• 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:
    The invention relates to a method and a device for filling an air conditioning system (16) with a defined filling quantity (M) of refrigerant from a storage reservoir (18) via a filling line system (19, 19 '). The refrigerant is conditioned to an initial value (100) before being filled in an intermediate tank (17), and the refrigerant is introduced into the evacuated air conditioning system (16) via the filling line system (19, 19 ') starting from this initial value (100) , At least when an aggregate state of the refrigerant in the two-phase region is reached, the further inflow to achieve a change in the state of matter that occurs essentially stepwise along the upper boundary line (O) of the two-phase region is interrupted at intervals.
    公开号:AT518500A1
    申请号:T50318/2016
    申请日:2016-04-13
    公开日:2017-10-15
    发明作者:
    申请人:Avl Ditest Gmbh；
    IPC主号:
    专利说明:

    Method and device for filling an air conditioning system with refrigerant
    The invention relates to a method for filling an air conditioner with a defined filling amount of refrigerant from a storage tank via a filling line, and a device for filling an air conditioner with a defined filling amount of refrigerant from a storage tank via a filling line, wherein the device is a filling unit with a load cell for determining the amount of refrigerant dispensed.
    When servicing an air conditioner, it will be connected to an A / C service unit, which will first completely drain the lines and volumes of the air conditioner and then fill the required amount of new refrigerant and oil into the system. In the draining step, the refrigerant is first drained and then exhausted by means of a compressor and / or a vacuum pump. Thereafter, the air conditioner is filled from a storage tank with new or recovered refrigerant.
    Air conditioning service units determine the filling quantity of the refrigerant by means of a load cell. It is simply the mass of the reservoir including inclining therein refrigerant measured. After opening the valves and the concomitant inflow of the refrigerant into the evacuated air conditioning system, the change in mass is continuously measured.
    When the corresponding value including a calculated compensation amount representing the refrigerant in the charging hose and in the service unit is reached, the filling valve is closed.
    Such filling operations are described for example in DE 202008003123 U1 or DE 102009054436 A1.
    However, especially for air conditioners that use R744 or carbon dioxide as a refrigerant, it may be difficult to determine the exact capacity of the replenished refrigerant. This is because the conditions of the refrigerant can greatly change during the flow of the refrigerant from the reservoir into the air conditioner, in particular, the ratio of liquid to gaseous phase is difficult to handle.
    The actual amount of compensation, which is the amount of refrigerant, which was determined by the load cell as part of the delivered amount, but remains in the lines of the service device after the filling process, often can not be determined with sufficient accuracy, since liquid refrigerant can collect in the filling hose.
    If, for example, an amount of 500 g of R744 is to be filled in the air conditioning system of a motor vehicle, it is necessary to remove from the storage tank 500 g + a compensation amount which is in the
    Air conditioning service unit remains, remove. The compensation amount corresponds to the content in the lines and hoses of the air conditioning service unit, that is, the amount of refrigerant that does not arrive in the vehicle.
    The term "quantity" may refer to the mass or volume, depending on the context, and in general, the mass is given in connection with quantities, since this information is clearly defined independently of any state changes.
    If a mixture of liquid and gaseous refrigerant (in particular C02 in a state of aggregation in the two-phase region) or only liquid refrigerant is filled, can not be determined exactly what percentage of the actual compensation amount in the device in the liquid, and how much in the gaseous state, yes through the additional volume in the air conditioning evaporates part of the refrigerant and some is liquid. Thus, at the lower points in the air conditioning service unit or in the filling hose liquid refrigerant accumulates and at higher points, the refrigerant is in the gaseous state. It is currently not possible to determine with conventional service devices and methods whether the actual quantity of refrigerant present in the lines of the service device (the actual compensation quantity) coincides with the calculated compensation quantity. Many factors can affect the actual amount of compensation, such as how the inflation hose runs to the air conditioner, whether it is on the ground or if the vehicle with the air conditioning system is on a lift, how fast the C02 flows in, etc.
    However, since the actual amount of compensation can not be uniquely determined, the amount of refrigerant actually charged in the air conditioner (i.e., the amount of charge) is not known. In some cases, therefore, it can no longer be guaranteed that the capacity after the air conditioning service meets the manufacturer's specifications.
    The possible effects of the state of aggregation of the refrigerant on the compensation quantity can be illustrated by means of an example: for example, the density of liquid CO 2 is 751 kg / m 3, for gaseous CO 2 it is 211 kg / m 3. This corresponds to a factor> 3.5.
    In a series of tests, values in a range between 50 g and 150 g were measured with an exemplary and in practice representative cable length for the actual compensation quantity under different conditions.
    The calculated mass values as a function of the mixing ratio of liquid to gaseous CO 2, starting from a line volume in which there are 50 g of gaseous CO 2 at 60 bar, are shown in Table 1 below.
    Table 1
    As can be seen from the above example, to accurately determine the actual amount of compensation (or actual fill), it is essential to optimize line lengths and cross-sections, and it is necessary to know the state of the CO 2 very accurately. This is currently difficult or impossible to implement with conventional air conditioning service units and filling methods.
    It is an object of the subject invention to provide methods and apparatus that significantly improve the possibilities of accurately determining the actual charge of a refrigerant, in particular the refrigerant R744 or C02.
    According to the invention, these and other objectives of the subject invention are achieved by a method of the type mentioned, wherein the refrigerant is conditioned to an initial value before filling in an intermediate container, wherein the refrigerant is allowed to flow from the starting value via the filling line in the evacuated air conditioning and wherein, at least when an aggregate state of the refrigerant in the two-phase region is reached, the further inflow to achieve a change in the state of aggregation which proceeds essentially stepwise along the upper boundary line of the two-phase region is interrupted at intervals. These intermittent interruptions result in an alternating sequence of interrupts and in-flow events, which can completely or almost completely avoid the accumulation of liquid refrigerant in the fill line system: as long as the inflowing refrigerant is supercritical, no liquid phase of the refrigerant can form. Since the supercritical refrigerant flows very quickly through the lines in the air conditioner, if necessary, forming liquid refrigerant would also be carried along by the flow and flushed into the air conditioner. It is only when the two-phase area is reached that a catchment of liquid refrigerant in the filling line system is to be feared. Since the pressure is lower than in the supercritical region, the flow velocity also drops, so that even larger amounts of refrigerant can form in the filling line system and accumulate there. This effect is enhanced with larger wire cross-sections (which are otherwise beneficial). However, the intervals interruptions prevent the formation of liquid refrigerant in the filling line, since the refrigerant undergoes phase separation during the interruptions on the one hand, wherein liquid refrigerant settles in the intermediate container, and at least in the gaseous removal of the intermediate container after a brief interruption only more gaseous refrigerant is present. On the other hand, the refrigerant may heat up at least locally, with refrigerant evaporating. The resulting change in the p-h diagram corresponds to a horizontal line in the two-phase region in the direction of the upper boundary line. A sequence of intermittent interruptions causes the desired according to the invention step-shaped course. At each inlet flow, liquid which may have formed in the filling line system if necessary, is either vaporized or entrained by the newly flowing refrigerant. Since the state of aggregation is always close to the upper limit line, only a small amount of new liquid refrigerant can form. The surge tank may preferably be charged with refrigerant from a reservoir prior to being let in by a compressor and conditioned to a desired pressure or temperature. In a further embodiment, the conditioning may take place directly in the reservoir, in which case the intermediate reservoir and the reservoir are the same parts.
    The initial value is preferably in a supercritical range. As a result, a large amount of refrigerant can be allowed to flow in before reaching the two-phase region.
    In an advantageous embodiment, the refrigerant can be at least after reaching the two-phase region via an inlet valve for a gaseous removal of the refrigerant from the intermediate container to flow into the air conditioner. This reduces the possible amount of liquid refrigerant that may be in the fill line system.
    Advantageously, the duration of the interruptions enables effective phase separation in the intermediate container. As a result, large quantities of condensate can not form in the filling line system in the subsequent inflow step.
    The simplest way of controlling the intermittent breaks can be achieved by making the interrupts according to a regular clock. It can also be interrupted at the beginning, in the supercritical area, the inflow with the same timing interval. Although this brings no benefit during the supercritical influx, but if the control of the clocking without sensors should only be controlled by fixed cycle times, the same predetermined clocking can be used consistently, without the time of entry into the two-phase area would have to be determined.
    For determination of interruption intervals, a volume of the filling line system, an inner diameter of lines of the filling line system, a volume of the air conditioning system to be filled, the defined capacity of the air conditioning system, an ambient temperature and / or a filling speed value may be taken into account. As a result, the respective filling strategy can be tailored precisely to the air conditioning system and the other prevailing conditions. Small diameters of the lines are advantageous in that only small amounts of refrigerant can be in the filling line system. Furthermore, a relatively large mass of the lines of the Befüllleitungssystems is a heat storage, and so can contribute to the rapid heating and evaporation of cool refrigerant in the system.
    Advantageously, the refrigerant can be heated in the intermediate container during the interruptions via a heating unit. As a result, the filling process can be accelerated. Via a heating unit, it is also possible to vaporize the entire amount of coolant in the intermediate container during the interruption, so that the step-shaped course of the state of matter could possibly also be extended into the gas region.
    The device of the type mentioned for filling an air conditioner according to the invention is characterized in that it comprises a control unit for controlling at least one inlet valve, via which the refrigerant flows when filling the air conditioner, wherein the control unit is designed to at least the inflow of the refrigerant After reaching an aggregate state of the refrigerant in the two-phase region to achieve an interval along the upper boundary line of the two-phase region substantially stepwise change of the state of aggregation to interrupt. This device allows the advantageous implementation of the method according to the invention.
    Advantageously, the filling unit can have a compressor and an intermediate container. The particular state of aggregation of the refrigerant in the intermediate container can thereby be adjusted when filling with the compressor.
    In a preferred embodiment, the compressor may be arranged to convey refrigerant from the storage reservoir into the surge tank, the load cell being arranged to weigh the amount of refrigerant in the surge tank. On the one hand, the use of intermediate containers allows the setting and monitoring of a well-defined state of aggregation before the filling process and during the filling process. The intermediate container can be made considerably smaller than conventional storage containers, each intermediate container can be equipped with a relatively simple load cell, which nevertheless has a greater accuracy than is possible with a load cell, which are required for the weighing of storage containers usual size. On the other hand, the intermediate containers, for example with regard to the seals or the thermal insulation, can be designed specifically for supercritical refrigerant, which is usually not the case with normal storage containers.
    In further advantageous embodiments, the device may have at least one inlet valve for a gaseous removal of refrigerant. Furthermore, the device can have a multiplicity of identical or different intermediate containers.
    In an advantageous manner, at least one intermediate container may have a heating unit. The heating unit allows a quick conditioning of the refrigerant in the intermediate container and the setting of the desired output value, such as when the intermediate container has cooled after filling. Furthermore, the refrigerant can be additionally heated during the interruptions in the intermediate container.
    In a further preferred embodiment, the heating unit may be based on an inductive heating of the container wall of the intermediate container. This represents a particularly simple form of heating and it is possible to use standard storage tanks, which as such have no heating unit, as intermediate tanks.
    The invention further comprises an air conditioning service unit for emptying and refilling an air conditioning system with refrigerant, wherein the air conditioning service device has a low-pressure connection and / or a high-pressure connection, a discharge unit, and a device according to the invention for filling the air conditioning system. With such a climate service device, a complete air conditioning service using the method according to the invention can be carried out quickly, easily and completely.
    With the help of the invention, the amount of refrigerant filled in the vehicle can be determined very accurately. Instead of the rather inaccurate method with the large load cell for the refrigerant storage, as is known from the prior art, the refrigerant can be measured more accurately with a correspondingly accurate load cell (optionally per intermediate container). In addition, by the dedicated filling of supercritical or gaseous refrigerant, in particular CO 2, the compensation amount can be determined much more accurately than would be possible with a mixture with a mixture of liquid and gaseous refrigerant.
    The subject invention will be explained in more detail below with reference to Figures 1 to 3, which show by way of example, schematically and not by way of limitation advantageous embodiments of the invention. It shows
    Figure 1 is a schematic representation of the filling of an air conditioner by means of a filling unit via a filling line system.
    Fig. 2 is a circuit diagram of an advantageous embodiment of the invention and
    3 shows a state diagram of R744, in which an exemplary profile of the states of the refrigerant when filling an air conditioning system is shown.
    In order to explain the designations used, FIG. 1 shows in a block-type diagram some essential elements, parameters and values to be considered when filling an air-conditioning system 16.
    The evacuated air conditioning system 16 is filled by means of a filling unit 20 via a filling line 19 with fresh refrigerant. The air conditioning system 16 has a (sometimes not exactly known) volume VK, whereas the volume VB of the filling line system 19 is known. When filling, the filling unit 20 discharges a defined filling quantity M of refrigerant plus a compensation quantity K, wherein this quantity of delivered M + K can be determined very accurately by means of one or more weighing cells 21 (not shown in FIG. 1).
    From the delivered amount M + K reaches an actual amount of filler M ± T, which is composed of the defined amount of filler M plus / minus a tolerance deviation T, in the air conditioning 16. In the filling line 19 thus remains an actual compensation amount K ± T, which is made a calculated compensation amount mi-nus / plus the tolerance deviation T composed.
