature control of a shaping tool BE1026654B1|2020-04-27|Oil-injected multi-stage compressor device and method for controlling a compressor device BE1024700B1|2018-06-01|Controller for controlling the speed of a motor that drives an oil-injected compressor and method for controlling that speed WO2014032672A1|2014-03-06|A method for controlling a chiller system BE1024101B1|2017-11-16|Method for protecting an electric motor of a device with a motor-driven consumer with a continuous capacity control system and selection of a motor for this. US10141884B2|2018-11-27|Cooling fan filtering KR20190138849A|2019-12-16|Compressor system with adjustable and / or controllable temperature monitoring device US20210095657A1|2021-04-01|Airend having a lubricant flow valve and controller WO2017138481A1|2017-08-17|Compressor surge generation prevention device and compressor system Paprocki2014|A Quantitative Analysis to Determine Methods to Improve an Industrial Compressed Air System. Corlman2015|Reducing energy waste in centrifugal pump systems through the implementation of BEP optimized pressure and flow control AU2013229569A1|2014-09-25|Improved pumping unit and method for controlling such a pumping unit
同族专利:
公开号 | 公开日 EP3500757B1|2020-04-22| EP3500757A1|2019-06-26| BE1024497A1|2018-03-13| KR20190035894A|2019-04-03| SG11201901173WA|2019-03-28| CN207470442U|2018-06-08| RU2721194C1|2020-05-18| US20190249660A1|2019-08-15| ES2805032T3|2021-02-10| KR102177193B1|2020-11-11| BR112019003237A2|2019-06-18| US11073148B2|2021-07-27|
引用文献:
公开号 | 申请日 | 公开日 | 申请人 | 专利标题 EP1300637A1|2000-07-13|2003-04-09|Daikin Industries, Ltd.|Refrigerant circuit of air conditioner| JP2006220342A|2005-02-09|2006-08-24|Samsung Electronics Co Ltd|Air conditioner| JP2011005980A|2009-06-26|2011-01-13|Denso Corp|Air conditioner for vehicle| US20120090331A1|2010-10-18|2012-04-19|General Electric Company|Systems and methods for supplying fuel to a gas turbine| BE1014611A3|2002-02-08|2004-01-13|Atlas Copco Airpower Nv|Method for oil return of driving in an oil injected screw compressor and thus controlled screw compressor.| KR100543215B1|2003-12-31|2006-01-20|국방과학연구소|Apparatus and method for controlling cooling fan speed| US9543787B2|2011-12-30|2017-01-10|Scrutiny, Inc.|FRAME | KR101326850B1|2012-10-04|2013-11-11|기아자동차주식회사|System and method for controlling an oil pump| WO2015073122A1|2013-11-14|2015-05-21|Parker-Hannifin Corporation|System and method for controlling fluid flow and temperature within a pumped two-phase cooling distribution unit| RU2572905C1|2014-07-09|2016-01-20|Общество с ограниченной ответственностью "Газхолодтехника"|Method of start-up of gas transfer unit| RU161853U1|2015-12-17|2016-05-10|Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Уфимский государственный нефтяной технический университет"|GAS PUMPING UNIT| US10724524B2|2016-07-15|2020-07-28|Ingersoll-Rand Industrial U.S., Inc|Compressor system and lubricant control valve to regulate temperature of a lubricant|WO2021205200A1|2020-04-06|2021-10-14|Edwards Korea Limited|Pumping system| CN111997921A|2020-07-31|2020-11-27|江苏久高电子科技有限公司|High-temperature fan with air circulation cooling function|
法律状态:
2018-03-21| FG| Patent granted|Effective date: 20180319 |
优先权:
[返回顶部]
申请号 | 申请日 | 专利标题 US201662376550P| true| 2016-08-18|2016-08-18| US62376550|2016-08-18| US201662412567P| true| 2016-10-25|2016-10-25|RU2019107352A| RU2721194C1|2016-08-18|2017-08-08|Control method of compressor or vacuum pump with oil injection and compressor or vacuum pump with oil injection for implementation of said method| SG11201901173WA| SG11201901173WA|2016-08-18|2017-08-08|A method for controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump implementing such method| PCT/IB2017/054836| WO2018033827A1|2016-08-18|2017-08-08|A method for controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump implementing such method| US16/318,172| US11073148B2|2016-08-18|2017-08-08|Method for controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump implementing such method| BR112019003237A| BR112019003237A2|2016-08-18|2017-08-08|method for controlling the outlet temperature of an oil injection compressor or vacuum pump and oil injection compressor or vacuum pump that implement such a method| ES17754491T| ES2805032T3|2016-08-18|2017-08-08|A method of controlling the outlet temperature of an oil-injected compressor or vacuum pump and the oil-injected compressor or vacuum pump implementing said method| KR1020197007262A| KR102177193B1|2016-08-18|2017-08-08|Method for controlling the outlet temperature of an oil-injected compressor or vacuum pump, and an oil-injected compressor or vacuum pump implementing the method| EP17754491.3A| EP3500757B1|2016-08-18|2017-08-08|A method for controlling the outlet temperature of an oil injected compressor or vacuum pump and oil injected compressor or vacuum pump implementing such method| CN201710709797.6A| CN107762851B|2016-08-18|2017-08-18|Method for controlling the outlet temperature of an oil-injected compressor or vacuum pump and oil-injected compressor or vacuum pump for carrying out the method| CN201721042306.9U| CN207470442U|2016-08-18|2017-08-18|Injected compressor and its controller unit and oil spout vacuum pump and its controller unit| 相关专利
Sulfonates, polymers, resist compositions and patterning process
Washing machine
Washing machine
Device for fixture finishing and tension adjusting of membrane
Structure for Equipping Band in a Plane Cathode Ray Tube
Process for preparation of 7 alpha-carboxyl 9, 11-epoxy steroids and intermediates useful therein an
国家/地区
|