WO2016076667A1 - Compresseur de type à plateau oscillant à cylindrée variable - Google Patents

Compresseur de type à plateau oscillant à cylindrée variable Download PDF

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Publication number
WO2016076667A1
WO2016076667A1 PCT/KR2015/012236 KR2015012236W WO2016076667A1 WO 2016076667 A1 WO2016076667 A1 WO 2016076667A1 KR 2015012236 W KR2015012236 W KR 2015012236W WO 2016076667 A1 WO2016076667 A1 WO 2016076667A1
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WO
WIPO (PCT)
Prior art keywords
swash plate
cap
flow path
valve
hole
Prior art date
Application number
PCT/KR2015/012236
Other languages
English (en)
Korean (ko)
Inventor
이건호
이태진
배인표
Original Assignee
학교법인 두원학원
주식회사 두원전자
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020150159136A external-priority patent/KR101800511B1/ko
Application filed by 학교법인 두원학원, 주식회사 두원전자 filed Critical 학교법인 두원학원
Priority to CN201580072379.XA priority Critical patent/CN107110137B/zh
Publication of WO2016076667A1 publication Critical patent/WO2016076667A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members

Definitions

  • the present invention relates to a variable displacement swash plate compressor, and more particularly, to prevent excessive leakage of oil in a state where the inclination of the swash plate is the maximum in the swash plate compressor, and the pressure of the crankcase through the valve while the inclination angle of the swash plate is variable.
  • the present invention relates to a variable displacement swash plate type compressor to facilitate supply of the swash plate.
  • a compressor is a device that compresses a fluid by receiving external power, and is widely used in an air conditioner or a cooling device.
  • the compressor constituting the air conditioner for the vehicle is selectively supplied with the power supplied from the power source by the intermittent action of the electromagnetic clutch, and the refrigerant gas is sucked in from the evaporator and compressed by the linear reciprocating motion of the piston to the condenser side. Discharge.
  • the swash plate type compressor which is widely used as a compressor of an automotive air conditioner, is provided with a disk-shaped swash plate having a predetermined inclination angle on a drive shaft that receives engine power, rotates by a drive shaft, and is rotated by the swash plate.
  • a plurality of pistons connected through a shoe along the circumference of the plurality of pistons is configured to suck, compress and discharge the refrigerant gas by linearly reciprocating the inside of the plurality of cylinder bores formed in the cylinder block.
  • the inclination of the swash plate may vary depending on the pressure of the suction chamber, the crank chamber, and the discharge chamber of the compressor.
  • the crankcase pressure is relatively high, so that the inclination angle of the swash plate can be maximized.
  • the compressor is operated with the swash plate at its maximum inclination angle, no oil moves out of the swash plate chamber.
  • the pressure of the crank chamber is relatively high, so that oil is excessively leaked into the discharge chamber, and thus, the lubrication ability is deteriorated, so that the inclination angle of the swash plate is not easily moved.
  • the pressure in the discharge chamber and the suction chamber is balanced, so that the inclination angle of the swash plate may be lowered.
  • the swash plate is operated in a variable state or the swash plate is operated in a minimum angle state, when the refrigerant flows through the inlet configured between the swash plate and the lug play, only the refrigerant separated by oil due to the high speed rotation of the compressor flows in, There is a problem that the inflow of oil is insufficient.
  • Korean Patent Publication No. 2011-21011 “Capacity Variable Compressor” has been disclosed.
  • the valve is arranged on the flow path connecting the suction chamber and the crank chamber of the swash plate compressor to open and close the flow path in response to the change of the inclination angle of the swash plate, the swash plate inclination angle is the maximum
  • the swash plate inclination angle is the maximum
  • an object of the present invention is to provide a variable displacement swash plate type compressor which can prevent the oil separated from the refrigerant from excessively remaining inside the crank chamber of the compressor to prevent the resistance from being generated on the flow path.
  • an object of the present invention is to provide a variable displacement swash plate type compressor that maintains the lubrication ability by preventing oil from excessive spillage into the discharge chamber when the swash plate inside the crank chamber is at the maximum inclination angle or is to be changed at the maximum inclination angle.
