WO2002066831A1 - Compresseur - Google Patents

Compresseur Download PDF

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Publication number
WO2002066831A1
WO2002066831A1 PCT/JP2001/005490 JP0105490W WO02066831A1 WO 2002066831 A1 WO2002066831 A1 WO 2002066831A1 JP 0105490 W JP0105490 W JP 0105490W WO 02066831 A1 WO02066831 A1 WO 02066831A1
Authority
WO
WIPO (PCT)
Prior art keywords
space
pressure space
muffler
compressor
suction
Prior art date
Application number
PCT/JP2001/005490
Other languages
English (en)
Japanese (ja)
Inventor
Yukio Kazahaya
Norikatsu Kiso
Keiichi Matsuda
Shoichi Enokido
Hiromichi Tanabe
Masahito Shimada
Hiroyuki Ishida
Original Assignee
Zexel Valeo Climate Control Corporation
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 Corporation filed Critical Zexel Valeo Climate Control Corporation
Publication of WO2002066831A1 publication Critical patent/WO2002066831A1/fr

Links

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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • 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
    • 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
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes

Definitions

  • the present invention relates to a compressor having a configuration for preventing a pulsating wave generated during a suction, compression, and discharge stroke of a compression mechanism.
  • Japanese Patent Application Laid-Open No. H11-1351142 discloses a suction port for sucking the refrigerant gas from the evaporator, a suction space for containing the refrigerant gas flowing from the suction port, and a rotation.
  • a swash plate that is slidably and tiltably mounted on the shaft, and that rotates integrally with the rotary shaft, a biston that reciprocates by the swinging motion of the swash plate, and the piston is slidably inserted.
  • a compressor that sucks and compresses refrigerant gas in a suction space and discharges the refrigerant gas to a discharge space.
  • the compressor raises the pressure in the crankcase to minimize the inclination of the swash plate to minimize the discharge capacity, and at the same time, closes the suction inlet to draw refrigerant gas. It has a clutchless mechanism that stops the evaporator and circulates the refrigerant gas in the compressor to prevent the evaporator from freezing.
  • the piston reciprocates with the rotation of the swash plate, and the suction valve and the discharge valve open and close in response to pressure fluctuations in the compression chamber. Compression and discharge are repeated. At this time, the opening and closing of the valve may be delayed, and the valve itself may flutter. Alternatively, a pressure wave may be released into a suction space or a discharge space (pressure space) provided between a discharge port and a compression chamber, and a resonance frequency in the chamber may be induced to grow as a very strong pulsating wave.
  • the outer pressure space has a circumference of 220 to 320 mm with a standard compressor, so It has a resonance frequency in the range of z to 70OHZ, and when combined with the eigenvalue (resonance frequency) of the heat exchanger, causes the heat exchanger body to vibrate, causing unpleasant noise to be transmitted to the passenger compartment as a problem.
  • damping mufflers were installed on the pipes to attenuate the suction pulsation, and the suction passage of the compressor was throttled. There is a problem that it causes a decrease.
  • the capacitor is arranged in the cabin, and the capacitor also vibrates due to pulsation waves generated by the discharge pulsation of the compressor. It was a source of noise.
  • an object of the present invention is to provide a compressor capable of attenuating vibration and noise caused by a pulsating wave with a simple structure. Disclosure of the invention
  • the present invention provides a housing including a front head, a cylinder block, and a rear head, and a compression mechanism provided in the housing and driven by rotation of a drive shaft provided through the front head.
  • a first pressure space located at the center of the rear head and communicating with one of a suction side and a discharge side of the compression mechanism; and a first pressure space formed outside the first pressure space.
  • the second pressure space formed outside the first pressure space is provided with the opening of the suction port or the discharge port communicating with the second pressure space (specifically, It has a predetermined length in the vicinity of the opening of the discharge port when the second pressure space is a discharge space, and the opening of the suction port when the second pressure space is a suction space. Since the muffler space is formed, the pulsation wave generated in the second pressure space by the compression mechanism, in particular, the pulsation wave having a resonance frequency of the second pressure space is attenuated in the muffler space having a predetermined length.
  • Pulsation waves and vibrations from the compressor discharge or suction port can be suppressed, preventing resonance in the heat exchanger (condenser on the discharge side, evaporator on the suction side), and noise in the vehicle interior Prevent Can and child.
  • the pipe end becomes a peak of the pulsation characteristic and the open end becomes a valley, so if the predetermined length is L and the sound speed of the refrigerant is C, (2 n-1).
  • the attenuation becomes maximum at the frequency where C / 4 L (n is a natural number).
  • the pulsation near 500, 1500, 2500---Hz can be attenuated.
  • the attenuation characteristics may be shifted to the low frequency side or high frequency side due to the uneven shape such as ribs in the muffler space. Therefore, it is desirable to accurately analyze by the finite element method.
  • the muffler space includes a pair of circumferential shielding portions defining a predetermined length in the circumferential direction from the vicinity of the opening, and an axial shielding fixed to axial ends of the pair of circumferential shielding portions.
