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WO2018181186A1 - Structure de roulement et compresseur électrique - Google Patents

Structure de roulement et compresseur électrique Download PDF

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Publication number
WO2018181186A1
WO2018181186A1 PCT/JP2018/012150 JP2018012150W WO2018181186A1 WO 2018181186 A1 WO2018181186 A1 WO 2018181186A1 JP 2018012150 W JP2018012150 W JP 2018012150W WO 2018181186 A1 WO2018181186 A1 WO 2018181186A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
bearing
housing
peripheral surface
rotating shaft
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.)
Ceased
Application number
PCT/JP2018/012150
Other languages
English (en)
Japanese (ja)
Inventor
国彰 飯塚
吉田　隆
達身 猪俣
拓也 小篠
海 飯嶋
良介 湯本
孝志 森
裕司 佐々木
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.)
IHI Corp
Original Assignee
IHI 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 IHI Corp filed Critical IHI Corp
Priority to JP2019509808A priority Critical patent/JP6725064B2/ja
Priority to DE112018001791.5T priority patent/DE112018001791T5/de
Priority to US16/492,375 priority patent/US20200040903A1/en
Priority to CN201880004998.9A priority patent/CN110073120A/zh
Publication of WO2018181186A1 publication Critical patent/WO2018181186A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00

Definitions

  • This disclosure relates to a bearing structure and an electric compressor.
  • the bearing structure described in Patent Document 1 includes a bearing that supports a shaft of a fan motor.
  • An O-ring is mounted in the groove of the outer ring of the bearing.
  • the O-ring is in contact with the housing.
  • a viscous fluid is filled between the two O-rings.
  • the bearing structure described in Patent Document 2 includes a bearing that supports a drive shaft.
  • An O-ring is mounted in the groove of the outer ring of the bearing. High viscosity oil is applied to the outer diameter surface of the outer ring.
  • JP 2000-120669 A Japanese Unexamined Patent Publication No. 2007-211865
  • the crushing margin of the O-ring is set so that the insertion force of the bearing when the bearing equipped with the O-ring is incorporated into the housing is reduced.
  • This insertion force is determined by the radial force and friction coefficient generated by the crushing margin of the O-ring. That is, the insertion force is reduced by reducing the radial force.
  • the coefficient of friction between the inner diameter surface of the housing and the outer diameter surface of the outer ring is reduced, thereby preventing the creep of the outer ring from rolling along the inner diameter surface of the housing.
  • the present disclosure describes a bearing structure that can reliably prevent vibrations from being transmitted to the housing via the bearing.
  • One aspect of the present disclosure is a bearing structure for supporting a rotating shaft of a rotating body housed in a housing with respect to the housing, the rotating shaft being attached to the housing, and the rotating shaft being attached to the housing.
  • a bearing to be supported the bearing having an inner ring through which the rotating shaft is inserted, and an outer ring including an annular groove formed on an outer peripheral surface facing the inner wall surface of the housing, and a bearing disposed in the groove of the outer ring of the bearing
  • An O-ring that protrudes radially outward from the outer peripheral surface and abuts against the inner wall surface of the housing, and a clearance is formed between the inner wall surface of the housing and the outer peripheral surface of the bearing. It is larger than the radial displacement of the O-ring.
  • vibration can be reliably prevented from being transmitted to the housing via the bearing.
  • FIG. 1 is a cross-sectional view illustrating an electric compressor according to an embodiment of the present disclosure.
  • FIG. 2 is an enlarged cross-sectional view showing a part of the bearing structure in FIG.
  • FIG. 3A is a diagram showing the relationship between the crushing margin of the O-ring and the O-ring reaction force
  • FIG. 3B is a diagram showing the relationship between the clearance and the crushing margin of the O-ring.
  • FIG. 4A is a diagram showing the relationship between the clearance and the O-ring reaction force
  • FIG. 4B is a diagram showing the relationship between the clearance and the spring constant of the O-ring.
  • FIG. 5 is a diagram showing the relationship between the clearance and the load displacement amount.
  • FIG. 6A is a diagram showing a clearance range in which an O-ring can be prevented from rotating
  • FIG. 6B is a diagram showing a clearance range in which vibration transmission can be reliably prevented