    The task in filling now is to ensure that the actual value of the tolerance deviation T is below a value defined for the respective air conditioning system. This object can be achieved, for example, with the device shown below in FIG. 2 and the method exemplified below with reference to FIG. 3.
    In an air conditioning service, the air conditioning service unit of FIG. 2 is connected to the low pressure side via a low pressure port 2 and to the low pressure side via a high pressure port 3
    High pressure side of an air conditioner 16 filled with used refrigerant. After connection, the temperature and pressure of the refrigerant can be determined via measuring devices 4, 4 '. The connection valves 5, 5 'are initially closed. The lines leading away from the connection valves 5, 5 'can be interconnected via a connection valve 6, for example to allow emptying of the air conditioning system 16 via both connections 2, 3 at the same time. However, it is also possible to empty the air conditioner 16 via only a single connection.
    For discharging the refrigerant, either only the connection valve 5 on the low-pressure side is opened, or the connection valve 6 and both connection valves 5, 5 'are opened on the high-pressure and low-pressure sides 6, the refrigerant flowing through a drain-check valve 7 and parallel to a plurality arranged drain-blocking valves 8a, 8b, 8c arranged to each other, which can be selectively opened or closed via a control unit 15 respectively. The control unit 15 is also connected to other units and sensors of the air conditioning service unit 1, wherein in Fig. 2, only the connections to the drain check valves 8a, 8b, 8c are shown schematically. In Fig. 2, three drain check valves 8a, 8b, 8c are provided, but the apparatus may also have more or less drain check valves 8a, 8b, 8c. Each bleed-off valve 8a, 8b, 8c leads to a pressure-reducing member 9a, 9b, 9c, each formed as a capillary tube heat exchanger, each of the pressure reducing members 9a, 9b, 9c having different flow conditions, in particular, capillary tube heat exchangers have different flow cross sections and / or different capillary tube lengths. Also, all pressure reducing organs may have the same flow conditions, but this reduces the number of adjustable deflation stages.
    The discharge rate of the refrigerant can now be controlled by selectively opening and closing the drain check valves 8a, 8b, 8c, with the illustrated three pressure reducing members 9a, 9b, 9c, seven different opening combinations being adjustable.
    Exemplary embodiments of the bleed-off valves 8a, 8b, 8c and of the pressure-reducing members 9a, 9b, 9c and advantageous methods for discharging the refrigerant are described in detail in Applicant's earlier application AT 515240 A2. It is believed that one skilled in the art will have extensive knowledge of the devices, methods and teachings disclosed in AT 515240 A2. Therefore, in the present case, a detailed description of these known elements will be omitted for the sake of clarity.
    The oil removed in the oil separator 10 is weighed via a weighing device to determine the amount of oil to be replenished.
    When the pressure in the air conditioner 16 has dropped to the ambient pressure, the drain check valves 8a, 8b, 8c are all closed, and the air conditioner 16 is completely exhausted by a vacuum pump 13.
    Instead of the venting unit 12 shown in Fig. 2, other apparatus and methods for evacuating an air conditioning system may also be used, such as the apparatus and methods disclosed in Applicant's AT 515239 A2, AT 514741 A2, AT 514742 A2 or AT514924 A4 documents ,
    After the air conditioner has been completely emptied, the air conditioner 16 can be filled with new refrigerant and fresh oil by means of the charging unit 20 via the inflow check valve 14. Since the devices for filling fresh oil are well known to those skilled in the art, a representation and description thereof has been omitted.
    The filling unit 20 has for the purpose of filling the air conditioning system 16 with refrigerant to an intermediate container 17, the filling amount can be determined with a load cell 21. The intermediate container 17 is provided with a heating unit 23. To fill the intermediate container 17, a compressor 22 pumps refrigerant from a storage reservoir 18 into the intermediate container 17, wherein the refrigerant is freed by means of an oil separator 26 of entrained compressor oil before it enters the intermediate container 17. The compressor 17 is preferably capable of compressing the refrigerant to a supercritical pressure, and the surge tank 17 and the other lines, valves and seals are also designed for a corresponding supercritical pressure of the refrigerant.
    When a sufficient amount of refrigerant has been pumped into the intermediate container 17 and the initial state selected for the filling operation (ie in particular the corresponding outlet pressure) has been reached, the air conditioning system can be opened by opening the inlet valves 24, 25 between the intermediate container 17 and the filling line system 19, 19 'are arranged to be filled. Optionally, the refrigerant in the intermediate container 17 may be previously heated by a heating unit 23 in order to achieve a favorable initial state for the filling process. A favorable initial state, for example, a spec. Enthalpy exceeding the spec. Enthalpy is in the critical point. This ensures that a phase state on the upper boundary line O of the p-h diagram (see FIG. 3) is achieved in the subsequent (isenthalpic) discharge step. The heating unit 23 can also be used to bring the filled intermediate container back to a required starting temperature after a work stoppage.
