WO2019026655A1 - Cellule de charge et palier - Google Patents

Cellule de charge et palier Download PDF

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Publication number
WO2019026655A1
WO2019026655A1 PCT/JP2018/027407 JP2018027407W WO2019026655A1 WO 2019026655 A1 WO2019026655 A1 WO 2019026655A1 JP 2018027407 W JP2018027407 W JP 2018027407W WO 2019026655 A1 WO2019026655 A1 WO 2019026655A1
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WO
WIPO (PCT)
Prior art keywords
load cell
load
strain
axis
strain gauge
Prior art date
Application number
PCT/JP2018/027407
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English (en)
Japanese (ja)
Inventor
持丸　昌己
五十嵐　美照
Original Assignee
オイレス工業株式会社
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 オイレス工業株式会社 filed Critical オイレス工業株式会社
Publication of WO2019026655A1 publication Critical patent/WO2019026655A1/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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L1/00—Measuring force or stress, in general
    • G01L1/20—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress
    • G01L1/22—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress using resistance strain gauges
    • 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

Definitions

  • the present invention relates to a load cell, and more particularly to a load cell suitable for measuring the load of a vehicle applied to a suspension.
  • Patent Document 1 discloses a bearing capable of measuring a load applied to a suspension while supporting the load of a vehicle.
  • the bearing is connected to a rotating body, a top race and a bottom race relatively rotatably combined via the rotating body, a top cup connected to the top race and disposed on the vehicle body side, and a bottom race And a deformation sensor such as a strain gauge attached to the top race or the top cup.
  • the top race or the top cup functions as a straining body
  • the strain of the straining body is detected by a deformation sensor
  • the load in the thrust direction (the load of the vehicle) is calculated based on the magnitude of the detected strain. ing.
  • Patent Document 1 since the bearing described in Patent Document 1 is configured to support the load of the vehicle applied to the suspension, it is designed to have sufficient rigidity with respect to the load in the thrust direction. Therefore, when the top race or the top cup is used as a strain generating body, the strain of the strain generating body against the load in the thrust direction is small, so the detection sensitivity of the deformation sensor becomes low, and the load of the vehicle can be measured accurately. difficult.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a load cell capable of accurately measuring a load in a thrust direction and a bearing using the load cell.
  • two annular flat plates are arranged in the axial direction, and the annular flat plates are connected by a connecting member to constitute a strain generating body, and the connecting member is axially
  • the strain gauge was attached to the connecting member while being inclined with respect to the heart.
  • the load cell of the present invention Strain generating body, A strain gauge for detecting strain generated in the strain generating body;
  • the strain body is Two annular flat plates arranged in the axial direction, And a connecting member for connecting between the two annular flat plates, The connecting member is inclined with respect to the axial center, The strain gauge is attached to the connecting member.
  • the bearing of the present invention is A bearing that supports the load of a vehicle applied to a suspension, An upper case attached to the vehicle body side, A lower case attached to a spring side constituting the suspension and rotatably combined with the upper case; The above-mentioned load cell disposed between the upper case and the vehicle body.
  • the connecting member constituting the strain generating body is inclined with respect to the axial center, the connecting member is compressed and deformed against the load in the thrust direction applied in the direction of contracting between the two annular flat plates. In addition to this, bending deformation also occurs, and distortion is greater than in the case of only compression deformation. This increases the detection sensitivity of the strain gauge. Therefore, according to the present invention, the load in the thrust direction can be measured accurately.
  • FIG. 1A and FIG. 1B are a front view and a side view of a load cell 1 according to an embodiment of the present invention.
  • FIGS. 2A and 2B are a cross-sectional view taken along the line AA and a cross-sectional view taken along the line BB of the load cell 1 shown in FIG. 1A.
  • 3 (A) and 3 (B) are a cross-sectional view and a cross-sectional view of the load cell 1 shown in FIG. 1 (B), respectively.
  • FIG. 4A is a diagram for explaining the strain of the strain generating body 2 with respect to the load in the thrust direction
  • FIG. 4B is a diagram for explaining the strain of the strain generating body 2 with respect to the load in the radial direction.
  • FIG. 5 is a partial cross-sectional view of the damper assembly 5, the bearing 6, and the upper support 7 that constitute the vehicle suspension 4.
  • 6 (A), 6 (B) and 6 (C) are a front view, a rear view and a side view of the sliding bearing 6, and
  • FIG. 6 (D) is a sliding bearing shown in FIG. 6 (A).
  • 6 is a cross-sectional view taken along line E-E of FIG.
  • FIG. 1A and FIG. 1B are a front view and a side view of a load cell 1 according to the present embodiment.
  • 2 (A) and 2 (B) are a cross-sectional view taken along the line AA and a cross-sectional view taken along the line BB of the load cell 1 shown in FIG. 1 (A).
  • 3 (A) and 3 (B) are a cross-sectional view taken along the line CC and a cross-sectional view taken along the line DD of the load cell 1 shown in FIG. 1 (B).
  • the load cell 1 is for measuring the load applied in the thrust direction (axial center O direction), and a plurality of strains for detecting strain generated in the strain generating body 2 and the strain generating body 2 Gauge sets 3a to 3d (hereinafter, also simply referred to as strain gauge set 3).