  • the muffler space and the second pressure space are desirably communicated with each other by a gas passage hole formed in the axial shielding portion.
  • the circumferential shielding portion may be formed integrally with the rear head.
  • the axial shielding portion may be a shielding plate fixed to an axial end of the circumferential shielding portion.
  • a stepped portion with which the shielding plate abuts is formed at a peripheral edge of the muffler space.
  • an elastic member that seals around the shielding plate is coated around the shielding plate, and a sealing member made of an elastic member is provided between the shielding plate and the step portion. May be pinched and fixed. Thereby, the sealing performance at the peripheral edge of the shielding plate can be improved, and the pulsation wave attenuation can be further improved.
  • the opening of the suction port or the discharge port communicating with the second pressure space and the gas passage hole may open substantially at the center of the muffler space.
  • the opening of the suction port or the discharge port communicating with the gas passage hole and the gas passage hole may open at one end of the muffler space. Accordingly, when the opening of the suction port or the discharge port communicating with the second pressure space and the gas passage hole are set at substantially the center of the muffler space, the predetermined length L is set to be short. When the opening of the suction port or the discharge port communicating with the second pressure space and the gas passage hole are set at one end of the muffler space, the predetermined length L Can be set longer.
  • the position of the opening of the suction port or the discharge port and the position of the gas passage hole can be set in accordance with this frequency.
  • FIG. 1 is a side sectional view of a compressor according to a first embodiment of the present invention
  • FIG. 2 is a front view of a rear head of the compressor according to the first embodiment of the present invention
  • FIG. 3 is a plan view of an axial shielding plate according to the first embodiment of the present invention
  • FIG. 4 is a side view of a rear head of the compressor according to the first embodiment of the present invention
  • FIG. 5 is a side cross-sectional view of a compressor according to a second embodiment of the present invention
  • FIG. 6 is a cross-sectional view of the compressor according to the second embodiment of the present invention.
  • FIG. 7 is a front view of a rear head
  • FIG. 7 is a plan view of an axial shielding plate according to a second embodiment of the present invention
  • FIG. 8 is a plan view of an axial shielding plate according to a third embodiment of the present invention
  • FIG. 9 is a front view of a rear head of the compressor
  • FIG. 9 is a view showing an A-A part of a muffler space according to a third embodiment of the present invention.
  • FIG. 10 is an explanatory sectional view of a portion BB of the muffler space according to the third embodiment of the present invention
  • FIG. 11 is a sectional view of the fourth embodiment of the present invention
  • FIG. 12 is an explanatory sectional view of a B-B portion of the muffler space according to the embodiment, and FIG.
  • FIG. 12 is a state in which a shield plate of a rear head of a compressor according to a fifth embodiment of the present invention is mounted.
  • FIG. 13 is a front view of a compressor according to a fifth embodiment of the present invention, before a shield plate is attached to a rear head, and
  • FIG. 14 is a front view of the compressor.
  • FIG. 15 is an explanatory sectional view of a C-C part of a muffler space according to a fifth embodiment of the present invention.
  • the compressor 1 shown in FIG. 1 has a housing 5 including a front head 2, a cylinder block 3, and a rear head 4.
  • the rotary shaft 6 penetrates the front head 2 and is rotatably supported by the front head 2 and the cylinder block 3. Is transmitted and rotated.
  • a crank chamber 8 is defined in the front head 2, and an opening of the crank chamber 8 is closed by the cylinder block 3.
  • a valve plate 9 is sandwiched and fixed between the cylinder block 3 and the rear head 4.
  • the cylinder block 3 is formed around the rotary shaft 6 with a plurality of cylinders 10 extending in the axial direction of the rotary shaft 6.
  • the formed suction port 11 and discharge port 12 are opened.
  • the discharge port 12 is opened and closed by a valve 13.
  • a piston 14 is slidably inserted into each cylinder 10, and an end of each piston 14 on the crank chamber 8 side is slidably attached to the rotary swash plate 15,
  • the rotary swash plate 15 is rotated by a rotary plate 17 fixed to the rotary shaft 6 via a coupling mechanism 16.
  • the rotation swash plate 15 is mounted on the rotation shaft 6 so that the angle of the rotation swash plate 15 can be freely changed with respect to the rotation shaft 6.
  • a central portion of the rear head 4 communicates with a suction port 11 formed in the valve plate 9.
  • a suction space (first pressure space) 18 is formed, and the suction space 18 communicates with the suction port 20.
  • a discharge space (second pressure space) 19 is formed in an annular shape on the outer peripheral portion of the suction space 18.
  • the discharge space 19 is formed in an annular groove 21 formed in an annular shape around the concave portion 25 forming the suction space 18 of the rear head 4.
  • the annular groove 21 is formed by dividing the vicinity of the opening 22 a of the discharge port 22 of the annular groove 21 into a predetermined range (a predetermined length) in the circumferential direction to form a muffler space.
  • a pair of circumferential shielding portions 24 that define the grooves 23 are provided.
  • a muffler space 27 is defined by fixing an axial shielding plate 26 as shown in FIG. 3 to the axial ends of the pair of circumferential shielding portions 24. Things.
  • the muffler space 27 communicates with the discharge space 19 via a gas passage hole 28 formed in the axial shielding plate 26.
  • the axial shielding plate 26 is formed by screwing a screw 29 into a screw hole 40 formed at an axial end of the circumferential shielding portion 24, thereby forming the circumferential shielding plate 26. It is fixed to the part 24, but may be formed integrally with the rear head 4 when the rear head 4 is formed.
  • the distance from the opening 22 a of the discharge port 22 and the gas passage hole 28 to the circumferential shielding part 24 causes the pulsating wave generated in the discharge space 19. It is set to the length L that can be attenuated.
  • the tube end becomes a peak of the pulsation characteristic and the open end becomes a valley, so that the frequency becomes (2 n-1) ⁇ CZ 4 L At which the attenuation peaks.
  • the gas passage hole 28 and the opening 22 of the discharge port 22 from the circumferential shielding part 24 on one or both sides are formed.
  • the pulsation in the vicinity of 500,150,250,000 Hz can be attenuated.
  • the attenuation characteristics of the muffler space 27 may be shifted to the low or high frequency side due to the unevenness of the ribs and the like in the muffler space 27. desirable.
  • the refrigerant gas evaporated in the evaporator which is the previous step of the refrigeration cycle, is drawn into the compression chamber 30 from the suction port 20 through the suction space 18, compressed, and discharged into the discharge space 19. Then, the gas is sent to the next process from the discharge port 22 via the muffler space 27 via the gas passage hole 28, for example, to the condenser.
  • the refrigerant gas is sucked, compressed and discharged by the suction, compression, and discharge strokes of the compressor 1, but even if the suction stroke is taken, it is intermittently executed by the multiple pistons 14 Therefore, pressure fluctuation occurs in the discharge space 19 and resonates in the discharge space 19 as a pulsating wave, but the pulsating wave can be attenuated in the muffler space 27.
  • resonance in the capacitor causes a problem as noise. It can prevent the generation of noise.
  • the compressor is configured such that the discharge space is the first pressure space and the suction space is the second pressure space. Since the pulsating waves generated in the second pressure space can be attenuated in the muffler space, it is possible to prevent the generation of noise in the evaporator.
  • the second embodiment of the present invention shown in FIGS. 5 to 7 is different from the second embodiment in that the discharge port 22 is formed so as to extend from the outer peripheral surface of the rear head 4 in the radial direction. 2 in that the opening 22 a and the gas passage hole 28 are located near one end of the muffler space 27. I have.
  • the circumferential length L of the muffler space 27 can be set longer than in the first embodiment described above. This makes it possible to set a frequency that can be attenuated to a lower frequency side than in the first embodiment.
  • the structure in which the discharge port 22 is formed to extend in the radial direction from the outer peripheral surface of the rear head 4 is such that the discharge port 22 shown in the first embodiment is opened substantially at the center of the muffler space 27.
  • the structure in which the discharge port 22 extends in the axial direction as disclosed in the first embodiment can be adopted, and the discharge port 22 is connected to one end of the muffler space 27. It can also be used when opening to a part.
  • the third embodiment shown in FIGS. 8 to 10 is characterized in that elasticity of rubber, synthetic rubber, synthetic resin, or the like is provided around an axial shielding plate 26 A closing the axial direction of the muffler space 23. It is characterized by being coated with a sealing material 50 made of a member, and has improved hermeticity at a peripheral portion of the axial shielding plate 26A.
  • the fourth embodiment shown in FIG. 11 is characterized in that a sealing member 51 made of an elastic member is fitted into a peripheral portion of the axial shielding plate 26A.
  • a sealing member 51 made of an elastic member is fitted into a peripheral portion of the axial shielding plate 26A.
  • the fifth embodiment shown in FIGS. 12 to 14 is characterized in that a step portion 60 is formed at the periphery of the muffler space 23 so that the periphery of the axial shielding plate 26 B abuts.
  • a sealing material made of an elastic member is interposed between the stepped portion 60 and the axial shielding plate 26B to seal the space therebetween, thereby improving the sealing performance in the axial direction. Things.
  • the manufacturing accuracy of the axially sealed plate 26B can be made somewhat rough, thereby improving workability. And achieve cost reductions.
  • the muffler space having a predetermined length in the circumferential direction is provided in the vicinity of the suction side or the discharge side and the corresponding port, so that the suction side or the discharge side is provided. It can effectively attenuate the problematic pulsating waves and prevent unpleasant noise in the cabin.
  • the muffler space is formed inside the rear head, even if a muffler is provided, it is possible to suppress an increase in the size of the compressor itself.
  • the sealing property of the muffler space can be improved with a simple structure, and thus the pulsation wave attenuation can be improved. You can do it. Further, by providing a sealing member made of an elastic member between the shielding plate and the periphery of the muffler space or between the shielding plate and the stepped portion, the sealing performance can be further improved, and the pulsation wave attenuation can be improved. Is what you can do.

