Air conditioning compression system and air conditioner

Abstract

The application provides an air conditioner compression system and an air conditioner. The air conditioner compression system comprises a compressor, a first heat exchanger, a throttling device and a second heat exchanger connected in sequence, the compressor comprises a roller and a sliding vane, and the head of the sliding vane cooperates with the outer peripheral part of the roller under the pressure difference between the suction port and the exhaust port of the compressor; further comprising a pressure maintaining valve arranged in the exhaust passage connected with the exhaust port; and / or further comprising a pressure reducing valve arranged in the suction passage connected with the suction port. The air conditioner comprises the above air conditioner compression system. Through the arrangement of the pressure reducing valve, the suction side pressure reduction is realized, and / or through the arrangement of the pressure maintaining valve, the exhaust side pressure maintaining is realized, so that the separation of the sliding vane 113 from the surface of the roller caused by the too low pressure difference ΔP=P1-P2 of the sliding vane 113 driven can be avoided, and then the impact noise of the compressor during the low frequency operation is reduced.

Description

Technical Field

[0001] This invention relates to the field of air conditioning equipment technology, specifically to an air conditioning compression system and air conditioner that improves the low-frequency impact noise of the compressor. Background Technology

[0002] See Figure 1 The existing air conditioning compressor system includes at least a compressor 11, a first heat exchanger 12, a throttling device 13, and a second heat exchanger 14 connected in sequence. Other existing air conditioning compressor systems also include a four-way valve, which allows switching between cooling and heating modes.

[0003] See Figure 1 and Figure 2 The compressor 11 is a rolling rotor compressor, which includes a cylinder 111, rollers 112, and vanes 113. A compression chamber 110 is located in the center of the cylinder 111. The rollers 112 rotate eccentrically within the compression chamber 110 under the drive of the crankshaft, and the rollers 112 maintain a fit with the inner wall surface of the cylinder 111. The cylinder 111 also has a sliding groove 1103 and a groove bottom hole 1104 located on the outer periphery of the compression chamber 110. The sliding groove 1103 extends radially along the compression chamber 110 and passes through the space between the compression chamber 110 and the groove bottom hole 1104. The vanes 113 are slidably mounted in the sliding groove 1103 radially along the compression chamber 110.

[0004] The pressure difference between the head and tail ends of the vane 113 causes the head 113a of the vane 113 to abut against the outer periphery of the roller 112, thereby allowing the compression chamber 110 to be divided into a relatively independent intake side 1101 and an exhaust side 1102. The intake side 1101 is connected to the intake port 1108 of the cylinder 111, and the exhaust side 1102 is connected to the exhaust port of the cylinder 111. The refrigerant is drawn into the intake side 1101 from the intake port, and is pressurized under the operation of the roller 112 to reach the exhaust side 1102 and be sent out from the exhaust port.

[0005] In this process, the high-pressure gas inside the compressor cylinder pushes open the valve plate on the flange, exits the cylinder body 111, and reaches the compressor cavity (inside the housing). The slot bottom hole 1104 is not sealed, and at this time, the gas pressure in the slot bottom hole 1104 is the same as the high-pressure gas pressure inside the compressor cavity. The slot bottom hole 1104 is connected to the exhaust side of the compression chamber 110 through the airflow channel. Assuming that the gas pressure on the exhaust side and the exhaust port is the first pressure P1, then the pressure in the slot bottom hole 1104 and the pressure acting on the tail 113b of the sliding vane 113 is also the first pressure P1; while the pressure on the suction side 1101 and the head 113a of the sliding vane 113 is the second pressure P2. The sliding vane 113 runs in close contact with the roller 112 under the action of the pressure difference ΔP=P1-P2.

