US20030138336A1 - Muffler for compressor - Google Patents

Muffler for compressor Download PDF

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Publication number
US20030138336A1
US20030138336A1 US09/897,169 US89716901A US2003138336A1 US 20030138336 A1 US20030138336 A1 US 20030138336A1 US 89716901 A US89716901 A US 89716901A US 2003138336 A1 US2003138336 A1 US 2003138336A1
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US
United States
Prior art keywords
chamber
compressor according
drive shaft
muffler
cylinder block
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.)
Abandoned
Application number
US09/897,169
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English (en)
Inventor
Yoshiyuki Nakane
Naoya Yokomachi
Kazuo Murakami
Tatsuya Koide
Yumin Hishinuma
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
Individual
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 Individual filed Critical Individual
Assigned to KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO reassignment KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HISHINUMA, YUUMIN, KOIDE, TATSUYA, MARAKAMI, KAZUO, NAKANE, YOSHIYUKI, YOKOMACHI, NAOY
Assigned to KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO reassignment KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HISHINUMA, YUUMIN, KOIDE TATSUYA, MURAKAMI, KAZUO, NAKANE, YOSHIYUKI, YOKOMACHI, NAOYA
Publication of US20030138336A1 publication Critical patent/US20030138336A1/en
Abandoned 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes

Definitions

  • the present invention relates to a compressor, for example, for use in an automobile climate control system, and more particularly to substantially reducing pulsations of refrigerant in compressors.
  • a typical compressor includes a swash plate double-headed piston type disclosed in, for example, Japanese Unexamined Patent Publication No. 8-261147.
  • a front housing is secured to a front end face of a front cylinder block through a valve plate
  • a rear housing is secured to a rear end face of a rear cylinder block through another valve plate.
  • a suction chamber and a discharge chamber are defined in each housing.
  • the cylinder blocks and the housings constitute a housing body.
  • a drive shaft is rotatably supported in center bores of both the cylinder blocks.
  • a plurality of cylinder bores is formed in the cylinder blocks around the drive shaft, and a piston is accommodated in each of the cylinder bore.
  • a crank chamber is formed between the front and rear cylinder blocks.
  • a swash plate is fixed on the drive shaft in the crank chamber and is in contact with each piston through a pair of shoes. As the drive shaft is rotated, the rotation of the swash plate is transmitted to each piston through the shoes, and each piston is reciprocated in the cylinder bores.
  • a muffler chamber is formed at a rear end of the drive shaft in the cylinder block. The muffler chamber communicates with a discharge chamber in the rear housing through a passage formed in the rear housing. With the reciprocating motion of the piston, the refrigerant in suction chambers opens flap suction valves and is drawn into the cylinder bores.
  • the compressed refrigerant in the cylinder bores opens flap discharge valves and is discharged to the discharge chambers.
  • the refrigerant in the discharge chambers is discharged to an external refrigerant circuit through the muffler chamber.
  • the muffler chamber functions to reduce pulsations of the refrigerant. Consequently, noise and vibrations are suppressed.
  • Japanese Unexamined Utility Model Publication No. 63-143776 discloses a double-headed piston type swash plate compressor with an external muffler.
  • the compressor has an external muffler chamber that is connected to discharge chambers through discharge passages formed between the cylinder bores in the cylinder block and is isolated from a crank chamber.
  • the compressor has almost the same construction as the swash plate compressor of a double-headed piston type according to Japanese Unexamined Patent Publication No. 8-261147 except for the external muffler chamber which increases the compressor in size. Accordingly, the pressure pulsations are reduced as the double-headed piston type swash plate compressor according to Japanese Unexamined Utility Model Publication No. 63-143776.
  • a muffler chamber is arranged at the rear of the drive shaft in a cylinder block.
  • CO 2 is applied as a refrigerant in a single-headed piston type compressor
  • following problems will occur.
  • the drive shaft is pressed to a front side when discharge pressure is introduced into the muffler chamber.
  • the single-headed piston type compressor the drive shaft is always pressed frontward by compressive reaction force through the pistons and the swash plate.
  • a large load acts on a thrust bearing arranged between a rotor and the front housing. Such an excessive load shortens the life of the thrust bearing.
  • the rear side of the drive shaft with respect to the swash plate is shortened because the muffler chamber occupies the same space. That is, the drive shaft portion supported in the cylinder block is not only limited in length, but also the distance between the swash plate and a radial bearing is reduced. Therefore, large force acts on the radial bearing. Accordingly, such a compressor needs a radial bearing in high strength.
  • the object of the present invention is to provide a compressor in which pressure pulsations can be reduced even when a compressor has high-pressure refrigerant such as CO 2 .
  • a compressor includes a cylinder block, a chamber housing, a drive shaft, a piston, and a cam mechanism.
  • the cylinder block has a plurality of cylinder bores and a muffler chamber.
  • the muffler chamber is formed within said cylinder block in a space between the cylinder bores.
  • the chamber housing is secured to one end of the cylinder block and has at least a pair of a suction chamber and a discharge chamber located near each of the cylinder bores.
  • the discharge chamber communicates with the muffler chamber.
  • the drive shaft is rotatably supported in the cylinder block.
  • the piston is disposed in each of the cylinder bores for compressing gas to generate compressed gas.
  • the cam mechanism converts rotation of the drive shaft to reciprocating movement of the piston.
  • FIG. 1 is a diagram in a cross-sectional view illustrating a first embodiment of the compressor according to the present invention
  • FIG. 1( a ) is an enlarged cross-sectional view as seen from line Ia-Ia in FIG. 1;
  • FIG. 1( b ) is an enlarged cross-sectional view as seen from line Ib-Ib in FIG. 1;
  • FIG. 2 is a diagram in a cross-sectional view illustrating a second embodiment of the compressor according to the present invention.
  • a swash plate 11 functioning as a cam mechanism is accommodated in a swash plate housing 12 .
  • the swash plate housing 12 is secured between one end of a cylinder block 13 and a motor housing 15 .
  • a chamber housing 14 is secured to the other end of the cylinder block 13 .
  • the motor housing 15 , the swash plate housing 12 , the cylinder block 13 and the chamber housing 14 are fixedly bolted by a plurality of bolts 10 which are not shown in FIG. 1 but in FIGS. 1 ( a ) and 1 ( b ).
  • a drive shaft 16 is rotatably supported in the cylinder block 13 and the motor housing 15 respectively by radial bearings 17 and 18 .
  • the drive shaft 16 extends through a support hole 132 formed in the cylinder block 13 , and the radial bearing 17 placed in the support hole 132 supports the drive shaft 16 .
  • the drive shaft 16 extends through a support hole 151 formed in the motor housing 15 , and the radial bearing 18 placed in the support hole 151 supports the drive shaft 16 which extends through an end wall 121 of the swash plate housing 12 .
  • the swash plate 11 is fixedly placed on the drive shaft 16 in the swash plate housing 12 .
  • a stator 19 is mounted on an inner surface of the motor housing 15 .
  • a rotor 20 is mounted on the drive shaft 16 .
  • the drive shaft 16 and the rotor 20 may be fixed to each other by press-fitting or key-fitting.
  • the rotor 20 rotates by generating electricity to the stator 19 .
  • the drive shaft 16 rotates integrally with the rotor 20 .
  • the stator 19 and the rotor 20 constitute a motor 21 .
  • a plurality (four in the embodiment) of cylinder bores 131 is formed in the cylinder block 13 .
  • the cylinder bores 131 are arranged around the drive shaft 16 at an equal distance.
  • a single-headed piston 22 is accommodated in each of the cylinder bores 131 .
  • the piston 22 is engaged with the swash plate 11 through a pair of shoes 23 . Accordingly, as the drive shaft 16 is rotated, the movement in the axial direction at a distal end of the swash plate 11 is transmitted to each piston 22 through the shoes 23 , and consequently, the piston 22 is reciprocated in the cylinder bore 131 .
