compressor
By designing oblique holes on the eccentric sleeve, the problem of lubricating medium not flowing easily to the sliding bearing is solved, simplifying the processing technology, reducing costs, and improving lubrication effect and equipment reliability.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- ZHEJIANG SANHUA LVNENG IND GROUP CO LTD
- Filing Date
- 2024-11-27
- Publication Date
- 2026-05-29
AI Technical Summary
In the existing technology, the lubricating medium does not easily flow to the sliding bearing of the compressor, resulting in poor lubrication effect, and the process is complicated and costly.
The oil hole on the eccentric sleeve is designed with an oblique hole structure, and the distance between the oil hole axis and the eccentric shaft axis gradually increases. Under the action of centrifugal force, the lubricating medium can easily flow into the sliding bearing, which simplifies the processing technology and improves the lubrication effect.
The lubricating medium flows more easily to the sliding bearing, reducing processing complexity and cost, while improving lubrication performance and equipment reliability.
Smart Images
Figure CN122106879A_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of compressor technology, and more particularly to a compressor for vehicle air conditioning. Background Technology
[0002] An eccentric sleeve and a sliding bearing are installed between the eccentric shaft and the moving scroll of the compressor. The sliding bearing has high lubrication requirements during use. In related technologies, the eccentric sleeve has an axial flow path extending along the eccentric sleeve axis and a radial flow path extending along the eccentric sleeve axis. When the compressor is in operation, the lubricating medium in the axial flow path flows to the radial flow path under the action of centrifugal force, and then flows to the sliding bearing through the radial flow path. However, the lubricating medium outside the eccentric sleeve does not easily flow into the axial flow path extending along the eccentric sleeve axis, making it difficult for the lubricating medium to flow to the sliding bearing. Summary of the Invention
[0003] This application provides a compressor designed to facilitate the flow of lubricating medium to a sliding bearing.
[0004] Embodiments of this application provide a compressor, including: a drive shaft assembly, a scroll assembly, and a connecting assembly. The drive shaft assembly includes a main shaft and an eccentric shaft, with the eccentric shaft and the main shaft connected axially at one end. The scroll assembly includes a moving scroll with a connecting groove located at the end of the moving scroll facing the drive shaft assembly. The connecting assembly includes an eccentric sleeve and a sliding bearing. The eccentric sleeve is fitted around the periphery of the eccentric shaft, and the sliding bearing is at least partially located in the connecting groove. The sliding bearing is connected to the moving scroll and is fitted around the periphery of the eccentric sleeve.
[0005] The eccentric sleeve has an oil hole, which includes a first inlet end and a first outlet end. From the first inlet end to the first outlet end, the distance between the oil hole axis and the eccentric shaft axis gradually increases.
[0006] This application achieves this by gradually increasing the distance between the oil hole axis and the eccentric shaft axis from the first inlet end to the first outlet end. When the compressor is in operation, the lubricating medium moves away from the eccentric shaft axis under the action of centrifugal force, making it easier for the lubricating medium to flow into the oil hole under the action of centrifugal force, thereby making it easier for the lubricating medium to flow to the sliding bearing. Attached Figure Description
[0007] Figure 1 This is a three-dimensional structural schematic diagram of the compressor of this application;
[0008] Figure 2 This is a cross-sectional structural schematic diagram of the compressor of this application;
[0009] Figure 3 This is a schematic diagram of the separate structure of the moving scroll and drive shaft assembly of the compressor in this application;
[0010] Figure 4 This is a schematic diagram of the separate structure of the drive shaft assembly and the connecting assembly of the compressor of this application;
[0011] Figure 5 This is a cross-sectional view of the oil hole structure of the compressor in this application;
[0012] Figure 6 This is a three-dimensional structural diagram of the eccentric sleeve of the compressor in this application;
[0013] Figure 7 This is a bottom view of the eccentric sleeve of the compressor in this application.
[0014] Figure 8 This is a cross-sectional schematic diagram of the oil hole structure of the compressor in this application;
[0015] Figure 9 This is a top view of the balance block of the compressor in this application;
[0016] Figure 10 This is a cross-sectional structural schematic diagram of an optional embodiment of the oil hole of the compressor in this application. Detailed Implementation
[0017] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.
