EP1462651A1 - Kolbenkompressor - Google Patents

Kolbenkompressor Download PDF

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Publication number
EP1462651A1
EP1462651A1 EP04007411A EP04007411A EP1462651A1 EP 1462651 A1 EP1462651 A1 EP 1462651A1 EP 04007411 A EP04007411 A EP 04007411A EP 04007411 A EP04007411 A EP 04007411A EP 1462651 A1 EP1462651 A1 EP 1462651A1
Authority
EP
European Patent Office
Prior art keywords
gasket
hole
cylinder block
imaginary circle
center
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.)
Withdrawn
Application number
EP04007411A
Other languages
English (en)
French (fr)
Inventor
Yoshio Kimoto
Sokichi Hibino
Yoshitami Kondo
Atsuyuki Morishita
Tomohiro Murakami
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1462651A1 publication Critical patent/EP1462651A1/de
Withdrawn legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to a piston compressor for a vehicular air conditioner and, more particularly, to a technology for restraining deformation of a cylinder block.
  • Japanese Laid-Open Patent Publication No. 8-14160 discloses a gasket 101 as shown in Fig. 13.
  • the gasket 101 is used for a piston compressor for a vehicular air conditioner.
  • the gasket 101 is formed with a plurality of through holes 103 that substantially coincide with opening edges of cylinder bores 102 each containing a piston, a plurality of insertion holes 105 through which through bolts 104 are inserted, and a center hole 106 through which a drive shaft is inserted.
  • a piston compressor provided with this gasket 101, a piston compressor is known in which as shown in a partially enlarged cross-sectional view of Fig.
  • a front housing member 108 is joined to a front end face (left-hand side in the figure) of a cylinder block 107
  • a rear housing member 110 is joined to a rear end face (right-hand side in the figure) thereof via a valve plate 109, and these three elements are fastened to each other by the through bolts 104.
  • the gasket 101 is interposed between the cylinder block 107 and the valve plate 109.
  • the cylinder block 107 is formed with the cylinder bores 102 and an accommodation chamber 111 for accommodating a rotary valve for sucking refrigerant gas.
  • the accommodation chamber 111 for the rotary valve is formed in the cylinder block 107 as shown in Fig. 15, the accommodation chamber 111 is easily deformed because the rigidity of the cylinder block 107 is low. Therefore, smooth rotation of the rotary valve can be hindered.
  • An object of the present invention is to provide a piston compressor in which bending moment acting on a cylinder block is reduced to restrain deformation of the cylinder block, and the motion of a piston and a rotary valve is performed smoothly to enhance the durability of the piston compressor.
  • a piston compressor having a cylinder block, a front housing member, a rear housing member, a through bolt, a plurality of pistons, a drive shaft, and a gasket.
  • the cylinder block has a plurality of cylinder bores.
  • the cylinder block has two end faces at which the cylinder bores open.
  • the front housing member is secured to one of the end faces of the cylinder block.
  • the rear housing member is secured to the other one of the end faces of the cylinder block with a valve plate in between.
  • the through bolt fastens the cylinder block, the rear housing member, and the front housing.
  • Each piston is accommodated and reciprocates in one of the cylinder bores.
  • the drive shaft drives the pistons, and is rotatably supported by the cylinder block. Reciprocation of the pistons compress and discharge refrigerant gas.
  • the gasket is located between the cylinder block and the valve plate.
  • the gasket has a center hole and a plurality of bore holes. Each bore hole is aligned with one of the cylinder bores.
  • a first through hole is formed in the gasket to reduce bending moment generated in the cylinder block when the through bolt is fastened.
  • the first through hole is located between an adjacent pair of the bore holes and in an imaginary circle.
  • the center of the imaginary circle coincides with the center of the bore hole, and the radius of the imaginary circle is a first radius.
  • the first radius is the distance from the center of the gasket to the center of one of the bore holes.
  • a front housing member 3 is joined to a front end face of a cylinder block 1 via a gasket 2, and a crank chamber 4 serving as a control chamber is defined on the inside thereof.
  • a rear housing member 6 is joined to a rear end face of the cylinder block 1 via a valve plate 5, and a discharge chamber 7 and a suction chamber 8 are defined on the inside thereof.
  • a gasket 9 Between the cylinder block 1 and the valve plate 5 is interposed a gasket 9, and between the valve plate 5 and the rear housing member 6 are interposed a discharge valve forming plate 10 formed integrally with a discharge valve and a retainer forming plate 11 for forming a retainer.
  • the cylinder block 1, the front housing member 3, and the rear housing member 6 are fastened by through bolts 12, not shown in Fig. 1.
  • a drive shaft 13 is rotatably supported by radial bearings 14a and 14b.
  • a shaft seal device 15 In a front end portion of the drive shaft 13 is provided a shaft seal device 15.
  • a lug plate 16 In the crank chamber 4, a lug plate 16 is fixed to the drive shaft 13 so as to be integrally rotatable, and a swash plate 17 serving as a cam plate is disposed in a state in which the drive shaft 13 is inserted through a through hole formed in the swash plate 17.
  • a hinge mechanism 18 is interposed between the lug plate 16 and the swash plate 17.
  • the swash plate 17 can be rotated in synchronism with the lug plate 16 and the drive shaft 13 by a hinge connection between the swash plate 17 and the lug plate 16 via the hinge mechanism 18 and the support of the drive shaft 13, and also can be tilted with respect to the drive shaft 13 while sliding in an axial direction of the drive shaft 13.
  • a plurality of cylinder bores 19 arranged in a circumferential direction in the cylinder block 1 each contain a piston 20 capable of reciprocating. Between each piston 20 and the valve plate 5, a compression chamber 21 whose volume is changed according to reciprocating motion of the piston 20 is defined. Each piston 20 is engaged with a peripheral edge portion of the swash plate 17 via a pair of shoe 22. Therefore, rotational motion of the swash plate 17 performed via the lug plate 16 and the hinge mechanism 18, which is caused by rotation of the drive shaft 13, is converted to reciprocating motion of the pistons 20 performed via the shoes 22.
  • the lug plate 16, the swash plate 17, the hinge mechanism 18, and the shoes 22 constitute a crank mechanism that converts the rotational motion of the drive shaft 13 to compressive motion for compressing refrigerant gas in the compression chamber 21.
  • a rotary valve accommodating chamber 23 is formed in the cylinder block 1, and in the rotary valve accommodating chamber 23, a rotary valve 24 is connected to the drive shaft 13 via a coupling 25 so as to be rotatable in synchronism with the drive shaft 13.
  • a suction passage 26 that always communicates with the suction chamber 8 is formed, and an outlet 27 of the suction passage 26 is open in an outer peripheral surface of the rotary valve 24.
  • communication holes 28 are formed in the cylinder block 1, communication holes 28 are formed. Each communication hole corresponds to one of the compression chambers 21 and allows the outlet 27 of the rotary valve 24 to communicate with the corresponding compression chamber 21.
  • a specific pressure f1 acts on a front end face of the cylinder block 1 from the front housing member 3.
  • a specific pressure f2 acts on a rear end face of the cylinder block 1 from the gasket 9.
  • action point P1 Taking one arbitrary point on the front end face of the cylinder block 1, on which the specific pressure f1 acts, as action point P1, and taking one arbitrary point on the rear end face of the cylinder block 1, on which the specific pressure f2 acts, as action point P2, bending moment M acts around the center P3 of straight line H connecting P1 and P2.
  • the gasket 9 in this embodiment is shown in Fig. 3.
  • the gasket 9 is formed of a rigid base consisting of an iron-base metallic sheet and an elastic layer having sealing ability, such as rubber, with which both surfaces of the base are coated.
  • the gasket 9 has a plurality of (six in this embodiment) bore holes 29 that substantially coincide with the opening edges of the cylinder bores 19 and a plurality of (six in this embodiment) bolt holes 30 through which the through bolts 12 are inserted.
  • a through hole is formed which corresponds to a center hole 31 (in a circle indicated by dotted line in Fig.
  • Fig. 4 shows a conventional gasket 34 formed with bore holes 29, bolt holes 30, and a center hole 31.
  • solid line hatched portions are seal portions that are necessary for function of sealing the bore holes 29, the bolt holes 30, and the interior of the compressor. That is to say, in the gasket 34, the range excluding the solid line hatched portions, the bore holes 29, the bolt holes 30, and the center hole 31 (dotted line hatched portions in Fig. 4) indicates portions that are unnecessary for the function of the gasket.
  • the length of seal portions that are necessary for the function on the circumference of a circle whose radius is a certain distance x from the center O of the gasket 34 and the length of seal portions that are unnecessary for the function on the circumference of a circle whose radius is a certain distance x from the center O are represented by graphs of Figs. 5 and 6, respectively.
  • Rg indicates the radius of the gasket 34.
  • a complement is given to the description of "the length of seal portions on the circumference of a circle whose radius is a certain distance x from the center O of the gasket 34".
  • Lb L2 + L4 + L6 + L8 + L10 + L12
  • an area S of seal portions of the gasket 34 is calculated by the following formula (3).
  • the function f(x) is a function for the graph of Fig. 5
  • the function g(x) is a function for the range of 0 ⁇ x ⁇ Rb in the graph of Fig. 6
  • the function h(x) is a function for the range of Rb ⁇ x ⁇ Rg in the graph of Fig. 6.
  • the total pressure F depends on the tightening force of bolt, and the shape, rigidity of the cylinder block and rear housing member, and it is thought that the total pressure F in this embodiment is equivalent to that of the conventional compressor.
  • ⁇ f2 F/S(x) - F/S using the above-described formulae (4) and (5).
  • ⁇ M is expressed by a graph shown in Fig. 7 using Formulae (6) and (7).
  • Fig. 7 means that if through holes are formed in a circle with the radius Rc from the center O, since the decrease in bending moment due to the through holes is larger than the increase in bending moment due to increased specific pressure, the total bending moment can be decreased.
  • a seal portion for sealing the compressor internally and externally is provided in an outer peripheral portion of the gasket 9.
  • bending moment is not generated on a joint surface 35 between the cylinder block 1 and the gasket 9, which faces a joint surface between the cylinder block 1 and the front housing member 3 in the axial direction of the drive shaft 13. Therefore, it is desirable that the gasket 9 be formed with a seal surface in the range of the joint surface 35 so as to decrease the specific pressure ⁇ f2 as much as possible.
  • the bending moment acting on the cylinder block 1 is reduced, and hence the deformation of the cylinder block 1 is restrained.
  • the deformation of the cylinder bore 19 is restrained, and hence the reciprocating motion of the piston 20 is made smooth.
  • the deformation of the rotary valve accommodating chamber 23 for the rotary valve 24 is restrained, and hence the rotational motion of the rotary valve 24 is made smooth.
  • the specific pressure of gasket is increased by reducing the seal surface, so that the sealing ability of gasket is improved, or sufficient sealing ability of gasket is secured even if the tightening force of bolts is decreased as compared with the conventional compressor. Therefore, the deformation of the cylinder block 1 can further be restrained by the decrease in bolt tightening force, and hence the durability of compressor is enhanced.
  • Fig. 8 shows a five-cylinder compressor.
  • the rotary valve 24 and the rotary valve accommodating chamber 23 are not used as a suction structure for refrigerant gas, and instead a suction valve forming plate 36 is interposed between the cylinder block 1 and the valve plate 5, and a gasket 37 is interposed between the suction valve forming plate 36 and the cylinder block 1.
  • a suction valve forming plate 36 is interposed between the cylinder block 1 and the valve plate 5
  • a gasket 37 is interposed between the suction valve forming plate 36 and the cylinder block 1.
  • Fig. 10 shows a conventional gasket 39 used for a five-cylinder piston compressor.
  • hatched portions are seal portions that are necessary for function of sealing the bore holes 29, the bolt holes 30, and the interior of the compressor.
  • seal portions that are unnecessary for the function are present even between the adjacent bore holes 29.
  • the integral through hole 38 it is possible to form the integral through hole 38 by allowing the center hole 31, the first through holes, and the second through holes to communicate with each other. Thereby, the bending moment is reduced, and resultantly the deformation of the cylinder block 1 is restrained. Also, by forming the integral through hole 38 in this manner, a mold necessary for manufacturing the gasket 37 is formed easily, and the life of mold is extended, which also achieves an effect of reducing the manufacturing cost.
  • the center hole 31 and the first through holes 32 may be separated from each other.
  • the deformation of the cylinder block is restrained by reducing bending moment, and hence the motion of the piston and rotary valve is made smooth, by which the durability of the piston compressor is enhanced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP04007411A 2003-03-27 2004-03-26 Kolbenkompressor Withdrawn EP1462651A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003087295 2003-03-27
JP2003087295A JP2004293421A (ja) 2003-03-27 2003-03-27 ピストン式圧縮機

Publications (1)

Publication Number Publication Date
EP1462651A1 true EP1462651A1 (de) 2004-09-29

Family

ID=32821535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04007411A Withdrawn EP1462651A1 (de) 2003-03-27 2004-03-26 Kolbenkompressor

Country Status (6)

Country Link
US (1) US20040247455A1 (de)
EP (1) EP1462651A1 (de)
JP (1) JP2004293421A (de)
KR (1) KR20040086130A (de)
CN (1) CN1294358C (de)
BR (1) BRPI0401434A (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7004734B2 (en) * 1999-12-28 2006-02-28 Zexel Valco Climate Control Corporation Reciprocating refrigerant compressor
JP2008064035A (ja) * 2006-09-07 2008-03-21 Toyota Industries Corp ピストン式圧縮機
JP2011163177A (ja) * 2010-02-08 2011-08-25 Sanden Corp 往復動型圧縮機
KR20200059555A (ko) * 2018-11-21 2020-05-29 엘지전자 주식회사 실린더 블록을 포함하는 압축기

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5556261A (en) * 1994-06-27 1996-09-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
US5782613A (en) * 1995-03-20 1998-07-21 Kabushiki Kaisha Toyoda Jodoshokki Seisakusho Piston type compressor with structure for reducing cylinder bore deformation
US6158974A (en) * 1997-03-25 2000-12-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating compressor
US6231315B1 (en) * 1996-06-24 2001-05-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor having a value plate and a gasket
US6454545B1 (en) * 1996-11-25 2002-09-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2102496A5 (de) * 1970-08-05 1972-04-07 Paulstra Sa
DE2453688A1 (de) * 1974-11-13 1976-05-20 Helmut Hartz Elastische kupplung
JPH11343974A (ja) * 1998-05-29 1999-12-14 Toyota Autom Loom Works Ltd 往復動型圧縮機
FR2793188A1 (fr) * 1999-05-06 2000-11-10 Michelin Soc Tech Element moulant et moule pour le moulage d'une decoupure dans une bande de roulement

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5556261A (en) * 1994-06-27 1996-09-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
US5782613A (en) * 1995-03-20 1998-07-21 Kabushiki Kaisha Toyoda Jodoshokki Seisakusho Piston type compressor with structure for reducing cylinder bore deformation
US6231315B1 (en) * 1996-06-24 2001-05-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor having a value plate and a gasket
US6454545B1 (en) * 1996-11-25 2002-09-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor
US6158974A (en) * 1997-03-25 2000-12-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating compressor

Also Published As

Publication number Publication date
KR20040086130A (ko) 2004-10-08
US20040247455A1 (en) 2004-12-09
CN1294358C (zh) 2007-01-10
CN1534191A (zh) 2004-10-06
BRPI0401434A (pt) 2005-01-18
JP2004293421A (ja) 2004-10-21

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