Refrigerant compressor

Abstract

A refrigerant compressor (12) for a refrigeration device includes a motor (60), at least two cylinder banks (42), and a mechanical power control unit (70) for activating and deactivating at least one cylinder bank (42) to activate or deactivate its refrigerant discharge. The refrigerant compressor (12) is capable of operating in at least two different operating modes (B) for operation in multiple partial power states. Each operating mode is configured to activate or deactivate the cylinder bank (12) differently from the other operating modes. A frequency converter (132) is assigned to the refrigerant compressor (12) for speed control of the motor (60). An operating state control device (130) is assigned to the refrigerant compressor (12) according to a power request signal (LA) input to the operating state control device and for the refrigerant compressor (12) to operate in a partial power state that conforms to the power request signal (LA), the operating state control device causes the refrigerant compressor (12) to operate in an operating mode selected from at least two different operating modes (B) and at a speed adapted to the selected operating mode to achieve such a partial power state.

Description

Technical Field

[0001] The present invention relates to a refrigerant compressor for a refrigeration device, comprising an electric motor, at least two cylinder banks, and a cylinder head and a mechanical power control unit assigned to each cylinder bank. Each cylinder bank has at least one cylinder unit having a cylinder housing and a piston driven by the electric motor and capable of oscillating motion. The cylinder head has an inlet chamber through which an inflow passes and an outlet chamber through which an outflow passes. The mechanical power control unit is used to activate and deactivate the corresponding cylinder bank to activate or deactivate the refrigerant discharge of the cylinder bank. Background Technology

[0002] Such refrigerant compressors are known from existing technologies, such as WO 2018 / 065071 A1.

[0003] There is a need to make these refrigerant compressors operate as ideally as possible. Summary of the Invention

[0004] According to the present invention, in the case of a refrigerant compressor of the type mentioned at the beginning, this task is solved in such a way that the refrigerant compressor can operate in at least two different operating modes in order to operate in various partial power states, wherein each operating mode is configured to activate or deactivate the cylinder group differently from other operating modes, the refrigerant compressor includes a frequency converter for motor speed control, an operating state control device is assigned to the refrigerant compressor, and according to a power request signal input to the operating state control device, and in order for the refrigerant compressor to operate in a partial power state that conforms to the power request signal, the operating state control device causes the refrigerant compressor to operate in an operating mode selected from at least two different operating modes and at a motor speed adapted to the selected operating mode, so as to achieve such a partial power state.

[0005] The advantage of the solution according to the present invention is that, in order to operate the refrigerant compressor in various power states, at least two, preferably multiple, operating modes are provided. Using these operating modes, the operating state control device can optimize the operation of the refrigerant compressor. In each operating mode, multiple power states can be achieved by changing the speed of the motor between the minimum speed and the maximum speed, especially by changing it steplessly.

[0006] In particular, it is possible to achieve the maximum or minimum partial power state by changing the rotational speed between the maximum and minimum speed in both the operating mode with the highest refrigerant emissions and the operating mode with the lowest refrigerant emissions.

[0007] Therefore, multiple partial power states can be provided by combining the selection of operating mode with the selection of speed, especially stepless speed.

[0008] The solution according to the present invention is particularly advantageous when using CO2 as a refrigerant.

[0009] In different operating modes, it is preferably specified that the operating status control device causes the refrigerant compressor to operate in a first operating mode, accompanied by the activation of all cylinder groups and the speed being adapted to the first operating mode, wherein the first operating mode is particularly suitable for operating states in a portion of the power range close to the maximum power.

[0010] Furthermore, it is preferably specified that the operating status control device causes the refrigerant compressor to operate in at least one additional operating mode, wherein at least one cylinder bank is deactivated and at least one cylinder bank is activated and the motor speed is adapted to the operating mode.

[0011] This means that, in this case, for a portion of the power range that is particularly suitable for achieving power request signals with medium or low power, an operating mode in which only a portion of the cylinder bank is activated is used.

[0012] In the solution according to the invention, it is particularly advantageous that the operating state control device selects an operating mode in a partial power state that can be achieved by a variety of operating modes, which achieves the highest relative efficiency or the highest COP or the lowest electrical power consumption of the motor in that partial power state.

[0013] This option can be achieved, for example, by having the operating state control device store information about relative efficiency or COP or the electrical power consumption of the motor for each operating mode and each partial power state.

[0014] In this alternative, an advantageous solution specifies that the operating state control device determines the relative efficiency or COP or the electrical power consumption of the motor for each possible operating mode in order to achieve a partial power state, and selects the operating mode by comparing the determined relative efficiency or COP or electrical power consumption.

[0015] In particular, it is stipulated that the control device stores data for each operating mode in order to determine relative efficiency or COP, or stores data during operation, especially by detecting the electrical power consumption of the motor, and will use the data in the future.

[0016] Furthermore, it is also advantageous to determine the relative efficiency or COP or electrical power consumption by the operating condition control device by detecting the suction pressure and / or the high pressure at the refrigerant compressor, since these parameters affect the relative efficiency of the corresponding operating mode under the corresponding partial power state.

[0017] Furthermore, it is preferred that the control device takes into account refrigerant, partial power status, motor power consumption and / or speed to determine relative efficiency or COP or electrical power consumption.

[0018] The relative efficiency, COP, or power consumption is determined by the control unit selecting a stored relative efficiency, COP, or power consumption based on the intake pressure and / or high pressure and / or refrigerant and / or partial power status and / or power consumption, or by calculation, depending particularly on the design of the operating control unit and the complexity and accuracy of determining the relative efficiency, COP, or power consumption.

[0019] For simplifying the operation, for example, there is the following possibility: In order to determine the relative efficiency or COP of the operating mode, the partial power states to be achieved are divided into partial power states above and below a threshold, and in the partial power states above the threshold, in the operating mode that requires a higher motor speed, higher relative efficiency or COP or lower power consumption is accepted and these operating modes are selected, and in the partial power states below the threshold, in the operating mode that requires a lower motor speed, higher relative efficiency or COP or lower power consumption is accepted and these operating modes are selected.

[0020] Various solutions can be envisioned for methods of disabling and activating cylinder assemblies.

[0021] Therefore, in an advantageous solution, the operating state control device is specified to continuously maintain a fixed, predetermined deactivation and activation operating mode with cylinder groups in the first type of operating mode, so as to achieve the partial power state required by the power request signal.

[0022] This means that in the first type of operating mode, the activation and deactivation of the cylinder bank remain unchanged while achieving partial power state.

[0023] However, another advantageous solution stipulates that the operating state control device causes the refrigerant compressor to operate in at least one operating mode corresponding to the second type of operating mode by rhythmically deactivating and activating at least one cylinder group within a defined shift interval, wherein, in particular, in this operating mode, the proportional deactivation and activation of at least one cylinder group within the shift interval is constant when achieving the corresponding partial power state.

[0024] This means that in the second type of operating mode, the cylinder bank is deactivated during the shift interval within a specific time period and activated during a corresponding additional time period, and this operating mode keeps the proportional deactivation and activation over time constant when achieving the corresponding partial power state.

