WO2000037915A1 - Procede permettant de tester des joints - Google Patents

Procede permettant de tester des joints Download PDF

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Publication number
WO2000037915A1
WO2000037915A1 PCT/AU1999/001122 AU9901122W WO0037915A1 WO 2000037915 A1 WO2000037915 A1 WO 2000037915A1 AU 9901122 W AU9901122 W AU 9901122W WO 0037915 A1 WO0037915 A1 WO 0037915A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
shaft
torsion bar
machine
joint
Prior art date
Application number
PCT/AU1999/001122
Other languages
English (en)
Inventor
Andrew William Hassett
Original Assignee
Bishop Manufacturing Technology Limited
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 claimed from AUPP7830A external-priority patent/AUPP783098A0/en
Priority claimed from AUPQ1867A external-priority patent/AUPQ186799A0/en
Application filed by Bishop Manufacturing Technology Limited filed Critical Bishop Manufacturing Technology Limited
Priority to AU22677/00A priority Critical patent/AU2267700A/en
Publication of WO2000037915A1 publication Critical patent/WO2000037915A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/08—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by type of steering valve used
    • B62D5/083—Rotary valves

Definitions

  • This invention relates to motor vehicle power steering gears, and in particular to a method of testing the strength of the joint between the torsion bar and input-shaft of a balanced hydraulic power steering valve or an assembled torque-sensing rotor.
  • Known hydraulic power steering rotary valves typically employ an input-shaft which extends upwardly from the steering gear assembly and is connected by a flexible coupling to the steering wheel shaft.
  • the extended end of the input- shaft is usually externally splined.
  • the steering gear assembly is provided with a valve housing containing an input- shaft and a sleeve member supported thereon.
  • some manufacturers support the sleeve member on the input-shaft via needle roller bearings, these needle roller bearings serving to maintain a small radial clearance between the outside diameter of the input shaft and inside a diameter of the sleeve.
  • the vast majority of manufacturers journal the sleeve member directly on the outside diameter of the input-shaft.
  • both these types of support will be referred to as "joumalling”.
  • the input-shaft extends through the sleeve and is journalled with respect to the steering gear driven member, which for a rack and pinion steering gear, is the pinion.
  • the driven member is normally the worm portion of a recirculating ball nut assembly.
  • the sleeve is usually arranged to be driven in a slack-free manner by a drive pin extending radially from the pinion although, in other less common hydraulic valves, this slack-free drive is facilitated by the sleeve and pinion being manufactured as an integral arrangement.
  • the downwardly-extending end of the input-shaft is splined in a loose-fitting manner to the pinion so allowing "limited relative rotation" between the input-shaft and the pinion, and hence also between the input-shaft and the sleeve.
  • the relative rotation must be limited to allow manual operation of the steering gear if the hydraulic power assistance fails.
  • Both the input-shaft and the sleeve member have respectively outwardly and inwardly facing longitudinal chambers formed on their interfacing surfaces which constitute an open centre four way valve operable on relative angular rotation of these components.
  • the sleeve operates within the valve housing and is provided with several circumferential grooves and seals which allow oil under pressure to be directed to and from an external hydraulic pump and to and from left and right assist cylinders in the manner well known in the art.
  • the input-shaft and the sleeve are normally biased towards a neutral position by a torsion bar secured at its lower end to the pinion.
  • the aforementioned slack-free drive of the sleeve therefore effectively means that the sleeve and torsion bar are rotationally connected via the pinion, the driven member in this case.
  • the torsion bar is secured to the input-shaft at the upper end of the torsion bar, from the pinion, henceforth referred to as the "fixing end" of the torsion bar.
  • the theoretically ideal neutral position of the input- shaft and sleeve components can be defined as the position about which an equal angular rotation or an equal input torque applied to the input-shaft in either direction, with respect to the sleeve, will result in equal magnitudes of differential pressure of hydraulic fluid being supplied to the left and right assist cylinders during valve operation.
  • the neutral position is typically determined by adjustment of the angular disposition of the input-shaft with respect to the torsion bar whilst angular rotation of the input shaft with respect to the sleeve, or alternatively the input torque applied to the input-shaft (which is temporarily locked to the torsion bar), is measured against the valve inlet pressure.
  • the operation of determining and fixing the neutral position is referred to as a "balancing" operation.
