Air cylinder assembly for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses an air cylinder assembly for a compressor. The air cylinder assembly comprises an air cylinder, a piston and a sliding piece. The air cylinder is provided with a working cavity and a sliding piece groove which are communicated. The piston is arranged in the working cavity; a mounting hole is formed in the outer wall surface of the piston; the slip sheet comprises a slip sheet main body and a connector, the slip sheet main body is slidably arranged in the slip sheet groove, the connector is arranged at one end, facing the working cavity, of the slip sheet main body, the connector is arranged in the mounting hole, and the connector is matched with the mounting hole; the piston can move in the working cavity, when the piston is located at an upper dead center or a lower dead center in the working cavity, the distance between the end, facing the piston, of the sliding piece body and the hole center of the mounting hole in the radial direction of the air cylinder is a first distance, and the distance between the hole opening edge of the mounting hole and the hole center of the mounting hole in the radial direction of the air cylinder is a second distance. The first distance is greater than the second distance. In this way, interference between the piston and the sliding piece in the moving process can be effectively avoided. The utility model further discloses the compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, specifically to cylinder assemblies for compressors and compressors. Background Technology

[0002] Currently, rotary compressors are widely used in refrigeration and air conditioning systems. In rotary compressors, the vanes are typically kept in close contact with the cylinder by springs, achieving good sealing and efficient compression. However, under low-frequency operating conditions, due to the low suction temperature, the vanes and piston are prone to running with liquid during compression. This worsens lubrication and prevents the vanes from constantly following the piston's movement, leading to connection between the compressor's suction and discharge sides. This reduces the compressor's effective suction volume and ultimately decreases its compression capacity.

[0003] Related technology discloses a compression cylinder, which includes a cylinder, a rolling piston, and a sliding vane. The cylinder includes a working chamber, in which an eccentrically mounted rolling piston is disposed. An arcuate groove is formed on the outer peripheral wall of the rolling piston to accommodate the connector of the sliding vane. The sliding vane can move radially along the cylinder, and the connector of the sliding vane matches the arcuate groove. The arcuate groove and the connector of the sliding vane are always in surface contact, reducing the possibility of leakage from the exhaust side to the intake side, thus greatly improving the operating efficiency of the compressor.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, although the sliding vane can always follow the piston by being accommodated in the arc groove of the rolling piston through the connecting head of the sliding vane, interference may occur between the sliding vane and the rolling piston during compressor operation. The design of this structure needs to avoid the phenomenon of operational interference between the sliding vane and the piston.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Utility Model Content

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a cylinder assembly and compressor for a compressor, which reduces or avoids interference between the piston and the vane during compressor operation.

[0009] According to a first aspect of the present invention, a cylinder assembly for a compressor is provided, including a cylinder, a piston, and a vane. The cylinder has a communicating working chamber and a vane groove. The piston is disposed in the working chamber, and the outer wall surface of the piston has a mounting hole. The vane includes a vane body and a connector. The vane body is slidably disposed in the vane groove, and the connector is disposed at one end of the vane body facing the working chamber. The connector is disposed in the mounting hole and is adapted to the mounting hole. The piston is capable of moving within the working chamber. When the piston is located at the top dead center or bottom dead center within the working chamber, the radial distance between the end of the vane body facing the piston and the center of the mounting hole along the cylinder is a first distance, and the radial distance between the edge of the mounting hole and the center of the mounting hole along the cylinder is a second distance. The first distance is greater than the second distance.

[0010] Optionally, the slide further includes: a transition section connected between the connector and the slide body, wherein the width of the transition section is smaller than the width of the connector and smaller than the width of the slide body; wherein, when the piston is located at the top dead center or bottom dead center in the working chamber, the distance between the edge of the mounting hole and the outer surface of the transition section is greater than 0.

[0011] Optionally, the mounting hole includes a connected arc segment and a straight groove segment. The straight groove segment is located at one end of the arc segment facing the outer wall of the piston, and the edge of the straight groove segment is the edge of the mounting hole opening. The cross-sectional area of ​​the arc segment along the piston axis is larger than the cross-sectional area of ​​the straight groove segment along the piston axis. The connector of the slide corresponds to the arc segment, and the transition section of the slide corresponds to the straight groove segment.

[0012] Optionally, along the axial direction of the cylinder, the cross-sectional shape of the connector is a first circular arc, and the cross-sectional shape of the mounting hole is a second circular arc. The centers of the first and second circular arcs coincide. The half-groove width d of the straight groove section, the width t of the transition section, the eccentricity e of the piston, the radial distance L between the center of the second circular arc and the center of the piston along the cylinder, the radial length h of the straight groove section along the piston, and the radius r of the second circular arc satisfy the following formula:

[0013]

[0014] Optionally, along the axial direction of the cylinder, the cross-sectional shape of the connector is a first circular arc, and the half-groove width of the straight groove section is smaller than the radius of the first circular arc.

[0015] Optionally, the width of the transition section is greater than half the width of the slider body.

[0016] Optionally, the end of the slide body facing the piston is provided with a relief slope, and the angle between the relief slope and the width direction of the slide is greater than 0° and less than or equal to 60°.

[0017] Optionally, the opening of the mounting hole is chamfered, and the chamfer is at the same angle as the relief slope of the slide body.

[0018] Optionally, a clearance is provided between the connector and the inner wall of the mounting hole to allow the connector to rotate relative to the mounting hole, thereby allowing the piston to swing relative to the slide plate; wherein the clearance between the connector and the inner wall of the mounting hole is greater than or equal to 0.03 mm and less than or equal to 0.06 mm.

[0019] According to a second aspect of the present invention, a compressor is provided, including a cylinder assembly for a compressor as described in the above-disclosed embodiments.

[0020] The cylinder assembly and compressor for a compressor provided in this disclosure can achieve the following technical effects:

[0021] By limiting the relative position between the slide body and the edge of the mounting hole when the piston is at top dead center or bottom dead center, the radial distance (first distance) between the end of the slide body facing the piston and the center of the mounting hole is made greater than the radial distance (second distance) between the edge of the mounting hole and the center of the mounting hole. This ensures that at the extreme position of the piston's maximum swing angle (top dead center or bottom dead center), the clearance between the slide and the piston is sufficiently large, effectively preventing interference such as collision or jamming between the piston and the slide during piston movement. Simultaneously, the connector fits the mounting hole, allowing for a stable connection and a certain degree of rotational freedom within the mounting hole. This allows the slide to flexibly follow the piston's movement, maintaining good sealing between the slide and the piston under various operating conditions.

[0022] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0023] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0024] Figure 1 This is a schematic diagram of a cylinder assembly for a compressor provided in an embodiment of this disclosure;

[0025] Figure 2 yes Figure 1 An enlarged schematic diagram of part A shown;

[0026] Figure 3 This is a schematic diagram of the structure of a slider provided in an embodiment of this disclosure;

[0027] Figure 4This is a schematic diagram of a sliding vane and piston assembly provided in an embodiment of this disclosure;

[0028] Figure 5 This is a schematic diagram of the structure of a piston provided in an embodiment of this disclosure;

[0029] Figure 6 yes Figure 5 An enlarged schematic diagram of part B is shown below;

[0030] Figure 7 This is a schematic diagram of another piston provided in an embodiment of this disclosure;

[0031] Figure 8 This is a schematic diagram of a cylinder assembly and crankshaft assembly provided in an embodiment of the present disclosure;

[0032] Figure 9 This is a schematic diagram of another cylinder assembly and crankshaft assembly provided in an embodiment of this disclosure;

[0033] Figure 10 yes Figure 9 A schematic cross-sectional view along the CC direction is shown.

[0034] Figure 11 yes Figure 10 An enlarged schematic diagram of part D is shown.

[0035] Figure label:

[0036] 10: Cylinder assembly;

[0037] 20: Cylinder; 21: Working chamber; 22: Sliding vane groove;

[0038] 30: Piston; 31: Outer wall surface; 32: Mounting hole; 321: Hole edge; 322: Arc segment; 323: Straight groove segment; 324: Second arc; 325: Chamfer; 326: Fit clearance; 327: Center of the second arc; 33: First piston body; 331: First slot; 34: Second piston body; 341: Second slot; 35: Center of the piston;

[0039] 40: Slider; 41: Slider body; 411: Yielding slope; 42: Connector; 421: First arc; 43: Transition section;

[0040] 50: Crankshaft. Detailed Implementation

[0041] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0042] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0043] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0044] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0045] Unless otherwise stated, the term "multiple" means two or more.

[0046] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0047] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0048] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0049] Combination Figures 1-11 As shown, this disclosure provides a cylinder assembly 10 for a compressor, including a cylinder 20, a piston 30, and a vane 40.

[0050] The cylinder 20 is provided with a working chamber 21 and a sliding vane groove 22 that are connected to each other; the piston 30 is provided in the working chamber 21, and the outer wall surface 31 of the piston 30 is provided with a mounting hole 32; the sliding vane 40 includes a sliding vane body 41 and a connector 42. The sliding vane body 41 is slidably provided in the sliding vane groove 22, and the connector 42 is provided at one end of the sliding vane body 41 facing the working chamber 21. The connector 42 is provided in the mounting hole 32 and is adapted to the mounting hole 32; wherein, the piston 30 can move in the working chamber 21. When the piston 30 is located at the top dead center or bottom dead center in the working chamber 21, the radial distance between the end of the sliding vane body 41 facing the piston 30 and the center of the mounting hole 32 along the cylinder 20 is the first distance, and the radial distance between the edge 321 of the mounting hole 32 and the center of the mounting hole 32 along the cylinder 20 is the second distance. The first distance is greater than the second distance.

[0051] When the compressor is running, the piston 30 swings within the working chamber 21 of the cylinder 20. For example... Figure 1 As shown, when the piston 30 moves to 90° within the working chamber 21, it is at the top dead center (TDC) within the working chamber 21. When the piston 30 moves to 270° within the working chamber 21, it is at the bottom dead center (BDC) within the working chamber 21. When the piston 30 is at TDC or BDC, the swing angle of the piston 30 relative to the slider 40 is at its maximum. At this point, the edge 321 of the mounting hole 32 of the piston 30 and the slider 40 are at the limit point where interference occurs. To ensure that the piston 30 does not interfere with the slider 40 when it is at TDC or BDC, the piston 30 will not interfere with the slider 40 throughout its entire swing stroke.

[0052] The radial direction of cylinder 20 is as follows Figure 8 As shown in the x1 axis direction.

[0053] The connector 42 of the slide vane 40 is embedded in the mounting hole 32 of the piston 30. The end of the slide vane body 41 faces the piston 30, and the slide vane body 41 moves along the slide vane groove 22 of the cylinder 20 outside the piston 30. When the piston 30 is at the top dead center or bottom dead center in the working chamber 21, the radial distance between the end of the slide vane body 41 facing the piston 30 and the center of the mounting hole 32 along the cylinder 20 is the first distance, and the radial distance between the edge 321 of the mounting hole 32 and the center of the mounting hole 32 along the cylinder 20 is the second distance. The first distance is as follows: Figure 2 As shown in H, the second distance is as followsFigure 2 As shown in Figure X. When the first distance is greater than the second distance, a gap is formed between the end of the slider body 41 facing the piston 30 and the edge 321 of the mounting hole 32, thereby preventing the slider body 41 from contacting or colliding with the edge 321 of the mounting hole 32 of the piston 30 during movement, thus avoiding interference.

[0054] The cylinder assembly 10 for a compressor provided in this disclosure defines the relative position between the vane body 41 and the edge 321 of the mounting hole 32 when the piston 30 is at top dead center or bottom dead center. This ensures that the radial distance (first distance) between the end of the vane body 41 facing the piston 30 and the center of the mounting hole 32 along the cylinder 20 is greater than the radial distance (second distance) between the edge 321 of the mounting hole 32 and the center of the mounting hole 32 along the cylinder 20. This results in a sufficiently large gap between the vane 40 and the piston 30 at the maximum swing angle limit position (top dead center or bottom dead center), effectively preventing interference phenomena such as collision or jamming between the piston 30 and the vane 40 during movement. Simultaneously, the connector 42 is adapted to the mounting hole 32, enabling a stable connection between them and allowing the connector 42 a certain degree of rotational freedom within the mounting hole 32. In this way, the sliding vane 40 can flexibly follow the movement of the piston 30, so that the sliding vane 40 can maintain good sealing with the piston 30 under different working conditions.

[0055] Optionally, combined Figure 1 and Figure 2 As shown, connector 42 is hinged to mounting hole 32.

[0056] The connector 42 is hinged to the mounting hole 32, ensuring that the connector 42 of the vane 40 is always fitted within the mounting hole 32, while also allowing the piston 30 to swing relative to the vane 40. This reduces the risk of the vane 40 detaching from the rollers when the compressor is running at high speed. The vane 40 and piston 30 form direct surface contact through the hinge, eliminating the need for a spring to provide elasticity and simplifying the structure of the cylinder assembly 10.

[0057] Optionally, combined Figure 2 and Figure 3 As shown, the slide 40 also includes a transition section 43, which connects the connector 42 and the slide body 41. The width of the transition section 43 is smaller than the width of the connector 42 and smaller than the width of the slide body 41. When the piston 30 is located at the top dead center or bottom dead center in the working chamber 21, the distance between the edge 321 of the mounting hole 32 and the outer surface of the transition section 43 is greater than 0.

[0058] The width of the transition section 43 is smaller than the width of the connector 42, and also smaller than the width of the slide body 41. This creates a width difference between the transition section 43 and the connector 42 and the slide body 41, allowing for clearance between the slide 40 and the piston 30. The relatively large connector 42 can be stably embedded in the mounting hole 32, achieving an effective limiting function and ensuring a reliable connection between the slide 40 and the piston 30. The mounting hole 32 has opening edges 321 on both sides. The size of the transition section 43 is smaller than the opening size of the mounting hole 32, preventing interference with the opening edges 321 of the mounting hole 32 during movement. During the piston 30's swing, the transition section 43 can move flexibly within the mounting hole 32 without colliding or getting stuck with the hole wall due to its excessive size, ensuring smooth movement of the slide 40 and the piston 30. The connector 42 is cylindrical and extends axially along the piston 30. The width of the transition section 43 is smaller than the width of the connector 42, that is, the width of the transition section 43 is smaller than the diameter of the connector 42.

[0059] The distance between the edge 321 of the mounting hole 32 and the outer surface of the transition section 43 is as follows: Figure 2 As shown in Figure S, when the piston 30 is at top dead center or bottom dead center within the working chamber 21, the distance between the edge 321 of the mounting hole 32 and the outer surface of the transition section 43 is greater than 0. This design provides sufficient space for the relative movement between the piston 30 and the slide 40. This avoids direct contact and collision between the slide body 41 and the edge 321 of the mounting hole 32 when the piston 30 is in its extreme position, thereby reducing the risk of interference between the slide 40 and the piston 30. Since the piston 30 swings at its maximum angle at the top dead center or bottom dead center, the distance S between the edge 321 of the mounting hole 32 and the outer surface of the transition section 43 is greater than 0 at these extreme positions. Therefore, when the piston 30 is in other positions within the working chamber 21, the distance between the edge 321 of the mounting hole 32 and the outer surface of the transition section 43 is always greater than 0. This cylinder assembly 10 structural design fully ensures the smooth movement of the piston 30 and the slide 40.

[0060] Optionally, combined Figure 2 and Figure 5 As shown, the mounting hole 32 includes a connected arc segment 322 and a straight groove segment 323. The straight groove segment 323 is located at one end of the arc segment 322 facing the outer wall surface 31 of the piston 30, and the edge of the straight groove segment 323 is the edge 321 of the opening of the mounting hole 32. The cross-sectional area of ​​the arc segment 322 along the axial direction of the piston 30 is greater than the cross-sectional area of ​​the straight groove segment 323 along the axial direction of the piston 30. The connector 42 of the slide 40 corresponds to the arc segment 322, and the transition section 43 of the slide 40 corresponds to the straight groove segment 323.

[0061] Piston axial directionFigure 5 The direction of the z2 axis is shown.

[0062] The mounting hole 32 includes a connected arc segment 322 and a straight groove segment 323. The arc segment 322 corresponds to the connector 42 of the slide 40, and the straight groove segment 323 corresponds to the transition segment 43 of the slide 40. The cross-sectional area of ​​the arc segment 322 along the piston 30 axis is larger than that of the straight groove segment 323. Correspondingly, the cross-sectional area of ​​the connector 42 along the piston 30 axis is larger than that of the transition segment 43 along the piston 30 axis. This allows the connector 42 of the slide 40 to be better supported and positioned within the arc segment 322, enabling a hinged fit between the connector 42 and the mounting hole 32.

[0063] Optionally, combined Figure 1 , Figure 2 and Figure 8 As shown, along the axial direction of the cylinder 20, the cross-sectional shape of the connector 42 is a first circular arc 421, and the cross-sectional shape of the mounting hole 32 is a second circular arc 324. The center 327 of the first circular arc 421 coincides with the center of the second circular arc. The half-groove width d of the straight groove section 323, the width t of the transition section 43, the eccentricity e of the piston 30, the radial distance L between the center 327 of the second circular arc and the center 35 of the piston along the cylinder 20, the radial length h of the straight groove section 323 along the piston 30, and the radius r of the second circular arc 324 satisfy the following formula:

[0064]

[0065] The radial direction of cylinder 20 is as follows Figure 8 As shown in the z1 axis direction. The axial direction of the piston is the same as that of the cylinder. Along the axial direction of the cylinder 20, the cross-section of the connecting end and the mounting hole 32 are both designed with arcs and coincident centers, so that the connector 42 can better adapt to the shape of the mounting hole 32, improve the accuracy of assembly, and also form a tighter seal between the piston 30 and the sliding plate 40.

