Hinge piston structure and compressor

Abstract

The utility model relates to rolling rotor compressor technical field especially relates to a hinge type piston structure and compressor. Wherein, the crankshaft penetrates the cylinder, the piston sleeve is located in the eccentric part of crankshaft, and the piston is located in the cylinder, the cylinder is provided with the sliding slot, one end of vane is arranged in the sliding slot and slides, the other end of vane is articulated with the piston, and the piston includes high bearing part, low bearing part and non bearing part, high bearing part and non bearing part are located at both sides of vane respectively, low bearing part is located between high bearing part and non bearing part, and the inner wall of low bearing part and / or the inner wall of non bearing part is provided with a plurality of spiral oil groove, and spiral oil groove is used for pumping oil. The hinge type piston structure sets up spiral oil groove in the inner wall of low bearing part and / or the inner wall of non bearing part, can improve lubricating oil pumping capacity, improves the lubrication state between piston and crankshaft eccentric part, reduces abrasion, simultaneously, lubricating oil can infiltrate the radial clearance of piston and cylinder, forms sealed oil film, and reduces radial leakage.

Description

Technical Field

[0001] This utility model relates to the field of rolling rotor compressor technology, and in particular to a hinged piston structure and compressor. Background Technology

[0002] Under dynamic energy efficiency requirements, compressors need to achieve wide-frequency operation, with the minimum operating frequency needing to be reduced to 8Hz or even lower. In conventional rolling rotor compressors, under low-speed, light-load conditions, the blades and piston are prone to detachment and impact, producing a "ticking" sound. To solve this problem, the industry proposed a "blade tip-piston hinge structure," which mechanically restricts the relative position of the blades and piston, fundamentally preventing detachment and impact and eliminating the clicking sound. However, this structure has two major technical drawbacks: increased wear on the eccentric bearing: the hinge structure not only makes the shaft system bear part of the blade load but also restricts the piston's rotation ability, leading to a significant increase in the load and relative speed between the piston and the eccentric part of the crankshaft, resulting in accelerated wear; increased risk of radial leakage between the piston and cylinder: the hinge structure restricts the piston-crankshaft axis self-adaptive trajectory to a certain extent. In conventional structures, the crankshaft can be finely adjusted under gas force to fit the cylinder wall, but with the axis trajectory restricted, the radial clearance between the piston and cylinder is difficult to compensate for, increasing the leakage of gas from the high-pressure chamber to the low-pressure chamber (radial leakage), leading to a decrease in volumetric efficiency.

[0003] Therefore, there is an urgent need for a hinged piston structure and compressor to solve the above-mentioned technical problems. Utility Model Content

[0004] The purpose of this invention is to propose a hinged piston structure and compressor that can reduce wear between the piston and the eccentric part of the crankshaft and reduce radial leakage.

[0005] To achieve this objective, the present invention adopts the following technical solution:

[0006] A hinged piston structure and compressor include: a cylinder, a piston, a crankshaft, and blades. The crankshaft passes through the cylinder, and the piston is sleeved on the eccentric portion of the crankshaft and located inside the cylinder. The cylinder is provided with a sliding groove. One end of the blade is slidably disposed in the sliding groove, and the other end of the blade is hinged to the piston. The piston includes a high-load-bearing portion, a low-load-bearing portion, and a non-load-bearing portion. The high-load-bearing portion and the non-load-bearing portion are respectively located on both sides of the blade, and the low-load-bearing portion is located between the high-load-bearing portion and the non-load-bearing portion. The inner wall of the low-load-bearing portion and / or the inner wall of the non-load-bearing portion are provided with a plurality of spiral oil grooves for pumping oil.

[0007] As a preferred technical solution for the aforementioned hinged piston structure and compressor, the width of the spiral oil groove is L, wherein 1mm≤L≤4mm.

[0008] As a preferred technical solution for the aforementioned hinged piston structure and compressor, the groove depth of the spiral oil groove is t, wherein 0.5mm≤t≤2mm.

[0009] As a preferred technical solution of the above-mentioned hinged piston structure and compressor, the height of the piston is H, and the pitch between two adjacent spiral oil grooves is P, wherein P>2H / π.