    The filling can then take place either via the filling line system 19 via the high-pressure connection 3, or via the filling line system 19 'and via the low-pressure connection 2, or via both connections simultaneously.
    Optionally, a plurality of intermediate container 17 may be arranged parallel to each other in order to provide larger amounts of supercritical refrigerant can. The contents of the plurality of intermediate containers can then be measured either with a common load cell 21 or via individual load cells and each intermediate container can be provided with its own inlet valves 24, 25.
    The intermediate container is provided with an inlet valve 24 for the liquid withdrawal and an inlet valve 25 for the gaseous removal. In the supercritical region and in the gas region, the removal via both inlet valves 24, 25 can take place simultaneously, wherein the removal in the two-phase region preferably takes place only via the inlet valve 25 for the gaseous removal. The physical state of the refrigerant in the intermediate container 17 can be monitored by a thermometer 27 and a pressure gauge 28.
    FIG. 3 shows by way of example curves of the state of aggregation of the refrigerant during the filling of the air conditioning system 16.
    The filling can first take place exclusively in a first section A, the refrigerant remaining in the supercritical region (supercritical filling). Since supercritical refrigerant, especially CO 2, has a density corresponding to the liquid phase but having a viscosity of the gas phase, a large amount of refrigerant flows into the air conditioner in a short time. Although it would be advantageous to fill the air conditioning exclusively supercritical, but this is usually prevented in practice by the legally regulated maximum values for pressure vessels (such as in accordance with the Austrian Steam Boiler Ordinance).
    If the pressure vessels were to be filled too much, the A / C service unit would fall into higher hazard classes, requiring additional safety measures that would make the A / C service unit complex and not competitive. In general, therefore, it will be necessary to continue filling below the critical pressure, so that the problems associated with the formation of a liquid phase in the two-phase region arise. If the required amount of coolant is therefore not reached with the supercritical filling, in a second section B, the refrigerant in the region of the two-phase region and / or the gas region is allowed to flow (subcritical filling).
    In the case of supercritical filling (subsection A), starting from an initial state 100 in the supercritical region, at least one of the inlet valves 24, 25 is opened, and the refrigerant flows into the air conditioning system 16, whereby (neglecting the heat losses) an essentially isenthal pressure reduction up to Point 101 shows. The point 101 is at the level of the critical pressure KP, wherein the phase of the refrigerant changes from supercritical to gaseous. Immediately thereafter, the aggregate state of the refrigerant reaches the upper limit line O passing between the two-phase region and the gas region of the p-h diagram, which point defines the occurrence of a liquid phase. The intermediate section between leaving the supercritical region and entering the two-phase region is in practice very short and generally negligible.
    As explained above, the occurrence of a liquid phase in the filling line system can lead to a (not exactly determinable) change in the actual amount of compensation. This has an immediate effect on the tolerance deviation T, ie the difference between the defined filling quantity M and the actual filling quantity M ± T of the air conditioning system. Therefore, if the refrigerant were allowed to continue to flow in, the inflowing refrigerant would become a phase state within the two-phase region where it is not possible to determine where and how a liquid phase is formed in the system. If, for example, a large amount of refrigerant could be allowed to flow in further from the inlet valve 25 for the gaseous removal, then a strong cooling would occur in the upper region of the intermediate container, thus reducing the pressure and forming a liquid phase. This happens when flowing out both in the tank and in the hose, in the valves, etc. If you were to fill the system of the air conditioning system in one go, the phase change would be somewhere in the middle of the wet steam zone without being able to determine where and how much refrigerant is condensing which temperature is present, etc.
    According to the invention, therefore, the inflow is briefly interrupted after reaching the two-phase region, wherein a phase separation occurs in the intermediate container 17, in which the liquid refrigerant on the one hand evaporates again and on the other hand partially settles in the intermediate container. After the interruption, the refrigerant in the upper region of the intermediate container is substantially 100% gaseous and in the lower region 100% liquid. If only one gaseous fraction is removed (via the inlet valve 25 for gaseous removal) in the next step, the state of aggregation of the withdrawn refrigerant is located on the wet steam curve on the far right, that is, on the upper boundary line O of the two-phase region. (Conversely, the state of aggregation of a refrigerant withdrawn via the inlet valve 24 for the liquid withdrawal on the
    Wet steam curve on the far left, that is, on the lower boundary of the two-phase area). If, therefore, a little refrigerant is now allowed to flow out via the gaseous removal inlet valve 25, on the one hand the pressure and the temperature of the gas will decrease and, moreover, a small part of the liquid phase will be formed. This sampling step must not take too long, so that not too much liquid phase can form in the withdrawn refrigerant. In the subsequent break, the phase separation then takes place, with the state of aggregation of the refrigerant in the area of the inlet valve 25 for the gaseous removal approaching the upper limit line O again.
    After a step of flowing in, a lower pressure is established in the upper area of the intermediate tank and a little condensed refrigerant forms at a slightly lower temperature. During the break, there is a balance with the surrounding refrigerant. The pressure is equalized everywhere, the condensed refrigerant is largely evaporated again and a small part may also sink into the liquid, while at the same time a part evaporates there. The container temperature changes only insignificantly, since the wall of the intermediate container has a relatively large mass (and thus represents a large heat storage), which is slightly above ambient temperature or by the previous inflation. Therefore, some heat is also released from the container wall to the refrigerant, so that in the system, the temperature and pressure at each Einströmschritt will only slightly decrease, the phase separation between liquid and gas, however, sets very quickly and the temperature of the refrigerant is thus not extreme drops.
    This process can now be continued stepwise, resulting in the step-shaped course of the refrigerant according to the invention in the region of the upper boundary line O of the two-phase region. During the Einströmtakte which optionally in the filling line 19, 19 'located condensate is partially evaporated, and if this effect is insufficient, residual condensate is entrained for the greater part of the flow of the refrigerant, so that in the filling line 19, 19' no significant amounts can form condensate.
    The material of the lines represents a relatively large heat reservoir, which helps to keep the temperature of the refrigerant in the filling line in the range of room temperature. In particular, by choosing very small line cross sections, the ratio of ambient volume (i.e., conduit material) to gas volume can be selected to be very large, which still aids in the heating and vaporization of the refrigerant in the fill line system.
    To accelerate the process, the refrigerant can be actively heated in the intermediate container during the interruptions, approximately via the heating unit 23 shown in Fig. 2. Thus, in each step step, the entire contents of the intermediate container 17 can be brought into a gaseous state of matter, possibly also on the Boundary line O of the two-phase region.
    The step-shaped course along the upper boundary line O can be controlled in particular by the length of the individual inflow steps and the intervening interruptions.
    In the case of a step-shaped course, it may be advantageous to completely vaporize the refrigerant in the intermediate container at each interruption and to extend the state of aggregation slightly beyond the upper limit line O into the gas region.
    In a simpler embodiment, the inflow process could be intermittently interrupted at least in the partial area B shown in FIG. 3, but possibly also in the partial area A, with a regular clocking. It is not even necessary to determine the respective state of matter and to install complex measuring and control means. For example, starting from the initial value 100, both inlet valves 24, 25 could be opened to allow supercritical refrigerant to flow into the evacuated air conditioning system until the critical pressure is reached. Then, the liquid sampling inlet valve 24 is closed, and the gaseous sampling inlet valve 25 is opened at intervals according to the timing. It would also be possible to carry out the entire filling by means of a constant timing, in which case it would not be necessary to monitor the state of matter in order to detect the time of entry into the two-phase area.
    The optimum cycle times are dependent on the dimensions of the respective filling device, in particular the line cross-sections, and can be determined by a person skilled in the art by routine tests. In tests conducted by the present inventor, at line diameters of 4 mm at a 100 ms injection stroke, which actually took about 70 ms, adjusted by the response time of the valve, between 8 g (at about 75 bar) and 3 g (at 55 bar) C02. For smaller cable cross-sections these values would probably be slightly lower due to the higher cable resistance.
    The timing can also be varied, for example, after a pre-filling of 50-80% of the total amount, the further filling with inflow cycles of 50-200 ms and pauses of about 5-10 s can be performed. The duration of the inflow cycles can either be constant or it can also be varied, for example, it is possible to start with inflow cycles of 100 ms after the pre-filling and to reduce the duration further to 50 ms.
    With the filling from the two-phase area out (ie in the sub-area B), although compared to the supercritical filling only relatively small amounts of refrigerant can be filled, but this may be sufficient to ensure complete filling of the air conditioning, the amount measured very accurately can be.
    The filling process ends (for example, at the end point 102) as soon as the defined filling quantity M plus the compensation amount K has flowed out of the intermediate container, which can be determined via the weighing cell 21. If the amount at the end of the interval filling (portion B) is not sufficient, the intermediate container 17 can be filled with refrigerant from the storage tank 18 again, and then to be able to fill the remaining amount of refrigerant can.
