• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Regulation procedure of an inverter compressor of a refrigeration system comprising the following stages: - establish a working area by means of limit values of evaporation temperatures, condensation temperatures, compressor speeds, maximum compression ratio and maximum reheat, - measure the working values of the compressor in terms of evaporation temperature, condensation temperature and compression ratio. If the compressor works outside the established work zone, the procedure includes the additional step of modifying the working parameters of the compressor by acting on elements to be selected between the speed of the compressor, the degree of opening of the expansion valve and a combination of the previous ones. If the compressor does not return to the work area within a certain time, it stops and an alarm is activated.
    公开号:ES2692207A1
    申请号:ES201700309
    申请日:2017-03-29
    公开日:2018-11-30
    发明作者:Vicente AVILA CHILLIDA
    申请人:Vicente AVILA CHILLIDA；
    IPC主号:
    专利说明:

    INVERTER COMPRESSOR REGULATION PROCEDURE IN COOLING FACILITIES

    DESCRIPTION
     5
    OBJECT OF THE INVENTION
    The present invention, as expressed in the description of this specification, consists of a procedure for the control, by means of the regulation of the inverter compressor, of a refrigeration unit in a refrigeration unit, both individually, and of the entire system . 10

    The improvements affect the management of the efficiency regulation and the operation of the inverter compressor of the refrigeration unit, the management of the production of refrigeration power and the management of defrosts of the refrigeration unit. All this without introducing new elements in the system. fifteen

    TECHNICAL PROBLEM TO BE RESOLVED AND BACKGROUND OF THE INVENTION
    In most existing industrial refrigeration systems, there are usually two cases that divide current technology.
     twenty
    The first of these is a cooling system consisting of a central unit from which the entire refrigeration cycle is carried out. These systems have a series of centralized compressors and condensers and of the appropriate size to be able to generate the volume of refrigerators necessary to reach the working conditions in the specified area. 25

    The other system consists of having a centralized zone and, in specific places where a certain temperature is required, having the individual refrigeration units that are required. The problem with this model is that the coolant performs the entire circuit, causing losses in the system due to connections in the communications.

    In both systems, the problem comes from the heat generated in the condensers, which heat the same area that is intended to cool.
     35
    Document ES2538306 refers to an industrial refrigeration system composed of several independent refrigeration units focused on both conservation and freezing, in which each refrigeration unit is installed in a thermally and acoustically insulated furniture, and the refrigeration system comprises The only unit of heat dissipation connected by a pipe by means of a water ring from which leads to each of the cooling units, and each of the cooling units and the heat dissipation unit having individual electronic control equipment.

    The refrigeration units comprise two compressors, of alternative and never simultaneous operation, to continue cooling even if a compressor breaks down. 10

    The individual electronic control units of each of the components are connected to each other and are also connected to a control unit that receives information on the status of all the components of the installation and has the capacity to detect warnings and alarms. fifteen

    In this invention, functionality has been considered as the main factor to consider, considering energy efficiency in the background.

    Document ES2558026 focuses on managing the energy efficiency of a refrigeration installation 20 as described in document P201331679 above by replacing the compressors of each of the refrigeration units with inverter compressors, eliminating the redundancy of compressors in the equipment of refrigeration. In the background is the possibility of maintaining the redundancy of compressors in their inverter variety as a valid design alternative for situations in which the criticality of the system is valued above efficiency.

    The present invention goes a step further in managing the efficiency of a refrigeration unit with inverter compressor or of the entire system by programming control management. 30

    DESCRIPTION OF THE INVENTION
    The present invention describes a method of regulating an inverter compressor of a refrigeration system comprising an expansion valve defined by an evaporation temperature Te, a condensing temperature Tc, a speed of the compressor vc and a compression ratio rc.

    The procedure comprises the following stages:
    a) establish a work zone using default values of:
    - minimum and maximum evaporation temperatures Te,
    - minimum and maximum condensation temperatures Tc, 5
    - minimum and maximum vc compressor speed,
    - a maximum compression ratio rc defining the relationship between an evaporation temperature Te and a condensing temperature Tc determined,
    - a maximum reheat value, 10
    b) measure the working values of the compressor in terms of:
    - evaporation temperature Te,
    - the condensation temperature Tc, and
    - the compression ratio rc,
    where, 15
    If the compressor is working on values outside the established working area, the procedure includes the additional stage of:
    c) proceed to modify the working parameters of the compressor acting on elements to be selected from:
    - vc compressor speed, 20
    - the degree of opening of the expansion valve,
    - a combination of the above.
    so that, if the compressor is not working again in values within the work area established in a certain time, the compressor stops and an alarm is activated. 25

    Considering this the general procedure, there may be a series of variations and alternatives, as indicated below.

