CN114183368A - Exhaust structure and compressor of compressor - Google Patents
Exhaust structure and compressor of compressor Download PDFInfo
- Publication number
- CN114183368A CN114183368A CN202111496339.1A CN202111496339A CN114183368A CN 114183368 A CN114183368 A CN 114183368A CN 202111496339 A CN202111496339 A CN 202111496339A CN 114183368 A CN114183368 A CN 114183368A
- Authority
- CN
- China
- Prior art keywords
- exhaust hole
- cylinder
- compressor
- hole
- roller
- 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.)
- Granted
Links
- 239000007787 solid Substances 0.000 claims description 10
- 101000634117 Arabidopsis thaliana RNA polymerase sigma factor sigD, chloroplastic Proteins 0.000 claims description 4
- 238000005096 rolling process Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 abstract description 22
- 230000006835 compression Effects 0.000 abstract description 18
- 238000007906 compression Methods 0.000 abstract description 18
- 238000007789 sealing Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000029058 respiratory gaseous exchange Effects 0.000 description 3
- 230000008719 thickening Effects 0.000 description 3
- 238000013022 venting Methods 0.000 description 3
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Images
Classifications
-
- 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
- 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
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a compressor and a gas exhaust structure thereof, wherein the gas exhaust structure of the compressor comprises: the cylinder comprises a cylinder cavity, the roller is arranged in the cylinder cavity, the first flange is arranged on the axial end face of the cylinder, a first exhaust hole is formed in the first flange, an air suction port is formed in the cylinder, and the first exhaust hole is arranged in the projection plane of the axial end face of the cylinder and is completely located in the cylinder cavity. According to the invention, the communication between the air suction cavity and the compression cavity through the exhaust hole can be avoided; at the same time, the refrigerant in the exhaust hole is not communicated with the air suction cavity, so that the amount of the refrigerant in the first exhaust hole flowing back to the air suction hole through the air suction cavity is reduced; thereby the compressor efficiency has been promoted by a wide margin.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to an exhaust structure of a compressor and the compressor.
Background
In the existing rotary compressor, generally, an exhaust hole is arranged on an end cover, a crescent groove is arranged on a cylinder, the edge of the exhaust hole and the edge of the crescent groove are generally basically attached, the exhaust hole projects towards the cylinder, and a part of the exhaust hole is generally positioned in the inner circle of the cylinder and a part of the exhaust hole is positioned outside the inner circle of the cylinder;
in every duty cycle of compressor, when the roller passes through the exhaust hole, the chamber of breathing in and the compression chamber of compressor can be through the exhaust hole UNICOM, and at this moment, remaining refrigerant can cause the backward flow to influence the compressor efficiency through breathing in chamber and suction hole UNICOM in the compression intracavity, and remaining refrigerant also can cause the backward flow to influence the compressor efficiency in breathing in through the exhaust hole in exhaust hole and the crescent moon groove simultaneously.
The compressor in the prior art has the technical problems that residual refrigerant exhausted by a cylinder flows back to a suction hole to affect suction of the compressor, affect the energy efficiency of the compressor and the like, so that the exhaust structure of the compressor and the compressor are researched and designed.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to overcome the defects that in the compressor in the prior art, residual refrigerant exhausted by the air cylinder flows back to the air suction hole to affect air suction of the compressor, the backflow problem exists, and the energy efficiency of the compressor is affected, so that the exhaust structure of the compressor and the compressor are provided.
In order to solve the above problems, the present invention provides a discharge structure of a compressor, including:
the cylinder comprises a cylinder cavity, the roller is arranged in the cylinder cavity, the first flange is arranged on the axial end face of the cylinder, a first exhaust hole is formed in the first flange, an air suction port is formed in the cylinder, and the first exhaust hole is arranged in the projection plane of the axial end face of the cylinder and is completely located in the cylinder cavity.
