Compressor and Refrigeration Equipment

Abstract

The present invention discloses a compressor and a refrigeration device, relating to the technical field of compressors. The compressor includes a first cylinder, a partition member, a second cylinder and a crankshaft. By providing a low-pressure compression chamber in the first cylinder and a high-pressure compression chamber in the second cylinder, the refrigerant compressed in the low-pressure compression chamber can enter the high-pressure compression chamber through a first cavity. Since the projection of the first cavity is located within a set area of 0° to 210°, and the area of 0° to 210° is the suction area of the high-pressure compression chamber with a lower temperature, while the area of 210° to 360° is the exhaust area of the high-pressure compression chamber with a higher temperature. Therefore, the first cavity being located within the set area can reduce the temperature rise caused by heat exchange with the exhaust area of the high-pressure compression chamber, thereby improving the overheating of the refrigerant in the first cavity, reducing the power consumption required for the high-pressure compression chamber to compress the refrigerant, and improving the energy efficiency of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a compressor and a refrigeration device. Background Art

[0002] In order to enable a compressor to heat in a low-temperature environment or cool in a high-temperature environment, in related technologies, the compressor compresses the refrigerant in a multi-stage compression manner to increase the pressure of the refrigerant, thereby improving the energy efficiency of the compressor. For example, the compressor is provided with a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The refrigerant compressed in the low-pressure compression chamber enters the high-pressure compression chamber through the intermediate chamber. However, the refrigerant is prone to overheating when discharged into the intermediate chamber, resulting in an increase in the power consumption required for compression in the high-pressure compression chamber and a decrease in the efficiency of the compressor. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. For this purpose, the present invention provides a compressor, which can improve the overheating of the refrigerant in the chamber by reasonably arranging the positions of the chambers, thereby reducing the power consumption required for compressing the refrigerant and improving the energy efficiency of the compressor.

[0004] The present invention also provides a refrigeration device having the above compressor.

[0005] The compressor according to the first aspect embodiment of the present invention includes: a pump body assembly, including a first cylinder, a partition member, and a second cylinder connected in sequence, and a crankshaft rotatably disposed in the first cylinder and the second cylinder. A first chamber is provided in the partition member, a low-pressure compression chamber is provided in the first cylinder, the low-pressure compression chamber discharges gas to the first chamber, a high-pressure compression chamber is provided in the second cylinder, and the first chamber supplies gas to the high-pressure compression chamber; wherein, the second cylinder is provided with a sliding vane groove. On the projection plane along the axial projection of the crankshaft, starting from the center line of the sliding vane groove and rotating along the rotation direction of the crankshaft, the region where the rotation angle is between 0° and 210° is defined as a set region, and the projection of the first chamber is located in the set region.

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

[0007] By providing a low-pressure compression chamber in the first cylinder and a high-pressure compression chamber in the second cylinder, and arranging a crankshaft to rotate in the first cylinder and the second cylinder, the processes of suction, compression, exhaust, etc. can be completed in the low-pressure compression chamber and the high-pressure compression chamber, and the refrigerant compressed in the low-pressure compression chamber can enter the high-pressure compression chamber through the first cavity. Since the projection of the first cavity is located in the set area from 0° to 210°, and the area from 0° to 210° is the suction area of the high-pressure compression chamber with a lower temperature, while the area from 210° to 360° is the exhaust area of the high-pressure compression chamber with a higher temperature. Therefore, the first cavity being located in the set area can reduce the temperature rise caused by heat exchange with the exhaust area of the high-pressure compression chamber, thereby improving the overheating situation of the refrigerant in the first cavity, reducing the power consumption required for the high-pressure compression chamber to compress the refrigerant, and improving the energy efficiency of the compressor.

[0008] According to some embodiments of the present invention, the compressor further includes an enthalpy-increasing component. The partition member is provided with an injection hole communicating with the first cavity, and the enthalpy-increasing component conveys refrigerant into the first cavity through the injection hole.

[0009] According to some embodiments of the present invention, the partition member is provided with a communication hole and an air inlet hole at the inlet of the high-pressure compression chamber at intervals, and the injection hole is located on the path of the refrigerant flowing from the communication hole to the air inlet hole.

[0010] According to some embodiments of the present invention, on the projection plane along the axial projection of the crankshaft, the connection line between the center of the communication hole and the rotation center of the crankshaft is L3, the central axis of the injection hole is L4, and the included angle a formed by L4 and L3 along the rotation direction of the crankshaft satisfies: 5° ≤ a ≤ 150°.

[0011] According to some embodiments of the present invention, on the projection plane along the axial projection of the crankshaft, the connection line between the center of the air inlet hole and the rotation center of the crankshaft is L5, the central axis of the injection hole is L4, and the included angle b formed by L5 and L4 along the rotation direction of the crankshaft satisfies: 0° < b ≤ 90°.

[0012] According to some embodiments of the present invention, along the reverse direction of the rotation direction of the crankshaft, the injection hole is located on the side of the communication hole away from the air inlet hole.

[0013] According to some embodiments of the present invention, the partition member includes an upper partition and a lower partition connected to each other. The upper partition is connected to the lower end surface of the second cylinder, the lower partition is connected to the upper end surface of the first cylinder, the first cavity is formed between the upper partition and the lower partition, the lower partition is provided with a first valve seat, and the low-pressure compression chamber exhausts to the first cavity through the first valve seat.

[0014] According to some embodiments of the present invention, a groove is provided on one side of the upper partition plate facing the lower partition plate, and a first cavity is formed between the wall surface of the groove and the wall surface of the lower partition plate facing the upper partition plate.

[0015] According to some embodiments of the present invention, the pump body assembly further includes a lower bearing and a lower muffler. The lower bearing is connected to the lower end surface of the first cylinder, the lower muffler is connected to the lower bearing, and a second cavity is formed between the lower muffler and the lower bearing. The second cavity is communicated with the first cavity through a communication channel. A second valve seat is provided on the lower end surface of the lower bearing, and the low-pressure compression chamber exhausts gas to the second cavity through the second valve seat.

[0016] The refrigeration device according to the second aspect embodiment of the present invention includes the compressor described in the above embodiments.

[0017] The refrigeration device according to the embodiment of the present invention has at least the following beneficial effects:

[0018] By using the compressor of the first aspect embodiment, the compressor is provided with a low-pressure compression chamber in the first cylinder and a high-pressure compression chamber in the second cylinder, and the crankshaft rotates and is arranged in the first cylinder and the second cylinder, which can enable the processes of suction, compression, exhaust, etc. to be completed in the low-pressure compression chamber and the high-pressure compression chamber. The refrigerant compressed in the low-pressure compression chamber can enter the high-pressure compression chamber through the first cavity. Since the projection of the first cavity is located in the set area of 0° to 210°, and the area of 0° to 210° is the suction area of the high-pressure compression chamber with a lower temperature, and the area of 210° to 360° is the exhaust area of the high-pressure compression chamber with a higher temperature. Therefore, the first cavity located in the set area can reduce the temperature rise caused by heat exchange with the exhaust area of the high-pressure compression chamber, thereby improving the overheating of the refrigerant in the first cavity, reducing the power consumption required for the high-pressure compression chamber to compress the refrigerant, and improving the energy efficiency of the compressor.

[0019] The additional aspects and advantages of the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. Description of the Drawings

[0020] The following further describes the present invention in conjunction with the drawings and embodiments, where:

[0021] Figure 1 is a schematic structural diagram of a compressor according to an embodiment of the present invention;

[0022] Figure 2 is a cross-sectional view of a compressor according to an embodiment of the present invention;

[0023] Figure 3 is a cross-sectional view of a pump body assembly according to an embodiment of the present invention;

[0024] Figure 4 is Figure 2 a sectional view taken along line A-A in

[0025] Figure 5 is Figure 2 a sectional view taken along line B-B in

[0026] Reference numerals in the drawings:

[0027] compressor 1000;

[0028] pump body assembly 100; first cylinder 110; low-pressure compression chamber 111; lower bearing 120; lower muffler 130; second cavity 131; communication channel 140; upper bearing 150; second cylinder 160; high-pressure compression chamber 161; vane slot 162; upper muffler 170; third cavity 171; partition member 190; first cavity 191; upper partition 192; lower partition 193; intermediate cavity 194; communication hole 195; intake hole 196; jet hole 197;

[0029] housing 200; inner cavity 210; outlet pipe 220;

[0030] liquid reservoir 300; exhaust pipe 310;

[0031] motor assembly 400; stator 410; rotor 420; crankshaft 430; first piston 431; second piston 432;

[0032] enthalpy-increasing assembly 500. Detailed implementation manners

[0033] Embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the drawings, where 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 drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0034] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by terms such as up and down, etc., is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0035] In the description of the present invention, "a plurality of" means more than two. If there is a description of first and second, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence of the indicated technical features.

