Rotor compressor and heat pump system including the same

Abstract

The invention relates to the technical field of heat pumps, particularly provides a rotor type compressor and a heat pump system comprising the rotor type compressor, and aims to solve the problems that the dissolving viscosity of refrigeration oil is reduced in the starting and running process of the compressor and the heat pump performance is affected due to the fact that the ratio of the oil pool volume to the compressor body volume of an existing heat pump rotor type compressor is unreasonable in design. And the reliability of the heat pump unit in the low-temperature starting and running process is influenced. In order to achieve the purpose, the rotor type compressor comprises a body, the body comprises a shell assembly and a driving device arranged in the shell assembly, the interior of the shell assembly comprises an oil pool used for containing refrigeration oil and a body cavity used for containing the driving device, the volume of the oil pool is V2, and the volume of the body cavity is V5; the volume V2 of the oil pool and the volume V5 of the body cavity meet the condition that V2 / V5 is larger than or equal to 0.75 and smaller than or equal to 1.25. The disturbance of the motor rotor assembly to the oil surface of the oil pool can be effectively reduced, so that the oil spitting rate of the compressor in the starting and running process is reduced, and the dissolution viscosity of refrigeration oil in the compressor is improved.

Description

Technical Field

[0001] This invention relates to the field of heat pump technology, and specifically provides a rotary compressor and a heat pump system including the rotary compressor. Background Technology

[0002] Driven by policies promoting dual-carbon and clean energy applications, the domestic and international air source heat pump market has experienced explosive growth. Air source heat pump units have many advantages, significantly reducing costs compared to gas boilers and electric heating, and their low-temperature heating performance meets customer needs. However, in low-temperature environments, the compressor, the "heart" of the air source heat pump unit, still suffers from low viscosity of the refrigerant oil, making it difficult to guarantee the reliability of the compressor and heat pump unit during low-temperature start-up and operation.

[0003] The existing design of the ratio of oil sump volume to compressor body volume in heat pump rotary compressors is unreasonable. This can easily lead to insufficient filling of refrigerant oil in the compressor and poor oil-gas separation. As a result, the oil discharge rate of the compressor is too high during startup and operation, reducing the amount of refrigerant oil in the compressor. Consequently, the viscosity of the refrigerant oil decreases during startup and operation, affecting the reliability of the heat pump unit during low-temperature startup and operation.

[0004] In view of this, there is a need in the art for a new rotary compressor and a heat pump system incorporating a rotary compressor to address the problem that the ratio of oil sump volume to compressor body volume in existing heat pump rotary compressors is poorly designed, leading to a decrease in the viscosity of the refrigeration oil during compressor start-up and operation, which affects the reliability of the heat pump unit during low-temperature start-up and operation. Summary of the Invention

[0005] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problem that the ratio of oil sump volume to compressor body volume in existing heat pump rotary compressors is not designed reasonably, which leads to a decrease in the viscosity of the refrigeration oil during compressor start-up and operation, thus affecting the reliability of the heat pump unit during low-temperature start-up and operation.

[0006] In a first aspect, the present invention provides a rotary compressor, the rotary compressor comprising a body, the body comprising a housing assembly and a drive device disposed inside the housing assembly, the housing assembly comprising an oil sump for holding refrigerant oil and a body chamber for housing the drive device, the oil sump having a volume of V2 and the body chamber having a volume of V5, wherein the volume of the oil sump V2 and the volume of the body chamber V5 satisfy 0.75≤V2 / V5≤1.25.

[0007] In the specific embodiment of the above-mentioned rotary compressor, the single discharge volume of the rotary compressor is V, and the single discharge volume V of the compressor and the volume V2 of the oil sump satisfy 0.028≤V / V2≤0.036.

[0008] In the specific embodiment of the rotary compressor described above, the rotary compressor further includes a distributor, which has a refrigerant pipeline inside. The distributor is connected to the compressor body through the refrigerant pipeline. The single discharge volume of the rotary compressor is V, and the effective volume of the distributor is V1. The single discharge volume V of the rotary compressor and the effective volume V1 of the distributor satisfy 0.025≤V / V1≤1.25, wherein the effective volume of the distributor is the volume inside the distributor used to hold the refrigerant.

[0009] In a specific embodiment of the above-mentioned rotary compressor, the housing of the distributor includes an upper cover, a cylinder and a lower cover. The distributor also includes an air inlet pipe, which is disposed on the upper cover. A filter assembly is also provided at the air outlet of the air inlet pipe to filter the gas entering the distributor.

[0010] In the specific embodiment of the above-mentioned rotary compressor, the refrigerant pipeline includes a first pipeline section and a second pipeline section. The first pipeline section is vertically arranged inside the distributor, and the second pipeline section is bent and connected to the compressor body. The first pipeline section and the second pipeline section are integrally formed or detachably connected.

[0011] In the specific embodiment of the above-mentioned rotary compressor, a partition is embedded inside the distributor, and the refrigerant pipeline is fixed inside the distributor through the partition.

[0012] In a specific embodiment of the rotary compressor described above, the rotary compressor further includes a pump body assembly, which is disposed in the oil sump, and the distributor is connected to the pump body assembly through the refrigerant pipeline.

[0013] In a specific embodiment of the rotary compressor described above, the drive device includes a motor stator and a motor rotor. The motor rotor is drivenly connected to the pump body assembly. The motor stator and the motor rotor divide the main body chamber into an upper motor chamber and a lower motor chamber.

[0014] In a specific embodiment of the rotary compressor described above, the housing assembly includes an upper housing cover, a housing body, and a lower housing cover. The upper housing cover and the lower housing cover are fixedly connected to or detachably connected to the housing body. The rotary compressor also includes an exhaust pipe, which is disposed on the upper housing cover.

[0015] The present invention also provides a heat pump system comprising a rotary compressor, wherein the heat pump system includes the rotary compressor described in any one of the above technical solutions.

[0016] The technical effects of this invention are as follows: By setting the volume of the oil sump inside the compressor body and the volume of the compressor body chamber within a suitable range, the rotary compressor of this invention avoids excessive oil in the oil sump during compressor start-up and operation, reducing the oil level in the oil sump. This effectively reduces the disturbance of the motor rotor assembly to the oil level in the oil sump and also effectively enhances the oil-gas separation effect of the rotating flow field in the upper cavity of the motor. This reduces the oil discharge rate of the compressor during start-up and operation, prevents the loss of refrigerant oil in the compressor, and increases the dissolution viscosity of the refrigerant oil during compressor start-up and operation. On the other hand, ensuring that the oil in the oil sump is not too low also ensures the normal operation of the compressor. This solves the problem that the ratio of oil sump volume to compressor body volume in existing heat pump rotary compressors is not designed reasonably, which leads to a decrease in the dissolution viscosity of the refrigerant oil during compressor start-up and operation, affecting the reliability of the heat pump unit during low-temperature start-up and operation. Attached Figure Description

[0017] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

[0018] Figure 1 This is a schematic diagram of the overall structure of the rotary compressor of the present invention;

[0019] Figure 2 This is a schematic diagram of the separator of the present invention.

[0020] List of reference numerals in the attached diagram:

[0021] 1-Rotor compressor; 11-Body; 1111-Upper cover of housing; 1112-Housing body; 1113-Lower cover of housing; 112-Drive unit; 1121-Motor stator; 1122-Motor rotor; 113-Oil sump; 114-Refrigeration oil; 1151-Upper chamber of motor; 1152-Lower chamber of motor; 12-Dispenser; 121-Refrigerant pipeline; 1211-First pipeline section; 1212-Second pipeline section; 122-Upper cover; 123-Cylinder; 124-Lower cover; 125-Inlet pipe; 126-Filter assembly; 127-Baffle plate; 13-Pump assembly; 14-Outlet pipe. Detailed Implementation

[0022] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the invention and are not intended to limit the scope of protection of the invention. Those skilled in the art can make adjustments as needed to adapt to specific applications.

[0023] It should be noted that in the description of this invention, terms such as "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," indicating directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation; therefore, they should not be construed as limitations on this invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0024] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0025] First, the existing heat pump rotary compressor is described.

[0026] The existing design of the ratio of oil sump volume to compressor body volume in heat pump rotary compressors is unreasonable, easily leading to insufficient refrigerant oil filling and poor oil-gas separation. Specifically, if the ratio of oil sump volume to compressor body volume is too small, insufficient refrigerant oil filling is likely to occur, resulting in excessively high compressor temperature and affecting compressor performance. On the other hand, if the ratio of oil sump volume to compressor body volume is too large, the amount of refrigerant oil filling the oil sump will be excessive. Excessive refrigerant oil will increase the disturbance of the oil surface in the oil sump by the motor rotor assembly during compressor start-up and operation, resulting in an excessively high oil discharge rate during compressor start-up and operation. This, in turn, reduces the dissolved viscosity of the refrigerant oil during compressor start-up and operation, affecting the reliability of the heat pump unit during low-temperature start-up and operation. Therefore, the following implementation method is proposed.

[0027] Example 1

[0028] like Figure 1 , Figure 2 As shown, to solve the problem of the volume of the oil sump 113 and the volume of the compressor body chamber in the existing heat pump rotary compressor 1 (i.e., Figure 1The unreasonable design of the ratio of regions 1151 and 1152 in the compressor leads to a decrease in the dissolution viscosity of the refrigeration oil 114 during compressor startup and operation, affecting the reliability of the heat pump unit during low-temperature startup and operation. The rotary compressor 1 of the present invention includes a body 11, which includes a housing assembly and a drive device 112 disposed inside the housing assembly. The housing assembly includes an oil sump 113 for holding the refrigeration oil 114 and a body chamber for placing the drive device 112. The oil sump 113 is disposed below the body chamber. The volume of the oil sump 113 is V2, and the volume of the body chamber is V5. The volume of the oil sump 113 V2 and the volume of the body chamber V5 satisfy 0.75≤V2 / V5≤1.25. The rotary compressor 1 also includes a pump body assembly 13 disposed inside the oil sump 113. The drive unit 112 includes a motor stator 1121 and a motor rotor 1122. The motor rotor 1122 is drivenly connected to the pump body assembly 13. The motor stator 1121 and the motor rotor 1122 divide the main body chamber into an upper motor chamber 1151 and a lower motor chamber 1152. The upper motor chamber 1151 and the lower motor chamber 1152 are combined to form the main body chamber V5 of the compressor. The housing assembly includes a housing upper cover 1111, a housing body 1112 and a housing lower cover 1113. The housing upper cover 1111 and the housing lower cover 1113 are fixedly connected to or detachably connected to the housing body 1112. The rotary compressor 1 also includes an exhaust pipe 14, which is disposed on the housing upper cover 1111. The rotary compressor 1 also includes a distributor 12, which is located on the left side of the compressor body 11. The housing of the distributor 12 includes an upper cover 122, a cylinder 123, and a lower cover 124. The distributor 12 also includes an intake pipe 125, which is located on the upper cover 122. A refrigerant line 121 is provided inside the distributor 12. The distributor 12 is connected to the compressor body 11 through the refrigerant line 121. The refrigerant line 121 includes a first line section 1211 and a second line section 1212. The first line section 1211 is vertically arranged inside the distributor 12, and the second line section 1212 is L-shaped. The first line section 1211 and the second line section 1212 are integrally formed or detachably connected. The distributor 12 is connected to the pump assembly 13 through the second line section 1212 of the refrigerant line 121.

[0029] In the case of adopting the above-described implementation method, the gas flow direction in the system will be described first. During the operation of the rotary compressor 1, before low-temperature start-up or during the four-way reversal of heating defrosting, the liquid refrigerant in the system will migrate into the distributor 12. At this time, there will be both gaseous and liquid refrigerant inside the distributor 12. Since the gaseous refrigerant and the liquid refrigerant have different densities, the gaseous refrigerant will rise to the upper part of the distributor 12, while the liquid refrigerant will sink to the lower part of the distributor 12 and collect there. As the compressor pump assembly 13 operates and draws in air, air flows in through the inlet pipe 125 of the upper cover 122 of the distributor 12, and then passes through the first pipe section 1211 and the second pipe section 1212 of the refrigerant pipe 121 inside the distributor 12 before entering the pump assembly 13. When the gas enters the first pipe section 1211, it will carry the gaseous refrigerant located on the upper part of the distributor 12 into the first pipe section 1211. After being processed by the pump assembly 13, the gas flows from the upper part of the pump assembly 13 into the lower chamber 1152 region V3 of the motor, and then flows into the upper chamber 1151 region V4 of the motor through the gap between the motor stator 1121 and the motor rotor 1122, and finally is discharged from the outlet pipe 14 located on the upper cover 1111 of the housing.

