CN113494456A - Bearing for compressor and compressor - Google Patents
Bearing for compressor and compressor Download PDFInfo
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- CN113494456A CN113494456A CN202010265920.1A CN202010265920A CN113494456A CN 113494456 A CN113494456 A CN 113494456A CN 202010265920 A CN202010265920 A CN 202010265920A CN 113494456 A CN113494456 A CN 113494456A
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- Prior art keywords
- bearing
- hole
- compressor
- piston
- oil
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- 238000003860 storage Methods 0.000 abstract description 30
- 238000005461 lubrication Methods 0.000 abstract description 7
- 230000003068 static effect Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 105
- 239000010687 lubricating oil Substances 0.000 description 17
- 230000001050 lubricating effect Effects 0.000 description 9
- 238000012545 processing Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 238000012546 transfer Methods 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Compressor (AREA)
Abstract
The invention discloses a bearing for a compressor and the compressor, wherein the bearing is provided with a through hole suitable for a crankshaft to pass through, the surface of the bearing facing a piston is provided with an oil storage groove and an oil delivery channel, the oil storage groove extends along the circumferential direction of the through hole, the oil storage groove is spaced from the through hole, one end of the oil delivery channel is communicated with the oil storage groove, and the other end of the oil delivery channel is communicated with the through hole. According to the bearing for the compressor, static pressure lubrication can be formed between the surface of the bearing facing the piston and the piston, so that the friction resistance between the bearing and the piston can be reduced, the power loss of the compressor can be reduced, and the working performance of the compressor can be improved.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a bearing for a compressor and the compressor.
Background
In the related art, a piston and a bearing in a compressor slide with each other, and the friction resistance between the piston and the bearing is large, so that the power consumption of the compressor is high, and the working performance of the compressor is reduced.
Disclosure of Invention
The invention provides a bearing for a compressor, wherein the friction force between the bearing for the compressor and a piston is relatively small, so that the power loss of the compressor can be reduced, and the working performance of the compressor can be improved.
The invention also provides a compressor, which comprises the bearing for the compressor.
According to the bearing for the compressor, the bearing is provided with the through hole suitable for the crankshaft to pass through, the surface of the bearing facing the piston is provided with the oil storage groove and the oil delivery channel, the oil storage groove extends along the circumferential direction of the through hole, the oil storage groove is spaced from the through hole, one end of the oil delivery channel is communicated with the oil storage groove, and the other end of the oil delivery channel is communicated with the through hole.
According to the bearing for the compressor, the oil storage groove and the oil delivery channel are arranged on the surface, facing the piston, of the bearing, one end of the oil delivery channel is communicated with the oil storage groove, the other end of the oil delivery channel is communicated with the through hole, and lubricating oil between the inner wall of the through hole and the crankshaft can enter the oil storage groove through the oil delivery channel, so that static pressure lubrication can be formed between the surface, facing the piston, of the bearing and the piston, friction resistance between the bearing and the piston can be reduced, power loss of the compressor can be reduced, and working performance of the compressor can be improved.
In some embodiments of the invention, the oil reservoir is formed in a ring shape surrounding the through-hole.
In some embodiments of the present invention, the oil reservoir includes a first side wall adjacent to the center axis of the through-hole and a second side wall facing away from the center axis of the through-hole in a radial direction of the bearing, and the first side wall is inclined toward a direction facing away from the center axis of the through-hole and the second side wall is inclined toward a direction close to the center axis of the through-hole in a direction from the open end of the oil reservoir to the closed end of the oil reservoir.
In some embodiments of the present invention, the included angle between the first sidewall and the second sidewall is α, and satisfies: alpha is more than or equal to 90 degrees and less than or equal to 140 degrees.
In some embodiments of the present invention, the oil reservoir has a depth d1 in the axial direction of the through-hole, and satisfies: d1 is more than or equal to 0.1 mm.
In some embodiments of the present invention, a radius of an outer edge of the piston is M, an eccentric amount of the crankshaft is e, a radius of the through hole is M, a radius of an outer edge of the oil reservoir is R1, a radius of an inner edge of the oil reservoir is R2, and: m is more than R2 and more than R1 and is not more than M-e-2.
In some embodiments of the present invention, the oil delivery passage has a depth d2 in an axial direction of the through hole, and satisfies: d2 is more than or equal to 0.1 mm.
In some embodiments of the invention, the oil transfer passage has a width d3 on the piston-facing surface of the bearing and satisfies: d3 is more than or equal to 1 mm.
In some embodiments of the present invention, a groove is formed on an inner wall of the through hole, one end of the groove communicates with the other end of the oil delivery passage, and the other end of the groove extends in a direction away from the piston.
In some embodiments of the invention, the groove is formed in a spiral shape.
The compressor according to the embodiment of the present invention includes: a motor assembly; a crankshaft connected with the motor assembly, the crankshaft having an eccentric portion; the piston is sleeved on the eccentric part; in the bearing for the compressor, the crankshaft is arranged in the through hole in a penetrating mode, and the bearing is located on one side, close to the motor assembly, of the piston or on one side, far away from the motor assembly.
According to the compressor provided by the embodiment of the invention, the oil storage groove and the oil delivery channel are arranged on the surface of the bearing facing the piston, one end of the oil delivery channel is communicated with the oil storage groove, the other end of the oil delivery channel is communicated with the through hole, and lubricating oil between the inner wall of the through hole and the crankshaft can enter the oil storage groove through the oil delivery channel, so that static pressure lubrication can be formed between the surface of the bearing facing the piston and the piston, the friction resistance between the bearing and the piston can be reduced, the power loss of the compressor can be reduced, and the working performance of the compressor can be improved.
In some embodiments of the present invention, the number of the bearings is two, and the two bearings are respectively located at both sides of the piston in the axial direction.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
FIG. 1 is a front view of a bearing according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view taken at A-A of FIG. 1;
FIG. 3 is a cross-sectional view taken at B-B of FIG. 1;
FIG. 4 is a schematic structural view of a bearing according to an embodiment of the present invention;
fig. 5 is a schematic structural view of a compressor according to an embodiment of the present invention.
Reference numerals:
the compressor 100, the bearing 1, the through-hole 11,
the oil reservoir 12, the first side wall 121, the second side wall 122,
the oil delivery passage 13, the third sidewall 131, the fourth sidewall 132, the groove 14,
motor element 2, bent axle 3, piston 4.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
The following disclosure provides many different embodiments, or examples, for implementing different features of the invention. To simplify the disclosure of the present invention, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. In addition, the present invention provides examples of various specific processes and materials, but one of ordinary skill in the art may recognize the applicability of other processes and/or the use of other materials.
A bearing 1 for a compressor 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
As shown in fig. 1 and 5, according to a bearing 1 for a compressor 100 of an embodiment of the present invention, the bearing 1 has a through-hole 11 adapted to pass a crankshaft 3 therethrough. It is understood that the crankshaft 3 may be inserted into the through hole 11 and rotated in the through hole 11. It should be noted that lubricating oil is provided between the inner wall of the through hole 11 of the bearing 1 and the crankshaft 3 to reduce frictional resistance between the crankshaft 3 and the bearing 1.
As shown in fig. 1 and 5, the surface of the bearing 1 facing the piston 4 has an oil reservoir 12 and an oil delivery passage 13, one end of the oil delivery passage 13 communicates with the oil reservoir 12, and the other end of the oil delivery passage 13 communicates with the through-hole 11. Specifically, in one example of the present invention, the pressure at the oil delivery passage 13 is lower than the pressure in the through hole 11, and the lubricating oil can flow from the through hole 11 toward the oil delivery passage 13 under the action of the pressure difference and then be delivered into the oil reservoir 12 through the oil delivery passage 13. In another example of the present invention, the lubricating oil between the inner wall of the through hole 11 and the crankshaft 3 may flow toward the oil delivery passage 13 by the driving of the crankshaft 3, and then be delivered to the oil reservoir 12 through the oil delivery passage 13.
