CN109611337B - Rolling rotor type compressor - Google Patents
Rolling rotor type compressor Download PDFInfo
- Publication number
- CN109611337B CN109611337B CN201710969320.1A CN201710969320A CN109611337B CN 109611337 B CN109611337 B CN 109611337B CN 201710969320 A CN201710969320 A CN 201710969320A CN 109611337 B CN109611337 B CN 109611337B
- Authority
- CN
- China
- Prior art keywords
- cylinder
- rolling rotor
- exhaust
- end cover
- wheel shaft
- 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.)
- Active
Links
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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
The invention discloses a rolling rotor type compressor, which belongs to the technical field of compressors and is characterized in that an exhaust channel is arranged on an eccentric wheel shaft, an exhaust hole is arranged on the cylindrical surface of a rolling rotor, a cylindrical key is embedded on the end surface of the rolling rotor, an exhaust port is arranged on a front end cover of a cylinder, and a radial key slot is arranged on the inner side surface of the front end cover of the cylinder. An exhaust channel on the eccentric shaft communicates the cylindrical surface of the eccentric part of the eccentric shaft with the end surface of the front end cover of the cylinder. In one rotation period of the eccentric wheel shaft, the exhaust channel on the eccentric wheel shaft, the exhaust hole on the rolling rotor and the exhaust hole on the front end cover of the cylinder are not communicated during compression; during exhaust, the exhaust channel on the eccentric wheel shaft, the exhaust hole on the rolling rotor and the exhaust hole on the cylinder end cover are communicated. The invention has the advantages that the rolling rotor compressor controls the exhaust through the change of the mutual positions of the rolling rotor, the eccentric wheel shaft and the front end cover of the cylinder, thereby omitting the exhaust valve, reducing the wearing parts and reducing the noise.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a rolling rotor type compressor.
Background
The rolling rotor compressor has the characteristics of simple structure and easy processing, and is often used as a refrigerating air-conditioning compressor. The working principle of the traditional rolling rotor compressor is that the wall surface of the inner cavity of the cylinder, the outer wall of the rolling rotor and the sliding sheets form a closed cylinder volume, namely a primitive volume, the volume size of the closed cylinder volume changes along with the rotation angle of the rolling rotor, and the pressure of gas in the volume changes along with the volume size of the primitive volume, so that the working process of the compressor is completed.
The conventional scroll-type compressor discharges air through a reed discharge valve. In the working process, the reed exhaust valve frequently collides with the valve seat, and the valve plate is fatigued and damaged while noise is generated.
Disclosure of Invention
In order to overcome the defects of large noise and easy damage of a reed exhaust valve of the traditional rolling rotor type compressor, the invention provides the rolling rotor type compressor which controls the exhaust by means of the change of the mutual positions of a rolling rotor, an eccentric wheel shaft and a front end cover of a cylinder, thereby discarding the structure of the reed exhaust valve, and avoiding the technical problems of frequent collision of a valve plate and a valve seat, noise generation and fatigue damage.
The technical scheme adopted by the invention is as follows: the utility model provides a rolling rotor formula compressor, includes cylinder block, rolling rotor, eccentric shaft, induction port, spring, gleitbretter, cylinder front end housing, cylinder rear end housing, its characterized in that: the cylinder face of the rolling rotor is provided with an exhaust hole, the end face of the rolling rotor is embedded with a cylindrical key, an eccentric part of the eccentric wheel shaft is provided with an exhaust channel communicated with the cylinder face and the end face close to the front end cover of the cylinder, the front end cover of the cylinder is provided with an exhaust port, the inner side face of the front end cover of the cylinder is provided with a radial key slot, and the cylindrical key is inserted into the radial key slot.
Furthermore, a locating pin is embedded on the side, close to the front end cover, of the cylinder body, and a locating hole is formed in the inner side face of the front end cover of the cylinder.
When the rotary compressor works, the motor drives the eccentric wheel shaft to rotate, and the movement of the cylindrical key embedded on the rolling rotor is limited in the radial key groove, so that the rolling rotor has relative rotation relative to the eccentric wheel shaft around the eccentric part of the eccentric wheel shaft, the front end cover of the cylinder is static, and finally, the relative positions of the exhaust channel, the exhaust hole and the exhaust port continuously change regularly in a rotation period. In the compression process, the exhaust channel, the exhaust hole and the exhaust port are not communicated, so that the compression is ensured. When compression is finished, the exhaust channel, the exhaust hole and the exhaust port are just communicated with each other, so that the exhaust is ensured. Through the cooperation of locating pin and locating hole, guaranteed that the relative position of cylinder body and cylinder front end housing in actual assembly is unanimous with the design value.
The specific design parameters are as follows:
the distance between the innermost end of the radial key groove and the center of the cylinder front end cover is smaller than the shortest distance between the point on the cylindrical surface of the eccentric part of the eccentric wheel shaft and the center of the rotation center, and the distance between the outermost end of the radial key groove and the center of the cylinder front end cover is equal to the radius of the inner cavity of the cylinder body, that is to say, the length of the radial key groove is required to ensure that the rolling rotor can rotate in the cylinder for a circle. When the normal line of the tangential point of the outer cylindrical surface of the rolling rotor and the cylindrical surface of the inner cavity of the cylinder body is parallel to the radial key groove, if the tangential point is far away from the radial key groove, the cylindrical key moves to the inner edge of the radial key groove body; if the tangent point is near the radial keyway, the cylindrical key moves to the outer edge of the radial keyway body.
The inlet of the exhaust channel is a strip arc-shaped sinking groove positioned on the cylindrical surface of the eccentric part of the eccentric wheel shaft, and the outlet of the exhaust channel is a strip arc-shaped sinking groove positioned on the end surface of the eccentric part of the eccentric wheel shaft, which is close to the front end cover of the cylinder and is concentric with the rotating shaft. The inlet and outlet of the exhaust channel are arranged in a strip shape, so that the compressor can have enough time to exhaust.
Defining a connecting line of the rotating circle center of the eccentric wheel shaft and a point farthest from the rotating circle center of the eccentric wheel shaft on the cylindrical surface of the eccentric part of the eccentric wheel shaft as a datum line; the included angle between the connecting line formed by the dead point of the outlet arc sinking groove of the exhaust channel along the rotation direction and the rotation center of the eccentric wheel shaft and the datum line is 40-90 degrees, and the included angle between the connecting line formed by the dead point of the outlet arc sinking groove of the exhaust channel along the rotation opposite direction and the rotation center of the eccentric wheel shaft and the datum line is 20 degrees; the included angle between the connecting line formed by the dead point of the arc sinking groove at the inlet of the exhaust channel along the rotation direction and the rotation center of the eccentric wheel shaft and the datum line is 35-85 degrees.
The distance from the center line of the arc sinking groove of the inlet of the exhaust channel to the rear end cover of the cylinder is equal to the distance from the center of the exhaust hole on the rolling rotor to the rear end cover of the cylinder, so that the eccentric wheel shaft can be communicated with the inlet of the exhaust channel in the rotating process.
The included angle between the connecting line of the center of the exhaust port and the center of the front end cover of the cylinder and the straight line where the radial key groove body is located is 135 degrees.
The minimum distance from the point on the exhaust port circle to the center of the front end cover of the cylinder is equal to the radius of the inner circular arc of the arc sinking groove of the exhaust channel outlet, so that the communication between the exhaust channel outlet and the exhaust port can be realized in the rotation process of the eccentric wheel shaft.
The maximum distance from a point on the exhaust port circle to the center of the front end cover of the cylinder is smaller than the shortest distance from a point on the eccentric part cylindrical surface of the eccentric wheel shaft to the rotating center of the circle plus the thickness of the rolling rotor, so that the inner cavity of the cylinder body is not communicated with the exhaust port under the condition of not passing through the exhaust channel.
The included angle between the connecting line formed by the circle center of the cylindrical key and the circle center of the rolling rotor and the connecting line formed by the circle center of the exhaust hole and the circle center of the rolling rotor is 165 degrees.
The diameter of the cylindrical key is consistent with the width of the radial key slot to ensure that movement of the cylindrical key within the radial key slot is strictly limited to one line.
Through the design scheme, the exhaust channel on the eccentric wheel shaft, the exhaust hole on the rolling rotor and the exhaust hole on the front end cover of the cylinder are not communicated when compression is needed, and are communicated when exhaust is needed.