  • the balancing operation is performed in a "balancing machine".
  • balancing machines take many different formats and may be either a conventional hydraulic balancing machine or a pneumatic balancing machine as described in US Pat. No. 5,727,443 (Baxter et. al.).
  • the neutral position is fixed by joining the fixing end of the torsion bar and the input- shaft, the resulting joint will henceforth be referred to as the "torsion bar to input-shaft joint".
  • the fixing end of the torsion bar is typically cylindrical and extends through an axial extending bore in the input-shaft, the torsion bar outer surface and input-shaft bore having "clearance” to allow relative rotation during the balancing operation.
  • a "sealing member” such as an o-ring is used to prevent hydraulic fluid from leaking through the clearance.
  • Various methods can be used to create the torsion bar to input-shaft joint. The most common method is to join the fixing end of the torsion bar and input-shaft by a pin pressed through a diametrically disposed hole drilled and reamed through both components during the balancing operation.
  • An alternative method of creating the torsion bar to input-shaft joint is the torsion bar having a pre-formed axially extending bore into which one or more diameteral members, such as a ball, are press fitted thereby expanding the outer surface of the fixing end of the torsion bar and forming an "interface" with the input-shaft bore.
  • the input-shaft bore surface or the torsion bar fixing end outer surface forming the interface are commonly smooth but may include a keying formation such as a spline on at least a portion of one or both surfaces.
  • the sealing member may or may not be included.
  • This joining method will henceforth be referred to as the "ball press fit" method.
  • Such a method is described in US Patent No. 5,431 ,379 (Takagi) and in International Patent Application No. PCT/AU98/00697 (Bishop Steering Pty Limited).
  • An alternative to hydraulic power steering is electric power steering wherein assistance is facilitated by an electric motor.
  • the input-shaft forms part of a "torque-sensing rotor" instead of a hydraulic valve.
  • the torque-sensing rotor differs from a hydraulic valve in that the sleeve and the hydraulic chambers are replaced by a device that measures the relative displacement between the input-shaft and the driven member.
  • the integrity of the torsion bar to input-shaft joint is critical to the safe operation of the motor vehicle.
  • the joint In service, the joint is subjected to repeated torsional cycling and random shock and vibration loading.
  • the joint must have adequate torsional and axial strength to perform satisfactorily. If the joint is not strong enough then it could fail during operation, which would cause the driver to lose control of the vehicle. It is desirable to test the joint strength of every valve produced, in particular if the joint comprises the ball press fit or bonding method, because weak joints can be produced by these methods if manufacturing tolerances or parameters vary. However, it is not possible to apply a large enough torque to the joint to test its torsional strength because of the limited relative rotation possible between the input-shaft and the pinion.
  • the essence of the present invention is the recognition of the relationship between the torsional and axial strength of the torsion bar to input-shaft joint, since both relate to the shear strength of the interface between the input-shaft bore and the outer surface of the fixing end of the torsion bar.
  • the torsional joint strength (measured as the breakaway torque) is approximately equal to the axial joint strength (measured as the breakaway force) multiplied by the radius of the input-shaft bore. This means that the torsional joint strength, which cannot be measured directly for reasons described above, can be indirectly measured by application of an axial force.
  • the present invention consists in a method of testing the integrity of a joint between an input-shaft and a torsion bar of a power steering input device, wherein the torsion bar has a fixing end extending through an axially disposed bore in the input-shaft, the outer surface of the fixing end of the torsion bar and the bore of the input-shaft having clearance to allow relative rotation therebetween before joining, characterised in that the method comprises the steps of: a) applying a predetermined axial force to the joint; and b) measuring the relative axial displacement between the input-shaft and the torsion bar as a result of the predetermined axial force being applied; and wherein, when the relative axial displacement is greater than a predetermined value, then the joint is deemed to have failed the test.
  • the joint between the input-shaft and the fixing end of the torsion bar comprises a pre-formed axially extending bore in the fixing end of the torsion bar into which one or more diametral members are press fitted thereby expanding the outer surface of the fixing end of the torsion bar and forming an interface with the input- shaft bore.
  • the surface of the input-shaft bore and the outer surface of the torsion bar fixing end forming the interface are both smooth.
  • the surface of the input-shaft bore and the outer surface of the torsion bar fixing end forming the interface include a keying formation, on at least a portion of one or both surfaces.
  • the joint between the input-shaft and the fixing end of the torsion bar comprises adhesive bonding, soldering, brazing, welding or a mechanical keying agent.
  • the power steering may be hydraulically assisted and the input device comprises a balanced hydraulic rotary valve having a sleeve joumalled to the input-shaft.
  • the power steering assistance may be facilitated by an electric motor and the input-shaft forms part of an assembled torque- sensing rotor.
  • the predetermined force is applied in a direction such that, if axial motion occurred, it would result in relative axial displacement of the input-shaft towards a driven member connected to the torsion bar.
  • the predetermined force may be applied to the input-shaft exterior whilst the driven member is supported.
  • the predetermined force is applied to the torsion bar via the driven member whilst the input shaft is supported.
  • the predetermined force may be applied to the fixing end of the torsion bar whilst the input shaft is supported.
  • the predetermined force is applied in a direction such that, if axial motion occurred, it would result in relative axial displacement of the input-shaft away from the driven member.
  • the predetermined force may be applied to the input shaft exterior whilst the driven member is held.
  • the predetermined force may be applied to the torsion bar via the driven member whilst the input-shaft is held.
  • the predetermined force may be applied to the fixing end of the torsion bar whilst the input shaft is supported.
  • the relative axial displacement between the input-shaft and the torsion bar is determined by measuring the axial distance between a datum point on the driven member and a datum point on the input-shaft before and after applying the predetermined force.
  • the present invention consists in a method of testing the integrity of a joint between an input-shaft and a torsion bar of a hydraulic valve for a power steering gear, the input-shaft having a first axial bore and the torsion bar having a second axial bore in a fixing end thereof, the surface of the first axial bore and the outer surface of the fixing end of the torsion bar forming an interface therebetween, the joint comprising a diametral member press fitted within the second axial bore thereby expanding the outer surface of the fixing end of the torsion bar and engaging with the surface of the first axial bore, characterised in that the method comprises the steps of: a) applying a predetermined axial force to the input-shaft whilst the torsion bar is supported; and b) measuring the relative axial displacement between the input-shaft and the torsion bar as a result of the predetermined axial force being applied; and wherein, when the relative axial displacement is greater than a predetermined value, then the joint is
  • the present invention consists in a machine for testing the integrity of a joint between an input-shaft and a torsion bar of a power steering input device, wherein the torsion bar has a fixing end extending through an axially disposed bore in the input-shaft, the outer surface of the fixing end of the torsion bar and the bore of the input-shaft having clearance to allow relative rotation therebetween before joining, characterised in that the machine comprises: a) means for applying a predetermined axial force to the joint; and b) means for measuring the relative axial displacement between the input-shaft and the torsion bar as a result of the predetermined axial force being applied.
  • the machine forms part of a balancing machine.
  • the machine comprises means to determine relative axial displacement between the input-shaft and the torsion bar by measuring the axial distance between a datum point on a driven member connected to the torsion bar, and a datum point on the input-shaft before and after applying the predetermined force.
  • the machine comprises a means for holding the power steering input device by the driven member, and means for urging the driven member towards the input-shaft whilst the end of the input-shaft is supported by a means for supporting. The driven member is urged until the predetermined axial force is reached.
  • the means for holding the driven member is fixed to a carriage, which can slide on linear bearings.
  • the means for urging the driven member is a motor, which moves the carriage.
  • the means for supporting the input-shaft includes a compression spring.
  • the means for supporting the input-shaft includes a force transducer.
  • the machine comprises a precision linear measuring device.
  • the machine consists of a means of holding the power steering input device by the driven member, and comprises means for applying a predetermined force to the end of the input-shaft.
  • the means for applying the predetermined force comprises a ram in contact with the end of the input shaft, and the ram is also connected to a piston, which is urged by a pressurised fluid.
  • a precision linear measuring device indicates the position of the ram.
  • Fig 1a is a sectional view of a typical hydraulic power steering valve
  • Fig 1 b is a sectional view of the valve of Fig 1a through line I-I;
  • Figs 2a and 2b depict a first embodiment of the method of testing the joint between the input-shaft and torsion bar according to the present invention
  • Figs 3a, 3b and 3c depict a second embodiment of the method of testing the joint between the input-shaft and torsion bar according to the present invention
  • Fig 4 depicts a first embodiment of a machine to implement the method of testing according to the present invention
  • Fig 5 depicts a second embodiment of a machine to implement the method of testing according to the present invention.
  • Fig 6 is a sectional view of a torque sensing rotor of an electric power steering embodiment
  • Fig 1 is a sectional view of a typical hydraulic power steering valve.
  • Valve 1 comprises input-shaft 2 having sleeve 3 journalled thereon.
  • the manner in which input-shaft 2 and sleeve 3 operate to direct oil to and from a hydraulic pump and assist cylinders (not shown) is well known in the art and will not be further described here.
  • the lower end of input-shaft 2 is journalled on the lower end of torsion bar 4.
  • Torsion bar 4 axially protrudes from and is rigidly connected to pinion 5.
  • Torsion bar 4 and input-shaft 2 are joined by pressing ball 7 into pre-formed bore 8, in torsion bar 4, thereby expanding the outer surface of the fixing end of torsion bar 4 and forming an interface 9 with input-shaft bore 11.
  • Sealing member 10 may or may not be included.
  • There are alternative methods of creating the torsion bar to input- shaft joint such as a pin pressed through a diametrically disposed hole drilled and reamed through both components, or by bonding comprising adhesive bonding, soldering, brazing, welding or a mechanical keying agent.
  • input-shaft 2 Prior to the joining of input-shaft 2 and torsion bar 4, input-shaft 2 must be rotationally oriented with respect to sleeve 3 such that the valve is in the neutral position. Joining torsion bar 4 to input-shaft 2 permanently fixes the neutral position.
  • the operation of determining and fixing the neutral position is referred to as a balancing operation and is performed in a balancing machine.
  • Figs 2a and 2b depict a first embodiment of the method of testing the joint between input-shaft 2 and torsion bar 4 according to the present invention.
  • Predetermined force 14 is applied to valve 1 such that the force is transmitted through the torsion bar 4 to input-shaft 2 joint.
  • Predetermined force 14 is applied in an axial direction such that if axial motion occurred, would result in the relative axial displacement of input- shaft 2 towards pinion 5.
  • Axial gap 16 between the lower end of input-shaft 2 and pinion 5 ensures that the load is transmitted through the torsion bar 4 to input-shaft 2 joint.
  • Predetermined force 14 can be applied to the upper end 15 of input-shaft 2 whilst supporting pinion 5 as depicted in fig 2a.
  • predetermined force 14 can be applied to pinion 5 whilst supporting input-shaft 2 as depicted in fig 2b.
  • Relative axial displacement between input-shaft 2 and torsion bar 4, as result of predetermined force 14 being applied is measured and if this displacement is greater than a predetermined value then the joint between input-shaft 2 and torsion bar 4 is deemed to have inadequate strength and therefore fails the test.
  • the torsion bar 4 to input-shaft 2 joint must have a minimum torsional and axial strength to perform satisfactorily. It is desirable to test the joint strength of every valve produced, in particular if the joint comprises the ball press fit or bonding method, because weak joints can be produced by these methods if manufacturing tolerances or parameters vary. However, it is not possible to apply a large enough torque to the joint to test its torsional strength because of the limited relative rotation possible between input-shaft and the pinion. The present invention overcomes this problem because the axial strength and torsional strength of the joint are related. Therefore the predetermined force 14 is chosen such that if the joint passes the test it will have both adequate torsional and axial strength.
  • the relative axial displacement between input-shaft 2 and torsion bar 4 is typically determined by measuring the distance between a datum point on the input-shaft 2 and a datum point on the pinion 5, as indicated by example dimension 17, before and after applying predetermined force 14.
  • Figs 3a, 3b and 3c depict a second embodiment of the method of testing the joint between the input-shaft and torsion bar according to the present invention.
  • Predetermined force 14 is applied to valve 1 such that the force is transmitted through the torsion bar 4 to input-shaft 2 joint.
  • predetermined force 14 applied in an axial direction such that if axial motion occurred, would result in the relative axial displacement of input-shaft 2 away from pinion 5.
  • Relative axial displacement between input-shaft 2 and torsion bar 4 is measured and if this displacement is greater than a predetermined value then the joint between input-shaft 2 and torsion bar 4 is deemed to have inadequate strength and therefore fails the test.
  • input-shaft 2 includes a shoulder 18 that can be used to apply predetermined force 14 to input-shaft 2.
  • Fig 3a depicts predetermined force 14 applied by pulling pinion 5 whilst supporting input-shaft 2 at shoulder 18.
  • Fig 3b depicts predetermined force 14 applied by pushing the upper end 19 of torsion bar 4 whilst supporting input-shaft 2 at shoulder 18.
  • Fig 3c depicts predetermined force 14 applied by pulling input-shaft 2 whilst supporting the top face 20 of sleeve 3, which transmits the load to pinion 5 via sleeve drive pin 6.
  • Fig 4 depicts a first embodiment of a machine to implement the method of testing according to the present invention.
  • Valve 1 is supported by block 21 , which is attached to carriage 22.
  • Carriage 22 contains linear bearings 23 that slide on rails 24.
  • Motor 27 rotates screw 26, which moves carriage 22 up and down via nut 25 fixed to carriage 22.
  • Precision linear measuring device 28 measures the vertical position of carriage 22.
  • Cap 29 can slide up and down on spigot 30, which is attached to force transducer 31. Cap 29 contacts the upper end 15 of input-shaft 2.
  • valve 1 before applying predetermined force 14, is measured by moving carriage 22 up and reading precision linear measuring device 28 at the exact instant that flag 33, attached to cap 29, is pushed upwards by valve 1 and triggers proximity switch 32.
  • Predetermined force 14 is then applied to upper end 15 of input- shaft 2 by slowly moving carriage 22 further upwards, which compresses spring 34, until force transducer 31 indicates that predetermined force 14 has been reached.
  • Carriage 22 then moves downward to release predetermined force 14 and until flag 33 resets proximity switch 32.
  • the length 17 of valve 1 after applying predetermined force 14 is measured by moving carriage 22 up again up and reading precision linear measuring device 28 at the exact instant that flag 33 triggers proximity switch 32.
  • the relative axial displacement between input-shaft 2 and torsion bar 4 is the change in length 17 from before and after applying predetermined force 14. If the change in length is greater than a predetermined value then the joint between input-shaft 2 and torsion bar 4 is deemed to have inadequate strength and therefore fails the test.
  • the apparatus depicted in Fig 4 can be included as part of a balancing machine.
  • Fig 5 depicts a second embodiment of a machine to implement the method of testing according to the present invention.
  • Valve 1 is supported by block 35.
  • Ram 36 moves up and down guided by bush 45 and contacts upper end 15 of input-shaft 2.
  • Precision linear measuring device 37 measures the vertical position of ram 36.
  • Piston 38 is contained in cylinder 40 and is connected to ram 36.
  • Ported valve 39 directs pressurised fluid, such as oil or air, to and from chambers 41 and 42 above and below piston 38 respectively, via supply lines 43 and 44.
  • Pressure gauge 46 indicates the pressure in chamber 41.
  • valve 1 before applying predetermined force 14, is measured by ported valve 39 admitting low-pressure fluid to chamber 41 , which moves ram 36 downward until it contacts upper end 15 of input-shaft 2. This low-pressure should only apply enough force for the ram 36 to positively contact upper end 15 of input- shaft 2, and the length 17 is then determined by reading precision linear measuring device 37 at this instant.
  • Predetermined force 14 is then applied to upper end 15 of input-shaft 2 by ported valve 39 admitting fluid to chamber 41 at a predetermined pressure. The predetermined pressure is calculated to give predetermined force 14 when acting over the area of piston 38. Predetermined force 14 is then released by ported valve 39 releasing fluid pressure from chamber 41.
  • valve 1 after applying predetermined force 14 is measured by ported valve 39 again admitting low-pressure fluid to chamber 41 , which moves ram 36 downward until it contacts upper end 15 of input-shaft 2, and the length 17 is then determined by reading precision linear measuring device 37 at this instant.
  • the relative axial displacement between input-shaft 2 and torsion bar 4 is the change in length 17 from before and after applying predetermined force 14. If the change in length is greater than a predetermined value then the joint between input-shaft 2 and torsion bar 4 is deemed to have inadequate strength and therefore fails the test.
  • the input-shaft 2 and torsion bar 4 forms part of a "torque-sensing rotor" 51 instead of a hydraulic valve.
  • the torque-sensing rotor differs from a hydraulic valve in that the sleeve and the hydraulic chambers are replaced by a device 50 that measures the relative rotational displacement between the input-shaft 2 and the pinion (driven member) 5.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Power Steering Mechanism (AREA)

