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

Abstract

The application 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, a sliding bearing is arranged on a dynamic scroll plate and is sleeved on the outer circumferential side of the eccentric sleeve, an oil film gap is formed between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve, and the design method comprises the following steps: in the case that the dynamic scroll plate does not tilt relative to the eccentric sleeve, the minimum oil film gap value σ min ensuring the smooth and normal working of the compression mechanism; in the case that the dynamic scroll plate tilts relative to the eccentric sleeve, the maximum oil film gap value σ max corresponding to the maximum allowable tilting angle of the dynamic scroll plate; and the radial dimension σ of the oil film gap satisfies the following formula: σ min ≤ σ ≤ σ max . According to the design method of the compression mechanism, the wear between the eccentric sleeve and the sliding bearing can be avoided or reduced, the noise can be reduced, the contact between the eccentric shaft and the sliding bearing in the case that the dynamic scroll plate tilts can be avoided or reduced, and the service life of the compressor can be ensured.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a design method of a compression mechanism, a compression mechanism, a compressor and a vehicle. BACKGROUND

[0002] The mechanical noise generated by the compressor is mainly generated by the contact of the dynamic scroll disc, the static scroll disc and the eccentric sleeve and other components. In the related art, the dynamic scroll disc inside the compressor is connected with the eccentric sleeve through the embedded sliding bearing, and there is a certain oil film gap between the sliding bearing and the eccentric sleeve to generate oil film lubrication. However, due to the unreasonable design of the oil film gap, the dynamic scroll disc drives the sliding bearing to tilt under the action of gas force and inertial force and other forces during the operation of the compressor, which changes the surface contact between the sliding bearing and the eccentric sleeve into line contact, and long-time work easily leads to the wear of the sliding bearing, greatly shortening the service life of the compressor. SUMMARY

[0003] The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a design method of a compression mechanism, the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential 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 circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too small, so as to avoid or reduce the noise generated by the contact friction between the sliding bearing and the eccentric sleeve; and the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too large, so as to avoid or reduce the contact wear between the eccentric shaft and the sliding bearing under the condition of tilting of the dynamic scroll disc, so as to ensure the service life of the compressor.

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

[0005] The present application also provides a compression mechanism.

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

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

[0008] According to a design method for a compression mechanism based on a 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, and the eccentric sleeve is fitted onto the other end of the eccentric shaft. The compression component includes a moving scroll and a stationary scroll that cooperate with each other. The sliding bearing is disposed on the moving scroll and fitted onto the outer periphery of the eccentric sleeve. An oil film gap is formed between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve. The design method includes: when the moving scroll is not tilted relative to the eccentric sleeve, the minimum oil film gap value for ensuring the smooth and normal operation of the compression mechanism is σ. min When the moving scroll plate is tilted relative to the eccentric sleeve, the maximum oil film clearance value corresponding to the maximum allowable tilt angle of the moving scroll plate is σ. max The radial dimension σ of the oil film gap shall satisfy: σ min ≤σ≤σ max .

[0009] According to the design method of the compression mechanism of the present invention, the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential 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 circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve should not be too small to avoid or reduce noise generated by contact friction between the sliding bearing and the eccentric sleeve; the oil film clearance value should not exceed σ. max The gap between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve should not be too large, which can avoid or reduce the contact wear between the eccentric shaft and the sliding bearing when the moving 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 moving scroll disk is not tilted 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. The oil film gap value obtained when the first maximum bearing capacity of the oil film is equal to the maximum inertial 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 minimum.

[0012] According to some embodiments of the present invention, the maximum permissible tilt angle of the moving scroll disk 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 application, the maximum allowable inclination angle θ max is less than or equal to 0.387°.

[0014] According to some embodiments of the present application, in the case that the orbiting scroll is inclined relative to the eccentric sleeve, the maximum load capacity of the oil film in the oil film gap is a second oil film maximum load capacity, and the allowable inclination angle obtained when the second oil film maximum load capacity is equal to the maximum inertial force of the eccentric sleeve is a maximum allowable inclination angle.

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

[0016] The compression mechanism according to the second aspect of the embodiments of the present application is designed according to the design method according to the first aspect of the embodiments described above.