Compared with the prior art, the structure of the exhaust system of the existing rolling rotor compressor is changed, the exhaust port of the prior art is designed on the side edge of the cylinder body and needs an exhaust valve for exhausting, and the exhaust port of the invention is arranged on the front end cover of the cylinder and realizes the exhaust by alternately connecting and disconnecting the exhaust channel, the exhaust hole and the exhaust port in one rotation period of the eccentric wheel shaft.
The invention has the beneficial effects that by adopting the technical scheme, the rolling rotor type compressor controls exhaust through the change of the mutual positions of the rolling rotor, the eccentric wheel shaft and the front end cover of the cylinder, thereby omitting a reed exhaust valve, reducing wearing parts and reducing noise.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic diagram of the relative sliding of the rolling rotor and the eccentric shaft.
FIG. 3 is a side view of the inside of the cylinder head cover.
Fig. 4 is a schematic view of an eccentric axle.
Fig. 5 is an end view of the eccentric shaft.
Fig. 6 is an elevation view of the eccentric axle.
Fig. 7 is an elevation view of the rolling rotor.
Fig. 8 is an end view of the rolling rotor.
Fig. 9 is a schematic diagram of the suction and compression process.
Fig. 10 is a schematic diagram of the suction and discharge process.
Fig. 11 is an exhaust end schematic.
In the figure: 1. the engine comprises a front end cover of a cylinder, an exhaust port, an air suction cavity, an air suction port, a sliding sheet, a spring, a compression cavity, an exhaust hole, an air cylinder rear end cover, an air cylinder body, an exhaust channel, a positioning pin, a cylindrical key, a rolling rotor, an eccentric axle, a radial key groove and a positioning hole.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
Referring to the structural schematic diagram of the invention shown in fig. 1, the rolling rotor compressor mainly comprises a cylinder block 10, a rolling rotor 14, an eccentric shaft 15, an air suction port 4, a spring 6, a sliding vane 5, a cylinder front end cover 1, a cylinder rear end cover 9, an air discharge hole 8 on the cylindrical surface of the rolling rotor 14, a cylindrical key 13 embedded on the end surface of the rolling rotor 14, an air discharge channel 11 communicating the cylindrical surface of the eccentric part of the eccentric shaft 15 and the end surface near the cylinder front end cover 1, an air discharge port 2 on the cylinder front end cover 1, a radial key slot 16 and a positioning hole 17 (see fig. 3) on the inner side surface of the cylinder front end cover 1, and a positioning pin 12 on the side near the cylinder front end cover 1 of the cylinder block 10.
In operation, the motor drives the eccentric shaft 15 to rotate, and the movement of the cylindrical key 13 embedded on the rolling rotor 14 is limited to one line, so that the rolling rotor 14 has relative rotation relative to the eccentric shaft 15 around the eccentric part axis of the eccentric shaft 15, and the cylinder front cover 1 is stationary, which finally causes the relative positions of the exhaust passage 11 on the eccentric shaft 15, the exhaust hole 8 on the rolling rotor 14 and the exhaust port 2 on the cylinder front cover 1 to change regularly during one rotation period of the eccentric shaft 15.
Referring to fig. 2, B represents a point on the end face of the rolling rotor 14, and a represents a point on the end face of the eccentric portion of the eccentric shaft 15, which are in contact with each other. Point B is constrained to move in the direction of the straight slot; the point a rotates with the eccentric shaft 15, and its position is not always maintained in the direction of the straight groove, that is, the point A, B separates with the rotation of the eccentric shaft 15, which represents that the rolling rotor 14 and the eccentric shaft 15 slip, that is, the rolling rotor 14 rotates relatively to the eccentric shaft 15 around the eccentric portion axis of the eccentric shaft 15.
Please refer to the schematic diagram of the inner side surface of the front end cover of the cylinder shown in fig. 3. The inner side surface of the front end cover 1 of the cylinder is provided with a radial key groove 16, the radial key groove 16 is used for limiting the movement of the rolling rotor 14 on one line, when the rolling rotor 14 is forced to rotate on the eccentric shaft 15, relative rotation around the axis of the eccentric part of the eccentric shaft 15 relative to the eccentric shaft 15 is generated, and the periodic connection and disconnection of the exhaust hole 8 on the rolling rotor 14 and the exhaust channel 11 on the eccentric shaft 15 are realized.
Distance R of innermost end of radial key groove 16 from circle center of cylinder front end cover 1 2 Less than the shortest distance L from the point on the cylindrical surface of the eccentric part of the eccentric axle 15 to the center of rotation 1 (see FIG. 5), i.e. R 2 ＜L 1 Distance R from the outermost end of radial key groove 16 to the center of cylinder front end cover 1 3 Equal to the radius of the internal cavity of the cylinder block 10 (see fig. 1), that is, the length of the radial key groove 16 is such that the rolling rotor 14 can rotate one revolution in the cylinder. When the normal line of the tangential point of the outer cylindrical surface of the rolling rotor 14 and the cylindrical surface of the inner cavity of the cylinder body 10 is parallel to the radial key groove 16, if the tangential point is far away from the radial key groove 16, the cylindrical key 13 moves to the inner edge of the groove body of the radial key groove 16; if the tangent point is close to the radial key groove 16, the cylindrical key 13 moves to the outer edge of the body of the radial key groove 16.
The included angle θ=135° between the connecting line m of the center of the exhaust port 2 and the center of the cylinder front end cover 1 and the straight line n of the radial key groove 16 body.
Minimum distance R from point on exhaust port 2 to center of cylinder front end cover 1 1 And radius R of inner circular arc of arc sinking groove at outlet of exhaust channel 11 5 (see FIG. 5) are equal, i.e. R 1 ＝R 5 So as to ensure that the communication between the outlet of the exhaust passage 11 and the exhaust port 2 can be realized during the rotation of the eccentric axle 15.
The maximum distance from the point on the exhaust port 2 circle to the center of the front end cover 1 of the cylinder is R 4 To satisfy R 4 ＜L 1 +δ (see fig. 5, 7), i.e. to ensure that the internal cavity of the cylinder block 10 (see fig. 1) does not communicate with the exhaust port 2 without passing through the exhaust passage 11.
Please refer to the eccentric axle diagram shown in fig. 4. The eccentric wheel shaft 15 is provided with an exhaust channel 11, the exhaust channel 11 is communicated with the cylindrical surface of the eccentric part of the eccentric wheel shaft 15 and the end surface of the front end cover 1 of the cylinder, and the inlet of the exhaust channel 11 is a strip arc sinking groove positioned on the cylindrical surface of the eccentric part of the eccentric wheel shaft 15. The outlet of the exhaust channel 11 is a strip arc sinking groove concentric with the rotating shaft and positioned on the end surface of the eccentric part of the eccentric wheel shaft 15, which is close to the front end cover 1 of the cylinder. The inlet and outlet of the exhaust passage 11 are provided in a strip shape so that the compressor can have enough time to exhaust.
Please refer to the end view of the eccentric axle shown in fig. 5. Defining a connecting line between the rotating center of the eccentric shaft 15 and a point farthest from the rotating center of the eccentric shaft 15 on the cylindrical surface of the eccentric part of the eccentric shaft as a datum line q; an included angle gamma=40° between a connecting line h formed by a dead point of the outlet arc-shaped sinking groove of the exhaust channel 11 along the rotation direction and the rotation center of the eccentric wheel shaft 15 and a datum line q, and an included angle alpha=20° between a connecting line g formed by a dead point of the outlet arc-shaped sinking groove of the exhaust channel 11 along the rotation opposite direction and the rotation center of the eccentric wheel shaft 15 and the datum line q; the included angle beta=35° between the connecting line k formed by the dead point of the arc sinking groove at the inlet of the exhaust channel 11 along the rotation direction and the rotation center of the eccentric wheel shaft 15 and the datum line q.
Please refer to the elevation of the eccentric axle shown in fig. 6 and the elevation of the rolling rotor shown in fig. 7. Distance L from center of exhaust hole 8 to rear end cover of cylinder 2 And the distance L from the center line of the arc-shaped sinking groove at the inlet of the exhaust channel 11 to the rear end cover 9 (see figure 1) of the cylinder 3 Equal, i.e. L 2 ＝L 3 So as to ensure that the eccentric axle 15 can realize the communication between the inlet of the exhaust channel 11 and the exhaust hole 8 in the rotating process.
Please refer to the rolling rotor end view shown in fig. 8. The included angle psi=165° between the connecting line e formed by the circle center of the cylindrical key 13 and the circle center of the rolling rotor 14 and the connecting line f formed by the circle center of the exhaust hole 8 and the circle center of the rolling rotor 14.