  • a thrust bearing 29 is arranged between a boss portion 111 of the swash plate 11 and the end wall 121 of the swash plate housing 12 to surround the drive shaft 16 .
  • the reciprocating movement of the piston 22 produces compressive reaction force.
  • the compressive reaction force is received by the end wall 121 through the pistons 22 , the shoes 23 , the swash plate 11 and the thrust bearing 29 .
  • a thrust bearing 30 and a spring 31 are arranged between the boss portion 111 and the radial bearing 17 in the support hole 132 to surround the drive shaft 16 .
  • the spring 31 urges the swash plate 11 and the drive shaft 16 towards the motor housing 15 through the thrust bearing 30 .
  • the urging force of the spring 31 is received by the end wall 121 through the thrust bearing 30 , the swash plate 11 and the thrust bearing 29 .
  • a valve plate 24 and a suction valve plate 25 are arranged between the chamber housing 14 and the cylinder block 13 .
  • a suction chamber 142 and a discharge chamber 143 are defined in the chamber housing 14 .
  • a discharge valve plate 26 and a retainer plate 27 are caulked to the valve plate 24 in the discharge chamber 143 by pins 28 which are not shown in FIG. 1 but in FIG. 1( a ).
  • suction ports 241 are formed so that the suction chambers 142 and the cylinder bores 131 are connected with each other.
  • discharge ports 242 are formed so that the discharge chambers 143 and the cylinder bores 131 are connected with each other.
  • suction valves 251 are formed on the suction valve plate 25 .
  • discharge valves 261 are formed on the discharge valve plate 26 .
  • the suction valves 251 open and close the suction ports 241 .
  • the discharge valves 261 open and close the discharge ports 242 .
  • a muffler chamber 34 includes at least one recess.
  • a first recess 134 which is opened to the chamber housing 14 is formed in the cylinder block 13 and is isolated from the support hole 132 in which the drive shaft 16 is inserted and the cylinder bore 131 .
  • a second recess 144 which is opened to the cylinder block 13 is optionally formed in the chamber housing 14 .
  • a muffler port is formed on the valve plate 24 and on the suction valve plate 25 to communicate the first recess 134 with the second recess 144 .
  • Both the first and second recesses 134 and 144 are connected via the muffler port when the cylinder block 13 is integrally secured to the chamber housing 14 .
  • the muffler chamber 34 is formed to include the first and second recesses 134 and 144 .
  • the discharge passage 145 crosses the muffler chamber 34 .
  • the muffler chamber 34 communicates with a pair of the discharge chambers 143 and the external refrigerant circuit through the discharge passage 145 . That is, the discharge chamber 143 receives refrigerant discharged from an adjacent pair of the cylinder bores 131 , and the muffler chamber 34 receives the refrigerant from the pair of the discharge chambers 143 . Then, the muffler chamber 34 discharges the interflowed refrigerant to the external refrigerant circuit as indicated by an arrow.
  • the refrigerant in the external refrigerant circuit returns to the suction chamber 142 through a condenser, an expansion valve and an evaporator in the external refrigerant circuit.
  • the external refrigerant circuit and the compressor constitute a refrigerant circuit for use in an automobile climate control system.
  • CO 2 is utilized as a refrigerant.
  • the muffler chamber 34 is formed not only in the cylinder block but also in the chamber housing 14 to extend from the cylinder block 13 .
  • the capacity of the muffler chamber 34 is increased. Accordingly, pressure pulsations are substantially reduced even in a compressor having high-pressure refrigerant such as CO 2 .
  • the muffler chamber 34 is arranged in a space between the cylinder bores 131 and is surrounded by three bolts 10 . Accordingly, the space between the cylinder bores 131 is effectively used, and the muffler chamber 34 endures the high-pressure refrigerant effectively by the bolts 10 .
  • the muffler chamber 34 is arranged so as to be isolated from an axis of the drive shaft 16 .
  • the length of the drive shaft 16 in the axial direction is not reduced by the muffler chamber 34 . That is, the distance between the swash plate 11 and the radial bearing 17 is increased by extending the drive shaft 16 in the axial direction, and the load acting on the radial bearing 17 is reduced.
  • the compressor with the motor is reduced in length in the axial direction.
  • a compressor is a double-headed piston type and pistons compress gas at both ends of cylinder bores.
  • a front housing 114 , a first cylinder block 113 , a second cylinder block 13 and a rear housing 14 are fixedly bolted by a plurality of bolts 10 (only one bolt is illustrated in FIG. 2), and these elements construct a housing body.
  • a drive shaft 16 is rotatably supported in the housing body.
  • a swash plate 11 is fixedly placed on the drive shaft 16 between the first and second cylinder blocks 113 and 13 .
  • the second cylinder block 13 has a plurality of cylinder bores 131 , and a piston 22 is disposed in each of the cylinder bores 131 .
  • a muffler chamber 34 includes at least one recess.
  • a first recess 134 is adjacent to the rear housing 14 and is formed in the second cylinder block 13 .
  • a second recess 144 is adjacent to the second cylinder block 13 and is formed in the rear housing 14 .
  • the muffler chamber 34 in the first embodiment is duplicated at both sides of the cylinder bore 131 in the second embodiment.
  • All the discharge chambers 143 are connected to the muffler chamber 34 so that all the discharge chambers 143 communicate therebetween.
  • a plurality of the muffler chambers 34 is formed to span between the cylinder block 13 and the chamber housing 14 . Capacity of the muffler chamber 34 is further increased, and the muffler operation is effectively performed.
  • the drive shaft 16 is operatively connected to a vehicle engine as an outer drive source through a clutch mechanism such as a magnetic clutch.
  • the compressor according to the present invention is applied to an air conditioner or a refrigerant cycle whose refrigerant is other than CO 2 .
  • the present invention is applied to a wobble plate type compressor or a variable displacement type compressor or the like that has different construction from the compressor according to the above described first embodiment.
  • the compressor has an inclinable swash plate which integrally rotates with the drive shaft 16 , and the variable rotational movement of the swash plate is converted to reciprocating movement of a single-headed piston through a pair of shoes.
  • pressure pulsations are substantially reduced without increasing the size of a compressor, even when the compressor has high-pressure refrigerant such as CO 2 . Accordingly, noise and vibrations due to the pressure pulsations are substantially reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
US09/897,169 2000-07-04 2001-07-02 Muffler for compressor Abandoned US20030138336A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000-201956 2000-07-04
JP2000201956A JP2002021717A (ja) 2000-07-04 2000-07-04 片頭ピストン型圧縮機

Publications (1)

Publication Number Publication Date
US20030138336A1 true US20030138336A1 (en) 2003-07-24

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US09/897,169 Abandoned US20030138336A1 (en) 2000-07-04 2001-07-02 Muffler for compressor

Country Status (3)

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US (1) US20030138336A1 (fr)
EP (1) EP1170504A3 (fr)
JP (1) JP2002021717A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050207905A1 (en) * 2004-03-18 2005-09-22 Koelzer Robert L Fixed angle swash plate compressor
US20060133943A1 (en) * 2004-10-18 2006-06-22 Danfoss Compressors Gmbh Piston compressor cylinder arrangement, particularly for a hermetically enclosed refrigerant compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004027847A (ja) * 2002-05-15 2004-01-29 Sanden Corp 電動圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4347046A (en) * 1978-12-04 1982-08-31 General Motors Corporation Swash plate compressor
US4768928A (en) * 1988-01-25 1988-09-06 General Motors Corporation Axial piston swash plate compressor muffler arrangement
US5253576A (en) * 1992-02-07 1993-10-19 Bethke Donald G Swashplate assembly for an axial piston pump
US5635687A (en) * 1994-07-05 1997-06-03 Necchi Compressori S.R.L. Muffler for motor compressors for refrigeration appliances
US6077049A (en) * 1996-09-30 2000-06-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Double-headed piston type compressor
US6296457B1 (en) * 1999-04-15 2001-10-02 Kabushiki Kaisha Toyoda Jidoshokki Discharge pulsation damping apparatus for compressor
US6508634B2 (en) * 2000-07-17 2003-01-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor utilizing spaces between cylinder bores

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994028305A1 (fr) * 1993-05-21 1994-12-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur a piston

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4347046A (en) * 1978-12-04 1982-08-31 General Motors Corporation Swash plate compressor
US4768928A (en) * 1988-01-25 1988-09-06 General Motors Corporation Axial piston swash plate compressor muffler arrangement
US5253576A (en) * 1992-02-07 1993-10-19 Bethke Donald G Swashplate assembly for an axial piston pump
US5635687A (en) * 1994-07-05 1997-06-03 Necchi Compressori S.R.L. Muffler for motor compressors for refrigeration appliances
US6077049A (en) * 1996-09-30 2000-06-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Double-headed piston type compressor
US6296457B1 (en) * 1999-04-15 2001-10-02 Kabushiki Kaisha Toyoda Jidoshokki Discharge pulsation damping apparatus for compressor
US6508634B2 (en) * 2000-07-17 2003-01-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor utilizing spaces between cylinder bores

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050207905A1 (en) * 2004-03-18 2005-09-22 Koelzer Robert L Fixed angle swash plate compressor
US20060133943A1 (en) * 2004-10-18 2006-06-22 Danfoss Compressors Gmbh Piston compressor cylinder arrangement, particularly for a hermetically enclosed refrigerant compressor
US7722337B2 (en) * 2004-10-18 2010-05-25 Danfoss Compressors Gmbh Piston compressor cylinder arrangement, particularly for a hermetically enclosed refrigerant compressor

Also Published As

Publication number Publication date
JP2002021717A (ja) 2002-01-23
EP1170504A2 (fr) 2002-01-09
EP1170504A3 (fr) 2003-08-20

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AS Assignment

Owner name: KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO, JAP

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NAKANE, YOSHIYUKI;YOKOMACHI, NAOY;MARAKAMI, KAZUO;AND OTHERS;REEL/FRAME:012061/0917

Effective date: 20010720

AS Assignment

Owner name: KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO, JAP

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NAKANE, YOSHIYUKI;YOKOMACHI, NAOYA;MURAKAMI, KAZUO;AND OTHERS;REEL/FRAME:012431/0308

Effective date: 20010720

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION