WO1998029660A1 - Structure pour recuperer l'huile qui fuit dans un compresseur - Google Patents

Structure pour recuperer l'huile qui fuit dans un compresseur Download PDF

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Publication number
WO1998029660A1
WO1998029660A1 PCT/JP1996/003823 JP9603823W WO9829660A1 WO 1998029660 A1 WO1998029660 A1 WO 1998029660A1 JP 9603823 W JP9603823 W JP 9603823W WO 9829660 A1 WO9829660 A1 WO 9829660A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
oil
drive shaft
boss
leaked
Prior art date
Application number
PCT/JP1996/003823
Other languages
English (en)
Japanese (ja)
Inventor
Kazuya Kimura
Masafumi Ito
Original Assignee
Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
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
Priority to JP7329197A priority Critical patent/JPH09170553A/ja
Priority claimed from JP7329197A external-priority patent/JPH09170553A/ja
Application filed by Kabushiki Kaisha Toyoda Jidoshokki Seisakusho filed Critical Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority to KR1019980706628A priority patent/KR100292784B1/ko
Priority to EP96943308A priority patent/EP0887550A4/fr
Priority to PCT/JP1996/003823 priority patent/WO1998029660A1/fr
Publication of WO1998029660A1 publication Critical patent/WO1998029660A1/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
    • 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
    • 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
    • F04B27/109—Lubrication

Definitions

  • the present invention relates to, for example, a compressor used for an air conditioner of a vehicle, and more particularly to a structure for collecting oil leaking from inside the compressor.
  • the drive shaft 51 is supported by a housing 52 that houses the compression mechanism.
  • the drive shaft 51 is connected to the compression mechanism, and a part of the drive shaft 51 projects from the housing 52.
  • the boss 53 is provided on the outer wall surface of the housing 52 and surrounds the protruding end of the drive shaft 51.
  • the shaft sealing device 54 is interposed between the boss 53 and the drive shaft 51 to seal the inside of the housing 52.
  • the rotor 56 of the electromagnetic clutch 55 is rotatably supported by the boss 53.
  • the armature 57 of the electromagnetic clutch 55 is fixed to the projecting end of the drive shaft 51 via the hub 58.
  • the armature 57 is attracted to the rotor 56, and the driving force from the vehicle engine is transmitted to the drive shaft 51. Then, the compression mechanism is operated by the rotation of the drive shaft 51, and the refrigerant gas is compressed.
  • the seal member is hardened by frictional heat between the continuously rotating drive shaft 51 and the seal member of the shaft sealing device 54, and the seal member deteriorates with time.
  • the sealing function of the shaft sealing device 54 is degraded due to foreign matter entering the seal portion. Therefore, the lubricating oil inside the housing 52 does not leak out of the housing 52 through the opening 53a of the boss 53. This leaked lubricating oil is attached to, for example, the suction surface of the electromagnetic clutch 55. For this reason, rotor 5 6 and armature 5
  • the ring-shaped damming member 60 is disposed on the periphery of the boss portion 53 around the opening 53 a of the boss portion 53 from the shaft sealing device 54.
  • the damping member 60 blocks the leaked lubricating oil that is to be moved to the opening 53 ⁇ side along the inner peripheral surface of the boss 53.
  • the oil absorbing member 61 is held by a housing 52, and the oil absorbing member 61 is connected to the inner space of the boss portion 53 via an oil guide passage 62.
  • the oil guide passage 62 is open on the inner peripheral surface of the boss 53 between the damming member 60 and the shaft sealing device 54. Accordingly, the leaked lubricating oil blocked by the damming member 60 is guided to the oil absorbing member 61 through the oil guide passage 62, and is absorbed and held by the oil absorbing member 61.
  • a ring member 63 separate from the drive shaft 51 is required, and the number of components constituting the compressor increases.
  • the present invention has been made in view of the problems existing in the prior art described above, and has as its object to reduce leakage oil transmitted through a drive shaft with a simple configuration without increasing the number of parts in an inner space of a housing.
  • An object of the present invention is to provide a structure for collecting leaked oil in a compressor that can be dropped at a predetermined position. Disclosure of the invention
  • a compressor of the present invention includes a housing for accommodating a compression mechanism.
  • the drive shaft is supported by the housing and connected to the compression mechanism.
  • the boss portion is provided on an outer wall surface of the housing so as to surround a protruding portion of the drive shaft from the housing.
  • the rotating body is connected to the drive shaft, and transmits power from an external drive source to the drive shaft.
  • the shaft sealing device is disposed in the inner space of the housing, and seals between the inner peripheral surface of the housing and the drive shaft.
  • the recovery means is provided for recovering oil leaked from the shaft sealing device.
  • the step portion is recessed on the outer peripheral surface of the rotating portion located on the opening side of the boss portion with respect to the shaft sealing device in the inner space of the housing. This step is provided so as to face the collecting means.
  • the oil that travels along the inner peripheral surface of the boss portion is recovered by the recovery means. Therefore, the leaked oil is not scattered toward the rotating body through the opening of the boss.
  • FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention.
  • FIG. 2A is an enlarged view of a main part of FIG.
  • FIG. 2 (b) is an enlarged view of a main part of FIG. 2 (a).
  • FIG. 3A is an enlarged cross-sectional view of a main part of the compressor according to the second embodiment.
  • FIG. 3B is a front view showing a part of the hub in the second embodiment.
  • FIG. 4A is an enlarged sectional view of a main part of a compressor according to the third embodiment.
  • FIG. 4B is a rear view showing a part of the cushion rubber according to the third embodiment.
  • FIG. 5 is an enlarged sectional view of a main part showing a conventional compressor. BEST MODE FOR CARRYING OUT THE INVENTION
  • the front housing 11 is joined and fixed to the front of the cylinder block 12.
  • the rear housing 13 is joined and fixed to the rear of the cylinder block 12 via a valve plate 34.
  • the crank chamber 14 is formed by an air gap surrounded by the cylinder block 12 and the front housing 11.
  • the drive shaft 15 is rotatably supported by the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 14.
  • the front end of the drive shaft 15 projects outward from the front housing 11.
  • the boss 16 is integrally formed on the outer wall surface of the front housing 11 so as to surround the protruding end of the drive shaft 15.
  • the lip seal 17 as a shaft sealing device is disposed in the inner space of the boss portion 16, and the lip ring 17 "of the lip seal 17 is driven by the pressure in the crank chamber 14.
