Design method of compression mechanism, compression mechanism, compressor and vehicle

Abstract

The invention discloses a design method of a compression mechanism, the compression mechanism, a compressor and a vehicle, an eccentric sleeve is arranged on an eccentric shaft in a sleeving mode, a sliding bearing is arranged on a movable scroll plate and arranged on the peripheral side of the eccentric sleeve in a sleeving mode, and an oil film gap is formed between the inner circumferential face of the sliding bearing and the outer circumferential face of the eccentric sleeve. The design method comprises the steps that under the condition that the movable scroll plate does not incline relative to the eccentric sleeve, it is guaranteed that the minimum oil film gap value of stable and normal work of the compression mechanism is sigma min; under the condition that the movable scroll plate inclines relative to the eccentric sleeve, the maximum oil film gap value corresponding to the maximum allowable inclination angle of the movable scroll plate is sigma max; and the radial size sigma of the oil film gap meets the condition that sigma < min > < = sigma < = sigma < max. According to the design method of the compression mechanism, abrasion between the eccentric sleeve and the sliding bearing can be avoided or reduced so as to reduce noise, and contact between the eccentric shaft and the sliding bearing under the condition that the stop scroll plate inclines can be avoided or reduced so as to guarantee the service life of the compressor.

Description

Technical Field

[0001] The invention relates to the technical field of compressors, and in particular to a design method for a compression mechanism, a compression mechanism, a compressor and a vehicle. Background Art

[0002] The mechanical noise generated by the compressor is mainly caused by the contact between the orbiting scroll, the fixed scroll, the eccentric sleeve and other components. In the related technology, the orbiting scroll inside the compressor is connected to the eccentric sleeve through an embedded sliding bearing. There is a certain oil film gap between the sliding bearing and the eccentric sleeve to produce oil film lubrication. However, due to the unreasonable design of the oil film gap, the orbiting scroll drives the sliding bearing to tilt under the action of gas force and inertia force during the operation of the compressor, which will change the surface contact between the sliding bearing and the eccentric sleeve to line contact. Long-term operation will easily cause the sliding bearing to wear, greatly shortening the service life of the compressor. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present invention is to provide a design method for a compression mechanism, wherein the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has an appropriate range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0004] The present invention also provides a compression mechanism designed according to the above design method.

[0005] The invention also provides a compression mechanism.

[0006] The present invention also provides a compressor having the above compression mechanism.

[0007] The present invention also provides a vehicle having the compressor.

[0008] According to the design method of the compression mechanism of the first aspect of the present invention, the compression mechanism includes a crankshaft assembly, a compression component and a sliding bearing, the crankshaft assembly includes a crankshaft, an eccentric shaft and an eccentric sleeve, one end of the eccentric shaft is connected to the crankshaft, the eccentric sleeve is sleeved on the other end of the eccentric shaft, the compression component includes a movable scroll and a fixed scroll that cooperate with each other, the sliding bearing is arranged on the movable scroll and sleeved on the outer peripheral side of the eccentric sleeve, an oil film gap is formed between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve, and the design method includes: when the movable scroll is not tilted relative to the eccentric sleeve, the minimum oil film gap value to ensure the smooth and normal operation of the compression mechanism is σ min When the movable scroll is tilted relative to the eccentric sleeve, the maximum oil film clearance value corresponding to the maximum allowable tilt angle of the movable scroll is σ max ; The radial dimension σ of the oil film gap satisfies: σ min ≤σ≤σ max .

[0009] According to the design method of the compression mechanism of the embodiment of the present invention, the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has an appropriate range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0010] According to some embodiments of the present invention, when the orbiting scroll does not tilt relative to the eccentric sleeve, the maximum bearing capacity of the oil film in the oil film gap is the first maximum bearing capacity of the oil film, and the oil film gap value obtained when the first maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve is the σ min .

[0011] According to some optional embodiments of the present invention, the maximum bearing capacity of the first oil film is the bearing capacity of the sliding bearing and the eccentric sleeve at the meshing point, and the meshing point is the position where the distance between the sliding bearing and the eccentric sleeve is the smallest.

[0012] According to some embodiments of the present invention, the maximum allowable inclination angle of the orbiting scroll is θ max , the axial length of the eccentric sleeve is h2, where σ max ,θ max And h2 satisfies: σmax =tanθ max *h2.

[0013] According to some embodiments of the present invention, the maximum allowable inclination angle θ of the orbiting scroll is max Less than or equal to 0.387.

[0014] According to some embodiments of the present invention, when the movable scroll plate is tilted relative to the eccentric sleeve, the maximum bearing capacity of the oil film in the oil film gap is the second maximum bearing capacity of the oil film, and the allowable inclination angle obtained when the second maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve is the maximum allowable inclination angle.

