CN114776560A - Pump body applied to compressor and compressor - Google Patents

Pump body applied to compressor and compressor Download PDF

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Publication number
CN114776560A
CN114776560A CN202210488355.4A CN202210488355A CN114776560A CN 114776560 A CN114776560 A CN 114776560A CN 202210488355 A CN202210488355 A CN 202210488355A CN 114776560 A CN114776560 A CN 114776560A
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CN
China
Prior art keywords
crankshaft
bearing
support bearing
compressor
support
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210488355.4A
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Chinese (zh)
Inventor
张赣波
陈涛
陈宗平
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangdong Meizhi Compressor Co Ltd
Original Assignee
Guangdong Meizhi Compressor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guangdong Meizhi Compressor Co Ltd filed Critical Guangdong Meizhi Compressor Co Ltd
Priority to CN202210488355.4A priority Critical patent/CN114776560A/en
Publication of CN114776560A publication Critical patent/CN114776560A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)

Abstract

The invention discloses a pump body applied to a compressor and the compressor, wherein the pump body comprises: the crankshaft penetrates through the cylinder, and the cylinder is provided with a first end and a second end which are opposite; the first support bearing is arranged at the first end and sleeved on the crankshaft; the second support bearing is arranged at the second end and sleeved on the crankshaft; and the third support bearing is arranged on one side, far away from the cylinder, of the second support bearing, and is connected with the second support bearing and sleeved on the crankshaft. Therefore, the first supporting bearing, the second supporting bearing and the third supporting bearing simultaneously support the crankshaft, the supporting rigidity of the crankshaft is effectively improved, the inherent frequency of the crankshaft rotary vibration is moved to be out of the range of the unbalanced radial electromagnetic force fundamental frequency in the rotating speed interval of the compressor, the crankshaft rotary vibration resonance is eliminated, the noise of the compressor is reduced, meanwhile, the bearing stress state of each supporting shaft can be improved, the eccentric wear of the crankshaft is relieved, and the working reliability of the compressor is improved.

Description

Pump body applied to compressor and compressor
Technical Field
The invention relates to the field of compressors, in particular to a pump body applied to a compressor and a compressor with the pump body applied to the compressor.
Background
In the related art, the compressor often has a phenomenon that the noise value of a certain frequency is abnormally higher, and analysis shows that the abnormal noise frequency is 6 times of the frequency of the compressor (hereinafter referred to as 6f, where f is the frequency of the compressor). The above 6f frequency noise problem is high in probability in the variable frequency air conditioner, and particularly, the noise problem is easy to occur after the power of a motor is improved, and researches find that the noise problem is related to the structural design of a pump body of a compressor, particularly, the reason is that a crankshaft of the pump body revolves and vibrates and resonates, and in addition, after the compressor runs for a long time, eccentric wear occurs at the contact part of the crankshaft and the end part of a main bearing.
The existing compressor supports the crankshaft of the pump body by a main bearing and an auxiliary bearing, the double-bearing supporting mode is a main factor causing the problems of crankshaft resonance and eccentric wear, on one hand, the direction of the support reaction force of the main bearing and the auxiliary bearing is opposite, so that the crankshaft runs in an inclined state for a long time, and the eccentric wear occurs at the contact part of the crankshaft and the end parts of the main bearing and the auxiliary bearing; on the other hand, the bearing support rigidity is insufficient, so that the inherent frequency of the crankshaft cyclotron vibration falls in an excitation frequency interval of 6 times of the rotation frequency of the compressor, and the problem of crankshaft resonance is easy to occur. The direct effect of the crankshaft cyclotron resonance is to worsen the non-uniformity of the motor air gap, generate larger unbalanced radial electromagnetic force, which in turn further increases the dynamic deflection of the crankshaft at the motor rotor end, forming a mutual strengthening effect.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, an object of the present invention is to provide a pump body for a compressor, which supports a crankshaft through three support bearings, thereby improving the support rigidity of the crankshaft, eliminating the rotational vibration resonance of the crankshaft, reducing the noise of the compressor, and simultaneously reducing the eccentric wear of the crankshaft.
The invention further provides a compressor.
The pump body applied to the compressor according to the present invention comprises: the crankshaft penetrates through the cylinder, and the cylinder is provided with a first end and a second end which are opposite in the axial direction of the cylinder; the first support bearing is arranged at the first end and sleeved on the crankshaft; the second support bearing is arranged at the second end and sleeved on the crankshaft; and the third supporting bearing is arranged on one side, far away from the cylinder, of the second supporting bearing, and is connected with the second supporting bearing and sleeved on the crankshaft.
According to the pump body applied to the compressor, the first supporting bearing, the second supporting bearing and the third supporting bearing are used for simultaneously supporting the crankshaft, so that the supporting rigidity of the crankshaft is effectively improved, the inherent frequency of the crankshaft rotary vibration is moved to be within the rotating speed range of the compressor and outside the range of the unbalanced radial electromagnetic force fundamental frequency, the crankshaft rotary vibration resonance is eliminated, the noise of the compressor is reduced, meanwhile, the bearing force state of each supporting shaft can be improved, the eccentric wear of the crankshaft is relieved, and the working reliability of the compressor is improved.
In some examples of the invention, the third support bearing comprises: the supporting part is sleeved outside the crankshaft, and the end part of the supporting part, far away from the second supporting bearing, is provided with a crumple structure surrounding the crankshaft.
In some examples of the invention, the crush feature extends circumferentially of the support portion and is configured as a closed loop.
In some examples of the present invention, the crush structure is configured as an annular groove recessed toward the inside of the support portion, the annular groove being spaced apart from the crankshaft in a radial direction of the crankshaft.
In some examples of the invention, the crush feature is configured as an annular gap spaced from the crankshaft in a radial direction of the crankshaft.
In some examples of the invention, the crankshaft is provided with a lubrication through hole adapted to communicate with a central passage of the crankshaft.
In some examples of the invention, the third support bearing further comprises: the connecting part is connected with the supporting part and provided with a first mounting hole, the axis of the first mounting hole extends in the radial direction of the third support bearing, and the second support bearing is provided with a second mounting hole matched with the first mounting hole.
In some examples of the invention, the connection part includes: the connecting wall is connected the supporting part with between the first periphery wall, the first periphery wall is equipped with first mounting hole.
In some examples of the invention, the connecting wall is provided with a through hole penetrating through the connecting wall.
In some examples of the invention, the connecting portion and the support portion together define a first recess that opens toward the second support bearing.
In some examples of the invention, the end of the second mounting hole remote from the third support bearing is provided with a counter bore recessed into the second support bearing, the counter bore surrounding the second mounting hole.
In some examples of the invention, the third support bearing is provided with a support boss at an end thereof adjacent to the second support bearing, the support boss being provided at the second support bearing.
In some examples of the invention, the second support bearing is provided with an oil return hole.
In some examples of the invention, the second support bearing comprises: the bearing comprises a bearing body and a second peripheral wall, wherein the second peripheral wall is arranged around the bearing body in the circumferential direction of the bearing body, and the second peripheral wall is provided with a second mounting hole.
In some examples of the invention, the bearing body and the second peripheral wall together define a second recess that is open towards the third support bearing.
In some examples of the invention, the crankshaft includes a long axis and a short axis, the first support bearing is for supporting the short axis, and the second support bearing and the third support bearing are for supporting the long axis.
The compressor comprises the pump body applied to the compressor.
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
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a cross-sectional view of a pump body according to an embodiment of the invention;
FIG. 2 is a cross-sectional view of a second support structure and a third support structure assembled in accordance with an embodiment of the present invention;
FIG. 3 is a perspective view of a third support bearing according to an embodiment of the invention;
fig. 4 is a perspective view of a second support bearing according to an embodiment of the present invention.
Reference numerals:
a pump body 100;
a crankshaft 10; a long axis 11; a short shaft 12; a central channel 13;
a first support bearing 20;
a cylinder 30; a first end 31; a second end 32;
a second support bearing 40; a bearing body 41; the second peripheral wall 42; a second mounting hole 421; a counterbore 422;
a second groove 43; an oil return hole 44; an oil return gap 45; an exhaust vent 46;
a third support bearing 50; a support portion 51; a crush structure 511;
a connecting portion 52; a connecting wall 521; a through hole 522; the first outer peripheral wall 523; a first mounting hole 524;
a support boss 525; the first groove 53;
a fastener 200.
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 accompanying drawings are illustrative only for the purpose of explaining the present invention and are not to be construed as limiting the present invention.
Referring to fig. 1 to 4, a pump body 100 applied to a compressor according to an embodiment of the present invention is described below, where the pump body 100 is composed of a crankshaft 10, a cylinder 30, a first support bearing 20, a second support bearing 40, and a third support bearing 50, the first support bearing 20, the second support bearing 40, and the third support bearing 50 are sleeved on the crankshaft 10, and the first support bearing 20, the second support bearing 40, and the third support bearing 50 play a role of supporting the crankshaft 10, thereby effectively improving the support rigidity of the crankshaft 10, eliminating the rotational vibration resonance of the crankshaft 10, and reducing the noise of the compressor.
As shown in fig. 1, a pump body 100 according to an embodiment of the present invention includes a crankshaft 10, a cylinder 30, a first support bearing 20, a second support bearing 40, and a third support bearing 50. As shown in fig. 1, the crankshaft 10 is disposed through the cylinder 30, and it can be understood that the crankshaft 10 passes through the cylinder 30, and the cylinder 30 has a first end 31 and a second end 32 opposite to each other in the axial direction of the cylinder 30, and as shown in fig. 1, when the pump body 100 is placed in the direction of fig. 1, the lower end of the cylinder 30 is the first end 31 of the cylinder 30, and the upper end of the cylinder 30 is the second end 32 of the cylinder 30. The first support bearing 20 is disposed at the first end 31 and sleeved outside the crankshaft 10, and the first support bearing 20 can support the crankshaft 10. The second support bearing 40 is disposed at the second end 32 and sleeved outside the crankshaft 10, and the second support bearing 40 can support the crankshaft 10. The third support bearing 50 is disposed on a side of the second support bearing 40 away from the cylinder 30, the third support bearing 50 is connected to the second support bearing 40 and sleeved outside the crankshaft 10, and the third support bearing 50 can support the crankshaft 10.
It should be noted that, as shown in fig. 1, the first support bearing 20 and the second support bearing 40 are respectively disposed at the first end 31 and the second end 32 of the cylinder 30, the first support bearing 20 may be configured as a lower end cover of the cylinder 30, the second support bearing 40 may be configured as an upper end cover of the cylinder 30, and the second support bearing 40 is also a connection fixing member of the third support bearing 50, and the third support bearing 50 is installed between the second support bearing 40 and the motor rotor of the motor of the compressor.
The first support bearing 20, the second support bearing 40 and the third support bearing 50 are sequentially arranged along the axial direction of the crankshaft 10, the first support bearing 20, the second support bearing 40 and the third support bearing 50 are sleeved outside the crankshaft 10 at the same time, the first support bearing 20, the second support bearing 40 and the third support bearing 50 can simultaneously support the crankshaft 10, the support rigidity of the crankshaft 10 can be effectively improved, the inherent frequency of the crankshaft cyclotron vibration can be moved to a range within the rotating speed range of a compressor and outside the fundamental frequency range of unbalanced radial electromagnetic force, the cyclotron vibration resonance of the crankshaft 10 is eliminated, the working noise of the compressor is reduced, and the cyclotron vibration resonance of the crankshaft 10 is eliminated, so that the air gap of a motor is more uniform, and the generated unbalanced radial electromagnetic force is reduced. Meanwhile, the first support bearing 20, the second support bearing 40 and the third support bearing 50 simultaneously support the crankshaft 10, so that the bearing stress state of each support bearing can be improved, eccentric wear of the crankshaft 10 can be reduced, the service life of the crankshaft 10 can be prolonged, and the working reliability of the compressor can be improved.
In some embodiments of the present invention, as shown in fig. 1-3, the third support bearing 50 may include: and the support part 51, the support part 51 is a cylindrical structure, the support part 51 is sleeved outside the crankshaft 10, the support part 51 is used for supporting the crankshaft 10, and the end of the support part 51 far away from the second support bearing 40 is provided with a crush structure 511 surrounding the crankshaft 10. Further, the supporting portion 51 is a cylindrical structure, wherein after the crankshaft 10 and the third support bearing 50 are assembled, the crumple structure 511 is disposed around the crankshaft 10, and during the rotation of the crankshaft 10, by disposing the crumple structure 511, when the crankshaft 10 moves in the radial direction relative to the third support bearing 50, the supporting portion 51 can deform to buffer the crankshaft 10, so as to slow down the eccentric wear of the crankshaft 10, reduce the wear of the crankshaft 10, further eliminate the rotational vibration resonance of the crankshaft 10, and further reduce the working noise of the compressor.