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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)

Abstract

Compresseur capable d'atténuer les vibrations et le bruit provoqués par l'impulsion d'aspiration ou de décharge au moyen d'une structure simple. Dans ce compresseur, on forme un espace de silencieux possédant une longueur prédéterminée dans une direction circulaire dans une tête arrière grâce à la formation d'un deuxième espace de pression, formé annulaire à l'extérieur d'un premier espace de pression, près d'un orifice correspondant au deuxième espace de pression au moyen d'un mécanisme de compression. Une résonance produite par la vague d'impulsions dans le deuxième espace de pression peut être efficacement amortie dans l'espace de silencieux possédant une longueur prédéterminée.
PCT/JP2001/005490 2001-02-21 2001-06-27 Compresseur WO2002066831A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001045237A JP4759771B2 (ja) 2001-02-21 2001-02-21 圧縮機
JP2001-045237 2001-02-21

Publications (1)

Publication Number Publication Date
WO2002066831A1 true WO2002066831A1 (fr) 2002-08-29

Family

ID=18907072

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/005490 WO2002066831A1 (fr) 2001-02-21 2001-06-27 Compresseur

Country Status (2)

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JP (1) JP4759771B2 (fr)
WO (1) WO2002066831A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4408389B2 (ja) * 2004-05-10 2010-02-03 サンデン株式会社 斜板式圧縮機
US7607900B2 (en) * 2004-09-10 2009-10-27 Purdue Research Foundation Multi-cylinder reciprocating compressor
KR101841279B1 (ko) * 2011-04-27 2018-03-23 학교법인 두원학원 사판식 압축기
JP5920367B2 (ja) * 2013-07-18 2016-05-18 株式会社豊田自動織機 片頭ピストン式可変容量型圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2590662Y2 (ja) * 1993-07-12 1999-02-17 株式会社豊田自動織機製作所 往復動型圧縮機
JP2000249059A (ja) * 1999-03-01 2000-09-12 Toyota Autom Loom Works Ltd 圧縮機の吸入マフラ構造
JP2001041160A (ja) * 1999-07-28 2001-02-13 Toyota Autom Loom Works Ltd 圧縮機の脈動減衰構造

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2590662Y2 (ja) * 1993-07-12 1999-02-17 株式会社豊田自動織機製作所 往復動型圧縮機
JP2000249059A (ja) * 1999-03-01 2000-09-12 Toyota Autom Loom Works Ltd 圧縮機の吸入マフラ構造
JP2001041160A (ja) * 1999-07-28 2001-02-13 Toyota Autom Loom Works Ltd 圧縮機の脈動減衰構造

Also Published As

Publication number Publication date
JP4759771B2 (ja) 2011-08-31
JP2002250279A (ja) 2002-09-06

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