Pump body assembly, rotary compressor, air conditioner

Abstract

The application provides a pump body assembly, a rotor compressor and an air conditioner. The pump body assembly comprises a first cylinder, first and second flanges assembled at both ends of the first cylinder, a first exhaust structure formed on the first flange, a first exhaust inclined notch corresponding to the first exhaust structure and formed on the first cylinder, a first drainage exhaust passage formed on the first cylinder, an outlet end of the first drainage exhaust passage communicated with the first exhaust inclined notch, a first radial surface of the first cylinder passing through a midpoint of an axial height of the first cylinder, a first target area corresponding to a space of a cylinder compression cavity between the first radial surface and a second end surface of the first cylinder, an inlet end of the first drainage exhaust passage communicated with the first target area and projected on the first radial surface, and the inlet end of the first drainage exhaust passage located in a projection range of the first exhaust inclined notch. The application can avoid over-compression of the pump body assembly at a very low modification cost.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning technology, specifically relating to a pump assembly, a rotary compressor, and an air conditioner, and more particularly to an energy-saving air conditioner. Background Technology

[0002] With the upgrading of air conditioner energy efficiency, rotary compressors have gradually evolved from early fixed-frequency compressors to variable-frequency compressors of 15~120Hz, reducing the weight of the compressor by half. The high speed and miniaturization of rotary compressors have become the mainstream trend in the industry. Research on compressors with higher speeds such as 160Hz and 200Hz is also being gradually promoted. However, the high speed of the compressor will bring serious exhaust over-compression problems.

[0003] Overcompression of the exhaust gas poses a serious threat to compressors. It not only causes a significant increase in compressor power and severely deteriorates noise and vibration, but also frequently leads to exhaust valve plate breakage. In more severe cases, it can cause the vane and roller to detach, resulting in the vane tail impacting the cylinder and causing breakage of the vane, cylinder, spring, and other components, compromising reliability. Research has found that during some ultra-high frequency operations, the pressure in the exhaust tail compression chamber increases sharply, exhibiting a pressure distribution pattern of low pressure near the oblique cut and extremely high pressure away from the oblique cut. This phenomenon is often caused by the inability to expel exhaust gas in a timely manner. Therefore, mitigating the overcompression problem of exhaust gas in high-speed compressors is an urgent issue that needs to be addressed.

[0004] A conventional approach to address exhaust overcompression is to increase the diameter of the flange exhaust port. However, due to limitations imposed by the minimum sealing clearance between the exhaust port and the inner circle of the roller, the enlarged exhaust port size is limited and cannot effectively solve the overcompression problem. Furthermore, single-cylinder dual exhaust is also a common industry solution for exhaust overcompression. This technology is highly effective, but it adds components such as valve plates, baffles, rivets, and mufflers, increasing compressor costs and complicating assembly processes. Therefore, how to reduce exhaust overcompression within the existing conventional compressor pump structure at a relatively low modification cost is a question worth considering. Summary of the Invention

[0005] Therefore, the present invention provides a pump body assembly, a rotary compressor, and an air conditioner that can overcome the shortcomings of related technologies, such as the need for many new components, high modification costs, and complex assembly processes in the technical solution of setting up dual exhaust for the cylinder to solve the problem of exhaust overcompression.

[0006] To address the aforementioned problems, the present invention provides a pump body assembly, including a first cylinder. A first flange and a second flange are sealed and assembled at two axial end faces of the first cylinder. A first exhaust structure is formed on the first flange. A first exhaust oblique cut corresponding to the first exhaust structure is formed on the first end face of the first cylinder. The first cylinder also forms a first drainage exhaust channel. The outlet end of the first drainage exhaust channel communicates with the first exhaust oblique cut. The first cylinder has a first radial surface passing through the midpoint of its axial height. The cylinder compression chamber space corresponding to the area between the first radial surface and the second end face of the first cylinder is a first target area. The inlet end of the first drainage exhaust channel communicates with the first target area and is projected onto the first radial surface. The inlet end of the first drainage exhaust channel is within the projection range of the first exhaust oblique cut.

[0007] In some embodiments, the first exhaust channel is an exhaust groove that extends axially along the first cylinder and is formed on the inner circular wall of the first cylinder.

[0008] In some embodiments, the drain groove extends to the second end face of the first cylinder; and / or, the opening of the drain groove on the second end face is a beveled opening.

[0009] In some embodiments, the projection of the drainage groove onto the first radial plane is an arc shape.

[0010] In some embodiments, the depth and / or width of the drainage channel decreases from the first end face to the second end face.

[0011] In some embodiments, projected onto the first radial plane, the maximum circumferential width of the first exhaust oblique cut is L1, and the maximum circumferential width of the drainage groove is L2, where L2 ≤ 0.8L1.

[0012] In some embodiments, the first cylinder has a first vane groove, and the drain groove is located in the area where the first vane groove intersects with the first exhaust oblique cut.

[0013] In some embodiments, the first exhaust channel is an exhaust hole extending axially along the first cylinder and formed in the wall of the first cylinder, and an overflow port is formed on the inner circular wall of the first cylinder, the overflow port connecting the inlet end of the exhaust hole and the first target area.

[0014] In some embodiments, the drainage hole includes an intermediate hole section and end hole sections at both axial ends of the intermediate hole section, wherein the diameter of the end hole sections is larger than the diameter of the intermediate hole section; and / or, the flow outlet is a beveled cut.

[0015] In some embodiments, the total volume of the first drainage and exhaust passage is V, the displacement of the compressor used in the pump assembly is Q, and the maximum operating frequency is fmax. .

[0016] In some embodiments, the pump assembly further includes a second cylinder and a partition plate. The partition plate is sandwiched between the second end face of the first cylinder and the first end face of the second cylinder. A second flange is sealed and assembled on the second end face of the second cylinder. A second exhaust structure is formed on the second flange. A second exhaust oblique cut is formed on the second end face of the second cylinder, corresponding to the first exhaust structure. The second cylinder has a second drainage exhaust channel. The outlet end of the second drainage exhaust channel communicates with the second exhaust oblique cut. The second cylinder has a second radial surface passing through the midpoint of its axial height. The cylinder compression chamber space corresponding to the area between the second radial surface and the first end face of the second cylinder is a second target area. The inlet end of the second drainage exhaust channel communicates with the second target area and is projected onto the second radial surface. The inlet end of the second drainage exhaust channel is within the projection range of the second exhaust oblique cut.

[0017] The present invention also provides a rotary compressor, including a pump body assembly, wherein the pump body assembly is the pump body assembly described above.

[0018] The present invention also provides an air conditioner including the above-described rotary compressor.

[0019] The pump assembly, rotary compressor, and air conditioner provided by this invention have the following beneficial effects:

[0020] By setting a first exhaust channel in the first cylinder and placing its inlet end at the aforementioned first target area, the flow area during the compression exhaust tail stroke can be effectively increased. This allows overcompressed gas to flow smoothly along the first exhaust channel to the first exhaust structure and be discharged from the cylinder compression chamber in a timely manner, effectively reducing or even eliminating overcompression. This effectively avoids adverse phenomena such as a significant increase in compressor power, severe deterioration of noise and vibration, exhaust valve plate breakage, and component breakage leading to reduced compressor reliability caused by overcompression of the pump body assembly exhaust. At the same time, since only one first exhaust channel needs to be processed on the existing single-cylinder single-exhaust pump body assembly structure without the need to add an exhaust valve assembly, the structure is extremely simple and the modification cost is extremely low. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the internal structure of the pump body assembly in one embodiment of the present invention;

[0023] Figure 2 yes Figure 1 The axial projection of the first or second cylinder (i.e., the projection of the cylinder on the radial plane).

[0024] Figure 3 yes Figure 2 A magnified view of a section at point A in the middle;

[0025] Figure 4 yes Figure 1 A schematic diagram of the axial section of the first or second cylinder in the cylinder;

[0026] Figure 5 yes Figure 1 A schematic diagram of the refrigerant flow direction when the first cylinder in the pump body assembly is venting (indicated by the arrows in the diagram).

[0027] Figure 6 yes Figure 1 A schematic diagram of the refrigerant flow direction during exhaust from the second cylinder in the pump body assembly (indicated by the arrows in the diagram).

[0028] Figure 7 This is an axial projection view of the first or second cylinder in the pump body assembly according to another embodiment of the present invention.

[0029] Figure 8 yes Figure 7 A magnified view of a section at point B in the middle;

[0030] Figure 9 This is a three-dimensional structural schematic diagram of the first cylinder or the second cylinder in the pump body assembly in another embodiment of the present invention;

[0031] Figure 10 yes Figure 9 A machining schematic diagram of the exhaust oblique cut and drain groove of the first or second cylinder in the cylinder;

[0032] Figure 11 yes Figure 1 The diagram shows a beveled groove formed at the inlet end of the flow channel in the pump body assembly.

[0033] Figure 12This is a schematic diagram of the internal structure of the pump body assembly in another embodiment of the present invention;

[0034] Figure 13 yes Figure 12 An axial projection view of the first or second cylinder in the cylinder;

[0035] Figure 14 yes Figure 12 A schematic diagram of the axial section of the first or second cylinder in the cylinder;

[0036] Figure 15 This is a schematic diagram of the internal structure of the pump body assembly in another embodiment of the present invention;

[0037] Figure 16 yes Figure 15 A schematic diagram of the axial section of the first or second cylinder;

[0038] Figure 17 This is a schematic diagram of the internal structure of a rotary compressor according to another embodiment of the present invention.

[0039] The attached figures are labeled as follows:

[0040] 11. First cylinder; 111. First exhaust oblique cut; 112. First vane groove; 12. Second cylinder; 121. Second exhaust oblique cut; 122. Second vane groove; 21. First flange; 211. First exhaust port; 22. Second flange; 221. Second exhaust port; 23. Middle partition plate; 31. Drainage channel; 311. Angled groove; 32. Drainage hole; 321. Flow port; 41. First silencer; 42. Second silencer; 5. Exhaust connection channel; 51. First connecting hole; 52. First cylinder connecting hole; 53. Second connecting hole; 54. Second cylinder connecting hole; 55. Third connecting hole; 61. Elastic valve plate; 62. Limiting baffle; 71. First roller; 72. Second roller; 73. First eccentric part; 74. Second eccentric part; 75. Crankshaft; 101. First cutting tool; 102. Second cutting tool; 200. Pump body assembly; 201. Compressor housing; 202. Distributor; 203. Motor assembly. Detailed Implementation

[0041] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0042] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not 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 on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0043] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90° or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0044] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0045] See also Figures 1 to 17As shown, according to an embodiment of the present invention, a pump body assembly is provided, including a first cylinder 11. A first flange 21 and a second flange 22 are sealed and assembled at the two axial end faces of the first cylinder 11. When the pump body assembly is a single-cylinder pump body assembly, the aforementioned first flange 21 and second flange 22 correspond to an upper flange and a lower flange, respectively. A first roller 71 is provided inside the first cylinder 11. The two ends of the crankshaft 75 of the pump body assembly are pivotally supported by the aforementioned first flange 21 and second flange 22. The crankshaft 75 has a first eccentric portion 73, and the first roller 71 is fitted onto the first eccentric portion 73. On the core 73, a first sliding vane (not shown in the figure) is provided in the first sliding vane groove 112 of the first cylinder 11. The head of the first sliding vane abuts against the outer circumferential wall of the first roller 71, dividing the working chamber of the first cylinder 11 into an intake chamber and a compression chamber. A first exhaust structure is formed on the first flange 21. The aforementioned first exhaust structure can be a conventional exhaust valve assembly. The aforementioned exhaust valve assembly is assembled in the first exhaust port 211. Specifically, the aforementioned exhaust valve assembly includes an elastic valve plate 61, a limiting baffle 62 for limiting the opening angle of the elastic valve plate 61, and a... The elastic valve plate 61 and the limiting baffle 62 are fixedly connected to the corresponding flange and enable the elastic valve plate 61 to fit against the connector (e.g., threaded post) on the first exhaust port 211. It is understood that a first exhaust oblique cut 111 is formed on the first end face of the first cylinder 11, which is configured corresponding to the first exhaust structure (i.e., corresponding to the position of the first exhaust port 211). The aforementioned first end face is also the side end face of the first cylinder 11 that mates with the first flange 21. The first cylinder 11 also forms a first drainage exhaust channel (not marked in the figure). The outlet end of the first drainage exhaust channel is connected to the first exhaust oblique cut 111. The first cylinder 11 has a first radial surface passing through the midpoint of its axial height (not marked in the figure). The cylinder compression chamber space corresponding to the area between the first radial surface and the second end face of the first cylinder 11 is the first target area (not marked in the figure). The inlet end of the first drainage exhaust channel is connected to the first target area and is projected on the first radial surface. The inlet end of the first drainage exhaust channel is within the projection range of the first exhaust oblique cut 111.