[0036] In the description of the present invention, unless otherwise clearly defined, terms such as "set", "installed", "connected", etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific content of the technical solution.

[0037] The compressor can be used in refrigeration equipment, such as heat pump water heaters, air conditioners, etc. The compressor can compress the refrigerant with low temperature and low pressure into the refrigerant with high temperature and high pressure, providing power for the circulation of the refrigeration system. Existing compressors have single-stage compression and multi-stage compression solutions. Multi-stage compression means that the refrigerant is discharged after being compressed multiple times by the pump body assembly. Single-stage compression is mainly suitable for occasions where the pressure requirement for the refrigerant is not high. Compared with single-stage compression, multi-stage compression can make the compressor have higher volumetric efficiency, increase the pressure of the refrigerant discharged by the pump body assembly, and enable the compressor to have a better effect in the occasions of low-temperature heating and high-temperature refrigeration.

[0038] For example, with reference to Figure 1 and Figure 2 As shown, a compressor 1000 according to an embodiment of the present invention includes a housing 200, a pump body assembly 100, a motor assembly 400, and a liquid reservoir 300. The housing 200 has an inner cavity 210, and an air outlet pipe 220 for discharging air is provided at the upper end of the housing 200. The pump body assembly 100 is installed in the inner cavity 210, and the liquid reservoir 300 is located outside the housing 200 and is connected to the pump body assembly 100 through an exhaust pipe 310. 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.

[0039] With reference to Figure 3As shown, the pump body assembly 100 includes a lower bearing 120, a first cylinder 110, a lower silencer 130, a partition member 190, a second cylinder 160, an upper bearing 150, an upper silencer 170, and a crankshaft 430. The motor assembly 400 can drive the crankshaft 430 to rotate. Along the axial direction of the crankshaft 430, the crankshaft 430 includes a first eccentric portion and a second eccentric portion arranged at intervals. A first piston 431 is sleeved on the first eccentric portion, and a second piston 432 is sleeved on the second eccentric portion. The first cylinder 110 forms a low-pressure compression chamber 111. The first piston 431 is rotatably arranged in the low-pressure compression chamber 111. The intake pipe of the liquid storage device 300 is connected to the first cylinder 110. The lower bearing 120 is connected to the lower end surface of the first cylinder 110, and the lower silencer 130 is connected to the side of the lower bearing 120 facing away from the second cylinder 160. The partition member 190 is arranged on the side of the first cylinder 110 facing away from the lower bearing 120, and the second cylinder 160 is connected to the side of the partition member 190 facing away from the first cylinder 110. The partition member 190 serves to separate the first cylinder 110 and the second cylinder 160. The pump body assembly 100 further has an intermediate chamber 194. The intermediate chamber 194 includes a plurality of cavities. Two of the plurality of cavities are respectively a first cavity 191 and a second cavity 131. The partition member 190 is provided with the first cavity 191, and the second cavity 131 is formed between the lower bearing 120 and the lower silencer 130. The first cavity 191 and the second cavity 131 are communicated through a communication channel 140.

[0040] Continue to refer to Figure 3 As shown, the second cylinder 160 forms a high-pressure compression chamber 161. The second piston 432 is rotatably arranged in the high-pressure compression chamber 161. The upper silencer 170 is connected to the upper bearing 150, and a third cavity 171 is formed between the upper silencer 170 and the upper bearing 150. The high-pressure compression chamber 161 is communicated with the third cavity 171. The upper silencer 170 serves to reduce the refrigerant exhaust noise to improve the user experience.

[0041] Therefore, when the compressor 1000 operates, the refrigerant at low temperature and low pressure enters the liquid receiver 300. The liquid receiver 300 can reduce the entry of liquid refrigerant into the interior of the pump body assembly 100 to avoid liquid hammer. The gaseous refrigerant enters the low-pressure compression chamber 111 through the exhaust pipe 310 of the liquid receiver 300. When the crankshaft 430 rotates, it drives the first piston 431 to rotate within the low-pressure compression chamber 111, thereby compressing the refrigerant at low temperature and low pressure, and then discharging it to the high-pressure compression chamber 161 through the intermediate chamber 194. The crankshaft 430 drives the second piston 432 to perform an eccentric motion within the high-pressure compression chamber 161 to further compress the refrigerant, and then the refrigerant is discharged to the inner cavity 210 through the second cavity 131. After being further heated by the stator 410 and the rotor 420, it becomes a refrigerant at high temperature and high pressure, and finally is discharged from the air outlet pipe 220 of the housing 200. The refrigerant completes the first-stage compression within the first cylinder 110 and the second-stage compression within the second cylinder 160. By adopting the two-stage compression method, the pressure of the refrigerant can be increased, enabling the compressor 1000 to achieve better performance in the occasions of low-temperature heating and high-temperature refrigeration.

[0042] The high-pressure compression chamber 161 is divided into a suction area and an exhaust area by the second piston 432. The refrigerant in the exhaust area is compressed, so its temperature is relatively high, causing the temperature at the corresponding position of the second cylinder 160 to rise. Since the partition member 190 is connected to the second cylinder 160, it is easy to heat the partition member 190 through heat conduction, and then heat the refrigerant in the first chamber 191, resulting in an increase in the temperature of the refrigerant. When the refrigerant at a relatively high temperature enters the high-pressure compression chamber 161 for secondary compression, it will increase the power consumption required for compression and reduce the energy efficiency of the compressor 1000.

[0043] To improve the overheating of the refrigerant in the first chamber 191, referring to Figure 4 As shown, in the embodiment of the present invention, the second cylinder 160 is provided with a sliding vane groove 162 for installing a spring and a sliding vane. The sliding vane is connected to the spring, and the spring can keep the sliding vane in contact with the second piston 432. On the axial projection plane of the crankshaft 430, starting from the center line L1 of the sliding vane groove 162 and rotating 210° along the rotation direction of the crankshaft 430 to the position of L2, the area where the rotation angle is between 0° and 210° is defined as the set area, and the projection of the first chamber 191 is located within the set area. It should be noted that the center line of the sliding vane groove 162 is its symmetric center line, and it extends along the radial direction of the housing 200 and is perpendicular to the axis L6 of the crankshaft 430.

[0044] It can be understood that the area of the high-pressure compression chamber 161 between 0° and 210° is mainly the suction area, and the area between 210° and 360° is mainly the exhaust area. The temperature of the exhaust area is higher than that of the suction area. Therefore, setting the projection of the first cavity 191 in the area between 0° and 210° can reduce the temperature rise caused by the heat exchange between the refrigerant in the first cavity 191 and the exhaust area of the high-pressure compression chamber 161, thereby improving the overheating of the refrigerant in the first cavity 191, reducing the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and improving the energy efficiency of the compressor 1000.

[0045] To increase the exhaust volume of the compressor 1000, referring to Figure 1 As shown, in the embodiment of the present invention, the compressor 1000 further includes an enthalpy-increasing component 500. The partition member 190 is provided with an injection hole 197 communicating with the first cavity 191, and the enthalpy-increasing component 500 transports the refrigerant into the first cavity 191 through the injection hole 197. Therefore, the refrigerant transported by the enthalpy-increasing component 500 and the refrigerant in the first cavity 191 are mixed and then enter the high-pressure compression chamber 161, which can increase the intake volume and exhaust volume of the high-pressure compression chamber 161; at the same time, the refrigerant transported by the enthalpy-increasing component 500 can be mixed with the refrigerant in the first cavity 191, and can also play a role in cooling, reducing the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and further improving the effects of the compressor 1000 in low-temperature heating and high-temperature refrigeration.

[0046] Referring to Figure 4 As shown, Figure 4 The dotted arrows in represent the flow direction of the refrigerant. In the embodiment of the present invention, the partition member 190 is provided with a communication hole 195 at the outlet of the communication channel 140 and an intake hole 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 second cavity 131, and then sequentially pass through the communication channel 140, the communication hole 195, the first cavity 191, the intake hole 196, and finally enter the high-pressure compression chamber 161. And the injection hole 197 is located on the path of the refrigerant flowing from the communication hole 195 to the intake hole 196. That is, the injection hole 197 can be located at a position of the first cavity 191 far from the communication hole 195 and the intake hole 196, which can avoid structural interference and is convenient for installation. And it is beneficial for the refrigerant transported by the enthalpy-increasing component 500 and the refrigerant in the first cavity 191 to have enough time to mix to reduce the temperature of the refrigerant in the first cavity 191, reduce the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and further improve the effects of the compressor 1000 in low-temperature heating and high-temperature refrigeration.

[0047] Continuing to refer to Figure 4As shown, in the embodiment of the present invention, on the projection plane projected along the axis of the crankshaft 430, the connecting line between the center of the communication hole 195 and the rotation center of the crankshaft 430 is L3, and the rotation center of the crankshaft 430 is located on the central axis L6 of the crankshaft 430. The central axis of the air injection hole 197 is L4, and L4 extends along the radial direction of the housing 200. L4 may intersect with the central axis L6 of the crankshaft 430, or L4 and L6 do not intersect but are perpendicular to each other. The included angle a formed between L4 and L3 along the rotation direction of the crankshaft 430 satisfies: 5° ≤ a ≤ 150°, for example, a = 10°, a = 30°, a = 90°, a = 120°. It should be noted that when a is less than 5°, the distance between the air injection hole 197 and the communication hole 195 is relatively close, and interference is likely to occur in the structure, making installation difficult. When a is greater than 150°, the distance between the air injection hole 197 and the intake hole 196 is relatively close, and the refrigerant ejected by the enthalpy-increasing assembly 500 does not have enough time to mix with the refrigerant in the first cavity 191, resulting in poor cooling effect; moreover, the pressures of the refrigerant inhaled into the high-pressure compression cavity 161 are different, and pulsation is likely to occur. Therefore, reasonably designing the size of a can avoid structural interference, facilitate installation, and is conducive to sufficient time for the refrigerant transported by the enthalpy-increasing assembly 500 to mix with the refrigerant in the first cavity 191, so as to reduce the temperature of the refrigerant in the first cavity 191, reduce the power consumption required for the high-pressure compression cavity 161 to compress the refrigerant, and further improve the effects of the compressor 1000 in low-temperature heating and high-temperature refrigeration.

[0048] Referring to Figure 5 As shown, in the embodiment of the present invention, on the projection plane projected along the axial direction of the crankshaft 430, the connecting line between the center of the intake hole 196 and the rotation center of the crankshaft 430 is L5, and the central axis of the air injection hole 197 is L4. L4 extends along the radial direction of the housing 200, or does not intersect but is perpendicular to the central axis L6 of the crankshaft 430. The included angle b formed between L5 and L4 along the rotation direction of the crankshaft 430 satisfies: 0° < b ≤ 90°, for example, b = 30°, b = 45°, b = 60°, b = 75°. When b = 0°, the air injection hole 197 and the intake hole 196 coincide, and interference is likely to occur in the structure, making manufacturing and assembly difficult. When b is greater than 90°, the distance that the refrigerant discharged by the enthalpy-increasing assembly 500 needs to enter the intake hole 196 is relatively long, increasing the flow loss. And the temperature of the suction area of the high-pressure compression cavity 161 changes gradually. The closer to the position of the intake hole 196, the lower the temperature. When b is greater than 90°, the distance between the air injection hole 197 and the intake hole 196 is relatively far, which is likely to cause the refrigerant ejected by the enthalpy-increasing assembly 500 to be heated for a longer time. Therefore, reasonably designing the size of b can avoid interference between the air injection hole 197 and the intake hole 196 in the structure, and at the same time can reduce the flow loss and the overheating of the refrigerant ejected by the enthalpy-increasing assembly 500.

[0049] In another embodiment of the present invention, along the reverse direction of the rotation direction of the crankshaft 430, the air injection hole 197 is located on the side of the communication hole 195 away from the air inlet hole 196, that is, the communication hole 195 is located between the air injection hole 197 and the air inlet hole 196. The enthalpy-increasing assembly 500 first jets air through the air injection hole 197, then the low-pressure compression chamber 111 exhausts air through the communication hole 195, and finally enters the high-pressure compression chamber 161 through the air inlet hole 196. It can be understood that by arranging the air injection hole 197 on the side of the communication hole 195 away from the air inlet hole 196, the refrigerant can also be supplemented in the first cavity 191. The refrigerant jetted by the enthalpy-increasing assembly 500 is mixed with the refrigerant exhausted from the low-pressure compression chamber 111 after a short distance, increasing the refrigerant density in the first cavity 191 to improve the air intake volume of the high-pressure compression chamber 161. At the same time, it can reduce the temperature of the refrigerant exhausted from the low-pressure compression chamber 111, effectively improving the situation of refrigerant overheating, thereby reducing the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and further improving the energy efficiency of the compressor 1000.

[0050] Referring to Figure 3 As shown, in the embodiment of the present invention, the partition member 190 includes an upper partition 192 and a lower partition 193 connected to each other. The upper end surface of the upper partition 192 is connected to the lower end surface of the second cylinder 160, and the lower partition 193 is connected to the upper end surface of the first cylinder 110. A first cavity 191 is formed between the upper partition 192 and the lower partition 193. The lower partition 193 is provided with a first valve seat, and the low-pressure compression chamber 111 exhausts refrigerant to the first cavity 191 through the first valve seat. Among them, the lower end surface of the lower bearing 120 is provided with a second valve seat, and the low-pressure compression chamber 111 exhausts refrigerant to the second cavity 131 through the second valve seat, that is, the low-pressure compression chamber 111 can exhaust refrigerant to the first cavity 191 and the second cavity 131 at the same time. It can be understood that due to the large displacement of the low-pressure compression chamber 111, in order to improve the refrigerant exhaust efficiency, the low-pressure compression chamber 111 can exhaust refrigerant to the first cavity 191 and the second cavity 131 at the same time. In another embodiment of the present invention, the low-pressure compression chamber 111 can also first exhaust refrigerant to the second cavity 131, and the refrigerant in the second cavity 131 then enters the first cavity 191 through the communication channel 140 and finally enters the high-pressure compression chamber 161 for secondary compression, and a suitable solution is selected according to the actual situation.

[0051] Continuing to refer to Figure 3 As shown, in the embodiment of the present invention, a groove is provided on the side of the upper partition 192 facing the lower partition 193, and a first cavity 191 is formed between the wall surface of the groove and the wall surface of the lower partition 193 facing the upper partition 192. The structure of the partition member 190 can be simplified, the manufacturing difficulty can be reduced, and the production efficiency can be improved.

[0052] In an embodiment of the present invention, the enthalpy-increasing component 500 can be provided with gaseous refrigerant for air injection through a flash evaporator, and the flash evaporator is arranged in the circulation loop of the refrigeration system or the heating system. Taking the heating system as an example: after the liquid refrigerant releases heat through the condenser, it flows through the first throttling device and changes from all-liquid refrigerant to gas-liquid mixed refrigerant under the action of the first throttling device. The gas-liquid mixed refrigerant then enters the flash evaporator, and the gaseous refrigerant flows towards the enthalpy-increasing component 500 along the air outlet of the flash evaporator. The liquid refrigerant flows out from the liquid outlet of the flash evaporator, passes through the second throttling device and then enters the evaporator. Finally, the refrigerant after absorbing heat enters the low-pressure compression chamber 111 through the accumulator 300. In another embodiment of the present invention, the flash evaporator can be replaced by a plate heat exchanger, that is, the refrigerant for air injection of the enthalpy-increasing component 500 can also be provided through the plate heat exchanger, and a suitable solution can be selected according to the actual situation.

[0053] A refrigeration device according to an embodiment of the present invention includes the compressor 1000 of the above embodiment. The refrigeration device can be a central air conditioner, an integrated air conditioner, a split air conditioner, a duct machine, a window machine, etc. By adopting the compressor 1000 of the above embodiment, a low-pressure compression chamber 111 is arranged in the first cylinder 110 of the compressor 1000, and a high-pressure compression chamber 161 is arranged in the second cylinder 160. The crankshaft 430 is rotatably arranged in the first cylinder 110 and the second cylinder 160, so that the processes of suction, compression, exhaust, etc. can be completed in the low-pressure compression chamber 111 and the high-pressure compression chamber 161. The refrigerant compressed in the low-pressure compression chamber 111 can enter the high-pressure compression chamber 161 through the first cavity 191 and the second cavity 131. Since the projection of the first cavity 191 is located in the set area of 0° to 210°, and the area of 0° to 210° is the suction area of the high-pressure compression chamber 161 with a lower temperature, and the area of 210° to 360° is the exhaust area of the high-pressure compression chamber 161 with a higher temperature. Therefore, the first cavity 191 located in the set area can reduce the temperature rise caused by heat exchange with the exhaust area of the high-pressure compression chamber 161, thereby improving the overheating of the refrigerant in the first cavity 191, reducing the power consumption required for the high-pressure compression chamber 161 to compress the refrigerant, and improving the energy efficiency of the compressor 1000.

