Pump body assembly and fluid machine

Abstract

The application provides a pump body assembly and a fluid machine. The pump body assembly comprises a rotating shaft, a piston, and a piston communication channel. The piston has a sliding hole, at least a part of the rotating shaft is arranged in the sliding hole, and the sliding hole and the rotating shaft are in sliding fit during rotation of the piston and the rotating shaft. The pump body assembly provided by the application can solve the problem that the piston hinders oil flow in the prior art.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of rotary cylinder compressor, in particular to a pump body assembly and fluid machinery. BACKGROUND

[0002] Taking the rotary cylinder compressor as an example, the rotary cylinder compressor is a new type of positive displacement compressor. The cylinder and the rotating shaft rotate around their respective centers, and the piston reciprocates relative to the cylinder and the rotating shaft. The reciprocating motion of the piston relative to the cylinder realizes the periodic expansion and contraction of the volume chamber. The circumferential motion of the cylinder relative to the cylinder sleeve realizes the communication of the volume chamber with the suction passage and the exhaust passage. The above two compound motions realize the suction, compression and exhaust processes of the compressor.

[0003] With the increasing demand for high efficiency and energy saving of the compressor, it is necessary to optimize the structure of the rotary cylinder compressor to further improve the efficiency of the compressor and achieve energy saving and emission reduction. At present, in the process of operating the rotary cylinder compressor, the rotating shaft divides the sliding hole inside the piston into two cavity bodies. When the rotating shaft of the pump body assembly slides relative to the piston, the two cavities of the sliding hole periodically increase and decrease. The inner wall of the sliding hole of the piston extrudes the oil inside the sliding hole to transfer the oil inside the two cavities to realize the oil pressing process. However, in the actual operation process of the compressor, the inner wall of the sliding hole of the piston extrudes the oil, which hinders the smoothness of the oil. In the oil pressing process, the oil increases the power consumption of the piston and the rotating shaft, resulting in an increase in the power consumption of the pump body assembly of the rotary cylinder compressor.

[0004] As can be seen from the above, the rotary cylinder compressor has the problem of piston hindering oil flow in the process of use. SUMMARY

[0005] The main purpose of the present application is to provide a pump body assembly and fluid machinery to solve the problem of piston hindering oil flow in the process of use of the rotary cylinder compressor in the prior art.

[0006] In order to achieve the above purpose, according to one aspect of the present application, a pump body assembly is provided, which comprises a rotating shaft; a piston, the piston having a sliding hole, at least a part of the rotating shaft being arranged in the sliding hole, the sliding hole being in sliding cooperation with the rotating shaft during rotation of the piston with the rotating shaft, and the piston having a piston communication passage in communication with the sliding hole.

[0007] Further, the piston communication passage is a plurality of, the plurality of piston communication passages being arranged on the hole wall surface of the sliding hole; and / or the plurality of piston communication passages being arranged on the end surface of the piston in the axial direction of the rotating shaft.

[0008] Further, the number of the piston communication passages is less than 4.

[0009] Further, the piston communication groove is arranged on the hole wall surface of the sliding hole, and extends along the sliding direction of the piston, and forms the piston communication channel.

[0010] Further, the depth of the piston communication groove is consistent.

[0011] Further, the depth H2 of the piston communication groove gradually deepens from both ends of the piston communication groove to the middle part of the piston communication groove along the sliding direction of the piston.

[0012] Further, the piston communication groove is a crescent-shaped groove.

[0013] Further, the piston communication groove is arranged on the end surface of the piston along the axial direction of the rotating shaft, and extends along the sliding direction of the piston, and forms the piston communication channel.

[0014] Further, at least one piston communication groove is arranged on the end surface of the same end of the piston at the two edges of the sliding hole.

[0015] Further, the top end surface and the bottom end surface of the piston are both provided with the piston communication groove along the axial direction of the rotating shaft.

[0016] Further, the end surface on the side of the piston communication groove includes a first surface P1 and a second surface P2, wherein the first surface P1 is located between the piston communication groove and the edge of the sliding hole on the side of the piston communication groove, and the second surface P2 is located between the piston communication groove and the outer edge of the piston.

[0017] Further, the height difference between the first surface P1 and the second surface P2 is equal to 0.1mm.

[0018] Further, the distance L2 between the piston communication groove and the outer edge of the end surface of the piston on the side of the piston communication groove is greater than or equal to 2mm.

[0019] Further, the flexible groove is arranged in the sliding hole of the piston, and extends along the axial direction of the rotating shaft, and the end part of the flexible groove is communicated with the piston communication groove.

[0020] Further, the flexible groove is located at the end part of the piston communication groove.

[0021] Further, the flexible groove is a plurality of flexible grooves, and one flexible groove is arranged at each end of the same piston communication groove, so that the sliding protrusion protruding from the hole wall surface of the sliding hole is formed in the sliding hole.

[0022] Further, the sliding protrusion has a sliding surface on the side surface of the middle part of the sliding hole.

[0023] Further, the sliding surface is a plane.

[0024] Further, the end of the flexible groove penetrates the end surface of the piston along the axial direction of the rotating shaft.

[0025] Further, the length H3 of the flexible groove is greater than or equal to 2 mm and less than or equal to 7 mm.

[0026] Further, the angle A between the surface of the flexible groove near the middle side of the sliding hole and the hole wall surface on the side where the flexible groove is located is 10 to 30 degrees.

[0027] Further, the flexible groove includes a first groove surface and a second groove surface connected in sequence in the direction close to the middle of the sliding hole, the first groove surface has a first transition round corner ∠1 with the hole wall surface of the sliding hole, the second groove surface has a second transition round corner ∠2 with the first groove surface, and the second groove surface has a third transition round corner ∠3 at the edge away from the side of the first groove surface.

[0028] Further, the first transition round corner ∠1 is 0.3 to 1 degree, and / or the second transition round corner ∠2 is 0.3 to 1 degree, and / or the third transition round corner ∠3 is 0.5 to 3 degrees.

[0029] Further, the width H1 of the piston communication groove accounts for 1% to 12% of the width W1 of the piston.

[0030] Further, the depth H2 of the piston communication groove accounts for 3% to 50% of the width W1 of the piston.

[0031] Further, the cylinder liner; the cylinder is rotatably arranged in the cylinder liner, the cylinder is provided with a piston hole along the radial direction thereof, the piston is slidably arranged in the piston hole, the rotating shaft penetrates the piston and drives the piston to reciprocate along the extension direction of the piston hole, and the cylinder rotates to drive the piston to rotate.

[0032] According to another aspect of the present application, a fluid machine including a pump body assembly is provided.

[0033] According to the technical scheme of the present application, the pump body assembly includes a rotating shaft and a piston, the piston has a sliding hole, at least a part of the rotating shaft penetrates the sliding hole, the sliding hole and the rotating shaft are in sliding fit during the rotation of the piston with the rotating shaft, and the piston has a piston communication channel in communication with the sliding hole.

[0034] From the above description, it can be seen that, in the above embodiments of the present application, the piston communication channel is arranged inside the sliding hole of the piston to increase the smoothness of oil flow and reduce the power consumption of the pump body assembly. At present, during the operation of the rotary cylinder compressor, when the rotating shaft of the pump body assembly slides relative to the piston, the inner wall of the sliding hole of the piston will hinder the smoothness of oil flow when extruding the oil, resulting in an increase in the power consumption of the pump body assembly.

[0035] Specifically, the rotating shaft passes through the sliding hole on the piston, divides the piston into two cavities, and reciprocates relative to the rotating shaft during the movement of the pump body assembly, so that the two cavities are periodically increased and decreased to realize the process of pressing oil. During the reciprocating movement of the piston, the inner wall of the sliding hole of the piston extrudes the oil to realize the transfer of the oil between the two cavities. By arranging the communication channel communicated with the sliding hole on the piston, the smoothness of the oil transfer is improved, the resistance of the piston extruding the oil is reduced, the power consumption of the rotating shaft and the piston during the oil pressing process is reduced, and the power consumption of the pump body assembly is reduced. BRIEF DESCRIPTION OF DRAWINGS

[0036] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the application, and together with the description of the application, explain the application. The illustrative embodiments of the application and its description serve to explain the application without imposing undue limitations on the application. In the drawings:

[0037] Figure 1 An exploded view of the pump body assembly in the application is shown; and

[0038] Figure 2 An installation relationship between the rotating shaft and the piston in the pump body assembly is shown. Figure 1

[0039] Figure 3 A schematic view of the piston communication groove arranged on the hole wall surface of the sliding hole of the piston in the application is shown, wherein the piston communication groove is a rectangular groove;

[0040] Figure 4 A schematic view of the piston communication groove arranged on the hole wall surface of the sliding hole of the piston in the application is shown, wherein the piston communication groove is a crescent-shaped groove;

[0041] Figure 5 A schematic view of the piston communication groove arranged on the end surface of the piston in the application is shown.