    In the case where the compressor operating temperature Tc of the compressor is greater than 30 the maximum condensation temperature Tc established, step c) consists in lowering the compressor speed vc to the established minimum. If, in addition, the situation in which the condensing temperature Tc of the compressor is higher than the maximum condensation temperature established Tc persists, the procedure comprises the following additional step:
    d) open the expansion valve until the predetermined maximum reheat value is reached.

    Alternatively, if the compressor working temperature Tc of the compressor is lower than the established minimum condensation temperature Tc, step c) consists in proceeding to close the expansion valve.

    Alternatively, if the evaporation temperature Te of the compressor is lower than the minimum evaporation temperature Te established, step c) consists in proceeding to increase the speed of the compressor vc. up to the maximum established. If, in addition, the situation persists in which the evaporation temperature Te of the compressor is lower than the minimum evaporation temperature Te established, the general procedure comprises the following additional step:
    d) open the expansion valve until the predetermined maximum reheat value is reached. fifteen

    Alternatively, if the evaporation temperature Te working of the compressor is higher than the maximum evaporating temperature Te, step c) consists in lowering the compressor speed vc to the established minimum.
     twenty
    Alternatively, if the compressor working rc compression ratio is lower than the established minimum rc compression ratio, step c) consists in proceeding to lower the compressor speed vc to the set minimum.

    BRIEF DESCRIPTION OF THE FIGURES 25
    To complete the invention that is being described and in order to help a better understanding of the features of the invention, according to a preferred embodiment of the invention, a set of drawings is attached where, for illustrative purposes and not limiting, the following figures have been represented:
     30
    - Figure 1 represents a refrigeration and hydraulic scheme of a refrigeration unit.
    - Figure 2 represents a refrigeration and hydraulic scheme of the cooling system.
    - Figure 3 represents a graph Evaporation temperature - Condensation temperature showing the optimum and non-optimal working areas of a compressor.
    - Figure 4 represents the graph of figure 3 showing the hazardous work areas for a compressor.
    - Figure 3 represents a graph Evaporation temperature - Condensation temperature showing the optimum and non-optimal working areas of a compressor.
    - Figure 5 represents a graph Pressure of discharge versus the speed of the compressor and the power of the compressor, which are directly related.
    - Figure 6 represents a graph of the product temperature as a function of the speed of the compressor.
    - Figure 7 represents the graph of Figure 5 applied to several spaces to be cooled by the same compressor. 10

    The following is a list of the references used in the figures:
    1. Evaporator.
    2. Fan.
    3. Expansion valve. fifteen
    4. Refrigeration unit.
    5. Water ring.
    6. Heatsink.
    7. Compressor.
    8. Heat exchanger. twenty
    15. Pressure valves.
    16. Suction pressure probe.
    17. Suction temperature probe.
    18. Coolant tank.
    19. Liquid temperature probe. 25
    20. Gas / liquid heat exchanger.
    21. Water temperature probes.
    22. Oil recovery.
    23. Discharge pressure probe.
    24. Discharge temperature probe 30
    25. Capillary liquid cooler.
    26. Suction vessel.
    DESCRIPTION OF A PREFERRED EMBODIMENT OF THE INVENTION
    In a preferred embodiment, as shown in Figure 2, the system is mainly composed of a water ring (5) connected to a heat sink (6).
    From the water ring (5) outlets to the heat exchangers (8) of the condensers of the different cooling units (4) that make up the respective cooling equipment of the system, where the water receives heat from the system refrigerant. On the refrigerant side, the refrigeration units (4) are connected to the evaporators (1) through the expansion valves (3). 5

    As a refrigerant, the system can use any of those known in the state of the art such as, for example, HFC, ammonia, propane, or even CO2.

    In figure 2 it can be seen how the water, coming from the closed ring (5), enters and leaves the heat exchanger (8) of each of the cooling units (4) controlled by two water temperature probes (21 ), as shown in Figure 1.

    Figure 1 represents the refrigeration scheme of a refrigeration unit (4) using an inverter compressor (7). The inverter compressors (7) do not stop working as the target setpoint temperatures of the space to be cooled are reached, as is the case with traditional compressors, but a built-in frequency inverter is responsible for decreasing the speed of the compressor (7) as the setpoint temperature is reached, so that its operation is focused on maintaining this setpoint temperature by adapting the cooling power delivered as needed at all times. In the absence of starts and stops, the inverter compressor (7) does not suffer so much and it is not necessary to incorporate a redundant system for the prevention of breakdowns, the system being able to focus on energy efficiency.

    It should be clarified that, for simplicity, throughout the specification, when referring to a compressor, it should be understood that it is an inverter compressor (7).

    In this way, it can be seen in this figure how the refrigerant, coming from the evaporator (1) and after passing through a pressure suction probe (16) and another temperature (17), reaches the gas / liquid heat exchanger (20) to go to the compressor (7) and continue 30 to enter the heat exchanger (8). As when leaving the evaporator (1), at the outlet of the compressor (7) the refrigerant passes through a pressure discharge probe (23) and another temperature probe (24).

    At the outlet of the compressor (7) the refrigerant passes through an oil recuperator (22) which is responsible for collecting part of the oil incorporated in the refrigerant and taking it to a liquid cooling capillary (25) in which it condenses.

    Subsequently, the refrigerant leaves the heat exchanger (8) after the heat 5 has been transferred to the water in the ring (5) to go to the expansion valve (3) and to the evaporator (1), both already shown in Figure 2.

    Before accessing the expansion valve (3), the refrigerant passes through a gas / liquid heat exchanger (20), incorporated in order to provide greater efficiency to the system.

    In the refrigerant circuit there is a refrigerant tank (18) so that the circuit is over-supplied and from which refrigerant is absorbed according to the necessary quantities.
     fifteen
    Referring to the operation of the circuit, it can be seen that it is as indicated below.

    When starting, the compressor (7) raises the pressure and temperature of the refrigerant in the gas phase, sending it to the heat exchanger (8) of the condenser. twenty

    In the heat exchanger (8), the refrigerant condenses by giving energy to the water, reducing its sensitive temperature and enthalpy but maintaining the constant pressure.

    The refrigerant exits in the liquid phase of the heat exchanger (8) of the condenser at a condensing temperature between 35 ° and 50 °, being sent to the evaporator (1) through the expansion valve (3).

    In the expansion process, the liquid refrigerant reduces its pressure until it reaches a certain evaporation temperature that varies depending on the type of product to be refrigerated.

    In the evaporator (1), the liquid refrigerant evaporates by capturing the energy of the product to be cooled, leaving the evaporator (1) in the gas phase.
     35
    When the refrigerant in the gas phase leaves the evaporator (1), it returns to the aspiration of the compressor (7) to repeat the process.

    This process is repeated until the temperature of the product to be cooled drops to the desired set point. 5

    As an improvement in energy efficiency, an energy transfer occurs in a gas / liquid heat exchanger (20) between the liquid phase refrigerant at the outlet of the condenser heat exchanger (8) and the gas phase refrigerant when it returns from the evaporator (1) to the refrigeration unit (4) towards the compressor (7). 10

    The heat dissipated in the heat exchanger (8) of the condenser, coming from the products, is transferred to a volume of water that is maintained in recirculation in a closed ring system (5) by means of water recirculation pumps that are They are located in the heat sink (6). fifteen

    The system collects all the water from the different cooling units (4) that are running, sending it to the water ring (5) by means of water recirculation pumps until it reaches the heat sink (6).
     twenty
    The recirculation pumps regulate the flow of water they move, necessary for the operation of the system, by means of a frequency inverter commanded well by a differential water pressure probe that keeps constant the pressure difference between the suction and the pump drive or by the modulating output that the control board of the unit has for water flow management. 25

    In the heat sink (6), the water passes through a water-air heat exchanger, whereby the heat captured in the cooling units (4) terminals is transferred to the outside air.
     30
    Once the operation and configuration of a refrigeration system with compressor (7) has been detailed, the improvements introduced in the system are detailed below.

    The compressor (7) is the element of the system in which most of the energy consumption is carried out. Therefore, its correct management and control will guarantee maximum savings in the electrical power consumption of the system and, therefore, the highest energy efficiency.

    By using the compressors (7), as mentioned, consumption is regulated directly by frequency inverters, which control the speed of the compressor (7) according to demand.
     5
    However, it is not only about reaching the setpoint temperature of the space to be cooled, but it must also be protected against operation out of range that could damage the compressor (7). For this reason, not only should the compressor adjustment (7) be improved according to demand, but it must also be ensured that operation is maintained within the proper range, combining both functions. 10

    One of the limitations that the system is required, in any case, is based on the limitation of the minimum speed of the compressor (7). This is due to the fact that the speed directly influences the correct cooling of the compressor (7), as the circulation of refrigerant is limited. Thus, regardless of the speed of the compressor (7) required by temperature demand, although that demand is very low, the minimum speed of the compressor (7) is limited to a minimum that cannot be exceeded.

    This lower speed limit of the compressor (7) is given by the working position in the high and low graph, as reflected in figure 3, where the abscissa axis represents the evaporation temperature and the ordinate axis represents Condensation temperature

    The graph shows an OPTIMAL zone, which is where it is desired that the compressor (7) is running. There is also a NON-OPTIMAL zone, where the compressor (7) must be prevented from entering work and, if it is, for a limited time.