  • the crank chamber 14 is sealed by being pressed against the shaft 15.
  • the electromagnetic clutch 18 as a rotating body is connected to a vehicle end (not shown) as an external drive source. It is interposed between the gin and the drive shaft 15. That is, the rotor 19 constituting the electromagnetic clutch 18 is rotatably supported on the outer peripheral surface of the boss 16 via the angular bearing 20.
  • a belt 42 connected to the vehicle engine is wound around the outer periphery of the rotor 19.
  • the hub 21 is fixed to the protruding end of the drive shaft 15 with a bush 21 ⁇ formed integrally with the hub.
  • the armature 22 is fixed to the hub 21 via a circular cushion rubber 23.
  • the cushioning rubber 23 is located on the power transmission path between the hub 21 and the armature 22, and the elastic force of the cushioning rubber 23 periodically transmits the driving torque transmitted to the belt 42 via the rotor 19. Small fluctuations.
  • the armature 22 When the core 24 accommodated in the rotor 19 is excited, the armature 22 is piled on the spring force of the cushion rubber 23 supporting the armature 22 and pressed against the rotor 19. Therefore, the driving force of the vehicle engine is transmitted to the drive shaft 15. Further, when the core 24 is demagnetized, the armature 22 is separated from the rotor 19 by the panel force of the cushion rubber 23, and the transmission of the driving force is interrupted.
  • the lug plate 25 is press-fitted and fixed to the drive shaft 15, and a guide hole 25) 3 is formed in the support arm 25 ⁇ of the lug plate 25.
  • the swash plate 26 is supported so as to be tiltable and slideable with respect to the drive shaft 15.
  • the guide pin 26 ⁇ is fixed to the swash plate 26 and is engaged with the guide hole 25
  • the cylinder bore 12a is formed in the cylinder block 12, and connects the crank chamber 14 with the suction chamber 13 ⁇ and the discharge chamber 13 ⁇ in the rear housing 13 to each other.
  • the single-headed piston 27 is housed in the cylinder bore 12 ⁇ .
  • the swash plate 26 is moored with a single-headed piston 27 via a pair of shoes 28 in a state of entering into a recess 27 formed in a single-headed biston 27. Therefore, the rotating motion of the swash plate 26 is converted to the back and forth reciprocating motion of the single-headed biston 27 via the shoe 28.
  • the refrigerant gas is sucked from the suction chamber 13 ⁇ into the cylinder pore 12 ⁇ via the suction valve 34 ⁇ of the valve plate 34, and the sucked refrigerant gas is compressed. While being discharged to the discharge chambers 13
  • the pressure supply passage 29 connects the discharge chamber 13) 3 to the crank chamber 14, and the electromagnetic valve 30 is disposed on the pressure supply passage 29.
  • the solenoid 30 ⁇ of the solenoid valve 30 When the solenoid 30 ⁇ of the solenoid valve 30 is excited or de-energized, the spool 30) 3 closes or opens the port 30 ⁇ , that is, the pressure supply passage 29 is closed or opened. .
  • the maximum inclination angle of the swash plate 26 is defined by the contact between the stopper 2613 provided on the swash plate 26 and the lug plate 25. Further, the minimum inclination is defined by the contact between the swash plate 26 and the ring 33 attached to the drive shaft 15.
  • the ring-shaped damming member 35 is formed on the inner peripheral surface of the boss 16 by an opening 16 a of the boss 16 from the lip seal 17.
  • the felt-made oil absorbing member 36 is accommodated and arranged in an accommodating portion 37 recessed at a lower portion of the outer wall surface of the front housing 11.
  • the oil guide passage 38 extends from the peripheral wall of the boss portion 16 to the outer wall surface of the front housing 11, and the oil guide passage 38 connects the oil absorbing member 36 to the inner space of the boss portion 16. I have.
  • the oil guide passage 38 is opened on the inner peripheral surface of the boss 16 between the dam member 35 and the lip seal 17.
  • the collecting means includes the dam member 35, the oil absorbing member 36, the oil guide passage 38, and the like.
  • the formation position of the storage part 37 is in a horizontal plane including the axis L of the drive shaft 15 (the axis L of this compressor is It is arranged in the engine room so that it is almost horizontal.
  • the annular groove 39 is formed at a position corresponding to a portion between the lip seal 17 and the dam member 35 constituting a part of the collecting means in the small-diameter portion 15 ⁇ of the drive shaft 15. ing.
  • the corner portion connecting the inner bottom surface of the annular groove 39 and the wall surface 40 ⁇ is formed in a curved shape.
  • the step on the side of the lip seal 17 that forms the annular groove 39 forms a step 40 in the present embodiment.
  • the inner wall surface 40 ⁇ of the step portion 40 is substantially perpendicular to the axis L.
  • the plurality of through holes 41 as pressure adjusting means are formed in the hub 21 of the electromagnetic clutch 18 at positions facing the openings 16 a of the boss 16. Due to the through holes 41, even when the armature 22 is pressed against the rotor 19, a space A surrounded by the electromagnetic clutch 18 and the boss 16 is opened to the outside of the compressor. By the way, when the sealing function of the lip seal 17 is deteriorated, the lubricating oil in the crank chamber 14 leaks over the lip seal 17. The leaking lubricating oil tends to move to the opening 16 ⁇ side along the circumferential surface of the boss 16, but since the damming member 35 is opposed to the flow of the leaking lubricating oil, any further Movement is blocked.
  • the leak lubricating oil is retained between the dam member 35 and the lip seal 1 ⁇ ⁇ ⁇ ⁇ in the lower part of the space inside the boss portion 16.