[0042] Figure 6 A top view of the pump body assembly is shown. Figure 5

[0043] A side view of the pump body assembly is shown. Figure 7 Figure 5

[0044] Figure 8 An axial sectional view of the pump body assembly is shown. Figure 7

[0045] A schematic view of the piston communication groove and the flexible groove arranged on the end surface of the piston in the application is shown. Figure 9

[0046] A top view of the pump body assembly is shown. Figure 10 Figure 9

[0047] ​​​​​Figure 11 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0048] Figure 12 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and Figure 11 The sectional view of A-A direction in the present application is shown;

[0049] Figure 13 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0050] Figure 14 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and Figure 13 The top view of the present application is shown;

[0051] Figure 15 The enlarged view of a in the present application is shown; Figure 14

[0052] Figure 16 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0053] Figure 17 The enlarged view of b in the present application is shown; Figure 16

[0054] The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and Figure 18

[0055] Figure 19 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0056] Figure 20 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0057] Figure 21 The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and

[0058] Figure 22 The top view of the present application is shown; Figure 21

[0059] The schematic diagram showing the installation relationship of the components in the pump body assembly in the present application is shown; and Figure 23

[0060] The sectional view of the avoidance recess in the present application is shown; Figure 24 Figure 23 The sectional view of the avoidance recess in the present application is shown;

[0061] Figure 25 Figure 23 The sectional view of the avoidance recess in the present application is shown;

[0062] Figure 26 ​​​​The axial sectional view of the rotating shaft, the cylinder, the lower flange and the piston in the present application along the direction perpendicular to the piston movement is shown.

[0063] Figure 27 The axial sectional view of the rotating shaft, the cylinder, the lower flange and the piston in the present application along the direction perpendicular to the piston movement is shown.

[0064] Figure 28 The structural schematic diagram of the lower flange in the present application with the avoidance recess is shown, wherein the avoidance recess is irregularly shaped.

[0065] Figure 29 The structural schematic diagram of the lower flange in the present application with the avoidance recess is shown, wherein the avoidance recess is irregularly shaped.

[0066] Wherein, the above-mentioned drawings include the following reference signs:

[0067] 10, cylinder; 106, piston hole; 1011, limiting convex ring; 1012, avoidance recess; 1013, first face section; 1014, second face section; 20, piston; 2011, sliding hole; 2021, piston communication groove; 2022, sliding convex boss; 2023, flexible groove; 2024, sliding face; 30, rotating shaft; 3011, sliding cooperation face; 3012, rotating shaft flow communication hole; 3013, rotating shaft communication groove; 3014, long axis section; 3015, short axis section; 3016, connecting face; 40, cylinder sleeve; 4001, volume cavity; 60, lower flange; 6001, positioning convex boss; 6002, avoidance recess; 6003, flange hole; 6004, first section; 6005, second section; 6006, support rib. DETAILED DESCRIPTION

[0068] It should be noted that the embodiments and the features in the embodiments in the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0069] It should be noted that, unless otherwise specified, all the technical and scientific terms used in the present application have the same meaning as that generally understood by the ordinary skilled in the art to which the present application belongs.

[0070] In the present application, the orientation words such as "upper", "lower", "top", "bottom" are generally directed to the directions shown in the drawings, or are directed to the vertical, perpendicular or gravity directions of the components themselves; similarly, for the convenience of understanding and description, "inner" and "outer" refer to the inner and outer relative to the contour of the components themselves, but the above-mentioned orientation words are not used to limit the present application.

[0071] In order to solve the problem that the cylinder 10, the piston 20, the rotating shaft 30 and the flange structure hinder the oil flow in the prior art, the application provides a pump body assembly and a fluid machine.

[0072] The fluid machine comprises the pump body assembly.

[0073] In order to solve the problem that the cylinder 10, the piston 20, the rotating shaft 30 and the flange structure hinder the oil flow in the prior art, the application provides a pump body assembly and a fluid machine.

[0074] Specifically, as shown in the drawings, the pump body assembly comprises a rotating shaft 30 and a piston 20. Figures 1 to 10 The piston 20 has a sliding hole 2011, at least a part of the rotating shaft 30 penetrates the sliding hole 2011, the sliding hole 2011 and the rotating shaft 30 are in sliding fit during the rotation of the piston 20 relative to the rotating shaft 30, and the piston 20 has a piston communication channel in communication with the sliding hole 2011.

[0075] From the above description, it can be seen that in the above embodiment of the application, the piston communication channel is arranged in the sliding hole 2011 of the piston 20 to increase the smoothness of the oil flow and reduce the power consumption of the pump body assembly.

[0076] Specifically, the rotating shaft 30 penetrates the sliding hole 2011 on the piston 20 to divide the piston 20 into two cavities, the piston 20 reciprocates relative to the rotating shaft 30 during the movement of the pump body assembly, and the two cavities periodically increase and decrease to realize the process of pressing oil.

[0077] Further, the number of the piston communication channels is less than 4, and the number of the piston communication channels greater than 4 will affect the strength of the piston 20, cause insufficient stability of the piston 20, reduce the oil pressing power, and affect the overall operation efficiency of the pump body assembly.

[0078] It should be noted that, as shown in the drawings, Figures 3 to 10In the specific embodiment shown, the piston communication passage is provided on the hole wall surface of the sliding hole 2011. The piston communication passage is a rectangular piston communication groove 2021 with a uniform depth.

[0079] Next, various embodiments of the piston communication passage provided on the piston 20 are provided. Figures 3 to 10

[0080] As shown in the specific embodiment, Figure 3 the piston communication passage is provided on the hole wall surface of the sliding hole 2011. The piston communication passage is a rectangular piston communication groove 2021 with a uniform depth.

[0081] Specifically, by providing the rectangular piston communication groove 2021 on the hole wall surface of the sliding hole 2011 of the piston 20, the piston communication groove 2021 extends in the sliding direction of the piston 20 to form the piston communication passage, thereby increasing the flow path of the oil. When the hole wall surface of the sliding hole 2011 of the piston 20 extrudes the oil, the oil can be transferred through the piston communication groove 2021, improving the smoothness of the oil transfer and reducing the power consumption of the piston 20 and the rotating shaft 30 during the oil pressing process.

[0082] As shown in the specific embodiment, Figure 4 the piston communication passage is provided on the hole wall surface of the sliding hole 2011. The piston communication passage is a crescent-shaped piston communication groove 2021.

[0083] It should be noted that in the sliding direction of the piston 20, the depth H2 of the piston communication groove 2021 gradually deepens from both ends of the piston communication groove 2021 to the middle of the piston communication groove 2021 to form the crescent-shaped piston communication groove 2021.

[0084] Specifically, by providing the crescent-shaped piston communication groove 2021 on the hole wall surface of the sliding hole 2011 of the piston 20, the piston communication groove 2021 extends in the sliding direction of the piston 20 to form the piston communication passage, thereby increasing the flow path of the oil. When the hole wall surface of the sliding hole 2011 of the piston 20 extrudes the oil, the oil can be transferred through the piston communication groove 2021, improving the smoothness of the oil transfer and reducing the power consumption of the piston 20 and the rotating shaft 30 during the oil pressing process.

[0085] As shown in the specific embodiment, Figures 5 to 8 the piston communication passage is provided on the hole wall surface of the sliding hole 2011. The piston communication passage is a crescent-shaped piston communication groove 2021.

[0086] ​Furthermore, the piston connecting groove 2021 extends along the sliding direction of the piston 20, and the piston connecting groove 2021 constitutes a piston connecting channel.

[0087] Specifically, by providing a piston connecting channel on the axial end face of the rotating shaft 30 of the piston 20, the flow path of the oil is increased. When the wall of the sliding hole 2011 of the piston 20 squeezes the oil, the oil can be transferred through the piston connecting groove 2021, which improves the smoothness of oil transfer and reduces the power consumption of the piston 20 and the rotating shaft 30 during the oil pressing process.

[0088] like Figures 5 to 8 As shown, on the end face of the piston 20 at the same end, at least one piston connecting groove 2021 is provided at each of the two oppositely arranged edges of the sliding hole 2011. By providing the piston connecting groove 2021 at the two oppositely positioned edges of the sliding hole 2011, the oil can be transferred through the piston connecting groove 2021 when the piston 20 squeezes the oil, thereby improving the smoothness of oil movement and reducing the power consumption of the pump assembly.

[0089] like Figures 5 to 8 As shown, piston connecting grooves 2021 are provided on both the top and bottom end faces of the piston 20 along the axial direction of the rotating shaft 30. The presence of piston connecting grooves 2021 on both the top and bottom end faces of the piston 20 increases the flow path of the oil, improving the smoothness of oil movement and reducing the power consumption of the pump assembly when the oil is squeezed against the inner wall of the sliding hole 2011 of the piston 20.

[0090] like Figure 7 As shown, with the piston connecting groove 2021 as the boundary, the end face on the side where the piston connecting groove 2021 is located includes a first surface P1 and a second surface P2. The first surface P1 is located in the region between the piston connecting groove 2021 and the edge of the sliding hole 2011 on its side, and the second surface P2 is located in the region between the piston connecting groove 2021 and the outer edge of the piston 20. Thus, during the movement of the piston 20, the second surface P2 will not contact the cylinder, thereby avoiding friction.

[0091] Specifically, the height difference between the first surface P1 and the second surface P2 is 0.1 mm. When the height difference is greater than 0.1 mm, the strength of the piston 20 may be affected due to the excessive height difference. When the height difference is less than 0.1 mm, the flowability of the oil cannot be effectively improved, and the power consumption of the pump body assembly during the oil pressing process cannot be reduced.