[0017] The compression mechanism according to the embodiments of the present application is designed according to the design method described above, and the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve has a suitable range, so that the value of the oil film gap is not less than σ min , and the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too small, so that noise generated by the contact friction between the sliding bearing and the eccentric sleeve can be avoided or reduced; and the value of the oil film gap is not greater than σ max , and the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too large, so that the contact wear between the eccentric shaft and the sliding bearing in the case that the orbiting scroll is inclined can be avoided or reduced, so as to ensure the service life of the compressor.

[0018] According to some embodiments of the present application, 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, d1, d2 and h2 are all in mm, and a, b and c are all preset values greater than 0.

[0019] According to some optional embodiments of the present application, 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 the compression mechanism of the third aspect of the present application, the compression mechanism comprises: a crankshaft assembly, comprising 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, comprising a dynamic scroll and a static scroll matched with each other; and a sliding bearing, which is arranged on the dynamic scroll and is sleeved on the outer circumferential side of the eccentric sleeve, and an oil film gap is formed between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve, and the radial dimension σ of the oil film gap satisfies: σ min ≤σ≤σ max , wherein 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, and h2 is the axial length of the eccentric sleeve, the units of d1, d2 and h2 are mm, and a, b and c are preset values greater than 0.

[0021] According to the compression mechanism of the present application, the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve has a suitable range, the oil film gap value is not less than σ min , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too small, and the noise generated by the contact friction between the sliding bearing and the eccentric sleeve can be avoided or reduced; and the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too large, and the contact wear between the eccentric shaft and the sliding bearing in the case of tilting of the dynamic scroll can be avoided or reduced, so as to ensure the service life of the compressor.

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

[0023] According to the compressor of the fourth aspect of the present application, the compressor comprises the compression mechanism according to the above embodiments of the present application.

[0024] According to the compressor of the present application, by arranging the above compression mechanism, the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve has a suitable range, the oil film gap value is not less than σ min , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too small, and the noise generated by the contact friction between the sliding bearing and the eccentric sleeve can be avoided or reduced; and the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too large, and the contact wear between the eccentric shaft and the sliding bearing in the case of tilting of the dynamic scroll can be avoided or reduced, so as to ensure the service life of the compressor.

[0025] The vehicle according to the fifth aspect of the present application comprises the compressor according to the fourth aspect of the present application.

[0026] The vehicle according to the present application has the compressor described above, so that the radial dimension of the oil film gap between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve has a proper range, the oil film gap value is not less than σ min , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too small, and the noise caused by the contact friction between the sliding bearing and the eccentric sleeve can be avoided or reduced; the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve is not too large, and the contact wear between the eccentric shaft and the sliding bearing in the case of the tilt of the orbiting scroll can be avoided or reduced, so as to ensure the service life of the compressor.

[0027] Additional aspects and advantages of the present application will be made apparent from the following description of embodiments, which proceeds with reference to the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0028] The above and / or additional aspects and advantages of the present application will become apparent and be readily appreciated from the following description of embodiments, taken in conjunction with the accompanying drawings, in which:

[0029] Figure 1 is a structural schematic diagram of a compressor according to some embodiments of the present application;

[0030] Figure 2 is a sectional view of the compressor in Figure 1

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

[0032] Figure 4 is a sectional view of the cooperation between the eccentric sleeve and the orbiting scroll in Figure 3 , wherein the orbiting scroll does not tilt relative to the eccentric sleeve;

[0033] Figure 5 is a partial sectional view of the cooperation between the eccentric sleeve and the orbiting scroll in Figure 3 , wherein the orbiting scroll does not tilt relative to the eccentric sleeve;

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

[0035] Figure 7 ​is a cross-sectional view of an eccentric sleeve and a orbiting scroll according to some embodiments of the present application, in which the orbiting scroll is tilted relative to the eccentric sleeve;

[0036] Figure 8 is Figure 7 is an enlarged view of A in FIG. 1;

[0037] Figure 9 is a schematic view of a vehicle according to some embodiments of the present application;

[0038] Figure 10 is a comparison of sound power level of a compressor according to some embodiments of the present application and a compressor in the related art.

[0039] Reference Signs:

[0040] 1000, vehicle; 200, compressor;

[0041] 100, compressor mechanism;

[0042] 10, crankshaft assembly; 11, crankshaft; 12, eccentric shaft; 13, eccentric sleeve;

[0043] 20, orbiting scroll; 30, sliding bearing; 40, oil film gap; 50, bracket; 60, meshing point. DETAILED DESCRIPTION

[0044] Embodiments of the present application are described in detail below with reference to the attached drawing figures, wherein the same or like designations indicate the same or like elements or elements having the same or similar function throughout the attached drawing figures. The embodiments described below are presented by way of example only, and are not intended to limit the present application as defined by the appended claims.

[0045] A design method of a compressor mechanism 100 according to embodiments of the present application is described below with reference to the attached drawing figures.

[0046] Referring to Figures 1-2 , the design method of the compressor mechanism 100 according to the first aspect embodiment of the present application, the compressor 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, the eccentric sleeve 13 is sleeved on the other end of the eccentric shaft 12, the compression component includes an orbiting scroll 20 and a fixed scroll which cooperate with each other. For example, the compressor mechanism 100 can also include a bracket 50, the bracket 50 is used to support the orbiting scroll 20.

[0047] Referring to Figures 3-5, the sliding bearing 30 is arranged on the orbiting scroll 20 and sleeved on the outer circumferential side of the eccentric sleeve 13, an oil film gap 40 is formed between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13, and the design method comprises the following steps: in the case that the orbiting scroll 20 does not tilt relative to the eccentric sleeve 13, the minimum oil film gap value σ min .

[0048] The orbiting scroll 20 does not tilt 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; in the case that the orbiting scroll 20 does not tilt relative to the eccentric sleeve 13, the stable and normal working of the compression mechanism 100 means that the inner circumferential surface of the sliding bearing 30 does not contact the outer circumferential surface of the eccentric sleeve 13.

[0049] When the size 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 is too small, the oil film gap value is too small, the oil film carrying capacity is insufficient, and when the oil film is subjected to an external force, the oil film is easily damaged, so that the inner circumferential surface of the sliding bearing 30 contacts the outer circumferential surface of the eccentric sleeve 13 and noise is generated.

[0050] Therefore, in the case that the orbiting scroll 20 does not tilt 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 and rub, and therefore it is necessary to determine the minimum value σ min of the oil film gap 40. min The minimum value σ min of the oil film gap 40 can be 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 when the sliding bearing 30 and the eccentric sleeve 13 are at a critical point between contact and non-contact. When the oil film gap 40 is not less than σ min , the oil film carrying capacity can resist the external force acting on the oil film, so that the oil film can be maintained, thereby ensuring that the compression mechanism 100 can work stably and normally in the case that the orbiting scroll 20 does not tilt relative to the eccentric sleeve 13.

[0051] Referring to Figure 7 and Figure 8 , in the case that the orbiting scroll 20 tilts relative to the eccentric sleeve 13, the maximum oil film gap value σ max corresponding to the maximum allowable tilt angle of the orbiting scroll 20 is determined.

[0052] The orbiting scroll 20 tilts relative to the eccentric sleeve 13, so that the sliding bearing 30 tilts relative to the eccentric sleeve 13, and it can be considered that there is a certain included 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 tilt angle of the orbiting scroll plate 20 relative to the eccentric sleeve 13 is too large, which causes the axial oil film gap to be unevenly distributed, and the load bearing capacity of the oil film at the minimum position of the axial oil film gap is difficult to support the orbiting scroll plate 20. Under the combined effects of the inertia moment, the lateral gas moment, the axial gas moment and the like in the working state, the orbiting scroll plate 20 is prone to tilting, thereby causing the orbiting scroll plate 20 to tilt the sliding bearing 30, and the sliding bearing 30 to contact the eccentric shaft 12. This can easily cause the sliding bearing 30 to be severely worn, and shorten the service life of the compressor 200.

[0054] When the orbiting scroll plate 20 tilts relative to the eccentric sleeve 13, the greater the tilt angle of the orbiting scroll plate 20, the smaller the maximum load bearing capacity of the oil film in the oil film gap 40. When the orbiting scroll plate 20 tilts to the point where the sliding bearing 30 is about to contact the eccentric sleeve 13, the tilt angle of the orbiting scroll plate 20 is the largest, but the maximum load bearing capacity of the oil film is small. The tilt angle of the orbiting scroll plate 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 can cause the sliding bearing 30 to contact the eccentric sleeve 13.

