EP3392507B1 - Cylindre à capacité variable à structure de commande de palette coulissante et compresseur à capacité variable - Google Patents

Cylindre à capacité variable à structure de commande de palette coulissante et compresseur à capacité variable Download PDF

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Publication number
EP3392507B1
EP3392507B1 EP16874597.4A EP16874597A EP3392507B1 EP 3392507 B1 EP3392507 B1 EP 3392507B1 EP 16874597 A EP16874597 A EP 16874597A EP 3392507 B1 EP3392507 B1 EP 3392507B1
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EP
European Patent Office
Prior art keywords
pin
variable
seal
sliding vane
cylinder
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
Application number
EP16874597.4A
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German (de)
English (en)
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EP3392507A4 (fr
EP3392507A1 (fr
Inventor
Hui Huang
Yusheng Hu
Huijun WEI
Bing Yu
Ouxiang YANG
Jun Wang
Pengke MIAO
Minghua Wang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Zhuhai Landa Compressor Co Ltd
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Zhuhai Landa Compressor Co Ltd
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Publication of EP3392507A1 publication Critical patent/EP3392507A1/fr
Publication of EP3392507A4 publication Critical patent/EP3392507A4/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C18/3564—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 the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated

Definitions

  • the present invention relates to a technical field of compressors, and more particularly to a variable-capacity cylinder with a sliding vane control structure, and a variable-capacity compressor.
  • variable-capacity compressors A common structure of existing variable-capacity compressors is that a compressor body comprises a main cylinder and a variable-capacity cylinder, and the variable-capacity cylinder may be selectively operated or not operated, so as to achieve a change in a working displacement to meet different load requirements of a refrigeration system, thereby achieving a purpose of energy saving.
  • a sliding vane, a cylinder, and a bearing and a division plate covering two ends of the cylinder form a sealed cavity at a tail of the sliding vane, and the sealed cavity may be selectively introduced with high-pressure/low-pressure gas; and a pin locking/unlocking device is provided on a side of the sliding vane, the device is consisted of a pin hole, a pin, a spring, etc., wherein a head of the pin communicates with the above-mentioned sealed cavity, a low pressure is introduced into a tail of the pin via a low-pressure passage, and the pin has a pre-approaching force approaching the sliding vane by means of a physical device (such as spring and magnet).
  • a physical device such as spring and magnet
  • the defects of the above-mentioned mode are as follows.
  • high-pressure refrigerant gas needs to be introduced into the sealed cavity, the high-pressure refrigerant gas leading to discharge of refrigeration oil in the sealed cavity; in order to ensure that the pin is slidablely up and down in the pin hole, there is a certain clearance between the pin and the pin hole, so that a lubrication oil clearance seal cannot be realized; in addition, a viscosity of the refrigerant is much smaller than that of lubricating oil, and the clearance leakage speed is high.
  • a solution in the prior art will have the following harmful effects: the leakage of the refrigerant from the sealed cavity to a gas inlet of the variable-capacity cylinder through a pin side clearance will be significantly increased, thereby resulting in a decrease in volumetric efficiency of the variable-capacity cylinder and a decrease in performance; in addition, the clearance size of different compressors cannot be completely consistent during mass production, which will lead to significant fluctuations in compressor refrigeration/heating capacity and is not conducive to controlling a quality stability of a compressor and an air-conditioning product.
  • CN 103953544 A discloses a compressor and air conditioner.
  • the compressor includes a low-pressure stage cylinder, a first high-pressure stage cylinder and a second high-pressure stage cylinder which are stacked, a partition is arranged between each two adjacent cylinders, the first and second high-pressure stage cylinders are both situated at a same side of the low-pressure stage cylinder or respectively situated at two sides of the low-pressure stage cylinder, the lower flange is situated below the low-pressure stage cylinder, the first high-pressure stage cylinder and the second high-pressure stage cylinder.
  • a first sliding sheet is provided in the first high-pressure stage cylinder, a second sliding sheet is provided in the second high-pressure stage cylinder, and a third sliding sheet is provided in the low-pressure stage cylinder.
  • the first and the second high-pressure stage cylinders are arranged in parallel, and the first and second high-pressure stage cylinders arranged in parallel are connected to the low-pressure stage cylinder in series.
  • the present invention provides a sliding vane control structure for a variable-capacity cylinder, capable of ensuring a seal effect, a variable-capacity cylinder with the sliding vane control structure, and a variable-capacity compressor.
  • variable-capacity cylinder comprises a sliding vane and a sliding vane control structure.
  • the sliding vane control structure comprises:
  • variable-capacity cylinder comprises a sliding vane and a sliding vane control structure.
  • the sliding vane control structure comprises:
  • a groove is provided at a lower part of the pin, and a first through hole is provided at a position, corresponding to the groove, on the seal division plate.
  • a maximum size of the first through hole in a horizontal plane is smaller than a maximum outer diameter of the pin.
  • a maximum size of the first through hole in a horizontal plane is smaller than the maximum size of the groove in a horizontal plane.
  • a second through hole is provided on the seal division plate, the second through hole enabling the low-pressure passage to communicate with a gas inlet of a variable-capacity cylinder.
  • variable-capacity compressor is provided.
  • the variable-capacity compressor is provided with a variable-capacity cylinder in the present application.
  • the surface seal structure is provided between the pin and the low-pressure passage, a seal effect of the surface seal is much better than that of a clearance seal, thereby greatly reducing a leakage of a refrigerant. Consequently, an efficiency of the compressor is increased when the variable-capacity cylinder is in a working mode, and a performance of the compressor is optimized. Moreover, due to the provision of the surface seal structure in the present application, the seal effect is good. Thus, a processing precision requirement of the pin hole may be reduced, and a processing cost and assembly cost of the pin hole are reduced, thereby stabilizing a production quality of the compressor.
  • a pump assembly of a variable-capacity compressor comprises a crankshaft 1, and an upper bearing 4 connected to the crankshaft 1, a lower bearing 5, a cover plate 7, and a first cylinder 2 and a second cylinder 3 sandwiched between the upper bearing 4 and the lower bearing 5.
  • the first cylinder 2 and the second cylinder 3 are separated by a division plate 6, wherein the second cylinder 3 is a variable-capacity cylinder.
  • the upper bearing 4, the first cylinder 2, the division plate 6, the second cylinder 3, the lower bearing 5 and the cover plate 7 are sequentially mounted in an axial direction of a compressor crankshaft 1.
  • a first sliding vane groove is provided in the first cylinder 2, a first sliding vane 10 is provided in the first sliding vane groove, and the first sliding vane 10 is pressed toward a first rolling piston 8 under an action of a spring force of a spring provided on a back of the first sliding vane 10, and the first sliding vane 10 is in contact with an outer surface of the first rolling piston 8, thereby separating an interior of the first cylinder 2 into an intake chamber and a compression chamber.
  • a second sliding vane groove is provided in the second cylinder 3
  • a second sliding vane is provided in the second sliding vane groove
  • a sealed cavity 18 is formed on a back of a second sliding vane 11 (one side on a right of the second sliding vane 11 in Fig.
  • a pressure switching pipe 12 is provided on the sealed cavity 18, the pressure switching pipe 12 may be connected with an external gas source (not shown in the figure), and preferably, the external gas source may be high-pressure/low-pressure gas from a gas outlet/suction port of the compressor.
  • the pressure switching pipe 12 may be connected with the external gas source via a control valve.
  • a control valve For example, preferably, a magnetic valve, a three-way valve or the like may be used as the control valve to control switching of the high/low-pressure gas introduced into the pressure switching pipe 12, so as to allow high-pressure or low-pressure gas to be introduced into the pressure switching pipe 12.
  • the second sliding vane 11 When the high-pressure gas is introduced into the pressure switching pipe 12, the second sliding vane 11 can be pressed against a second rolling piston 9 under a pressure action of the introduced gas, and the second sliding vane 11 is in contact with an outer surface of the second rolling piston 9, so as to separate an interior of the second cylinder 3 into an intake chamber and a compression chamber, wherein the first rolling piston 8 and the second rolling piston 9 are fixedly mounted on an eccentric portion of the compressor crankshaft 1 and are eccentrically rotated in the cylinder by the compressor crankshaft 1, so as to compress refrigerant gas entering a cylinder cavity.
