CN111794963A - Pump body subassembly, compressor and air conditioner - Google Patents

Pump body subassembly, compressor and air conditioner Download PDF

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Publication number
CN111794963A
CN111794963A CN202010607612.2A CN202010607612A CN111794963A CN 111794963 A CN111794963 A CN 111794963A CN 202010607612 A CN202010607612 A CN 202010607612A CN 111794963 A CN111794963 A CN 111794963A
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CN
China
Prior art keywords
groove
back pressure
pump body
roller
width
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Granted
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CN202010607612.2A
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Chinese (zh)
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CN111794963B (en
Inventor
胡余生
魏会军
徐嘉
任丽萍
万鹏凯
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to CN202010607612.2A priority Critical patent/CN111794963B/en
Publication of CN111794963A publication Critical patent/CN111794963A/en
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Publication of CN111794963B publication Critical patent/CN111794963B/en
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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. This pump body subassembly includes main shaft (1), lower flange (3), cylinder (4) and roller (5), roller (5) are fixed for main shaft (1) circumference, 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) and the inner wall butt of cylinder (4), form tail chamber (8) between the afterbody of gleitbretter (7) and the afterbody of slide groove (6), be provided with the back pressure groove on lower flange (3), the back pressure groove communicates with tail chamber (8), along the axial direction of main shaft (1), the interval has between the projection of gleitbretter (7) and the projection in back pressure groove. According to the pump body assembly, the problem that the energy efficiency and the reliability of a compressor are affected due to the fact that oil impacts the tail of the sliding piece in the operation process of the existing compressor and the head of the sliding piece is separated from the inner wall of an air cylinder in an inclined mode due to the fact that the oil impacts the tail of the sliding piece is solved.

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 of the compressor.
The oil of the slip sheet backpressure is mainly pumped from an oil pool through an oil pump, then enters the flange backpressure groove through the main shaft center hole and the main shaft side hole connected with the main shaft center hole, and further fills the backpressure cavity.
Referring to fig. 1 to 3, in the conventional scheme, back pressure oil in the motion process of the sliding vane 1 ' is provided by an oil sump, after the oil in the oil sump comes out of the oil sump, the oil firstly enters the lower flange back pressure groove 2 ', fills the lower flange back pressure groove 2 ', and then enters the tail cavity of the sliding vane 1 ', and in the process that the oil surface gradually rises, an impact effect is formed on the tail part of the sliding vane 1 ' located in the tail cavity of the sliding vane 1 ', so that the sliding vane 1 ' is stressed and inclined. The head of the slip sheet 1 'can be obliquely separated from the inner wall 3' of the air cylinder to cause leakage and influence the performance of the compressor, and meanwhile, the slip sheet 1 'can be impacted with the inner wall 3' of the air cylinder when being restored again to influence the reliability of the compressor.
Therefore, in the operation process of the existing compressor, oil impacts the tail of the sliding sheet, so that the head of the sliding sheet is obliquely separated from the inner wall of the air cylinder, leakage occurs, and the energy efficiency and reliability of the compressor are affected.
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 and in the operation process, there is fluid to lead to the gleitbretter afterbody to cause the impact, lead to gleitbretter head and cylinder inner wall to take place the slope and break away from, and then take place to leak, influence the problem of compressor efficiency and reliability.
In order to solve the problem, the application provides a pump body subassembly, including the main shaft, 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 in gleitbretter groove, be provided with the back pressure groove on the lower flange, back pressure groove and tail chamber intercommunication, axial direction along the main shaft, the interval has between the projection of gleitbretter and the projection in back.
Preferably, the communication position of the back pressure groove and the tail cavity is located between the tail end of the sliding piece and the tail end of the tail cavity.
Preferably, the back pressure groove comprises a C-shaped groove.
Preferably, the back pressure groove includes a C-shaped groove and a connecting section, a first end of the connecting section is connected to a first end of the C-shaped groove, a second end of the connecting section is connected to a second end of the C-shaped groove, and a width of the connecting section is smaller than a width of the C-shaped groove.
Preferably, the width of the C-shaped groove is constant.
Preferably, the backpressure groove further comprises an outer ring section arranged on the periphery of the C-shaped groove, the circumferential length of the outer ring section is smaller than that of the C-shaped groove, and the outer ring section is communicated with the C-shaped groove.
Preferably, the outer ring section is concentric with the C-shaped groove; and/or the outer ring section is positioned at the maximum clearance between the roller and the cylinder along the circumferential direction of the roller.
Preferably, the C-shaped groove includes a constant-width section and a widening section, the widening section gradually changes in width in a circumferential direction of the roller, and a width of the widening section is greater than a width of the constant-width section.
Preferably, the widening section is located at the maximum clearance of the roller and the cylinder in the circumferential direction of the roller; and/or, the widening section comprises a convex arc projecting radially outwardly of the roller, the convex arc being tangential to the peripheral wall of the constant-width section.
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, including the main shaft, the lower flange, cylinder and roller, the roller is fixed for main shaft circumference, is 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 in gleitbretter and the afterbody in gleitbretter groove, be provided with the back pressure groove on the lower flange, back pressure groove and tail chamber intercommunication, along the axial direction of main shaft, the interval has between the projection of gleitbretter and the projection in back. In this pump body subassembly, with gleitbretter and backpressure groove along the axial direction's of main shaft projection relation set up to, the interval has between the two, can make projection between them non-overlapping, thereby make the gleitbretter bottom in whole motion process, all be in outside the direct impact scope of the fluid that comes from the backpressure groove, even fluid enters into the tail chamber bottom from the backpressure groove, also can't cause the impact and produce the axial effort to the gleitbretter bottom that lies in the gleitbretter inslot, only can enter into the tail chamber after, form outside gliding backpressure effect to the gleitbretter from the gleitbretter tail end, effectively guarantee the gleitbretter and press and paste on the cylinder inner wall, guarantee the stability of gleitbretter operation in-process, avoid gleitbretter head and cylinder inner wall to take place the slope and break away from, and then take.
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 schematic diagram of the oil flow of the pump block assembly of FIG. 1;
FIG. 3 is a schematic view of the structure of the vane of the pump block assembly of FIG. 1 tilted by an axial impact;
FIG. 4 is a cross-sectional structural view of a pump block assembly according to an embodiment of the present application;
FIG. 5 is an exploded view of the pump block assembly of the embodiment of the present application;
FIG. 6 is a first schematic structural view of a pump block assembly according to an embodiment of the present application;
FIG. 7 is a second schematic view of the pump block assembly of the embodiment of the present application;
FIG. 8 is a third schematic view of the pump block assembly of the embodiment of the present application;
FIG. 9 is a schematic view of a first lower flange back pressure groove configuration of a pump block assembly according to an embodiment of the present application;
FIG. 10 is a schematic view of a second lower flange back pressure groove configuration of the pump block assembly according to an embodiment of the present application;
FIG. 11 is a schematic view of a third lower flange back pressure groove configuration of the pump block assembly according to an embodiment of the present application;
FIG. 12 is a schematic view of a fourth lower flange back pressure groove configuration of the pump block assembly according to an embodiment of the present application;
FIG. 13 is a schematic view of a fifth lower flange back pressure groove configuration of the pump block assembly according to an embodiment of the present application;
FIG. 14 is a schematic view of a sixth lower flange back pressure groove configuration of the pump block assembly according to an embodiment of the present application;
FIG. 15 is a schematic diagram of the oil flow of the pump block assembly according to an embodiment of the present application;
FIG. 16 is a graph comparing the performance testing of the pump block assembly of the present application with that of a prior art pump block assembly;
FIG. 17 is a comparison graph of COP tests of a pump block assembly according to an embodiment of the present application and a pump block assembly according to the prior art;
fig. 18 is a comparison graph of acoustic power testing of the pump body assembly of the embodiment of the present application and the pump body assembly of the prior art.
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 C-shaped groove; 10. a connecting section; 11. an outer ring segment; 12. a constant width section; 13. a variable width section; 14. a lower cover plate; 15. a gear oil pump; 16. a first back pressure groove; 17. a second back pressure groove.
Detailed Description
With reference to fig. 4 to 15, according to an embodiment of the present application, the pump body assembly includes a main shaft 1, 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 lower flange 3, the back pressure groove is communicated with the tail cavity 8, and a gap is provided between a projection of the slide 7 and a projection of the back pressure groove along an axial direction of the main shaft 1. The pump body assembly further comprises an upper flange 2, a back pressure groove is also formed in the upper flange 2, and in order to distinguish the back pressure groove in the upper flange 2 from the back pressure groove in the lower flange 3, the back pressure groove in the upper flange 2 is named as a first back pressure groove 16, and the back pressure groove in the lower flange 3 is named as a second back pressure groove 17.
In the pump body component, the projection relation of the sliding sheet 7 and the second back pressure groove 17 along the axial direction of the main shaft 1 is set to have a space between the sliding sheet 7 and the second back pressure groove, so that the projections of the sliding sheet and the second back pressure groove are not overlapped, so that the bottom of the sliding vane 7 is out of the direct impact range of the oil liquid from the second back pressure groove 17 in the whole movement process, even if oil enters the bottom of the tail cavity 8 from the second back pressure groove 17, the bottom of the sliding vane 7 in the sliding vane groove 6 cannot be impacted to generate axial acting force, and only after the oil enters the tail cavity 8, form outside gliding backpressure effect to gleitbretter 7 from 7 tail ends of gleitbretter, effectively guarantee that gleitbretter 7 presses and paste on 4 inner walls of cylinder, guarantee the stability of 7 operation in-processes of gleitbretter, avoid 7 heads of gleitbretter and 4 inner walls of cylinder to take place the slope and break away from, and then take place to leak, influence the problem of compressor efficiency and reliability.
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.
In the process that the roller 5 rotates along with the cylinder 4, the gap between the roller 5 and the cylinder 4 is gradually changed, so that the volume of a cavity positioned among the roller 5, the cylinder 4 and the sliding sheet 7 is also changed, when the roller rotates towards the direction that the gap is reduced, the volume of the cavity is gradually reduced, and a refrigerant positioned in the cavity is compressed and is discharged through an exhaust port. In the whole rotation process of roller 5, because along main shaft 1's axial direction, the interval has all the time between the projection of gleitbretter 7 and the projection of second backpressure groove 17, consequently no matter which position gleitbretter 7 moves to, fluid can not reach the bottom surface of gleitbretter 7 via second backpressure groove 17 and form the impact to gleitbretter 7, and only can enter into tail chamber 8 earlier, then from 8 internal side directions of tail chamber to gleitbretter 7 exerted pressure, guarantee the backpressure power to gleitbretter 7, make gleitbretter 7 can laminate on the inner wall of cylinder 4 all the time.
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.
The communicating position of the second back pressure groove 17 and the tail cavity 8 is located between the tail end of the sliding piece 7 and the tail end of the tail cavity 8, so that oil can only enter the tail cavity 8 from a communicating channel located between the tail end of the sliding piece 7 and the tail end of the tail cavity 8 after reaching the tail cavity 8 through the second back pressure groove 17, and axial impact can not be formed on the sliding piece 7 by reaching the bottom position of the sliding piece 7.
The second back pressure groove 17 and the communicating position of the tail cavity 8 can also be located at the tail end of the tail cavity 8, and the communicating position is far away from the tail end of the sliding piece 7 more, so that oil can not directly impact the sliding piece 7 in the axial direction, and stability and reliability in the working process of the sliding piece 7 can be guaranteed better. In this embodiment, the tail end of tail chamber 8 is the column hole, and in the cross-section of the central axis of perpendicular to main shaft 1, the diameter in column hole is greater than the width of gleitbretter 7, consequently can effectively avoid fluid on the basis that the backpressure groove forms axial impact to gleitbretter 7, increases the area of intercommunication between tail chamber 8 and the second backpressure groove 17, guarantees that fluid can supply to tail chamber 8 pairs in time fully, provides sufficient backpressure to gleitbretter 7.
Referring to fig. 9 to 14 in combination, the pump body assembly of the present application has several structural forms of the second back pressure groove 17.
Referring to fig. 9, in the first structure of the second back pressure groove 17, the second back pressure groove 17 includes a C-shaped groove 9, the width of the C-shaped groove 9 is constant, and both ends are not communicated, thereby making each back pressure groove not communicated along the circumferential direction, thereby in the process that the sliding vane 7 is withdrawn or extended, oil can be kept in the back pressure groove and can not flow along the circumferential direction, it is ensured that the oil in the back pressure groove can provide sufficient back pressure to the sliding vane 7, the phenomenon of insufficient pressure maintaining caused by the oil flowing along the circumferential direction is avoided, and the stability and reliability of the pump body assembly during operation are improved.
Referring to fig. 10 in combination, in the second structure of the second back pressure groove 17, it is substantially the same as the first structure, except that in this structure, the second back pressure groove 17 further includes an outer ring segment 11 disposed on the outer periphery of the C-shaped groove 9, the circumferential length of the outer ring segment 11 is smaller than that of the C-shaped groove 9, and the outer ring segment 11 communicates with the C-shaped groove 9. This outer ring section 11 has increased the width of C shape groove 9 to can be when the slide groove 6 rotates to outer ring section 11 position, increase the area of intercommunication between second backpressure groove 17 and the tail chamber 8, make fluid can more in time enter into in the tail chamber 8 fully. Since the projections of the sliding vane 7 and the second back pressure groove 17 along the axial direction of the main shaft 1 are not overlapped, even if the outer ring segment 11 is increased and the contact area of the second back pressure groove 17 and the tail cavity 8 is increased, the axial impact on the sliding vane 7 is not caused. For convenience of description, a communication position of the C-shaped groove 9 with the vane groove 6 is defined as a first communication position, and a communication position of the outer ring segment 11 with the vane groove 6 is defined as a second communication position.
In order to further improve the stability of the sliding sheet 7 during operation, when the sliding sheet groove 6 rotates to the position of the outer ring section 11, the second communication position of the outer ring section 11 and the sliding sheet groove 6 is always located between the tail end of the sliding sheet 7 and the tail end of the tail cavity 8, and the first communication position of the C-shaped groove 9 and the second back pressure groove 17 is located between the second communication position and the tail end of the tail cavity 8, so that when the sliding sheet groove 6 rotates to the position of the outer ring section 11, the sliding sheet groove 6 can be communicated through the two communication positions, and oil supply is carried out on the tail cavity 8. When the slide groove 6 rotates out of the outer ring segment 11, the second communication position is now disconnected, and the second back pressure groove 17 can still be supplied with oil via the first communication position.
Preferably, the outer ring segment 11 is concentric with the C-shaped groove 9.
Preferably, the outer ring segment 11 is located at the maximum gap between the roller 5 and the cylinder 4 along the circumferential direction of the roller 5, so that the position of the outer ring segment 11 can be set more reasonably, and the stability and reliability of the sliding sheet 7 during operation can be further improved.
Referring to fig. 11 in combination, in the third structure of the second back pressure groove 17, it is substantially the same as the second structure except that, in the present structure, the C-shaped groove 9 includes a constant-width section 12 and a widening section 13, the widening section 13 is gradually changed in width in the circumferential direction of the roller, and the width of the widening section 13 is larger than that of the constant-width section 12. The structure of this embodiment is relatively similar with the second structure, but in the structure of this embodiment, constant width section 12 and wide width section 13 all belong to the structure of C-shaped groove 9 itself, have adjusted C-shaped groove 9's structure itself, have increased the groove width in the longer position that the gleitbretter 7 stretches out to make the gleitbretter groove 6 when moving to wide width section 13 department, can form the passageway of bigger area with between the second backpressure groove 17, make things convenient for the entering of fluid.
Preferably, the widening section 13 is located at the maximum clearance of the roller 5 from the cylinder 4 in the circumferential direction of the roller 5.
Preferably, the widening section 13 comprises a convex arc projecting radially outwards of the roller 5, the convex arc being tangential to the peripheral wall of the constant-width section 12. The outer side of the variable width section 13 may also be a multi-segment line or a smooth curve.
Referring to fig. 12 in combination, in the fourth structure of the second back pressure groove 17, the second back pressure groove 17 includes a C-shaped groove 9 and a connecting section 10, a first end of the connecting section 10 is connected to a first end of the C-shaped groove 9, a second end of the connecting section 10 is connected to a second end of the C-shaped groove 9, and a width of the connecting section 10 is smaller than a width of the C-shaped groove 9.
In this structure, since both ends of the C-shaped groove 9 communicate with each other through the connecting section 10, the second back pressure groove 17 is formed as a circular groove as a whole, except that this circular groove is not a circular groove of an equal width but is narrowed in width at the connecting section 10. Because the existence of linkage segment 10 for second backpressure groove 17 circumference intercommunication, at gleitbretter 7 motion in-process, can utilize the circumference of fluid to flow and form the damping effect, simultaneously, because the width of linkage segment 10 is less than the width of C shape groove 9, consequently when fluid reachs linkage segment 10 position, linkage segment 10 still can form certain resistance to fluid, thereby plays the pressurize effect that can play when being similar to C shape groove both ends seal to a certain extent.
Referring to fig. 13 in combination, in the fifth structure of the second back pressure groove 17, it is substantially the same as the fourth structure, except that in this structure, the second back pressure groove 17 further includes an outer ring section 11 disposed on the outer periphery of the C-shaped groove 9, the circumferential length of the outer ring section 11 is smaller than that of the C-shaped groove 9, and the outer ring section 11 communicates with the C-shaped groove 9.
Referring collectively to fig. 14, in a sixth configuration of the second back pressure groove 17, which is substantially the same as the fifth configuration, the difference is that, in the present configuration, the C-shaped groove 9 includes a constant-width section 12 and a widening section 13, the widening section 13 gradually changes in width in the circumferential direction of the roller, and the widening section 13 has a width larger than that of the constant-width section 12.
Referring to fig. 15 in combination, after the pump body assembly of the embodiment of the present application is adopted, the oil flows out from the second back pressure groove 17, does not reach the bottom surface of the sliding vane 7, but directly enters the tail cavity 8, and then flows out through the first back pressure groove 16. When fluid enters into tail chamber 8, can form the backpressure effect to the lateral wall of gleitbretter 7 simultaneously for sealed contact can be formed between the tip of gleitbretter 7 and the inner wall of cylinder 4.
Referring to fig. 16 in combination, by comparing the capacity test of the pump body assembly of the embodiment of the present application with the capacity test of the pump body assembly in the prior art, it can be seen that, after the pump body assembly of the embodiment of the present application is adopted, the capacity of the compressor of the embodiment of the present application is maximally improved by 3% compared with the compressor adopting the pump body assembly in the prior art.
Referring to fig. 17 in combination, by comparing the COP test of the pump body assembly according to the embodiment of the present application with the COP test of the pump body assembly according to the prior art, it can be seen that, after the pump body assembly according to the embodiment of the present application is adopted, the COP (energy efficiency) of the compressor according to the embodiment of the present application is improved by 3% at most compared to the compressor adopting the pump body assembly according to the prior art.
With reference to fig. 18, the noise test of the pump body assembly of the embodiment of the present application is compared with the noise test of the pump body assembly in the prior art, and it can be seen that, after the pump body assembly of the embodiment of the present application is adopted, compared with the compressor adopting the pump body assembly in the prior art, the noise of the compressor of the embodiment of the present application can be reduced by 2-4 dB.
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 (11)

1. The utility model provides a pump body subassembly, its characterized in that, includes main shaft (1), 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), be provided with the back pressure groove on lower flange (3), the back pressure groove with tail chamber (8) intercommunication is followed the axial direction of main shaft (1), the projection of gleitbretter (7) with the interval has between the projection in back pressure groove.
2. The pump block assembly according to claim 1, characterized in that the communication position of the back pressure groove with the tail cavity (8) is located between the tail end of the sliding vane (7) and the tail end of the tail cavity (8).
3. The pump block assembly according to claim 1, characterized in that the back pressure groove comprises a C-shaped groove (9).
4. The pump block assembly according to claim 1, characterized in that the back pressure groove comprises a C-shaped groove (9) and a connecting section (10), a first end of the connecting section (10) being connected to a first end of the C-shaped groove (9), a second end of the connecting section (10) being connected to a second end of the C-shaped groove (9), the connecting section (10) having a width smaller than the width of the C-shaped groove (9).
5. Pump body assembly according to claim 3 or 4, characterized in that the width of the C-shaped groove (9) is constant.
6. The pump body assembly according to claim 3 or 4, characterized in that the backpressure groove further comprises an outer ring segment (11) arranged at the periphery of the C-shaped groove (9), the circumferential length of the outer ring segment (11) being smaller than the circumferential length of the C-shaped groove (9), the outer ring segment (11) being in communication with the C-shaped groove (9).
7. The pump body assembly according to claim 6, characterized in that the outer ring segment (11) is concentric with the C-shaped groove (9); and/or the outer ring section (11) is located at the maximum clearance between the roller (5) and the cylinder (4) along the circumferential direction of the roller (5).
8. The pump block assembly according to claim 3 or 4, characterized in that the C-shaped groove (9) comprises a constant-width section (12) and a variable-width section (13), the variable-width section (13) having a width that varies gradually in the circumferential direction of the roller, the variable-width section (13) having a width that is greater than the width of the constant-width section (12).
9. The pump body assembly according to claim 8, characterized in that the variable width section (13) is located, in the circumferential direction of the roller (5), at the maximum clearance of the roller (5) from the cylinder (4); and/or the variable-width section (13) comprises a convex arc protruding towards the radial outer side of the roller (5), and the convex arc is tangent to the peripheral wall of the constant-width section (12).
10. A compressor comprising a pump body assembly, characterized in that it is a pump body assembly according to any one of claims 1 to 9.
11. An air conditioner comprising a pump body assembly, wherein the pump body assembly is as claimed in any one of claims 1 to 9.
CN202010607612.2A 2020-06-29 2020-06-29 Pump body subassembly, compressor and air conditioner Active CN111794963B (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63186982A (en) * 1987-01-28 1988-08-02 Diesel Kiki Co Ltd Vane type compressor
CN107882728A (en) * 2017-10-30 2018-04-06 珠海格力电器股份有限公司 Rotary blade type compressor and its pump assembly
CN108087271A (en) * 2017-11-08 2018-05-29 珠海格力电器股份有限公司 Pump assembly and with its compressor
CN208330729U (en) * 2018-06-05 2019-01-04 珠海格力电器股份有限公司 Compressor pump, compressor and air conditioner
CN109578279A (en) * 2017-09-29 2019-04-05 株式会社丰田自动织机 Vane compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63186982A (en) * 1987-01-28 1988-08-02 Diesel Kiki Co Ltd Vane type compressor
CN109578279A (en) * 2017-09-29 2019-04-05 株式会社丰田自动织机 Vane compressor
CN107882728A (en) * 2017-10-30 2018-04-06 珠海格力电器股份有限公司 Rotary blade type compressor and its pump assembly
CN108087271A (en) * 2017-11-08 2018-05-29 珠海格力电器股份有限公司 Pump assembly and with its compressor
CN208330729U (en) * 2018-06-05 2019-01-04 珠海格力电器股份有限公司 Compressor pump, compressor and air conditioner

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