WO2010058998A2 - Compresseur à plateau oscillant avec soupape rotative - Google Patents

Compresseur à plateau oscillant avec soupape rotative Download PDF

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Publication number
WO2010058998A2
WO2010058998A2 PCT/KR2009/006870 KR2009006870W WO2010058998A2 WO 2010058998 A2 WO2010058998 A2 WO 2010058998A2 KR 2009006870 W KR2009006870 W KR 2009006870W WO 2010058998 A2 WO2010058998 A2 WO 2010058998A2
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WO
WIPO (PCT)
Prior art keywords
rotary valve
refrigerant
swash plate
drive shaft
cylinder block
Prior art date
Application number
PCT/KR2009/006870
Other languages
English (en)
Korean (ko)
Other versions
WO2010058998A3 (fr
Inventor
이권희
박성균
김기범
이건호
Original Assignee
두원공과대학교
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
Application filed by 두원공과대학교, 주식회사 두원전자 filed Critical 두원공과대학교
Priority to CN200980153670.4A priority Critical patent/CN102272450B/zh
Publication of WO2010058998A2 publication Critical patent/WO2010058998A2/fr
Publication of WO2010058998A3 publication Critical patent/WO2010058998A3/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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical 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
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • 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
    • F04B27/10—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 having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • 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
    • F04B39/1066—Valve plates
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/40—Organic materials
    • F05B2280/4003—Synthetic polymers, e.g. plastics
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a swash plate type compressor equipped with a rotary valve, and more particularly, to a swash plate type compressor equipped with a rotary valve capable of efficiently sucking refrigerant flowing into the swash plate chamber through a cylinder block.
  • a vehicle air conditioner is a device that maintains a temperature inside a car lower than an external temperature by using a refrigerant, and includes a compressor, a condenser, and an evaporator to configure a circulation cycle of the refrigerant.
  • the compressor is a device that compresses and pumps refrigerant, and is driven by engine power or a motor.
  • swash plate type compressor which is a kind of reciprocating compressor
  • a disc shaped swash plate is installed on a drive shaft to which engine power is transmitted in a state in which the inclination angle is variable or fixed to the rotation of the drive shaft, and the circumference of the swash plate is caused by the rotation of the swash plate.
  • a plurality of pistons installed via a shoe along the structure 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.
  • a valve plate is disposed between the housing and the cylinder block to control the suction and discharge of the refrigerant gas.
  • the front housing (A10) is built in the front cylinder block (A20)
  • the rear housing (A10a) is coupled to the front housing (A10) and built in the rear cylinder block (A20a)
  • the front and rear A plurality of pistons A50 reciprocating in the plurality of cylinder bores A21 formed in the cylinder blocks A20 and A20a, respectively, and a shoe A45 inclinedly coupled to the drive shaft A30 and installed on an outer circumference thereof.
  • Valve plate (A60) installed between the swash plate (A40) and the front and rear housings (A10) (A10a) and the front and rear cylinder blocks (A20) (A20a) to be coupled to the piston (A50) via a).
  • a coolant discharge chamber A12 and a coolant suction chamber A11 are formed inside and outside the partition A13 in the front and rear housings A10 and A10a, respectively.
  • the coolant discharge chamber A12 is formed in the first discharge chamber A12a formed inside the partition A13 and outside the partition A13 and is partitioned from the coolant suction chamber A11 to form the first discharge chamber. It consists of the 2nd discharge chamber A12b which communicates with A12a and the discharge hole A12c. Accordingly, the refrigerant in the first discharge chamber A12a passes through the small diameter discharge hole A12c and moves to the second discharge chamber A12b. As a result, the pulsation pressure due to the periodic suction of the refrigerant is attenuated. This can reduce vibration and noise.
  • the front and rear cylinder block (A20) so that the refrigerant supplied to the swash plate chamber (A24) provided between the front and rear cylinder blocks (A20, A20a) can flow to each of the refrigerant suction chamber (A11).
  • a plurality of suction passages A22 are formed in A20a, and the second discharge chamber A12b of the front and rear housings A10 and A10a passes through the front and rear cylinder blocks A20 and A20a. It communicates with each other by the formed connection path A23. Therefore, the suction and compression of the refrigerant may be simultaneously performed in the bore A21 of the front and rear cylinder blocks A20 and A20a according to the reciprocating motion of the piston A50.
  • the conventional swash plate compressor configured as described above compresses the refrigerant through the following process.