[0030] To avoid the problems caused by an excessively large or small ratio between the volume of the oil sump 113 and the volume of the compressor body 11, as mentioned above, this embodiment sets the volume V2 of the oil sump 113 and the volume V5 of the body chamber to satisfy the range of 0.75 ≤ V2 / V5 ≤ 1.25. This prevents excessive oil accumulation in the oil sump 113 during compressor startup and operation, reducing the oil level and effectively minimizing disturbance to the oil level in the oil sump 113 caused by the motor rotor 1122 assembly. It also enhances the oil-gas separation effect of the rotating flow field in the upper cavity of the motor, thereby reducing pressure. The increased oil discharge rate during compressor startup and operation prevents the loss of refrigerant oil 114 within the compressor and improves the dissolution viscosity of refrigerant oil 114 during compressor startup and operation. On the other hand, it also ensures that the amount of oil in the oil sump 113 is not too low, which would prevent the expected cooling and lubrication effects from being achieved, thereby ensuring the normal operation of the compressor. This solves the problem that the ratio of the volume of the oil sump 113 to the volume of the compressor body 11 in the existing heat pump rotary compressor 1 is not designed reasonably, which leads to a decrease in the dissolution viscosity of refrigerant oil 114 during compressor startup and operation, affecting the reliability of the heat pump unit during low-temperature startup and operation.

[0031] Furthermore, those skilled in the art will understand that the upper cover 1111 and lower cover 1113 of the housing assembly can also be fixedly connected to the housing body 1112 or detachably connected. A fixed connection helps to enhance the structural strength of the housing assembly, thereby better protecting the internal components of the housing assembly. A detachable connection makes it easier for maintenance personnel to disassemble and repair the compressor when problems occur, saving maintenance costs and improving maintenance efficiency. Those skilled in the art can choose the connection method of the housing assembly itself according to actual needs, and all of these are within the protection scope of this invention.

[0032] It is also worth mentioning that, although not mentioned above, as can be seen from the accompanying drawings, the refrigerant pipeline 121 in this invention can be provided in one or more sets. Those skilled in the art can adjust the number and diameter of the refrigerant pipeline 121 according to specific heat exchange requirements and the effective volume of the distributor 12. These changes do not exceed the technical principles of this invention and are therefore all within the scope of protection of this invention. Similarly, the first pipeline section 1211 and the second pipeline section 1212 of the refrigerant pipeline 121 can also be provided as an integrally formed or detachably connected form. The specific technical effects are similar to those of the aforementioned housing assembly and will not be repeated here. Regarding the shape of the second pipeline section 1212, although it was mentioned above that the second pipeline section 1212 is L-shaped, this is not the only arrangement. Those skilled in the art can also set the second pipeline section 1212 to other common shapes, such as J-shaped. These changes are all within the scope of protection of this invention.

[0033] Example 2

[0034] The foregoing embodiments disclose a method to avoid the decrease in the dissolved viscosity of the refrigerant oil 114 during compressor startup and operation by limiting the range of the ratio of the compressor oil sump 113 volume V2 to the compressor body volume V5, thus affecting the reliability of the heat pump unit during low-temperature startup and operation. However, when the compressor starts at low temperatures, if the ratio of the compressor's single discharge volume to the oil sump 113 volume is not designed reasonably, it can easily lead to insufficient charging of the refrigerant oil 114 in the compressor and poor oil-gas separation. Specifically, as mentioned above, during the operation of the rotary compressor 1, the gaseous refrigerant in the distributor 12 will... The gaseous refrigerant enters the pump body assembly 13 and the lower chamber 1152 region V3 and the upper chamber 1151 region V4 of the motor through the first pipeline section 1211 and the second pipeline section 1212. After entering the lower chamber 1152 region V3 and the upper chamber 1151 region V4 of the motor, some of the refrigerant will dissolve in the refrigeration oil 114 in the oil sump 113, thereby reducing the dissolution viscosity of the refrigeration oil 114. This embodiment is proposed for this purpose. In this embodiment, the single discharge volume of the rotary compressor 1 is V, and the single discharge volume V of the compressor and the volume V2 of the oil sump 113 satisfy 0.028≤V / V2≤0.036.

[0035] In this embodiment, by limiting the ratio of the compressor's single discharge volume V to the volume V2 of the oil sump 113 to the range of 0.028 ≤ V / V2 ≤ 0.036, on the one hand, it avoids the situation where the volume V2 of the oil sump 113 is too small, resulting in an excessively high proportion of refrigerant in the oil sump 113 relative to the refrigeration oil 114 when some refrigerant is dissolved in the refrigeration oil 114 in the oil sump 113, thus leading to significant dilution of the refrigeration oil 114 in the oil sump 113 and reducing the solubility viscosity of the refrigeration oil 114. On the other hand, by setting an upper limit for the compressor's single discharge volume V and the volume V2 of the oil sump 113, it avoids the situation where the volume V2 of the oil sump 113 is too small, resulting in the refrigeration oil 114 in the oil sump 113 failing to achieve the expected cooling and lubrication effect. Therefore, by limiting the ratio of the compressor's single discharge volume V to the volume V2 of the oil sump 113 to the range of 0.028≤V / V2≤0.036 in this embodiment, the solubility viscosity of the refrigeration oil 114 can be avoided while ensuring the normal operation of the compressor, thus solving the above-mentioned problem.

[0036] Example 3

[0037] like Figure 1 , Figure 2As shown, the internal space of the distributor 12 is enclosed by an upper cover 122, a cylinder 123, and a lower cover 124. A filter assembly 126 is also provided at the outlet end of the air inlet pipe 125 to filter the gas entering the distributor 12. A baffle 127 is embedded inside the distributor 12. The annular baffle 127 is installed inside the distributor 12 by cold pressing. The refrigerant pipe 121 is fixed inside the distributor 12 by the baffle 127. The cavity volume from the end face of the first pipe section 1211 near the filter assembly 126 to the bottom of the lower cover 124 is... The volume of the distributor 12, excluding the straight pipe and baffle 127, is the volume of the distributor 12 used to hold the refrigerant, i.e., the effective volume V1 of the distributor 12. Before the compressor starts at low temperature or when the four-way valve for defrosting in heating mode switches, the liquid refrigerant in the system migrates into the distributor 12. If the ratio of the single discharge volume V of the rotary compressor 1 to the effective volume V1 of the distributor 12 is unreasonable, the liquid refrigerant in the distributor 12 will overflow the end face of the first pipe section 1211 and migrate into the compressor, resulting in a high dilution rate of the refrigerant oil 114 in the compressor. This embodiment is proposed to solve this problem. In this embodiment, the single discharge volume V of the rotary compressor 1 and the effective volume V1 of the distributor 12 satisfy 0.025≤V / V1≤1.25.

[0038] When using the above-described implementation, if the ratio of the single-discharge volume V of the rotary compressor 1 to the effective volume V1 of the distributor 12 is too large, it indicates that the effective volume V1 of the distributor 12 is too small. When the liquid refrigerant in the system migrates into the distributor 12, the liquid level of the refrigerant in the distributor 12 may be higher than the end face height of the first pipe section 1211. As a result, the refrigerant in the distributor 12 will enter the oil sump 113 of the compressor body 11 along the first pipe section 1211 and the second pipe section 1212, diluting the refrigerant oil 114 in the oil sump 113, thus affecting the performance, noise, and reliability of the compressor. On the other hand, if the ratio of the single-discharge volume V of the rotary compressor 1 to the effective volume V1 of the distributor 12 is too small, it indicates that the effective volume V1 of the distributor 12 is too large. This will not only increase the cost of the distributor 12 but also increase the space occupied by the distributor 12, making it inconvenient to install in the air conditioning system and prone to interference with other components in the system.

[0039] In addition, by providing a filter assembly 126 at the outlet end of the intake pipe 125, the gas entering the distributor 12 can be filtered, preventing impurities in the outside air from entering the distributor 12 and entering the compressor body 11 along the refrigerant line 121, which could damage the pump assembly 13 or the drive device 112.

[0040] Furthermore, by providing a baffle 127 inside the distributor 12, it facilitates the fixing of the refrigerant pipeline 121. On the other hand, the annular baffle 127 also enhances the structural strength of the distributor 12, increases the fixing frequency of the distributor 12, and thus reduces the vibration noise of the distributor 12. At the same time, those skilled in the art will understand that the shape and installation method of the baffle 127 described above are only one feasible implementation method. Those skilled in the art can also set the baffle 127 to other common shapes, such as semi-circular or square, as long as it can achieve the technical effects of fixing the refrigerant pipeline 121 and enhancing the structural strength of the distributor 12. In addition, those skilled in the art can also choose other installation methods to install the baffle 127, such as snap-fit ​​installation. These simple changes do not exceed the technical principles of this invention and are therefore all included within the protection scope of this invention.

[0041] Furthermore, the present invention also provides a heat pump system comprising a rotary compressor 1, wherein the heat pump system comprises the rotary compressor 1 as described in any of the above embodiments.

[0042] It should be noted that the above embodiments are merely used to illustrate the principles of the present invention and are not intended to limit the scope of protection of the present invention. Without departing from the principles of the present invention, those skilled in the art can adjust the above structure so that the present invention can be applied to more specific application scenarios.

[0043] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A rotary compressor, characterized in that, The rotary compressor includes a body, which includes a housing assembly and a drive unit disposed inside the housing assembly. The housing assembly includes an oil sump for holding refrigerant oil and a body chamber for housing the drive unit. The volume of the oil sump is V2, and the volume of the body chamber is V5. The volume of the oil sump V2 and the volume of the body chamber V5 satisfy 0.75≤V2 / V5≤1.

25.

2. The rotary compressor according to claim 1, characterized in that, The single discharge volume of the rotary compressor is V, and the single discharge volume V of the compressor and the volume V2 of the oil sump satisfy 0.028≤V / V2≤0.

036.

3. The rotary compressor according to claim 1, characterized in that, The rotary compressor also includes a distributor, which has a refrigerant pipeline inside. The distributor is connected to the compressor body through the refrigerant pipeline. The single discharge volume of the rotary compressor is V, and the effective volume of the distributor is V1. The single discharge volume V of the rotary compressor and the effective volume V1 of the distributor satisfy 0.025≤V / V1≤1.25, where the effective volume of the distributor is the volume inside the distributor used to hold the refrigerant.

4. The rotary compressor according to claim 3, characterized in that, The housing of the liquid separator includes an upper cover, a cylindrical body, and a lower cover. The liquid separator also includes an air inlet pipe, which is disposed on the upper cover. A filter assembly is also provided at the air outlet of the air inlet pipe to filter the gas entering the liquid separator.

5. The rotary compressor according to claim 4, characterized in that, The refrigerant pipeline includes a first pipeline section and a second pipeline section. The first pipeline section is vertically arranged inside the distributor, and the second pipeline section is bent and connected to the compressor body. The first pipeline section and the second pipeline section are integrally formed or detachably connected.

6. The rotary compressor according to claim 5, characterized in that, The distributor is equipped with a partition, and the refrigerant pipeline is fixed inside the distributor through the partition.

7. The rotary compressor according to claim 3, characterized in that, The rotary compressor also includes a pump body assembly, which is disposed in the oil sump, and the distributor is connected to the pump body assembly through the refrigerant pipeline.

8. The rotary compressor according to claim 7, characterized in that, The drive device includes a motor stator and a motor rotor. The motor rotor is drivenly connected to the pump body assembly. The motor stator and the motor rotor divide the main body chamber into an upper motor chamber and a lower motor chamber.

9. The rotary compressor according to claim 1, characterized in that, The housing assembly includes an upper housing cover, a housing body, and a lower housing cover. The upper housing cover and the lower housing cover are fixedly connected to or detachably connected to the housing body. The rotary compressor also includes an exhaust pipe, which is disposed on the upper housing cover.

10. A heat pump system comprising a rotary compressor, characterized in that, The heat pump system includes the rotary compressor as described in any one of claims 1-9.

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