[0025] Regarding the foregoing description of the solution according to the present invention, the details of how to activate and deactivate each cylinder group have not yet been discussed.

[0026] Therefore, an advantageous solution stipulates that the activation and deactivation of each cylinder block is carried out by means of a mechanical power control unit controlled by an operating status control device.

[0027] This means that the operating status control device manipulates the mechanical power control unit of each cylinder group.

[0028] In principle, the mechanical power control unit can be located anywhere in the refrigerant compressor.

[0029] A particularly advantageous feature is that the mechanical power control unit is allocated to the cylinder head of the cylinder group.

[0030] Furthermore, it is advantageously specified that the mechanical power control unit controls the inflow into the inlet chamber of the cylinder head for the activation or deactivation of the corresponding cylinder group.

[0031] This means that the power control unit will interrupt the inlet flow into the inlet chamber, thereby deactivating the corresponding cylinder group, and vice versa.

[0032] Another advantageous solution stipulates that the power control unit connects the exhaust chamber and the intake chamber in the cylinder head in order to activate or deactivate the corresponding cylinder group.

[0033] This means that, in this case, the power control unit directly connects the exhaust chamber and the intake chamber, thereby driving the cylinder assembly without torque fluctuations. This solution is particularly suitable for situations where CO2 is used as the refrigerant.

[0034] Regarding the operating status control device, for example, it is specified that it can be a control device separate from the frequency converter.

[0035] This means that, for example, when the frequency converter is integrated into the refrigerant compressor, the operating status control device is arranged separately, for example, on the refrigerant compressor or independently of the refrigerant compressor.

[0036] Alternatively, the operating status control device can be arranged in the housing that houses the frequency converter. In the simplest case, this housing is arranged on or inside the compressor housing.

[0037] One advantageous implementation of a refrigerant compressor specifies that the cylinder banks operate in parallel.

[0038] In particular, advantageous power output can be achieved when each cylinder bank of the refrigerant compressor has at least two cylinder units.

[0039] When the refrigerant compressor has more than two cylinder groups, the number of operating modes can be as large as possible.

[0040] Furthermore, the present invention relates to a refrigeration device, comprising a refrigerant compressor, a high-pressure side heat exchanger, an expansion mechanism, and a low-pressure side heat exchanger.

[0041] According to the present invention, in order to optimize the operation of such refrigeration equipment, the refrigerant compressor is configured according to one of the aforementioned embodiments.

[0042] Furthermore, it is preferred that the refrigeration equipment has an equipment control device, which generates a power request signal, for example, based on the item to be cooled.

[0043] In this case, it is also possible that the operating status control device is located inside the housing of the equipment control device.

[0044] Therefore, the foregoing description of the solution according to the present invention particularly includes various combinations of features defined by the following numbered embodiments:

[0045] 1. A refrigerant compressor for refrigeration equipment, comprising an electric motor, at least two cylinder banks, cylinder heads assigned to each cylinder bank, and a mechanical power control unit, wherein each cylinder bank has at least one cylinder unit, each cylinder unit having at least one cylinder housing and at least one piston driven by the electric motor and capable of oscillating motion, the cylinder head having an inlet chamber through which an inflow is passed and an outlet chamber through which an outflow is passed, the mechanical power control unit being used to activate and deactivate at least one cylinder bank to activate or deactivate refrigerant discharge from the cylinder bank, wherein the refrigerant compressor is capable of operating at at least two partial power states. The system operates in several different operating modes, each with a different activation or deactivation setting for the cylinder group compared to the other operating modes. A frequency converter is assigned to the refrigerant compressor for motor speed control, and an operating status control device is assigned to the refrigerant compressor. Based on a power request signal input to the operating status control device, and in order for the refrigerant compressor to operate in a partial power state that conforms to the power request signal, the operating status control device causes the refrigerant compressor to operate in an operating mode selected from at least two different operating modes and at a motor speed adapted to the selected operating mode, thereby achieving this partial power state.

[0046] 2. The refrigerant compressor according to embodiment 1, wherein the operating state control device causes the refrigerant compressor to operate in a first operating mode, accompanied by the activation of all cylinder groups and the adaptation of the motor speed to the first operating mode.

[0047] 3. The refrigerant compressor according to embodiment 1 or 2, wherein the operating state control device causes the refrigerant compressor to operate in at least one additional operating mode, wherein at least one cylinder group is deactivated and at least one cylinder group is activated and the operating mode is adapted to the speed of the motor.

[0048] 4. The refrigerant compressor according to one of the above embodiments, wherein the operating state control device selects an operating mode in a partial power state that can be achieved by multiple operating modes, and the operating mode achieves the highest relative efficiency or the highest COP or the lowest electrical power consumption of the motor in that partial power state.

[0049] 5. The refrigerant compressor according to embodiment 4, wherein the operating state control device determines the relative efficiency or COP or the electrical power consumption of the motor for each possible operating mode to achieve a partial power state, and selects the operating mode by comparing the determined relative efficiency or COP or electrical power consumption.

[0050] 6. The refrigerant compressor according to embodiment 4 or 5, wherein the operating state control device has stored data for each operating mode in order to determine the relative efficiency or COP or electrical power consumption for each operating mode.

[0051] 7. A refrigerant compressor according to any one of embodiments 4 to 6, wherein the relative efficiency or COP or electrical power consumption is determined by an operating state control device by detecting the suction pressure and / or the high pressure at the refrigerant compressor.

[0052] 8. A refrigerant compressor according to any one of embodiments 4 to 7, wherein the operating state control device considers the refrigerant, partial power state, motor power consumption and / or speed to determine relative efficiency or COP or electrical power consumption.

[0053] 9. The refrigerant compressor according to one of the above embodiments, wherein, in order to determine the relative efficiency or COP of the operating mode, the partial power state to be realized is divided into partial power states above and below a threshold, and in the partial power state above the threshold and in the operating mode with a higher speed of the required motor, a higher relative efficiency or COP or a lower power consumption is received and thus these operating modes are selected, and in the partial power state below the threshold and in the operating mode with a lower speed of the required motor, a higher relative efficiency or COP or a lower power consumption is received and thus these operating modes are selected.

[0054] 10. The refrigerant compressor according to one of the above embodiments, wherein the operating state control device continuously maintains a fixed predetermined shutdown and activation operating mode with cylinder groups in a first type of operating mode to achieve a partial power state required by the power request signal.

[0055] 11. The refrigerant compressor according to one of the above embodiments, wherein the operating state control device causes the refrigerant compressor to operate in at least one operating mode corresponding to the second type of operating mode by rhythmically deactivating and activating at least one cylinder group within a defined shift interval, wherein, particularly in this operating mode, when achieving the corresponding partial power state, the deactivation and activation of at least one cylinder group within the shift interval is constant in terms of time proportion.

[0056] 12. The refrigerant compressor according to one of the above embodiments, wherein the activation and deactivation of each cylinder group are performed by means of a mechanical power control unit controlled by an operating state control device.

[0057] 13. The refrigerant compressor according to embodiment 12, wherein a mechanical power control unit (70) is assigned to the cylinder head of the cylinder assembly.