[0092] like Figure 6As shown, the distance L2 between the piston communication groove 2021 and the outer edge of the end face of the piston 20 on the side where the piston communication groove 2021 is located is greater than or equal to 2 mm. When the distance between the piston communication groove 2021 and the outer edge of the end face of the piston 20 on the side where the piston communication groove 2021 is located is less than 2 mm, the strength of the piston 20 is affected due to the excessively small wall thickness of the piston 20, and the piston 20 is prone to damage during operation of the piston 20, which causes the pump body assembly to fail to operate normally.

[0093] As shown in the specific embodiment, the piston communication passage is a plurality of piston communication grooves 2021 and flexible grooves 2023 cooperating structures. The flexible grooves 2023 are arranged in the sliding hole 2011 of the piston 20 and located at the end of the piston communication groove 2021. Figures 9 to 10 Further, the flexible grooves 2023 extend in the axial direction of the rotating shaft 30, and the end of the flexible groove 2023 communicates with the piston communication groove 2021.

[0094] Specifically, by arranging the piston communication groove 2021 and the flexible groove 2023 in the sliding hole 2011 of the piston 20, the oil liquid path is increased, the oil liquid transfer is improved in smoothness when the wall of the sliding hole 2011 of the piston 20 extrudes the oil liquid, the resistance of the oil liquid to the piston 20 and the rotating shaft 30 is reduced, and the power consumption of the pump body assembly is reduced.

[0095] As shown in 9 to

[0096] Specifically, the flexible groove 2023 is a plurality of flexible grooves 2023, and one flexible groove 2023 is arranged at each end of the same piston communication groove 2021. Among them, along the axial direction of the rotating shaft 30, the end of the flexible groove 2023 penetrates the end face of the piston 20 at both ends, so that the sliding convex 2022 protruding from the hole wall surface of the sliding hole 2011 is formed in the sliding hole 2011. Figure 10 Specifically, the sliding convex 2022 has a sliding surface 2024 on the side surface of the middle part of the sliding hole 2011. The sliding surface 2024 is a plane, and the sliding surface 2024 and the rotating shaft 30 slide relative to each other to realize the process of pressing oil during operation of the pump body assembly. The piston communication groove 2021 and the flexible groove 2023 improve the smoothness of the oil liquid transfer, reduce the resistance of the oil liquid to the piston 20 and the rotating shaft 30, and reduce the power consumption of the pump body assembly.

[0097] As shown in

[0098] Figure 10 ​As shown, the length H3 of the flexible groove 2023 is greater than or equal to 2 mm and less than or equal to 7 mm. When the length H3 of the flexible groove 2023 is less than 2 mm, the flexible groove 2023 is too small, which is not conducive to improving the smoothness of oil flow. When the length H3 of the flexible groove 2023 is greater than 7 mm, the strength of the sliding boss 2022 is affected, and the sliding boss 2022 is prone to damage during the sliding engagement with the rotating shaft 30.

[0099] like Figure 10 As shown, the angle A between the surface of the flexible groove 2023 near the middle of the sliding hole 2011 and the hole wall surface of the flexible groove 2023 on the side where it is located in the sliding hole 2011 is 10 degrees to 30 degrees. If the angle A is too large, it will affect the strength of the flexible groove 2023 on the sliding boss 2022, and the sliding boss 2022 is prone to damage during sliding engagement with the rotating shaft 30. If the angle A is too small, it will not improve the smoothness of oil transfer, reduce the resistance of oil to the piston 20 and the rotating shaft 30, and reduce the power consumption of the pump assembly.

[0100] like Figure 10 As shown, the flexible groove 2023 includes a first groove surface and a second groove surface connected in sequence along the direction near the middle of the sliding hole 2011. The first groove surface has a first transition fillet ∠1 between itself and the hole wall of the sliding hole 2011, the second groove surface has a second transition fillet ∠2 between itself and the first groove surface, and the edge of the second groove surface away from the first groove surface has a third transition fillet ∠3.

[0101] Specifically, the first transition fillet ∠1 is 0.3 to 1 degree, the second transition fillet ∠2 is 0.3 to 1 degree, and the third transition fillet ∠3 is 0.5 to 3 degrees. By setting the fillets and their corresponding angle ranges, the flowability of the oil is improved and the power consumption of the pump body components is reduced without affecting the strength of the sliding boss 2022. The fillet setting helps to reduce the concentrated stress on the sliding boss 2022, enabling stable operation during oil pressure.

[0102] It should be noted that the piston 20 can also be manufactured using 3D printing technology, with a large hollow area inside and an outer shell, which cannot be completed by ordinary machining. An irregularly shaped piston connecting groove 2021 is provided on the inner wall of the sliding hole 2011. The width 1 of the piston connecting groove 2021 is 12% to 70% of the width W1 of the piston 20, the width 2 of the piston connecting groove 2021 is 1% to 12% of the width W1 of the piston 20, and the wall thickness of the piston connecting groove 2021 is 2mm-4mm.

[0103] like Figure 6As shown, the width H1 of the piston connecting groove 2021 accounts for 1%-12% of the width W1 of the piston 20. Specifically, when the width H1 of the piston connecting groove 2021 is too small, the smoothness of oil transfer during the oil pressing process cannot be effectively improved, and the effect of reducing the power consumption of the pump body assembly cannot be achieved. When the width H1 of the piston connecting groove 2021 is too large, it affects the strength of the rotating shaft 30, and the rotating shaft 30 is prone to breakage during the movement of the rotating shaft 30 relative to the piston 20.

[0104] like Figure 3 , Figure 5 and Figure 6 As shown, the depth H2 of the piston connecting groove 2021 accounts for 3%-50% of the width W1 of the piston 20. Specifically, when the depth H2 of the piston connecting groove 2021 is too small, it cannot effectively improve the smoothness of oil transfer during the oil pressing process, and cannot achieve the effect of reducing the power consumption of the pump body assembly. When the depth H2 of the piston connecting groove 2021 is too large, it affects the strength of the rotating shaft 30, and the rotating shaft 30 is prone to breakage during the movement of the rotating shaft 30 relative to the piston 20.

[0105] The pump assembly of the present invention also includes a cylinder 10 and a cylinder liner 40. The cylinder 10 is rotatably disposed in the cylinder liner 40. A piston hole 106 is provided on the cylinder 10 along its radial direction. The piston 20 is slidably disposed in the piston hole 106. The rotating shaft 30 passes through the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole 106. The cylinder 10 rotates to drive the piston 20 to rotate.

[0106] Specifically, during the process of the rotating shaft 30 driving the piston 20 to reciprocate along the extension direction of the piston hole 106, the piston 20 squeezes the oil to realize the oil pressing process of the pump body assembly. The oil is transferred inside the two cavities formed by the rotating shaft 30, the piston 20 and the cylinder 10. By setting a piston connecting channel on the piston 20, the resistance of the piston 20 to the oil transfer during the oil flow process is reduced, and the power consumption of the pump body assembly during the oil pressing process is reduced.

[0107] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0108] By setting a piston connecting channel inside the sliding hole 2011 of the piston 20, the smoothness of oil flow is increased and the power consumption of the pump body assembly is reduced. Currently, during the operation of the rotary compressor, when the rotating shaft 30 of the pump body assembly slides relative to the piston 20, the inner wall of the sliding hole 2011 of the piston 20 obstructs the smoothness of oil flow when squeezing the oil, resulting in an increase in the power consumption of the pump body assembly.

[0109] Specifically, the rotating shaft 30 passes through the sliding hole 2011 on the piston 20, and divides the piston 20 into two cavities. During the movement of the pump body assembly, the piston 20 reciprocates relative to the rotating shaft 30, and the two cavities are periodically increased and decreased to realize the process of oil compression. During the reciprocating movement of the piston 20, the inner wall of the sliding hole 2011 of the piston 20 extrudes the oil to realize the transfer of the oil between the two cavities. By arranging the communication channel in communication with the sliding hole 2011 on the piston 20, the smoothness of the oil transfer is improved, the resistance of the piston 20 extruding the oil is reduced, the power consumption of the rotating shaft 30 and the piston 20 during the oil compression process is reduced, and the power consumption of the pump body assembly is reduced.

[0110] To solve the problem of hindering the flow of oil in the rotating cylinder compressor in the prior art, the gap between the limiting convex ring 1011 on the cylinder 10 and the rotating shaft 30 can be optimized to reduce the hindering of the limiting convex ring 1011 on the cylinder 10 to the oil, so as to reduce the power consumption of the pump body assembly.

[0111] Specifically, as shown in Figures 11 to 15 the pump body assembly comprises a cylinder 10 and a rotating shaft 30. The cylinder 10 is rotatably arranged, and the cylinder 10 has a limiting convex ring 1011 along the axial direction thereof. The rotating shaft 30 passes through the limiting convex ring 1011 and extends into the cylinder 10. The limiting convex ring 1011 is provided with a clearance avoiding recess 1012 on the inner annular surface of the side facing the rotating shaft 30, so that a flow gap is formed between the rotating shaft 30 and the clearance avoiding recess 1012.