[0015] According to some optional embodiments of the present invention, the second maximum oil film bearing capacity is the bearing capacity at the oil film minimum radial thickness in the oil film gap.

[0016] According to the compression mechanism of the second embodiment of the present invention, the compression mechanism is designed according to the design method described in the first embodiment.

[0017] According to the compression mechanism of the embodiment of the present invention, the compression mechanism is designed according to the above-mentioned design method, and the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0018] According to some embodiments of the present invention, σ=d1-d2, σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing, d2 is the outer diameter of the eccentric sleeve, h2 is the axial length of the eccentric sleeve, the units of d1, d2 and h2 are all mm, and a, b, c are all preset values ​​greater than 0.

[0019] According to some optional embodiments of the present invention, the value of a is 0.001, the value of c is 0.045, and the value of b is 0.0067.

[0020] According to a third aspect of the present invention, a compression mechanism includes: a crankshaft assembly, including a crankshaft, an eccentric shaft and an eccentric sleeve, one end of the eccentric shaft is connected to the crankshaft, and the eccentric sleeve is sleeved on the other end of the eccentric shaft; a compression component, the compression component includes a movable scroll and a fixed scroll that cooperate with each other; a sliding bearing, the sliding bearing is arranged on the movable scroll and sleeved on the outer peripheral side of the eccentric sleeve, an oil film gap is formed between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve, and the radial dimension σ of the oil film gap satisfies: σ min ≤σ≤σ max , where σ=d1-d2, σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing, d2 is the outer diameter of the eccentric sleeve, h2 is the axial length of the eccentric sleeve, the units of d1, d2 and h2 are all mm, and a, b, c are all preset values ​​greater than 0.

[0021] According to the compression mechanism of the embodiment of the present invention, the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has an appropriate range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0022] According to some embodiments of the present invention, the value of a is 0.001, the value of c is 0.045, and the value of b is 0.0067.

[0023] A compressor according to an embodiment of the fourth aspect of the present invention comprises: a compression mechanism according to the above embodiment of the present invention.

[0024] According to the compressor of the embodiment of the present invention, by setting the above-mentioned compression mechanism, the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0025] A vehicle according to an embodiment of a fifth aspect of the present invention comprises: a compressor according to the embodiment of the fourth aspect of the present invention.

[0026] According to the vehicle of the embodiment of the present invention, by providing the above-mentioned compressor, the radial dimension of the oil film gap between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing and the eccentric sleeve; the oil film gap value is not greater than σ max The distance between the inner circumference of the sliding bearing and the outer circumference of the eccentric sleeve is not too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the movable scroll plate is tilted, so as to ensure the service life of the compressor.

[0027] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0029] Figure 1 is a schematic structural diagram of a compression mechanism according to some embodiments of the present invention;

[0030] Figure 2 yes Figure 1 A cross-sectional view of the compression mechanism;

[0031] Figure 3 is a schematic diagram of the cooperation between the eccentric sleeve and the movable scroll according to some embodiments of the present invention;

[0032] Figure 4 yes Figure 3 A cross-sectional view of the middle eccentric sleeve and the orbiting scroll, wherein the orbiting scroll is not tilted relative to the eccentric sleeve;

[0033] Figure 5 yes Figure 3 A partial cross-sectional view of the middle eccentric sleeve and the orbiting scroll, wherein the orbiting scroll is not tilted relative to the eccentric sleeve;

[0034] Figure 6 yes Figure 5 A schematic diagram of another angle of cooperation between the middle eccentric sleeve and the orbiting scroll, showing the position of the meshing point;

[0035] Figure 7is a cross-sectional view of an eccentric sleeve and a movable scroll according to some embodiments of the present invention, wherein the movable scroll is inclined relative to the eccentric sleeve;

[0036] Figure 8 yes Figure 7 The enlarged view of point A in the middle;

[0037] Fig. 9 is a simplified diagram of a vehicle according to some embodiments of the present invention;

[0038] Fig.10 1 is a comparison of the sound power levels of the compressors according to some embodiments of the present invention and the compression mechanisms in the related art.

[0039] Reference numerals:

[0040] 1000, vehicle; 200, compressor;

[0041] 100. Compression mechanism;

[0042] 10. Crankshaft assembly; 11. Crankshaft; 12. Eccentric shaft; 13. Eccentric sleeve;

[0043] 20. Orbiting scroll; 30. Sliding bearing; 40. Oil film clearance; 50. Bracket; 60. Engagement point. DETAILED DESCRIPTION

[0044] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0045] The following describes a design method of the compression mechanism 100 according to an embodiment of the present invention with reference to the accompanying drawings.