Fig. 9 is a schematic diagram of the suction and compression process. When the rolling rotor 14 passes over the suction port 4, a working cycle starts, and the compressor starts to compress and suction a new round. In the process, the exhaust hole 8 on the rolling rotor 14, the exhaust channel 11 on the eccentric shaft 15 and the exhaust hole 2 on the front end cover 1 of the cylinder are not communicated, the air suction cavity 3 sucks air by increasing the volume continuously, and the compression cavity 7 compresses by decreasing the volume continuously.
Fig. 10 is a schematic diagram of the suction and discharge process. When compression is completed, the exhaust hole 8 on the rolling rotor 14, the exhaust channel 11 on the eccentric axle 15 and the exhaust hole 2 on the front end cover 1 of the cylinder are communicated, and the exhaust is started. In this process, the suction chamber 3 is further enlarged to suck air.
Fig. 11 is an exhaust end schematic. After the compressor rotates until the discharge hole 8, the discharge passage 11 and the discharge hole 2 are no longer in communication with each other, the discharge ends. When the rolling rotor 14 passes further over the suction port 4, the suction ends and the compressor enters the next working cycle.
While the invention has been described and illustrated in the drawings as embodied in a specific structure, other variations are possible in light of the spirit of the invention, and while the invention described above sets forth a presently preferred embodiment, these are not intended to be limiting.
Various alterations and modifications will no doubt become apparent to those skilled in the art after having read the above description. Therefore, the appended claims should be construed to cover all such variations and modifications as fall within the true spirit and scope of the invention. Any and all equivalents and alternatives falling within the scope of the claims are intended to be embraced therein.
Claims (8)
1. The utility model provides a rolling rotor formula compressor, includes cylinder block, rolling rotor, eccentric shaft, induction port, spring, gleitbretter, cylinder front end housing, cylinder rear end housing, its characterized in that: the cylinder front end cover is provided with an exhaust port, the inner side surface of the cylinder front end cover is provided with a radial key slot, and the cylindrical key is inserted into the radial key slot; the included angle between the connecting line of the center of the exhaust port and the center of the front end cover of the cylinder and the straight line of the radial key groove body is 135 degrees, the minimum distance from the point on the exhaust port to the center of the front end cover of the cylinder is equal to the radius of the inner circular arc of the arc sinking groove of the outlet of the exhaust channel, and the maximum distance from the point on the exhaust port to the center of the front end cover of the cylinder is smaller than the sum of the shortest distance from the point on the eccentric part cylindrical surface of the eccentric wheel shaft to the rotating center of the cylinder and the thickness of the rolling rotor; the included angle between the connecting line formed by the circle center of the cylindrical key and the circle center of the rolling rotor and the connecting line formed by the circle center of the exhaust hole on the cylindrical surface of the rolling rotor and the circle center of the rolling rotor is 165 degrees; defining a connecting line of the rotating circle center of the eccentric wheel shaft and a point farthest from the rotating circle center of the eccentric wheel shaft on the cylindrical surface of the eccentric part of the eccentric wheel shaft as a datum line; the included angle between the connecting line formed by the dead point of the outlet arc sinking groove of the exhaust channel along the rotation direction and the rotation center of the eccentric wheel shaft and the datum line is 40-90 degrees, and the included angle between the connecting line formed by the dead point of the outlet arc sinking groove of the exhaust channel along the rotation opposite direction and the rotation center of the eccentric wheel shaft and the datum line is 20 degrees; the included angle between the connecting line formed by the dead point of the arc sinking groove at the inlet of the exhaust channel along the rotation direction and the rotation center of the eccentric wheel shaft and the datum line is 35-85 degrees.
2. A rolling rotor compressor according to claim 1, characterized in that: the diameter of the cylindrical key is consistent with the width of the radial key groove.
3. A rolling rotor compressor according to claim 2, characterized in that: the distance between the innermost end of the radial key groove and the circle center of the front end cover of the cylinder is smaller than the shortest distance between the point on the eccentric part cylindrical surface of the eccentric wheel shaft and the circle center of the rotation, and the distance between the outermost end of the radial key groove and the circle center of the front end cover of the cylinder is equal to the radius of the inner cavity of the cylinder body.
4. A rolling rotor compressor according to claim 3, characterized in that: when the normal line of the tangential point of the outer cylindrical surface of the rolling rotor and the cylindrical surface of the inner cavity of the cylinder body is parallel to the radial key groove, if the tangential point is far away from the radial key groove, the cylindrical key moves to the inner edge of the radial key groove body; if the tangent point is near the radial keyway, the cylindrical key moves to the outer edge of the radial keyway body.
