Pump body assembly, rotary compressor and refrigeration equipment

Abstract

The application discloses a pump body assembly, a rotary compressor and a refrigeration device, wherein the pump body assembly comprises a cylinder, an end cover and an exhaust hole; the cylinder is formed with a compression cavity; the end cover is arranged at the end of the cylinder along the axial direction; the exhaust hole is arranged on the end cover and is communicated with the compression cavity; the exhaust hole comprises an inlet section, an intermediate section and an outlet section which are connected in sequence; along the exhaust direction, the cross-sectional area of the inlet section gradually decreases, and the cross-sectional area of the outlet section gradually increases. The application can effectively reduce the vortex of the inlet end and the outlet end of the exhaust hole, reduce the local resistance loss of the airflow, reduce the exhaust resistance, increase the effective exhaust cross-sectional area and minimize the clearance volume, so that the performance of the scroll compressor is improved.

Description

Technical Field

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

[0002] In related technologies, the exhaust port of a rotary compressor is located on the main bearing. For multi-cylinder rotary compressors, the exhaust port can be located on both the auxiliary bearing and the partition plate. The exhaust port is generally cylindrical. Refrigerant gas tends to generate eddies at both the inlet and outlet ends of the exhaust port, leading to increased local resistance loss during exhaust, which in turn increases the power consumption and reduces the performance of the rotary compressor. 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 pump body assembly that can reduce eddies at the inlet and outlet ends of the exhaust port, reduce exhaust resistance, and improve compressor performance.

[0004] The present invention also proposes a rotary compressor having the above-described pump assembly.

[0005] The present invention also proposes a refrigeration device having the above-mentioned rotary compressor.

[0006] According to a first aspect of the present invention, a pump body assembly includes: a cylinder having a compression chamber; an end cap disposed at an axial end of the cylinder; and an exhaust port disposed on the end cap and communicating with the compression chamber; the exhaust port includes an inlet section, an intermediate section, and an outlet section connected in sequence; along the exhaust direction, the cross-sectional area of ​​the inlet section gradually decreases, and the cross-sectional area of ​​the outlet section gradually increases.

[0007] The pump assembly according to embodiments of the present invention has at least the following beneficial effects:

[0008] By setting an exhaust port formed by sequentially connecting an inlet section, an intermediate section, and an outlet section, with the cross-sectional area of ​​the inlet section gradually decreasing along the exhaust direction and the cross-sectional area of ​​the outlet section gradually increasing along the exhaust direction, the vortex at the inlet and outlet ends of the exhaust port is effectively reduced, local airflow resistance loss is reduced, exhaust resistance is reduced, and the effective exhaust cross-sectional area is increased while the clearance volume is minimized, thereby improving the performance of the scroll compressor.

[0009] According to some embodiments of the present invention, the cross-sectional area of ​​the intermediate section remains unchanged along the exhaust direction.

[0010] According to some embodiments of the present invention, the diameter of the inlet end of the inlet section is D1, the diameter of the intermediate section is D2, and the diameter of the outlet end of the outlet section is D3, wherein D1, D2, and D3 satisfy: D3>D1>D2.

[0011] According to some embodiments of the present invention, D1 and D2 satisfy: D1 / D2 = 1.1-1.2; D2 and D3 satisfy: D3 / D2 = 1.1-1.3.

[0012] According to some embodiments of the present invention, along the axial direction of the cylinder, the length of the outlet section is H3, the length of the inlet section is H1, and H3 and H1 satisfy: H3>H1.

[0013] According to some embodiments of the present invention, H3 and H1 satisfy: H3 / H1 = 1.5-2.5.

[0014] According to some embodiments of the present invention, the length of the exhaust port along the axial direction of the cylinder is H, wherein H and H3 satisfy: 0.25≤H3 / H≤0.5; and H and H1 satisfy: 0.125≤H1 / H≤0.25.

[0015] According to some embodiments of the present invention, on a cross section passing through the axis of the exhaust port, the outline of the inner side of the inlet section is an arc, a straight line or a polyline, and the outline of the inner side of the outlet section is an arc, a straight line or a polyline.

[0016] According to some embodiments of the present invention, the outlet section is a tapered hole with a tapered angle of A, wherein A satisfies: 60°≤A≤120°; the inlet section is a tapered hole with a tapered angle of B, wherein B satisfies: 60°≤B≤120°.

