WO2019180896A1 - Tubular motor mount for electric vehicle, and method of manufacturing same - Google Patents

Tubular motor mount for electric vehicle, and method of manufacturing same Download PDF

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Publication number
WO2019180896A1
WO2019180896A1 PCT/JP2018/011529 JP2018011529W WO2019180896A1 WO 2019180896 A1 WO2019180896 A1 WO 2019180896A1 JP 2018011529 W JP2018011529 W JP 2018011529W WO 2019180896 A1 WO2019180896 A1 WO 2019180896A1
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WO
WIPO (PCT)
Prior art keywords
shaft member
inner shaft
elastic body
rubber elastic
cylindrical
Prior art date
Application number
PCT/JP2018/011529
Other languages
French (fr)
Japanese (ja)
Inventor
豊士 瀬戸山
Original Assignee
住友理工株式会社
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 住友理工株式会社 filed Critical 住友理工株式会社
Priority to PCT/JP2018/011529 priority Critical patent/WO2019180896A1/en
Priority to JP2019538276A priority patent/JP7079784B2/en
Publication of WO2019180896A1 publication Critical patent/WO2019180896A1/en

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    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal

Definitions

  • the present invention relates to a cylindrical motor mount for an electric vehicle in which an electric motor is connected to a vehicle body in a vibration-proof manner in an electric vehicle, and a method for manufacturing the same.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2000-304080
  • the resonance frequency of the mass-spring system having the mass on the inner shaft member side attached to the electric motor side is set to be higher than that of the conventional engine mount. Is required.
  • the resonance frequency can be tuned to a high frequency by reducing the mass on the inner shaft member side. Therefore, the radial length of the main rubber elastic body is shortened so that the mass mass on the inner shaft member side is reduced. It is conceivable to tune the resonance frequency to a high frequency by reducing the rubber volume of the main rubber elastic body that contributes.
  • the resonance frequency is tuned to the high frequency required for a motor mount for an electric vehicle, the main body rubber In some cases, it is difficult to ensure sufficient durability of the elastic body.
  • the present invention has been made in the background of the above-mentioned circumstances, and its solution is to realize sufficient durability while realizing low dynamic spring characteristics in a high frequency range required in an electric vehicle. It is an object of the present invention to provide a cylindrical motor mount having a novel structure that can be used.
  • Another object of the present invention is to provide a method of manufacturing a cylindrical motor mount for an electric vehicle having a novel structure, which can easily manufacture the cylindrical motor mount for an electric vehicle as described above.
  • the main rubber elastic body is an inner part of the outer cylindrical member.
  • the main rubber elastic body includes a plurality of protrusions that are fixed to the peripheral surface and protrude from the outer cylindrical member toward the inner periphery, and the protrusions are narrow in the circumferential direction toward the protruding tip.
  • the inner shaft member is non-fixedly inserted into the inner periphery of the main rubber elastic body, and the projecting tips of the plurality of protrusions are cylindrical with a circular cross-section in the inner shaft member.
  • the inner shaft member is elastically supported by the main rubber elastic body in a state of being pressed against the outer peripheral surface, the inner shaft member is attached to the motor side of the electric vehicle, and the outer cylinder member is a vehicle of the electric vehicle. That is attached to the body side, characterized.
  • the inner shaft member is inserted into the main rubber elastic body in a non-fixed manner and is elastically supported. Even if vibration in the direction perpendicular to the axis is input between the shaft member and the outer cylinder member, no tensile load acts on the main rubber elastic body. As a result, the durability of the main rubber elastic body can be secured while setting the free length of the main rubber elastic body to be short, so the rubber volume of the main rubber elastic body contributing to the mass of the inner shaft member can be reduced. it can. As a result, the substantial mass on the inner shaft member side can be reduced, and the resonance frequency of the cylindrical motor mount that supports the motor for vibration isolation can be set to a higher frequency. It is possible to achieve both the sufficient durability of the elastic body and the low spring characteristics in the high frequency range required for practical use of electric vehicles.
  • the main rubber elastic body has a plurality of protrusions protruding from the outer cylindrical member toward the inner shaft member, and the protrusions are tapered toward the inner shaft member side.
  • the rubber volume at the tip portion of the pressed projection is reduced, and the mass of the portion that contributes to the mass mass on the inner shaft member side in the main rubber elastic body is reduced. Therefore, in the cylindrical motor mount, the resonance frequency can be tuned to a high frequency required for practical use of an electric vehicle.
  • a second aspect of the present invention is the cylindrical motor mount for an electric vehicle described in the first aspect, wherein the cylindrical outer peripheral surface of the inner shaft member has a true circular cross section.
  • the inner shaft member is supported by the main rubber elastic body regardless of the direction in which the vibration in the direction perpendicular to the axis acts. It is supported stably. Further, in a state where the protrusion is pressed against the outer peripheral surface of the inner shaft member, the contact force is exerted on the inner shaft member in a balanced manner, so that the inner shaft member is easily positioned with respect to the main rubber elastic body.
  • a third aspect of the present invention is the cylindrical motor mount for an electric vehicle described in the first aspect, wherein the cylindrical outer peripheral surface of the inner shaft member has an elliptical cross section.
  • the free length of the main rubber elastic body can be made different between the major axis direction and the minor axis direction of the inner shaft member while making the outer cylinder member a perfect circular cross section that is easy to process and manufacture. This makes it possible to easily set the spring ratio between the major axis direction and the minor axis direction.
  • a concave portion extending in the axial direction is formed at the projecting tip of the projecting portion.
  • the inner peripheral surface of the inner shaft member is in contact with the inner surface of the recess.
  • the cylindrical outer peripheral surface of the inner shaft member is received by the concave portion of the protruding portion, so that the tip portion of the protruding portion is easily positioned in the circumferential direction with respect to the inner shaft member.
  • the member is stably elastically supported by the main rubber elastic body, and the generation of noise due to stick-slip can be prevented.
  • a positioning recess in which the inner shaft member opens on the cylindrical outer peripheral surface is provided.
  • the protrusion is provided with a positioning protrusion protruding from the protruding tip to the inner periphery, and the positioning protrusion is inserted into the positioning recess to position the inner shaft member with respect to the protrusion.
  • the relative position between the protrusion and the inner shaft member is easily defined by inserting the positioning protrusion of the protrusion into the positioning recess of the inner shaft member. Further, for example, if the positioning convex portion is locked to the inner surface of the positioning concave portion in the axial direction, the inner shaft member can be prevented from coming off in the axial direction with respect to the main rubber elastic body.
  • the elastic main shaft in the protruding direction of the protrusion is a diameter of the inner shaft member. It extends in the direction.
  • the contact force of the plurality of protrusions acts in the radial direction of the inner shaft member, so that the moment in the torsional direction is unlikely to act on the inner shaft member, and the inner shaft member is attached to the plurality of protrusions. It can be supported stably between.
  • a seventh aspect of the present invention is the cylindrical motor mount for an electric vehicle described in any one of the first to sixth aspects, wherein the radial resonance frequency is set to 800 Hz or more. .
  • the characteristics are tuned so that the high dynamic spring due to anti-resonance is generated at a higher frequency than the frequency range of vibration that is practically problematic in an electric vehicle. It is possible to realize an excellent low dynamic spring characteristic.
  • An eighth aspect of the present invention is a method of manufacturing a cylindrical motor mount for an electric vehicle in which an inner shaft member and an outer cylindrical member are elastically connected by a main rubber elastic body, wherein (i) the main rubber elastic body is Forming a plurality of protrusions that are molded and fixed to the inner peripheral surface of the outer cylinder member and project from the outer cylinder member toward the inner periphery, and (ii) prepared in advance After the inner shaft member is inserted into the inner periphery of the main rubber elastic body fixed to the outer cylinder member, the outer cylinder member is reduced in diameter to project the plurality of protrusions of the main rubber elastic body And a step of pressing the tip against the outer peripheral surface of the inner shaft member.
  • the inner shaft member has a plurality of protrusions as compared with the case where the inner shaft member is press-fitted into the inner periphery of the plurality of protrusions. It is easy to arrange at an appropriate position with respect to the part.
  • the plurality of protrusions are not deformed so as to bend while being in sliding contact with the cylindrical outer peripheral surface of the inner shaft member. For example, the protruding tips of the plurality of protrusions are easily brought into contact with the cylindrical outer peripheral surface of the inner shaft member.
  • the inner shaft member is stably elastically supported in an appropriate manner by the plurality of protrusions.
  • the inner shaft member is elastically supported by the main rubber elastic body in a non-fixed manner, a tensile load does not act on the main rubber elastic body with respect to vibration input in the direction perpendicular to the axis, and the main rubber elasticity Since the durability can be sufficiently secured while setting the free length of the body short, the substantial mass on the inner shaft member side including the main rubber elastic body is reduced. Moreover, even when the protrusion of the main rubber elastic body is tapered toward the inner shaft member side, the rubber volume of the portion of the main rubber elastic body contributing to the mass of the inner shaft member is reduced. As a result, it is easy to set the resonance frequency of the cylindrical motor mount to a higher frequency while ensuring the durability of the main rubber elastic body sufficiently. Therefore, it is possible to obtain an anti-vibration performance with low dynamic spring characteristics.
  • FIG. XII-XII sectional view of FIG. The front view of the cylindrical motor mount for electric vehicles as 4th embodiment of this invention.
  • FIG. 1 and 2 show a cylindrical motor mount 10 for an electric vehicle as a first embodiment of the present invention.
  • the cylindrical motor mount 10 has a structure in which an inner shaft member 12 and an outer cylindrical member 14 are elastically connected to each other by a main rubber elastic body 16.
  • the vertical direction refers to the vertical direction in FIG. 1
  • the horizontal direction refers to the horizontal direction in FIG. 1
  • the front-rear direction refers to the direction perpendicular to the plane of FIG.
  • the inner shaft member 12 is a highly rigid member made of metal or the like, and has a substantially cylindrical shape with a thick and small diameter.
  • the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a substantially perfect circle shape in the cross section, and has a substantially cylindrical shape extending in the front-rear direction with a substantially constant cross-sectional shape.
  • the inner peripheral surface of the inner shaft member 12 is also substantially circular in cross section.
  • the outer cylinder member 14 is a highly rigid member made of metal or the like, and has a thin cylindrical shape with a large diameter.
  • the outer cylindrical member 14 of the present embodiment has an inner peripheral surface that is substantially circular in cross section, and linearly extends in the front-rear direction with a substantially constant cross-sectional shape.
  • the outer peripheral surface of the outer cylindrical member 14 has a substantially circular cross-sectional shape in the axial center and linearly extends in the front-rear direction, and both end portions in the axial direction gradually become smaller in diameter toward the outer side in the axial direction. It is a tapered surface.
  • the outer cylinder member 14 has a smaller axial dimension than the inner shaft member 12.
  • the outer cylinder member 14 preferably has an outer diameter of 75 mm or less. Further, preferably, the difference between the inner diameter dimension of the outer cylindrical member 14 and the outer diameter dimension of the inner shaft member 12 is 45 mm or less, and the outer diameter dimension of the inner shaft member 12 is equal to the inner diameter dimension of the outer cylindrical member 14. The ratio is 4 or less. In the present embodiment, for example, the outer diameter of the outer cylinder member 14 is 60 mm, and the difference between the inner diameter of the outer cylinder member 14 and the outer diameter of the inner shaft member 12 is 35 mm.
  • the main rubber elastic body 16 is vulcanized and bonded to the inner peripheral surface of the outer cylinder member 14.
  • the main rubber elastic body 16 includes an outer peripheral rubber layer 20 formed on the inner peripheral surface of the outer cylinder member 14 and four protrusions 22, 22, 22, 22 protruding from the outer peripheral rubber layer 20 toward the inner periphery. And has.
  • the main rubber elastic body 16 is formed as an integrally vulcanized molded product 24 including the outer cylinder member 14.
  • the outer peripheral rubber layer 20 has a thin cylindrical shape and covers the inner peripheral surface of the outer cylindrical member 14 over the entire circumference.
  • the axial dimension of the outer peripheral rubber layer 20 is smaller than the axial dimension of the outer cylindrical member 14 and larger than the axial dimension of the protruding portion 22. Has a thickness of 1 mm or more.
  • the projecting portions 22 are provided at four locations on the top, bottom, left, and right, respectively, projecting from the outer cylindrical member 14 toward the inner periphery, and having a tapered shape that narrows in the circumferential direction toward the projecting tip 26. And the cross-sectional area on the plane perpendicular to the protruding direction is reduced from the base end toward the protruding tip 26.
  • the four protrusions 22, 22, 22, 22 of the present embodiment have substantially the same shape.
  • the protruding portion 22 of the present embodiment includes a proximal curved surface 28 that is concave toward the outer side in the circumferential direction and a distal curved surface 30 that is convex toward the outer side in the circumferential direction.
  • the circumferential side surfaces are formed by providing them continuously, and both ends of the base end curved surface 28 are smoothly continuous with each of the inner peripheral surface of the outer peripheral rubber layer 20 and the distal end curved surface 30.
  • the circumferential side surface of the protrusion 22 is configured by the proximal curved surface 28 and the distal curved surface 30, the protrusion 22 has a large change amount in cross-sectional area toward the projected distal end 26 at the proximal end portion.
  • the amount of change in the cross-sectional area gradually increases toward the projecting tip 26 at the tip portion. Furthermore, the amount of change in the cross-sectional area is small at the intermediate portion of the protruding portion 22 in the protruding direction.
  • the tip portion of the semicircular cross section provided with the tip curved surfaces 30, 30 occupies 1/4 or more, more preferably 1/3 or more of the projecting dimension of the protrusion 22, In the motor mount 10, the resonance frequency is increased and the dynamic spring is reduced.
  • the protrusion 22 extends in the radial direction with a substantially constant axial dimension, and has a smaller axial dimension than the outer peripheral rubber layer 20.
  • the axial end surface of the protrusion 22 is a concave curved surface that inclines inward in the axial direction toward the inner periphery at the outer peripheral end, and inward in the axial direction toward the inner periphery at the inner peripheral end.
  • the outer peripheral end is smoothly continuous with the inner peripheral surface of the outer peripheral rubber layer 20, and the inner peripheral end is smoothly continuous with the distal end surface of the protrusion 22.
  • each protrusion 22 extends in the radial direction of the outer cylindrical member 14.
  • the elastic main axes of the two protrusions 22 and 22 extend in the vertical direction, and the elastic main axes of the two protrusions 22 and 22 extend in the left-right direction.
  • the two protrusions 22, 22 arranged adjacent to each other in the circumferential direction are separated from each other in the circumferential direction, for example, 5 mm or more in the circumferential direction at the base end, more preferably 10 mm or more away.
  • the projecting dimension of the protruding portion 22 is smaller than half of the inner diameter dimension of the outer peripheral rubber layer 20, and in this embodiment is about 1 / of the inner diameter dimension of the outer peripheral rubber layer 20.
  • the four protrusions 22, 22, 22, 22 are fixed to the outer cylinder member 14 via the outer peripheral rubber layer 20, and the protrusions 22, 22, 22, 22 are fixed to the outer cylinder member 14 with a large fixing area.
  • the base end portion of the protruding portion 22 spreads in a smooth curved shape toward the entire periphery, and the outer peripheral rubber layer 20 covers the inner peripheral surface of the outer cylindrical member 14 with a constant thickness over substantially the entire surface.
  • the axial dimension and the circumferential dimension of the protrusion 22 are reduced, and these dimensions are such that the stress and deformation of the protrusion 22 are not substantially transmitted to the other protrusions 22 and the outer rubber layer 20. ing.