    Finally, there is a cut area in the graph, where the compressor (7) does not work. To understand this area of the graph, one must first take into account the law of the 30 ideal gases, applied at a constant volume together with the definition of the compression ratio, that is:
     (P × V) T = cte → PT = cte

    rcomp = P (high) P (low) = P (condensation) P (evaporation) → rcomp = T (condensation) T (evaporation)

    Thus, in the graph it can be seen that, when the compression ratio increases, the lower limit of the low pressure or, what is the same, the condensation temperature, is limited to the rise. 5

    This limitation is due to the fact that high compression factors imply greater heating of the compressor (7), which can cause damage to the compressor (7) and reduce its useful life, so they try to avoid it.
     10
    In addition, it should be borne in mind that the situation of having the compressor (7) working at high compression factors and, at the same time, at a low rotation speed could occur, as the space to be cooled is found at a temperature close to the setpoint , which would result in damage to the compressor (7) due to overheating due to the high compression ratio, on the one hand, and the lack of cooling, due to the lack of circulation of the refrigerant, on the other.

    To avoid this overheating, it is essential to increase the volume of refrigerant in circulation, since this is the only way to cool the compressor (7) and, above all, not allow it to exceed minimum levels. twenty

    A control that is important to carry out is related to the compressor (7) entering to work outside the OPTIMAL zone indicated in the graph, because it is operating under conditions of pressure, temperature, speed or consumption not desired due to the fault system performance and exposure to damage that could cause the compressor to fail (7).

    It should be taken into account that the values of the condensation and evaporation temperatures that delimit the areas of the graph marked OPTIMAL and NOT OPTIMAL depend on the particular compressor model (7) and is specified by the manufacturer. 30

    In any case, the position in the graph in which a compressor (7) is working may be due to the demand for conditions for the space to be cooled and be conditioned by water and coolant temperatures, but it may also be due to a failure in the refrigeration unit (4). For this reason, a control is established for 35
    determine if this situation is temporary or if, on the contrary, it is durable, due to a failure of the refrigeration unit (4).

    In this way, if the operation of the compressor (7) is positioned in an undesired area, a time range is established during which actions will be taken to position the compressor (7) in the OPTIMAL area.

    In the event that a predetermined time elapses, during which the unit has attempted to return to its OPTIMAL area of operation and has failed to exit the unwanted area, the system shall consider that the refrigeration unit (4) is undergoing an abnormal operation. , will stop and issue an alarm notice.

    In this way, depending on the position in which the compressor (7) is working, in terms of deviation from the OPTIMAL work zone, certain corrective actions are taken. fifteen

    Based on the graph of figure 3, the graph of figure 4 is considered, in which the areas considered dangerous for the operation of the compressor (7) are more accurately represented, differentiating them to determine the type of corrective action to be carried out. If the compressor (7) comes into operation in any of them. twenty

    Thus, the effect of finding the compressor (7) working in each of the marked areas and the corrective actions to be taken to avoid placing the compressor (7) working in areas where it may be damaged are described below.
     25
    In the graph of figure 4, it should be taken into account that, based on the ideal gas law for a constant volume, as seen above, the relationship between pressure and temperature remains constant. In this way, zones of high or low temperatures imply zones of high or low pressures, respectively. It should also be remembered that an increase in the speed of the compressor (7) implies an increase in condensation pressure and a decrease in evaporation pressure, which implies that the compression ratio also increases.

    ZONE 1: The condensation temperature and, therefore, the condensation pressure, is very high. To avoid triggering the high pressure alarm, the pressure of 35
    Condensation should be reduced, for which the speed of the compressor (7) is reduced, by being directly proportional, to the lower limit set.

    If this lower minimum speed limit is reached and the compressor (7) still does not leave zone 1, an order is given to open the electronic expansion valve (3) of the refrigeration equipment to try to reduce the high and that the compressor is positioned in the OPTIMAL zone. The opening of this valve (3) is limited by the reheating value, always ensuring a positive value so that no return of coolant to the compressor (7) is created. Overheating is the difference between the temperature at the evaporator outlet and the evaporation temperature at the evaporator inlet. It can be considered as the excess from the evaporation temperature, which gives a margin so that the steam does not become liquid again.

    If these actions do not position the compressor (7) back to the OPTIMAL area in the predetermined time, the compressor (7) must be stopped and an alarm message issued. fifteen

    ZONE 2: The condensation temperature and, therefore, the condensation pressure, is very low. To avoid triggering the low pressure alarm, the first action is given to close the electronic expansion valve (3) of the refrigeration equipment, in order to create an obstruction that increases the condensing pressure. The limit of this action is established by the routine in the expansion valve (3) conditioned by the maximum reheating value.

    The operation of this routine is as described below. When the expansion valve (3) is closed, less refrigerant passes through the evaporator (1), which increases the value of overheating.

    The expansion valve (3) closes until the maximum superheat value is reached, at which time it opens what is necessary so as not to exceed said maximum value.
     30
    This is necessary to control since maintaining superheat values greater than the maximum reheating value may involve excessive heating of the compressor, since the compressor (7) is cooled by the refrigerant itself that passes through it.