  • variable displacement swash plate compressor including a capacity control valve for adjusting a discharge capacity, comprising: a flow path configured to communicate the suction chamber with the crank chamber; A supply control valve for controlling a coolant supply through the flow path in response to the pressure of the crank chamber; And a valve arrangement in which one end is connected to one end of the flow path and the other end is formed to receive the pressure of the suction chamber through a pressure inflow path connected to the suction chamber, and the supply control valve is disposed.
  • the supply control valve is cylindrical, and has a first through hole formed on a central axis thereof, one end of which is disposed in the pressure inflow path through a side of the fixing cap, and the other end of which includes a second through hole disposed in the first through hole.
  • a fixed cap disposed on the valve plate, a cylindrical shape, one end of which is trapezoidal or hemispherical in shape, and the other end of which has an operating cap protruding from the opening and closing rod for opening and closing the first through hole, and between the fixing cap and the operating cap. It may include a spring disposed to apply an elastic force to the operation cap to open and close the flow path.
  • the diameter of the operation cap may correspond to the diameter of the valve arrangement.
  • the end portion of the valve arrangement in contact with the end side of the operation cap may be in the form of an attachment.
  • the diameter of the spring may correspond to the diameter of the valve arrangement.
  • the supply control valve is cylindrical and fixed having a first through hole on a central axis, one end of which is disposed through the side of the fixing cap to the pressure inflow path, and the other end of which is a second through hole disposed to the first through hole.
  • the inner end may include a valve case protruding from the separation prevention end in contact with the side of the end of the operation cap.
  • the diameter of the valve case may correspond to the diameter of the valve arrangement.
  • the diameter of the operation cap may correspond to the inner diameter of the valve case.
  • the end of the separation prevention end may be in the form of an attachment.
  • the diameter of the spring may correspond to the inner diameter of the valve case.
  • One end of the valve case may have a third through hole communicating with the second through hole.
  • the supply control valve, the operation cap closes the flow path if the pressure difference between the crank chamber and the suction chamber is less than the elastic force of the spring, and the operation cap is closed if the pressure difference between the crank chamber and the suction chamber is greater than the elastic force of the spring.
  • the flow path may be opened to allow the refrigerant to move from the flow path to the suction chamber.
  • a valve for opening and closing the flow path in response to a change in the inclination angle of the swash plate is disposed in the flow path connecting the suction chamber and the crank chamber of the swash plate compressor, and the swash plate inclination angle is the maximum and the swash plate inclination angle at the maximum angle.
  • the pressure of the crankcase can be supplied by intermittent opening and closing of the valve, thereby making it easy to change the inclination angle of the swash plate.
  • the present invention can prevent the oil separated from the refrigerant from excessively remaining in the crank chamber of the compressor to generate resistance on the flow path.
  • the present invention when the swash plate inside the crank chamber is at the maximum inclination angle or is going to change at the maximum inclination angle, the oil is prevented from excessive spillage into the discharge chamber to maintain the lubrication capacity.
  • FIG. 1 is a cross-sectional view showing an example of the configuration of a variable displacement swash plate compressor according to an embodiment of the present invention.
  • FIG. 2 is an exploded view showing an example of the configuration of a supply control valve used in the variable displacement swash plate compressor shown in FIG.
  • 3 and 4 are operation state diagrams showing the operation of the variable displacement swash plate compressor using the supply control valve shown in FIG.
  • FIG. 5 is an exploded view showing another example of the configuration of a supply control valve used in the variable displacement swash plate compressor shown in FIG. 1.
  • FIG. 6 is a cross-sectional view showing another example of a configuration of a supply control valve used in the variable displacement swash plate compressor shown in FIG. 1.
  • 7 and 8 are operation state diagrams showing the operation of the variable displacement swash plate compressor using the supply control valve shown in FIG.
  • FIG. 1 is a cross-sectional view showing an example of the configuration of a variable displacement swash plate compressor according to an embodiment of the present invention.
  • variable displacement swash plate compressor 100 includes a flow path 150, a supply control valve 170, and a valve arrangement path 160.
  • the swash plate compressor 100 basically includes a cylinder block 110, a front housing 120, a valve plate 140, and a rear housing 130.
  • the cylinder block 110 forms the body of the compressor. Inside the cylinder block 110 may include a plurality of cylinder bores parallel to each other. Since the cylinder block 110 is a well-known configuration in the swash plate type compressor, a detailed description thereof will be omitted.
  • the front housing 120 is coupled to the front of the cylinder block 110.
  • the crank chamber 122 may be provided inside the front housing 120.
  • the lug plate 125 and the swash plate 126 may be installed inside the crank chamber 122 along the circumference of the driving shaft 124.
  • the first refrigerant inlet 124a and the second refrigerant inlet 124b through which the refrigerant flows are formed on the drive shaft 124 on which the lug plate 125 and the swash plate 126 are installed.
  • the first refrigerant inlet 124a is formed on the central axis of the drive shaft 124, and the second refrigerant inlet 124b is formed from the outer circumferential surface of one end of the drive shaft 124 to one end of the first refrigerant inlet 124a. It is arranged to penetrate vertically. Therefore, the refrigerant introduced through the second refrigerant inlet 124b may flow through the first refrigerant inlet 124a. In addition, when the refrigerant is introduced, the refrigerant is introduced as the oil is separated by the rotation of the drive shaft 124.
  • the valve plate 140 is in the form of a plate having a predetermined thickness and is disposed behind the cylinder block 110.
  • a CS hole may be formed through a predetermined diameter at a portion crossing the fluid supply path connecting the suction chamber and the crank chamber of the compressor.
  • the rear housing 130 is disposed rearward of the cylinder block 110. At this time, the valve plate 140 is interposed between the rear housing 130 and the cylinder block 110.
  • the flow path 150 connects the crank chamber 122 of the front housing 120 and the discharge chamber of the rear housing 130 to allow fluid to flow between the crank chamber 122 and the discharge chamber.
  • the flow path 150 preferably connects the crank chamber 122 and the discharge chamber in a shortest distance, that is, in a straight line to facilitate fluid flow.
  • the flow path 150 is disposed diagonally with respect to the central axis of the compressor 100, but may be formed in parallel with the central axis of the compressor 100 as required by the user.
  • an end portion of the valve arrangement passage 160 that is, a portion where one end of the operation cap 174 to be described below contacts is formed to minimize the area in contact with the end of the operation cap 174. That is, if the end of the operating cap 174 is protruding in the hemispherical shape, or if the end of the operating cap 174 is trapezoidal, as shown in the figure in the valve arrangement contacting the end side of the operating cap 174 ( It is preferable that the end of 160 has a predetermined cross-sectional shape.
  • the valve arrangement passage 160 may be formed through the cylinder block. On the valve arrangement path 160, the supply control valve mentioned later is arrange
  • valve arrangement passage 160 may be connected to the flow passage 150, and the other end thereof may be connected to the suction chamber 132.
  • the other end of the valve arrangement passage 160 has a pressure inflow passage 180 orthogonal to the central axis of the compressor 100. It can be formed in the direction.
  • the pressure inflow path 180 is formed in a direction orthogonal to the central axis of the compressor 100, so that the pressure of the suction chamber 132 can be applied to the valve arrangement path 160.
  • the pressure inlet 180 may be formed along the valve plate 140.
  • a predetermined hole may be formed at a portion where the pressure inflow passage 180 is connected to the suction chamber 132.
  • the supply control valve 170 may operate by receiving the refrigerant discharge pressure of the suction chamber 132 to intermittently supply the fluid through the flow path 150.
  • the fluid may be a refrigerant supplied by the compressor.
  • the fluid can be changed depending on the use of the compressor.
  • FIG. 2 is an exploded view showing an example of the configuration of a supply control valve used in the variable displacement swash plate compressor shown in FIG. 1.
  • the supply control valve 170 includes a fixed cap 172, an operation cap 174, and a spring 176.
  • Fixing cap 172 is a cylindrical having a predetermined height and diameter, is disposed on the valve plate.
  • the fixed cap 172 is formed with a first through hole 173a having a predetermined diameter on the central axis, and the second through hole 173b is formed in a direction orthogonal to the central axis of the fixed cap 172. .
  • One end of the second through hole 173b is connected to the first through hole 173a, and the other end thereof is formed toward the outer circumferential surface of the fixing cap 172.
  • the other end of the second through hole 173b may be disposed to be connected to the pressure inflow path 180 to be described later.
  • the second through hole 173b may be formed in a groove shape on the bottom surface of the fixing cap 172.
  • the first through hole 173a and the second through hole 173b transfer the pressure applied from the suction chamber 132 to the operation cap 174 which will be described later.
  • the operation cap 174 is a cylindrical having a predetermined height and diameter, one end may protrude in the form of a trapezoid or hemispherical. The other end of the operation cap 174 protrudes the opening and closing rod 175 having a predetermined diameter and length. The opening and closing rod 175 may open and close the first through hole 173a according to the movement of the operation cap 174.
  • the opening and closing rod 175 is formed to a predetermined length and diameter.
  • the diameter of the opening and closing rod 175 may correspond to the inner diameter of the spring 176 to be described later so that the shaking does not occur when the operation cap 174 is moved.
  • the diameter of the opening / closing rod 175 may correspond to the diameter of the first through hole 173a to facilitate opening and closing of the first through hole 173a.
  • the length of the opening / closing rod 175 may be appropriately set by the user within the range in which the opening and closing of the first through hole 173a is made to move the operation cap 174.
  • the diameter of the operating cap 174 may correspond to the diameter of the valve arrangement 160.
  • the operation cap 174 may move by the pressure of the suction chamber 132 and the crank chamber 122, and may move from the valve arrangement path 160 to the flow path 150. Supply of the refrigerant through the flow path 150 may be interrupted by the movement of the operation cap 174.
  • the spring 176 is disposed between the fixed cap 172 and the operation cap 174, by applying an elastic force to the operation cap 174, to facilitate the movement of the operation cap 174.
  • 3 and 4 are operation state diagrams showing the operation of the variable displacement swash plate compressor shown in FIG.
  • the inclination angle of the swash plate is maximum.
  • the pressure in the crank chamber 122 is low, and the pressure difference between the crank chamber and the suction chamber 132 is smaller than the elastic force of the spring 176. That is, since the pressure applied to the operation cap 174 is less than the elastic force of the spring 176, the operation cap 174 by the elastic force of the spring 176, the valve arrangement path 160 as shown in FIG. Located at the intersection of the flow path 150 and the flow path 150 to be in a closed state.
  • the refrigerant flows into the suction chamber 132 through the second refrigerant inlet 124b and the first refrigerant inlet 124a.
  • the pressure of the crank chamber 122 may increase.
  • the rotation speed increases and the inclination angle of the swash plate 126 of the compressor 100 decreases below its maximum state.
  • the pressure of the crank chamber 122 of the compressor 100 increases, the difference between the pressure of the crank chamber 122 and the pressure of the suction chamber 132 may be greater than the elastic force of the spring 176. Therefore, the pressure of the crank chamber 122 is applied to the operation cap 174, so that the operation cap 174 as shown in Figure 4 in the valve arrangement path 160 and the flow path 150 side valve arrangement ( 160 to move inside, the flow path 150 is open to allow the refrigerant to move from the flow path 150 to the suction chamber 132, thereby, can be easily reduced the inclination of the swash plate. .
  • 5 and 6 are exploded views and cross-sectional views showing another example of the configuration of the supply control valve used in the variable displacement swash plate compressor according to the present invention.
  • the supply control valve 270 includes a fixed cap 272, an operation cap 274, a spring 276, and a valve case 278.
  • Fixing cap 272 is a cylindrical having a predetermined height and diameter.
  • the fixed cap 272 is formed with a first through hole 273a having a predetermined diameter on the central axis, and the second through hole 273b is formed in a direction orthogonal to the central axis of the fixed cap 272. .
  • One end of the second through hole 273b is connected to the first through hole 273a, and the other end thereof is formed toward the outer circumferential surface of the fixing cap 272.
  • the second through hole 273b may be formed in a groove shape on the bottom surface of the fixing cap 272.
  • the first through hole 273a and the second through hole 273b transmit the pressure applied to the outside to the operation cap 274 which will be described later.
  • the operation cap 274 is cylindrical having a predetermined height and diameter, and one end thereof may protrude in a trapezoidal shape or a hemisphere shape. The other end of the operation cap 274 protrudes the opening and closing rod 275 having a predetermined diameter and length. The opening / closing rod 275 may open and close the first through hole 273a according to the movement of the operation cap 274.
  • the opening and closing rod 275 is formed to a predetermined length and diameter.
  • the diameter of the opening and closing rod 275 may correspond to the inner diameter of the spring 276 to be described later to prevent the shaking occurs when the operation cap 274 is moved.
  • the diameter of the opening / closing rod 275 may correspond to the diameter of the first through hole 273a to facilitate opening and closing of the first through hole 273a.
  • the length of the opening / closing rod 275 may be appropriately set by the user in the range in which the opening and closing of the first through hole 273a is made to move the operation cap 274.
  • the diameter of the operation cap 274 may correspond to the inner diameter of the valve case 278 to be described later.
  • the operation cap 274 moves by the pressure of the suction chamber 232 and the crank chamber 222, and may move inside the valve case 278. Supply of the refrigerant supplied by the movement of the operation cap 274 may be interrupted.
  • the spring 276 is disposed between the fixed cap 272 and the operation cap 274, to apply an elastic force to the operation cap 274, to facilitate the movement of the operation cap 274.
  • the valve case 278 is in the form of a tube having a predetermined length and an inner diameter, the outer diameter of which corresponds to the diameter of the valve arrangement path 260.
  • a fixed cap 272, an operation cap 274, and a spring 276 are disposed inside the valve case 278.
  • the diameters of the fixing cap 272 and the spring 276 correspond to the inner diameter of the valve case 278.
  • valve case 278 where one end of the operation cap 274 abuts is protruded to prevent the departure end 278a at a predetermined height along the inner circumference thereof to prevent the departure of the operation cap 274.
  • the shape of the separation prevention end 278a is preferably in the form of minimizing the contact area with the end of the operation cap 274.
  • the end of the operation cap 274 is trapezoidal shape, the slope is a predetermined slope.
  • the end of the separation preventing end 278a in contact with the end of the operation cap 274 is preferably in the form of a predetermined attachment so that the contact area with the slope of the end of the operation cap 274 is minimized.
  • valve case 278 One side of the valve case 278 is formed with a flow hole 278b through which the refrigerant is moved.
  • the flow path is opened as the operation cap 274 moves, the fluid moves through the front end of the flow hole 278b and the valve case 278.
  • a third through hole 278c communicating with the second through hole 273b is formed at one end of the valve case 278.
  • the supply control valve 270 is configured such that the operation elements are arranged inside the valve case 278 of a predetermined size, and the supply control valve 270 is arranged by the arrangement of the valve case 278. Therefore, the management of the supply control valve 270 becomes easier.
  • the supply control valve 270 may operate by receiving the refrigerant discharge pressure of the suction chamber 232 to intermittently supply the fluid through the flow path 250.
  • the fluid may be a refrigerant supplied by the compressor.
  • the fluid can be changed depending on the use of the compressor.
  • 7 and 8 are operation state diagrams showing the operation of the variable displacement swash plate compressor using the supply control valve shown in FIG.
  • the inclination angle of the swash plate is the maximum.
  • the pressure of the crank chamber 222 is low, and the pressure difference between the crank chamber and the suction chamber 232 is smaller than the elastic force of the spring 276. That is, since the pressure applied to the operation cap 274 is smaller than the elastic force of the spring 276, the operation cap 274 by the elastic force of the spring 276, the valve arrangement path 260 as shown in FIG. Located at the inner end of the valve case 278 which is the intersection of the flow path 250 and the flow path 250, the flow hole 278b and the flow path 250 are closed.
  • the refrigerant flows into the suction chamber 232 through the second refrigerant inlet 224b and the first refrigerant inlet 224a while the flow path 250 is closed.
  • the pressure of the crank chamber 222 may increase.
  • the rotation speed increases and the inclination angle of the swash plate 226 of the compressor 200 decreases below the maximum state.
  • the difference between the pressure of the crank chamber 222 and the pressure of the suction chamber 232 may be greater than the elastic force of the spring 276.
  • the pressure of the crank chamber 222 is applied to the operation cap 274, the operation cap 274 moves to the inside of the valve case 278, as shown in Figure 8, flows with the flow hole 278b
  • the furnace 250 may be opened to allow the refrigerant to move from the flow path 250 to the suction chamber 232, thereby facilitating the degree of inclination of the swash plate.
  • a valve is provided to open and close the flow path in response to a change in the inclination angle of the swash plate in a flow path connecting the suction chamber and the crank chamber of the swash plate type compressor, and when the inclination angle of the swash plate is maximum, the supply of fluid flowing into the crank chamber is interrupted.
  • the inclination angle can be easily changed.
  • the present invention can prevent the oil separated from the refrigerant from excessively remaining in the crank chamber of the compressor to generate resistance on the flow path.
  • the present invention when the swash plate inside the crank chamber is at the maximum inclination angle or is going to change at the maximum inclination angle, the oil is prevented from excessive spillage into the discharge chamber to maintain the lubrication capacity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention agence, au niveau d'un chemin d'écoulement reliant une chambre d'aspiration et une chambre de manivelle d'un compresseur du type à plateau oscillant, une soupape destinée à ouvrir et à fermer un trajet d'écoulement en réponse à un changement de l'angle d'inclinaison d'un plateau oscillant ; et de telle sorte que la pression de la chambre de vilebrequin puisse être fournie, commande l'ouverture et la fermeture de la soupape en réponse au cas où l'angle d'inclinaison du plateau oscillant est le maximum et au cas où l'angle d'inclinaison du plateau oscillant passe de l'angle maximal à un angle plus petit, ce qui permet de faciliter un changement de l'angle d'inclinaison du plateau oscillant du compresseur.
PCT/KR2015/012236 2014-11-13 2015-11-13 Compresseur de type à plateau oscillant à cylindrée variable WO2016076667A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201580072379.XA CN107110137B (zh) 2014-11-13 2015-11-13 变排量斜盘式压缩机

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2014-0158086 2014-11-13
KR20140158086 2014-11-13
KR1020150159136A KR101800511B1 (ko) 2014-11-13 2015-11-12 용량 가변형 사판식 압축기
KR10-2015-0159136 2015-11-12

Publications (1)

Publication Number Publication Date
WO2016076667A1 true WO2016076667A1 (fr) 2016-05-19

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PCT/KR2015/012236 WO2016076667A1 (fr) 2014-11-13 2015-11-13 Compresseur de type à plateau oscillant à cylindrée variable

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20110134167A (ko) * 2010-06-08 2011-12-14 한라공조주식회사 가변용량형 사판식 압축기
KR20120090312A (ko) * 2011-02-07 2012-08-17 한라공조주식회사 가변용량형 사판식 압축기
KR20130121329A (ko) * 2012-04-27 2013-11-06 한라비스테온공조 주식회사 가변 용량형 사판식 압축기
KR20130121328A (ko) * 2012-04-27 2013-11-06 한라비스테온공조 주식회사 사판식 압축기
KR20140101052A (ko) * 2013-02-07 2014-08-19 학교법인 두원학원 용량 가변형 사판식 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20110134167A (ko) * 2010-06-08 2011-12-14 한라공조주식회사 가변용량형 사판식 압축기
KR20120090312A (ko) * 2011-02-07 2012-08-17 한라공조주식회사 가변용량형 사판식 압축기
KR20130121329A (ko) * 2012-04-27 2013-11-06 한라비스테온공조 주식회사 가변 용량형 사판식 압축기
KR20130121328A (ko) * 2012-04-27 2013-11-06 한라비스테온공조 주식회사 사판식 압축기
KR20140101052A (ko) * 2013-02-07 2014-08-19 학교법인 두원학원 용량 가변형 사판식 압축기

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