  • the four protrusions 22, 22, 22 of the main rubber elastic body 16 are inserted in the inner periphery of the main rubber elastic body 16 fixed to the inner peripheral surface of the outer cylinder member 14. , 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12 in a non-fixed manner, so that the inner shaft member 12 is elastically supported by the main rubber elastic body 16. Thereby, the cylindrical motor mount 10 in which the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 16 is configured.
  • the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a circular cross section, and the protrusion 22 has a tapered shape that becomes narrower in the circumferential direction toward the protrusion tip 26.
  • the contact area of the protruding tip 26 against the inner shaft member 12 is very small in the stationary state. Specifically, for example, it is 1/10 or less with respect to the cross-sectional area on the plane orthogonal to the protruding direction at the base end portion of the protrusion 22.
  • the radial resonance frequency of the mass-spring system in which the inner shaft member 12 side is a mass and the main rubber elastic body 16 is a spring is set to a high frequency of 800 Hz or more.
  • the cylindrical motor mount 10 is made to have a high dynamic spring due to the anti-resonance of the mass-spring system at a frequency higher than 800 Hz.
  • the cylindrical motor mount 10 can be preferably manufactured by the following manufacturing method, for example.
  • the outer cylindrical member 14 prepared in advance is set in a molding die for the main rubber elastic body 16, and the main rubber elastic body 16 including the outer peripheral rubber layer 20 and the plurality of protrusions 22 is attached to the outer cylindrical member 14.
  • Vulcanization molding is performed with the inner peripheral surface fixed.
  • the inner peripheral surface of the outer cylindrical member 14 is covered with the outer peripheral rubber layer 20 of the main rubber elastic body 16, and a plurality of protrusions 22 are formed so as to protrude from the outer cylindrical member 14 to the inner periphery.
  • the inner shaft member 12 prepared in advance is inserted into the inner periphery of the main rubber elastic body 16 fixed to the outer cylinder member 14.
  • the distance between the projecting tips 26, 26 of the projecting portions 22, 22 arranged facing each other in the front-rear direction or the left-right direction is made larger than the outer diameter dimension of the inner shaft member 12, and the inner shaft The member 12 is inserted between the protrusions 22 and 22 with a gap therebetween.
  • the integrally vulcanized molded product 24 of the main rubber elastic body 16 and the inner shaft member 12 are held in a mutually positioned state by being set, for example, in a jig for diameter reduction processing described later.
  • the outer cylinder member 14 is subjected to diameter reduction processing such as eight-way drawing.
  • the main rubber elastic body 16 fixed to the inner peripheral surface of the outer cylinder member 14 is reduced in diameter together with the outer cylinder member 14, and the protruding tip 26 of the protrusion 22 of the main rubber elastic body 16 is connected to the cylinder of the inner shaft member 12.
  • the outer peripheral surface 18 is pressed.
  • the inner shaft member 12 is elastically supported by the plurality of protrusions 22, and the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 16 to obtain the cylindrical motor mount 10.
  • each protrusion 22 extends in the radial direction of the inner shaft member 12.
  • Each projecting portion 22 is compressed in the projecting direction by the projecting tip 26 being pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12.
  • the four projecting portions 22, 22, 22, 22 are pressed against the inner shaft member 12 in the radial direction from both the upper and lower sides and the left and right sides, so that the contact force acting on the inner shaft member 12 is exerted.
  • the inner shaft member 12 is prevented from shifting in the radial direction by the contact force.
  • the inner shaft member 12 is attached to the motor 32 by a bolt or the like (not shown), and the outer cylindrical member 14 is press-fitted and fixed to the subframe. For example, it is attached to the vehicle body 34.
  • the motor 32 is connected to the vehicle body 34 with vibration isolation via the cylindrical motor mount 10.
  • the inner shaft member 12 is directly attached to the motor 32.
  • the inner shaft member 12 and the motor 32 are attached to each other via a bracket (not shown). May be.
  • the cylindrical motor mount 10 having the structure according to this embodiment, even if vibration is input and the inner shaft member 12 and the outer cylindrical member 14 are relatively displaced in the radial direction, the inner shaft member 12 and the main rubber elastic body 16 are not fixed, and no tensile stress acts on the main rubber elastic body 16. Therefore, the main rubber elastic body 16 is hardly damaged such as a crack, and the durability of the main rubber elastic body 16 can be improved.
  • the durability of the main rubber elastic body 16 is ensured by the inner shaft member 12 and the main rubber elastic body 16 being not fixed, the radial free length of the main rubber elastic body 16 is set short. be able to. Therefore, the rubber volume of the main rubber elastic body 16 that contributes to the mass mass on the inner shaft member 12 side can be reduced, and the substantial mass mass on the inner shaft member 12 side is reduced. It becomes possible to tune the resonance frequency of the motor mount 10 to a higher frequency.
  • the abutting portions of the main rubber elastic body 16 with respect to the inner shaft member 12 are formed as a plurality of protrusions 22, and the rubber volume of the inner peripheral portion of the main rubber elastic body 16 on the inner shaft member 12 side is reduced. Therefore, an increase in mass of the inner shaft member 12 due to the contribution of the main rubber elastic body 16 is suppressed, and the resonance frequency of the cylindrical motor mount 10 can be easily set to a high frequency.
  • the protrusion 22 is tapered toward the protrusion tip 26, and the rubber volume at the tip of the protrusion 22 pressed against the inner shaft member 12 is further reduced. An increase in mass of the inner shaft member 12 is further suppressed, and the resonance frequency of the cylindrical motor mount 10 can be easily set to a high frequency.
  • the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a curved shape that is convex toward the outer periphery, and the protruding tip 26 of the protrusion 22 is convex toward the inner periphery. Because of the curved shape, the contact area of the protrusion 22 with the cylindrical outer peripheral surface 18 of the inner shaft member 12 is reduced. As a result, a soft spring characteristic is realized in a state where the relative displacement between the inner shaft member 12 and the outer cylinder member 14 is small, and the tip portion of the protrusion 22 is less likely to contribute to the mass of the inner shaft member 12 side. Thus, it is easy to set the resonance frequency of the cylindrical motor mount 10 to a high frequency.
  • the cylindrical motor mount 10 can set a higher frequency range in which high dynamic springs due to a resonance phenomenon (anti-resonance) occur, and low dynamic spring characteristics up to a high frequency range in an electric vehicle. It is possible to respond to demands.
  • the radial resonance frequency of the cylindrical motor mount 10 is tuned to a high frequency of 800 Hz or more, and in a high frequency region where high dynamic springs due to anti-resonance are unlikely to be a problem in practical use of an electric vehicle. As a result, it is possible to effectively obtain the vibration isolation performance by the low dynamic spring in the frequency range of the vibration which is a problem in the electric vehicle.
  • the base end portion of the protrusion 22 is wider in the circumferential direction toward the base end, it is possible to ensure deformation stability and durability of the protrusion 22.
  • the protrusion 22 has a substantially constant axial dimension in the projecting direction and a circumferential dimension that changes, so that a high-frequency resonance frequency in the direction perpendicular to the axis is secured while securing a support spring in the twisting direction. It is planned.
  • the protruding portion 22 is formed integrally with the outer peripheral rubber layer 20 and is fixed to the outer cylinder member 14 via the outer peripheral rubber layer 20, whereby the fixing strength of the protruding portion 22 to the outer cylindrical member 14 is increased. be able to.
  • the thickness of the outer peripheral rubber layer 20 is 1 mm or more, the stress distribution at the base end portion of the protrusion 22 is also achieved.
  • the cylindrical motor mount 10 has a higher frequency range in which high dynamic springs due to anti-resonance are generated, so that even if the input load changes in advance due to acceleration / deceleration, the cylindrical motor mount 10 is resistant to vibration.
  • the anti-vibration performance based on the low dynamic spring characteristics is stably exhibited. That is, generally, when the load input in advance is relatively small, such as when the vehicle is stopped or at a stable running at a substantially constant speed, the elastic deformation amount of the main rubber elastic body 16 is relatively small.
  • the low dynamic spring characteristic with respect to vibration input is effectively exhibited, when a large load is input by acceleration / deceleration or the like, the main rubber elastic body 16 is largely elastically deformed in advance, so that vibration is input in that state. As compared with a case where the load is small, hard spring characteristics (high dynamic spring characteristics) are easily exhibited.
  • the high dynamic spring due to anti-resonance occurs at a higher frequency than the frequency range of vibrations that is a problem in an electric vehicle. Even in a state where a load is input, the vibration isolation effect due to the low dynamic spring characteristic is effectively exhibited.
  • the cylindrical motor mount 10 it is possible to maintain a dynamic spring constant of 1500 N / mm or less in a frequency range of 800 Hz or less regardless of a change in preload.
  • the cross-sectional shape of the cylindrical outer peripheral surface 18 of the inner shaft member 12 is a substantially circular shape, the outer cylindrical member 14 is reduced in diameter over the entire circumference, and the four protrusions 22, 22, When pressing 22, 22 against the cylindrical outer peripheral surface 18 of the inner shaft member 12, it is difficult for the inner shaft member 12 to be displaced.
  • cylindrical outer peripheral surface 18 of the inner shaft member 12 has a substantially perfect circular cross section, and the four protrusions 22, 22, 22, 22 are arranged in a balanced manner in the circumferential direction, thereby forming a cylindrical shape.
  • the inner shaft member 12 is stably elastically supported when a radial vibration is input to the motor mount 10.
  • the four protrusions 22, 22, 22, 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12 from both the upper and lower sides and the left and right sides, and the elastic main shaft of each protrusion 22 is the inner shaft member 12. It extends in the radial direction. Therefore, when the four protrusions 22, 22, 22, 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12, the inner shaft member 12 is not easily displaced, and the inner shaft member 12 is stable. While being elastically supported, the inner shaft member 12 is held in a stable elastic support state even when vibration is input.
  • FIG. 6 shows a cylindrical motor mount 40 for an electric vehicle as a second embodiment of the present invention.
  • the inner shaft member 12 is attached to the integrally vulcanized molded product 44 of the main rubber elastic body 42 in a non-fixed manner, and the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 42.
  • parts and members that are substantially the same as those of the first embodiment are denoted by the same reference numerals in the drawings, and description thereof is omitted.
  • the main rubber elastic body 42 is fixed to the inner peripheral surface of the outer cylinder member 14, and includes four protrusions 46, 46, 46, 46 that protrude from the outer peripheral rubber layer 20 toward the inner periphery. I have.
  • the protrusion 46 has a tapered shape that becomes narrower in the circumferential direction toward the protruding tip 26, and a recess 48 is formed in the protruding tip 26.
  • the recess 48 is open to the protruding tip 26 of the protrusion 46, and in this embodiment, has a groove shape that is linearly continuous over substantially the entire length in the axial direction.
  • the inner surface of the recess 48 of the present embodiment is a curved surface that extends in the circumferential direction with a curvature substantially corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12.
  • the specific shape of the recess 48 is not particularly limited, and it is not always necessary to have an inner surface constituted by a concave curved surface corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12.
  • the outer cylinder member 14 is reduced in diameter in a state where the inner shaft member 12 is inserted into the inner periphery of the main rubber elastic body 42.
  • the protruding tip 26 is pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12.
  • the cylindrical outer peripheral surface 18 of the inner shaft member 12 enters the recess 48 provided at the protruding tip 26 of the protrusion 46 and is in contact with the inner surface of the recess 48.
  • the protruding tip 26 is easily positioned in the circumferential direction by the recess 48 with respect to the inner shaft member 12. Therefore, when the protruding tip 26 of the protrusion 46 is pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12, the protrusion 46 is compressed by a predetermined amount in the protruding direction, and the inner shaft member 12 has a plurality of protrusions. It is elastically supported stably between the parts 46.
  • the inner surface of the recess 48 is a curved concave surface corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12, so that the positioning of the protrusion 46 in the circumferential direction with respect to the inner shaft member 12 is more effective. Is realized.
  • FIGS. 8 and 9 show a cylindrical motor mount 50 for an electric vehicle as a third embodiment of the present invention.
  • the inner shaft member 51 is attached to the integrally vulcanized molded product 54 of the main rubber elastic body 52 in a non-fixed manner, and the inner shaft member 51 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 52.
  • the inner shaft member 51 of the present embodiment includes a positioning recess 56 that opens to the outer peripheral surface, as shown in FIG.
  • the positioning concave portion 56 is an annular concave groove extending in the circumferential direction with a substantially semicircular cross-sectional shape, and is formed in the central portion of the inner shaft member 51 in the axial direction.
  • the main rubber elastic body 52 includes a plurality of protrusions 57.
  • the protruding portion 57 has a positioning convex portion 58 formed integrally with the protruding tip 26.
  • the positioning convex portion 58 has a tapered shape with a small diameter toward the tip side by being a small hemispherical shape with a small diameter, and the protruding tip of the protruding portion 57 at the approximate center in the circumferential direction and the axial direction of the protruding portion 57. 26 protrudes from the inner periphery.
  • the inner shaft member 51 is inserted into the inner circumference of the main rubber elastic body 52 fixed to the outer cylinder member 14 as shown in FIGS.
  • the distance between the positioning projections 58 and 58 of the projecting portions 57 and 57 facing in the radial direction is set to be larger than the outer diameter of the portion of the inner shaft member 51 that is out of the positioning recess 56.
  • the distance between the positioning convex portions 58 and 58 is made smaller than the outer diameter of the portion of the inner shaft member 51 that is out of the positioning concave portion 56, and the inner shaft member 51 elastically deforms the positioning convex portion 58, while You may make it insert in the inner peripheral side of the projection part 57.
  • the protrusion 57 of the main rubber elastic body 52 is moved to the inner shaft member 51.
  • the inner shaft member 51 is elastically supported by the main rubber elastic body 52 by being pressed against the cylindrical outer peripheral surface 18.
  • the positioning projection 58 of the projection 57 is inserted into the positioning recess 56 of the inner shaft member 51, and the projection 57 and the inner shaft member 51 are relatively moved in the axial direction by the positioning projection 58 and the positioning recess 56. It is positioned.
  • the inner shaft member 51 is less likely to come off in the axial direction with respect to the main rubber elastic body 52, and the integral vulcanized molded product 54 of the inner shaft member 51 and the main rubber elastic body 52 is stably positioned in the axial direction. Retained.
  • the position of each protrusion 57 in the axial direction with respect to the inner shaft member 51 is held by the positioning protrusion 58 and the positioning recess 56, the inner shaft member 51 is stably between the plurality of protrusions 57. Elastically supported.
  • the positioning concave portion 56 and the positioning convex portion 58 of the present embodiment are formed at axial positions corresponding to each other, and have a shape that substantially corresponds to each other in the longitudinal section. It is possible to put it in.
  • the positioning recess 56 is a groove extending in the circumferential direction
  • the inner shaft member 51 and the main rubber elastic body 52 are positioned in the axial direction by the positioning protrusion 58 and the positioning recess 56.
  • the positioning recess is a circular recess corresponding to the positioning projection 58
  • the inner shaft member 51 and the main rubber elastic body 52 are axially moved by the positioning projection 58 and the positioning recess. It is also possible to position both in the circumferential direction.
  • the positioning recess can be a groove extending in the axial direction
  • the inner shaft member 51 and the main rubber elastic body 52 can be positioned in the circumferential direction by the positioning recess and the positioning protrusion 58.
  • FIG. 13 shows a cylindrical motor mount 60 for an electric vehicle as a fourth embodiment of the present invention.
  • the inner shaft member 62 is non-fixedly attached to the integrally vulcanized molded product 66 of the main rubber elastic body 64, and the inner shaft member 62 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 64.
  • the inner shaft member 62 of the present embodiment includes a cylindrical outer peripheral surface 68 having a substantially elliptical cross section, and the vertical direction is a short axis and the horizontal direction is a long axis.