[0006] As a core power component of residential air conditioning systems, the operating noise level of the rotary compressor directly determines user comfort. With the widespread adoption and deepening of inverter technology in the air conditioning field, the proportion of compressor operation under low-frequency conditions has significantly increased. However, a problem with existing air conditioning compressor systems is that during low-frequency operation, the contact force between the vane 113 and the roller 112 is insufficient, causing them to periodically separate and collide during movement. The vibration generated by the collision is transmitted and forms noise. Summary of the Invention

[0007] The primary objective of this invention is to provide an air conditioning compression system that reduces impact noise during low-frequency operation of the compressor.

[0008] The second objective of this invention is to provide an air conditioner that reduces impact noise when the compressor is operating at low frequencies.

[0009] The air conditioning compression system provided by the first objective of this invention includes a compressor, a first heat exchanger, a throttling device, and a second heat exchanger connected in sequence. The compressor includes rollers and vanes. Under the pressure difference between the compressor's intake port and exhaust port, the head of the vane cooperates with the outer periphery of the roller. The system also includes a pressure holding valve, which is disposed in an exhaust passage connected to the exhaust port. And / or, the system also includes a pressure reducing valve, which is disposed in an intake passage connected to the intake port.

[0010] A further option is to use an overflow valve or a back pressure valve for the pressure holding valve.

[0011] As can be seen from the above scheme, the present invention achieves suction-side pressure reduction by setting a pressure reducing valve, and / or achieves discharge-side pressure maintenance by setting a pressure maintaining valve. This configuration can prevent the pressure difference ΔP=P1-P2 on the driving vane 113 from being too low, which would cause the vane 113 to separate from the roller surface. In particular, the dual effect of suction-side pressure reduction and discharge-side pressure maintenance significantly improves the adhesion force between the vane and the roller, suppresses periodic detachment impacts, and reduces the "clicking" noise. In addition, the modular valve integration design eliminates the need to modify core components such as cylinders, vanes, and rollers, and can be directly adapted to existing compressor housings and piping systems, reducing design and modification costs and making mass production feasible. Furthermore, under medium- and high-frequency operating conditions, the suction-side pressure reducing valve is automatically in a fully open state, with no additional flow resistance loss, ensuring suction efficiency, while the discharge-side pressure maintaining valve automatically opens after the pressure reaches the set value, ensuring smooth discharge. Therefore, the addition of the pressure reducing valve and the pressure maintaining valve has little impact on compressor performance.

[0012] A further option is to use a direct-acting pneumatic pressure reducing valve for the pressure reducing valve, and an overflow valve for the pressure holding valve, wherein the overflow valve is a pneumatic overflow valve.

[0013] As can be seen from the above, in this configuration, a direct-acting pressure reducing valve is installed in the suction channel before the compressor distributor. This valve consists of a diaphragm, a spring, and a valve port. The diaphragm senses changes in suction pressure and automatically adjusts the valve opening. When the suction pressure increases, the diaphragm moves upward, and excess gas is discharged through the overflow port; when the suction pressure decreases, the diaphragm moves downward, increasing the valve opening to compensate for the flow and ensure that the suction pressure remains stable at the set value. During low-frequency operation, this pressure reducing valve actively reduces the suction pressure, thereby increasing the suction and discharge pressure difference, enhancing the gas pressure on the back of the vane, and making the vane fit more tightly against the roller. A pneumatic relief valve is installed in the compressor discharge channel, and the stiffness of the pressure regulating spring is set so that the valve remains closed under low-frequency conditions, maintaining a high-pressure environment inside the compressor, thereby enhancing the pressure on the back of the vane and improving the fit. When the compressor frequency increases and the discharge pressure reaches the set value, the gas thrust overcomes the spring force, causing the valve to open automatically, restoring the normal discharge process and preventing excessive internal pressure from affecting compression efficiency. Mainly, this setup achieves dynamic control of the contact state between the slide and the roller through optimized mechanical structure design, reducing low-frequency abnormal noise while maintaining high-frequency operating performance unaffected, and has good prospects for engineering applications.

[0014] Another further option is to use a proportional pressure reducing valve for the pressure reducing valve and a relief valve for the pressure holding valve, with the relief valve being an electromagnetically controlled relief valve.