In some embodiments of the present invention, as shown in fig. 1-3, the crush structure 511 extends in a circumferential direction of the support portion 51, and the crush structure 511 is configured as a closed loop structure. So set up and all to form the structure 511 that bursts on the whole circumferencial direction of bent axle 10, guarantee that the structure 511 that bursts sets up around bent axle 10, bent axle 10 rotates the in-process, no matter bent axle 10 moves towards which direction in the radial direction relative third support bearing 50, and supporting part 51 homoenergetic takes place to be out of shape, guarantees to cushion bent axle 10, guarantees to slow down bent axle 10 eccentric wear, can further reduce the wearing and tearing of bent axle 10.
According to an embodiment of the present invention, as shown in fig. 1 to 3, the crush structure 511 is configured as an annular groove depressed toward the inside of the support portion 51, and the annular groove is disposed spaced apart from the crankshaft 10 in a radial direction of the crankshaft 10. In this embodiment, the annular groove extends in the circumferential direction of the support portion 51, is a closed-loop groove, and is disposed such that an end portion of the annular groove, which is far from the second support bearing 40, is opened in the axial direction of the crankshaft 10, and is spaced apart from the crankshaft 10 by an inner side wall of the annular groove in the radial direction of the crankshaft 10. During the rotation of the crankshaft 10, when the crankshaft 10 moves in the radial direction relative to the third support bearing 50, the inner side wall of the annular groove deforms toward the inside of the annular groove to buffer the crankshaft 10, thereby preventing the crankshaft 10 from being connected with the support part 51, reducing the eccentric wear of the crankshaft 10, and reducing the wear of the crankshaft 10.
According to another embodiment of the present invention, the crush structure 511 is configured as an annular gap that is spaced apart from the crankshaft 10 in a radial direction of the crankshaft 10. Wherein, in this embodiment, the crush structure 511 is provided on the outer side wall of the support portion 51, the crush structure 511 is configured as an annular gap extending along the circumferential direction of the support portion 51, the upper end of the annular gap is provided to be open, and the radial outer end of the annular gap is provided to be open in the radial direction of the support portion 51, and the annular gap is spaced apart from the crankshaft 10 by the inner side wall of the annular gap. During the rotation of the crankshaft 10, when the crankshaft 10 moves in the radial direction relative to the third support bearing 50, the inner side wall of the annular gap deforms toward the inside of the annular gap to buffer the crankshaft 10, so that the crankshaft 10 is prevented from being hard-connected with the support part 51, the eccentric wear of the crankshaft 10 is reduced, and the wear of the crankshaft 10 can be reduced.
In some embodiments of the present invention, as shown in FIGS. 1-3, the crankshaft 10 is provided with a lubrication through-hole adapted to communicate with the central passage 13 of the crankshaft 10. Further, the shaft section department that bent axle 10 and third support bearing 50 contact is equipped with lubricated through-hole, lubricated through-hole runs through the lateral wall of central channel 13 in the radial direction of bent axle 10, the pump body 100 during operation, bent axle 10 rotates, lubricating oil in the oil sump of compressor is inhaled in the central channel 13 of bent axle 10, lubricating oil can flow to lubricated through-hole along the central channel 13 of bent axle 10, lubricating oil flows out bent axle 10 through lubricated through-hole and in order to carry out effective lubrication to third support bearing 50, guarantee that bent axle 10 rotates smoothly, alleviate wearing and tearing between bent axle 10 and the third support bearing 50, reduce compressor noise, further improve compressor operational reliability.
In some embodiments of the present invention, as shown in fig. 1-3, the third support bearing 50 may further include: and a connection part 52, the connection part 52 being connected to the support part 51, the connection part 52 having a first mounting hole 524, an axis of the first mounting hole 524 extending in a radial direction of the third support bearing 50, and the second support bearing 40 having a second mounting hole 421 fitted to the first mounting hole 524. Further, the connecting portion 52 is disposed around the supporting portion 51 in the circumferential direction of the supporting portion 51, and the connecting portion 52 and the supporting portion 51 may be integrally formed, or it can be understood that the third supporting bearing 50 is an integrally formed component, so as to enhance the connection strength between the connecting portion 52 and the supporting portion 51, so that the third supporting bearing 50 has a good supporting effect on the crankshaft 10. The first mounting hole 524 penetrates the connecting portion 52 in the thickness direction of the connecting portion 52, the axis of the second mounting hole 421 extends in the radial direction of the second support bearing 40, the centerline axis of the second mounting hole 421 is collinear with the centerline axis of the first mounting hole 524, it can also be understood that the centerline axis of the second mounting hole 421 coincides with the centerline axis of the first mounting hole 524, the third support bearing 50 and the second support bearing 40 are fastened by a fastener 200 (e.g. a bolt, a screw, etc.) passing through the first mounting hole 524 and the second mounting hole 421 at the same time, by fitting the fastener 200 in the radial direction of the pump body 100, the fastener 200 has no shear force, the bearing load is transmitted by the side walls of the third support bearing 50 and the second support bearing 40 together, the rigidity of the third support bearing 50 is increased, and, an effect of stable connection between the third support bearing 50 and the second support bearing 40 can be achieved.
In some embodiments of the present invention, as shown in fig. 1-3, the connection portion 52 may include: a connecting wall 521 and a first outer peripheral wall 523, the connecting wall 521 is connected between the support portion 51 and the first outer peripheral wall 523, and the first outer peripheral wall 523 is provided with a first mounting hole 524. Further, the connection wall 521 is provided to extend in the circumferential direction of the connection portion 52, the first outer circumferential wall 523 is provided to extend in the circumferential direction of the connection portion 52, the connection wall 521 may be configured as a circular ring-shaped wall, and the first outer circumferential wall 523 may be configured as a cylindrical structure. When the pump body 100 is placed in the orientation shown in fig. 1, the radially inner end of the connecting wall 521 is fixedly connected to the support portion 51, and the radially outer end of the connecting wall 521 is fixedly connected to the upper end of the first outer peripheral wall 523, wherein the connecting wall 521 is integrally formed with the first outer peripheral wall 523, and further, the central axis of the support portion 51 is collinear with the central axis of the connecting wall 521. The first mounting hole 524 penetrates through the first peripheral wall 523 in the thickness direction of the first peripheral wall 523, and the axis of the first mounting hole 524 extends in the radial direction of the third support bearing 50, so that the first mounting hole 524 can extend in the radial direction of the third support bearing 50, the fastener 200 can be assembled with the third support bearing 50 and the second support bearing 40 in the radial direction, no shearing force is generated by the fastener 200, the bearing load is transmitted by the first peripheral wall 523 of the third support bearing 50 and the side wall of the second support bearing 40 together, and the rigidity of the third support bearing 50 is further increased.
In some embodiments of the present invention, as shown in fig. 1 and 3, the connecting portion 52 and the supporting portion 51 together define a first recess 53 that is open toward the second support bearing 40. The support portion 51 is connected to the connection portion 52, when the pump body 100 is placed in the direction shown in fig. 1, the radially inner end of the connection wall 521 is fixedly connected to the support portion 51, the radially outer end of the connection wall 521 is fixedly connected to the upper end of the first outer circumferential wall 523, so that the connection portion 52 and the support portion 51 jointly define a first groove 53 which is open toward the second support bearing 40, and the gas (refrigerant) is compressed in the cylinder 30 and then flows into the first groove 53 through the second support bearing 40.
In some embodiments of the present invention, as shown in fig. 3, the connecting wall 521 is provided with a through hole 522 penetrating through the connecting wall 521, the through hole 522 forms a channel in an axial direction of the connecting wall 521, the through hole 522 is communicated with the first groove 53, after the gas (refrigerant) is compressed and flows into the first groove 53 in the cylinder 30, the gas in the first groove 53 can flow out of the pump body 100 from the through hole 522 to achieve an exhaust effect, and meanwhile, the lubricating oil above the pump body 100 can flow back to the oil pool through the through hole 522, so that oil accumulation above the pump body 100 is prevented, and the risk of oil accumulation is eliminated.
In some embodiments of the present invention, as shown in fig. 1 and 2, the end of the second mounting hole 421 remote from the third support bearing 50 is provided with a counterbore 422 recessed into the second support bearing 40, the counterbore 422 surrounding the second mounting hole 421. Further, as shown in fig. 2, a counter bore 422 is provided on the outer circumferential wall of the second support bearing 40, the counter bore 422 is a groove body recessed toward the inside of the second support bearing 40, an end face of the counter bore 422 close to the third support bearing 50 and an end face of the second mounting hole 421 far from the third support bearing 50 are on the same plane, and the counter bore 422 is provided around the second mounting hole 421 in the circumferential direction of the second mounting hole 421. Further, the second mounting hole 421 is a circular hole, the counterbore 422 is a circular hole, the bottom of the counterbore 422 is communicated with the second mounting hole 421, and the diameter of the counterbore 422 is larger than that of the second mounting hole 421. When the second support bearing 40 and the third support bearing 50 are assembled by using bolts or screws, the counter bores 422 can avoid the head structure of the bolts or screws, so that the structure of the fastening piece 200 does not protrude out of the outer surface of the second support bearing 40, and the fastening piece 200 can be hidden in the second support bearing 40 to prevent the fastening piece 200 from interfering with other parts in the compressor.
In some embodiments of the present invention, as shown in fig. 3, the end of the third support bearing 50 near the second support bearing 40 is provided with a support boss 525, and the support boss 525 is supported by the second support bearing 40. Further, the end of the first peripheral wall 523 adjacent to the second support bearing 40 is provided with a plurality of support bosses 525, and the plurality of support bosses 525 may be provided, and the plurality of support bosses 525 are sequentially spaced apart in the circumferential direction of the third support bearing 50. Further, the support boss 525 and the first peripheral wall 523 are integrally formed, so that the connection strength between the support boss 525 and the first peripheral wall 523 is improved. When the third support bearing 50 is matched with the second support bearing 40, the support boss 525 extends into the second support bearing 40 to be abutted against the second support bearing 40, so that the first mounting hole 524 corresponds to the second mounting hole 421, and the assembly efficiency of the second support bearing 40 and the third support bearing 50 is improved.
In some embodiments of the present invention, as shown in fig. 4, the second support bearing 40 is provided with an oil return hole 44, a plurality of support bosses 525 are provided at an end of the third support bearing 50 close to the second support bearing 40, an oil return gap 45 is formed between adjacent support bosses 525, after the third support bearing 50 and the second support bearing 40 are fitted, the oil return gap 45 is communicated with the oil return hole 44, the lubricating oil between the third support bearing 50 and the second support bearing 40 can flow to the oil return hole 44 through the oil return gap 45, and finally the lubricating oil flows back to an oil sump of the compressor through the oil return hole 44.
In some embodiments of the present invention, as shown in fig. 2 and 4, the second support bearing 40 may include: the bearing body 41 and the second peripheral wall 42, the second peripheral wall 42 is provided around the bearing body 41 in the circumferential direction of the bearing body 41, and the second peripheral wall 42 is provided with the second mounting hole 421. Further, the second peripheral wall 42 may be configured as a cylindrical structure, the second peripheral wall 42 is disposed around the circumferential edge of the bearing body 41, and after the third support bearing 50 is assembled with the second support bearing 40, the side surface of the first peripheral wall 523 away from the connecting wall 521 is in contact with the second peripheral wall 42, so that the first mounting hole 524 and the second mounting hole 421 correspond, thereby making the location of the second mounting hole 421 reasonable.
Further, the bearing body 41 and the second peripheral wall 42 are integrally formed, so as to enhance the connection strength between the bearing body 41 and the second peripheral wall 42, the bearing body 41 and/or the second peripheral wall 42 are formed with oil return holes 44, that is, the oil return holes 44 may be formed only on the bearing body 41, the oil return holes 44 may be formed only on the second peripheral wall 42, the oil return holes 44 may be formed on both the second peripheral wall 42 and the bearing body 41, as shown in fig. 4, the oil return holes 44 are plural, the plural oil return holes 44 are in one-to-one correspondence communication with the plural oil return gaps 45, the plural oil return holes 44 are sequentially arranged at intervals in the circumferential direction of the second support bearing 40, the same oil return hole 44 is formed on the second peripheral wall 42 and the bearing body 41 at the same time, the axis of the oil return hole 44 extends in the axial direction of the second support bearing 40, this arrangement enables the lubricating oil between the third support bearing 50 and the second support bearing 40 to quickly flow back to the oil sump of the compressor.