  • the inner peripheral surface of the inner shaft member 62 has a substantially circular cross section, and the upper and lower thickness dimensions of the peripheral wall of the inner shaft member 62 are smaller than the left and right thickness dimensions.
  • the main rubber elastic body 64 includes upper and lower protrusions 70 and 70 and left and right protrusions 72 and 72.
  • the upper and lower protrusions 70, 70 and the left and right protrusions 72, 72 both have a tapered shape that becomes narrower in the circumferential direction toward each protrusion tip 26, and the upper and lower protrusions 70, 70 have a tapered shape.
  • the dimension in the projecting direction is made larger than the dimension in the projecting direction of the left and right protrusions 72, 72.
  • the radial distance between the upper and lower protrusions 70 and 70 is made smaller than the radial distance between the left and right protrusions 72 and 72. It is also possible to make the left and right thickness dimensions substantially the same.
  • the inner shaft member 62 is inserted into the inner periphery of the main rubber elastic body 64 fixed to the outer cylinder member 14.
  • the vertical distance between the upper and lower protrusions 70, 70 is larger than the outer diameter dimension of the inner shaft member 62 in the minor axis direction, and the left and right protrusions 72, 72 in the left-right direction. The distance is made larger than the outer diameter dimension of the inner shaft member 62 in the major axis direction.
  • the projecting dimensions of the upper and lower projecting portions 70, 70 are larger than the projecting dimensions of the left and right projecting portions 72, 72, the distance between the radial directions of the upper and lower projecting portions 70, 70 and the inner
  • the difference between the outer diameter dimension of the shaft member 62 in the minor axis direction and the difference between the distance between the radial directions of the left and right protrusions 72 and 72 and the outer diameter dimension of the inner shaft member 62 in the major axis direction are substantially the same. It is said that.
  • the outer cylindrical member 14 when the outer cylindrical member 14 is reduced in diameter in a state where the inner shaft member 62 is inserted into the inner periphery of the main rubber elastic body 64, the upper and lower protrusions 70, 70 of the main rubber elastic body 64 are formed.
  • the inner shaft member 62 is pressed against the cylindrical outer peripheral surface 18 in the short axis direction, and the left and right protrusions 72 and 72 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 62 in the long axis direction.
  • the shaft member 62 is elastically supported by the main rubber elastic body 64.
  • the projecting dimensions of the upper and lower projecting portions 70, 70 are larger than the projecting dimensions of the left and right projecting portions 72, 72, so that the inner shaft member 62 of the projecting portions 70, 70, 72, 72 is.
  • the contact force to is substantially the same.
  • the cylindrical motor mount 60 having the structure according to this embodiment, it is easy to set different spring characteristics in the vertical direction and the horizontal direction. That is, since the cylindrical outer peripheral surface 18 of the inner shaft member 62 has an elliptical cross section and the inner peripheral surface of the outer cylindrical member 14 has a circular cross section, the inner shaft member 62 and the outer cylindrical member 14 The space between the radial directions of the inner shaft member 62 is larger in the short axis direction of the inner shaft member 62 than in the long axis direction. Therefore, it becomes easy to make the protrusion dimensions in the radial direction of the upper and lower protrusions 70 and 70 and the left and right protrusions 72 and 72 different from each other, and it becomes easy to adjust the spring ratio in the vertical and horizontal directions. In the present embodiment, the vertical dimension of the upper and lower protrusions 70, 70 is larger than the horizontal dimension of the left and right protrusions 72, 72, and the vertical spring is set to be softer than the horizontal spring. Yes.
  • the shape of the protrusion is not particularly limited as long as it is a tapered shape that becomes narrower in the circumferential direction toward the protruding tip. Can be employed.
  • the plurality of protrusions may have different shapes. Specifically, for example, when the shared support load of the motor is applied as a static load in a specific radial direction, the specific protrusion is considered in consideration that the specific protrusion is compressed by the shared support load. Can also be shaped differently from other protrusions.
  • the number of protrusions is not limited to four as shown in the above embodiment as long as it is plural, and may be three or five or more, for example.
  • the protrusion has an elastic main shaft in the protruding direction extending in the radial direction of the inner shaft member, but the direction of the elastic main shaft of the protrusion does not necessarily coincide with the radial direction of the inner shaft member. good.
  • the inner shaft member when the inner shaft member is inserted into the inner circumference of the main rubber elastic body, it can be inserted in a press-fitted state with a tightening margin.
  • the outer cylindrical member after the inner shaft member is inserted into the inner periphery of the main rubber elastic body, the outer cylindrical member may be subjected to diameter reduction processing, or the protrusion of the main rubber elastic body may be inserted into the inner shaft member. You may make it fully press on this cylindrical outer peripheral surface.
  • the inner shaft member is not necessarily limited to a straight cylindrical shape.
  • the central portion in the axial direction may be partially expanded, and the annular central portion may be annular or cylindrical.
  • the member may be fixed in an extrapolated state.
  • the inner shaft member may be solid.
  • the inner shaft member has a solid rod shape, and a plate-like attachment portion is provided at an end portion in the axial direction, and a bolt hole penetrated through the attachment portion. It is also possible to adopt a structure in which the inner shaft member is attached to the motor by a bolt inserted into the motor.
  • the outer cylinder member is preferably a cylindrical shape having a substantially perfect circular cross section for ease of diameter reduction processing, but may be, for example, an elliptic cylinder shape.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
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  • Vibration Prevention Devices (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

Provided are a tubular motor mount having a novel structure and a method of manufacturing the same with which it is possible to achieve sufficient durability while achieving low dynamic spring characteristics in a high frequency range required in electric vehicles. A body rubber elastic body 16 fixedly attached to an inner peripheral surface of an outer tube member 14 is provided with a plurality of projection portions 22 protruding radially inward from the outer tube member 14. The projection portions 22 have a tapering shape decreasing in width circumferentially toward a protrusion tip 26. An inner shaft member 12 is inserted without being fixedly attached to the inner periphery of the body rubber elastic body 16. The protrusion tips 26 of the plurality of projection portions 22 are pressed against a tubular outer peripheral surface 18 in the circular cross section of the inner shaft member 12, whereby the inner shaft member 12 is elastically supported by the body rubber elastic body 16. The inner shaft member 12 is mounted to the motor 32 of an electric vehicle, and the outer tube member 14 is adapted to be mounted to the vehicle body 34 side of the electric vehicle.

Description

電気自動車用の筒形モータマウントとその製造方法Cylindrical motor mount for electric vehicles and manufacturing method thereof
　本発明は、電気自動車において電気モータを車両ボデーに防振連結する電気自動車用の筒形モータマウントとその製造方法に関するものである。 The present invention relates to a cylindrical motor mount for an electric vehicle in which an electric motor is connected to a vehicle body in a vibration-proof manner in an electric vehicle, and a method for manufacturing the same.
　従来から、エンジンと車両ボデーを防振連結するエンジンマウントとして、インナ軸部材とアウタ筒部材が本体ゴム弾性体によって径方向で相互に弾性連結された構造を有する筒形防振装置が採用されている。例えば、特開２０００－３０４０８０号公報（特許文献１）に開示されているのが、それである。 Conventionally, as an engine mount for anti-vibration connection between an engine and a vehicle body, a cylindrical anti-vibration device having a structure in which an inner shaft member and an outer cylinder member are elastically connected to each other in a radial direction by a main rubber elastic body has been adopted. Yes. For example, it is disclosed in Japanese Unexamined Patent Publication No. 2000-304080 (Patent Document 1).
　ところで、昨今では、環境問題や化石燃料の枯渇などへの配慮から、従来のエンジンを原動機とする自動車から電気モータを原動機とする電気自動車への転換が検討されている。電気自動車では、エンジンに変えて電気モータを採用することで原動機において生じる振動が減少すると考えられており、電気モータと車両ボデーを防振連結するモータマウントは、エンジンマウントと同様の筒形防振装置を採用可能であると考えられていた。 By the way, recently, in consideration of environmental problems and depletion of fossil fuels, a switch from a vehicle using a conventional engine as a prime mover to an electric vehicle using a motor as a prime mover is being considered. In an electric vehicle, it is thought that the vibration generated in the prime mover is reduced by adopting an electric motor instead of an engine. The motor mount that connects the electric motor and the vehicle body in an anti-vibration manner is a cylindrical anti-vibration similar to the engine mount. It was thought that the device could be adopted.
　しかしながら、電気モータにおいて発生する振動の特性がエンジンにおいて発生する振動の特性と大きく異なることによって、電気自動車用のモータマウントは、従来のエンジンマウントでは問題になり難かった高周波数域の振動に対しても、低動ばねによる振動絶縁効果が要求される場合がある。その場合には、反共振による高動ばね化を防ぐために、電気モータ側に取り付けられるインナ軸部材側をマスとするマス－バネ系の共振周波数が、従来のエンジンマウントよりも高周波に設定されることが求められる。このマス－バネ系では、インナ軸部材側のマス質量を小さくすることによって共振周波数を高周波にチューニングできることから、本体ゴム弾性体の径方向長さを短くして、インナ軸部材側のマス質量に寄与する本体ゴム弾性体のゴムボリュームを小さくすることで、共振周波数を高周波にチューニングすることが考えられる。 However, because the characteristics of vibrations generated in electric motors are significantly different from the characteristics of vibrations generated in engines, motor mounts for electric vehicles are resistant to vibrations in the high frequency range, which has not been a problem with conventional engine mounts. However, there is a case where a vibration insulation effect by a low dynamic spring is required. In that case, in order to prevent high dynamic springs due to anti-resonance, the resonance frequency of the mass-spring system having the mass on the inner shaft member side attached to the electric motor side is set to be higher than that of the conventional engine mount. Is required. In this mass-spring system, the resonance frequency can be tuned to a high frequency by reducing the mass on the inner shaft member side. Therefore, the radial length of the main rubber elastic body is shortened so that the mass mass on the inner shaft member side is reduced. It is conceivable to tune the resonance frequency to a high frequency by reducing the rubber volume of the main rubber elastic body that contributes.
　ところが、本体ゴム弾性体の径方向の自由長を短くすると、本体ゴム弾性体の耐久性が低下することから、電気自動車用のモータマウントにおいて求められる高周波に共振周波数をチューニングしようとすると、本体ゴム弾性体の耐久性を十分に確保することが難しい場合があった。 However, if the free length in the radial direction of the main rubber elastic body is shortened, the durability of the main rubber elastic body is reduced. Therefore, when the resonance frequency is tuned to the high frequency required for a motor mount for an electric vehicle, the main body rubber In some cases, it is difficult to ensure sufficient durability of the elastic body.
特開２０００－３０４０８０号公報JP 2000-304080 A
　本発明は、上述の事情を背景に為されたものであって、その解決課題は、電気自動車において要求される高周波域での低動ばね特性を実現しながら、十分な耐久性も実現することができる、新規な構造の筒形モータマウントを提供することにある。 The present invention has been made in the background of the above-mentioned circumstances, and its solution is to realize sufficient durability while realizing low dynamic spring characteristics in a high frequency range required in an electric vehicle. It is an object of the present invention to provide a cylindrical motor mount having a novel structure that can be used.
　また、本発明は、上述の如き電気自動車用の筒形モータマウントを容易に製造することができる、新規な構造の電気自動車用の筒形モータマウントの製造方法を提供することも目的とする。 Another object of the present invention is to provide a method of manufacturing a cylindrical motor mount for an electric vehicle having a novel structure, which can easily manufacture the cylindrical motor mount for an electric vehicle as described above.
　以下、このような課題を解決するために為された本発明の態様を記載する。なお、以下に記載の各態様において採用される構成要素は、可能な限り任意の組み合わせで採用可能である。 Hereinafter, embodiments of the present invention made to solve such problems will be described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible.
　すなわち、本発明の第一の態様は、インナ軸部材とアウタ筒部材が本体ゴム弾性体によって弾性連結された電気自動車用の筒形モータマウントにおいて、前記本体ゴム弾性体が前記アウタ筒部材の内周面に固着されていると共に、該本体ゴム弾性体が該アウタ筒部材から内周へ向けて突出する複数の突起部を備えており、該突起部が突出先端に向けて周方向で幅狭となる先細形状を有していると共に、該インナ軸部材が該本体ゴム弾性体の内周に非固着で差し入れられて該複数の突起部の突出先端が前記インナ軸部材における円形断面の筒状外周面に押し付けられた状態で該インナ軸部材が該本体ゴム弾性体によって弾性支持されており、該インナ軸部材が電気自動車のモータ側へ取り付けられるとともに該アウタ筒部材が電気自動車の車両ボデー側へ取り付けられることを、特徴とする。 That is, according to a first aspect of the present invention, in the cylindrical motor mount for an electric vehicle in which the inner shaft member and the outer cylindrical member are elastically connected by the main rubber elastic body, the main rubber elastic body is an inner part of the outer cylindrical member. The main rubber elastic body includes a plurality of protrusions that are fixed to the peripheral surface and protrude from the outer cylindrical member toward the inner periphery, and the protrusions are narrow in the circumferential direction toward the protruding tip. The inner shaft member is non-fixedly inserted into the inner periphery of the main rubber elastic body, and the projecting tips of the plurality of protrusions are cylindrical with a circular cross-section in the inner shaft member. The inner shaft member is elastically supported by the main rubber elastic body in a state of being pressed against the outer peripheral surface, the inner shaft member is attached to the motor side of the electric vehicle, and the outer cylinder member is a vehicle of the electric vehicle. That is attached to the body side, characterized.
　このような第一の態様に従う構造とされた電気自動車用の筒形モータマウントによれば、インナ軸部材が本体ゴム弾性体に対して非固着で差し入れられて弾性支持されていることにより、インナ軸部材とアウタ筒部材の間に軸直角方向の振動が入力されても、本体ゴム弾性体に引張荷重が作用しない。これによって、本体ゴム弾性体の自由長を短く設定しながら、本体ゴム弾性体の耐久性を確保できることから、インナ軸部材側のマス質量に寄与する本体ゴム弾性体のゴムボリュームを小さくすることができる。その結果、インナ軸部材側の実質的なマス質量が小さくすることができて、モータを防振支持する筒形モータマウントの共振周波数をより高周波に設定することが可能となることから、本体ゴム弾性体の十分な耐久性と、電気自動車の実用上で要求される高周波領域での低ばね特性とを、両立して実現することができる。 According to the cylindrical motor mount for an electric vehicle having the structure according to the first aspect, the inner shaft member is inserted into the main rubber elastic body in a non-fixed manner and is elastically supported. Even if vibration in the direction perpendicular to the axis is input between the shaft member and the outer cylinder member, no tensile load acts on the main rubber elastic body. As a result, the durability of the main rubber elastic body can be secured while setting the free length of the main rubber elastic body to be short, so the rubber volume of the main rubber elastic body contributing to the mass of the inner shaft member can be reduced. it can. As a result, the substantial mass on the inner shaft member side can be reduced, and the resonance frequency of the cylindrical motor mount that supports the motor for vibration isolation can be set to a higher frequency. It is possible to achieve both the sufficient durability of the elastic body and the low spring characteristics in the high frequency range required for practical use of electric vehicles.
