WO2016132692A1 - Dispositif d'étanchéité d'arbre - Google Patents

Dispositif d'étanchéité d'arbre Download PDF

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Publication number
WO2016132692A1
WO2016132692A1 PCT/JP2016/000549 JP2016000549W WO2016132692A1 WO 2016132692 A1 WO2016132692 A1 WO 2016132692A1 JP 2016000549 W JP2016000549 W JP 2016000549W WO 2016132692 A1 WO2016132692 A1 WO 2016132692A1
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WO
WIPO (PCT)
Prior art keywords
shaft
lip seal
housing
ring
fixed
Prior art date
Application number
PCT/JP2016/000549
Other languages
English (en)
Japanese (ja)
Inventor
秋山　訓孝
亨 大隈
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112016000784.1T priority Critical patent/DE112016000784T5/de
Publication of WO2016132692A1 publication Critical patent/WO2016132692A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/38—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member sealed by a packing
    • 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 disclosure relates to a shaft seal device applied to a compressor that compresses a fluid.
  • Patent Document 1 discloses a shaft seal device applied to a compressor that compresses carbon dioxide as a refrigerant in a vapor compression refrigeration cycle apparatus.
  • the shaft seal device of Patent Document 1 includes a rotary ring fixed to a rotary shaft of a compressor, and a fixed ring fixed around a shaft hole provided in a housing of the compressor. By bringing the stationary ring into surface contact, the refrigerant in the housing is prevented from leaking outside through the gap between the rotating ring and the stationary ring.
  • the shaft seal device applied to the compressor of the refrigeration cycle apparatus when the compressor is operated, the refrigeration oil enclosed in the refrigeration cycle apparatus together with the refrigerant is caused to flow into the gap between the rotating ring and the stationary ring. Can do. Thereby, a clearance gap can be filled up with highly viscous refrigerating machine oil, and the sealing performance of a shaft seal apparatus can be improved.
  • Patent Document 1 in a refrigeration cycle apparatus that constitutes a supercritical refrigeration cycle that employs carbon dioxide as a refrigerant and the pressure of the high-pressure side refrigerant of the cycle is equal to or higher than the critical pressure of the refrigerant, The pressure difference between the refrigerant pressure and the atmospheric pressure outside the housing becomes relatively large. For this reason, the improvement of the sealing performance of the shaft seal device by the refrigerating machine oil described above is effective.
  • the outer peripheral side of an annular lip seal formed of rubber or the like is fixed to the housing, and the inner peripheral side of the lip seal is brought into contact with the periphery of the rotating shaft.
  • a means for improving the sealing performance can be considered.
  • the lip seal is likely to be worn or damaged when the rotating shaft rotates. For this reason, when adding a lip seal, there exists a possibility that it may be difficult to maintain a sealing performance over a long period of time.
  • a shaft seal device is applied to a compressor having a housing that forms a space in which a part of a rotating shaft is accommodated, and includes a shaft hole provided in the housing and a rotating shaft. It is possible to suppress leakage of the fluid to be compressed in the housing from the gap.
  • the shaft sealing device includes an annular rotating ring fixed to the outer peripheral side of the rotating shaft and an annular ring fixed to the periphery of the shaft hole of the housing and in surface contact with the rotating ring when the rotating shaft is inserted into the shaft hole.
  • the rotation shaft and the member fixed thereto are defined as the rotation shaft side member
  • the housing and the member fixed thereto are defined as the housing side member, the rotation shaft side member and the housing side
  • the rotating ring and the stationary ring are in surface contact with each other during the operation of the compressor whose rotating shaft is rotating, the fluid to be compressed in the housing leaks to the outside like a so-called mechanical seal. Can be suppressed.
  • the shape of the lip seal changes to a non-contact state with the rotating shaft side member or the housing side member due to the action of the deformed portion. Therefore, even if the rotating shaft rotates, it is possible to suppress the lip seal from being worn or damaged.
  • the temperature of the deforming portion is lowered, so that the lip seal is deformed into a shape in contact with the rotating shaft side member or the housing side member by the action of the deforming portion.
  • the lip seal causes the fluid to be compressed in the housing. Can be prevented from leaking outside.
  • the rotating shaft side member corresponds to a rotating shaft, a rotating ring, and the like
  • the housing side member corresponds to a housing, a fixed ring, and the like.
  • FIG. 3 is an enlarged cross-sectional view of a part III in FIG. 2, and is a schematic enlarged cross-sectional view showing a shape of a lip seal when the compressor of the first embodiment is stopped. It is an expanded sectional view corresponding to Drawing 2 of a 2nd embodiment. It is an expanded sectional view corresponding to Drawing 2 of a 3rd embodiment. It is a typical expanded sectional view of the lip seal of 4th Embodiment.
  • the shaft seal device 50 of the present embodiment is applied to a compressor 10 that compresses and discharges a refrigerant that is a compression target fluid in a vapor compression refrigeration cycle apparatus.
  • the refrigeration cycle apparatus of the present embodiment is applied to a vehicle air conditioner, and fulfills a function of cooling blown air blown into the vehicle interior.
  • this refrigeration cycle apparatus employs carbon dioxide as a refrigerant, and constitutes a so-called supercritical refrigeration cycle in which the refrigerant pressure on the high pressure side of the cycle is equal to or higher than the critical pressure of the refrigerant. Furthermore, refrigeration oil for lubricating the sliding part of the compressor 10 is mixed in the refrigerant, and at least a part of the refrigeration oil circulates in the cycle together with the refrigerant. As this refrigeration oil, what has compatibility with a liquid phase refrigerant is adopted.
  • the compressor 10 is configured as a swash plate type variable displacement compressor.
  • the compressor 10 includes a compression mechanism unit 20 that compresses and discharges a refrigerant, a shaft 30 that is a rotation shaft that transmits a rotational driving force output from the engine to the compression mechanism unit 20, and a compression mechanism unit 20 and a shaft therein. And a housing 40 that forms a space for accommodating a part of the housing 30 and the like.
  • the housing 40 of this embodiment is formed in a bottomed cylindrical shape by combining a plurality of constituent members such as a front housing 41, a middle housing 42, a rear housing 43, and the like.
  • the front housing 41 is formed of a cup-shaped metal member and forms a control pressure chamber 41a therein.
  • the rear housing 43 is formed of a cup-shaped metal member, and forms a discharge chamber 43a and the like into which the refrigerant discharged from the compression mechanism unit 20 flows.
  • the middle housing 42 is arranged between the front housing 41 and the rear housing 43 so as to close both openings of the front housing 41 and the rear housing 43, and forms the cylinder 21 of the compression mechanism section 20. It is.
  • a cylindrical boss 41b protruding in the central axis direction is formed.
  • a pulley (not shown) is rotatably attached to the outer peripheral surface of the boss portion 41b via a bearing member such as a bearing.
  • a rotational driving force output from the engine is transmitted to the pulley via the belt.
  • a shaft hole 41c that penetrates the inside and outside of the front housing 41 is formed at the center of the boss 41b formed on the bottom surface of the front housing 41.
  • the shaft 30 is inserted into the shaft hole 41c.
  • the shaft 30 is formed of a substantially cylindrical member made of metal, and the central axis thereof is disposed substantially parallel to the central axis of the housing 40. Furthermore, a part of the shaft 30 protrudes outward from the shaft hole 41c of the front housing 41 and is connected to a pulley. Thereby, the rotational driving force output from the engine is transmitted to the shaft 30 via the pulley.
  • an electromagnetic clutch for intermittently connecting the pulley and the shaft 30 may be interposed at the connecting portion between the pulley and the shaft 30.
  • the remaining part of the shaft 30 is arranged so as to penetrate the inside of the control pressure chamber 41a, and the lug plate 22 extending in the radial direction is fixed to the part accommodated in the control pressure chamber 41a. Therefore, the lug plate 22 rotates with the shaft 30. Furthermore, the link part 23 is provided in the outer peripheral side of the lug plate 22, The swash plate 24 is connected with this link part 23 so that the inclination angle with respect to the central axis of the shaft 30 can be changed.
  • a plurality of pistons 26 that reciprocate in parallel with the central axis of the shaft 30 are connected to the swash plate 24 via a shoe 25 that is a spherical bearing.
  • the plurality of pistons 26 reciprocate inside the plurality of cylinders 21 formed in the middle housing 42 in conjunction with the rotation of the swash plate 24. Thereby, the refrigerant is sucked into the compression chamber surrounded by the end face of the piston 26 and the inner wall of the cylinder 21, and the sucked refrigerant is compressed.
  • the stroke of the reciprocating motion of the piston 26 can be changed by changing the inclination angle of the swash plate 24.