  • the refrigerant supplied from the evaporator is sucked into the suction part of the muffler A70 and then supplied to the swash plate chamber A24 between the front and rear cylinder blocks A20 and A20a through the refrigerant suction port A71, and the swash plate chamber
  • the refrigerant supplied to A24 flows into the refrigerant suction chamber A11 of the front and rear housings A10 and A10a along the suction passage A22 formed in the front and rear cylinder blocks A20 and A20a. do.
  • the suction lead valve is opened during the suction stroke of the piston A50, so that the refrigerant in the refrigerant suction chamber A11 is sucked into the cylinder bore A21 through the refrigerant suction hole of the valve plate A60.
  • the piston A50 is compressed, the refrigerant inside the cylinder bore A21 is compressed, and the discharge lead valve is opened, and the refrigerant flows through the refrigerant discharge hole of the valve plate A60.
  • A10a flows to the first discharge chamber A12a.
  • the refrigerant flowing into the first discharge chamber A12a is discharged to the discharge portion of the muffler A70 through the refrigerant discharge port A72 of the muffler A70 via the second discharge chamber A12b and then flows to the condenser. .
  • the refrigerant compressed in the cylinder bore A21 of the front cylinder block A20 is discharged to the first discharge chamber A12a of the front housing A10 and then flows to the second discharge chamber A12b.
  • the second discharge chamber A12b of the rear housing A10a flows to the refrigerant discharge port A72 together with the refrigerant therein.
  • the discharge portion of the muffler A70 is discharged.
  • the suction of the refrigerant is caused by a loss due to a suction resistance caused by a complicated internal refrigerant flow path and a loss due to elastic resistance of the suction lead valve during opening and closing of the valve plate A60.
  • the volumetric efficiency is reduced.
  • Korean Patent Publication No. 2007-19564 discloses a technique for reducing the loss caused by the elastic resistance of the suction lead valve.
  • the prior art relates to a compressor to which a suction shaft integrated suction drive valve without a suction lead valve is applied.
  • the refrigerant allows the refrigerant to directly enter the cylinder bore through the inside of the drive shaft in order to reduce the loss caused by the suction resistance. will be.
  • the swash plate B160 is inclinedly coupled and a flow path B151 through which a refrigerant flows is formed, and the swash plate B160 is coupled to the flow plate B151 on the side of the swash plate hub.
  • One or more suction ports B152 are formed to communicate with each other, and a drive shaft B150 having an outlet B153 formed at a position spaced apart from the suction ports B152, and the drive shaft B150 is rotatably installed, and the swash plate chamber B136.
  • a plurality of cylinder bores B131 and B141 are provided at both sides, and the refrigerant sucked into the flow path B151 of the drive shaft B150 sequentially moves to each cylinder bore B131 and B141 when the drive shaft B150 rotates.
  • the cylinder bore (B131) (B141) mounted on the outer circumference of the (B160) via a shoe and linked to the rotational motion of the swash plate (B160)
  • Compressor comprising a plurality of pistons (B170) for reciprocating inside and the front and rear housings (B110) (B120) coupled to both sides of the cylinder block (B130) (B140) and the discharge chamber is formed therein, respectively Is disclosed.
  • the refrigerant introduced through the suction port flows into the drive shaft B150 through the suction port B152 formed on the hub side of the swash plate B160, and then the drive shaft B150. It is configured to flow into the cylinder bores B131 and B141 via the flow path B151 formed in the interior thereof.
  • the suction port of the drive shaft is formed on the swash plate hub side to suck the refrigerant in the swash plate chamber while the drive shaft rotates, the suction shaft has a sufficient suction flow rate due to the flow resistance caused by the centrifugal force. There was a problem that can not be.
  • an object of the present invention is to allow the suction of the refrigerant in the swash plate chamber through the cylinder block and at the same time the rotary valve which can be stably supplied in a state sufficiently secured refrigerant intake It is to provide a swash plate compressor equipped with.
  • another object of the present invention is to provide a swash plate compressor equipped with a rotary valve that can further improve the volumetric efficiency of the compressor by reducing the flow path resistance and suction loss of the refrigerant by the rotary valve.
  • a swash plate type compressor equipped with a rotary valve includes a housing, a cylinder block having a plurality of cylinder bores and coupled to the housing, and reciprocally accommodated in the cylinder bore, respectively.
  • the swash plate-type compressor including a rotary valve formed to rotate together and the sliding rotation is freely installed on the inner surface of the coupling hole formed in the cylinder block,
  • a coolant discharge port is formed on an outer circumferential surface of the rotary valve, and a communication hole connected to the plurality of cylinder bores is formed on an inner circumferential surface of a coupling hole facing the outer circumferential surface of the rotary valve, and the refrigerant communicates from the swash chamber to the housing. Characterized in that the suction groove is formed.
  • the cylinder block is further formed with a refrigerant supply passage communicating from the swash plate chamber to the housing, a connection flow path groove is formed between the refrigerant supply passage and the refrigerant suction groove, the refrigerant supply passage when viewed from the drive shaft direction Is characterized in that it is disposed outside the refrigerant suction groove.
  • the refrigerant suction groove for sucking the refrigerant in the swash plate chamber is formed in the coupling hole of the cylinder block, so that the refrigerant can be stably sucked regardless of the rotational force of the drive shaft rotating at high speed. There is an effect that can greatly reduce the loss caused by the suction resistance.
  • the coolant supply path and the connecting flow path groove are additionally formed in the cylinder block, so that sufficient coolant can be sucked from the swash plate chamber, thereby increasing the amount of coolant flowing into the cylinder bore, thereby further improving the volumetric efficiency.
  • the rotary valve formed in the coupling hole of the cylinder block has an advantage of supplying the refrigerant to the cylinder bore more quickly and smoothly by sucking the refrigerant flowing from the swash plate chamber in a double suction method.
  • the rotary valve is provided with a discharge hole for bypassing the refrigerant remaining in the communication hole of the cylinder bore during the compression stroke of the piston, so that the refrigerant re-supplied into the cylinder bore after the compression stroke is smoothly introduced into the cylinder bore without a suction obstacle. It is mobile.
  • FIG. 1 is a front sectional view and a side sectional view showing the configuration of a conventional swash plate type compressor.
  • FIG. 2 is a cross-sectional view showing a swash plate compressor equipped with a rotary valve according to the prior art.
  • FIG. 3 is a sectional view showing a swash plate compressor equipped with a rotary valve according to Embodiment 1 of the present invention.
  • FIG. 4 is a perspective view illustrating the cylinder block of FIG. 3.
  • FIG. 5 is a perspective view schematically illustrating a refrigerant flow structure with respect to FIG. 4.
  • FIG. 6 is a perspective view illustrating a state in which a rotary valve is mounted on the driving shaft of FIG. 3.
  • FIG. 7 is a cross-sectional view of FIG. 4.
  • FIG. 8 is a cross-sectional view showing a swash plate compressor equipped with a rotary valve according to a second embodiment of the present invention.
  • FIG. 9 is a perspective view illustrating the cylinder block of FIG. 8.
  • FIG. 10 is a cross-sectional view of FIG. 9.
  • FIG. 11 is a partial cross-sectional perspective view schematically illustrating the refrigerant flow structure with respect to FIG. 9.
  • the swash plate compressor 1000 is applied to an embodiment of the double-headed piston compressor, but may be applied to a conventional double-headed piston compressor not necessarily limited to the double-headed piston compressor.
  • the swash plate compressor 1000 includes a cylinder block 100 having a plurality of cylinder bores 110 and a cylinder bore 110 of the cylinder block 100.
  • Piston 200 which is accommodated in the reciprocating motion respectively, the front and rear housings 310 and 320 to be hermetically coupled to the front and rear of the cylinder block 100, respectively, the front housing 310 and the cylinder block ( Of the drive shaft 400 rotatably installed with respect to 100, the swash plate 500 interlocked with the drive shaft 400 and the piston 200, the cylinder block 100, and the front and rear housings 310 and 320. It is composed of a valve plate 600 interposed therebetween.
  • the cylinder block 100 is interposed between the front and rear housings 310 and 320, and a plurality of cylinder bores 110 in which the piston 200 reciprocates. ) Is formed.
  • the cylinder block 100 is provided with a coupling hole 120, the rotary valve (R) is provided in the coupling hole 120 is free to slide rotation.
  • the rotary valve (R) is coupled to the drive shaft 400 rotates with the rotation of the drive shaft (400).
  • the inner circumferential surface of the coupling hole 120 facing the outer circumferential surface of the rotary valve R is formed with a communication hole 130 for supplying refrigerant to each of the plurality of cylinder bores 110, and the swash plate chamber ( A refrigerant suction groove 140 communicating with each of the housings 310 and 320 is formed.
  • the refrigerant suction groove 140 is disposed between the adjacent cylinder bores (110, 110) is effective for the refrigerant suction. Strictly, as shown in the drawing, the refrigerant suction grooves 140 may be disposed one by one between the neighboring communication holes 130 and 130.
  • the configuration of the rotary valve (R) adopted in the embodiment of the present invention is as follows.
  • the rotary valve (R) is coupled to surround the drive shaft 400, but is coupled to the outer peripheral surface of the drive shaft 400, the outer peripheral surface of the rotary valve (R) is coupled to the coupling hole 120 of the cylinder block 100 It is.
  • the rotary valve (R) is a cylindrical shape having a predetermined length, one side of the outer peripheral surface of the refrigerant in the refrigerant suction groove 140 in the circumferential direction directly communicating with the communication hole 130 of the cylinder block 100
  • a refrigerant discharge port R1 is formed to discharge while communicating with each other
  • a refrigerant bypass groove R2 for introducing a refrigerant in the refrigerant storage chamber P1 of the front and rear housings 310 and 320 is formed at one end thereof.
  • the inner diameters of the refrigerant bypass grooves R2 are greater than the outer diameter of the drive shaft 400 and are spaced apart from each other.
  • the rotary valve R may suck the refrigerant in a quick and stable state by a double suction method.
  • a snap ring 402 between the rotary valve (R) and the drive shaft 400 to increase the sealing force.
  • the rotary valve (R) is formed with a discharge through-hole (R3) for removing the residual gas trapped in the communication hole 130 at the time of the suction action of the piston 200 do.
  • the discharge through hole (R3) is formed through the neighboring in front of the rotational direction of the refrigerant discharge port (R1) of the rotary valve (R).
  • the piston 200 when the piston 200 reaches the top dead center to complete the compression, most of the compressed high-pressure refrigerant is discharged to the refrigerant discharge chamber (P2) of the front and rear housings (310, 320), but some of the refrigerant is in communication It remains in the hole 130. At this time, the refrigerant gas remaining in the high pressure state in the communication hole 130 may cause a suction failure by preventing the suction of the refrigerant (low pressure state) flowing from the refrigerant discharge port R1 of the rotary valve R. .
  • the discharge hole R3 of the rotary valve R communicates with the communication hole 130 first after the compression stroke of the piston 200 reaches a top dead center, and the refrigerant remaining in the rotary valve R is rotated. Bypassing the inside to facilitate the subsequent suction of the refrigerant to the cylinder bore (110).
  • the discharge hole R3 of the rotary valve R may be formed in a shape corresponding to the width and width of the communication hole 130 of the cylinder block 100.
  • the discharge hole (R3) of the rotary valve (R) is preferably manufactured in a penetrating form, but not necessarily limited to the form of a groove recessed to a predetermined height to bypass the refrigerant in the longitudinal direction outside. It can also be produced in a form that can.
  • Teflon (Teflon) coating treatment to minimize overheating and wear.
  • the refrigerant introduced into the swash plate chamber 101 from the evaporator is a cylinder block (B) by the suction stroke of the piston 200. It is introduced into the refrigerant suction groove 140 of 100.
  • a part of the refrigerant moving in the axial direction through the refrigerant suction groove 140 moves to the refrigerant discharge port R1 in the rotary valve R and is directly sucked into the cylinder bore 110, and the other refrigerant is a rotary.
  • valve (R) Guided along the outer circumferential surface of the valve (R) is moved to the refrigerant bypass groove (R2) of the rotary valve (R) through the refrigerant storage chamber (P1) of the front and rear housings (310, 320) and then the cylinder bore through the refrigerant discharge port (R1) Inhaled at 110.
  • the rotary valve R has a structure in which the refrigerant is sucked in both directions, and not only maintains the suction amount of the refrigerant stably but also quickly discharges the cylinder bore.
  • the discharge valve R3 is formed in the rotary valve R, after the compression stroke of the piston 200 reaches a top dead center, the communication hole 130 of the cylinder bore 110 communicates therewith. Since the residual refrigerant is bypassed into the rotary valve R, the suction of the refrigerant into the cylinder bore 110 can be smoothly performed thereafter.
  • the rotary valve R is detachably coupled around the outer circumferential surface of the drive shaft 400, but may be formed by directly processing the existing drive shaft 400.
  • the swash plate compressor 1000 includes a cylinder block 100 having a plurality of cylinder bores 110 and a piston 200 reciprocally accommodated in the cylinder bores 110 of the cylinder block 100, respectively. ), The front and rear housings 310 and 320 which are hermetically coupled to the front and rear of the cylinder block 100, respectively, and a drive shaft rotatably installed with respect to the front housing 310 and the cylinder block 100 ( 400, the swash plate 500 interlocked with the drive shaft 400 and the piston 200, and the valve plate 600 interposed between the cylinder block 110 and the front and rear housings 310 and 320, respectively. It is composed.
  • the cylinder block 100 is interposed between the front and rear housings 310 and 320, and a cylinder bore 110 is formed therein to allow the piston 200 to reciprocate.
  • the cylinder block 100 is provided with a coupling hole 120, the rotary valve (R) is provided in the coupling hole 120 is free to slide rotation.
  • the rotary valve R is configured to rotate together with the drive shaft 400.
  • the inner circumferential surface of the coupling hole 120 facing the outer circumferential surface of the rotary valve R is formed with a communication hole 130 for supplying refrigerant to each of the plurality of cylinder bores 110, and the swash plate chamber ( A refrigerant suction groove 140 communicating with each of the housings 310 and 320 is formed.
  • the refrigerant suction groove 140 is disposed between the adjacent cylinder bores (110, 110) is effective for the refrigerant suction. Strictly, as shown in the drawing, the refrigerant suction grooves 140 may be disposed one by one between the neighboring communication holes 130 and 130.
  • a coolant supply path 170 for supplying a coolant to a coolant storage chamber P1 of the front and rear housings 310 and 320 is further formed near the outer circumferential surface of the coolant suction groove 140 and the coolant supply path 170.
  • the refrigerant suction groove 140 has a structure in which a connection flow path groove 180 is formed.
  • connection flow path groove 180 may be formed at an end surface of the cylinder block 100 facing the front and rear housings 310 and 320.
  • the refrigerant supply path 170 is formed through a plurality of cylinder bore 110 in a state spaced apart from the coupling hole 120 by a predetermined distance, it is possible to more smoothly suck the refrigerant in the swash plate chamber (101) In addition, it serves to significantly reduce the flow path resistance of the refrigerant.
  • the rotary valve (R) is formed integrally with the drive shaft 400 by processing the outer diameter of the drive shaft (400).
  • the rotary valve (R) is formed on the drive shaft 400, while the refrigerant introduced into the refrigerant suction groove 140 of the cylinder block 100 directly communicates with the cylinder bore 110 on one side of the outer peripheral surface.
  • a refrigerant discharge port R1 for discharging is formed.
  • the inner circumferential surface of the coupling hole 120 of the cylinder block 100 and the outer circumferential surface of the rotary valve R communicate with each other to remove residual high pressure gas in the communication hole 130 of the cylinder bore 110.
  • the first discharge groove 190 and the second discharge grooves R4 and R5 are formed.
  • the first discharge groove 190 has a circular shape recessed to a predetermined depth along the circumference of the inner circumferential surface of the coupling hole 120.
  • the first discharge groove 190 serves as an intermediate passage for supplying the residual gas moved from one side second discharge groove (R4) to the other side second discharge groove (R5).
  • the second discharge grooves R4 and R5 are formed with the refrigerant discharge port R1 formed in the drive shaft 400 interposed therebetween.
  • one side of the second discharge groove (R4) serves to suck the refrigerant in the communication hole 130
  • the second discharge groove (R5) formed on the other side residual gas passing through the first discharge groove 190 It serves to discharge to the expanded cylinder bore 110 through the communication hole 130 opposite.
  • the refrigerant remaining in the communication hole 130 may be configured to allow the second discharge groove R4, the first discharge groove 190, and the second discharge groove R5 on the other side of the driving shaft 400 to be rotated. After passing sequentially, it is discharged to the expanded cylinder bore 110 through the communication hole 130 on the opposite side.
  • the refrigerant discharge port of the rotary valve (R) formed in the drive shaft 400 in the process of the refrigerant flowing through the refrigerant suction groove 140 of the cylinder block 100 is moved. Through the R1 is discharged to the communication hole 130 of the cylinder bore 110.
  • the refrigerant introduced into the refrigerant supply path 170 of the cylinder block 100 is supplied to the refrigerant suction groove 140 through the connection flow path groove 180 and through the refrigerant discharge port R1 of the rotary valve R. It is discharged to the communication hole 130.
  • the coolant stored in the coolant storage chamber P1 flows back into the coolant suction groove 140 and the coolant discharge port R1. And it may move to the cylinder bore 110 through the communication hole 130.
  • the cylinder block 100 is formed in the vicinity of the outer circumferential surface in addition to the refrigerant suction groove 140 to form a refrigerant supply path 170 and a connection flow path groove 180 for moving the refrigerant, thereby allowing the refrigerant to the cylinder bore 110.
  • the volumetric efficiency of the compressor can be greatly improved by reducing the suction loss for discharging the gas.

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

Abstract

La présente invention concerne un compresseur à plateau oscillant avec soupape rotative pouvant siphonner efficacement un frigorigène dans une chambre de plateau oscillant par l'intermédiaire d'un bloc cylindres. Le compresseur à plateau oscillant comprend un boîtier relié au bloc cylindres, qui présente une pluralité d'alésages de cylindre, des pistons logés dans les alésages de cylindre respectifs et effectuant un mouvement de va-et-vient dans ceux-ci, un arbre d'entraînement installé de façon à tourner par rapport au boîtier et au bloc cylindres, un plateau oscillant installé de manière à être entraîné en rotation par l'arbre d'entraînement et à entrer en prise avec les pistons, une plaque porte-soupape intercalée entre le boîtier et le bloc cylindres, ainsi qu'une soupape rotative conçue pour tourner conjointement avec l'arbre d'entraînement et installée de manière à rouler dans un trou de joint ménagé dans le bloc cylindres. Une sortie de frigorigène est formée sur l'extérieur de la soupape rotative, des trous de raccordement reliés aux alésages de cylindre respectifs sont formés sur l'intérieur du trou de joint venant buter contre l'extérieur de la soupape rotative, et une rainure d'entrée de frigorigène est formée de façon à traverser l'intérieur de la chambre de plateau oscillant jusqu'au boîtier. Ainsi, la perte causée par la résistance à l'entrée de frigorigène peut être sensiblement réduite par siphonnage du frigorigène indépendamment du couple de l'arbre d'entraînement tournant à vitesse élevée.
PCT/KR2009/006870 2008-11-20 2009-11-20 Compresseur à plateau oscillant avec soupape rotative WO2010058998A2 (fr)

Priority Applications (1)

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CN200980153670.4A CN102272450B (zh) 2008-11-20 2009-11-20 具有旋转阀的斜盘式压缩机

Applications Claiming Priority (2)

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KR10-2008-0115742 2008-11-20
KR1020080115742A KR101001564B1 (ko) 2008-11-20 2008-11-20 로터리밸브를 장착한 사판식 압축기

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WO2010058998A2 true WO2010058998A2 (fr) 2010-05-27
WO2010058998A3 WO2010058998A3 (fr) 2010-07-29

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KR100624795B1 (ko) * 2004-09-14 2006-09-18 엘지전자 주식회사 권장 세제량 표시 기능을 갖는 세탁기의 제어 방법
KR101768934B1 (ko) * 2010-07-06 2017-08-18 학교법인 두원학원 사판식 압축기
CN102678864A (zh) * 2012-05-18 2012-09-19 中山市亚泰机械实业有限公司 斜盘式传动机构

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JP2000054955A (ja) * 1998-08-10 2000-02-22 Toyota Autom Loom Works Ltd 可変容量型圧縮機
KR20060035063A (ko) * 2004-10-20 2006-04-26 엘지전자 주식회사 가변 반경식 스크롤 압축기
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JP3018801B2 (ja) * 1992-12-24 2000-03-13 株式会社豊田自動織機製作所 往復動型圧縮機
TW400919U (en) * 1996-03-12 2000-08-01 Toyoda Automatic Loom Works Variable volume capacity typed compressor
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JP2000054955A (ja) * 1998-08-10 2000-02-22 Toyota Autom Loom Works Ltd 可変容量型圧縮機
KR20060035063A (ko) * 2004-10-20 2006-04-26 엘지전자 주식회사 가변 반경식 스크롤 압축기
KR20080072526A (ko) * 2007-02-02 2008-08-06 가부시키가이샤 도요다 지도숏키 양두 피스톤식 압축기

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CN102272450A (zh) 2011-12-07
KR20100056772A (ko) 2010-05-28
WO2010058998A3 (fr) 2010-07-29
KR101001564B1 (ko) 2010-12-17
CN102272450B (zh) 2015-05-06

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