　また、本体ゴム弾性体がアウタ筒部材からインナ軸部材へ向けて突出する複数の突起部を備えており、突起部がインナ軸部材側に向けて先細とされていることにより、インナ軸部材に押し付けられる突起部の先端部分のゴムボリュームが小さくなって、本体ゴム弾性体においてインナ軸部材側のマス質量に寄与する部分の質量が小さくなる。それ故、筒形モータマウントにおいて、共振周波数を電気自動車の実用上で必要とされる高周波にチューニングすることが可能となる。 Further, the main rubber elastic body has a plurality of protrusions protruding from the outer cylindrical member toward the inner shaft member, and the protrusions are tapered toward the inner shaft member side. The rubber volume at the tip portion of the pressed projection is reduced, and the mass of the portion that contributes to the mass mass on the inner shaft member side in the main rubber elastic body is reduced. Therefore, in the cylindrical motor mount, the resonance frequency can be tuned to a high frequency required for practical use of an electric vehicle.
　本発明の第二の態様は、第一の態様に記載された電気自動車用の筒形モータマウントにおいて、前記インナ軸部材の前記筒状外周面が真円形断面を有しているものである。 A second aspect of the present invention is the cylindrical motor mount for an electric vehicle described in the first aspect, wherein the cylindrical outer peripheral surface of the inner shaft member has a true circular cross section.
　第二の態様によれば、各突起部が真円筒状とされる筒状外周面に当接することから、軸直角方向の振動が作用する向きに関わらず、インナ軸部材が本体ゴム弾性体によって安定して支持される。また、インナ軸部材の外周面に突起部が押し付けられた状態において、当接力がインナ軸部材にバランスよく及ぼされることから、インナ軸部材が本体ゴム弾性体に対して位置決めされ易くなる。 According to the second aspect, since each protrusion comes into contact with the cylindrical outer peripheral surface that is formed into a true cylindrical shape, the inner shaft member is supported by the main rubber elastic body regardless of the direction in which the vibration in the direction perpendicular to the axis acts. It is supported stably. Further, in a state where the protrusion is pressed against the outer peripheral surface of the inner shaft member, the contact force is exerted on the inner shaft member in a balanced manner, so that the inner shaft member is easily positioned with respect to the main rubber elastic body.
　本発明の第三の態様は、第一の態様に記載された電気自動車用の筒形モータマウントにおいて、前記インナ軸部材の前記筒状外周面が楕円形断面を有しているものである。 A third aspect of the present invention is the cylindrical motor mount for an electric vehicle described in the first aspect, wherein the cylindrical outer peripheral surface of the inner shaft member has an elliptical cross section.
　第三の態様によれば、アウタ筒部材を加工や製造が容易な真円形断面としながら、インナ軸部材の長軸方向と短軸方向で本体ゴム弾性体の自由長を相互に異ならせることが可能となって、長軸方向と短軸方向のばね比を容易に設定することができる。 According to the third aspect, the free length of the main rubber elastic body can be made different between the major axis direction and the minor axis direction of the inner shaft member while making the outer cylinder member a perfect circular cross section that is easy to process and manufacture. This makes it possible to easily set the spring ratio between the major axis direction and the minor axis direction.
　本発明の第四の態様は、第一～第三の何れか１つの態様に記載された電気自動車用の筒形モータマウントにおいて、前記突起部の突出先端には軸方向に延びる凹部が形成されており、該凹部の内面に前記インナ軸部材の外周面が当接しているものである。 According to a fourth aspect of the present invention, in the cylindrical motor mount for an electric vehicle described in any one of the first to third aspects, a concave portion extending in the axial direction is formed at the projecting tip of the projecting portion. The inner peripheral surface of the inner shaft member is in contact with the inner surface of the recess.
　第四の態様によれば、インナ軸部材の筒状外周面が突起部の凹部によって受けられることで、突起部の先端部分がインナ軸部材に対して周方向で位置決めされ易くなって、インナ軸部材が本体ゴム弾性体によって安定して弾性支持されると共に、スティックスリップによる異音の発生なども防止され得る。 According to the fourth aspect, the cylindrical outer peripheral surface of the inner shaft member is received by the concave portion of the protruding portion, so that the tip portion of the protruding portion is easily positioned in the circumferential direction with respect to the inner shaft member. The member is stably elastically supported by the main rubber elastic body, and the generation of noise due to stick-slip can be prevented.
　本発明の第五の態様は、第一～第四の何れか１つの態様に記載された電気自動車用の筒形モータマウントにおいて、前記インナ軸部材が前記筒状外周面に開口する位置決め凹部を備えていると共に、前記突起部が突出先端から内周へ突出する位置決め凸部を備えており、該位置決め凸部が該位置決め凹部に差し入れられて該インナ軸部材が該突起部に対して位置決めされているものである。 According to a fifth aspect of the present invention, in the cylindrical motor mount for an electric vehicle described in any one of the first to fourth aspects, a positioning recess in which the inner shaft member opens on the cylindrical outer peripheral surface is provided. And the protrusion is provided with a positioning protrusion protruding from the protruding tip to the inner periphery, and the positioning protrusion is inserted into the positioning recess to position the inner shaft member with respect to the protrusion. It is what.
　第五の態様によれば、突起部の位置決め凸部がインナ軸部材の位置決め凹部に差し入れられることによって、突起部とインナ軸部材の相対的な位置が容易に規定される。また、例えば、位置決め凸部が位置決め凹部の内面に軸方向で係止されるようにすれば、インナ軸部材が本体ゴム弾性体に対して軸方向へ抜けるのを防ぐこともできる。 According to the fifth aspect, the relative position between the protrusion and the inner shaft member is easily defined by inserting the positioning protrusion of the protrusion into the positioning recess of the inner shaft member. Further, for example, if the positioning convex portion is locked to the inner surface of the positioning concave portion in the axial direction, the inner shaft member can be prevented from coming off in the axial direction with respect to the main rubber elastic body.
　本発明の第六の態様は、第一～第五の何れか１つの態様に記載された電気自動車用の筒形モータマウントにおいて、前記突起部の突出方向の弾性主軸が前記インナ軸部材の径方向に延びているものである。 According to a sixth aspect of the present invention, in the cylindrical motor mount for an electric vehicle described in any one of the first to fifth aspects, the elastic main shaft in the protruding direction of the protrusion is a diameter of the inner shaft member. It extends in the direction.
　第六の態様によれば、複数の突起部の当接力がインナ軸部材の径方向に作用することで、インナ軸部材にねじり方向のモーメントが作用し難く、インナ軸部材を複数の突起部の間で安定して支持することができる。 According to the sixth aspect, the contact force of the plurality of protrusions acts in the radial direction of the inner shaft member, so that the moment in the torsional direction is unlikely to act on the inner shaft member, and the inner shaft member is attached to the plurality of protrusions. It can be supported stably between.
　本発明の第七の態様は、第一～第六の何れか１つの態様に記載された電気自動車用の筒形モータマウントにおいて、径方向の共振周波数が８００Ｈｚ以上に設定されているものである。 A seventh aspect of the present invention is the cylindrical motor mount for an electric vehicle described in any one of the first to sixth aspects, wherein the radial resonance frequency is set to 800 Hz or more. .
　第七の態様によれば、反共振による高動ばね化が電気自動車において実用上で問題となる振動の周波数域よりも高周波において生じるように特性がチューニングされることで、電気自動車の実用周波数域において優れた低動ばね特性を実現することができる。 According to the seventh aspect, the characteristics are tuned so that the high dynamic spring due to anti-resonance is generated at a higher frequency than the frequency range of vibration that is practically problematic in an electric vehicle. It is possible to realize an excellent low dynamic spring characteristic.
　本発明の第八の態様は、インナ軸部材とアウタ筒部材が本体ゴム弾性体によって弾性連結された電気自動車用の筒形モータマウントの製造方法であって、（ｉ）前記本体ゴム弾性体を成形して前記アウタ筒部材の内周面に固着し、該アウタ筒部材から内周へ向けて突出する複数の突起部を該本体ゴム弾性体に形成する工程と、（ｉｉ）予め準備された前記インナ軸部材を該アウタ筒部材に固着された該本体ゴム弾性体の内周へ差し入れた後、該アウタ筒部材を縮径加工して、該本体ゴム弾性体の該複数の突起部の突出先端を該インナ軸部材の外周面に押し付ける工程とを、含むことを特徴とする。 An eighth aspect of the present invention is a method of manufacturing a cylindrical motor mount for an electric vehicle in which an inner shaft member and an outer cylindrical member are elastically connected by a main rubber elastic body, wherein (i) the main rubber elastic body is Forming a plurality of protrusions that are molded and fixed to the inner peripheral surface of the outer cylinder member and project from the outer cylinder member toward the inner periphery, and (ii) prepared in advance After the inner shaft member is inserted into the inner periphery of the main rubber elastic body fixed to the outer cylinder member, the outer cylinder member is reduced in diameter to project the plurality of protrusions of the main rubber elastic body And a step of pressing the tip against the outer peripheral surface of the inner shaft member.
　このような第八の態様に従う電気自動車用の筒形モータマウントの製造方法によれば、複数の突起部の内周にインナ軸部材を圧入する場合に比して、インナ軸部材を複数の突起部に対して適切な位置に配置し易い。しかも、複数の突起部がインナ軸部材の筒状外周面に摺接して曲がるように変形することがなく、例えば複数の突起部の突出先端をインナ軸部材の筒状外周面に突き当て易くなることから、インナ軸部材が複数の突起部によって適当な態様で安定して弾性支持される。 According to the method of manufacturing the cylindrical motor mount for an electric vehicle according to the eighth aspect, the inner shaft member has a plurality of protrusions as compared with the case where the inner shaft member is press-fitted into the inner periphery of the plurality of protrusions. It is easy to arrange at an appropriate position with respect to the part. In addition, the plurality of protrusions are not deformed so as to bend while being in sliding contact with the cylindrical outer peripheral surface of the inner shaft member. For example, the protruding tips of the plurality of protrusions are easily brought into contact with the cylindrical outer peripheral surface of the inner shaft member. Thus, the inner shaft member is stably elastically supported in an appropriate manner by the plurality of protrusions.
　本発明によれば、インナ軸部材が本体ゴム弾性体によって非固着で弾性支持されていることにより、軸直角方向の振動入力に対して本体ゴム弾性体に引張荷重が作用せず、本体ゴム弾性体の自由長を短く設定しながら耐久性を十分に確保することが可能となることから、本体ゴム弾性体を含んで構成されるインナ軸部材側の実質的なマス質量が小さくなる。しかも、本体ゴム弾性体の突起部がインナ軸部材側に向けて先細とされていることによっても、本体ゴム弾性体においてインナ軸部材側のマス質量に寄与する部分のゴムボリュームが小さくなる。その結果、本体ゴム弾性体の耐久性を十分に確保しながら、筒形モータマウントの共振周波数をより高周波に設定し易くなって、電気自動車の実用周波数域において、反共振による著しい高動ばね化を防いで、低動ばね特性による防振性能を得ることができる。 According to the present invention, since the inner shaft member is elastically supported by the main rubber elastic body in a non-fixed manner, a tensile load does not act on the main rubber elastic body with respect to vibration input in the direction perpendicular to the axis, and the main rubber elasticity Since the durability can be sufficiently secured while setting the free length of the body short, the substantial mass on the inner shaft member side including the main rubber elastic body is reduced. Moreover, even when the protrusion of the main rubber elastic body is tapered toward the inner shaft member side, the rubber volume of the portion of the main rubber elastic body contributing to the mass of the inner shaft member is reduced. As a result, it is easy to set the resonance frequency of the cylindrical motor mount to a higher frequency while ensuring the durability of the main rubber elastic body sufficiently. Therefore, it is possible to obtain an anti-vibration performance with low dynamic spring characteristics.
本発明の第一の実施形態としての電気自動車用の筒形モータマウントの正面図。BRIEF DESCRIPTION OF THE DRAWINGS The front view of the cylindrical motor mount for electric vehicles as 1st embodiment of this invention. 図１のＩＩ－ＩＩ断面図。II-II sectional drawing of FIG. 図１に示す筒形モータマウントを構成する一体加硫成形品の正面図。The front view of the integral vulcanization molded product which comprises the cylindrical motor mount shown in FIG. 図３のＩＶ－ＩＶ断面図。IV-IV sectional drawing of FIG. 図３に示す一体加硫成形品の内周へインナ軸部材を差し入れた状態を示す正面図。The front view which shows the state which inserted the inner shaft member to the inner periphery of the integral vulcanization molded product shown in FIG. 本発明の第二の実施形態としての電気自動車用の筒形モータマウントの正面図。The front view of the cylindrical motor mount for electric vehicles as 2nd embodiment of this invention. 図６に示す筒形モータマウントを構成する一体加硫成形品の正面図。The front view of the integral vulcanization molded product which comprises the cylindrical motor mount shown in FIG. 本発明の第三の実施形態としての電気自動車用の筒形モータマウントの正面図。The front view of the cylindrical motor mount for electric vehicles as 3rd embodiment of this invention. 図８のＩＸ－ＩＸ断面図。IX-IX sectional view of FIG. 図８に示す筒形モータマウントを構成する一体加硫成形品の正面図。The front view of the integral vulcanization molded product which comprises the cylindrical motor mount shown in FIG. 図１０に示す一体加硫成形品の内周へインナ軸部材を差し入れた状態を示す正面図。The front view which shows the state which inserted the inner shaft member to the inner periphery of the integral vulcanization molded product shown in FIG. 図１１のＸＩＩ－ＸＩＩ断面図。XII-XII sectional view of FIG. 本発明の第四の実施形態としての電気自動車用の筒形モータマウントの正面図。The front view of the cylindrical motor mount for electric vehicles as 4th embodiment of this invention. 図１３に示す筒形モータマウントを構成する一体加硫成形品の内周へインナ軸部材を差し入れた状態を示す正面図。The front view which shows the state which inserted the inner shaft member to the inner periphery of the integral vulcanization molded product which comprises the cylindrical motor mount shown in FIG.
　以下、本発明の実施形態について、図面を参照しつつ説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
　図１，２には、本発明の第一の実施形態として、電気自動車用の筒形モータマウント１０を示す。筒形モータマウント１０は、インナ軸部材１２とアウタ筒部材１４が、本体ゴム弾性体１６によって相互に弾性連結された構造を有している。以下の説明では、原則として、上下方向とは図１中の上下方向を、左右方向とは図１中の左右方向を、前後方向とは図１中の紙面直交方向を、それぞれいう。 1 and 2 show a cylindrical motor mount 10 for an electric vehicle as a first embodiment of the present invention. The cylindrical motor mount 10 has a structure in which an inner shaft member 12 and an outer cylindrical member 14 are elastically connected to each other by a main rubber elastic body 16. In the following description, in principle, the vertical direction refers to the vertical direction in FIG. 1, the horizontal direction refers to the horizontal direction in FIG. 1, and the front-rear direction refers to the direction perpendicular to the plane of FIG.
　より詳細には、インナ軸部材１２は、金属などで形成された高剛性の部材であって、厚肉小径の略円筒形状を有している。また、インナ軸部材１２の筒状外周面１８は、横断面において略真円形とされており、略一定の断面形状で前後方向に直線的に延びる真円筒状とされている。なお、本実施形態では、インナ軸部材１２の内周面も横断面において略真円形とされている。 More specifically, the inner shaft member 12 is a highly rigid member made of metal or the like, and has a substantially cylindrical shape with a thick and small diameter. Moreover, the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a substantially perfect circle shape in the cross section, and has a substantially cylindrical shape extending in the front-rear direction with a substantially constant cross-sectional shape. In the present embodiment, the inner peripheral surface of the inner shaft member 12 is also substantially circular in cross section.
　アウタ筒部材１４は、金属などで形成された高剛性の部材であって、薄肉大径の略円筒形状を有している。本実施形態のアウタ筒部材１４は、内周面が横断面において略真円形とされており、略一定の断面形状で前後方向に直線的に延びている。また、アウタ筒部材１４の外周面は、軸方向中央部分が略真円形の横断面形状で前後方向に直線的に延びていると共に、軸方向両端部分が軸方向外側に向けて次第に小径となるテーパ面とされている。なお、アウタ筒部材１４は、インナ軸部材１２よりも軸方向寸法が小さくされている。 The outer cylinder member 14 is a highly rigid member made of metal or the like, and has a thin cylindrical shape with a large diameter. The outer cylindrical member 14 of the present embodiment has an inner peripheral surface that is substantially circular in cross section, and linearly extends in the front-rear direction with a substantially constant cross-sectional shape. In addition, the outer peripheral surface of the outer cylindrical member 14 has a substantially circular cross-sectional shape in the axial center and linearly extends in the front-rear direction, and both end portions in the axial direction gradually become smaller in diameter toward the outer side in the axial direction. It is a tapered surface. The outer cylinder member 14 has a smaller axial dimension than the inner shaft member 12.
　アウタ筒部材１４は、好適には外径寸法が７５ｍｍ以下とされている。更に、好適には、アウタ筒部材１４の内径寸法とインナ軸部材１２の外径寸法との差が４５ｍｍ以下とされていると共に、アウタ筒部材１４の内径寸法のインナ軸部材１２の外径寸法に対する比が４以下とされている。本実施形態では、例えば、アウタ筒部材１４の外径寸法が６０ｍｍ、アウタ筒部材１４の内径寸法とインナ軸部材１２の外径寸法との差が３５ｍｍとされている。 The outer cylinder member 14 preferably has an outer diameter of 75 mm or less. Further, preferably, the difference between the inner diameter dimension of the outer cylindrical member 14 and the outer diameter dimension of the inner shaft member 12 is 45 mm or less, and the outer diameter dimension of the inner shaft member 12 is equal to the inner diameter dimension of the outer cylindrical member 14. The ratio is 4 or less. In the present embodiment, for example, the outer diameter of the outer cylinder member 14 is 60 mm, and the difference between the inner diameter of the outer cylinder member 14 and the outer diameter of the inner shaft member 12 is 35 mm.
　また、図３，４に示すように、アウタ筒部材１４の内周面には、本体ゴム弾性体１６が加硫接着されている。本体ゴム弾性体１６は、アウタ筒部材１４の内周面に被着形成された外周ゴム層２０と、外周ゴム層２０から内周へ向けて突出する４つの突起部２２，２２，２２，２２とを、備えている。本実施形態では、本体ゴム弾性体１６がアウタ筒部材１４を備える一体加硫成形品２４として形成されている。 3 and 4, the main rubber elastic body 16 is vulcanized and bonded to the inner peripheral surface of the outer cylinder member 14. The main rubber elastic body 16 includes an outer peripheral rubber layer 20 formed on the inner peripheral surface of the outer cylinder member 14 and four protrusions 22, 22, 22, 22 protruding from the outer peripheral rubber layer 20 toward the inner periphery. And has. In this embodiment, the main rubber elastic body 16 is formed as an integrally vulcanized molded product 24 including the outer cylinder member 14.
　外周ゴム層２０は、薄肉筒状とされて、アウタ筒部材１４の内周面を全周に亘って覆っている。また、外周ゴム層２０の軸方向寸法は、アウタ筒部材１４の軸方向寸法よりも小さくされていると共に、突起部２２の軸方向寸法よりも大きくされており、外周ゴム層２０は、好適には１ｍｍ以上の厚さを有している。 The outer peripheral rubber layer 20 has a thin cylindrical shape and covers the inner peripheral surface of the outer cylindrical member 14 over the entire circumference. In addition, the axial dimension of the outer peripheral rubber layer 20 is smaller than the axial dimension of the outer cylindrical member 14 and larger than the axial dimension of the protruding portion 22. Has a thickness of 1 mm or more.
　突起部２２は、上下左右の４か所にそれぞれ設けられており、それぞれアウタ筒部材１４から内周へ向けて突出していると共に、突出先端２６に向けて周方向で狭幅となる先細形状を有して、突出方向と直交する平面上での断面積が基端から突出先端２６に向けて小さくなっている。本実施形態の４つの突起部２２，２２，２２，２２は、互いに略同一形状とされている。 The projecting portions 22 are provided at four locations on the top, bottom, left, and right, respectively, projecting from the outer cylindrical member 14 toward the inner periphery, and having a tapered shape that narrows in the circumferential direction toward the projecting tip 26. And the cross-sectional area on the plane perpendicular to the protruding direction is reduced from the base end toward the protruding tip 26. The four protrusions 22, 22, 22, 22 of the present embodiment have substantially the same shape.
　本実施形態の突起部２２は、図３に示すように、周方向外側に向けて凹形状となる基端湾曲面２８と、周方向外側に向けて凸形状となる先端湾曲面３０とを、連続的に設けることで周方向側面が構成されており、基端湾曲面２８の両端が外周ゴム層２０の内周面と先端湾曲面３０との各一方に滑らかに連続している。このように突起部２２の周方向側面が基端湾曲面２８と先端湾曲面３０によって構成されていることで、突起部２２は、基端部分において断面積が突出先端２６に向けて大きな変化量で小さくなっていると共に、先端部分において突出先端２６に向けて漸変的に断面積の変化量が大きくなっている。更に、突起部２２の突出方向の中間部分では、断面積の変化量が小さくなっている。なお、先端湾曲面３０，３０を備える半円状断面の先端部分は、突起部２２の突出寸法の１／４以上、より好適には１／３以上の部分を占めるようにされており、筒形モータマウント１０における共振周波数の高周波化や低動ばね化が図られている。 As shown in FIG. 3, the protruding portion 22 of the present embodiment includes a proximal curved surface 28 that is concave toward the outer side in the circumferential direction and a distal curved surface 30 that is convex toward the outer side in the circumferential direction. The circumferential side surfaces are formed by providing them continuously, and both ends of the base end curved surface 28 are smoothly continuous with each of the inner peripheral surface of the outer peripheral rubber layer 20 and the distal end curved surface 30. Thus, since the circumferential side surface of the protrusion 22 is configured by the proximal curved surface 28 and the distal curved surface 30, the protrusion 22 has a large change amount in cross-sectional area toward the projected distal end 26 at the proximal end portion. In addition, the amount of change in the cross-sectional area gradually increases toward the projecting tip 26 at the tip portion. Furthermore, the amount of change in the cross-sectional area is small at the intermediate portion of the protruding portion 22 in the protruding direction. The tip portion of the semicircular cross section provided with the tip curved surfaces 30, 30 occupies 1/4 or more, more preferably 1/3 or more of the projecting dimension of the protrusion 22, In the motor mount 10, the resonance frequency is increased and the dynamic spring is reduced.
　さらに、突起部２２は、図４に示すように、略一定の軸方向寸法で径方向に延びていると共に、外周ゴム層２０に比して軸方向寸法が小さくされている。なお、突起部２２の軸方向端面は、外周端部において内周へ向けて軸方向内側へ傾斜する凹状湾曲面とされていると共に、内周端部において内周へ向けて軸方向内側へ傾斜する凸状湾曲面とされており、外周端部が外周ゴム層２０の内周面に滑らかに連続していると共に、内周端部が突起部２２の先端面に滑らかに連続している。 Further, as shown in FIG. 4, the protrusion 22 extends in the radial direction with a substantially constant axial dimension, and has a smaller axial dimension than the outer peripheral rubber layer 20. The axial end surface of the protrusion 22 is a concave curved surface that inclines inward in the axial direction toward the inner periphery at the outer peripheral end, and inward in the axial direction toward the inner periphery at the inner peripheral end. The outer peripheral end is smoothly continuous with the inner peripheral surface of the outer peripheral rubber layer 20, and the inner peripheral end is smoothly continuous with the distal end surface of the protrusion 22.
　更にまた、各突起部２２の突出方向の弾性主軸は、何れもアウタ筒部材１４の径方向に延びている。本実施形態では、２つの突起部２２，２２の弾性主軸が上下方向に延びていると共に、２つの突起部２２，２２の弾性主軸が左右方向に延びている。 Furthermore, the elastic main shaft in the protruding direction of each protrusion 22 extends in the radial direction of the outer cylindrical member 14. In the present embodiment, the elastic main axes of the two protrusions 22 and 22 extend in the vertical direction, and the elastic main axes of the two protrusions 22 and 22 extend in the left-right direction.
　本実施形態では、周方向で隣り合って配された２つの突起部２２，２２は、全体が周方向で相互に離れており、例えば、基端部において周方向に５ｍｍ以上、より好適には１０ｍｍ以上離れている。また、突起部２２の突出寸法は、外周ゴム層２０の内径寸法の半分よりも小さくされており、本実施形態では外周ゴム層２０の内径寸法の１／３程度とされている。これにより、前後両側の突起部２２，２２および左右両側の突起部２２，２２は、それぞれ径方向で相互に離れて向き合うように配置されている。 In the present embodiment, the two protrusions 22, 22 arranged adjacent to each other in the circumferential direction are separated from each other in the circumferential direction, for example, 5 mm or more in the circumferential direction at the base end, more preferably 10 mm or more away. Further, the projecting dimension of the protruding portion 22 is smaller than half of the inner diameter dimension of the outer peripheral rubber layer 20, and in this embodiment is about １ ／ of the inner diameter dimension of the outer peripheral rubber layer 20. Thereby, the protrusion parts 22 and 22 on both the front and rear sides and the protrusion parts 22 and 22 on both the left and right sides are arranged so as to face each other in the radial direction.
　４つの突起部２２，２２，２２，２２は、外周ゴム層２０を介してアウタ筒部材１４に固着されており、突起部２２，２２，２２，２２が大きな固着面積でアウタ筒部材１４に固着されている。更に、突起部２２の基端部は、全周囲に向かって滑らかな湾曲状に広がっており、アウタ筒部材１４の内周面を略全面に亘って一定の厚さ寸法で覆う外周ゴム層２０に対して一体化されている。また、突起部２２の軸方向寸法と周方向寸法が小さくされており、それらの寸法は突起部２２の応力や変形が他の突起部２２や外周ゴム層２０に実質的に伝達されない大きさとされている。 The four protrusions 22, 22, 22, 22 are fixed to the outer cylinder member 14 via the outer peripheral rubber layer 20, and the protrusions 22, 22, 22, 22 are fixed to the outer cylinder member 14 with a large fixing area. Has been. Further, the base end portion of the protruding portion 22 spreads in a smooth curved shape toward the entire periphery, and the outer peripheral rubber layer 20 covers the inner peripheral surface of the outer cylindrical member 14 with a constant thickness over substantially the entire surface. Are integrated. In addition, the axial dimension and the circumferential dimension of the protrusion 22 are reduced, and these dimensions are such that the stress and deformation of the protrusion 22 are not substantially transmitted to the other protrusions 22 and the outer rubber layer 20. ing.
　そして、アウタ筒部材１４の内周面に固着された本体ゴム弾性体１６の内周に、インナ軸部材１２が挿通された状態で、本体ゴム弾性体１６の４つの突起部２２，２２，２２，２２の各突出先端２６がインナ軸部材１２の筒状外周面１８に非固着で押し付けられることにより、インナ軸部材１２が本体ゴム弾性体１６によって弾性支持されている。これにより、インナ軸部材１２とアウタ筒部材１４が本体ゴム弾性体１６によって弾性連結された筒形モータマウント１０が構成されている。 The four protrusions 22, 22, 22 of the main rubber elastic body 16 are inserted in the inner periphery of the main rubber elastic body 16 fixed to the inner peripheral surface of the outer cylinder member 14. , 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12 in a non-fixed manner, so that the inner shaft member 12 is elastically supported by the main rubber elastic body 16. Thereby, the cylindrical motor mount 10 in which the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 16 is configured.
　インナ軸部材１２の筒状外周面１８が円形断面を有していると共に、突起部２２が突出先端２６に向けて周方向で狭幅となる先細形状とされていることから、突起部２２の突出先端２６におけるインナ軸部材１２に対する当接面積は、静置状態において非常に小さくされている。具体的には、例えば、突起部２２の基端部分における突出方向と直交する平面上での断面積に対して１／１０以下とされている。 The cylindrical outer peripheral surface 18 of the inner shaft member 12 has a circular cross section, and the protrusion 22 has a tapered shape that becomes narrower in the circumferential direction toward the protrusion tip 26. The contact area of the protruding tip 26 against the inner shaft member 12 is very small in the stationary state. Specifically, for example, it is 1/10 or less with respect to the cross-sectional area on the plane orthogonal to the protruding direction at the base end portion of the protrusion 22.
　これにより、本実施形態に係る筒形モータマウント１０は、インナ軸部材１２側をマス、本体ゴム弾性体１６をばねとするマス－バネ系の径方向の共振周波数が、８００Ｈｚ以上の高周波に設定されている。これにより、筒形モータマウント１０は、マス－バネ系の反共振に起因する高動ばね化が８００Ｈｚよりも高周波において生じるようになっている。 Thereby, in the cylindrical motor mount 10 according to the present embodiment, the radial resonance frequency of the mass-spring system in which the inner shaft member 12 side is a mass and the main rubber elastic body 16 is a spring is set to a high frequency of 800 Hz or more. Has been. As a result, the cylindrical motor mount 10 is made to have a high dynamic spring due to the anti-resonance of the mass-spring system at a frequency higher than 800 Hz.
　なお、筒形モータマウント１０は、好適には、例えば、以下の如き製造方法によって製造され得る。 The cylindrical motor mount 10 can be preferably manufactured by the following manufacturing method, for example.
　先ず、予め準備したアウタ筒部材１４を本体ゴム弾性体１６の成形用金型にセットして、外周ゴム層２０と複数の突起部２２とを備える本体ゴム弾性体１６を、アウタ筒部材１４の内周面に固着された状態で加硫成形する。これにより、アウタ筒部材１４の内周面を本体ゴム弾性体１６の外周ゴム層２０で覆うと共に、複数の突起部２２をアウタ筒部材１４から内周へ突出するように形成する。 First, the outer cylindrical member 14 prepared in advance is set in a molding die for the main rubber elastic body 16, and the main rubber elastic body 16 including the outer peripheral rubber layer 20 and the plurality of protrusions 22 is attached to the outer cylindrical member 14. Vulcanization molding is performed with the inner peripheral surface fixed. Thus, the inner peripheral surface of the outer cylindrical member 14 is covered with the outer peripheral rubber layer 20 of the main rubber elastic body 16, and a plurality of protrusions 22 are formed so as to protrude from the outer cylindrical member 14 to the inner periphery.
　次に、図５に示すように、予め準備したインナ軸部材１２をアウタ筒部材１４に固着された本体ゴム弾性体１６の内周へ差し入れる。本実施形態では、前後方向又は左右方向で向かい合わせに配置された突起部２２，２２の突出先端２６，２６間の距離が、インナ軸部材１２の外径寸法よりも大きくされており、インナ軸部材１２が突起部２２，２２の間で締め込まれることなく隙間をもって差し入れられる。なお、本体ゴム弾性体１６の一体加硫成形品２４とインナ軸部材１２は、例えば後述する縮径加工用の治具にそれぞれセットされることにより、相互に位置決めされた状態で保持される。 Next, as shown in FIG. 5, the inner shaft member 12 prepared in advance is inserted into the inner periphery of the main rubber elastic body 16 fixed to the outer cylinder member 14. In the present embodiment, the distance between the projecting tips 26, 26 of the projecting portions 22, 22 arranged facing each other in the front-rear direction or the left-right direction is made larger than the outer diameter dimension of the inner shaft member 12, and the inner shaft The member 12 is inserted between the protrusions 22 and 22 with a gap therebetween. The integrally vulcanized molded product 24 of the main rubber elastic body 16 and the inner shaft member 12 are held in a mutually positioned state by being set, for example, in a jig for diameter reduction processing described later.
　また次に、インナ軸部材１２が本体ゴム弾性体１６に内挿された状態で、アウタ筒部材１４に八方絞りなどの縮径加工を施す。そして、アウタ筒部材１４の内周面に固着された本体ゴム弾性体１６をアウタ筒部材１４とともに縮径して、本体ゴム弾性体１６の突起部２２の突出先端２６をインナ軸部材１２の筒状外周面１８に押し付ける。これにより、インナ軸部材１２を複数の突起部２２によって弾性支持して、インナ軸部材１２とアウタ筒部材１４を本体ゴム弾性体１６によって弾性連結し、筒形モータマウント１０を得る。 Next, in the state where the inner shaft member 12 is inserted into the main rubber elastic body 16, the outer cylinder member 14 is subjected to diameter reduction processing such as eight-way drawing. The main rubber elastic body 16 fixed to the inner peripheral surface of the outer cylinder member 14 is reduced in diameter together with the outer cylinder member 14, and the protruding tip 26 of the protrusion 22 of the main rubber elastic body 16 is connected to the cylinder of the inner shaft member 12. The outer peripheral surface 18 is pressed. As a result, the inner shaft member 12 is elastically supported by the plurality of protrusions 22, and the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 16 to obtain the cylindrical motor mount 10.
　なお、筒形モータマウント１０において、インナ軸部材１２とアウタ筒部材１４が同軸的に配されていることから、各突起部２２の突出方向の弾性主軸は、インナ軸部材１２の径方向に延びており、各突起部２２は、突出先端２６がインナ軸部材１２の筒状外周面１８に押し付けられることで突出方向に圧縮されている。本実施形態では、４つの突起部２２，２２，２２，２２がインナ軸部材１２に対して上下両側と左右両側から径方向で押し付けられていることから、インナ軸部材１２に作用する当接力が相殺されており、インナ軸部材１２が当接力によって径方向でずれるのが防止されている。 In the cylindrical motor mount 10, since the inner shaft member 12 and the outer cylindrical member 14 are coaxially arranged, the elastic main shaft in the protruding direction of each protrusion 22 extends in the radial direction of the inner shaft member 12. Each projecting portion 22 is compressed in the projecting direction by the projecting tip 26 being pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12. In the present embodiment, the four projecting portions 22, 22, 22, 22 are pressed against the inner shaft member 12 in the radial direction from both the upper and lower sides and the left and right sides, so that the contact force acting on the inner shaft member 12 is exerted. The inner shaft member 12 is prevented from shifting in the radial direction by the contact force.
　かくの如き構造とされた筒形モータマウント１０は、図２に示すように、インナ軸部材１２が図示しないボルトなどによってモータ３２に取り付けられると共に、アウタ筒部材１４がサブフレームに圧入固定されるなどして車両ボデー３４に取り付けられる。これにより、モータ３２が車両ボデー３４に対して筒形モータマウント１０を介して防振連結されるようになっている。 In the cylindrical motor mount 10 having such a structure, as shown in FIG. 2, the inner shaft member 12 is attached to the motor 32 by a bolt or the like (not shown), and the outer cylindrical member 14 is press-fitted and fixed to the subframe. For example, it is attached to the vehicle body 34. As a result, the motor 32 is connected to the vehicle body 34 with vibration isolation via the cylindrical motor mount 10.
　なお、図中では、インナ軸部材１２がモータ３２に直接的に取り付けられた構造が示されているが、例えば、インナ軸部材１２とモータ３２が図示しないブラケットを介して相互に取り付けられるようにしても良い。 In the drawing, the inner shaft member 12 is directly attached to the motor 32. For example, the inner shaft member 12 and the motor 32 are attached to each other via a bracket (not shown). May be.
　このような本実施形態に従う構造とされた筒形モータマウント１０によれば、振動が入力されて、インナ軸部材１２とアウタ筒部材１４が径方向で相対的に変位しても、インナ軸部材１２と本体ゴム弾性体１６が固着されておらず、本体ゴム弾性体１６に対して引張応力が作用することがない。それ故、本体ゴム弾性体１６に亀裂などの損傷などが生じ難く、本体ゴム弾性体１６の耐久性の向上が図られる。 According to the cylindrical motor mount 10 having the structure according to this embodiment, even if vibration is input and the inner shaft member 12 and the outer cylindrical member 14 are relatively displaced in the radial direction, the inner shaft member 12 and the main rubber elastic body 16 are not fixed, and no tensile stress acts on the main rubber elastic body 16. Therefore, the main rubber elastic body 16 is hardly damaged such as a crack, and the durability of the main rubber elastic body 16 can be improved.
　また、インナ軸部材１２と本体ゴム弾性体１６が非固着とされることで本体ゴム弾性体１６の耐久性が確保されることから、本体ゴム弾性体１６の径方向の自由長を短く設定することができる。それ故、インナ軸部材１２側のマス質量に寄与する本体ゴム弾性体１６のゴムボリュームを小さくすることができて、インナ軸部材１２側の実質的なマス質量が軽減されることによって、筒形モータマウント１０の共振周波数をより高周波にチューニングすることが可能となる。 Further, since the durability of the main rubber elastic body 16 is ensured by the inner shaft member 12 and the main rubber elastic body 16 being not fixed, the radial free length of the main rubber elastic body 16 is set short. be able to. Therefore, the rubber volume of the main rubber elastic body 16 that contributes to the mass mass on the inner shaft member 12 side can be reduced, and the substantial mass mass on the inner shaft member 12 side is reduced. It becomes possible to tune the resonance frequency of the motor mount 10 to a higher frequency.
　さらに、本体ゴム弾性体１６のインナ軸部材１２に対する当接部分が、複数の突起部２２とされており、インナ軸部材１２側となる本体ゴム弾性体１６の内周部分のゴムボリュームが小さくされていることから、本体ゴム弾性体１６の寄与によるインナ軸部材１２側のマス質量の増大が抑えられて、筒形モータマウント１０の共振周波数を高周波に設定し易い。 Further, the abutting portions of the main rubber elastic body 16 with respect to the inner shaft member 12 are formed as a plurality of protrusions 22, and the rubber volume of the inner peripheral portion of the main rubber elastic body 16 on the inner shaft member 12 side is reduced. Therefore, an increase in mass of the inner shaft member 12 due to the contribution of the main rubber elastic body 16 is suppressed, and the resonance frequency of the cylindrical motor mount 10 can be easily set to a high frequency.
　しかも、突起部２２が突出先端２６に向けて先細とされて、インナ軸部材１２に押し付けられる突起部２２の先端部分のゴムボリュームが一層小さくされていることから、本体ゴム弾性体１６の寄与によるインナ軸部材１２側のマス質量の増大が更に抑えられており、筒形モータマウント１０の共振周波数を高周波に設定し易くなっている。 In addition, the protrusion 22 is tapered toward the protrusion tip 26, and the rubber volume at the tip of the protrusion 22 pressed against the inner shaft member 12 is further reduced. An increase in mass of the inner shaft member 12 is further suppressed, and the resonance frequency of the cylindrical motor mount 10 can be easily set to a high frequency.
　加えて、本実施形態では、インナ軸部材１２の筒状外周面１８が外周に向けて凸となる湾曲形状とされていると共に、突起部２２の突出先端２６が内周に向けて凸となる湾曲形状とされていることから、インナ軸部材１２の筒状外周面１８に対する突起部２２の当接面積が小さくされている。これにより、インナ軸部材１２とアウタ筒部材１４の相対変位量が小さい状態において柔らかいばね特性が実現されると共に、突起部２２の先端部分がインナ軸部材１２側のマス質量に寄与し難くなっており、筒形モータマウント１０の共振周波数を高周波に設定し易くなっている。 In addition, in this embodiment, the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a curved shape that is convex toward the outer periphery, and the protruding tip 26 of the protrusion 22 is convex toward the inner periphery. Because of the curved shape, the contact area of the protrusion 22 with the cylindrical outer peripheral surface 18 of the inner shaft member 12 is reduced. As a result, a soft spring characteristic is realized in a state where the relative displacement between the inner shaft member 12 and the outer cylinder member 14 is small, and the tip portion of the protrusion 22 is less likely to contribute to the mass of the inner shaft member 12 side. Thus, it is easy to set the resonance frequency of the cylindrical motor mount 10 to a high frequency.
　これらにより、筒形モータマウント１０は、共振現象（反共振）による高動ばね化が生じる周波数域をより高周波に設定することが可能とされており、電気自動車において高周波域まで低動ばね特性を要求される場合にも対応することができる。特に本実施形態では、筒形モータマウント１０の径方向の共振周波数が８００Ｈｚ以上の高周波にチューニングされており、反共振による高動ばね化が電気自動車の実用上で問題となり難いほどの高周波域において生じるようになっていることから、電気自動車において問題となる振動の周波数域では低動ばねによる防振性能を有効に得ることができる。 As a result, the cylindrical motor mount 10 can set a higher frequency range in which high dynamic springs due to a resonance phenomenon (anti-resonance) occur, and low dynamic spring characteristics up to a high frequency range in an electric vehicle. It is possible to respond to demands. In particular, in the present embodiment, the radial resonance frequency of the cylindrical motor mount 10 is tuned to a high frequency of 800 Hz or more, and in a high frequency region where high dynamic springs due to anti-resonance are unlikely to be a problem in practical use of an electric vehicle. As a result, it is possible to effectively obtain the vibration isolation performance by the low dynamic spring in the frequency range of the vibration which is a problem in the electric vehicle.
　また、本実施形態では、突起部２２の基端部分が基端側に向けて周方向で幅広となっていることから、突起部２２の変形安定性や耐久性の確保が実現されている。更に、突起部２２は、突出方向において軸方向寸法が略一定とされているとともに周方向寸法が変化していることから、こじり方向の支持ばねを確保しつつ、軸直角方向の共振周波数の高周波化が図られている。また、突起部２２が外周ゴム層２０と一体形成されており、外周ゴム層２０を介してアウタ筒部材１４に固着されていることにより、突起部２２のアウタ筒部材１４に対する固着強度を大きく得ることができる。更にまた、外周ゴム層２０の厚さ寸法が１ｍｍ以上とされていることにより、突起部２２の基端部における応力分散も図られている。 Further, in the present embodiment, since the base end portion of the protrusion 22 is wider in the circumferential direction toward the base end, it is possible to ensure deformation stability and durability of the protrusion 22. Further, the protrusion 22 has a substantially constant axial dimension in the projecting direction and a circumferential dimension that changes, so that a high-frequency resonance frequency in the direction perpendicular to the axis is secured while securing a support spring in the twisting direction. It is planned. Further, the protruding portion 22 is formed integrally with the outer peripheral rubber layer 20 and is fixed to the outer cylinder member 14 via the outer peripheral rubber layer 20, whereby the fixing strength of the protruding portion 22 to the outer cylindrical member 14 is increased. be able to. Furthermore, since the thickness of the outer peripheral rubber layer 20 is 1 mm or more, the stress distribution at the base end portion of the protrusion 22 is also achieved.
　さらに、筒形モータマウント１０は、反共振による高動ばね化が生じる周波数域がより高周波に設定されていることにより、例えば加減速などによって予め入力される荷重が変化しても、振動に対して低動ばね特性に基づいた防振性能が安定して発揮される。即ち、一般的に、停車時や略一定速度での安定走行時のように予め入力される荷重が比較的に小さい状態では、本体ゴム弾性体１６の弾性変形量が比較的に小さいことから、振動入力に対する低動ばね特性が有効に発揮される一方、加減速などによって大きな荷重が入力されると、本体ゴム弾性体１６が予め大きく弾性変形せしめられることから、その状態で振動が入力されると、荷重が小さい場合に比して硬いばね特性（高動ばね特性）が発揮され易い。ここにおいて、本実施形態の筒形モータマウント１０では、反共振による高動ばね化が電気自動車において問題となる振動の周波数域よりも高周波において生じることから、ばね特性が比較的に硬くなる大きな予荷重が入力された状態においても、低動ばね特性による防振効果が有効に発揮される。具体的には、例えば、筒形モータマウント１０を採用することにより、８００Ｈｚ以下の周波数域において、予荷重の変化に関わらず１５００Ｎ／ｍｍ以下の動的ばね定数を維持させることも可能となる。 Furthermore, the cylindrical motor mount 10 has a higher frequency range in which high dynamic springs due to anti-resonance are generated, so that even if the input load changes in advance due to acceleration / deceleration, the cylindrical motor mount 10 is resistant to vibration. In addition, the anti-vibration performance based on the low dynamic spring characteristics is stably exhibited. That is, generally, when the load input in advance is relatively small, such as when the vehicle is stopped or at a stable running at a substantially constant speed, the elastic deformation amount of the main rubber elastic body 16 is relatively small. While the low dynamic spring characteristic with respect to vibration input is effectively exhibited, when a large load is input by acceleration / deceleration or the like, the main rubber elastic body 16 is largely elastically deformed in advance, so that vibration is input in that state. As compared with a case where the load is small, hard spring characteristics (high dynamic spring characteristics) are easily exhibited. Here, in the cylindrical motor mount 10 of the present embodiment, the high dynamic spring due to anti-resonance occurs at a higher frequency than the frequency range of vibrations that is a problem in an electric vehicle. Even in a state where a load is input, the vibration isolation effect due to the low dynamic spring characteristic is effectively exhibited. Specifically, for example, by adopting the cylindrical motor mount 10, it is possible to maintain a dynamic spring constant of 1500 N / mm or less in a frequency range of 800 Hz or less regardless of a change in preload.
　また、インナ軸部材１２の筒状外周面１８の断面形状が略真円形とされていることから、アウタ筒部材１４を全周に亘って縮径加工して、４つの突起部２２，２２，２２，２２をインナ軸部材１２の筒状外周面１８に押し付ける際に、インナ軸部材１２の位置ずれが生じ難い。 In addition, since the cross-sectional shape of the cylindrical outer peripheral surface 18 of the inner shaft member 12 is a substantially circular shape, the outer cylindrical member 14 is reduced in diameter over the entire circumference, and the four protrusions 22, 22, When pressing 22, 22 against the cylindrical outer peripheral surface 18 of the inner shaft member 12, it is difficult for the inner shaft member 12 to be displaced.
　さらに、インナ軸部材１２の筒状外周面１８が略真円形断面を有していると共に、４つの突起部２２，２２，２２，２２が周方向でバランスよく配されていることによって、筒形モータマウント１０に対する径方向の振動入力時にインナ軸部材１２が安定して弾性支持される。 Further, the cylindrical outer peripheral surface 18 of the inner shaft member 12 has a substantially perfect circular cross section, and the four protrusions 22, 22, 22, 22 are arranged in a balanced manner in the circumferential direction, thereby forming a cylindrical shape. The inner shaft member 12 is stably elastically supported when a radial vibration is input to the motor mount 10.
　更にまた、４つの突起部２２，２２，２２，２２がインナ軸部材１２の筒状外周面１８に上下両側および左右両側から押し付けられており、各突起部２２の弾性主軸がインナ軸部材１２の径方向に延びている。それ故、４つの突起部２２，２２，２２，２２がインナ軸部材１２の筒状外周面１８に押し付けられる際に、インナ軸部材１２の位置ずれが生じ難く、インナ軸部材１２が安定して弾性支持されると共に、振動入力時にもインナ軸部材１２が安定した弾性支持状態に保持される。 Furthermore, the four protrusions 22, 22, 22, 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12 from both the upper and lower sides and the left and right sides, and the elastic main shaft of each protrusion 22 is the inner shaft member 12. It extends in the radial direction. Therefore, when the four protrusions 22, 22, 22, 22 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12, the inner shaft member 12 is not easily displaced, and the inner shaft member 12 is stable. While being elastically supported, the inner shaft member 12 is held in a stable elastic support state even when vibration is input.
　図６には、本発明の第二の実施形態としての電気自動車用の筒形モータマウント４０を示す。筒形モータマウント４０は、インナ軸部材１２が本体ゴム弾性体４２の一体加硫成形品４４に非固着で取り付けられて、インナ軸部材１２とアウタ筒部材１４が本体ゴム弾性体４２によって弾性連結された構造を有している。以下の説明において、第一の実施形態と実質的に同一の部位および部材には、図中に同一の符号を付すことにより、説明を省略する。 FIG. 6 shows a cylindrical motor mount 40 for an electric vehicle as a second embodiment of the present invention. In the cylindrical motor mount 40, the inner shaft member 12 is attached to the integrally vulcanized molded product 44 of the main rubber elastic body 42 in a non-fixed manner, and the inner shaft member 12 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 42. Has a structured. In the following description, parts and members that are substantially the same as those of the first embodiment are denoted by the same reference numerals in the drawings, and description thereof is omitted.
　より詳細には、本体ゴム弾性体４２は、アウタ筒部材１４の内周面に固着されており、外周ゴム層２０から内周へ向けて突出する４つの突起部４６，４６，４６，４６を備えている。 More specifically, the main rubber elastic body 42 is fixed to the inner peripheral surface of the outer cylinder member 14, and includes four protrusions 46, 46, 46, 46 that protrude from the outer peripheral rubber layer 20 toward the inner periphery. I have.
　突起部４６は、突出先端２６に向けて周方向で狭幅となる先細形状を有していると共に、突出先端２６には凹部４８が形成されている。凹部４８は、突起部４６の突出先端２６に開口しており、本実施形態では軸方向の略全長に亘って直線的に連続する溝状とされている。更に、本実施形態の凹部４８の内面は、インナ軸部材１２の筒状外周面１８と略対応する曲率で周方向に広がる湾曲面とされている。尤も、凹部４８の具体的な形状は特に限定されず、必ずしもインナ軸部材１２の筒状外周面１８に対応する凹状湾曲面で構成された内面を有していなくて良い。 The protrusion 46 has a tapered shape that becomes narrower in the circumferential direction toward the protruding tip 26, and a recess 48 is formed in the protruding tip 26. The recess 48 is open to the protruding tip 26 of the protrusion 46, and in this embodiment, has a groove shape that is linearly continuous over substantially the entire length in the axial direction. Furthermore, the inner surface of the recess 48 of the present embodiment is a curved surface that extends in the circumferential direction with a curvature substantially corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12. However, the specific shape of the recess 48 is not particularly limited, and it is not always necessary to have an inner surface constituted by a concave curved surface corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12.
　そして、図７に示すように、インナ軸部材１２が本体ゴム弾性体４２の内周へ挿入された状態でアウタ筒部材１４が縮径されることにより、図６に示すように、突起部４６の突出先端２６がインナ軸部材１２の筒状外周面１８に押し付けられている。 As shown in FIG. 7, the outer cylinder member 14 is reduced in diameter in a state where the inner shaft member 12 is inserted into the inner periphery of the main rubber elastic body 42. The protruding tip 26 is pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12.
　ここにおいて、本実施形態では、インナ軸部材１２の筒状外周面１８が、突起部４６の突出先端２６に設けられた凹部４８に入り込んで、凹部４８の内面に当接しており、突起部４６の突出先端２６がインナ軸部材１２に対して凹部４８によって周方向で位置決めされ易くなっている。それ故、突起部４６の突出先端２６がインナ軸部材１２の筒状外周面１８に押し付けられることで、突起部４６が突出方向で所定の量だけ圧縮されて、インナ軸部材１２が複数の突起部４６の間で安定して弾性支持される。 Here, in the present embodiment, the cylindrical outer peripheral surface 18 of the inner shaft member 12 enters the recess 48 provided at the protruding tip 26 of the protrusion 46 and is in contact with the inner surface of the recess 48. The protruding tip 26 is easily positioned in the circumferential direction by the recess 48 with respect to the inner shaft member 12. Therefore, when the protruding tip 26 of the protrusion 46 is pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 12, the protrusion 46 is compressed by a predetermined amount in the protruding direction, and the inner shaft member 12 has a plurality of protrusions. It is elastically supported stably between the parts 46.
　特に本実施形態では、凹部４８の内面がインナ軸部材１２の筒状外周面１８に対応する湾曲凹面とされていることから、突起部４６のインナ軸部材１２に対する周方向での位置決めがより効果的に実現される。 In particular, in the present embodiment, the inner surface of the recess 48 is a curved concave surface corresponding to the cylindrical outer peripheral surface 18 of the inner shaft member 12, so that the positioning of the protrusion 46 in the circumferential direction with respect to the inner shaft member 12 is more effective. Is realized.
　図８，９には、本発明の第三の実施形態として、電気自動車用の筒形モータマウント５０を示す。筒形モータマウント５０は、インナ軸部材５１が本体ゴム弾性体５２の一体加硫成形品５４に非固着で取り付けられて、インナ軸部材５１とアウタ筒部材１４が本体ゴム弾性体５２によって弾性連結された構造を有している。 8 and 9 show a cylindrical motor mount 50 for an electric vehicle as a third embodiment of the present invention. In the cylindrical motor mount 50, the inner shaft member 51 is attached to the integrally vulcanized molded product 54 of the main rubber elastic body 52 in a non-fixed manner, and the inner shaft member 51 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 52. Has a structured.
　本実施形態のインナ軸部材５１は、図９に示すように、外周面に開口する位置決め凹部５６を備えている。位置決め凹部５６は、略半円形の断面形状で周方向に延びる環状の凹溝とされており、インナ軸部材５１の軸方向中央部分に形成されている。 The inner shaft member 51 of the present embodiment includes a positioning recess 56 that opens to the outer peripheral surface, as shown in FIG. The positioning concave portion 56 is an annular concave groove extending in the circumferential direction with a substantially semicircular cross-sectional shape, and is formed in the central portion of the inner shaft member 51 in the axial direction.
　また、本体ゴム弾性体５２は、複数の突起部５７を備えている。突起部５７は、図９，１０に示すように、突出先端２６に位置決め凸部５８が一体形成されている。位置決め凸部５８は、小径の略半球形状であることによって先端側に向けて小径となる先細形状を有しており、突起部５７の周方向および軸方向の略中央において突起部５７の突出先端２６から内周へ突出している。 The main rubber elastic body 52 includes a plurality of protrusions 57. As shown in FIGS. 9 and 10, the protruding portion 57 has a positioning convex portion 58 formed integrally with the protruding tip 26. The positioning convex portion 58 has a tapered shape with a small diameter toward the tip side by being a small hemispherical shape with a small diameter, and the protruding tip of the protruding portion 57 at the approximate center in the circumferential direction and the axial direction of the protruding portion 57. 26 protrudes from the inner periphery.
　そして、インナ軸部材５１は、図１１，１２に示すように、アウタ筒部材１４に固着された本体ゴム弾性体５２の内周へ差し入れられる。本実施形態では、径方向に対向する突起部５７，５７の位置決め凸部５８，５８間の距離は、インナ軸部材５１における位置決め凹部５６を外れた部分の外径寸法よりも大きくされており、インナ軸部材５１を複数の突起部５７の突出先端２６間へ差し入れる際に、位置決め凸部５８，５８がインナ軸部材５１に押し付けられることがないようになっている。尤も、位置決め凸部５８，５８間の距離がインナ軸部材５１における位置決め凹部５６を外れた部分の外径寸法よりも小さくされて、インナ軸部材５１が位置決め凸部５８を弾性変形させながら複数の突起部５７の内周側へ差し入れられるようにしても良い。 The inner shaft member 51 is inserted into the inner circumference of the main rubber elastic body 52 fixed to the outer cylinder member 14 as shown in FIGS. In the present embodiment, the distance between the positioning projections 58 and 58 of the projecting portions 57 and 57 facing in the radial direction is set to be larger than the outer diameter of the portion of the inner shaft member 51 that is out of the positioning recess 56. When the inner shaft member 51 is inserted between the projecting tips 26 of the plurality of projecting portions 57, the positioning convex portions 58 and 58 are not pressed against the inner shaft member 51. However, the distance between the positioning convex portions 58 and 58 is made smaller than the outer diameter of the portion of the inner shaft member 51 that is out of the positioning concave portion 56, and the inner shaft member 51 elastically deforms the positioning convex portion 58, while You may make it insert in the inner peripheral side of the projection part 57. FIG.
　このようにインナ軸部材５１が本体ゴム弾性体５２の内周へ差し入れられた状態で、アウタ筒部材１４が縮径されることにより、本体ゴム弾性体５２の突起部５７がインナ軸部材５１の筒状外周面１８に押し付けられて、インナ軸部材５１が本体ゴム弾性体５２によって弾性支持される。ここにおいて、突起部５７の位置決め凸部５８がインナ軸部材５１の位置決め凹部５６に差し入れられており、突起部５７とインナ軸部材５１が位置決め凸部５８と位置決め凹部５６によって軸方向で相対的に位置決めされている。これにより、インナ軸部材５１が本体ゴム弾性体５２に対して軸方向に抜け難くなっており、インナ軸部材５１と本体ゴム弾性体５２の一体加硫成形品５４が軸方向で安定して位置決め保持される。しかも、各突起部５７のインナ軸部材５１に対する軸方向での位置が、位置決め凸部５８と位置決め凹部５６によって保持されることから、インナ軸部材５１が複数の突起部５７の間で安定して弾性支持される。 When the outer cylindrical member 14 is reduced in diameter in a state where the inner shaft member 51 is inserted into the inner periphery of the main rubber elastic body 52 in this manner, the protrusion 57 of the main rubber elastic body 52 is moved to the inner shaft member 51. The inner shaft member 51 is elastically supported by the main rubber elastic body 52 by being pressed against the cylindrical outer peripheral surface 18. Here, the positioning projection 58 of the projection 57 is inserted into the positioning recess 56 of the inner shaft member 51, and the projection 57 and the inner shaft member 51 are relatively moved in the axial direction by the positioning projection 58 and the positioning recess 56. It is positioned. As a result, the inner shaft member 51 is less likely to come off in the axial direction with respect to the main rubber elastic body 52, and the integral vulcanized molded product 54 of the inner shaft member 51 and the main rubber elastic body 52 is stably positioned in the axial direction. Retained. In addition, since the position of each protrusion 57 in the axial direction with respect to the inner shaft member 51 is held by the positioning protrusion 58 and the positioning recess 56, the inner shaft member 51 is stably between the plurality of protrusions 57. Elastically supported.
　本実施形態の位置決め凹部５６と位置決め凸部５８は、互いに対応する軸方向位置に形成されていると共に、縦断面において互いに略対応する形状とされていることで、位置決め凸部５８を位置決め凹部５６に差し入れることが可能とされている。 The positioning concave portion 56 and the positioning convex portion 58 of the present embodiment are formed at axial positions corresponding to each other, and have a shape that substantially corresponds to each other in the longitudinal section. It is possible to put it in.
　なお、本実施形態では、位置決め凹部５６が周方向に延びる凹溝とされていることから、インナ軸部材５１と本体ゴム弾性体５２が位置決め凸部５８と位置決め凹部５６によって軸方向で位置決めされるようになっていたが、例えば、位置決め凹部が位置決め凸部５８に対応する円形の凹所とされていれば、インナ軸部材５１と本体ゴム弾性体５２を位置決め凸部５８と位置決め凹部によって軸方向と周方向の両方で位置決めすることも可能となる。更に、位置決め凹部が軸方向に延びる凹溝とされて、位置決め凹部と位置決め凸部５８によってインナ軸部材５１と本体ゴム弾性体５２が周方向で位置決めされるようにもできる。 In the present embodiment, since the positioning recess 56 is a groove extending in the circumferential direction, the inner shaft member 51 and the main rubber elastic body 52 are positioned in the axial direction by the positioning protrusion 58 and the positioning recess 56. For example, if the positioning recess is a circular recess corresponding to the positioning projection 58, the inner shaft member 51 and the main rubber elastic body 52 are axially moved by the positioning projection 58 and the positioning recess. It is also possible to position both in the circumferential direction. Further, the positioning recess can be a groove extending in the axial direction, and the inner shaft member 51 and the main rubber elastic body 52 can be positioned in the circumferential direction by the positioning recess and the positioning protrusion 58.
　図１３には、本発明の第四の実施形態として、電気自動車用の筒形モータマウント６０を示す。筒形モータマウント６０は、インナ軸部材６２が本体ゴム弾性体６４の一体加硫成形品６６に非固着で取り付けられて、インナ軸部材６２とアウタ筒部材１４が本体ゴム弾性体６４によって弾性連結された構造を有している。 FIG. 13 shows a cylindrical motor mount 60 for an electric vehicle as a fourth embodiment of the present invention. In the cylindrical motor mount 60, the inner shaft member 62 is non-fixedly attached to the integrally vulcanized molded product 66 of the main rubber elastic body 64, and the inner shaft member 62 and the outer cylindrical member 14 are elastically connected by the main rubber elastic body 64. Has a structured.
　本実施形態のインナ軸部材６２は、略楕円形断面を有する筒状外周面６８を備えており、上下方向が短軸とされているとともに左右方向が長軸とされている。なお、インナ軸部材６２の内周面は、略円形断面とされており、インナ軸部材６２の周壁の上下厚さ寸法が左右厚さ寸法よりも小さくされている。 The inner shaft member 62 of the present embodiment includes a cylindrical outer peripheral surface 68 having a substantially elliptical cross section, and the vertical direction is a short axis and the horizontal direction is a long axis. The inner peripheral surface of the inner shaft member 62 has a substantially circular cross section, and the upper and lower thickness dimensions of the peripheral wall of the inner shaft member 62 are smaller than the left and right thickness dimensions.
　また、本体ゴム弾性体６４は、上下の突起部７０，７０と左右の突起部７２，７２を備えている。上下の突起部７０，７０と左右の突起部７２，７２は、何れも各突出先端２６に向けて周方向で幅狭となる先細形状を有していると共に、上下の突起部７０，７０の突出方向の寸法が左右の突起部７２，７２の突出方向の寸法よりも大きくされている。これにより、上下の突起部７０，７０間の径方向距離が、左右の突起部７２，７２間の径方向距離よりも小さくされているが、内周面を楕円形断面として上下厚さ寸法と左右厚さ寸法を略同じにすることも可能である。 The main rubber elastic body 64 includes upper and lower protrusions 70 and 70 and left and right protrusions 72 and 72. The upper and lower protrusions 70, 70 and the left and right protrusions 72, 72 both have a tapered shape that becomes narrower in the circumferential direction toward each protrusion tip 26, and the upper and lower protrusions 70, 70 have a tapered shape. The dimension in the projecting direction is made larger than the dimension in the projecting direction of the left and right protrusions 72, 72. As a result, the radial distance between the upper and lower protrusions 70 and 70 is made smaller than the radial distance between the left and right protrusions 72 and 72. It is also possible to make the left and right thickness dimensions substantially the same.
　そして、インナ軸部材６２は、図１４に示すように、アウタ筒部材１４に固着された本体ゴム弾性体６４の内周へ差し入れられる。本実施形態では、上下の突起部７０，７０の上下方向の距離が、インナ軸部材６２の短軸方向の外径寸法よりも大きくされていると共に、左右の突起部７２，７２の左右方向の距離が、インナ軸部材６２の長軸方向の外径寸法よりも大きくされている。これにより、インナ軸部材６２を上下の突起部７０，７０および左右の突起部７２，７２の内周側へ差し入れる際に、上下の突起部７０，７０および左右の突起部７２，７２の各突出先端２６が、インナ軸部材６２に押し付けられないようになっている。本実施形態では、上下の突起部７０，７０の突出寸法が左右の突起部７２，７２の突出寸法よりも大きくされていることから、上下の突起部７０，７０の径方向間の距離とインナ軸部材６２の短軸方向の外径寸法との差と、左右の突起部７２，７２の径方向間の距離とインナ軸部材６２の長軸方向の外径寸法との差とが、略同じとされている。 Then, as shown in FIG. 14, the inner shaft member 62 is inserted into the inner periphery of the main rubber elastic body 64 fixed to the outer cylinder member 14. In the present embodiment, the vertical distance between the upper and lower protrusions 70, 70 is larger than the outer diameter dimension of the inner shaft member 62 in the minor axis direction, and the left and right protrusions 72, 72 in the left-right direction. The distance is made larger than the outer diameter dimension of the inner shaft member 62 in the major axis direction. Thus, when the inner shaft member 62 is inserted into the inner peripheral side of the upper and lower protrusions 70 and 70 and the left and right protrusions 72 and 72, each of the upper and lower protrusions 70 and 70 and the left and right protrusions 72 and 72. The protruding tip 26 is not pressed against the inner shaft member 62. In the present embodiment, since the projecting dimensions of the upper and lower projecting portions 70, 70 are larger than the projecting dimensions of the left and right projecting portions 72, 72, the distance between the radial directions of the upper and lower projecting portions 70, 70 and the inner The difference between the outer diameter dimension of the shaft member 62 in the minor axis direction and the difference between the distance between the radial directions of the left and right protrusions 72 and 72 and the outer diameter dimension of the inner shaft member 62 in the major axis direction are substantially the same. It is said that.
　このように、インナ軸部材６２が本体ゴム弾性体６４の内周へ差し入れられた状態で、アウタ筒部材１４が縮径されることにより、本体ゴム弾性体６４の上下の突起部７０，７０がインナ軸部材６２の筒状外周面１８に短軸方向で押し付けられていると共に、左右の突起部７２，７２がインナ軸部材６２の筒状外周面１８に長軸方向で押し付けられており、インナ軸部材６２が本体ゴム弾性体６４によって弾性支持される。本実施形態では、上下の突起部７０，７０の突出寸法が左右の突起部７２，７２の突出寸法よりも大きくされていることにより、それら突起部７０，７０，７２，７２のインナ軸部材６２への当接力が略同じとされている。 As described above, when the outer cylindrical member 14 is reduced in diameter in a state where the inner shaft member 62 is inserted into the inner periphery of the main rubber elastic body 64, the upper and lower protrusions 70, 70 of the main rubber elastic body 64 are formed. The inner shaft member 62 is pressed against the cylindrical outer peripheral surface 18 in the short axis direction, and the left and right protrusions 72 and 72 are pressed against the cylindrical outer peripheral surface 18 of the inner shaft member 62 in the long axis direction. The shaft member 62 is elastically supported by the main rubber elastic body 64. In the present embodiment, the projecting dimensions of the upper and lower projecting portions 70, 70 are larger than the projecting dimensions of the left and right projecting portions 72, 72, so that the inner shaft member 62 of the projecting portions 70, 70, 72, 72 is. The contact force to is substantially the same.
　このような本実施形態に従う構造とされた筒形モータマウント６０によれば、上下方向と左右方向で異なるばね特性を設定し易くなる。即ち、インナ軸部材６２の筒状外周面１８が楕円形断面を有しているとともにアウタ筒部材１４の内周面が円形断面を有していることから、インナ軸部材６２とアウタ筒部材１４の径方向間のスペースが、インナ軸部材６２の短軸方向において長軸方向よりも大きくなる。従って、上下の突起部７０，７０と左右の突起部７２，７２の径方向の突出寸法を互いに異ならせることが容易となって、上下方向と左右方向のばね比を調節し易くなる。なお、本実施形態では、上下の突起部７０，７０の上下寸法が左右の突起部７２，７２の左右寸法よりも大きくされており、上下方向のばねが左右方向のばねよりも柔らかく設定されている。 According to the cylindrical motor mount 60 having the structure according to this embodiment, it is easy to set different spring characteristics in the vertical direction and the horizontal direction. That is, since the cylindrical outer peripheral surface 18 of the inner shaft member 62 has an elliptical cross section and the inner peripheral surface of the outer cylindrical member 14 has a circular cross section, the inner shaft member 62 and the outer cylindrical member 14 The space between the radial directions of the inner shaft member 62 is larger in the short axis direction of the inner shaft member 62 than in the long axis direction. Therefore, it becomes easy to make the protrusion dimensions in the radial direction of the upper and lower protrusions 70 and 70 and the left and right protrusions 72 and 72 different from each other, and it becomes easy to adjust the spring ratio in the vertical and horizontal directions. In the present embodiment, the vertical dimension of the upper and lower protrusions 70, 70 is larger than the horizontal dimension of the left and right protrusions 72, 72, and the vertical spring is set to be softer than the horizontal spring. Yes.
　以上、本発明の実施形態について詳述してきたが、本発明はその具体的な記載によって限定されない。例えば、突起部の形状は、突出先端に向けて周方向で幅狭となる先細形状とされていれば、特に限定されるものではなく、例えば、周方向両面が平面で構成された形状なども採用され得る。 As mentioned above, although embodiment of this invention has been explained in full detail, this invention is not limited by the specific description. For example, the shape of the protrusion is not particularly limited as long as it is a tapered shape that becomes narrower in the circumferential direction toward the protruding tip. Can be employed.
　さらに、複数の突起部は、互いに異なる形状とされていても良い。具体的には、例えば、モータの分担支持荷重が特定の径方向に静荷重として及ぼされる場合には、特定の突起部が分担支持荷重によって圧縮されることを考慮して、当該特定の突起部を他の突起部とは異なる形状とすることもできる。 Furthermore, the plurality of protrusions may have different shapes. Specifically, for example, when the shared support load of the motor is applied as a static load in a specific radial direction, the specific protrusion is considered in consideration that the specific protrusion is compressed by the shared support load. Can also be shaped differently from other protrusions.
　また、突起部の数は、複数であれば、前記実施形態で示した４つに限定されるものではなく、例えば、３つであっても良いし、５つ以上であっても良い。 Further, the number of protrusions is not limited to four as shown in the above embodiment as long as it is plural, and may be three or five or more, for example.
　また、突起部は、突出方向の弾性主軸がインナ軸部材の径方向に延びていることが望ましいが、突起部の弾性主軸の方向は、必ずしもインナ軸部材の径方向と一致していなくても良い。 In addition, it is desirable that the protrusion has an elastic main shaft in the protruding direction extending in the radial direction of the inner shaft member, but the direction of the elastic main shaft of the protrusion does not necessarily coincide with the radial direction of the inner shaft member. good.
　また、インナ軸部材は、本体ゴム弾性体の内周へ差し入れられる際に、締め代をもって圧入状態で差し入れられるようにもできる。この場合には、インナ軸部材を本体ゴム弾性体の内周へ差し入れた後でアウタ筒部材に縮径加工を施しても良いし、差し入れられることで本体ゴム弾性体の突起部がインナ軸部材の筒状外周面に十分に押し付けられるようにしても良い。 Also, when the inner shaft member is inserted into the inner circumference of the main rubber elastic body, it can be inserted in a press-fitted state with a tightening margin. In this case, after the inner shaft member is inserted into the inner periphery of the main rubber elastic body, the outer cylindrical member may be subjected to diameter reduction processing, or the protrusion of the main rubber elastic body may be inserted into the inner shaft member. You may make it fully press on this cylindrical outer peripheral surface.
　また、インナ軸部材は、必ずしもストレートな筒状に限定されず、例えば、軸方向の中央部分が部分的に拡径されていても良いし、軸方向の中央部分に環状乃至は筒状の別部材が外挿状態で固定されていても良い。更に、インナ軸部材は中実であっても良く、例えば、中実ロッド状とされていると共に、軸方向端部に板状の取付部が設けられており、取付部に貫通されたボルト孔に挿通されるボルトによって、インナ軸部材がモータに取り付けられる構造も採用可能である。 Further, the inner shaft member is not necessarily limited to a straight cylindrical shape. For example, the central portion in the axial direction may be partially expanded, and the annular central portion may be annular or cylindrical. The member may be fixed in an extrapolated state. Further, the inner shaft member may be solid. For example, the inner shaft member has a solid rod shape, and a plate-like attachment portion is provided at an end portion in the axial direction, and a bolt hole penetrated through the attachment portion. It is also possible to adopt a structure in which the inner shaft member is attached to the motor by a bolt inserted into the motor.
　また、アウタ筒部材は、縮径加工の容易さから略真円形断面の円筒形状であることが望ましいが、例えば、楕円筒形状などであっても良い。 In addition, the outer cylinder member is preferably a cylindrical shape having a substantially perfect circular cross section for ease of diameter reduction processing, but may be, for example, an elliptic cylinder shape.
１０，４０，５０，６０：筒形モータマウント、１２，５１，６２：インナ軸部材、１４：アウタ筒部材、１６，４２，５２，６４：本体ゴム弾性体、１８，６８：筒状外周面、２２，４６，５７，７０，７２：突起部、２６：突出先端、３２：モータ、３４：車両ボデー、４８：凹部、５６：位置決め凹部、５８：位置決め凸部 10, 40, 50, 60: cylindrical motor mount, 12, 51, 62: inner shaft member, 14: outer cylindrical member, 16, 42, 52, 64: main rubber elastic body, 18, 68: cylindrical outer peripheral surface 22, 46, 57, 70, 72: protrusion, 26: protruding tip, 32: motor, 34: vehicle body, 48: recess, 56: positioning recess, 58: positioning protrusion

Claims (8)

  1. 　インナ軸部材とアウタ筒部材が本体ゴム弾性体によって弾性連結された電気自動車用の筒形モータマウントにおいて、
    　前記本体ゴム弾性体が前記アウタ筒部材の内周面に固着されていると共に、該本体ゴム弾性体が該アウタ筒部材から内周へ向けて突出する複数の突起部を備えており、該突起部が突出先端に向けて周方向で幅狭となる先細形状を有していると共に、該インナ軸部材が該本体ゴム弾性体の内周に非固着で差し入れられて該複数の突起部の突出先端が前記インナ軸部材における円形断面の筒状外周面に押し付けられた状態で該インナ軸部材が該本体ゴム弾性体によって弾性支持されており、該インナ軸部材が電気自動車のモータ側へ取り付けられるとともに該アウタ筒部材が電気自動車の車両ボデー側へ取り付けられることを特徴とする電気自動車用の筒形モータマウント。     In the cylindrical motor mount for an electric vehicle in which the inner shaft member and the outer cylindrical member are elastically connected by the main rubber elastic body,
    The main rubber elastic body is fixed to the inner peripheral surface of the outer cylinder member, and the main rubber elastic body includes a plurality of protrusions protruding from the outer cylinder member toward the inner periphery. And the inner shaft member is inserted non-adheringly into the inner periphery of the main rubber elastic body so that the plurality of protrusions protrude. The inner shaft member is elastically supported by the main rubber elastic body in a state in which the tip is pressed against the cylindrical outer peripheral surface of the circular cross section of the inner shaft member, and the inner shaft member is attached to the motor side of the electric vehicle. A cylindrical motor mount for an electric vehicle, wherein the outer cylinder member is attached to a vehicle body side of the electric vehicle.
  2. 　前記インナ軸部材の前記筒状外周面が真円形断面を有している請求項１に記載の電気自動車用の筒形モータマウント。 The cylindrical motor mount for an electric vehicle according to claim 1, wherein the cylindrical outer peripheral surface of the inner shaft member has a true circular cross section.
  3. 　前記インナ軸部材の前記筒状外周面が楕円形断面を有している請求項１に記載の電気自動車用の筒形モータマウント。 The cylindrical motor mount for an electric vehicle according to claim 1, wherein the cylindrical outer peripheral surface of the inner shaft member has an elliptical cross section.
  4. 　前記突起部の突出先端には軸方向に延びる凹部が形成されており、該凹部の内面に前記インナ軸部材の外周面が当接している請求項１～３の何れか一項に記載の電気自動車用の筒形モータマウント。 4. The electricity according to claim 1, wherein a recess extending in the axial direction is formed at a protruding tip of the protrusion, and an outer peripheral surface of the inner shaft member is in contact with an inner surface of the recess. A cylindrical motor mount for automobiles.
  5. 　前記インナ軸部材が前記筒状外周面に開口する位置決め凹部を備えていると共に、前記突起部が突出先端から内周へ突出する位置決め凸部を備えており、該位置決め凸部が該位置決め凹部に差し入れられて該インナ軸部材が該突起部に対して位置決めされている請求項１～４の何れか一項に記載の電気自動車用の筒形モータマウント。 The inner shaft member includes a positioning recess that opens in the cylindrical outer peripheral surface, and the protrusion includes a positioning protrusion that protrudes from the protruding tip to the inner periphery. The positioning protrusion is formed in the positioning recess. The cylindrical motor mount for an electric vehicle according to any one of claims 1 to 4, wherein the inner shaft member is inserted and positioned with respect to the protrusion.
  6. 　前記突起部の突出方向の弾性主軸が前記インナ軸部材の径方向に延びている請求項１～５の何れか一項に記載の電気自動車用の筒形モータマウント。 The cylindrical motor mount for an electric vehicle according to any one of claims 1 to 5, wherein an elastic main shaft in a protruding direction of the protruding portion extends in a radial direction of the inner shaft member.
  7. 　径方向の共振周波数が８００Ｈｚ以上に設定されている請求項１～６の何れか一項に記載の電気自動車用の筒形モータマウント。 The cylindrical motor mount for an electric vehicle according to any one of claims 1 to 6, wherein the radial resonance frequency is set to 800 Hz or more.
  8. 　インナ軸部材とアウタ筒部材が本体ゴム弾性体によって弾性連結された電気自動車用の筒形モータマウントの製造方法であって、
    　前記本体ゴム弾性体を成形して前記アウタ筒部材の内周面に固着し、該アウタ筒部材から内周へ向けて突出する複数の突起部を該本体ゴム弾性体に形成する工程と、
    　予め準備された前記インナ軸部材を該アウタ筒部材に固着された該本体ゴム弾性体の内周へ差し入れた後、該アウタ筒部材を縮径加工して、該本体ゴム弾性体の該複数の突起部の突出先端を該インナ軸部材の外周面に押し付ける工程と
    を、含むことを特徴とする電気自動車用の筒形モータマウントの製造方法。     A method of manufacturing a cylindrical motor mount for an electric vehicle in which an inner shaft member and an outer cylindrical member are elastically connected by a main rubber elastic body,
    Forming the main rubber elastic body and fixing the main rubber elastic body to the inner peripheral surface of the outer cylinder member, and forming a plurality of protrusions protruding from the outer cylinder member toward the inner circumference on the main rubber elastic body;
    After the inner shaft member prepared in advance is inserted into the inner circumference of the main rubber elastic body fixed to the outer cylinder member, the outer cylinder member is subjected to diameter reduction processing, and the plurality of main rubber elastic bodies are A method of manufacturing a cylindrical motor mount for an electric vehicle, comprising the step of pressing a protruding tip of a protruding portion against an outer peripheral surface of the inner shaft member.
PCT/JP2018/011529 2018-03-22 2018-03-22 Tubular motor mount for electric vehicle, and method of manufacturing same WO2019180896A1 (en)

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JPH112289A (en) * 1997-06-11 1999-01-06 Honda Motor Co Ltd Vibration controlling mount
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