Low-vibration compressor balancing weight

Abstract

The utility model discloses a low-vibration compressor balancing weight and belongs to the technical field of compressor balancing weights. A low-vibration compressor balancing weight comprises an eccentric shaft part and a balance part, the eccentric shaft part is fixedly connected with the inner side of the balance part, and the eccentric shaft part is used for being detachably connected with an eccentric pin end of a compressor main shaft, so that the balancing weight is driven by the compressor main shaft to synchronously rotate to achieve dynamic balance of a compressor; one side surface, close to the compressor main shaft, of the balance part is an inner side surface; the inner side surface of the balance part is formed by connecting a plurality of cambered surfaces with unequal diameters; the side face, away from the compressor spindle, of the balance part is an outer side face which is in clearance fit with the inner wall of an eccentric balancing weight shaft hole in a compressor faceplate. The inner side face of the balance part is in abutting connection with the compressor spindle and used for supporting the balancing weight, and it is guaranteed that the balancing weight is stable on the compressor spindle.

Description

Technical Field

[0001] The utility model belongs to the field of compressor counterweights, and more specifically, relates to a compressor counterweight with low vibration. Background Art

[0002] Under the background of the gradual depletion of energy and the continuous aggravation of environmental pollution problems, new energy vehicles have obtained active promotion and strong support at the national level due to their dual advantages of environmental protection and energy conservation. Among them, the electric compressor, as a key part in the structure of new energy vehicles, is of great importance. As the heart of the new energy vehicle air conditioning system, the electric compressor plays an irreplaceable role. Factors such as its performance, vibration and noise control, operation reliability, and sealing performance are directly related to the efficient and stable operation of the entire system and are the core elements affecting its working efficiency.

[0003] For the eccentric sleeve counterweight in the prior art, since the diameter of the compressor main shaft is slightly smaller than the inner side diameter of the counterweight, the swing angle of the counterweight is relatively large. During the normal operation of the compressor, due to the large swing angle, the knocking noise is relatively large, and the unbalance of the compressor is also relatively large. Taking the counterweight balance block assembly, compressor, and vehicle-mounted air conditioner (CN201921052817.8) disclosed in the Chinese invention patent document as an example, this invention is provided with a second limiting part on the balance block. When the balance block reciprocally swings relative to the output shaft, the first limiting part can be in abutting cooperation with the second limiting part to limit the swing angle of the balance block, thereby reducing the collision intensity between the balance block and the output shaft and reducing the knocking noise. However, this solution requires opening a slot on the surface of the balance block and also requires additionally matching a corresponding elastic part. The overall structure is relatively complex, and the local opening will change the mass distribution of the balance block, affecting the eccentric effect of the balance block.

[0004] Therefore, we need a balance block with a simple structure and capable of reducing the vibration amplitude of the compressor main shaft relative to the balance block. Summary of the Utility Model

[0005] The technical problem to be solved by the utility model is to provide a compressor counterweight with low vibration, which has a simple structure and is convenient for processing. By setting an inner side with unequal diameters to cooperate with the compressor main shaft, the knocking noise during the normal operation of the compressor is reduced, the low-vibration operation of the counterweight on the compressor main shaft is realized, and the operation stability of the compressor is improved.

[0006] A compressor counterweight with low vibration of the utility model includes an eccentric shaft part and a balance part. The eccentric shaft part is fixedly connected to the inner side of the balance part. The eccentric shaft part is used for detachably connecting with the eccentric pin end of the compressor main shaft, so that the counterweight is driven by the compressor main shaft to rotate synchronously to achieve the dynamic balance of the compressor.

[0007] One side of the balance part close to the main shaft of the compressor is the inner side. The inner side of the balance part is formed by connecting several arc surfaces with different diameters, and is in contact connection with the main shaft of the compressor, used to support the counterweight and ensure the stability of the counterweight on the main shaft of the compressor.

[0008] As a further improvement of the present utility model, the inner side includes the first arc surface, the transition surface and the second arc surface. The first arc surface and the second arc surface are respectively connected to both sides of the transition surface. The main shaft of the compressor is movably connected to the inner side and in surface contact, and the contact surfaces between the main shaft of the compressor and the inner side are respectively on the first arc surface and the second arc surface.

[0009] As a further improvement of the present utility model, the main shaft of the compressor is located between the first arc surface and the second arc surface, and the swing range of the counterweight relative to the main shaft of the compressor is from the position where the main shaft of the compressor contacts the first arc surface to the position where the main shaft of the compressor contacts the second arc surface.

[0010] As a further improvement of the present utility model, the diameter of the circle where the first arc surface is located is larger than the diameter of the circle where the second arc surface is located, which is used to reduce the swing range of the counterweight relative to the main shaft of the compressor, so that the counterweight runs with low vibration on the main shaft of the compressor.

[0011] As a further improvement of the present utility model, the eccentric shaft part is provided with an eccentric pin hole, which is detachably connected to the eccentric pin end of the main shaft of the compressor; an oil inlet groove is opened at the lower part of the eccentric pin hole, which is used for oil to enter the eccentric pin hole for lubrication, so as to reduce wear and noise.

[0012] As a further improvement of the present utility model, one side of the balance part away from the main shaft of the compressor is the outer side, and the outer side is in clearance fit with the inner wall of the eccentric counterweight shaft hole inside the compressor flower disc, so that the counterweight is driven by the compression shaft main shaft and restricted by the inner wall of the eccentric counterweight shaft hole to rotate.

[0013] Compared with the prior art, the beneficial effects of the present utility model are as follows: by setting the inner side of the balance part formed by connecting several arc surfaces with different diameters to be in contact connection with the main shaft of the compressor, the purpose of supporting the counterweight is achieved, the knocking noise during the normal operation of the compressor is reduced, and the operation stability of the compressor is improved; by connecting the main shaft of the compressor with the first arc surface with a large diameter and the second arc surface with a small diameter of the balance part in surface contact respectively, the swing range of the counterweight is limited to the position where the main shaft of the compressor contacts the first arc surface to the position where the main shaft of the compressor contacts the second arc surface, achieving the effect of reducing the swing range of the counterweight relative to the main shaft of the compressor, and realizing the low-vibration operation of the counterweight on the main shaft of the compressor; by arranging an oil inlet groove at the lower part of the eccentric pin hole for oil to enter the eccentric pin hole for lubrication, the purpose of reducing the noise during the operation of the compressor is achieved. Description of the Drawings

[0014] Figure 1Schematic diagram of the assembly structure of the counterweight of the present utility model and the compressor main shaft;

[0015] Figure 2 Schematic diagram of the counterweight structure of the present utility model;

[0016] Figure 3 Schematic diagram of the inner side structure of the present utility model;

[0017] Figure 4 Schematic diagram of the axial cross-sectional structure at the inner side of the present utility model;

[0018] Figure 5 Enlarged schematic diagram of the structure at position A of the present utility model.

[0019] Description of the reference numerals in the figure:

[0020] 1 Eccentric shaft part, 11 Eccentric pin hole, 12 Oil inlet groove, 2 Balancing part, 21 Outer side surface, 22 Inner side surface, 221 First arc surface, 222 Transition surface, 223 Second arc surface, 3 Compressor main shaft, 31 Eccentric pin end. Specific implementation mode

[0021] Specific embodiment 1: Please refer to Figures 1 - 5 A low-vibration compressor counterweight, including an eccentric shaft part 1 and a balancing part 2. The eccentric shaft part 1 is fixedly connected to the inner side of the balancing part 2. The eccentric shaft part 1 is used for detachably connecting with the eccentric pin end 31 of the compressor main shaft 3 in a sleeved manner, so that the counterweight is driven by the compressor main shaft 3 to rotate synchronously to achieve the dynamic balance inside the compressor.

[0022] As shown in Figure 2 One side surface of the balancing part 2 close to the compressor main shaft 3 is the inner side surface 22. The inner side surface 22 of the balancing part 2 is connected by a plurality of arc surfaces with different diameters, and is in contact connection with the compressor main shaft 3, used to support the counterweight and ensure the stability of the counterweight on the compressor main shaft 3, and reduce the swing of the counterweight relative to the compressor main shaft 3.

[0023] Specifically, one side surface of the balancing part 2 away from the compressor main shaft 3 is the outer side surface 21. The outer side surface 21 is in clearance fit with the inner wall of the eccentric counterweight shaft hole inside the compressor flower disc, so that the counterweight rotates under the drive of the compression shaft main shaft 3 and the restriction of the inner wall of the eccentric counterweight shaft hole.

[0024] Specifically, the eccentric shaft part 1 is provided with an eccentric pin hole 11, which is detachably connected with the eccentric pin end 31 of the compressor main shaft 3 in a sleeved manner; an oil inlet groove 12 is opened at the lower part of the eccentric pin hole 11, used for oil to enter the eccentric pin hole 11 through the oil inlet groove 12 from the gap between the counterweight and the compressor main shaft 3 for lubrication, so as to reduce the wear caused by relative rotation between the eccentric pin end 31 and the eccentric pin hole 11, and at the same time achieve the purpose of reducing noise.

[0025] Specifically, as Figure 3 shown, the inner side surface 22 includes a first arc surface 221, a transition surface 222, and a second arc surface 223. The first arc surface 221 and the second arc surface 223 are respectively connected to both sides of the transition surface 222. The compressor main shaft 3 is movably connected to the inner side surface 22 in surface contact, and the contact surfaces between the compressor main shaft 3 and the inner side surface 22 are respectively on the first arc surface 221 and the second arc surface 223. The transition surface 222 is used for the smooth transition from the first arc surface 221 to the second arc surface 223, avoiding large vibrations caused by sudden changes in the contact surface when the counterweight rotates relative to the compressor main shaft 3 due to direct step transitions.

[0026] Specifically, as Figure 4 shown, the compressor main shaft 3 is located between the first arc surface 221 and the second arc surface 223, and the swinging range of the counterweight relative to the compressor main shaft 3 is from the position where the compressor main shaft 3 contacts the first arc surface 221 to the position where the compressor main shaft 3 contacts the second arc surface 223.

[0027] Specifically, as Figure 5 shown, the diameter of the circle where the first arc surface 221 is located is larger than the diameter of the circle where the second arc surface 223 is located. Thus, when the compressor main shaft 3 contacts the first arc surface 221 and drives the counterweight to rotate, causing the counterweight to swing relative to the compressor main shaft 3, since the diameter of the circle where the second arc surface 223 is located is smaller than the diameter of the circle where the first arc surface 221 is located, the swinging range of the counterweight relative to the compressor main shaft 3 is reduced. Furthermore, the counterweight can operate with low vibration on the compressor main shaft 3, thereby reducing the dynamic unbalance generated by the compressor during normal operation, reducing the noise and vibration during the operation of the compressor, and improving the customer experience.

[0028] During the use process, after the counterweight and the compressor main shaft 3 are assembled on the compressor faceplate, the compressor main shaft 3 is driven to rotate. The compressor main shaft 3 drives the counterweight to rotate through the eccentric pin end 31. During the rotation of the counterweight, due to the small gap between the inner side surface 22 of the counterweight and the compressor main shaft 3, the counterweight swings. The compressor main shaft 3 swings from the position where the compressor main shaft 3 contacts the first arc surface 221 to the position where the compressor main shaft 3 contacts the second arc surface 223. Since the diameter of the circle where the second arc surface 223 is located is smaller than the diameter of the circle where the first arc surface 221 is located, the swinging range of the counterweight relative to the compressor main shaft 3 is reduced under the influence of the second arc surface 223, thereby reducing the noise and vibration of the counterweight on the compressor main shaft 3. At the same time, the oil also enters the eccentric pin hole 11 through the oil inlet groove 12 from the gap between the counterweight and the compressor main shaft 3 for lubrication, thereby reducing the wear caused by the rotation of the eccentric pin end 31 relative to the eccentric pin hole 11. At the same time, the purposes of noise reduction and performance improvement are achieved, improving the product reliability and product service life.

[0029] The above are only the preferred specific embodiments of the present utility model; however, the protection scope of the present utility model is not limited thereto. Any person skilled in the art within the technical scope disclosed by the present utility model, according to the technical solution and its improved concept of the present utility model, making equivalent substitutions or changes, should be covered by the protection scope of the present utility model.

Claims

1. A low-vibration compressor counterweight, characterized in that: It comprises an eccentric shaft portion (1) and a balancing portion (2), the eccentric shaft portion (1) being fixedly connected to the inner side of the balancing portion (2), and the eccentric shaft portion (1) being used for being detachably connected to an eccentric pin end (31) of a compressor main shaft (3); A side surface of the balancing portion (2) close to the compressor main shaft (3) is an inner side surface (22); the inner side surface (22) of the balancing portion (2) is formed by connecting a plurality of arc surfaces of unequal diameters, is abuttingly connected to the compressor main shaft (3), and is used to support a counterweight.

2. A low-vibration compressor counterweight according to claim 1, characterized in that: The inner side surface (22) comprises an arc surface 1 (221), a transition surface (222) and an arc surface 2 (223); the arc surface 1 (221) and the arc surface 2 (223) are respectively connected to two sides of the transition surface (222); the compressor main shaft (3) and the inner side surface (22) are movably connected and in surface contact; the contact surfaces of the compressor main shaft (3) and the inner side surface (22) are respectively on the arc surface 1 (221) and the arc surface 2 (223).

3. A low-vibration compressor counterweight according to claim 2, characterized in that: The compressor main shaft (3) is located between the first arc surface (221) and the second arc surface (223), and the swing range of the counterweight relative to the compressor main shaft (3) is from the contact position between the compressor main shaft (3) and the first arc surface (221) to the contact position between the compressor main shaft (3) and the second arc surface (223).

4. A low-vibration compressor counterweight according to claim 3, characterized in that: The diameter of the circle where the arc surface one (221) is located is greater than the diameter of the circle where the arc surface two (223) is located, and is used to reduce the swing range of the counterweight relative to the compressor main shaft (3).

5. A low-vibration compressor counterweight according to claim 1, characterized in that: The eccentric shaft portion (1) is provided with an eccentric pin hole (11) which is detachably connected to the eccentric pin end (31) of the compressor main shaft (3); an oil inlet groove (12) is provided at the lower portion of the eccentric pin hole (11) for oil to enter the eccentric pin hole (11).

6. A low-vibration compressor counterweight according to claim 1, characterized in that: A side surface of the balancing portion (2) that is away from the compressor main shaft (3) is an outer side surface (21), and the outer side surface (21) is clearance-matched with an inner wall of an eccentric counterweight block shaft hole inside the compressor faceplate.

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