  • a pin hole 17 is provided in the lower bearing 5.
  • an axis of the pin hole 17 is parallel to an axis of the compressor crankshaft 1.
  • An upper end of the pin hole 17 communicates with the sealed cavity 18.
  • a low-pressure passage 15 (see Fig. 3 ) communicating with an air intake 16 is provided below the pin hole 17.
  • a part of the low-pressure passage 15 is preferably provided on the cover plate 7.
  • a pin 13 is provided in the pin hole 17, the pin 13 is movable up and down in the pin hole 17.
  • a biasing member 14 is provided on a lower side of the pin 13, wherein the biasing member may be a physical device such as a spring. The biasing member 14 provides an upward biasing force for the pin 13.
  • a groove 131 is provided on the lower side of the pin 13, and the biasing member 14 is provided between a top wall of the groove and the cover plate 7 below the pin 13.
  • a pin groove 111 (see Fig. 1 ) capable of matching with an upper end of the pin 13 is provided on a lower surface of the second sliding vane 11.
  • the pin 13 overcomes a pre-force of the biasing member 14 and a gas pressure of the low-pressure passage under the action of the high-pressure gas, so that the pin 13 moves downward and leaves the pin groove 111 on the second sliding vane 11, so that the pin 13 is at an unlocked position (the pin 13 is at a second position at this time) that makes the second sliding vane 11 unconstrained, the second sliding vane 11 is pressed against the second rolling piston 9 under the action of the high-pressure gas on the back thereof, and a head of the second sliding vane 11 is in contact with the outer surface of the second rolling piston 9, so that a normal compression process of the second cylinder 3 (variable-capacity cylinder) is implemented.
  • the high-pressure refrigerant gas enters the air intake 16 of the second cylinder 3 via the clearance between the outer wall of the pin 13 and the inner wall of the pin hole 17 and the low-pressure passage 15 below the pin 13, the expansion of the high-pressure refrigerant gas causes actual reduction of the amount of gas circulation in the second cylinder 3 and repeated compression of the leaked gas, which not only reduces a cooling capacity, but also consumes additional power, thereby reducing the performance of the existing variable-capacity compressor during dual-cylinder operation.
  • the present invention is an improvement on the basis of the variable-capacity compressor described in the related art, in which the variable-capacity compressor sliding vane control structure according to the present invention is provided, that is to say, the sliding vane control structure in the present invention is applied to the variable-capacity compressor having the above-mentioned construction and components.
  • the sliding vane control structure for the variable-capacity compressor in the present invention will be described in detail below in order to avoid excessive repetition. The same parts as those described above will not be repeated.
  • a second cylinder 103 of the variable-capacity compressor is provided above a lower bearing 105, and a cover plate 107 is provided below the lower bearing 105.
  • a pin hole 117 formed in a stepped shape is provided in the lower bearing 105.
  • An inner diameter of a portion, close to a lower end, of the pin hole 117 is smaller than an inner diameter of a portion of an upper side, and thus a step surface extending inward in a radial direction is formed at a portion, close to the lower end, of the pin hole 117.
  • the step surface is provided with a seal gasket 109.
  • the seal gasket 109 is preferably but not limited to a metal seal gasket or a rubber seal gasket.
  • the seal gasket 109 is an annular seal gasket and is provided with a through hole in a center.
  • a pin 113 provided with a groove 1131 on a lower side is provided in the pin hole 17, and a lower end surface of the pin 113 abuts against an upper surface of the seal gasket 109 on the step surface.
  • the groove 1131 of the pin 113 is provided with a biasing member 114 passing through a through hole on the seal gasket 109 and contacting the cover plate 107.
  • the biasing member 114 is preferably a spring for providing an upward biasing force for the pin 113.
  • the lower end of the pin 113 communicates with a low-pressure passage 115 on the cover plate 107, and further communicates with an air intake 116 of the second air cylinder 103.
  • the seal gasket 109 is made of metal or rubber.
  • a high-pressure refrigerant gas is introduced into a sealed cavity (not shown in the drawings) above the pin 113.
