Compressor seal structure and compressor

Abstract

The utility model provides a kind of compressor sealing structure and compressor, the sealing structure includes crankshaft, cylinder cover, cylinder and piston;The crankshaft at least includes eccentric part, the crankshaft is provided with the central oil hole extending along the axial direction;The piston is sleeved in the eccentric part of the crankshaft, the piston and the eccentric part of the crankshaft are arranged in the space enclosed by the cylinder and the cylinder cover;One end surface of the eccentric part is provided with thrust portion and the protruding portion outside the thrust portion, recess is arranged between the thrust portion and the protruding portion, both ends of the recess extend to the side surface of the eccentric part;The eccentric part is provided with at least one oil passage, and the oil passage communicates the central oil hole and the recess.The utility model's crankshaft is provided with central oil hole, at least one oil passage connected with the recess between thrust portion and protruding portion is used to realize that central oil hole supplies lubricating oil to protruding portion, and reduce the friction loss of protruding portion and cylinder cover.

Description

Technical Field

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

[0002] In the structural design of rotary compressors, to improve efficiency, the exhaust port on the cylinder head is typically moved closer to the cylinder axis. This design increases the projected area of ​​the exhaust port within the cylinder while reducing the volume of the cylinder's oblique exhaust port (DV port), effectively reducing clearance volume and exhaust resistance losses, thus improving the overall performance of the compressor. However, if the exhaust port is moved excessively inward, it will connect the inner and outer cavities of the rotor piston during piston rotation, causing gas leakage and severely affecting the compressor's sealing performance. Therefore, the design must ensure a sufficient minimum sealing distance when the piston passes the cylinder head exhaust port to prevent gas leakage between the inner and outer cavities. However, the existence of this minimum sealing distance also limits the extent to which the exhaust port can be moved inward.

[0003] On the other hand, if the exhaust resistance is reduced by increasing the diameter of the exhaust port, the volume of the DV port needs to be increased accordingly. This will not only increase the clearance volume, but also reduce the effective flow area, which may weaken the efficiency advantage of the compressor.

[0004] In existing technologies, sealing structures, such as upper protrusions, are often added to the crankshaft to increase the minimum sealing distance, thereby allowing the exhaust port to move further inward. However, such crankshaft sealing structures also bring new technical challenges. Taking the upper protrusion as an example, the gap between it and the upper cylinder head usually needs to be controlled at the micrometer level, which makes it extremely prone to friction during operation. This not only affects the compressor's operating efficiency but may also reduce its operational reliability and service life.

[0005] Therefore, optimizing the location and structural design of the exhaust port while ensuring sufficient sealing distance, and taking into account the friction and reliability issues caused by crankshaft sealing, has become a key technical challenge that urgently needs to be solved in the design of rotary compressors.

[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 utility model, and therefore may include information that does not constitute prior art known to those skilled in the art. Utility Model Content

[0007] In view of the problems in the prior art, the purpose of this utility model is to provide a compressor sealing structure and a compressor, which has low friction loss and can improve the stability and efficiency of compressor operation.

[0008] The first aspect of this utility model provides a compressor sealing structure, including a crankshaft, a cylinder head, a cylinder, and a piston;

[0009] The crankshaft includes at least an eccentric portion, and the crankshaft is provided with a central oil hole extending along the axial direction;

[0010] The piston is sleeved on the eccentric part of the crankshaft, and the piston and the eccentric part of the crankshaft are arranged within the space enclosed by the cylinder and the cylinder head;

[0011] One end face of the eccentric part is provided with a thrust portion and a protrusion on the outer side of the thrust portion, and a groove is provided between the thrust portion and the protrusion, with both ends of the groove extending to the side of the eccentric part.

[0012] The eccentric portion is provided with at least one oil passage, which connects the central oil hole and the groove.

[0013] According to a first aspect of the present invention, the axis of the oil passage intersects the axis of the central oil hole.

[0014] According to a first aspect of the present invention, the angle between the axis of the oil passage and the axis of the crankshaft is α, and the angle α is between 20° and 90°.

[0015] According to a first aspect of the present invention, the projection of the axis of the oil passage onto a plane perpendicular to the axis of the crankshaft coincides with the centerline of the protrusion, and the centerline of the protrusion is the perpendicular bisector of the line connecting the two ends of the protrusion.

[0016] According to a first aspect of the present invention, the diameter of the oil passage is R, and the vertical height of the thrust portion is H, satisfying: R = (0.9 ± 0.05)H.

[0017] According to a first aspect of the present invention, the height of the intersection point of the axis of the oil passage and the side of the thrust portion is h, and the vertical height of the thrust portion is H, satisfying: h≤H / 2.

[0018] According to a first aspect of the present invention, the crankshaft is provided with a plurality of oil passages;

[0019] The axes of the plurality of oil passages are parallel to each other; or

[0020] The plurality of oil passages are evenly arranged along the circumference of the crankshaft.

[0021] According to a first aspect of the present invention, the crankshaft is provided with a plurality of oil passages, the plurality of oil passages being evenly arranged along the circumference of the crankshaft, and the included angle between any two adjacent oil passages being β, the included angle β being between 0° and 45°.

[0022] According to a first aspect of the present invention, the angle between the sidewall of the groove on one side of the protrusion and the end face of the protrusion is θ, and the angle θ is between 40° and 90°.

[0023] The second aspect of this utility model provides a compressor, including the compressor sealing structure described in the first aspect.

[0024] The crankshaft of this invention has an eccentric part with an oil passage at both ends, which are connected to the central oil hole of the crankshaft and the groove between the thrust part and the protrusion of the crankshaft. When the compressor is running, the lubricating oil in the central oil hole of the crankshaft is collected in the groove through the oil passage under the action of centrifugal force, and fills the gap between the protrusion and the cylinder head, reducing the motion friction between the protrusion and the cylinder head, and improving the efficiency and stability of the compressor operation. Attached Figure Description

[0025] Other features, objects, and advantages of this invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0026] Figure 1 and Figure 2 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the first embodiment of this utility model;

[0027] Figure 3 This is a transverse sectional view of the eccentric portion of the crankshaft according to the second embodiment of this utility model;

[0028] Figure 4 This is a radial cross-sectional view of the eccentric portion of the crankshaft according to the third embodiment of this utility model;

[0029] Figure 5 and Figure 6 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the fourth embodiment of this utility model;

[0030] Figure 7 and Figure 8 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the fifth embodiment of this utility model. Detailed Implementation

[0031] 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 present 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 present invention, and should not be construed as limiting the present invention. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.

[0032] In the description of this utility model, 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 technical features indicated. Therefore, features defined as "first" and "second" may explicitly or implicitly include one or more features. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0033] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" 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 utility model according to the specific circumstances.

[0034] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present 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 scope of 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.

[0035] The compressor sealing structure and compressor of this utility model are 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 this utility model.

[0036] This utility model provides a compressor sealing structure, including a crankshaft, cylinder head, cylinder and piston;

[0037] The crankshaft 1 includes at least an eccentric portion 11. Of course, in the embodiment, the crankshaft 1 also includes a long shaft portion 13 connected to one end of the eccentric portion 11, or the crankshaft also includes a long shaft portion and a short shaft portion at both ends of the eccentric portion.

[0038] The piston is fitted onto the eccentric portion of the crankshaft. The piston and the eccentric portion of the crankshaft are located within the space enclosed by the cylinder and the cylinder head. For example, when the compressor is a single-cylinder compressor, the cylinder head includes an upper cylinder head and a lower cylinder head. The upper cylinder head, the cylinder, and the lower cylinder head enclose the space that houses the eccentric portion of the piston and the crankshaft. In this case, the area enclosed by the piston and the eccentric portion is the piston inner cavity, and the area enclosed by the piston and the cylinder is the piston outer cavity.

[0039] One end face of the eccentric portion is provided with a thrust portion and a protrusion on the outer side of the thrust portion. The end face of the protrusion mates with the end face of the piston to jointly achieve a seal between the inner and outer piston cavities when the crankshaft rotates, preventing gas leakage in the cylinder due to communication between the inner and outer piston cavities, thus reducing the efficiency of the compressor. It should be noted that the end face of the eccentric portion with the thrust portion and the protrusion is the end face of the compressor with the exhaust structure. Therefore, when the compressor has an upper exhaust structure, the thrust portion and the protrusion are located on the upper end face of the eccentric portion, forming the upper sealing structure of the compressor; conversely, they are located on the lower end face of the eccentric portion, forming the lower sealing structure of the compressor. The above sealing structures are all compressor sealing structures of this utility model. The following description uses the example of the thrust portion and the protrusion being located on the upper end face of the eccentric portion.

[0040] In this utility model, a groove is provided between the thrust portion and the protrusion of the eccentric portion 11. The two ends of the groove extend to the side of the eccentric portion. The crankshaft 1 is provided with a central oil hole 12 extending along the axial direction. The central oil hole 12 extends from the long shaft portion 13 of the crankshaft 1 to the eccentric portion 11. The eccentric portion 11 is provided with at least one oil passage, which connects the central oil hole and the groove.

[0041] Figure 1 and Figure 2 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the first embodiment of this utility model. The transverse sectional view is a sectional view on the plane formed by the axis of the crankshaft (long shaft portion) and the centerline of the protrusion. The radial sectional view is a sectional view on a plane perpendicular to the axis of the crankshaft (long shaft portion) and including the centerline of the protrusion. In the first embodiment, the groove 113 between the thrust portion 111 and the protrusion 112 is an arc-shaped groove, and the sidewall of the groove 113 is perpendicular to the end face of the eccentric portion 11. Figure 2In the radial sectional view, the two sidewalls of the groove 113 are arcs, and the centers of the arcs of the two sidewalls lie on the axis of the long axis portion 13 of the crankshaft 1. An oil passage 114a is provided in the eccentric portion 11. The oil passage 114a can be cylindrical, and its axis can intersect with the axis of the central oil hole 12. Simultaneously, the projection of the axis of the oil passage 114a onto a plane perpendicular to the axis of the crankshaft 1 coincides with the centerline of the protrusion 112, where the centerline of the protrusion 112 is the perpendicular bisector of the line connecting the two ends of the protrusion. The perpendicular bisector of the protrusion 112 is parallel. On a plane passing through the axis of the crankshaft 1, the axis of the oil passage 114a is perpendicular to the axis of the central oil hole 12. Axially, the two ends of the oil passage 114a are located on the sidewall of the central oil hole 12 and the sidewall of the groove 113 near the long axis portion 13, respectively. The above structure allows the lubricating oil from the oil passage to be evenly distributed to the protruding part, thereby improving the lubrication effect.

[0042] The crankshaft of this invention is provided with a central oil hole. Lubricating oil is supplied to the protrusion through at least one oil passage that is connected to the groove between the thrust part and the protrusion, thereby reducing the friction loss between the protrusion and the cylinder head at that location.

[0043] In the embodiment where the oil passage 114a is cylindrical, the diameter of the oil passage is R, and the vertical height of the thrust portion 111 is H, where R = (0.9 ± 0.05)H. This structure ensures smooth oil flow through the oil passage while also preventing the oil passage from significantly affecting the structural strength at that location.

[0044] The height of the intersection point between the axis of the oil passage 114a and the side wall of the thrust portion 111 (the side wall of the groove 113 near the long shaft portion 13) is h, satisfying: h≤H / 2. The position of the end of the oil passage in the groove ensures the structural integrity of the oil passage. At the same time, appropriately reducing the height facilitates faster oil delivery from the central oil hole to the oil passage, improving the lubrication effect.

[0045] In the first embodiment, the axis of the oil passage is parallel to the end face of the thrust portion, that is, the angle α between the axis of the oil passage and the axis of the crankshaft is 90°. In some other embodiments, the angle α between the axis of the oil passage and the axis of the crankshaft is not 90°. Figure 3 This is a transverse sectional view of the eccentric portion of the crankshaft according to a second embodiment of the present invention, wherein the angle between the axis of the oil passage and the axis of the crankshaft is 60°. In some other embodiments, the angle α between the axis of the oil passage and the axis of the crankshaft can be between 20° and 90°. The parallel or upward tilt of the oil passage ensures that the oil path is parallel or tilted upward during oil supply, which is beneficial to smooth oil supply and improves lubrication effect.

[0046] In some embodiments, the eccentric portion of the crankshaft is provided with multiple oil passages. The axes of the multiple oil passages can be parallel to each other, that is, the projections of the axes of two adjacent oil passages onto a plane perpendicular to the axis of the crankshaft are parallel to each other. The multiple oil passages can also be evenly arranged along the circumference of the crankshaft. Figure 4 In one embodiment, the eccentric crankshaft is provided with three oil passages 114c. The angles between the axes of the three oil passages 114c and the axis of the crankshaft can be equal. The three oil passages can also be evenly arranged along the circumference of the crankshaft, meaning that the angle β between the projections of the axes of two adjacent oil passages 114c onto a plane perpendicular to the axis of the crankshaft is equal, and the angle β can be between 0° and 45°. Figure 4 The angle between the projections of the axes of two adjacent oil passages 114c onto a plane perpendicular to the crankshaft axis is 45°. Multiple oil passages provide a more significant oil supply and lubrication effect. The number and location of oil passages can be designed according to the specific compressor structure, balancing lubrication effect and structural strength; this will not be elaborated upon here.

[0047] In some embodiments, the angle between the sidewall of the groove 113d on the side of the protrusion 112d and the end face of the protrusion 112d is θ, and the angle θ can be between 40° and 90°. Figure 5 and Figure 6 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the fourth embodiment of this utility model. The inclination of the sidewall of the groove on the protrusion side facilitates faster delivery of lubricating oil to the end face of the protrusion through the inclined surface, further reducing the friction between the protrusion and the cylinder head.

[0048] In the first embodiment, one end of the oil passage 114a is on the side wall of the groove 113 near the long axis portion 13, and one end of the oil passage 114e is on both the side wall of the groove 113 near the long axis portion 13 and the bottom wall of the groove 113. See Figure 7 and Figure 8 These are, respectively, a transverse sectional view and a radial sectional view of the eccentric portion of the crankshaft according to the fifth embodiment of this utility model.

[0049] This invention also provides a compressor, including the aforementioned compressor sealing structure. The compressor sealing structure can be an upper sealing structure or a lower sealing structure. The compressor sealing structure of this invention achieves lubrication of the protrusion through at least one oil passage connected to the groove between the thrust portion and the protrusion, thereby reducing friction loss between the protrusion and the cylinder head, resulting in more stable operation and higher efficiency.

[0050] 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.

[0051] 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 or substitutions should be considered within the protection scope of the present invention.

Claims

1. A compressor sealing structure, characterized in that, This includes the crankshaft, cylinder head, cylinder, and piston; The crankshaft includes at least an eccentric portion, and the crankshaft is provided with a central oil hole extending along the axial direction; 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 space enclosed by the cylinder and the cylinder head; One end face of the eccentric part is provided with a thrust portion and a protrusion on the outer side of the thrust portion, and a groove is provided between the thrust portion and the protrusion, with both ends of the groove extending to the side of the eccentric part. The eccentric portion is provided with at least one oil passage, which connects the central oil hole and the groove.

2. The compressor sealing structure according to claim 1, characterized in that, The axis of the oil passage intersects the axis of the central oil hole.

3. The compressor sealing structure according to claim 1, characterized in that, The angle between the axis of the oil passage and the axis of the crankshaft is α, and the angle α is between 20° and 90°.

4. The compressor sealing structure according to claim 1, characterized in that, The projection of the axis of the oil passage onto a plane perpendicular to the axis of the crankshaft coincides with the centerline of the protrusion, and the centerline of the protrusion is the perpendicular bisector of the line connecting the two ends of the protrusion.

5. The compressor sealing structure according to claim 1, characterized in that, The diameter of the oil passage is R, and the vertical height of the thrust section is H, satisfying: R = (0.9 ± 0.05)H.

6. The compressor sealing structure according to claim 1, characterized in that, The height of the intersection point between the axis of the oil passage and the side of the thrust member is h, and the vertical height of the thrust member is H, satisfying: h≤H / 2.

7. The compressor sealing structure according to claim 1, characterized in that, The crankshaft is provided with multiple oil passages; The axes of the plurality of oil passages are parallel to each other; or The plurality of oil passages are evenly arranged along the circumference of the crankshaft.

8. The compressor sealing structure according to claim 1, characterized in that, The crankshaft is provided with a plurality of oil passages, which are evenly arranged along the circumference of the crankshaft. The included angle between any two adjacent oil passages is β, which is between 0° and 45°.

9. The compressor sealing structure according to claim 1, characterized in that, The angle between the sidewall of the groove on one side of the protrusion and the end face of the protrusion is θ, and the angle θ is between 40° and 90°.

10. A compressor, characterized in that, The compressor sealing structure includes any one of claims 1 to 9.

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