Pump body assembly, compressor and refrigeration equipment

Abstract

The invention relates to the field of electric appliances, and provides a pump body assembly, a compressor and refrigeration equipment. The pump body assembly comprises a roller, a sliding piece and a flange. The roller is provided with a first connecting part, the sliding piece is hinged to the first connecting part, the end face of the flange is in sliding fit with the end face of the roller, and an air outlet adjacent to the first connecting part is formed in the flange. A chamfer structure and a non-chamfer structure are arranged at the joint of the inner circumferential surface and the end surface of the roller, and the non-chamfer structure is arranged adjacent to the first connecting part; and the non-chamfering structure is used for blocking a communication gap between the air outlet hole and the inner hole of the roller. On the premise that the lubricating performance is not sacrificed, local sealing reinforcement is achieved, and the technical obstacle that the sealing performance and the lubricating performance are mutually restricted in the prior art is overcome.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of electrical appliances, in particular to a pump body assembly, a compressor and a refrigeration device. BACKGROUND

[0002] In the prior art, a rotary compressor generally comprises a cylinder, a roller, a vane, a crankshaft and an end flange. The roller is sleeved on the eccentric portion of the crankshaft and performs eccentric rotation in the cylinder. The vane is embedded in the vane groove of the cylinder at one end and is in contact with the outer peripheral surface of the roller at the other end, thereby separating the inner cavity of the cylinder into a suction chamber and a compression chamber. The compressed high-pressure gas is discharged through the gas outlet hole provided on the flange. In order to reduce the friction loss between the end surface of the roller and the end surface of the flange, a chamfer is usually provided at the joint between the inner peripheral surface of the roller and the end surface thereof in the prior art, so as to form an oil storage space and improve the lubrication condition.

[0003] However, in the above structure, the chamfer with an excessively large size may form a through gap connecting the gas outlet hole and the inner hole of the roller. When the pressure in the compression chamber rises and the gas is discharged through the gas outlet hole, the high-pressure gas may leak to the inner hole of the roller through the gap, and then flow into the suction side or the crankshaft cavity, thereby causing the volumetric efficiency to decrease and the compression performance to deteriorate.

[0004] In order to avoid leakage, some existing designs choose to reduce or cancel the chamfer size, but this leads to the deterioration of the lubrication condition, the increase of the friction power and the decrease of the energy efficiency. Therefore, in the prior art, there is an irreconcilable contradiction between the sealing performance and the lubrication performance: if good lubrication is pursued, the sealing is sacrificed; if the sealing is ensured, the friction is aggravated. SUMMARY

[0005] The present application provides a pump body assembly, a compressor and a refrigeration device to solve the defects in the prior art and achieve the following effects: local sealing is strengthened without sacrificing the lubrication performance, and the technical obstacle that the sealing performance and the lubrication performance are mutually restricted in the prior art is overcome.

[0006] In a first aspect, the present application provides a pump body assembly, comprising: a roller, a vane and a flange; The roller is provided with a first connecting portion, the vane is hinged to the first connecting portion, the end surface of the flange is in sliding cooperation with the end surface of the roller, and the flange is provided with a gas outlet hole adjacent to the first connecting portion; The joint between the inner peripheral surface of the roller and the end surface thereof is provided with a chamfer structure and a non-chamfer structure, and the non-chamfer structure is provided adjacent to the first connecting portion; the non-chamfer structure is used to block the communication gap between the gas outlet hole and the inner hole of the roller.

[0007] According to some embodiments of the present invention, a sealing surface is formed on the side of the non-beveled structure facing the vent, and the sealing surface is flush with the end face of the roller; during the movement of the roller, the wall of the vent never extends beyond the edge of the sealing surface in the direction toward the inner hole of the roller.

[0008] According to some embodiments of the present invention, the non-beveled structure is provided not beyond the inner circumferential surface of the roller in the direction toward the inner bore of the roller.

[0009] According to some embodiments of the present invention, the angle formed by the lines connecting the two ends of the non-beveled structure to the center of the roller along the circumferential direction of the roller is α, and the value range is 0 < α ≤ 30°.

[0010] According to some embodiments of the present invention, on a projection plane perpendicular to the central axis of the roller, the radial width of the chamfer structure is d, and its value ranges from d≥2mm; and / or, the vertical distance between the outer periphery of the chamfer structure and the outer periphery of the roller is c, and its value ranges from c≥1mm.

[0011] According to some embodiments of the present invention, an eccentric portion is further included, the eccentric portion is installed in the inner hole of the roller, and the inner circumferential surface of the roller is slidably connected to the outer circumferential surface of the eccentric portion. A groove is provided on the inner circumferential surface of the roller adjacent to the first connecting portion, the groove extending circumferentially and penetrating the upper and lower end surfaces of the roller.

[0012] According to some embodiments of the present invention, the central angle corresponding to the groove is β, and its value ranges from 0 to 180°; and / or, the central angle corresponding to the portion of the groove adjacent to the edge of the first connecting portion and the first connecting portion is γ, and its value ranges from 0 to γ ​​to 180°.

[0013] According to some embodiments of the present invention, the inner diameter of the roller is R1, the radius of curvature of the groove is R2, and R1 and R2 satisfy 0.2mm≤R2-R1≤1mm.

[0014] Secondly, the present invention provides a compressor, comprising: Pump body assembly as described in the first aspect of the present invention.

[0015] Thirdly, the present invention provides a refrigeration device, comprising: The compressor as described in the second aspect of the present invention.

[0016] In summary, the present invention effectively solves the problem of high-pressure gas leakage caused by full-circumference chamfering in the prior art by partially setting a non-chamfered structure at the joint between the inner circumferential surface and the end face of the roller and arranging it in the area adjacent to the first connection part (i.e. the position corresponding to the flange vent).

[0017] Specifically, the non-chamfered structure maintains the geometric continuity between the inner circumferential surface and the end face of the roller in the circumferential direction of the outlet, physically blocking the communication gap between the outlet and the inner bore of the roller. This prevents high-pressure gas during compression from entering the inner bore of the roller through the chamfered groove, thereby significantly improving the volumetric efficiency and exhaust sealing reliability of the compressor. At the same time, retaining the chamfered structure in the non-outlet area still creates an oil storage space, ensuring lubrication conditions between the roller end face and the flange end face, and avoiding an increase in frictional power caused by eliminating the chamfer.

[0018] Therefore, this invention achieves enhanced local sealing without sacrificing lubrication performance, overcoming the technical obstacle of mutual constraint between sealing and lubrication in the prior art, and improving the overall energy efficiency and operational stability of the compressor. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0020] Figure 1 This is one of the partial structural schematic diagrams of the pump body assembly provided by the present invention.

[0021] Figure 2 This is the second partial structural schematic diagram of the pump body assembly provided by the present invention.

[0022] Figure 3 This is a partial schematic diagram of a pump assembly provided in another embodiment of the present invention.

[0023] Figure 4 This is the third partial structural schematic diagram of the pump body assembly provided by the present invention.

[0024] Figure label: 1. Roller; 11. First connecting part; 12. Inner hole; 2. Sliding piece; 31. Chamfered structure; 32. Non-chamfered structure; 33. Groove. Detailed Implementation

[0025] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0026] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and 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. Therefore, they should not be construed as limitations on the embodiments of the present invention. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0027] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0028] In embodiments of the present invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0029] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0030] The following description, with reference to the accompanying drawings, illustrates a pump assembly, a compressor, and a refrigeration device according to the present invention. It should be noted that the compressor of the present invention is a rotary compressor.

[0031] The basic structure and working principle of a rotary compressor are described below: A rotary compressor mainly includes a housing, motor, crankshaft, and pump assembly. The pump assembly includes a cylinder, rollers, vanes, main / auxiliary bearings, and flanges. The motor drives the crankshaft to rotate. An eccentric part is provided on the crankshaft, which inserts into the inner hole of the roller, causing the roller to rotate eccentrically within the cylinder. The inner wall of the cylinder has vane grooves, along which the vanes can slide back and forth, with one end always in contact with the outer circumference of the roller, thus dividing the cylinder cavity into an intake chamber and a compression chamber. As the rollers rotate eccentrically with the crankshaft, the volume of the intake chamber increases, and low-pressure refrigerant gas enters through the inlet. Subsequently, the volume of the compression chamber gradually decreases, and the gas is compressed to high pressure before being discharged through exhaust ports located on the flange or bearings, completing the compression cycle.

[0032] During the aforementioned operation, sliding friction exists between the roller end face and the main / secondary bearing end face. Simultaneously, the inner bore of the roller and the eccentric portion of the crankshaft also bear significant loads, especially during the exhaust phase, where the pressure in the contact area is highest, easily leading to wear and power loss. Therefore, effectively improving lubrication conditions and reducing frictional power while ensuring sealing performance has become a key technical issue for improving compressor energy efficiency.

[0033] To address the contradiction between sealing performance and lubrication caused by the limited chamfering of the inner diameter of rollers in existing technologies, this invention proposes a novel roller structure design. By setting a non-full-circumference chamfer on the inner circumferential surface of roller 1, the sealing distance on the exhaust side is maintained while a chamfer is formed in the non-exhaust area, significantly improving the lubrication effect, thereby reducing the compressor's operating power and improving overall energy efficiency. The pump assembly, compressor, and refrigeration equipment of this invention will be described in detail below.

