US20100003146A1 - Piston type compressor - Google Patents

Piston type compressor Download PDF

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Publication number
US20100003146A1
US20100003146A1 US12/492,245 US49224509A US2010003146A1 US 20100003146 A1 US20100003146 A1 US 20100003146A1 US 49224509 A US49224509 A US 49224509A US 2010003146 A1 US2010003146 A1 US 2010003146A1
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US
United States
Prior art keywords
chamber
discharge chamber
type compressor
piston type
discharge
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
US12/492,245
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English (en)
Inventor
Shinichi Sato
Akio Saiki
Manabu Sugiura
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
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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
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Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SAIKI, AKIO, SATO, SHINICHI, SUGIURA, MANABU
Publication of US20100003146A1 publication Critical patent/US20100003146A1/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
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • 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
    • F04B27/12—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 having plural sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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

Definitions

  • the present invention relates to a suction structure in a piston type refrigerant compressor.
  • a piston type compressor with a housing having formed therein a discharge chamber and a suction chamber, wherein refrigerant gas is supplied to the suction chamber from the outer periphery of the housing and discharged from the discharge chamber toward the outer periphery of the housing, the suction chamber is disposed on the radially outer side of the discharge chamber or on the radially inner side of an annular discharge chamber.
  • a compressor with the suction chamber located on the outer side of the discharge chamber is disclosed in Japanese Utility Model Application Publication No. 59-105076 and Japanese Patent Application Publication No. 2000-120532 and a compressor with the suction chamber located on the inner side of the annular discharge chamber is disclosed in Japanese Patent Application Publication No. 7-233783.
  • an oil reservoir is formed on the inner side of the annular discharge chamber and the suction chamber and the oil reservoir are connected through a communication passage extending across the discharge chamber. Lubrication oil separated from the refrigerant gas flowing through the communication passage is reserved in the oil reservoir.
  • the communication passage through which refrigerant gas is supplied to the suction chamber should be formed so as to extend across the discharge chamber in view of the need of downsizing the housing. If the discharge chamber is divided in the circumferential direction, discharge pulsation is not sufficiently suppressed. Therefore, it is desirable that the annular discharge chamber should not be divided by the communication passage, but formed as a single chamber, as disclosed in the Japanese Utility Model Application Publication No. 59-105076.
  • the Japanese Patent Application Publication No. 7-233783 discloses a compressor in which a plurality of ribs are formed in the discharge chamber thereby to form a plurality of small chambers. According to this Publication, since any two adjacent small chambers are not isolated but communicate with each other, the discharge pulsation is effectively suppressed. However, the Publication makes no reference to the structure of a suction passage extending across the discharge chamber to contribute to increasing the suction efficiency.
  • the present invention is directed to providing a piston type compressor in which refrigerant gas is supplied to a suction chamber from an outer peripheral region of the compressor outward of a discharge chamber located outward of the suction chamber, and which reduces the discharge pulsation and improves the suction efficiency.
  • a piston type compressor has a cylinder block, a cylinder bore formed in the cylinder block, a rotary shaft, a piston and a compression chamber formed in the cylinder bore.
  • the piston is received in the cylinder bore and reciprocates in accordance with the rotation of the rotary shaft.
  • the compressor further has a main suction chamber communicable with the compression chamber, a discharge chamber formed annularly so as to surround the main suction chamber, a subsidiary suction chamber formed so as to surround the discharge chamber, partitions formed in the discharge chamber so as to protrude into the discharge chamber and a suction passage formed in each partition so as to interconnect the subsidiary suction chamber and the main suction chamber.
  • FIG. 1 is a longitudinal sectional view of a fixed displacement double-headed piston type compressor according to a first preferred embodiment of the present invention
  • FIG. 2A is a sectional view taken along the line A-A of FIG. 1 ;
  • FIG. 2B is a sectional view taken along the line B-B of FIG. 1 ;
  • FIG. 3 is a longitudinal sectional view of a fixed displacement double-headed piston rotary valve type compressor according to a second preferred embodiment of the present invention
  • FIG. 4A is a sectional view taken along the line C-C of FIG. 3 ;
  • FIG. 4B is a sectional view taken along the line D-D of FIG. 3 .
  • the compressor is generally designated by numeral 10 .
  • the front and rear sides of the compressor correspond to the left and right sides in the drawing, respectively.
  • the compressor has a housing assembly including a pair of front and rear cylinder blocks 11 , 12 and a pair of front and rear housings 13 , 14 .
  • the front cylinder block 11 is connected to the rear cylinder block 12 .
  • the front and rear housings 13 , 14 are connected to the front and rear cylinder blocks 11 , 12 , respectively.
  • the front and rear cylinder blocks 11 , 12 and the front and rear housings 13 , 14 cooperate to form the housing assembly of the fixed displacement double-headed piston type compressor 10 .
  • a rotary shaft 25 is rotatably supported by the front and rear cylinder blocks 11 , 12 through front and rear radial bearings 26 , 27 .
  • a swash plate 28 is secured to the rotary shaft 25 .
  • a shaft seal device 35 is interposed between the front housing 13 and the rotary shaft 25 so as to prevent refrigerant gas from leaking between the outer surface of the rotary shaft 25 and the front housing 13 .
  • the front housing 13 has formed therein a subsidiary suction chamber 130 as a part of the suction-pressure region of the compressor, a main suction chamber 131 as a part of the suction-pressure region and a discharge chamber 132 as a part of the discharge-pressure region of the compressor.
  • the main suction chamber 131 and the discharge chamber 132 are separated by an annular partition wall 15 A and the annular discharge chamber 132 is formed so as to surround the main suction chamber 131 .
  • the subsidiary suction chamber 130 and the discharge chamber 132 are separated by an annular partition wall 15 B and the annular subsidiary suction chamber 130 is formed so as to surround the discharge chamber 132 .
  • the front housing 13 has formed therein a lubrication passage 134 interconnecting the main suction chamber 131 and a seal chamber 351 having therein the aforementioned shaft seal device 35 .
  • the lubrication oil flows together with the refrigerant gas from the main suction chamber 131 into the seal chamber 351 through the lubrication passage 134 for lubricating the shaft seal device 35 .
  • the front housing 13 has formed therein a plurality of partitions 33 (four partitions in the embodiment as shown in FIG. 2A ) protruding from the inner wall 133 of the front housing 13 into the discharge chamber 132 toward a valve plate 16 .
  • the partitions 33 extend from the inner partition wall 15 A to the outer partition wall 15 B across the discharge chamber 132 .
  • Each partition 33 has formed therethrough a radial suction passage 331 interconnecting the subsidiary suction chamber 130 and the main suction chamber 131 .
  • a valve plate 16 , valve forming plates 17 , 18 and a retainer forming plate 19 are interposed between the front cylinder block 11 and the front housing 13 .
  • the valve plate 16 , the valve forming plate 18 and the retainer forming plate 19 have formed therethrough a suction port 161
  • the valve plate 16 and the valve forming plate 17 have formed therethrough a discharge port 162 , respectively.
  • the valve forming plates 17 , 18 have formed therewith a suction valve 171 and a discharge valve 181 , respectively.
  • the suction valve 171 and the discharge valve 181 open and close the suction port 161 and the discharge port 171 , respectively.
  • the retainer forming plate 19 has formed therewith a retainer 191 for regulating the opening degree of the discharge valve 181 .
  • the front cylinder block 11 , the valve plate 16 and the front housing 13 have formed therethrough inlet and outlet passages 111 , 112 extending in the axial direction of the rotary shaft 25 .
  • the inlet passage 111 communicates with the subsidiary suction chamber 130 and the outlet passage 112 communicates with the discharge chamber 132 .
  • the partitions 33 are located so as to space apart each other along the circumferential direction of the annular discharge chamber 132 . Therefore, the annular discharge chamber 132 is divided into a plurality of small chambers R 1 , R 2 , R 3 , R 4 by the plurality of partitions 33 , as shown in FIG. 2A , but these small chambers R 1 -R 4 communicate each other so as to form a single annular discharge chamber. Each cross-sectional area of the discharge chamber 132 where the partition 33 is formed between adjacent small chambers is smaller than that of the other annular part of the discharge chamber 132 . Each of the small chambers R 3 , R 4 located far from the outlet passage 112 is provided in one-to-one relation to its corresponding cylinder bore 29 .
  • each of the small chambers R 1 , R 2 located close to the inlet passage 112 is also provided in one-to-one relation to its corresponding cylinder bore 29 .
  • the front outlet passage 112 is connected with only the small chamber R 1 of the discharge chamber 132 .
  • the refrigerant gas flows through the respective small chamber R 1 , R 2 , R 3 and R 4 before reaching the front outlet passage 112 .
  • the rear housing 14 has formed therein a subsidiary suction chamber 140 as a part of the suction-pressure region of the compressor 10 , a main suction chamber 141 also as a part of the suction-pressure region and a discharge chamber 142 as a part of the discharge-pressure region.
  • the main suction chamber 141 and the discharge chamber 142 are separated by an annular partition wall 24 A and the discharge chamber 142 is formed annularly so as to surround the main suction chamber 141 .
  • the subsidiary suction chamber 140 and the discharge chamber 142 are separated by an annular partition wall 24 B and the subsidiary suction chamber 140 is formed annularly so as to surround the discharge chamber 142 .
  • the rear housing 14 has formed therein a plurality of partitions 34 (four partitions in the embodiment as shown in FIG. 2B ) protruding from the inner wall 143 of the rear housing 14 into the discharge chamber 142 toward a valve plate 20 .
  • the partitions 34 extend from the inner partition wall 24 A to the outer partition wall 24 B across the discharge chamber 142 .
  • Each partition 34 has formed therethrough a suction passage 341 interconnecting the subsidiary suction chamber 140 and the main suction chamber 141 .
  • the valve plate 20 , valve forming plates 21 , 22 and a retainer forming plate 23 are interposed between the rear cylinder block 12 and the rear housing 14 .
  • the valve plate 20 , the valve forming plate 22 and the retainer forming plate 23 have formed therethrough a suction port 201
  • the valve plate 20 and the valve forming plate 21 have formed therethrough a discharge port 202 .
  • the valve forming plates 21 , 22 have formed therewith a suction valve 211 and a discharge valve 221 , respectively.
  • the suction valve 211 and the discharge valve 221 open and close the suction port 201 and the discharge port 202 , respectively.
  • the retainer forming plate 23 has formed therewith a retainer 231 for regulating the opening degree of the discharge valve 221 .
  • the rear cylinder block 12 , the valve plate 20 and the rear housing 14 have formed therethrough an inlet passage 121 and an outlet passage 122 extending in the axial direction of the rotary shaft 25 .
  • the inlet passage 121 communicates with the subsidiary suction chamber 140 and the outlet passage 122 communicates with the discharge chamber 142 , respectively.
  • the annular discharge chamber 142 is separated into a plurality of small chambers S 1 , S 2 , S 3 , S 4 by the partitions 34 , but these small chambers communicate each other so as to form a single annular discharge chamber.
  • Each of the small chambers S 3 , S 4 located far from the outlet passage 122 is provided in one-to-one relation to its corresponding cylinder bore 30 .
  • each small chambers S 1 , S 2 located close to the inlet passage 122 is also provided in one-to-one relation to its corresponding cylinder bore 30 .
  • the front and rear inlet passages 111 , 121 are distributed from a main passage 123 which is formed in the rear cylinder block 12 and the front and rear outlet passage 112 , 122 are merged into a joint passage 124 formed in the rear cylinder block 12 .
  • the main passage 123 communicates with the joint passage 124 through an external refrigerant circuit (not shown) of the air conditioning system in which the compressor 10 is connected.
  • the front and rear cylinder blocks 11 , 12 have formed therethrough a plurality of pairs of front and rear cylinder bores 29 , 30 (five cylinder bores in the embodiment as shown in FIGS. 2A , 2 B) arranged around the rotary shaft 25 , respectively.
  • Each pair of front and rear cylinder bores 29 , 30 receives therein a double-headed piston 31 .
  • the refrigerant gas discharged into the discharge chambers 132 , 142 flows out to the external refrigerant circuit through the outlet passages 112 , 122 and the joint passage 124 , respectively.
  • the refrigerant gas flowed out to the external refrigerant circuit flows back into the subsidiary suction chambers 130 , 140 through the main passage 123 and the inlet passages 111 , 121 , respectively.
  • the refrigerant gas flows into the main suction chambers 131 , 141 through the suction passages 331 , 341 , respectively.
  • the frequency of the contraction and expansion of the refrigerant gas is reduced, which is not desirable for the reduction of the discharge pulsation. If there is only one partition 33 , 34 and hence only one suction passage 331 , 341 in the discharge chamber 132 , 142 , the amount of the refrigerant gas flowing to the suction ports 161 , 201 located far from the suction passages 331 , 341 is smaller than that of the refrigerant gas flowing to the suction ports 161 , 201 located close to the suction passages 331 , 341 , with the result that the suction efficiency deteriorates.
  • the structure of the discharge chamber with a plurality of partitions 33 , 34 and hence with a plurality of small chambers R 1 through R 4 each corresponding to one cylinder bore 29 contributes to equalizing the amount of the refrigerant gas drawn through the respective suction ports 161 , 201 thereby to improve the suction efficiency.
  • the front and rear cylinder blocks 11 , 12 of the double-headed piston type compressor 10 A have formed therethrough shaft holes 36 , 37 through which the rotary shaft 25 extends.
  • the rotary shaft 25 is directly supported by the front and rear cylinder blocks 11 , 12 through the inner surfaces of the shaft holes 36 , 37 which are in contact with the outer surface of the rotary shaft 25 .
  • the outer surface of the rotary shaft 25 in contact with the shaft holes 36 , 37 provide sealing surfaces 251 , 252 , respectively.
  • the rotary shaft 25 has formed therethrough an axial passage 38 extending in axial direction of the rotary shaft 25 .
  • the axial passage 38 communicates with the main suction chamber 131 through an inlet passage 135 formed in the front housing 13 , so that the refrigerant gas in the main suction chamber 131 can be drawn into the axial passage 38 through the inlet passage 135 . Since the inlet passage 135 communicates with the seal chamber 351 , the lubrication oil in the main suction chamber 131 can flow to the seal chamber 351 thereby to lubricate the shaft seal device 35 .
  • the axial passage 38 also communicates with the main suction chamber 141 in the rear housing 14 , so that the refrigerant gas in the main suction chamber 141 can flow from the rear end of the rotary shaft 25 into the axial passage 38 .
  • the rotary shaft 25 in the shaft holes 36 , 37 are formed with front and rear suction ports 381 , 382 of the axial passage 38 which are opened to the front and rear seal surfaces 251 , 252 of the rotary shaft 25 , respectively.
  • the front and rear cylinder blocks 11 , 12 have formed therethrough front and rear communication passages 39 , 40 interconnecting the cylinder bores 29 , 30 and the shaft holes 36 , 37 , respectively.
  • the front and rear suction ports 381 , 382 of the axial passage 38 intermittently communicate with the front and rear communication passages 39 , 40 , respectively, in accordance with the rotation of the rotary shaft 25 .
  • the rear suction port 382 communicates with the rear communication passage 40 .
  • the refrigerant gas in the main suction chamber 141 is drawn into the compression chamber 301 in the cylinder bore 30 through the axial passage 38 , the rear suction port 382 and the rear communication passage 40 .
  • the front suction port 381 communicates with the front communication passage 39 .
  • the refrigerant gas in the main suction chamber 131 is drawn into the compression chamber 291 in the cylinder bore 29 through the inlet passage 135 , the axial passage 38 , the front suction port 381 and the front communication passage 39 .
  • front and rear seal surfaces 251 , 252 of the rotary shaft 25 form front and rear rotary valves 41 , 42 , respectively, which are integrally formed with the rotary shaft 25 .
  • the front suction port 381 and the axial passage 38 cooperate to form a supply passage of the front rotary valve 41 and, similarly, the rear suction port 382 and the axial passage 38 cooperate to form a supply passage of the rear rotary valve 42 .
  • the second embodiment also offers the same advantageous effects as the first embodiment. Since the piston type compressor 10 A with the rotary valves 41 , 42 inevitably has the main suction chamber located radially inward of the discharge chamber, the present invention may be applied suitably to the piston type compressor 10 A with the rotary valves 41 , 42 .
  • the present invention is not limited to the embodiments described above, but it may be modified in various way as exemplified by the following alternative embodiments.
  • the number of the partitions in the discharge chamber may be two, three or more than five.
  • the present invention may be applied also to a variable displacement compressor as disclosed in the Japanese Patent Application Publications No. 7-233783 and No. 2000-120532.
  • the present invention is applicable further to a fixed displacement piston type compressor with a single-headed piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US12/492,245 2008-07-02 2009-06-26 Piston type compressor Abandoned US20100003146A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-173652 2008-07-02
JP2008173652A JP2010013987A (ja) 2008-07-02 2008-07-02 ピストン式圧縮機における冷媒吸入構造

Publications (1)

Publication Number Publication Date
US20100003146A1 true US20100003146A1 (en) 2010-01-07

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ID=41464532

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/492,245 Abandoned US20100003146A1 (en) 2008-07-02 2009-06-26 Piston type compressor

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US (1) US20100003146A1 (ko)
JP (1) JP2010013987A (ko)
KR (1) KR20100004046A (ko)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100189576A1 (en) * 2009-01-23 2010-07-29 Kabushiki Kaisha Toyota Jidoshokki Piston compressor
CN103459846A (zh) * 2011-03-31 2013-12-18 株式会社丰田自动织机 斜盘式压缩机
US20160238001A1 (en) * 2015-02-12 2016-08-18 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5915576B2 (ja) * 2013-03-27 2016-05-11 株式会社豊田自動織機 ピストン型斜板式圧縮機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4431378A (en) * 1979-02-16 1984-02-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor
US5702236A (en) * 1994-02-23 1997-12-30 Kabushiki Kaisha Toyoda Jiboshokki Seisakusho Reciprocating piston type compressor having a discharge chamber with a plurality of pulsation attenuating subchambers
US6293768B1 (en) * 1999-05-11 2001-09-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
US6862975B2 (en) * 2001-12-21 2005-03-08 Kabushiki Kaisha Toyota Jidoshokki Apparatus for lubricating piston type compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4431378A (en) * 1979-02-16 1984-02-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor
US5702236A (en) * 1994-02-23 1997-12-30 Kabushiki Kaisha Toyoda Jiboshokki Seisakusho Reciprocating piston type compressor having a discharge chamber with a plurality of pulsation attenuating subchambers
US6293768B1 (en) * 1999-05-11 2001-09-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type compressor
US6862975B2 (en) * 2001-12-21 2005-03-08 Kabushiki Kaisha Toyota Jidoshokki Apparatus for lubricating piston type compressor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100189576A1 (en) * 2009-01-23 2010-07-29 Kabushiki Kaisha Toyota Jidoshokki Piston compressor
US8419382B2 (en) * 2009-01-23 2013-04-16 Kabushiki Kaisha Toyota Jidoshokki Piston compressor
CN103459846A (zh) * 2011-03-31 2013-12-18 株式会社丰田自动织机 斜盘式压缩机
US20130343922A1 (en) * 2011-03-31 2013-12-26 Kabushiki Kaisha Toyota Jidoshokki Swash-plate-type compressor
US20160238001A1 (en) * 2015-02-12 2016-08-18 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type compressor

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JP2010013987A (ja) 2010-01-21
KR20100004046A (ko) 2010-01-12

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AS Assignment

Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SATO, SHINICHI;SAIKI, AKIO;SUGIURA, MANABU;REEL/FRAME:022941/0545

Effective date: 20090629

STCB Information on status: application discontinuation

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