[0058] 14. The refrigerant compressor according to embodiment 12 or 13, wherein the mechanical power control unit controls the inlet flow into the inlet chamber of the cylinder head for the activation or deactivation of the corresponding cylinder group.

[0059] 15. A refrigerant compressor according to any one of embodiments 1 to 14, wherein a power control unit connects the discharge chamber and the inlet chamber in the cylinder head for the activation or deactivation of a corresponding cylinder group.

[0060] 16. The refrigerant compressor according to one of the above embodiments, wherein the operating status control device is an operating status control device separate from the frequency converter.

[0061] 17. A refrigerant compressor according to any one of embodiments 1 to 16, wherein the operating status control device is arranged in a housing that houses the frequency converter.

[0062] 18. The refrigerant compressor according to one of the above embodiments, wherein each cylinder group of the refrigerant compressor operates in parallel.

[0063] 19. The refrigerant compressor according to one of the above embodiments, wherein each cylinder group of the refrigerant compressor has at least two cylinder units.

[0064] 20. The refrigerant compressor according to one of the above embodiments, wherein the refrigerant compressor has more than two cylinder groups.

[0065] 21. A refrigeration device, comprising a refrigerant compressor, a high-pressure side heat exchanger, an expansion mechanism, and a low-pressure side heat exchanger, wherein the refrigerant compressor is constructed according to one of the above embodiments.

[0066] 22. The refrigeration equipment according to embodiment 21, wherein the refrigeration equipment has an equipment control device that generates a power request signal.

[0067] 23. The refrigeration equipment according to embodiment 22, wherein the operating status control device is arranged in the housing of the equipment control device. Attached Figure Description

[0068] Other features and advantages of the invention are the subject of the following description and views of some embodiments.

[0069] In the picture:

[0070] Figure 1 A schematic view of a refrigeration device according to the present invention is shown;

[0071] Figure 2 The cross-section of the refrigerant compressor of the refrigeration device according to the invention is shown along line 2-2;

[0072] Figure 3 A cross-section is shown passing through the mechanical power control unit integrated into the cylinder head, wherein the valve body of the mechanical power control unit is in the open position;

[0073] Figure 4 Showing something similar to Figure 3 The cross-section of the mechanical power control unit is in the closed position;

[0074] Figure 5 A schematic diagram showing the shift interval, including the open interval and the close interval;

[0075] Figure 6 A schematic diagram showing the temperature profile of the heat exchanger on the low-pressure side of a refrigeration unit when the compression of the refrigerant is interrupted;

[0076] Figure 7 A flowchart illustrating the working method according to the present invention is shown;

[0077] Figure 8 Showing according to Figure 2 A view of the power status of the refrigerant compressor in the first and second operating modes;

[0078] Figure 9 A view showing a second embodiment of a refrigerant compressor, whose structural principle corresponds to that of the first embodiment;

[0079] Figure 10 Showing according to Figure 9 A view of the power status of the refrigerant compressor in the first, second, and third operating modes;

[0080] Figure 11 A side view of a third embodiment of a refrigerant compressor according to the present invention is shown;

[0081] Figure 12 A front view of a third embodiment of a refrigerant compressor according to the present invention is shown;

[0082] Figure 13 Show along Figure 11 The cross-section of half of line 13-13 in the middle is staggered;

[0083] Figure 14 A longitudinal section is shown of a third embodiment of a refrigerant compressor according to the present invention;

[0084] Figure 15 This shows the passageway between the inlet and outlet chambers open, along... Figure 11 The cross section of line 15-15 in the middle;

[0085] Figure 16 This illustrates a similar situation when the connecting passage between the exhaust chamber and the intake chamber is closed. Figure 15 The cross section. Detailed Implementation

[0086] An embodiment of the refrigeration apparatus according to the invention, generally marked 10, includes a refrigerant compressor 12 and a pipeline 16 leading from a high-pressure connector 14 of the refrigerant compressor to a high-pressure side heat exchanger, generally marked 18, in which the compressed refrigerant condenses by dissipating heat to a radiator (e.g., circulating ambient air or other cooling medium).

[0087] Liquid refrigerant in line 20 flows from the high-pressure side heat exchanger 18 to the collector 22, where the liquid refrigerant is collected, and then flows from the collector through line 28 to the expansion valve 30 of the low-pressure side heat exchanger 32.

[0088] After the heat exchanger 32 on the low-pressure side, the vaporized refrigerant flows through the pipeline 34 to the low-pressure connector 36 of the refrigerant compressor 12.

[0089] like Figure 2As shown, the refrigerant compressor 12 according to the invention is constructed as a piston compressor and includes a compressor housing 40, in which, for example, two parallel cylinder groups 42a and 42b are provided, which are V-shaped relative to each other, wherein each cylinder group includes at least one, in particular two or more cylinder units 44.

[0090] Each of the cylinder units 44 is formed by a cylinder housing 46, and the piston 48 in the cylinder housing can oscillate in such a way that the piston 48 can be driven by a connecting rod 50, which itself is located on the eccentric wheel 52 of the eccentric wheel shaft 54 ​​or driven by a crankshaft, for example driven by a motor 60, which can be configured as a synchronous or asynchronous motor.

[0091] The cylinder housing 46 of each cylinder unit 44 is enclosed by a valve plate 56, on which a cylinder head 58 is arranged.

[0092] Here, the valve plate 56 preferably covers not only the cylinder housing 46 of one cylinder unit 44, but all the cylinder housings 46 of the corresponding cylinder group 42, and the cylinder head 58 also spans all the cylinder housings 46 of the corresponding cylinder group 42 in the same manner.

[0093] In addition, the compressor housing 40 also includes an inlet channel 62 connected to the low-pressure connector 36, which is integrated, for example, within the compressor housing 40.

[0094] As in Figure 3 As shown in the enlarged view, at least one cylinder bank 42 (each cylinder bank 42 in the figure) is assigned an integral mechanical power control unit marked 70, which is used to allow the refrigerant to enter the corresponding cylinder head 58 (and the cylinder head's inlet chamber 72 and through the valve plate 56) via the inlet channel 62, so as to activate the corresponding cylinder bank 42, or to interrupt the inlet flow, so as to deactivate the corresponding cylinder bank 42.

[0095] If the mechanical power control unit 70 is open (e.g.) Figure 3 As shown), the inlet flow 74 has the opportunity to enter the cylinder chamber 80 defined by the corresponding piston 48, cylinder housing 46 and valve plate 56 through the inlet 76 provided in valve plate 56 and the inlet valve 78 provided on valve plate 56, so that it is compressed by the oscillating motion of piston 48 in the cylinder chamber, thereby the outlet flow 86 is discharged from cylinder chamber 80 through outlet 82 and outlet valve 84 and enters outlet chamber 88 of cylinder head 58.

[0096] The mechanical power control unit 70 is configured, for example, as a servo valve, which is integrated in the cylinder head 58 and has a valve body 90, through which the inlet 92 of the inlet chamber 72 located in the valve plate 56 can be closed.

[0097] Furthermore, the valve body 90 is mounted on the shift piston 94, which is guided in the shift cylinder housing 96, so that the shift piston 94 moves toward the valve plate 56 by the pressure energy present in the shift cylinder chamber 98, so as to close the inlet 92 in the valve plate.

[0098] The shift cylinder unit 100, formed by the shift cylinder housing 96, the shift piston 94, and the shift cylinder chamber 98, is integrated into the cylinder head 58. Here, the shift cylinder unit can be controlled by a control valve 110, which includes a control piston 112 that can move electromagnetically, and a control valve seat 114 that can be closed by the control piston. The control piston 112 and the control valve seat 114 are configured to interrupt or release the connection between the high-pressure passage 116 leading to the outlet chamber 88 and the pressure supply passage 118 leading to the shift cylinder chamber 98 for the shift cylinder 100.

[0099] If the connection between the high-pressure passage 116 and the pressure supply passage 118 is released, then the shift cylinder chamber 98 is under the high pressure present in the discharge chamber 88, and the shift piston 94 thus moves toward the valve plate 56 and presses the valve body 90 against the valve plate to close the inlet 92 in the valve plate 56. Figure 4 ).

[0100] In this situation, the force acting on the shift piston 94 by the high pressure in the shift cylinder chamber 98 resists the force of the elastic accumulator 120, which is supported on the shift cylinder housing 96 on the one hand, and acts on the shift piston 94 in this way, causing the shift piston to move away from the valve plate 56, and the shift piston thus moves the valve body 90 to the position of the release inlet 92.

[0101] In particular, the shift piston 94 is equipped with a pressure relief passage 122, which leads from an opening toward the shift cylinder chamber 98 to... Figure 4 The outlet 124 shown leads to the inlet chamber 72 in the position where the valve body 90 and the shift piston 94 are closed at the inlet 92. Here, when the connection between the high-pressure passage 116 and the pressure supply passage 118 is interrupted, the pressure relief passage 124 causes a rapid drop in the pressure in the shift cylinder chamber 98, thus causing the shift piston 94, along with the valve body 90, to move to the position of the release inlet 92 under the action of the elastic accumulator 120. Figure 3 In the position shown.

[0102] Mechanical power control unit 70 can be powered by Figure 1 The operating status control device 130 shown is operated in such a way that the mechanical power control unit 70 can be turned off and on to activate or deactivate the corresponding cylinder groups 42a, 42b, and thus cause the refrigerant compressor 12 to operate in operating mode B, which defines the range of activation and deactivation of the cylinder groups 42.

[0103] In addition, the motor 60 can also be controlled by the operating state control device 130, especially by the frequency converter 132 that controls the motor 60, so that the motor can operate at variable speed and thereby achieve the necessary load state or partial power state when using the appropriate operating mode.

[0104] In addition, the operating status control device 130 detects the corresponding load status or partial power status of the refrigerant compressor 12, for example by measuring the suction pressure PS by means of the suction pressure sensor 134 arranged near or at the low-pressure connector 36 and by measuring the high pressure PH by means of the high pressure sensor 136 arranged near or at the high-pressure connector 14.

[0105] In addition, the power consumed by the motor 60 can also be detected by the inverter 132.

[0106] In addition, a power request signal LA is transmitted to the operating status control device 130. This power request signal is generated by the device control device 138, which detects the cooling power requested by the low-pressure side heat exchanger 32 for cooling the object 146 (e.g., a cooling chamber), for example by temperature sensors 142 and 144 assigned to the low-pressure side heat exchanger 32. These temperature sensors allow the detection of the temperature of the medium 148 flowing through the low-pressure side heat exchanger 32 and the object 146 (e.g., before and after the low-pressure side heat exchanger 32), and allow the comparison of the temperature with the required temperature of the medium 146.

[0107] The operation status control device 130 can adapt the cooling power of the refrigeration equipment 10 to the cooling power required by the object being cooled 146 (the required cooling power is preset by the power request signal LA). This is achieved on the one hand by selecting an appropriate operating mode B and on the other hand by adjusting the speed of the motor 60 by means of the frequency converter 132.

[0108] However, in this case, only the speed range limited by the design of motor 60 can be used for speed adjustment, and this speed range must also be considered when selecting an appropriate operating mode.

[0109] For example, the possible operating mode B under partial power conditions can be set as follows:

[0110] - The refrigerant compressor 12 operates as follows: all cylinder groups 42 are in an active state and are adapted to a partial power state only by adjusting the speed of the motor 12 by the frequency converter 132.

[0111] - The refrigerant compressor 12 operates as follows: it has activated and deactivated cylinder banks 42, and the speed of the motor 12 is adapted to the degree of activation and deactivated cylinder banks by means of the frequency converter 132.

[0112] - The refrigerant compressor 12 operates as follows: it has only one activated cylinder bank 42 and is adapted to partial power conditions by adjusting the speed of the motor 12 by a frequency converter.

[0113] In the first type of operating mode, the activation or deactivation of at least one of the cylinder groups 42a, 42b can be performed, for example, throughout the entire time period of the corresponding partial power state, such that, for example, during a specific time period when the partial power state is required to be at X% of the full load state, one cylinder group 42 is continuously deactivated and the refrigerant compressor 12 operates using the other activated cylinder group 42, and in addition, the motor speed is adjusted accordingly by the corresponding operation of the inverter 132.

[0114] Alternatively, in the second type of operating mode, at least one cylinder group 42a, 42b or two cylinder groups 42 can be activated or deactivated in a rhythmic manner during a period of partial power operation, and in addition, the speed of the motor 60 can be adjusted in an appropriate manner by controlling the frequency converter 132.

[0115] Therefore, the mechanical power control unit 70 can be powered by... Figure 1 The operating state control device 130 shown is operated such that the mechanical power control unit 70 is turned on and off within consecutive shift intervals S, wherein each shift interval S has an open interval O and a closed interval S. In the open interval, the valve body 90 is in its released position, allowing the inlet flow 74 to flow through the inlet 92 and activate the corresponding cylinder group 42. In the closed interval, the valve body 90 (as shown) is in its released position. Figure 4 (As shown) is in its closed position, preventing the inflow 74 from flowing through the inlet 92 and thus disabling the corresponding cylinder group 42.

[0116] During the duration of the corresponding shift interval SI, the durations of the open interval O and the closed interval S can now be variably adjusted relative to each other to specify the corresponding operating mode, such that either the open interval O is greater than the closed interval, or vice versa.

[0117] In extreme cases, the open interval O can extend for almost the entire duration of the shift interval SI, while the closed interval S becomes arbitrarily small, or vice versa, with the closed interval S extending for almost the entire duration of the shift interval SI, thus making the open interval O arbitrarily small.

[0118] Because the liquid refrigerant is continuously vaporized by the expansion valve 30 in the refrigeration device 10 according to the invention, the interruption of the compression of the refrigerant by the refrigerant compressor 12 causes the temperature T in the heat exchanger 32 on the low-pressure side to rise.

[0119] However, this system exhibits reactive inertia, meaning that when the refrigerant extraction from the low-pressure side heat exchanger 32 is interrupted, the temperature T of the low-pressure side heat exchanger 32 does not rise immediately, but rather gradually decreases. Figure 6 As shown, a duration Z is required to increase to the value D.

