CN104806733A - Bearing stress based torque detection structure and method - Google Patents

Bearing stress based torque detection structure and method Download PDF

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Publication number
CN104806733A
CN104806733A CN201510129002.5A CN201510129002A CN104806733A CN 104806733 A CN104806733 A CN 104806733A CN 201510129002 A CN201510129002 A CN 201510129002A CN 104806733 A CN104806733 A CN 104806733A
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CN
China
Prior art keywords
adjusting sleeve
eccentric adjusting
bearing
shaft
torque
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CN201510129002.5A
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CN104806733B (en
Inventor
陈辛波
杭鹏
王叶枫
王弦弦
王威
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Tongji University
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Tongji University
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0061—Force sensors associated with industrial machines or actuators
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/01—Monitoring wear or stress of gearing elements, e.g. for triggering maintenance
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0009—Force sensors associated with a bearing
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0028—Force sensors associated with force applying means
    • G01L5/0042—Force sensors associated with force applying means applying a torque
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/01—Monitoring wear or stress of gearing elements, e.g. for triggering maintenance
    • F16H2057/018—Detection of mechanical transmission failures

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

A torque real-time signal has very important significance on control of an electric automobile stabilization system and a driving system, but most of torques of a wheel edge driving motor are indirectly calculated by means of an energy conversion method through conversion and are low in accuracy. The invention provides a bearing stress based torque detection structure and method. a torque detection mechanism is reasonably arranged on a wheel edge speed reducer, the torque transferred by the speed reducer can be detected and output in an electric signal mode so as to achieve control on the driving system on the premise that the basic driving requirement is ensured. The bearing stress based torque detection structure and method have the advantages of being high in measurement accuracy, simple in structure, low in cost and the like.

Description

A kind of Torque test structure based on shaft strength and method
Technical field
The invention belongs to electric vehicle to drive/transmission system field, be specifically related to a kind of Torque test structure based on shaft strength and detecting method.
Background technique
Torque is the basic load form of various drive shaft in construction machinery, be closely connected with the element such as the ability to work of dynamic power machine, energy consumption, efficiency, running life and Safety performance, Torque test all has great importance by the Inspect and control of dynamic load, the Intensity Design of each component of transmission system, the diagnosis of fault, the selection etc. of prime mover capacity to drive bearing.
Current torque sensing approach mainly comprises balance force method, transformation of energy method and TRANSFER METHOD.Balance force method torque measuring device, also known as making dynamometer, is generally made up of whirler, balanced support and equilibrant measuring mechanism, according to the kinds of machine be arranged on balanced support, can be divided into Electric Dynamometer, hydrodynamometer etc.Balanced support has rolling bearing, double rolling-supporting type, fan-shaped supporting, hydraulic support and air pressure supporting etc.Balance force method directly surveys moment of torsion from body, there is not the moment of torsion problem of transmission from revolving part to static element, but it is only applicable to detecting the moment of torsion under at the uniform velocity working condition, can not measure dynamic torque.Conversion of Energy method is according to law of conservation of energy, the mechanical energy of rotating machinery is measured by measuring other forms of energy such as electric energy, heat energy parameter, and then obtain the method that the energetic coefficient (as electric energy coefficient) relevant with moment of torsion determines tested torque, measurement error is larger, and general only have more application in motor and the torque measurement of liquid machine.TRANSFER METHOD adopts non-contact measurement mostly, easy to use, and structure is simple, but the impact of non-contact measurement due to the factor such as temperature, algorithm and the collection difficulty of coherent signal, precision also needs further raising.
The Vehicle Stability System of electric vehicle and power-driven system all need to use dtc signal.The acquisition of electric vehicle dtc signal is normally according to electric moter voltage, electric current and tach signal, and indirectly estimate motor instantaneous torque according to transformation of energy method, precision is poor.Up to the present, little to the Torque test research of power-driven system.
Summary of the invention
The present invention proposes a kind of Torque test structure based on shaft strength.By reasonable Arrangement torque detection means on wheel reductor, ensureing under the prerequisite that basic transmission requires, the torque of wheel reductor input shaft can be detected in real time, and export as electronic signals, thus for the control of drive system, have that measuring accuracy is high, structure simple, low cost and other advantages.
The present invention also proposes a kind of torque sensing approach based on shaft strength.
Technological scheme of the present invention is:
The torque detection means should applied based on the torque sensing approach of shaft strength comprise reducer shell,
Intermediate gear shaft, first order driven gear, eccentric adjusting sleeve, force snesor, block bearing etc.
Jack shaft and second level driving gear become the form of gear shaft as Integral design, first order driven gear and intermediate gear shaft pass through key connecting, intermediate gear shaft right-hand member is supported in reducer shell by bearing inner race, and left end is supported in the endoporus of eccentric adjusting sleeve by bearing inner race.
Eccentric adjusting sleeve is supported in reducer shell by eccentric adjusting sleeve bearing inner race.In eccentric adjusting sleeve, axially bored line does not overlap with its outer coil axis, and the radial force direction that both are subject at countershaft-gear exists eccentric distance e, and this direction both can radially force direction, also can circumferentially force direction, and this is the key that the present invention can realize Torque test.There is stud at force snesor two ends, can be screwed into respectively in eccentric adjusting sleeve and the corresponding tapped hole of reducer shell.Force snesor can bear pulling force and pressure simultaneously, when it is subject to the effect of power, will has voltage signal and export.During retarder work, eccentric adjusting sleeve can be subject to from the power of intermediate gear shaft left end bearing, eccentric adjusting sleeve bearing and force snesor, and make it remain state of rest, therefore jack shaft rotates around himself axis all the time, and do not have other to move, thus ensure the normal transmission of gear.
Special way of the present invention is the outer ring of intermediate gear shaft left end bearing and is supported on reducer shell unlike other bearing, but is supported in the endoporus of eccentric adjusting sleeve, and interior axially bored line is , this axis is similarly the axis of intermediate gear shaft left end bearing.Eccentric adjusting sleeve is by eccentric adjusting sleeve bearings on reducer shell, and eccentric adjusting sleeve outer shaft axis is , this axis is similarly the axis of eccentric adjusting sleeve bearing.It can thus be appreciated that the axis of intermediate gear shaft left bearing does not overlap with the axis of eccentric adjusting sleeve bearing, there is throw of eccentric in the radial force direction that both are subject at gear .
Stressed and the equalising torque relation according to intermediate gear shaft, can obtain the stressed of intermediate gear shaft left end bearing place:
In formula ---the power parallel with gear peripheral force that intermediate gear shaft left bearing is subject to
---the power radial parallel with gear that intermediate gear shaft left end shaft affords
---gear compound graduation circle radius
---the peripheral force that gear is subject to
---the radial force that gear is subject to
---the axial force that gear is subject to
---intermediate gear shaft left and right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
In the present invention, the axial force that intermediate gear shaft is subject to all is born by intermediate gear shaft right-hand member bearing, and intermediate gear shaft left end bearing does not bear axial force.The active force that intermediate gear shaft left end shaft affords from intermediate gear shaft will be balanced by eccentric adjusting sleeve, can obtain the stressing conditions of eccentric adjusting sleeve thus.
According to the relation of active force and reaction force, the power that can obtain the intermediate gear shaft left bearing that eccentric adjusting sleeve is subject to is with , its respectively with , equal and opposite in direction, direction is contrary, with direction must pass through a little .Eccentric adjusting sleeve is supported in reducer shell by eccentric adjusting sleeve bearing inner race, therefore the power from eccentric adjusting sleeve bearing that eccentric adjusting sleeve is subject to must be passed through a little , be also decomposed into simultaneously with .
Force snesor two ends are arranged in the tapped hole of eccentric adjusting sleeve and reducer shell respectively, and the axis of force snesor remains parallel with Y direction (i.e. gear radial force direction), therefore the direction that force snesor acts on eccentric adjusting sleeve power is parallel with Y-axis all the time.
During wheel reductor work, eccentric adjusting sleeve remains static all the time, according to the stress balance condition (ignoring gravity effect) of eccentric adjusting sleeve, can obtain:
In formula 5 ---force snesor axis arrives the distance of line
---intermediate gear shaft left bearing and eccentric adjusting sleeve bearing act on the static friction torque of eccentric adjusting sleeve.
Bearing static friction torque maximum value is:
In formula ---deep groove ball bearing friction factor,
---bearing radial load, wherein
---the inner radii of intermediate gear shaft left end bearing
---the inner radii of eccentric adjusting sleeve bearing
Due to bearing maximum friction moment be far smaller than , therefore can ignore in calculating derivation.Therefore ignore in the present invention.
Thus can obtain:
---the input gear axle number of teeth
---the first order driven gear number of teeth
---first order driven gear reference radius
---intermediate gear shaft reference radius
Can obtain after conversion:
From formula 10, scaling factor only relevant with wheel reductor setting type, throw of eccentric and gear parameter, after wheel reductor design is determined, scaling factor for definite value.I.e. wheel reductor input torque the power be subject to force snesor between be linear ratio relation, therefore can be converted by the signal of force snesor when wheel reductor works and obtain the real-time torque of wheel reductor.
The invention provides a kind of torque sensing approach based on shaft strength, this torque sensing approach is all applicable for most of retarder, be specifically related to core type retarder and expansion retarder, single reduction gear and multi-stage speed reducer, Spur Gear Driving retarder, Helical gear Transmission retarder and bevel gear drive retarder etc.Only this need be overlapped torque detection means is arranged on the block bearing of transmission shaft one end, just can detect in real time reducer input shaft torque.The present invention is described this torque sensing approach based on shaft strength for gear reducer, is applicable to the transmission system of other types too, by improving this torque sensing approach of mechanism also within protection scope of the present invention.
Compared with prior art, superiority of the present invention is:
1. should be applicable to the Torque test of most of retarder based on the torque sensing approach of shaft strength, structure is simple, and convenient test, has good versatility;
2., under the prerequisite ensureing the normal transmission of retarder, can realize the real-time detection to retarder torque, measuring accuracy is high;
3. should be applied to wheel reductor Torque test based on the torque sensing approach of shaft strength to be conducive to improving electric vehicle control stability and drive-train efficiency.
Accompanying drawing explanation
Accompanying drawing 1 has the wheel reductor general assembly sketch of torque real-time detection function;
Accompanying drawing 2 torque detection means assembling partial view;
Accompanying drawing 3 torque detection means test lead left view;
Accompanying drawing 4 eccentric adjusting sleeve sectional view;
Accompanying drawing 5 wheel reductor intermediate gear shaft force analysis sketch;
Accompanying drawing 6 eccentric adjusting sleeve force analysis sketch.
Attached number in the figure illustrates:
1---reducer shell; 2---input gear axle;
3---first order driven gear; 4---intermediate gear shaft;
5---second level driven gear; 6---output shaft;
7---force snesor; 8---eccentric adjusting sleeve;
9---bearing; 10---eccentric adjusting sleeve bearing.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
The present invention is described this torque sensing approach based on shaft strength for two-stage expansion wheel reductor.Based on a Torque test structure for shaft strength, mainly comprise the parts such as reducer shell 1, input gear axle 2, first order driven gear 3, intermediate gear shaft 4, second level driven gear 5, output shaft 6, force snesor 7, eccentric adjusting sleeve 8, bearing 9, eccentric adjusting sleeve bearing 10.
As shown in Figure 1, Figure 3, input gear axle 2 two ends are supported in reducer shell 1 by bearing inner race.First order driven gear 3 is connected by key with intermediate gear shaft 4, and intermediate gear shaft 4 right-hand member is supported in reducer shell 1 by bearing inner race, and intermediate gear shaft 4 left end is supported in the endoporus of eccentric adjusting sleeve 8 by bearing 9 inner ring.Eccentric adjusting sleeve 8 is supported in reducer shell 1 by eccentric adjusting sleeve bearing 10 inner ring.There is stud at force snesor 7 two ends, can be screwed into respectively in eccentric adjusting sleeve 8 and the corresponding tapped hole of reducer shell 1.Second level driven gear 5 is connected by key with output shaft 6, and output shaft 6 two ends are supported in reducer shell 1 by bearing inner race.
Again as shown in Figure 2, Figure 4 shows, in eccentric adjusting sleeve 8, axially bored line does not overlap with its outer coil axis, and the radial force direction that both are subject at countershaft-gear exists eccentric distance e, and this direction both can radially force direction, also can circumferentially force direction, this is the key that the present invention can realize Torque test.There is stud at force snesor 7 two ends, can be screwed into respectively in eccentric adjusting sleeve and the corresponding tapped hole of reducer shell.Force snesor 7 can bear pulling force and pressure simultaneously, when it is subject to the effect of power, will has voltage signal and export.During retarder work, eccentric adjusting sleeve 8 can be subject to the power from intermediate gear shaft 4 left end bearing, eccentric adjusting sleeve bearing 10 and force snesor 7, and make it remain state of rest, therefore jack shaft rotates around himself axis all the time, and do not have other to move, thus ensure the normal transmission of gear.
As shown in Figure 6, when wheel reductor normally works, eccentric adjusting sleeve 8 will be subject to the reaction force of bearing 9, and the torque that the component of its X-direction produces will make eccentric adjusting sleeve 8 have around the outer coil axis of eccentric adjusting sleeve the trend of rotating, the torque of the power generation that force snesor 7 acts on eccentric adjusting sleeve 8 will balance mutually with former torque, make eccentric adjusting sleeve be in state of equilibrium.When wheel reductor normally works, be linear ratio relation between the power that force snesor 7 is surveyed and the torque of wheel reductor input gear axle 2, therefore when wheel reductor works, can be converted by the signal of force snesor 7 and obtain the real-time torque of wheel reductor.
Special way of the present invention is the outer ring of intermediate gear shaft left end bearing and is supported on reducer shell unlike other bearing, but is supported in the endoporus of eccentric adjusting sleeve, and interior axially bored line is , as shown in Figure 2 and Figure 4, this axis is similarly the axis of intermediate gear shaft left end bearing.Eccentric adjusting sleeve is by eccentric adjusting sleeve bearings on reducer shell, and eccentric adjusting sleeve outer shaft axis is , this axis is similarly the axis of eccentric adjusting sleeve bearing.It can thus be appreciated that the axis of intermediate gear shaft left bearing does not overlap with the axis of eccentric adjusting sleeve bearing, there is throw of eccentric in the radial force direction that both are subject at gear .
As shown in Figure 5.Stressed and the equalising torque relation according to intermediate gear shaft, can obtain the stressed of intermediate gear shaft left end bearing place:
In formula ---the power parallel with gear peripheral force that intermediate gear shaft left bearing is subject to
---the power radial parallel with gear that intermediate gear shaft left end shaft affords
---gear compound graduation circle radius
---the peripheral force that gear is subject to
---the radial force that gear is subject to
---the axial force that gear is subject to
---intermediate gear shaft left and right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
In the present invention, the axial force that intermediate gear shaft is subject to all is born by intermediate gear shaft right-hand member bearing, and intermediate gear shaft left end bearing does not bear axial force.The active force that intermediate gear shaft left end shaft affords from intermediate gear shaft will be balanced by eccentric adjusting sleeve, can obtain the stressing conditions of eccentric adjusting sleeve thus, as shown in Figure 6.
According to the relation of active force and reaction force, the power that can obtain the intermediate gear shaft left bearing that eccentric adjusting sleeve is subject to is with ( do not draw in figure 6), its respectively with , equal and opposite in direction, direction is contrary, with direction must pass through a little .Eccentric adjusting sleeve is supported in reducer shell by eccentric adjusting sleeve bearing inner race, therefore the power from eccentric adjusting sleeve bearing that eccentric adjusting sleeve is subject to must be passed through a little , be also decomposed into simultaneously with ( do not draw in figure 6).
Force snesor two ends are arranged in the tapped hole of eccentric adjusting sleeve and reducer shell respectively, and the axis of force snesor remains parallel with Y direction (i.e. gear radial force direction), therefore the direction that force snesor acts on eccentric adjusting sleeve power is parallel with Y-axis all the time.
During wheel reductor work, eccentric adjusting sleeve remains static all the time, according to the stress balance condition (ignoring gravity effect) of eccentric adjusting sleeve, can obtain:
In formula 5 ---force snesor axis arrives the distance of line
---intermediate gear shaft left bearing and eccentric adjusting sleeve bearing act on the static friction torque of eccentric adjusting sleeve.
Bearing static friction torque maximum value is:
In formula ---deep groove ball bearing friction factor,
---bearing radial load, wherein
---the inner radii of intermediate gear shaft left end bearing
---the inner radii of eccentric adjusting sleeve bearing
Due to bearing maximum friction moment be far smaller than , therefore can ignore in calculating derivation.Thus can obtain:
---the input gear axle number of teeth
---the first order driven gear number of teeth
---first order driven gear reference radius
---intermediate gear shaft reference radius
Can obtain after conversion:
From formula 10, scaling factor only relevant with wheel reductor setting type, throw of eccentric and gear parameter, after wheel reductor design is determined, scaling factor for definite value.I.e. wheel reductor input torque the power be subject to force snesor between be linear ratio relation, therefore can be converted by the signal of force snesor when wheel reductor works and obtain the real-time torque of wheel reductor.
The invention provides a kind of torque sensing approach based on shaft strength, this torque sensing approach is all applicable for most of retarder, be specifically related to core type retarder and expansion retarder, single reduction gear and multi-stage speed reducer, Spur Gear Driving retarder, Helical gear Transmission retarder and bevel gear drive retarder etc.Only this need be overlapped torque detection means is arranged on the block bearing of transmission shaft one end, just can detect in real time reducer input shaft torque.The present invention is described this torque sensing approach based on shaft strength for gear reducer, is applicable to the transmission system of other types too, by improving this torque sensing approach of mechanism also within protection scope of the present invention.

Claims (5)

1. based on a Torque test structure for shaft strength, it is characterized in that: comprise reducer shell, intermediate gear shaft, first order driven gear, eccentric adjusting sleeve, force snesor, block bearing; Jack shaft and second level driving gear become the form of gear shaft as Integral design, first order driven gear and intermediate gear shaft pass through key connecting, intermediate gear shaft right-hand member is supported in reducer shell by bearing inner race, and left end is supported in the endoporus of eccentric adjusting sleeve by bearing inner race.
2. a kind of Torque test structure based on shaft strength according to claim 1, it is characterized in that: intermediate gear shaft right-hand member is supported in reducer shell by bearing inner race, left end is supported in the endoporus of eccentric adjusting sleeve by bearing inner race; Eccentric adjusting sleeve is supported in retarder left shell by eccentric adjusting sleeve bearing inner race; In eccentric adjusting sleeve, axially bored line does not overlap with its outer coil axis, and the radial force direction that both are subject at countershaft-gear exists throw of eccentric.
3. a kind of Torque test structure based on shaft strength according to claim 2, is characterized in that: described radial force direction both can radially force direction, also can circumferentially force direction.
4. a kind of Torque test structure based on shaft strength according to claim 1, is characterized in that: there is stud at force snesor two ends, can be screwed into respectively in eccentric adjusting sleeve and the corresponding tapped hole of reducer shell.
5. the torque sensing approach based on shaft strength as described in arbitrary Claims 1-4, when retarder normally works, eccentric adjusting sleeve will be subject to the effect of intermediate gear shaft left end bearing, force snesor and eccentric adjusting sleeve bearing, thus remain static all the time, ensure the normal transmission of retarder; Be linear ratio relation between the power that force snesor is subject to and reducer input shaft torque, the power that force snesor is subject to exports as electronic signals, can obtain the real-time torque of retarder after converting; Be specially:
Wherein
---eccentric adjusting sleeve throw of eccentric
---the input gear axle number of teeth
---the first order driven gear number of teeth
---first order driven gear reference radius
---intermediate gear shaft reference radius
---intermediate gear shaft left and right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
---first order driven gear facewidth center is to intermediate gear shaft right bearing widthwise central distance
---force snesor axis arrives the distance of line
Scaling factor only relevant with wheel reductor setting type, throw of eccentric and gear parameter, after wheel reductor design is determined, scaling factor for definite value.
CN201510129002.5A 2015-03-20 2015-03-20 A kind of Torque test structures and methods based on shaft strength Active CN104806733B (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109236953A (en) * 2018-11-01 2019-01-18 上海理工大学 The high durable lightweight hub reduction gear of distributed-driving electric automobile
CN109598044A (en) * 2018-11-22 2019-04-09 成都飞机工业（集团）有限责任公司 A kind of engineering calculating method of gear type fax front steer systems precision
CN114526911A (en) * 2022-02-28 2022-05-24 河南科技大学 Testing machine for testing bearing capacity of RV reducer main shaft