[0112] From the above description, it can be seen that in the above embodiments of the present application, the clearance avoiding recess 1012 is arranged on the inner annular surface of the side of the limiting convex ring 1011 on the cylinder 10 facing the rotating shaft 30, so as to increase the flow gap between the rotating shaft 30 and the cylinder 10, reduce the resistance of the rotating shaft 30 and the piston 20 to the oil, and improve the operation stability. The flow gap formed between the rotating shaft 30 and the limiting convex ring 1011 on the cylinder 10 in the existing pump body assembly is too small. The piston 20 and the rotating shaft 30 are hindered by the oil during the movement, which increases the power consumption of the piston 20 and the rotating shaft 30 for oil compression, and affects the stability of the rotating shaft 30 and the piston 20.

[0113] Specifically, the rotating shaft 30 passes through the cylinder 10, and a flow gap is formed between the rotating shaft 30 and the inner annular surface of the limiting convex ring 1011 of the cylinder 10. The clearance avoiding recess 1012 is arranged on the inner annular surface of the limiting convex ring 1011 to expand the flow gap between the rotating shaft 30 and the cylinder 10, so that the oil can flow and transfer conveniently, and the resistance of the rotating shaft 30 and the piston 20 to the oil during the rotation is effectively reduced. The phenomenon that the rotating shaft 30 and the piston 20 are hindered by the oil, which leads to the increase of the power consumption of the rotating shaft 30 and the piston 20 and the instability, is avoided.

[0114] AsFigures 12 to 15 As shown, the recessed portion 1012 extends to the two sides of the limiting protrusion 1011 on the axial direction of the rotating shaft 30.

[0115] Specifically, the recessed portion 1012 extends to the two sides of the limiting protrusion ring 1011 to form a gap channel, thereby expanding the flow gap, improving the smoothness of oil flow in the flow gap, reducing the obstruction of oil to the rotating shaft 30, and reducing the power consumption of the pump body assembly.

[0116] like Figures 12 to 15 As shown, the recessed portion 1012 is a recessed groove provided on the inner ring surface. The recessed groove makes the wall thickness of the limiting protrusion 1011 at its location thinner than the wall thickness of the limiting protrusion 1011 where no recessed groove is provided.

[0117] Specifically, the recessed portion 1012 is a recessed groove on the inner ring surface. The recessed groove increases the flow clearance at the recessed portion. During the oil pressing process of the pump body assembly, when the oil is squeezed and flows through the recessed portion, the obstruction to the oil can be reduced, the smoothness of the oil flow can be improved, and the power consumption of the pump body assembly can be reduced.

[0118] In this invention, the flow gap is greater than 1 mm and less than 3 mm. Controlling the flow gap within the range of 1 mm to 3 mm effectively improves the smoothness of oil flow and reduces the power consumption of the pump assembly. When the flow gap is less than 1 mm, the excessively small gap cannot improve the smoothness of oil flow and fails to reduce the power consumption of the pump assembly. When the flow gap is greater than 3 mm, the excessively large flow gap will affect the strength of the limiting protrusion 1011 of the cylinder 10, easily causing damage to the limiting protrusion 1011. This can lead to tilting and oil leakage problems during operation of the cylinder 10, and also affect the stable operation of the pump assembly.

[0119] Specifically, the circumferential width of the recess 1012 along the inner annular surface is 2%-5% of the diameter of the inner annular surface. If the circumferential width of the recess 1012 along the inner annular surface is too small, the width of the flow gap formed at the recess 1012 will be too small, which cannot effectively improve the smoothness of oil flow through the flow gap and cannot achieve the effect of reducing the power consumption of the pump body assembly. If the circumferential width of the recess 1012 along the inner annular surface is too large, it will affect the stability of the limiting protrusion 1011 of the cylinder 10, causing the cylinder 10 to easily tilt and leak oil during operation, and also affecting the stable operation of the pump body assembly.

[0120] It should be noted that the circumferential width of the clearance recess 1012 along the inner ring surface can be changed according to the size of the limiting protrusion 1011 on the cylinder 10. Different models of cylinder 10 can have clearance recesses 1012 of different widths opened on the inner ring surface of the limiting protrusion 1011 of the cylinder 10.

[0121] As shown in Figures 14 to 15 , the flow gap is 2%-30% of the diameter of the inner annular surface. Specifically, when the pump body assembly is pressurized, the oil can flow through the flow gap to reduce the resistance of the limiting convex ring 1011 to the oil, thereby improving the smoothness of the oil flow and reducing the power consumption of the pump body during pressurization. When the flow gap is too small, the flow gap cannot improve the smoothness of the oil flowing through the flow gap, and the effect of reducing the power consumption of the pump body assembly cannot be achieved. When the flow gap is too large, the large flow gap will affect the strength of the limiting convex ring 1011 of the cylinder 10, which is easy to cause damage to the limiting convex ring 1011, resulting in problems such as inclination and oil leakage of the cylinder 10 during operation, and affecting the stable operation of the pump body assembly.

[0122] It should be noted that the flow gap can be changed according to the size of the limiting convex ring 1011 on the cylinder 10. Different models of the cylinder 10 can correspond to different flow gaps on the inner annular surface of the limiting convex ring 1011 of the cylinder 10.

[0123] As shown in Figure 15 , the minimum wall thickness t of the limiting convex ring 1011 at the location of the clearance recess 1012 is greater than or equal to 1 mm. The wall thickness of the limiting convex ring 1011 is greater than or equal to 1 mm, which has a positioning effect during rotation of the cylinder 10, and affects the stability of the cylinder 10 to avoid inclination of the cylinder 10. The limiting convex ring 1011 has strength, so the minimum wall thickness t of the limiting convex ring 1011 is greater than or equal to 1 mm. To ensure the strength of the limiting convex ring 1011, the cylinder 10 can be stably operated.

[0124] As shown in Figure 11 , Figure 13 , Figure 14 and Figure 15 , the cylinder 10 has a piston hole 106 extending in the radial direction, the inner annular surface of the limiting convex ring 1011 has opposite first and second face segments 1013 and 1014, the line connecting the first and second face segments 1013 and 1014 is perpendicular to the extension direction of the piston hole 106, and the first and second face segments 1013 and 1014 each have a clearance recess 1012.

[0125] Specifically, the line connecting the first and second face segments 1013 and 1014 of the limiting convex ring 1011 of the cylinder 10 is perpendicular to the extension direction of the piston hole 106 on the cylinder 10, the oil flows through the first and second face segments, and the clearance recess 1012 is provided on the first and second face segments 1013 and 1014 to increase the smoothness of the oil in the flow gap, facilitate the transfer of the oil, and reduce the power consumption of the pump body assembly.

[0126] It should be noted that during the installation of the pump body assembly, the rotating shaft 30 can be close to the first segment surface or the second segment surface, and the avoidance recess 1012 is arranged on the first segment surface and the second segment surface, so that the rotating shaft 30 close to the first segment surface or the rotating shaft 30 close to the second segment surface achieves the same technical effect, which can improve the smoothness of the oil and facilitate installation.

[0127] As shown in Figures 11 to 15 , the pump body assembly further comprises a piston 20, the piston 20 has a sliding hole 2011, the rotating shaft 30 passes through the sliding hole 2011, and the inner ring surface of the limiting convex ring 1011 is provided with an avoidance recess 1012 on each segment surface in the extension direction of the sliding hole 2011.

[0128] Specifically, the piston 20 is provided with a sliding hole 2011, and the piston 20 moves in the cylinder 10 to realize oil pressing. The piston 20 extrudes the oil to transfer the oil. After the oil is extruded by the piston 20, the oil will flow through a segment surface of the limiting convex ring 1011 in the extension direction of the sliding hole 2011, and the avoidance recess 1012 is arranged on the segment surface. The avoidance recess 1012 can reduce the extrusion resistance of the piston 20, reduce the vibration of the piston 20, avoid the problem of damage of the piston 20, improve the smoothness of the oil flow, reduce the resistance between the rotating shaft 30 and the oil, and reduce the power consumption of the pump body assembly. Here, only the reference is changed. Previously, the extension direction of the piston hole 106 was used as a reference. Here, the extension direction of the sliding hole 2011 is used as a reference. The extension direction of the piston hole 106 and the extension direction of the sliding hole 2011 can be the same or perpendicular. Specifically, Figure 12 , it is obvious that the extension direction of the piston hole 106 and the extension direction of the sliding hole 2011 are perpendicular.

[0129] As shown in Figure 11 , the pump body assembly further comprises a cylinder sleeve 40, the cylinder sleeve 40 has a volume cavity 4001, the cylinder 10 is rotatably arranged in the volume cavity 4001, the piston 20 is slidingly arranged in the piston hole 106 of the cylinder 10, the rotating shaft 30 passes through the sliding hole 2011 of the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole 106, and the cylinder 10 rotates to drive the piston 20 to rotate.

[0130] Specifically, the cylinder 10 rotates with the rotating shaft 30, and the cylinder 10 can drive the piston 20 to rotate. The rotating shaft 30 penetrates the sliding hole 2011 of the piston 20 and divides the volume cavity 4001 inside the cylinder 10 and the piston 20 into two cavities. Under the action of the rotating shaft 30, the piston 20 reciprocates along the extension direction of the piston hole 106 inside the piston hole 106. The reciprocation of the piston 20 causes the two cavities to periodically increase and decrease, and the piston 20 extrudes the oil inside the cylinder 10 to achieve the periodic transfer of the oil in the two cavities. By providing the avoidance recess 1012 on the inner ring surface of the limiting convex ring 1011 of the cylinder 10, the oil transfer can be facilitated, and the power consumption of the pump body assembly can be reduced.

