CN110805557A - Cylinder, pump body subassembly, compressor and air conditioner - Google Patents

Cylinder, pump body subassembly, compressor and air conditioner Download PDF

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Publication number
CN110805557A
CN110805557A CN201911016533.8A CN201911016533A CN110805557A CN 110805557 A CN110805557 A CN 110805557A CN 201911016533 A CN201911016533 A CN 201911016533A CN 110805557 A CN110805557 A CN 110805557A
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CN
China
Prior art keywords
exhaust
cylinder
exhaust section
section
compressor
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
CN201911016533.8A
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Chinese (zh)
Inventor
张心爱
王珺
吴健
孙成龙
闫鹏举
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 Green Refrigeration Technology Center Co Ltd of Zhuhai
Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd 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 Green Refrigeration Technology Center Co Ltd of Zhuhai filed Critical Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority to CN201911016533.8A priority Critical patent/CN110805557A/en
Publication of CN110805557A publication Critical patent/CN110805557A/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
    • F04C18/356—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 outer member
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

The application provides a cylinder, a pump body assembly, a compressor and an air conditioner, wherein the cylinder comprises a first end face, an exhaust port is arranged on the first end face, and the exhaust port comprises at least two exhaust sections; each the oblique cut angle of exhaust section is followed the exhaust direction angle of gas vent is steadilyd decrease, when the tank bottom of exhaust section extends along the straight line, the oblique cut angle does the straight line at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the plane, the oblique cut angle does the plane at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the arc, the oblique cut angle be the tangent line of arc tank bottom with the contained angle that first terminal surface formed. The cylinder can increase the effective exhaust flow area of the cylinder while controlling the clearance volume of the compressor not to be increased, reduce the exhaust resistance and the over-compression loss of the compressor, reduce the energy consumption of the compressor and improve the working efficiency of the compressor, thereby improving the energy efficiency of the compressor.

Description

Cylinder, pump body subassembly, compressor and air conditioner
Technical Field
The application belongs to the technical field of air conditioning, and particularly relates to an air cylinder, a pump body assembly, a compressor and an air conditioner.
Background
The cylinder is an important core part of a pump body component of a rolling rotor compressor, an exhaust port 1 of the existing cylinder is generally designed into a crescent groove exhaust section with an opening facing the inner circumferential surface and the end surface of the cylinder, and the clearance volume of the compressor pump body needs to be controlled within a smaller reasonable range, so that the exhaust port 1 of the cylinder is generally arranged as small as possible, the exhaust circulation resistance is relatively large, and unsmooth exhaust is easily caused, the exhaust resistance of the compressor pump body is too large or unsmooth exhaust is caused, the gas pulsation in a compression cavity is greatly increased, the energy consumption of the compressor is increased, and the energy efficiency is reduced.
Disclosure of Invention
Therefore, the technical problem that this application will be solved lies in providing a cylinder, pump body subassembly, compressor and air conditioner, can increase the effective through flow area of cylinder exhaust when the control compressor clearance volume does not increase, reduces compressor exhaust resistance and excessive compression loss, reduces the compressor energy consumption, improves compressor work efficiency to improve the compressor efficiency.
In order to solve the above problems, the present application provides a cylinder, including a first end surface, where an exhaust port is disposed, and the exhaust port includes at least two exhaust sections; each the oblique cut angle of exhaust section is followed the exhaust direction angle of gas vent is steadilyd decrease, when the tank bottom of exhaust section extends along the straight line, the oblique cut angle does the straight line at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the plane, the oblique cut angle does the plane at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the arc, the oblique cut angle be the tangent line of arc tank bottom with the contained angle that first terminal surface formed.
Preferably, each of the exhaust sections is of a symmetrical configuration.
Preferably, the axes of symmetry of each of said exhaust sections lie in the same plane.
Preferably, at least two exhaust sections include a first exhaust section and a second exhaust section, the chamfer angle of the first exhaust section is greater than the chamfer angle of the second exhaust section, and the groove depth of the first exhaust section is greater than the groove depth of the second exhaust section.
Preferably, at least two exhaust sections include first exhaust section and second exhaust section, first exhaust section the chamfer is greater than second exhaust section the chamfer, first exhaust section is followed cylinder circumference's maximum width is less than first exhaust section is followed cylinder circumference's maximum width, or, first exhaust section with second exhaust section is followed cylinder circumference's maximum width equals.
Preferably, the junctions of adjacent exhaust sections have rounded corners.
Preferably, the slot bottom of the exhaust port is streamlined.
Preferably, the exhaust port further includes an introduction section provided on an inner wall of the cylinder and arranged in an axial direction of the cylinder.
Preferably, the height H of the cylinder and the depth of the exhaust port along the axial direction of the cylinder are H0，1/8H ＜H0＜1/2H。
In another aspect of the invention, a pump body assembly is provided, which comprises the cylinder.
In another aspect of the invention, a compressor is provided, which comprises the cylinder.
In another aspect of the invention, an air conditioner is provided, which comprises the cylinder.
Advantageous effects
The air cylinder provided by the embodiment of the invention can increase the effective exhaust flow area of the air cylinder while controlling the clearance volume of the compressor not to be increased, reduce the exhaust resistance and the over-compression loss of the compressor, reduce the energy consumption of the compressor, and improve the working efficiency of the compressor, thereby improving the energy efficiency of the compressor.
Drawings
FIG. 1 is a schematic diagram of a cylinder of the prior art;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
fig. 3 is a schematic structural view of a cylinder according to embodiment 1 of the present application;
FIG. 4 is a first cross-sectional view B-B of FIG. 3;
FIG. 5 is a second cross-sectional view B-B of FIG. 3;
FIG. 6 is a schematic structural view of a cylinder according to embodiment 2 of the present application;
fig. 7 is a first cross-sectional view of C-C of fig. 6.
FIG. 8 is a second cross-sectional view C-C of FIG. 6;
FIG. 9 is a graph comparing the results of the torque resistance simulation of the conventional cylinder, example 1 and example 2.
The reference numerals are represented as:
1. exhaust ports in the prior art; 2. a cylinder; 21. an exhaust port; 211. a first exhaust section; 212. a second exhaust section; 213. and a lead-in section.
Detailed Description
Referring to fig. 1 to 5 in combination, according to embodiment 1 of the present application, a cylinder 2 includes a first end surface, an exhaust port 21 is provided on the first end surface, and the exhaust port 21 includes at least two exhaust sections; each the oblique cut angle of exhaust section is followed the exhaust direction angle of gas vent 21 is steadilyd decrease, when the tank bottom of exhaust section extends along the straight line, the oblique cut angle does the straight line at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the plane, the oblique cut angle does the plane at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the arc, the oblique cut angle be the tangent line of arc tank bottom with the contained angle that first terminal surface formed. The exhaust port 21 is set into at least two exhaust sections, the oblique angles of the exhaust sections are set into different angles, the oblique angles of the sections are decreased progressively along the exhaust direction, the effective exhaust flow area of the air cylinder 2 can be increased while the clearance volume of the compressor is controlled not to be increased, the exhaust resistance and the over-compression loss of the compressor are reduced, the energy consumption of the compressor is reduced, the working efficiency of the compressor is improved, the energy efficiency of the compressor is improved, meanwhile, the airflow pulsation caused by unsmooth exhaust in a pump body is reduced, and the pneumatic noise of the compressor is reduced.
Specifically, in this embodiment, including two exhaust section, as shown in fig. 3, two among the exhaust section, the tank bottom is close to cylinder 2 axis one side exhaust section is first exhaust section 211, and the tank bottom is kept away from cylinder 2 axis one side exhaust section is second exhaust section 212, and the chamfer angle of first exhaust section 211 is A1, and the chamfer angle of second exhaust section 212 is A2.
As shown in fig. 4, the groove bottom of the first venting section 211 is a straight line, and the chamfer angle of the first venting section 211 is the included angle between the straight line of the groove bottom and the first end surface, i.e., a 1. The groove bottom of the second exhaust section 212 is a straight line, and the chamfer angle of the second exhaust section 212 is the included angle between the straight line of the groove bottom and the first end surface, namely A2.
Further, the distance between the joint of the groove bottom and the first end surface of the second exhaust section 212 and the central axis of the cylinder 2 is L, and in the prior art, if the distance between the groove bottom and the central axis of the cylinder is L, the clearance space is inevitably larger than that in the present embodiment, that is, the cross-sectional area of the exhaust port 1 in the prior art in fig. 2 is larger than that of the exhaust port 21 in the present application in fig. 4.
The exhaust section is of a symmetrical structure, so that the stability and the smoothness of gas flowing through the exhaust section are ensured when the cylinder 2 exhausts.
Specifically, in this embodiment, the exhaust section is U type groove, and the tank bottom is the straight line, has further ensured the smooth and easy degree of exhausting.
The symmetry axes of the exhaust sections are located in the same plane.
As shown in fig. 3, the symmetry axes of the exhaust sections in this embodiment are located in the same vertical plane, so that smooth exhaust of gas is ensured, exhaust resistance and over-compression loss of the compressor are reduced, energy consumption of the compressor is reduced, and working efficiency of the compressor is improved, thereby improving energy efficiency of the compressor.
At least two the exhaust section includes first exhaust section 211 and second exhaust section 212, first exhaust section 211 the chamfer is greater than second exhaust section 212 the chamfer, the groove depth of first exhaust section 211 is greater than the groove depth of second exhaust section 212, smooth and easy when having guaranteed the gas vent and exhausting.
Further, the groove depth is the vertical distance from the opening of each exhaust section to the groove bottom.
Specifically, in the present embodiment, the groove depth of the first exhaust section 211 and the second exhaust section 212 is the vertical distance between the opening of the first exhaust section 211 and the second exhaust section 212 and the straight line of the groove bottom.
In this embodiment, the chamfer angle of the first exhaust section 211 is greater than the chamfer angle of the second exhaust section 212, the maximum widths of the first exhaust section 211 and the second exhaust section 212 in the circumferential direction of the cylinder 2 are equal, that is, the circumferential widths of the first exhaust section 211 and the second exhaust section 212 on the inner wall of the cylinder 2 are equal, so that the two exhaust sections with different chamfer angles can be joined smoothly without causing a sharp increase and decrease of the exhaust flow cross-sectional area, thereby minimizing exhaust resistance and airflow pulsation on the premise of minimizing the exhaust clearance volume.
In yet another embodiment, the chamfer angle of the first exhaust section 211 is larger than the chamfer angle of the second exhaust section 212, and the maximum width of the first exhaust section 211 in the circumferential direction of the cylinder 2 is smaller than the maximum width of the first exhaust section 211 in the circumferential direction of the cylinder 2.
The joint of the adjacent exhaust sections is provided with a round angle so as to reduce the exhaust resistance and the airflow pulsation to the maximum extent.
In a preferred embodiment, the groove bottom of the exhaust port 21 is streamlined, that is, the groove bottom of the first exhaust section 211 and the groove bottom of the second exhaust section 212 are connected to form a streamline shape, so that the exhaust port 21 can further reduce the exhaust resistance and the over-compression loss of the compressor, reduce the energy consumption of the compressor, and improve the working efficiency of the compressor.
Further, the resistance to the movement of an object in a fluid is caused by both internal friction and vortex. At very low speeds, the amount of drag is largely determined by internal friction. At higher velocities the swirl is mainly determined, the faster the velocity the greater the effect of the swirl. In order to reduce the resistance effectively, it is sought to avoid the formation of vortices. Through observation of swimming of fishes, the fishes which swim fast, such as hairtails, sharks and the like, are found to have a special cigar-type shape. It has been concluded through a number of experiments that shaping the body in such a shape does reduce the swirling action or avoids the formation of vortices, thus considerably reducing the resistance of the fluid to it, which shape is called streamlined.
The height H of the cylinder 2 and the depth H of the exhaust port 21 along the axial direction of the cylinder 20，1/8H ＜H0< 1/2H, by setting the depth of the exhaust port 21 along the axial direction of the cylinder 2 to be more than 1/8H and less than 1/2H, and the chamfer angle of the first exhaust section 211 to be more than the chamfer angle of the second exhaust section 212, the two exhaust sections with different chamfer angles can be joined smoothly without causing a sharp increase and decrease in the exhaust flow cross-sectional area, thereby minimizing exhaust resistance and airflow pulsation while achieving as small an exhaust clearance volume as possible.
Example 2
As shown in fig. 6 to 8, the exhaust port 21 further includes an introduction section 213, the introduction section 213 is disposed on an inner wall of the cylinder 2 and is disposed along an axial direction of the cylinder 2, and by disposing the introduction section 213, gas in the cylinder 2 is introduced into the first exhaust section 211 through the introduction section 213, so that exhaust resistance and over-compression loss of the compressor can be reduced, energy consumption of the compressor can be reduced, working efficiency of the compressor can be improved, and energy efficiency of the compressor can be improved
As shown in fig. 9, fig. 9 is a transient moment of resistance-rotation angle variation curve, according to theoretical simulation verification, on the premise that the structures of other pump body components are consistent, in example 1 and example 2, compared with the exhaust port 1 in the prior art, the power consumption of the compressor caused by the exhaust resistance is reduced by 24.7%, the transient moment of resistance of the compression mechanism is reduced remarkably in the exhaust process, and the exhaust opening angles of example 1 and example 2 are about 196 °.
Specifically, as can be seen from fig. 9, before the valve plate is opened, the gas pressure in the compression cavity gradually increases along with the rotation angle, the resistance moment gradually increases, the pressure in the compression cavity increases to a certain degree, the valve plate is opened, after the valve plate is opened, the compression cavity of the compressor is in a pressure relief process, and the resistance moment gradually decreases, after the exhaust port 1 in the prior art rotates until the valve plate is opened, the resistance moment does not decrease, but the pressure pulsation and over-compression problems are caused by unsmooth exhaust, so that the resistance moment further increases, and the power consumption of the compressor is increased Phenomena, thereby reducing the compressor reliability risk.
In fig. 9, the abscissa is a rotation angle, which refers to a rotation angle of the pump body of the compressor, i.e., the rotation angle of the crankshaft is located at a position of 0 ° in the sliding vane slot of the cylinder 2 in the eccentric direction of the eccentric portion of the crankshaft (i.e., a position where the sliding vane extends out of the cylinder 2 by a length of 0).
In another aspect of the present embodiment, a pump body assembly is provided, which includes the cylinder 2 described above.
In another aspect of the present embodiment, a compressor is provided, which includes the cylinder 2 described above.
In another aspect of the present embodiment, an air conditioner is provided, which includes the cylinder 2 described above.
The air cylinder provided by the embodiment of the invention can increase the effective exhaust flow area of the air cylinder 2 while controlling the clearance volume of the compressor not to be increased, reduce the exhaust resistance and the over-compression loss of the compressor, reduce the energy consumption of the compressor, improve the working efficiency of the compressor and further improve the energy efficiency of the compressor.
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. A cylinder, characterized in that the cylinder (2) comprises a first end surface, on which an exhaust port (21) is arranged, the exhaust port (21) comprising at least two exhaust sections;
each the oblique cut angle of exhaust section is followed the exhaust direction angle of gas vent (21) is steadilyd decrease, when the tank bottom of exhaust section extends along the straight line, the oblique cut angle does the straight line at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the plane, the oblique cut angle does the plane at tank bottom place with the contained angle that first terminal surface formed, when the tank bottom of exhaust section is the arc, the oblique cut angle be the tangent line of arc tank bottom with the contained angle that first terminal surface formed.
2. The cylinder of claim 1, wherein each exhaust segment is of symmetrical construction.
3. The cylinder of claim 2, wherein axes of symmetry of each exhaust segment lie in the same plane.
4. The cylinder of claim 1, wherein at least two of the exhaust sections comprise a first exhaust section (211) and a second exhaust section (212), the chamfer angle of the first exhaust section (211) being greater than the chamfer angle of the second exhaust section (212), the groove depth of the first exhaust section (211) being greater than the groove depth of the second exhaust section (212).
5. The cylinder according to claim 1, characterized in that at least two of the exhaust sections comprise a first exhaust section (211) and a second exhaust section (212), the chamfer angle of the first exhaust section (211) being larger than the chamfer angle of the second exhaust section (212), the maximum width of the first exhaust section (211) in the circumferential direction of the cylinder (2) being smaller than the maximum width of the first exhaust section (211) in the circumferential direction of the cylinder (2), or the maximum widths of the first exhaust section (211) and the second exhaust section (212) in the circumferential direction of the cylinder (2) being equal.
6. The cylinder according to claim 1, characterized in that the junctions of adjacent exhaust sections have rounded corners and/or the groove bottoms of the exhaust ports (21) are streamlined.
7. The cylinder according to claim 1, wherein the exhaust port (21) further comprises an introduction section (213), and the introduction section (213) is provided on an inner wall of the cylinder (2) and is arranged in an axial direction of the cylinder (2).
8. Cylinder according to claim 1, wherein the height H of the cylinder (2) and the depth H of the exhaust port (21) in the axial direction of the cylinder (2) are equal to each other0，1/8H＜H0＜1/2H。
9. A pump block assembly comprising a cylinder according to any one of claims 1 to 8.
10. A compressor, characterized by comprising a cylinder according to any one of claims 1 to 8.
11. An air conditioner characterized by comprising the cylinder according to any one of claims 1 to 8.
CN201911016533.8A 2019-10-24 2019-10-24 Cylinder, pump body subassembly, compressor and air conditioner Pending CN110805557A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911016533.8A CN110805557A (en) 2019-10-24 2019-10-24 Cylinder, pump body subassembly, compressor and air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911016533.8A CN110805557A (en) 2019-10-24 2019-10-24 Cylinder, pump body subassembly, compressor and air conditioner

Publications (1)

Publication Number Publication Date
CN110805557A true CN110805557A (en) 2020-02-18

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CN201911016533.8A Pending CN110805557A (en) 2019-10-24 2019-10-24 Cylinder, pump body subassembly, compressor and air conditioner

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023020033A1 (en) * 2021-08-20 2023-02-23 珠海格力节能环保制冷技术研究中心有限公司 Cylinder and compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023020033A1 (en) * 2021-08-20 2023-02-23 珠海格力节能环保制冷技术研究中心有限公司 Cylinder and compressor

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