Compressor seal structure and compressor

Abstract

The application provides a compressor sealing structure and a compressor, and the sealing structure comprises a crankshaft, a cylinder cover, a cylinder and a piston; the crankshaft comprises at least an eccentric part; the piston is sleeved on the eccentric part of the crankshaft, and the piston and the eccentric part of the crankshaft are arranged in the cylinder; one end of the eccentric part is provided with a thrust part and a sealing part outside the thrust part; the inner edge of the end surface of the sealing part is a circular arc in the projection on the plane perpendicular to the axis of the eccentric part, and the center axis of the circular arc coincides with the axis of the eccentric part. The eccentric part of the sealing structure of the application is provided with the sealing part, and the inner edge of the sealing part is coaxial with the eccentric part. During the operation of the compressor, the sealing part can better follow the movement of the eccentric part, so that the dynamic gap between the sealing structure and the piston is more uniform, the stability and reliability of the sealing performance at the place are improved, and the operation efficiency of the compressor is ensured. Meanwhile, the inner edge of the sealing part is coaxial with the eccentric part, which can reduce the area of the sealing part and thus reduce the friction loss.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a compressor sealing structure and a compressor. Background Technology

[0002] In the design of rotary compressors, to improve compressor efficiency, it is common practice to move the exhaust port on the cylinder head inwards towards the cylinder axis to reduce the corresponding bevel (DV port) on the cylinder, thereby reducing clearance volume and exhaust resistance losses. Furthermore, further demands for pump efficiency lead to increased crankshaft eccentricity and reduced cylinder volume (reduced cylinder height and diameter). Consequently, the piston wall thickness is further reduced. This results in insufficient sealing distance between the thin-walled piston and the exhaust port, causing leakage as the cylinder head exhaust port connects the piston's inner and outer cavities, ultimately reducing compressor efficiency.

[0003] The existing technology adopts a sealing structure concentric with the short shaft. This design has the following problems: when the sealing structure is concentric with the short shaft, the sealing structure deforms to different degrees under the action of force, which may result in uneven distribution of the gap between the piston and the sealing structure during operation, and unstable sealing performance between the piston and the sealing structure; the narrow areas at both ends of the sealing structure have redundant design, which means that the contact area between the cylinder head and the sealing structure increases, resulting in significant friction loss and reduced compressor efficiency; the crescent-shaped design of the sealing structure is prone to burrs at both ends, increasing the processing difficulty and manufacturing cost.

[0004] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of the present invention, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0005] To address the problems in the prior art, the present invention aims to provide a compressor sealing structure and a compressor. In this sealing structure, the inner edge of the sealing part located on the crankshaft eccentric part is coaxial with the eccentric part. During compressor operation, the sealing part can better follow the movement of the eccentric part, making the dynamic gap between the sealing structure and the piston more uniform, improving the stability and reliability of the sealing performance at this point, and ensuring the operating efficiency of the compressor.

[0006] A first aspect of the present invention provides a compressor sealing structure, including a crankshaft, a cylinder head, a cylinder, and a piston;

[0007] The crankshaft includes at least an eccentric portion;

[0008] The piston is sleeved on the eccentric part of the crankshaft, and the piston and the eccentric part of the crankshaft are disposed inside the cylinder;

[0009] One end of the eccentric part is provided with a thrust part and a sealing part on the outside of the thrust part;

[0010] The projection of the inner edge of the sealing part onto a plane perpendicular to the axis of the eccentric part is an arc, and the central axis of the arc coincides with the axis of the eccentric part.

[0011] According to a first aspect of the invention, the central angle of the arc is β, which satisfies: 45°≤β≤70°.

[0012] According to a first aspect of the invention, the cylinder head is provided with an exhaust port, the radius of the exhaust port is r, and the vertical distance between the center of the exhaust port and the axis of the eccentric portion is L;

[0013] The radius of the arc is r1;

[0014] The following condition must be met: Lr-r1≥0.5mm.

[0015] According to a first aspect of the invention, the height difference between the end face of the thrust portion on the axis of the eccentric portion and the height of the end face of the sealing portion on the axis of the eccentric portion is H, satisfying: 10μm≤H≤20μm.

[0016] According to a first aspect of the invention, the cylinder head is provided with an exhaust port;

[0017] The cylinder has a beveled cut on one end face that abuts against the cylinder head;

[0018] The projection of the vent hole onto a plane perpendicular to the axis of the eccentric portion at least partially coincides with the projection of the oblique cut onto a plane perpendicular to the axis of the eccentric portion.

[0019] According to a first aspect of the invention, the end face of the sealing portion and the end face of the piston form a continuous surface.

[0020] According to a first aspect of the invention, the cylinder head is an upper cylinder head or a lower cylinder head.

[0021] A second aspect of the present invention provides a compressor including the compressor exhaust sealing structure described in the first aspect.