  • the strain generating body 2 is formed of a thermoplastic resin such as polyacetal resin or polyamide resin, and is a connecting member for connecting between two annular flat plates 20a and 20b arranged in the axial center O direction and the two annular flat plates 20a and 20b. And 21.
  • the annular flat plates 20a and 20b are disposed parallel to each other with their centers aligned with the axis O.
  • the connecting member 21 has a plurality of arm portions 22 arranged at equal intervals on the circumference centering on the axial center O and in line symmetry with respect to the axial center O.
  • the arm portion 22 is inclined in a direction away from the axial center O as the sectional shape in the plane including the axial center O goes from the annular flat plate 20 a to the annular flat plate 20 b. Therefore, the two arm portions 22 arranged in line symmetry with respect to the axis O have a cross-sectional shape in a plane including the axis O inclined in line symmetry with respect to the axis O to form a V shape. There is no. As a result, in the strain-generating body 2, the cross-sectional shape in the plane including the axial center O becomes a Z shape that is line symmetrical with respect to the axial center O (see FIGS. 2A and 2B).
  • the strain gauge set 3 is arranged to be line symmetrical with respect to the axis O. Specifically, the strain gauge sets 3a and 3b are arranged to be axisymmetric with respect to the axis O, and the strain gauge sets 3c and 3d are arranged to be axisymmetrical with respect to the axis O.
  • the strain gauge set 3 is constituted by four strain gauges 30a to 30d constituting a Wheatstone bridge circuit.
  • the strain gauge 30a is attached to the outer wall surface (surface on the radially outer side) 221 of the end 220a of the arm 22 on the side of the annular flat plate 20a
  • the strain gauge 30b is on the side of the annular flat 20b of the arm 22.
  • the strain gauge 30c is attached to the inner wall surface (surface on the radially inward side) 222 of the end 220a of the arm 22 on the side of the annular flat plate 20a
  • the strain gauge 30d is on the side of the annular flat 20b of the arm 22. It is attached to the inner wall surface 222 of the end 220 b.
  • FIG. 4A is a diagram for explaining the strain of the strain generating body 2 with respect to the load in the thrust direction
  • FIG. 4B is a diagram for explaining the strain of the strain generating body 2 with respect to the load in the radial direction.
  • FIG. FIG. 4A and FIG. 4B correspond to a diagram in which a part of FIG. 2B is omitted.
  • the plurality of arm portions 22 constituting the connecting member 21 of the strain generating body 2 are at equal intervals on the circumference centered on the axis O and are line symmetrical with respect to the axis O It is arranged as. Further, the cross-sectional shape in the plane including the axis O is inclined in the direction away from the axis O as it goes from the annular flat plate 20 a to the annular flat plate 20 b. Therefore, as shown in FIG.
  • each arm portion 22 is distorted in the direction in which the outer wall surface 221 extends, and is distorted in the direction in which the inner wall surface 222 contracts. For this reason, distortion of the strain generating body 3 becomes larger than that in the case of only compression deformation, and the detection sensitivity of distortion which can be detected by the strain gauge set 3 becomes high.
  • strain gauge set 3 is arranged so as to be line symmetrical with respect to axis O. Therefore, the influence of radial load R is canceled by averaging the detection values of each strain gauge set 3. can do.
  • the strain detection sensitivity that can be detected by the strain gauge set 3 can be increased, and furthermore, by averaging the detection values of the strain gauge set 3 Since the influence of the radial load R included in the detection value can be offset, the thrust load T can be accurately measured by calculating the thrust load T based on the average value of the detection values of the strain gauge set 3 . Further, by changing the inclination of the plurality of arm portions 22 constituting the connecting member 21 with respect to the axial center O, it is possible to adjust the detection sensitivity of distortion which can be detected by the strain gauge set 3.
  • FIG. 5 is a partial cross-sectional view of the damper assembly 5, the slide bearing 6, and the upper support 7 that constitute the vehicle suspension 4. As shown in FIG.
  • the vehicle suspension 4 is used for suspension of a vehicle such as a car, and as shown, a damper assembly 5 including a shock absorber 50, an upper support 7 for mounting the damper assembly 5 on the vehicle body side, and a damper assembly And a sliding bearing 6 disposed between the upper support 7 and the upper support 7.
  • a damper assembly 5 including a shock absorber 50, an upper support 7 for mounting the damper assembly 5 on the vehicle body side, and a damper assembly And a sliding bearing 6 disposed between the upper support 7 and the upper support 7.
  • the damper assembly 5 includes a coil spring 51, a lower spring seat 52, a bump stopper 53, and a dust boot 54, in addition to the shock absorber 50.
  • the coil spring 51 is coaxially disposed with the shock absorber 50 so as to surround the shock absorber 50, and its upper end 510 is supported by an upper spring seat 55 provided on the slide bearing 6, and its lower end 511 is It is supported by a lower spring seat 52 provided on the shock absorber 50.
  • the bump stopper 53 is mounted on the piston rod 56 of the shock absorber 50 and prevents the shock absorber 50 from colliding with the body of the vehicle when the piston rod 56 is compressed.
  • the dust boot 54 is mounted so as to cover the piston rod 56 on which the bump stopper 53 is mounted, and prevents dust, muddy water and the like from adhering to the piston rod 56.
  • the slide bearing 6 is disposed between the damper assembly 5 and the upper support 7 and supports the load applied to the damper assembly 5 while allowing relative rotation between the coil spring 51 and the upper support 7.