  • the stopped lubricating oil is guided to the oil absorbing member 36 through the oil guide passage 38 opened to the stopped portion, and is absorbed and held by the oil absorbing member 36.
  • part of the leaked lubricating oil forms a film on the outer surface of the drive shaft 15 and tends to move to the opening 16 ⁇ side of the boss 16 along the outer surface of the drive shaft 15. .
  • the leakage lubricating oil is prevented from further moving to the opening 16 ⁇ side at the step portion 40 of the annular groove 39. That is, since the wall surface 40 ⁇ of the step portion 40 is substantially perpendicular to the axis L, the leakage lubricating oil transmitted on the surface of the drive shaft 15 resists the centrifugal force caused by the rotation of the drive shaft 15. The wall 40 ⁇ cannot be moved to the axis L side.
  • the leaked lubricating oil stays at the outer edge of the step portion 40 and the centrifugal force Is swung in a radial direction perpendicular to the axis L.
  • the leaked lubricating oil that has been shaken off is guided to the oil absorbing member 36 through the oil guide passage 38 by its own weight, and is absorbed and held by the oil absorbing member 36.
  • the space ⁇ ⁇ surrounded by the electromagnetic clutch 18 and the boss 16 is opened to the outside of the compressor by the through hole 41 formed in the haptic 21 of the electromagnetic clutch 18. Have been. Therefore, the inside of the space A does not always have a negative pressure, and the leakage of the lubricating oil from the damming member 35 can be prevented.
  • the first embodiment having the above configuration has the following effects.
  • annular groove 39 is, of course, not projected into the inner space of the boss 16. Therefore, by forming the annular groove 39, the lip seal 17 side is not sealed and the thermal environment does not become severe, and the annular groove 39 causes the thermal deterioration of the lip seal 17 Does not.
  • the wall surface 40 ⁇ of the step portion 40 is a vertical wall. Therefore, the table of drive shaft 15 The lubrication oil leaking down the surface is effectively shaken off at the step portion 40, and the drive shaft 15 is easily cut.
  • the connecting portion between the bottom surface and the wall surface of the annular groove 39 has a circular curved surface. Therefore, the stress acting on the drive shaft 15 does not concentrate on the connection portion, and the strength reduction of the drive shaft 15 due to the provision of the annular groove 39 can be prevented.
  • FIGS. 3 (a) and 3 (b) show a second embodiment.
  • the outer opening 45 ⁇ of the through hole 45 is disposed on the ⁇ side of the radial direction of the hub 21 from the inner opening 45 ⁇ . Therefore, the through hole 45 is inclined with respect to the radial direction of the hub 21 to form a centrifugal fan. As a result, the outside air is positively introduced into the space ⁇ through the through hole 45 by the rotation of the hub 21.
  • the present embodiment has the following effects.
  • the air gap A ⁇ ⁇ ⁇ can be positive pressure, and the effect of (1-5) in the first embodiment is synergistically achieved.
  • FIGS. 4A and 4B show a third embodiment.
  • a plurality of ventilation grooves 46 ⁇ are formed in the radial direction on the surface of the cushioning rubber 46 facing the armature 22.
  • the rotation of the hub 21 causes the through-hole 45 and the cushion rubber 46 to form a centrifugal fan, and an external air flow flowing through the through-hole 45 ⁇ space ⁇ ⁇ vent groove 46 ⁇ is formed. Due to this external air flow, the heat radiation effect of the hub 21 and the armature 22 is enhanced, and as a result, The temperature of the entire electromagnetic clutch 18 is reduced. This is effective in lowering the temperature of the lip seal 17 adjacent to the electromagnetic clutch 18, and can suppress the deterioration of the sealing function due to the thermal deterioration of the lip seal 17.
  • the space A # can be maintained at a positive pressure.
  • the oil absorbing member 36 is fixedly arranged at the radial position of the step portion 40 in the inner space of the boss portion 16.
  • the oil guide passage 38 shall be composed of a tube separate from the compressor housing (11, 12, 23). In this way, maintenance such as removal when foreign matter is clogged in the oil guide passage 38 can be easily performed only by removing the pipe.
  • the through hole 45 is inclined in the radial direction of the hub 21, but this is changed and the through hole 45 is inclined in the rotation direction of the hap 21.
  • the rotating body is the electromagnetic clutch 18, but this may be changed to a pulley having no intermittent power structure. That is, the present invention may be embodied in a clutchless compressor.
  • An annular groove 39 is formed on the outer peripheral surface of the push 21 ⁇ (rotating part) of the hap 21 to form a step portion 40.
  • the dam member 35 is moved to the opening 16 ⁇ side of the boss 16 from the position shown in FIG.
  • the compressor is a variable displacement swash plate compressor, but other compressors include a fixed displacement swash plate compressor, a scroll compressor, a wave force compressor, and the like. It may be embodied.
  • a blower fin shall be attached near the through hole 41 in the hub 21 and outside air shall be introduced into the space A by the blower fin.
  • the compressor according to the present invention not only can the adverse effect of the leaked oil be reliably prevented, but also the number of parts can be reduced by reducing the number of parts, and the compressor can be reduced in number. Can be easily assembled. Moreover, the thermal environment of the shaft sealing device can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressor (AREA)