Accordingly, static pressure lubrication can be formed between the surface of the bearing 1 facing the piston 4 and the piston 4, so that frictional resistance between the bearing 1 and the piston 4 can be reduced, and thus power loss of the compressor 100 can be reduced and the operating performance of the compressor 100 can be improved. In addition, since the frictional resistance between the bearing 1 and the piston 4 is reduced, the service life of the piston 4 and the bearing 1 can be improved.
As shown in fig. 1 and 5, the oil reservoir 12 extends in the circumferential direction of the through-hole 11, and the oil reservoir 12 is spaced apart from the through-hole 11. Therefore, the complexity of the structure of the oil storage tank 12 can be simplified, the difficulty of processing and manufacturing the oil storage tank 12 can be reduced, and the production period and the processing cost of the oil storage tank 12 can be reduced. Furthermore, since the piston 4 and the bearing 1 are relatively rotated, by providing the oil reservoir 12 to extend in the circumferential direction of the through-hole 11, the uniformity of the oiling of the lubricating surface between the piston 4 and the bearing 1 can be improved, and the frictional resistance between the bearing 1 and the piston 4 can be further reduced.
According to the bearing 1 for the compressor 100 provided by the embodiment of the invention, the oil storage groove 12 and the oil delivery channel 13 are arranged on the surface of the bearing 1 facing the piston 4, one end of the oil delivery channel 13 is communicated with the oil storage groove 12, the other end of the oil delivery channel 13 is communicated with the through hole 11, and lubricating oil between the inner wall of the through hole 11 and the crankshaft 3 can enter the oil storage groove 12 through the oil delivery channel 13, so that static pressure lubrication can be formed between the surface of the bearing 1 facing the piston 4 and the piston 4, the friction resistance between the bearing 1 and the piston 4 can be reduced, the power loss of the compressor 100 can be reduced, and the working performance of the compressor 100 can be improved.
In some embodiments of the present invention, as shown in fig. 1 and 5, the reservoir 12 is formed in a ring shape surrounding the through-hole 11. Therefore, the oil storage amount of the oil storage tank 12 can be further increased, so that the distribution of the lubricating oil between the piston 4 and the bearing 1 is more uniform, the friction coefficient between the piston 4 and the bearing 1 is further reduced, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved.
Specifically, through comparative experiments of the bearing 1 (recorded as an experimental group) in the present invention and the bearing in the related art (recorded as a control group), experimental data are as follows:
first experiment of Table
Second experiment
Wherein, COP is the energy efficiency ratio of the compressor, and COP is the ratio of the refrigerating capacity to the input power.
From the above experimental data, it can be found that the input power of the bearing 1 of the present invention is significantly reduced (the reduction amount is more than 25W), the COP is significantly improved (the increase amount is more than 8%), and the working current is also reduced, compared to the bearing of the related art. Further, the wear of the bearing in the control group was severe, while the wear of the bearing 1 in the experimental group was slight.
In some embodiments of the present invention, as shown in fig. 1 and 2, in the radial direction of the bearing 1, the oil reservoir 12 includes a first side wall 121 adjacent to the central axis of the through-hole 11 and a second side wall 122 facing away from the central axis of the through-hole 11, and in the direction from the open end of the oil reservoir 12 to the closed end of the oil reservoir 12 (from top to bottom as shown in fig. 2), the first side wall 121 is inclined toward the direction facing away from the central axis of the through-hole 11, and the second side wall 122 is inclined toward the direction close to the central axis of the through-hole 11.
It can be understood that, in the direction from the open end of the oil reservoir 12 to the closed end of the oil reservoir 12, the first side wall 121 is inclined toward the direction away from the central axis of the through hole 11, and the second side wall 122 is inclined toward the direction close to the central axis of the through hole 11, so that an oil reservoir 12 with a large top opening width and a small bottom width can be formed, thereby reducing the processing difficulty of the oil reservoir 12, reducing the processing cost of the oil reservoir 12, and shortening the processing period of the oil reservoir 12. In addition, the difficulty of overflowing of the lubricating oil from the oil storage tank 12 can be reduced, so that the lubricating oil can overflow to the surface where the piston 4 and the bearing 1 are contacted more easily, and the lubricating effect is improved. For example, in one example of the present invention, the first side wall 121 and the second side wall 122 extend obliquely toward each other in a direction from the open end of the oil reservoir 12 to the closed end of the oil reservoir 12.
In some embodiments of the present invention, as shown in fig. 1, 2 and 5, the included angle between the first sidewall 121 and the second sidewall 122 is α, and satisfies: alpha is more than or equal to 90 degrees and less than or equal to 140 degrees. Therefore, the oil storage amount of the oil storage tank 12 can be further increased, so that the lubricating oil between the piston 4 and the bearing 1 is supplied more sufficiently, the lubricating effect between the piston 4 and the bearing 1 is further increased, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved. For example, in one example of the present invention, the included angle between the first sidewall 121 and the second sidewall 122 is 90 °, 100 °, 110 °, 120 °, 130 °, or 140 °. It should be noted that the first sidewall 121 and the second sidewall 122 may be formed in a V shape.
In some embodiments of the present invention, as shown in fig. 1, 2 and 5, the depth of the reservoir 12 in the axial direction of the through-hole 11 is d1, and satisfies: d1 is more than or equal to 0.1 mm. Therefore, the oil storage amount of the oil storage tank 12 can be further increased, so that the lubricating oil between the piston 4 and the bearing 1 is supplied more sufficiently, the lubricating effect between the piston 4 and the bearing 1 is further increased, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved. For example, in one example of the present invention, the depth of the reservoir 12 in the axial direction of the through-hole 11 is between 0.5 and 1 mm.
In some embodiments of the present invention, as shown in fig. 1, 2 and 5, the radius of the outer edge of the piston 4 is M, the eccentric amount of the crankshaft 3 is e, the radius of the through hole 11 is M, the radius of the outer edge of the oil reservoir 12 is R1, the radius of the inner edge of the oil reservoir 12 is R2, and the following are satisfied: m is more than R2 and more than R1 and is not more than M-e-2. It is understood that the radius of the inner edge of the oil reservoir 12 is larger than M while the radius of the outer edge of the oil reservoir 12 is equal to or smaller than M-e-2, that is, the oil reservoir 12 can be disposed in the sealed region space of the piston 4, whereby the leakage of the lubricating oil in the oil reservoir 12 to the outside of the piston 4 can be prevented, and the reliability of lubrication can be improved.
In some embodiments of the present invention, as shown in fig. 1, 3 and 5, the oil delivery passage 13 has a depth d2 in the axial direction of the through hole 11, and satisfies: d2 is more than or equal to 0.1 mm. Therefore, the oil delivery amount of the oil delivery passage 13 can be further increased, so that the lubricating oil between the piston 4 and the bearing 1 is supplied more sufficiently, the lubricating effect between the piston 4 and the bearing 1 is further increased, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved. For example, in one example of the present invention, the oil delivery passage 13 has a depth in the axial direction of the through-hole 11 of between 0.5 and 1 mm.
In some embodiments of the invention, as shown in fig. 1, 3 and 5, the oil delivery channel 13 has a width d3 on the surface of the bearing 1 facing the piston 4, and satisfies: d3 is more than or equal to 1 mm. Therefore, the oil delivery amount of the oil delivery passage 13 can be further increased, so that the lubricating oil between the piston 4 and the bearing 1 is supplied more sufficiently, the lubricating effect between the piston 4 and the bearing 1 is further increased, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved. For example, in one example of the invention, the oil delivery channel 13 has a width of between 1-10mm on the surface of the bearing 1 facing the piston 4.
In some embodiments of the present invention, as shown in fig. 1, 3 and 5, the oil transfer passage 13 includes a third sidewall 131 and a fourth sidewall 132 opposite to each other, and the third sidewall 131 and the fourth sidewall 132 extend obliquely toward each other in a direction from the open end of the oil transfer passage 13 to the closed end of the oil transfer passage 13 (a direction from top to bottom as shown in fig. 3). Specifically, in one example of the present invention, the included angle between the third sidewall 131 and the fourth sidewall 132 is β, and satisfies: beta is more than or equal to 90 degrees and less than or equal to 120 degrees. Therefore, the oil delivery amount of the oil delivery passage 13 can be further increased, so that the lubricating oil between the piston 4 and the bearing 1 is supplied more sufficiently, the lubricating effect between the piston 4 and the bearing 1 is further increased, the input power of the compressor 100 is further reduced, and the working performance of the compressor 100 is further improved.
In some embodiments of the invention, as shown in fig. 1, 4 and 5, a groove 14 is provided on an inner wall of the through hole 11, one end of the groove 14 communicates with the other end of the oil delivery passage 13, and the other end of the groove 14 extends in a direction away from the piston 4. It can be understood that the lubricant between the through hole 11 and the crankshaft 3 can be delivered into the oil delivery channel 13 through the groove 14, so that not only can the flowing resistance of the lubricant be reduced, but also the flow rate of the delivered lubricant can be increased, thereby improving the lubricating effect between the piston 4 and the bearing 1, reducing the input power of the compressor 100, and improving the working performance of the compressor 100.
In some embodiments of the invention, the groove 14 is formed as a spiral. It can be understood that the spiral groove 14 can further reduce the resistance of the flow of the lubricating oil, and further increase the oil output of the groove 14, so as to further increase the lubricating effect between the piston 4 and the bearing 1, further reduce the input power of the compressor 100, and further improve the working performance of the compressor 100.
A compressor 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings. The compressor 100 may be a rotary compressor.
As shown in fig. 1, 4 and 5, a compressor 100 according to an embodiment of the present invention includes: a motor assembly 2, a crankshaft 3, a piston 4 and a bearing 1 for a compressor 100.
Specifically, bent axle 3 is connected with motor element 2, and bent axle 3 has the eccentric portion, and piston 4 cover is established on the eccentric portion, and bent axle 3 wears to establish in through hole 11, and bearing 1 is located one side that is close to motor element 2 or keeps away from motor element 2 of piston 4. For example, in one example of the invention, the bearing 1 is located on the side of the piston 4 that is closer to the motor assembly 2; in another example of the invention, the bearing 1 is located on the side of the piston 4 remote from the motor assembly 2.
According to the compressor 100 of the embodiment of the invention, the oil storage groove 12 and the oil delivery channel 13 are arranged on the surface of the bearing 1 facing the piston 4, one end of the oil delivery channel 13 is communicated with the oil storage groove 12, the other end of the oil delivery channel 13 is communicated with the through hole 11, and the lubricating oil between the inner wall of the through hole 11 and the crankshaft 3 can enter the oil storage groove 12 through the oil delivery channel 13, so that static pressure lubrication can be formed between the surface of the bearing 1 facing the piston 4 and the piston 4, the friction resistance between the bearing 1 and the piston 4 can be reduced, the power loss of the compressor 100 can be reduced, and the working performance of the compressor 100 can be improved.
In some embodiments of the present invention, there are two bearings 1, and the two bearings 1 are respectively located on both sides of the piston 4 in the axial direction. Thereby, the frictional resistance between the piston 4 and the bearings 1 on the upper and lower sides in the axial direction thereof can be reduced, so that the power loss of the compressor 100 is further reduced, and the operation performance of the compressor 100 is further improved.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (12)
1. A bearing for a compressor, characterized in that the bearing has a through-hole adapted for a crankshaft to pass through, the surface of the bearing facing a piston has an oil reservoir and an oil delivery channel, the oil reservoir extends in the circumferential direction of the through-hole, and the oil reservoir is spaced apart from the through-hole, one end of the oil delivery channel communicates with the oil reservoir, the other end of the oil delivery channel communicates with the through-hole.
