WO2021064793A1 - Système d'arbre d'entrée - Google Patents

Système d'arbre d'entrée Download PDF

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Publication number
WO2021064793A1
WO2021064793A1 PCT/JP2019/038514 JP2019038514W WO2021064793A1 WO 2021064793 A1 WO2021064793 A1 WO 2021064793A1 JP 2019038514 W JP2019038514 W JP 2019038514W WO 2021064793 A1 WO2021064793 A1 WO 2021064793A1
Authority
WO
WIPO (PCT)
Prior art keywords
input shaft
bearing
case
outer ring
peripheral surface
Prior art date
Application number
PCT/JP2019/038514
Other languages
English (en)
Japanese (ja)
Inventor
浩介 琴尾
和彦 西宮
淳司 大塚
Original Assignee
東芝三菱電機産業システム株式会社
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 東芝三菱電機産業システム株式会社 filed Critical 東芝三菱電機産業システム株式会社
Priority to CN201980067974.2A priority Critical patent/CN112997014B/zh
Priority to JP2020558061A priority patent/JP6921470B1/ja
Priority to PCT/JP2019/038514 priority patent/WO2021064793A1/fr
Publication of WO2021064793A1 publication Critical patent/WO2021064793A1/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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
    • G01L3/16—Rotary-absorption dynamometers, e.g. of brake type
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/02—Gearings; Transmission mechanisms
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles

Definitions

  • the present invention relates to an input shaft system having an input shaft connected to a specimen.
  • the input shaft system is used for testing drive system units such as power trains in chassis dynamometers, for example.
  • drive system units such as power trains in chassis dynamometers
  • an input shaft system rotates the input shaft by a drive source simulating a HEV (Hybrid Electric Vehicle) motor or an EV (Electric Vehicle) motor, which is becoming smaller at high speed, and the input shaft is used as a transmission or the like. It is rotatably connected to the specimen.
  • HEV Hybrid Electric Vehicle
  • EV Electric Vehicle
  • Such an input shaft system has a shaft torque meter for measuring the shaft torque of the input shaft, and is used as a test system capable of measuring the shaft torque of the input shaft.
  • Examples of the input shaft system described above include main components (low inertia motor, torque detector, etc.) of the automobile test apparatus disclosed in Patent Document 1.
  • An object of the present invention is to solve the above-mentioned problems and to provide an input shaft system capable of accurately measuring the shaft torque of the input shaft.
  • the input shaft system is an input shaft system having an input shaft connected to a specimen, and is provided between a drive source for rotating the input shaft and the drive source and the specimen.
  • the intermediate bearing device includes an intermediate bearing device that supports the input shaft, and a shaft torque meter that is provided between the intermediate bearing device and the drive source and measures the shaft torque of the input shaft.
  • the intermediate bearing device has an oil film forming region. It is characterized by having a damping function of reducing the vibration applied to the input shaft by the oil film forming region.
  • the intermediate bearing device in the input shaft system of the present invention according to claim 1 has a damping function of reducing vibration applied to the input shaft by an oil film forming region.
  • the intermediate bearing device is provided between the specimen and the shaft torque meter, and due to the damping function of the intermediate bearing device, vibration or eccentric load from the specimen side causes the shaft torque meter to be installed on the input shaft. The impact can be significantly reduced.
  • the input shaft system of the present invention according to claim 1 has an effect that the shaft torque of the input shaft can be accurately measured by the shaft torque meter.
  • FIG. 1 is an explanatory diagram showing a configuration of a drive system dynamo stem 500 using the input shaft system JS of the embodiment.
  • the drive system dynamo stem 500 includes an input shaft system JS, a specimen 300, an output shaft 250, and front wheel dynamo pairs 201 and 202 as main components.
  • the input shaft 150 of the input shaft system JS is rotatably connected to the specimen 300, and the output shafts 250 of the front wheel dynamo pairs 201 and 202 are also rotatably connected to the specimen 300. There is.
  • the input shaft system JS includes a low inertia motor 110 and an intermediate shaft structure JM as main components.
  • the input shaft system JS is shown in a simplified manner, and the actual structure shows the structure shown in FIG. 2 which will be described later. Further, the input shaft system JS and the front wheel right dynamo 202 have no connection relationship.
  • the low inertia motor 110 which is the drive source, rotates the directly connected input shaft 150.
  • the rotational force of the input shaft 150 is transmitted to the specimen 300 via the intermediate shaft structure JM.
  • FIG. 1 shows the FF transmission as the specimen 300.
  • the "FF transmission” means a transmission for a front engine / front drive (Front Engine / Front Drive).
  • the input shaft 150 is rotatably connected to the low inertia motor 110, the input shaft 150 is rotatably supported by the intermediate shaft structure JM, and the tip portion thereof is connected in the specimen 300.
  • the specimen 300 receives the rotational movement force of the input shaft 150 from the low inertia motor 110, and rotates the output shaft 250 based on this rotational movement force. This point will be described in detail below.
  • the input shaft 150 is rotated, and the rotational kinetic force of the input shaft 150 is transmitted to the specimen 300 via the intermediate shaft structure JM. ..
  • the specimen 300 has an input shaft 150, internal gears 351 to 354, a relay shaft 330, and an input shaft 150 as main components.
  • the tip portion of the input shaft 150 is connected in the specimen 300, and the central portion of the output shaft 250 is connected in the specimen 300.
  • the internal gear 351 is attached to the tip of the input shaft 150 and rotates with the rotation of the input shaft 150.
  • Internal gears 352 and 353 are provided at both ends of the relay shaft 330.
  • the internal gear 354 is attached to the central portion of the output shaft 250, and rotates the output shaft 250 as it rotates. Further, the internal gear 351 and the internal gear 352 are meshed with each other, and the internal gear 353 and the internal gear 354 are meshed with each other.
  • the rotational force of the input shaft 150 is transmitted to the relay shaft 330 via the internal gears 351 and 352 that mesh with each other, and the rotational force of the relay shaft 330 is transmitted to the relay shaft 330 via the internal gears 353 and 354 that mesh with each other. It is transmitted to 250.
  • the rotational kinetic force of the input shaft 150 is transmitted from above to below between the plurality of internal gears 351 to 354, and then is transmitted to the output shaft 250.
  • the front wheel dynamos pairs 201 and 202 can be rotated with the rotation of the output shaft 250.
  • FIG. 2 is an explanatory diagram showing a detailed structure of the input axis system JS shown in FIG.
  • the input shaft system JS includes a low inertia motor 110, an intermediate shaft structure JM, and a base 106 as main components.
  • the intermediate shaft structure JM includes an intermediate bearing device 100, a shaft torque meter 102, and a shaft joint 104.
  • the input shaft 150 (not shown in FIG. 2) is rotatably supported by the intermediate bearing device 100 via the shaft joint 104 and the shaft torque meter 102.
  • the base 106 has a flush upper surface, and the low inertia motor 110 and the intermediate bearing device 100 are fixedly arranged on the upper surface to support the low inertia motor 110 and the intermediate bearing device 100 from below. Further, the base 106 is integrally configured with the low inertia motor 110 (including the input shaft 150), the shaft joint 104, the shaft torque meter 102, and the low inertia motor 110.