    REFERENCE CHARACTERS:
    Air conditioning service unit 1 low-pressure connection 2 high-pressure connection 3 measuring devices 4, 4 '
    Connection valves 5, 5 'Connection valve 6 Drain check valve 7 Drain check valves 8a, 8b, 8c Capillary tube heat exchanger 9a, 9b, 9c Oil separator 10 Outlet check valve 11 Drain unit 12 Vacuum pump 13 Inflow check valve 14 Control unit 15 Air conditioning 16 Intermediate tank 17 Reservoir 18 Fill piping system 19, 19 'Filling unit 20 Load cell 21 Compressor 22 Heating unit 23 Inlet valves 24, 25 Oil separator 26
    Parameters and values: defined filling quantity M permissible tolerance deviation T first section A second section B upper limit line O compensation quantity K volume filling system VB volume air conditioning VA
    权利要求:
    Claims (15)
    [1]
    1. A method for filling an air conditioning system (16) with a defined filling quantity (M) of refrigerant from a storage reservoir (18) via a filling line system (19, 19 '), characterized in that the refrigerant before filling in an intermediate container (17) is conditioned to an initial value (100), wherein the refrigerant is flowed starting from this initial value (100) via the Befüllleitungssystem (19, 19 ') in the evacuated air conditioner (16) and wherein at least when an aggregate state of the refrigerant in the two-phase region Further inflow to achieve along the upper boundary line (O) of the two-phase region substantially stepwise change in the state of aggregation is intermittently interrupted.
    [2]
    2. The method according to claim 1, characterized in that the output value (100) is in the supercritical range.
    [3]
    3. The method of claim 1 or 2, characterized in that the refrigerant is at least after reaching the two-phase region via an inlet valve (25) for a gaseous removal of the refrigerant from the intermediate container (17) into the air conditioning (16) to flow.
    [4]
    4. The method according to any one of claims 1 to 3, characterized in that the duration of the interruptions enables effective phase separation in the intermediate container (17).
    [5]
    5. The method according to any one of claims 1 to 4, characterized in that the interruptions are carried out according to a regular clocking.
    [6]
    6. The method according to any one of claims 1 to 5, characterized in that for the determination of interruption intervals, a volume (VB) of the Befüllleitungssystems (19, 19 '), an inner diameter of lines of the Befüllleitungssystems (19, 19') has a volume (VK) the air conditioning system (16) to be filled, the defined filling quantity (M) of the air conditioning system (16), an ambient temperature and / or a filling speed value are taken into account.
    [7]
    7. The method according to any one of claims 1 to 6, characterized in that the refrigerant in the intermediate container (17) during the interruptions via a heating unit (23) is heated.
    [8]
    8. An apparatus for filling an air conditioner (16) with a defined capacity (M) of refrigerant from a storage reservoir (18) via a filling line (19, 19 '), wherein the device is a filling unit (20) with a load cell (21) Determining the quantity delivered (M + K) to refrigerant, characterized in that the device comprises a control unit (15 ') for controlling at least one inlet valve (24, 25), via which the refrigerant flows when filling the air conditioning system (16), wherein the control unit (15 ') is designed to intermittently interrupt the inflow of the refrigerant at least after reaching an aggregate state of the refrigerant in the two-phase region to achieve a change in the state of matter substantially stepwise along the upper boundary line (O) of the two-phase region.
    [9]
    9. Apparatus according to claim 8, characterized in that the filling unit (20) has a compressor (22) and an intermediate container (17).
    [10]
    10. The device according to claim 9, characterized in that the compressor (22) is arranged to convey refrigerant from the storage reservoir (18) in the intermediate container (17) and wherein the load cell (21) for weighing the in the intermediate container (17). located amount of refrigerant is arranged.
    [11]
    11. Device according to one of claims 8 to 10, characterized in that the device comprises at least one inlet valve (25) for a gaseous removal of refrigerant.
    [12]
    12. Device according to one of claims one of claims 9 to 11, characterized in that the device has a plurality of identical or different intermediate containers (17).
    [13]
    13. Device according to one of claims 9 to 12, characterized in that at least one intermediate container (17) has a heating unit (23).
    [14]
    14. The apparatus according to claim 13, characterized in that the heating unit (23) is based on an inductive heating of the container wall of the intermediate container.
    [15]
    15. An air conditioning service unit (1) for emptying and refilling an air conditioning system (16) with refrigerant, wherein the air conditioning service device (1) has a low-pressure connection (2) and / or a high-pressure connection (3), a discharge unit (12), and a device according to one of the Claims 8 to 14 has.
    类似技术:
    公开号 | 公开日 | 专利标题
    DE102006021820B4|2008-10-30|Overfill protection for a liquid hydrogen tank
    EP3231646B1|2018-11-21|Method and device for filling an air conditioning unit with refrigerant
    EP2944486B1|2016-06-15|Device and method for maintenance of an air conditioner
    EP2713133A1|2014-04-02|Device for determining the charge status of a thermal storage device
    DE10160763B4|2009-11-19|Device for automatic recirculation of coolant
    DE102014200250A1|2015-07-09|A method of conditioning a liquid pharmaceutical filling device into a container and filling device for carrying out the method
    EP2539788B1|2014-05-28|Apparatus and method for filling level measurement
    DE202011051378U1|2012-06-11|cooling device
    EP2697435B1|2015-04-15|Method for filling and emptying a liquid tank of a spreader device for winter service vehicles, and spreader device
    EP2817426B1|2016-05-18|Pressure stabilisation method
    EP3594554A1|2020-01-15|Device for supercooling of liquefied gases
    DE2014438A1|1971-10-07|Milk pumping/metering equipment
    EP3018435B1|2018-01-03|Device and method for maintenance of an air conditioner
    EP1321730A2|2003-06-25|Low pressure accumulator particularly for a CO2 operated air conditioning system
    EP2933442B1|2016-11-02|Device and method for detecting leaks in closed cycle processes
    EP1616336B1|2008-07-09|Nuclear facility and method for operating a nuclear facility
    EP2409580A1|2012-01-25|Method and device for guiding media through a thermic treatment assembly for a liquid product
    EP3017980A2|2016-05-11|Device and method for maintenance of an air conditioner
    DE202013003972U1|2014-08-04|Liquid feeding system
    DE10318141B4|2005-07-07|Nuclear facility with overflow facility between flood basin and condensation chamber and method for operating such a nuclear facility
    WO2021001162A1|2021-01-07|Cooling section with valves and pressure vessels for preventing pressure shocks
    DE1227036B|1966-10-20|Cooling system with a separation room
    WO2020048665A1|2020-03-12|Air-conditioning servicing appliance, and method for filling a vehicle air-conditioning system
    DE544699C|1932-02-20|Continuous absorption refrigeration apparatus
    AT515240A2|2015-07-15|Air conditioning service unit and method for discharging refrigerant from an air conditioner
    同族专利:
    公开号 | 公开日
    EP3231646A1|2017-10-18|
    EP3231646B1|2018-11-21|
    AT518500B1|2018-04-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2009132836A1|2008-04-29|2009-11-05|Vulkan Lokring-Rohrverbindungen Gmbh & Co. Kg|Filling cooling circuits with liquid refrigerant|
    DE102009031293A1|2008-07-02|2010-01-07|Tkr Spezialwerkzeuge Gmbh|Fluid e.g. oil, system e.g. motor vehicle-air conditioning system, filling device for use in workshop, has pressure container provided with volume-changeable cavities for receiving fluids, respectively|
    US20110214436A1|2010-03-05|2011-09-08|William Brown|Air conditioning system recharging method and apparatus|
    AT514924A4|2014-05-12|2015-05-15|Ditest Fahrzeugdiagnose Gmbh|Apparatus and method for servicing an air conditioner|CN112577223A|2020-10-22|2021-03-30|张家港市智恒电子有限公司|Refrigerant recovery machine circuit|DE10061545A1|2000-12-11|2002-06-13|Behr Gmbh & Co|Procedure for refrigerant level monitoring|
    JP5083282B2|2009-07-31|2012-11-28|ダイキン工業株式会社|Refrigerant charging method in refrigeration apparatus using carbon dioxide as refrigerant|
    JP2011012958A|2010-10-22|2011-01-20|Mitsubishi Electric Corp|Method for controlling refrigeration cycle apparatus|
    法律状态:
    2018-06-15| HA| Change or addition of new inventor|Inventor name: PETER KERSCHENBAUER, AT Effective date: 20180507 Inventor name: ANTON KOHL, AT Effective date: 20180507 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50318/2016A|AT518500B1|2016-04-13|2016-04-13|Method and device for filling an air conditioning system with refrigerant|ATA50318/2016A| AT518500B1|2016-04-13|2016-04-13|Method and device for filling an air conditioning system with refrigerant|
    EP17164889.2A| EP3231646B1|2016-04-13|2017-04-05|Method and device for filling an air conditioning unit with refrigerant|
    [返回顶部]