  • the pin 113 overcomes the pre-force of the biasing member 114 and the gas pressure in the low-pressure passage, and the pin 113 moves downward in the pin hole 117 to the second position, so that the pin 113 is separated from the sliding vane of the second cylinder 103, while the lower end of the pin 113 is tightly pressed against an upper surface of the seal gasket 109, and a surface seal is formed at the lower end of the pin 113.
  • the second cylinder 103 performs normal compression operation.
  • the high-pressure refrigerant gas will flow downward along a clearance between the pin 113 and the pin hole 117, but because the lower end of the pin 113 is tightly pressed against the seal gasket 109, a surface seal structure is formed between the pin 113 and a step surface of the pin hole 17, so that a surface seal is formed between the clearance between the pin 113 and the pin hole 117 and the low-pressure passage 115 on the lower side of the pin 113.
  • the seal performance of the surface seal structure is much better than that of a clearance seal between the pin 113 and the pin hole 117, so that the leakage amount of a refrigerant is greatly reduced, thereby effectively improving the performance of the compressor.
  • a second cylinder 203 of the variable-capacity compressor is provided above a lower bearing 205, and a seal division plate 218 and a cover plate 207 are sequentially provided below the lower bearing 205, wherein a pin hole 217 is provided in the lower bearing 205, and a pin 213 having a groove 2131 is provided in the pin hole 217.
  • a biasing member 214 such as a spring, capable of generating a pre-force is provided between a top wall of the groove 2131 of the pin 213 and the seal division plate 218 below the pin 213.
  • a first through hole 219 is provided at a position, corresponding to the groove 2131 in the pin hole 17, on the seal division plate 218.
  • a maximum size of the through hole 219 in a horizontal plane is smaller than an outer diameter of the pin 213, so that a lower end of the pin 213 abuts against on an upper surface of the seal division plate 218. More preferably, the maximum size of the through hole 219 in the horizontal plane is smaller than a maximum size of the groove 2131 in the horizontal plane, so that a bottom of the biasing member 214 abuts against the upper surface of the seal division plate 218.
  • the through hole 219 is a circular hole, its maximum size is its diameter.
  • a low-pressure passage 215 communicating with an air intake 216 is provided on the cover plate 207.
  • a second through hole 220 is provided on the seal division plate 218.
  • the low-pressure passage 215, the first through hole 219 and the second through hole 220 are not provided in a unique manner and may have various structural forms as long as the lower side of the pin 213 can communicate with the air intake 216 of the second cylinder 203.
  • the seal division plate 218 is machined or stamped modeling.
  • a high-pressure refrigerant gas is introduced into a sealed cavity (not shown) above the pin 213.
  • the pin 213 overcomes the pre-force of the biasing member and the gas pressure in the low-pressure passage, so that the pin 213 moves downward in the pin hole 17 to the second position, thereby making the pin 213 separated from a sliding vane of the second cylinder 203, and the second cylinder 203 performs normal compression operation at this time.
  • the high-pressure refrigerant gas will flow down along the clearance between the pin 213 and the pin hole 217, but due to a surface contact between a bottom end surface of the pin 213 and the seal division plate 218, a surface seal is formed at the lower end of the pin 213.
  • the lower end of the pin 213 is tightly pressed against the upper end surface of the seal division plate 218, so that a surface seal is formed between the lower end of the pin 213 and the upper end surface of the seal division plate 218.
  • the seal performance of the seal structure is much better than that of the clearance seal between the pin 213 and the pin hole 217, so that the leakage amount of a refrigerant is greatly reduced, thereby improving the performance of the compressor.
  • the seal effect of the surface seal is much better than that of the clearance seal, thereby greatly reducing the leakage of a refrigerant. Consequently, the efficiency of a compressor is increased when a variable-capacity cylinder is in a working mode, and the performance of the compressor is optimized. Moreover, due to the provision of the surface seal structure in the present application, the seal effect is good. Thus, the processing precision requirement of a pin hole may be reduced, and the processing cost and assembly cost of the pin hole are reduced, thereby stabilizing the production quality of a compressor.

