Air cylinder structure and compressor
By setting a throttling section on the inner peripheral wall of the piston chamber in the cylinder structure, an alternating undulating wall surface is formed, which solves the leakage problem caused by the expansion of the reverse clearance in the traditional design, and realizes the high-efficiency operation and low loss of the compressor.
Patent Information
- Application Number
- CN202511964899.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-12-24
- Publication Date
- 2026-02-13
AI Technical Summary
In pursuing the design of minimum eccentric clearance, traditional rotary compressors cause the reverse clearance between the piston and the cylinder wall to expand, forming new leakage paths, reducing exhaust volume and efficiency, and increasing power loss.
A throttling section is provided on the inner peripheral wall of the piston chamber in the cylinder structure, including multiple first wall sections extending toward the center of the cylinder and second wall sections extending away from the center, forming an interlaced undulating wall surface, providing throttling resistance, and suppressing leakage of high-pressure working gas to the low-pressure area.
It effectively suppressed the backflow and leakage of high-pressure working gas, improved the overall energy efficiency and operational stability of the compressor, and reduced power loss.
Smart Images
Figure CN121520192A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of compressor technology, and more particularly to a cylinder structure and a compressor. Background Technology
[0002] The core pump body of a rotary compressor mainly consists of key components such as a cylinder, vanes (or sliding vanes), and pistons (or rollers). Its working principle relies on the eccentric rotational motion of the piston within the cylinder, working in conjunction with the vanes to complete the intake, compression, and discharge of refrigerant gas.
[0003] In traditional design and assembly processes, to achieve the highest volumetric efficiency and energy efficiency, manufacturers take a key measure: adjusting the "eccentric clearance" between the piston and cylinder on the exhaust side to an absolute minimum. The direct purpose of this is to minimize working fluid leakage from high-pressure exhaust to the low-pressure compression or intake chambers. However, this optimization triggers an unavoidable chain reaction—the dimensional chain effect. All compressor components have machining tolerances, which accumulate into a closed dimensional chain during assembly. When the eccentric clearance is forcibly adjusted to a minimum during assembly, the piston-cylinder wall clearance on the opposite side (the side with the smallest eccentric clearance) passively expands to its maximum value. This results in the expanded clearance side becoming a new and significant leakage path. High-pressure working fluid gas leaks back into the low-pressure area through this increased clearance. This internal leakage not only directly reduces the compressor's discharge volume and efficiency but also leads to additional power loss and performance degradation, becoming an irreconcilable contradiction in traditional design. Summary of the Invention
[0004] The purpose of this invention is to provide a cylinder structure that can provide throttling resistance for high-pressure working gas and effectively improve leakage.
[0005] To achieve this objective, the present invention adopts the following technical solution:
[0006] A cylinder structure, comprising:
[0007] A cylinder block has a piston chamber, the inner peripheral wall of which includes a throttling portion, the throttling portion including a first wall segment, a plurality of the first wall segments being spaced apart along the circumference of the piston chamber, the first wall segments having a tendency to extend toward the center of the cylinder block;
[0008] The piston is eccentrically disposed in the piston chamber. During the rotation of the piston in the piston chamber, there is always a gap between the piston and the first wall section, and the first wall section is used to provide throttling resistance to the working gas in the piston chamber.
[0009] Preferably, the throttling section further includes a second wall segment, which connects two adjacent first wall segments, and the second wall segment tends to extend in a direction away from the center of the cylinder block compared to the first wall segment.
[0010] Preferably, the distance between the extension vertex of the first wall segment and the center of the cylinder is h1, and the distance between the extension vertex of the second wall segment and the center of the cylinder is h2.
[0011] Let Δh = h1 - h2, then the range of Δh is 3μm - 50μm.
[0012] Preferably, there is an eccentric gap between the piston and the inner peripheral wall of the piston chamber, the side of the cylinder body corresponding to the side with the smallest eccentric gap is the eccentric gap side, the side of the cylinder body opposite to the eccentric gap side is the reverse gap side, and the throttling part is disposed on the reverse gap side.
[0013] Preferably, there is an eccentric gap between the piston and the inner peripheral wall of the piston chamber. The side of the cylinder body corresponding to the side with the smallest eccentric gap is the eccentric gap side, and the side of the cylinder body opposite to the eccentric gap side is the reverse gap side. Both the eccentric gap side and the reverse gap side are provided with the throttling section, and the number of first wall segments in the throttling section corresponding to the reverse gap side is greater than the number of first wall segments in the throttling section corresponding to the eccentric gap side.
[0014] Preferably, the cylinder body has a vane groove that communicates with the piston chamber, and a vane is slidably disposed in the vane groove. The vane divides the piston chamber into an intake side and an exhaust side, and the throttling part is disposed on the intake side.
[0015] Preferably, the cylinder body has a vane groove that communicates with the piston chamber. A vane is slidably disposed in the vane groove, and the vane divides the piston chamber into an intake side and an exhaust side. Both the intake side and the exhaust side are provided with the throttling section, and the number of the first wall segments in the throttling section corresponding to the intake side is greater than the number of the first wall segments in the throttling section corresponding to the exhaust side.
[0016] Preferably, both the first wall segment and the second wall segment are configured to be arc-shaped.
[0017] Preferably, the first wall segment and the second wall segment are configured as toothed structures, and the tips of the toothed structures are rounded.
[0018] Preferably, during the process of the piston rotating once in the piston cavity, there is always a gap between the piston and the inner peripheral wall of the piston cavity.
[0019] The present invention also provides a compressor including the above-described cylinder structure, which can provide throttling resistance for high-pressure working gas, effectively improve leakage, reduce compressor power loss, and ensure performance.
[0020] A compressor includes the cylinder structure described in any of the preceding claims, and further includes a housing, wherein the cylinder structure is disposed within the housing.
[0021] Beneficial effects:
[0022] The cylinder structure provided by this invention has a throttling section on the inner circumferential wall of the piston chamber. The throttling section includes multiple first wall segments spaced circumferentially along the piston chamber, with each segment tending to extend towards the center of the cylinder. The inner wall of the piston chamber can form a undulating wall surface through the throttling section, i.e., through the multiple first wall segments. The profile change of the inner wall surface reconstructs the gap distribution between the piston and the piston chamber, thereby forming a throttling barrier. When the eccentrically positioned piston rotates within the piston chamber, the throttling section of the piston chamber, i.e., the undulating wall surface composed of multiple first wall segments, forms a series of tiny throttling structures. When the piston passes through these areas during rotation, the originally relatively wide leakage gap is effectively narrowed or blocked by these throttling structures. When the piston rotation drives the working gas flow, the flow resistance increases sharply when the gas passes through the throttling section, forming a significant throttling effect, which greatly suppresses the backflow and leakage of high-pressure working gas to the low-pressure area.
[0023] The compressor provided by this invention includes the aforementioned cylinder structure, which can provide throttling resistance for high-pressure working gas, effectively improve leakage, reduce compressor power loss, and ensure performance. Attached Figure Description
[0024] Figure 1 This is a schematic diagram of the cylinder structure provided by the present invention;
[0025] Figure 2 The cylinder structure provided by the present invention is Figure 1 A magnified schematic diagram of the throttling section in the middle;
[0026] Figure 3 This is a partial schematic diagram of the throttling section of a cylinder structure provided in another embodiment of the present invention.
[0027] In the picture:
[0028] 1. Cylinder block; 11. Piston chamber; 111. First wall section; 112. Second wall section; 12. Blade groove; 13. Blade;
[0029] 2. Piston. Detailed Implementation
[0030] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.
[0031] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for 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 invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. The terms "first position" and "second position" refer to two different positions. Furthermore, "above," "on top of," and "over" the first feature in relation to the second feature includes the first feature directly above and diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "under," and "below" the first feature in relation to the second feature includes the first feature directly below and diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.
[0032] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" 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; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.
[0033] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.
[0034] This invention provides a cylinder structure. (Refer to...) Figures 1 to 3As shown, the cylinder structure includes a cylinder body 1 and a piston 2. The cylinder body 1 has a piston chamber 11, the inner circumferential wall of which includes a throttling section. The throttling section includes a first wall segment 111 and a second wall segment 112. Multiple first wall segments 111 are spaced apart circumferentially along the piston chamber 11, and the first wall segments 111 tend to extend towards the center of the cylinder body 1. The piston 2 is eccentrically disposed within the piston chamber 11. During rotation within the piston chamber 11, a gap always exists between the piston 2 and the first wall segment 111, and the throttling section provides throttling resistance to the working gas within the piston chamber 11.
[0035] In this embodiment, the inner circumferential wall of the piston cavity 11 is provided with a throttling section, which includes a first wall segment 111. Multiple first wall segments 111 are provided and spaced apart circumferentially along the piston cavity 11, and the first wall segments 111 tend to extend towards the center of the cylinder 1. The inner wall of the piston cavity 11 can form a undulating wall surface through the throttling section, i.e., through multiple first wall segments 111. The profile change of the inner wall surface of the piston cavity 11 reconstructs the gap distribution between the piston 2 and the piston cavity 11, thereby forming a throttling barrier. When the eccentrically positioned piston 2 rotates within the piston cavity 11, the throttling section of the piston cavity 11, i.e., the undulating wall surface composed of multiple first wall segments 111, forms a series of tiny throttling structures. When the piston 2 passes through these areas during rotation, the originally relatively spacious leakage gap is effectively narrowed or blocked by the aforementioned throttling structures. When piston 2 rotates and drives the working gas to flow, the flow resistance will increase sharply when the gas passes through the throttling part, forming a significant throttling effect, which will greatly suppress the backflow and leakage of high-pressure working gas to the low-pressure area.
[0036] It is worth mentioning that the center of cylinder 1 is the center of the main body of cylinder 1 located in the protruding part. Figure 1 Point O in the diagram is the center point of cylinder 1. If the piston chamber 11 of cylinder 1 is a perfect circle, then point O is also the center point of piston chamber 11.
[0037] Specific reference Figure 2 As shown, Figure 2 The thickened curve on the left side of the filling area represents the inner wall of the piston chamber 11, which is also the inner wall of the cylinder 1. The thickened curve on the right side of the filling area represents the edge trajectory of the piston 2 during rotation. The filling area corresponds to the leakage gap. By setting the first wall section 111 to form a throttling structure, the first wall section 111 can be close to the edge trajectory of the piston 2 during rotation, thereby effectively narrowing or blocking the originally relatively wide leakage gap.
[0038] In this embodiment, the throttling section further includes a second wall section 112, which connects two adjacent first wall sections 111. The second wall section 112 extends away from the center of the cylinder block 1 relative to the first wall sections 111. Specifically, by providing the second wall section 112, a smooth transition connection between two adjacent first wall sections 111 is achieved. The throttling section as a whole consists of a continuous undulating wall surface with alternating first wall sections 111 and second wall sections 112. This continuous undulating wall surface forms a reliable throttling structure. When the piston 2 passes through these areas during rotation, the alternating continuous undulating wall surface creates a significant throttling effect, further suppressing the backflow and leakage of high-pressure working gas to the low-pressure area.
[0039] In terms of specific shape, the first wall segment 111 protrudes outward relative to the inner wall of the piston cavity 11, towards the center of the cylinder body 1. The second wall segment 112 is concave inward relative to the first wall segment 111, away from the center of the cylinder body 1. It is worth mentioning that both the outward protrusion and the inward concavity are relative to the inner circumferential wall of the piston cavity 11, and the second wall segment 112 as a whole also protrudes outward relative to the theoretically circular inner wall of the piston cavity 11, although the degree of protrusion is not as obvious as that of the first wall segment 111.
[0040] In this embodiment, the distance between the extension vertex of the first wall segment 111 and the center of the cylinder 1 is h1, and the distance between the extension vertex of the second wall segment 112 and the center of the cylinder 1 is h2. Let Δh = h1 - h2, then Δh ranges from 3 μm to 50 μm. Specifically, Figures 2 to 3 In this diagram, point A is the extended vertex of the first wall segment 111, and point B is the extended vertex of the second wall segment 112. Δh is the difference between the distance between the extended vertex of the first wall segment 111 and the center of the cylinder block 1, and the distance between the extended vertex of the second wall segment 112 and the center of the cylinder block 1, with a range of 3μm-50μm. This configuration ensures that the leakage gap is effectively narrowed or blocked by the aforementioned throttling section, achieving a better leak-proof effect.