[0131] From the above description, it can be seen that the above-mentioned embodiments of the present application achieve the following technical effects:

[0132] By providing the avoidance recess 1012 on the inner ring surface of the limiting convex ring 1011 of the cylinder 10 towards the rotating shaft 30 side, the flow gap between the rotating shaft 30 and the cylinder 10 is increased, the resistance of the oil to the rotating shaft 30 and the piston 20 is reduced, and the operation stability is improved. The flow gap between the rotating shaft 30 and the inner wall of the limiting convex ring 1011 of the cylinder 10 in the existing pump body assembly is too small. The piston 20 and the rotating shaft 30 are hindered by the oil during movement, which increases the power consumption of the piston 20 and the rotating shaft 30 for pressing oil, and affects the stability of the rotating shaft 30 and the piston 20.

[0133] Specifically, the rotating shaft 30 penetrates the cylinder 10, and the rotating shaft 30 and the inner ring surface of the limiting convex ring 1011 of the cylinder 10 form a flow gap. By providing the avoidance recess 1012 on the inner ring surface of the limiting convex ring 1011, the flow gap between the rotating shaft 30 and the cylinder 10 is expanded, the oil can flow and transfer conveniently, the resistance of the oil to the rotating shaft 30 and the piston 20 during rotation is effectively reduced, and the phenomenon that the rotating shaft 30 and the piston 20 are hindered by the oil, which increases the power consumption of the rotating shaft 30 and the piston 20 and causes instability, is avoided.

[0134] To solve the problem of hindering the flow of oil in the rotating cylinder compressor in the prior art, the rotating shaft 30 can be optimized to reduce the hindering of the piston 20 by the rotating shaft 30 to facilitate the flow of oil, thereby reducing the power consumption of the pump body assembly.

[0135] Specifically, as Figures 16 to 19As shown in the figure, the pump body assembly comprises a rotating shaft 30 and a piston 20, the piston 20 has a sliding hole 2011, at least a part of the rotating shaft 30 is arranged in the sliding hole 2011, the sliding hole wall of the sliding hole 2011 is in sliding fit with the rotating shaft 30 during the rotation of the piston 20 along with the rotating shaft 30, and the shaft section of the rotating shaft 30 in the sliding hole 2011 is provided with a rotating shaft flow channel, and the rotating shaft flow channel extends along the sliding direction of the piston 20.

[0136] As can be seen from the above description, in the above embodiment of the present application, the flow channel is arranged on the shaft section of the rotating shaft 30 inside the sliding hole 2011 of the piston 20, so as to enhance the smoothness of oil flow and reduce the power consumption of the pump body assembly. At present, during the operation of the rotary cylinder compressor, when the rotating shaft of the pump body assembly slides relative to the piston, the area of the rotating shaft inside the piston hinders the flow of oil, which causes the oil to hinder the movement of the piston and the rotating shaft, and increases the power consumption of the pump body assembly.

[0137] Specifically, the rotating shaft 30 passes through the sliding hole 2011 on the piston 20, and divides the piston 20 into two cavities, the piston 20 reciprocates relative to the rotating shaft 30 during the movement of the pump body assembly, and the two cavities periodically increase and decrease to realize the process of pressing oil, the shaft section of the rotating shaft 30 inside the sliding hole 2011 of the piston 20 extrudes the oil, so that the oil is transferred in the two cavities. By arranging the rotating shaft flow channel on the shaft section of the rotating shaft 30 inside the sliding hole 2011, the hindering of the rotating shaft 30 to the oil is reduced, and the power consumption of the piston 20 and the rotating shaft 30 during the process of pressing oil is reduced, so as to reduce the power consumption of the pump body assembly.

[0138] As shown in the figure, Figure 16 and Figure 18 As shown in the figure, the rotating shaft flow channel is a plurality of rotating shaft flow channels, and the plurality of rotating shaft flow channels are arranged at intervals along the axial direction of the rotating shaft 30. By arranging a plurality of rotating shaft flow channels on the rotating shaft 30, the oil can be transferred through the plurality of rotating shaft flow channels during the process of pressing oil, the flow path is increased, and the power consumption of the piston 20 and the rotating shaft 30 during the process of pressing oil is reduced.

[0139] Further, the number of rotating shaft flow channels is less than 4. When the number of flow channels is greater than 4, too many rotating shaft flow channels will reduce the strength of the rotating shaft 30, and the rotating shaft 30 is prone to breakage during the relative operation of the rotating shaft 30 and the piston 20. When the number of rotating shaft flow channels is less than 4, the flow path of the oil is increased without affecting the strength of the rotating shaft 30.

[0140] It should be noted that, in the Figures 16 to 19In the specific embodiment shown, the rotating shaft flow passage is a passage provided on the rotating shaft 30 to increase the oil flow path. In specific embodiments, the rotating shaft flow passage can have various specific structures, as long as it can reduce the obstruction of the rotating shaft 30 to the oil transfer inside the sliding hole 2011 of the piston 20. Here, specific embodiments are not listed one by one.

[0141] Next, according to the different structures of the rotating shaft flow passage, the following specific embodiments are provided for illustration.

[0142] As shown in the specific embodiment, Figures 16 to 17 the sliding hole 2011 has a set of oppositely arranged sliding hole 2011 hole wall surfaces, the rotating shaft 30 has a sliding fit surface 3011 on the shaft segment located in the sliding hole 2011, and the rotating shaft flow passage is a rotating shaft communication groove 3013 provided on the sliding fit surface 3011.

[0143] Specifically, when the rotating shaft 30 moves relative to the sliding hole 2011 of the piston 20, the sliding fit surface 3011 on the rotating shaft 30 is used in relative sliding fit with the hole wall surface of the sliding hole 2011. The rotating shaft communication groove 3013 is provided on the sliding fit surface 3011, and the sliding fit surface 3011 is pressed against the hole wall surface of the sliding hole 2011 during relative sliding. The oil can be transferred through the rotating shaft communication groove 3013, reducing the resistance between the rotating shaft 30 and the piston 20 and the oil, and reducing the power consumption of the pump body assembly.

[0144] It should be noted that the sliding fit surface 3011 is a flat surface, i.e., the hole wall surface of the sliding hole 2011 is a flat surface. The sliding fit surface 3011 reciprocally slides relative to the hole wall surface of the sliding hole 2011, and the rotating shaft communication groove 3013 is opened on the surface of the sliding fit surface 3011.

[0145] As shown in the specific embodiment, Figure 17 and Figure 19 the width t1 of the rotating shaft communication groove 3013 accounts for 5%-20% of the diameter R1 of the shaft segment of the rotating shaft 30 located in the sliding hole 2011. When the width t1 of the rotating shaft communication groove 3013 is too small, it cannot effectively improve the smoothness of oil transfer during oil pressing, and cannot achieve the effect of reducing the power consumption of the pump body assembly. When the width t1 of the rotating shaft communication groove 3013 is too large, it affects the strength of the rotating shaft 30, and the rotating shaft 30 is prone to breaking during movement relative to the piston 20.

[0146] It should be noted that the width t1 of the rotating shaft communication groove 3013 can be changed according to different models of the rotating shaft 30, as long as it can improve the smoothness of the oil and reduce the power consumption of the pump body assembly during oil pressing.

[0147] As shown in the specific embodiment, Figure 17 and Figure 19As shown, the depth h1 of the shaft communication groove 3013 accounts for 5%-20% of the diameter R1 of the shaft segment of the shaft 30 located in the sliding hole 2011.

[0148] Specifically, when the depth h1 of the shaft communication groove 3013 is too small, the smoothness of the oil transfer during the oil pressing process cannot be effectively improved, and the effect of reducing the power consumption of the pump body assembly cannot be achieved. When the depth h1 of the shaft communication groove 3013 is too large, the strength of the shaft 30 is affected, and the shaft 30 is prone to breakage during the movement of the shaft 30 relative to the piston 20.

[0149] It should be noted that the depth h1 of the shaft communication groove 3013 can be changed according to different models of the shaft 30, so as to improve the smoothness of the oil and reduce the power consumption of the pump body assembly during the oil pressing process.

[0150] As shown in the specific embodiment, Figure 18 the sliding hole 2011 has a set of oppositely arranged sliding hole 2011 wall surfaces, the shaft segment of the shaft 30 located in the sliding hole 2011 has a sliding fit surface 3011 matched with the sliding hole 2011 wall surface, and the shaft segment of the shaft 30 located in the sliding hole 2011 also has a set of opposite connecting surfaces 3016 for connecting the two sliding fit surfaces 3011. The shaft flow passage is a shaft flow hole 3012, and the shaft flow hole 3012 penetrates the two connecting surfaces 3016.

[0151] Specifically, the shaft 30 penetrates the sliding hole 2011 of the piston 20, which divides the sliding hole 2011 into two cavities. During the oil pressing process, the oil transfers between the two cavities. By arranging the shaft flow hole 3012 between the two connecting surfaces 3016, the smoothness of the oil flow is improved, the resistance of the oil to the shaft 30 and the piston 20 is reduced, and the power consumption of the pump body assembly during the oil pressing process is reduced.

[0152] It should be noted that the sliding fit surface 3011 is a plane, so that the distance L1 between the two sliding fit surfaces 3011 is greater than the diameter of the shaft flow hole 3012 by 2mm. The sliding fit surface 3011 slides relative to the sliding hole 2011 wall surface, and the plane design reduces friction. At the same time, the distance L1 between the two sliding fit surfaces 3011 is greater than the diameter of the shaft flow hole 3012 by 2mm, so as to ensure the strength of the shaft 30 and avoid the problem that the diameter of the shaft flow hole 3012 is too large, causing damage and breakage of the shaft 30 during operation.

[0153] Further, the diameter of the shaft flow hole 3012 is greater than or equal to 1mm. When the diameter of the shaft flow hole 3012 is less than 1mm, the effect of reducing the pump body assembly cannot be achieved. In order to improve the smoothness of the oil flow, the diameter of the flow hole needs to be greater than or equal to 1mm.

[0154] As shown in the specific embodiment,Figure 16 and Figure 18 As shown in the figure, the rotating shaft 30 comprises a long shaft section 3014 and a short shaft section 3015 connected in sequence, the length of the long shaft section 3014 is greater than the length of the short shaft section 3015, and the long shaft section 3014 is provided with a sliding fit surface 3011, and at least a part of the long shaft section 3014 extends into the sliding hole 2011.

[0155] Specifically, the sliding fit surface 3011 on the long shaft section 3014 slides with the hole wall surface of the sliding hole 2011 inside the piston 20, and the rotating shaft flow passage provided on the long shaft section 3014 realizes the reduction of the power consumption of the rotating shaft 30 and the piston 20 in the oil compression process.

[0156] As shown in the figure, Figure 16 , Figure 18 and Figure 19 The diameter of the shaft section inside the sliding hole 2011 is greater than the diameter of the short shaft section 3015. The interface between the end surface of the shaft section and the short shaft section 3015 forms a stepped shape, and the interface between the end surface of the shaft section and the short shaft section 3015 forms a support surface.

[0157] The pump body assembly in the application further comprises a cylinder sleeve 40, the cylinder 10 is rotatably arranged in the cylinder sleeve 40, the cylinder 10 is provided with a piston hole 106 along the radial direction thereof, the piston 20 is slidably arranged in the piston hole 106, the rotating shaft 30 penetrates the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole 106, and the cylinder 10 rotates to drive the piston 20 to rotate.

[0158] Specifically, in the process that the rotating shaft 30 drives the piston 20 to reciprocate along the extension direction of the piston hole 106, the piston 20 extrudes the oil, so as to realize the oil compression process of the pump body assembly, the oil is transferred inside the two cavities formed by the rotating shaft 30, the piston 20 and the cylinder 10, and the rotating shaft flow passage provided on the shaft section of the rotating shaft 30 reduces the obstruction of the oil transfer by the rotating shaft 30 in the oil flow process, and reduces the power consumption in the oil compression process of the pump body assembly.

[0159] From the above description, it can be seen that the above-mentioned embodiments of the application achieve the following technical effects:

[0160] By providing the flow passage on the shaft section of the rotating shaft 30 inside the sliding hole 2011 of the piston 20, the smoothness of the oil flow is enhanced, and the power consumption of the pump body assembly is reduced. At present, in the process that the rotating shaft 30 of the pump body assembly slides relative to the piston 20 in the operation of the rotating cylinder compressor, the area of the rotating shaft 30 inside the piston 20 hinders the flow of the oil, which causes the oil to hinder the movement of the piston 20 and the rotating shaft 30, and increases the power consumption of the pump body assembly.

[0161] Specifically, the rotating shaft 30 passes through the sliding hole 2011 on the piston 20, and divides the piston 20 into two cavities. During the movement of the pump body assembly, the piston 20 reciprocates relative to the rotating shaft 30, and the two cavities are periodically increased and decreased to realize the process of pressing oil. The shaft section of the rotating shaft 30 inside the sliding hole 2011 of the piston 20 can press the oil, so that the oil is transferred in the two cavities. By arranging the rotating shaft flow channel on the shaft section of the rotating shaft 30 inside the sliding hole 2011, the resistance of the rotating shaft 30 to the oil is reduced, and the power consumption of the piston 20 and the rotating shaft 30 during the oil pressing process is reduced, so as to reduce the power consumption of the pump body assembly.

[0162] To solve the problem of hindering the flow of oil in the rotating cylinder compressor in the prior art, the flange structure can be optimized to reduce the hindering of the piston 20 by the flange structure, so as to increase the smoothness of the oil flow and reduce the power consumption of the pump body assembly.

[0163] Specifically, as shown in Figures 20 to 29 The pump body assembly comprises a cylinder 10 and a flange structure. The cylinder 10 is rotatably arranged. The flange structure is located on one side of the cylinder 10 and has a positioning boss 6001 extending into the cylinder 10. The positioning boss 6001 is provided with a clearance avoiding recess 6002.

[0164] From the above description, it can be seen that in the above embodiment of the present application, the clearance avoiding recess 6002 is arranged on the positioning boss 6001 to reduce the hindering of the flange structure to the flow path and reduce the power consumption of the compressor. The flange structure of the existing pump body seriously blocks the flow path inside the cylinder 10 and the piston 20 near the flange structure, so that the refrigeration oil cannot be smoothly transferred inside the flow path, which increases the resistance of the rotating shaft 30 during rotation and increases the power consumption of the compressor. Specifically, when the flange structure is a lower flange 60, the flow path near the lower part of the flow path is easily blocked.

[0165] Specifically, the positioning boss 6001 of the flange structure extends into the cylinder 10, and the clearance avoiding recess 6002 is arranged on the positioning boss 6001 to reduce the hindering of the positioning boss 6001 to the flow path inside the cylinder 10. During the rotation of the cylinder 10, the oil inside the cylinder 10 flows back and forth inside the cylinder 10 through the flow path. When the oil flows to the positioning boss 6001, the oil can flow along the clearance avoiding recess 6002, which increases the flow volume and reduces the power consumption of the compressor during operation. At the same time, the noise and vibration of the compressor are reduced.

[0166] As shown in Figures 23 to 29As shown, the positioning boss 6001 is arranged concentrically with the center of the flange structure. The positioning boss 6001 is integrally formed on the flange structure and partially extends into the cylinder 10 to position the cylinder 10 and avoid tilting of the cylinder 10 during rotation. Meanwhile, the flange structure has a bearing capacity, and when the positioning boss 6001 is arranged concentrically with the flange structure, the eccentric force between the positioning boss 6001 and the flange structure is reduced, the stability of the flange structure and the positioning boss 6001 is increased, the stability of the pump body assembly in operation is improved, and the service life of the flange structure and the positioning boss 6001 is also improved.

[0167] As shown in the drawings, Figures 23 to 29 The flange structure also has a flange hole 6003 penetrating the positioning boss 6001, and the flange hole 6003 is arranged eccentrically with the center of the flange structure. The pump body assembly also includes a rotating shaft 30 penetrating the cylinder 10 and the flange hole 6003.

[0168] Specifically, the rotating shaft 30 penetrates the piston 20 and the cylinder 10 and is inserted into the flange hole 6003. At this time, the flange hole 6003 is arranged eccentrically with the positioning boss 6001. The positioning boss 6001 has a bearing function for the rotating shaft 30. Therefore, the eccentrically arranged flange hole 6003 can effectively reduce the concentrated stress between the positioning boss 6001 and the flange structure, which is conducive to improving the service life of the flange structure. At the same time, it is convenient to open the clearance recess 6002 on the positioning boss 6001. The clearance recess 6002 increases the flow path of the oil, reduces the resistance of the oil to the rotating shaft 30, and reduces the power consumption of the pump body assembly.

[0169] As shown in the drawings, Figures 23 to 29 The positioning boss 6001 has a stepped structure including a first segment 6004 and a second segment 6005. The first segment 6004 is away from the center of the cylinder 10 relative to the second segment 6005. The outer peripheral surface of the first segment 6004 is matched with the inner wall surface of the cylinder 10. The surface of the second segment 6005 towards the center of the cylinder 10 serves as a support surface to support the rotating shaft 30 of the pump body assembly. The flange hole 6003 penetrates the first segment 6004 and the second segment 6005.

[0170] Specifically, the second segment 6005 and the first segment 6004 cooperate to form a stepped structure. The outer peripheral surface of the first segment 6004 is matched with the inside of the cylinder 10 and does not affect the rotation of the cylinder 10. The end surface of the second segment 6005 towards the center of the cylinder 10 supports the rotating shaft 30. The flange hole 6003 is arranged concentrically with the second segment 6005. The first segment 6004 and the second segment 6005 cooperate to form the clearance recess 6002 to increase the flow path inside the cylinder 10, reduce the rotation resistance of the rotating shaft 30, and reduce the power consumption of the pump body assembly.

[0171] It should be noted that, as shown in the drawings, Figures 23 to 29In the specific embodiment shown, both the first segment 6004 and the second segment 6005 are circular bosses. However, in actual manufacturing, both the first segment 6004 and the second segment 6005 do not necessarily have to be circular bosses simultaneously. Only one of the first segment 6004 and the second segment 6005 may be a circular boss, or neither may be a circular boss. The first segment 6004 should be able to mate with the inner surface of the cylinder 10 without obstruction, and the second segment 6005 should be able to support the rotating shaft 30. Since there are many possible shapes and combinations of the first segment 6004 and the second segment 6005, further specific embodiments are not provided here.

[0172] It should be noted that, depending on the different positions of the second segment 6005 relative to the first segment 6004, various shapes of clearance recesses 6002 can be formed. Since there are many combinations of shapes, they will not be listed one by one. The following describes different implementation methods based on the different shapes of the clearance recesses 6002.

[0173] like Figures 23 to 27 In the specific embodiment shown, both the first segment 6004 and the second segment 6005 are circular bosses. The orthographic projection of the second segment 6005 onto the first segment 6004 does not completely coincide with the outer periphery of the first segment 6004. A clearance recess 6002 is formed at the step surface between the outer periphery of the second segment 6005 and the first segment 6004. At this time, the clearance recess 6002 is a crescent-shaped recess and the outer circle of the crescent shape is concentric with the flange structure.

[0174] Specifically, both the first segment 6004 and the second segment 6005 are circular bosses. Since a recessed area 6002 is formed at the step surface between the outer periphery of the second segment 6005 and the first segment 6004, when the outer periphery of the second segment 6005 partially overlaps with the outer periphery of the first segment 6004, a crescent-shaped recessed area 6002 is formed at the step surface between the outer periphery of the second segment 6005 and the first segment 6004. The crescent-shaped recessed area 6002 increases the flow path of the oil, reduces the obstruction of the oil to the rotating shaft 30, and reduces the power consumption of the pump body assembly.

[0175] like Figure 28In the specific embodiment shown in FIG. 29, the first section 6004 and the second section 6005 are both circular bosses, the orthographic projection of the second section 6005 on the first section 6004 does not completely coincide with the outer periphery of the first section 6004, and the first section 6004 is further provided with a support rib 6006 extending toward the center of the cylinder 10, the height of the support rib 6006 is not higher than that of the second section 6005, at least one side surface of the support rib 6006 is flush with the outer periphery of the first section 6004, and the support rib 6006 is spaced apart from the second section 6005, forming an avoidance recess 6002 therebetween, which is in the shape of a crescent moon.

[0176] Specifically, the support rib 6006 is arranged on the first section 6004, and the support rib 6006, the first section 6004 and the second section 6005 cooperatively form the avoidance recess 6002 in the shape of an irregularity, which can expand the flow path inside the cylinder 10, reduce the resistance between the rotating shaft 30 and the oil, and reduce the power consumption of the pump body assembly. Meanwhile, the addition of the support rib 6006 can strengthen the stability between the positioning boss 6001 and the cylinder 10.

[0177] It should be noted that the area of the irregular shape is not greater than the end area of the first section 6004 toward the center of the cylinder 10.

[0178] In the specific embodiment shown in FIG. 29, the first section 6004 and the second section 6005 are both circular bosses, the orthographic projection of the second section 6005 on the first section 6004 does not completely coincide with the outer periphery of the first section 6004, and the first section 6004 is further provided with a support rib 6006 extending toward the center of the cylinder 10, the height of the support rib 6006 is not higher than that of the second section 6005, at least one side surface of the support rib 6006 is flush with the outer periphery of the first section 6004, and the support rib 6006 is spaced apart from the second section 6005, forming an avoidance recess 6002 therebetween, which is in the shape of a crescent moon.

[0179] Specifically, the support rib 6006 is arranged on the first section 6004, and the support rib 6006, the first section 6004 and the second section 6005 cooperatively form the avoidance recess 6002 in the shape of an irregularity, which can expand the flow path inside the cylinder 10, reduce the resistance between the rotating shaft 30 and the oil, and reduce the power consumption of the pump body assembly. Meanwhile, the addition of the support rib 6006 can strengthen the stability between the positioning boss 6001 and the cylinder 10.

[0180] In an embodiment not shown in the drawings, the first section 6004 and the second section 6005 are both circular bosses, and the orthographic projection of the second section 6005 on the first section 6004 does not completely coincide with the outer periphery of the first section 6004, so that the outer periphery of the second section 6005 and the first section 6004 form a stepped surface at the location of the clearance recess 6002, and the clearance recess 6002 is a ring-shaped recess.

[0181] Specifically, the outer periphery of the first section 6004 and the second section 6005 do not coincide, and the outer periphery of the second section 6005 and the first section 6004 form a stepped surface at the location of the clearance recess 6002, and the clearance recess 6002 is a ring-shaped recess, which can expand the flow path, reduce the obstruction of the flange structure to the flow path, and reduce the power consumption of the pump body assembly.

[0182] It should be noted that when the clearance recess 6002 is a ring-shaped recess, the inner ring surface and the outer ring surface of the ring-shaped recess can be concentric or eccentric. When the inner ring surface and the outer ring surface are concentric or eccentric, the same technical effect can be achieved, i.e., the ring-shaped clearance recess 6002 can expand the flow path and reduce the obstruction of the oil to the shaft 30. Therefore, the concentric or eccentric arrangement of the inner ring surface and the outer ring surface will not be introduced separately here.

[0183] As shown in FIG. 6, the depth h of the clearance recess 6002 is 4%-25% of the diameter of the first section 6004. Figure 25 Specifically, the depth of the clearance recess 6002 is limited by the diameter of the first section 6004 to avoid affecting the stability of the positioning boss 6001 and the flange structure in cooperation with the shaft 30 and the cylinder 10 when the depth of the clearance recess 6002 is too large. When the depth h of the clearance recess 6002 is 4%-25% of the diameter of the first section 6004, the clearance recess 6002 can increase the flow path of the oil, reduce the rotational resistance of the shaft 30, reduce power consumption, and not affect the stability of the pump body assembly in operation.

[0184] As shown in FIG. 6, the wall thickness d of the second section 6005 is 10%-80% of the maximum wall thickness D of the first section 6004. Figure 25 Since the second section 6005 is eccentric to the flange structure, the first section 6004 is concentric to the flange structure, and thus the second section 6005 is eccentric to the first section 6004. It should be noted that when the wall thickness of the second section 6005 is 10%-80% of the maximum wall thickness of the first section 6004, the eccentricity ratio of the second section 6005 relative to the first section 6004 is fixed and does not change with the ratio of the wall thickness of the first section 6004 to the maximum wall thickness of the second section 6005, and at the same time, the wall thickness of the second section 6005 is fixed, and the wall thickness of the first section 6004 can be changed, so as to achieve the effect of expanding the flow path by arranging the clearance recess 6002 on the stepped surface between the second section 6005 and the first section 6004, thereby reducing the power consumption of the pump body.

[0185] Further, the wall thickness d of the second section 6005 is 20%-40% of the maximum wall thickness D of the first section 6004. Specifically, by further limiting the wall thickness d of the second section 6005 and the maximum wall thickness D of the first section 6004, it is known that when the wall thickness d of the second section 6005 is 20%-40% of the maximum wall thickness D of the first section 6004, the flow effect of the oil liquid in the flow path is best, the resistance of the shaft 30 to the oil liquid is smallest, and the power consumption of the pump body assembly is smallest.

[0186] As shown in Figure 25 The depth h of the clearance recess 6002 is 5%-60% of the height H of the flange structure. Specifically, when the depth h of the clearance recess 6002 is less than 5%-60% of the height H of the flange structure, the depth of the clearance recess 6002 on the positioning boss 6001 is too small at this time, the first section 6004 of the positioning boss 6001 hinders the flow of the oil liquid inside the flow path, and the oil liquid hinders the rotation of the shaft 30, resulting in an increase in the power consumption of the pump body assembly. When the depth h of the clearance recess 6002 is greater than 5%-60% of the height H of the flange structure, the depth of the clearance recess 6002 on the positioning boss 6001 is too large, resulting in a decrease in the strength of the positioning boss 6001, a decrease in stability during operation of the pump body assembly, and a problem of easy deviation of the shaft 30 and the cylinder 10.

[0187] Further, the depth h of the clearance recess 6002 is 15%-35% of the height H of the flange structure. Specifically, the depth h of the clearance recess 6002 being 15%-35% of the height H of the flange structure is a further limitation of the depth h of the clearance recess 6002 being 5%-60% of the height H of the flange structure. When the depth h of the clearance recess 6002 is 15%-35% of the height H of the flange structure, the clearance recess 6002 can effectively expand the flow path of the oil liquid, reducing the resistance of the oil liquid to the shaft 30 during rotation of the shaft 30, and reducing the power consumption of the pump body assembly.

[0188] The flange structure in the present application includes a lower flange 60, and the shaft 30 has a long shaft section and a short shaft section, the diameter of the long shaft section being greater than the diameter of the short shaft section to form a shaft support surface at the junction of the long shaft section and the short shaft section, the shaft support surface being supported at the positioning boss 6001, and the short shaft section being arranged in the lower flange 60.

[0189] Specifically, the second section 6005 of the positioning boss 6001 on the lower flange 60 supports the support surface of the shaft 30, and the clearance recess 6002 on the lower flange 60 expands the flow path of the oil liquid inside the cylinder 10 during rotation of the shaft 30, reducing the resistance of the oil liquid to the shaft 30 and reducing power consumption.

[0190] The pump body assembly in the application further comprises a cylinder sleeve, the cylinder sleeve has a volume cavity, the cylinder 10 is rotatably arranged in the volume cavity, the cylinder 10 is provided with a piston hole 106 along the radial direction thereof, the piston 20 is slidably arranged in the piston hole 106, the rotating shaft 30 penetrates through the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole 106, the cylinder 10 rotates to drive the piston 20 to rotate, and the flange structure is located at the end of the cylinder sleeve in the axial direction, and at least a part of the rotating shaft 30 penetrates through the flange structure.

[0191] Specifically, the cylinder 10 rotates synchronously with the rotating shaft 30 in the cylinder sleeve, and the piston 20 reciprocates in the piston hole 106. The relative movement between the piston 20 and the rotating shaft 30 realizes the transfer of the oil in the two flow paths formed by the cooperation of the cylinder 10, the piston 20 and the rotating shaft 30, and the two flow paths periodically increase and decrease with the reciprocation of the piston 20 to drive the transfer of the oil. The avoidance recess 6002 arranged on the positioning boss 6001 of the lower flange 60 can reduce the obstruction of the positioning boss 6001 to the oil flow in the flow path, reduce the resistance between the rotating shaft 30 and the oil, and reduce the power consumption of the pump body assembly.

[0192] From the above description, it can be seen that the above-mentioned embodiments of the application achieve the following technical effects:

[0193] By arranging the avoidance recess 6002 on the positioning boss 6001, the obstruction of the flange structure to the flow path is reduced, and the power consumption of the compressor is reduced. The flange structure of the existing pump body seriously blocks the lower part of the flow path inside the cylinder 10 and the piston 20, so that the refrigeration oil cannot be smoothly transferred inside the flow path, resulting in increased resistance during the rotation of the rotating shaft 30 and increased power consumption of the compressor.

[0194] Specifically, the positioning boss 6001 of the flange structure extends into the cylinder 10, and the avoidance recess 6002 is arranged on the positioning boss 6001 to reduce the obstruction of the positioning boss 6001 to the flow path inside the cylinder 10. During the rotation of the cylinder 10, the oil inside the cylinder 10 flows back and forth inside the cylinder 10 through the flow path, and when the oil flows to the positioning boss 6001, the oil can flow along the avoidance recess 6002, thereby increasing the flow volume to reduce the operating power consumption of the compressor, and at the same time, reducing the noise and vibration of the compressor.

[0195] Obviously, the above-described embodiments are only part of the embodiments of the application, not all the embodiments. Based on the embodiments in the application, all other embodiments obtained by those skilled in the art without creative labor should belong to the protection scope of the application.

[0196] It is to be understood that the terminology used herein is for the purpose of describing specific embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, devices, components and / or combinations thereof, but do not preclude the presence or addition of one or more other features, steps, operations, devices, components and / or combinations thereof.

[0197] The preferred embodiments of the application described herein merely illustrate specific applications of the application and do not limit the scope of the application, which is defined by the claims. Any modification of the application in accordance with the principles of the application and the appended claims is intended to be included within the scope of the application.

[0198] It is apparent that the above-described embodiments are only some of the embodiments of the present application, and thus many modifications and variations of the embodiments are possible in light of the above teachings. It is therefore to be understood that within the scope of the application, many modifications, equivalent replacements, improvements and the like can be made thereto without departing from the spirit and scope of the application.

[0199] It is to be understood that the terminology used herein is for the purpose of describing specific embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, devices, components and / or combinations thereof, but do not preclude the presence or addition of one or more other features, steps, operations, devices, components and / or combinations thereof.

[0200] It should be noted that the terms "first", "second", and the like, used in the description and the claims of this application are intended to distinguish between similar objects, but are not intended to limit the scope of the application to the specific examples described. It is understood that the use of such terms as "first", "second", and the like, are interchangeable under appropriate circumstances to designate a similar object.

Claims

1. A pump body assembly, characterized in that, include: Rotating shaft (30); A piston (20) has a sliding hole (2011), at least a portion of the rotating shaft (30) passes through the sliding hole (2011), and during the rotation of the piston (20) with the rotating shaft (30), the sliding hole (2011) is in sliding engagement with the rotating shaft (30), and the piston (20) has a piston communication channel communicating with the sliding hole (2011). In the axial direction of the rotating shaft (30), the piston (20)... A piston connecting groove (2021) is provided on the end face. The piston connecting groove (2021) extends along the sliding direction of the piston (20) and forms the piston connecting channel. A flexible groove (2023) is also provided in the sliding hole (2011) of the piston (20). The flexible groove (2023) extends axially along the rotating shaft (30), and the end of the flexible groove (2023) communicates with the piston connecting groove (2021).

2. The pump body assembly according to claim 1, characterized in that, The piston communication channel is multiple, and the multiple piston communication channels are arranged on the end face of the piston (20) located in the axial direction of the rotating shaft (30).

3. The pump body assembly according to claim 2, characterized in that, The number of piston connecting channels is less than 4.

4. The pump body assembly according to claim 1, characterized in that, On the end face of the piston (20) at the same end, at least one piston communication groove (2021) is provided at each of the two oppositely arranged edges of the sliding hole (2011).

5. The pump body assembly according to claim 1, characterized in that, Along the axial direction of the rotating shaft (30), the piston (20) is provided with piston communication grooves (2021) on both the top and bottom end faces.

6. The pump body assembly according to claim 1, characterized in that, With the piston connecting groove (2021) as the boundary, the end face on the side where the piston connecting groove (2021) is located includes a first surface P1 and a second surface P2, wherein the first surface P1 is located in the region between the piston connecting groove (2021) and the edge of the sliding hole (2011) on the same side, and the second surface P2 is located in the region between the piston connecting groove (2021) and the outer edge of the piston (20).

7. The pump body assembly according to claim 6, characterized in that, The height difference between the first surface P1 and the second surface P2 is 0.1 mm.

8. The pump body assembly according to claim 1, characterized in that, The distance L2 between the piston connecting groove (2021) and the outer edge of the end face of the piston (20) on the same side is greater than or equal to 2 mm.

9. The pump body assembly according to claim 1, characterized in that, The flexible groove (2023) is located at the end of the piston connecting groove (2021).

10. The pump body assembly according to claim 9, characterized in that, There are multiple flexible grooves (2023), and one flexible groove (2023) is provided at each end of the same piston connecting groove (2021) so that a sliding boss (2022) protruding from the hole wall surface of the sliding hole (2011) is formed inside the sliding hole (2011).

11. The pump body assembly according to claim 10, characterized in that, The sliding boss (2022) has a sliding surface (2024) on the side facing the middle of the sliding hole (2011).

12. The pump body assembly according to claim 11, characterized in that, The sliding surface (2024) is a plane.

13. The pump body assembly according to claim 1, characterized in that, Along the axial direction of the rotating shaft (30), the end of the flexible groove (2023) passes through the two end faces of the piston (20).

14. The pump body assembly according to claim 1, characterized in that, The length H3 of the flexible groove (2023) is greater than or equal to 2 mm and less than or equal to 7 mm.

15. The pump body assembly according to claim 1, characterized in that, The angle A between the surface of the flexible groove (2023) near the middle of the sliding hole (2011) and the hole wall surface of the flexible groove (2023) on the side where it is located in the sliding hole (2011) is 10 degrees to 30 degrees.

16. The pump body assembly according to claim 1, characterized in that, The flexible groove (2023) includes a first groove surface and a second groove surface connected in sequence along the direction near the middle of the sliding hole (2011). The first groove surface has a first transition fillet ∠1 between itself and the hole wall of the sliding hole (2011), the second groove surface has a second transition fillet ∠2 between itself and the first groove surface, and the second groove surface has a third transition fillet ∠3 at the edge of the second groove surface away from the first groove surface.

17. The pump body assembly according to claim 16, characterized in that, The first transition fillet ∠1 is 0.3 degrees to 1 degree; and / or The second transition fillet ∠2 is 0.3 degrees to 1 degree; and / or The third transition fillet ∠3 is between 0.5 degrees and 3 degrees.

18. The pump body assembly according to claim 4, characterized in that, The width H1 of the piston connecting groove (2021) is 1%-12% of the width W1 of the piston (20).

19. The pump body assembly according to claim 4, characterized in that, The depth H2 of the piston connecting groove (2021) is 3%-50% of the width W1 of the piston (20).

20. The pump body assembly according to any one of claims 1 to 17, characterized in that, The pump assembly also includes: Cylinder liner (40); A cylinder (10) is rotatably disposed within a cylinder liner (40). A piston hole (106) is provided on the cylinder (10) along its radial direction. A piston (20) is slidably disposed within the piston hole (106). A rotating shaft (30) passes through the piston (20) and drives the piston (20) to reciprocate along the extension direction of the piston hole (106). The cylinder (10) rotates to drive the piston (20) to rotate.

21. A fluid machine, characterized in that, Includes the pump body assembly according to any one of claims 1 to 20.

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