[0018] It should be understood that the described embodiments are merely some embodiments of this application, and not all embodiments. All other technical solutions obtained by those skilled in the art based on the technical solutions in this application without inventive effort are within the scope of protection of this application.
[0019] According to a specific embodiment of the compressor of this application, such as Figure 1 and Figure 2 As shown, the compressor includes a drive shaft assembly 1, a scroll assembly 2, and a connecting assembly 3. The drive shaft assembly 1 and the scroll assembly 2 are connected by the connecting assembly 3. The compressor also includes a drive assembly 4, which is also connected to the drive shaft assembly 1. The drive assembly 4 can be a stator or rotor, or other components capable of outputting driving force. The driving force output by the drive assembly 4 is transmitted to the scroll assembly 2 through the drive shaft assembly 1, causing the scroll assembly 2 to compress the relatively low-pressure working medium into a relatively high-pressure working medium. The compressor also includes a housing assembly 5, which has a receiving cavity 51. The drive shaft assembly 1, the scroll assembly 2, the connecting assembly 3, and the drive assembly 4 are all located in the receiving cavity 51.
[0020] like Figures 3 to 5As shown, the drive shaft assembly 1 includes a main shaft 11 and an eccentric shaft 12. The eccentric shaft 12 and the main shaft 11 are axially connected at one end, and the axis of the eccentric shaft 12 is parallel to the axis of the main shaft 11. The eccentric shaft 12 and the main shaft 11 can be integrally formed, or the eccentric shaft 12 can be fixedly connected to the main shaft 11, for example, by interference fit, welding, etc. The scroll assembly 2 includes a moving scroll 21, which has a connecting groove 211 located at the end of the moving scroll 21 facing the drive shaft assembly 1. The connecting assembly 3 includes an eccentric sleeve 31 and a sliding bearing 32. The eccentric sleeve 31 is fitted around the circumference of the eccentric shaft 12, and the eccentric sleeve 31 and the eccentric shaft 12 are fixedly connected, for example, by interference fit, etc. The sliding bearing 32 is at least partially located in the connecting groove 211. The sliding bearing 32 is connected to the side wall of the connecting groove 211, and the sliding bearing 32 and the side wall of the connecting groove 211 can be fixedly connected by means of interference fit or other methods. The sliding bearing 32 is sleeved on the circumference of the eccentric sleeve 31. When the compressor is in working condition, the sliding bearing 32 can slide relative to the eccentric sleeve 31. The scroll assembly 2 also includes a stationary scroll 22, which meshes with the moving scroll 21. There is a compression chamber 23 between the stationary scroll 22 and the moving scroll 21. When the main shaft 11 rotates, the eccentric shaft 12 drives the moving scroll 21 to rotate eccentrically, so that the moving scroll 21 rotates relative to the stationary scroll 22. The volume of the compression chamber 23 decreases, and the relatively low temperature and low pressure working medium is compressed into a relatively high temperature and high pressure working medium.
[0021] The sliding bearing 32 requires a high-quality lubrication environment during operation. Under good lubrication conditions, the sliding surfaces can be separated by the lubricating medium without direct contact, thus greatly reducing friction loss and surface wear. Simultaneously, the oil film between the sliding surfaces also has a certain vibration-absorbing capacity, ensuring smooth and reliable operation of the sliding bearing 32. To provide a better lubrication environment for the sliding bearing 32, in related technologies, the eccentric sleeve 31 is provided with a "T"-shaped axial flow path and a radial flow path. The axial flow path extends axially along the eccentric sleeve 31, and the radial flow path extends radially along the eccentric sleeve 31. When the compressor is in operation, the lubricating medium in the axial flow path flows to the radial flow path under the action of centrifugal force, and then flows to the sliding bearing 32 through the radial flow path. This structure of the eccentric sleeve 31 is relatively complex. During the manufacturing process of the eccentric sleeve 31, the axial and radial flow paths need to be machined separately, resulting in a complex and costly manufacturing process. Furthermore, the lubricating medium does not easily flow into the axial flow path extending axially along the eccentric sleeve 31, making it difficult for the lubricating medium to flow to the sliding bearing 32.
