Crankshaft, compressor and refrigeration equipment

Abstract

The invention provides a crankshaft, a compressor and refrigeration equipment. The crankshaft comprises a long shaft part, an eccentric part and a short shaft part which are sequentially arranged in the axial direction, the shaft diameter of the long shaft part is r1, the shaft diameter of the short shaft part is r2, r1 is larger than or equal to 18 mm and smaller than or equal to 20 mm, and r2 is larger than or equal to 16 mm and smaller than or equal to 18 mm. By reducing the shaft diameters of the long and short shafts of the crankshaft, the contact area between the crankshaft and the upper and lower bearings is reduced, the contact friction between the crankshaft and the upper and lower bearings is reduced, the mechanical loss of the compressor can be reduced, the working efficiency of the compressor is improved, and the performance of the compressor is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration, and in particular to a crankshaft, a compressor and a refrigeration device. Background Art

[0002] The hermetic compressor includes a motor that is arranged inside a sealed housing and can generate a driving force, and a pump assembly connected to the motor for compressing the refrigerant. The hermetic compressor can be classified into a reciprocating compressor, a vortex compressor, and a rolling rotor compressor according to the different structures of the refrigerant compressor.

[0003] Rolling rotor compressors have outstanding advantages such as small size and low cost, and are widely used in air conditioning, heat pumps and other fields. The working principle of existing rolling rotor compressors is: the crankshaft of the pump body rotates under the drive of the motor, and the rotation of the crankshaft drives the roller to perform eccentric circular motion, thereby compressing the refrigerant. The crankshaft is constantly performing highly rotating motion. Therefore, the moving pairs in the compressor include the long and short axes of the crankshaft and the inner walls of the upper and lower bearings, and the eccentric part of the crankshaft and the inner circle of the roller. The friction between the moving pairs is intense, and sufficient lubrication is required to reduce contact friction and reduce the mechanical loss of the compressor, thereby ensuring the stable operation of the compressor. However, with the development trend of miniaturization of compressors, the mechanical loss of existing small compressors is still relatively large, affecting the performance of the compressor.

[0004] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include but not constitute information on the prior art known to ordinary technicians in the field. Summary of the invention

[0005] In view of the problems in the prior art, the object of the present invention is to provide a crankshaft, a compressor and a refrigeration device to reduce the mechanical loss of the compressor and improve the efficiency of the compressor.

[0006] An embodiment of the present invention provides a crankshaft, comprising a long axis portion, an eccentric portion and a short axis portion arranged in sequence along the axial direction, the shaft diameter of the long axis portion is r1, the shaft diameter of the short axis portion is r2, satisfying: 18mm≤r1≤20mm, 16mm≤r2≤18mm.

[0007] In some embodiments, the height of the eccentric portion is 17.5 mm to 18 mm.

[0008] An embodiment of the present invention further provides a compressor, comprising a pump body assembly, wherein the pump body assembly comprises the crankshaft as claimed in claim 1.

[0009] In some embodiments, the compressor further includes a shell, and the pump body assembly is disposed inside the shell.

[0010] In some embodiments, the shell includes a middle shell and an upper shell and a lower shell located at two ends of the middle shell.

[0011] In some embodiments, the ratio of the inner diameter of the intermediate shell to the axial diameter of the major axis portion is in a range of 6.61 to 7.34.

[0012] In some embodiments, the ratio of the inner diameter of the intermediate housing to the axial diameter of the short shaft portion is in a range of 7.34 to 8.26.

[0013] In some embodiments, the pump body assembly also includes a cylinder body, an upper bearing, a lower bearing and a roller; the upper bearing and the lower bearing are respectively located at two ends of the cylinder body, the crankshaft passes through two ends of the cylinder body, and the roller is sleeved on the outside of the eccentric part and is located inside the cylinder body.

[0014] In some embodiments, a motor assembly is also included, which is located inside the housing and connected to the crankshaft.

[0015] An embodiment of the present invention further provides a refrigeration device, comprising the compressor as described above.

[0016] The crankshaft, compressor and refrigeration equipment provided by the present invention have the following advantages:

[0017] The crankshaft provided in the compressor includes a long axis portion, an eccentric portion and a short axis portion arranged in sequence along the axial direction, the shaft diameter of the long axis portion is r1, and the shaft diameter of the short axis portion is r2, which satisfies: 18mm≤r1≤20mm, 16mm≤r2≤18mm. Compared with the crankshaft shaft diameter of the compressor in the prior art, the crankshaft shaft diameter of the compressor in the present invention is small, thereby reducing the contact area between the crankshaft and the upper and lower bearings, reducing the contact friction between the crankshaft and the upper and lower bearings, thereby reducing the mechanical loss of the compressor, improving the working efficiency of the compressor, and improving the performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Other features, objectives and advantages of the present invention will become more apparent from a reading of the detailed description of non-limiting embodiments made with reference to the following accompanying drawings.

[0019] Figure 1 It is a schematic structural diagram of a compressor according to an embodiment of the present invention.

[0020] Reference numerals:

[0021] 10 Crankshaft

[0022] 11 Long axis

[0023] 12 Eccentric part

[0024] 13 Short axis

[0025] 21 Intermediate housing

[0026] 22 Upper shell

[0027] 23 Lower shell

[0028] 30 cylinder block

[0029] 40 upper bearing

[0030] 50 lower bearing

[0031] 60 roller

[0032] 70 motor assembly DETAILED DESCRIPTION

[0033] Example embodiments will now be described more fully with reference to the accompanying drawings. However, example embodiments can be implemented in a variety of 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 fully convey the concepts of the example embodiments to those skilled in the art. The same reference numerals in the figures represent the same or similar structures, and thus their repeated description will be omitted.

[0034] In the representations of the present application, the representations with reference to the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" etc. mean that the specific features, structures, materials or characteristics represented in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. Moreover, the represented specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples represented in the present application and the features of the different embodiments or examples, unless they contradict each other.

[0035] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the representation of this application, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0036] It should be further understood that the terms "comprises" and "includes" indicate the presence of features, steps, operations, elements, components, items, kinds, and / or groups, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms "or" and "and / or" used herein are interpreted as inclusive, or mean any one or any combination. Therefore, "A, B or C" or "A, B and / or C" means "any of the following: A; B; C; A and B; A and C; B and C; A, B and C". Exceptions to this definition will only occur when the combination of elements, functions, steps or operations is inherently mutually exclusive in some way.

[0037] Compared with small-displacement compressors, the crankshaft diameter of the compressor in the prior art is relatively large, and the contact area between the crankshaft and the upper and lower bearings is larger, resulting in greater contact friction, which will cause greater mechanical losses to the compressor and affect the performance of the compressor.

[0038] In order to solve the problems in the prior art, an embodiment of the present invention provides a crankshaft, including a long axis portion, an eccentric portion and a short axis portion arranged in sequence along the axial direction, the shaft diameter of the long axis portion is r1, and the shaft diameter of the short axis portion is r2, which satisfies: 18mm≤r1≤20mm, 16mm≤r2≤18mm. By reducing the shaft diameters of the long and short axes of the crankshaft, the contact area between the crankshaft and the upper and lower bearings is reduced, and the contact friction between the crankshaft and the upper and lower bearings is reduced, thereby reducing the mechanical loss of the compressor, improving the working efficiency of the compressor, and improving the performance of the compressor.

[0039] Furthermore, an embodiment of the present invention also provides a compressor, including a pump body assembly, and the pump body assembly includes the crankshaft as described above. The compressor includes the crankshaft as described above, so all the technical effects of the crankshaft as described above can be achieved, the contact area between the crankshaft and the upper and lower bearings can be reduced, and the contact friction between the crankshaft and the upper and lower bearings can be reduced, thereby reducing the mechanical loss of the compressor, improving the working efficiency of the compressor, and improving the compression performance.

[0040] The electric vacuum pump of the present invention will be further described below in conjunction with the accompanying drawings. It should be understood that the various specific embodiments are not intended to limit the protection scope of the present invention.

[0041] Figure 1 FIG. 2 shows a schematic diagram of a compressor provided by an embodiment of the present invention. Figure 1As shown, the pump assembly of the compressor includes a crankshaft 10, and the crankshaft 10 includes a long axis portion 11, an eccentric portion 12, and a short axis portion 13 arranged in sequence along the axial direction. The axial diameter of the long axis portion 11 is r1, and the axial diameter of the short axis portion 13 is r2, which satisfies: 18mm≤r1≤20mm, 16mm≤r2≤18mm. By reducing the axial diameters of the long axis portion 11 and the short axis portion 13 of the crankshaft 10, the contact area between the crankshaft 10 and the upper and lower bearings is reduced, and the contact friction between the crankshaft 10 and the upper and lower bearings is reduced, thereby reducing the mechanical loss of the compressor and improving the mechanical efficiency of the compressor.

[0042] Further, usually the major axis portion 11 is coaxial with the minor axis portion 13, and the eccentric portion 12 is not coaxial with the major axis portion 11 and the minor axis portion 13. Exemplarily, r1 can be 18.2mm, 18.4mm, 18.6mm, 18.8mm, 19mm, 19.2mm, 19.4mm, 19.6mm and 19.8mm. Exemplarily, r2 can be 16.2mm, 16.4mm, 16.6mm, 16.8mm, 17mm, 17.2mm, 17.4mm, 17.6mm and 17.8mm.

[0043] Furthermore, in some embodiments, the height of the eccentric portion 12 is 17.5 mm to 18 mm. The height of the eccentric portion 12 is limited to reduce the contact area between the eccentric portion 12 and the inner circle of the roller of the compressor, thereby reducing the contact friction between the two and reducing the mechanical loss of the compressor.

[0044] Furthermore, the compressor also includes a housing, and the pump assembly is arranged inside the housing. Figure 1 As shown, the compressor housing in the embodiment of the present invention includes an intermediate housing 21 and an upper housing 22 and a lower housing 23 located at both ends of the intermediate housing 21. The intermediate housing 21 is a cylindrical structure with a hollow interior, and the inner diameter of the intermediate housing 21 is R. The ratio of the inner diameter R of the intermediate housing 21 to the axial diameter r1 of the long axis 11 is in the range of 6.61 to 7.34. The unreasonable setting of the intermediate housing 21 may cause poor flow of compressed gas, increase energy consumption, and reduce the efficiency of the compressor. Therefore, by reasonably setting the range of the axial diameter ratio of the inner diameter of the intermediate housing 21 to the axial diameter of the long axis 11, the friction loss of the gas during the compression process can be reduced and the compression efficiency can be improved. It has been found that the axial diameter ratio of the intermediate housing 21 to the long axis 11 is between 6.61 and 7.34, which can have good compression efficiency. In some embodiments, the axial diameter ratio of the inner diameter of the intermediate housing 21 to the axial diameter of the short axis 13 is in the range of 7.34 to 8.26. Similarly, by reasonably setting the range of the axial diameter ratio of the inner diameter of the intermediate housing 21 to the short axis 13, the friction loss of the gas during the compression process can be reduced and the efficiency of the compressor can be improved. Studies have shown that a good compression efficiency can be achieved when the axial diameter ratio of the intermediate housing 21 to the short axis 13 is between 6.61 and 7.34.

[0045] Furthermore, if Figure 1 As shown, the pump assembly further includes a cylinder 30, an upper bearing 40, a lower bearing 50 and a roller 60; the upper bearing 40 and the lower bearing 50 are respectively located at both ends of the cylinder 30, the crankshaft 10 passes through both ends of the cylinder 30, and the roller 60 is sleeved on the outside of the eccentric portion 12 and is located inside the cylinder 30. It should be noted that since the long axis portion 11 and the short axis portion 13 of the crankshaft 10 are respectively connected to the upper bearing 40 and the lower bearing 50, when the shaft diameters of the long axis portion 11 and the short axis portion 13 change, the sizes of the upper bearing 40 and the lower bearing 50 can be adjusted accordingly to obtain a compressor with better performance.

[0046] Furthermore, the compressor also includes a motor assembly 70, which is located inside the shell and connected to the crankshaft 10. When the motor assembly 70 is running, it drives the crankshaft 10 to rotate, and the crankshaft 10 drives the roller 60 to roll along the inner wall of the cylinder. The outer wall of the roller 60 and the inner wall of the cylinder body 30 form a crescent-shaped working chamber, and the crescent-shaped working chamber is divided into two parts: a suction chamber and a compression chamber. The low-pressure refrigerant is sucked into the suction chamber, and then the low-pressure refrigerant is compressed into a high-pressure refrigerant as the roller 60 rotates. When the pressure of the high-pressure refrigerant is greater than the pressure of the exhaust valve, it is discharged from the high-pressure chamber and then enters the refrigeration cycle system for heat exchange.

[0047] The compressor provided in the embodiment of the present invention has a model height of 315.5 mm to 325.5 mm, a displacement of 24.4 cc to 29.5 cc, a maximum motor stack height of 110 L, and a refueling volume of 520 to 610 ml.

[0048] In order to further explore the beneficial effects of the compressor provided by the embodiment of the present invention, the coefficient of performance (COP) of the existing compressor and the compressor provided by the embodiment of the present invention under the same working conditions is compared. COP is an important indicator for measuring the performance of the compressor, which indicates the amount of cooling that can be obtained per unit power consumption. COP = Q / W, Q represents the cooling capacity, and W represents the input power of the motor.

[0049] It should be noted that the model height of the rolling rotor compressor in the prior art compared here is 315mm-325.5mm, the inner diameter of the intermediate housing of the compressor is 132.1mm, the diameter of the long axis of the crankshaft is 21mm, the diameter of the short axis of the crankshaft is 18mm, the height of the eccentric part of the crankshaft is 17.5mm-18mm, the displacement is 24.4cc-29.5cc, the maximum motor stack height is 110L, and the oil filling amount is 520ml-610ml. The model height of the compressor provided in the embodiment of the present invention for comparison is 315mm-325.5mm, the inner diameter of the intermediate housing of the compressor is 132.1mm, the diameter of the long axis of the crankshaft is 19mm, the diameter of the short axis of the crankshaft is 17mm, the height of the eccentric part of the crankshaft is 17.5mm-18mm, the displacement is 24.4cc-29.5cc, the maximum motor stack height is 110L, and the oil filling amount is 520ml-610ml. Table 1 shows the refrigeration capacity, motor input power and COP of the compressor in the prior art and the compressor provided by the embodiment of the present invention under two working conditions.

[0050] Table 1 Refrigeration capacity, motor input power and COP of a compressor in the prior art and a compressor provided by an embodiment of the present invention under two working conditions.

[0051]

[0052]

[0053] According to Table 1, when both compressors are working in working condition 1, compared with the compressor in the prior art, the refrigeration capacity of the compressor provided by the embodiment of the present invention is increased by 2.3%, the power is reduced by 1%, and the COP is increased by 3%. When both compressors are working in working condition 2, compared with the compressor in the prior art, the refrigeration capacity of the compressor provided by the embodiment of the present invention is increased by 1.6%, the power is increased by 1%, and the COP is increased by 1%.

[0054] Therefore, the compressor provided by the embodiment of the present invention has a better COP, and the performance of the compressor is improved.

[0055] Furthermore, an embodiment of the present invention also provides a refrigeration device, including the compressor described above. The refrigeration device includes the compressor described above, and thus can achieve all the technical effects of the compressor, which will not be described in detail here.

[0056] In summary, the crankshaft, compressor and refrigeration equipment provided by the present invention have the following advantages:

[0057] The crankshaft provided in the compressor includes a long axis portion, an eccentric portion and a short axis portion arranged in sequence along the axial direction, wherein the shaft diameter of the long axis portion is r1, and the shaft diameter of the short axis portion is r2, satisfying: 18mm≤r1≤20mm, 16mm≤r2≤18mm. Compared with the shaft diameter of the crankshaft in the prior art, the shaft diameters of the long and short axes of the crankshaft are reduced, thereby reducing the contact area between the crankshaft and the upper and lower bearings, reducing the contact friction between the crankshaft and the upper and lower bearings, thereby reducing the mechanical loss of the compressor, improving the working efficiency of the compressor, and improving the performance of the compressor.

[0058] The above contents are further detailed descriptions of the present invention in combination with specific preferred embodiments, and it cannot be determined that the specific implementation of the present invention is limited to these descriptions. For ordinary technicians in the technical field to which the present invention belongs, several simple deductions or substitutions can be made without departing from the concept of the present invention, which should be regarded as falling within the protection scope of the present invention.

Claims

1. A crankshaft, characterized in that: It comprises a long axis portion, an eccentric portion and a short axis portion which are arranged in sequence along the axial direction, the shaft diameter of the long axis portion is r1, the shaft diameter of the short axis portion is r2, and the following conditions are satisfied: 18mm≤r1≤20mm, 16mm≤r2≤18mm.

2. The crankshaft according to claim 1, characterized in that The height of the eccentric portion is 17.5 mm to 18 mm.

3. A compressor, characterized in that: It comprises a pump body assembly, the pump body assembly comprising the crankshaft as claimed in claim 1 or 2.

4. The compressor according to claim 3, characterized in that The compressor further comprises a shell, and the pump body assembly is arranged inside the shell.

5. The compressor according to claim 4, characterized in that The shell comprises an intermediate shell and an upper shell and a lower shell located at two ends of the intermediate shell.

6. The compressor according to claim 5, characterized in that The ratio of the inner diameter of the intermediate housing to the axial diameter of the major axis portion is in a range of 6.61 to 7.

34.

7. The compressor according to claim 5, characterized in that The ratio of the inner diameter of the intermediate housing to the axial diameter of the short axis portion is in a range of 7.34 to 8.

26.

8. The compressor according to claim 3, characterized in that The pump body assembly also includes a cylinder body, an upper bearing, a lower bearing and a roller; the upper bearing and the lower bearing are respectively located at two ends of the cylinder body, the crankshaft passes through two ends of the cylinder body, and the roller is sleeved on the outside of the eccentric part and located inside the cylinder body.

9. The compressor according to claim 8, characterized in that It also includes a motor assembly, which is located inside the shell and connected to the crankshaft.

10. A refrigeration device, characterized in that: Comprising a compressor as claimed in any one of claims 3 to 9.

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