[0066] Since top dead center (TDC) and bottom dead center (BDC) are two symmetrical positions, this application uses the relationship between various parameters when the piston is at TDC as an example for explanation. Referring to the figure, the explanation is based on the piston reaching the TDC position at 90°. At this time, the gap S between the side wall of the piston mounting port and the transition section of the sliding vane is greater than 0. The gap S between the side wall of the piston mounting port and the transition section of the sliding vane is equal to the auxiliary line segment in the figure. The difference. S > 0, that is... The calculation can be performed by referring to the auxiliary lines in the diagram. l3 = h × cosβ, Where angles α, β, and γ are as follows: Figure 2 The auxiliary angle shown.

[0067] Therefore, the radius r of the second arc, the length h of the straight groove section along the piston radial direction, and the width t of the transition section along the piston circumference satisfy the following formula:

[0068]

[0069] The radial direction of the piston is as follows Figure 5 As shown by the direction of the x2 axis, the circumferential direction of the piston is as follows. Figure 5 The direction of the y2 axis is shown. When the piston moves to the 90° or 270° position within the working chamber 21, the schematic line segment representing the eccentricity e of the piston 30 is exactly perpendicular to the schematic line segment representing the distance L between the center 327 of the second arc and the center 35 of the piston along the radial direction of the cylinder 20. Combining this with the trigonometric function relationships between the schematic line segments representing the half-width d of the straight groove section 323 along the circumference of the piston 30, the width t of the transition section 43 along the circumference of the piston 30, the length h of the straight groove section 323 along the radial direction of the piston 30, and the radius r of the second arc 324, we can conclude that:

[0070]

[0071] Thus, the formula is derived:

[0072]

[0073] The above formula provides a verification method for detecting whether the relationship between the sliding vane 40 and the piston 30 meets production requirements. When the parameters satisfy the above formula relationship, it ensures that the piston 30 does not interfere with the transition section 43 of the sliding vane 40 during the oscillation process. The left side of the formula involves multiple parameters, including the half-width d of the straight groove section 323 along the circumference of the piston 30, the width t of the transition section 43 along the circumference of the piston 30, the eccentricity e of the piston 30, the distance L between the center 327 of the second arc and the center 35 of the piston along the radial direction of the cylinder 20, and the length h of the straight groove section 323 along the radial direction of the piston 30. The right side of the formula involves multiple parameters, including the radius r of the second arc 324, the half-width d of the straight groove section 323 along the circumference of the piston 30, the eccentricity e of the piston 30, and the distance L between the center 327 of the second arc and the center 35 of the piston along the radial direction of the cylinder 20. Based on the above derivation, it can be seen that by ensuring the left side of the formula is greater than the right side, the gap S between the side wall of the piston 30 mounting port and the transition section 43 of the vane 40 is greater than 0. This ensures that the transition section 43 will not interfere with the straight groove section 323 during the movement of the piston 30 and the vane 40. Thus, under complex operating conditions such as piston 30 oscillation, the transition section 43 can move smoothly within the straight groove section 323 without jamming or collision, thereby ensuring the normal operation of the compressor. Simultaneously, the precise fit between the eccentricity e of the piston 30 and the center 327 of the second arc and the radial distance L of the piston center 35 along the cylinder 20 prevents the piston 30 from colliding with the inner wall of the cylinder 20 or other components due to excessive offset during movement, improving the stability of the piston 30's movement.

[0074] Optionally, combined Figure 2 As shown, along the axial direction of the cylinder 20, the cross-sectional shape of the connector 42 is a first circular arc 421, and the half-groove width of the straight groove section 323 is smaller than the radius of the first circular arc 421.

[0075] The half-groove width of the straight groove section 323 is smaller than the radius of the first arc 421, meaning the groove width of the straight groove section 323 is smaller than the diameter of the first arc 421. This allows the straight groove section 323 of the mounting hole 32 to limit the movement of the connector 42. Because the groove width of the straight groove section 323 is small, it restricts the connector 42 of the slide plate 40 to rotate only within the arc section 322 of the mounting hole 32, preventing the connector 42 from moving radially outward along the piston 30, thereby preventing the connector 42 from disengaging from the mounting hole 32.

[0076] Optionally, combined Figure 3 As shown, the width of the transition section 43 is greater than half the width of the slider body 41.

[0077] The width of the transition section 43 is smaller than the width of the slide body 41, while the width of the transition section 43 is greater than half the width of the slide body 41, which enhances the structural strength of the transition section 43. This allows the transition section 43 to both accommodate the piston 30 and securely connect the slide body 41 and the connector 42, improving the connection strength between the slide body 41 and the connector 42 and providing strong support for the connector 42. This improves the stability of the slide 40 under gas pressure and inertial forces, reduces the risk of deformation and damage to the slide 40, and thus extends its service life.

[0078] Optionally, combined Figure 3 As shown, the end of the slide body 41 facing the piston 30 is provided with a relief slope 411, and the angle between the relief slope 411 and the width direction of the slide 40 is greater than 0° and less than or equal to 60°.

[0079] The angle between the inclined plane 411 and the slider 40 in the width direction is as follows: Figure 3 As shown by angle θ.

[0080] When the angle between the clearance ramp 411 and the width direction of the slide 40 is greater than 0°, the clearance ramp 411 can be formed at the end of the slide body 41 facing the piston 30. The clearance ramp 411 slopes from the middle of the slide body 41 to the side along the direction from the piston 30 towards the slide body 41. By providing the clearance ramp 411 at the end of the slide body 41 facing the piston 30, the slide 40 can avoid the piston 30 during movement, preventing interference between the slide body 41 and the piston 30, thereby allowing the slide 40 to flexibly follow the movement trajectory of the piston 30.

[0081] When the angle between the clearance ramp 411 and the width direction of the slide 40 is less than or equal to 60°, the excessive inclination angle of the clearance ramp 411 can be avoided, thus ensuring that the slide body 41 has sufficient structural strength and preventing excessive deformation or damage to the slide 40 under gas pressure and inertial force. The clearance ramp 411 is located at the end of the slide body 41 facing the piston 30. The angle between the clearance ramp 411 and the width direction of the slide 40 is less than or equal to 60°, which also prevents excessive inclination angles from causing excessive gaps between the slide body 41 and the outer wall surface 31 of the piston 30, thereby enhancing the sealing performance between the slide 40 and the piston 30.

[0082] This embodiment of the invention specifies that the angle between the clearance ramp 411 and the width direction of the slide vane 40 is greater than 0° and less than or equal to 60°. This ensures that the slide vane 40 maintains good contact and sealing performance with the piston 30 during movement, while reducing friction and wear between the slide vane 40 and the piston 30. This not only improves the service life of the slide vane 40 but also enhances the operating efficiency of the compressor.

[0083] On both sides of the vane body 41 facing the piston 30, clearance ramps 411 are formed along the width direction of the vane 40. This allows the vane body 41 to more flexibly avoid the piston 30 during movement, effectively preventing interference between the vane body 41 and the piston 30. The clearance ramps 411 on both sides also improve the contact effect between the vane 40 and the piston 30, improving the sealing performance of the compressor.

[0084] Optionally, combined Figure 5 and Figure 6 As shown, the opening of the mounting hole 32 is provided with a chamfer 325, and the chamfer 325 has the same inclination angle as the relief slope 411 of the slide body 41.

[0085] The sliding vane body 41 has a relief slope 411 at the end facing the piston 30. The mounting hole 32 of the piston 30 has a chamfer 325 structure corresponding to the relief slope 411. This reduces the impact between the sliding vane 40 and the piston 30 during installation and movement, thus reducing wear. Simultaneously, the chamfer 325 further reduces the impact between the sliding vane 40 and the piston 30 during installation and movement, reducing wear. Furthermore, the cooperation between the chamfer 325 and the relief slope 411 allows the sliding vane 40 to fit more tightly against the outer wall surface 31 of the piston 30 during movement, thereby enhancing sealing performance and improving the compressor's compression efficiency. The chamfer 325 on both sides of the mounting hole 32 further prevents interference between the sliding vane 40 and the piston 30, enhancing the compressor's sealing performance.

[0086] Optionally, combined Figure 2 As shown, a fitting clearance 326 is provided between the connector 42 and the inner wall surface of the mounting hole 32, so that the connector 42 can rotate relative to the mounting hole 32, thereby allowing the piston 30 to swing relative to the slide plate 40; wherein, the fitting clearance 326 between the connector 42 and the inner wall surface of the mounting hole 32 is greater than or equal to 0.03mm and less than or equal to 0.06mm.

[0087] During compressor operation, the piston 30 oscillates around the connector 42 of the vane 40, reducing the piston 30's rotation and avoiding excessive energy consumption. A clearance 326 is provided between the connector 42 and the inner wall of the mounting hole 32, providing space for lubricating oil flow, which helps lubricate the piston 30 and the vane 40, reducing frictional losses and extending the compressor's service life. Simultaneously, the clearance 326 also provides space for the connector 42's rotational freedom. Since the connector 42 of the vane 40 in this embodiment is embedded in the mounting hole 32 of the piston 30, both ends of the connector 42 along the piston 30's axial direction are limited, preventing the vane 40 from disengaging from the piston 30. Therefore, the clearance 326 between the connector 42 and the inner wall of the mounting hole 32 can be appropriately increased to achieve better lubrication while preventing the vane 40 from disengaging. It is understood that a clearance is also provided between the transition section 43 and the straight groove section 323 of the mounting hole 32, providing movement and lubrication space for the transition section 43.

[0088] When the clearance 326 between the connector 42 and the inner wall of the mounting hole 32 is greater than or equal to 0.03 mm, sufficient flow space is provided for the lubricating oil, improving the lubrication effect between the connector 42 and the inner wall of the mounting hole 32. The lubricating oil can form an effective lubricating film between the connector 42 and the inner wall of the mounting hole 32, thereby reducing the coefficient of friction and minimizing heat and wear caused by friction. The connector 42 can rotate within the mounting hole 32, allowing the piston 30 to swing relative to the vane 40 within a certain range. This allows the piston 30 to better adapt to the movement trajectory of the vane 40, reducing the piston 30's rotation and avoiding excessive energy consumption due to excessive piston rotation, thus improving the compressor's operating efficiency.

[0089] When the fitting clearance 326 between the connector 42 and the inner wall of the mounting hole 32 is less than or equal to 0.06mm, it can prevent the slide vane 40 from shaking excessively or disengaging from the piston 30 during operation due to excessive fitting clearance 326, thereby improving the connection stability between the slide vane 40 and the piston 30 and thus enhancing the reliability of the compressor when it is running at high speed.

[0090] This embodiment of the invention specifies that the fit clearance 326 between the connector 42 and the inner wall surface of the mounting hole 32 is greater than or equal to 0.03 mm and less than or equal to 0.06 mm. Within this fit clearance 326 range, the connection stability, lubrication, and movement flexibility between the sliding vane 40 and the piston 30 can be effectively balanced, thereby improving the operating stability and reliability of the compressor. It can be understood that the fit clearance 326 between the connector 42 and the inner wall surface of the mounting hole 32 can be 0.03 mm, 0.04 mm, 0.05 mm, or 0.06 mm.

[0091] Optionally, combined Figure 4 and Figure 7 As shown, the piston 30 includes a first piston body 30 and a second piston body 30, which are separately arranged and opposite to each other along the piston 30 axis. The first piston body 30 is provided with a first slot 331, and the second piston body 30 is provided with a second slot 341. The first piston body 30 and the second piston body 30 abut against each other, and the first slot 331 and the second slot 341 together form a mounting hole 32. The connecting end of the slide plate 40 is respectively embedded in the first slot 331 and the second slot 341 so that the slide plate 40 is connected to the piston 30.

[0092] The split design of piston 30 along its own axial direction allows one end of connector 42 of vane 40 to pre-position with the first slot 331. When the first piston 30 body and the second piston 30 body are engaged and abutted, the other end of connector 42 naturally embeds into the second slot 341, thereby achieving overall positioning. This split assembly method reduces the assembly precision requirements of vane 40 and piston 30, making their assembly more convenient and effectively reducing the assembly difficulty. Mounting hole 32 is formed by the first slot 331 of the first piston 30 body and the second slot 341 of the second piston 30 body, creating a surface contact between vane 40 and piston 30, providing stable support and positioning for connector 42 of vane 40. This effectively improves the connection stability between vane 40 and piston 30, thereby reducing the risk of vane 40 detaching from piston 30 during high-speed compressor operation.

[0093] Optionally, combined Figure 4 and Figure 7 As shown, the first piston 30 body and the second piston 30 body are symmetrically arranged along the axial direction of the piston 30, and the sliding plate 40 is symmetrically arranged along the axial direction of the piston 30.

[0094] The first piston 30 and the second piston 30 are symmetrically arranged along the axial direction of the piston 30, meaning that the overall structure of both pistons 30 and the second piston 30 is symmetrically arranged along the axial direction of the piston 30. For example, the first slot 331 in the first piston 30 and the second slot 341 in the second piston 30 are symmetrically arranged along the axial direction of the piston 30. The slider 40 is symmetrically arranged along the axial direction of the piston 30, meaning that the connector 42, the transition section 43, and the slider body 41 are all symmetrically arranged along the axial direction of the piston 30.

[0095] This disclosure provides a compressor, including a cylinder assembly 10 for the compressor as described in any of the above-disclosed embodiments.

[0096] The compressor provided in this disclosure includes the cylinder assembly 10 as described in any of the above-disclosed embodiments, and therefore has all the beneficial effects of the cylinder assembly 10 as described in any of the above-disclosed embodiments, which will not be repeated here.

[0097] Optionally, combined Figures 8-11 As shown, the compressor also includes a crankshaft 50, and a piston 10 is sleeved on the outside of the crankshaft 50; when the piston 10 includes a first piston body 33 and a second piston body 34, the first piston body 33 and the second piston body 34 are sleeved on the outside of the crankshaft 50.

[0098] The crankshaft 50 limits the movement of the first piston body 33 and the second piston body 34, while the inner wall of the working chamber 21 also limits the fit between the first piston body 33 and the second piston body 34. Furthermore, the connector 42 of the sliding vane 40 is connected to the piston 10, so that the sliding vane 40 also limits the movement of the piston 10. Thus, through multiple limiting mechanisms, misalignment of the first piston body 33 and the second piston body 34 can be effectively prevented. It is understood that other connecting structures could also be used to secure the first piston body 33 and the second piston body 34.

[0099] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A cylinder assembly for a compressor, characterized by, The application relates to a cylinder assembly for a compressor. The cylinder assembly comprises: a cylinder provided with a working chamber and a sliding vane groove in communication; a piston arranged in the working chamber, an outer wall surface of the piston being provided with a mounting hole; a sliding vane comprising a sliding vane main body and a connecting head, the sliding vane main body being slidably arranged in the sliding vane groove, the connecting head being arranged at one end of the sliding vane main body facing the working chamber, the connecting head being arranged in the mounting hole and being matched with the mounting hole; 2. The cylinder assembly for a compressor of claim 1, wherein, wherein the piston is capable of moving in the working chamber, when the piston is at a top dead center or a bottom dead center in the working chamber, a distance between an end of the sliding vane main body facing the piston and a center of the mounting hole along a radial direction of the cylinder is a first distance, a distance between an edge of an opening of the mounting hole and the center of the mounting hole along the radial direction of the cylinder is a second distance, and the first distance is greater than the second distance. The sliding vane further comprises: a transition section connected between the connecting head and the sliding vane main body, a width of the transition section being smaller than a width of the connecting head and smaller than a width of the sliding vane main body; wherein, when the piston is at the top dead center or the bottom dead center in the working chamber, a distance between the edge of the opening of the mounting hole and an outer surface of the transition section is greater than 0.

3. The cylinder assembly for a compressor according to claim 2, wherein the mounting hole comprises a circular arc section and a straight groove section in communication, the straight groove section being arranged at one end of the outer wall surface of the cylinder facing the piston, an edge of the straight groove section being the edge of the opening of the mounting hole; wherein a cross-sectional area of the circular arc section along an axial direction of the piston is greater than a cross-sectional area of the straight groove section along the axial direction of the piston, the connecting head of the sliding vane corresponds to the circular arc section, and the transition section of the sliding vane corresponds to the straight groove section.

4. The cylinder assembly for a compressor according to claim 3, wherein in the axial direction of the cylinder, a cross-sectional shape of the connecting head is a first circular arc, a cross-sectional shape of the mounting hole is a second circular arc, a center of the first circular arc coincides with a center of the second circular arc, a half groove width d of the straight groove section, a width t of the transition section, an eccentricity e of the piston, a distance L between the center of the second circular arc and a center of the piston along a radial direction of the cylinder, a length h of the straight groove section along the radial direction of the piston, and a radius r of the second circular arc satisfy the following formula:

5. The cylinder assembly for a compressor according to claim 3, wherein in the axial direction of the cylinder, a cross-sectional shape of the connecting head is a first circular arc, and a half groove width of the straight groove section is smaller than a radius of the first circular arc.

6. The cylinder assembly for a compressor according to any one of claims 2 to 5, wherein the width of the transition section is greater than half of the width of the sliding vane main body.

7. The cylinder assembly for a compressor according to any one of claims 1 to 5, wherein an end of the sliding vane main body facing the piston is provided with a clearance inclined surface, and an angle between the clearance inclined surface and a width direction of the sliding vane is greater than 0° and less than or equal to 60°.

8. The cylinder assembly for a compressor according to claim 7, wherein a chamfer is arranged at the opening of the mounting hole, and an inclination angle of the chamfer is the same as that of the clearance inclined surface of the sliding vane main body.

9. The cylinder assembly for a compressor according to any one of claims 1 to 5, wherein a matching gap is arranged between the connecting head and an inner wall surface of the mounting hole, so that the connecting head is capable of rotating relative to the mounting hole, and the piston is capable of swinging relative to the sliding vane. In the connection head, the fitting gap between the connection head and the inner wall surface of the mounting hole is greater than or equal to 0.03 mm and less than or equal to 0.06 mm.

10. A compressor characterized by, A cylinder assembly for a compressor as claimed in any one of claims 1 to 9.

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