In some embodiments, a distance between the first exhaust hole and the inner circle of the cylinder is 0.2mm or more.
In some embodiments, the air cylinder further comprises a sliding sheet, the air cylinder has a cylinder center, the sliding sheet has a sliding sheet center line, and an included angle θ between a line connecting any point on the first exhaust hole and the cylinder center and the sliding sheet center line satisfies: theta is more than or equal to minus 5 degrees and less than or equal to 20 degrees.
In some embodiments, the first exhaust port is sealed by a thickness direction of the roller, the thickness direction being a radial direction; the radial maximum span of the first exhaust hole is Lmax, the thickness of the roller is sigma, and the condition that sigma is more than or equal to Lmax +0.2mm is met;
in some embodiments, the first exhaust port is sealed by a thickness direction of the roller, the thickness direction being a radial direction; the thickness of the roller is sigma, the first exhaust hole is a round hole, the diameter of the first exhaust hole is D, and the requirement that sigma-D is larger than or equal to 0.2mm is met.
In some embodiments, there is a partial region of the first vent that falls within a region through which the inner bore of the roller passes; and when the inner hole of the roller passes through the first exhaust hole, the part of the first exhaust hole in the inner hole of the roller can be sealed by a solid part in the inner hole of the roller.
In some embodiments, the solid portion is a crankshaft thrust face.
In some embodiments, the cylinder further comprises a sliding vane, a second exhaust hole and a second flange, the first flange is arranged on one axial side end face of the cylinder, the second flange is arranged on the other axial side end face of the cylinder, the second exhaust hole is arranged on the second flange or on the first flange, and the second exhaust hole is arranged close to the sliding vane relative to the first exhaust hole in a projection plane of the axial end face of the cylinder.
In some embodiments, the second vent has a vent area S2 that is less than a vent area S1 of the first vent.
The invention also provides a compressor, which comprises the exhaust structure of the compressor.
In some embodiments, the compressor is a rolling rotor compressor, a swing rotor compressor, or a sliding vane compressor.
The invention provides an exhaust structure of a compressor and the compressor, which have the following beneficial effects:
1. according to the improved exhaust hole, the position of the first exhaust hole formed in the first flange is set to enable the first exhaust hole to be completely positioned in the cylinder cavity in the projection plane of the axial end face of the cylinder, and the projection of the exhaust hole is not intersected with the inner circle of the cylinder and is arranged in the inner circle of the cylinder; by the arrangement, the communication between the air suction cavity and the compression cavity through the exhaust hole is avoided; at the same time, the refrigerant in the exhaust hole is not communicated with the air suction cavity, so that the amount of the refrigerant in the first exhaust hole flowing back to the air suction hole through the air suction cavity is reduced; thereby greatly improving the energy efficiency of the compressor;
2. the first exhaust hole is arranged on the first flange, so that the first exhaust hole is opened after the first exhaust hole is completely closed, sucked and closed through the movement of the roller when the suction port is opened, high-pressure refrigerants remained in the first exhaust hole can be further prevented from being communicated with the suction hole, the suction is not influenced, refrigerants remained in the exhaust of the cylinder are prevented from flowing back to the suction hole, the normal suction of the compressor is ensured, and the energy efficiency of the compressor is further improved. The second exhaust hole is arranged close to the sliding sheet relative to the first exhaust hole through the arrangement of the second exhaust hole, so that the clearance volume can be reduced through the second exhaust hole, the high pressure of the residual refrigerant can be effectively utilized, and the problem that the high pressure of the part of refrigerant is released inefficiently is solved.
