EP1384888A2 - Kolbenverdichter - Google Patents

Kolbenverdichter Download PDF

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Publication number
EP1384888A2
EP1384888A2 EP03015179A EP03015179A EP1384888A2 EP 1384888 A2 EP1384888 A2 EP 1384888A2 EP 03015179 A EP03015179 A EP 03015179A EP 03015179 A EP03015179 A EP 03015179A EP 1384888 A2 EP1384888 A2 EP 1384888A2
Authority
EP
European Patent Office
Prior art keywords
suction
guiding hole
rotary valve
type compressor
piston type
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Withdrawn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
EP03015179A
Other languages
English (en)
French (fr)
Other versions
EP1384888A3 (de
Inventor
Masaki Ota
Kenji Mochizuki
Hisato Kawamura
Yoshinori Inoue
Junichi Takahata
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 EP1384888A2 publication Critical patent/EP1384888A2/de
Publication of EP1384888A3 publication Critical patent/EP1384888A3/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Withdrawn legal-status Critical Current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
    • 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
    • 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 piston type compressor for compressing a gas by reciprocation of a piston.
  • a reed valve type of suction valve causes abnormal sound due to self-exited vibration and thereby obstructs a silent operation of the compressor.
  • Japanese Unexamined Patent Publication No. 5-164044 discloses a rotary valve, which does not cause self-exited vibration, in a piston type compressor. The rotary valve is used as a suction valve.
  • the compressor has a plurality of cylinder bores and a valve accommodating chamber therein.
  • a suction communicating passage is formed for interconnecting the respective cylinder bore with the valve accommodating chamber.
  • a rotary valve is accommodated in the valve accommodating chamber.
  • the rotary valve has a suction guiding hole for communicating with the suction communicating passage in a suction process.
  • the suction guiding hole has a first end surface at a preceding side in a rotational direction of the rotary valve and a second end surface at a following side in the rotary direction. The rotation of the rotary valve is adjusted in a such manner that the first end surface of the suction guiding hole meets the suction communicating passage after compressed gas remaining in a top clearance of the compression chamber finishes re-expansion.
  • a notch is formed on the outer circumferential surface of the rotary valve near the first end surface of the suction guiding hole, otherwise, the notch is formed on the inner circumferential surface of the valve accommodating chamber near the suction communicating passage. The notch allows inflow and outflow of a small amount of gas until the first end surface meets the suction communicating passage after the remaining compressed gas finishes the re-expansion.
  • first time that the remaining gas in a working chamber of the cylinder bore finishes the re-expansion is compared with second time that the rotary valve starts intake through the notch.
  • the notch reduces the amount of the remaining gas that flows backward from the suction communicating passage toward the suction guiding hole of the rotary valve.
  • a small-sized notch is formed only on the first end surface of the suction guiding hole and nothing is performed on the second end surface. Therefore, in a structure where the suction guiding hole of the rotary valve simultaneously communicates with a plurality of the cylinder bores, a total amount of intake gas is obtained by adding each amount of gas drawn into the respective cylinder bores, which communicates with the suction guiding hole. In that case, as shown in FIG. 4A, suction pulsation caused due to a rapid increase of gas that is drawn into the working chambers of the cylinder bores, which communicates with the suction guiding hole, is not sufficiently reduced. Therefore, the object of the prior art, that is, restraining the noise of the compressor, is not sufficiently accomplished.
  • the present invention directed to a piston type compressor whose suction pulsation and noise are restrained.
  • a piston type compressor includes a housing, a drive shaft, a cam, a piston, a refrigerant gas passage and a rotary valve.
  • the housing defines a suction pressure region.
  • the housing includes a cylinder block which defines a plurality of cylinder bores to form a compression chamber.
  • the drive shaft is supported for rotation by the housing.
  • the cam is operatively connected to the drive shaft.
  • the piston is accommodated in each cylinder bore.
  • the piston is operatively connected to the cam so as to be reciprocated by converting the rotation of the drive shaft.
  • the reciprocation of the piston varies a volume of the compression chamber.
  • the refrigerant gas passage interconnects the suction pressure region with at least one of the compression chambers.
  • the rotary valve is integrally formed with the drive shaft so as to synchronously rotate with the drive shaft.
  • the rotary valve includes a suction guiding hole which forms a part of the refrigerant gas passage.
  • the suction guiding hole connects each compression chamber by turns with the suction pressure region as the rotary valve is rotated.
  • the suction guiding hole communicates with a plurality of the compression chambers at least at early and last stages in a suction process.
  • the suction guiding hole has a first end formed at a preceding side in a rotational direction of the rotary valve.
  • the suction guiding hole also has a second end formed at a following side in the rotational direction of the rotary valve.
  • the suction guiding hole further has a middle between the first end and the second end.
  • the suction guiding hole further has a predetermined area per unit length in the rotational direction. The predetermined area gradually increases from the first end to the middle and gradually decreases from the middle to the second end.
  • FIG. 1 A variable displacement piston type compressor for use in a vehicle air conditioning apparatus according to a preferred embodiment of the present invention will now be described with reference to FIG. 1.
  • a left side of FIG. 1 is a front side and a right side thereof is a rear side.
  • a variable displacement piston type compressor includes a cylinder block 11, a front hosing 12 and a rear housing 14.
  • the variable displacement piston type compressor is hereinafter referred to as a compressor.
  • the cylinder block 11 is made of metallic material of aluminum series.
  • the front end of the cylinder block 11 is joined to the rear end of the front housing 12.
  • the rear end of the cylinder block 11 is joined to the front end of the rear housing 14 through a valve plate assembly 13.
  • the cylinder block 11, the front housing 12 and the rear housing 14 form a compressor housing.
  • the cylinder block 11 and the front housing 12 define a crank chamber 15.
  • a drive shaft 16 is supported for rotation by the compressor housing.
  • the drive shaft 16 is made of metallic material of iron series and is connected to an engine for operation.
  • the engine serves as a drive source for running a vehicle and is not shown in the drawing.
  • the drive shaft 16 is rotated under power of the engine.
  • a lug plate 21 is fixed on the drive shaft 16 so as to integrally rotate with the drive shaft 16.
  • a swash plate 23 that serves as a cam is accommodated in the crank chamber 15.
  • a hinge mechanism 24 is interposed between the lug plate 21 and the swash plate 23.
  • the swash plate 23 is connected to the lug plate 21 through the hinge mechanism 24 and is supported by the drive shaft 16. Therefore, the swash plate 23 is synchronously rotated with the lug plate 21 and the drive shaft 16. At the same time, the swash plate 23 is inclined relative to a rotary axis of the drive shaft 16 while moving slidably along the direction of the rotary axis of the drive shaft 16.
  • a plurality of cylinder bores 11a is formed through the cylinder block 11 so as to surround the rear side of the drive shaft 16, although only one cylinder bore is illustrated in FIG. 1.
  • a single-head piston 25 is accommodated for reciprocation in each cylinder bore 11 a.
  • the single-head piston 25 is hereinafter referred to as a piston 25.
  • the front opening of each cylinder bore 11a is blocked by the associated piston 25 and the rear opening of each cylinder bore 11 a is blocked by the valve plate assembly 13.
  • a compression chamber 26, whose volume is varied in accordance with the reciprocation of the associated piston 25, is defined.
  • Each piston 25 is engaged with the periphery of the swash plate 23 through a pair of shoes 27. Therefore, the rotation of the swash plate 23, which is accompanied by the rotation of the drive shaft 16, is converted to the reciprocation of the pistons 25 through the shoes 27.
  • a suction chamber 28 and a discharge chamber 29 are defined.
  • the suction chamber 28 is located substantially at the middle of the rear housing 14 while the discharge chamber 29 is located so as to surround the outer circumference of the suction chamber 28.
  • the valve plate assembly 13 includes discharge ports 32 and discharge valves 33. Each discharge port 32 interconnects the associated compression chamber 26 with the discharge chamber 29.
  • Each discharge valve 33 which is a reed valve, opens and closes the associated discharge port 32.
  • a suction valve mechanism 35 which includes a rotary valve 41, is provided in the cylinder block 11.
  • a refrigerant gas in the suction chamber 28 is drawn into each compression chamber 26 through the suction valve mechanism 35 while the associated piston 25 moves from the top dead center thereof to the bottom dead center thereof.
  • the refrigerant gas, which is drawn into the compression chamber 26 is compressed to a predetermined pressure value while the associated piston 25 moves from the bottom dead center thereof to the top dead center thereof, and the compressed refrigerant gas is discharged to the discharge chamber 29 through the discharge port 32 by pushing the associated discharge valve 33 aside.
  • a valve accommodating chamber 42 which is surrounded by the cylinder bores 11a, is formed from the middle of the cylinder block 11 to the middle of the rear housing 14.
  • the valve accommodating chamber 42 which has a cylindrical shape, communicates with the suction chamber 28 at the rear side thereof.
  • a suction communicating passage 43 which is illustrated in FIG. 3, is formed in the cylinder block 11 for interconnecting the valve accommodating chamber 42 with the respective compression chamber 26 in the suction process.
  • the rotary valve 41 is accommodated for rotation.
  • the rotary valve 41 has a cylindrical shape and openings to the suction chamber 28 and the crank chamber 15.
  • An installation hole 41 a is formed on the opening of the rotary valve 41 at the side of the crank chamber 15.
  • the rotary valve 41 is made of metallic material of aluminum series.
  • the rear end of the drive shaft 16 is placed in the valve accommodating chamber 42.
  • a minor diametrical portion 16a is provided with the rear end of the drive shaft 16 and is fixedly press-fitted into the installation hole 41 a of the rotary valve 41. Therefore, the rotary valve 41 and the drive shaft 16 are unified so as to serve as a single shaft and have a common rotary axis. That is, the rotary valve 41 is synchronously rotated with the rotation of the drive shaft 16, that is, the reciprocation of each piston 25.
  • an introducing chamber 44 is formed in the rotary valve 41 so as to communicate with the suction chamber 28. That is, the suction chamber 28 and the introducing chamber 44 are equivalent to a suction pressure region.
  • a suction guiding hole 45 is formed in the outer circumferential surface 41 b of the rotary valve 41 in a predetermined range of a rotational direction of the rotary valve 41.
  • the suction guiding hole 45 has a substantially oval shape and has a major axis along the rotational direction.
  • the suction guiding hole 45 extends from the outer circumferential surface 41b to the introducing chamber 44 and continuously communicates with the introducing chamber 44. That is, as shown in FIG.
  • the suction guiding hole 45 has a predetermined area Sn per unit length ⁇ L in the rotational direction of the rotary valve 41.
  • the predetermined area Sn gradually increases from a first end surface 45a, which serves as a first end, formed at a preceding side in the rotational direction to a middle 45c of the oval shape.
  • the predetermined area Sn gradually decreases from the middle 45c to a second end surface 45b, which serves as a second end, formed at a following side in the rotational direction.
  • the middle 45c is located between the first end surface 45a and the second end surface 45b.
  • the suction guiding hole 45 and each suction communicating passage 43 form a refrigerant gas passage for interconnecting the introducing chamber 44 with at least the one compression chamber 26.
  • the suction guiding hole 45 connects each compression chamber 26 by turns with the suction pressure region.
  • the rotary valve 41 is moved in a such manner that the first end surface 45a of the suction guiding hole 45, which precedes in the rotational direction of the rotary valve 41, opens the suction communicating passage 43 of the cylinder block 11. Therefore, the refrigerant gas in the suction chamber 28 is drawn into the compression chamber 26 through the introducing chamber 44 of the rotary valve 41, the suction guiding hole 45, and the suction communicating passage 43 of the cylinder block 11.
  • the suction guiding hole 45 continuously communicates with at least the one suction communicating passage 43. Meanwhile, as described above, since the suction guiding hole 45 is formed in the oval shape, an amount of the refrigerant gas, which is drawn into the compression chamber 26, continuously increases until the suction communicating passage 43 relatively reaches the middle 45c of the suction guiding hole 45 from the beginning of the suction stroke. That is, the amount of the refrigerant gas gradually increases. In contrast, after the suction communicating passage 43 relatively passes through the middle 45c of the suction guiding hole 45, the amount of the refrigerant gas, which is drawn into the compression chamber 26, continuously decreases. That is, the amount of the refrigerant gas gradually decreases.
  • the rotary valve 41 is moved in a such manner that the second end surface 45b of the suction guiding hole 45, which follows in the rotational direction of the rotary valve 41, closes the suction communicating passage 43 of the cylinder block 11. Thereby, the introduction of the refrigerant gas drawn into the compression chamber 26 is stopped. Subsequently, when the piston 25 is shifted to the discharge stroke, the suction communicating passage 43 is closed by the outer circumferential surface 41 b of the rotary valve 41. Therefore, the refrigerant gas in the suction chamber 28 is not leaked through the suction communicating passage 43. Thereby, the compression of the refrigerant gas and the discharge of the refrigerant gas to the discharge chamber 29 are not prevented.
  • the suction guiding hole 45 communicates with two compression chambers 26 (A, E). Also, at a last stage in the suction process, that is, while the predetermined area, by which the suction guiding hole 45 communicates with the suction communicating passage 43, gradually decreases, the suction guiding hole 45 communicates with two compression chambers 26 (A, E). Furthermore, during a slight time in the suction process, that is, at a stage other than the early and last stage in the suction process, the suction guiding hole 45 communicates with only one compression chamber 26.
  • the suction guiding hole 45 has an opening angle ⁇ in the rotational direction of the rotary valve 41. The opening angle a is set so as to fulfill the communicating state.
  • the suction guiding hole 45 has the oval shape. In an alternative embodiment to the embodiment, however, the suction guiding hole 45 has, as shown in FIG. 5, a substantially rhombic shape. In this structure, similar effects to the above-described effects are also obtained.
  • the suction guiding hole 45 communicates with two compression chambers 26 at the early and last stages in the suction process.
  • the opening angle of the suction guiding hole 45 is set in a such manner that the suction guiding hole 45 communicates with three compression chambers 26 at the early and last stages in the suction process.
  • similar effects (1) through (3) are also obtained.
  • the total amount of intake gas is increased. Thereby, cooling capacity of the compressor is increased.
  • the rotary valve 41 is made of metallic material of aluminum series. In alternative embodiments to the embodiment, however, the rotary valve 41 is made of metallic material of iron series or resin. Furthermore, the rotary valve 41 may be coated with resin.
  • the present invention is applied to a single-head piston type compressor. In an alternative embodiment to the embodiment, however, the present invention is applied to a double-head piston type compressor.
  • the swash plate 23 is adopted as a cam.
  • a wave cam is adopted as the cam and the present invention is applied to a piston type compressor, which is a wave cam type.
  • a piston type compressor includes a housing, a refrigerant gas passage and a rotary valve.
  • the housing defines a suction pressure region.
  • the refrigerant gas passage interconnects the suction pressure region with at least a compression chamber.
  • the rotary valve includes a suction guiding hole which forms a part of the refrigerant gas passage.
  • the suction guiding hole connects each compression chamber by turns with the suction pressure region as the rotary valve is rotated.
  • the suction guiding hole communicates with a plurality of the compression chambers at least at early and last stages in a suction process.
  • the suction guiding hole has a predetermined area per unit length in a rotational direction of the rotary valve. The predetermined area gradually increases from a preceding side of the rotation of the rotary valve to a middle and gradually decreases from the middle to a following side of the rotary valve.

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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)
  • Applications Or Details Of Rotary Compressors (AREA)
EP03015179A 2002-07-05 2003-07-03 Kolbenverdichter Withdrawn EP1384888A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002196599 2002-07-05
JP2002196599A JP2004036548A (ja) 2002-07-05 2002-07-05 ピストン式圧縮機

Publications (2)

Publication Number Publication Date
EP1384888A2 true EP1384888A2 (de) 2004-01-28
EP1384888A3 EP1384888A3 (de) 2005-03-09

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ID=29997054

Family Applications (1)

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EP03015179A Withdrawn EP1384888A3 (de) 2002-07-05 2003-07-03 Kolbenverdichter

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US (1) US20040005224A1 (de)
EP (1) EP1384888A3 (de)
JP (1) JP2004036548A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1953385A3 (de) * 2007-02-02 2013-08-14 Kabushiki Kaisha Toyota Jidoshokki Taumelscheibenverdichter

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016133094A (ja) * 2015-01-21 2016-07-25 株式会社豊田自動織機 両頭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
JPH05164044A (ja) * 1991-12-17 1993-06-29 Toyota Autom Loom Works Ltd ピストン型圧縮機における冷媒ガス吸入案内機構
US5232349A (en) * 1991-09-01 1993-08-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Axial multi-piston compressor having rotary valve for allowing residual part of compressed fluid to escape
US5342178A (en) * 1992-01-29 1994-08-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in compressor
EP0979942A2 (de) * 1998-08-10 2000-02-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variabler Verdrängungskompressor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2295862A (en) * 1942-05-04 1942-09-15 Reed Roller Bit Co Valve
US2902253A (en) * 1956-10-18 1959-09-01 George D Page Rotary plug valve
US3204534A (en) * 1963-01-24 1965-09-07 Raymond Int Inc Drawbar multiplier
US3516437A (en) * 1968-05-17 1970-06-23 Walter E Folkerts Valve for automobile power steering gear
US4993453A (en) * 1986-06-16 1991-02-19 Agf Manufacturing, Inc. Valve and arrangement for fire suppression water sprinkler system
US5242150A (en) * 1992-09-30 1993-09-07 The United States Of America As Represented By The Secretary Of The Navy Rotary hydraulic servo or throttle valve
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5232349A (en) * 1991-09-01 1993-08-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Axial multi-piston compressor having rotary valve for allowing residual part of compressed fluid to escape
JPH05164044A (ja) * 1991-12-17 1993-06-29 Toyota Autom Loom Works Ltd ピストン型圧縮機における冷媒ガス吸入案内機構
US5342178A (en) * 1992-01-29 1994-08-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in compressor
EP0979942A2 (de) * 1998-08-10 2000-02-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variabler Verdrängungskompressor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 017, no. 572 (M-1497), 18 October 1993 (1993-10-18) & JP 05 164044 A (TOYOTA AUTOM LOOM WORKS LTD), 29 June 1993 (1993-06-29) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1953385A3 (de) * 2007-02-02 2013-08-14 Kabushiki Kaisha Toyota Jidoshokki Taumelscheibenverdichter

Also Published As

Publication number Publication date
US20040005224A1 (en) 2004-01-08
JP2004036548A (ja) 2004-02-05
EP1384888A3 (de) 2005-03-09

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