[0034] like Figures 1 to 4As shown, the pump body assembly according to a first aspect embodiment of the present invention includes a roller 1, a vane 2, and a flange.

[0035] The roller 1 is provided with a first connecting part 11, the slide 2 is hinged to the first connecting part 11, the end face of the flange is slidably engaged with the end face of the roller 1, and the flange is provided with an air outlet near the first connecting part 11.

[0036] The inner circumferential surface of the roller 1 and its end face are provided with a chamfered structure 31 and a non-chamfered structure 32. The non-chamfered structure 32 is provided adjacent to the first connecting part 11. The non-chamfered structure 32 is used to block the communication gap between the air outlet and the inner hole 12 of the roller 1.

[0037] According to an embodiment of the present invention, the pump body assembly has the following general structure: The pump body assembly includes a roller 1, a vane 2, and a flange. The roller 1 is provided with a first connecting portion 11, and one end of the vane 2 is hinged to the first connecting portion 11, allowing the vane 2 to swing relative to the roller 1 to accommodate the eccentric rotational movement of the roller 1 within the cylinder. The flange is disposed on the axial end side of the roller 1, and its end face forms a sliding fit pair with the corresponding end face of the roller 1, constituting the axial sealing surface of the compression chamber. The flange is provided with an exhaust port, which is located adjacent to the first connecting portion 11, for discharging the compressed high-pressure gas to the outside of the compressor housing.

[0038] The inner circumferential surface of roller 1 and its end face are provided with a chamfered structure 31 and a non-chamfered structure 32 at the joint. The non-chamfered structure 32 is located in the area adjacent to the first connecting part 11, corresponding to the circumferential position of the vent on the flange; the remaining area is provided with the chamfered structure 31. The non-chamfered structure 32 retains the right angle transition or slight transition between the inner circumferential surface and the end face of roller 1, thereby forming a continuous sealing surface in the axial and radial directions, effectively sealing the communication gap between the vent and the inner hole 12 of roller 1, and preventing high-pressure exhaust from leaking from the vent through the inner hole 12 of roller 1 to the low-pressure area.

[0039] It should be explained that "chamfer structure 31" refers to the inclined transition area formed at the joint between the inner circumferential surface of the roller 1 and its axial end face after cutting, grinding or forming processes. Its cross-section is usually a straight inclined surface, a circular arc surface or a composite curved surface, used to form a depression or gentle slope at the edge of the inner hole 12 of the roller 1 to accommodate lubricating oil and improve lubrication conditions.

[0040] Accordingly, "non-beveled structure 32" refers to an area where the aforementioned bevel or curved transition is not provided at the junction of the inner circumferential surface and the end face of the roller 1, retaining the original right angle, acute angle, or only a slight transition. This structure maintains geometric continuity in the axial and radial directions, effectively blocking the leakage path of gas along the junction of the inner hole 12 of the roller 1 and the end face. It should be noted that "non-beveled structure 32" in this invention does not mean absolutely no surface treatment, but rather refers to an area without functional oil reservoir grooves 33 or significant bevel features; its main function is to maintain sealing integrity, not lubrication.

[0041] For example, the non-beveled structure 32 can be a partially planar preserved structure, that is, within a specific circumferential angle range, the original boundary shape between the end face and the inner hole wall is completely preserved without bevel processing, while the remaining areas are beveled.

[0042] It is understood that the core of this invention lies in the combined design of a chamfered structure 31 and a non-chamfered structure 32 at the junction of the inner circumferential surface and the end face of the roller 1. In related technologies, during the operation of a rotary compressor, the inner bore 12 of the roller 1 is fitted onto the eccentric portion of the crankshaft, and there is relative rotation between the two, bearing a large load. The chamfered structure 31 can form an annular groove 33 in non-critical sealing areas, which helps to store lubricating oil, establish a stable oil film between the end face of the roller 1 and the flange end face, and reduce sliding friction power. However, if a chamfer is also provided in the circumferential area corresponding to the air outlet, a leakage channel will be formed between the inner bore 12 of the roller 1 and the air outlet, causing high-pressure gas to enter the interior of the roller 1, reducing volumetric efficiency.

[0043] To avoid the technical defects existing in the aforementioned related technologies, the present invention provides a non-beveled structure 32 near the first connecting part 11 (i.e., the position corresponding to the vent hole) to maintain the geometric continuity between the inner circumferential surface and the end face of the roller 1 in this area, thereby blocking the gas leakage path and ensuring the reliability of the exhaust seal. This design effectively solves the technical contradiction between sealing and lubrication without sacrificing lubrication performance.