[0015] As can be seen from the above, the combination of a proportional control pressure reducing valve and an electromagnetic control relief valve achieves active regulation of the suction and discharge pressures. In this setup, the suction side uses a proportional pressure reducing valve, which adjusts the suction pressure setpoint in real time according to the compressor's operating frequency via an external controller to achieve precise control of the suction and discharge pressure difference. The discharge side uses an electromagnetic control relief valve, whose opening and closing are controlled by the controller based on the discharge pressure feedback signal to dynamically maintain the compressor's internal pressure. Although this setup introduces an electronic control system, it offers higher adjustment accuracy and response speed, adapting to more complex and variable operating conditions. It is suitable for high-end variable frequency air conditioning systems, further enhancing noise reduction.

[0016] Another further option is to use a pilot-operated pressure reducing valve and a back pressure valve for maintaining pressure.

[0017] As can be seen from the above, the combination of a pilot-operated pressure reducing valve and a back pressure valve can improve the accuracy and stability of pressure control. The pilot-operated pressure reducing valve controls the main valve's operation through a pilot valve, achieving a pressure reduction accuracy far superior to a direct-acting pressure reducing valve. When the system's intake pressure experiences instantaneous fluctuations, the pilot valve can respond quickly, controlling the main valve opening to offset the pressure fluctuations and preventing instantaneous attenuation of the slide plate's contact force. The back pressure valve achieves its pressure-holding function through a preset back pressure value. Unlike the overpressure opening logic of a relief valve, the back pressure valve can actively limit the exhaust flow when the exhaust pressure is lower than the preset value, quickly establishing a stable back pressure. When the exhaust pressure is higher than the preset value, the valve opens fully without obstructing exhaust. Furthermore, the back pressure valve's built-in damping structure slows down the valve core's movement, preventing pressure surges during operating condition changes and further reducing instantaneous noise.

[0018] Another further option is to connect at least two pressure-reducing valves in series between the second heat exchanger and the suction port.

[0019] As can be seen from the above, the intake side uses two or more pressure reducing valves for pressure regulation. By using multiple pressure reducing valves to reduce pressure in stages, the accuracy of intake pressure control is improved and pressure fluctuations are reduced.

[0020] Another further solution includes a reversing valve, through which the air conditioning compression system switches between cooling and heating modes; a pressure holding valve is located between the exhaust port and the reversing valve; and a pressure reducing valve is located between the reversing valve and the intake port.

[0021] As can be seen from the above, under this setting, the air conditioner is a cooling and heating air conditioner, and whether it is cooling or heating, it can reduce the impact noise of the compressor when it is working at low frequency, thus improving the user experience.

[0022] Another further option is that the pressure reducing valve includes an inlet, an outlet, and a pressure relief port, with the outlet connected to the intake port and the pressure relief port connected to the intake port.

[0023] As can be seen from the above, since the pressure reducing valve is used in the air conditioning compression system, the refrigerant should not leak directly into the external environment. Therefore, the refrigerant delivered from the pressure relief port needs to be recovered. For this purpose, the pressure relief port is connected to the intake port through a channel. Because the pressure is permanently reduced due to energy loss in the pressure reducing valve, even if the refrigerant delivered from the pressure relief port 2610 merges with the refrigerant from the outlet 2602, the pressure of the mixture is lower than before entering the pressure reducing valve 26.

[0024] The second objective of this invention is to provide an air conditioner that includes the aforementioned air conditioning compression system. Attached Figure Description

[0025] Figure 1 This is a system schematic diagram of an existing air conditioning compressor system.

[0026] Figure 2 This is a structural diagram of an existing rotary compressor cylinder.

[0027] Figure 3 This is a system schematic diagram of the first embodiment of the air conditioning compression system of the present invention.

[0028] Figure 4 This is a schematic diagram of the first state of the pneumatic overflow valve in the first embodiment of the air conditioning compression system of the present invention.