Drawings
FIG. 1a is a perspective view of a pump body in the prior art;
FIG. 1b is a longitudinal cross-sectional view of a pump body of the prior art;
FIG. 1c is a top view of a prior art cylinder and roller arrangement;
FIG. 1d is a top view of a prior art flange portion;
FIG. 2 is a view of the mating configuration of the cylinder, roller and first exhaust port in the flange of the present invention;
fig. 2a is a partially enlarged view of a portion B in fig. 2;
FIG. 3 is a graph of the fit dimension relationship of the cylinder, roller and first exhaust port in the first flange of the present invention;
4.1-4.4 are views of the engagement of the rollers of the present invention at different crank angle positions;
5.1-5.5 are structural views of the seal fit of the thickening of the roller to the first exhaust port at different crank angle positions of the roller of the present invention;
fig. 6.1 is a bottom view of the first flange of the present invention;
FIG. 6.2 is a longitudinal cross-sectional view of the cylinder, roller, crankshaft and first flange of the present invention in combination;
fig. 6.3 is a longitudinal section (solid part of crankshaft) of the cylinder, roller, crankshaft and first flange of the invention in cooperation.
The reference numerals are represented as:
1. a cylinder; 10. a cylinder cavity; 101. an air suction cavity; 102. an exhaust chamber; 11. an air suction port; 12. a crescent groove; 13. the center of the cylinder; 2. a roller; 21. an inner bore; 3. a first flange; 31. a first exhaust port; 32. a second vent hole; 4. sliding blades; 40. the slide sheet central line; 41. a high-pressure side edge; 7. a crankshaft; 71. a solid portion; a. a sealing distance; b. a leakage path.
Detailed Description
As shown in fig. 2 to 6.3, the present invention provides a discharge structure of a compressor, which includes:
the cylinder 1 comprises a cylinder cavity 10, the roller 2 is arranged in the cylinder cavity 10, the first flange 3 is arranged on the axial end face of the cylinder 1, the first flange 3 is provided with a first exhaust hole 31, the cylinder 1 is provided with an air suction port 11, and the first exhaust hole 31 is arranged at a position such that the first exhaust hole 31 is completely positioned in the cylinder cavity 1 in a projection plane of the axial end face of the cylinder 1.
According to the improved exhaust hole, the position of the first exhaust hole formed in the first flange is set to enable the first exhaust hole to be completely positioned in the cylinder cavity in the projection plane of the axial end face of the cylinder, and the projection of the exhaust hole is not intersected with the inner circle of the cylinder and is arranged in the inner circle of the cylinder; by the arrangement, the communication between the air suction cavity 101 and the compression cavity (the exhaust cavity 102) through the exhaust hole is avoided; at the same time, the refrigerant in the exhaust hole is not communicated with the air suction cavity, so that the amount of the refrigerant in the first exhaust hole flowing back to the air suction hole through the air suction cavity is reduced; thereby the compressor efficiency has been promoted by a wide margin.
As shown in fig. 1, in the conventional compressor, an exhaust hole (i.e., a second exhaust hole 32) is formed in an end cover, a crescent groove 12 is formed in a cylinder, an edge of the exhaust hole and an edge of the crescent groove are generally arranged in a substantially fitting manner, and the exhaust hole generally has a portion within an inner circle of the cylinder and a portion outside the inner circle of the cylinder in projection to the cylinder. When the roller passes through the exhaust hole, the suction cavity and the compression cavity of the compressor can be communicated through the exhaust hole, at the moment, the residual refrigerant in the compression cavity can be communicated with the suction hole through the suction cavity, the compressor energy efficiency is influenced by backflow, and meanwhile, the residual refrigerant in the exhaust hole and the crescent groove can also flow back into the suction hole through the exhaust hole to influence the compressor energy efficiency.
In the exhaust structure of the compressor, as shown in fig. 2, at least one exhaust hole on the end cover is arranged in the projection range of the inner circle of the cylinder and is not intersected with the inner circle of the cylinder; the projection of the exhaust hole is not intersected with the inner circle of the cylinder after the improvement, and the exhaust hole is arranged in the inner circle of the cylinder; by the arrangement, the communication between the air suction cavity and the compression cavity through the exhaust hole is avoided; at the same time, the refrigerant in the exhaust hole is not communicated with the air suction cavity, so that the amount of the refrigerant in the exhaust hole flowing back to the air suction hole through the air suction cavity is reduced; thereby the compressor efficiency has been promoted by a wide margin.