[0046] Reference Figure 1-Figure 2 According to the design method of the compression mechanism 100 of the first embodiment of the present invention, the compression mechanism 100 includes a crankshaft assembly 10, a compression component and a sliding bearing 30. The crankshaft assembly 10 includes a crankshaft 11, an eccentric shaft 12 and an eccentric sleeve 13. One end of the eccentric shaft 12 is connected to the crankshaft 11, and the eccentric sleeve 13 is sleeved on the other end of the eccentric shaft 12. The compression component includes a movable scroll 20 and a fixed scroll that cooperate with each other. For example, the compression mechanism 100 may also include a bracket 50, and the bracket 50 is used to support the movable scroll 20.

[0047] Reference Figure 3-Figure 5The sliding bearing 30 is provided on the movable scroll 20 and sleeved on the outer peripheral side of the eccentric sleeve 13. An oil film gap 40 is formed between the inner peripheral surface of the sliding bearing 30 and the outer peripheral surface of the eccentric sleeve 13. The design method includes: when the movable scroll 20 is not tilted relative to the eccentric sleeve 13, the minimum oil film gap value to ensure the stable and normal operation of the compression mechanism 100 is σ min .

[0048] The movable scroll 20 is not tilted relative to the eccentric sleeve 13, and it can be considered that the central axis of the sliding bearing 30 is parallel to the central axis of the eccentric sleeve 13; when the movable scroll 20 is not tilted relative to the eccentric sleeve 13, the compression mechanism 100 works smoothly and normally, which means that the inner circumferential surface of the sliding bearing 30 is not in contact with the outer circumferential surface of the eccentric sleeve 13.

[0049] When the size of the oil film gap 40 between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is too small, the oil film gap value is too small, and the oil film bearing capacity is insufficient. When the oil film is subjected to external force, the oil film is easily damaged, resulting in contact between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 and generating noise.

[0050] Therefore, while ensuring that the movable scroll 20 does not tilt relative to the eccentric sleeve 13, it is also necessary to ensure that there is no contact friction between the sliding bearing 30 and the eccentric sleeve 13, so it is necessary to determine the minimum value σ of the oil film gap 40 min , the minimum value of the oil film gap 40σ min It can be the oil film gap value between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 when the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of contact and non-contact. min The oil film bearing capacity can resist the external force exerted on the oil film so that the oil film can be maintained, thereby ensuring that the compression mechanism 100 can operate smoothly and normally when the movable scroll 20 is not tilted relative to the eccentric sleeve 13.

[0051] Reference Figure 7 and Figure 8 When the orbiting scroll 20 is tilted relative to the eccentric sleeve 13, the maximum oil film clearance value corresponding to the maximum allowable tilt angle of the orbiting scroll 20 is σ max .

[0052] When the movable scroll 20 is tilted relative to the eccentric sleeve 13 , the sliding bearing 30 is tilted relative to the eccentric sleeve 13 . It can be considered that there is a certain angle between the central axis of the sliding bearing 30 and the central axis of the eccentric sleeve 13 .

[0053] When the oil film gap 40 is too large, the inclination angle of the movable scroll 20 relative to the eccentric sleeve 13 is too large, which will cause uneven distribution of the axial oil film gap. The bearing capacity of the oil film at the minimum position of the axial oil film gap is difficult to support the movable scroll 20. The movable scroll 20 is easily tilted under the combined influence of the inertia moment, the lateral gas moment, the axial gas moment, etc. in the working state, so that the movable scroll 20 drives the sliding bearing 30 to tilt, and the sliding bearing 30 contacts the eccentric shaft 12, which can easily cause serious wear between the sliding bearings 30 and shorten the service life of the compressor 200.

[0054] When the movable scroll 20 is tilted relative to the eccentric sleeve 13, the greater the tilt angle of the movable scroll 20 is, the smaller the maximum bearing capacity of the oil film in the oil film gap 40 is. When the movable scroll 20 is tilted until the sliding bearing 30 is about to contact the eccentric sleeve 13, the tilt angle of the movable scroll 20 is the largest, but the maximum bearing capacity of the oil film is small. The tilt angle of the movable scroll 20 is not allowed to continue to increase. If it continues to increase, the oil film between the sliding bearing 30 and the eccentric sleeve 13 will be difficult to maintain, which will cause the sliding bearing 30 to contact the eccentric sleeve 13.

[0055] Therefore, when the movable scroll 20 is tilted relative to the eccentric sleeve 13, the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of contact and non-contact. At this time, the angle between the sliding bearing 30 and the eccentric sleeve 13 is the maximum allowable tilt angle of the movable scroll 20. The maximum oil film clearance value corresponding to the maximum allowable tilt angle is σ max .

[0056] By determining the maximum oil film gap value σ max , which can ensure that the radial dimension σ of the oil film gap 40 between the sliding bearing 30 and the eccentric sleeve 13 is within an appropriate range. When the movable scroll 20 is tilted relative to the eccentric sleeve 13, the contact wear between the sliding bearing 30 and the eccentric sleeve 13 is avoided or reduced, thereby ensuring the service life of the compressor 200.

[0057] The radial dimension σ of the oil film gap 40 satisfies: σ min ≤σ≤σ max The clearance through the oil film is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0058] Reference Fig.10 Compared with the compression mechanism in the related art, when the rotation speed of the compressor 200 is the same, the compression mechanism 100 of the embodiment of the present application has a smaller sound power level and generates less noise; and as the rotation speed of the compressor 200 increases, the sound power level increases, and the noise reduction effect of the compression mechanism 100 of the embodiment of the present application becomes more obvious.

[0059] According to the design method of the compression mechanism 100 of the embodiment of the present invention, the radial dimension of the oil film gap 40 between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0060] According to some embodiments of the present invention, when the orbiting scroll 20 is not tilted relative to the eccentric sleeve 13, the maximum bearing capacity of the oil film in the oil film gap 40 is the first maximum bearing capacity of the oil film, and the oil film gap value obtained when the first maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve 13 is σ min .

[0061] The maximum inertia force of the eccentric sleeve 13 is related to the rotation speed, suction pressure, exhaust pressure, suction temperature, exhaust temperature and displacement of the compressor 200 .

[0062] When the oil film gap 40 is small, the distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is small, and the movable scroll 20 is not easy to tilt relative to the eccentric sleeve 13. However, when the oil film gap 40 is too small, the distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is too small, and the sliding bearing 30 and the eccentric sleeve 13 are prone to contact and friction.

[0063] Therefore, while ensuring that the movable scroll 20 does not tilt relative to the eccentric sleeve 13, it is also necessary to ensure that there is no contact friction between the sliding bearing 30 and the eccentric sleeve 13. When the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of contact and non-contact, the oil film gap value between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13, that is, the minimum value of the oil film gap 40.

[0064] When the movable scroll 20 is not tilted relative to the eccentric sleeve 13, the larger the oil film clearance value, the larger the maximum bearing capacity of the first oil film. When the maximum bearing capacity of the first oil film is not less than the maximum inertia force of the eccentric sleeve 13, the oil film is maintained and is not easily damaged, and the sliding bearing 30 and the eccentric sleeve 13 are not easily in contact. Therefore, when the maximum bearing capacity of the first oil film is equal to the maximum inertia force of the eccentric sleeve 13, the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of contact and non-contact, and the oil film clearance 40 has a minimum value at this time, so the minimum oil film clearance value can be determined to be σ min .

[0065] Reference Figure 6 According to some optional embodiments of the present invention, the maximum bearing capacity of the first oil film is the bearing capacity of the sliding bearing 30 and the eccentric sleeve 13 at the meshing point 60, and the meshing point 60 is the position where the distance between the sliding bearing 30 and the eccentric sleeve 13 is the minimum.

[0066] At the minimum distance between the sliding bearing 30 and the eccentric sleeve 13, the thickness of the oil film is the smallest, the oil film is more easily damaged, and the sliding bearing 30 is more likely to contact the eccentric sleeve 13. When the bearing capacity of the oil film at the meshing point 60 is not less than the maximum inertia force of the eccentric sleeve 13, it can be ensured that the oil film at the meshing point 60 is not damaged, and the sliding bearing 30 is not in contact with the eccentric sleeve 13.

[0067] Therefore, by ensuring that the position with the smallest spacing between the sliding bearing 30 and the eccentric sleeve 13 does not contact, it can be ensured that no contact wear occurs between the sliding bearing 30 and other positions of the eccentric sleeve 13, thereby ensuring that the compression mechanism 100 can operate smoothly and normally when the movable scroll 20 is not tilted relative to the eccentric sleeve 13.

[0068] Reference Figure 8 According to some embodiments of the present invention, the maximum allowable inclination angle of the orbiting scroll 20 is θ max , the axial length of the eccentric sleeve 13 is h2, where σ max ,θ max And h2 satisfies: σ max =tanθ max *h2. According to the maximum allowable tilt angle θ max The axial length of the eccentric sleeve 13 can determine the maximum oil film clearance value as σ max The determined data is more accurate, so that the radial dimension σ of the oil film gap 40 has a smaller error during the actual design process, which better ensures that the compressor 200 can work normally and smoothly.

[0069] The maximum permissible inclination angle θ of the orbiting scroll 20 is max It can be less than or equal to 0.387. For example, the maximum allowable tilt angle θmax is equal to 0.387, and combined with σ max =tanθ max *h2, it can be determined that the relationship satisfied by the maximum oil film clearance value corresponding to the maximum allowable inclination angle of the orbiting scroll 20 is σ max =0.0067*h2. Therefore, the maximum allowable inclination angle θ of the movable scroll 20 is max When the ratio is less than or equal to 0.387, the bearing capacity of the oil film gap 40 can avoid or reduce the contact between the sliding bearing 30 and the eccentric sleeve 13 .

[0070] It should be noted that the angles in the embodiment of the present invention are expressed in radians, and the maximum allowable tilt angle θ is max Less than or equal to 0.387, refers to the maximum allowable tilt angle θ max Less than or equal to 0.387 radians.

[0071] According to some embodiments of the present invention, when the orbiting scroll 20 is tilted relative to the eccentric sleeve 13, the maximum bearing capacity of the oil film in the oil film gap 40 is the second maximum bearing capacity of the oil film, and the allowable tilt angle obtained when the second maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve 13 is the maximum allowable tilt angle θ max .

[0072] When the movable scroll 20 is tilted relative to the eccentric sleeve 13, the greater the tilt angle of the movable scroll 20, the smaller the maximum bearing capacity of the oil film. When the maximum bearing capacity of the oil film is the second maximum bearing capacity of the oil film, it is equal to the maximum inertia force of the eccentric sleeve 13. At this time, the oil film can also separate the eccentric sleeve 13 from the sliding bearing 30, and there is no wear between the eccentric sleeve 13 and the sliding bearing 30; however, the tilt angle of the movable scroll 20 is not allowed to continue to increase. If it continues to increase, the maximum bearing capacity of the oil film will be less than the maximum inertia force of the eccentric sleeve 13, and the oil film will be easily damaged, which will cause contact between the sliding bearing 30 and the eccentric sleeve 13.

[0073] Therefore, when the movable scroll 20 is tilted relative to the eccentric sleeve 13, it is also necessary to ensure that the sliding bearing 30 and the eccentric sleeve 13 do not contact each other. When the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of contact and non-contact, the maximum bearing capacity of the second oil film is equal to the maximum inertia force of the eccentric sleeve 13, and the oil film will not be damaged. At this time, the tilt angle of the movable scroll 20 is the maximum allowable tilt angle θmax; the maximum allowable tilt angle θ can be determined by the maximum bearing capacity of the second oil film being equal to the maximum inertia force of the eccentric sleeve 13. max . Through the maximum permissible tilt angle θ max , the maximum oil film clearance value σ corresponding to the maximum allowable inclination angle of the orbiting scroll 20 can be determined max For example, combining the above σmax =tanθ max *h2,θ max is equal to 0.387, we can determine σ max =0.0067*h2.

[0074] According to some optional embodiments of the present invention, the maximum bearing capacity of the second oil film is the bearing capacity at the minimum radial thickness of the oil film in the oil film gap 40. The minimum radial thickness of the oil film refers to the position where the spacing between the sliding bearing 30 and the eccentric sleeve 13 is the smallest when the movable scroll 20 is tilted relative to the eccentric sleeve 13. The bearing capacity of the oil film at this position is the smallest. When the position where the oil film bearing capacity is the smallest can satisfy a maximum inertia force greater than or equal to the eccentric sleeve 13, the position where the spacing between the sliding bearing 30 and the eccentric sleeve 13 is the smallest will not cause contact wear, that is, it can be ensured that the sliding bearing 30 and other positions of the eccentric sleeve 13 will not cause contact wear, thereby ensuring the service life of the compressor 200.

[0075] Refer to the following Figure 1-Figure 8 A method for designing a compression mechanism 100 according to an embodiment of the present invention is described.

[0076] Reference Figure 1-Figure 8 In this embodiment, the compression mechanism 100 includes a crankshaft assembly 10, a compression component, a bracket 50 and a sliding bearing 30, wherein the bracket 50 is used to support the movable scroll 20; the crankshaft assembly 10 includes a crankshaft 11, an eccentric shaft 12 and an eccentric sleeve 13, wherein one end of the eccentric shaft 12 is connected to the crankshaft 11, and the eccentric sleeve 13 is sleeved on the other end of the eccentric shaft 12. The compression component includes a movable scroll 20 and a fixed scroll that cooperate with each other; the sliding bearing 30 is provided on the movable scroll 20 and sleeved on the outer peripheral side of the eccentric sleeve 13, and an oil film gap 40 is formed between the inner peripheral surface of the sliding bearing 30 and the outer peripheral surface of the eccentric sleeve 13. The design method includes: when the movable scroll 20 is not tilted relative to the eccentric sleeve 13, the minimum oil film gap value for ensuring the stable and normal operation of the compression mechanism 100 is σ min When the movable scroll 20 is tilted relative to the eccentric sleeve 13, the maximum oil film clearance value corresponding to the maximum allowable tilt angle of the movable scroll 20 is σ max ; The radial dimension σ of the oil film gap 40 satisfies: σ min ≤σ≤σ max .

[0077] When the orbiting scroll 20 is not tilted relative to the eccentric sleeve 13, the maximum bearing capacity of the oil film in the oil film gap 40 is the first maximum bearing capacity of the oil film, which is the bearing capacity of the sliding bearing 30 and the eccentric sleeve 13 at the meshing point 60, and the meshing point 60 is the minimum distance between the sliding bearing 30 and the eccentric sleeve 13. The oil film gap value obtained when the first maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve 13 is σ min .

[0078] When the orbiting scroll 20 is tilted relative to the eccentric sleeve 13, the maximum bearing capacity of the oil film in the oil film gap 40 is the second maximum bearing capacity of the oil film, and the second maximum bearing capacity of the oil film is the bearing capacity at the minimum radial thickness of the oil film in the oil film gap 40. The allowable tilt angle obtained when the second maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve 13 is the maximum allowable tilt angle θ max , the axial length of the eccentric sleeve 13 is h2, σ max ,θ max And h2 satisfies: σ max =tanθ max *h2. The maximum permissible inclination angle θ of the orbiting scroll 20 is max is less than or equal to 0.387, the maximum oil film clearance value σ corresponding to the maximum allowable inclination angle of the orbiting scroll 20 can be determined max =0.0067*h2.

[0079] Reference Figure 1 and Figure 2 According to the compression mechanism 100 of the second embodiment of the present invention, the compression mechanism 100 is designed according to the design method of the above-mentioned first embodiment.

[0080] Reference Fig.10 Compared with the compression mechanism in the related art, when the rotation speed of the compressor 200 is the same, the compression mechanism 100 of the embodiment of the present application has a smaller sound power level and generates less noise; and as the rotation speed of the compressor 200 increases, the sound power level increases, and the noise reduction effect of the compression mechanism 100 of the embodiment of the present application becomes more obvious.

[0081] According to the compression mechanism 100 of the embodiment of the present invention, the compression mechanism 100 is designed according to the above-mentioned design method, and the radial dimension of the oil film gap 40 between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ maxThe distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0082] Reference Figure 5-Figure 8 , according to some embodiments of the present invention, σ = d1 - d2, σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing 30, d2 is the outer diameter of the eccentric sleeve 13, h2 is the axial length of the eccentric sleeve 13, the units of d1, d2 and h2 are all mm, and a, b and c are all preset values ​​greater than 0. Among them, the value of a can be 0.001, the value of c can be 0.045, and the value of b can be 0.0067, so that the radial dimension σ of the oil film gap 40 can be within a suitable range.

[0083] If the size of the oil film gap 40 between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is too small, it is easy to cause contact wear between the eccentric sleeve 13 and the sliding bearing 30 and generate noise; if the size of the oil film gap 40 is too large, the movable scroll 20 is easily tilted under the combined influence of the inertia moment, the lateral gas moment, the axial gas moment, etc. in the working state, so that the movable scroll 20 drives the sliding bearing 30 to tilt, and the sliding bearing 30 contacts the eccentric shaft 12, which easily leads to serious wear between the sliding bearings 30 and shortens the service life of the compressor 200.

[0084] When the inner diameter d1 of the sliding bearing 30, the outer diameter d2 of the eccentric sleeve 13, and the axial length h2 of the eccentric sleeve 13 satisfy the above matching relationship, the radial dimension σ of the oil film gap 40 is within a suitable range. min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0085] Optionally, when the inner diameter d1 of the sliding bearing 30, the outer diameter d2 of the eccentric sleeve 13 and the axial length h2 of the eccentric sleeve 13 satisfy the above-mentioned matching relationship, when the inner diameter of the sliding bearing 30 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the outer diameter of the eccentric sleeve 13, so that the radial dimension σ of the oil film gap 40 is within an appropriate range; or, when the outer diameter of the eccentric sleeve 13 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30, so that the radial dimension σ of the oil film gap 40 is within an appropriate range; or, when the outer diameter of the eccentric sleeve 13 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30, so that the radial dimension σ of the oil film gap 40 is within an appropriate range.

[0086] Reference Figure 1-Figure 4 The compression mechanism 100 according to the third embodiment of the present invention comprises: a crankshaft assembly 10, a compression component and a sliding bearing 30, wherein the crankshaft assembly 10 comprises a crankshaft 11, an eccentric shaft 12 and an eccentric sleeve 13, wherein one end of the eccentric shaft 12 is connected to the crankshaft 11, and the eccentric sleeve 13 is sleeved on the other end of the eccentric shaft 12; the compression component comprises a movable scroll 20 and a fixed scroll that cooperate with each other; the sliding bearing 30 is arranged on the movable scroll 20, for example, the sliding bearing 30 and the movable scroll 20 can be riveted, clamped or welded, and the movement of the movable scroll 20 can drive the sliding bearing 30 to move accordingly. The compression mechanism 100 according to the third embodiment of the present invention can also be designed according to the design method of the first embodiment described above.

[0087] Reference Figure 4 and Figure 5 The sliding bearing 30 is sleeved on the outer peripheral side of the eccentric sleeve 13, and an oil film gap 40 is formed between the inner peripheral surface of the sliding bearing 30 and the outer peripheral surface of the eccentric sleeve 13. The radial dimension σ of the oil film gap 40 satisfies: σ min ≤σ≤σ max , where σ=d1-d2, σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing 30, d2 is the outer diameter of the eccentric sleeve 13, h2 is the axial length of the eccentric sleeve 13, the units of d1, d2 and h2 are all mm, and a, b, c are all preset values ​​greater than 0.

[0088] The value of a may be 0.001, the value of c may be 0.045, and the value of b may be 0.0067, so that the radial dimension σ of the oil film gap 40 is within a suitable range.

[0089] If the size of the oil film gap 40 between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is too small, it is easy to cause contact wear between the eccentric sleeve 13 and the sliding bearing 30 and generate noise; if the size of the oil film gap 40 is too large, the movable scroll 20 is easily tilted under the combined influence of the inertia moment, the lateral gas moment, the axial gas moment, etc. in the working state, so that the movable scroll 20 drives the sliding bearing 30 to tilt, and the sliding bearing 30 contacts the eccentric shaft 12, which easily leads to serious wear between the sliding bearings 30 and shortens the service life of the compressor 200.

[0090] When the inner diameter d1 of the sliding bearing 30, the outer diameter d2 of the eccentric sleeve 13, and the axial length h2 of the eccentric sleeve 13 satisfy the above matching relationship, the radial dimension σ of the oil film gap 40 is within a suitable range. min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0091] Reference Fig.10 Compared with the compression mechanism in the related art, when the rotation speed of the compressor 200 is the same, the compression mechanism 100 of the embodiment of the present application has a smaller sound power level and generates less noise; and as the rotation speed of the compressor 200 increases, the sound power level increases, and the noise reduction effect of the compression mechanism 100 of the embodiment of the present application becomes more obvious.

[0092] Optionally, when the inner diameter d1 of the sliding bearing 30, the outer diameter d2 of the eccentric sleeve 13 and the axial length h2 of the eccentric sleeve 13 satisfy the above-mentioned matching relationship, when the inner diameter of the sliding bearing 30 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the outer diameter of the eccentric sleeve 13, so that the radial dimension σ of the oil film gap 40 is within an appropriate range; or, when the outer diameter of the eccentric sleeve 13 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30, so that the radial dimension σ of the oil film gap 40 is within an appropriate range; or, when the outer diameter of the eccentric sleeve 13 is constant, the radial dimension σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30, so that the radial dimension σ of the oil film gap 40 is within an appropriate range.

[0093] In some embodiments of the present invention, reference Figure 1 and Figure 2The compression mechanism 100 may further include a bracket 50 , and the bracket 50 is used to support the movable scroll 20 .

[0094] According to the compression mechanism 100 of the embodiment of the present invention, the radial dimension of the oil film gap 40 between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0095] The compressor 200 according to the fourth aspect of the embodiment of the present invention comprises: the compression mechanism 100 according to the above-mentioned present invention.

[0096] Optionally, the compressor 200 may further include a housing and a motor component. When the compressor 200 is in operation, the motor component may drive the crankshaft 11 to rotate at high speed, the crankshaft 11 drives the eccentric shaft 12 to rotate, the eccentric shaft 12 drives the eccentric sleeve 13 to rotate, and the eccentric sleeve 13 may drive the orbiting scroll 20 to move relative to the fixed scroll. A compression chamber is formed between the fixed scroll and the orbiting scroll 20, and there is refrigerant in the compression chamber. When the compressor 200 is in operation, the refrigerant in the compression chamber completes the process of suction, compression and exhaust in the compression chamber.

[0097] According to the compressor 200 of the embodiment of the present invention, by setting the above-mentioned compression mechanism 100, the radial dimension of the oil film gap 40 between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0098] The vehicle 1000 according to the fifth aspect of the present invention comprises: the compressor 200 according to the fourth aspect of the present invention.

[0099] Here, vehicle 1000 can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with a motor as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid vehicle with an internal combustion engine and a motor as the main driving force. Regarding the internal combustion engine and motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy for the motor can use power batteries, hydrogen fuel cells, etc., which are not specifically limited here. It should be noted that this is only an exemplary description of the structure of new energy vehicles, etc., and it does not limit the scope of protection of the present invention.

[0100] According to the vehicle 1000 of the embodiment of the present invention, by providing the compressor 200, the radial dimension of the oil film gap 40 between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 has a suitable range, and the oil film gap value is not less than σ min The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too small, which can avoid or reduce the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13; the oil film clearance value is not greater than σ max The distance between the inner circumference of the sliding bearing 30 and the outer circumference of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact wear between the eccentric shaft 12 and the sliding bearing 30 when the movable scroll 20 is tilted, so as to ensure the service life of the compressor 200.

[0101] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0102] In the description of the present invention, a first feature being “on” or “under” a second feature may include that the first and second features are directly in contact with each other, or may include that the first and second features are not in direct contact with each other but are in contact with each other via another feature therebetween.

[0103] In the description of the present invention, “on”, “over” and “above” a first feature from a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature.

[0104] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0105] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A method for designing a compression mechanism, characterized in that: The compression mechanism includes a crankshaft assembly, a compression component and a sliding bearing. The crankshaft assembly includes a crankshaft, an eccentric shaft and an eccentric sleeve. One end of the eccentric shaft is connected to the crankshaft, and the eccentric sleeve is sleeved on the other end of the eccentric shaft. The compression component includes a movable scroll and a fixed scroll that cooperate with each other. The sliding bearing is provided on the movable scroll and sleeved on the outer peripheral side of the eccentric sleeve. An oil film gap is formed between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve. The design method includes: When the movable scroll does not tilt relative to the eccentric sleeve, the minimum oil film clearance value to ensure the smooth and normal operation of the compression mechanism is σ min ; When the movable scroll is tilted relative to the eccentric sleeve, the maximum oil film clearance value corresponding to the maximum allowable tilt angle of the movable scroll is σ max ; The radial dimension σ of the oil film gap satisfies: σ min ≤σ≤σ max .

2. The method for designing a compression mechanism according to claim 1, characterized in that: When the orbiting scroll does not tilt relative to the eccentric sleeve, the maximum bearing capacity of the oil film in the oil film gap is the first maximum bearing capacity of the oil film, and the oil film gap value obtained when the first maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve is the σ min .

3. The design method of a compression mechanism according to claim 2, characterized in that: The maximum bearing capacity of the first oil film is the bearing capacity of the sliding bearing and the eccentric sleeve at the meshing point, and the meshing point is the position where the distance between the sliding bearing and the eccentric sleeve is the smallest.

4. The design method of a compression mechanism according to claim 1, characterized in that: The maximum allowable inclination angle of the movable scroll is θ max , the axial length of the eccentric sleeve is h2, where σ max ,θ max And h2 satisfies: σ max =tanθ max *h2.

5. The method for designing a compression mechanism according to claim 1, characterized in that: The maximum allowable inclination angle θ of the orbiting scroll max Less than or equal to 0.

387.

6. The method for designing a compression mechanism according to claim 1, characterized in that: When the movable scroll plate is tilted relative to the eccentric sleeve, the maximum bearing capacity of the oil film in the oil film gap is the second maximum bearing capacity of the oil film, and the allowable inclination angle obtained when the second maximum bearing capacity of the oil film is equal to the maximum inertia force of the eccentric sleeve is the maximum allowable inclination angle.

7. The method for designing a compression mechanism according to claim 6, characterized in that: The second maximum oil film bearing capacity is the bearing capacity at the oil film minimum radial thickness in the oil film gap.

8. A compression mechanism, characterized in that: The compression mechanism is designed according to the design method described in any one of claims 1-7.

9. The compression mechanism according to claim 8, characterized in that: σ=d1-d2,σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing, d2 is the outer diameter of the eccentric sleeve, h2 is the axial length of the eccentric sleeve, the units of d1, d2 and h2 are all mm, and a, b, c are all preset values ​​greater than 0.

10. The compression mechanism according to claim 9, characterized in that: The value of a is 0.001, the value of c is 0.045, and the value of b is 0.0067.

11. A compression mechanism, characterized in that: include: A crankshaft assembly, comprising a crankshaft, an eccentric shaft and an eccentric sleeve, wherein one end of the eccentric shaft is connected to the crankshaft, and the eccentric sleeve is sleeved on the other end of the eccentric shaft; A compression component, the compression component comprising a movable scroll and a fixed scroll that cooperate with each other; A sliding bearing is provided on the movable scroll and sleeved on the outer peripheral side of the eccentric sleeve, an oil film gap is formed between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the eccentric sleeve, and the radial dimension σ of the oil film gap satisfies: σ min ≤σ≤σ max , where σ=d1-d2, σ min =a*d2+c,σ max =b*h2, d1 is the inner diameter of the sliding bearing, d2 is the outer diameter of the eccentric sleeve, h2 is the axial length of the eccentric sleeve, the units of d1, d2 and h2 are all mm, and a, b, c are all preset values ​​greater than 0.

12. The compression mechanism according to claim 11, characterized in that: The value of a is 0.001, the value of c is 0.045, and the value of b is 0.0067.

13. A compressor, characterized in that: include: A compression mechanism according to any one of claims 8 to 12.

14. A vehicle, characterized in that: include: A compressor according to claim 13.

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