[0029] Figure 5 This is a schematic diagram of the second state of the pneumatic overflow valve in the first embodiment of the air conditioning compression system of the present invention.

[0030] Figure 6 This is a schematic diagram of a direct-acting pneumatic pressure reducing valve in the first embodiment of the air conditioning compression system of the present invention.

[0031] Figure 7 This is a system schematic diagram of the second embodiment of the air conditioning compression system of the present invention.

[0032] Figure 8 This is a system schematic diagram of the first working state of the third embodiment of the air conditioning compression system of the present invention.

[0033] Figure 9 This is a system schematic diagram of the second working state of the third embodiment of the air conditioning compression system of the present invention.

[0034] Figure 10 This is a schematic diagram of the first state of the back pressure valve in the fourth embodiment of the air conditioning compression system of the present invention.

[0035] Figure 11 This is a schematic diagram of the second state of the back pressure valve in the fourth embodiment of the air conditioning compression system of the present invention.

[0036] Figure 12 This is a system schematic diagram of the fifth embodiment of the air conditioning compression system of the present invention.

[0037] Figure 13 This is a system schematic diagram of the sixth embodiment of the air conditioning compression system of the present invention. Detailed Implementation

[0038] First embodiment of air conditioning compressor system and air conditioner See Figure 3 The air conditioning compression system includes a compressor 21, a first heat exchanger 22, a throttling device 23, and a second heat exchanger 24 connected in sequence, such as... Figure 2 Similar to existing technology, compressor 21 includes rollers and vanes. Under the pressure difference between the compressor's intake port 2102 and exhaust port 2101, the head of the vane engages with the outer periphery of the roller. Figure 1In comparison, the improvement of the present invention is that it also includes an overflow valve 25, which is the pressure holding valve of the present invention. The overflow valve 25 is disposed on the exhaust channel a connected to the exhaust port 2101. The improvement of this embodiment is that it also includes a pressure reducing valve 26, which is disposed on the intake channel b connected to the intake port 2102.

[0039] Combination Figure 4 and Figure 5 In this embodiment, the overflow valve 25 is a pneumatic overflow valve, which is existing technology. The pneumatic overflow valve mainly works by adjusting the handle 253, the pressure regulating spring 252, and the piston 251. Its air inlet 2501 is connected to the exhaust port 2101 of the compressor 11, and its air outlet 2502 is connected to the inlet of the first heat exchanger 22.

[0040] When the incoming air pressure is below the spring set pressure, the airflow entering from the inlet 2501 fails to push up the piston 251, and temporarily stops outputting to the outlet 2502. At this time, the pressure at the inlet 2501 and the exhaust port 2101 of the compressor 11 gradually increases. When the incoming air pressure equals the spring set pressure, the airflow entering from the inlet 2501 slightly pushes up the piston 251, and the piston is in a slightly open critical state. The system pressure is then steadily maintained at the safety pressure pre-adjusted by the overflow valve, and the refrigerant is stably delivered to the outlet 2502. At this point, the pressure will not continue to rise, and the valve maintains a stable system pressure. When the incoming air pressure exceeds the spring set pressure, the airflow entering from the inlet 2501 completely pushes up the piston 251, and the refrigerant is then sent to the outlet 2502. Figure 5 Show).

[0041] See Figure 6 In this embodiment, the pressure reducing valve 26 is a direct-acting pneumatic pressure reducing valve, which is existing technology. The pressure reducing valve 26 includes an inlet 2601, an outlet 2602, and a pressure relief port 2610. The inlet 2610 is connected to the outlet of the second heat exchanger 24, and the outlet 2602 is connected to the suction port 2102 of the compressor 11. When the outlet 2602 of the pressure reducing valve 26 has a low air pressure, rotating the handle 261 compresses the pressure regulating springs 262 and 263 downwards. The downward force of the springs is much greater than the upward thrust of the air pressure on the outlet 2602 side acting on the diaphragm 265 through the feedback conduit 266. At this time, the diaphragm 265 deforms downwards under the spring pressure and drives the valve stem 267 to move downwards, overcoming the spring force of the reset spring 269 to fully open the intake valve 268. The high-pressure input gas continuously flows from the inlet 2601 through the fully open intake valve 268 to the outlet 2602. At this time, the overflow valve port 264 is slightly open or even closed, and the pressure relief port 2610 has little or no gas discharge. The valve continues to intake and pressurize, and the air pressure at the outlet 2602 continues to rise.

[0042] When the outlet pressure at 2602 is high, the higher pressure at outlet 2602 acts on the diaphragm 265 via feedback conduit 266. The upward thrust is greater than the downward force of the pressure regulating springs 262 and 263, causing the diaphragm 265 to deform and lift upward. The valve stem 267 moves upward accordingly, significantly reducing the opening of the intake valve 268. The incoming pressure decreases, and after the intake valve 268 lifts, it opens the overflow valve port 264. Excess high-pressure gas in the valve is discharged through the overflow valve port 264 and finally through the pressure relief port 2610. Simultaneously, the return spring 269 assists in lifting the valve stem, reinforcing the action of closing the intake valve and opening the overflow port, until the outlet pressure drops back to the set equilibrium pressure. The overflow stops, and the valve returns to a medium-pressure equilibrium and stable state. It is important to note that since the pressure reducing valve 26 is used in the air conditioning compression system, the refrigerant should not be directly leaked into the external environment. Therefore, the refrigerant discharged from the pressure relief port 2610 needs to be recovered. For this purpose, the pressure relief port 2610 is connected to the intake port 2101 via a channel. Since the pressure is permanently reduced due to energy loss in the pressure reducing valve 26, even if the refrigerant from the pressure relief port 2610 merges with the refrigerant from the outlet 2602, the pressure of the mixture is lower than before it enters the pressure reducing valve 26.

[0043] See Figure 3 The present invention achieves pressure reduction on the suction side of compressor 21 by setting pressure reducing valve 26, and achieves pressure maintenance on the discharge side of compressor 21 by setting overflow valve 25. Under this setting, it can avoid the pressure difference ΔP=P1-P2 on the sliding vane inside the compressor being too low, which would cause the vane head to separate from the outer peripheral surface of the roller.

[0044] In particular, in this embodiment, the dual action of suction-side pressure reduction and discharge-side pressure holding significantly improves the adhesion between the sliding vane and the roller, suppressing periodic detachment impacts and reducing the "clicking" noise. Furthermore, the modular valve integration design eliminates the need to modify core components such as cylinders, sliding vanes, and rollers, allowing direct adaptation to existing compressor housings and piping systems, reducing design and modification costs and ensuring mass production feasibility. Additionally, under medium- and high-frequency operating conditions, the suction-side pressure reducing valve automatically remains fully open, eliminating additional flow resistance and ensuring suction efficiency, while the discharge-side pressure holding valve automatically opens after reaching the set pressure, ensuring smooth discharge. Therefore, the addition of the pressure reducing and pressure holding valves has minimal impact on compressor performance.

[0045] In addition, in this embodiment, a direct-acting pressure reducing valve is installed in the suction channel before the compressor distributor. This valve consists of a diaphragm, a spring, and a valve port. The diaphragm senses changes in suction pressure and automatically adjusts the valve opening. When the suction pressure increases, the diaphragm moves upward, and excess gas is discharged through the overflow port; when the suction pressure decreases, the diaphragm moves downward, increasing the valve opening to compensate for the flow and ensure the suction pressure remains stable at the set value. During low-frequency operation, this pressure reducing valve actively reduces the suction pressure, thereby increasing the suction and discharge pressure difference, enhancing the gas pressure on the back of the vane, and making the vane fit more tightly against the rollers. A pneumatic relief valve is installed in the compressor discharge channel, and the stiffness of the regulating spring is set so that the valve remains closed under low-frequency conditions, maintaining a high-pressure environment inside the compressor, thereby enhancing the pressure on the back of the vane and improving the fit. When the compressor frequency increases and the discharge pressure reaches the set value, the gas thrust overcomes the spring force, causing the valve to automatically open, restoring the normal discharge process and preventing excessive internal pressure from affecting compression efficiency. Mainly, this setup achieves dynamic control of the contact state between the slide and the roller through optimized mechanical structure design, reducing low-frequency abnormal noise while maintaining high-frequency operating performance unaffected, and has good prospects for engineering applications.