Further, the bearing body 41 is provided with the gas discharge hole 46, and the gas compressed by the cylinder 30 can be discharged from the gas discharge hole 46 to between the third support bearing 50 and the second support bearing 40, and finally discharged from the through hole 522.
In some embodiments of the invention, as shown in fig. 2 and 4, the bearing body 41 and the second peripheral wall 42 together define a second recess 43 that opens toward the third support bearing 50. Wherein the second peripheral wall 42 is disposed around the circumferential edge of the bearing body 41, so that the bearing body 41 and the second peripheral wall 42 jointly define a second groove 43 that is open toward the third support bearing 50, and after the second support bearing 40 is engaged with the third support bearing 50, the first groove 53 and the second groove 43 jointly define a cavity that provides the pump body 100 with a gas flow cavity.
In some embodiments of the present invention, as shown in fig. 1, the crankshaft 10 includes a major axis 11 and a minor axis 12, a first support bearing 20 for supporting the minor axis 12, a second support bearing 40 and a third support bearing 50 for supporting the major axis 11. By the arrangement, the supporting rigidity of the crankshaft 10 can be further improved, the inherent frequency of the rotary vibration of the crankshaft 10 can be moved to the range of the rotating speed of the compressor and beyond the range of the fundamental frequency of unbalanced radial electromagnetic force, the rotary vibration resonance of the crankshaft 10 is eliminated, the working noise of the compressor is further reduced, meanwhile, the bearing force state of each supporting shaft can be further improved, the eccentric wear of the crankshaft 10 is further reduced, the service life of the crankshaft 10 is further prolonged, and the working reliability of the compressor is further improved.
In some embodiments of the present invention, the pump body 100 may be fixedly connected with the housing of the compressor through the cylinder 30 and/or the second support bearing 40.
According to the compressor of the embodiment of the present invention, including the pump body 100 in the above embodiment, the first support bearing 20, the second support bearing 40, and the third support bearing 50 are simultaneously sleeved outside the crankshaft 10, and the first support bearing 20, the second support bearing 40, and the third support bearing 50 can simultaneously support the crankshaft 10, so as to effectively improve the support stiffness of the crankshaft 10, and can move the natural frequency of the crankshaft cyclotron vibration to a range within the compressor rotation speed range and outside the fundamental frequency range of the unbalanced radial electromagnetic force, so as to eliminate the cyclotron vibration resonance of the crankshaft 10, reduce the compressor operation noise, and because the cyclotron vibration resonance of the crankshaft 10 is eliminated, the air gap of the motor is more uniform, and the generated unbalanced radial electromagnetic force is reduced. Meanwhile, the first support bearing 20, the second support bearing 40 and the third support bearing 50 simultaneously support the crankshaft 10, so that the stress state of each support bearing can be improved, eccentric wear of the crankshaft 10 is reduced, the service life of the crankshaft 10 is prolonged, and the working reliability of the compressor is improved.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like 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 do not necessarily 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.
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 (17)

1. A pump body for a compressor, comprising:
the crankshaft penetrates through the cylinder, and the cylinder is provided with a first end and a second end which are opposite in the axial direction of the cylinder;
the first support bearing is arranged at the first end and sleeved on the crankshaft;
the second support bearing is arranged at the second end and sleeved on the crankshaft;
and the third supporting bearing is arranged on one side, far away from the cylinder, of the second supporting bearing, and the third supporting bearing is connected with the second supporting bearing and sleeved on the crankshaft.
2. The pump body applied to a compressor according to claim 1, characterized in that said third support bearing comprises: the supporting part is sleeved outside the crankshaft, and the end part of the supporting part, far away from the second supporting bearing, is provided with a crumple structure surrounding the crankshaft.
3. The pump body applied to a compressor according to claim 2, wherein the crush structure extends in a circumferential direction of the support portion, and the crush structure is configured in a closed ring shape.
4. The pump body applied to a compressor according to claim 2, wherein the crush structure is configured as an annular groove recessed toward the inside of the support portion, the annular groove being spaced from the crankshaft in a radial direction of the crankshaft.
5. The pump body applied to a compressor according to claim 2, wherein said crush structure is configured as an annular gap spaced from said crankshaft in a radial direction of said crankshaft.
6. Pump body for a compressor, according to claim 2, characterized in that said crankshaft is provided with a lubricating through hole adapted to communicate with a central channel of said crankshaft.
7. The pump body applied to a compressor according to claim 2, characterized in that said third support bearing further comprises: the connecting part is connected with the supporting part and provided with a first mounting hole, the axis of the first mounting hole extends in the radial direction of the third supporting bearing, and the second supporting bearing is provided with a second mounting hole matched with the first mounting hole.
8. Pump body for compressor application, according to claim 7, characterized in that said connection portion comprises: the connecting wall is connected the supporting part with between the first periphery wall, the first periphery wall is equipped with first mounting hole.
9. The pump body applied to a compressor according to claim 8, characterized in that said connecting wall is provided with a through hole passing through said connecting wall.
10. Pump body applied to a compressor, according to claim 7, characterized in that said connection portion and said support portion jointly define a first recess open towards said second support bearing.
11. The pump body applied to the compressor according to claim 7, characterized in that the end of the second mounting hole remote from the third support bearing is provided with a counter-bore recessed towards the inside of the second support bearing, said counter-bore surrounding the second mounting hole.
12. The pump body applied to the compressor according to claim 1, wherein the end of the third support bearing close to the second support bearing is provided with a support boss supported by the second support bearing.
13. Pump body applied to a compressor, according to claim 12, characterised in that said second support bearing is provided with oil return holes.
14. Pump body for compressor application, according to claim 7, characterized in that said second support bearing comprises: the bearing comprises a bearing body and a second peripheral wall, wherein the second peripheral wall is arranged around the bearing body in the circumferential direction of the bearing body, and the second peripheral wall is provided with a second mounting hole.
15. The pump body applied to a compressor according to claim 7, wherein said bearing body and said second peripheral wall jointly define a second recess open towards said third support bearing.
16. The pump body applied to a compressor according to claim 1, wherein the crankshaft comprises a long shaft and a short shaft, the first support bearing being for supporting the short shaft, the second support bearing and the third support bearing being for supporting the long shaft.
17. Compressor, characterized in that it comprises a pump body applied to a compressor according to any one of claims 1 to 16.
CN202210488355.4A 2022-05-06 2022-05-06 Pump body applied to compressor and compressor Pending CN114776560A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210488355.4A CN114776560A (en) 2022-05-06 2022-05-06 Pump body applied to compressor and compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210488355.4A CN114776560A (en) 2022-05-06 2022-05-06 Pump body applied to compressor and compressor

Publications (1)

Publication Number Publication Date
CN114776560A true CN114776560A (en) 2022-07-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210488355.4A Pending CN114776560A (en) 2022-05-06 2022-05-06 Pump body applied to compressor and compressor

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Country Link
CN (1) CN114776560A (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN85106952A (en) * 1984-11-13 1986-07-23 特库姆塞制品公司 The lubricating fitting of rotary compressor
CN105201840A (en) * 2014-06-17 2015-12-30 广东美芝制冷设备有限公司 Compressor
CN106704198A (en) * 2017-01-24 2017-05-24 广东美芝制冷设备有限公司 Compressor and vehicle provided with same
CN206738154U (en) * 2017-04-28 2017-12-12 广东美芝制冷设备有限公司 Rotary compressor
CN111287975A (en) * 2018-12-10 2020-06-16 广东美芝精密制造有限公司 Pump body subassembly and compressor
CN215521262U (en) * 2021-06-03 2022-01-14 珠海格力节能环保制冷技术研究中心有限公司 Compressor, fixing device and air conditioner

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN85106952A (en) * 1984-11-13 1986-07-23 特库姆塞制品公司 The lubricating fitting of rotary compressor
CN105201840A (en) * 2014-06-17 2015-12-30 广东美芝制冷设备有限公司 Compressor
CN106704198A (en) * 2017-01-24 2017-05-24 广东美芝制冷设备有限公司 Compressor and vehicle provided with same
CN206738154U (en) * 2017-04-28 2017-12-12 广东美芝制冷设备有限公司 Rotary compressor
CN111287975A (en) * 2018-12-10 2020-06-16 广东美芝精密制造有限公司 Pump body subassembly and compressor
CN215521262U (en) * 2021-06-03 2022-01-14 珠海格力节能环保制冷技术研究中心有限公司 Compressor, fixing device and air conditioner

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Application publication date: 20220722