In some embodiments, the cylinder 1 is a full circular cylinder without a crescent. The position of the cylinder corresponding to the first exhaust hole on the end cover (the first flange) is not provided with a crescent groove; when the exhaust holes arranged on the end cover are not intersected with the inner circle of the roller, the air cylinder does not need to be provided with a crescent groove and the exhaust holes for exhaust in a matched manner; and after the crescent groove on the cylinder is further cancelled, the condition that the roller passes through the exhaust hole can be further reduced, the compression cavity and the air suction cavity are communicated through the exhaust hole, and the energy efficiency of the compressor is further improved.
In some embodiments, the distance between the first exhaust hole 31 and the inner circle of the cylinder 1 is 0.2mm or more. Preferably, the distance between the point of the exhaust hole closest to the inner circle of the cylinder and the inner circle of the cylinder is more than or equal to 0.2 mm; the sealing distance a of more than 0.2mm is set, so that a better sealing effect can be ensured; as shown in fig. 3.
In some embodiments, the air cylinder 1 further comprises a slide sheet 4, the air cylinder 1 has a cylinder center 13, the slide sheet 4 has a slide sheet center line 40, and an included angle θ between a line connecting any point on the first exhaust hole 31 and the cylinder center 13 and the slide sheet center line 40 satisfies: theta is more than or equal to minus 5 degrees and less than or equal to 20 degrees.
The included angle theta between the connecting line of the exhaust hole closest to the air suction cavity and the center of the air cylinder and the central line of the sliding sheet meets the following requirements: theta is more than or equal to 5 degrees and less than or equal to 20 degrees, and theta is more preferably more than or equal to 5 degrees and less than or equal to 15 degrees; the closest point is defined as a negative angle to the left of the vane center and a positive angle to the right of the vane center.
And defining the compression end point as the intersection point of one side of the sliding vane close to the exhaust side and the inner circle of the cylinder. Wherein the closer the vent hole area is to the compression end point, the more efficient the area is to vent; as the more closed the angle by the roller (the closer to the end of compression). The exhaust holes are arranged close to the sliding sheet as much as possible so as to have a good exhaust effect, so that the exhaust holes are prevented from being closed by the rollers too early; i.e. the vent should be made to cover the compression end point as much as possible. Therefore, the included angle theta between the connecting line of any point of the exhaust hole and the center of the cylinder and the central line of the slip sheet meets the following requirements: theta is less than or equal to 20 degrees; meanwhile, the sliding sheet is attached to the outer circle of the roller, and a working cavity of the compressor is divided into a high-pressure compression cavity and a low-pressure suction cavity. The exhaust port should therefore not occupy too many positions of the slide, which would otherwise result in too small a sealing distance of the compression chamber through the slide to the leakage path b of the suction chamber or in direct leakage, and is generally required to satisfy-5 deg. ≦ θ.
Fig. 4.1 to 4.3 show, respectively, embodiments corresponding to θ ═ 6.4 °, θ ═ 5.4 °, θ ═ 2.3 °; FIG. 4.4 shows that the leak path sealing distance is reduced due to the bleed hole arrangement occupying the slide position;
in some embodiments, the first venting holes 31 are sealed by the thickness direction of the roller 2, which is the radial direction; the radial maximum span of the first exhaust holes 31 is Lmax, the thickness of the roller 2 is sigma, and the requirement that sigma is larger than or equal to Lmax +0.2mm is met. The exhaust hole is thickened and sealed by a roller; the radial maximum span of the exhaust hole is Lmax, the thickness of the roller is sigma, and the requirement that sigma is more than or equal to Lmax +0.2mm is met; as shown in fig. 5.1, in the existing exhaust hole structure, there is a sealing distance between the roller inner hole 21 and the exhaust hole; fig. 5.2 is this scheme exhaust hole, compares 5.1, in order to guarantee exhaust area, satisfies this scheme requirement simultaneously, will exhaust the hole and remove great distance toward the cylinder center to the problem that fig. 5.3 shows has been caused. In fig. 5.3, the roller inner hole is a high-pressure area, the exhaust hole covers the roller inner hole, the roller wall thickness and the air suction cavity of the compressor can cause the refrigerant in the roller inner hole to flow back to the air suction cavity of the cylinder through the exhaust hole, and the energy efficiency of the compressor is affected.
FIGS. 5.4 and 5.5 show the two shapes of vent structures of this solution, which ensure σ ≧ Lmax +0.2mm by roller thickening, thus ensuring no leakage.
In some embodiments, the first venting holes 31 are sealed by the thickness direction of the roller 2, which is the radial direction; the thickness of the roller 2 is sigma, the first exhaust holes 31 are round holes, the diameter of the first exhaust holes 31 is D, and the requirement that sigma-D is larger than or equal to 0.2mm is met. When the vent hole is a round hole, the diameter of the vent hole is D, and the requirement that sigma-D is more than or equal to 0.2mm is met; when the vent hole is a round hole, the maximum radial span of the vent hole is Lmax ═ D. Can guarantee like this to form sufficient sealed effect through roller thickness to first exhaust hole, prevent that the gas of roller hole from getting into in the first exhaust hole.
In some embodiments, there is a partial area of the first venting hole 31, falling in the area where the inner bore of the roller 2 passes; and when the inner hole 21 of the roller passes through the first exhaust hole 31, the part of the first exhaust hole 31 in the inner hole of the roller can be sealed by a solid part 71 in the inner hole of the roller. Part of the exhaust hole area falls into the roller inner hole passing area, and when the roller inner hole passes through the exhaust hole, the exhaust hole is closed by a crankshaft or other solid parts; through roller thickening, can realize sealing the exhaust hole, but the roller is too thick, can bring the high scheduling problem of consumption, and in addition, roller thickness is a critical dimension, and the change of thickness also can influence the change of other critical dimensions of compressor to influence the efficiency of compressor.
As shown in fig. 6.1 and 6.2, the exhaust holes are opened to the roller inner holes in the scheme, but corresponding technical means are not adopted to prevent the high-pressure areas of the roller inner holes from being communicated with the air replenishing holes. A leak as shown in figure 5.3 can result.
Fig. 6.3 shows that the exhaust hole exists a part of the area which falls into the roller inner hole passing area, and when the roller inner hole passes through the exhaust hole, the exhaust hole is closed by the solid part of the crankshaft.
In some embodiments, the solid portion is a crankshaft thrust face.
In some embodiments, the cylinder further includes a sliding vane 4, a second exhaust hole, and a second flange, the first flange 3 is disposed on one axial side end face of the cylinder 1, the second flange is disposed on the other axial side end face of the cylinder 1, the second exhaust hole is disposed on the second flange or on the first flange, and the second exhaust hole is disposed close to the sliding vane 4 with respect to the first exhaust hole 31 in a projection plane of the axial end face of the cylinder.
The cylinder is provided with two exhaust holes; the other vent hole is a conventional vent hole; this scheme of adoption exhaust hole, there is certain region, and this exhaust hole has closed in the compression chamber, but compression intracavity volume still reduces again. In order to prevent the partial refrigerant from being over-compressed, another conventional exhaust hole is needed to exhaust the refrigerant which cannot be exhausted by the exhaust hole.
In some embodiments, the discharge area S2 of the second discharge hole is smaller than the discharge area S1 of the first discharge hole 31.
The exhaust holes are main exhaust holes, the exhaust area is S1, the other conventional exhaust hole is used for residual refrigerant which cannot be exhausted by the exhaust holes, the area of the conventional exhaust hole is S2, and S1 is larger than or equal to S2; this scheme exhaust hole can avoid the compression chamber through the exhaust hole with inhale chamber UNICOM, consequently set up this scheme exhaust hole and be main exhaust hole, can set up great, conventional exhaust hole can set up lessly to reduce the adverse effect that conventional exhaust hole brought.
The invention also provides a compressor, which comprises the exhaust structure of the compressor.
In some embodiments, the compressor is a rolling rotor compressor, a swing rotor compressor, or a sliding vane compressor.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, 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 invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (12)
1. A discharge structure of a compressor, characterized in that: the method comprises the following steps:
the air cylinder comprises an air cylinder (1), a roller (2) and a first flange (3), wherein the air cylinder (1) comprises an air cylinder cavity (10), the roller (2) is arranged in the air cylinder cavity (10), the first flange (3) is arranged on the axial end face of the air cylinder (1), a first exhaust hole (31) is formed in the first flange (3), an air suction port (11) is formed in the air cylinder (1), and the first exhaust hole (31) is arranged at a position which enables the first exhaust hole (31) to be completely located in the air cylinder cavity (1) in the projection plane of the axial end face of the air cylinder (1).
2. The discharge structure of a compressor according to claim 1, wherein:
the air cylinder (1) is of a structure of a whole circular cylinder body without a crescent groove.
3. The discharge structure of a compressor according to claim 1, wherein:
the distance between the first exhaust hole (31) and the inner circle of the cylinder (1) is larger than or equal to 0.2 mm.
4. The discharge structure of a compressor according to claim 1, wherein:
still include gleitbretter (4), cylinder (1) has cylinder center (13), gleitbretter (4) has gleitbretter central line (40), arbitrary one on first exhaust hole (31) with the line of cylinder center (13) with contained angle theta between gleitbretter central line (40) satisfies: theta is more than or equal to minus 5 degrees and less than or equal to 20 degrees.
5. The discharge structure of a compressor according to claim 1, wherein:
the first exhaust hole (31) is sealed in the thickness direction of the roller (2), and the thickness direction is a radial direction; the radial maximum span of the first exhaust holes (31) is Lmax, the thickness of the roller (2) is sigma, and the requirement that sigma is larger than or equal to Lmax +0.2mm is met.
6. The discharge structure of a compressor according to claim 1, wherein:
the first exhaust hole (31) is sealed in the thickness direction of the roller (2), and the thickness direction is a radial direction; the thickness of the roller (2) is sigma, the first exhaust holes (31) are round holes, the diameter of the first exhaust holes (31) is D, and the requirement that sigma-D is larger than or equal to 0.2mm is met.
7. The discharge structure of a compressor according to any one of claims 1 to 6, wherein:
the first exhaust hole (31) has a partial area which falls on the area where the inner hole (21) of the roller (2) passes; and when the inner hole of the roller passes through the first exhaust hole (31), the part of the first exhaust hole (31) in the inner hole of the roller can be sealed by a solid part (71) in the inner hole of the roller.
8. The discharge structure of a compressor according to claim 7, wherein:
the solid part is a crankshaft thrust end face.
9. The discharge structure of a compressor according to any one of claims 1 to 8, wherein:
still include gleitbretter (4), second exhaust hole and second flange, first flange (3) set up on the axial side terminal surface of cylinder (1), the second flange sets up on the axial another side terminal surface of cylinder (1), the second exhaust hole sets up on the second flange or on the first flange, and in the projection plane of the axial terminal surface of cylinder the second exhaust hole for first exhaust hole (31) and be close to gleitbretter (4) and set up.
10. The discharge structure of a compressor according to claim 9, wherein:
the discharge area S2 of the second discharge hole is smaller than the discharge area S1 of the first discharge hole (31).
11. A compressor, characterized by: a discharge structure including the compressor of any one of claims 1 to 10.
12. The discharge structure of a compressor according to claim 11, wherein:
the compressor is a rolling rotor compressor, a swing rotor compressor or a sliding vane compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111496339.1A CN114183368B (en) | 2021-12-08 | 2021-12-08 | Exhaust structure of compressor and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111496339.1A CN114183368B (en) | 2021-12-08 | 2021-12-08 | Exhaust structure of compressor and compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114183368A true CN114183368A (en) | 2022-03-15 |
| CN114183368B CN114183368B (en) | 2023-09-05 |
Family
ID=80603971
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111496339.1A Active CN114183368B (en) | 2021-12-08 | 2021-12-08 | Exhaust structure of compressor and compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114183368B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN204877945U (en) * | 2015-08-18 | 2015-12-16 | 珠海凌达压缩机有限公司 | Rolling rotor type compressor |
| CN107100842A (en) * | 2017-06-30 | 2017-08-29 | 广东美芝制冷设备有限公司 | The compression mechanism of compressor and the compressor with it |
| US20170342982A1 (en) * | 2015-01-28 | 2017-11-30 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Sliding Vane Type Compressor and Exhaust Structure Thereof |
-
2021
- 2021-12-08 CN CN202111496339.1A patent/CN114183368B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20170342982A1 (en) * | 2015-01-28 | 2017-11-30 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Sliding Vane Type Compressor and Exhaust Structure Thereof |
| EP3252313A1 (en) * | 2015-01-28 | 2017-12-06 | Gree Green Refrigeration Technology Center Co. Ltd. of Zhuhai | Sliding vane compressor and exhaust structure thereof |
| CN204877945U (en) * | 2015-08-18 | 2015-12-16 | 珠海凌达压缩机有限公司 | Rolling rotor type compressor |
| CN107100842A (en) * | 2017-06-30 | 2017-08-29 | 广东美芝制冷设备有限公司 | The compression mechanism of compressor and the compressor with it |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114183368B (en) | 2023-09-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7896631B2 (en) | Vane pump | |
| CN216554388U (en) | Pump body subassembly, compressor, air conditioner | |
| CN110360111A (en) | Cylinder, pump assembly, compressor and air conditioner | |
| CN110805555B (en) | Pump body structure, compressor, air conditioner | |
| CN114183368A (en) | Exhaust structure and compressor of compressor | |
| CN212202465U (en) | Compression mechanism and scroll compressor | |
| CN210829717U (en) | Cylinder, pump body subassembly, compressor and air conditioner | |
| CN114087180B (en) | Pump body assembly, compressor and air conditioner | |
| CN201288665Y (en) | Rotary compressor cylinder | |
| CN216518626U (en) | Pump body subassembly, compressor, air conditioner | |
| CN212003586U (en) | Leakage-reducing matched cylinder for rotor compressor | |
| CN108425845A (en) | A kind of screw compressor | |
| CN205190207U (en) | Scroll compressor's stator and rotor | |
| CN110145465B (en) | Scroll sealing device of scroll compressor, scroll compressor and air conditioner | |
| CN114183369B (en) | Exhaust structure of compressor and compressor | |
| CN210196017U (en) | Thrust surface lubricating structure, compressor and air conditioner | |
| CN109026696B (en) | Compressor pump body, compressor and air conditioner | |
| CN114251268B (en) | Exhaust structure of compressor and compressor | |
| CN207513827U (en) | Screw compressor and air conditioner | |
| CN207813928U (en) | The compression mechanism and compressor of compressor | |
| CN114183367B (en) | Exhaust structure of compressor and compressor | |
| CN220667824U (en) | Piston for compressor and compressor | |
| CN100455801C (en) | Air leakage preventing device for closed compressor | |
| CN210106172U (en) | Rotary compressor and compression mechanism and refrigerating device thereof | |
| WO2022205802A1 (en) | Scroll plate assembly, scroll compressor, and air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |