Compressor and refrigeration apparatus
By setting inclined grooves on the crankshaft to increase the contact area, the problem of eccentric wear between the crankshaft and the main bearing is solved, achieving more stable lubrication and protection, and improving the mechanical efficiency of the compressor.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SHANGHAI HITACHI ELECTRICAL APPLIANCES CO LTD
- Filing Date
- 2025-05-23
- Publication Date
- 2026-06-02
AI Technical Summary
In existing rotary compressors, the eccentric structure of the crankshaft and main bearings makes them prone to uneven wear during high-speed rotation. After long-term operation, this leads to increased wear on the cylinder head and crankshaft sidewalls, resulting in decreased mechanical efficiency.
Grooves with a first inclined surface and a second inclined surface are provided on the long shaft of the crankshaft to increase the contact area between the crankshaft and the main bearing when the crankshaft is tilted during operation, forming a surface contact to reduce the pressure of the oil film per unit area and improve lubrication and protection.
By increasing the contact area, the oil film becomes more stable, preventing wear and improving the mechanical and operational efficiency of the compressor.
Smart Images
Figure CN224315112U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of compressor technology, specifically to a compressor and refrigeration equipment. Background Technology
[0002] The compressor is the core component of refrigeration equipment. In a rotary compressor, the crankshaft transmits the rotational force of the motor to the piston in the cylinder to compress the refrigerant. The compressed refrigerant then exchanges heat in different spaces, thereby achieving cooling or heating of a specific space. Due to the eccentric structure of the crankshaft, especially in single-cylinder compressors, high-speed rotation inevitably leads to the crankshaft tilting. When the crankshaft and its mating bearings are not concentric, the part where the long axis of the compressor crankshaft mates with the upper and lower cylinder head bearings is prone to uneven wear. After prolonged operation, this can easily lead to increased wear on the cylinder head and crankshaft sidewalls, resulting in a decrease in the compressor's mechanical efficiency. Utility Model Content
[0003] In view of the problems in the prior art, the purpose of this utility model is to provide a compressor and refrigeration equipment that improves the oil film bearing capacity, enhances the lubrication and protection effect of the oil film between the crankshaft and the main bearing, makes the compressor run more smoothly, and improves the mechanical efficiency of the compressor.
[0004] This utility model provides a compressor, including a crankshaft and a main bearing. The crankshaft includes a long shaft, an eccentric portion, and a short shaft arranged sequentially along the axial direction. The main bearing is sleeved on the long shaft. The long shaft includes a first part and a second part. The outer wall of the first part has a first groove in the circumferential direction. The first groove is disposed opposite to the end of the main bearing away from the eccentric portion. The first groove includes at least a first inclined surface, and the angle between the first inclined surface and the axis of the long shaft is 0.5° to 2°.
[0005] The outer circumferential portion of the second part is provided with a second groove, which is disposed opposite to one end of the main bearing near the eccentric part; the second groove includes at least a second inclined surface, and the angle between the second inclined surface and the axis of the long shaft is 0.5° to 2°.
[0006] In some embodiments, the first groove and the second groove are inclined grooves, V-grooves, or arc grooves.
[0007] In some embodiments, the depth of the first groove is 5μm to 30μm; the depth of the second groove is 5μm to 30μm.
[0008] In some embodiments, the maximum groove depth of the first groove is H1, satisfying: 0.0002≤H1 / R≤0.002, 0.001≤H1 / X≤0.005; the maximum groove depth of the second groove is H2, satisfying: 0.0002≤H2 / R≤0.002, 0.001≤H2 / X≤0.005;
[0009] Where R is the diameter of the major axis and X is the eccentricity of the crankshaft.
[0010] In some embodiments, the grooving angle of the first groove in the circumferential direction of the first part is t1, which satisfies: 60°≤t1≤180°; the grooving angle of the second groove in the circumferential direction of the second part is t2, which satisfies: 60°≤t2≤180°.
[0011] In some embodiments, the first cutting area of the first groove is S1, the second cutting area of the second groove is S2, the first curved surface area of the first groove relative to the main bearing is b1, the second curved surface area of the second groove relative to the main bearing is b2, and S1+S2 accounts for 3% to 20% of the sum of b1 and b2.
[0012] In some embodiments, the cutting area of the first groove and the eccentricity of the crankshaft satisfy: 5≤S1 / X≤80; the cutting area of the second groove and the eccentricity of the crankshaft satisfy: 5≤S2 / X≤80.
[0013] In some embodiments, the length of the first groove in the axial direction of the long shaft is L1, and the ratio of L1 to the contact length between the first groove and the main bearing is 10% to 50%.
[0014] In some embodiments, the length of the second groove in the axial direction of the long shaft is L2, and the ratio of L2 to the contact length between the second groove and the main bearing is 10% to 50%.
[0015] This utility model embodiment also provides a refrigeration device, including the compressor described above.
[0016] The compressor and refrigeration equipment provided by this utility model have the following advantages:
[0017] This technical solution, by setting a first groove with a first inclined surface and a second groove with a second inclined surface, allows the first and second inclined surfaces to form surface contact with the main bearing when the crankshaft tilts during operation. Therefore, the first and second grooves increase the contact area between the crankshaft and the main bearing when the crankshaft tilts, thereby reducing the pressure on the oil film per unit area. The oil film between them can more easily withstand the load and is less prone to being squeezed and damaged, resulting in a more stable and intact oil film. This ensures continuous and good lubrication and protection between the crankshaft and the main shaft, preventing wear caused by direct contact between the main bearing and the main shaft, and improving the compressor's working efficiency. Attached Figure Description
[0018] 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.
[0019] Figure 1 This is a schematic diagram showing the eccentric wear phenomenon that occurs when the crankshaft long shaft and the main bearing are fitted together;
[0020] Figure 2 This is a schematic diagram of a crankshaft provided in one embodiment of the present invention;
[0021] Figure 3 yes Figure 2 An enlarged view of position a1 is shown below;
[0022] Figure 4 yes Figure 2 An enlarged view of position a2 shown;
[0023] Figure 5 This is a top view schematic diagram of the crankshaft provided in an embodiment of this utility model;
[0024] Figure 6 This is a schematic diagram showing the first part of the crankshaft moving to the Z1 direction according to an embodiment of the present invention;
[0025] Figure 7 This is a schematic diagram showing the second part of the crankshaft moving to the Z2 direction according to an embodiment of the present invention;
[0026] Figure 8 This is a comparison chart of the cooling capacity, compressor input, and COP of the compressor provided in this embodiment under different operating conditions.
[0027] Figure label:
[0028] 10 Crankshaft 112 Part Two
[0029] 11 Long shaft 1121 Second groove
[0030] 111 Part 12 Eccentric Section
[0031] 1111 First groove 13 Short shaft
[0032] 1111a First Inclined Surface 20 Main Bearing
[0033] 1121a Second Inclined Surface Detailed Implementation
[0034] 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 comprehensive and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.
[0035] Furthermore, the terms "first" and "second" are used for illustrative purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the representation of this application, "multiple" means two or more, unless otherwise explicitly specified.
[0036] like Figure 1 As shown, when the long shaft 11' of the existing crankshaft 10' tilts during operation, the upper end of the long shaft 11' contacts the upper end of the main bearing 20', and the lower end of the long shaft 11' contacts the lower end of the main bearing 20'. The contact between these two parts is mainly line contact. The line contact between the long shaft 11' and the main bearing 20' increases the stress on the oil film between them, thereby destroying the integrity of the oil film. When the integrity of the oil film is destroyed, the long shaft 11' will directly contact the main bearing 20' during operation, resulting in eccentric wear between these two parts. Eccentric wear increases the wear between the long shaft 11' and the main bearing 20', and affects the working efficiency of the compressor.
[0037] To solve the above-mentioned technical problems, this utility model provides a compressor, including a crankshaft and a main bearing. The crankshaft includes a long shaft, an eccentric portion, and a short shaft arranged sequentially along the axial direction. The main bearing is sleeved on the long shaft. The long shaft includes a first part and a second part. The outer wall of the first part is provided with a first groove in the circumferential direction. The first groove is disposed opposite to the end of the main bearing away from the eccentric portion. The first groove includes at least a first inclined surface, and the angle between the first inclined surface and the axis of the long shaft is 0.5° to 2°.