[0010] As a preferred technical solution for the aforementioned hinged piston structure and compressor, the surface roughness of the spiral oil groove is R. Z , where R Z ≤3.2μm.

[0011] As a preferred technical solution for the aforementioned hinged piston structure and compressor, the spiral oil groove rotates in the same direction as the crankshaft.

[0012] As a preferred technical solution for the above-mentioned hinged piston structure and compressor, the central angle of the non-load-bearing part is α, wherein 90°≤α≤180°.

[0013] As a preferred technical solution of the above-mentioned hinged piston structure and compressor, the spiral oil groove extends from the lower end face of the piston to the upper end face, and neither end of the spiral oil groove falls into the high load-bearing part.

[0014] As a preferred technical solution of the above-mentioned hinged piston structure and compressor, the radial force f exerted by the crankshaft on the low load-bearing part is the same as that on the high load-bearing part, and the radial force F exerted by the crankshaft on the high load-bearing part is the same as that on the high load-bearing part, wherein f ≤ 1 / 3F.

[0015] A compressor includes a housing, and the compressor further includes a hinged piston structure as described in any of the preferred embodiments above, the hinged piston structure being disposed within the housing.

[0016] The beneficial effects of this utility model are:

[0017] This invention provides a hinged piston structure and compressor. The hinged piston structure and compressor include: a cylinder, a piston, a crankshaft, and blades. The crankshaft passes through the cylinder, and the piston is sleeved on the eccentric portion of the crankshaft and located inside the cylinder. The cylinder is provided with a sliding groove. One end of the blade is slidably disposed in the sliding groove, and the other end of the blade is hinged to the piston. The piston includes a high-load-bearing portion, a low-load-bearing portion, and a non-load-bearing portion. The high-load-bearing portion and the non-load-bearing portion are located on opposite sides of the blade, and the low-load-bearing portion is located between the high-load-bearing portion and the non-load-bearing portion. The inner wall of the low-load-bearing portion and / or the inner wall of the non-load-bearing portion are provided with several spiral oil grooves for pumping oil. Compared to the prior art, this hinged piston structure, by providing spiral oil grooves on the inner wall of the low-load-bearing portion and / or the inner wall of the non-load-bearing portion, can improve the lubricating oil pumping capacity, improve the lubrication state between the piston and the eccentric portion of the crankshaft, and reduce wear between the piston and the eccentric portion of the crankshaft. Simultaneously, the lubricating oil can penetrate into the radial clearance between the piston and the cylinder, forming a sealing oil film and reducing radial leakage. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments of this utility model will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the content of the embodiments of this utility model and these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the hinged piston structure provided in an embodiment of the present invention;

[0020] Figure 2 This is a force diagram of the hinged piston structure provided in this embodiment of the utility model;

[0021] Figure 3 This is a schematic diagram of the first structure of the piston provided in this embodiment of the present invention;

[0022] Figure 4 This is a cross-sectional view of the piston provided in an embodiment of the present invention;

[0023] Figure 5 This is a schematic diagram of the second structure of the piston provided in an embodiment of the present invention.

[0024] In the picture:

[0025] 1. Cylinder; 11. Slide groove; 2. Piston; 21. High load-bearing section; 22. Low load-bearing section; 23. Non-load-bearing section; 24. Mounting groove; 3. Crankshaft; 4. Blade; 5. Spiral oil groove. Detailed Implementation

[0026] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, not the entire structure.

[0027] In the description of this utility model, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0028] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0029] In the description of this embodiment, the terms "upper," "lower," "left," and "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, 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 this utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0030] like Figures 1 to 5 As shown, this utility model provides a hinged piston structure and compressor. The hinged piston structure and compressor include: a cylinder 1, a piston 2, a crankshaft 3, and blades 4.

