CN111794966A - Pump body subassembly, compressor and air conditioner - Google Patents

Pump body subassembly, compressor and air conditioner Download PDF

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Publication number
CN111794966A
CN111794966A CN202010608380.2A CN202010608380A CN111794966A CN 111794966 A CN111794966 A CN 111794966A CN 202010608380 A CN202010608380 A CN 202010608380A CN 111794966 A CN111794966 A CN 111794966A
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CN
China
Prior art keywords
groove
tail
pump body
back pressure
gleitbretter
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
CN202010608380.2A
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Chinese (zh)
Inventor
万鹏凯
邹鹏
吴飞
扶峥
苏永强
任丽萍
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.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
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 Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to CN202010608380.2A priority Critical patent/CN111794966A/en
Publication of CN111794966A publication Critical patent/CN111794966A/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3445—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
    • 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

The application provides a pump body subassembly, compressor and air conditioner. The pump body assembly comprises a main shaft (1), an upper flange (2), a lower flange (3), a cylinder (4) and a roller (5), wherein a sliding sheet groove (6) is formed in the roller (5), a sliding sheet (7) is arranged in the sliding sheet groove (6), the head of the sliding sheet (7) is abutted to the inner wall of the cylinder (4), a tail cavity (8) is formed between the tail of the sliding sheet (7) and the tail of the sliding sheet groove (6), a back pressure groove is formed in the upper flange (2) and/or the lower flange (3), the back pressure groove is an annular groove, the tail cavity (8) is communicated with the back pressure groove, and a buffer structure is arranged between the tail of the sliding sheet (7) and the tail of the sliding sheet groove (6). According to the pump body subassembly of this application, can solve current compressor at the operation in-process, when the gleitbretter is in the shrink stage, it is higher to have the gleitbretter tail chamber oil pressure to promote, causes the gleitbretter backpressure too big easily, causes the problem of the unusual wearing and tearing of gleitbretter head.