  • FIG. 7 is a diagram in which FIGS. 6 (a) and 6 (b) are superimposed, and is a diagram illustrating a clearance range in which vibration transmission can be prevented and the outer ring can be prevented from rotating.
  • One aspect of the present disclosure is a bearing structure for supporting a rotating shaft of a rotating body housed in a housing with respect to the housing, the rotating shaft being attached to the housing, and the rotating shaft being attached to the housing.
  • a bearing to be supported the bearing having an inner ring through which the rotating shaft is inserted, and an outer ring including an annular groove formed on an outer peripheral surface facing the inner wall surface of the housing, and a bearing disposed in the groove of the outer ring of the bearing
  • An O-ring that protrudes radially outward from the outer peripheral surface and abuts against the inner wall surface of the housing, and a clearance is formed between the inner wall surface of the housing and the outer peripheral surface of the bearing. It is larger than the radial displacement of the O-ring.
  • the rotating shaft of the rotating body is supported by the bearing structure.
  • An O-ring provided between the outer ring of the bearing and the inner wall surface of the housing functions in the same manner as a spring.
  • the radial displacement is determined based on the mass of the rotating body and the spring constant of the O-ring. Since the clearance formed between the inner wall surface of the housing and the outer peripheral surface of the bearing is larger than the radial displacement amount of the O-ring, the outer ring of the bearing is prevented from coming into contact with the housing. According to this bearing structure, vibration can be reliably prevented from being transmitted to the housing via the bearing.
  • the inner wall surface of the housing, the bearing, and the O-ring are configured such that the frictional force between the inner wall surface of the housing and the O-ring is greater than the rotational force of the rotating body. In this case, rotation of the outer ring of the bearing can be suppressed when the rotating body rotates.
  • the electric compressor according to another aspect of the present disclosure is a housing, a compressor impeller that is attached to an end of the rotating shaft and forms a part of a rotating body, and the rotating shaft is supported with respect to the housing.
  • the bearing structure described in 2. is provided. According to this electric compressor, the outer ring of the bearing is prevented from contacting the housing when the rotating body including the compressor impeller rotates. Therefore, vibration can be reliably prevented from being transmitted to the housing via the bearing, and as a result, generation of vibration and noise in the electric compressor can be suppressed.
  • the electric compressor 1 which concerns on one Embodiment is demonstrated.
  • the electric compressor 1 is applied to an internal combustion engine of a vehicle or a ship, for example.
  • the electric compressor 1 includes a compressor 7.
  • the electric compressor 1 rotates the compressor impeller 8 by the interaction of the rotor portion 13 and the stator portion 14, compresses a fluid such as air, and generates compressed air.
  • the electric compressor 1 may be connected to a supercharger (not shown) applied to an internal combustion engine of a vehicle or a ship, for example. In that case, the electric compressor 1 sends a compressed fluid such as compressed air to the compressor of the supercharger. By combining the electric compressor 1 and the supercharger, the electric compressor 1 helps to start up the supercharger.
  • the electric compressor 1 includes a rotating shaft 12 that is rotatably supported in the housing 2, and a compressor impeller 8 fastened to a distal end portion 12 a of the rotating shaft 12.
  • the housing 2 includes a motor housing 3 that houses the rotor portion 13 and the stator portion 14, and an end wall 3 a that closes an opening on the second end side of the motor housing 3 (right side in the drawing, opposite to the compressor impeller 8).
  • a compressor housing 6 that houses the compressor impeller 8 is provided on the first end side of the motor housing 3 (the left side in the figure, the compressor impeller 8 side).
  • the compressor housing 6 includes a suction port 9, a scroll portion 10, and a discharge port 11.
  • an inverter 19 for supplying current to the stator unit 14 may be provided outside the end wall 3a.
  • the rotor portion 13 is attached to the central portion of the rotating shaft 12 in the axial direction, and includes one or a plurality of permanent magnets (not shown) attached to the rotating shaft 12.
  • the stator portion 14 is attached to the inner surface of the motor housing 3 so as to surround the rotor portion 13 and includes a coil portion (not shown).
  • an alternating current is passed through the coil portion of the stator portion 14, the rotation shaft 12 and the compressor impeller 8 are united and rotate around the rotation axis A by the interaction between the rotor portion 13 and the stator portion 14.
  • the compressor impeller 8 rotates, the compressor 7 sucks external air through the suction port 9, compresses the air through the scroll unit 10, and discharges the compressed air from the discharge port 11.
  • the compressed air discharged from the discharge port 11 is supplied to the internal combustion engine described above.
  • the electric compressor 1 includes two bearings 20 that rotatably support the rotary shaft 12 with respect to the housing 2.
  • the bearing 20 is attached in the motor housing 3 of the housing 2.
  • the bearing 20 supports the rotating shaft 12 with respect to the motor housing 3 by both ends.
  • the first bearing 20 is provided on a sleeve portion 17 formed on the compressor impeller 8 side of the motor housing 3.
  • the second bearing 20 is provided on the sleeve portion 18 that protrudes in the axial direction (compressor impeller 8 side) from the end wall 3a.
  • the compressor impeller 8 is attached to the rotary shaft 12 by a shaft end nut 16 provided at the distal end portion 12 a of the rotary shaft 12.
  • the rotating shaft 12, the compressor impeller 8 fixed to the rotating shaft 12, the rotor portion 13, and the bearing 20 constitute a rotating body C integrally in the housing 2.
  • the rotating shaft 12, the compressor impeller 8, the rotor unit 13, and the bearing 20 each form a part of the rotating body C.
  • the rotating body C is biased to one side in the axial direction while being accommodated in the motor housing 3.
  • An annular wall surface 17b (see FIG. 2) of the sleeve portion 17 is in contact with and in contact with the end surface of the bearing 20 in the axial direction, whereby the rotating body C is positioned in the axial direction.
  • the electric compressor 1 of the present embodiment vibration that may be caused by the rotation of the rotating body C is suppressed. More specifically, transmission of vibration of the rotating body C to the housing 2 is prevented, and as a result, vibration of the electric compressor 1 is suppressed.
  • the electric compressor 1 includes a bearing structure including the bearing 20 described above.
  • the bearing structures provided at two locations in the axial direction with respect to the rotating shaft 12 have the same configuration. Each bearing structure supports the rotating shaft 12 of the rotating body C with respect to the motor housing 3.
  • first bearing 20 and the bearing structure provided on the first end side will be described.
  • a description of the second bearing 20 provided on the second end side and the bearing structure is omitted.
  • the arrangement of the second bearing 20 with respect to the sleeve portion 18 may be the same as the arrangement of the first bearing 20 with respect to the sleeve portion 17.
  • the bearing 20 is, for example, a ball bearing. More specifically, the bearing 20 is, for example, a grease lubricated radial bearing. The bearing 20 may be a deep groove bearing or an angular bearing.
  • the bearing 20 includes an inner ring 21 through which the rotary shaft 12 is inserted, and an outer ring 22 that can rotate relative to the inner ring 21 via a plurality of balls 23.
  • the inner ring 21 is press-fitted into the rotary shaft 12.
  • the inner peripheral surface 21 a of the inner ring 21 is in contact with the outer peripheral surface 12 b of the rotating shaft 12.
  • the end surface on the compressor impeller 8 side of the inner ring 21 may abut on the end surface perpendicular to the rotation axis A in the boss portion 8 a of the compressor impeller 8.
  • the sleeve portion 17 of the motor housing 3 includes a cylindrical inner peripheral surface (inner wall surface) 17a facing inward in the radial direction.
  • the sleeve portion 17 supports the outer ring 22.
  • the outer ring 22 includes an outer peripheral surface 22a facing the inner peripheral surface 17a of the sleeve portion 17, and two annular groove portions 22c formed on the outer peripheral surface 22a.
  • the diameter of the outer peripheral surface 22 a of the outer ring 22 is smaller than the inner peripheral surface 17 a of the sleeve portion 17.
  • a cylindrical clearance B is formed between the inner peripheral surface 17 a of the sleeve portion 17 and the outer peripheral surface 22 a of the outer ring 22.
  • An end surface of the outer ring 22 on the compressor impeller 8 side may abut on a wall surface 17b perpendicular to the rotation axis A in an annular portion disposed on the outer peripheral side of the boss portion 8a of the compressor impeller 8. Note that the shape of the clearance B can be changed according to the displacement of the rotating body C when the electric compressor 1 is operated.
  • the two groove portions 22c are formed so as to be separated in the axial direction. Each groove portion 22c is continuous with the outer peripheral surface 22a and is opened outward in the radial direction.
  • An annular O-ring 30 is disposed in each groove 22c.
  • the O-ring 30 is directly fitted into the outer ring 22.
  • the O-ring 30 is made of an elastic material.
  • the O-ring 30 is made of rubber, for example.
  • the inner peripheral surface of the O-ring 30 fitted into the groove 22c is in contact with the bottom surface of the groove 22c. A part of the outer peripheral side of the O-ring 30 protrudes outward in the radial direction from the outer peripheral surface 22a.
  • An annular outer peripheral end surface farthest from the rotation axis A in the O-ring 30 is in contact with the inner peripheral surface 17 a of the sleeve portion 17.
  • the O-ring 30 has, for example, a circular cross section in a natural state (a state in which no external force is received) before being disposed between the bearing 20 and the sleeve portion 17.
  • the O-ring 30 sandwiched between the groove portion 22c of the bearing 20 and the inner peripheral surface 17a of the sleeve portion 17 is compressed (crushed).
  • the compressed O-ring 30 has, for example, a non-circular cross section.
  • the size of the clearance B described above is set in consideration of the diameter (wire diameter) of the cross section of the O-ring 30, the crushing allowance of the O-ring 30, and the spring characteristics of the crushed O-ring 30.
  • the size of the clearance B is not limited to these elements, and may be set in consideration of the hardness (hardness) of the O-ring 30, for example.
  • the term “crushing allowance” has the same concept as “crushing amount” or “crushing rate”.
  • the term “crush” is the same concept as “compression”.
  • F reaction force of the O-ring 30 x: crushing allowances a, b, c of the O-ring 30: coefficient when the wire diameter of the O-ring 30 is 1 mm (however, the coefficient varies depending on the material and / or hardness, etc.)
  • D wire diameter of the O-ring 30 d0: diameter ⁇ of the O-ring 30: coefficient.
  • the crushing amount x of the O-ring 30 is expressed by the following equation (2) from the dimensional relationship shown in FIG. here, X: Diameter of the bottom surface of the groove portion 22c Y: Inner diameter of the sleeve portion 17.
  • the size ⁇ in the radial direction of the clearance B is also expressed by the following formula (3) from the dimensional relationship shown in FIG. here, Z: outer diameter of outer ring 22 (diameter of outer peripheral surface 22a) It is.
  • the relationship between the radial size ⁇ of the clearance B and the crushing allowance x of the O-ring 30 is expressed by the following equation (4).
  • the expression (4) is expressed as shown in FIG.
  • the wire diameter D is shown for the compressed O-ring 30 so that the structure can be easily imagined with reference to the drawing, but this is not strictly accurate.
  • the wire diameter D is the diameter of the linear portion of the O-ring 30 in the natural state.
  • the dimensions X, Y, and Z are diameters with respect to the rotation axis A, respectively.
  • the condition for preventing the outer ring 22 (and the O-ring 30) from rotating is that the frictional force Fr is larger than the rotational force Ft. That is, the establishment of the following expression (5) is the first condition.
  • the inner peripheral surface 17 a of the sleeve portion 17 of the motor housing 3, the bearing 20 and the O-ring 30 are such that the frictional force Fr between the inner peripheral surface 17 a and the O-ring 30 is greater than the rotational force Ft of the rotating body C. It is configured.
  • the accompanying phenomenon of the outer ring 22 is prevented when the clearance range is 1.0 or more.
  • K Spring constant of the O-ring 30
  • Mg Load applied to the bearing 20 (rotor mass load + eccentric load + vibration load received by the bearing 20)
  • g Gravitational acceleration.
  • Equation (8) is established.
  • the condition for the outer ring 22 not to hit the sleeve portion 17 is that the radial size ⁇ of the clearance B is larger than the displacement amount r. Therefore, from the expressions (3) and (8), the establishment of the following expression (9) is the second condition.
  • the clearance range is the range indicated by the arrows in the figure. There is a need. Further, as shown in FIG. 6B, in order to effectively suppress vibration from the second condition, the clearance range needs to be a range indicated by an arrow in the drawing.
  • the clearance B in the range indicated by the arrow in FIG. 7 is set. Is done.
  • the size ⁇ of the clearance B is set in a range where both rotation prevention and vibration suppression are compatible in consideration of the rotational load and the load applied to the O-ring 30 as described above. The feature of this embodiment is that both of these are satisfied.
  • the rotating shaft 12 of the rotating body C is supported by the bearing structure.
  • An O-ring 30 provided between the outer ring 22 of the bearing 20 and the inner peripheral surface 17a of the motor housing 3 functions in the same manner as a spring against a radial load.
  • the amount of radial displacement is determined based on the mass of the rotating body C, the eccentric load, vibration, and the spring constant of the O-ring 30. Since the clearance B formed between the inner peripheral surface 17a of the housing 2 and the outer peripheral surface 22a of the bearing 20 is larger than the radial displacement amount of the O-ring 30, the outer ring 22 of the bearing 20 contacts the sleeve portion 17. Is prevented. According to this bearing structure, vibration can be reliably prevented from being transmitted to the housing 2 via the bearing 20. An impact load is not applied to the sleeve portion 17 but a damped load is applied.
  • the outer ring 22 of the bearing 20 is prevented from coming into contact with the housing 2 when the rotating body C including the compressor impeller 8 rotates. Therefore, it is possible to reliably prevent vibration from being transmitted to the housing 2 via the bearing 20, and as a result, generation of vibration and noise in the electric compressor 1 can be suppressed.
  • this invention is not limited to the said embodiment.
  • two bearings 20 are provided, and the bearing structure described above may not be provided for one of them.
  • One of the two bearings 20 may be omitted.
  • the bearing structure may be provided only on the first end side of the rotating shaft 12 or may be provided only on the second end side of the rotating shaft 12.
  • the relationship between the frictional force between the inner peripheral surface 17a and the O-ring 30 and the rotational force of the rotating body C may not satisfy the relationship described in the above embodiment. That is, a bearing structure that satisfies the second condition but does not satisfy the first condition may be employed. Even in such a case, the effect of reliably preventing vibrations from being transmitted to the housing 2 is achieved.
  • the cross-sectional shape of the O-ring 30 is not limited to a circle.
  • vibration can be reliably prevented from being transmitted to the housing via the bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Supercharger (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne une structure de roulement comprenant : un arbre rotatif ; un roulement qui est fixé à l'intérieur d'un boîtier et qui supporte l'arbre rotatif par rapport au boîtier, le roulement comprenant un chemin de roulement interne à travers lequel l'arbre rotatif est inséré et un chemin de roulement externe comprenant une partie de rainure de forme annulaire formée dans une surface périphérique externe qui fait face à une surface périphérique interne du boîtier ; et un joint torique qui est placé dans la partie de rainure du chemin de roulement externe du roulement et qui fait saillie diamétralement vers l'extérieur au-delà de la surface périphérique externe pour entrer en contact avec la surface périphérique interne du boîtier. Un espace libre est formé entre la surface périphérique interne du boîtier et la surface périphérique externe du roulement. L'espace libre est supérieur à la quantité de déplacement diamétral du joint torique.
PCT/JP2018/012150 2017-03-31 2018-03-26 Structure de roulement et compresseur électrique Ceased WO2018181186A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2019509808A JP6725064B2 (ja) 2017-03-31 2018-03-26 軸受構造および電動コンプレッサ
DE112018001791.5T DE112018001791T5 (de) 2017-03-31 2018-03-26 Lageraufbau und elektrischer Kompressor
US16/492,375 US20200040903A1 (en) 2017-03-31 2018-03-26 Bearing structure and electric compressor
CN201880004998.9A CN110073120A (zh) 2017-03-31 2018-03-26 轴承构造以及电动压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017071204 2017-03-31
JP2017-071204 2017-03-31

Publications (1)

Publication Number Publication Date
WO2018181186A1 true WO2018181186A1 (fr) 2018-10-04

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PCT/JP2018/012150 Ceased WO2018181186A1 (fr) 2017-03-31 2018-03-26 Structure de roulement et compresseur électrique

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Country Link
US (1) US20200040903A1 (fr)
JP (1) JP6725064B2 (fr)
CN (1) CN110073120A (fr)
DE (1) DE112018001791T5 (fr)
WO (1) WO2018181186A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021116016A1 (fr) 2019-12-11 2021-06-17 Efficient Energy Gmbh Support de palier permettant de recevoir un palier
WO2021166136A1 (fr) * 2020-02-20 2021-08-26 三菱重工エンジン＆ターボチャージャ株式会社 Compresseur

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2563617B (en) 2017-06-20 2020-04-08 Dyson Technology Ltd An electric machine
CN112041573B (zh) 2018-04-27 2021-12-28 株式会社Ihi 轴承及增压器
JP2020148316A (ja) * 2019-03-15 2020-09-17 Ntn株式会社 転がり軸受
JP7479944B2 (ja) * 2020-06-08 2024-05-09 ミネベアミツミ株式会社 モータ

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013228108A (ja) * 2007-01-11 2013-11-07 Nsk Ltd 転がり軸受
JP2016148429A (ja) * 2015-02-13 2016-08-18 日本精工株式会社 摩擦ローラ式変速機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2545028B2 (ja) * 1993-02-12 1996-10-16 川崎重工業株式会社 軸受装置
JPH0989045A (ja) * 1995-09-27 1997-03-31 Nec Eng Ltd 緩衝支持構造
JP2000120669A (ja) 1998-10-07 2000-04-25 Nsk Ltd 転がり軸受
JP4340145B2 (ja) * 2003-12-26 2009-10-07 株式会社日立製作所 防振工具ホルダ
JP2005321006A (ja) * 2004-05-07 2005-11-17 Nsk Ltd 転がり軸受装置
JP2006161876A (ja) * 2004-12-03 2006-06-22 Nsk Ltd 転がり軸受
JP2006234097A (ja) * 2005-02-25 2006-09-07 Nsk Ltd クリープ防止装置及び転がり軸受
JP2007211865A (ja) 2006-02-08 2007-08-23 Ntn Corp クリープ防止転がり軸受
JP2009190141A (ja) * 2008-02-15 2009-08-27 Mitsubishi Heavy Ind Ltd 工作機械及び加工方法
JP6035732B2 (ja) * 2011-12-16 2016-11-30 日本精工株式会社 転がり軸受
JP6155573B2 (ja) * 2012-08-28 2017-07-05 株式会社Ihi 遠心圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013228108A (ja) * 2007-01-11 2013-11-07 Nsk Ltd 転がり軸受
JP2016148429A (ja) * 2015-02-13 2016-08-18 日本精工株式会社 摩擦ローラ式変速機

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021116016A1 (fr) 2019-12-11 2021-06-17 Efficient Energy Gmbh Support de palier permettant de recevoir un palier
DE102020210331B4 (de) * 2019-12-11 2026-01-08 Vertiv Srl Lagerhalter zum Aufnehmen eines Lagers
WO2021166136A1 (fr) * 2020-02-20 2021-08-26 三菱重工エンジン＆ターボチャージャ株式会社 Compresseur
JPWO2021166136A1 (fr) * 2020-02-20 2021-08-26
JP7391180B2 (ja) 2020-02-20 2023-12-04 三菱重工エンジン＆ターボチャージャ株式会社 コンプレッサ
US11976665B2 (en) 2020-02-20 2024-05-07 Mitsubishi Heavy Industries Engine & Turbocharger Ltd. Compressor

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