[0120] As long as the value D is less than the outlet temperature T of the heat exchanger on the low-pressure side... A If the fluctuation is 10%, then such fluctuation is irrelevant to the function of the refrigeration equipment according to the present invention.

[0121] For the reasons stated above, the shift interval SI is selected to be less than the duration Z. When the refrigerant extraction from the low-pressure side heat exchanger 32 is suddenly interrupted and the supply of the medium under high pressure at the high-pressure connector 14 is suddenly interrupted, the duration Z continues until the temperature T of the low-pressure side heat exchanger 32 drops from its previous value. A Start by increasing the value of D by approximately 10%, preferably approximately 5%.

[0122] Therefore, it is ensured that the opening interval O and closing interval S within the corresponding shift interval SI have little impact on the function of the refrigeration equipment, and only cause minor temperature fluctuations in the heat exchanger 32 on the low-pressure side of the refrigeration equipment according to the present invention.

[0123] The duration of the shift interval SI is typically less than approximately 10 seconds, preferably less than approximately 5 seconds.

[0124] On the other hand, in order to ensure a sufficient opening range O, the shift range is longer than about 1 second, preferably longer than 2 seconds.

[0125] The preferred operating range provides shift intervals SI with a duration between 2 and 10 seconds.

[0126] To ensure such a short shift interval SI, it is preferable to set the shift piston 94 together with the valve body 90 and the elastic accumulator 120 to have a natural frequency that is higher than the frequency corresponding to the maximum shift interval SI, so that the shift piston 94 can realize the opening interval O and the closing interval S with essentially no delay within the shift interval SI.

[0127] The natural frequency of the system consisting of the shift piston 94, the valve body 90 and the elastic accumulator 120 is preferably at least 5 times or preferably at least 10 times higher than the frequency corresponding to the shift interval SI.

[0128] In addition, the operating status control device 130 can identify or detect the relative efficiency or COP of the refrigerant compressor 12 in the corresponding operating mode and in the corresponding load state or partial power state, wherein the relative efficiency or COP depends in particular on the refrigerant used, the speed of the motor 60, the number of activated cylinder groups 42 and the ratio of high pressure PH to suction pressure PS.

[0129] In the case of accurate calculations, relative efficiency or COP is determined, for example, based on the content of publications such as:

[0130] Refrigeration compressors and condensing units - performance testing and test methods - Part 1, refrigerant compressors

[0131] Especially Chapter 4.1.5.2 and, for example, Formula 7 of the European Standard.

[0132] CEN / TC 113, date 2014-04, prEN 13 771-1:2014.

[0133] Therefore, with the help of the operating state control device 130, it is possible in the refrigerant compressor 12 to optimize the operation of the refrigerant compressor 12 in the partial power state when multiple operating modes are provided in order to realize the partial power state required by the power request signal, taking into account the highest possible efficiency (expressed as the highest possible relative efficiency or COP or the lowest possible power consumption of the motor 60), and to optimize by selecting an appropriate operating mode of the refrigerant compressor 12, and to control or adjust the speed of the motor 60 in this partial power state to be suitable for the corresponding operating mode by operating the inverter 132, so as to perform operation in the preset partial power state.

[0134] The electrical power consumption for relative efficiency or COP, or the corresponding possible operating mode B, can be considered or determined in advance, or it can be considered or determined by querying data determined in advance during test operation and stored in the operating state control device 130 while the refrigerant compressor 12 is running continuously. For this purpose, relative efficiency or COP or electrical power consumption is assigned to the corresponding possible operating mode B for this partial power state, or a set of corresponding possible operating modes B for a set of possible partial power states. Thus, the operating state control device 130 can select the operating mode B with the most advantageous relative efficiency or COP or the lowest electrical power consumption for the partial power state requested by the power request signal LA, and can operate the refrigerant compressor 12 according to this operating mode B.

[0135] Another possibility is to operate the refrigerant compressor 12 in a possible operating mode B under the corresponding partial power state, and detect the power consumed by the motor 60 in each operating state, so that the operating state control device 130 can then evaluate the operating mode B with the lowest power consumption as the highest efficiency, and can store the operating mode, and can use the operating mode B as the operating mode with the highest efficiency only in the future for that partial power state.

[0136] exist Figure 7 The diagram shows the operating mode B, which is selected by the operating status control device 130.

[0137] First, when the operating status control device 130 receives a power request LA, it checks whether only one operating mode B or multiple operating modes B are provided to fulfill the power request LA.

[0138] In partial power conditions close to the maximum power of the refrigerant compressor 12, only one operating mode Bx is typically provided, in which all cylinder groups 42 are fully activated and the partial power condition is adapted by adjusting the speed of the drive motor 60.

[0139] In partial power conditions within the medium or low power range, multiple operating modes By to Bz are typically available, depending on the number of cylinder groups 42 and whether the refrigerant compressor 12 can operate in the first type of operating mode and / or the second type of operating mode.

[0140] Next, for these operating modes, the speed of motor 60 necessary to achieve the required partial power state is determined, and then relative efficiency or COP or power consumption is considered or determined based on this in the manner and method described above.

[0141] By using the relative efficiency, COP, or power consumption assigned to the corresponding operating modes By to Bz, an operating mode with the best relative efficiency, COP, or lowest power consumption can be selected. Then, the operating state control device 130 applies this operating mode to the operation of the refrigerant compressor 12 in order to achieve the partial state required by the power request signal LA.

[0142] The general operating mode previously described can then be elaborated in detail using an example of the refrigerant compressor 12 described at the beginning, with the aid of a simplified operating mode for determining relative efficiency or COP or electrical power consumption.

[0143] In the refrigerant compressor with two cylinder groups 42a and 42b according to the first embodiment, under partial power conditions, limited to the first type of operating mode, only the following possibilities exist: the refrigerant compressor is operated in a first operating mode B1 with both cylinder groups 42a and 42b in an active state, or the refrigerant compressor is operated in a second operating mode B2, in which only one cylinder group of cylinder groups 42a and 42b is activated and the other is deactivated. Figure 8 As shown.

[0144] In each of the operating modes B1 and B2, the speed of the motor 60 can be changed by means of the frequency converter 132, for example, between 25Hz and 70Hz.

[0145] Because all cylinder groups 42a and 42b must be active in partial power conditions exceeding 50%, these can only be achieved in operating mode B1. Furthermore, partial power conditions below 35% can be achieved by disabling one of the cylinder groups 42a and 42b, thus allowing optimization to be made only in partial power conditions between 35% and 50% by considering relative efficiency or COP, since the refrigerant compressor 12 can operate in either the first operating mode B1 or the second operating mode B2 in partial power conditions between 35% and 50%.

[0146] Therefore, the choice between the first operating mode B1 and the second operating mode B2 can be achieved by determining the relative efficiency or COP of the operating mode.

[0147] In order to simplify the consideration of relative efficiency or COP or power consumption, for example, the possible partial power states between 35% and 70% will be divided into two groups, or more precisely, in the simplest case, depending on the high voltage PH detected by the high voltage sensor 136.

[0148] For example, under a certain refrigerant, if the high pressure pH is greater than the high pressure threshold PHG, then operation mode B2 is selected; if the high pressure pH is lower than the threshold PHG, then operation mode B1 is selected.