    If, after closing the expansion valve (3), it is not possible to increase the pressure of condensation in a given period of time, the speed of the
    compressor (7) and, when the condensing pressure increases, re-open the expansion valve (3) so that a certain value of the condensing pressure and, consequently, the condensing temperature is reached, within the OPTIMAL zone.

    If these actions do not position the compressor (7) back to the OPTIMAL area in the predetermined time 5, the compressor (7) must be stopped and an alarm message issued.

    ZONE 3: The evaporation temperature and, therefore, the evaporation pressure is very low. Therefore, the speed of the compressor (7) must be increased to the upper limit set to decrease the evaporation pressure and, therefore, the evaporation temperature.

    If this action fails to raise the evaporation temperature, the expansion valve (3) must be opened, limiting the positive superheat value. In this way, as more volume of refrigerant passes to the evaporator (1), the evaporation pressure increases and, therefore, the evaporation temperature also increases until the compressor (7) enters the OPTIMAL operating area.

    If these actions do not position the compressor (7) back to the OPTIMAL area in the predetermined time, the compressor (7) must be stopped and an alarm message issued. twenty

    ZONE 4: The evaporation temperature and, therefore, the evaporation pressure is very high. Therefore, the speed of the compressor (7) must be decreased to increase the evaporation pressure and, therefore, the evaporation temperature until the compressor is brought to the OPTIMAL operating area. 25

    If with this action it is not possible to take the compressor to the OPTIMAL area, the expansion valve (3) must be closed, having as a limit the maximum reheating value, so as to reduce the evaporation pressure and, therefore, the temperature evaporation
     30
    If these actions do not position the compressor (7) back to the OPTIMAL area in the predetermined time, the compressor (7) must be stopped and an alarm message issued.

    ZONE 5: The understanding ratio is very low. Therefore, the speed of the compressor (7) must be increased, so that the understanding ratio increases. In this way, the evaporation temperature decreases and the condensation temperature increases.

    If this action does not position the compressor (7) back to the OPTIMAL area in the predetermined time, the compressor (7) must be stopped and an alarm message issued.

    The control functions are carried out by electronic systems of the known 5 in the state of the art and, therefore, will not be described.

    Establishing the previous safety routines, which are activated in case the compressor (7) enters any of the dangerous zones of operation 1 to 5 described, with the operating limits imposed by the own operation of the 10 compressor (7) and , based on the demand for cooling power, the refrigeration equipment is configured to work at a point located in the OPTIMAL area of the graph shown in Figure 4, based on the fact that the actual demand for cooling power is directly proportional to the speed of the compressor (7) and, therefore, to the power of the compressor (7) as reflected in figure 5 where, on the axis of abscissa, the power demanded PD is reflected and, in that of ordinates, the power of the Pc compressor and the speed of the Vc compressor.

    In this way, a programmable parameter is established in the control system with the demand for the cooling power demand, increased by an adjustment factor to take into account the losses of the system, especially due to fouling and aging of the system.

    It should be taken into account that the limitation in the speed of the compressor (7) is not considered when the compressor (7) enters to work outside the OPTIMAL operating zone 25 established in figure 4, so that none of the the possible tools to return to the OPTIMAL work zone in the shortest possible time.

    The working point at which the compressor (7) is positioned must be compensated between the set temperature or set, preset by the user, and the temperature marked by the temperature probe of the refrigeration unit (4), or temperature real to which said refrigeration unit (4) is located, for which a series of parameters must be established such as the dead zone or temperature range from the setpoint temperature within which the refrigeration unit (4) does not no action, and the differential, temperature that marks the working point at which the compressor (7) must work in the maximum limit allowed, reaching a speed of operation at 100% of
    allowed. The dead zone is established so that the compressor (7) does not have to be varying the working conditions due to minor temperature variations that do not matter. It is a value that is usually set at 0.5 degrees. The differential is used as the maximum allowable temperature increase in which a rapid decrease in temperature is required. Normally, it is set to 1 degree. 5

    In a compressor operating curve (7), in addition, the minimum operating limit of the compressor (7), already established as mentioned above, is taken into account. This is the regime below which the compressor (7) begins to suffer and should not be transferred. 10

    This situation is represented in Figure 6.

    When the temperature of the product rises above the set setpoint value increased in the value of the dead zone, the compressor starts in a low speed of 15 revolutions to compensate for the temperature increase suffered. If the temperature continues to rise, the compressor increases in revolutions so that, if the differential is reached, the compressor (7) reaches the maximum operating limit, at 100% of the permissible speed. When the temperature decreases, the revolutions of the compressor (7) decrease. The compressor (7) stops when it reaches the setpoint set. It should be noted that the compressor (7) could also stop if it reaches the minimum limit before having reached the setpoint set, without the circuit shown varying widely.