[0038] The outer circumferential portion of the second part is provided with a second groove, which is disposed opposite to one end of the main bearing near the eccentric part; the second groove includes at least a second inclined surface, and the angle between the second inclined surface and the axis of the long shaft is 0.5° to 2°.
[0039] This technical solution, by setting a first groove with a first inclined surface and a second groove with a second inclined surface, allows the first and second inclined surfaces to form surface contact with the main bearing when the crankshaft tilts during operation. Therefore, the first and second grooves increase the contact area between the crankshaft and the main bearing when the crankshaft tilts, thereby reducing the pressure on the oil film per unit area. The oil film between them can more easily withstand the load and is less prone to being squeezed and damaged, resulting in a more stable and intact oil film. This ensures continuous and good lubrication and protection between the crankshaft and the main shaft, preventing wear caused by direct contact between the main bearing and the main shaft, and improving the compressor's working efficiency.
[0040] The compressor of this utility model embodiment will be further explained below with reference to the accompanying drawings.
[0041] like Figures 2 to 4 As shown, the crankshaft 10 of the compressor includes a long shaft 11, an eccentric portion 12, and a short shaft 13 arranged sequentially along the axial direction. The main bearing is sleeved on the long shaft 11 of the crankshaft 10 (see reference). Figure 1 The long shaft 11 includes a first part 111 and a second part 112. The outer circumferential portion of the first part 111 has a first groove 1111, which is opposite to the end of the main bearing away from the eccentric portion 12. The first groove 1111 includes a first inclined surface 1111a, and the angle between the first inclined surface 1111a and the axis of the long shaft 11 is 0.5° to 2°. The outer circumferential portion of the second part 112 has a second groove 1121, which is opposite to the end of the main bearing near the eccentric portion 12. The second groove 1121 includes at least one second inclined surface 1121a, and the angle between the second inclined surface 1121a and the axis of the long shaft 11 is 0.5° to 2°.
[0042] By providing a first groove 1111 on the first part 111, when the first part 111 tilts during operation, the first inclined surface 1111a of the first groove 1111 will form a surface contact with the upper end of the main bearing. This increases the contact area between the first part 111 and the upper end of the main bearing, resulting in a relatively large oil film area on the contact surface. Consequently, the oil film bears relatively less pressure per unit area, making it easier to withstand loads. It is less prone to being squeezed and damaged, and less likely to experience localized oil film loss. The oil film experiences less disturbance, which is beneficial for its stable existence and provides good lubrication and protection for the first part 111 and the upper end of the main bearing.
[0043] Similarly, by providing a second groove 1121 on the second part 112, when the second part 112 deforms during operation, the second inclined surface 1121a will form a surface contact with the lower end of the main bearing. This increases the contact area between the second part 112 and the lower end of the main bearing, resulting in a relatively large oil film on the contact surface. The oil film bears relatively less pressure per unit area, making it easier to withstand loads and less prone to being squeezed and damaged. It is also less likely to experience local oil film loss, and the oil film has less disturbance, which is conducive to the stable existence of the oil film. This provides good lubrication and protection for the second part 112 and the lower end of the main bearing.
[0044] Furthermore, in some embodiments, the first groove 1111 and the second groove 1121 are V-grooves, inclined grooves, or arc-shaped grooves. For example, Figure 3 As shown, the first groove 1111 is a V-shaped groove, and the second groove 1121 is an inclined groove. When the first inclined surface 1111a or the second inclined surface 1121a is set as an inclined arc surface, the first groove 1111 and the second groove 1121 can be arc-shaped grooves. The specific shape of the first groove 1111 and the second groove 1121 can be set according to actual needs, and is not limited to the example above.
[0045] Furthermore, in this embodiment, the groove depth of the first groove 1111 is 5μm to 30μm, and the groove depth of the second groove 1121 is 5μm to 30μm. The shallow groove depths of the first groove 1111 and the second groove 1121 in this embodiment reduce cutting on the crankshaft 10, thereby improving the strength, reliability, and service life of the crankshaft 10.
[0046] Furthermore, such as Figure 3 As shown, the maximum groove depth of the first groove 1111 is H1, satisfying: 0.0002≤H1 / R≤0.002, 0.001≤H1 / X≤0.005; Figure 4 As shown, the maximum groove depth of the second groove 1121 is H2, satisfying: 0.0002≤H2 / R≤0.002, 0.001≤H2 / X≤0.005. Wherein, as... Figure 6 and Figure 7 As shown, R is the shaft diameter of the major axis 11, as... Figure 5 As shown, X represents the eccentricity of the crankshaft 10, which is the distance between the center of the major shaft 11 and the center of the eccentric portion 12. The strength of the crankshaft 10 is controlled by adjusting the relationship between the maximum groove depth of the first groove 1111 and the second groove 1121 and the shaft diameter of the major shaft 11. The eccentricity affects the tilt angle of the crankshaft 10 during operation; a larger eccentricity results in greater force and a larger tilt angle during crankshaft operation. To achieve good surface contact, the relationship between the groove depth and the eccentricity needs to be carefully defined.
[0047] Furthermore, such as Figure 6 As shown, the first groove 1111 has a grooving angle of t1 in the circumferential direction of the first part 111, satisfying: 60°≤t1≤180°; Figure 7 As shown, the grooving angle of the second groove 1121 in the circumferential direction of the second part 112 is t2, satisfying: 60°≤t2≤180°. By reasonably setting the range of the first groove 1111 and the second groove 1121 in the circumferential direction of the long shaft 11, the lubrication between the long shaft 11 and the main bearing is improved without reducing the strength of the crankshaft 10. Please continue reading. Figure 6 and Figure 7 When the crankshaft 10 is rotating, the first part 111 of the long shaft 11 contacts the main bearing in the Z1 direction, and the second part 112 of the long shaft 11 contacts the main bearing in the Z2 direction. The angle t1 between the first groove 1111 and the Z1 direction is between 0° and 90° (t3); the angle t2 between the second groove 1121 and the Z2 direction is between 90° and 180° (t4). The distribution angle of the first groove 1111 and the second groove 1121 in the Z, Z1 or Z2 direction during operation ensures that the long shaft 11 receives sufficient lubrication during operation, reducing wear.
[0048] Furthermore, the first groove 1111 and the second groove 1121 are formed by a cutting process. The first cutting area of the first groove 1111 is S1, the second cutting area of the second groove 1121 is S2, the first curved surface area of the first groove 1111 relative to the main bearing is b1, and the second curved surface area of the second groove 1121 relative to the main bearing is b2. S1 + S2 accounts for 3% to 20% of the sum of b1 and b2. It should be noted that the first curved surface of the first groove 1111 relative to the main bearing is the side surface area of the first groove 1111 relative to the cylindrical part of the main bearing; the second curved surface of the second groove 1121 relative to the bearing shaft is the side surface area of the second groove 1121 relative to the cylindrical part of the main bearing. By using the cutting area of the grooves and the curved surface area of the corresponding main bearing, sufficient lubrication protection is ensured between the long shaft 11 and the bearing shaft.
[0049] Furthermore, the eccentricity between the first cutting area S1 of the first groove 1111 and the crankshaft 10 satisfies: 5 ≤ S1 / X ≤ 80; the eccentricity between the second cutting area S2 of the second groove 1121 and the crankshaft 10 satisfies: 5 ≤ S2 / X ≤ 80. By setting the relationship between the cutting area and the eccentricity, the strength of the crankshaft 10 is ensured while the lubrication protection during crankshaft 10 operation is guaranteed, reducing eccentric wear between the crankshaft 10 and the main bearing.
[0050] Furthermore, such as Figure 3As shown, the length of the first groove 1111 in the axial direction of the long shaft 11 is L1, and the ratio of L1 to the contact length between the first groove 1111 and the main bearing is 10% to 50%; the length of the second groove 1121 in the axial direction of the long shaft 11 is L2, and the ratio of L2 to the contact length between the second groove 1121 and the main bearing is 10% to 50%.
[0051] The strength of the crankshaft 10 is ensured by displaying the lengths of the first groove 1111 and the second groove 1121 in the axial direction of the long shaft 11, and the crankshaft 10 is ensured to have sufficient lubrication protection by setting the ratio between the groove length and the contact length of the main bearing.
[0052] To further confirm the beneficial effects of the compressor provided in this embodiment of the present invention, a comparison was made of the cooling capacity, compressor input, and COP (Coefficient of Performance) of the compressor provided in this embodiment of the present invention under different operating conditions. Figure 8 As shown, the compressor provided in this embodiment of the present invention has low compressor input, high efficiency, and the compressor input is reduced by about 0.5% when heating at low temperature.
[0053] This utility model embodiment also provides a refrigeration device, including the compressor described above. This refrigeration device includes the compressor described above, and therefore achieves all the technical effects of the compressor described above. Further details will not be elaborated here.
[0054] In summary, the compressor and refrigeration equipment provided by this utility model have the following advantages:
[0055] By setting a first groove with a first inclined surface and a second groove with a second inclined surface, when the crankshaft tilts during operation, the first inclined surface can form a surface contact with the main bearing, and the second inclined surface can also form a surface contact with the main bearing. Therefore, the setting of the first groove and the second groove increases the contact area between the crankshaft and the main bearing when the crankshaft tilts during operation, thereby reducing the pressure borne by the oil film between the two per unit area. The oil film between the two can more easily bear the load and is not easily squeezed and damaged. The oil film is more stable and intact, so that the crankshaft and the main shaft can continuously form a good lubrication and protection effect, avoid the wear caused by direct contact between the main bearing and the main shaft, and improve the working efficiency of the compressor.
[0056] The first and second grooves in this design are shallow, and the grooves are only made in the circumferential part of the long shaft, which can improve the strength of the crankshaft.
[0057] 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 protection scope of the present invention.
Claims
1. A compressor comprising a crankshaft and a main bearing, the crankshaft comprising a long shaft, an eccentric portion, and a short shaft arranged sequentially along the axial direction, the main bearing being sleeved on the long shaft, characterized in that, The long shaft includes a first part and a second part. The outer wall of the first part is provided with a first groove in the circumferential direction. The first groove is disposed opposite to the end of the main bearing that is away from the eccentric part. The first groove includes at least a first inclined surface. The angle between the first inclined surface and the axis of the long shaft is 0.5° to 2°. The outer circumferential portion of the second part is provided with a second groove, which is disposed opposite to one end of the main bearing near the eccentric part; the second groove includes at least a second inclined surface, and the angle between the second inclined surface and the axis of the long shaft is 0.5° to 2°.
2. The compressor according to claim 1, characterized in that, The first groove and the second groove are inclined grooves, V-shaped grooves or arc grooves.
3. The compressor according to claim 1, characterized in that, The depth of the first groove is 5μm to 30μm; the depth of the second groove is 5μm to 30μm.
4. The compressor according to claim 1, characterized in that, The maximum groove depth of the first groove is H1, satisfying: 0.0002≤H1 / R≤0.002, 0.001≤H1 / X≤0.005; the maximum groove depth of the second groove is H2, satisfying: 0.0002≤H2 / R≤0.002, 0.001≤H2 / X≤0.005; Where R is the diameter of the major axis and X is the eccentricity of the crankshaft.
5. The compressor according to claim 1, characterized in that, The first groove has a grooving angle of t1 in the circumferential direction of the first part, which satisfies: 60°≤t1≤180°; the second groove has a grooving angle of t2 in the circumferential direction of the second part, which satisfies: 60°≤t2≤180°.
6. The compressor according to claim 1, characterized in that, The first cutting area of the first groove is S1, the second cutting area of the second groove is S2, the first curved surface area of the first groove relative to the main bearing is b1, the second curved surface area of the second groove relative to the main bearing is b2, and S1+S2 accounts for 3% to 20% of the sum of b1 and b2.
7. The compressor according to claim 6, characterized in that, The cutting area of the first groove and the eccentricity of the crankshaft satisfy: 5≤S1 / X≤80; the cutting area of the second groove and the eccentricity of the crankshaft satisfy: 5≤S2 / X≤80.
8. The compressor according to claim 1, characterized in that, The length of the first groove along the axial direction of the long shaft is L1, and the ratio of L1 to the contact length between the first groove and the main bearing is 10% to 50%.
9. The compressor according to claim 1, characterized in that, The length of the second groove along the axial direction of the long shaft is L2, and the ratio of L2 to the contact length between the second groove and the main bearing is 10% to 50%.
10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.