[0022] The compressor sealing structure of the present invention has a sealing part provided on the crankshaft eccentric part, and the inner edge of the sealing part is coaxial with the eccentric part. During the operation of the compressor, the sealing part can better follow the movement of the eccentric part, making the dynamic gap between the sealing structure and the piston more uniform, improving the stability and reliability of the sealing performance at this point, and ensuring the operating efficiency of the compressor. At the same time, the coaxiality of the inner edge of the sealing part with the eccentric part can reduce the area of ​​the sealing part, thereby reducing friction loss and improving the compressor efficiency. Furthermore, after the sealing part is coaxial with the eccentric part, the entire sealing part is of equal width from one end to the other, avoiding the generation of burrs and improving the machining accuracy and sealing effect. Attached Figure Description

[0023] Other features, objects, and advantages of the invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0024] Figure 1 A partial cross-sectional view of a crankshaft according to an embodiment of the present invention;

[0025] Figure 2 This is a cross-sectional view of the cylinder portion of the compressor sealing mechanism according to an embodiment of the present invention. Detailed Implementation

[0026] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that the invention will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the invention, and should not be construed as limiting the invention. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.

[0027] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined as "first" and "second" may explicitly or implicitly include one or more features. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0028] 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, an electrical connection, or a connection that allows communication between them; 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 invention according to the specific circumstances.

[0029] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and settings are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples; such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or settings discussed. In addition, examples of various specific processes and materials are provided in this invention, but those skilled in the art will recognize the application of other processes and / or the use of other materials.

[0030] The compressor sealing structure and compressor of the present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments are not intended to limit the scope of protection of the present invention.

[0031] This invention provides a compressor sealing structure, including a crankshaft, cylinder head, cylinder, and piston. Figure 1 This is a partial cross-sectional view of a crankshaft according to an embodiment of the present invention. Typically, the crankshaft 1 includes a long shaft (not fully shown in the figure), an eccentric portion 11, and a short shaft 12 connected in sequence. The present invention focuses on the sealing between the eccentric portion of the crankshaft, the piston, and the cylinder head.

[0032] Figure 2 This is a cross-sectional view of the cylinder portion of a compressor sealing mechanism according to an embodiment of the present invention. The piston 3 is fitted onto the eccentric portion 11 of the crankshaft 1, and the piston 3 and the eccentric portion 11 of the crankshaft 1 are disposed within the cylinder 2. A cylinder head (not shown in the figure) is disposed on both end faces of the cylinder and encloses a compression space. This cylinder head can be either an upper cylinder head or a lower cylinder head. The area enclosed by the piston 3 and the eccentric portion 11 is the piston inner cavity; the area enclosed by the piston 3 and the cylinder 2 is the piston outer cavity.

[0033] The end face of the eccentric part 11 that mates with the cylinder head is provided with a thrust part 111 and a sealing part 112 on the outside of the thrust part 111. The thrust part 111 is used to make clearance fit with the cylinder head to prevent the crankshaft 1 from moving axially.

[0034] The projection of the inner edge 112A of the sealing part 112 onto a plane perpendicular to the axis of the eccentric part is an arc, and the central axis of the arc coincides with the axis of the eccentric part. That is, the sealing part 112 can be regarded as a fan ring with the same central axis as the eccentric part. The distance (radially) between the inner edge 112A and the outer edge 112B of the sealing part 112 is equal in width. This structure avoids the generation of burrs and improves the machining accuracy and sealing effect of the eccentric part.

[0035] The cylinder head is provided with an exhaust port, the projection of which on the end face of the crankshaft's sealing end is shown as K. The piston 3 is fitted around the outer periphery of the eccentric portion 11 of the crankshaft. The end face of the sealing portion 112 of the crankshaft 1 mates with the end face of the piston 3, and the end faces of the two at this point form a continuous surface. When the crankshaft 1 rotates, the continuous surface moves to the exhaust port, and this continuous surface covers the projection K of the exhaust port on the end face. That is, the end face of the sealing portion 112 of the crankshaft 1 serves as an extension of the sealing end face of the piston 3, jointly achieving the seal between the piston's inner cavity and outer cavity when the crankshaft rotates. Since the inner edge of the sealing portion 112 of this invention is coaxial with the eccentric portion, during compressor operation, the sealing portion can better follow the movement of the eccentric portion 11, making the dynamic gap between the sealing structure formed thereand the piston more uniform, better preventing the connection between the piston's inner cavity and outer cavity, which would lead to gas leakage in the cylinder, improving the stability and reliability of the sealing performance at this point, and ensuring the operating efficiency of the compressor.

[0036] Since the inner edge of the sealing portion 112 is coaxial with the eccentric portion, the sealing portion does not need to be machined to be slender. In some embodiments, the arc length of the sealing portion 112 can be reduced. Preferably, the central angle β of the arc of the sealing portion 112 satisfies: 45°≤β≤70°. Reducing the arc length of the sealing portion 112 can also effectively reduce the area at the sealing end. The reduced contact area between the cylinder head and the sealing end reduces friction loss and further improves compressor efficiency.

[0037] In a specific embodiment, the sealing portion of the eccentric part is used to mate with the exhaust port provided in the cylinder head. Therefore, the sealing portion of the eccentric part can be provided on the end face that mates with the upper cylinder head or on the end face that mates with the lower cylinder head. When the sealing portion of the eccentric part is provided on the end face that mates with the upper cylinder head, the compressor exhausts from the top; when the sealing portion of the eccentric part is provided on the end face that mates with the lower cylinder head, the compressor exhausts from the bottom.

[0038] The vertical distance from the inner edge 112A of the end face of the sealing part 112 to the axis of the eccentric part should be less than the minimum vertical distance from the exhaust hole to the axis of the eccentric part. For example, if the radius of the exhaust hole is r, the vertical distance between the center of the exhaust hole and the axis of the eccentric part is L; the radius of the arc of the inner edge 112A is r1; and the radial sealing distance d0 = Lr - r1, preferably, Lr - r1 ≥ 0.5 mm. This arrangement ensures that even when the piston wall thickness is reduced, the sealing end still has sufficient radial sealing distance to the exhaust hole after mating with the piston, improving the stability and reliability of the sealing performance at this location.

[0039] Furthermore, the end face of the cylinder that abuts against the cylinder head is provided with a bevel; the projection of the exhaust port onto a plane perpendicular to the axis of the eccentric portion at least partially coincides with the projection of the bevel onto a plane perpendicular to the axis of the eccentric portion.

[0040] In addition, the end face of the thrust portion 111 of the eccentric part 11 has a clearance fit with the cylinder head to prevent axial movement of the crankshaft 1. Since the sealing portion 112 is outside the thrust portion 111, the eccentric part 11 of the crankshaft 1 tilts under the action of gas force. Data shows that the maximum tilt deformation during normal compressor operation is a few micrometers. To prevent the end face of the sealing portion 112 from rubbing against the cylinder head, thereby increasing friction loss, the height difference H between the end face of the thrust portion 111 and the end face of the sealing portion 112 on the eccentric part's axis is: 10μm ≤ H ≤ 20μm, such as 15μm. During compressor operation, the pressure difference between the piston's inner and outer chambers accelerates leakage. By further reducing the height difference H between the end face of the thrust portion and the end face of the sealing portion on the eccentric part's axis, leakage loss can be reduced, sealing performance can be further improved, and thus the compressor's operating efficiency can be increased.

[0041] The present invention also provides a compressor, including a compressor exhaust sealing structure of the first aspect, wherein the compressor has higher operating efficiency due to the higher sealing performance at the cylinder.

[0042] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

[0043] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention. It should not be construed that the specific implementation of the present invention is limited to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of the present invention, and all such modifications and substitutions should be considered within the scope of protection of the present invention.

Claims

1. A compressor sealing structure, characterized in that, Including crankshaft, cylinder head, cylinder, and piston; The crankshaft includes at least an eccentric portion; The piston is sleeved on the eccentric part of the crankshaft, and the piston and the eccentric part of the crankshaft are disposed inside the cylinder; One end of the eccentric part is provided with a thrust part and a sealing part on the outside of the thrust part; The projection of the inner edge of the end face of the sealing part onto a plane perpendicular to the axis of the eccentric part is an arc. The central axis of the arc coincides with the axis of the eccentric part. The distance between the inner and outer edges of the sealing part is equal in the radial direction. During the operation of the compressor, the sealing part moves with the eccentric part, making the dynamic gap between the sealing part and the piston uniform.

2. The compressor sealing structure according to claim 1, characterized in that, The central angle of the arc is β, which satisfies: 45°≤β≤70°.

3. The compressor sealing structure according to claim 1, characterized in that, The cylinder head is provided with an exhaust port, the radius of which is r, and the vertical distance between the center of the exhaust port and the axis of the eccentric part is L; The radius of the arc is r1; The following condition must be met: Lr-r1≥0.5mm.

4. The compressor sealing structure according to claim 1, characterized in that, The height difference H between the height of the end face of the thrust portion on the axis of the eccentric portion and the height of the end face of the sealing portion on the axis of the eccentric portion satisfies: 10μm≤H≤20μm.

5. The compressor sealing structure according to claim 1, characterized in that, The cylinder head is provided with an exhaust port; The cylinder has a beveled cut on one end face that abuts against the cylinder head; The projection of the vent hole onto a plane perpendicular to the axis of the eccentric portion at least partially coincides with the projection of the oblique cut onto a plane perpendicular to the axis of the eccentric portion.

6. The compressor sealing structure according to claim 1, characterized in that, The end face of the sealing part and the end face of the piston form a continuous surface.

7. The compressor sealing structure according to claim 1, characterized in that, The cylinder head is either an upper cylinder head or a lower cylinder head.

8. A compressor, characterized in that, The compressor exhaust sealing structure includes any one of claims 1 to 7.

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