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SU486230A1 (en) * 1974-03-18 1975-09-30 Предприятие П/Я А-1469 Device for measuring the torque on the shaft
SU1108403A1 (en) * 1982-02-15 1984-08-15 Киевский Ордена Ленина Политехнический Институт Им.50-Летия Великой Октябрьской Социалистической Революции Torque generator
US20040060369A1 (en) * 2002-09-30 2004-04-01 Keming Liu Transducer
CN1798962A (en) * 2003-06-04 2006-07-05 盖茨公司 Apparatus and method of belt dynamic tension measurement
US7418862B2 (en) * 2005-12-09 2008-09-02 Wisconsin Alumni Research Foundation Electromechanical force-magnitude, force-angle sensor
CN101305271A (en) * 2005-11-09 2008-11-12 S.N.R.鲁尔门斯公司 Deformation-sensor bearing comprising at least three strain gauges
CN201201674Y (en) * 2008-04-01 2009-03-04 铨阳能源科技股份有限公司 Torque force detector of electric bicycle
CN101865275A (en) * 2010-05-28 2010-10-20 上海应用技术学院 Torque sensor combined with reducer

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Publication number Priority date Publication date Assignee Title
SU486230A1 (en) * 1974-03-18 1975-09-30 Предприятие П/Я А-1469 Device for measuring the torque on the shaft
SU1108403A1 (en) * 1982-02-15 1984-08-15 Киевский Ордена Ленина Политехнический Институт Им.50-Летия Великой Октябрьской Социалистической Революции Torque generator
US20040060369A1 (en) * 2002-09-30 2004-04-01 Keming Liu Transducer
CN1685206A (en) * 2002-09-30 2005-10-19 盖茨公司 Transducer for measuring a shaft dynamic behavior
CN1798962A (en) * 2003-06-04 2006-07-05 盖茨公司 Apparatus and method of belt dynamic tension measurement
CN101305271A (en) * 2005-11-09 2008-11-12 S.N.R.鲁尔门斯公司 Deformation-sensor bearing comprising at least three strain gauges
US7418862B2 (en) * 2005-12-09 2008-09-02 Wisconsin Alumni Research Foundation Electromechanical force-magnitude, force-angle sensor
CN201201674Y (en) * 2008-04-01 2009-03-04 铨阳能源科技股份有限公司 Torque force detector of electric bicycle
CN101865275A (en) * 2010-05-28 2010-10-20 上海应用技术学院 Torque sensor combined with reducer

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109236953A (en) * 2018-11-01 2019-01-18 上海理工大学 The high durable lightweight hub reduction gear of distributed-driving electric automobile
CN109598044A (en) * 2018-11-22 2019-04-09 成都飞机工业（集团）有限责任公司 A kind of engineering calculating method of gear type fax front steer systems precision
CN109598044B (en) * 2018-11-22 2022-05-10 成都飞机工业（集团）有限责任公司 Engineering calculation method for gear type telex front wheel control system precision
CN114526911A (en) * 2022-02-28 2022-05-24 河南科技大学 Testing machine for testing bearing capacity of RV reducer main shaft

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