[0017] According to some embodiments of the present invention, the cone angle A of the outlet section is equal to 60°; the cone angle B of the inlet section is equal to 90°.

[0018] A rotary compressor according to a second aspect of the present invention includes the pump assembly described in the above embodiments.

[0019] The rotary compressor according to embodiments of the present invention has at least the following beneficial effects:

[0020] The pump body assembly of the first aspect embodiment has an exhaust port formed by sequentially connecting an inlet section, an intermediate section and an outlet section. The cross-sectional area of ​​the inlet section gradually decreases along the exhaust direction, and the cross-sectional area of ​​the outlet section gradually increases along the exhaust direction. This effectively reduces the vortex at the inlet and outlet ends of the exhaust port, reduces local airflow resistance loss, reduces exhaust resistance, and increases the effective exhaust cross-sectional area while minimizing the clearance volume, thereby improving the performance of the scroll compressor.

[0021] A refrigeration device according to a third aspect of the present invention includes the rotary compressor described in the above embodiments.

[0022] The refrigeration device according to embodiments of the present invention has at least the following beneficial effects:

[0023] The rotary compressor of the second aspect embodiment includes a pump body assembly. The pump body assembly forms an exhaust port by sequentially connecting an inlet section, an intermediate section, and an outlet section. The cross-sectional area of ​​the inlet section gradually decreases along the exhaust direction, while the cross-sectional area of ​​the outlet section gradually increases along the exhaust direction. This effectively reduces the vortex at the inlet and outlet ends of the exhaust port, reduces local airflow resistance loss, lowers exhaust resistance, and increases the effective exhaust cross-sectional area while minimizing the clearance volume, thereby improving the performance of the scroll compressor.

[0024] 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

[0025] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0026] Figure 1 This is a schematic diagram of the structure of a rotary compressor according to an embodiment of the present invention;

[0027] Figure 2 This is a schematic diagram of the upper bearing structure of a pump body assembly according to an embodiment of the present invention;

[0028] Figure 3 for Figure 2 A cross-sectional view;

[0029] Figure 4 for Figure 3 A partially enlarged schematic diagram of the central exhaust port;

[0030] Figure 5 This is a schematic diagram of the structure of a rotary compressor according to another embodiment of the present invention;

[0031] Figure 6 This is a cross-sectional schematic diagram of the first partition of the pump body assembly according to another embodiment of the present invention;

[0032] Figure 7 for Figure 6 A partially enlarged schematic diagram of the central exhaust port;

[0033] Figure 8a The exhaust flow field diagram is for the exhaust port of the prior art;

[0034] Figure 8b This is an exhaust flow field diagram of an exhaust port according to an embodiment of the present invention.

[0035] Icon labels:

[0036] Gas-liquid separator 100;

[0037] Housing 200; Upper housing 210; Exhaust pipe 211; Lower housing 220; Main housing 230;

[0038] Motor assembly 300; Rotor 310; Stator 320;

[0039] Pump body assembly 400; cylinder 410; main bearing 420; valve seat 421; exhaust valve plate 422; lift limiter 423; auxiliary bearing 430; crankshaft 440; piston 450; first cylinder 460; second cylinder 470; first partition 480; second partition 490;

[0040] Exhaust port 500; inlet section 510; intermediate section 520; outlet section 530. Detailed Implementation

[0041] 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.

[0042] 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.

[0043] 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.

[0044] 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.

[0045] Reference Figure 1As shown, one embodiment of the rotary compressor of the present invention is a single-cylinder compressor, including a gas-liquid separator 100, a housing 200, a motor assembly 300, and a pump assembly 400. The motor assembly 300 and the pump assembly 400 are disposed within the housing 200. The housing 200 includes an upper housing 210, a lower housing 220, and a main housing 230, which are connected to form a sealed space for accommodating the motor assembly 300 and the pump assembly 400. It is understood that the motor assembly 300 includes a rotor 310 and a stator 320, and the stator 320 and the pump assembly 400 are fixed within the main housing 230. The pump assembly 400 includes a cylinder 410, a main bearing 420, a secondary bearing 430, and a crankshaft 440. Cylinder 410 has a compression chamber (not shown in the figure). The main bearing 420 and the auxiliary bearing 430 are respectively connected to the two ends of cylinder 410 along the axial direction, thereby sealing the two ends of the compression chamber along the axial direction. The gas-liquid separator 100 provides refrigerant to the pump body assembly 400. The rotor 310 is connected to the crankshaft 440, thereby driving the crankshaft 440 to rotate through the motor assembly 300. A piston 450 is sleeved on the crankshaft 440. The piston 450 is located in the cylinder 410 and rotates eccentrically relative to the center of the cylinder 410, thereby causing the compression chamber to change periodically, so that the pump body assembly 400 completes the process of intake, compression and exhaust. The refrigerant is discharged through the exhaust pipe 211 of the upper housing 210 and then enters the refrigeration system for circulation.

[0046] In this embodiment of the rotary compressor, refrigerant enters the compression chamber through the suction port (not shown in the figure) of cylinder 410, and is compressed by piston 450 to reach a set pressure. The refrigerant is then discharged through the exhaust port 500 on the main bearing 420. It is understood that the exhaust port 500 can also be located on the auxiliary bearing 430, or simultaneously on both the main bearing 420 and the auxiliary bearing 430; this is not specifically limited here. It should be noted that in this embodiment of the invention, both the main bearing 420 and the auxiliary bearing 430 can be considered as end caps.

[0047] Reference Figure 2 and Figure 3 As shown, in this embodiment of the pump body assembly 400, an exhaust port 500 is disposed on the main bearing 420. The main bearing 420 is provided with a valve seat 421, an exhaust valve plate 422, and a lift limiter 423. The exhaust port 500 is disposed on the valve seat 421, and the exhaust valve plate 422 and the lift limiter 423 are mounted on the valve seat 421 by rivets. The end of the exhaust valve plate 422 away from the rivet is a free end, which covers the exhaust port 500. After the pressure in the compression chamber reaches the set pressure, the exhaust valve plate 422 rebounds and covers the exhaust port 500, preventing high-pressure gas in the housing 200 from leaking into the compression chamber.

[0048] Reference Figure 3 and Figure 4As shown, it can be understood that the exhaust port 500 penetrates the main bearing 420. The inlet end of the exhaust port 500 can be a planar structure, which communicates with the compression chamber, and the outlet end of the exhaust port 500 can be an arc structure, which is covered by the exhaust valve plate 422 to achieve a seal. The exhaust port 500 includes an inlet section 510, an intermediate section 520, and an outlet section 530. The inlet section 510, intermediate section 520, and outlet section 530 are connected sequentially along the exhaust direction of the pump body assembly 400. Along the exhaust direction, the cross-sectional area of ​​the inlet section 510 gradually decreases, that is, the inlet section 510 adopts a tapered structure, for example, the inlet section 510 can be set as a tapered orifice. Along the exhaust direction, the cross-sectional area of ​​the outlet section 530 gradually increases, and the outlet section 530 adopts a tapered structure, for example, the outlet section 530 can be set as a tapered orifice. The structure of the exhaust port 500 in this embodiment of the invention can better conform to the flow rate and direction change law of the exhaust gas, increase the effective flow area at the inlet and outlet ends of the exhaust port 500, reduce the vortex at the inlet and outlet ends of the exhaust port 500, reduce the local resistance loss of the airflow, reduce the exhaust resistance, and increase the effective exhaust cross-sectional area while minimizing the clearance volume, thereby improving the performance of the scroll compressor.

[0049] Reference Figure 4 As shown, it can be understood that the intermediate section 520 has a columnar structure, meaning that along the exhaust direction, the intermediate section 520 has a constant diameter and a constant cross-sectional area. This allows it to stabilize the flow direction and velocity of the exhaust airflow, reducing pressure pulsations. Of course, the intermediate section 520 can also adopt a non-constant diameter structure, such as a tapered orifice, while ensuring that the changes in exhaust airflow velocity and direction are not affected.

[0050] Reference Figure 4 As shown, it can be understood that the longitudinal section profile of the inner side of the inlet section 510 is an arc, and the longitudinal section profile of the inner side of the outlet section 530 is an arc. The longitudinal section referred to here is the section passing through the axis of the exhaust port 500. (Refer to...) Figure 7 As shown, in the longitudinal section, the outline of the inner side of the inlet section 510 can also be a straight line, and the outline of the inner side of the outlet section 530 can also be a straight line. Furthermore, in the longitudinal section, the outlines of the inner sides of the inlet section 510 and the outlet section 530 can also be polylines; this is not specifically limited here, as long as the cross-sectional area of ​​the inlet section 510 gradually decreases and the cross-sectional area of ​​the outlet section 530 gradually increases along the exhaust direction.

[0051] Reference Figure 4As shown, it can be understood that the diameter of the inlet end of the inlet section 510 is defined as D1, the diameter of the intermediate section 520 is defined as D2, and the diameter of the outlet end of the outlet section 530 is defined as D3. In this embodiment of the invention, the diameter of the outlet end of the inlet section 510 is the same as the diameter of the intermediate section 520, and the diameter of the inlet end of the outlet section 530 is the same as the diameter of the intermediate section 520, thereby making the exhaust more stable.

[0052] It should be noted that the diameter D3 of the outlet end of the outlet section 530 is larger than the diameter D1 of the inlet end of the inlet section 510, and the diameter D1 of the inlet end of the inlet section 510 is larger than the diameter D2 of the intermediate section 520. It can be understood that when the refrigerant is discharged from the exhaust port 500, according to the adiabatic process gas state equation: P*V k = constant. Since k is a constant, as the gas pressure P gradually decreases, the gas volume V gradually increases, the internal energy of the gas pressure is converted into mechanical energy, and the gas velocity also increases with the gas expansion. According to the continuity equation: ρ1A1v1=ρ2A2v2, due to gas expansion, the gas density ρ2 at the outlet end of exhaust port 500 is less than the gas density ρ1 at the inlet end, and the velocity v2 at the outlet end of exhaust port 500 is greater than the velocity v1 at the inlet end. At the same volumetric flow rate, the velocity and cross-sectional area are inversely proportional. Therefore, in order to prevent the excessive velocity at the outlet end of exhaust port 500 from causing exhaust noise and impact problems of exhaust valve plate 422, the cross-sectional area A2 at the outlet end of exhaust port 500 should be greater than the cross-sectional area A1 at the inlet end. Therefore, the outlet diameter D3 of outlet section 530 should be set to be greater than the inlet diameter D1 of inlet section 510.

[0053] Reference Figure 4 As shown, it can be understood that the diameter D1 of the inlet end of the inlet section 510 and the diameter D2 of the intermediate section 520 satisfy the relationship: D1 / D2 = 1.1-1.2. This increases the effective flow area at the inlet end of the exhaust port 500, reduces the vortex at the inlet end, and avoids an excessive increase in clearance volume, which would affect the intake volume of the cylinder 410 in each compression cycle. The diameter D2 of the intermediate section 520 and the diameter D3 of the outlet end of the outlet section 530 satisfy the relationship D3 / D2 = 1.1-1.3. This increases the effective flow area at the outlet end of the exhaust port 500, reduces the vortex at the outlet end, and avoids an excessive increase in clearance volume, which would affect the intake volume of the cylinder 410 in each compression cycle.

[0054] Reference Figure 4As shown, it can be understood that the axial direction of the exhaust port 500 is parallel to the axial direction of the cylinder 410, which facilitates processing and forming. Along the axial direction of the exhaust port 500, the length of the outlet section 530 is defined as H3, and the length of the inlet section 510 is defined as H1. The length H3 of the outlet section 530 is greater than the length H1 of the inlet section 510. Because the flow velocity v2 at the outlet end of the exhaust port 500 is greater than the flow velocity v1 at the inlet end, the diameter D3 at the outlet end of the exhaust port 500 should be greater than the diameter D1 at the inlet end. Therefore, the gradient of the flow velocity and flow direction change in the outlet section 530 is larger than that in the inlet section 510. Thus, the length H3 of the outlet section 530 should be greater than the length H1 of the inlet section 510.

[0055] Reference Figure 4 As shown, it can be understood that the length H3 of the outlet section 530 and the length H1 of the inlet section 510 satisfy the relationship: H3 / H1 = 1.5 - 2.5. Therefore, when the axial length of the exhaust port 500 is constant, the exhaust airflow can be made more stable, improving local turbulence and reducing local resistance.

[0056] Reference Figure 4 As shown, it can be understood that in order to ensure that the inlet section 510 and the outlet section 530 have sufficient flow length to eliminate local eddies, the length of the exhaust port 500 along the axial direction of the cylinder 410 is defined as H. The length H of the exhaust port 500 along the axial direction of the cylinder 410 and the length H3 of the outlet section 530 satisfy the relationship: 0.25≤H3 / H≤0.5; the length H of the exhaust port 500 along the axial direction of the cylinder 410 and the length H1 of the inlet section 510 satisfy the relationship: 0.125≤H1 / H≤0.25.

[0057] Reference Figure 5 As shown, another embodiment of the rotary compressor of the present invention is a two-cylinder compressor. The structure of the rotary compressor of the present invention is basically the same as that of the rotary compressor of the previous embodiment, except that: the pump body assembly 400 of the present invention is provided with two cylinders 410, including a first cylinder 460 and a second cylinder 470. A first partition 480 and a second partition 490 are provided between the first cylinder 460 and the second cylinder 470. The first partition 480 and the main bearing 420 are respectively connected to the two ends of the first cylinder 460 along the axial direction, and the second partition 490 and the auxiliary bearing 430 are respectively connected to the two ends of the second cylinder 470 along the axial direction.

[0058] Reference Figure 6As shown, it can be understood that the exhaust port 500 in this embodiment of the invention is located on the first partition 480, which also has a valve seat 421, an exhaust valve plate 422, and a lift limiter 423. Refrigerant is discharged through the exhaust port 500. It can also be understood that the exhaust port 500 can be located on the main bearing 420, the auxiliary bearing 430, or the second partition 490, or simultaneously on the main bearing 420, auxiliary bearing 430, the first partition 480, and the second partition 490, or on one end cap of the first cylinder 460 and one end cap of the second cylinder 470. No specific limitations are specified here, as long as the inner cavity of the first cylinder 460 and the inner cavity of the second cylinder 470 are both connected to the exhaust port 500. In this embodiment of the invention, the main bearing 420, the auxiliary bearing 430, the first partition 480, and the second partition 490 can all be considered as end caps.

[0059] The exhaust port 500 of this embodiment of the invention is formed by sequentially connecting an inlet section 510, an intermediate section 520, and an outlet section 530. The cross-sectional area of ​​the inlet section 510 gradually decreases along the exhaust direction, while the cross-sectional area of ​​the outlet section 530 gradually increases along the exhaust direction. This effectively reduces the vortex at the inlet and outlet ends of the exhaust port 500, reduces local airflow resistance loss, lowers exhaust resistance, and increases the effective exhaust cross-sectional area while minimizing the clearance volume, thereby improving the performance of the scroll compressor.

[0060] Reference Figure 7 As shown, it can be understood that, in the longitudinal section, the outline of the inner side of the inlet section 510 is a straight line, that is, the inlet section 510 is a tapered hole; the outline of the inner side of the outlet section 530 is also a straight line, that is, the outlet section 530 is also a tapered hole. The exhaust hole 500 of this embodiment is easier to process, has higher processing efficiency, and a more stable structure.

[0061] Reference Figure 7 As shown, it can be understood that the cone angle A of the outlet section 530 satisfies the relationship: 60°≤A≤120°. The cone angle B of the inlet section 510 satisfies the relationship: 60°≤B≤120°. This makes the machining of the exhaust port 500 easier and prevents the clearance volume from being too large, which would affect the intake volume of the cylinder 410 in each compression cycle, thus improving the performance of the compressor.

[0062] Reference Figure 8a and Figure 8b As shown, Figure 8a The existing cylindrical exhaust port has a constant exhaust channel cross-sectional area. However, at the inlet and outlet ends of the exhaust port 500, due to the significant changes in the velocity and direction of the exhaust airflow, vortices are generated at the corners of the inlet and outlet ends, thereby increasing the local resistance loss of the airflow. Figure 8bThe exhaust port 500 of this embodiment of the invention has a cross-sectional diameter and shape that are gradually adjusted with the exhaust flow velocity and direction, which reduces the eddy currents at the inlet and outlet ends of the exhaust port 500 and ensures the stability of the exhaust flow velocity and direction.

[0063] Reference Figure 1 As shown, a rotary compressor according to an embodiment of the present invention includes the pump assembly 400 described in the above embodiments. The rotary compressor of this embodiment employs the pump assembly 400 of the first aspect embodiment. The pump assembly 400 forms an exhaust port 500 by sequentially connecting an inlet section 510, an intermediate section 520, and an outlet section 530. The cross-sectional area of ​​the inlet section 510 gradually decreases along the exhaust direction, while the cross-sectional area of ​​the outlet section 530 gradually increases along the exhaust direction. This effectively reduces vortices at the inlet and outlet ends of the exhaust port 500, reduces local airflow resistance loss, lowers exhaust resistance, and while increasing the effective exhaust cross-sectional area, minimizes the clearance volume, thereby improving the performance of the scroll compressor.

[0064] Since the rotary compressor adopts all the technical solutions of the pump body assembly 400 of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.

[0065] Referring to Tables 1 and 2, a comparison of parameters and effects is presented for three specific embodiments of the rotary compressor of the prior art and the present invention.

[0066] Table 1: Exhaust port 500 structural schemes with different size parameters in the prior art and this embodiment

[0067]

[0068] Table 2: Verification results of single-factor performance tests conducted on the rotary compressor of the prior art and this embodiment.

[0069]

[0070] Based on the above test results, it can be concluded that although the clearance volume of the exhaust port 500 structure adopted in the invention embodiment is slightly larger than that of the prior art, resulting in a slight decrease in cooling capacity, the input power of the rotary compressor is significantly reduced, and the overall COP is improved by about 1%, that is, the performance of the rotary compressor is improved by about 1%.

[0071] Understandably, through repeated verification using experimental data, it was found that the overall performance of the rotary compressor was optimal when the cone angle A of the outlet section 530 was set to 60° and the cone angle B of the inlet section 510 was set to 90°.

[0072] This invention provides a refrigeration device that can be used in air conditioners, refrigerators, freezers, or other devices that achieve a refrigeration cycle through a rotary compressor. The refrigeration device of this invention employs the rotary compressor described in the previous embodiment. The rotary compressor includes a pump assembly 400. The pump assembly 400 forms an exhaust port 500 by sequentially connecting an inlet section 510, an intermediate section 520, and an outlet section 530. The cross-sectional area of ​​the inlet section 510 gradually decreases along the exhaust direction, while the cross-sectional area of ​​the outlet section 530 gradually increases along the exhaust direction. This effectively reduces vortices at the inlet and outlet ends of the exhaust port 500, reduces local airflow resistance loss, lowers exhaust resistance, and while increasing the effective exhaust cross-sectional area, minimizes the clearance volume, thereby improving the performance of the scroll compressor.

[0073] 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 pump body assembly, characterized in that, include: A cylinder, which has a compression chamber; An end cap is provided at the axial end of the cylinder; An exhaust port is provided on the end cap and communicates with the compression chamber; the exhaust port includes an inlet section, an intermediate section and an outlet section connected in sequence; along the exhaust direction of the exhaust port, the cross-sectional area of ​​the inlet section gradually decreases and the cross-sectional area of ​​the outlet section gradually increases; The cross-sectional area of ​​the intermediate section remains unchanged along the exhaust direction; Along the axial direction of the cylinder, the length of the exhaust port is H, the length of the outlet section is H3, and the length of the inlet section is H1. H3 and H1 satisfy: H3>H1, H and H3 satisfy: 0.25≤H3 / H≤0.5, H and H1 satisfy: 0.125≤H1 / H≤0.25; H3 and H1 satisfy: H3 / H1=1.5-2.

5.

2. The pump body assembly according to claim 1, characterized in that: The diameter of the inlet end of the inlet section is D1, the diameter of the middle section is D2, and the diameter of the outlet end of the outlet section is D3. D1, D2, and D3 satisfy the following condition: D3>D1>D2.

3. The pump body assembly according to claim 2, characterized in that: The following conditions are met: D1 and D2 satisfy: D1 / D2 = 1.1-1.2; D2 and D3 satisfy: D3 / D2 = 1.1-1.

3.

4. The pump body assembly according to claim 1, characterized in that: On a cross-section passing through the axis of the exhaust port, the outline of the inner side of the inlet section is an arc, a straight line, or a polyline, and the outline of the inner side of the outlet section is an arc, a straight line, or a polyline.

5. The pump body assembly according to claim 1, characterized in that: The outlet section is a tapered hole with a tapered angle of A, where A satisfies: 60°≤A≤120°; the inlet section is a tapered hole with a tapered angle of B, where B satisfies: 60°≤B≤120°.

6. The pump body assembly according to claim 5, characterized in that: The cone angle A of the outlet section is 60°; the cone angle B of the inlet section is 90°.

7. A rotary compressor, characterized in that: Includes the pump body assembly as described in any one of claims 1 to 6.

8. A refrigeration device, characterized in that: Including the rotary compressor as described in claim 7.

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