EP1357288A1 - Compresseur - Google Patents

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Publication number
EP1357288A1
EP1357288A1 EP01945621A EP01945621A EP1357288A1 EP 1357288 A1 EP1357288 A1 EP 1357288A1 EP 01945621 A EP01945621 A EP 01945621A EP 01945621 A EP01945621 A EP 01945621A EP 1357288 A1 EP1357288 A1 EP 1357288A1
Authority
EP
European Patent Office
Prior art keywords
communication path
suction
chamber
rear head
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.)
Withdrawn
Application number
EP01945621A
Other languages
German (de)
English (en)
Other versions
EP1357288A4 (fr
Inventor
Keiichi c/o ZEXEL VALEO CLIMATE CONT.CO. MATSUDA
Yukio c/o ZEXEL VALEO CLIMATE CONT.CO. KAZAHAYA
Norikatsu c/o ZEXEL VALEO CLIMATE CONT.CO. KISO
Shoichi c/o ZEXEL VALEO CLIMATE CONT.CO. ENOKIDO
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.)
Valeo Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control 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 Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Publication of EP1357288A1 publication Critical patent/EP1357288A1/fr
Publication of EP1357288A4 publication Critical patent/EP1357288A4/fr
Withdrawn legal-status Critical Current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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings

Definitions

  • the present invention relates to a compressor achieving a structure for preventing pressure waves generated during suction, compression and discharge phases of the compression mechanism.
  • compressors in the related art include the compressor disclosed in Japanese Unexamined Patent Publication No. H 11-351142, comprising at least an air inlet port through which a coolant gas from an evaporator is taken in, a suction chamber for containing the coolant gas having flowed in through the air inlet port, a cam plate that is slidably and tiltably mounted at a rotating shaft and is made to rotate with the rotating shaft, a piston that engages in a reciprocal movement as the cam plate oscillates and a cylinder having the piston slidably inserted therein that is allowed to communicate with the suction chamber or a discharge chamber as necessary, which translates the rotation of the rotating shaft to a reciprocal movement of the piston via the cam plate, takes in and compresses the coolant gas from the suction chamber as the piston reciprocates inside the cylinder and thus changes the volumetric capacity of the cylinder and discharges the compressed coolant gas into the discharge chamber.
  • this compressor includes a clutchless mechanism that sets the discharge capacity to the lowest level by raising the pressure in a crank case and thus minimizing the tilt of the cam plate and, at the same time, stops the coolant gas intake by closing the inlet port so as to circulate the coolant gas inside the compressor to prevent the evaporator from becoming frozen when the load is at the smallest level.
  • the piston engages in a reciprocal movement as the cam plate rotates and a suction valve and a discharge valve open/close as the pressure in the compression space fluctuates to repeat suction, compression and discharge. Since delays in opening/closing the valves and tramping of the valves themselves are bound to occur during this process, pressure waves are released into the suction chamber or the discharge chamber provided between the suction port and the compression space, which may induce a resonance frequency in the chamber to develop into an extremely intense pulsating wave.
  • a pulsating wave occurring on the suction chamber side having a frequency within a specific range of 400 Hz ⁇ 1,000 Hz, which, together with the inherent value (the resonance frequency) of the evaporator, causes a vibration of the evaporator main unit that, in turn, is communicated into the vehicle cabin as unpleasant noise.
  • a damping muffler is provided on a piping to damp the suction pulsation or the suction path of the compressor is constricted as a solution to the problem discussed above in the related art, these measures are bound to increase the production cost and to lower the performance of the compressor.
  • the condenser needs to be installed inside the cabin, which gives a rise to an added problem of noise occurring as a result of a vibration of the condenser caused by the discharge pulsation at the compressor.
  • an object of the present invention is to provide a compressor capable of damping a suction pulsation or a discharge pulsation of the compressor by adopting a simple structure.
  • the compressor according to the present invention having at least a housing constituted of a front head, a cylinder block and a rear head, a compression mechanism that is driven in response to a rotation of a drive shaft passing through the front head, a suction chamber formed at the rear head, at which an inlet port of the compression mechanism opens and a discharge chamber formed at the rear head at which an outlet of the compression mechanism opens, either the suction chamber or the discharge chamber is formed toward the center of the rear head with the other chamber formed further outward relative to the chamber at the center, a tunnel-shaped communication path passing through the suction chamber or the discharge chamber formed toward the center of the rear head and the other chamber formed further outward at the rear head, which communicates the chamber with corresponding port is formed and a muffler space is formed between the communication path and a pipe connection part at which the port is mounted.
  • the suction chamber or the discharge chamber formed toward the center of the rear head is made to communicate with the corresponding port via the tunnel-shaped communication path and a muffler space is formed between the tunnel-shaped communication path and the pipe connection part at which the port is mounted, the suction pulsation can be suppressed if the suction chamber and the pipe connection part at which the suction port is mounted are made to communicate with each other via the communication path and the discharge pulsation can be prevented if the discharge chamber and the pipe connection part at which the discharge port is mounted are made to communicate with each other via the communication path.
  • the muffler space communicate with the outer end of the communication path.
  • the tunnel portion defining the communication path may be formed as an integrated part of the rear head, or a separate pipe member may be inserted at the rear head to form the tunnel.
  • the compression mechanism should include at least a plurality of cylinders formed at the cylinder block, each having an inlet to communicate with the suction chamber and an outlet to communicate with the discharge chamber, pistons each slidably inserted at one of the cylinders so as to freely move reciprocally a rotary cam plate that rotates together with the drive shaft to cause a reciprocal movement of the pistons and a volumetric capacity varying mechanism capable of changing the angle of the rotary cam plate.
  • the communication path be a suction path that communicates between the suction chamber and the corresponding suction port. Since this prevents the pulsating wave on the intake chamber side from resonating with the inherent value (resonance frequency ) of the evaporator, a vibration of the evaporator installed in the cabin can be particularly effectively suppressed or prevented.
  • a small hole to communicate with the suction path be formed at the furthest end of the muffler space so as to allow the oil remaining in the muffler space to return to the suction path. Since a specific effective volumetric capacity and a specific effective length are assured with regard to the muffler space as a result, the capability of the muffler space can be maintained at a desirable level.
  • a valve mechanism capable of opening/closing of the suction path in response to an external signal be provided at the suction path. Since the suction path is shut off even when the pistons are moving over a very small stroke in this structure, the evaporator does not freeze, and a so-called clutchless structure is achieved.
  • the small hole mentioned earlier be formed so as to open toward the upstream side of the valve mechanism. In this case, no bypass passage bypassing the valve mechanism is formed and the clutchless structure can be utilized effectively.
  • a compressor 1 in FIG. 1 includes a housing 5 constituted of a front head 2, a cylinder block 3 and a rear head 4.
  • a rotating shaft 6 passes through the front head 2 and is rotatably supported at the front head 2 and the cylinder block 3.
  • a crank case 7 is formed inside the front head 2, and an opening of the crank case 7 is blocked by the cylinder block 3.
  • a valve plate 8 is clamped and locked between the cylinder block 3 and the rear head 4.
  • a plurality of cylinders 9 extending along the axis of the rotating shaft 6 are formed around the rotating shaft 6 at the cylinder block 3, and an intake 10 and an outlet 11 formed at the valve plate 8 are made to open at each of the cylinders 9.
  • the inlet 10 and the outlet 11 are opened/closed by valve elements.
  • a piston 12 is slidably inserted at each cylinder 9, the end of the piston 12 toward the crank case slidably interlocks with a rotary cam plate 13 and the rotary cam plate 13 is caused to rotate by a rotating plate 14 secured the rotating shaft 6 via a linking mechanism 30.
  • the rotary cam plate 13 is attached to the rotating shaft 6 so that its angle relative to the rotating shaft 6 can be freely adjusted.
  • a baffle plate 31 and a cover 32 are provided on the outside of the cylinder block 3, with a discharge path 15 to communicate with a discharge port (not shown) formed at the cover 32.
  • discharge gas path holes 33a are formed to reduce the extent of the discharge pulsation.
  • a discharge chamber 16 that communicates with the outlet 11 formed at the valve plate 8 is formed ofurther outward at the rear head 4 and a suction chamber 17 to communicate with the suction chamber 10 is formed at the center of the rear head 4.
  • the discharge chamber 16 communicates with the crank case 7 via a pressure control valve 18 mounted at the rear head 4. It is to be noted that the pressure control valve 18 is controlled with an external control signal, that the power supply to the pressure control valve 18 is stopped if the freezing capability is judged to be unnecessary and that the level of the electrical current that is supplied rises as the heat load rises.
  • a suction port 20 at which a suction-side connector 19 connected with the piping and extending from the evaporator (not shown) is mounted, is formed at an external circumferential side surface of the rear head 4.
  • the suction port 20 is made to communicate with the suction chamber 17 via a communication path 21 defined by a tunnel portion 25 which is formed as an integrated part of the rear head 4.
  • a cutoff valve 22 that opens/closes the communication path 21 is provided on the communication path 21 and the communication path 21 is blocked by the cutoff valve 22 when the freezing operation is judged to be unnecessary so as to ensure that no coolant gas is taken in from the evaporator.
  • a muffler space 23 is formed around the tunnel portion 25 defining the communication path 21, as shown in FIGS. 1 and 2.
  • One end of the muffler space 23 opens at the suction port 20 and a small hole 24 which communicates with the upstream side of the cutoff valve 22 at the communication path 21 is formed at the other end (the furthest end).
  • the muffler space 23 be formed over a length of approximately 30mm along the communication path 21 around the tunnel portion 25.
  • a damping peak frequency of approximately 800 Hz is achieved. Under normal circumstances, it is desirable to estimate the damping frequency relative to the length of the muffler space 23 through the finite element method and to set the length of the muffler space 23 in correspondence to the desired damping frequency band.
  • the rotating plate 14 fixed to the rotating shaft 6 also rotates, which, in turn, causes the rotary cam plate 13 to rotate and oscillate via the linking mechanism 30.
  • the rotary cam plate 13 rotates and oscillates, with the pistons 12 each having one end thereof slidably fixed to the rotary cam plate 13 make reciprocal movement relative to the cylinders 9, thereby changing the volumetric capacity of the compression space defined by the pistons 12 and the cylinders 9.
  • the coolant gas is taken in from the suction chamber 17, becomes compressed and is discharged into the discharge chamber 16.
  • the coolant gas having been evaporated at the evaporator is taken into the suction chamber 17 from the suction port 20 via the communication path 21, becomes compressed and is then let out from the discharge chamber 16 through the discharge path 15 to the next process, e.g., to the condenser.
  • the high-level pressure supplied to the crank case 7 is reduced through the pressure control valve 18 to lower the pressure in the crank case and thus, the back pressure at the pistons 12 is lowered.
  • the stroke of the pistons 12 becomes larger to increase the quantity of the discharge from the compressor 1.
  • the high-level pressure is supplied to the crank case 7 through the pressure control valve 18, thereby raising the back pressure of the pistons 12 and, as a result, the stroke of the pistons 12 becomes smaller to reduce the quantity of the discharge from the compressor 1.
  • the communication path 21 is blocked with the cutoff valve 22, and thus, the coolant gas supply to the suction chamber 17 stops. In this case, the coolant gas is made to circulate inside the compressor 1 with the compressor 1 discharging no coolant gas, thereby achieving a clutchless compressor.
  • the individual phases e.g., the suction phase
  • the individual phases are executed intermittently with the plurality of pistons 12 and, as a result, a pressure fluctuation occurs, for instance, in the suction chamber 17, which is then transmitted toward the evaporator as a pulsating wave.
  • this pulsating wave would be communicated as unpleasant noise if its frequency matched the resonance frequency of the evaporator (which varies depending upon the model but is normally within a range of 300 Hz ⁇ 1,000 Hz).
  • the pulsating wave can be damped in the frequency band.
  • a communication path that communicates between a discharge chamber and a discharge port may be provided by forming the discharge chamber toward the center of the rear head 4 and forming a suction chamber around the discharge chamber and a muffler space to communicate with this communication path may be formed around the communication path.
  • the small hole 24 which communicates between the muffler space 23 and the upstream side of the cutoff valve 22 at the communication path 21 is formed at the furthest end of the muffler space 23 so as to prevent stagnation of the oil in the muffler space 23.
  • the damping effect achieved by providing the muffler space 23 normally corresponds to the length (depth) of the muffler space 23. For this reason, the small hole 24 is formed to prevent any stagnation of the oil so as to ensure that the damping target frequency band does not change due to a change in the depth of the muffler space 23 caused by remaining oil in the muffler space 23.
  • the diameter of the small hole 24 may be varied to achieve an intentional change in the damping frequency band.
  • the suction chamber 17and the suction port 20 are not allowed to communicate with age other via the small hole 24 when the communication path 21 is blocked by the cutoff valve 22 and, as a result, the communication path 21 is blocked with a high degree of reliability.
  • the pulsating wave generated at the suction side or the discharge side can be damped to prevent unpleasant noise in the cabin.
  • the muffler space is formed at the external circumference of the tunnel portion which defines the communication path at the rear head and thus the communication path can be formed as an integrated part of the rear head, the production cost does not go up. Even when the communication path is formed by using a separate part, the communication path can be formed with ease by forming spaces to constitute the communication path and the muffler space in advance at the rear head and then mounting a pipe for defining the communication path subsequently. Thus, an increase in the production cost can be minimized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP01945621A 2000-12-28 2001-06-27 Compresseur Withdrawn EP1357288A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2000399676A JP2002202054A (ja) 2000-12-28 2000-12-28 圧縮機
JP2000399676 2000-12-28
PCT/JP2001/005489 WO2002053913A1 (fr) 2000-12-28 2001-06-27 Compresseur

Publications (2)

Publication Number Publication Date
EP1357288A1 true EP1357288A1 (fr) 2003-10-29
EP1357288A4 EP1357288A4 (fr) 2004-03-03

Family

ID=18864407

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01945621A Withdrawn EP1357288A4 (fr) 2000-12-28 2001-06-27 Compresseur

Country Status (4)

Country Link
US (1) US20040052648A1 (fr)
EP (1) EP1357288A4 (fr)
JP (1) JP2002202054A (fr)
WO (1) WO2002053913A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7181926B2 (en) 2005-05-23 2007-02-27 Visteon Global Technologies, Inc. Oil separator and muffler structure
JP4888803B2 (ja) 2005-07-04 2012-02-29 株式会社ヴァレオジャパン 圧縮機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1972750A (en) * 1932-07-30 1934-09-04 Westinghouse Air Brake Co Air compressor
JPH07139463A (ja) * 1993-11-12 1995-05-30 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH09273477A (ja) * 1996-04-05 1997-10-21 Sanden Corp 往復動圧縮機
JP2000249059A (ja) * 1999-03-01 2000-09-12 Toyota Autom Loom Works Ltd 圧縮機の吸入マフラ構造

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51105608A (fr) * 1975-03-13 1976-09-18 Sentoraru Jidosha Kogyo Kk
JP2000337255A (ja) * 1999-05-26 2000-12-05 Toyota Autom Loom Works Ltd 減衰装置及び圧縮機の吸入構造
JP2001041160A (ja) * 1999-07-28 2001-02-13 Toyota Autom Loom Works Ltd 圧縮機の脈動減衰構造
KR100576631B1 (ko) * 1999-12-21 2006-05-04 한라공조주식회사 맥동압 저감구조를 가지는 압축기

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1972750A (en) * 1932-07-30 1934-09-04 Westinghouse Air Brake Co Air compressor
JPH07139463A (ja) * 1993-11-12 1995-05-30 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH09273477A (ja) * 1996-04-05 1997-10-21 Sanden Corp 往復動圧縮機
JP2000249059A (ja) * 1999-03-01 2000-09-12 Toyota Autom Loom Works Ltd 圧縮機の吸入マフラ構造

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 08, 29 September 1995 (1995-09-29) & JP 07 139463 A (TOYOTA AUTOM LOOM WORKS LTD), 30 May 1995 (1995-05-30) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 02, 30 January 1998 (1998-01-30) & JP 09 273477 A (SANDEN CORP), 21 October 1997 (1997-10-21) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 12, 3 January 2001 (2001-01-03) & JP 2000 249059 A (TOYOTA AUTOM LOOM WORKS LTD), 12 September 2000 (2000-09-12) *
See also references of WO02053913A1 *

Also Published As

Publication number Publication date
WO2002053913A1 (fr) 2002-07-11
EP1357288A4 (fr) 2004-03-03
JP2002202054A (ja) 2002-07-19
US20040052648A1 (en) 2004-03-18

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