[0046] Second embodiment of air conditioning compressor system and air conditioner See Figure 7 In this embodiment, two pressure reducing valves 26 are connected in series between the second heat exchanger and the suction port. Two or more pressure reducing valves are used on the suction side for pressure regulation. By using multiple pressure reducing valves to reduce pressure in stages, the accuracy of suction pressure control is improved, and pressure fluctuations are reduced.

[0047] Third embodiment of air conditioning compressor system and air conditioner See Figure 8 and Figure 9 In addition to the compressor 91, the first heat exchanger 92, the throttling device 93, and the second heat exchanger 94, the air conditioning compression system of this embodiment also includes a reversing valve 95. The reversing valve 95 is a conventional four-way valve. The four-way valve is configured according to existing methods in conventional air conditioning compression systems, enabling the air conditioning compression system to switch between cooling and heating modes via the reversing valve. Figure 8 The air conditioning compressor system shown is in cooling operation. Figure 9 The air conditioning compressor system shown is in heating mode.

[0048] In this embodiment, the pressure holding valve 97 is disposed between the exhaust port 9101 and the reversing valve 95, and the pressure reducing valve 98 is disposed between the reversing valve 95 and the intake port 9102. The pressure holding valve 97 is an overflow valve or a back pressure valve.

[0049] In this setting, the air conditioner functions as both a cooling and heating unit, and whether in cooling or heating mode, it reduces the impact noise from the compressor during low-frequency operation, thus improving the user experience.

[0050] Fourth embodiment of air conditioning compressor system and air conditioner In this embodiment, the pressure holding valve is a back pressure valve 27, and the pressure reducing valve is a pilot-operated pressure reducing valve. Both the back pressure valve and the pilot-operated pressure reducing valve are existing technologies in the field. The combination of the pilot-operated pressure reducing valve and the back pressure valve can improve the pressure control accuracy and stability.

[0051] Among them, the pilot-operated pressure reducing valve controls the main valve's operation through the pilot valve, and its pressure reducing accuracy is much higher than that of the direct-acting pressure reducing valve. When the system's suction pressure fluctuates instantaneously, the pilot valve can respond quickly and offset the pressure fluctuation by controlling the opening of the main valve, thus avoiding instantaneous attenuation of the sliding plate's contact force.

[0052] Then, see Figure 10 When the inlet pressure of the back pressure valve 27 is lower than the preset opening pressure of the adjusting spring 272, the low-pressure gas enters the valve body cavity from the inlet 2701. The upward pressure thrust on the bottom of the valve core diaphragm assembly 273 is small and less than the downward elastic force of the pressure adjusting spring 272 pre-compressed by the adjusting handle 275. The pressure adjusting spring 272 pushes the valve core diaphragm assembly 273 downward to press the valve port sealing surface, completely blocking the flow path between the inlet 2701 and the outlet 2702. The lower return spring 274 is in a compressed and tightened state. At this time, the gas cannot flow to the outlet 2702, the valve is closed and pressure is maintained, and the back pressure continues to gradually increase.

[0053] See Figure 11 When the inlet pressure of the back pressure valve 27 is higher than the preset opening pressure of the regulating spring 272, the high-pressure gas entering through the inlet 2701 pushes the valve core diaphragm assembly 273 upward, which is greater than the downward elastic force of the regulating spring 272. The high-pressure gas pushes the valve core diaphragm assembly 273 upward, compressing the regulating spring 272, and the valve port is fully opened and connected, with the inlet 2701 and outlet 2702 fully connected. The lower reset spring 274 assists the valve core to open upward, and excess high-pressure gas is quickly discharged from the outlet 2702 to relieve pressure, and the outlet back pressure drops rapidly. When the pressure drops back to the set equilibrium pressure, the regulating spring 272 pushes the valve core diaphragm assembly 273 downward to reset and close the valve port, returning to the medium pressure stabilization state, thereby stabilizing and controlling the outlet back pressure.

[0054] Thus, the back pressure valve achieves pressure holding function by preset back pressure value. Unlike the overpressure opening logic of the relief valve, the back pressure valve can actively limit the exhaust flow when the exhaust pressure is lower than the preset value, quickly establish a stable back pressure, and when the exhaust pressure is higher than the preset value, the valve is fully open and exhaust is unobstructed. In addition, the built-in damping structure of the back pressure valve can slow down the valve core movement speed, avoid pressure shock during operation switching, and further reduce instantaneous noise.

[0055] Fifth embodiment of air conditioning compressor system and air conditioner See Figure 12 In this embodiment, a pressure reducing valve 81 is provided on the air intake channel b connected to the air intake port, but no pressure maintaining valve is provided on the exhaust channel a connected to the exhaust port.

[0056] This setting reduces P2, thereby increasing the pressure difference ΔP = P1 - P2, ensuring that the vane head is in close contact with the outer circumferential surface of the roller.

[0057] Sixth Embodiment of Air Conditioning Compressor System and Air Conditioner See Figure 13 In this embodiment, a pressure-holding valve 82 is provided on the exhaust channel a connected to the exhaust port, but no pressure-reducing valve is provided on the intake channel b connected to the intake port.

[0058] This setting increases P1, thereby increasing the pressure difference ΔP = P1 - P2, ensuring that the vane head is in close contact with the outer circumferential surface of the roller.

[0059] Finally, it should be emphasized that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. An air conditioning compression system, comprising a compressor, a first heat exchanger, a throttling device, and a second heat exchanger connected in sequence, wherein the compressor includes rollers and vanes, and under the pressure difference between the compressor's intake port and exhaust port, the head of the vanes engages with the outer periphery of the rollers; Its features are: It also includes a pressure holding valve, which is disposed in an exhaust passage connected to the exhaust port; And / or, It also includes a pressure reducing valve, which is disposed in the air intake channel connected to the air intake port.

2. The air conditioning compressor system according to claim 1, characterized in that: The pressure holding valve is either an overflow valve or a back pressure valve.

3. The air conditioning compressor system according to claim 1, characterized in that: The pressure reducing valve is a direct-acting pneumatic pressure reducing valve, the pressure holding valve is a relief valve, and the relief valve is a pneumatic relief valve.

4. The air conditioning compressor system according to claim 1, characterized in that: The pressure reducing valve is a proportional pressure reducing valve, the pressure holding valve is a relief valve, and the relief valve is an electromagnetically controlled relief valve.

5. The air conditioning compressor system according to claim 1, characterized in that: The pressure reducing valve is a pilot-operated pressure reducing valve, and the pressure holding valve is a back pressure valve.

6. The air conditioning compressor system according to any one of claims 1 to 5, characterized in that: At least two of the pressure reducing valves are connected in series between the second heat exchanger and the air intake.

7. The air conditioning compressor system according to any one of claims 1 to 5, characterized in that: It also includes a reversing valve, through which the air conditioning compression system switches between cooling mode and heating mode; The pressure-holding valve is disposed between the exhaust port and the reversing valve; The pressure reducing valve is located between the reversing valve and the air intake.

8. The air conditioning compressor system according to any one of claims 1 to 5, characterized in that: The pressure reducing valve includes an inlet, an outlet, and a pressure relief port. The outlet is connected to the intake port, and the pressure relief port is connected to the intake port.

9. An air conditioner, characterized in that, Includes the air conditioning compressor system described in any one of claims 1 to 8.

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