5. A rolling rotor compressor according to claim 1, characterized in that: the outlet of the exhaust channel is a strip arc sinking groove concentric with the rotating shaft and positioned on the end face of the eccentric part of the eccentric wheel shaft, which is close to the front end cover of the cylinder, and the inlet of the exhaust channel is a strip arc sinking groove positioned on the cylindrical surface of the eccentric part of the eccentric wheel shaft.
6. A rolling rotor compressor according to claim 1, characterized in that: the distance from the center line of the arc sinking groove at the inlet of the exhaust channel to the rear end cover of the cylinder is equal to the distance from the center of the exhaust hole on the rolling rotor to the rear end cover of the cylinder.
7. A rolling rotor compressor according to any one of claims 1 to 6, characterized in that: the cylinder body is embedded with a locating pin at the side close to the front end cover of the cylinder, and a locating hole is arranged on the inner side surface of the front end cover of the cylinder.
8. A method of controlling compression discharge of a rolling rotor compressor, for use in a rolling rotor compressor as claimed in claim 1, wherein: the control method at least comprises the following two steps:
step one: and (3) suction compression: when a working cycle starts, the compressor starts to compress and suck, the exhaust hole on the rolling rotor, the exhaust channel on the eccentric wheel shaft and the exhaust hole on the front end cover of the cylinder are not communicated, the suction cavity sucks air by increasing the volume continuously, and the compression cavity compresses by decreasing the volume continuously;
step two: inspiration and exhaustion: when compression is finished, the exhaust hole on the rolling rotor, the exhaust channel on the eccentric wheel shaft and the exhaust hole on the front end cover of the cylinder are communicated, and exhaust is started; the suction cavity is further enlarged for suction in the process; after the compressor rotates until the exhaust hole, the exhaust channel and the exhaust port are not communicated with each other, the exhaust is finished; when the rolling rotor further passes over the air suction port, the air suction is finished, the compressor enters the next working period, and the step one is repeated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969320.1A CN109611337B (en) | 2017-10-05 | 2017-10-05 | Rolling rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969320.1A CN109611337B (en) | 2017-10-05 | 2017-10-05 | Rolling rotor type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109611337A CN109611337A (en) | 2019-04-12 |
| CN109611337B true CN109611337B (en) | 2023-09-26 |
Family
ID=66001418
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710969320.1A Active CN109611337B (en) | 2017-10-05 | 2017-10-05 | Rolling rotor type compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109611337B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115126696B (en) * | 2022-06-02 | 2023-06-23 | 广州市德善数控科技有限公司 | Compressor pump body, compressor and temperature regulating system |
| WO2023098102A1 (en) * | 2021-11-30 | 2023-06-08 | 广州市德善数控科技有限公司 | Compressor rotor, compressor pump body, compressor, and temperature-regulating system |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57146088A (en) * | 1981-03-04 | 1982-09-09 | Mitsubishi Heavy Ind Ltd | Rotary compressor |
| CN2074383U (en) * | 1990-07-07 | 1991-04-03 | 西安交通大学 | Rotary-piston compressor |
| JPH08193584A (en) * | 1995-01-13 | 1996-07-30 | Toshiba Corp | Rotary type compressor |
| JPH1122673A (en) * | 1997-07-04 | 1999-01-26 | Matsushita Electric Ind Co Ltd | Rotary fluid machinery |
| KR20010011427A (en) * | 1999-07-28 | 2001-02-15 | 윤종용 | A compressed gas discharging structure of cylinder for compressor |
| KR20010056633A (en) * | 1999-12-16 | 2001-07-04 | 윤종용 | A discharge valve apparatus of compressor |
| KR20040007004A (en) * | 2002-07-16 | 2004-01-24 | 삼성전자주식회사 | Rotary compprersor |
