US20050142016A1 - Heat insulating structure in piston type compressor - Google Patents

Heat insulating structure in piston type compressor Download PDF

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Publication number
US20050142016A1
US20050142016A1 US11/015,525 US1552504A US2005142016A1 US 20050142016 A1 US20050142016 A1 US 20050142016A1 US 1552504 A US1552504 A US 1552504A US 2005142016 A1 US2005142016 A1 US 2005142016A1
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US
United States
Prior art keywords
heat insulating
insulating member
cylinder block
piston
structure according
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
US11/015,525
Other languages
English (en)
Inventor
Fuminobu Enokijima
Masaki Ota
Tetsuhiko Fukanuma
Masakazu Murase
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
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ENOKIJIMA, FUMINOBU, FUKANUMA, TETSUHIKO, MURASE, MASAKAZU, OTA, MASAKI
Publication of US20050142016A1 publication Critical patent/US20050142016A1/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
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • F04B53/168—Mounting of cylinder liners in cylinders

Definitions

  • the present invention relates to a heat insulating structure in a piston type compressor, in which a piston is reciprocated in accordance with the rotation of a rotary shaft to draw refrigerant gas from a suction pressure region to a compression chamber as well as to discharge the refrigerant gas from the compression chamber to a discharge pressure chamber.
  • refrigerant gas is introduced into a compression chamber.
  • the temperature of the introduced refrigerant gas in the compression chamber affects the performance of the compressor. As the temperature is higher, the density of the refrigerant gas in the compression chamber is lower, so that the performance of the compressor deteriorates. On the other hand, as the temperature is lower, the density of the refrigerant gas in the compression chamber is higher, so that the performance of the compressor improves.
  • the refrigerant gas By compressing the refrigerant gas, its temperature rises. Thus, heat is transmitted from the compressed refrigerant gas to a wall that defines the compression chamber, and the temperature of the wall rises. After compressing and discharging the refrigerant gas, the refrigerant gas is newly introduced into the compression chamber. The newly introduced refrigerant gas receives the heat from the wall, and its temperature rises. Therefore, if the temperature of the wall substantially rises or the wall has high heat conductivity, the temperature of the refrigerant gas in the compression chamber substantially rises before compression, and the performance of the compression deteriorates.
  • the present invention is directed to boosting the heat insulating characteristics of the compression chamber in a piston type compressor.
  • a heat insulating structure in a piston type compressor includes a heat insulating member.
  • the piston type compressor includes a cylinder block and a cover housing connected to the cylinder block, a piston is accommodated in a cylinder bore defined in the cylinder block to define a compression chamber. A suction pressure region and a discharge pressure region are defined in the cover housing.
  • the piston is reciprocated in the cylinder bore in accordance with rotation of a rotary shaft so that refrigerant gas is drawn from the suction pressure region to the compression chamber and discharged from the compression chamber to the discharge pressure region.
  • the heat insulating member has a predetermined shape and is located in the cylinder block.
  • the heat insulating member has an inner peripheral surface that defines the cylinder bore.
  • FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first preferred embodiment
  • FIG. 2 is a cross-sectional view of the compressor taken along the line I-I in FIG. 1 ;
  • FIG. 3 is a cross-sectional view of the compressor taken along the line II-II in FIG. 1 ;
  • FIG. 4 is a partially enlarged cross-sectional view of the compressor when a piston is located at its top dead center according to the first preferred embodiment
  • FIG. 5 is a partially enlarged cross-sectional view of the compressor when the piston is located at its bottom dead center according to the first preferred embodiment
  • FIG. 6 is a partially enlarged cross-sectional view of a compressor according to a second preferred embodiment
  • FIG. 7 is a partially enlarged cross-sectional view of a compressor according to a third preferred embodiment
  • FIG. 8 is a partially enlarged cross-sectional view of a compressor according to a fourth preferred embodiment.
  • FIG. 9A is a partially enlarged cross-sectional view of a compressor according to a fifth preferred embodiment.
  • FIG. 9B is a cross-sectional view of the compressor taken along the line III-III in FIG. 9A ;
  • FIG. 10A is a partially enlarged cross-sectional view of a compressor according to a sixth preferred embodiment
  • FIG. 10B is a cross-sectional view of the compressor taken along the line IV-IV in FIG. 10A ;
  • FIG. 11 is a partially enlarged cross-sectional view of a compressor according to a seventh preferred embodiment.
  • FIG. 12 is a partially enlarged cross-sectional view of a compressor according to an eighth preferred embodiment.
  • FIGS. 1 through 5 A first preferred embodiment will be described with reference to FIGS. 1 through 5 , in which the present invention is applied to a piston type variable displacement compressor.
  • the housing of a piston type variable displacement compressor 10 includes a cylinder block 11 of aluminum, a front housing 12 of aluminum and a rear housing or cover housing 13 of aluminum.
  • the front housing 12 is joined to the front end of the cylinder block 11
  • the rear housing 13 is joined to the rear end of the cylinder block 11 through a valve plate 14 and gasket type valve forming plates 15 , 16 .
  • the cylinder block 11 , the front housing 12 and the rear housing 13 are combined by a screw 53 .
  • the valve forming plate 15 includes a metallic plate 152 and rubber layers 153 , 154 that are respectively provided on the surfaces of the metallic plate 152 .
  • the valve forming plate 16 includes a metallic plate 162 and rubber layers 163 , 164 that are respectively provided on the surfaces of the metallic plate 162 .
  • the front housing 12 and the cylinder block 11 define a pressure control chamber 121 and rotatably support a rotary shaft 18 through radial bearings 19 , 20 , respectively.
  • the rotary shaft 18 extends in the pressure control chamber 121 and protrudes to the outside therefrom.
  • the rotary shaft 18 receives driving power from a vehicle engine 17 as an external drive source through a pulley (not shown) and a belt (not shown).
  • a lug plate 21 is mounted on the rotary shaft 18 , and a swash plate 22 is supported on the rotary shaft 18 so as to slide in and incline with respect to the axial direction of the rotary shaft 18 .
  • a connection member 23 is mounted on the swash plate 22 , and a guide pin 24 is mounted on the connection member 23 .
  • a guide hole 211 is formed in the lug plate 21 .
  • the head portion of the guide pin 24 is slidably inserted into the guide hole 211 .
  • the cooperation of the guide hole 211 and the guide pin 24 allows the swash plate 22 to incline with respect to the axial direction of the rotary shaft 18 and to rotate together with the rotary shaft 18 .
  • the inclination of the swash plate 22 is guided by the slide guide relation between the guide hole 211 and the guide pin 24 and the slide support of the rotary shaft 18 .
  • an inclination angle of the swash plate 22 is increased.
  • the swash plate 22 comes into contact with the lug plate 21 to restrict the maximum inclination angle.
  • the inclination angle of the swash plate 22 is the maximum.
  • the middle part of the swash plate 22 moves toward the cylinder block 11 , the inclination angle of the swash plate 22 is decreased.
  • the inclination angle of the swash plate 22 is the minimum.
  • a plurality of holes 111 are formed through the cylinder block 11 for forming compression chambers.
  • a cylindrical-shaped heat insulating member 30 of synthetic resin is press-fitted into each of the hole 111 .
  • the inner peripheral surface of the cylinder block 21 that defines the hole 111 is covered by the heat insulating member 30 .
  • a piston 25 of aluminum is accommodated in each of the heat insulating members 30 . Only one piston 25 is shown in FIG. 2 .
  • the piston 25 includes a cylindrical-shaped head portion 252 and a neck portion 253 as shown in FIG. 1 .
  • the head portion 252 is inserted into the heat insulating member 30 , and the neck portion 253 is engaged with the swash plate 22 through a pair of shoes 26 .
  • the rotational movement of the swash plate 22 is converted into the reciprocating movement of the piston 25 , and the piston 25 is reciprocated in the heat insulating member 25 .
  • the inside of the heat insulating member 30 is a cylinder bore 43 for reciprocating the piston 25 therein, and the heat insulating member 30 has an inner peripheral surface 431 that defines the cylinder bore 43 as shown in FIGS. 2 and 3 .
  • a compression chamber 112 is defined by the piston 25 , the heat insulating member 30 and the valve forming plate 15 in the inside of the heat insulating member 30 (the cylinder bore 43 ) as shown in FIG. 1 .
  • FIG. 5 shows a state where the piston 25 is located at its bottom dead center.
  • the rear housing 13 and the valve plate 14 define a suction chamber or suction pressure region 27 and a discharge chamber or discharge pressure region 28 that are separated by an annular partition wall 29 .
  • the suction chamber 27 is located on the radially outer side of the rear housing 13 and surrounds the discharge chamber 28 around an axial line 181 of the rotary shaft 18 .
  • the compression chamber 112 is separated from the suction chamber 27 and the discharge chamber 28 by the valve plate 14 .
  • the valve forming plates 15 , 16 and a retainer 31 are combined with the valve plate 14 by a screw 32 .
  • a suction port 141 is formed in the valve plate 14 and the valve forming plate 16
  • a discharge port 142 is formed in the valve plate 14 and the valve forming plate 15
  • a suction valve 151 is formed in the valve forming plate 15
  • a discharge valve 161 is formed in the valve forming plate 16 .
  • Gaseous refrigerant in the suction chamber 27 pushes away the suction valve 151 and is drawn into the compression chamber 112 through the suction port 141 by the movement of the piston 25 from the right to the left as seen in FIG. 1 .
  • a regulating recess 301 is formed on the end face of the heat insulating member 30 near the valve forming plate 15 , and a metallic member 302 is mounted on the bottom of the regulating recess 301 .
  • the suction valve 151 comes into contact with the metallic member 302 at the bottom of the regulating member 301 to regulate its opening degree.
  • the drawn gaseous refrigerant in the compression chamber 112 pushes away the discharge valve 161 and is discharged into the discharge chamber 28 through the discharge port 142 by the movement of the piston 25 from the left to the right as seen in FIG. 1 .
  • the discharge valve 161 comes into contact with the retainer 31 to regulate its opening degree.
  • an inlet 33 for introducing the gaseous refrigerant into the suction chamber 27 and an outlet 34 for discharging the gaseous refrigerant from the discharge chamber 28 are formed in the rear housing 13 .
  • the inlet 33 and the outlet 34 is interconnected by an external refrigerant circuit 35 on which a heat exchanger 36 for obtaining heat from the refrigerant, a fixed throttle 37 , a heat exchanger 38 for transmitting heat from the surrounding air to the refrigerant and an accumulator 39 are arranged.
  • the accumulator 39 feeds the only gaseous refrigerant to the compressor 10 .
  • the refrigerant in the discharge chamber 28 flows into the suction chamber 27 via the outlet 34 , the heat exchanger 36 , the fixed throttle 37 , the heat exchanger 38 , the accumulator 39 and the inlet 33 .
  • the discharge chamber 28 and the pressure control chamber 121 are interconnected by a supply passage 40 formed in the cylinder block 11 .
  • the pressure control chamber 121 and the suction chamber 27 are interconnected by a bleed passage 41 formed in the cylinder block 11 and the rear housing 13 .
  • the refrigerant in the pressure control chamber 121 flows out to the suction chamber 27 through the bleed passage 41 .
  • An electromagnetic displacement control valve 42 is arranged on the supply passage 40 .
  • the displacement control valve 42 When the displacement control valve 42 is de-energized, the displacement control valve 42 is closed so that the refrigerant does not flow from the discharge chamber 28 to the pressure control chamber 121 through the supply passage 40 . Since the refrigerant in the pressure control chamber 121 flows out to the suction chamber 27 through the bleed passage 41 , the pressure in the pressure control chamber 121 falls. Therefore, the inclination angle of the swash plate 22 is increased, and the displacement is increased.
  • the displacement control valve 42 When the displacement control valve 42 is energized, the displacement control valve 42 is opened so that the refrigerant flows from the discharge chamber 28 to the pressure control chamber 121 through the supply passage 40 . Therefore, the pressure in the pressure control chamber 121 rises, the inclination angle of the swash plate 22 is decreased and the displacement is decreased.
  • carbon dioxide is used as the refrigerant.
  • the heat insulating member 30 having the inner peripheral surface 431 that defines the cylinder bore 43 is hard to be heated by the refrigerant gas in the compression chamber 112 , and the temperature of the heat insulating member 30 substantially does not rise. Therefore, a small amount of heat is transmitted from the heat insulating member 30 to the refrigerant gas that is newly drawn into the compression chamber 112 after compressing and discharging the previously drawn refrigerant gas. Namely, the temperature of the refrigerant gas in the compression chamber 112 is substantially prevented from being increased by the heat insulating member 30 .
  • the heat insulating member 30 enhances the heat insulating characteristics of the compression chamber 112 and contributes to the improvement in the performance of the piston type variable displacement compressor 10 .
  • the heat insulating member 30 having a predetermined shape or the cylindrical shape is made thicker to enhance the heat insulation effectiveness.
  • the heat insulation member 30 is made of synthetic resin that has low heat conductivity.
  • the heat insulating member 30 reduces the heat transmission from the cylinder block 11 of aluminum, which has high heat conductivity, to the refrigerant gas in the compression chamber 112 .
  • the heat insulating member 30 contributes to the improvement in the performance of the compressor.
  • FIGS. 6 through 12 the following preferred embodiments are practiced as shown in FIGS. 6 through 12 .
  • similar elements are referred to by the same reference numerals as the first is preferred embodiment.
  • a heat insulating member 44 includes a cylindrical portion 441 and a flange 442 that is located at the end of the cylindrical portion 441 near the valve plate 14 and is integrated with the cylindrical portion 441 .
  • the cylindrical portion 441 is inserted into the hole 111 , and the flange 442 is sandwiched between the cylinder block 11 and the valve plate 14 . Since the flange 442 is sandwiched between the cylinder block 11 and the valve plate 14 , the cylindrical portion 441 is held in the hole 111 without following the reciprocating movement of the piston 25 .
  • the cylinder block 11 is formed with a protrusion 114 on its inner peripheral surface that defines the hole 111 .
  • a cylindrical-shaped heat insulating member 45 is inserted into the hole 111 and sandwiched between the protrusion 114 and the valve plate 14 .
  • the heat insulating member 45 is held in the hole 111 without following the reciprocating movement of the piston 25 .
  • a valve forming plate 15 A is made of metal, and a seal ring 46 is interposed between the cylinder block 11 and the valve forming plate 15 A near the outer periphery of the cylinder block 11 so as to surround the axial line 181 of the rotary shaft 18 and all of the is heat insulating members 44 .
  • the flange 442 of the heat insulating member 44 serves to seal the compression chamber 112 , so that the refrigerant gas is prevented from leaking along the surface of the valve forming plate 15 A from the compression chamber 112 to a hole 115 that is formed in the cylinder block 11 for inserting the rotary shaft 18 therein.
  • the seal ring 46 prevents the refrigerant gas from leaking along the surface of the valve forming plate 15 A from the compression chamber 112 to the outside of the compressor.
  • a heat insulating member 47 includes a cylindrical portion 471 and an end wall 472 .
  • the cylindrical portion 471 is inserted into the hole 111 , and the end wall 472 is in contact with the valve forming plate 15 A of metal and faces the top end surface of the piston 25 .
  • the heat insulating member 47 is sandwiched between the protrusion 114 and the valve plate 14 .
  • the end wall 472 has formed therein a suction hole 473 facing the suction port 141 and a discharge hole 474 facing the discharge port 142 .
  • the refrigerant gas in the suction chamber 27 is drawn into the compression chamber 112 through the suction port 112 and the suction hole 473 while the refrigerant gas in the compression chamber 112 is discharged into the discharge chamber 28 through the discharge hole 474 and the discharge port 142 .
  • the end wall 472 further improves the heat insulating characteristics of the compression chamber 112 .
  • a cylinder block 11 A includes an annular base block 48 of aluminum and an annular block 49 of synthetic resin.
  • the base block 48 includes a radially outer portion 481 , a radially inner portion 482 and an end wall 483 , and the annular block 49 is interposed between the radially outer portion 481 and the radially inner portion 482 to surround the axial line 181 of the rotary shaft 18 .
  • a plurality of the cylinder bores 43 are formed in the annular block 49 .
  • the annular block 49 or a heat insulating member of synthetic resin has the inner peripheral surface 431 that defines the cylinder bore 43 .
  • the end wall 483 has formed therein a through hole 484 corresponding to each of the cylinder bore 43 .
  • the piston 25 is inserted into the cylinder bore 43 through the through hole 484 .
  • the peripheral surface of the head portion 252 of the piston 25 is covered with a coating layer 50 made of the same material as the heat insulating member 45 .
  • a disc-shaped heat insulating member 51 is bound to a top end surface 251 of the piston 25 to cover the top end surface 251 .
  • the heat insulating member 51 further improves the heat insulating characteristics of the compression chamber 112 .
  • the coating layer 50 is made of the same material as the heat insulating member 45 .
  • the coating layer is made of material that has abrasive resistance higher than the heat insulating member or sliding characteristics better than the heat insulating member, so that the lifetime of the compressor improves.
  • the coating layer is provided in the other preferred embodiments.
  • Hard rubber or ceramics is used as material for the heat insulating member having the inner peripheral surface that defines the cylinder bore.
  • the cylindrical-shaped heat insulating member includes two parts, or a radially inner part and a radially outer part that are made of different synthetic resins.
  • Synthetic resin having high abrasive resistance e.g. polytetrafluoroethylene
  • the present invention is applicable to a piston type compressor in which the discharge chamber is defined on the outer peripheral side of the rear housing 13 so as to surround the suction chamber around the axial line 181 of the rotary shaft 18 .
  • the present invention is applicable to a piton type fixed displacement compressor.
  • the present invention is applicable to a compressor in which refrigerant other than carbon dioxide is used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US11/015,525 2003-12-25 2004-12-17 Heat insulating structure in piston type compressor Abandoned US20050142016A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003431650A JP2005188407A (ja) 2003-12-25 2003-12-25 ピストン式圧縮機における断熱構造
JP2003-431650 2003-12-25

Publications (1)

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US20050142016A1 true US20050142016A1 (en) 2005-06-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
US11/015,525 Abandoned US20050142016A1 (en) 2003-12-25 2004-12-17 Heat insulating structure in piston type compressor

Country Status (4)

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US (1) US20050142016A1 (de)
EP (1) EP1553293B1 (de)
JP (1) JP2005188407A (de)
DE (1) DE602004007611T2 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060177329A1 (en) * 2003-06-06 2006-08-10 Markus Firmann Peristaltic pump
US20060237552A1 (en) * 2005-04-26 2006-10-26 Satoshi Umemura Displacement control valve for clutchless type variable displacement compressor
US20090068027A1 (en) * 2005-10-25 2009-03-12 Iwao Uchikado Reciprocating Fluid Machine
US20130272859A1 (en) * 2010-12-22 2013-10-17 Yukihiko Taguchi Compressor
US20140341766A1 (en) * 2013-05-16 2014-11-20 Kabushiki Kaisha Toyota Jidoshokki Compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015207909A1 (de) * 2015-04-29 2016-11-03 Mahle International Gmbh Axialkolbenmaschine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4370104A (en) * 1980-07-22 1983-01-25 White Consolidated Industries, Inc. Suction muffler for refrigeration compressor
US6457947B1 (en) * 1997-08-29 2002-10-01 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Piston compressor for refrigerant, with thermal insulation

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW504546B (en) * 2000-10-17 2002-10-01 Fisher & Amp Paykel Ltd A linear compressor
DE10051420B4 (de) * 2000-10-17 2009-03-05 Valeo Compressor Europe Gmbh Zylinderblock eines Axialkolbenverdichters mit verlängerter Zylinderlauffläche
DE10231212B4 (de) * 2001-07-21 2014-06-05 Volkswagen Ag Taumelscheibenkompressor
JP2003247487A (ja) * 2002-02-21 2003-09-05 Sanden Corp 斜板式圧縮機
DE10223844B4 (de) * 2002-05-28 2013-04-04 Danfoss A/S Wasserhydraulische Maschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4370104A (en) * 1980-07-22 1983-01-25 White Consolidated Industries, Inc. Suction muffler for refrigeration compressor
US6457947B1 (en) * 1997-08-29 2002-10-01 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Piston compressor for refrigerant, with thermal insulation

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060177329A1 (en) * 2003-06-06 2006-08-10 Markus Firmann Peristaltic pump
US20060237552A1 (en) * 2005-04-26 2006-10-26 Satoshi Umemura Displacement control valve for clutchless type variable displacement compressor
US20090068027A1 (en) * 2005-10-25 2009-03-12 Iwao Uchikado Reciprocating Fluid Machine
US20130272859A1 (en) * 2010-12-22 2013-10-17 Yukihiko Taguchi Compressor
US20140341766A1 (en) * 2013-05-16 2014-11-20 Kabushiki Kaisha Toyota Jidoshokki Compressor

Also Published As

Publication number Publication date
DE602004007611T2 (de) 2008-04-10
EP1553293A2 (de) 2005-07-13
JP2005188407A (ja) 2005-07-14
DE602004007611D1 (de) 2007-08-30
EP1553293A3 (de) 2006-03-08
EP1553293B1 (de) 2007-07-18

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Legal Events

Date Code Title Description
AS Assignment

Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ENOKIJIMA, FUMINOBU;OTA, MASAKI;FUKANUMA, TETSUHIKO;AND OTHERS;REEL/FRAME:016110/0557

Effective date: 20041208

STCB Information on status: application discontinuation

Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION