WO2002040866A1 - Compresseur de type a plateau oscillant - Google Patents

Compresseur de type a plateau oscillant Download PDF

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Publication number
WO2002040866A1
WO2002040866A1 PCT/JP2000/008083 JP0008083W WO0240866A1 WO 2002040866 A1 WO2002040866 A1 WO 2002040866A1 JP 0008083 W JP0008083 W JP 0008083W WO 0240866 A1 WO0240866 A1 WO 0240866A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
piston
cylinder
type compressor
plate type
Prior art date
Application number
PCT/JP2000/008083
Other languages
English (en)
Japanese (ja)
Inventor
Shunji Muta
Nobuhiko Suzuki
Original Assignee
Zexel Valeo Climate Control Corporation
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 to JP26694499A priority Critical patent/JP2001090656A/ja
Application filed by Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Priority to PCT/JP2000/008083 priority patent/WO2002040866A1/fr
Publication of WO2002040866A1 publication Critical patent/WO2002040866A1/fr

Links

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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F04B27/0886—Piston shoes

Definitions

  • FIG. 5 is a longitudinal sectional view of a conventional swash plate type compressor.
  • the swash plate type compressor has a cylindrical port 110 formed with a plurality of cylinder holes 106. And a shaft h105 supported rotatably at the center of the cylindrical opening 101, and a tiltable tiltable movable shaft 105.
  • the swash plate 110 and the swash plate 110 are connected to the thrust flange 140 via a link mechanism 141 while being attached. Is connected to the swash plate 110 via a lug 150 that rotates relatively on the sliding surface 110a of the swash plate.
  • A) A plurality of pistons 107 sliding in the inside 106 are provided.
  • FIG. 6 is a partially enlarged view of FIG.
  • the shoe 150 supports the ball 111a at one end of the connecting rod 111 so as to be relatively rollable. Show 150 is the sliding surface of the swash plate 110 It is held by retainer 15 3.
  • Radial bearings are provided on the boss section 110b of the swash plate 110.
  • Rod section 1 1 1 1b at the other end of V-d 1 1 1 is fixed to piston 107
  • the shroud 150 is a dish-shaped shroud body 15 that supports the tip of the pole 11a of the connecting rod 1111 so that it can roll relatively. 1 and an annular disk 152 that supports the rear end face of the pole 1 11a of the connecting cut 11 1 1 so as to be relatively rotatable. ing .
  • the swash plate compressor operates as follows.
  • the rotating force is transmitted to the swash plate 110 via the storage flange 140 and the link mechanism 141.
  • the swash plate 110 rotates.
  • the rotation of the swash plate 110 causes the shoe 150 to rotate relative to the sliding surface 110a of the swash plate 110, and the rotational force from the swash plate 11 This is converted into a linear reciprocating motion of the tongue 107.
  • the suction, compression, and discharge of the refrigerant gas are performed sequentially according to the change in the volume, and the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 110 is discharged.
  • a compression reaction force of the refrigerant gas acts on the piston 107, so that the side load (piston is tilted) according to the inclination angle of the swash plate 110. (Falling load) F (see Fig. 7 (a)) occurs.
  • the present invention provides a swash plate type compressor which improves the slidability of the piston by reducing the side load and which can improve the reliability.
  • the purpose is. Disclosure of the invention
  • the present invention is directed to a cylinder block in which a plurality of cylinder pores are formed and a cylinder block in which the cylinder block is formed.
  • a rotating shaft rotatably supported at the center and a rotation according to the rotation of the rotating shaft
  • the swash plate is connected to the swash plate via a shaft that relatively rotates on a sliding surface of the swash plate, and the cylinder hole is rotated as the swash plate rotates.
  • a swash plate type compressor provided with a plurality of pistons sliding in the inside, a shudder that contacts the slide with a sliding surface of the swash plate.
  • Fig. 7 (a) is an anti-chamber model diagram illustrating the anti-force added to the piston in the conventional example
  • Fig. 7 (b) is the anti-piston model according to the present invention
  • FIG. 4 is an anti-chamber model diagram illustrating anti-mosquitoes added to a ton.
  • F indicates side load
  • R1 and R2 indicate resistance
  • the side load F is a force acting on spherical bodies (poles 11a, 50b), and the forces acting on each spherical body are equal.
  • R 2 is a drag acting on the top side of the piston,
  • the spherical body of the present invention (Fig. 7 (b)) is a conventional example (Fig. 7 (A) It is located closer to the rear. Therefore, in the present invention (FIG. 7 (b)), the distance between the point of action of the side load F and the point of action of the resistance R1, that is, the distance b, is reduced. In this case, since the distance a is equal to that of the conventional example, it can be seen from the equation (2) that the resistance R 1 is smaller than that of the conventional example. Further, when the resistance R1 is smaller than the conventional example, it is understood from the expression (1) that the resistance R2 is smaller than the conventional example.
  • the distance b between the point of action of the side load F and the point of action of the anti-force R 2 acting on the top side of the piston becomes shorter, and in particular, the distance of the piston The anti-power R 2 acting on the top side is greatly reduced.
  • the spherical body is supported by the bottom portion of the piston through a dasher. 'Since the spherical body is pressed onto the piston's bottom part via the dash, it is necessary to assemble the chassis into the piston beforehand. It is also good. For this reason, swash plate compression The machine can be easily manufactured.
  • FIG. 1 is a longitudinal sectional view showing an entire swash plate type compressor according to a second embodiment of the present invention.
  • FIG. 2 is a partially enlarged view of FIG.
  • Fig. 3 (a) is a side view of the shoe
  • Fig. 3 (b) is a front view of the shower
  • Fig. 3 (c) is a perspective view of the shower.
  • FIG. 4 is a partially enlarged view of a swash plate type compressor according to a second embodiment of the present invention.
  • FIG. 5 is a longitudinal sectional view of a conventional swash plate type compressor.
  • FIG. 6 is a partially enlarged view of FIG.
  • Fig. 7 (a) is an anti-chamber model diagram illustrating the anti-force added to the piston in the conventional example
  • Fig. 7 (b) is the anti-piston model according to the present invention
  • FIG. 2 is an anti-chamber model diagram illustrating anti-mosquitoes added to the ton. The best form to carry out the invention
  • FIG. 1 is a longitudinal sectional view showing the whole of a swash plate type compressor according to a first embodiment of the present invention.
  • This swash plate compressor is C 0 2 Shi Li down da blanking lock one component and to this have found that Ru use in the swash plate type compressor of the refrigeration apparatus shall be the (carbon dioxide) the refrigerant 1 end face
  • a head 3 is arranged via a valve plate 2 and a front head 4 is arranged on the other end surface.
  • the front head 4, the cylinder opening 1, the valve plate 2 and the rear head 3 pass through the port 31 and the shaft (rotation) (Shaft) 5 is integrally connected to the center axis direction
  • a plurality of cylinder pores 6 are formed in the cylinder opening 1 at predetermined intervals along a circumference centered on the shaft 5. .
  • a piston 7 is slidably inserted into each of the cylinder pores 6.
  • the front head 4 has a crank chamber 8 for accommodating a swash plate 10 and a thrust flange 40, which will be described later.
  • a suction chamber 13 and a discharge chamber 12 are formed in the lid head 3.
  • the suction chamber 13 is located around the discharge chamber 12.
  • the low pressure refrigerant gas sent to the compression chamber 22 is accommodated in the suction chamber 13.
  • the discharge chamber 12 contains the high-pressure refrigerant gas discharged from the compression chamber 22.
  • the discharge chamber 12 communicates with the discharge P3a via the communication passage 60.
  • Valve plates 2 are provided at predetermined intervals along the circumferential direction, respectively.
  • the discharge port 16 is opened and closed by the discharge valve 17, and the discharge valve 17 is pressed against the end face of the knob plate 2 on the rear head side 18 Both are fixed by Port 19.
  • suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is arranged on the front end face of the normal plate 2. .
  • One end of the shaft 5 is rotatably supported on the front head 4 via a radial bearing 26, and the other end of the shaft 5 is radial. It is rotatably supported by the cylinder block 1 via the bearing 25 and the thrust bearing 24. .
  • the swash plate 10 is attached to the shaft 5 so as to be inclined and slidable.
  • the swash plate 10 is connected to the thrust flange 40 via a link mechanism 41, and rotates as the thrust flange 40 rotates. They rotate together.
  • the thrust flange 40 fixed to the front end of the shaft 5 is connected to the front head 4 via a thrust bearing 33. It is rotatably supported on the inner wall. As described above, the thrust flange 40 and the swash plate 10 are connected via the link mechanism 41, and the swash plate 10 is at a right angle to the shaft 5. It can be tilted with respect to the virtual plane.
  • the link mechanism 41 is connected to the front end face 1 of the swash plate 10.
  • a pair of protrusions 10 d provided at 0 c and a Between the arm 40a provided on the swash plate side end face 40c of the to flange 40 and the projecting portion 10d k: It is bridged and the arm 40 and a connecting pin 43 engaged with the elongated hole 40b of the a.
  • a winding spring 47 is mounted between the thrust flange 40 and the swash plate 10, and the swash plate 10 is moved by the biasing force of the winding spring 47.
  • the plate spring 48 is urged toward the side, and a countersink 48 is mounted between the thrust bearing 24 and the swash plate 10. 0 is biased to the front.
  • FIG. 2 is a partially enlarged view of FIG.
  • the table 50 is composed of a shadow disk 50a, a pole (spherical body) 50b, and a rod (connecting portion) 50c. .
  • the new disk 50a contacts the sliding surface 10a of the swash plate 10 and is held by the retainer 53.
  • a radial bearing 55 is mounted on the post portion 10b of the swash plate 10, and the retainer 53 can rotate relative to the swash plate 10. . Further, the radial bearing 55 is stopped by a stopper 54 fixed to the boss 10b.
  • the pole 5 Ob is supported by the pot portion 7 a of the piston 7 so as to be able to relatively rotate.
  • the port 50b is mounted on the bottom 7a of the piston 7.
  • Rod 50c is connected to the show disk 50a and the pole. 50 b and are connected.
  • Figure 3 (a) is a side view of the show
  • Figure 3 (b) is an excerpt.
  • FIG. 3 (c) is a perspective view of the show.
  • swash plate 0 causes the sh — 50 (new disk 50 a) to rotate relative to the sliding surface 10 a of swash plate 10, and the rotational force from swash plate 0 Is converted to the linear reciprocating motion of piston 7.
  • the volume of the compression chamber 22 in the cylinder 6 changes, and the suction and compression of the refrigerant gas are performed by this volume increase. Then, the refrigerant gas is discharged, and the refrigerant gas having a high volume corresponding to the inclination angle of the swash plate 10 is discharged.
  • the suction valve 21 is opened, low-pressure refrigerant is sucked from the suction chamber 13 into the compression chamber 22 of the cylinder 6, and the discharge valve 17 at the time of discharge is opened. High-pressure refrigerant gas is discharged from the compression chamber 22 to the discharge 12.
  • the compression reaction force of the refrigerant gas acts on the swash plate 10 via the pole 50b, the rod 50c and the shadow disk 50a. Since the refrigerant is CO 2 , the compression reaction is greater than when the refrigerant is fluorinated as described above.
  • the pole 50b is force-strained relative to the bottom 7a of the piston 7 so that the pole 50b is rotatable, and the pole 50b is a conventional example. Because it is located on the rear side as compared to the top, the anti-power R1 and the piston 7 that act on the piston 7 at the opening edge of the cylinder 6 The anti-mouse R 2 acting on b is reduced.
  • the distance b between the point of action of the side load F and the point of action of the drag R 2 is shorter than that of the conventional example (see FIG. 6), so that the pi The resistance R 2 acting on the top portion 7 b of the ton 7 is greatly reduced, and is caused by the sliding friction between the piston 7 and the cylinder 6.
  • the wear and peeling of the thin film on the outer surface of the piston 7 are reduced, and the durability is improved.
  • the friction loss when the piston 7 slides inside the cylinder 6 is reduced, and the sliding characteristic of the piston 7 is improved.
  • Driving force can be reduced, and performance and reliability are improved.
  • FIG. 4 is a partially enlarged view of a swash plate type compressor according to a second embodiment of the present invention.
  • the same parts as those in the first embodiment are denoted by the same reference numerals and the description is given. Omitted.
  • the port 50b of the shower 50 when the port 50b of the shower 50 is attached to the port portion 97a of the piston 97, the port 50b is closed. It differs from the first embodiment in that the shaft 56 supports the piston 97 on the port portion 97a of the piston 97.
  • the pedestal 56 is caulked and supported on the bottom part 97a of the piston 97, but the pedestal 56 A male screw is formed on the outer peripheral surface of the nut and a female screw is formed on the inner peripheral surface of the pot portion 977a, and the zipper 56 is screwed into the pot portion 977a.
  • the pusher 56 may be supported by the bottom 97 a of the piston 97.
  • the swash plate type compressor according to the present invention is C-type. 0 2 Ri Oh useful as the use of Medical Ru car dual-purpose refrigerant compressor as a refrigerant, if Re good to the call of the swash plate type compressor, the sliding of the bi-scan tons in Tsu by the reduction of side load It can improve the reliability and improve the reliability.

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

Abstract

L'invention concerne un compresseur de type à plateau oscillant pourvu d'un bloc-cylindres (1) comportant une pluralité d'alésages (6), d'un arbre supporté rotatif sur le bloc cylindre (1) au niveau d'une partie centrale, d'un plateau oscillant (10) tournant conformément à la rotation de l'arbre, et d'une pluralité de pistons (7) raccordés au plateau oscillant (10) par l'intermédiaire de patins (50) mis en rotation respective sur la surface de glissement (10a) du plateau oscillant (10) et coulissant dans les alésages (6) conformément à la rotation dudit plateau oscillant (10). Le patin (50) comprend également un disque de patin (50a), une sphère (50b) et une tige (50c) destinée à raccorder le disque de patin (50a) à la sphère (50b), ce disque de patin (50a) étant amené au contact de la surface de glissement (10a) du plateau oscillant (10) et la sphère étant supportée sur une partie inférieure (7a) du piston (7), d'où un mouvement de pivotement réciproque. Une distance entre un point d'application d'une charge latérale (F) et un point d'application d'une force de résistance (R2) agissant sur une partie supérieure (7b) du piston (7) est réduite en vue de diminuer sensiblement la force de résistance (R2) agissant sur la partie supérieure (7b) dudit piston (7).
PCT/JP2000/008083 1999-09-21 2000-11-16 Compresseur de type a plateau oscillant WO2002040866A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP26694499A JP2001090656A (ja) 1999-09-21 1999-09-21 斜板式圧縮機
PCT/JP2000/008083 WO2002040866A1 (fr) 1999-09-21 2000-11-16 Compresseur de type a plateau oscillant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP26694499A JP2001090656A (ja) 1999-09-21 1999-09-21 斜板式圧縮機
PCT/JP2000/008083 WO2002040866A1 (fr) 1999-09-21 2000-11-16 Compresseur de type a plateau oscillant

Publications (1)

Publication Number Publication Date
WO2002040866A1 true WO2002040866A1 (fr) 2002-05-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2000/008083 WO2002040866A1 (fr) 1999-09-21 2000-11-16 Compresseur de type a plateau oscillant

Country Status (2)

Country Link
JP (1) JP2001090656A (fr)
WO (1) WO2002040866A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007198249A (ja) * 2006-01-26 2007-08-09 Sanden Corp 斜板式圧縮機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5742180U (fr) * 1980-08-14 1982-03-08
JPS59150987A (ja) * 1983-02-17 1984-08-29 Diesel Kiki Co Ltd 揺動板式ピストンポンプ
JPH1047231A (ja) * 1996-08-02 1998-02-17 Zexel Corp 可変容量型圧縮機
JPH10220355A (ja) * 1997-02-05 1998-08-18 Denso Corp 斜板型圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5742180U (fr) * 1980-08-14 1982-03-08
JPS59150987A (ja) * 1983-02-17 1984-08-29 Diesel Kiki Co Ltd 揺動板式ピストンポンプ
JPH1047231A (ja) * 1996-08-02 1998-02-17 Zexel Corp 可変容量型圧縮機
JPH10220355A (ja) * 1997-02-05 1998-08-18 Denso Corp 斜板型圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007198249A (ja) * 2006-01-26 2007-08-09 Sanden Corp 斜板式圧縮機
JP4562661B2 (ja) * 2006-01-26 2010-10-13 サンデン株式会社 斜板式圧縮機

Also Published As

Publication number Publication date
JP2001090656A (ja) 2001-04-03

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