  • the input shaft 150 directly connected to the low inertia motor 110 is removable from the specimen 300.
  • the input shaft system JS is provided between the low inertia motor 110 as a drive source for rotating the input shaft 150, the low inertia motor 110, and the specimen 300, and rotatably supports the input shaft 150.
  • a shaft torque meter 102 which is provided between the intermediate bearing device 100 and the intermediate bearing device 100 and the low inertia motor 110 and measures the shaft torque applied to the input shaft 150, is provided as a main component.
  • the intermediate bearing device 100 has an oil film forming region R5 described later, and the oil film forming region R5 has a damping function for reducing vibration applied to the input shaft 150.
  • the intermediate bearing device 100 in the input shaft system JS of the present embodiment has a damping function of reducing the vibration applied to the input shaft 150 by the oil film forming region R5.
  • An intermediate bearing device 100 is provided between the specimen 300 and the shaft torque meter 102, and the shaft torque on the input shaft 150 due to vibration or eccentric load from the specimen 300 side due to the damping function of the intermediate bearing device 100.
  • the influence on the installation locations of 102 in total can be significantly reduced.
  • the input shaft system JS of the present embodiment has an effect that the shaft torque of the input shaft 150 can be accurately measured by the shaft torque meter 102.
  • the low inertia motor 110 and the intermediate bearing device 100 can be fixedly arranged on the upper surface of the base 106 and supported with good stability, and the input shaft is supported by the shaft torque meter 102.
  • the shaft torque of 150 can be measured more accurately.
  • the base 106, the low inertia motor 110 (including the input shaft 150), the shaft joint 104, the shaft torque meter 102, and the intermediate bearing device 100 are integrally configured.
  • the input axis system JS including the above can be easily handled.
  • the input shaft 150 of the input shaft system JS can be removed from the specimen 300 and connected to another specimen, etc., which can be performed relatively easily.
  • FIG. 3 is an explanatory diagram showing the overall configuration of the intermediate bearing device 100 shown in FIG.
  • the intermediate bearing device 100 includes a cylindrical bearing 4 that rotatably supports the input shaft 150, a cylindrical bearing case 5 that supports the bearing 4 from the outer peripheral surface side of the bearing 4, and a bearing.
  • a bearing For bearings that have a facing surface (inner peripheral surface) facing the outer peripheral surface of the case 5 and support the bearing case 5 by bringing the outer peripheral surface and the facing surface of the bearing case 5 into contact with each other via a pair of O-rings 51.
  • the housing 1 is included as a main component.
  • FIG. 4 is a perspective view schematically showing the external structure of the bearing case 5 shown in FIG. As shown in FIGS. 3 and 4, the bearing case 5 has a cylindrical shape having a hollow portion for accommodating the bearing 4 inside.
  • the bearing case 5 has a pair of O-ring grooves 53 (a pair of grooves) provided in an annular shape along the circumferential direction on the outer peripheral surface, and a pair of O-rings 51 provided in the pair of O-ring grooves 53. And four case through holes 50 (two case through holes in FIG. 4) that are selectively provided on one semicircular side (upper semicircular side) of the side surface of the bearing case 5 in the circumferential direction and each penetrates the side surface. (Only 50 is shown) is included as a main component. In FIG. 4, for convenience of explanation, the pair of O-rings 51 are not shown.
  • the bearing case 5 has four case through holes 50 as a plurality of case through holes penetrating the side surface. Further, as shown in FIG. 4, the pair of O-ring grooves 53 are provided near both ends in the axial direction (direction connecting the bottom surface and the top surface) on the side surface of the bearing case 5. Then, the region on the outer peripheral surface of the bearing case 5 between the pair of O-rings 51 becomes the oil film forming region R5, and the four case through holes 50 are selectively provided in the oil film forming region R5.
  • a pair of detent dents 55 are provided on the side surface of the bearing case 5 at the boundary between the upper semicircle and the lower semicircle.
  • the bearing 4 includes an inner ring 6, an outer ring 7, and a rolling ball 8 as main components.
  • the outer ring 7 has a cylindrical shape having an outer peripheral surface in contact with the inner peripheral surface of the bearing case 5, and the inner ring 6 has a cylindrical shape provided so as to have an internal space between the outer ring 7 and the outer ring 7. Then, the rolling ball 8 is arranged in the internal space between the inner ring 6 and the outer ring 7.
  • the outer ring 7 is composed of an outer ring side portion 7a, an outer ring side portion 7b, and an outer ring center portion 7c, and has a positional relationship in which the outer ring center portion 7c is sandwiched between the outer ring side portions 7a and 7b. ..
  • An outer ring through hole 70 penetrating the outer ring center 7c is provided in the outer ring center 7c above the outer ring 7. Further, in the outer ring center portion 7c below the outer ring 7, a through hole 71 penetrating the outer ring center portion 7c is provided.
  • the through hole 71 is formed with a recess in the lower region for restraining the structure wider than the upper region in the rotational direction, and this recess becomes the screw accommodating region 71x.
  • FIG. 5 is a perspective view schematically showing the external structure of the outer ring 7.
  • each of the outer ring 7 selectively corresponds to a plurality of case through holes 50 on one semicircular side (upper semicircular side of FIG. 5) in the circumferential direction of the side surface.
  • It has four outer ring through holes 70 (only two outer ring through holes 70 are shown in FIG. 5), which are provided and are a plurality of outer ring through holes penetrating the side surface.
  • the outer ring 7 has one through hole 71 provided on the other semicircular side (lower semicircular side) facing the one semicircular side in the circumferential direction of the side surface.
  • FIG. 6 is an explanatory view schematically showing the positional relationship of the side surfaces of the bearing case 5 and the outer ring 7 in the circumferential direction.
  • the cross section AA shown in FIG. 6 has the structure shown in FIG.
  • the four case through holes 50 of the bearing case 5 and the four outer ring through holes 70 of the outer ring 7 are continuously connected between the corresponding case through holes 50 and the outer ring through holes 70.
  • the common center of the circle defining the circumferential direction of the side surface of the bearing case 5 and the circle defining the circumferential direction of the side surface of the outer ring 7 is the center point C1, from the center point C1.
  • the outer ring through hole 70 of one of the four outer ring through holes 70 is provided so as to be always located on the four straight lines extending over the four case through holes 50. That is, the four case through holes 50 and the four outer ring through holes 70 have a one-to-one correspondence, and the corresponding case through holes 50 and the outer ring through holes 70 exist on the same straight line starting from the center point C1.
  • the tip region of the outer ring through hole 70 has a narrower oil flow path than the other regions and has a throttle structure 70s that branches into two, and the flow of oil is restricted by these throttle structures 70s.
  • Stable oil can be supplied to the inner ring 6 and the rolling ball 8 of the bearing 4.
  • a pair of detent dents 55 are provided on the side surface of the bearing case 5 at the boundary between the upper semicircle and the lower semicircle. Therefore, the center point C1 exists on the line connecting the pair of detent dents 55.
  • the bearing case 5 and the outer ring 7 have through holes 57 and through holes 71 of the bearing case 5 provided on the other semicircular side in the circumferential direction of the respective side surfaces.
  • FIG. 7 is a perspective view schematically showing the external structure of the inner ring 6.
  • the inner ring 6 has a side surface having a diameter smaller than the side surface of the outer ring 7 and is formed in a cylindrical shape so that an internal space is formed between the inner ring 6 and the outer ring 7.
  • the bottom screw 73 which is a fixing screw, is provided between the outer ring 7 and the bearing case 5 on the other semicircular side of the side surface of the bearing case 5 and the outer ring 7, and is centered on the outer ring.
  • the movement of the portion 7c in the rotation direction is restrained. That is, the bottom screw 73 is provided so as to penetrate the through hole 57 of the bearing case 5 and be housed in the screw accommodating area 71x of the through hole 71.
  • FIG. 8 is a block diagram schematically showing an oil supply system in the intermediate bearing device 100 shown in FIG. Oil is supplied from the oil supply circuit 10 shown in the figure onto the outer peripheral surface of the bearing case 5. The oil supplied on the outer peripheral surface of the bearing case 5 is supplied to the inside of the bearing 4 only through the four case through holes 50 of the bearing case 5 and the four outer ring through holes 70 of the outer ring 7.
  • the flow of oil is indicated by an arrow.
  • the oil supplied from the oil supply circuit 10 to the outer ring 7 and the rolling ball 8 of the bearing 4 via the outer ring center 7c of the bearing case 5 and the outer ring 7 is the other half of the outer ring 7 in the outer peripheral direction. It is discharged to the outside from the bearing 4 on the circular side.
  • FIG. 9 is an explanatory diagram schematically showing the formation state of the oil film.
  • the region on the outer peripheral surface of the bearing case 5 between the pair of O-rings 51 is the oil film forming region R5. Therefore, when oil is supplied from the oil supply circuit 10 onto the outer peripheral surface of the bearing case 5, the oil film 25 is formed in the oil film forming region R5 between the outer peripheral surface of the bearing case 5 and the facing surface (inner peripheral surface) of the housing 1. It is formed.
  • an oil film 25 is formed in the oil film forming region R5 as shown in FIGS. 3 and 9 by refueling from the refueling circuit 10. This is because the pair of O-rings 51 closes the oil film forming region R5 on the outer peripheral surface of the bearing case 5 from other regions except for the four case through holes 50 selectively provided in the oil film forming region R5. Because it becomes a space.
  • the oil film 25 is shown in a mode having a predetermined thickness, but the thickness of the oil film 25 is actually very small.
  • the intermediate bearing device 100 used in the input shaft system JS of the present embodiment can exhibit the above damping function of effectively reducing the vibration applied to the supporting input shaft 150 by the oil film forming region R5. it can.
  • the intermediate bearing device 100 has the oil film forming region R5, and has the damping function of reducing the vibration applied to the input shaft 150 by the oil film forming region R5.
  • the oil film 25 in the oil film forming region R5 is formed through the four case through holes 50 (plural case through holes) of the bearing case 5 and the four outer ring through holes 70 (plural outer ring through holes) of the bearing 4. A part of the oil is supplied to the bearing 4. Therefore, the intermediate bearing device 100 can cool the bearing 4 without increasing the size of the device.
  • the oil is supplied to the bearing 4 only through the four case through holes 50 and the four outer ring through holes 70 selectively formed in the oil film forming region R5.
  • the oil film 25 can be stably formed in the oil film forming region R5.
  • the tip region of each of the plurality of outer ring through holes 70 has a drawing structure 70s in which the oil flow path is narrower than the other regions. That is, in the intermediate bearing device 100, the tip region of the outer ring through hole 70 provided in the outer ring center portion 7c of the outer ring 7 has a drawing structure 70s in which the oil flow path is narrower than the other regions.
  • the oil is smoothly supplied to the inner ring 6 and the rolling ball 8 in the bearing 4, and the formation of the oil film 25 in the oil film forming region R5 is stably maintained. Can be done.
  • the intermediate bearing device 100 of the present embodiment has the effect of reducing vibration due to the input shaft 150 and cooling the bearing 4 with a relatively small number of members.
  • the FF transmission is shown as the specimen 300, but the present invention is not limited to this, and for example, a differential gear or the like may be used. That is, all the constituent parts that can be connected to the input shaft 150 can be used as the specimen 300.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Ocean & Marine Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Sealing Of Bearings (AREA)

Abstract

Le but de la présente invention est de fournir un système d'arbre d'entrée qui permet de mesurer avec précision le couple d'arbre d'un arbre d'entrée. Ce système d'arbre d'entrée (JS) comprend, en tant que composants principaux, un moteur à faible inertie (110) qui amène un arbre d'entrée (150) en rotation, un dispositif de palier intermédiaire (100) qui est disposé entre le moteur à faible inertie (110) et une pièce de test (300) et supporte de manière rotative l'arbre d'entrée (150), et un dispositif de mesure de couple d'arbre (102) qui est disposé entre le dispositif de palier intermédiaire (100) et le moteur à faible inertie (110) et mesure le couple exercé sur l'arbre d'entrée (150). Le dispositif de palier intermédiaire (100) présente une fonction d'amortissement grâce à laquelle la vibration appliquée à l'arbre d'entrée (150) est réduite au moyen d'une région de formation de film d'huile (R5).
PCT/JP2019/038514 2019-09-30 2019-09-30 Système d'arbre d'entrée WO2021064793A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201980067974.2A CN112997014B (zh) 2019-09-30 2019-09-30 输入轴系统
JP2020558061A JP6921470B1 (ja) 2019-09-30 2019-09-30 入力軸システム
PCT/JP2019/038514 WO2021064793A1 (fr) 2019-09-30 2019-09-30 Système d'arbre d'entrée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/038514 WO2021064793A1 (fr) 2019-09-30 2019-09-30 Système d'arbre d'entrée

Publications (1)

Publication Number Publication Date
WO2021064793A1 true WO2021064793A1 (fr) 2021-04-08

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JP (1) JP6921470B1 (fr)
CN (1) CN112997014B (fr)
WO (1) WO2021064793A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT525716A1 (de) * 2021-12-03 2023-06-15 Avl List Gmbh Dynamischer prüfstand für prüflinge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58187752U (ja) * 1982-06-10 1983-12-13 トヨタ自動車株式会社 動力伝達系の試験装置
JPS639428U (fr) * 1986-07-02 1988-01-22
JPH07324972A (ja) * 1994-04-06 1995-12-12 Nippon Seiko Kk 転がり軸受の振動測定装置
JP2017187086A (ja) * 2016-04-04 2017-10-12 Ntn株式会社 制振軸受装置

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226400A (ja) * 2005-02-17 2006-08-31 Jtekt Corp シャフト装置
JP2014119080A (ja) * 2012-12-19 2014-06-30 Hitachi Ltd すべり軸受装置
JP6205803B2 (ja) * 2013-04-05 2017-10-04 日本精工株式会社 ラジアル転がり軸受用試験装置
JP6144216B2 (ja) * 2014-02-14 2017-06-07 大豊工業株式会社 すべり軸受
JP2018076780A (ja) * 2016-11-07 2018-05-17 日立ジョンソンコントロールズ空調株式会社 冷媒圧縮機
CN107560855B (zh) * 2017-10-12 2019-03-01 重庆大学 一种油膜轴承动静态性能试验装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58187752U (ja) * 1982-06-10 1983-12-13 トヨタ自動車株式会社 動力伝達系の試験装置
JPS639428U (fr) * 1986-07-02 1988-01-22
JPH07324972A (ja) * 1994-04-06 1995-12-12 Nippon Seiko Kk 転がり軸受の振動測定装置
JP2017187086A (ja) * 2016-04-04 2017-10-12 Ntn株式会社 制振軸受装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT525716A1 (de) * 2021-12-03 2023-06-15 Avl List Gmbh Dynamischer prüfstand für prüflinge

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Publication number Publication date
JP6921470B1 (ja) 2021-08-18
JPWO2021064793A1 (ja) 2021-11-04
CN112997014A (zh) 2021-06-18
CN112997014B (zh) 2023-07-21

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