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

[0056] By determining the maximum oil film gap value σ max , the radial size σ of the oil film gap 40 between the sliding bearing 30 and the eccentric sleeve 13 can be ensured to be within an appropriate range. In the case where the orbiting scroll plate 20 tilts relative to the eccentric sleeve 13, the contact and wear between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced, thereby ensuring the service life of the compressor 200.

[0057] The radial size σ of the oil film gap 40 satisfies: σ min ≤ σ ≤ σ max . By ensuring that the oil film gap value is not less than σ min , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface 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. By ensuring that the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, which can avoid or reduce the contact and wear between the eccentric shaft 12 and the sliding bearing 30 in the case where the orbiting scroll plate 20 tilts, thereby ensuring the service life of the compressor 200.

[0058] Referring toFigure 10 Compared with the compression mechanism in the related art, the sound power level of the compression mechanism 100 is smaller, and the noise generated is smaller under the same rotation speed of the compressor 200, and the noise reduction effect of the compression mechanism 100 is more obvious as the rotation speed of the compressor 200 increases.

[0059] According to the design method of the 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 circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, so that the noise generated by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced, and the oil film gap value is not greater than σ max The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, so that the contact wear between the eccentric shaft 12 and the sliding bearing 30 under the tilting condition of the orbiting scroll 20 can be avoided or reduced, and the service life of the compressor 200 is ensured.

[0060] According to some embodiments of the application, under the condition that the orbiting scroll 20 does not tilt relative to the eccentric sleeve 13, the maximum bearing capacity of the oil film in the oil film gap 40 is a first oil film maximum bearing capacity, and the oil film gap value obtained when the first oil film maximum bearing capacity 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, discharge pressure, suction temperature, discharge temperature and displacement of the compressor 200.

[0062] When the oil film gap 40 is small, the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is small, and the orbiting scroll 20 is not easy to tilt relative to the eccentric sleeve 13, but when the oil film gap 40 is too small, the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is too small, and the sliding bearing 30 and the eccentric sleeve 13 are easy to contact and rub.

[0063] Therefore, under the condition that the orbiting scroll 20 does not tilt 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 and rub, and 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] In the case that the dynamic scroll 20 does not tilt relative to the eccentric sleeve 13, when the oil film gap value is larger, the first oil film maximum load capacity is larger. When the first oil film maximum load capacity is not smaller than the maximum inertial force of the eccentric sleeve 13, the oil film can be maintained, and the oil film is not easily damaged, and the sliding bearing 30 and the eccentric sleeve 13 are not easily in contact. Thus, when the first oil film maximum load capacity is equal to the maximum inertial force of the eccentric sleeve 13, the sliding bearing 30 and the eccentric sleeve 13 are at a critical point of contact and non-contact, and at this time, the oil film gap 40 has a minimum value, so that the minimum oil film gap value σ min .

[0065] With reference to Figure 6 , according to some optional embodiments of the present application, the first oil film maximum load capacity is the load capacity of the sliding bearing 30 and the eccentric sleeve 13 at the meshing point 60 position, which is the minimum distance position between the sliding bearing 30 and the eccentric sleeve 13.

[0066] At the minimum distance position 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 and the eccentric sleeve 13 are more easily in contact. When the oil film load capacity at the meshing point 60 position is not smaller than the maximum inertial force of the eccentric sleeve 13, it can be ensured that the oil film at the meshing point 60 position is not damaged, and the sliding bearing 30 and the eccentric sleeve 13 are not in contact.

[0067] Thus, by ensuring that the position with the minimum distance between the sliding bearing 30 and the eccentric sleeve 13 is not in contact, it can be ensured that the other positions of the sliding bearing 30 and the eccentric sleeve 13 will not also be in contact and wear, so that it can be ensured that the compression mechanism 100 can work smoothly and normally in the case that the dynamic scroll 20 does not tilt relative to the eccentric sleeve 13.

[0068] With reference to Figure 8 , according to some embodiments of the present application, the maximum allowable tilt angle of the dynamic scroll 20 is θ max , the axial length of the eccentric sleeve 13 is h2, and σ max , θ max , and h2 satisfy: σ max =tanθ max * h2. According to the maximum allowable tilt angle θ max and the axial length of the eccentric sleeve 13, the maximum oil film gap value σ max can be determined, and the determined data is more accurate, so that the radial dimension σ of the oil film gap 40 has a smaller error in the actual design process, and the compressor 200 can work more smoothly and normally.

[0069] The maximum allowable tilt angle θ max of the dynamic scroll 20 can be less than or equal to 0.387°. For example, the maximum allowable tilt angle θmax equal to 0.387°, and in combination with σ max = tan θ max * h2, a relationship that can be determined is σ max = 0.0067 * h2. Thus, at the maximum allowable tilt angle θ max max of the orbiting scroll 20, the oil film gap 40 satisfies a condition of being less than or equal to 0.387°, and in combination with σ

[0070] It should be noted that the angle of the present embodiment is in units of degrees, and the maximum allowable tilt angle θ max max is less than or equal to 0.387°, which means that the maximum allowable tilt angle θ max max is less than or equal to 0.387 degrees.

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

[0072] When the orbiting scroll 20 is tilted relative to the eccentric sleeve 13, the greater the tilt angle of the orbiting scroll 20, the smaller the maximum load capacity of the oil film, and when the maximum load capacity of the oil film is the second maximum load capacity of the oil film, it is equal to the maximum inertial force of the eccentric sleeve 13, at which time the oil film can also separate the eccentric sleeve 13 and 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 orbiting scroll 20 is not allowed to continue to increase, and if it continues to increase, the maximum load capacity of the oil film is less than the maximum inertial force of the eccentric sleeve 13, and the oil film is easily damaged, which can result in contact between the sliding bearing 30 and the eccentric sleeve 13.

[0073] Thus, when the orbiting 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 come into contact. When the sliding bearing 30 and the eccentric sleeve 13 are at the critical point of being in contact and not in contact, the second maximum load capacity of the oil film is equal to the maximum inertial force of the eccentric sleeve 13, and the oil film is not damaged, at which time the tilt angle of the orbiting scroll 20 is the maximum allowable tilt angle θ max max. The maximum allowable tilt angle θ max max can be determined by the second maximum load capacity of the oil film being equal to the maximum inertial force of the eccentric sleeve 13. The maximum oil film gap value σ maxFor example, in combination with the above σ max = tan θ max * h2, θ max = 0.387°, σ max = 0.0067* h2.

[0074] According to some optional embodiments of the present application, the second oil film maximum load capacity is the load capacity at the radial minimum thickness of the oil film in the oil film gap 40. The radial minimum 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, and the load capacity of the oil film is the smallest, when the position where the load capacity of the oil film is the smallest can satisfy the maximum inertia force of 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, i.e. it can be ensured that the other positions of the sliding bearing 30 and the eccentric sleeve 13 will not cause contact wear, thereby ensuring the service life of the compressor 200.

[0075] The design method of the compression mechanism 100 according to an embodiment of the present application will be described below with reference to the accompanying drawings. Figures 1-8

[0076] Referring to Figures 1-8 , in this embodiment, the compression mechanism 100 comprises a crankshaft assembly 10, a compression component, a support 50 for supporting the orbiting scroll 20, a sliding bearing 30, the crankshaft assembly 10 comprises 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 comprises an orbiting scroll 20 and a fixed scroll which cooperate with each other; the sliding bearing 30 is arranged on the orbiting scroll 20 and is sleeved on the outer circumferential side of the eccentric sleeve 13, and an oil film gap 40 is formed between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13, and the design method comprises: in the case where the orbiting scroll 20 does not tilt relative to the eccentric sleeve 13, the minimum oil film gap value σ min for ensuring the smooth and normal operation of the compression mechanism 100 is determined; in the case where the orbiting scroll 20 tilts relative to the eccentric sleeve 13, the maximum oil film gap value σ max corresponding to the maximum allowable tilt angle of the orbiting scroll 20 is determined; and the radial size σ of the oil film gap 40 satisfies: σ min ≤ σ ≤ σ max .