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

Claims (8)

  1. Cylindre à capacité variable, comprenant une palette coulissante (11) et une structure de commande de palette coulissante comprenant :
    une goupille (113), fournie sur un côté inférieur de la palette coulissante (11), la goupille (113) ayant une première position capable d'arrêter la palette coulissante (11) et une seconde position pouvant être séparée de la palette coulissante (11), un passage basse pression (115) est fourni sous la goupille,
    caractérisé en ce qu'une structure de joint de surface est fournie entre la goupille (113) et le passage basse pression (115), et lorsque la goupille (113) est dans la seconde position, un joint de surface est formé à une extrémité inférieure de la goupille (113) ;
    dans lequel
    la goupille (113) est fournie dans un trou de goupille (117), le trou de goupille (117) est un trou étagé, un diamètre intérieur d'une partie, proche de l'extrémité inférieure du trou de goupille (117) est plus petit qu'un diamètre intérieur d'une partie d'un côté supérieur, et ainsi une surface étagée s'étendant vers l'intérieur dans une direction radiale est formée au niveau d'une partie, proche de l'extrémité inférieure, du trou de goupille (117) ;
    un joint d'étanchéité (109) est fourni sur la surface étagée, l'extrémité inférieure de la goupille (113) peut être fermement pressée contre une surface supérieure du joint d'étanchéité (109), et le joint de surface est formé entre l'extrémité inférieure de la goupille (113) et la surface supérieure du joint d'étanchéité (109).
  2. Cylindre à capacité variable selon la revendication 1, dans lequel un trou traversant est formé au milieu du joint d'étanchéité (109).
  3. Cylindre à capacité variable, comprenant une palette coulissante (11) et une structure de commande de palette coulissante comprenant :
    une goupille (213), fournie sur un côté inférieur de la palette coulissante (11), la goupille (213) ayant une première position capable d'arrêter la palette coulissante (11) et une seconde position pouvant être séparée de la palette coulissante (11), un passage basse pression (215) est fourni sous la goupille,
    caractérisé en ce qu'une structure de joint de surface est fournie entre la goupille (213) et le passage basse pression (215), et lorsque la goupille (213) est dans la seconde position, un joint de surface est formé à une extrémité inférieure de la goupille (213) ;
    dans lequel une plaque de division de joint (218) est fournie sur un côté inférieur de la goupille (113), une extrémité inférieure de la goupille (213) bute contre une surface supérieure de la plaque de division de joint (218), et le joint de surface est formé entre l'extrémité inférieure de la goupille (213) et la surface supérieure de la plaque de division de joint (218) .
  4. Cylindre à capacité variable selon la revendication 3, dans lequel une rainure (2131) est fournie au niveau d'une partie inférieure de la goupille (213), et un premier trou traversant (219) est fourni au niveau d'une position correspondant à la rainure (2131), sur la plaque de division de joint (218).
  5. Cylindre à capacité variable selon la revendication 4, dans lequel une taille maximale du premier trou traversant (219) dans un plan horizontal est inférieure à un diamètre extérieur maximal de la goupille (213).
  6. Cylindre à capacité variable selon la revendication 4, dans lequel une taille maximale du premier trou traversant (219) dans un plan horizontal est inférieure à une taille maximale de la rainure (2131) dans un plan horizontal.
  7. Cylindre à capacité variable selon la revendication 4, dans lequel un second trou traversant (220) est fourni sur la plaque de division de joint (218), le second trou traversant (220) permettant au passage basse pression (215) de communiquer avec une entrée de gaz (216) d'un cylindre à capacité variable (203) .
  8. Compresseur à capacité variable, muni d'un cylindre à capacité variable selon l'une quelconque des revendications 1 à 7.
EP16874597.4A 2015-12-18 2016-09-14 Cylindre à capacité variable à structure de commande de palette coulissante et compresseur à capacité variable Active EP3392507B1 (fr)

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CN201510965018.XA CN105464978A (zh) 2015-12-18 2015-12-18 变容气缸的滑片控制结构、变容气缸及变容压缩机
PCT/CN2016/099111 WO2017101537A1 (fr) 2015-12-18 2016-09-14 Structure de commande de palette coulissante pour cylindre pneumatique à capacité variable, cylindre pneumatique à capacité variable et compresseur à capacité variable

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Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
CN105464978A (zh) * 2015-12-18 2016-04-06 珠海格力节能环保制冷技术研究中心有限公司 变容气缸的滑片控制结构、变容气缸及变容压缩机
CN107476979A (zh) * 2017-08-10 2017-12-15 珠海格力节能环保制冷技术研究中心有限公司 压缩机、空调器及压缩机的装配方法
CN109058108B (zh) * 2018-09-18 2023-10-03 珠海格力节能环保制冷技术研究中心有限公司 变容气缸组件、压缩机泵体及压缩机
CN109958625B (zh) * 2018-12-20 2020-01-07 珠海格力电器股份有限公司 销钉弹性部变形控制方法及控制系统、变容压缩机
CN111075721B (zh) * 2019-12-26 2021-11-19 珠海格力节能环保制冷技术研究中心有限公司 泵体组件及变容压缩机
CN117846961B (zh) * 2024-03-08 2024-05-17 四川华油中蓝能源有限责任公司 一种用于lng生产中的变容式机械泵

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953544A (zh) * 2014-04-10 2014-07-30 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5612085A (en) * 1979-07-12 1981-02-05 Sanyo Electric Co Ltd Capacity controller for multicylinder rotary compressor
DE2946906C2 (de) * 1979-11-21 1985-02-14 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter
JPS5910792A (ja) * 1982-07-09 1984-01-20 Hitachi Ltd ロ−タリ式圧縮機
JPH05106576A (ja) * 1991-08-05 1993-04-27 Daikin Ind Ltd 多気筒密閉形回転圧縮機
KR20050011549A (ko) * 2003-07-23 2005-01-29 삼성전자주식회사 용량가변 회전압축기
KR100577200B1 (ko) * 2003-12-20 2006-05-10 엘지전자 주식회사 이중용량 로터리 압축기
KR100620040B1 (ko) * 2005-02-23 2006-09-11 엘지전자 주식회사 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘
WO2006090977A1 (fr) * 2005-02-23 2006-08-31 Lg Electronics Inc. Compresseur rotatif a capacite variable et systeme de refrigeration le comprenant
CN202579193U (zh) * 2012-05-22 2012-12-05 珠海格力节能环保制冷技术研究中心有限公司 双级变容量压缩机
CN103573628B (zh) * 2012-08-10 2016-02-03 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN104179685A (zh) * 2013-05-20 2014-12-03 珠海格力节能环保制冷技术研究中心有限公司 滚动转子式压缩机及其运行控制方法
CN203285689U (zh) * 2013-05-20 2013-11-13 珠海格力节能环保制冷技术研究中心有限公司 滚动转子式压缩机
JP2014206173A (ja) * 2014-07-04 2014-10-30 ▲荒▼田 哲哉 容積型圧縮機の吐出機構
CN103982426B (zh) * 2014-05-15 2016-08-17 珠海格力节能环保制冷技术研究中心有限公司 滚动转子式压缩机及其泵体结构
CN204344461U (zh) * 2014-12-19 2015-05-20 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN105464978A (zh) * 2015-12-18 2016-04-06 珠海格力节能环保制冷技术研究中心有限公司 变容气缸的滑片控制结构、变容气缸及变容压缩机
CN205446037U (zh) * 2015-12-18 2016-08-10 珠海格力节能环保制冷技术研究中心有限公司 变容气缸的滑片控制结构、变容气缸及变容压缩机

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953544A (zh) * 2014-04-10 2014-07-30 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器
US20170022988A1 (en) * 2014-04-10 2017-01-26 Gree Electric Appliances, Inc. Of Zhuhai Compressor and air conditioner

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JP2019500536A (ja) 2019-01-10
CN105464978A (zh) 2016-04-06
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EP3392507A1 (fr) 2018-10-24
KR20180081778A (ko) 2018-07-17
JP6609051B2 (ja) 2019-11-20
WO2017101537A1 (fr) 2017-06-22

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