Compressors and refrigeration equipment

Abstract

This invention discloses a compressor and refrigeration equipment, relating to the field of compressor technology. The compressor includes a pump assembly, a receiver, a first enthalpy-increasing assembly, and a second enthalpy-increasing assembly. When the pump assembly compresses the refrigerant, the refrigerant is compressed in the low-pressure compression chamber and then enters the high-pressure compression chamber through the intermediate chamber for further compression. This increases the pressure of the discharged refrigerant, thereby increasing its temperature and widening the temperature difference with the surrounding environment, thus improving the compressor's heating capacity in low-temperature environments. The first enthalpy-increasing assembly is connected to the intermediate chamber, and the second enthalpy-increasing assembly is connected to either the low-pressure or high-pressure compression chamber. Both enthalpy-increasing assemblies replenish the refrigerant, increasing the intake density of the high-pressure compression chamber, increasing the compressor's discharge volume, improving the circulation flow rate, and enhancing the compressor's volumetric efficiency, thereby improving the compressor's heating capacity in even lower-temperature environments.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] Air conditioners, heat pumps, and other similar products have heating functions, but in low-temperature environments, the heat exchange efficiency decreases due to the reduced temperature difference between the ambient environment and the evaporator, leading to a decline in heating capacity. To improve heating capacity in low-temperature environments, related technologies employ two-stage or multi-stage compression compressors. However, in even lower-temperature environments, this approach still struggles to achieve satisfactory results. Summary of the Invention

[0003] This invention aims to at least solve one of the technical problems existing in the prior art. To this end, this invention proposes a compressor capable of improving heating capacity in lower temperature environments.

[0004] The present invention also proposes a refrigeration device having the above-mentioned compressor.

[0005] A compressor according to a first aspect of the present invention includes: a pump body assembly having a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber, wherein the exhaust port of the low-pressure compression chamber is connected to the inlet of the high-pressure compression chamber through the intermediate chamber; a liquid receiver connected to the inlet of the low-pressure compression chamber; a first enthalpy-increasing assembly connected to the intermediate chamber, the first enthalpy-increasing assembly being used to supply refrigerant to the intermediate chamber; and a second enthalpy-increasing assembly connected to either the low-pressure compression chamber or the high-pressure compression chamber, the second enthalpy-increasing assembly being used to supply refrigerant to either the low-pressure compression chamber or the high-pressure compression chamber.

[0006] The compressor according to embodiments of the present invention has at least the following beneficial effects:

[0007] When the pump assembly compresses the refrigerant, the refrigerant is compressed in the low-pressure compression chamber and then enters the high-pressure compression chamber through the intermediate chamber for further compression. This increases the pressure of the discharged refrigerant, thereby raising its temperature and increasing the temperature difference with the surrounding environment. This enhances the compressor's heating capacity in low-temperature environments. The first enthalpy-increasing component is connected to the intermediate chamber, and the second enthalpy-increasing component is connected to either the low-pressure or high-pressure compression chamber. Both components replenish the refrigerant, increasing the intake density of the high-pressure compression chamber, increasing the compressor's discharge volume, improving the circulation flow rate, and enhancing the compressor's volumetric efficiency. Ultimately, this improves the compressor's heating capacity in even lower-temperature environments.

[0008] According to some embodiments of the present invention, the volume of the first enthalpy-increasing component is greater than or equal to the volume of the second enthalpy-increasing component.

[0009] According to some embodiments of the present invention, the second enthalpy-increasing component is connected to the low-pressure compression chamber, and the ratio of the jet pressure of the first enthalpy-increasing component to the jet pressure of the second enthalpy-increasing component is a, which satisfies: 1≤a≤2.

[0010] According to some embodiments of the present invention, the second enthalpy-increasing component is connected to the high-pressure compression chamber, and the ratio of the jet pressure of the second enthalpy-increasing component to the jet pressure of the first enthalpy-increasing component is b, which satisfies: 1≤b≤2.

[0011] According to some embodiments of the present invention, the compressor further includes a housing, the pump assembly is installed inside the housing, the second enthalpy-increasing assembly is installed outside the housing, and the second enthalpy-increasing assembly includes an exhaust pipe that passes through the housing and is fixedly connected to the pump assembly.

[0012] According to some embodiments of the present invention, the second enthalpy-increasing component further includes a check mechanism for preventing refrigerant from flowing back from the low-pressure compression chamber or the high-pressure compression chamber to the second enthalpy-increasing component.

[0013] According to some embodiments of the present invention, the check valve is an exhaust valve seat, the pump body assembly is provided with an air intake channel communicating with the exhaust pipe and the low-pressure compression chamber or the high-pressure compression chamber, and the exhaust valve seat is installed at the end of the air intake channel away from the exhaust pipe.

[0014] According to some embodiments of the present invention, the check mechanism is a one-way valve, which is installed on the side of the exhaust pipe adjacent to the low-pressure compression chamber or the high-pressure compression chamber.

[0015] According to some embodiments of the present invention, the low-pressure compression chamber is provided in multiple ways, and the exhaust ports of the multiple low-pressure compression chambers are all connected to the intermediate chamber; and / or, the high-pressure compression chamber is provided in multiple ways, and the air inlets of the multiple high-pressure compression chambers are all connected to the intermediate chamber.

[0016] According to some embodiments of the present invention, the intermediate cavity includes multiple cavities connected by a communication channel, and the exhaust port of the low-pressure compression cavity is configured to exhaust gas into one of the cavities or to exhaust gas into the multiple cavities respectively.

[0017] According to some embodiments of the present invention, the pump body assembly further includes an upper bearing, a second cylinder, an upper partition, a lower partition, a first cylinder, and a lower bearing connected sequentially along the axial direction of the pump body assembly. The lower partition, the first cylinder, and the lower bearing enclose the low-pressure compression chamber, the upper partition and the lower partition form the intermediate cavity, and the upper bearing, the second cylinder, and the upper partition enclose the high-pressure compression chamber.

[0018] According to some embodiments of the present invention, the pump body assembly further includes an upper bearing, a second cylinder, an upper partition, a lower partition, a first cylinder, and a lower bearing connected in sequence. The lower partition, the first cylinder, and the lower bearing enclose the low-pressure compression chamber, and the upper bearing, the second cylinder, and the upper partition enclose the high-pressure compression chamber. The lower bearing is provided with a lower muffler, and the lower bearing and the lower muffler enclose the first cavity. The upper partition and the lower partition enclose the second cavity. The first cavity and the second cavity constitute the intermediate cavity, and the first cavity and the second cavity are connected by a communicating channel.

[0019] A refrigeration device according to a second aspect of the present invention includes the compressor described in the above embodiments.

[0020] The refrigeration device according to embodiments of the present invention has at least the following beneficial effects:

[0021] In the compressor of the first embodiment, when the compressor's pump assembly compresses the refrigerant, the refrigerant is compressed in the low-pressure compression chamber and then enters the high-pressure compression chamber through the intermediate chamber for further compression. This increases the pressure of the discharged refrigerant, thereby increasing its temperature and the temperature difference with the surrounding environment, thus improving the compressor's heating capacity in low-temperature environments. The first enthalpy-increasing component is connected to the intermediate chamber, and the second enthalpy-increasing component is connected to either the low-pressure or high-pressure compression chamber. Both components replenish the refrigerant, increasing the intake density of the high-pressure compression chamber, increasing the compressor's discharge volume, improving the circulation flow rate, and enhancing the compressor's volumetric efficiency, thereby improving the compressor's heating capacity in even lower-temperature environments.

[0022] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0023] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0024] Figure 1 This is a schematic diagram of the structure of a compressor according to an embodiment of the present invention;

[0025] Figure 2 This is a cross-sectional view of a compressor according to an embodiment of the present invention;

[0026] Figure 3 This is a cross-sectional view of a pump body assembly according to an embodiment of the present invention;

[0027] Figure 4 This is a cross-sectional view of a compressor according to another embodiment of the present invention;

[0028] Figure 5This is a cross-sectional view of a compressor at the first cylinder according to an embodiment of the present invention;

[0029] Figure 6 This is a simplified schematic diagram of the first cylinder according to an embodiment of the present invention;

[0030] Figure 7 This is a cross-sectional view of a compressor at the second cylinder according to an embodiment of the present invention;

[0031] Figure 8 This is a simplified schematic diagram of a partition member according to an embodiment of the present invention;

[0032] Figure 9 This is a cross-sectional view of a compressor at the partition plate according to an embodiment of the present invention;

[0033] Figure 10 This is a cross-sectional view of a compressor according to an embodiment of the present invention, positioned above the first cavity of the partition member;

[0034] Figure 11 This is a cross-sectional view of a compressor according to another embodiment of the present invention;

[0035] Figure 12 This is a cross-sectional view of the first cylinder according to an embodiment of the present invention;

[0036] Figure 13 This is a cross-sectional view of the second cylinder according to an embodiment of the present invention;

[0037] Figure 14 This is a cross-sectional view of the crankshaft and the first and second cylinders in cooperation according to an embodiment of the present invention;

[0038] Figure 15 This is a cross-sectional view of a crankshaft according to an embodiment of the present invention;

[0039] Figure 16 This is a cross-sectional view of a pump body assembly according to another embodiment of the present invention;

[0040] Figure 17 This is a simplified schematic diagram of a heating system according to an embodiment of the present invention.

[0041] Icon labels:

[0042] Compressor 1000;

[0043] Pump body assembly 100; intake channel 101; connecting channel 102; first cylinder 110; low-pressure compression chamber 111; intake zone 112; compression zone 113; first air inlet 114; first exhaust port 115; first vane groove 116; lower bearing 120; lower muffler 130; first cavity 131; heat shield 140; upper bearing 150; second cylinder 160; high-pressure compression chamber 161; second vane groove 162; upper muffler 170; third cavity 171; guide channel 180; partition 190; second cavity 191; upper partition 192; lower partition 193; intermediate cavity 194; connecting hole 195; air inlet 196; jet outlet 197;

[0044] 200 housing; 210 inner cavity; 220 vent pipe;

[0045] Liquid reservoir 300;

[0046] Motor assembly 400; stator 410; rotor 420; crankshaft 430; first piston 431; second piston 432; first eccentric part 433; second eccentric part 434; main shaft 435;

[0047] First enthalpy-increasing component 500; first intake pipe 510; first intermediate housing 520; first exhaust pipe 530;

[0048] Second enthalpy-increasing component 600; second intake pipe 610; second intermediate housing 620; second exhaust pipe 630;

[0049] Heating system 700; first flash evaporator 710; second flash evaporator 720; first throttling device 730; second throttling device 740; third throttling device 750; evaporator 760; condenser 770. Detailed Implementation

[0050] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0051] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the drawings and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0052] In the description of this invention, "multiple" refers to two or more. The use of "first" and "second" is for distinguishing technical features only and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features or their sequential relationship.

[0053] In the description of this invention, unless otherwise explicitly defined, terms such as "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0054] Compressors can be used in refrigeration or heating equipment, such as heat pump water heaters and air conditioners. They compress low-temperature, low-pressure refrigerant into high-temperature, high-pressure refrigerant, providing power for the refrigeration system's circulation. Compressors can employ multi-stage compression, which allows for higher volumetric efficiency and increases the refrigerant pressure discharged from the pump assembly, enabling them to perform well in both low-temperature heating and high-temperature cooling applications.

[0055] For example, refer to Figure 1 , Figure 2 and Figure 3 As shown, a compressor 1000 according to an embodiment of the present invention includes a housing 200, a pump assembly 100, a motor assembly 400, and a liquid receiver 300. The housing 200 has an inner cavity 210, and an outlet pipe 220 for discharging gas is provided at the upper end of the housing 200. The pump assembly 100 is installed inside the inner cavity 210, and the liquid receiver 300 is located outside the housing 200 and connected to the pump assembly 100 through a pipe. The motor assembly 400 includes a stator 410 and a rotor 420. The stator 410 is fixedly connected to the inner wall of the housing 200, and the rotor 420 is located between the stators 410.

[0056] Reference Figure 3As shown, the pump assembly 100 includes a lower bearing 120, a first cylinder 110, a partition 190, a second cylinder 160, an upper bearing 150, and a crankshaft 430. The motor assembly 400 drives the crankshaft 430 to rotate. Along the axial direction of the crankshaft 430, the crankshaft 430 includes a first eccentric portion 433 and a second eccentric portion 434 spaced apart. A first piston 431 is fitted onto the first eccentric portion 433, and a second piston 432 is fitted onto the second eccentric portion 434. The lower bearing 120 is connected to the lower end face of the first cylinder 110. The first cylinder 110 forms a low-pressure compression chamber 111. The first piston 431 is rotatably disposed within the low-pressure compression chamber 111. The reservoir 300 is connected to the first cylinder 110. A partition 190 is disposed on the side of the first cylinder 110 opposite to the lower bearing 120, and a second cylinder 160 is connected to the side of the partition 190 opposite to the first cylinder 110. The partition 190 serves to separate the first cylinder 110 and the second cylinder 160. The second cylinder 160 forms a high-pressure compression chamber 161, and a second piston 432 is rotatably disposed within the high-pressure compression chamber 161. The pump body assembly 100 is provided with an intermediate chamber 194, through which the exhaust port of the low-pressure compression chamber 111 communicates with the intake port of the high-pressure compression chamber 161. An upper bearing 150 is connected to the upper end face of the second cylinder 160, and a crankshaft 430 passes through the upper bearing 150 and the lower bearing 120 to reduce friction during crankshaft 430 rotation and ensure stable operation of the crankshaft 430.

[0057] Therefore, when the compressor 1000 is operating, the low-temperature, low-pressure refrigerant enters the receiver 300. The receiver 300 reduces the amount of liquid refrigerant entering the pump assembly 100, preventing liquid slugging. Gaseous refrigerant enters the low-pressure compression chamber 111 through the receiver 300. When the crankshaft 430 rotates, it drives the first piston 431 to rotate within the low-pressure compression chamber 111, thus performing a primary compression of the low-temperature, low-pressure refrigerant. The refrigerant is then discharged through the exhaust port of the low-pressure compression chamber 111 into the intermediate chamber 194. From the intermediate chamber 194, the refrigerant enters the high-pressure compression chamber 161 for a secondary compression, and finally enters the inner cavity 210 of the housing 200. After further heating by the stator 410 and rotor 420, it becomes a high-temperature, high-pressure refrigerant, which is then discharged from the outlet pipe 220 of the housing 200. By employing a two-stage compression method, the refrigerant pressure can be increased, enabling the compressor 1000 to perform well in both low-temperature heating and high-temperature cooling applications.

[0058] To improve the heating performance of compressor 1000 in lower temperature environments (e.g., -25°C and below), refer to Figure 2 and Figure 4As shown in the embodiments of the present invention, the compressor 1000 further includes a first enthalpy-increasing component 500 and a second enthalpy-increasing component 600. The first enthalpy-increasing component 500 is connected to the intermediate cavity 194 and is used to supply refrigerant to the intermediate cavity 194. The second enthalpy-increasing component 600 is connected to either the low-pressure compression cavity 111 or the high-pressure compression cavity 161, or each of the low-pressure compression cavity 111 and the high-pressure compression cavity 161 is connected to a second enthalpy-increasing component 600. The second enthalpy-increasing component 600 is used to supply refrigerant to the low-pressure compression cavity 111 and / or the high-pressure compression cavity 161. Both the low-pressure compression cavity 111 and the high-pressure compression cavity 161 include an intake zone and an exhaust zone, and the second enthalpy-increasing component 600 typically supplies refrigerant to the exhaust zone. For ease of explanation, in all subsequent embodiments, unless otherwise specified, the connection between the second enthalpy-increasing component 600 and the low-pressure compression cavity 111 will be used as an example for description.

[0059] Understandably, the second enthalpy-increasing component 600 is connected to the low-pressure compression chamber 111, which can increase the discharge volume of the low-pressure compression chamber 111. The refrigerant compressed in the low-pressure compression chamber 111 is discharged into the intermediate chamber 194, while the first enthalpy-increasing component 500 can supply refrigerant to the intermediate chamber 194. Therefore, the supplied refrigerant can mix with the original refrigerant in the intermediate chamber 194, increasing the refrigerant density and lowering the original refrigerant temperature. This prevents excessively hot refrigerant from entering the high-pressure compression chamber 161, thereby reducing the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and thus improving the energy efficiency of the compressor 1000. Therefore, by supplementing the low-pressure compression chamber 111 and the intermediate chamber 194 with refrigerant, the intake density of the high-pressure compression chamber 161 can be increased, the discharge volume of the compressor 1000 can be increased, the circulation flow rate can be improved, and the volumetric efficiency of the compressor 1000 can be improved, thereby improving the heating capacity of the compressor 1000 in lower temperature environments.

[0060] For example, experiments show that when compressor 1000 uses only the first enthalpy-enhancing component 500 and the intermediate cavity 194 connected, without using the second enthalpy-enhancing component 600, the energy efficiency is improved by 4% at -15℃ and by 6.1% at -25℃. However, when both the first enthalpy-enhancing component 500 and the second enthalpy-enhancing component 600 are used, the energy efficiency is improved by 2.1% at -15℃ and by 6.4% at -25℃. Therefore, when both the first enthalpy-enhancing component 500 and the second enthalpy-enhancing component 600 are used, the lower the temperature, the more significant the energy efficiency improvement and the stronger the heating capacity.

[0061] Reference Figure 2As shown in the embodiment of the present invention, both the first enthalpy-increasing component 500 and the second enthalpy-increasing component 600 are located outside the housing 200. The first enthalpy-increasing component 500 includes a first intake pipe 510, a first intermediate housing 520, and a first exhaust pipe 530 connected to each other. The first exhaust pipe 530 penetrates the housing 200 and is fixedly connected to the partition member 190. The refrigerant enters the interior of the first intermediate housing 520 through the first intake pipe 510 and is then exhausted into the intermediate cavity 194 through the first exhaust pipe 530. The volume of the first enthalpy-increasing component 500 refers to the sum of the volumes of the first intake pipe 510, the first intermediate housing 520, and the first exhaust pipe 530.

[0062] Reference Figure 4 As shown, the second enthalpy-enhancing assembly 600 includes a second intake pipe 610, a second intermediate housing 620, and a second exhaust pipe 630 connected to each other. The second exhaust pipe 630 passes through the housing 200 and is fixedly connected to the pump assembly 100. For example, the second exhaust pipe 630 is fixedly connected to the first cylinder 110. Refrigerant enters the interior of the second intermediate housing 620 through the second intake pipe 610 and is then exhausted to the low-pressure compression chamber 111 through the second exhaust pipe 630. The volume of the second enthalpy-enhancing assembly 600 refers to the sum of the volumes of the second intake pipe 610, the second intermediate housing 620, and the second exhaust pipe 630. The volume of the first enthalpy-increasing component 500 is greater than or equal to the volume of the second enthalpy-increasing component 600. Therefore, the jet volume of the first enthalpy-increasing component 500 is greater than that of the second enthalpy-increasing component 600, which makes the gas replenishment more complete and the mixing between different refrigerants more uniform, thereby further improving the heating capacity of the compressor 1000 in a lower temperature environment.

[0063] In embodiments of the present invention, the ratio of the jet pressure of the first enthalpy-increasing component 500 to the jet pressure of the second enthalpy-increasing component 600 is 'a', satisfying: 1 ≤ a ≤ 2, for example, a = 1.2, a = 1.5, a = 1.6, a = 1.8. It is understood that after the refrigerant is compressed in the low-pressure compression chamber 111, the refrigerant pressure increases, meaning the refrigerant pressure in the intermediate chamber 194 is higher than the pressure before the refrigerant enters the compressor 1000. Since the refrigerant needs to flow from high pressure to low pressure, when a is less than 1 (i.e., the jet pressure of the first enthalpy-increasing component 500 is less than the jet pressure of the second enthalpy-increasing component 600), the first enthalpy-increasing component 500 cannot deliver refrigerant into the intermediate chamber 194, and the refrigerant in the intermediate chamber 194 will flow back to the first enthalpy-increasing component 500, posing a risk of backflow. When 'a' is greater than 2, the refrigerant pressure in the intermediate cavity 194 will increase significantly, affecting the exhaust from the low-pressure compression cavity 111 and increasing the load on the first cylinder 110. It will also affect the gas supply to the low-pressure compression cavity 111, leading to a decrease in the heating capacity of the compressor 1000. Therefore, a properly designed value for 'a' can ensure that the first enthalpy-increasing component 500 can stably supply gas to the intermediate cavity 194 while minimizing the impact on the exhaust from the low-pressure compression cavity 111, thereby improving the heating capacity of the compressor 1000.

[0064] In another embodiment of the present invention, when the second enthalpy-increasing component 600 is connected to the high-pressure compression chamber 161, the ratio of the jet pressure of the second enthalpy-increasing component 600 to the jet pressure of the first enthalpy-increasing component 500 is b, satisfying 1 ≤ b ≤ 2, for example, b = 1.2, b = 1.5, b = 1.6, b = 1.8. Since the refrigerant pressure in the exhaust zone of the high-pressure compression chamber 161 is higher than the refrigerant pressure in the intermediate chamber 194, when b is less than 1, the second enthalpy-increasing component 600 cannot exhaust gas into the high-pressure compression chamber 161, resulting in gas replenishment failure. When b is greater than 2, the jet pressure of the second enthalpy-increasing component 600 increases, the gas replenishment amount decreases during the thermodynamic cycle, it cannot further increase the refrigerant flow rate inside the high-pressure compression chamber 161, and power consumption increases, leading to a decrease in the performance of the compressor 1000. Therefore, by rationally designing the size of b, it is possible to ensure that the second enthalpy-increasing component 600 supplies gas to the high-pressure compression chamber 161, while also improving the problems of high power consumption and performance degradation of the compressor 1000, thereby enhancing the heating capacity of the compressor 1000.

[0065] It is understandable that, as the refrigerant pressure in the low-pressure compression chamber 111 gradually increases during compression, when the pressure exceeds the discharge pressure of the second enthalpy-increasing assembly 600, the refrigerant in the low-pressure compression chamber 111 will enter the second enthalpy-increasing assembly 600. To improve this situation, in embodiments of the present invention, the second enthalpy-increasing assembly 600 further includes a check mechanism to prevent refrigerant from flowing back from the low-pressure compression chamber 111 to the second enthalpy-increasing assembly 600. When the second enthalpy-increasing assembly 600 is connected to the high-pressure compression chamber 161, the check mechanism prevents refrigerant from flowing back from the high-pressure compression chamber 161 to the second enthalpy-increasing assembly 600. Therefore, providing a check mechanism can prevent refrigerant backflow and ensure the discharge volume of either the low-pressure compression chamber 111 or the high-pressure compression chamber 161.

[0066] In an embodiment of the present invention, the check mechanism is an exhaust valve seat, which includes a valve plate located above the exhaust port of the low-pressure compression chamber 111 and a lift limiter. The pump body assembly 100 is provided with an intake passage 101 connecting the second exhaust pipe 630 and the low-pressure compression chamber 111, and the exhaust valve seat is installed at the end of the intake passage 101 away from the second exhaust pipe 630. Therefore, the refrigerant sprayed by the second enthalpy-increasing assembly 600 can push the valve plate and the exhaust port of the low-pressure compression chamber 111 to separate, thereby entering the low-pressure compression chamber 111. The lift limiter is used to limit the lifting height of the valve plate, and also has the function of guiding the direction of the valve plate, reducing the possibility of misalignment or swaying of the valve plate. When the refrigerant in the low-pressure compression chamber 111 is compressed by the first piston 431 to a pressure greater than the jet pressure of the second enthalpy-increasing component 600, the valve plate can seal the exhaust port of the low-pressure compression chamber 111 under the pressure of the refrigerant in the low-pressure compression chamber 111, thereby reducing the refrigerant from entering the second enthalpy-increasing component through the low-pressure compression chamber 111. Therefore, it can effectively improve the refrigerant backflow and increase the exhaust volume of the low-pressure compression chamber 111.

[0067] In embodiments of the present invention, the check valve is a one-way valve, which is installed on the side of the second exhaust pipe 630 adjacent to the low-pressure compression chamber 111. When the second enthalpy-increasing assembly 600 and the high-pressure compression chamber 161 are connected, the one-way valve is installed on the side of the second exhaust pipe 630 adjacent to the high-pressure compression chamber 161. It is understood that the one-way valve only allows refrigerant in the second enthalpy-increasing assembly 600 to enter the low-pressure compression chamber 111 or the high-pressure compression chamber 161, and does not allow refrigerant in the low-pressure compression chamber 111 or the high-pressure compression chamber 161 to enter the second enthalpy-increasing assembly 600, thereby effectively preventing refrigerant backflow.

[0068] In embodiments of the present invention, multiple low-pressure compression chambers 111 are provided, and the exhaust ports of the multiple low-pressure compression chambers 111 are all connected to the intermediate chamber 194. For example, the multiple low-pressure compression chambers 111 are arranged sequentially in a vertical direction. In embodiments of the present invention, multiple high-pressure compression chambers 161 can also be provided, and the inlets of the multiple high-pressure compression chambers 161 are all connected to the intermediate chamber 194, and the multiple high-pressure compression chambers 161 are arranged sequentially in a vertical direction. It is understood that providing multiple low-pressure compression chambers 111 or multiple high-pressure compression chambers 161 can improve the compression efficiency of the refrigerant.

[0069] In embodiments of the present invention, the gaseous refrigerant used for replenishing the first enthalpy-increasing component 500 can be provided by a flash evaporator, which is installed in the circulation loop of the refrigeration system or heating system 700. (Refer to...) Figure 17 As shown, taking the heating system 700 as an example: after the liquid refrigerant releases heat through the condenser 770, it flows through the first throttling device 730. Under the action of the first throttling device 730, the liquid refrigerant changes from a completely liquid refrigerant to a gas-liquid mixture. The gas-liquid mixture then enters the first flash evaporator 710. The gaseous refrigerant flows along the outlet of the first flash evaporator 710 to the first enthalpy-increasing component 500. The liquid refrigerant flows out from the liquid outlet of the first flash evaporator 710 and enters the evaporator 760 after passing through the second throttling device 740. Finally, the refrigerant that has absorbed heat enters the low-pressure compression chamber 111 through the liquid receiver 300.

[0070] Continue to refer to Figure 17 As shown, the refrigerant used for replenishing the gas in the second enthalpy-enhancing component 600 can be provided by the second flash evaporator 720. For example, if the opening of the second throttling device 740 is zero, the liquid refrigerant flows out of the liquid outlet of the first flash evaporator 710 and passes through the third throttling device 750. Under the action of the third throttling device 750, the refrigerant changes from a completely liquid state to a gas-liquid mixture before entering the second flash evaporator 720. The gaseous refrigerant flows along the gas outlet of the second flash evaporator 720 to the second enthalpy-enhancing component 600, while the liquid refrigerant flows out of the liquid outlet of the second flash evaporator 720 and enters the evaporator 760. The refrigerant that has absorbed heat passes through the liquid receiver 300 and enters the low-pressure compression chamber 111. Therefore, the first flash evaporator 710 and the second flash evaporator 720 respectively supply gaseous refrigerant to the first enthalpy-enhancing component 500 and the second enthalpy-enhancing component 600. In another embodiment of the present invention, the flash evaporator can be replaced by a plate heat exchanger, that is, the refrigerant used for gas replenishment in the first enthalpy-increasing component 500 and the second enthalpy-increasing component 600 can also be provided by a plate heat exchanger, and the appropriate solution can be selected according to the actual situation.

[0071] In embodiments of the present invention, the intermediate cavity 194 includes multiple cavities connected by a connecting channel 102, and the exhaust port of the low-pressure compression cavity 111 is configured to exhaust air into one of the cavities or to exhaust air into multiple cavities respectively. For example, refer to... Figure 2As shown, two of the multiple cavities are designated as the first cavity 131 and the second cavity 191. The pump assembly 100 also includes a lower silencer 130, which is connected to a lower bearing 120. The first cavity 131 is formed between the lower silencer 130 and the lower bearing 120, and the second cavity 191 is formed within a partition 190. The first cavity 131 and the second cavity 191 are connected by a connecting channel 102. Since the displacement of the low-pressure compression chamber 111 is usually larger than that of the high-pressure compression chamber 161, the low-pressure compression chamber 111 can simultaneously exhaust gas into the first cavity 131 and the second cavity 191 before mixing it into the high-pressure compression chamber 161 to improve exhaust efficiency. Alternatively, in another embodiment, the low-pressure compression chamber 111 can discharge refrigerant into the first cavity 131 and then into the second cavity 191 through the connecting channel 102. The appropriate solution can be selected based on the actual situation.

[0072] Continue to refer to Figure 2 As shown, in an embodiment of the present invention, the partition 190 includes an upper partition 192 and a lower partition 193, with the upper partition 192 fixedly connected to the lower partition 193. The upper partition 192 is also fixedly connected to the lower end face of the second cylinder 160, and the lower partition 193 is fixedly connected to the upper end face of the first cylinder 110. A groove is provided on the side of the upper partition 192 facing the lower partition 193, and the wall of the groove and the wall of the lower partition 193 facing the upper partition 192 together form a second cavity 191. The lower partition 193 is provided with a first valve seat, which has an exhaust port for the low-pressure compression chamber 111; the lower bearing 120 is provided with a second valve seat, which also has an exhaust port for the low-pressure compression chamber 111. That is, the low-pressure compression chamber 111 has two exhaust ports, and the low-pressure compression chamber 111 discharges refrigerant to the first cavity 131 and the second cavity 191 through the two exhaust ports. Of course, the exhaust port of the low-pressure compression chamber 111 can also be one, three, four, etc., and the appropriate solution can be selected according to the actual situation.

[0073] Reference Figure 3 As shown in the embodiment of the present invention, the pump body assembly 100 further includes an upper silencer 170, which is connected to an upper bearing 150. A third cavity 171 is formed between the upper silencer 170 and the upper bearing 150. The high-pressure compression chamber 161 can discharge the compressed refrigerant into the third cavity 171, and finally into the inner cavity 210 of the housing 200. The upper silencer 170 can reduce the noise during refrigerant discharge and improve the user experience.

[0074] To increase the displacement of compressor 1000 and thus improve its cooling capacity in high-temperature environments or its heating capacity in low-temperature environments, refer to... Figure 5As shown in the embodiment of the present invention, the first cylinder 110 is provided with a first vane groove 116. On the projection plane along the axial direction of the crankshaft 430, the center line of the first vane groove 116 is S8, and the center line S8 of the first vane groove 116 is its center line of symmetry. S8 can extend along the radial direction of the housing 200, for example, parallel to the sliding direction of the vane, and perpendicular to the rotation axis S4 of the crankshaft 430. The line connecting the center of the second enthalpy-increasing component 600 and the rotation center of the crankshaft 430 is S6. The center of the second enthalpy-increasing component 600 is located on the axial center line S3 of the second enthalpy-increasing component 600, and the rotation center of the crankshaft 430 is located on the rotation axis S4 of the crankshaft 430. Starting from S8, and rotating in the opposite direction to the rotation direction of crankshaft 430, the included angle between S8 and S6 is c, satisfying: 10°≤c≤180°, for example, c=20°, c=50°, c=100°, c=150°. The axial centerline S3 of the second enthalpy-increasing component 600 and the rotation axis S4 of crankshaft 430 both extend vertically and are spaced apart, while S6 extends radially along the housing 200.

[0075] It should be noted that, referring to Figure 6 The diagram shown is a simplified schematic of compressor 1000. Figure 6 The dashed arrow indicates the direction of refrigerant flow. A sliding vane connected by a spring is provided on the first vane groove 116. The vane is held in contact with the first piston 431 by the spring force. Therefore, the first piston 431 and the vane divide the low-pressure compression chamber 111 into an intake zone 112 and a compression zone 113. During the rotation of the first piston 431, the sizes of the intake zone 112 and the compression zone 113 gradually change. Taking the center line S8 of the first vane groove 116 as the 0° line, the interval from 0° to 10° in the direction opposite to the rotation direction of the crankshaft 430 is the first exhaust port 115 of the low-pressure compression chamber 111. Therefore, when c is less than 10°, the distance between the exhaust port of the second enthalpy-increasing assembly 600 and the first exhaust port 115 of the low-pressure compression chamber 111 is too close, which can easily cause structural interference. The interval from 0° to 180° is mainly the compression zone 113, and the interval from 180° to 360° is the intake zone 112. When c is greater than 180°, the exhaust port of the second enthalpy-increasing component 600 is located within the intake zone 112. To ensure air intake, the exhaust pressure of the second enthalpy-increasing component 600 will be greater than the pressure within the intake zone 112. This will cause some refrigerant to be discharged from the first intake port 114 of the first cylinder 110, reducing the amount of refrigerant supplied. Therefore, by rationally designing the relative positions of the exhaust port of the second enthalpy-increasing component 600 and the low-pressure compression chamber 111, structural interference can be avoided, while increasing the amount of refrigerant supplied, enabling the compressor 1000 to be suitable for low-temperature heating or high-temperature cooling applications.

[0076] Reference Figure 7As shown in the embodiment of the present invention, the second cylinder 160 is provided with a second sliding vane groove 162. On the projection plane along the axial projection of the crankshaft 430, the center line of the second sliding vane groove 162 is S13. S13 can extend along the radial direction of the housing 200, for example, parallel to the sliding direction of the vane, and perpendicular to the axis S4 of the crankshaft 430. The line connecting the center of the first enthalpy-increasing component 500 and the rotation center of the crankshaft 430 is S7. The center of the first enthalpy-increasing component 500 is located on the center line S5 of the first enthalpy-increasing component 500. Rotating from S13 along the rotation direction of the crankshaft 430, the included angle between S7 and S13 is d, satisfying 20°≤d≤350°, for example, d=30°, d=90°, d=150°, d=210°. Among them, the axial center line S5 of the first enthalpy-increasing component 500 extends in the vertical direction, and S7 can extend radially along the housing 200.

[0077] It should be noted that, referring to Figure 8 The diagram shown is a simplified schematic of partition 190. Figure 8 The dashed arrows indicate the direction of refrigerant flow. The partition 190 contains an intermediate cavity 194, which is annular with an air inlet 196 and a connecting hole 195 at each end. The connecting hole 195 connects to the first exhaust port 115 of the low-pressure compression chamber 111, and the air inlet 196 connects to the air inlet of the high-pressure compression chamber 161. Therefore, the area from 0° to 20° is where the air inlet 196 is located, which is a negative pressure area. When d is less than 20°, the replenished refrigerant will be directly discharged from the air inlet 196, rendering the air replenishment ineffective and failing to lower the refrigerant temperature in the intermediate cavity 194. The area from 350° to 360° is where the connecting hole 195 is located. This area is close to the exhaust port of the high-pressure compression chamber 161, resulting in a higher temperature and potentially causing the replenished refrigerant temperature to rise, thus failing to lower the refrigerant temperature in the intermediate cavity 194. Therefore, by rationally designing the relative positions of the exhaust port of the second enthalpy-increasing component 600 and the intermediate cavity 194, it is possible to ensure that the refrigerant discharged from the second enthalpy-increasing component 600 and the refrigerant in the intermediate cavity 194 are mixed before entering the high-pressure compression cavity 161, and the temperature of the refrigerant in the intermediate cavity 194 can be reduced, thereby reducing the power consumption required by the high-pressure compression cavity 161 when compressing the refrigerant.

[0078] Reference Figure 5As shown in the embodiment of the present invention, the included angle between S6 and S7 relative to the axis of crankshaft 430 is e, satisfying: 10°≤e≤180°, for example, e=30°, e=90°, e=120°, e=150°. It is understood that if e is less than 10° or greater than 180°, the distance between the first enthalpy-increasing component 500 and the second enthalpy-increasing component 600 is too small, and their structures are prone to interference, leading to increased installation difficulty. Therefore, a reasonable design of the positions of the first enthalpy-increasing component 500 and the second enthalpy-increasing component 600 facilitates their installation, is beneficial for pipeline layout, and improves installation efficiency.

[0079] To improve the overheating of the refrigerant in the second cavity 191, refer to Figure 9 As shown, in an embodiment of the present invention, the second cylinder 160 is provided with a second sliding vane groove 162. The second sliding vane groove 162 is used to install a spring and a sliding vane. The sliding vane and the spring are connected, and the spring enables the sliding vane and the second piston 432 to remain in contact. Along the axial projection plane of the crankshaft 430, taking the center line S13 of the second sliding vane groove 162 as the starting point and rotating S9 along the rotation direction of the crankshaft 430, a region with a rotation angle between 0° and 210° is defined as a set region. The projection of the second cavity 191 lies within this set region. It should be noted that the center line S13 of the second sliding vane groove 162 is a symmetrical center line.

[0080] Understandably, the high-pressure compression chamber 161 is primarily an intake region between 0° and 210°, and primarily an exhaust region between 210° and 360°. The temperature in the exhaust region is higher than that in the intake region. Therefore, setting the projection of the second chamber 191 within the 0° to 210° range reduces the temperature rise caused by heat exchange between the refrigerant in the second chamber 191 and the exhaust region of the high-pressure compression chamber 161. This improves the refrigerant overheating situation in the second chamber 191, reduces the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and improves the energy efficiency of the compressor 1000.

[0081] Reference Figure 9 As shown, Figure 9The dashed arrows indicate the flow direction of the refrigerant. In an embodiment of the invention, the partition 190 is provided with a connecting hole 195 at the outlet of the connecting channel and an air inlet 196 at the inlet of the high-pressure compression chamber 161. Therefore, the low-pressure compression chamber 111 can discharge the compressed refrigerant into the first chamber 131, and then sequentially through the connecting channel, connecting hole 195, second chamber 191, and air inlet 196, finally entering the high-pressure compression chamber 161. The jet hole 197 is located on the path of the refrigerant flowing from the connecting hole 195 to the air inlet 196. That is, the jet hole 197 can be located in the second chamber 191 away from the connecting hole 195 and the air inlet 196, which can avoid structural interference and facilitate installation. Furthermore, this allows sufficient time for the refrigerant delivered by the first enthalpy-increasing component 500 and the refrigerant in the second cavity 191 to mix, thereby reducing the temperature of the refrigerant in the second cavity 191, reducing the power consumption required when the high-pressure compression chamber 161 compresses the refrigerant, and further improving the performance of the compressor 1000 in low-temperature heating and high-temperature cooling.

[0082] Continue to refer to Figure 9 As shown in the embodiment of the present invention, on the projection plane along the axis of the crankshaft 430, the central axis of the connecting hole 195 and the axis S4 of the crankshaft 430 are parallel to each other and spaced apart. The line connecting the center of the connecting hole 195 and the rotation center of the crankshaft 430 is S11. The central axis of the jet hole 197 is S10, which extends radially along the housing 200. S10 may intersect the central axis S4 of the crankshaft 430, or S10 and S4 may not intersect but are perpendicular to each other. The angle f formed between S10 along the rotation direction of the crankshaft 430 and S11 satisfies: 5°≤f≤150°, for example, f=10°, f=30°, f=90°, f=120°. When f is less than 5°, the distance between the jet hole 197 and the connecting hole 195 is relatively close, which can easily cause structural interference and make installation difficult. When f is greater than 150°, the distance between the jet port 197 and the inlet port 196 is relatively close. The refrigerant ejected from the first enthalpy-increasing component 500 does not have enough time to mix with the refrigerant in the second chamber 191, resulting in poor cooling. Furthermore, the refrigerant pressure drawn into the high-pressure compression chamber 161 is different, which can easily cause pulsations. Therefore, a reasonable design of the value of f can avoid structural interference, facilitate installation, and ensure that the refrigerant delivered by the first enthalpy-increasing component 500 has sufficient time to mix with the refrigerant in the second chamber 191. This reduces the temperature of the refrigerant in the second chamber 191, decreases the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and further improves the compressor 1000's performance in low-temperature heating and high-temperature cooling.

[0083] Reference Figure 10As shown in the embodiment of the present invention, the projection plane along the axial direction of the crankshaft 430 shows that the central axis of the air intake 196 and the axis S4 of the crankshaft 430 are parallel to each other and spaced apart. The line connecting the center of the air intake 196 and the rotation center of the crankshaft 430 is S12. The angle between S12 and S10 along the rotation direction of the crankshaft 430 is g, which satisfies: 0° < g ≤ 90°, for example, g = 30°, g = 45°, g = 60°, g = 75°. When g = 0°, the jet port 197 and the air intake 196 coincide, which easily causes structural interference and increases the difficulty of manufacturing and assembly. When g is greater than 90°, the refrigerant discharged by the first enthalpy-increasing component 500 needs to travel a longer distance to enter the air intake 196, increasing flow loss. The temperature of the intake area of ​​the high-pressure compression chamber 161 changes gradually, and the temperature is lower closer to the air intake 196. When g is greater than 90°, the distance between the jet port 197 and the air inlet 196 is relatively large, which can easily lead to the refrigerant ejected by the first enthalpy-increasing component 500 undergoing a longer heating time. Therefore, by properly designing the value of g, structural interference between the jet port 197 and the air inlet 196 can be avoided, while flow losses and overheating of the refrigerant ejected by the first enthalpy-increasing component 500 can be reduced.

[0084] In an embodiment of the present invention, the jet port 197 is located on the side of the connecting hole 195 opposite to the air intake port 196, in the opposite direction to the rotation direction of the crankshaft 430; that is, the connecting hole 195 is located between the jet port 197 and the air intake port 196. It is understood that placing the jet port 197 on the side of the connecting hole 195 opposite to the air intake port 196 also allows for the replenishment of refrigerant within the second cavity 191, thereby increasing the intake volume of the high-pressure compression chamber 161.

[0085] Reference Figure 11 As shown, a reservoir for storing refrigeration oil 240 is formed at the bottom of the casing 200. Refrigeration oil 240, also known as lubricating oil, possesses suitable viscosity, good oil-water separation properties, corrosion resistance, and good oxidation resistance, among other characteristics. Refrigeration oil 240 is miscible with the refrigerant, serving functions such as lubrication and energy regulation. Due to the high pressure and temperature inside the casing 200, the refrigeration oil 240 maintains a relatively high temperature, typically between 90℃ and 100℃. Since the first cavity 131 is located slightly below the inner cavity 210, it is relatively close to the refrigeration oil 240. Furthermore, the refrigerant temperature inside the first cavity 131 is lower than the temperature of the refrigeration oil 240, making it easier for heat exchange to occur between the refrigerant and the high-temperature refrigeration oil 240, leading to an increase in the refrigerant temperature within the first cavity 131. Since the refrigerant in the first cavity 131 needs to enter the high-pressure compression cavity 161 for secondary compression, the refrigerant density increases when the temperature rises, reducing the air intake of the high-pressure compression cavity 161 and increasing the power consumption of the second cylinder 160 during compression, resulting in a decrease in the energy efficiency of the compressor 1000.

[0086] To improve the above problems, refer to Figure 11 As shown in the embodiment of the present invention, the pump body assembly 100 further includes a heat insulation cover 140, which covers at least a portion of the structure of the lower muffler 130, for example, covering a portion of the structure of the lower muffler 130, or completely covering the lower muffler 130. A heat insulation cavity 141 is formed between the heat insulation cover 140 and the lower muffler 130, and the heat insulation cavity 141 is isolated from the first cavity 131. The heat insulation cavity 141 can be evacuated to reduce air convection and lower the thermal conductivity, thereby reducing the temperature rise caused by heat exchange with the refrigerant in the first cavity 131, thus reducing power consumption during high-pressure compression and improving energy efficiency.

[0087] It should be noted that two temperature cloud maps of the pump body assembly 100 with and without the heat insulation cavity 141 were generated through simulation. The comparison shows that the refrigerant temperature in the first cavity 131 is lower with the heat insulation cavity 141 installed than without it. Therefore, installing the heat insulation cavity 141 provides a better effect, effectively reducing the temperature rise of the refrigerant in the first cavity 131 due to heat exchange.

[0088] In another embodiment of the present invention, an insulating medium can be provided within the heat insulation cavity 141. For example, it can be filled with refrigeration oil 240, high-temperature resistant polystyrene, or other insulating media that do not react with the refrigerant or refrigeration oil 240. It is understood that by providing an insulating medium within the heat insulation cavity 141, the sealing requirements for the heat insulation cavity 141 are not high. Even if there are gaps at the connection between the heat insulation cover 140 and the lower muffler 130 or the lower bearing 120, the insulating medium can still provide insulation. Therefore, the thickness of the heat insulation cover 140 can be made thinner, the sealing requirements for the connection are not high, the production process can be simplified, the yield rate can be improved, and the manufacturing cost can be reduced.

[0089] Furthermore, in embodiments of the present invention, the refrigerant oil 240 in the oil bath can be directly used for heat insulation. For example, the edge of the heat insulation cover 140 and the lower muffler 130 are connected by spot welding, thus creating a gap between the heat insulation cover 140 and the lower muffler 130, allowing some refrigerant oil 240 to enter the heat insulation cavity 141 through the gap. Since the refrigerant oil 240 in the heat insulation cavity 141 does not participate in the refrigerant circulation and its position remains essentially unchanged, there is a temperature gradient between the refrigerant oil 240 in the heat insulation cavity 141 and the refrigerant oil 240 in the oil bath. That is, the temperature of the refrigerant oil 240 in the heat insulation cavity 141 near the first cavity 131 is lower, and the temperature near the oil bath is slightly higher. Therefore, the presence of refrigerant oil 240 in the heat insulation cavity 141 can also provide a certain degree of heat insulation. It should be noted that, in another embodiment, in addition to entering the heat insulation cavity 141 through the gap, the refrigeration oil 240 can also enter the heat insulation cover 140 through a through hole 142 provided on the heat insulation cover 140. The appropriate solution can be selected according to the actual situation.

[0090] It is understandable that when the insulation chamber 141 is insulated with refrigeration oil 240, during the long-term operation of the compressor 1000, the temperature of the refrigeration oil 240 in the insulation chamber 141 will eventually tend to be the same as the temperature of the refrigeration oil 240 in the oil sump, which will lead to a deterioration in the insulation effect, resulting in greater power consumption required for two-stage or multi-stage compression, and affecting the energy efficiency of the compressor 1000.

[0091] Therefore, referring to Figure 11 As shown in the embodiment of the present invention, the pump body assembly 100 further includes a flow guide channel 180, which connects the third chamber 171 and the heat insulation chamber 141. Therefore, in addition to entering the inner cavity 210 of the housing 200, a portion of the refrigerant discharged from the third chamber 171 will also enter the heat insulation chamber 141 through the flow guide channel 180. When the bottom of the heat insulation chamber 141 is provided with a through hole 142, when the crankshaft 430 or other components agitate the oil pool, refrigerant oil 240 will enter the heat insulation chamber 141 through the through hole 142. The refrigerant enters the heat insulation chamber 141 through the flow guide channel 180. Since the refrigerant at this time has been compressed by the second cylinder 160, it has a high pressure and temperature (around 60°C), which can squeeze the refrigerant oil 240 out of the through hole 142, so that the heat insulation chamber 141 is filled with refrigerant at a temperature of around 60°C. Compared to the refrigeration oil 240 at 90℃-100℃, the refrigerant filled in the insulation cavity 141 at around 60℃ provides a certain degree of insulation, effectively reducing the temperature rise caused by heat exchange between the refrigeration oil 240 and the refrigerant in the first cavity 131. This reduces power consumption during high-pressure compression and improves energy efficiency. Simultaneously, the insulation cover 140 can be made thinner, with less stringent requirements for sealing connections, simplifying production, increasing yield, and reducing manufacturing costs.

[0092] To address the issues of unbalanced torque, high vibration, and low efficiency in the low-pressure compression chamber 111 of the pump body assembly 100, referencing Figure 12 As shown, in the embodiments of the present invention, the total height of the low-pressure compression chamber 111 is L1 (in mm), and the maximum diameter of the low-pressure compression chamber 111 is D1 (in mm), L1 / D1 = h, satisfying: 1.3 ≤ h ≤ 3.8, for example, h = 1.5, h = 2, h = 2.5, h = 3.5. It should be noted that when multiple first cylinders 110 are provided, the multiple first cylinders 110 are arranged vertically and connected to each other. The total height of the low-pressure compression chamber 111 refers to the sum of the heights of the low-pressure compression chambers 111 of each first cylinder 110, and the maximum diameter of the low-pressure compression chamber 111 refers to the low-pressure compression chamber 111 with the largest diameter among all the low-pressure compression chambers 111. When there is only one first cylinder 110, that is, only one low-pressure compression chamber 111, the total height of the low-pressure compression chamber 111 is the height of this single low-pressure compression chamber 111, and the maximum diameter is the diameter of this single low-pressure compression chamber 111.

[0093] Since the outer diameter of the first cylinder 110 is determined, the inner diameter of the low-pressure compression chamber 111 is usually also determined to ensure the strength of the first cylinder 110. To achieve different displacements, the height of the first cylinder 110 usually needs to be adjusted. The torque inside the low-pressure compression chamber 111 is determined by its height, diameter, eccentricity, and pressure difference (the difference between the intake and exhaust pressures of the low-pressure compression chamber 111). With a constant pressure difference, the larger the diameter and the higher the height of the low-pressure compression chamber 111, the heavier the load and the greater the torque. Therefore, when h is less than 1.3, the total height of the low-pressure compression chamber 111 is low, and the radial dimension is large, leading to an increase in the radial dimension of the pump body assembly 100, increasing its volume and weight, and raising costs. When h is greater than 3.8, the total height of the low-pressure compression chamber 111 is high, and the radial dimension is small, resulting in too large a torque. This leads to insufficient structural strength of the first cylinder 110, making it prone to deformation and reducing reliability. Therefore, by rationally designing the ratio of the total height to the maximum diameter of the low-pressure compression chamber 111, the strength of the first cylinder 110 can be improved, thereby resisting the torque inside the low-pressure compression chamber 111, reducing vibration, lowering costs, and improving energy efficiency.

[0094] Reference Figure 13As shown, in the embodiment of the present invention, the total height of the high-pressure compression chamber 161 is L2 (in mm), the maximum diameter of the high-pressure compression chamber 161 is D2 (in mm), and L2 / D2 = j, satisfying: 1.4 ≤ j ≤ 2.8, for example, j = 1.5, j = 1.8, j = 2, j = 2.5. Since the height of the second cylinder 160 is usually lower than that of the first cylinder 110, the numerical range of j differs from that of a. Once the outer diameter of the second cylinder 160 is determined, the inner diameter of the high-pressure compression chamber 161 is usually also determined to ensure the strength of the second cylinder 160. To allow the second cylinder 160 to obtain different displacements, the height of the second cylinder 160 usually needs to be adjusted. The torque inside the high-pressure compression chamber 161 is determined by its height, diameter, eccentricity, and pressure difference (the difference between the intake and exhaust pressures of the high-pressure compression chamber 161). With a constant pressure difference, the larger the diameter and the higher the height of the high-pressure compression chamber 161, the heavier the load and the greater the torque. Therefore, when j is less than 1.4, the total height of the high-pressure compression chamber 161 is low, and its radial dimension is large, leading to an increase in the radial dimension of the pump body assembly 100, increasing its volume and weight, and raising costs. When j is greater than 2.8, the total height of the high-pressure compression chamber 161 is high, and its radial dimension is small, resulting in excessive torque. This leads to insufficient structural strength of the second cylinder 160, making it prone to deformation and reducing reliability. Therefore, rationally designing the ratio of the total height to the maximum diameter of the high-pressure compression chamber 161 can improve the strength of the second cylinder 160, thereby resisting the torque inside the high-pressure compression chamber 161, reducing vibration, lowering costs, and improving energy efficiency.

[0095] It should be noted that when multiple second cylinders 160 are provided, the multiple second cylinders 160 are arranged vertically and connected to each other. The total height of the high-pressure compression chamber 161 refers to the sum of the heights of the high-pressure compression chambers 161 of each second cylinder 160, and the maximum diameter of the high-pressure compression chamber 161 refers to the high-pressure compression chamber 161 with the largest diameter among all the high-pressure compression chambers 161. When there is only one second cylinder 160, that is, only one high-pressure compression chamber 161, the total height of the high-pressure compression chambers 161 is the height of this single high-pressure compression chamber 161, and the maximum diameter is the diameter of this single high-pressure compression chamber 161.

[0096] In the embodiments of the present invention, the ratio of the total height of the low-pressure compression chamber 111 to the total height of the high-pressure compression chamber 161 is k, satisfying: 1 ≤ k ≤ 1.7. Once the diameters, eccentricities, and intake / exhaust pressure differences of the low-pressure compression chamber 111 and the high-pressure compression chamber 161 are determined, the factors affecting the load and torque mainly lie in the heights of the low-pressure compression chamber 111 and the high-pressure compression chamber 161. Since the high-pressure compression chamber 161 requires a higher output pressure refrigerant, its total height is lower than that of the low-pressure compression chamber 111, thereby increasing the refrigerant output pressure and improving the stability of the compression process. Assuming the height of the low-pressure compression chamber 111 remains constant, when k is less than 1, the height of the high-pressure compression chamber 161 is higher, increasing the gap between the second piston 432 and the high-pressure compression chamber 161, which exacerbates internal leakage and affects compression efficiency. When k is greater than 1.7, the height of the high-pressure compression chamber 161 decreases. To maintain the displacement, the diameter of the high-pressure compression chamber 161 increases, leading to a decrease in the strength of the second cylinder 160. Under the same load, the deformation of the second cylinder 160 increases, and the leakage further increases, which in severe cases leads to increased power consumption and decreased energy efficiency. Therefore, a reasonable design of the value of k can ensure the strength of the first cylinder 110 and the second cylinder 160, reduce leakage, and improve the reliability of the first cylinder 110 and the second cylinder 160.

[0097] To reduce the work done by the compressor 1000 to overcome friction during startup and operation, refer to Figure 14 As shown, in an embodiment of the present invention, the first cylinder 110 is provided with a low-pressure compression chamber 111, and the second cylinder 160 is provided with a high-pressure compression chamber 161. The crankshaft 430 includes a main shaft 435, a first eccentric portion 433, and a second eccentric portion 434. The first eccentric portion 433 and the second eccentric portion 434 are spaced apart on the main shaft 435, and the first piston 431 and the second piston 432 are respectively sleeved on the first eccentric portion 433 and the second eccentric portion 434.

[0098] Continue to refer to Figure 14As shown, the contact length between the first eccentric part 433 and the first piston 431 is L3 (in mm), and the height of the low-pressure compression chamber 111 is L4 (in mm). L3 / L4 = n, satisfying 0.28 ≤ n ≤ 0.9, for example, n = 0.3, n = 0.5, n = 0.6, n = 0.8. When n is less than 0.28, the contact length between the first eccentric part 433 and the first piston 431 is short, and the first piston 431 is prone to wobbling, deformation, and misalignment, affecting transmission accuracy. When n is greater than 0.9, the contact length between the first eccentric part 433 and the first piston 431 is long, making it difficult to reduce friction. Since the height of the low-pressure compression chamber 111 is equal to or nearly equal to the height of the first piston 431, n is limited to the range of 0.28 to 0.9. This reduces the friction between the first eccentric part 433 and the first piston 431, thereby reducing the work done by the compressor 1000 to overcome friction during startup and operation, and improving the energy efficiency of the compressor 1000.

[0099] The contact length between the second eccentric part 434 and the second piston 432 is L5 (in mm), and the height of the high-pressure compression chamber 161 is L6 (in mm). L5 / L6 = p, satisfying 0.28 ≤ p ≤ 0.9, for example, p = 0.3, p = 0.5, p = 0.6, p = 0.8. When p is less than 0.28, the contact length between the second eccentric part 434 and the second piston 432 is short, and the second piston 432 is prone to wobbling, deformation, and misalignment, affecting transmission accuracy. When p is greater than 0.9, the contact length between the second eccentric part 434 and the second piston 432 is long, making it difficult to reduce friction. Since the height of the high-pressure compression chamber 161 is equal to or nearly equal to the height of the second piston 432, p is limited to the range of 0.28 to 0.9. This reduces the friction between the second eccentric part 434 and the second piston 432, thereby reducing the work done by the compressor 1000 to overcome friction during startup and operation, and improving the energy efficiency of the compressor 1000.

[0100] In embodiments of the present invention, the contact length L3 between the first eccentric portion 433 and the first piston 431 is less than or equal to the contact length L5 between the second eccentric portion 434 and the second piston 432. It is understood that because the refrigerant pressure in the high-pressure compression chamber 161 is relatively high, the pressure applied to the second piston 432 is also high, requiring the second eccentric portion 434 to possess sufficient strength to resist deformation. Conversely, the refrigerant pressure in the low-pressure compression chamber 111 is relatively lower than that in the high-pressure compression chamber 161, thus the strength requirement for the first eccentric portion 433 is less than that for the second eccentric portion 434. To further reduce friction, L3 can be designed to be smaller than L5. Therefore, by rationally designing the dimensions of L3 and L5, it is possible to ensure that the first eccentric portion 433 and the second eccentric portion 434 possess appropriate strength while also reducing the friction between the first piston 431 and the first eccentric portion 433, and between the second piston 432 and the second eccentric portion 434.

[0101] Reference Figure 15 As shown, in an embodiment of the present invention, the span between adjacent first eccentric portions 433 and second eccentric portions 434 is H1, where H1 refers to the distance between the end of the first eccentric portion 433 furthest from the second eccentric portion 434 and the end of the second eccentric portion 434 furthest from the first eccentric portion 433. The diameter of the main shaft 435 is D5 (in mm), and H1 / D5 = m, satisfying: 2.5 ≤ m ≤ 4.5, for example, m = 3, m = 3.5, m = 3.9, m = 4. It can be understood that when the diameter of the main shaft 435 remains unchanged, assuming m is less than 2.5, the span between the first eccentric portion 433 and the second eccentric portion 434 is small, and there is not enough space between the first eccentric portion 433 and the second eccentric portion 434 to place the partition member 190. Since the partition member 190 generally has an intermediate cavity 194, it is easy to reduce the volume of the intermediate cavity 194, making it difficult to play the role of mixing refrigerant. Assuming m is greater than 4.5, the span between the first eccentric part 433 and the second eccentric part 434 is large, reducing the strength of the crankshaft 430. Therefore, by rationally designing the size of m, the crankshaft 430 can be guaranteed to have sufficient strength, and there can be a suitable space between the first eccentric part 433 and the second eccentric part 434 to arrange the partition 190, ensuring the flexibility of the crankshaft 430 and that the volume of the intermediate cavity 194 is of a suitable size. This can improve the stability and energy efficiency of the compressor 1000 and reduce the vibration and noise of the compressor 1000.

[0102] Continue to refer to Figure 15As shown, in the embodiment of the present invention, the diameter of the first eccentric part 433 is D3 (in mm), and the diameter of the second eccentric part 434 is D4 (in mm), satisfying: 1.5 ≤ H1 / max(D3, D4) ≤ 2.8. It should be noted that max(D3, D4) represents the largest one. For example, if D4 is greater than D3, then 1.5 ≤ H1 / D4 ≤ 2.8; if D4 is less than D3, then 1.5 ≤ H1 / D3 ≤ 2.8. It can be understood that the diameters of the first eccentric part 433 and the second eccentric part 434 affect their connection strength with the main shaft 435. The larger the cross-sectional area of ​​the first eccentric part 433 and the second eccentric part 434 connected to the main shaft 435, the higher the strength of the crankshaft 430. Therefore, when H1 / max(D3, D4) is greater than 2.8, the overall strength of the crankshaft 430 is low, making it prone to bending deformation. This also easily leads to stress concentration at the connection between the first eccentric part 433, the second eccentric part 434, and the main shaft 435, increasing power consumption and reducing reliability. When H1 / max(D3, D4) is less than 1.5, the crankshaft 430 has excessive strength, resulting in a heavy crankshaft. The power consumption of the compressor 1000 is related to the weight of the crankshaft 430 itself; excessive strength in the design leads to additional power consumption, which is detrimental to the performance improvement of the compressor 1000. Therefore, rationally designing the relationship between the diameters of the first eccentric part 433 and the second eccentric part 434 and H1 can reduce the weight of the crankshaft 430 while ensuring sufficient strength, thus reducing power consumption and improving the performance of the compressor 1000.

[0103] To address the issue of significant refrigerant flow loss, refer to Figure 16 As shown, in one embodiment of the pump assembly 100 of the present invention, the first chamber 131 and the second chamber 191 of the pump assembly 100 are connected by a connecting channel 102. The ratio of the minimum flow area of ​​the connecting channel 102 to the displacement of the low-pressure compression chamber 111 is q, which satisfies: q ≥ 0.75, for example, q = 1, q = 2, q = 3, q ​​= 5, q = 6.8. If q is less than 0.75, the flow area of ​​the connecting channel 102 is too small, the flow velocity of the refrigerant increases, the sum of the squares of the flow velocity and the loss are positively correlated, the friction between the refrigerant and the wall of the connecting channel 102 increases, resulting in increased friction loss; and if the connecting channel 102 undergoes abrupt changes, such as when the connecting channel 102 suddenly turns, the refrigerant with a higher flow velocity will directly impact the wall of the connecting channel 102, resulting in increased pressure loss. As q gradually increases, the COP first increases and then decreases. Therefore, by rationally designing the ratio between the minimum flow area of ​​the connecting channel 102 and the displacement of the low-pressure compression chamber 111, the flow velocity of the refrigerant in the connecting channel 102 can be reduced, friction loss and pressure loss can be reduced, thereby reducing the flow loss of the refrigerant and improving the energy efficiency of the compressor 1000.

[0104] It should be noted that the unit of minimum flow area is mm.2 The unit of displacement is cc, and the unit of volume is ml. In all subsequent embodiments, unless otherwise specified, the units of minimum flow area, displacement and volume are the above units.

[0105] In embodiments of the present invention, the ratio of the minimum flow area of ​​the connecting channel 102 to the displacement of the high-pressure compression chamber 161 is x, satisfying x ≥ 1.95, for example, x = 2.7, x = 5, x = 10, x = 17. It is understood that since the displacement of the high-pressure compression chamber 161 is generally smaller than that of the low-pressure compression chamber 111, the minimum value of x is larger than the minimum value of q. When x is less than 1.95, the flow area of ​​the connecting channel 102 is too small, the refrigerant flow velocity increases, the friction between the refrigerant and the wall of the connecting channel 102 increases, leading to increased friction loss; and when the connecting channel 102 undergoes abrupt changes, such as a sudden turn, the refrigerant with a higher flow velocity will directly impact the wall of the connecting channel 102, leading to increased pressure loss. As x gradually increases, the COP first increases and then decreases. Therefore, by rationally designing the ratio between the minimum flow area of ​​the connecting channel 102 and the displacement of the low-pressure compression chamber 111, the flow velocity of the refrigerant in the connecting channel 102 can be reduced, friction loss and pressure loss can be reduced, thereby reducing the flow loss of the refrigerant and improving the energy efficiency of the compressor 1000.

[0106] In embodiments of the present invention, the ratio y of the minimum flow area of ​​the connecting channel 102 to the total volume of the intermediate cavity 194 satisfies 6.8 ≥ y ≥ 0.15, for example, y = 0.2, y = 2, y = 4, y = 6.8. As y gradually increases, the COP first increases and then decreases. If y is less than 0.15, the minimum flow area of ​​the connecting channel 102 is too small or the total volume of the intermediate cavity 194 is too large. When the minimum flow area of ​​the connecting channel 102 is too small, the flow resistance of the refrigerant increases, and it takes more time to fill the intermediate cavity 194, resulting in a decrease in the exhaust capacity of the low-pressure compression cavity 111 and a reduction in the volumetric efficiency of the compressor 1000. When the total volume of the intermediate cavity 194 is too large, it increases the total volume of the pump body assembly 100, and more refrigerant is needed to fill the intermediate cavity 194. This causes the low-pressure compression chamber 111 to take longer to discharge enough gas into the intermediate cavity 194, and the residence time of the refrigerant in the intermediate cavity 194 becomes longer. The refrigerant is more likely to exchange heat with the high-temperature lubricating oil outside the pump body assembly 100, resulting in a temperature rise. This, in turn, increases the energy consumption required for the high-pressure compression chamber 161 to compress the refrigerant, leading to a decrease in the overall efficiency of the compressor 1000.

[0107] If y is greater than 6.8, the minimum flow area of ​​the connecting channel 102 is too large or the total volume of the intermediate cavity 194 is too small. When the minimum flow area of ​​the connecting channel 102 is too large, the volume of the pump assembly 100 increases, which has a greater impact on the overall size of the compressor 1000. When the total volume of the intermediate cavity 194 is too small, the amount of refrigerant that the intermediate cavity 194 can hold is limited, which causes the low-pressure compression cavity 111 to frequently discharge refrigerant into the intermediate cavity 194 to meet the needs of the high-pressure compression cavity 161. Frequent discharge increases the workload and energy efficiency of the compressor 1000.

[0108] Therefore, by rationally designing the range of the ratio between the minimum flow area of ​​the connecting channel 102 and the total volume of the intermediate cavity 194, the pump body assembly 100 has a compact structure, which can reduce the resistance during refrigerant flow, reduce the residence time of the refrigerant in the intermediate cavity 194, reduce the temperature rise of the refrigerant in the intermediate cavity 194, reduce the energy consumption required by the high-pressure compression chamber 161, and improve the volumetric efficiency of the compressor 1000.

[0109] Because the exhaust process of the low-pressure compression chamber 111 is intermittent and discontinuous, it exhibits significant pulsation characteristics, which greatly affects the intake process of the next stage. Since pulsation is inversely proportional to volume (i.e., the larger the volume, the smaller the pulsation), in order to reduce the pulsation of the compressor 1000, in this embodiment of the invention, the intermediate chamber 194 includes at least two chambers connected by a connecting channel 102, which increases the volume of the intermediate chamber 194 and thus reduces the impact of pulsation. The volume ratio z of the two adjacent chambers satisfies: 0.2 ≤ z ≤ 5, for example, z = 0.5, z = 1.5, z = 2, z = 3. If z is less than 0.2 or greater than 5, the volume difference between the two adjacent chambers is too large, leading to an increased pressure change amplitude of the refrigerant as it moves from one chamber to another, which easily generates pulsation. Therefore, by limiting z to the range of 0.2 to 5 and by rationally designing the volume of two adjacent chambers, the pressure change amplitude when the refrigerant enters from one chamber to another can be reduced, thereby reducing pulsation, reducing refrigerant flow loss, increasing the intake volume of the high-pressure compression chamber 161, and thus improving the performance of the compressor 1000.

[0110] In embodiments of the present invention, the arrangement of the multiple cavities can be such that the volume of the cavity near the high-pressure compression cavity 161 is smaller than the volume of the cavity near the low-pressure compression cavity 111. For example, the refrigerant discharged from the low-pressure compression cavity 111 passes sequentially through the first cavity 131 and the second cavity 191, and finally enters the high-pressure compression cavity 161. That is, along the flow direction of the refrigerant, the volume of the first cavity 131 is larger than the volume of the second cavity 191. In another embodiment, the volume of the cavity near the high-pressure compression cavity 161 can also be larger than the volume of the cavity near the low-pressure compression cavity 111. For example, to improve exhaust efficiency, the refrigerant from the low-pressure compression cavity 111 is simultaneously discharged to the first cavity 131 and the second cavity 191. Since the first cavity 131 is located below the first cylinder 110, the refrigerant needs to flow upward to the second cavity 191, resulting in a long flow path and significant losses. To balance the upward and downward exhaust, that is, along the flow direction of the refrigerant, the volume of the first cavity 131 is smaller than the volume of the second cavity 191. In another embodiment, the volume of the multiple cavities may not be distributed in a regular pattern along the flow direction of the refrigerant, and a suitable solution may be selected based on the actual situation.

[0111] Reference Figure 2 As shown, in the embodiment of the present invention, the sum of the volumes of the first intake pipe 510, the first intermediate housing 520, and the first exhaust pipe 530 is V1, and the volume of the intermediate cavity 194 is V2, satisfying: V1 ≥ 0.5V2, for example, V1 = 0.8V2, V1 = V2, V1 = 1.2V2, V1 = 1.5V2. It is understood that if V1 is less than 0.5V2, the volume of the first enthalpy-increasing component 500 is too small, the refrigerant replenishment is insufficient, and the pulsation during refrigerant replenishment increases, leading to increased vibration amplitude and noise of the compressor 1000. Therefore, a reasonable design of the ratio of the volume of the first enthalpy-increasing component 500 to the volume of the intermediate cavity 194 reduces the pulsation during refrigerant replenishment and improves the performance of the compressor 1000.

[0112] Reference Figure 4As shown, in the embodiment of the present invention, the sum of the volume of the second intake pipe 610, the volume of the second intermediate housing 620, and the volume of the second exhaust pipe 630 is V3, and the displacement of the low-pressure compression chamber 111 is C1, satisfying: V3 ≥ 0.2C1. For example, V3 = 0.4C1, V3 = 0.8C1, V3 = 1.2C1, V3 = 1.5C1. Since the low-pressure compression chamber 111 has both intake and compression states, the refrigerant supplied by the second enthalpy-increasing component 600 to the low-pressure compression chamber 111 is intermittent, and the actual refrigerant replenishment time is relatively short. If V3 is less than 0.2C1, the volume of the second enthalpy-increasing component 600 is too small, the refrigerant replenishment amount is insufficient, and it is difficult to achieve the corresponding effect. Therefore, by rationally designing the relationship between the volume of the second enthalpy-increasing component 600 and the displacement of the low-pressure compression chamber 111, the pulsation impact during the gas replenishment process can be reduced while meeting the gas replenishment requirements, thereby improving the stability of the compressor 1000 and reducing the vibration and noise of the compressor 1000.

[0113] In another embodiment of the present invention, the second enthalpy-increasing component 600 can also be connected to the high-pressure compression chamber 161, and the second enthalpy-increasing component 600 is used to supply refrigerant into the high-pressure compression chamber 161. The displacement of the high-pressure compression chamber 161 is C2, satisfying V3 ≥ 0.2C2, for example, V3 = 0.4C2, V3 = 0.8C2, V3 = 1.2C2, V3 = 1.5C2. Since both intake and compression states exist within the high-pressure compression chamber 161, the second enthalpy-increasing component 600 intermittently supplies refrigerant into the high-pressure compression chamber 161, resulting in a relatively short actual supply time. If V3 is less than 0.2C2, the volume of the second enthalpy-increasing component 600 is too small, resulting in insufficient refrigerant supply and failing to achieve the desired effect. Therefore, by rationally designing the relationship between the volume of the second enthalpy-increasing component 600 and the displacement of the high-pressure compression chamber 161, the pulsation impact during the gas replenishment process can be reduced while meeting the gas replenishment requirements, as well as the vibration and noise of the compressor 1000, thereby improving the stability of the compressor 1000's operation.

[0114] In embodiments of the present invention, the ratio of the sum of the volumes V1 of the first intake pipe 510, the first intermediate housing 520, and the first exhaust pipe 530 to the flow area S1 of the first intake pipe 510 is r1, satisfying 13 ≥ r1 ≥ 1.2, for example, r1 = 1.5, r1 = 2, r1 = 5, r1 = 8, r1 = 12. If r1 is less than 1.2, that is, the volume of the first enthalpy-increasing component 500 is too small or the flow area of ​​the first intake pipe 510 is too large, it is easy to cause pressure fluctuations in the refrigerant, reduce the enthalpy-increasing effect, and increase the noise of the compressor 1000 during operation. If r1 is greater than 13, meaning the volume of the first enthalpy-increasing component 500 is too large or the flow area of ​​the first intake pipe 510 is too small, when the volume of the first enthalpy-increasing component 500 is too large, the density of the refrigerant in the second intermediate shell 620 decreases, resulting in insufficient gas supply and an inability to effectively reduce the temperature of the refrigerant in the intermediate cavity 194, leading to increased energy consumption when the high-pressure compression chamber 161 compresses the refrigerant. When the flow area of ​​the first intake pipe 510 is too small, the intake resistance is high, leading to increased flow loss. Therefore, rationally designing the relationship between the volume of the first enthalpy-increasing component 500 and the flow area of ​​the first intake pipe 510 can reduce pulsation and noise, improve the situation of high intake resistance and increased flow loss, and thus improve the working performance of the compressor 1000.

[0115] In embodiments of the present invention, the ratio of the sum of the volumes V2 of the second intake pipe 610, the second intermediate housing 620, and the second exhaust pipe 630, to the flow area S2 of the second intake pipe 610 is r2, satisfying 1 / 3 ≥ r2 ≥ 1.2, for example, r2 = 1.5, r2 = 2, r2 = 5, r2 = 8, r2 = 12. If r2 is less than 1.2, that is, the volume of the second enthalpy-enhancing component 600 is too small or the flow area of ​​the second intake pipe 610 is too large, it is easy to cause pressure fluctuations in the refrigerant, reduce the enthalpy-enhancing effect, and increase the noise of the compressor 1000 during operation. If r2 is greater than 13, meaning the volume of the second enthalpy-increasing component 600 is too large or the flow area of ​​the second intake pipe 610 is too small, when the volume of the second enthalpy-increasing component 600 is too large, the density of the refrigerant in the second intermediate shell 620 decreases, resulting in insufficient gas supply and an inability to effectively reduce the temperature of the refrigerant in the intermediate cavity 194, leading to increased energy consumption when the high-pressure compression chamber 161 compresses the refrigerant. When the flow area of ​​the second intake pipe 610 is too small, the intake resistance is high, leading to increased flow loss. Therefore, rationally designing the relationship between the volume of the second enthalpy-increasing component 600 and the flow area of ​​the second intake pipe 610 can reduce pulsation and noise, improve the situation of high intake resistance and increased flow loss, and thus improve the working performance of the compressor 1000.

[0116] According to Figure 3As shown in the embodiment of the present invention, the ratio s of the minimum flow area of ​​the intake passage 101 to the displacement of the low-pressure compression chamber 111 satisfies: 1 ≥ s ≥ 0.039. For example, s can be 0.8, 0.6, 0.5, 0.35, 0.2, 0.1, etc. It should be noted that the unit of flow area is mm. 2 The unit of displacement is cc, and this unit will be used in subsequent embodiments. It is understandable that when s is less than 0.039, the minimum flow area of ​​the intake passage 101 is too small, resulting in significant refrigerant flow loss and hindering the increase in refrigerant supply; when s is greater than 1, the minimum flow area of ​​the intake passage 101 is too large, easily leading to refrigerant backflow. As the value of s gradually increases, within the range of 0.039 to 1, the COP increase of the compressor 1000 first gradually increases and then decreases. Therefore, a reasonable design of the relationship between the minimum flow cross-sectional area of ​​the first enthalpy-increasing component 500 and the displacement of the low-pressure compression chamber 111 can improve the performance of the compressor 1000 and meet the heating requirements in low-temperature environments. It should be noted that during cooling, COP refers to the ratio of the cooling capacity of the compressor 1000 to the input power; during heating, it is the COP of cooling + 1. The higher the COP value, the higher the efficiency of the compressor 1000, and the more energy-efficient it is.

[0117] In embodiments of the present invention, the ratio of the minimum flow area of ​​the intake passage 101 to the displacement of the high-pressure compression chamber 161 is t, which satisfies: 4.7 ≥ t ≥ 0.18. For example, t can be 4.5, 4.3, 3, 3.8, 3.5, 3, 2.5, 1.6, etc. It should be noted that since the displacement of the high-pressure compression chamber 161 is generally smaller than that of the low-pressure compression chamber 111, the value of t is generally greater than s. It can be understood that when t is less than 0.18, the minimum flow cross-section of the intake passage 101 is too small, which easily increases the refrigerant flow loss and leads to a reduction in the supply. When t is greater than 4.7, it easily leads to refrigerant backflow, increased pressure fluctuations, and affects the performance of the compressor 1000. As the value of t gradually increases, within the range of 0.18 to 6, the performance improvement of the compressor 1000 first increases and then decreases. Therefore, by rationally designing the relationship between the minimum flow cross-sectional area of ​​the first enthalpy-increasing component 500 and the displacement of the high-pressure compression chamber 161, the performance of the compressor 1000 can be improved, meeting the heating requirements in low-temperature environments.

[0118] In embodiments of the present invention, the ratio of the displacement of the low-pressure compression chamber 111 to the displacement of the high-pressure compression chamber 161 is u, satisfying: 0.4 ≤ u ≤ 0.8, for example, u = 0.5, 0.6, 0.7. Taking the displacement of the high-pressure compression chamber 161 as constant as an example, when u is less than 0.4, for low-temperature heating conditions, the displacement of the low-pressure compression chamber 111 is too small, resulting in insufficient heating capacity and a poor user experience; when u is greater than 0.8, the displacement of the low-pressure compression chamber 111 is too large, and the high-pressure compression chamber 161 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 111, resulting in excess performance and a decrease in the volumetric efficiency of the compressor 1000. Therefore, rationally designing the ratio of the displacement of the low-pressure compression chamber 111 to the displacement of the high-pressure compression chamber 161 can improve the high exhaust resistance, reduce vibration and noise, and improve the volumetric efficiency of the compressor 1000.

[0119] Reference Figure 3 As shown, in an embodiment of the present invention, the first cylinder 110 is provided with an intake channel 101, and the outlet pipe of the first enthalpy-enhancing component 500 is inserted into the intake channel 101. The intake channel 101 gradually increases in size towards the first enthalpy-enhancing component 500, thereby facilitating connection with the outlet pipe of the first enthalpy-enhancing component 500 and improving the sealing at the connection point, thus mitigating leakage. In another embodiment of the present invention, the intake channel 101, in addition to employing... Figure 3 The air intake channel 101 can also be in the form of a pipe, as shown in the diagram. The appropriate solution can be selected based on the actual situation.

[0120] A refrigeration device according to one embodiment of the present invention includes the compressor 1000 of the above embodiments. The refrigeration device can be a central air conditioner, a packaged air conditioner, a split air conditioner, a ducted air conditioner, a window air conditioner, etc. By employing the compressor 1000 of the above embodiments, when the pump assembly 100 of the compressor 1000 compresses the refrigerant, the refrigerant is compressed through the low-pressure compression chamber 111 and then enters the high-pressure compression chamber 161 through the intermediate chamber 194 for further compression. This increases the pressure of the discharged refrigerant, thereby increasing the temperature of the refrigerant and increasing the temperature difference with the surrounding environment, thus improving the heating capacity of the compressor 1000 in low-temperature environments. The first enthalpy-increasing component 500 is connected to the intermediate cavity 194, and the second enthalpy-increasing component 600 is connected to the low-pressure compression cavity 111 or the high-pressure compression cavity 161. The first enthalpy-increasing component 500 and the second enthalpy-increasing component 600 are used to supplement the refrigerant, which can increase the intake density of the high-pressure compression cavity 161, increase the discharge volume of the compressor 1000, increase the circulation flow, increase the volumetric efficiency of the compressor 1000, and thus improve the heating capacity of the compressor 1000 in a lower temperature environment.

[0121] Since the refrigeration equipment adopts all the technical solutions of the compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments, which will not be repeated here.

[0122] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. A compressor, characterized in that, include: A pump assembly includes a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is connected to the inlet of the high-pressure compression chamber through the intermediate chamber. The pump assembly includes an upper bearing, a second cylinder, an upper partition, a lower partition, a first cylinder, and a lower bearing connected in sequence. The lower partition, the first cylinder, and the lower bearing enclose the low-pressure compression chamber. The upper bearing, the second cylinder, and the upper partition enclose the high-pressure compression chamber. The lower bearing is equipped with a lower muffler. The lower bearing and the lower muffler enclose a first cavity. The upper partition and the lower partition enclose a second cavity. The first cavity and the second cavity constitute the intermediate chamber. The first cavity and the second cavity are connected through a connecting channel. The pump assembly also includes an upper muffler connected to the upper bearing, and a third cavity is formed between the upper muffler and the upper bearing. A liquid reservoir is connected to the air inlet of the low-pressure compression chamber; A first enthalpy-increasing component is connected to the intermediate cavity, and the first enthalpy-increasing component is used to deliver refrigerant to the intermediate cavity; The second enthalpy-increasing component is connected to the low-pressure compression chamber or the high-pressure compression chamber, and the second enthalpy-increasing component is used to deliver refrigerant to the low-pressure compression chamber or the high-pressure compression chamber. The pump body assembly further includes a heat insulation cover, which covers at least a portion of the structure of the lower muffler. A heat insulation cavity is formed between the heat insulation cover and the lower muffler. The heat insulation cavity is isolated from the first cavity. The heat insulation cover is provided with a through hole. The pump body assembly also includes a flow guiding channel, which connects the third cavity and the heat insulation cavity.

2. The compressor according to claim 1, characterized in that: The volume of the first enthalpy-increasing component is greater than or equal to the volume of the second enthalpy-increasing component.

3. The compressor according to claim 1, characterized in that: The second enthalpy-increasing component is connected to the low-pressure compression chamber. The ratio of the jet pressure of the first enthalpy-increasing component to the jet pressure of the second enthalpy-increasing component is a, which satisfies: 1≤a≤2.

4. The compressor according to claim 1, characterized in that: The second enthalpy-increasing component is connected to the high-pressure compression chamber. The ratio of the jet pressure of the second enthalpy-increasing component to the jet pressure of the first enthalpy-increasing component is b, which satisfies: 1≤b≤2.

5. The compressor according to claim 1, characterized in that: The compressor also includes a housing, the pump assembly is installed inside the housing, the second enthalpy-increasing assembly is installed outside the housing, and the second enthalpy-increasing assembly includes an exhaust pipe that passes through the housing and is fixedly connected to the pump assembly.

6. The compressor according to claim 5, characterized in that: The second enthalpy-increasing component further includes a check valve mechanism for preventing refrigerant from flowing back from the low-pressure compression chamber or the high-pressure compression chamber to the second enthalpy-increasing component.

7. The compressor according to claim 6, characterized in that: The check valve is an exhaust valve seat. The pump body assembly is provided with an air intake channel that connects the exhaust pipe and the low-pressure compression chamber or the high-pressure compression chamber. The exhaust valve seat is installed at the end of the air intake channel away from the exhaust pipe.

8. The compressor according to claim 6, characterized in that: The check valve is a one-way valve, which is installed on the side of the exhaust pipe adjacent to the low-pressure compression chamber or the high-pressure compression chamber.

9. The compressor according to claim 1, characterized in that: The low-pressure compression chamber is provided in multiple ways, and the exhaust ports of the multiple low-pressure compression chambers are all connected to the intermediate chamber; And / or, the high-pressure compression chamber is provided in multiple ways, and the air inlets of the multiple high-pressure compression chambers are all connected to the intermediate chamber.

10. The compressor according to claim 1, characterized in that: The intermediate cavity includes multiple chambers that are connected by a communication channel. The exhaust port of the low-pressure compression chamber is configured to exhaust air into one of the chambers or into each of the multiple chambers.

11. The compressor according to claim 1, characterized in that: The pump assembly further includes an upper bearing, a second cylinder, an upper partition, a lower partition, a first cylinder, and a lower bearing connected sequentially along the axial direction of the pump assembly. The lower partition, the first cylinder, and the lower bearing enclose the low-pressure compression chamber, the upper partition and the lower partition form the intermediate cavity, and the upper bearing, the second cylinder, and the upper partition enclose the high-pressure compression chamber.

12. A refrigeration device, characterized in that: Includes the compressor as described in any one of claims 1 to 11.

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