CN114183368B - Exhaust structure of compressor and compressor - Google Patents
Exhaust structure of compressor and compressor Download PDFInfo
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- CN114183368B CN114183368B CN202111496339.1A CN202111496339A CN114183368B CN 114183368 B CN114183368 B CN 114183368B CN 202111496339 A CN202111496339 A CN 202111496339A CN 114183368 B CN114183368 B CN 114183368B
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- cylinder
- exhaust hole
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- roller
- hole
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- 239000007787 solid Substances 0.000 claims description 9
- 101000634117 Arabidopsis thaliana RNA polymerase sigma factor sigD, chloroplastic Proteins 0.000 claims description 4
- 238000005096 rolling process Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 abstract description 22
- 230000006835 compression Effects 0.000 abstract description 18
- 238000007906 compression Methods 0.000 abstract description 18
- 238000004891 communication Methods 0.000 abstract description 4
- 238000007789 sealing Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 230000013011 mating Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000008719 thickening Effects 0.000 description 2
- 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
- 238000000034 method Methods 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000029058 respiratory gaseous exchange Effects 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
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
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- 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 discharge structure thereof, wherein the discharge 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, the arrangement position of the first exhaust hole is in the projection plane of the axial end face of the cylinder, and the first exhaust hole 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 suction cavity, so that the quantity of the refrigerant in the first exhaust hole flowing back to the suction hole through the suction cavity is reduced; thereby greatly improving the compressor efficiency.
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 formed in an end cover, a crescent groove is formed in a cylinder, the edge of the exhaust hole and the edge of the crescent groove are generally basically attached, the exhaust hole projects to the cylinder, and a part of the exhaust hole is generally located inside the inner circle of the cylinder, and a part of the exhaust hole is located outside the inner circle of the cylinder;
in every working cycle of the compressor, when the roller passes through the exhaust hole, the air suction cavity and the compression cavity of the compressor are communicated through the exhaust hole, at the moment, residual refrigerant in the compression cavity is communicated with the air suction hole through the air suction cavity, so that backflow is caused to influence the energy efficiency of the compressor, and meanwhile, residual refrigerant in the exhaust hole and the crescent groove is also caused to flow back into the air suction hole through the exhaust hole, so that backflow is caused to influence the energy efficiency of the compressor.
Because the compressor in the prior art has the technical problems that the residual refrigerant in the exhaust of the air cylinder flows back to the air suction hole to influence the air suction of the compressor, the energy efficiency of the compressor is influenced and the like, the invention designs an exhaust structure of the compressor and the compressor.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to overcome the defects that the air suction of the compressor is influenced by the fact that residual refrigerant in the exhaust of the air cylinder flows back to the air suction hole and the energy efficiency of the compressor is influenced by the fact that the reflux problem exists in the compressor in the prior art, and therefore 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, comprising:
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, the arrangement position of the first exhaust hole is in the projection plane of the axial end face of the cylinder, and the first exhaust hole is completely located in the cylinder cavity.
In some embodiments, the distance between the first exhaust hole and the inner circle of the cylinder is greater than or equal to 0.2mm.
In some embodiments, the method further comprises a sliding vane, wherein the cylinder is provided with a cylinder center, the sliding vane is provided with a sliding vane center line, and an included angle theta between a connecting line of any point on the first exhaust hole and the cylinder center and the sliding vane center line is as follows: θ is more than or equal to 5 degrees and less than or equal to 20 degrees.
In some embodiments, the first vent 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 sigma is more than or equal to Lmax plus 0.2mm;
in some embodiments, the first vent 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 sigma-D is more than or equal to 0.2mm.
In some embodiments, the first vent has a partial region that falls in a region through which the inner bore of the roller passes; and a portion of the first vent hole located in the inner bore of the roller is sealable by a solid portion of the inner bore of the roller as the inner bore of the roller passes through the first vent hole.
In some embodiments, the solid portion is a crankshaft thrust end face.
In some embodiments, the engine further comprises a sliding sheet, a second exhaust hole and a second flange, wherein the first flange is arranged on one axial side end surface of the cylinder, the second flange is arranged on the other axial side end surface of the cylinder, the second exhaust hole is arranged on the second flange or the first flange, and the second exhaust hole is arranged close to the sliding sheet relative to the first exhaust hole in a projection plane of the axial end surface of the cylinder.
In some embodiments, the exhaust area S2 of the second exhaust hole is smaller than the exhaust area S1 of the first exhaust hole.
The invention also provides a compressor comprising the discharge structure of the compressor of any one of the preceding claims.
In some embodiments, the compressor is a rolling rotor compressor, a wobble rotor compressor, or a sliding vane compressor.
The exhaust structure of the compressor and the compressor provided by the invention have the following beneficial effects:
1. according to the improved scheme, the position of the first exhaust hole formed in the first flange is set to be in the projection plane of the axial end face of the cylinder, the first exhaust hole is completely positioned in the cylinder cavity, 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; the arrangement avoids the communication between the air suction cavity and the compression cavity through the exhaust hole; at the same time, the refrigerant in the exhaust hole is not communicated with the suction cavity, so that the quantity of the refrigerant in the first exhaust hole flowing back to the suction hole through the suction cavity is reduced; thereby greatly improving the energy efficiency of the compressor;
2. the position of the first exhaust hole formed in the first flange is set so that the first exhaust hole is opened after the first exhaust hole is completely closed and the air suction hole is closed through the movement of the roller when the air suction port is opened, so that the residual high-pressure refrigerant in the first exhaust hole can be further prevented from being communicated with the air suction hole, the air suction is not influenced, the residual refrigerant in the air cylinder is prevented from flowing back to the air suction hole, the normal air suction of the compressor is ensured, and the energy efficiency of the compressor is further improved. The invention also enables the second exhaust hole to be arranged close to the sliding sheet relative to the first exhaust hole through the arrangement of the second exhaust hole, can reduce the clearance volume through the second exhaust hole, can effectively utilize the high pressure of the residual refrigerant, and solves the problem that the high pressure of the part of refrigerant is released ineffectively.
Drawings
FIG. 1a is a perspective view of a pump body according to 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 block diagram of a prior art cylinder and roller combination;
FIG. 1d is a top view of a prior art flange portion;
FIG. 2 is a mating block diagram of a first exhaust port on a cylinder, roller and flange of the present invention;
FIG. 2a is an enlarged partial view of portion B of FIG. 2;
FIG. 3 is a diagram of the mating dimensions of the cylinder, roller and first exhaust port on the first flange of the present invention;
FIGS. 4.1-4.4 are block diagrams showing the mating of the rollers of the present invention at different crank angle positions;
FIGS. 5.1-5.5 are block diagrams showing the seal fit of the thickened rollers to the first vent at different crank angle positions of the rollers of the present invention;
FIG. 6.1 is a bottom view of a 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 mated;
fig. 6.3 is a longitudinal section (solid portion of the crankshaft) of the cylinder, roller, crankshaft and first flange of the present invention mated.
The reference numerals are expressed as:
1. a cylinder; 10. a cylinder chamber; 101. an air suction cavity; 102. an exhaust chamber; 11. an air suction port; 12. crescent grooves; 13. a cylinder center; 2. a roller; 21. an inner bore; 3. a first flange; 31. a first exhaust hole; 32. a second exhaust hole; 4. a sliding sheet; 40. a sliding vane central line; 41. a high pressure side; 7. a crankshaft; 71. a physical portion; a. a sealing distance; b. a leakage path.
Detailed Description
2-6.3, the present invention provides a discharge structure of a compressor, comprising:
the cylinder 1 comprises a cylinder cavity 10, a roller 2 and a first flange 3, wherein 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, a first exhaust hole 31 is formed in the first flange 3, an air suction port 11 is formed in the cylinder 1, and the first exhaust hole 31 is arranged in a position in which the first exhaust hole 31 is completely located in the cylinder cavity 1 in the projection plane of the axial end face of the cylinder 1.
According to the improved scheme, the position of the first exhaust hole formed in the first flange is set to be in the projection plane of the axial end face of the cylinder, the first exhaust hole is completely positioned in the cylinder cavity, 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 this arrangement, communication between the suction chamber 101 and the compression chamber (the discharge chamber 102) through the discharge hole is avoided; at the same time, the refrigerant in the exhaust hole is not communicated with the suction cavity, so that the quantity of the refrigerant in the first exhaust hole flowing back to the suction hole through the suction cavity is reduced; thereby greatly improving the compressor efficiency.
As shown in fig. 1, in the conventional compressor, an exhaust hole (i.e., the second exhaust hole 32) is formed in an end cover, a crescent 12 is formed in a cylinder, the edge of the exhaust hole and the edge of the crescent are generally basically fit, the exhaust hole projects toward the cylinder, and a part of the exhaust hole is generally located inside the cylinder and a part of the exhaust hole is located outside the cylinder. When the roller passes through the exhaust hole, the air suction cavity and the compression cavity of the compressor are communicated through the exhaust hole, at the moment, residual refrigerant in the compression cavity is communicated with the air suction hole through the air suction cavity, so that backflow is caused to influence the compressor energy efficiency, and meanwhile, residual refrigerant in the exhaust hole and the crescent groove is also caused to flow back into the air suction hole through the exhaust hole, so that backflow is caused to influence the compressor energy efficiency.
According to the exhaust structure of the compressor, as shown in fig. 2, at least one exhaust hole on an end cover is arranged in the projection range of the inner circle of a cylinder and does not intersect with the inner circle of the cylinder; after improvement, the projection of the exhaust hole in the scheme is not intersected with the inner circle of the cylinder and is arranged in the inner circle of the cylinder; the arrangement avoids the communication between the air suction cavity and the compression cavity through the exhaust hole; at the same time, the refrigerant in the exhaust hole is not communicated with the suction cavity, so that the quantity of the refrigerant in the exhaust hole flowing back to the suction hole through the suction cavity is reduced; thereby greatly improving the compressor efficiency.
In some embodiments, the cylinder 1 is a full circular cylinder without a crescent groove. A crescent groove is not arranged at the position of the cylinder corresponding to the first exhaust hole on the end cover (the first flange); when the exhaust hole arranged on the end cover is not intersected with the inner circle of the roller, a crescent groove is not required to be processed on the cylinder and the exhaust hole is matched for exhausting; and further cancel the crescent moon groove on the cylinder, can further reduce the roller when passing through the exhaust hole position, compression chamber and suction chamber pass through exhaust hole UNICOM, further promoted the compressor efficiency.
In some embodiments, the distance between the first exhaust hole 31 and the inner circumference of the cylinder 1 is 0.2mm or more. Preferably, the distance between the nearest point of the exhaust hole and the inner circle of the cylinder is more than or equal to 0.2mm; the sealing distance a of more than 0.2mm is set, so that a good sealing effect can be ensured; as shown in fig. 3.
In some embodiments, the air cylinder 1 further comprises a sliding vane 4, the air cylinder 1 has an air cylinder center 13, the sliding vane 4 has a sliding vane center line 40, and an included angle θ between a line connecting any point on the first air exhaust hole 31 and the air cylinder center 13 and the sliding vane center line 40 meets the following conditions: θ is more than or equal to 5 degrees and less than or equal to 20 degrees.
The included angle theta between the connecting line of the nearest point of the exhaust hole from the air suction cavity and the center of the air cylinder and the center line of the sliding vane is as follows: θ is not less than 5 ° and not more than 20 °, further preferably not less than 5 ° and not more than 15 °; the nearest point is defined as negative angle on the left side of the slide center and positive angle on the right side of the slide center.
The compression end point is defined as the intersection of the cylinder inner circle and one side of the vane close to the exhaust side. Wherein the closer the region of the vent is to the compression end point, the more efficient the region is in venting; because the more rearward the angle closed by the roller (closer to the end of compression). In order to achieve a good exhaust effect of the exhaust holes, the exhaust holes should be arranged as close to the sliding sheets as possible, so that the exhaust holes are prevented from being closed too early by the rollers; i.e. the vent should be as far as possible to cover the compression end point. 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 sliding vane meets the following conditions: θ is less than or equal to 20 degrees; meanwhile, the sliding sheets are attached to the outer circles of the rollers, and the working cavity of the compressor is divided into a high-pressure compression cavity and a low-pressure air suction cavity. The discharge holes should not occupy too many positions of the vane, otherwise the sealing distance of the leakage path b of the compression chamber through the vane to the suction chamber is too small or leakage is directly caused, and it is generally required to satisfy-5 deg. theta.