[0046] Traditional single-cylinder, single-exhaust pump assemblies (i.e., each cylinder of the pump assembly has only one exhaust structure, as mentioned above, the first exhaust structure) have an exhaust structure only at one end of the cylinder's axial direction. This results in a small exhaust flow area relative to the cylinder's compression chamber. Especially during high-frequency operation of the pump assembly, this easily leads to a significant increase in pressure at the axial end of the cylinder furthest from the exhaust structure. Specifically, in the cylinder height direction, the area near the exhaust structure (i.e., the aforementioned first exhaust oblique cut 111) easily discharges refrigerant, but the refrigerant in the area corresponding to the axial end of the cylinder furthest from the exhaust structure (i.e., the aforementioned first target area) is difficult to discharge due to a lack of necessary guidance, leading to a sharp increase in local pressure in that area. This application adopts a first... The cylinder 11 is provided with a first exhaust channel and its inlet end is located at the aforementioned first target area. This can effectively increase the flow area during the exhaust tail stroke of the compression, allowing the overcompressed gas to flow smoothly along the first exhaust channel to the first exhaust structure and be discharged from the cylinder compression chamber in a timely manner. This effectively reduces or even eliminates the occurrence of overcompression, thereby effectively avoiding adverse phenomena such as a significant increase in compressor power, severe deterioration of noise and vibration, exhaust valve plate breakage, and component breakage leading to reduced compressor reliability caused by overcompression of the pump body assembly exhaust. At the same time, since only one first exhaust channel needs to be processed on the existing single-cylinder single-exhaust pump body assembly structure without the need to add an exhaust valve assembly, the structure is extremely simple and the modification cost is extremely low.

[0047] See also Figures 1 to 11 As shown, in some embodiments, the first exhaust channel is an exhaust groove 31 that extends along the axial direction of the first cylinder 11 and is formed on the inner circular wall of the first cylinder 11. That is, the aforementioned exhaust groove 31 is formed on the surface of the inner circular wall of the first cylinder 11, and the opening of the exhaust groove 31 directly connects with the aforementioned first target area in a full axial length. The manufacturing process is extremely simple and the exhaust is extremely smooth.

[0048] See details Figure 9 As shown, in some embodiments, the aforementioned drainage groove 31 does not need to extend along the axial direction of the first cylinder 11 to the second end face of the first cylinder 11, but only extends to the area below the aforementioned first radial surface, which can have a smaller clearance volume. The aforementioned second end face is the side end face of the first cylinder 11 opposite to the aforementioned first end face. See details. Figure 10As shown, in the specific processing, a machining tool with a slightly larger diameter (first tool 101) is used for the aforementioned first exhaust oblique cut 111, and the angle between it and the center line support of the first cylinder 11 (a in the figure) is a large value, generally greater than 60°. On the other hand, a machining tool with a smaller diameter (second tool 102) is used for the diversion groove 31, and the angle between it and the center line support of the first cylinder 11 (b in the figure) is a small value, generally less than 20°. In this way, the pressure fluid can be discharged smoothly and in a timely manner while taking into account the small clearance volume of the diversion groove 31.

[0049] Especially for compressors that do not operate at very high frequencies, the design of the flow channel 31 can adopt the aforementioned method of not extending to the second end face.

[0050] In some implementations, see reference Figures 1 to 8 As shown, the drainage groove 31 extends to the second end face of the first cylinder 11. That is, the drainage groove 31 basically covers the entire height of the first exhaust oblique cut 111 along the axial direction of the first cylinder 11, making the corresponding pump body assembly more suitable for compressors with high operating frequency.

[0051] In some embodiments, the projection of the flow channel 31 onto the first radial plane is an arc shape, that is, the channel wall of the flow channel 31 is a smooth arc surface. On the one hand, this can improve its guiding effect on airflow, and on the other hand, it can facilitate its processing and reduce processing burrs.

[0052] In some embodiments, the depth and / or width of the drainage channel 31 decreases from the first end face of the first cylinder 11 to its second end face, which can further reduce the clearance volume while guiding the pressurized fluid (refrigerant) to the first exhaust structure through the drainage channel 31.

[0053] See details Figure 11 As shown, in some embodiments, the groove 31 on the second end face is a beveled groove 311, which can further increase the fluid flow during the exhaust tail stroke.

[0054] In some implementation methods, see details. Figure 3 As shown, when projected onto the first radial plane, the maximum circumferential width of the first exhaust oblique cut 111 is L1, and the maximum circumferential width of the guide groove 31 is L2, where L2≤0.8L1. This reduces the risk of connection between the cylinder's compression chamber and intake chamber (i.e., high and low pressure chambers) at the guide groove 31.

[0055] See also Figure 7 and Figure 8As shown, in some embodiments, the first cylinder 11 has a first vane groove 112 extending through both ends of its axial direction, and the guide groove 31 is located in the area where the first vane groove 112 intersects with the first exhaust oblique cut 111. In a specific embodiment, the aforementioned guide groove 31 is implemented by chamfering the groove wall of the aforementioned first vane groove 112 near the first exhaust oblique cut 111.

[0056] In this technical solution, placing the diversion groove 31 in the area where the first sliding vane groove 112 intersects with the first exhaust oblique cut 111 can effectively relieve pressure and discharge the fluid in the tail of the compression stroke.

[0057] See also Figures 12 to 16 As shown, in some embodiments, the first exhaust channel is an exhaust hole 32 extending along the axial direction of the first cylinder 11 and formed in the wall of the first cylinder 11, and an overflow port 321 is formed on the inner circular wall of the first cylinder 11. The overflow port 321 connects the inlet end of the exhaust hole 32 with the first target area, that is, the exhaust hole 32 is constructed in the body of the first cylinder 11.

[0058] In this technical solution, a drainage hole 32 is used to guide and discharge the pressurized fluid. The drainage hole 32 is located inside the cylinder body instead of the opening groove structure opened on the inner circular wall as mentioned above. This makes the contact surface between the first roller 71 and the inner circular wall of the first cylinder 11 smoother, which can effectively reduce or even eliminate fluid over-compression while reducing contact wear between the roller and the cylinder.

[0059] See details Figure 15 and Figure 16 As shown, in some embodiments, the drainage hole 32 includes an intermediate hole section and end hole sections at both ends of the intermediate hole section along the axial direction. The diameter of the end hole sections is larger than that of the intermediate hole section, so that the drainage hole 32 is formed as a stepped hole structure with a large end diameter and a small center diameter. This can effectively solve the problem that the tool diameter is too small and difficult to process when the axial height of the cylinder is large.

[0060] In some implementations, the flow port 321 is a beveled cut. Specifically, the depth of the beveled cut increases as it extends toward the axial end face of the cylinder, thereby minimizing the clearance volume.

[0061] In some embodiments, the total volume of the first drainage and exhaust passage is V, the displacement of the compressor used in the pump assembly is Q, and the maximum operating frequency is fmax. In practical applications, the unit of the aforementioned V is mm. 3 The unit of Q is mm. 3The unit of fmax is Hz.

[0062] In this technical solution, the total volume of the first exhaust channel and the displacement of the compressor are optimized and limited, which can prevent V from being too large, resulting in an excessive clearance volume, and prevent V from being too small, resulting in an insignificant exhaust effect.

[0063] In some embodiments, the pump assembly further includes a second cylinder 12 and a partition plate 23. The partition plate 23 is sandwiched between the second end face of the first cylinder 11 and the first end face of the second cylinder 12. The second flange 22 is sealed and assembled on the second end face of the second cylinder 12. In this case, the pump assembly objectively forms a double-cylinder pump assembly. Specifically, the second cylinder 12 is provided with a second roller 72. The aforementioned first cylinder 11 is also the upper cylinder, and the second cylinder 12 is also the lower cylinder. The aforementioned first flange 21 and second flange 22 correspond to the upper flange and lower flange, respectively. The crankshaft 75 of the pump body assembly is pivotally supported at both ends by the aforementioned first flange 21 and second flange 22. The crankshaft 75 also has a second eccentric portion 74, which is 180° opposite to the first eccentric portion 73. A second roller 72 is fitted onto the second eccentric portion 74. A second vane (not shown in the figure) is provided in the second vane groove 122 of the second cylinder 12. The head of the second vane abuts against the outer circumferential wall of the second roller 72, dividing the working chamber of the second cylinder 12 into an intake chamber and a compression chamber. A second exhaust structure is formed on the second flange 22. The aforementioned second exhaust structure can... Similar to the aforementioned first exhaust structure, that is, an exhaust valve assembly consisting of an elastic valve plate 61, a limiting baffle 62, and a connecting member, a second exhaust port 221 is formed on the second flange 22. The aforementioned exhaust valve assembly is assembled within the second exhaust port 221. A second exhaust oblique cut 121 corresponding to the first exhaust structure is formed on the second end face of the second cylinder 12. The second cylinder 12 forms a second drainage exhaust channel, and the outlet end of the second drainage exhaust channel communicates with the second exhaust oblique cut 121. The second cylinder 12 has a passage through which... The second radial surface at the midpoint of the axial height, the cylinder compression chamber space corresponding to the area between the second radial surface and the first end face of the second cylinder 12 is the second target area. The inlet end of the second exhaust channel is connected to the second target area and is projected on the second radial surface. The inlet end of the second exhaust channel is within the projection range of the second exhaust oblique cut 121. In this way, the anti-refrigerant over-compression design of the two cylinders in the dual-cylinder pump body assembly is realized. The implementation principle of the aforementioned second exhaust channel is the same as that of the first exhaust channel, and will not be elaborated here.

[0064] In some implementations, the aforementioned second drainage and exhaust channel can be designed in the same way as the first drainage and exhaust channel, which will not be elaborated here.

[0065] The second flange 22 is sealed with a second muffler 42 on the end face away from the second cylinder 12. The second exhaust structure is within the coverage area of ​​the second muffler 42. The pump body assembly also forms an exhaust communication channel 5 that connects the first muffler 41 and the second muffler 42. Specifically, the exhaust communication channel 5 is formed by splicing together the first communication hole 51, the first cylinder communication hole 52, the second communication hole 53, the second cylinder communication hole 54, and the third communication hole 55 that are axially connected. It can be understood that the first exhaust structure of the first cylinder 11 and the second exhaust structure of the second cylinder 12 are opened alternately. When the second exhaust structure exhausts, it first enters the second muffler 42 and then enters the first muffler 41 through the exhaust communication channel 5.

[0066] See details Figure 5 As shown, when the first cylinder 11 exhausts, part of the refrigerant is discharged from the first exhaust oblique cut 111 of the first cylinder 11 through the first exhaust structure to the first muffler 41, and the other part of the refrigerant enters the first muffler 41 through the aforementioned first drainage exhaust channel. Since there is a 180° phase difference between the first eccentric part 73 and the second eccentric part 74 of the crankshaft 75, the compression chamber of the second cylinder 12 is still in a low-pressure state at this time, and the second exhaust structure is in a closed state (that is, not open).

[0067] See details Figure 6 As shown, when the second cylinder 12 exhausts, part of the refrigerant enters the second muffler 42 through the second exhaust oblique cut 121 of the second cylinder 12 via the second exhaust structure and enters the first muffler 41 through the aforementioned exhaust connecting channel 5. Another part of the refrigerant enters the second muffler 42 through the bleed exhaust channel of the second cylinder 12 and is finally introduced into the first muffler 41 through the aforementioned exhaust connecting channel 5. Since there is a 180° phase difference between the first eccentric part 73 and the second eccentric part 74 of the crankshaft 75, the compression chamber of the first cylinder 11 is still in a low-pressure state at this time, so the first exhaust structure is in a closed state (i.e., not open).

[0068] The exhaust refrigerant in the first muffler 41 is further discharged into the internal exhaust chamber of the compressor, and then further discharged into the external refrigerant circulation system through the compressor's exhaust pipe.

[0069] According to an embodiment of the present invention, a rotary compressor is also provided, including a pump body assembly 200, wherein the pump body assembly 200 is the pump body assembly described above.