2. The bearing for the compressor as claimed in claim 1, wherein the oil reservoir is formed in a ring shape surrounding the through-hole.
3. The bearing for the compressor according to claim 1, wherein the oil sump includes a first side wall adjacent to a central axis of the through-hole and a second side wall facing away from the central axis of the through-hole in a radial direction of the bearing, and the first side wall is inclined toward a direction facing away from the central axis of the through-hole and the second side wall is inclined toward a direction close to the central axis of the through-hole in a direction from an open end of the oil sump to a closed end of the oil sump.
4. The bearing for the compressor of claim 3, wherein an included angle between the first sidewall and the second sidewall is α, and satisfies: alpha is more than or equal to 90 degrees and less than or equal to 140 degrees.
5. The bearing for a compressor according to claim 1, wherein a depth of the oil reservoir in an axial direction of the through-hole is d1, and satisfies: d1 is more than or equal to 0.1 mm.
6. The bearing for a compressor according to claim 1, wherein a radius of an outer edge of the piston is M, an eccentric amount of the crankshaft is e, a radius of the through hole is M, a radius of an outer edge of the oil reservoir is R1, a radius of an inner edge of the oil reservoir is R2, and the following are satisfied: m is more than R2 and more than R1 and is not more than M-e-2.
7. The bearing for a compressor according to claim 1, wherein a depth of the oil delivery passage in an axial direction of the through-hole is d2, and satisfies: d2 is more than or equal to 0.1 mm.
8. Bearing for a compressor according to claim 1, characterized in that the oil delivery channel has a width d3 on the piston-facing surface of the bearing and satisfies: d3 is more than or equal to 1 mm.
9. The bearing for the compressor as claimed in claim 1, wherein a groove is provided on an inner wall of the through-hole, one end of the groove communicates with the other end of the oil delivery passage, and the other end of the groove extends in a direction away from the piston.
10. The bearing for the compressor as claimed in claim 9, wherein the groove is formed in a spiral shape.
11. A compressor, comprising:
a motor assembly;
a crankshaft connected with the motor assembly, the crankshaft having an eccentric portion;
the piston is sleeved on the eccentric part;
the bearing for a compressor according to any one of claims 1 to 10, said crankshaft being inserted in said through hole, said bearing being located on a side of said piston closer to or further from said motor assembly.
12. The compressor of claim 11, wherein the number of the bearings is two, and the two bearings are respectively located at both sides of the piston in the axial direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010265920.1A CN113494456B (en) | 2020-04-07 | 2020-04-07 | Bearing for compressor and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010265920.1A CN113494456B (en) | 2020-04-07 | 2020-04-07 | Bearing for compressor and compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113494456A true CN113494456A (en) | 2021-10-12 |
| CN113494456B CN113494456B (en) | 2023-10-24 |
Family
ID=77994702
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| Application Number | Title | Priority Date | Filing Date |
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| CN202010265920.1A Active CN113494456B (en) | 2020-04-07 | 2020-04-07 | Bearing for compressor and compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115289018A (en) * | 2022-07-22 | 2022-11-04 | 广州市德善数控科技有限公司 | Compressor and temperature adjusting system |
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| CN108386353A (en) * | 2018-04-17 | 2018-08-10 | 珠海凌达压缩机有限公司 | Pump body subassembly and compressor and air conditioner |
| JP6704555B1 (en) * | 2019-10-24 | 2020-06-03 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
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| JPS6345084U (en) * | 1986-09-11 | 1988-03-26 | ||
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| JPH08319975A (en) * | 1995-05-29 | 1996-12-03 | Hitachi Ltd | Rotary compressor |
| CN201757059U (en) * | 2010-05-24 | 2011-03-09 | 松下·万宝(广州)压缩机有限公司 | Compressor |
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| JP6704555B1 (en) * | 2019-10-24 | 2020-06-03 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
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| CN115289018A (en) * | 2022-07-22 | 2022-11-04 | 广州市德善数控科技有限公司 | Compressor and temperature adjusting system |
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| CN113494456B (en) | 2023-10-24 |
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