Fig. 4.1-4.3 show, respectively, each corresponding embodiment, θ=6.4 °, θ=5.4 °, θ= -2.3 °; FIG. 4.4 shows that the sealing distance of the leakage path is reduced as the vent hole arrangement occupies the slide position;
in some embodiments, the first vent 31 is sealed by a thickness direction of the roller 2, the thickness direction being a radial direction; the radial maximum span of the first exhaust hole 31 is Lmax, the thickness of the roller 2 is sigma, and sigma is more than or equal to Lmax+0.2mm. 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 sigma is more than or equal to Lmax plus 0.2mm; as shown in fig. 5.1, in the prior art, there is a sealing distance between the roller inner hole 21 and the vent hole; fig. 5.2 shows the exhaust hole in the scheme, compared with fig. 5.1, in order to ensure the exhaust area, and meet the requirement of the scheme, the exhaust hole is moved to the center of the cylinder by a larger distance, so that the problem shown in fig. 5.3 is 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, so that the refrigerant in the roller inner hole flows back to the air suction cavity of the cylinder through the exhaust hole, and the compressor energy efficiency is affected.
FIGS. 5.4 and 5.5 show two vent structures of the present solution, ensuring sigma. Gtoreq.Lmax+0.2 mm by roller thickening, thus ensuring no leakage.
In some embodiments, the first vent 31 is sealed by a thickness direction of the roller 2, the thickness direction being a radial direction; the thickness of the roller 2 is sigma, the first exhaust hole 31 is a round hole, the diameter of the first exhaust hole 31 is D, and sigma-D is more than or equal to 0.2mm. When the exhaust hole is a round hole, the diameter of the exhaust hole is D, and sigma-D is more than or equal to 0.2mm; when the vent is a round hole, the vent radial maximum span is lmax=d. This ensures that a sufficient seal is formed with the first vent through the thickness of the roller to prevent gas from the roller bore from entering the first vent.
In some embodiments, the first vent hole 31 has a partial area, which falls in the area where the inner hole of the roller 2 passes; and a portion of the first exhaust hole 31 located in the inner bore of the roller can be sealed by the solid portion 71 in the inner bore of the roller when the inner bore 21 of the roller passes through the first exhaust hole 31. When the partial area of the exhaust hole falls into the roller inner hole passing area and the roller inner hole passes through the exhaust hole, the exhaust hole is closed by a crankshaft or other solid parts; through the roller thickening, can realize sealing the exhaust hole, but the roller is too thick, can bring the high scheduling problem of consumption, in addition, the 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 energy efficiency of compressor.
As shown in fig. 6.1 and 6.2, the vent holes are opened to the inner holes of the roller in the scheme, but corresponding technical means are not adopted to prevent the high-pressure areas of the inner holes of the roller from communicating with the air supplementing holes. Causing leakage as shown in fig. 5.3.
Fig. 6.3 shows that the partial area where the exhaust hole exists falls into the roller inner hole passing area, and the exhaust hole is closed by the solid part of the crankshaft when the roller inner hole passes through the exhaust hole.
In some embodiments, the solid portion is a crankshaft thrust end face.
In some embodiments, the air cylinder further comprises a sliding vane 4, a second air exhaust hole and a second flange, wherein the first flange 3 is arranged on one axial side end surface of the air cylinder 1, the second flange is arranged on the other axial side end surface of the air cylinder 1, the second air exhaust hole is arranged on the second flange or the first flange, and the second air exhaust hole is arranged close to the sliding vane 4 relative to the first air exhaust hole 31 in the projection plane of the axial end surface of the air cylinder.
The cylinder is provided with two exhaust holes; the other vent is a conventional vent; by adopting the scheme, the exhaust hole has a certain area, and the exhaust hole is closed in the compression cavity, but the volume in the compression cavity is still reduced. In order to prevent the refrigerant from being excessively compressed, another conventional vent hole is required to discharge the refrigerant which cannot be discharged by the vent hole in the present embodiment.
In some embodiments, the exhaust area S2 of the second exhaust hole is smaller than the exhaust area S1 of the first exhaust hole 31.