[0022] like Figure 5As shown, in this embodiment, the eccentric sleeve 31 has an oil hole 311, which includes a first inlet end 3111 and a first outlet end 3112. When the compressor is in operation, the lubricating medium flows into the oil hole 311 through the first inlet end 3111 and flows out of the oil hole 311 through the first outlet end 3112. From the first inlet end 3111 to the first outlet end 3112, the distance between the axis of the oil hole 311 and the axis of the eccentric shaft 12 gradually increases, that is, the oil hole 311 is an oblique hole. From the first inlet end 3111 to the first outlet end 3112, the oil hole 311 is inclined towards the side closer to the sliding bearing 32, and the oil hole 311 is inclined towards the side away from the eccentric shaft 12. It can be understood that the technical solution in which only part of the flow path of the eccentric sleeve 31 for the lubricating medium flows is inclined towards the side away from the eccentric shaft 12 is also within the protection scope of this application, and this part of the flow path can be defined as the oil hole 311 of this application. In this embodiment, the distance between the axis of the oil hole 311 and the axis of the eccentric shaft 12 gradually increases from the first inlet end 3111 to the first outlet end 3112. Under the action of centrifugal force, the lubricating medium moves away from the eccentric shaft 12, making it easier for the lubricating medium to flow into the oil hole 31. Furthermore, from the first inlet end 3111 to the first outlet end 3112, the oil hole 311 is inclined towards the side closer to the sliding bearing 32, facilitating the flow of the lubricating medium through the oil hole 311 to the sliding bearing 32 for lubrication. Compared to related technologies, the structure of the oil hole 311 in this embodiment is simpler; it can be formed by machining the oil hole 311 on the eccentric sleeve 31, simplifying the manufacturing process and reducing costs. Moreover, the eccentric sleeve 31 in this embodiment has fewer open sections, resulting in better reliability and strength. Meanwhile, compared to the "T"-shaped flow path in related technologies, the oblique hole can guide the lubricating medium to flow directly to the sliding bearing 32. The flow path of the lubricating medium in the oblique hole is also shorter, making it easier for the lubricating medium to lubricate the sliding bearing 32. In addition, in related technologies, the lubricating medium is not subject to centrifugal force when flowing in the axial flow path. In this embodiment, the oil hole 311 is an oblique hole, from the first inlet end 3111 to the first outlet end 3112. The oil hole 311 is inclined to the side away from the eccentric shaft 12. Under the action of centrifugal force, the lubricating medium moves to the side away from the eccentric shaft 12, making it easier for the lubricating medium to flow into the oil hole 311. Moreover, the lubricating medium is subject to centrifugal force throughout its flow in the oil hole 311, making it easier for the lubricating medium to flow to the sliding bearing 32.
[0023] like Figure 5 As shown, the receiving cavity 51 includes an oil cavity 511, which is used to store lubricating medium. In this embodiment, the compressor is a horizontal compressor, and the oil cavity 511 is located at the bottom of the housing assembly 5. The position of the oil cavity 511 can be referred to as shown below. Figure 5The position shown is below the dotted line. The eccentric sleeve 31 includes a first end face 312, which is the end face of the eccentric sleeve 31 facing the main shaft 11. The first inlet end 3111 is located on the first end face 312. The main shaft 11 includes a second end face 111, which is located on the main shaft 11 facing the first inlet end 3111. The main shaft 11 has a connecting groove 112, which is recessed from the second end face 111 towards the side opposite to the first inlet end 3111. The first inlet end 3111 and the connecting groove 112 are connected. Figure 5 The direction indicated by the dotted line with arrows is the flow direction of the lubricating medium in the oil cavity 511 into the oil hole 311. When the compressor is in operation, the main shaft 11, eccentric shaft 12 and eccentric sleeve 31 rotate and agitate the lubricating medium in the oil cavity 511 at the bottom of the housing assembly 5, causing some of the lubricating medium to splash to the positions of the first end face 312 and the second end face 111. The connecting groove 112 can guide the working medium to flow to the first inlet end 3111 and into the oil hole 311. At the same time, the connecting groove 112 can increase the agitation of the lubricating medium, further facilitating the flow of the lubricating medium into the oil hole 311.
[0024] like Figure 6 and Figure 7 As shown, in one alternative implementation, the eccentric sleeve 31 includes a first protruding structure 313, which protrudes from a first end face 312 toward the main shaft 11. The first inlet end 3111 is located in front of the first protruding structure 313 along the rotational direction of the eccentric sleeve 31 during operation. Figure 7The dotted line with arrows points in the direction of rotation of the eccentric sleeve 31 during operation. When the compressor is in operation, the first inlet end 3111 is located in front of the first protruding structure 313 along the rotation direction of the eccentric sleeve 31. The first protruding structure 313 has a certain guiding effect. When the eccentric sleeve 31 rotates, the first protruding structure 313 obstructs the lubricating medium along the rotation direction of the eccentric sleeve 31, causing the lubricating medium to accumulate in front of the first protruding structure 313. At the same time, the lubricating medium in front of the first protruding structure 313 is further splashed under the impact and agitation of the first protruding structure 313. Some of the lubricating medium will flow to the first inlet end 3111 and oil hole 311 in front of the first protruding structure 313, so that the lubricating medium can more easily flow through the oil hole 311 to the position of the sliding bearing 32 and lubricate the sliding bearing 32. It is understandable that when the distance between the first protruding structure 313 and the first inlet end 3111 is relatively close, especially when the front end face of the first protruding structure 313 along the rotation direction of the eccentric sleeve 31 roughly coincides with the wall surface of the oil hole 311, the guiding effect of the first protruding structure 313 is better. When the area of the front end face of the first protruding structure 313 along the rotation direction of the eccentric sleeve 31 is large, the first protruding structure 313 also has a good guiding effect. At the same time, the front end face of the first protruding structure 313 along the rotation direction of the eccentric sleeve 31 can be an inclined surface with a slope of approximately the same as that of the oil hole 311, so as to further improve the guiding effect of the first protruding structure 313.
[0025] like Figures 3 to 5 As shown, the drive shaft assembly 1 includes a balance block 13. Since the axis of the eccentric shaft 12 deviates from the axis of the main shaft 11, the eccentric shaft 12 will generate a certain radial force on the main shaft 11 when it rotates. The balance block 13 is used to balance the radial force generated when the eccentric shaft 12 rotates. The balance block 13 includes a connecting part 131 and a counterweight part 132. The connecting part 131 and the counterweight part 132 can be integrally formed. The connecting part 131 is connected to the main shaft 11. The direction in which the counterweight part 132 deviates from the axis of the main shaft 11 is opposite to the direction in which the axis of the eccentric shaft 12 deviates from the axis of the main shaft 11. The radial dimension of the balance block 13 along the main shaft 11 is generally larger than that of the eccentric sleeve 31 along the main shaft 11. When the compressor is in operation, the balance block 13 can agitate more lubricating medium. Therefore, the connecting groove 112 is set on the main shaft 11 near the counterweight 132, and the oil hole 311 is set on the eccentric shaft 12 near the counterweight 132, so that the lubricating medium can flow to the connecting groove 112 and the oil hole 311.
[0026] like Figure 3 , Figure 4 and Figure 9As shown, the counterweight 132 includes a third end face 1321 and a fourth end face 1322. The fourth end face 1322 is located at the end of the counterweight 132 facing the connecting groove 112 along the radial direction of the main shaft 11. The third end face 1321 is located at the end of the counterweight 132 opposite to the fourth end face 1322. That is, along the radial direction of the main shaft 11, the third end face 1321 and the fourth end face 1322 are the end faces of opposite ends of the counterweight 132. The counterweight 132 has a connecting channel 1323, which includes a second inlet end 1324 and a second outlet end 1325. The second inlet end 1324 is located at the third end face 1321, and the second outlet end 1325 is located at the fourth end face 1322. That is, the connecting channel 1323 passes through the third end face 1321 and the fourth end face 1322. The connecting channel 1323 can be a groove structure or a hole structure, allowing the lubricating medium to flow through the connecting channel 1323 to the positions of the connecting groove 112 and the oil hole 311. The radial direction of the spindle 11 can be referenced as follows: Figure 9 The direction of extension of the dotted line shown is as follows: Figure 9 The direction indicated by the dashed line with arrows is the rotation direction of the balance block 13 during operation. From the second outlet end 1325 to the second inlet end 1324, relative to the radial direction of the main shaft 11, the connecting channel 1323 is inclined towards the front side of the rotation direction of the balance block 13 during operation, so that the working medium can easily flow into the connecting channel 1323.
[0027] like Figure 9 As shown, in one alternative embodiment, the counterweight 132 includes a second protruding structure 1326, which protrudes from a third end face 1321. The second protruding structure 1326 can protrude along the extension direction of the connecting channel 1323 or along the radial direction of the main shaft 11. The second inlet end 1324 is located in front of the second protruding structure 1326 in the direction of rotation of the balance block 13 during operation. The second protruding structure 1326 has a guiding effect on the lubricating medium. When the balance block 13 rotates, the second protruding structure 1326 obstructs the lubricating medium along the rotation direction of the balance block 13, causing the lubricating medium to accumulate in front of the second protruding structure 1326. At the same time, the lubricating medium in front of the second protruding structure 1326 splashes under the impact and agitation of the second protruding structure 1326, enabling the second protruding structure 1326 to guide the working medium into the second inlet end 1324 and the connecting channel 1323. It is understandable that when the distance between the second protruding structure 1326 and the second inlet end 1324 is relatively close, such as... Figure 9As shown, the flow guiding effect of the second protruding structure 1326 is better when the end face of the second protruding structure 1326 along the rotation direction of the balance block 13 is approximately coincident with the hole wall of the connecting channel 1323. The flow guiding effect of the second protruding structure 1326 is also better when the end face area of the second protruding structure 1326 along the rotation direction of the balance block 13 is large. At the same time, the end face of the second protruding structure 1326 along the rotation direction of the balance block 13 can be an inclined surface with an inclination approximately the same as that of the connecting channel 1323, so as to further improve the flow guiding effect of the second protruding structure 1326.
[0028] like Figure 8 As shown, in an alternative embodiment, relative to the radial direction of the eccentric shaft 12, from the first inlet end 3111 to the first outlet end 3112, the oil hole 311 is inclined towards the rear side of the rotation direction of the eccentric sleeve 31 during operation; that is, the oil hole 311 is inclined both towards the side away from the eccentric shaft 12 and towards the rear side of the rotation direction of the eccentric sleeve 31 during operation. Figure 8 The path indicated by the dashed line with arrows is the flow path of the lubricating medium as it flows through the connecting channel 1323, the connecting groove 112 and the oil hole 311. This structure can make the tilt direction of the oil hole 311 more compatible with the movement direction of the lubricating medium under the action of centrifugal force, thereby increasing the flow rate of the lubricating medium into the oil hole 311.
[0029] like Figure 10 As shown, in one alternative implementation, the eccentric sleeve 31 includes a sliding connection surface 314, which is a side surface around the eccentric sleeve 31. The sliding bearing 32 is connected to the sliding connection surface 314, and the first outlet end 3112 is located on the sliding connection surface 314 to facilitate the direct flow of the lubricating medium to the sliding surface of the sliding bearing 32. The flow area of the first inlet end 3111 is smaller than the flow area of the first outlet end 3112, so as to increase the flow area of the first outlet end 3112 while minimizing the perforations on the eccentric sleeve 31, making it easier for the lubricating medium to flow to the sliding bearing 32. Of course, the oil hole 311 can also penetrate through the two ends of the eccentric sleeve 31 that are axially opposite, and the first outlet end 3112 can also be located at the junction of the side surface around the eccentric sleeve 31 and the axial end face. The oil hole 311 can extend in a straight line or in a spiral direction around the axis of the eccentric shaft 12.
[0030] In this application, the distance between the axis of the oil hole 311 and the axis of the eccentric shaft 12 gradually increases from the first inlet end 3111 to the first outlet end 3112. Under the action of centrifugal force, the lubricating medium moves away from the eccentric shaft 12, making it easier for the lubricating medium to flow into the oil hole 31 under the action of centrifugal force. Furthermore, from the first inlet end 3111 to the first outlet end 3112, the oil hole 311 is inclined towards the side closer to the sliding bearing 32, facilitating the flow of the lubricating medium through the oil hole 311 to the sliding bearing 32 and lubricating it. In addition, the lubricating medium is subjected to centrifugal force throughout its flow in the oil hole 311, making it even easier for the lubricating medium to flow to the sliding bearing 32.
[0031] The technical solutions described in this application should be understood by those skilled in the art. For example, directional descriptions such as "front," "back," "left," "right," "up," and "down" are only used to describe the relationship between objects and are not substantive limitations. "Multiple" means at least two or more.
[0032] Although this application has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still make modifications or equivalent substitutions to this application, and all technical solutions and improvements that do not depart from the spirit and scope of this application should be covered within this application.
Claims
1. A compressor, characterized in that, include: A drive shaft assembly, a scroll assembly, and a connecting assembly are provided. The drive shaft assembly includes a main shaft and an eccentric shaft, the eccentric shaft and the main shaft being connected axially at one end. The scroll assembly includes a moving scroll with a connecting groove located at one end of the moving scroll facing the drive shaft assembly. The connecting assembly includes an eccentric sleeve and a sliding bearing. The eccentric sleeve is fitted around the circumference of the eccentric shaft, and the sliding bearing is at least partially located in the connecting groove. The sliding bearing is connected to the moving scroll and is fitted around the circumference of the eccentric sleeve. The eccentric sleeve has an oil hole, which includes a first inlet end and a first outlet end. From the first inlet end to the first outlet end, the distance between the axis of the oil hole and the axis of the eccentric shaft gradually increases.
2. The compressor as described in claim 1, characterized in that, The eccentric sleeve includes a first end face, which is the end face of the eccentric sleeve facing one end of the main shaft, and the first inlet end is located on the first end face; The spindle includes a second end face located at the position of the spindle facing the first inlet end. The spindle has a connecting groove recessed from the second end face toward the side opposite to the first inlet end. The first inlet end and the connecting groove are connected.
3. The compressor as described in claim 2, characterized in that, The eccentric sleeve includes a first protruding structure, which protrudes from the first end face toward the main shaft, and the first inlet end is located in front of the first protruding structure in the direction of rotation when the eccentric sleeve is working.
4. The compressor as described in claim 2, characterized in that, The drive shaft assembly includes a balance block connected to the main shaft. The balance block includes a third end face and a fourth end face. The fourth end face is located on the balance block facing the communicating groove along the radial direction of the main shaft. The third end face is located on the end of the balance block opposite to the fourth end face. The balance block has a connecting channel that extends between the third end face and the fourth end face.
5. The compressor as described in claim 4, characterized in that, The connecting channel includes a second inlet end and a second outlet end, the second inlet end being located on the third end face and the second outlet end being located on the fourth end face; Relative to the radial direction of the main shaft, from the second outlet end to the second inlet end, the connecting channel is inclined towards the front side of the rotation direction of the balance block during operation.
6. The compressor as described in claim 5, characterized in that, The balance block includes a second protruding structure, which protrudes from the third end face, and the second inlet end is located in front of the second protruding structure in the direction of rotation of the balance block during operation.
7. The compressor as claimed in claim 1, characterized in that, The eccentric sleeve includes a sliding connection surface, which is located at one end of the eccentric sleeve facing the sliding bearing, and the first outlet end is located at the sliding connection surface.
8. The compressor as claimed in claim 1, characterized in that, Relative to the radial direction of the eccentric shaft, from the first inlet end to the first outlet end, the oil hole is inclined toward the rear side in the rotation direction of the eccentric sleeve during operation.
9. The compressor as claimed in claim 1, characterized in that, The flow area at the first inlet is smaller than the flow area at the first outlet.
10. The compressor according to any one of claims 1 to 9, characterized in that, The oil hole extends in a straight line, or the oil hole extends in a spiral direction around the axis of the eccentric shaft.