[0054] Since the refrigeration device adopts all the technical solutions of the compressor 1000 of the above embodiment, it at least has all the beneficial effects brought by the technical solutions of the above embodiment, which will not be elaborated here.

[0055] The above has described the embodiments of the present invention in detail with reference to the drawings, but the present invention is not limited to the above embodiments. Various changes can be made without departing from the gist of the present invention within the knowledge scope of those of ordinary skill in the art.

Claims

1. Compressor, characterized in that, Comprising: A pump body assembly, including a first cylinder, a partition member, and a second cylinder connected in sequence, and a crankshaft rotatably disposed in the first cylinder and the second cylinder. A first cavity is provided in the partition member, a low-pressure compression cavity is provided in the first cylinder, the low-pressure compression cavity discharges gas to the first cavity, a high-pressure compression cavity is provided in the second cylinder, and the first cavity supplies gas to the high-pressure compression cavity; Wherein, the second cylinder is provided with a sliding vane groove. On the projection plane along the axial projection of the crankshaft, starting from the center line of the sliding vane groove and rotating along the rotation direction of the crankshaft, the region where the rotation angle is between 0° and 210° is defined as the set region, and the projection of the first cavity is located within the set region.

2. The compressor according to claim 1, wherein: The compressor further includes an enthalpy-increasing assembly. The partition member is provided with an injection hole communicating with the first cavity, and the enthalpy-increasing assembly conveys refrigerant into the first cavity through the injection hole.

3. The compressor according to claim 2, characterized in that: The partition member is provided with a communication hole and an air inlet hole located at the inlet of the high-pressure compression cavity at intervals, and the injection hole is located on the path of the refrigerant flowing from the communication hole to the air inlet hole.

4. The compressor according to claim 3, wherein: On the projection plane along the axial projection of the crankshaft, the connection line between the center of the communication hole and the rotation center of the crankshaft is L3, the central axis of the injection hole is L4, and the included angle a formed by the L4 and the L3 along the rotation direction of the crankshaft satisfies: 5° ≤ a ≤ 150°.

5. The compressor according to claim 3, characterized in that: On the projection plane along the axial projection of the crankshaft, the connection line between the center of the air inlet hole and the rotation center of the crankshaft is L5, the central axis of the injection hole is L4, and the included angle b formed by the L5 and the L4 along the rotation direction of the crankshaft satisfies: 0° < b ≤ 90°.

6. The compressor according to claim 3, wherein: Along the opposite direction of the rotation direction of the crankshaft, the injection hole is located on the side of the communication hole away from the air inlet hole.

7. The compressor according to claim 1, wherein: The partition member includes an upper partition and a lower partition connected to each other. The upper partition is connected to the lower end face of the second cylinder, the lower partition is connected to the upper end face of the first cylinder, the first cavity is formed between the upper partition and the lower partition, the lower partition is provided with a first valve seat, and the low-pressure compression cavity discharges gas to the first cavity through the first valve seat.

8. The compressor according to claim 7, characterized in that: A groove is provided on the side of the upper partition facing the lower partition, and the first cavity is formed between the wall surface of the groove and the wall surface of the lower partition facing the upper partition.

9. The compressor according to claim 1 or 7, characterized in that: The pump body assembly further includes a lower bearing and a lower muffler. The lower bearing is connected to the lower end face of the first cylinder, the lower muffler is connected to the lower bearing, and a second cavity is formed between the lower muffler and the lower bearing. The second cavity is communicated with the first cavity through a communication channel. A second valve seat is provided on the lower end face of the lower bearing, and the low-pressure compression cavity discharges gas to the second cavity through the second valve seat.

10. Refrigeration equipment, characterized in that: Including the compressor according to any one of claims 1 to 9.

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