  • the discharge capacity can be changed by changing the stroke amount.
  • the discharge capacity is the geometric volume of the compression chamber, that is, the cylinder volume between the top dead center and the bottom dead center of the piston stroke.
  • the inclination angle of the swash plate 24 includes the pressure acting on the front and rear of the piston 26, the refrigerant pressure Pc in the space in which the swash plate and the like in the housing 40 are accommodated (that is, the control pressure chamber 41a in the front housing 41), and the compression chamber. Can be changed according to a balance with the pressure (refrigerant discharge pressure Pd and refrigerant suction pressure Ps).
  • the refrigerant pressure Pc in the control pressure chamber 41a adjusts the valve opening degree of the electromagnetic capacity control valve 27 attached to the rear housing 43, and the refrigerant discharge pressure Pd and the suction pressure Pd introduced into the control pressure chamber 41a. This is done by changing the introduction ratio.
  • the opening degree of the electromagnetic capacity control valve 27 is controlled by a control current output from an air conditioning control device (not shown).
  • a plurality of cylinders 21 are formed in the middle housing 42 of the present embodiment, and the same number of pistons 26 as the cylinders 21 are connected to the swash plate 24.
  • FIG. 1 for clarity of illustration, a pair of cylinders 21 and pistons 26 is illustrated, and the remaining cylinders 21 and pistons 26 are not illustrated.
  • the shaft seal device 50 includes an annular rotary ring 51 fixed to the outer peripheral side of the shaft 30, an annular fixed ring 52 fixed around the shaft hole 41 c of the front housing 41, and the front housing 41. It is configured to have a lip seal 53 or the like that is fixed to the inner peripheral side (housing side member) of the boss portion 41b and arranged so as to be in contact with the outer peripheral surface (rotary shaft side member) of the shaft 30.
  • Rotating ring 51 is formed of an annular member made of silicon carbide (silicon carbide).
  • the outer peripheral side of the rotating ring 51 is supported by a guide member 55 formed of an annular metal member.
  • the guide member 55 is fixed to the shaft 30 and restricts the displacement of the rotating ring 51 in the rotation direction.
  • a spring 55 a that is an elastic member is disposed between the guide member 55 and the rotating ring 51.
  • the spring 55a applies a load that biases the rotating ring 51 toward one end side in the axial direction of the shaft 30 (the end portion side on the shaft hole 31 side).
  • an O-ring 51 a as a seal member is disposed between the inner peripheral surface of the rotary ring 51 and the outer peripheral surface of the shaft 30, and the inner peripheral surface of the rotary ring 51 and the outer peripheral surface of the shaft 30 are arranged. There is no leakage of refrigerant.
  • the fixed ring 52 is formed of an annular member made of silicon carbide similarly to the rotating ring 51.
  • the stationary ring 52 is disposed on one axial end side of the shaft 30 with respect to the rotating ring 51 and is disposed so as to be in surface contact with the rotating ring 51.
  • the rotating ring 51 when the shaft 30 is assembled to the housing 40 and inserted into the shaft hole 41c, the rotating ring 51 receives a load from the spring 55a, thereby reliably bringing the rotating ring 51 and the stationary ring 52 into surface contact. Can do. At this time, a contact surface (seal surface) between the rotating ring 51 and the stationary ring 52 is formed in an annular shape around the shaft 30.
  • an O-ring 52 a as a seal member is disposed between the outer peripheral surface of the fixed ring 52 and the inner peripheral surface of the boss portion 41 b of the housing 40, and the outer peripheral surface of the fixed ring 52 and the boss of the housing 40 are disposed. The refrigerant does not leak from the space between the inner peripheral surface of the portion 41b.
  • the guide member 55, the spring 55 a, the rotating ring 51, the lug plate 22, and the like of this embodiment rotate integrally with the shaft 30. Therefore, the shaft 30, the guide member 55, the rotating ring 51, and the like constitute a rotating shaft side member described in the claims.
  • the housing 40, the stationary ring 52, and the like constitute a housing side member described in the claims.
  • the lip seal 53 is made of rubber having excellent heat resistance (specifically, HNBR: hydrogenated nitrile rubber). Further, the lip seal 53 is disposed on one end side in the axial direction of the shaft 30 with respect to the fixed ring 52 in a state of being integrated with the annular metal protection member 53a.
  • HNBR hydrogenated nitrile rubber
  • the lip seal 53 is disposed downstream of the contact surface between the rotating ring 51 and the stationary ring 52 in the refrigerant leakage direction.