| CN103821715A (en) * | 2014-01-15 | 2014-05-28 | 卞雨花 | Translational rotation type compression machinery |
| JP2014152621A (en) * | 2013-02-05 | 2014-08-25 | Mitsubishi Electric Corp | Vane type compressor |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN204436804U (en) * | 2015-01-08 | 2015-07-01 | 广东美芝制冷设备有限公司 | Compressing mechanism and the compressor with it |
| CN106968947A (en) * | 2016-11-10 | 2017-07-21 | 桂林航天工业学院 | Swinging rotor type compressor |
| CN106989019A (en) * | 2017-05-03 | 2017-07-28 | 江苏昊科汽车空调有限公司 | A kind of turbine disk of vehicle-mounted automobile air conditioner compressor |
| CN107120280A (en) * | 2017-07-12 | 2017-09-01 | 张均 | Compression set and compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN207920873U (en) * | 2017-10-05 | 2018-09-28 | 桂林航天工业学院 | A kind of rolling rotor compressor |
-
2017
- 2017-10-05 CN CN201710969320.1A patent/CN109611337B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57146088A (en) * | 1981-03-04 | 1982-09-09 | Mitsubishi Heavy Ind Ltd | Rotary compressor |
| CN2074383U (en) * | 1990-07-07 | 1991-04-03 | 西安交通大学 | Rotary-piston compressor |
| JPH08193584A (en) * | 1995-01-13 | 1996-07-30 | Toshiba Corp | Rotary type compressor |
| JPH1122673A (en) * | 1997-07-04 | 1999-01-26 | Matsushita Electric Ind Co Ltd | Rotary fluid machinery |
| KR20010011427A (en) * | 1999-07-28 | 2001-02-15 | 윤종용 | A compressed gas discharging structure of cylinder for compressor |
| KR20010056633A (en) * | 1999-12-16 | 2001-07-04 | 윤종용 | A discharge valve apparatus of compressor |
| KR20040007004A (en) * | 2002-07-16 | 2004-01-24 | 삼성전자주식회사 | Rotary compprersor |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| JP2014152621A (en) * | 2013-02-05 | 2014-08-25 | Mitsubishi Electric Corp | Vane type compressor |
| CN103821715A (en) * | 2014-01-15 | 2014-05-28 | 卞雨花 | Translational rotation type compression machinery |
| CN204436804U (en) * | 2015-01-08 | 2015-07-01 | 广东美芝制冷设备有限公司 | Compressing mechanism and the compressor with it |
| CN106968947A (en) * | 2016-11-10 | 2017-07-21 | 桂林航天工业学院 | Swinging rotor type compressor |
| CN106989019A (en) * | 2017-05-03 | 2017-07-28 | 江苏昊科汽车空调有限公司 | A kind of turbine disk of vehicle-mounted automobile air conditioner compressor |
| CN107120280A (en) * | 2017-07-12 | 2017-09-01 | 张均 | Compression set and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109611337A (en) | 2019-04-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101988504B (en) | Rotary compressor | |
| CN109611337B (en) | Rolling rotor type compressor | |
| CN105201835A (en) | Swing rotor compressor | |
| CN101454573B (en) | Vane machine | |
| CN109611336B (en) | Rolling rotor type compressor | |
| CN103821715B (en) | Translation revolving compressor mechanical | |
| CN113339259A (en) | Rotor air compressor | |
| CN105649983A (en) | Air compressor pump | |
| CN207920873U (en) | A kind of rolling rotor compressor | |
| CN204755313U (en) | Scroll compressor of two whirlpools dish | |
| CN109611332B (en) | Double-exhaust-pressure rolling rotor type compressor | |
| CN109209879B (en) | Closed rotor compressor | |
| CN109611334B (en) | Double-row-pressure rolling rotor compressor | |
| CN207920858U (en) | A kind of double atmospheric pressure compressor with rolling rotor | |
| CN207920874U (en) | A kind of rolling rotor compressor | |
| WO2019052080A1 (en) | Pump assembly, fluid machinery and heat exchange apparatus | |
| CN210196011U (en) | Pump body subassembly, compressor and refrigeration plant | |
| CN202545249U (en) | Vaned translational rotor compressor | |
| CN111706508A (en) | Gap-adjustable swing compressor piston | |
| CN220227177U (en) | Novel positive displacement fan | |
| CN204126893U (en) | Air condition compressor | |
| CN102953993B (en) | The slide plate of rotary compressor, rotary compressor and air conditioner | |
| CN102588282B (en) | Vane type translational rotor compressor | |
| CN2525282Y (en) | Jacket cylinder type rolling rotor compressor | |
| CN212536069U (en) | Gap-adjustable swing compressor piston |
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 |