[0031] Specifically, the crankshaft 3 passes through the cylinder 1, the piston 2 is sleeved on the eccentric part of the crankshaft 3 and is located inside the cylinder 1, the cylinder 1 is provided with a sliding groove 11, one end of the blade 4 is slidably disposed in the sliding groove 11, and the other end of the blade 4 is hinged to the piston 2. The piston 2 includes a high load-bearing part 21, a low load-bearing part 22 and a non-load-bearing part 23. The high load-bearing part 21 and the non-load-bearing part 23 are respectively located on both sides of the blade 4, and the low load-bearing part 22 is located between the high load-bearing part 21 and the non-load-bearing part 23. The inner wall of the low load-bearing part 22 and / or the inner wall of the non-load-bearing part 23 are provided with a plurality of spiral oil grooves 5, which are used for pumping oil. Compared to existing technologies, this hinged piston structure improves lubricant pumping capacity by providing spiral oil grooves 5 on the inner wall of the low-load-bearing section 22 and / or the inner wall of the non-load-bearing section 23. The spiral oil grooves 5 actively pump lubricant to the eccentric bearing pair of the crankshaft 3, solving the problem of uneven lubricant distribution caused by the piston 2 not rotating. The oil film thickness on the eccentric bearing mating surface increases, reducing wear. At the same time, the lubricant can penetrate into the radial gap between the piston 2 and the cylinder 1, forming a sealing oil film to fill the tiny gap between the piston 2 and the cylinder 1, reducing radial leakage and improving the compressor volumetric efficiency by 5%-8%, significantly optimizing dynamic energy efficiency (especially under low-speed conditions). It should be noted that the non-load-bearing section 23 refers to the area where the inner wall of the piston 2 experiences less radial force from the crankshaft 3 during piston 2 operation (determined through dynamic simulation, usually the quadrant opposite to the high-pressure zone of the cylinder 1 compression chamber).

[0032] Furthermore, the piston 2 is provided with a mounting groove 24, and the other end of the blade 4 is hinged in the mounting groove 24.

[0033] Optionally, the spiral oil groove 5 rotates in the same direction as the crankshaft 3. With this configuration, the spiral oil groove 5 rotates in the same direction as the crankshaft 3, thereby utilizing the centrifugal force of rotation to improve the efficiency of lubricating oil pumping. When the crankshaft 3 rotates clockwise, the spiral oil groove 5 is set to right-hand rotation; when the crankshaft 3 rotates counterclockwise, the spiral oil groove 5 is set to left-hand rotation.

[0034] Optionally, the depth of the spiral oil groove 5 is t, where 0.5mm ≤ t ≤ 2mm. This setting ensures sufficient oil storage while avoiding weakening the strength of the piston 2's inner diameter.

[0035] Optionally, the width of the spiral oil groove 5 is L, where 1mm ≤ L ≤ 4mm. This setting can adapt to the viscosity of the lubricating oil and prevent oil flow blockage.

[0036] Optionally, the height of piston 2 is H, and the pitch between two adjacent spiral oil grooves 5 is P, where P > 2H / π; the spiral oil grooves 5 extend from the lower end face of piston 2 to the upper end face, and neither end of the spiral oil grooves 5 falls into the high bearing portion 21. With this configuration, the pitch matches the height of piston 2, ensuring that the spiral oil grooves 5 extend from the lower end face of piston 2 to near the upper end face without falling into the high bearing portion 21.

[0037] Optionally, the surface roughness of the spiral oil groove 5 is R. Z , where R Z ≤3.2μm. This setting allows the lubricating oil to flow smoothly within the spiral oil groove 5.

[0038] Optionally, the central angle of the non-load-bearing portion 23 is α, where 90°≤α≤180°, meaning the non-load-bearing portion 23 is 1 / 4 to 1 / 2 of the circumference of the inner wall of the piston 2; the low-load-bearing portion 22 is subjected to a radial force f from the crankshaft 3, and the high-load-bearing portion 21 is subjected to a radial force F from the crankshaft 3, where f≤1 / 3F. This arrangement avoids the spiral oil groove 5 weakening the structural strength of the critical stress area of ​​the piston 2, ensuring that the piston 2 has no risk of deformation under high-frequency conditions above 120Hz or low-frequency conditions below 8Hz, thus ensuring the stability of the compressor's wide-frequency operation, while also ensuring the efficient operation of the spiral oil groove 5.

[0039] Optionally, at least one spiral oil groove 5 is formed in the low-load-bearing portion 22 or the non-load-bearing portion 23 of the inner wall of the piston 2. A single spiral oil groove 5 can meet the basic pumping requirements, while multiple spiral oil grooves 5 can further improve efficiency and avoid the structural strength reduction caused by too many spiral oil grooves 5. Furthermore, the spiral oil groove 5 is directly formed in the low-load-bearing portion 22 or the non-load-bearing portion 23 of the inner diameter of the piston 2, without the need to modify the hinge structure, cylinder 1, crankshaft 3 and other core components. The processing technology is mature (it can be achieved through CNC lathe or milling), the cost is low, it is easy to mass-produce, and it is compatible with the assembly process of existing wide-frequency compressors.

[0040] The lubricating oil flow path of the hinged piston structure provided by this utility model is as follows: When the piston 2 rotates with the crankshaft 3, the spiral oil groove 5 uses the "screw pump principle" to pump the lubricating oil at the bottom of the piston 2 upward: part of the lubricating oil is delivered through the spiral oil groove 5 to the mating surface (eccentric bearing pair) between the inner hole of the piston 2 and the crankshaft 3 to form a stable oil film and improve the lubrication condition; another part of the lubricating oil extends with the spiral oil groove 5 to the upper end face of the piston 2. Because there is a small gap between the upper end face and the end cover of the cylinder 1, the lubricating oil naturally seeps into the radial gap between the piston 2 and the cylinder 1 to form a sealing oil film and reduce the radial leakage from the high pressure chamber to the low pressure chamber.

[0041] This utility model also provides a compressor, including a housing, and the compressor also includes the hinged piston structure of any of the above embodiments, the hinged piston structure being disposed inside the housing, and the compressor also includes other essential components that constitute a compressor in the prior art.

[0042] Furthermore, the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the protection scope of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. A hinged piston structure, characterized in that, include: The cylinder (1), piston (2), crankshaft (3), and vane (4) are provided. The crankshaft (3) passes through the cylinder (1). The piston (2) is fitted onto the eccentric part of the crankshaft (3) and is located inside the cylinder (1). The cylinder (1) is provided with a sliding groove (11). One end of the vane (4) is slidably disposed in the sliding groove (11), and the other end of the vane (4) is hinged to the piston (2). The piston (2) includes... The blade (4) has a high load-bearing section (21), a low load-bearing section (22), and a non-load-bearing section (23). The high load-bearing section (21) and the non-load-bearing section (23) are located on opposite sides of the blade (4). The low load-bearing section (22) is located between the high load-bearing section (21) and the non-load-bearing section (23). The inner wall of the low load-bearing section (22) and / or the inner wall of the non-load-bearing section (23) are provided with a plurality of spiral oil grooves (5). The spiral oil grooves (5) are used for pumping oil.

2. The hinged piston structure according to claim 1, characterized in that, The width of the spiral oil groove (5) is L, where 1mm≤L≤4mm.

3. The hinged piston structure according to claim 1, characterized in that, The depth of the spiral oil groove (5) is t, where 0.5mm≤t≤2mm.

4. The hinged piston structure according to claim 1, characterized in that, The height of the piston (2) is H, and the pitch between the two adjacent spiral oil grooves (5) is P, where P>2H / π.

5. The hinged piston structure according to claim 1, characterized in that, The surface roughness of the spiral oil groove (5) is R. Z , where R Z ≤3.2μm.

6. The hinged piston structure according to claim 1, characterized in that, The spiral oil groove (5) rotates in the same direction as the crankshaft (3).

7. The hinged piston structure according to claim 1, characterized in that, The central angle of the non-load-bearing part (23) is α, where 90°≤α≤180°.

8. The hinged piston structure according to claim 1, characterized in that, The spiral oil groove (5) extends from the lower end face of the piston (2) to the upper end face, and neither end of the spiral oil groove (5) falls into the high bearing portion (21).

9. The hinged piston structure according to claim 1, characterized in that, The low-load-bearing part (22) is subjected to a radial force f from the crankshaft (3), and the high-load-bearing part (21) is subjected to a radial force F from the crankshaft (3), wherein f ≤ 1 / 3F.

10. A compressor, including a housing, characterized in that, The compressor further includes a hinged piston structure as described in any one of claims 1-9, the hinged piston structure being disposed within the housing.

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