[0044] Furthermore, the specific working process of the compressor used in the pump body assembly of the present invention is as follows: When the compressor is running, the crankshaft drives the roller 1 to rotate eccentrically within the cylinder, and the sliding vane 2 swings with the roller 1, dividing the cylinder cavity into an intake chamber and a compression chamber. As the roller 1 rotates, the volume of the compression chamber gradually decreases, and the gas is compressed to a high-pressure state. When the compression chamber rotates to communicate with the outlet port on the flange, the high-pressure gas is discharged through the outlet port. During this process, the area of ​​the roller 1 adjacent to the outlet port (i.e., the part with the non-chamfered structure 32) is always in close contact with the flange end face, and there is no chamfered recess at the junction of its inner circumferential surface and the end face, thereby avoiding the formation of a communication gap between the outlet port and the inner hole 12 of the roller 1. At the same time, the chamfered structure 31 in other areas of the roller 1 continues to play an oil storage role, lubricating the sliding contact surface between the end face of the roller 1 and the flange, reducing friction loss. Thus, the non-chamfered structure 32 ensures the sealing performance during the exhaust stage, while the chamfered structure 31 optimizes the lubrication conditions, and the two work together to achieve efficient and stable operation of the compressor.

[0045] In summary, the present invention effectively solves the problem of high-pressure gas leakage caused by full-circumference chamfering in the prior art by partially setting a non-chamfered structure 32 at the junction of the inner circumferential surface and the end face of the roller 1 and arranging it in the area adjacent to the first connecting part 11 (i.e., the position corresponding to the flange vent).

[0046] Specifically, the non-chamfered structure 32 maintains the geometric continuity between the inner circumferential surface and the end face of the roller 1 in the circumferential position of the outlet, physically blocking the communication gap between the outlet and the inner hole 12 of the roller 1. This prevents high-pressure gas during the compression stage from entering the inner hole 12 of the roller 1 through the chamfered groove 33, thereby significantly improving the volumetric efficiency and exhaust sealing reliability of the compressor. At the same time, retaining the chamfered structure 31 in the non-outlet area still forms an oil storage space, ensuring the lubrication conditions between the end face of the roller 1 and the flange end face, and avoiding the increase in frictional power caused by the removal of the chamfer.

[0047] Therefore, this invention achieves enhanced local sealing without sacrificing lubrication performance, overcoming the technical obstacle of mutual constraint between sealing and lubrication in the prior art, and improving the overall energy efficiency and operational stability of the compressor.

[0048] like Figure 1 As shown, according to some embodiments of the present invention, a sealing surface is formed on the side of the non-beveled structure 32 facing the air outlet, and the sealing surface is flush with the end face of the roller 1; during the movement of the roller 1, the hole wall of the air outlet never exceeds the edge of the sealing surface in the direction facing the inner hole 12 of the roller 1.

[0049] It is understandable that the sealing surface is flush with the end face of roller 1, which allows the sealing surface and the vent port to fit tightly in the axial direction, thereby avoiding the risk of leakage due to axial gaps and ensuring that there is no exposed gap in the axial direction between the vent port and the inner cavity of roller 1; furthermore, the limitation of the vent port wall and the edge of the sealing surface can ensure that there is no exposed gap in the radial direction between the vent port and the inner cavity of roller 1.

[0050] It should be noted that during the entire eccentric rotation of roller 1 with the crankshaft, the position of the vent hole on the flange relative to roller 1 will change periodically. The statement that "the wall of the vent hole never extends beyond the edge of the sealing surface in the direction towards the inner hole 12 of roller 1" means that when viewed outward from the inner hole 12 of roller 1, the innermost edge of the vent hole wall, in the axial projection or radial extension direction, is always located outside or aligned with the edge of the sealing surface, and will not extend beyond the edge of the sealing surface into the area of ​​the inner hole 12 of roller 1.

[0051] In this way, the sealing surface can form a continuous and complete shielding boundary in the circumferential and axial directions, ensuring that there is no direct communication channel between the vent and the inner hole 12 of the roller 1, thereby preventing high-pressure exhaust from leaking into the inner hole 12 of the roller 1 through the gap between the edge of the vent and the inner circumferential surface of the roller 1.

[0052] In summary, the above embodiments enhance the stability of local sealing through precise spatial matching between the sealing surface and the outlet hole wall, effectively avoiding instantaneous leakage caused by structural misalignment or dynamic operation, and further improving the sealing reliability and volumetric efficiency of the compressor.

[0053] like Figure 1 As shown, according to some embodiments of the present invention, the non-beveled structure 32 is provided not beyond the inner circumferential surface of the roller 1 in the direction toward the inner hole 12 of the roller 1. That is, the innermost boundary of the non-beveled structure 32 is flush with or located outside the inner circumferential surface of the roller 1, and will not protrude inward and intrude into the flow or mating area of ​​the inner hole 12 of the roller 1.

[0054] The above design ensures that the inner circumferential surface of roller 1, as the bearing surface that mates with the eccentric part of the crankshaft, maintains its integrity and geometric consistency. The non-beveled structure 32 exists only as a local sealing area at the junction of the end face and the inner circumferential surface, without changing the effective inner diameter of the inner hole 12 of roller 1, nor interfering with the assembly and relative movement between roller 1 and the eccentric part of the crankshaft.

[0055] Thus, based on the above structure, the pump body assembly of the present invention can achieve the function of partial sealing while avoiding assembly interference, stress concentration or obstruction of lubricating oil flow caused by structural protrusions, ensuring normal fit and lubrication between roller 1 and crankshaft, and improving the reliability and stability of compressor operation.

[0056] likeFigure 2 As shown, in some specific embodiments of the present invention, the angle formed by the lines connecting the two ends of the non-beveled structure 32 to the center of the roller 1 along the circumferential direction of the roller 1 is α, and its value range is 0 < α ≤ 30°.

[0057] It is understandable that the non-beveled structure 32 occupies only a small portion of the circumference of roller 1, concentrated in a local circumferential position corresponding to the flange outlet. For example, the specific values ​​of α can include, but are not limited to: 1°, 3°, 5°, 8°, 10°, 12°, 15°, 18°, 20°, 22°, 25°, 27°, and 30°. It should be noted that the above values ​​have all been experimentally verified and can effectively balance sealing and lubrication under different compressor specifications and operating conditions.

[0058] On the one hand, if α is equal to or close to 0°, the non-beveled structure 32 is almost non-existent in the circumferential direction, making it impossible to form an effective continuous sealing surface and posing a risk of high-pressure gas leakage. Therefore, α must be greater than 0° to ensure that the non-beveled structure 32 has sufficient circumferential coverage width to achieve a reliable seal.

[0059] On the other hand, if α exceeds 30°, the circumferential area occupied by the non-beveled structure 32 becomes too large, significantly compressing the area available for setting the beveled structure 31. This results in insufficient oil storage space, deterioration of lubrication conditions between the roller 1 end face and the flange, increased frictional power, and decreased compressor efficiency. Experiments show that when α exceeds 30°, the energy loss is significantly aggravated. Therefore, limiting the upper limit of α to 30° allows for the maximum preservation of the beveled area required for lubrication while ensuring sealing.

[0060] In summary, limiting α to the range of 0°<α≤30° is an optimized result after comprehensively considering sealing reliability, lubrication performance, manufacturing tolerance, and energy efficiency. The above angle design can not only ensure that the leakage path of high-pressure gas to the inner hole 12 of roller 1 is effectively blocked during the gas discharge stage, but also maximize the preservation of the remaining circumferential area for setting the chamfer structure 31 to maintain good lubrication performance.

[0061] like Figure 3 As shown, in some embodiments of the present invention, on the projection plane perpendicular to the central axis of the roller 1, the radial width of the chamfer structure 31 is d, and its value range is d≥2mm.

[0062] For example, specific possible values ​​for d include, but are not limited to: 2.0 mm, 2.2 mm, 2.5 mm, 2.8 mm, 3.0 mm, 3.5 mm, 4.0 mm, 4.5 mm, 5.0 mm, 5.5 mm, 6.0 mm, 6.5 mm, and 7.0 mm. It should be noted that the above values ​​have been verified in compressor prototypes of different specifications, and all of them effectively form a stable oil storage area, improving lubrication conditions.

[0063] It should be explained that if the radial width of the chamfered structure 31 is less than 2 mm, the resulting groove 33 will be too narrow, resulting in insufficient oil storage capacity and making it difficult to establish a continuous and stable lubricating oil film between the end face of the roller 1 and the end face of the flange. Especially under high speed or high temperature conditions, the lubricating oil is easily thrown out or evaporated, leading to boundary lubrication or even dry friction, significantly increasing frictional power and accelerating wear. Experiments show that when d < 2 mm, the compressor input power increases by more than 3%, and energy efficiency deteriorates significantly. Therefore, setting the lower limit of d to 2 mm is the minimum structural guarantee to ensure effective lubrication.

[0064] In summary, by setting the radial width d of the chamfer structure 31 to not less than 2 mm, efficient lubrication can be achieved while ensuring the structural strength and sealing function of the roller 1, thereby significantly reducing compressor friction loss and improving energy efficiency.

[0065] like Figure 3 As shown, in some embodiments of the present invention, the vertical distance between the outer periphery of the chamfer structure 31 and the outer periphery of the roller 1 is c, and the value range is c≥1mm.

[0066] For example, specific possible values ​​for c include, but are not limited to: 1.0 mm, 1.2 mm, 1.5 mm, 1.8 mm, 2.0 mm, 2.3 mm, 2.5 mm, 2.8 mm, 3.0 mm, 3.2 mm, 3.5 mm, 4.0 mm, and 4.5 mm. It should be noted that the above values ​​have been verified in different compressor models and all effectively form an oil storage area with sufficient volume, without affecting the overall structural strength of roller 1 and the movement coordination of vane 2.

[0067] If c is less than 1 mm, the chamfer structure 31 is too close to the outer circumference of the roller 1, and the depth of the groove 33 formed is insufficient, resulting in limited oil storage space and difficulty in maintaining stable lubricating oil retention during the high-speed rotation of the roller 1. For example, under compressor start-up or low oil conditions, the lubricating film is prone to rupture, leading to increased friction between the end face of the roller 1 and the end face of the flange, and increased power loss.

[0068] In summary, setting the vertical distance c between the chamfered structure 31 and the outer circumferential surface of the roller 1 to not less than 1 mm can achieve good lubrication while ensuring structural strength and motion reliability.

[0069] like Figure 1 As shown, according to some embodiments of the present invention, it further includes an eccentric portion, which is installed in the inner hole 12 of the roller 1, and the inner circumferential surface of the roller 1 is slidably connected to the outer circumferential surface of the eccentric portion. A groove 33 is provided on the inner circumferential surface of the roller 1 adjacent to the first connecting portion 11. The groove 33 extends circumferentially and penetrates the upper and lower end surfaces of the roller 1.

[0070] In this embodiment, the groove 33 is disposed on the inner circumferential surface of the roller 1, and is essentially a partially recessed step structure that forms an annular oil storage space on the surface of the inner bore 12 of the roller 1. During compressor operation, lubricating oil enters the mating clearance between the roller 1 and the eccentric part through the crankshaft oil supply channel or splash lubrication within the housing. Because the groove 33 has a radial position lower than the surrounding inner circumferential surface, lubricating oil easily accumulates and remains in this area under centrifugal force and capillary action.

[0071] When the compressor enters the exhaust stage, the high-pressure gas inside the cylinder acts on roller 1, causing it to make close contact with the eccentric part in a certain local area. This contact point is the load-bearing part, which is the tangential contact area between the outer circumferential surface of the eccentric part and the inner circumferential surface of roller 1. This area bears the maximum mechanical load, and without effective lubrication, boundary friction or even dry friction is very likely to occur, leading to wear, temperature rise, or increased rotational resistance. At this time, the lubricating oil stored in the groove 33 can replenish this high-stress load-bearing part in a timely manner, forming a continuous and stable lubricating oil film, achieving fluid lubrication or mixed lubrication, thereby effectively isolating direct contact between metal surfaces.

[0072] Specifically, the working process of the groove 33 inside the pump body assembly is as follows: After the compressor starts, the crankshaft drives the eccentric part to rotate, and the roller 1 then performs eccentric rotational motion inside the cylinder. Lubricating oil enters the inner hole 12 of the roller 1 and is distributed on the inner circumferential surface of the roller 1. Since the groove 33 is located in the circumferential region adjacent to the first connecting part 11, its position corresponds to the high-pressure contact point between the eccentric part and the roller 1 in the compressor exhaust phase. During the intake and compression phases, the groove 33 continuously collects and stores lubricating oil. When the roller 1 rotates to the exhaust position, the high pressure inside the cylinder pushes the roller 1 to press tightly against the eccentric part, and the two form a high-load contact pair locally. At this time, the lubricating oil in the groove 33 is dynamically supplied to this contact area under the action of pressure gradient and relative motion, maintaining the oil film thickness. Even under high speed or high temperature conditions, this oil storage structure can still ensure lubrication continuity and avoid oil film rupture.

[0073] After the venting is complete, roller 1 continues to rotate, and groove 33 is refilled with oil in the next cycle, preparing for lubrication in the next venting stage. The entire process is repeated, achieving on-demand, continuous, and reliable lubrication of key friction pairs.

[0074] In this embodiment, the step difference on the inner circumferential surface of the roller 1 forms an oil storage space, thereby forming a lubricating oil film between the inner wall of the roller 1 and the outer wall of the eccentric part. By maintaining a stable oil film, direct metal-to-metal contact is reduced, effectively reducing the sliding friction resistance between the roller 1 and the eccentric part, and avoiding adhesion, scratches, or poor rotation caused by insufficient local lubrication. This reduces the compressor input power, improves energy efficiency, and enhances the reliability and lifespan of the compressor.

[0075] like Figure 2 As shown, in some specific embodiments of the present invention, the central angle corresponding to the groove 33 is β, and its value range is 0<β≤180°.

[0076] For example, specific selectable values ​​for β include, but are not limited to: 0°, 10°, 20°, 30°, 45°, 60°, 90°, 120°, 135°, 150°, 160°, 170°, and 180°. It should be noted that the above values ​​have been verified in different compressor prototypes, and all of them can achieve effective oil film supply to high-pressure areas based on actual load distribution and lubrication requirements.

[0077] It is understandable that if β exceeds 180°, the groove 33 will cover more than half of the inner circumferential surface of the roller 1. Although this can increase the oil storage capacity, it will significantly reduce the effective bearing area of ​​the inner hole 12 of the roller 1, weaken the structural strength, and may interfere with the stable fit between the eccentric part and the roller 1.

[0078] like Figure 2 As shown, in some specific embodiments of the present invention, the central angle corresponding to the portion of the groove 33 adjacent to the edge of the first connecting portion 11 and the first connecting portion 11 is γ, and its value range is 0≤γ<180°.

[0079] For example, specific selectable values ​​for γ include, but are not limited to: 0°, 10°, 20°, 30°, 45°, 60°, 75°, 90°, 105°, 120°, 135°, 150°, and 180°. These values ​​have been verified in different compressor structures and can adapt to diverse design requirements regarding outlet location, vane 2 connection method, and load distribution.

[0080] When γ = 0°, it means that the edge of the groove 33 is completely aligned with the first connecting part 11 in the circumferential direction, that is, the groove 33 is initially positioned adjacent to the first connecting part 11. This arrangement ensures that the groove 33 covers the area where high-pressure contact occurs earliest during the exhaust phase, achieving immediate lubrication of the critical friction pair. If γ is negative (i.e., the groove 33 extends beyond the first connecting part 11 to the other side), it may intrude into non-target areas, affecting structural symmetry or conflicting with the sealing design. Therefore, setting the lower limit of γ to 0° ensures that the groove 33 is always located downstream of or aligned with the first connecting part 11, conforming to the actual direction of load development during the exhaust phase.

[0081] As γ increases, the groove 33 gradually moves away from the first connecting portion 11, and its starting position shifts circumferentially further away. If γ exceeds 180°, the groove 33 will be located in the half-circumference region opposite to the first connecting portion 11, far from the high-stress area corresponding to the vent hole, and cannot effectively serve the tangential bearing portion of the eccentric portion and roller 1 during the venting stage. At this time, the oil storage function of the groove 33 is disconnected from the actual lubrication requirements, resulting in a significant decrease in lubrication efficiency. Therefore, the upper limit of γ is limited to 180° to ensure that the groove 33 is always arranged within the half-circumference range measured from the first connecting portion 11, covering all possible high-load areas, and ensuring the timeliness and effectiveness of lubrication.

[0082] In summary, limiting γ to the range of 0°≤γ≤180° allows the groove 33 to flexibly adjust its starting position according to specific working conditions, while ensuring that it is always within a reasonable circumferential range in the high-pressure area of ​​the lubrication and venting stage, thus balancing structural adaptability and functional reliability.

[0083] like Figure 2 As shown, in some specific embodiments of the present invention, the inner diameter of the roller 1 is R1, the radius of curvature of the groove 33 is R2, and R1 and R2 satisfy 0.2mm≤R2-R1≤1mm.

[0084] For example, R2-R1 can be 0.2, 0.3, 0.5, 0.7, 0.9, 0.6, 0.8, 0.5, 0.3, 0.7, 0.6, 0.9, or 1.0 mm. All of the above values ​​fall within the range, which can effectively form an oil storage space and maintain structural strength.

[0085] If the radial depth of the groove 33 is less than 0.2 mm, the resulting step is too shallow, resulting in insufficient oil storage capacity and making it difficult to maintain an effective oil film in the high-pressure contact area between the eccentric part and the roller 1. For example, under high temperature and high speed conditions, the lubricating oil is easily squeezed out or evaporated, leading to boundary lubrication or even dry friction, which aggravates wear and increases friction power. Therefore, setting 0.2 mm as the lower limit is the minimum structural depth to ensure that the groove 33 has a basic oil storage function.

[0086] If the depth of the groove 33 exceeds 1 mm, the local wall thickness of the inner circumference of the roller 1 will be significantly reduced, leading to a decrease in structural strength and making it prone to deformation or fatigue cracking under high-pressure exhaust load. Simultaneously, an excessively deep groove 33 will weaken the effective contact area between the eccentric part and the roller 1, affecting motion stability and potentially causing vibration or abnormal noise. Furthermore, an excessively large oil reservoir may result in excessive lubricant retention, which in turn reduces the oil pressure response speed.

[0087] In summary, limiting R2-R1 to the range of 0.2 mm ≤ R2-R1 ≤ 1 mm ensures that the groove 33 has sufficient oil storage capacity to form a stable lubricating oil film, while maintaining the mechanical strength and motion stability of the roller 1.

[0088] According to some embodiments of the present invention, the roller 1 and the slide 2 can be integrally formed or hinged together, for example... Figures 1 to 2 As shown, the sliding plate 2 is integrally formed on the outer peripheral surface of the roller 1; for example... Figure 3 As shown, the slider 2 is hinged to the outer peripheral surface of the roller 1, and the outer peripheral surface of the roller 1 forms a hinged connection area. The above structure can be used for rocking rollers or hinged rollers.

[0089] like Figures 1 to 4 As shown, the present invention also protects a compressor, the compressor protected by the second aspect of the present invention including the pump body assembly described in the first aspect of the present invention.

[0090] like Figures 1 to 4 As shown, the present invention also protects a refrigeration device, the refrigeration device protected by the second aspect of the present invention including the compressor described in the first aspect embodiment of the present invention. The refrigeration device can be a wall-mounted air conditioner, a floor-standing air conditioner, a central air conditioner, etc., and the present invention does not impose any special limitations thereon.

[0091] The "range" disclosed in this application is defined by a lower limit and an upper limit. A given range is defined by selecting a lower limit and an upper limit, which define the boundaries of a particular range. Ranges defined in this way can include or exclude endpoints and can be arbitrarily combined; that is, any lower limit can be combined with any upper limit to form a range. For example, if ranges of 60-120 and 80-110 are listed for a specific parameter, it is expected that ranges of 60-110 and 80-120 are also included. Furthermore, if minimum range values ​​of 1 and 2 are listed, and if maximum range values ​​of 3, 4, and 5 are listed, then the following ranges are all expected: 1-3, 1-4, 1-5, 2-3, 2-4, and 2-5. In this application, unless otherwise stated, the numerical range "ab" represents a shortened representation of any combination of real numbers between a and b, where a and b are real numbers. For example, the numerical range "0-5" indicates that all real numbers between "0-5" have been listed in this article; "0-5" is simply a shortened representation of these numerical combinations. Furthermore, when a parameter is stated as an integer ≥2, it is equivalent to disclosing that the parameter is, for example, an integer such as 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, etc.

[0092] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A pump body assembly, characterized by, Comprising: a roller, a slide and a flange; the roller is provided with a first connecting part, the slide is hinged to the first connecting part, an end surface of the flange is in sliding fit with an end surface of the roller, and the flange is provided with a gas outlet hole arranged adjacent to the first connecting part; a chamfer structure and a non-chamfer structure are arranged at the junction of the inner circumferential surface of the roller and the end surface thereof, and the non-chamfer structure is arranged adjacent to the first connecting part; the non-chamfer structure is used for plugging a communication gap between the gas outlet hole and the inner hole of the roller.

2. The pump body assembly of claim 1, wherein, A sealing surface is formed on the side of the non-chamfer structure facing the gas outlet hole, and the sealing surface is flush with the end surface of the roller; during the movement of the roller, the hole wall of the gas outlet hole does not exceed the edge of the sealing surface in the direction facing the inner hole of the roller.

3. The pump body assembly of claim 2, wherein, In the direction facing the inner hole of the roller, the non-chamfer structure does not exceed the inner circumferential surface of the roller.

4. The pump body assembly of claim 2, wherein, In the circumferential direction of the roller, the included angle between the two ends of the non-chamfer structure and the center line of the roller is α, and the value range of α is 0 < α ≤ 30°.

5. The pump body assembly of claim 2, wherein, In the projection plane perpendicular to the central axis of the roller, the radial width of the chamfer structure is d, and the value range of d is d ≥ 2 mm; and / or, the vertical distance between the outer periphery of the chamfer structure and the outer circumferential surface of the roller is c, and the value range of c is c ≥ 1 mm.

6. The pump body assembly of any one of claims 1 to 5, wherein, Further comprising an eccentric part, the eccentric part is installed in the inner hole of the roller, and the inner circumferential surface of the roller is in sliding fit connection with the outer circumferential surface of the eccentric part, and a groove is arranged on the inner circumferential surface of the roller adjacent to the first connecting part, and the groove extends in the circumferential direction and penetrates through the upper and lower end surfaces of the roller.

7. The pump body assembly of claim 6, wherein, The central angle corresponding to the groove is β, and the value range of β is 0 < β ≤ 180°; and / or, the central angle corresponding to the part between the edge of the groove adjacent to the first connecting part and the first connecting part is γ, and the value range of γ is 0 ≤ γ < 180°.

8. The pump body assembly of claim 7, wherein, The inner diameter of the roller is R1, the curvature radius of the groove is R2, and R1 and R2 satisfy 0.2 mm ≤ R2-R1 ≤ 1 mm.

9. A compressor characterized by, Comprising: the pump body assembly according to any one of claims 1 to 8.

10. A refrigeration appliance characterized in that, Comprising: the compressor according to claim 9.

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