    In addition, not only the accelerations, positive and negative, of the compressor (7) are considered, but also the speed with which they occur, that is, the accelerations. 25

    It should be taken into account that the situation described is valid for a refrigeration unit that is focused on cooling a single space and also for several spaces, being able, in the latter case, to be focused on the variation of the compressor speed (7 ) or the opening and closing of the electronic expansion valve (3). 30

    Referring to the speed of the compressor (7), this situation has been represented in figure 7, based on figure 5, where it can be seen that the cooling capacity demanded is limited by the sum of the different cooling capacities demanded by each of the spaces to be cooled, so that the total power demanded from the compressor (7) in 35
    Each moment is the sum of the instantaneous powers demanded in each of the spaces to be cooled connected to the refrigeration unit (4).

    The cooling power demand of each space to be cooled is carried out with the same criteria described above, each of the parameters defined for the 5 working conditions, that is, set, differential and dead zone, being different in each of cold services, since, in real operating situations it is the way in which the service will be produced.

    Referring to the electronic expansion valve (3), the variation of the speed 10 of the compressor (7) also influences the opening or closing of said valve (3), insofar as it controls the distribution of the volume of refrigerant moved by the compressor (7) in the different spaces to be cooled. It should also be considered that, due to the installation of the refrigeration pipe itself, it is necessary to ensure that the refrigerant is distributed correctly. Thus, as the demand for cooling power decreases, the valve (3) must be closed and, as the demand increases, the valve (3) must be opened.

    With the compressor (7) stopped, the expansion valves (3) are closed. Prior to the start of the compressor (7), the expansion valve (3) is positioned open a certain percentage that is programmable in quantity and time, regardless of the working curves and the limitations described.

    The operation of the expansion valve (3) is always limited by the fact that it is focused on maintaining positive overheating, and by situations focused on compressor protection (7) due to its working situation. 25

    The last improvement implemented in the present invention consists in the treatment of defrosts.

    The defrost programming parameters may be different from one refrigerated space to another.

    To avoid abnormal operation, when one of the services is in the process of defrosting, the expansion valve (3) will always be closed.
     35
    The present invention should not be limited to the embodiment described herein. Other
    configurations can be made by those skilled in the art in view of the present description. Accordingly, the scope of the invention is defined by the following claims.
    权利要求:
    Claims (8)
    [1]

    1. Procedure for regulating an inverter compressor (7) of a refrigeration system comprising an expansion valve (3) defined by an evaporation temperature Te, a condensing temperature Tc, a compressor speed (7) vc and 5 a compression ratio rc, characterized in that it comprises the following steps:
    a) establish a work zone using default values of:
    - minimum and maximum evaporation temperatures Te,
    - minimum and maximum condensation temperatures Tc,
    - a minimum and maximum compressor speed (7) vc, and 10
    - a maximum compression ratio rc defining the relationship between an evaporation temperature Te and a condensing temperature Tc determined,
    - a maximum reheating value,
    b) measure the working values of the compressor (7) in terms of: 15
    - evaporation temperature Te,
    - the condensation temperature Tc, and
    - the compression ratio rc,
    where,
    If the compressor (7) is working on values outside the established working area 20, the procedure comprises the additional step of:
    c) proceed to modify the working parameters of the compressor (7) acting on elements to be selected from:
    - the speed of the compressor (7) vc,
    - the degree of opening of the expansion valve (3), and 25
    - a combination of the above.
    so that,
    If the compressor (7) is not working again in values within the work area established in a certain time, the compressor (7) stops and an alarm is activated.
     30
    [2]
    2. Procedure for regulating an inverter compressor (7) of a refrigeration system, according to claim 1, characterized in that if the condensing temperature Tc working of the compressor (7) is higher than the maximum condensing temperature Tc established, step c) consists in proceeding to lower the speed of the compressor (7) vc to the established minimum. 35

    [3]
    3. Procedure for regulating an inverter compressor (7) of a refrigeration system, according to claim 2, characterized in that, if the compressor working temperature Tc of the compressor (7) is higher than the maximum set condensing temperature Tc , the procedure, after step c) and before considering the situation of the compressor in the work area, comprises the following additional stage:
    d) open the expansion valve (3) until the predetermined maximum reheat value is reached.

    [4]
    4. Procedure for regulating an inverter compressor (7) of a refrigeration system according to claim 1, characterized in that if the compressor working temperature Tc of the compressor (7) is lower than the minimum established condensation temperature Tc , step c) consists in proceeding to close the expansion valve (3).

    [5]
    5. Procedure for regulating an inverter compressor (7) of a refrigeration system according to claim 1, characterized in that if the evaporating temperature Te working of the compressor (7) is lower than the evaporation temperature Minimum established te , step c) consists in proceeding to increase the speed of the compressor vc. up to the maximum established.

    [6]
    6. Procedure for regulating an inverter compressor (7) of a refrigeration system according to claim 5, characterized in that, if the evaporating temperature Te working of the compressor (7) is lower than the evaporating temperature Te minimum established, the procedure, after step c) and before considering the situation of the compressor in the work area, comprises the following additional stage:
    d) open the expansion valve (3) until the predetermined maximum reheat value 25 is reached.

    [7]
    7. Procedure for regulating an inverter compressor (7) of a refrigeration system, according to claim 1, characterized in that if the evaporating temperature Te working of the compressor (7) is higher than the maximum evaporating temperature Te 30 established , step c) consists in proceeding to lower the speed of the compressor vc to the established minimum.

    [8]
    8. Procedure for regulating an inverter compressor (7) of a refrigeration system, according to claim 1, characterized in that if the working compression ratio 35 rc of the compressor (7) is lower than the minimum established compression ratio rc ,
    step c) consists in proceeding to raise the speed of the compressor vc to the maximum set.
    类似技术:
    公开号 | 公开日 | 专利标题
    EP3500805B1|2022-03-09|Systems and methods for controlling a refrigeration system
    ES2611980T3|2017-05-11|Refrigerant cycle device
    KR890003630B1|1989-09-28|Method and apparatus for controlling a refrigerant expansion valve in a refrigeration system
    ES2699436T3|2019-02-11|Procedure and device for heat recovery in a steam cooling system
    EP3414497B1|2020-04-08|Systems and methods for controlling a refrigeration system
    US20180031292A1|2018-02-01|Condenser Pressure Control System and Method
    ES2692207B1|2019-09-16|Regulation procedure for inverter compressors in refrigeration installations
    ES2594155T3|2016-12-16|Cooling circuit overheating control
    JP6781034B2|2020-11-04|Refrigerant circuit system and control method of refrigerant circuit system
    JP2012047415A|2012-03-08|Waste heat utilizing system of refrigerating device
    US20210033326A1|2021-02-04|Heat source device and refrigeration cycle device
    KR102191560B1|2020-12-15|Heat pump system and control method of the same
    JP6267952B2|2018-01-24|Refrigeration cycle equipment
    KR20200126589A|2020-11-09|Cooling System with Self-Controlling of condensing Temperature
    US11112151B2|2021-09-07|Heat source unit for refrigeration apparatus including a heat-source-side heat exchanger having a heat exchange region of variable size
    JP6024241B2|2016-11-09|Heat pump system
    ES2558026B1|2016-11-16|INDUSTRIAL REFRIGERATION SYSTEM, IMPROVED
    ES2702727T3|2019-03-05|Air conditioning device
    KR101642437B1|2016-07-25|Cooling and heating system
    ES2318941B1|2010-01-21|COMBINED COOLING AND AIR CONDITIONING SYSTEM.
    ES2306746T3|2008-11-16|METHOD FOR LIMITING CONDENSATION PRESSURE IN A REFRIGERATING MACHINE.
    ES2730555T3|2019-11-11|Procedure for the operation of a refrigeration circuit
    JP2021148424A|2021-09-27|Air conditioning unit and system including the same
    JP2021148376A|2021-09-27|Air conditioner
    KR100639488B1|2006-10-27|Air conditional and overload controlling method the same
    同族专利:
    公开号 | 公开日
    WO2018178485A1|2018-10-04|
    PT3388760T|2019-10-29|
    MA45351A|2019-08-28|
    US20180283756A1|2018-10-04|
    ES2692207B1|2019-09-16|
    EP3388760A1|2018-10-17|
    EP3388760B1|2019-08-28|
    PL3388760T3|2020-02-28|
    US10955178B2|2021-03-23|
    MX2017012109A|2018-11-12|
    ES2751086T3|2020-03-30|
    MA45351B1|2019-11-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4523435A|1983-12-19|1985-06-18|Carrier Corporation|Method and apparatus for controlling a refrigerant expansion valve in a refrigeration system|
    JPS6484055A|1987-09-25|1989-03-29|Matsushita Refrigeration|Multiple chamber type air conditioner|
    US6430951B1|1991-04-26|2002-08-13|Denso Corporation|Automotive airconditioner having condenser and evaporator provided within air duct|
    US5209076A|1992-06-05|1993-05-11|Izon, Inc.|Control system for preventing compressor damage in a refrigeration system|
    IL109967A|1993-06-15|1997-07-13|Multistack Int Ltd|Compressor|