[0041] In this embodiment, there is an eccentric clearance between the piston 2 and the inner peripheral wall of the piston chamber 11. The side of the cylinder body 1 with the smallest eccentric clearance is designated as the eccentric clearance side, and the side of the cylinder body 1 opposite to the eccentric clearance side is designated as the reverse clearance side. The throttling section is located on the reverse clearance side. Specifically, since the piston 2 is forcibly adjusted to its minimum eccentric clearance during assembly, and the cylinder body 1 is located opposite the side with the smallest eccentric clearance (i.e., the reverse clearance side), the clearance between the piston 2 and the cylinder inner wall will passively expand to its maximum value. The expanded clearance side of the reverse clearance side becomes a new and significant leakage path. Therefore, by providing a throttling section on the reverse clearance side, effective throttling can be achieved specifically on the reverse clearance side, preventing leakage on the reverse clearance side, while minimizing changes to the shape of the inner wall of the piston chamber 11 in other locations, thus reducing processing difficulty.
[0042] In some alternative embodiments, both the eccentric clearance side and the reverse clearance side are provided with throttling sections, and the number of first wall segments 111 in the throttling section corresponding to the reverse clearance side is greater than the number of first wall segments 111 in the throttling section corresponding to the eccentric clearance side. This arrangement ensures that the inner circumference of the piston chamber 11 has a throttling and leak-proof effect, and the greater number of first wall segments 111 corresponding to the throttling section on the reverse clearance side, i.e., a more pronounced continuous undulating trend of the sidewall, enhances the throttling effect on the reverse clearance side and prevents leakage on the reverse clearance side.
[0043] In this embodiment, the cylinder body 1 has a vane groove 12 that communicates with the piston chamber 11. A vane 13 is slidably disposed on the vane groove 12, and the vane 13 divides the piston chamber 11 into an intake side and an exhaust side. A throttling section is disposed on the intake side. Specifically, since the eccentric clearance side corresponds to the exhaust side and the reverse clearance side corresponds to the intake side, the throttling section is disposed on the intake side to effectively throttle the intake side, prevent leakage on the intake side, and minimize changes to the shape of the inner wall of the piston chamber 11 in other positions, thus reducing the difficulty of machining.
[0044] In some alternative embodiments, both the intake and exhaust sides are provided with throttling sections, and the number of first wall segments 111 in the throttling section corresponding to the intake side is greater than the number of first wall segments 111 in the throttling section corresponding to the exhaust side. This arrangement ensures that the inner circumference of the piston chamber 11 has a throttling and leak-proof effect, and the greater number of first wall segments 111 corresponding to the intake side throttling section results in a more pronounced continuous undulating trend of the sidewalls, improving the throttling effect on the intake side and preventing intake side leakage.
[0045] As an optional implementation method, please refer to the following for details. Figure 2 As shown, both the first wall section 111 and the second wall section 112 are designed with an arc shape. This design allows for smooth, alternating, continuous undulations on the sidewalls of the piston chamber 11 in the throttling section, resulting in a simple structure that is easy to manufacture.
[0046] As an optional implementation method, please refer to the following for details. Figure 3 As shown, the first wall segment 111 and the second wall segment 112 are configured with a toothed structure, and the tips of the toothed structure are rounded. This configuration simplifies the processing steps and enables a seamless fit between straight and curved segments, ensuring a reliable throttling effect.
[0047] In this embodiment, during one revolution of the piston 2 within the piston cavity 11, a gap is always maintained between the piston 2 and the inner peripheral wall of the piston cavity 11. This arrangement avoids contact friction between the piston 2 and the inner peripheral wall of the piston cavity 11, ensuring reliable and stable rotation of the piston 2.
[0048] This embodiment also provides a compressor, which includes the cylinder structure described above, and a housing, with the cylinder structure disposed within the housing. The compressor, including the cylinder structure, can provide throttling resistance for high-pressure working gas, effectively improving leakage, reducing compressor power loss, and ensuring performance.
[0049] For example, compressors using this cylinder structure achieve improved overall energy efficiency (COP) and smoother operation over a wide range of operating conditions, especially at both ends of the inverter range. See the table below for details.
[0050]
[0051] As shown in the table above, the compressor provided in this embodiment exhibits a performance improvement of over 1% under various operating conditions, especially under low speed and high pressure ratio conditions, where traditional designs show significant performance degradation. In this embodiment, the continuously undulating wall surface composed of the first wall section 111 and the second wall section 112 forms a series of tiny throttling structures. By reconstructing the geometry of the inner circumferential wall of the piston chamber 11, a throttling barrier is formed. When the piston 2 rotates and drives the working gas to flow, the flow resistance increases sharply when the gas passes through the throttling section, resulting in a significant throttling effect. This greatly suppresses the backflow and leakage of high-pressure working gas to the low-pressure area, providing a new and effective technical path for the high efficiency and reliability of the compressor under variable frequency and wide operating conditions.
[0052] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.
Claims
1. A cylinder structure characterized by comprising: The application relates to a cylinder (1) with a piston cavity (11), wherein the inner circumferential wall of the piston cavity (11) comprises a throttling part, the throttling part comprises a plurality of first wall segments (111) which are arranged at intervals along the circumference of the piston cavity (11), and the first wall segments (111) have a tendency to extend towards the center of the cylinder (1). A piston (2) is arranged eccentrically in the piston cavity (11), and during rotation of the piston (2) in the piston cavity (11), the piston (2) is always in a gap with the first wall segments (111), and the first wall segments (111) are used to provide throttling resistance to working gas in the piston cavity (11). The throttling part further comprises second wall segments (112), and the second wall segments (112) are connected between adjacent two first wall segments (111) and have a tendency to extend away from the center of the cylinder (1) compared with the first wall segments (111).
2. The cylinder structure according to claim 1, characterized by The distance between the extension vertex of the first wall segment (111) and the center of the cylinder (1) is h1, and the distance between the extension vertex of the second wall segment (112) and the center of the cylinder (1) is h2.
3. The cylinder structure according to claim 2, characterized in that The difference between h1 and h2 is denoted as Delta h, and the range of Delta h is 3-50 mu m. The piston (2) and the inner circumferential wall of the piston cavity (11) have an eccentric gap, one side of the cylinder (1) corresponding to the minimum side of the eccentric gap is an eccentric gap side, and the side of the cylinder (1) away from the eccentric gap side is an opposite gap side, and the throttling part is arranged on the opposite gap side.
4. The cylinder structure according to claim 1, characterized by The piston (2) and the inner circumferential wall of the piston cavity (11) have an eccentric gap, one side of the cylinder (1) corresponding to the minimum side of the eccentric gap is an eccentric gap side, and the side of the cylinder (1) away from the eccentric gap side is an opposite gap side, and the throttling part is arranged on the opposite gap side.
5. The cylinder structure according to claim 1, characterized by The cylinder (1) is provided with a vane groove (12) which is connected with the piston cavity (11), the vane groove (12) is slidably provided with a vane (13), the vane (13) divides the piston cavity (11) into an air suction side and an air exhaust side, and the throttling part is arranged on the air suction side.
6. The cylinder structure according to claim 1, characterized by The cylinder (1) is provided with a vane groove (12) which is connected with the piston cavity (11), the vane groove (12) is slidably provided with a vane (13), the vane (13) divides the piston cavity (11) into an air suction side and an air exhaust side, and the throttling part is arranged on the air suction side.
7. The cylinder structure according to claim 1, characterized by The shapes of the first wall segments (111) and the second wall segments (112) are both circular arcs.
8. The cylinder structure according to claim 2, characterized by 9. The cylinder structure according to claim 2, characterized by The first wall segment (111) and the second wall segment (112) are arranged in a tooth-like structure, and the tooth-like structure is provided with a rounded transition at the tip.
10. A compressor characterized by, The cylinder structure according to any one of claims 1-9, further comprising a housing, wherein the cylinder structure is arranged in the housing.