[0070] According to an embodiment of the present invention, an air conditioner is also provided, including the rotary compressor described above.

[0071] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0072] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A pump body assembly, characterized in that, The system includes a first cylinder (11), with a first flange (21) and a second flange (22) sealed at the two axial end faces of the first cylinder (11). A first exhaust structure is formed on the first flange (21). A first exhaust oblique cut (111) corresponding to the first exhaust structure is formed on the first end face of the first cylinder (11). The first cylinder (11) also has a first drainage exhaust channel. The outlet end of the first drainage exhaust channel is connected to the first exhaust oblique cut (111). The first cylinder (11) has a first radial surface passing through the midpoint of its axial height. The cylinder compression chamber space corresponding to the area between the first radial surface and the second end face of the first cylinder (11) is a first target area. The inlet end of the first drainage exhaust channel is connected to the first target area and is projected on the first radial surface. The inlet end of the first drainage exhaust channel is within the projection range of the first exhaust oblique cut (111).

2. The pump body assembly according to claim 1, characterized in that, The first exhaust channel is an exhaust groove (31) that extends along the axial direction of the first cylinder (11) and is formed on the inner circular wall of the first cylinder (11).

3. The pump body assembly according to claim 2, wherein the flow channel (31) extends to the second end face of the first cylinder (11); and / or, the opening of the flow channel (31) on the second end face is a beveled opening (311).

4. The pump body assembly according to claim 2, characterized in that, The projection of the drainage groove (31) on the first radial plane is an arc shape.

5. The pump body assembly according to claim 4, characterized in that, The depth of the drainage groove (31) decreases from the first end face of the first cylinder (11) to its second end face.

6. The pump body assembly according to claim 2, characterized in that, Projected onto the first radial plane, the maximum circumferential width of the first exhaust oblique cut (111) is L1, and the maximum circumferential width of the diversion groove (31) is L2, where L2≤0.8L1.

7. The pump body assembly according to claim 2, characterized in that, The first cylinder (11) has a first vane groove (112), and the drain groove (31) is located in the area where the first vane groove (112) intersects with the first exhaust oblique cut (111).

8. The pump body assembly according to claim 1, characterized in that, The first exhaust channel is an exhaust hole (32) extending along the axial direction of the first cylinder (11) and formed in the wall of the first cylinder (11), and an overflow port (321) is formed on the inner circular wall of the first cylinder (11), the overflow port (321) connecting the inlet end of the exhaust hole (32) and the first target area.

9. The pump body assembly according to claim 8, characterized in that, The drainage hole (32) includes a middle hole section and end hole sections at both ends of the middle hole section along the axial direction. The diameter of the end hole section is larger than the diameter of the middle hole section. And / or, the flow port (321) is a beveled cut.

10. The pump body assembly according to claim 1, characterized in that, The total volume of the first drainage and exhaust channel is V, and the displacement of the compressor used in the pump assembly is Q, with a maximum operating frequency of fmax. .

11. The pump body assembly according to claim 1, characterized in that, It also includes a second cylinder (12) and a partition plate (23). The partition plate (23) is sandwiched between the second end face of the first cylinder (11) and the first end face of the second cylinder (12). The second flange (22) is sealed and assembled on the second end face of the second cylinder (12). A second exhaust structure is formed on the second flange (22). A second exhaust oblique cut (121) corresponding to the first exhaust structure is formed on the second end face of the second cylinder (12). The second cylinder (12) forms a second drainage exhaust channel. The outlet end of the second drainage exhaust channel is connected to the second exhaust oblique cut (121). The second cylinder (12) has a second radial surface passing through the midpoint of its axial height. The cylinder compression chamber space corresponding to the area between the second radial surface and the first end face of the second cylinder (12) is the second target area. The inlet end of the second drainage exhaust channel is connected to the second target area and is projected on the second radial surface. The inlet end of the second drainage exhaust channel is within the projection range of the second exhaust oblique cut (121).

12. A rotary compressor, comprising a pump body assembly (200), characterized in that, The pump assembly (200) is the pump assembly according to any one of claims 1 to 11.

13. An air conditioner, characterized in that, Including the rotary compressor as described in claim 12.

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