    US5570585A|1994-10-03|1996-11-05|Vaynberg; Mikhail|Universal cooling system automatically configured to operate in compound or single compressor mode|
    US6148627A|1999-03-26|2000-11-21|Carrier Corp|High engine coolant temperature control|
    US6318100B1|2000-04-14|2001-11-20|Carrier Corporation|Integrated electronic refrigerant management system|
    JP3624910B2|2003-05-27|2005-03-02|ダイキン工業株式会社|Humidity control device|
    JPWO2009037759A1|2007-09-20|2011-01-06|三菱電機株式会社|Refrigeration air conditioner|
    CN101809372B|2007-09-28|2013-12-18|大金工业株式会社|Compressor operation control device and air conditioner using same|
    US8459053B2|2007-10-08|2013-06-11|Emerson Climate Technologies, Inc.|Variable speed compressor protection system and method|
    US8539786B2|2007-10-08|2013-09-24|Emerson Climate Technologies, Inc.|System and method for monitoring overheat of a compressor|
    EP2414749B1|2009-04-03|2019-06-19|Carrier Corporation|Systems and methods involving heating and cooling system control|
    JP5253541B2|2011-04-27|2013-07-31|三菱電機株式会社|Air conditioning system and remote monitoring device|
    WO2013039684A1|2011-09-13|2013-03-21|Carrier Corporation|Systems and methods for compressor overspeed control|
    JP5370560B2|2011-09-30|2013-12-18|ダイキン工業株式会社|Refrigerant cycle system|
    JP5634389B2|2011-12-22|2014-12-03|三菱電機株式会社|Air conditioner|
    US9574782B2|2012-01-20|2017-02-21|Innovent Air Handling Equipment, LLC|Dehumidification system|
    EP2835602A4|2012-03-27|2016-05-25|Mitsubishi Electric Corp|Air conditioning device|
    US9188376B2|2012-12-20|2015-11-17|Mitsubishi Electric Corporation|Refrigerant charge assisting device, air-conditioning apparatus, and refrigerant charge assisting program|
    JP5744081B2|2013-02-19|2015-07-01|三菱電機株式会社|Air conditioner|
    US9816742B2|2013-03-13|2017-11-14|Trane International Inc.|Variable frequency drive apparatuses, systems, and methods and controls for same|
    AU2013101085A4|2013-08-14|2013-09-26|Actron Engineering Pty Ltd|System and method for over heat protection of an air conditioning system|
    US9638434B2|2013-09-18|2017-05-02|Alaska Structures, Inc.|Environment control system and devices|
    ES2538306B1|2013-11-18|2016-04-20|Vicente AVILA CHILLIDA|INDUSTRIAL REFRIGERATION SYSTEM|
    JP6320731B2|2013-11-26|2018-05-09|三菱重工サーマルシステムズ株式会社|Air conditioner|
    ES2558026B1|2014-06-30|2016-11-16|Vicente AVILA CHILLIDA|INDUSTRIAL REFRIGERATION SYSTEM, IMPROVED|
    ES2692207B1|2017-03-29|2019-09-16|Chillida Vicente Avila|Regulation procedure for inverter compressors in refrigeration installations|ES2692207B1|2017-03-29|2019-09-16|Chillida Vicente Avila|Regulation procedure for inverter compressors in refrigeration installations|
    法律状态:
    2018-11-30| BA2A| Patent application published|Ref document number: 2692207 Country of ref document: ES Kind code of ref document: A1 Effective date: 20181130 |
    2019-09-16| FG2A| Definitive protection|Ref document number: 2692207 Country of ref document: ES Kind code of ref document: B1 Effective date: 20190916 |
    优先权:
    申请号 | 申请日 | 专利标题
    ES201700309A|ES2692207B1|2017-03-29|2017-03-29|Regulation procedure for inverter compressors in refrigeration installations|ES201700309A| ES2692207B1|2017-03-29|2017-03-29|Regulation procedure for inverter compressors in refrigeration installations|
    MX2017012109A| MX2017012109A|2017-03-29|2017-09-25|Regulation method for inverter compressors in refrigeration facilities.|
    PL18162445T| PL3388760T3|2017-03-29|2018-03-19|Regulation method for inverter compressors in refrigeration facilities|
    MA45351A| MA45351B1|2017-03-29|2018-03-19|Control method for inverter compressors in refrigeration installations|
    PT181624453T| PT3388760T|2017-03-29|2018-03-19|Regulation method for inverter compressors in refrigeration facilities|
    ES18162445T| ES2751086T3|2017-03-29|2018-03-19|Regulation procedure for inverter compressors in refrigeration installations|
    EP18162445.3A| EP3388760B1|2017-03-29|2018-03-19|Regulation method for inverter compressors in refrigeration facilities|
    US15/936,816| US10955178B2|2017-03-29|2018-03-27|Regulation method for inverter compressors in refrigeration facilities|
    PCT/ES2018/070274| WO2018178485A1|2017-03-29|2018-03-28|Method for regulating inverter compressors in refrigeration facilities|
    [返回顶部]