Abstract

L'invention concerne un procédé permettant de tester l'intégrité d'un joint situé entre l'arbre d'entrée et l'extrémité de fixation de la barre de torsion d'un dispositif d'entrée de servodirection. Ce procédé consiste à appliquer une force axiale prédéterminée sur le joint, puis à mesurer le déplacement axial relatif entre l'arbre d'entrée et la barre de torsion résultant de l'application de la force prédéterminée. Si le déplacement axial relatif est supérieur à une valeur prédéterminée, on considère que le joint n'a pas passé le test.
PCT/AU1999/001122 1998-12-22 1999-12-21 Procede permettant de tester des joints WO2000037915A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU22677/00A AU2267700A (en) 1998-12-22 1999-12-21 Joint testing method

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AUPP7830 1998-12-22
AUPP7830A AUPP783098A0 (en) 1998-12-22 1998-12-22 Joint testing method
AUPQ1867 1999-07-28
AUPQ1867A AUPQ186799A0 (en) 1999-07-28 1999-07-28 Joint testing method

Publications (1)

Publication Number Publication Date
WO2000037915A1 true WO2000037915A1 (fr) 2000-06-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1999/001122 WO2000037915A1 (fr) 1998-12-22 1999-12-21 Procede permettant de tester des joints

Country Status (1)

Country Link
WO (1) WO2000037915A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1747965A2 (fr) * 2005-07-25 2007-01-31 Delphi Technologies, Inc. Ensemble de direction assistée pour véhicule automobile et son procédé de montage
CN104155193A (zh) * 2014-08-14 2014-11-19 浙江巨人控股有限公司 一种电梯主轴测试装置
CN104458449A (zh) * 2014-11-21 2015-03-25 太原轨道交通装备有限责任公司 一种橡胶关节扭转、偏转试验装置以及试验方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431379A (en) * 1993-05-25 1995-07-11 Trw Steering Systems Japan Co., Ltd. Method of interconnecting an input shaft and a torsion bar of steering mechanism and a torsion bar therefore
US5600895A (en) * 1994-09-22 1997-02-11 Mts Systems Corporation Extensometer
US5727443A (en) * 1994-11-28 1998-03-17 A.E. Bishop & Associates Pty Limited Method of balancing a hydraulic valve for a power steering gear

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431379A (en) * 1993-05-25 1995-07-11 Trw Steering Systems Japan Co., Ltd. Method of interconnecting an input shaft and a torsion bar of steering mechanism and a torsion bar therefore
US5600895A (en) * 1994-09-22 1997-02-11 Mts Systems Corporation Extensometer
US5727443A (en) * 1994-11-28 1998-03-17 A.E. Bishop & Associates Pty Limited Method of balancing a hydraulic valve for a power steering gear

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1747965A2 (fr) * 2005-07-25 2007-01-31 Delphi Technologies, Inc. Ensemble de direction assistée pour véhicule automobile et son procédé de montage
EP1747965A3 (fr) * 2005-07-25 2011-08-31 GM Global Technology Operations LLC Ensemble de direction assistée pour véhicule automobile et son procédé de montage
CN104155193A (zh) * 2014-08-14 2014-11-19 浙江巨人控股有限公司 一种电梯主轴测试装置
CN104458449A (zh) * 2014-11-21 2015-03-25 太原轨道交通装备有限责任公司 一种橡胶关节扭转、偏转试验装置以及试验方法

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