  • the lip seal 53 is disposed on the outer side of the housing 40 with respect to the contact surface between the rotating ring 51 and the fixed ring 52. As shown in FIG. 2, the lip seal 53 extends beyond the contact surface between the rotating ring 51 and the fixed ring 52 to the outside of the diameter of the rotating shaft 30.
  • the protective member 53a has a disk-shaped part 53b that spreads in the radial direction of the shaft 30, and a cylindrical part 53c provided on the outer peripheral side of the disk-shaped part. And the axial direction both ends of the cylindrical part 53c are sandwiched between the annular projecting part 41d formed on the inner peripheral side of the boss part 41b and the surface of one end side in the axial direction of the stationary ring 52, The lip seal 53 and the protective member 53a are fixed inside the boss portion 41b.
  • the lip seal 53 is slightly crushed in the axial direction by the fixed ring 52, but the deformation amount is restricted by the cylindrical portion 53c. As a result, leakage from the gap between the lip seal 53 and the stationary ring 52 is suppressed, and unnecessary deformation of the lip seal 53 can be suppressed to protect the lip seal 53. Furthermore, since the disk-shaped part 53b is provided in the protection member 53a, it is possible to suppress the lip seal 53 from being bent to the outside of the housing 40.
  • the tip portion on the inner peripheral side of the lip seal 53 is inclined so as to gradually approach the shaft 30 toward the inner side of the housing 40 in the axial section.
  • the tip of the lip seal 53 is pressed against the outer peripheral surface of the shaft 30 by the pressure of the refrigerant, and the leakage from the gap between the lip seal 53 and the shaft 30 is suppressed. It is possible to improve the sealing performance.
  • a bimetal 54 is integrally formed in the lip seal 53 of this embodiment by insert molding.
  • the bimetal 54 is a laminate of two types of metal plates having different coefficients of thermal expansion, and changes to a specific shape according to a temperature change.
  • the inner peripheral side of the lip seal 53 comes into contact with the shaft 30, as shown in FIG.
  • a shape is adopted in which the inner peripheral side of the lip seal 53 is deformed into a shape that does not contact the shaft 30, that is, a non-contact shape.
  • the bimetal 54 of the present embodiment constitutes an example of a deformed portion of the present application.
  • FIG. 2 also shows a state where the temperature of the bimetal 54 itself has not risen, as in FIG.
  • the compressor 10 mounted on the vehicle when the temperature of the bimetal 54 itself becomes at least 50 ° C. or more, the inner peripheral side of the lip seal 53 is deformed into a shape that does not contact the shaft 30. It is desirable to adopt one.
  • the shaft 30 rotates by transmitting the rotational driving force output from the engine. Then, when the rotational driving force is transmitted from the shaft 30 to the compression mechanism unit 20, the compression mechanism unit 20 compresses and discharges the refrigerant.
  • the shaft seal device 50 of the present embodiment since the rotary ring 51 and the fixed ring 52 are in surface contact with each other at the contact surface formed in an annular shape, the inside of the housing 40 is similar to a so-called mechanical seal.
  • the refrigerant can be prevented from leaking outside.
  • the refrigeration oil is mixed in the refrigerant of the refrigeration cycle apparatus of the present embodiment, the refrigeration oil can flow into the gap between the rotating ring 51 and the stationary ring 52.
  • the clearance gap between the rotating ring 51 and the stationary ring 52 can be filled with highly viscous refrigerating machine oil, and the sealing performance of the shaft seal device 50 can be improved effectively.
  • the temperature of the refrigerant and the compressor 10 rises due to a temperature rise due to adiabatic compression of the refrigerant, friction of a sliding portion in the compressor 10, and the like.
  • this temperature rise is transmitted to the bimetal 54 via the contact portion between the refrigerant and the bimetal 54.
  • the lip seal 53 is deformed into a shape that does not come into contact with the shaft 30 due to deformation accompanying the temperature rise of the bimetal 54.
  • the refrigerating machine oil may not be able to fill the gap between the rotating ring 51 and the stationary ring 52, and the sealing performance of the gap between the rotating ring 51 and the stationary ring 52 may not be improved.
  • the shaft seal device 50 of the present embodiment when the rotation of the shaft 30 is stopped and the compressor 10 is stopped, the temperature of the bimetal 53 is lowered. The shape is deformed to contact the shaft 30. Therefore, when the operation of the compressor 10 is stopped, the lip seal 53 can prevent the refrigerant in the housing 40 from leaking outside.
  • the shaft seal device 50 of the present embodiment high sealing performance can be exhibited regardless of the operating state of the compressor 10 (rotation state of the shaft 30), and wear and damage of the lip seal 53 are suppressed.
  • a highly durable shaft seal device can be provided.
  • the lip seal 53 and the protective member 53a are arranged outside the housing 40 rather than the contact surface between the rotating ring 51 and the fixed ring 52. It is easy to adopt a configuration in which the inner peripheral side is in direct contact with the shaft 30. Therefore, the lip seal 53, the protection member 53 a, and the bimetal 54 can be prevented from being enlarged, and the shape can be easily assembled in the housing 40.
  • the bimetal 54 and the lip seal 53 are integrally formed by insert molding. Accordingly, it is possible to easily realize a deformed portion that deforms the lip seal 53 from a shape that contacts the shaft 30 to a shape that does not contact the shaft 30 as the temperature rises.
  • the refrigerating machine oil can improve the sealing performance of the gap between the rotating ring 51 and the stationary ring 52, and when the compressor 10 is stopped, the lip seal 53 It is extremely effective that the refrigerant in the housing 40 can be prevented from leaking outside.
  • FIG. 5 is a drawing corresponding to FIG. 2 described in the first embodiment, and the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.
  • the lip seal 53 and the bimetal 54 of the present embodiment are integrated by insert molding as in the first embodiment. Further, as shown in FIG. 5, the lip seal 53 is fixed to a portion closer to the control pressure chamber side than the boss portion 41 d in the housing 40, and the inner peripheral side thereof is disposed so as to be in contact with the outer peripheral surface of the shaft 30. ing.
  • the lip seal 53 of the present embodiment is arranged upstream of the contact surface between the rotating ring 51 and the stationary ring 52 in the refrigerant leakage direction.
  • the lip seal 53 is disposed on the inner side of the housing 40 with respect to the contact surface between the rotating ring 51 and the fixed ring 52.
  • the lip seal 53 is disposed on the inner side of the housing 40 with respect to the contact surface between the rotating ring 51 and the fixed ring 52. Accordingly, when the rotation of the shaft 30 is stopped and the lip seal 53 is deformed into a shape in contact with the shaft 30, the seal portion between the lip seal 53 and the shaft 30 reaches the seal portion between the rotating ring 51 and the fixed ring 52. The refrigerant pressure in the range is unlikely to rise.
  • FIG. 6 is a drawing corresponding to FIG. 2 described in the first embodiment.
  • the lip seal 53 and the bimetal 54 of the present embodiment are integrated by insert molding as in the first embodiment. Further, as shown in FIG. 6, the lip seal 53 is fixed to the rotary ring 51 (rotary shaft side member), and the outer peripheral side thereof is disposed so as to be able to contact the fixed ring 52 (housing side member).
  • FIG. 7 is a drawing corresponding to FIG. 3 described in the first embodiment.
  • locking portions 53b and 53c for locking the bimetal 54 at the outer peripheral end and the inner peripheral end are formed.
  • the bimetal 54 and the lip seal 53 are integrally deformed. That is, with the deformation of the bimetal 54, the lip seal 53 is similarly deformed.
  • the compression mechanism unit 20 is not limited thereto.
  • any compression mechanism that compresses fluid by transmitting a rotational driving force from the shaft 30 such as a scroll-type compression mechanism, a vane-type compression mechanism, or a rolling piston-type compression mechanism can be widely used.
  • the deforming portion is not limited to this.
  • the deforming portion is formed by joining two types of resin plates having different thermal expansion coefficients. Alternatively, it may be formed by bonding resins and metals having different thermal expansion coefficients.
  • the example in which the rotating ring 51 and the stationary ring 52 formed of silicon carbide are used has been described.
  • the material of the rotating ring 51 and the stationary ring 52 is not limited thereto.
  • it may be formed of carbon fiber or a carbon fiber reinforced composite material.
  • the above-mentioned embodiment demonstrated the example which employ
  • the example in which the shaft seal device 50 according to the present disclosure is applied to the compressor 10 of the refrigeration cycle device that employs carbon dioxide as a refrigerant has been described. It is not limited.
  • the present invention may be applied to a compressor of a refrigeration cycle apparatus constituting a subcritical refrigeration cycle in which the refrigerant pressure on the high pressure side does not exceed the critical pressure of the refrigerant, or can be applied to compressors for a wide variety of other uses.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Mechanical Sealing (AREA)
  • Sealing Devices (AREA)

Abstract

L'invention concerne un dispositif d'étanchéité d'arbre pourvu : d'une bague rotative (51) fixée à la circonférence externe d'un arbre (30) ; d'une bague fixe (52) fixée à la circonférence d'un trou d'arbre (41c) d'un boîtier (40) et en contact de surface avec la bague rotative (51) ; d'un joint à lèvre (53), dont la circonférence externe est fixée au boîtier (40) et la circonférence interne entre en contact avec l'arbre (30) ; et d'un bilamétal (54) destiné à faire passer le joint à lèvre (53) d'une forme qui est en contact avec l'arbre (30) à une forme qui n'est pas en contact avec celui-ci lorsque la température augmente. De ce fait, lorsqu'un compresseur (10) est arrêté et que la température du bimétal (54) est basse, l'étanchéité est améliorée en amenant le joint à lèvre (53) en contact avec l'arbre (30) et lorsque le compresseur (10) est en fonctionnement et que la température du bimétal est élevée, le joint à lèvre (53) est protégé en empêchant le joint à lèvre (53) d'entrer en contact avec l'arbre (30).
PCT/JP2016/000549 2015-02-17 2016-02-03 Dispositif d'étanchéité d'arbre WO2016132692A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112016000784.1T DE112016000784T5 (de) 2015-02-17 2016-02-03 Wellendichtungsvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015028747A JP6455209B2 (ja) 2015-02-17 2015-02-17 軸封装置
JP2015-028747 2015-02-17

Publications (1)

Publication Number Publication Date
WO2016132692A1 true WO2016132692A1 (fr) 2016-08-25

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PCT/JP2016/000549 WO2016132692A1 (fr) 2015-02-17 2016-02-03 Dispositif d'étanchéité d'arbre

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JP (1) JP6455209B2 (fr)
DE (1) DE112016000784T5 (fr)
WO (1) WO2016132692A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0669531U (ja) * 1993-03-16 1994-09-30 エヌオーケー株式会社 密封装置
EP1336778A2 (fr) * 2002-02-14 2003-08-20 ROLLS-ROYCE plc Joint à brosses
JP2007239943A (ja) * 2006-03-10 2007-09-20 Toyota Motor Corp オイルシール
JP2009174376A (ja) * 2008-01-23 2009-08-06 Valeo Thermal Systems Japan Corp 圧縮機の軸封構造

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0669531U (ja) * 1993-03-16 1994-09-30 エヌオーケー株式会社 密封装置
EP1336778A2 (fr) * 2002-02-14 2003-08-20 ROLLS-ROYCE plc Joint à brosses
JP2007239943A (ja) * 2006-03-10 2007-09-20 Toyota Motor Corp オイルシール
JP2009174376A (ja) * 2008-01-23 2009-08-06 Valeo Thermal Systems Japan Corp 圧縮機の軸封構造

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DE112016000784T5 (de) 2017-10-26
JP2016151311A (ja) 2016-08-22
JP6455209B2 (ja) 2019-01-23

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