  • the slide bearing 6 is equipped with the load cell 1 which concerns on this Embodiment.
  • the load cell 1 outputs signals from the plurality of strain gauge sets 3 according to the strain generated in the strain generating body 2 by the load supported by the slide bearing 6.
  • the signals output from the plurality of strain gauge sets 3 are input to the load measuring unit 8 mounted on the vehicle.
  • the load measuring unit 8 calculates an average value of detection values indicated by the signals output from the plurality of strain gauge sets 3 and measures a load applied to the damper assembly 5 based on the average value. Then, the vehicle weight is calculated based on the detected load.
  • the vehicle weight is calculated by summing the loads measured by the load cells 1. Further, for example, when the slide bearing 6 including the load cell 1 is mounted only on the suspension of the front wheel or the rear wheel, the vehicle weight is calculated by doubling the total of the loads detected by the load cells 1. Further, for example, in the case where the slide bearing 6 including the load cell 1 is mounted on only one suspension of four wheels, the vehicle weight is calculated by quadrupling the load detected by the load cell 1.
  • FIG. 6 (A), 6 (B) and 6 (C) are a front view, a rear view and a side view of the sliding bearing 6, and FIG. 6 (D) is a sliding bearing shown in FIG. 6 (A). 6 is a cross-sectional view taken along line E-E of FIG.
  • the slide bearing 6 has a receiving hole 60 for receiving the piston rod 56 on which the bump stopper 53 is mounted.
  • the slide bearing 6 is rotatably combined with the upper case 61 and the upper case 61, and is disposed in the lower case 62 forming an annular space 64 between the upper case 61 and the lower case 62.
  • An annular center plate 63 and a load cell 1 disposed between the upper case 61 and the upper support 7 are provided.
  • Upper case 61 is formed of thermoplastic resin having excellent sliding characteristics such as polyacetal resin impregnated with lubricating oil as needed, and is inserted to upper support 7 through load cell 1 with piston rod 56 inserted. It is attached.
  • Lower case 62 is formed of thermoplastic resin such as polyamide resin reinforced with glass fiber etc. if necessary, and upper end portion 510 of coil spring 51 in a state where piston rod 56 mounted with bump stopper 53 is inserted. It also functions as an upper spring seat 55 that supports the
  • the center plate 63 is an annular member formed of a material excellent in sliding characteristics, such as PTFE (polytetrafluoroethylene), a thermoplastic resin to which PTFE is added, a brass alloy, etc.
  • strain gauge sets 3a to 3d are used as the plurality of strain gauge sets 3 for detecting distortion generated in the strain generating body 2 is described as an example.
  • the present invention is not limited to this.
  • a plurality of strain gauge sets 3 may be arranged in line symmetry with respect to the axis O.
  • the strain gauge set 3 is constituted by the four strain gauges 30a to 30d constituting the Wheatstone bridge circuit, and the strain gauges 30a to 30d are formed by the outer wall surfaces of both end portions 220a and 220b of the arm portion 22. And 221 attached to the inner wall surface 222.
  • the strain gauge set 3 may be configured to include at least one strain gauge, and the mounting position thereof may be any connecting member 21 that bends in addition to compressive deformation with respect to the thrust load T. You may attach it.
  • the connecting members 21 for connecting the annular flat plates 20a and 20b are arranged at equal intervals on the circumference centering on the axial center O and in line symmetry to the axial center O. It is comprised by the several arm part 22 arrange
  • the connecting member may have a cross-sectional shape in a plane including the axial center O inclined in line symmetry with respect to the axial center O.
  • the connecting member may be a tubular member whose diameter increases from one of the annular flat plates 20a and 20b to the other.
  • the annular flat plates 20a and 20b have the same diameter, but the present invention is not limited to this.
  • the annular flat plate 20a is adjusted to the size of the upper support 7 to which the annular flat plate 20a is attached, and the annular flat plate 20b is annular
  • the sizes of the annular flat plates 20a and 20b may be made different from each other.
  • the slide bearing 6 is described as an example.
  • the bearing combined with the load cell 1 is not limited to the sliding bearing.
  • it may be a rolling bearing.
  • the load cell of the present invention can be used not only for bearings but also for various applications for measuring thrust loads.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)
  • Measurement Of Force In General (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne une cellule de charge permettant de mesurer avec précision une charge dans une direction de poussée ; et un palier utilisant la cellule de charge. Ladite cellule de charge (1) comprend : un corps déformable (2) ; des ensembles de jauge de contrainte (3a-3d) permettant de détecter une contrainte se produisant dans le corps déformable (2). Le corps déformable (2) comprend : deux plaques plates annulaires (20a, 20b) disposées dans la direction d'un axe O ; et un élément de liaison (21) reliant les plaques plates annulaires (20a, 20b). L'élément de liaison (21) comprend une pluralité de bras (22) disposés sur un cercle centré sur l'axe O, la pluralité de bras (22) étant positionnés à des intervalles égaux et étant symétriques par rapport à l'axe O, et l'élément de liaison (21) étant incliné par rapport à l'axe O. Les ensembles de jauge de contrainte (3a-3d) comprennent chacun quatre jauges de contrainte (30a-30d) constituant un circuit en pont de Wheatstone, et sont fixés à des emplacements symétriques en ligne par rapport à l'axe O de l'élément de liaison (21).
PCT/JP2018/027407 2017-07-31 2018-07-20 Cellule de charge et palier WO2019026655A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017148456A JP2019027958A (ja) 2017-07-31 2017-07-31 ロードセルおよび軸受
JP2017-148456 2017-07-31

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WO2019026655A1 true WO2019026655A1 (fr) 2019-02-07

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110095217A (zh) * 2019-04-26 2019-08-06 杭州电子科技大学 一种测量滚动轴承摩擦力矩的装置及方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080226409A1 (en) * 2007-03-13 2008-09-18 Thomas Hasenzahl Dental machining unit with tool spindle
JP2008233008A (ja) * 2007-03-23 2008-10-02 Toyota Motor Corp 車輪軸保持装置
WO2012028177A1 (fr) * 2010-08-31 2012-03-08 Aktiebolaget Skf Palier de butée de suspension doté d'un élément filtrant
JP2015049209A (ja) * 2013-09-04 2015-03-16 トヨタ自動車株式会社 トルクセンサ
WO2016052106A1 (fr) * 2014-09-29 2016-04-07 オイレス工業株式会社 Palier de butée pour véhicule

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080226409A1 (en) * 2007-03-13 2008-09-18 Thomas Hasenzahl Dental machining unit with tool spindle
JP2008233008A (ja) * 2007-03-23 2008-10-02 Toyota Motor Corp 車輪軸保持装置
WO2012028177A1 (fr) * 2010-08-31 2012-03-08 Aktiebolaget Skf Palier de butée de suspension doté d'un élément filtrant
JP2015049209A (ja) * 2013-09-04 2015-03-16 トヨタ自動車株式会社 トルクセンサ
WO2016052106A1 (fr) * 2014-09-29 2016-04-07 オイレス工業株式会社 Palier de butée pour véhicule

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110095217A (zh) * 2019-04-26 2019-08-06 杭州电子科技大学 一种测量滚动轴承摩擦力矩的装置及方法

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