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

[0078] When the orbiting scroll 20 tilts relative to the eccentric sleeve 13, the maximum load capacity of the oil film in the oil film gap 40 is a second oil film maximum load capacity, the second oil film maximum load capacity is the load capacity of the oil film at the radially minimum thickness position in the oil film gap 40. The allowable tilting angle obtained when the second oil film maximum load capacity is equal to the maximum inertial force of the eccentric sleeve 13 is a maximum allowable tilting angle θ max , the axial length of the eccentric sleeve 13 is h2, σ max , θ max , and h2 satisfy: σ max =tanθ max * h2. Wherein the maximum allowable tilting angle θ max of the orbiting scroll 20 is less than or equal to 0.387°, it can be determined that the maximum oil film gap value σ max =0.0067* h2 corresponding to the maximum allowable tilting angle of the orbiting scroll 20.

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

[0080] Referring to Figure 10 , compared with the compression mechanism in the related art, the sound power level of the compression mechanism 100 according to the embodiment of the present application is smaller, and the noise generated is smaller under the same rotation speed of the compressor 200; and with the increase of the rotation speed of the compressor 200, the sound power level increases, and the noise reduction effect of the compression mechanism 100 according to the embodiment of the present application is more obvious.

[0081] The compression mechanism 100 according to the embodiment of the present application is designed according to the design method mentioned above, 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 through the oil film gap value being not less than σ min , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, and the noise generated by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; and through the oil film gap value being not greater than σ max, the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 are not too large, and the contact abrasion between the eccentric shaft 12 and the sliding bearing 30 in the case of the tilting of the dynamic scroll plate 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0082] With reference to Figures 5-8 , according to some embodiments of the present application, 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, d1, d2 and h2 are all in mm, and a, b and c are all preset values greater than 0. 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 is in a suitable range.

[0083] When the size 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 is too small, the contact abrasion between the eccentric sleeve 13 and the sliding bearing 30 and the noise are easily caused; when the size of the oil film gap 40 is too large, the dynamic scroll plate 20 is easily tilted under the combined action of the inertial moment, the transverse gas moment and the axial gas moment in the working state, so that the dynamic scroll plate 20 drives the sliding bearing 30 to be tilted, the sliding bearing 30 contacts the eccentric shaft 12, and the serious abrasion between the sliding bearing 30 is easily caused, so as to shorten 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 matching relationship, the radial dimension σ of the oil film gap 40 is in a suitable range. Through the oil film gap value not less than σ min , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, and the noise caused by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; through the oil film gap value not greater than σ max , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, and the contact abrasion between the eccentric shaft 12 and the sliding bearing 30 in the case of the tilting of the dynamic scroll plate 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0085] Optionally, in the case that 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 matching relationship described above, when the inner diameter of the sliding bearing 30 is fixed, the radial size σ of the oil film gap 40 can be adjusted by adjusting the outer diameter of the eccentric sleeve 13, so that the radial size σ of the oil film gap 40 is within the appropriate range; or, in the case that the outer diameter of the eccentric sleeve 13 is fixed, the radial size σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30, so that the radial size σ of the oil film gap 40 is within the appropriate range; or, the radial size σ of the oil film gap 40 can also be adjusted by adjusting the outer diameter of the eccentric sleeve 13 and the inner diameter of the sliding bearing 30, so that the radial size σ of the oil film gap 40 is within the appropriate range.

[0086] With reference to Figures 1-4 , the compression mechanism 100 according to the third aspect of the present application comprises: a crankshaft assembly 10, a compression component, and a sliding bearing 30. The crankshaft assembly 10 comprises 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 comprises a dynamic scroll 20 and a static scroll. The sliding bearing 30 is arranged on the dynamic scroll 20, for example, the sliding bearing 30 and the dynamic scroll 20 can be connected by riveting, clamping, or welding. The dynamic scroll 20 can drive the sliding bearing 30 to move. The compression mechanism 100 according to the third aspect of the present application can also be designed according to the design method of the first aspect of the present application.

[0087] With reference to Figure 4 and Figure 5 , the sliding bearing 30 is sleeved on the outer periphery of the eccentric sleeve 13. An oil film gap 40 is formed between the inner periphery of the sliding bearing 30 and the outer periphery of the eccentric sleeve 13. The radial size 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, and h2 is the axial length of the eccentric sleeve 13. The units of d1, d2, and h2 are mm. a, b, and c are all preset values greater than 0.

[0088] 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 size σ of the oil film gap 40 is within the appropriate range.

[0089] When the size 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 is too small, the contact wear between the eccentric sleeve 13 and the sliding bearing 30 is prone to occur and noise is generated; when the size of the oil film gap 40 is too large, the dynamic scroll plate 20 is prone to tilt under the combined action of the inertial moment, the lateral gas moment, the axial gas moment and the like, so that the sliding bearing 30 is tilted with the dynamic scroll plate 20, the sliding bearing 30 contacts the eccentric shaft 12, and the sliding bearing 30 is prone to serious wear, thereby shortening 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 matching relationship, the radial size σ of the oil film gap 40 is in a proper range. When the oil film gap value is not less than σ min , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, and the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; when the oil film gap value is not greater than σ max , the distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, and the contact wear between the eccentric shaft 12 and the sliding bearing 30 under the tilt of the dynamic scroll plate 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0091] With reference to Figure 10 , compared with the compression mechanism in the related art, the sound power level of the compression mechanism 100 in the embodiment is smaller, and the noise generated is smaller under the same rotation speed of the compressor 200; 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 in the embodiment is 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 matching relationship, the radial size σ of the oil film gap 40 can be adjusted by adjusting the outer diameter of the eccentric sleeve 13 when the inner diameter of the sliding bearing 30 is constant, so that the radial size σ of the oil film gap 40 is in a proper range; or the radial size σ of the oil film gap 40 can be adjusted by adjusting the inner diameter of the sliding bearing 30 when the outer diameter of the eccentric sleeve 13 is constant, so that the radial size σ of the oil film gap 40 is in a proper range; or the radial size σ of the oil film gap 40 can be adjusted by adjusting the outer diameter of the eccentric sleeve 13 and the inner diameter of the sliding bearing 30, so that the radial size σ of the oil film gap 40 is in a proper range.

[0093] In some embodiments of the present application, with reference to Figure 1 and Figure 2The compression mechanism 100 can further include a support 50 for supporting the orbiting scroll 20.

[0094] According to the compression mechanism 100 of the embodiment of the present application, 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, the oil film gap value is not less than σ min The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, so that the noise generated by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; the oil film gap value is not greater than σ max The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, so that the contact wear between the eccentric shaft 12 and the sliding bearing 30 in the case of the inclination of the orbiting scroll 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0095] According to the compressor 200 of the fourth aspect of the embodiment of the present application, it includes the compression mechanism 100 as described above.

[0096] Optionally, the compressor 200 can further include a housing and a motor component. When the compressor 200 is running, the motor component can 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 can drive the orbiting scroll 20 to move relative to the fixed scroll. The fixed scroll and the orbiting scroll 20 form a compression chamber therebetween, and the compression chamber has a refrigerant therein. When the compressor 200 is running, the refrigerant in the compression chamber completes the processes of suction, compression and discharge in the compression chamber.

[0097] According to the compressor 200 of the embodiment of the present application, by setting the compression mechanism 100 as described above, 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, the oil film gap value is not less than σ min The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, so that the noise generated by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; the oil film gap value is not greater than σ max The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, so that the contact wear between the eccentric shaft 12 and the sliding bearing 30 in the case of the inclination of the orbiting scroll 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0098] According to the vehicle 1000 of the fifth aspect of the embodiment of the present application, it includes the compressor 200 as described above according to the fourth aspect of the embodiment of the present application.

[0099] Here, the vehicle 1000 can be a new energy vehicle, and in some embodiments, the new energy vehicle can be a pure electric vehicle with a motor as the main driving force, and 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 the motor mentioned in the above embodiments to provide driving force for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide power for the motor can use power batteries, hydrogen fuel cells, etc. Here, no special limitation is made. It should be noted that here is only an exemplary description of the structure of the new energy vehicle, and is not intended to limit the protection scope of the present application.

[0100] According to the vehicle 1000 of the embodiment of the present application, by arranging the above-mentioned 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 circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too small, so that the noise generated by the contact friction between the sliding bearing 30 and the eccentric sleeve 13 can be avoided or reduced; and the oil film gap value is not greater than σ max The distance between the inner circumferential surface of the sliding bearing 30 and the outer circumferential surface of the eccentric sleeve 13 is not too large, so that the contact wear between the eccentric shaft 12 and the sliding bearing 30 in the case of tilting of the orbiting scroll 20 can be avoided or reduced, so as to ensure the service life of the compressor 200.

[0101] In the description of the present application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0102] In the description of the present application, the first feature "above" or "below" the second feature can include that the first and second features are in direct contact, or can include that the first and second features are not in direct contact but are in contact through another feature between them.

[0103] In the description of the present application, the first feature "above", "above" and "above" the second feature includes that the first feature is directly above and obliquely above the second feature, or only indicates that the first feature is higher than the second feature in horizontal height.

[0104] In the description of the specification, reference to "one embodiment", "some embodiments", "an exemplary embodiment", "an example", "a specific example", or "some examples" means that a particular feature, structure, material, or characteristic being described is included in at least one embodiment or example of the application. The appearances of the phrases "in one embodiment", "in some embodiments", "in an exemplary embodiment", "an example", "a specific example", or "some examples" in various places in the specification are not necessarily referring to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0105] Although embodiments of the application have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions, and alterations can be made hereto without departing from the principles and the scope of the application, which is defined by the claims and their equivalents.

Claims

1. A method of designing a compression mechanism, characterized by, The compression mechanism comprises a crankshaft assembly, a compression component and a sliding bearing, the crankshaft assembly comprises a crankshaft, an eccentric shaft and an eccentric sleeve, one end of the eccentric shaft is connected with the crankshaft, the eccentric sleeve is sleeved on the other end of the eccentric shaft, the compression component comprises a dynamic scroll and a static scroll matched with each other, the sliding bearing is arranged on the dynamic scroll and is sleeved on the outer circumferential side of the eccentric sleeve, an oil film gap is formed between the inner circumferential surface of the sliding bearing and the outer circumferential surface of the eccentric sleeve, and the design method comprises: In the case that the orbiting scroll plate does not tilt relative to the eccentric sleeve, the minimum oil film gap value for ensuring smooth and normal operation of the compression mechanism is σ min ; In the case where the orbiting scroll plate tilts relative to the eccentric sleeve, a maximum oil film gap value corresponding to a maximum allowable tilting angle of the orbiting scroll plate is σ max , the maximum allowable tilting angle of the orbiting scroll plate is θ max , and an axial length of the eccentric sleeve is h2, wherein σ max , θ max , and h2 satisfy: σ max =tanθ max * h2, and the maximum allowable tilting angle θ max of the orbiting scroll plate is less than or equal to 0.387°. The radial dimension of the oil film gap σ is satisfied: σ min ≤ σ ≤ σ max .

2. The design method of a compression mechanism according to claim 1, characterized in that, In the case where the orbiting scroll does not tilt relative to the eccentric sleeve, the maximum load capacity of the oil film in the oil film gap is a first maximum load capacity of the oil film, and the oil film gap value obtained when the first maximum load capacity of the oil film is equal to the maximum inertial force of the eccentric sleeve is the σ min .

3. The method of designing a compression mechanism according to claim 2, wherein, The first oil film maximum carrying capacity is the carrying capacity of the sliding bearing and the eccentric sleeve at the meshing point position, and the meshing point position is the minimum position of the distance between the sliding bearing and the eccentric sleeve.

4. The method of designing a compression mechanism according to claim 1, wherein In the case that the dynamic scroll is inclined relative to the eccentric sleeve, the maximum carrying capacity of the oil film in the oil film gap is a second oil film maximum carrying capacity, and the allowable inclination angle obtained when the second oil film maximum carrying capacity is equal to the maximum inertia force of the eccentric sleeve is a maximum allowable inclination angle.

5. The method of designing a compression mechanism according to claim 4, wherein, The second oil film maximum carrying capacity is the carrying capacity at the radial minimum thickness of the oil film in the oil film gap.

6. A compression mechanism characterized by, The compression mechanism is designed according to the design method in any one of claims 1-5.

7. The compression mechanism of claim 6, wherein, 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 mm, a, b and c are all preset values greater than 0.

8. The compression mechanism of claim 7, wherein, The value of a is 0.001, the value of c is 0.045, and the value of b is 0.0067.

9. A compressor characterized by, Comprise: The compression mechanism according to any one of claims 6-8.

10. A vehicle characterized by comprising: Comprise: The compressor according to claim 9.

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