Description

Pump body subassembly, compressor and air conditioner
Technical Field
The application relates to the technical field of air conditioning, in particular to a pump body assembly, a compressor and an air conditioner.
Background
The existing rotary vane compressor can smoothly extend a sliding vane in the operation process, a back pressure cavity (a sliding vane tail cavity formed by the sliding vane and a main shaft sliding vane groove + an upper flange back pressure groove + a lower flange back pressure groove) is generally arranged at the tail part of the sliding vane, high-pressure oil in an oil pool is introduced to provide power for the back part of the sliding vane, the gas pressure and the friction force of a front cavity and a rear cavity of the head part of the sliding vane are overcome, and the head part of the sliding vane is always in contact with the inside of a cylinder in the whole operation process.
As shown in fig. 1 and 2, the back pressure oil of the sliding vane 2 'is pumped from the oil sump mainly through an oil pump, and then enters the flange back pressure groove 1' through the main shaft center hole and the main shaft side hole connected with the main shaft center hole, thereby filling the back pressure cavity.
In the process of one circle of rotation of the compressor, the pressure of a compression cavity is gradually increased, the pressure of a front cavity and a rear cavity of the head of the slide sheet 2' can simultaneously reach the exhaust pressure under the working condition of small partial pressure ratio along with the complexity and variability of the working condition of the air conditioner at present, and simultaneously, due to the resistance of an exhaust valve sheet, the pressure of the cavity is higher than the exhaust pressure in a shell, the oil pressure of an oil pool is equivalent to the exhaust pressure of the shell, namely, the pressure in a backpressure cavity is high exhaust pressure, so that F existsFront side+FRear end＞FBack of bodyAnd under the pressure action of the cavities on the two sides of the slip sheet 2 ', the head of the slip sheet 2 ' is separated from the inner wall of the air cylinder, so that leakage occurs, the performance of the compressor is influenced, and meanwhile, when the back pressure is enough, the slip sheet 2 ' stretches out again to collide with the air cylinder, and the reliability of the compressor is influenced.
In order to solve the problem, a back pressure groove 1 ' of a sliding vane 2 ' in the prior scheme is designed with a section of non-slotted structure, when the pressure of a cavity is equal to the back pressure, the sliding vane 2 ' returns to a sliding vane groove 3 ', the back pressure volume is reduced, back pressure oil needs to be discharged from a back pressure cavity, oil can only leak to the back pressure groove 1 ' or other parts through a gap because the back pressure groove 1 ' of an upper flange and a lower flange does not exist at the position, and oil does not leak to the back pressure groove 1 ' or other partsThe characteristic of pressing is that the oil pressure of the tail cavity of the slip sheet 2' rises, thereby meeting the requirement of FBack of body＞FFront side+FRear endAnd the back pressure of the sliding vane 2' is ensured to be sufficient.
But this scheme is in order to satisfy the oily demand of holding back of light operating mode, and the angle scope of not slotting enlarges, then along with gleitbretter 2 ' in the increase of holding back the oily section and returning the distance, add the incompressibility of oiling, gleitbretter 2 ' tail chamber oil pressure promotes higher, arouses easily that gleitbretter 2 ' backpressure is too big, and then leads to gleitbretter 2 ' head and cylinder inner wall frictional force to increase, and the compressor consumption increases, causes the abnormal wear of gleitbretter 2 ' head even, arouses compressor reliability problem. Wherein the position A' in figure 1 is the oil holding position of the slide.
Therefore, current compressor is at the operation in-process, and when the gleitbretter was in the shrink stage, it was higher to have had gleitbretter tail chamber oil pressure to promote, arouses easily that the gleitbretter backpressure is too big, causes the problem of the unusual wearing and tearing of gleitbretter head.
Disclosure of Invention
Therefore, the technical problem that this application will be solved lies in providing a pump body subassembly, compressor and air conditioner to solve current compressor at the operation in-process, when the gleitbretter is in the shrink stage, there is the gleitbretter tail chamber oil pressure to promote higher, arouses easily that the gleitbretter backpressure is too big, causes the problem of the unusual wearing and tearing of gleitbretter head.
In order to solve the problem, the application provides a pump body subassembly, which comprises a main shaft, go up the flange, the lower flange, cylinder and roller, the roller is fixed for main shaft circumference, be provided with the slide groove on the roller, it is provided with the gleitbretter to slide in the slide groove, the head of gleitbretter and the inner wall butt of cylinder, form the tail chamber between the afterbody of gleitbretter and the afterbody of slide groove, upward be provided with the back pressure groove on flange and/or the lower flange, the back pressure groove is the ring channel, tail chamber and back pressure groove intercommunication, be provided with buffer structure between the afterbody of gleitbretter and the afterb.
Preferably, the buffer structure is an elastic member.
Preferably, the resilient member is mounted to the trailing portion of the slider.
Preferably, the tail part of the sliding sheet is provided with an embedded groove, an elastic piece is embedded in the embedded groove, and the elastic piece extends out of the embedded groove; and/or the elastic element is arranged at the middle area of the tail part of the sliding sheet.
Preferably, the mounting area of the elastic piece at the tail part of the sliding sheet is S1, the end surface area of the tail part of the sliding sheet is S2, wherein 2S1 is less than or equal to S2.
Preferably, the elastic member is made of a polymer material or engineering plastic.
Preferably, the elastic member is polytetrafluoroethylene, polyamide or polyimide.
Preferably, the buffer structure comprises a first magnet and a second magnet, the first magnet is arranged at the tail part of the sliding sheet, the second magnet is arranged at the tail part of the sliding sheet groove, and the magnetic poles of the opposite sides of the first magnet and the second magnet are the same.
According to another aspect of the present application, there is provided a compressor, comprising the pump body assembly as described above.
According to another aspect of the present application, there is provided an air conditioner, comprising the pump body assembly as described above.
The application provides a pump body subassembly, which comprises a main shaft, go up the flange, the lower flange, cylinder and roller, the roller is fixed for main shaft circumference, be provided with the gleitbretter groove on the roller, it is provided with the gleitbretter to slide in the gleitbretter groove, the head of gleitbretter and the inner wall butt of cylinder, form the tail chamber between the afterbody of gleitbretter and the afterbody of gleitbretter groove, upward be provided with the back pressure groove on flange and/or the lower flange, the back pressure groove is the ring channel, tail chamber and back pressure groove intercommunication, be provided with buffer structure between the afterbody of gleitbre. The back pressure groove of the application adopts a ring-shaped groove structure, so that oil can flow in the back pressure groove along the circumferential direction, when the slip sheet is in a contraction stage, the compression effect of the slip sheet is buffered through the circumferential flow of the oil, thereby avoiding the oil-holding phenomenon, avoiding the problem of excessive slip sheet back pressure caused by excessive oil pressure lifting of a slip sheet tail cavity, further avoiding the abnormal abrasion problem of the slip sheet head part caused by excessive slip sheet back pressure, meanwhile, because of the existence of the ring-shaped back pressure groove, the problem of insufficient slip sheet back pressure caused by the possibility that the slip sheet needs to extend out can be solved, through the arrangement of the buffer structure, the buffer effect of the buffer structure can be utilized, in the contraction process of the slip sheet, the slip sheet is prevented from directly impacting the cylinder, under the condition that the slip sheet does not extend out, tail pressure is provided through the buffer structure, so that the slip sheet, the operational reliability of the compressor is improved.
Drawings
FIG. 1 is a diagram illustrating a structure of a back pressure groove and a slide vane of a pump body assembly according to the prior art;
FIG. 2 is a diagram of a force structure of a slide of the pump block assembly of FIG. 1;
FIG. 3 is a cross-sectional structural view of a pump block assembly according to an embodiment of the present application;
FIG. 4 is an exploded view of the pump block assembly of the embodiment of the present application;
FIG. 5 is an exploded view of the vane and spindle of the pump assembly according to the embodiment of the present disclosure;
FIG. 6 is a perspective view of a slider of the pump assembly according to an embodiment of the present disclosure;
FIG. 7 is a schematic structural view of the pump body assembly of the embodiment of the present application when the resilient member is not compressed;
FIG. 8 is a schematic view of the pump block assembly of the present embodiment when one of the resilient members is compressed;
fig. 9 is a schematic structural diagram of a pump body assembly according to another embodiment of the present application.
The reference numerals are represented as:
1. a main shaft; 2. an upper flange; 3. a lower flange; 4. a cylinder; 5. a roller; 6. a slide groove; 7. sliding blades; 8. a tail cavity; 9. a first back pressure groove; 10. a second back pressure groove; 11. an elastic member; 12. caulking grooves; 13. a first magnet; 14. a lower cover plate; 15. a gear oil pump; 16. a second magnet.
Detailed Description
With reference to fig. 3 to 9, according to an embodiment of the present application, the pump body assembly includes a main shaft 1, an upper flange 2, a lower flange 3, a cylinder 4 and a roller 5, the roller 5 is circumferentially fixed with respect to the main shaft 1, a slide groove 6 is provided on the roller 5, a slide 7 is slidably provided in the slide groove 6, a head of the slide 7 abuts against an inner wall of the cylinder 4, a tail cavity 8 is formed between a tail of the slide 7 and a tail of the slide groove 6, a back pressure groove is provided on the upper flange 2 and/or the lower flange 3, the back pressure groove is an annular groove, the tail cavity 8 is communicated with the back pressure groove, and a buffer structure is provided between the tail of the slide 7 and the tail of the slide groove 6. In order to distinguish the back pressure groove on the upper flange 2 from the back pressure groove on the lower flange 3, the back pressure groove of the upper flange 2 is designated as a first back pressure groove 9 and the back pressure groove of the lower flange 3 is designated as a second back pressure groove 10. In this embodiment, the back pressure groove may be provided only on the upper flange 2, may be provided only on the lower flange 3, or may be provided on both the upper flange 2 and the lower flange 3.
The back pressure groove of the application adopts a ring-shaped groove structure, so that oil can flow in the back pressure groove along the circumferential direction, namely an oil-retaining structure is cancelled, when the sliding vane 7 is in a contraction stage, the compression effect of the sliding vane 7 is buffered through the circumferential flow of the oil, so that the oil-retaining phenomenon is avoided, the problem that the back pressure of the sliding vane is too large due to the fact that the oil pressure in the tail cavity 8 of the sliding vane groove 6 is lifted too high is avoided, the problem that the head part of the sliding vane is abnormally abraded due to the too large back pressure is further avoided, meanwhile, due to the existence of the ring-shaped back pressure groove, the problem that the back pressure of the sliding vane is not enough when the sliding vane 7 extends out is possibly caused, through the arrangement of the buffer structure, in the contraction process of the sliding vane, the impact effect of the sliding vane 7 can be buffered by the buffer structure, the sliding vane is prevented from directly impacting a cylinder, under the condition that the back pressure of, provide afterbody pressure for gleitbretter 7 through reaction force for the gleitbretter can keep the contact of head with the cylinder inner wall, improves the operational reliability of compressor. In addition, the annular backpressure groove is adopted, so that the oil pressure is more stable, and the oil liquid flows more smoothly.
In the working process of the pump body assembly, the cylinder 4 is fixed differently, the main shaft 1 is eccentrically installed relative to the cylinder 4, the roller 5 and the main shaft 1 are concentrically arranged, the relative positions of the centers of the roller 5 and the cylinder 4 are fixed, the gap between the roller 5 and the cylinder 4 is changed along the circumferential direction, the roller 5 and the cylinder 4 are internally tangent at a certain position, and the gap between the roller 5 and the cylinder 4 is the largest at the other end in the same radial direction as the tangent point position.
The main shaft 1 and the roller 5 may be fixedly connected after being separately molded, or at least fixed in relative position in the circumferential direction, or may be directly and integrally molded.
The pump body assembly further comprises a lower cover plate 14 and a gear oil pump 15, wherein the lower cover plate 14 is arranged at one end, far away from the cylinder 4, of the lower flange 3, and the gear oil pump 15 is arranged on the outer side of the lower cover plate 14 and used for pumping oil into the central hole and conveying the oil into the second back pressure groove 17 through the central hole and the side hole formed in the main shaft 1.
In one embodiment, the cushioning structure is an elastic member 11. In the process of contracting the sliding sheet 7, the sliding sheet can slide into the sliding sheet groove 6 under the extrusion action of the air cylinder 4, in the process, when the sliding sheet 7 moves inwards to a certain position, the elastic piece 11 is extruded, the elastic piece 11 generates elastic deformation after being extruded, the impact action of the sliding sheet 7 can be absorbed by the elastic deformation, thereby avoiding the problem of insufficient back pressure stability caused by adopting an annular back pressure groove, avoiding the damage caused by the direct impact of the sliding sheet 7 on the cylinder 4, when the sliding vane 7 reaches the minimum sliding position, along with the rotation of the roller 5, the sliding vane 7 can extend out under the elastic action of the elastic piece 11, the elastic piece 11 can provide enough back pressure for the sliding vane 7, the head of the sliding vane 7 can be ensured to be always contacted with the inner wall of the cylinder, the operation reliability of the compressor is ensured, meanwhile, the problem of abnormal abrasion of the head of the slip sheet caused by overlarge back pressure of the slip sheet can be effectively avoided.
In this embodiment, the elastic member 11 is mounted on the tail of the slider 7. In other embodiments, the elastic member 11 may be mounted at the rear of the slide slot 6 and extend toward the slide 7.
The tail part of the sliding sheet 7 is provided with an embedded groove 12, an elastic piece 11 is embedded in the embedded groove 12, and the elastic piece 11 extends out of the embedded groove 12. The sliding sheet 7 can be in interference fit with the caulking groove 12, and can also be fixed in the caulking groove 12 in an adhesion mode.
Preferably, the elastic member 11 is disposed in the middle area of the tail portion of the sliding vane 7, so that a relatively uniform cavity can be formed around the elastic member 11, and when the back pressure oil is filled in the cavity, a balanced back pressure acting force can be formed at the tail portion of the sliding vane 7, thereby preventing the sliding vane 7 from being inclined due to unbalanced stress, improving the stability of the stress structure of the sliding vane 7, and improving the reliability of the sliding vane 7.
Preferably, the mounting area of the elastic piece 11 at the tail part of the sliding sheet 7 is S1, the end surface area at the tail part of the sliding sheet 7 is S2, wherein 2S1 is less than or equal to S2. Because when the sliding sheet 7 extends out of the sliding sheet groove 6 and the elastic piece 11 at the tail part just recovers the original size, the elastic piece 11 is in contact with the groove bottom of the sliding sheet groove 6 but has no elastic acting force, at the moment, the sliding sheet 7 extends out of the groove bottom and needs to rely on the oil pressure action at the tail part of the sliding sheet 7, in order to ensure enough oil action, the tail part of the sliding sheet 7 needs to have a larger oil stress surface, verification proves that when the installation area S1 at the tail part and the end surface area S2 at the tail part of the sliding sheet 7 meet the requirement that 2S1 is not more than or equal to S2, the back pressure oil can be ensured to be capable of providing enough back pressure force for the sliding sheet 7 when the elastic piece 11 does not release the elastic force, and the.
Since the trailing end face of the slider 7 is generally rectangular, the elastic member 11 is preferably a rectangular block.
The elastic member 11 is made of a high polymer material or engineering plastic, has excellent impact resistance, has a compressive strength of 50-150 Mpa, and can provide sufficient back pressure.
Preferably, the elastic member 11 is made of polytetrafluoroethylene, polyamide or polyimide, so that the elastic member 11 has good heat resistance, refrigerant resistance and oil resistance, thereby having good working performance.
Referring to fig. 9 in combination, in another embodiment of the present application, the buffering structure includes a first magnet 13 and a second magnet 16, the first magnet 13 is installed at the tail of the sliding piece 7, the second magnet 16 is installed at the tail of the sliding piece slot 6, and the magnetic poles of the opposite sides of the first magnet 13 and the second magnet 16 are the same.
First magnet 13 inlays the afterbody at gleitbretter 7, and second magnet 16 inlays the afterbody at gleitbretter groove 6, can utilize the magnet homopolar repulsion principle for gleitbretter 7 is nearer at the tail distance of exhaust end and gleitbretter groove 6, and the repulsion that magnet provided is bigger, thereby effectively satisfies the backpressure demand.
According to the embodiment of the application, the compressor comprises the pump body assembly, and the pump body assembly is the pump body assembly.
According to the embodiment of the application, the air conditioner comprises the pump body assembly, and the pump body assembly is the pump body assembly.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed. The foregoing is only a preferred embodiment of the present application, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present application, and these modifications and variations should also be considered as the protection scope of the present application.

Claims (10)

1. The utility model provides a pump body subassembly, its characterized in that, includes main shaft (1), upper flange (2), lower flange (3), cylinder (4) and roller (5), roller (5) for main shaft (1) circumference is fixed, be provided with slide groove (6) on roller (5), it is provided with gleitbretter (7) to slide in slide groove (6), the head of gleitbretter (7) with the inner wall butt of cylinder (4), the afterbody of gleitbretter (7) with form tail chamber (8) between the afterbody of slide groove (6), upper flange (2) and/or be provided with the back pressure groove on lower flange (3), the back pressure groove is the ring channel, tail chamber (8) with back pressure groove intercommunication, the afterbody of gleitbretter (7) with be provided with buffer structure between the afterbody of slide groove (6).
2. Pump body assembly according to claim 1, characterized in that the damping structure is an elastic element (11).
3. The pump body assembly according to claim 2, characterized in that said elastic member (11) is mounted at the tail of said slide (7).
4. The pump body assembly according to claim 3, wherein a caulking groove (12) is formed at the tail part of the sliding piece (7), the elastic piece (11) is embedded in the caulking groove (12), and the elastic piece (11) extends out of the caulking groove (12); and/or the elastic piece (11) is arranged at the middle area of the tail part of the sliding piece (7).
5. The pump block assembly according to claim 4, characterized in that the elastic member (11) has a mounting area S1 at the tail of the slider (7), and an end surface area S2 at the tail of the slider (7), wherein 2S1 ≦ S2.
6. The pump body assembly according to any one of claims 2 to 5, characterized in that the elastic member (11) is a polymeric material or an engineering plastic.
7. Pump body assembly according to claim 6, characterized in that said elastic element (11) is polytetrafluoroethylene, polyamide or polyimide.
8. The pump body assembly according to claim 1, wherein the damping structure comprises a first magnet (13) and a second magnet (16), the first magnet (13) is mounted at the tail of the slide (7), the second magnet (16) is mounted at the tail of the slide slot (6), and the magnetic poles of the opposite sides of the first magnet (13) and the second magnet (16) are the same.
9. A compressor comprising a pump body assembly, characterized in that it is a pump body assembly according to any one of claims 1 to 8.
10. An air conditioner comprising a pump body assembly, wherein the pump body assembly is as claimed in any one of claims 1 to 8.
CN202010608380.2A 2020-06-29 2020-06-29 Pump body subassembly, compressor and air conditioner Pending CN111794966A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010608380.2A CN111794966A (en) 2020-06-29 2020-06-29 Pump body subassembly, compressor and air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010608380.2A CN111794966A (en) 2020-06-29 2020-06-29 Pump body subassembly, compressor and air conditioner

Publications (1)

Publication Number Publication Date
CN111794966A true CN111794966A (en) 2020-10-20

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Application Number Title Priority Date Filing Date
CN202010608380.2A Pending CN111794966A (en) 2020-06-29 2020-06-29 Pump body subassembly, compressor and air conditioner

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Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113982925A (en) * 2021-11-08 2022-01-28 珠海格力电器股份有限公司 Roller assembly, compressor and air conditioner with same

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO940809A1 (en) * 1994-10-11 1996-04-11 Alliedsignal Automotive It Spa VACUUM ROTARY PUMP, WITH SPHERICAL FILLING ORGANS
CN107013456A (en) * 2017-05-08 2017-08-04 珠海格力节能环保制冷技术研究中心有限公司 The slide plate and rotary blade type compressor of a kind of rotary blade type compressor
CN207500118U (en) * 2017-10-30 2018-06-15 珠海格力电器股份有限公司 Rotary blade type compressor and its pump assembly
CN210196009U (en) * 2019-07-09 2020-03-27 林成好 Oil-free air compressor
CN111271277A (en) * 2018-12-04 2020-06-12 上海海立电器有限公司 Pump body structure and rotor type compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO940809A1 (en) * 1994-10-11 1996-04-11 Alliedsignal Automotive It Spa VACUUM ROTARY PUMP, WITH SPHERICAL FILLING ORGANS
CN107013456A (en) * 2017-05-08 2017-08-04 珠海格力节能环保制冷技术研究中心有限公司 The slide plate and rotary blade type compressor of a kind of rotary blade type compressor
CN207500118U (en) * 2017-10-30 2018-06-15 珠海格力电器股份有限公司 Rotary blade type compressor and its pump assembly
CN111271277A (en) * 2018-12-04 2020-06-12 上海海立电器有限公司 Pump body structure and rotor type compressor
CN210196009U (en) * 2019-07-09 2020-03-27 林成好 Oil-free air compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113982925A (en) * 2021-11-08 2022-01-28 珠海格力电器股份有限公司 Roller assembly, compressor and air conditioner with same

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Application publication date: 20201020