[0149] Under the first type of operating modes B1 and B2, the corresponding cylinder groups are continuously activated or deactivated, and this is done throughout the entire time of achieving partial power state.

[0150] However, based on the fact that a second type of operating mode can be achieved in the same way (where the activation or deactivation of the corresponding cylinder group 42 can be proportionally performed over time during the continuous shift interval SI), the first embodiment of the refrigerant compressor according to the invention provides the following possibility: for example, in the case of selecting only one cylinder group 42, by cyclically activating and deactivating this cylinder group 42 in the shift interval SI, for example, at a ratio of 1:1, and deactivating the other cylinder group 42, operating mode B2' is selected, in which even a lower partial power state may occur, for example, in the partial power range between 17% and 25%; similarly, considering relative efficiency or COP, the operation of the refrigerant compressor 12 is optimized by selecting between operating state B2 or operating state B2', for example, operating mode B2' is selected when the high pressure PH is higher than the high pressure threshold PHG, and operating mode B2 is selected when the high pressure PH is lower than the threshold PHG.

[0151] However, depending on the refrigerant used, these relationships can also be reversed.

[0152] If a refrigerant compressor 12' with three cylinder groups 42a, 42b and 42c is used according to the second embodiment ( Figure 9 For example, each cylinder bank 42 has two cylinders, wherein each of the cylinder banks 42a, 42b, and 42c can be individually activated or deactivated by means of an associated mechanical power control unit 70. Figure 10 As shown, there can be three operating modes B1, B2, and B3: the first operating mode B1 in which all cylinder groups 42a, 42b, and 42c are in an active state; the second operating mode B2 in which two cylinder groups 42 are in an active state; and the third operating mode in which only one cylinder group 42 is in an active state.

[0153] Regarding the specific structure, the second embodiment corresponds to the first embodiment.

[0154] In this embodiment, there is a possibility of selecting between operating modes B1 and B2 when the partial power state is in the range of 35% to 65%, and there is a possibility of selecting between operating modes B2 and B3 when the partial power state is in the range of 23% to 33%.

[0155] Similarly, in the second embodiment, for the purpose of simplifying the determination of the relative efficiency of the operating mode, the power states are divided into two groups by setting a high voltage threshold PHG. When the high voltage PH is higher than the high voltage threshold PHG, operating mode B2 is selected when choosing between operating modes B1 and B2, and operating mode B3 is selected when choosing between operating modes B2 and B3. When the high voltage PH is lower than the high voltage threshold PHG, operating mode B1 is selected when choosing between operating modes B1 and B2, and operating mode B2 is selected when choosing between operating modes B2 and B3.

[0156] Furthermore, the maximum partial power state can be achieved using operating mode B1 in the same manner as in the first embodiment, and the minimum partial power state can be achieved using operating mode B3 and by adjusting the speed of motor 60 accordingly.

[0157] The third embodiment of the refrigerant compressor 12” is particularly suitable for the case where CO2 is used as the refrigerant, and the refrigerant compressor includes a high-pressure connector 14” and a low-pressure connector 36”.

[0158] like Figure 13 As shown, the refrigerant compressor 12” is constructed as a reciprocating compressor and includes a compressor housing 40”, in which, for example, two parallel cylinder groups 42”a and 42”b are provided, which are V-shaped relative to each other, wherein each cylinder group includes at least one, in particular two or more cylinder units 44”.

[0159] Each of the cylinder units 44” is formed by a cylinder housing 46”, and the piston 48” in the cylinder housing can oscillate in such a way that the piston 48” can be driven by a connecting rod 50”, the connecting rod itself being located on the eccentric wheel 52” of the eccentric wheel shaft 54”, which is driven, for example, by a motor 60” that can be configured as a synchronous or asynchronous motor.

[0160] The cylinder housing 46” of each cylinder unit 44” is closed by a valve plate 56”, on which a cylinder head 58 is arranged.

[0161] Here, the valve plate 56” preferably does not cover only the cylinder housing 46” of one cylinder group 42”, but covers all the cylinder housings 46” of the corresponding cylinder group 42”, and the cylinder head 58” also spans all the cylinder housings 46” of the corresponding cylinder group 42” in the same way.

[0162] In addition, the compressor housing 40” also includes an inlet channel 62” connected to the low-pressure connector 36”, which is integrated, for example, in the compressor housing 40”.

[0163] like Figure 15 and Figure 16As shown, each of the cylinder heads 42”a and 42”b is provided with an inlet chamber 162 and an outlet chamber 164, which are allocated to two cylinder units 44 of the corresponding cylinder group 42”.

[0164] The entrance chamber 162 is located above the inlet 172 of the cylinder unit 44” of the cylinder group 42”.

[0165] Furthermore, the discharge chamber 164 is located above the discharge port 174 of the cylinder unit 44” located in the valve plate 56”, the discharge port 174 is provided with a discharge valve 176 located on the valve plate 56”, and the discharge chamber 164 is particularly directly adjacent to the discharge valve.

[0166] like Figure 15 and Figure 16 As shown, each cylinder head 42” includes an outer shell 182 that extends over a corresponding valve plate 56” and surrounds an inlet chamber 162 and an outlet chamber 164, which are themselves separated from each other by a partition 184 extending within the outer shell 182, wherein the partition 184 protrudes from the corresponding valve plate 56” and extends through and across the inlet chamber 162.

[0167] Therefore, in the region of valve plate 56", the discharge chamber 164 is located next to the side of the inlet chamber 162, but extends at least partially over the inlet chamber 162 between the outer casing 182 and the partition 184.

[0168] In order to control the operating status of the refrigerant compressor 12”, that is, to control the operating status of the compressor delivery efficiency, a mechanical power control unit 70” is assigned to each cylinder head 58”, which is actively operated by the operating status control device 130. The mechanical power control unit can close or open the connection channel 192 between the discharge chamber 164 and the inlet chamber 162. The cylinder unit 44” associated with the cylinder head 58” is closed when the connection channel 192 is closed. Figure 16 The refrigerant is compressed at full power and not compressed when the connection channel 192 is open, because the refrigerant flows back from the discharge chamber 164 to the inlet chamber 162.

[0169] Here, the connecting channel 192 extends through an insert 194 disposed in the partition 184, the insert forming a sealing seat 196 facing the discharge chamber 164 and adjacent to the portion of the discharge chamber 164 that surrounds the sealing seat 196 and is connected to the sealing seat.

[0170] Furthermore, the sealing seat 196 faces the sealing piston 202, which can be placed on the sealing seat 196, for example, using a sealing area 204 made of metal, to seal the connection channel 192. The sealing piston can also be lifted a certain distance from the sealing seat 192, so that the sealing area 204 is spaced apart from the sealing seat 196, thereby allowing refrigerant to flow from the discharge chamber 162 into the inlet chamber 164.

[0171] Preferably, the closed piston 202 is coaxial with the insert 194 having a sealing seat 196 and is guided in a sealed manner in a guide hole 208 by means of piston rings 206, which is formed by a guide sleeve body 212 molded on the outer casing 182 of the cylinder head 58".

[0172] Preferably, the closed piston 202 itself or at least the sealing region 204 is made of metal, such as a non-ferrous metal, the hardness of which is lower than that of the metal of the sealing seat 196, the sealing seat being made of steel, especially hardened steel.

[0173] In order to achieve rapid movement of the closed piston 202, the stroke of the closed piston 202 between the closed and open positions is particularly within the range of one-quarter to one-half of the average diameter of the connecting channel 192.

[0174] Here, the sealing piston 202 defines a pressure chamber 214, which is located on the side of the sealing piston 202 opposite to the sealing area 204 and is closed on the side opposite to the sealing piston 202 by a sealing body 216.

[0175] The volume of pressure chamber 214 is particularly small, being less than one-third, preferably less than one-quarter, more preferably less than one-fifth, even more preferably less than one-sixth, and still preferably less than one-eighth of the maximum volume of pressure chamber 214 when the closed piston is in the open position, and when the closed piston 202 is in the closed position.

[0176] In addition, a pressure spring 218 is provided in the pressure chamber 214, which supports the closed body 216 on one hand and acts on the closed piston 202 in the direction of its closed position on the sealing seat 196 on the other hand.

[0177] Based on the pressure loading in pressure chamber 214, the closed piston 202 can move to... Figure 15 The opening position shown is in or Figure 16 As shown in its closed position.

[0178] For this purpose, the closed piston 202 is penetrated by a throttling channel 222 that extends from the pressure chamber 214 through the closed piston 202 to a port that is radially located outside the sealing area on the side facing the sealing seat 196. However, since it is radially located outside the sealing area 204, in the closed position of the closed piston 202, the port allows refrigerant under pressure in the discharge chamber 164 and circulating through the sealing seat 196 to enter and deliver refrigerant to the pressure chamber 214 in a throttling manner.

[0179] In addition, the pressure relief passage 224 is directed to the pressure chamber 214, or more precisely, for example, through the enclosure 216. This pressure relief passage can be connected to the pressure reducing passage 228 via a solenoid valve marked integrally with 226, which is connected to the inlet chamber 162.

[0180] Solenoid valve 226 is configured, for example, to have valve body 232, which allows the connection between pressure reducing channel 228 and pressure relief channel 224 to be interrupted or established.

[0181] If a connection is established between the pressure relief passage 224 and the pressure reduction passage 228, the pressure chamber 214 is mainly filled with suction pressure, while the closed piston 202 is subjected to the pressure in the discharge chamber 64 on its side facing the discharge chamber 164 and thus moves to its open position.

[0182] However, if the connection between the pressure reducing channel 228 and the pressure relief channel 224 is interrupted by the valve body 232, the pressure spring 218 will press the closed piston 202 against the sealing seat 196 and the high pressure will also flow into the pressure chamber 214 through the throttling channel 222, thereby creating high pressure in the pressure chamber 214. In addition to the action of the compression spring 218, this high pressure will also press the closed piston 202 together with the sealing element 204 against the sealing seat 196.

[0183] If the valve body 232 of the solenoid valve 226 establishes a connection between the pressure relief passage 224 and the pressure reducing passage 228 (which causes a suction pressure in the pressure chamber 214), then the closing piston 202 is specifically configured to extend radially beyond the sealing seat 196, so that even if the closing piston 202 is in the closed position, the piston surface radially outside the sealing seat 196 and subjected to high pressure will cause the closing piston 202 to move against the force of the pressure spring 218 to the open position. Figure 15 As shown),

[0184] The refrigerant under suction pressure is delivered through a delivery channel 62” recessed in the compressor housing 40”, which leads to an inlet leading to the valve plate 56”. The refrigerant under suction pressure flows through this inlet to the through hole 236 in the valve plate 56” and is transferred to the inlet chamber 162 through the through hole.

[0185] In addition, such as Figure 15 and Figure 16 As shown, the discharge chamber 164 is directed to the discharge port 242 located in the valve plate 56”, through which the refrigerant under pressure in the discharge chamber 164 is transferred to the discharge passage 244 located in the compressor housing and can flow to the high-pressure connector 16”.

[0186] In particular, a check valve 246 is provided for the outlet 244 of the valve plate 56”. This check valve is held on the valve plate 56” and ensures that the pressure in the outlet passage 244 does not drop when the closed piston 202 is in the open position and when refrigerant flows from the outlet chamber 164 into the inlet chamber 162, but is maintained by the closed check valve 246.

[0187] The third embodiment of the refrigerant compressor 12” can operate in the same manner as the first embodiment, so that its operation in operating modes B1, B2 and B2' can be fully referred to the description of the first embodiment.

Claims

1. A refrigerant compressor (12) for a refrigeration device (10), comprising an electric motor (60), at least two cylinder banks (42), and cylinder heads (58) assigned to each cylinder bank (42) and a mechanical power control unit (70), wherein, Each cylinder bank has at least one cylinder unit (44), each cylinder unit having at least one cylinder housing (46) and at least one piston (48) driven by an electric motor (60) and capable of oscillating motion. The cylinder head has an inlet chamber (72, 162) through which an inlet flow (74) flows and an outlet chamber (88, 164) through which an outlet flow (86) flows. The mechanical power control unit is used to activate and deactivate at least one cylinder bank (42) in order to activate or deactivate the refrigerant discharge of the cylinder bank. The refrigerant compressor (12) is characterized in that it can operate in at least two different operating modes in order to operate in multiple partial power states, wherein each operating mode is configured to activate or deactivate the cylinder group (42) differently from other operating modes (B), a frequency converter (132) for speed control of the motor (60) is assigned to the refrigerant compressor (12), an operating state control device (130) is assigned to the refrigerant compressor (12), and the operating state control device causes the refrigerant compressor (12) to operate in an operating mode (B) selected from at least two different operating modes (B) in order to operate the refrigerant compressor (12) in a partial power state that conforms to the power request signal (LA) input to the operating state control device. The motor (60) operates at a speed adapted to the selected operating mode (B) to achieve this partial power state. In order to determine the relative efficiency or COP of the operating mode, the partial power state to be achieved is divided into partial power states above the threshold (PHG) and partial power states below the threshold (PHG). In the partial power state above the threshold (PHG), and in the operating mode (B) at the higher speed of the required motor (60), higher relative efficiency or higher COP or lower power consumption is accepted and therefore these operating modes are selected. In the partial power state below the threshold (PHG), and in the operating mode at the lower speed of the required motor (60), higher relative efficiency or higher COP or lower power consumption is accepted and therefore these operating modes are selected.

2. The refrigerant compressor according to claim 1, characterized in that, The operating status control device (130) causes the refrigerant compressor (12) to operate in the first operating mode (B1), accompanied by the activation of all cylinder groups (42) and the adaptation of the motor (60) speed to the first operating mode (B1).

3. The refrigerant compressor according to claim 1, characterized in that, The operating status control device causes the refrigerant compressor (12) to operate in at least one additional operating mode (B), wherein at least one cylinder group (42) is deactivated and at least one cylinder group (42) is activated and the speed of the motor (60) is adapted to the at least one additional operating mode (B).

4. The refrigerant compressor according to claim 2, characterized in that, The operating status control device causes the refrigerant compressor (12) to operate in at least one additional operating mode (B), wherein at least one cylinder group (42) is deactivated and at least one cylinder group (42) is activated and the speed of the motor (60) is adapted to the at least one additional operating mode (B).

5. The refrigerant compressor according to claim 1, characterized in that, The operating state control device (130) selects an operating mode (B) that can be achieved by a variety of operating modes (B) in a partial power state, which achieves the highest relative efficiency or the highest COP or the lowest power consumption of the motor (60) in that partial power state.

6. The refrigerant compressor according to claim 4, characterized in that, The operating state control device (130) selects an operating mode (B) that can be achieved by a variety of operating modes (B) in a partial power state, which achieves the highest relative efficiency or the highest COP or the lowest power consumption of the motor (60) in that partial power state.

7. The refrigerant compressor according to claim 5, characterized in that, The operating state control device (130) determines the relative efficiency or COP or the electrical power consumption of the motor (60) for each possible operating mode (B) to achieve a partial power state, and selects the operating mode (B) by comparing the determined relative efficiency or COP or electrical power consumption.

8. The refrigerant compressor according to claim 6, characterized in that, The operating state control device (130) determines the relative efficiency or COP or the electrical power consumption of the motor (60) for each possible operating mode (B) to achieve a partial power state, and selects the operating mode (B) by comparing the determined relative efficiency or COP or electrical power consumption.

9. The refrigerant compressor according to any one of claims 5 to 8, characterized in that, The operating status control device (130) has stored data to determine the relative efficiency or COP or power consumption for each operating mode (B).

10. The refrigerant compressor according to claim 5, characterized in that, The relative efficiency or COP or power consumption is determined by the operating status control device (130) by detecting the suction pressure (PS) and / or the high pressure (PH) at the refrigerant compressor (12).

11. The refrigerant compressor according to claim 9, characterized in that, The relative efficiency or COP or power consumption is determined by the operating status control device (130) by detecting the suction pressure (PS) and / or the high pressure (PH) at the refrigerant compressor (12).

12. The refrigerant compressor according to claim 5, characterized in that, The operating status control device (130) takes into account the refrigerant, partial power status, power consumption and / or speed of the motor (60) to determine the relative efficiency or COP or electrical power consumption.

13. The refrigerant compressor according to claim 11, characterized in that, The operating status control device (130) takes into account the refrigerant, partial power status, power consumption and / or speed of the motor (60) to determine the relative efficiency or COP or electrical power consumption.

14. The refrigerant compressor according to claim 1, characterized in that, The operating state control device (130) continuously maintains a fixed predetermined deactivation and activation operating mode (B) with cylinder group (42) in the first type of operating mode to achieve the partial power state required by the power request signal (LA).

15. The refrigerant compressor according to claim 13, characterized in that, The operating state control device (130) continuously maintains a fixed predetermined deactivation and activation operating mode (B) with cylinder group (42) in the first type of operating mode to achieve the partial power state required by the power request signal (LA).

16. The refrigerant compressor according to claim 1, characterized in that, The operating status control device (130) causes the refrigerant compressor (12) to operate in at least one operating mode (B) corresponding to the second type of operating mode by activating and deactivating at least one cylinder group (42) in a defined shift interval (SI).

17. The refrigerant compressor according to claim 15, characterized in that, The operating status control device (130) causes the refrigerant compressor (12) to operate in at least one operating mode (B) corresponding to the second type of operating mode by activating and deactivating at least one cylinder group (42) in a defined shift interval (SI).

18. The refrigerant compressor according to claim 1, characterized in that, The activation and deactivation of each cylinder group (42) are carried out by means of a mechanical power control unit (70) controlled by an operating status control device (130).

19. The refrigerant compressor according to claim 17, characterized in that, The activation and deactivation of each cylinder group (42) are carried out by means of a mechanical power control unit (70) controlled by an operating status control device (130).

20. The refrigerant compressor according to claim 18, characterized in that, The mechanical power control unit (70) is assigned to the cylinder head (58) of the cylinder group (42).

21. The refrigerant compressor according to claim 19, characterized in that, The mechanical power control unit (70) is assigned to the cylinder head (58) of the cylinder group (42).

22. The refrigerant compressor according to any one of claims 18 to 21, characterized in that, The mechanical power control unit (70) controls the inlet flow (74) into the inlet chamber (72) of the cylinder head (58) for the activation or deactivation of the corresponding cylinder group (42).

23. The refrigerant compressor according to claim 1, characterized in that, The power control unit (70) connects the exhaust chamber (164) and the intake chamber (162) in the cylinder head (58) for the activation or deactivation of the corresponding cylinder group (42').

24. The refrigerant compressor according to claim 22, characterized in that, The power control unit (70) connects the exhaust chamber (164) and the intake chamber (162) in the cylinder head (58) for the activation or deactivation of the corresponding cylinder group (42').

25. The refrigerant compressor according to claim 1, characterized in that, The operation status control device (130) is a separate operation status control device from the frequency converter (132).

26. The refrigerant compressor according to claim 24, characterized in that, The operation status control device (130) is a separate operation status control device from the frequency converter (132).

27. The refrigerant compressor according to claim 1, characterized in that, The operating status control device (130) is arranged in the housing (40) that houses the frequency converter (132).

28. The refrigerant compressor according to claim 26, characterized in that, The operating status control device (130) is arranged in the housing (40) that houses the frequency converter (132).

29. The refrigerant compressor according to claim 1, characterized in that, The cylinder groups (42) of the refrigerant compressor (12) operate in parallel.

30. The refrigerant compressor according to claim 28, characterized in that, The cylinder groups (42) of the refrigerant compressor (12) operate in parallel.

31. The refrigerant compressor according to claim 1, characterized in that, Each cylinder group (42) of the refrigerant compressor (12) has at least two cylinder units (44).

32. The refrigerant compressor according to claim 30, characterized in that, Each cylinder group (42) of the refrigerant compressor (12) has at least two cylinder units (44).

33. The refrigerant compressor according to claim 1, characterized in that, The refrigerant compressor (12) has more than two cylinder groups (42).

34. The refrigerant compressor according to claim 32, characterized in that, The refrigerant compressor (12) has more than two cylinder groups (42).

35. The refrigerant compressor according to claim 16 or 17, characterized in that, In the at least one operating mode (B) corresponding to the second type of operating mode, when the corresponding partial power state is achieved, the deactivation and activation of at least one cylinder bank (42) in a proportional manner within the shift interval (SI) is constant.

36. A refrigeration device, comprising a refrigerant compressor (12), a high-pressure side heat exchanger (18), an expansion mechanism (30), and a low-pressure side heat exchanger (32), characterized in that, The refrigerant compressor (12) is a refrigerant compressor according to any one of claims 1 to 35.

37. The refrigeration equipment according to claim 36, characterized in that, The refrigeration equipment (10) has an equipment control device (138) that generates a power request signal (LA).

38. The refrigeration equipment according to claim 37, characterized in that, The operating status control device (130) is arranged in the housing of the equipment control device (138).

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