Abstract

Un boîtier (11, 12, 13) abrite un mécanisme de compression et supporte un arbre d'entraînement (15) qui est raccordé au mécanisme de compression. Un bossage (16) est prévu sur la paroi extérieure du boîtier (11, 12, 13) de façon à entourer la partie de l'arbre d'entraînement (15) qui fait saillie par rapport au boîtier (11, 12, 13). Un rotor (18) est raccordé à l'arbre d'entraînement (15) et transmet l'énergie d'une source d'entraînement extérieure à l'arbre d'entraînement (15). Un dispositif d'étanchéité d'arbre (17) est placé dans le boîtier (11, 12, 13) et obture l'espace entre l'arbre d'entraînement (15) et la surface périphérique interne du boîtier (11, 12, 13). Une unité de récupération (35, 36, 38) sert à récupérer l'huile qui fuit du dispositif d'étanchéité d'arbre (17). Une partie à gradins (40) est conçue pour entourer la périphérie de la partie rotative (15, 21α) positionnée sur le côté d'une ouverture (16α) du bossage (16) par rapport au dispositif d'étanchéité d'arbre (17) dans le boîtier (11, 12, 13). La partie à gradins (40) est placée face à l'unité de récupération (35, 36, 38).
PCT/JP1996/003823 1995-12-18 1996-12-26 Structure pour recuperer l'huile qui fuit dans un compresseur WO1998029660A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP7329197A JPH09170553A (ja) 1995-12-18 1995-12-18 圧縮機における漏出油の回収構造
KR1019980706628A KR100292784B1 (ko) 1996-12-26 1996-12-26 압축기에서의 누출유의 회수 구조
EP96943308A EP0887550A4 (fr) 1996-12-26 1996-12-26 Structure pour recuperer l'huile qui fuit dans un compresseur
PCT/JP1996/003823 WO1998029660A1 (fr) 1995-12-18 1996-12-26 Structure pour recuperer l'huile qui fuit dans un compresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP7329197A JPH09170553A (ja) 1995-12-18 1995-12-18 圧縮機における漏出油の回収構造
PCT/JP1996/003823 WO1998029660A1 (fr) 1995-12-18 1996-12-26 Structure pour recuperer l'huile qui fuit dans un compresseur

Publications (1)

Publication Number Publication Date
WO1998029660A1 true WO1998029660A1 (fr) 1998-07-09

Family

ID=14154300

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1996/003823 WO1998029660A1 (fr) 1995-12-18 1996-12-26 Structure pour recuperer l'huile qui fuit dans un compresseur

Country Status (3)

Country Link
EP (1) EP0887550A4 (fr)
KR (1) KR100292784B1 (fr)
WO (1) WO1998029660A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0999364A2 (fr) * 1998-11-04 2000-05-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Assemblage d'étanchéité d'arbre avec passage de drainage

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000240571A (ja) * 1999-02-19 2000-09-05 Gomuno Inaki Kk 圧縮機の吸油部材
JP2002242829A (ja) * 2001-02-16 2002-08-28 Sanden Corp 容量可変圧縮機
JP2002276775A (ja) 2001-03-19 2002-09-25 Toyota Industries Corp 回転体装置
US6698232B1 (en) * 2002-10-30 2004-03-02 Carrier Corporation Oil leak diversion and collection system for mechanical shaft seals
JP6751314B2 (ja) * 2016-06-24 2020-09-02 三菱重工サーマルシステムズ株式会社 開放型圧縮機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5280103U (fr) * 1975-12-12 1977-06-15
JPS588764U (ja) * 1981-07-10 1983-01-20 三菱重工業株式会社 圧縮機
JPH0667871U (ja) * 1993-02-25 1994-09-22 サンデン株式会社 開放型コンプレッサ
JPH07145780A (ja) * 1993-11-24 1995-06-06 Toyota Autom Loom Works Ltd 車両空調用圧縮機の堰構造

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4314705A (en) * 1979-05-23 1982-02-09 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Oil seal device
JPS58206826A (ja) * 1982-05-28 1983-12-02 Aisin Seiki Co Ltd タ−ボチヤ−ジヤ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5280103U (fr) * 1975-12-12 1977-06-15
JPS588764U (ja) * 1981-07-10 1983-01-20 三菱重工業株式会社 圧縮機
JPH0667871U (ja) * 1993-02-25 1994-09-22 サンデン株式会社 開放型コンプレッサ
JPH07145780A (ja) * 1993-11-24 1995-06-06 Toyota Autom Loom Works Ltd 車両空調用圧縮機の堰構造

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0887550A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0999364A2 (fr) * 1998-11-04 2000-05-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Assemblage d'étanchéité d'arbre avec passage de drainage
EP0999364A3 (fr) * 1998-11-04 2001-02-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Assemblage d'étanchéité d'arbre avec passage de drainage

Also Published As

Publication number Publication date
EP0887550A1 (fr) 1998-12-30
EP0887550A4 (fr) 2001-05-02
KR19990087230A (ko) 1999-12-15
KR100292784B1 (ko) 2001-06-15

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