The exhaust hole in the scheme is a main exhaust hole, the exhaust area is S1, the other conventional exhaust hole is used for residual refrigerant which cannot be exhausted by the exhaust hole in the scheme, the conventional exhaust hole area is S2, and the requirement that S1 is more than or equal to S2 is met; the compression chamber can be avoided through exhaust hole and chamber UNICOM of breathing in to this scheme exhaust hole, consequently sets up this scheme exhaust hole and be main exhaust hole, can set up great, and conventional exhaust hole can set up less to reduce the adverse effect that conventional exhaust hole brought.
The invention also provides a compressor comprising the discharge structure of the compressor of any one of the preceding claims.
In some embodiments, the compressor is a rolling rotor compressor, a wobble rotor compressor, or a sliding vane compressor.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention. The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (9)
1. An exhaust structure of a compressor, characterized in that: comprising the following steps:
the cylinder comprises a cylinder (1), a roller (2) and a first flange (3), wherein 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), a first exhaust hole (31) is formed in the first flange (3), an air suction port (11) is formed in the cylinder (1), and the first exhaust hole (31) is arranged at a position in a projection plane of the axial end face of the cylinder (1), and the first exhaust hole (31) is completely located inside the cylinder cavity;
still include gleitbretter (4), cylinder (1) have cylinder center (13), gleitbretter (4) have gleitbretter central line (40), arbitrary point on first exhaust hole (31) with the line at cylinder center (13) with contained angle θ between gleitbretter central line (40) satisfies: theta is more than or equal to 5 degrees and less than or equal to 20 degrees;
the cylinder also comprises a second exhaust hole and a second flange, wherein the first flange (3) is arranged on one axial side end surface of the cylinder (1), the second flange is arranged on the other axial side end surface of the cylinder (1), the second exhaust hole is arranged on the second flange or the first flange, and the second exhaust hole is arranged close to the sliding sheet (4) relative to the first exhaust hole (31) in the projection plane of the axial end surface of the cylinder; the exhaust area S2 of the second exhaust hole is smaller than the exhaust area S1 of the first exhaust hole (31).
2. The compressor discharge structure according to claim 1, wherein:
the cylinder (1) is of a whole circular cylinder body without a crescent groove.
3. The compressor discharge structure according to claim 1, wherein:
the distance between the first exhaust hole (31) and the inner circle of the cylinder (1) is more than or equal to 0.2mm.
4. The compressor discharge structure according to claim 1, wherein:
the first exhaust hole (31) is sealed by the thickness direction of the roller (2), and the thickness direction is a radial direction; the radial maximum span of the first exhaust hole (31) is Lmax, the thickness of the roller (2) is sigma, and sigma is more than or equal to Lmax+0.2mm.
5. The compressor discharge structure according to claim 1, wherein:
the first exhaust hole (31) is sealed by 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 hole (31) is a round hole, the diameter of the first exhaust hole (31) is D, and sigma-D is more than or equal to 0.2mm.
6. The compressor discharge structure according to any one of claims 1 to 5, wherein:
the first exhaust hole (31) has a partial area and falls in the area where the inner hole (21) of the roller (2) passes; and a portion of the first vent hole (31) located in the bore of the roller is sealable by a solid portion (71) of the bore of the roller as the bore of the roller passes through the first vent hole (31).
7. The compressor discharge structure of claim 6, wherein:
the solid part is a crankshaft thrust end face.
8. A compressor, characterized in that: a discharge structure comprising the compressor of any one of claims 1-7.
9. The compressor as set forth in claim 8, wherein:
the compressor is a rolling rotor compressor, a swinging 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 |
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| Publication Number | Publication Date |
|---|---|
| CN114183368A CN114183368A (en) | 2022-03-15 |
| CN114183368B true CN114183368B (en) | 2023-09-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111496339.1A Active CN114183368B (en) | 2021-12-08 | 2021-12-08 | Exhaust structure of compressor and compressor |
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| 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 |
| EP3252313A1 (en) * | 2015-01-28 | 2017-12-06 | Gree Green Refrigeration Technology Center Co. Ltd. of Zhuhai | Sliding vane compressor and exhaust structure thereof |
-
2021
- 2021-12-08 CN CN202111496339.1A patent/CN114183368B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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| Publication number | Publication date |
|---|---|
| CN114183368A (en) | 2022-03-15 |
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