WO2016132926A1 - 下側ばね受け部材 - Google Patents
下側ばね受け部材 Download PDFInfo
- Publication number
- WO2016132926A1 WO2016132926A1 PCT/JP2016/053412 JP2016053412W WO2016132926A1 WO 2016132926 A1 WO2016132926 A1 WO 2016132926A1 JP 2016053412 W JP2016053412 W JP 2016053412W WO 2016132926 A1 WO2016132926 A1 WO 2016132926A1
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- WO
- WIPO (PCT)
- Prior art keywords
- spring
- suspension spring
- receiving member
- load
- rubber pad
- Prior art date
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Classifications
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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
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/12—Attachments or mountings
- F16F1/122—Attachments or mountings where coils, e.g. end coils, of the spring are rigidly clamped or similarly fixed
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/14—Resilient suspensions characterised by arrangement, location or kind of springs having helical, spiral or coil springs only
- B60G11/16—Resilient suspensions characterised by arrangement, location or kind of springs having helical, spiral or coil springs only characterised by means specially adapted for attaching the spring to axle or sprung part of the vehicle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
- B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
- B60G15/062—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper
- B60G15/063—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper characterised by the mounting of the spring on the damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
- B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
- B60G15/062—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper
- B60G15/065—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper characterised by the use of a combination of springs
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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
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/12—Attachments or mountings
- F16F1/126—Attachments or mountings comprising an element between the end coil of the spring and the support proper, e.g. an elastomeric annulus
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
- F16F9/5126—Piston, or piston-like valve elements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/12—Wound spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/14—Plastic spring, e.g. rubber
- B60G2202/143—Plastic spring, e.g. rubber subjected to compression
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/30—Spring/Damper and/or actuator Units
- B60G2202/31—Spring/Damper and/or actuator Units with the spring arranged around the damper, e.g. MacPherson strut
- B60G2202/312—The spring being a wound spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/10—Mounting of suspension elements
- B60G2204/12—Mounting of springs or dampers
- B60G2204/124—Mounting of coil springs
- B60G2204/1242—Mounting of coil springs on a damper, e.g. MacPerson strut
- B60G2204/12422—Mounting of coil springs on a damper, e.g. MacPerson strut anchoring the end coils on the spring support plate
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/10—Mounting of suspension elements
- B60G2204/12—Mounting of springs or dampers
- B60G2204/125—Mounting of rubber type springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/70—Materials used in suspensions
- B60G2206/73—Rubber; Elastomers
-
- 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
- F16F2230/00—Purpose; Design features
- F16F2230/0023—Purpose; Design features protective
Definitions
- the present invention relates to a lower spring receiving member that receives a compression spring on the lower side.
- Patent Document 1 describes the following configuration regarding upper and lower spring receiving members that receive suspension springs at the upper and lower portions.
- a spring seat rubber 20 is interposed between the upper end portion of the coil spring 2 and the fitting convex portion 14 of the upper body side member 10.
- a spring seat rubber 22 is interposed between the lower end portion of the coil spring 2 and the fitting convex portion 16 of the lower arm member 12.
- the conventional lower spring seat rubber mount 22 (lower spring receiving member) including Patent Document 1 is deformed by the lower spring seat rubber mount 22 (lower spring) when the wheel moves up and down.
- the receiving member does not follow, and a gap between the two may occur.
- FIG. 6 is a cross-sectional view showing a contact portion between a conventional suspension spring and a lower rubber pad.
- the conventional lower rubber pad 103 does not have an inclination along the lower rising portion 102t of the suspension spring 102, has a flat shape for receiving the lower winding portion 102s of the suspension spring 102, and has no lip portion.
- the amount of deformation of the lower rising portion 102t of the suspension spring 102 increases as it approaches the central effective portion, and the amount of deformation of the lower rubber pad 103 also gradually increases. As a result, a portion where a large amount of deformation is generated in the lower rubber pad 103 and a portion where a small amount of deformation is generated are generated.
- the coating of the suspension spring 102 is worn away and peeled off by the foreign matter j, and the suspension spring 102 is broken, damaged or broken.
- the lower rubber pad 103 when the suspension spring 102 is vibrated, the lower rubber pad 103 does not follow the suspension spring 102 and a gap is formed between them, and foreign matter j such as sand and gravel entering the gap is generated.
- the coating film on the surface of the suspension spring 102 is worn away. As a result, the base of the suspension spring 102 is exposed and corrosion of the suspension spring 102 may occur.
- the present invention has been devised in view of the above circumstances, and an object of the present invention is to provide a highly reliable lower spring receiving member that can suppress breakage and breakage of a compression spring and can extend its life.
- the lower spring receiving member of the first aspect of the present invention has an effective portion, an end winding portion that is not elastically deformed, and a rising portion between the effective portion and the end winding portion.
- a lower spring receiving member that receives the compression spring on the lower side, and is formed so as to protrude outward from one end portion in the extending direction so that there is no gap between the rising portion and the rising portion.
- the contact portion contacts the rising portion by an elastic force due to its elastic deformation regardless of a load by the compression spring.
- the compression spring and the lower spring have the contact portion that comes into contact with or comes into contact with the rising portion regardless of the load caused by the compression spring. Intrusion of foreign matter such as sand and gravel between the receiving member and the receiving member is suppressed or prevented. Therefore, it is avoided that the coating film of the compression spring is worn out and peeled off by the foreign matter, and the compression spring is broken, damaged or broken. Therefore, the life of the compression spring can be extended.
- the lower spring receiving member according to the second aspect of the present invention is a lower spring receiving member according to the first aspect of the present invention, wherein the lower spring receiving member protrudes outwardly on the opposite side of the contact portion at one end in the extending direction. And a load receiver that receives the spring load of the compression spring.
- the lower spring receiving member of the second aspect of the present invention is formed in a shape projecting outward on the opposite side of the contact portion at one end in the extending direction, and the spring load (load) of the compression spring ),
- the lower spring receiving member can reasonably receive the spring load (load) of the compression spring, and the generation of excessive internal stress can be suppressed or prevented. For this reason, the deterioration of the lower spring receiving member over time is suppressed, and the life of the lower spring receiving member can be extended.
- the lower spring receiving member of the third aspect of the present invention is the lower spring receiving member of the first or second aspect of the present invention, provided between the contact portion and the load receiving portion of the end portion on the one side, An expansion / contraction deformation part that expands and contracts according to the load of the compression spring is provided, and the expansion / contraction deformation part has a shape narrower than the load receiving part.
- the contact portion contacts the rising portion of the compression spring regardless of the load by the compression spring. Or it can be surely contacted. Therefore, foreign matter is suppressed or prevented from entering between the compression spring and the lower spring receiving member, deterioration of the compression spring with time is suppressed, and a long life can be achieved.
- the lower spring receiving member according to the second aspect of the present invention, wherein the load receiving portion has a convex curvature and bulges outward. ing.
- the load receiving portion is formed in a bulged shape having a convex curvature, the spring load (load) of the compression spring is applied to the lower spring receiving member. ) Is applied, it is possible to receive the spring load (load) of the compression spring without excessively pushing the load receiving portion.
- the lower spring receiving member of the fifth aspect of the present invention is the lower spring receiving member of the second or fourth aspect of the present invention, wherein the load receiving portion is more than the contact portion as viewed in the axial direction of the compression spring. It is formed to protrude outward in the winding direction of the compression spring.
- the load receiving portion is formed to protrude outward in the winding direction of the compression spring from the contact portion in the axial direction view of the compression spring. It is reliably prevented that the end portion of the lower spring receiving member falls outward in the winding direction of the compression spring. Further, when the load of the compression spring is large, the contact portion can abut against the load receiving portion, so that the contact portion is prevented from being damaged.
- the lower spring bearing member of the sixth aspect of the present invention is the lower spring bearing member of the first aspect of the present invention, wherein the lower spring bearing member is formed continuously with the flat part, and the thickness gradually increases along the rising part. And a slope portion for receiving the rising portion.
- the thickness gradually increases along the rising portion of the compression spring and the slope portion that receives the rising portion is provided. It can be received where the slope is thick. Therefore, since the compression spring is flexibly received by the lower spring receiving member even when the deformation amount is large, it is possible to suppress or prevent an excessive stress from being generated in the compression spring. Further, since the slope portion of the lower spring receiving member has a thickness corresponding to the amount of deformation of the compression spring, it can be reasonably deformed according to the amount of deformation of the compression spring. The generation of stress in the lower spring receiving member can be equalized.
- the lower spring receiving member of the seventh aspect of the present invention is the lower spring receiving member of the sixth aspect of the present invention, wherein the width of the slope portion as viewed in the extending direction of the compression spring is further away from the end turn portion. It is getting wider.
- the lower spring receiving member of the seventh aspect of the present invention since the width of the slope portion seen in the extending direction of the compression spring becomes wider as the distance from the end winding portion increases, the deformation of the compression spring increases.
- the volume of the lower spring receiving member is increased. Therefore, the deformation per unit volume of the lower spring receiving member is made uniform, a nearly equal stress is generated, and the generated stress can be dispersed. Therefore, the durability of the lower spring receiving member is improved, and the life can be extended.
- the lower spring bearing member of the present invention is the lower spring bearing member according to any one of the first, second, fourth, sixth, or seventh aspect, wherein the contact portion is the rising portion. When the portion is deformed, it is in contact with or in contact with substantially the same portion of the rising portion.
- the contact portion contacts or abuts on substantially the same portion of the rising portion when the rising portion is deformed, so that the wear and wear of the contact portion are reduced. Therefore, the life of the lower spring receiving member can be extended.
- the lower spring bearing member of the ninth aspect of the present invention is the lower spring bearing member according to any one of the first, second, fourth, sixth, or seventh to eighth aspects of the present invention.
- the upper spring receiving member on the other side that receives the upper spring receiving member together with the lower spring receiving member on one side has a similar configuration symmetrical to the lower spring receiving member.
- the upper spring receiving member that receives the compression spring on the other side has a similar configuration symmetrical to the lower spring receiving member.
- the same effects as the lower spring bearing members of the first to eighth aspects of the present invention are exhibited.
- FIG. 1 is a longitudinal sectional view of a suspension device to which a lower rubber pad according to an embodiment of the present invention is attached.
- the perspective view which looked at the lower rubber pad from diagonally above.
- the top view which looked at the lower rubber pad from the upper part.
- FIG. 2 is a cross-sectional view taken along line AA in FIG. 1.
- FIG. 3B is a perspective view as viewed in the direction of the arrow B in FIG. 3A showing a contact state between the lower rising portion of the suspension spring and the lip portion of the lower rubber pad.
- FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1 when the load of the suspension spring is minimized.
- FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1 when the load on the suspension spring is maximized.
- FIG. 6 is a cross-sectional view corresponding to the AA cross section of FIG.
- FIG. 6 is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the suspension spring of the second embodiment is minimized.
- FIG. 6 is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the second embodiment is maximized.
- FIG. 6 is a cross-sectional view corresponding to the AA cross section of FIG. FIG.
- FIG. 6 is a cross-sectional view corresponding to AA in FIG. 1 when the load of the suspension spring of the third embodiment is reduced.
- FIG. 10 is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the third embodiment is maximized. Sectional drawing which shows the contact part of the conventional suspension spring and a lower rubber pad.
- FIG. 1 is a longitudinal sectional view of a suspension device to which a lower bar pad according to an embodiment of the present invention is attached.
- the suspension device S to which the lower rubber pad 3 according to the first embodiment is attached is interposed between a vehicle body (not shown) and the wheel T, and is a device that attenuates and absorbs fluctuations of the wheel T, impact received by the wheel T, and the like. is there.
- the suspension device S includes a shock absorber 1 and a suspension spring 2 through which the shock absorber 1 is inserted in the center.
- the suspension device S includes a lower rubber pad 3 and an upper bar pad 4 on the end winding part 2u and the lower end winding part 2s of the suspension spring 2, respectively.
- the lower rubber pad 3 and the upper rubber pad 4 receive the elastic force F generated by the compression deformation of the suspension spring 2 in a flexible structure having elastic properties (details will be described later).
- shock absorber 1 expands and contracts with the load when the wheel T receives an impact force or impact energy from the road surface. At this time, the shock absorber 1 attenuates the impact force and impact energy by the viscous damping force of the fluid to be enclosed. At the same time, the suspension spring 2 absorbs the impact force by elastic force, elastic energy, and internal friction due to compression deformation.
- shock absorber 1 oil is enclosed in the shock absorber 1 and a viscous damping force is generated by the flow of oil due to the movement of the piston. Thereby, a viscous damping force is applied to the expansion / contraction operation of the shock absorber 1, and the relative motion of the wheel T with respect to the vehicle body is attenuated.
- the shock absorber 1 includes an outer tube 1a in which oil is sealed, and a piston rod 1b to which a piston (not shown) that slides in the outer tube 1a is fixed.
- the outer tube 1a has a cylindrical sealing structure, and oil is sealed inside.
- piston rod 1b the one end side to which a piston is fixed is accommodated in the inside of outer tube 1a.
- the other end of the piston rod 1b that receives the load extends outward (upward in FIG. 1) of the outer tube 1a.
- a stepped annular step portion 1a3 is formed in which an upper small diameter portion 1a1 and a lower large diameter portion 1a2 are formed.
- the lower large-diameter portion 1a2 has a larger diameter than the upper thin-diameter portion 1a1.
- a steel disk-like lower spring seat 5 is locked and fixed to the annular step portion 1a3.
- the lower spring seat 5 has an annular support plate portion 5a having a center hole 5a1 and a low-height side wall portion 5b formed around the flat plate portion 5a.
- the lower spring seat 5 is a bottomed cylindrical shape is illustrated, it may be a dish-shaped mortar shape.
- the small diameter portion 1a1 of the outer tube 1a is inserted into the center hole 5a1 of the flat plate portion 5a.
- a substantially annular upper spring seat 6 is provided through the piston rod 1b.
- the upper spring seat 6 is fixed to a vehicle body (not shown).
- the lower spring seat 5 and the upper spring seat 6 are press-formed products.
- a suspension spring 2 is suspended between the lower spring seat 5 and the upper spring seat 6.
- the suspension spring 2 is a compression coil spring that generates an elastic force in the extension direction by being compressed and deformed.
- a lower winding 2s that does not function (elastically deform) as a spring is formed.
- an upper winding portion 2 u that does not function (elastically deform) as a spring is formed at the upper end portion of the suspension spring 2.
- an effective part 2y that functions as a spring is formed.
- x is a displacement amount of the suspension spring 2.
- a lower rising portion 2t is formed between the lower winding portion 2s of the suspension spring 2 and the central effective portion 2y.
- the lower rising portion 2t is formed to rise from the lower winding portion 2s in a spiral shape with a predetermined gradient.
- the lower rising portion 2t is elastically deformed by a compressive load applied by the suspension spring 2.
- An upper rising portion 2v is formed between the upper winding portion 2u of the suspension spring 2 and the central effective portion 2y.
- the upper rising portion 2v is formed by rising from the upper winding portion 2u into a spiral shape with a predetermined gradient, and is elastically deformed by an applied compressive load.
- the lower winding portion 2s and the upper winding portion 2u are each formed about 0.5 turns with respect to one turn of the effective portion 2y, but are not particularly limited thereto.
- the total number of turns of the suspension spring 2 can be reduced by reducing the lower winding part 2s and the upper winding part 2u to about 0.5 turns.
- the material of the suspension spring 2 is reduced, and the manufacturing cost of the suspension spring 2 can be reduced.
- a lower rubber pad 3 is interposed between the lower spring seat 5 and the lower end of the suspension spring 2.
- an upper bar pad 4 is interposed between the upper spring seat 6 and the upper end of the suspension spring 2.
- the lower seat winding portion 2 s and the lower rising portion 2 t of the lower end of the suspension spring 2 are supported by the support plate portion 5 a of the lower spring seat 5 via the lower rubber pad 3.
- the upper winding portion 2 u and the upper rising portion 2 v of the upper end of the suspension spring 2 are supported by the upper spring seat 6 via the upper bar pad 4.
- the lower rubber pad 3 and the upper bar pad 4 are members having a function of receiving the spring load F of the suspension spring 2 and receiving the suspension spring 2 with flexibility and suppressing the damage.
- the lower rubber pad 3 and the upper rubber pad 4 are made of hard rubber formed of, for example, NR (natural rubber).
- NR natural rubber
- the material is not particularly limited as long as it has predetermined properties such as flexibility and elasticity.
- the lower rubber pad 3 is compressed by an elastic force that resists the compressive deformation of the suspension spring 2 when the suspension spring 2 is compressed by the vehicle weight or the like. In this state, the lower rubber pad 3 is supported between the support plate portion 5 a of the lower spring seat 5 and the suspension spring 2. That is, the lower rubber pad 3 receives the lower winding portion 2 s and the lower rising portion 2 t of the suspension spring 2, so that an elastic force due to compressive deformation of the suspension spring 2 is applied.
- FIG. 2A is a perspective view of the lower rubber pad as viewed obliquely from above
- FIG. 2B is a top view of the lower rubber pad as viewed from above
- FIG. 2C is a top view of the vicinity of the lip portion of another example of the lower rubber pad as viewed from above
- FIG. 2D is a top view of the vicinity of the lip portion of another example of the lower rubber pad as viewed from above.
- the lower rubber pad 3 is formed of rubber such as NR (natural rubber). As shown in FIG.
- the lower rubber pad 3 has a shape that forms a part of an annular shape along the shape of the suspension spring 2 viewed from the axial direction, and the lower winding 2s and the lower part of the suspension spring 2 It has a shape that rises so as to eliminate (fill) the gap with the rising portion 2t (see FIG. 1).
- the lower rubber pad 3 has a curved surface 3w that is a guide surface that contacts the lower winding portion 2s and the lower rising portion 2t of the suspension spring 2.
- the curved surface 3w is formed in an annular shape having a diameter substantially the same as the diameter of the suspension spring 2 in a top view, and is recessed downward with a diameter substantially the same as or slightly smaller than the wire diameter of the suspension spring 2. .
- the lower rubber pad 3 has a base end portion 3a formed on one end side, and a flat flat portion 3h including the base end portion 3a.
- a flat flat portion 3h including the base end portion 3a.
- an inclined slope portion 3s is formed on the other end side of the lower rubber pad 3.
- the slope portion 3 s is formed in a shape in which the thickness gradually increases so as to have an inclination that contacts the lower rising portion 2 t of the lower end portion of the suspension spring 2.
- the spring holding part 3o holding the suspension spring 2.
- the base end portion 3a is attached by inserting the end portion of the suspension spring 2.
- the base end portion 3a of the lower rubber pad 3 is formed in a wall shape having an upper cutout opening 3a1 cut out at the upper portion, and the end portion of the suspension spring 2 is held by both side walls. Is formed.
- the upper cutout opening 3a1 of the base end portion 3a is formed in a shape in which the end portion extends toward both sides toward the edge portion. Thereby, it is easy to insert the terminal portion of the suspension spring 2 from above the lower rubber pad 3 into the base end portion 3a from the upper cutout opening 3a1.
- the suspension spring 2 can be easily mounted on the curved surface 3w of the guide surface that is curved in a substantially annular shape along the extending direction of the lower rubber pad 3 from the location where the end portion abuts.
- the upper notch opening 3a1 has a shape that becomes gradually narrower as it is separated from the edge side, so that the lower rubber pad 3 after the suspension spring 2 is mounted has a high holding performance when holding the suspension spring 2. is doing.
- the length from one end side to the other end side of the lower rubber pad 3 is not particularly limited.
- the lower rubber pad 3 is formed to have a length corresponding to approximately 0.6 to 0.9 turns of the suspension spring 2. Yes.
- the suspension spring 2 has a lower rising portion 2t that rises in a spiral shape with a predetermined gradient.
- the lower rubber pad 3 has a length corresponding to approximately 0.6 to 0.9 turns for holding a part of the lower winding portion 2s and the lower rising portion 2t of the suspension spring 2. Therefore, the lower rubber pad 3 Manufacturing costs such as material costs can be reduced. In addition, you may set the length of the lower rubber pad 3 to the length which hold
- the lower rubber pad 3 is interposed between the lower winding portion 2s and the lower rising portion 2t of the suspension spring 2 and the support plate 5a of the lower spring seat 5 (see FIG. 1). Therefore, as shown in FIG. 2A, the lower rubber pad 3 has a shape that receives a part of the lower rising portion 2t (see FIG. 1) from the lower winding portion 2s of the suspension spring 2.
- FIG. 3A is a cross-sectional view taken along the line AA in FIG. 1
- FIG. 3B is a view in the direction of arrow B in FIG. 3A showing a contact state between the lower rising portion of the suspension spring and the lip portion of the lower rubber pad
- FIG. 1 is a cross-sectional view taken along line AA in FIG. 1 when the load on the spring is the smallest
- FIG. 3D is a cross-sectional view taken along line AA in FIG. 1 when the load on the suspension spring is the largest.
- the AA cross section of FIG. 1 is a cross section along the winding direction of the suspension spring 2 when the suspension spring 2 is attached to the lower rubber pad 3.
- FIG. 3A shows a state of the suspension spring 2 and the lower rubber pad 3 in which the suspension spring 2 is fully rebounded, that is, only the load of the vehicle body is applied to the suspension spring 2.
- FIG. 3C shows the state of the suspension spring 2 and the lower rubber pad 3 when the load of the suspension spring 2 suddenly becomes the smallest.
- FIG. 3D shows the state of the suspension spring 2 and the lower rubber pad 3 when the load on the suspension spring 2 is maximized.
- the lower rubber pad 3 has a flat portion 3h including a base end portion 3a of a portion that receives the lower winding portion 2s of the suspension spring 2 in accordance with the shape of the lower winding portion 2s of the suspension spring 2. The thickness is changed. That is, the thickness of the flat portion 3h is changed so as to contact or contact the lower winding portion 2s of the suspension spring 2.
- the slope portion 3s of the portion that receives a part of the lower rising portion 2t of the suspension spring 2 gradually increases from the thickness dimension h1 to the thickness dimension h2 (where h1 ⁇ h2).
- the slope portion 3 s is formed into a shape that rises in a spiral shape that inclines so as to be separated from the bottom surface 3 t of the lower rubber pad 3 as it moves away from the flat portion 3 h (see FIG. 2A).
- the lower rubber pad 3 has the flat part 3h and the slope part 3s, and the slope part 3s has the thickness of the extending direction of the suspension spring 2 in the shape of the lower rising part 2t of the suspension spring 2. Thicken along.
- the slope portion 3s of the lower rubber pad 3 is viewed in plan view according to the distance from the flat portion 3h, that is, according to the shape of the lower rising portion 2t of the suspension spring 2 that rises in a spiral shape. 2), the width w of the slope portion 3s is gradually increased.
- the width dimension w0 of the flat part 3h, the width dimension w1 of the slope part 3s near the flat part 3h, the width dimension w2 near the center of the slope part 3s, and the width dimension w3 near the end of the slope part 3s is formed so as to have a magnitude relationship of w0 ⁇ w1 ⁇ w2 ⁇ w3.
- the slope portion 3s has a configuration in which the volume gradually increases as the slope portion 3s that receives the lower rising portion 2t moves away from the flat portion 3h along the shape of the lower rising portion 2t of the suspension spring 2. It is said.
- the amount of deformation of the lower rising portion 2t gradually increases as the lower rising portion 2t is separated from the lower winding portion 2s. Therefore, the amount of deformation of the slope portion 3s with which the lower rising portion 2t of the suspension spring 2 abuts increases as it is separated from the flat portion 3h.
- the deformation amount per unit volume accompanying the deformation of the suspension spring 2 of the slope portion 3s of the lower rubber pad 3 is evenly distributed. You can get closer. That is, the stress generated in the slope portion 3s of the lower rubber pad 3 can be made to approach evenly. Therefore, the stress of the lower rubber pad 3 is equalized, the durability of the lower rubber pad 3 is improved, and deterioration with time can be suppressed. Therefore, the lifetime of the lower rubber pad 3 can be extended.
- ⁇ Lip part L of lower rubber pad 3> As shown in FIG. 2A and FIG. 3A, a lip portion L that extends outward from the upper portion of the slope portion 3s and contacts or abuts against the lower rising portion 2t of the suspension spring 2 is provided at the edge of the slope portion 3s. It has been.
- the lip portion L gradually decreases in thickness dimension t from the upper side of the edge wall 3s1 of the slope portion 3s so as to come into contact with or come into contact with the lower rising portion 2t of the suspension spring 2 in a side view shown in FIG. It is formed protruding in the shape.
- the lip portion L is formed so that the thickness dimension t increases (thickens) from the front end portion L1 to the lip base end portion L2.
- the lip L is formed so as to protrude in the winding direction of the suspension spring 2 from the lower edge wall 3s0 of the edge wall 3s1.
- the width dimension b of the lip portion L is substantially the same from the lip base end portion L2 to the tip end portion L1 when viewed from the axial direction of the suspension spring 2.
- the lip portion 10L may be formed in a tapered shape in which the width dimension b is gradually narrowed from the lip base end portion L2 to the tip end portion L1 when viewed from the axial direction of the suspension spring 2.
- the width dimension bw of the curved surface 3w is also gradually narrowed in the axial direction of the suspension spring 2 from the lip base end portion L2 to the tip end portion L1 in the extending direction of the wire rod of the suspension spring 2.
- the tip edge L0 of the tip portion L1 of the lip portion L is formed in an R shape (curved shape) so that the tip side of the tip portion L1 of the lip portion L is not destroyed due to wear or breakage.
- the tip end portion L1 of the lip portion 20L may be formed in a concave shape when the suspension spring 2 is viewed in the axial direction. That is, the tip edge L0 of the lip portion 20L may be formed in a concave shape as viewed in the axial direction of the suspension spring 2.
- the lip portion L formed on the edge wall 3s1 of the slope portion 3s is changed from the original shape shown by the two-dot chain line in FIG. 3A to the shape shown by the solid line in FIG. 3A. It is always elastically deformed and in contact with the lower rising portion 2t. That is, the lip portion L formed on the slope portion 3 s is configured to always contact or contact the lower rising portion 2 t of the suspension spring 2 with an elastic force regardless of the deformation of the suspension spring 2. In this way, the lip portion L always keeps a contact state with the lower rising portion 2t of the suspension spring 2 regardless of the deformation of the suspension spring 2, so that gravel and pebbles are provided between the lower rubber pad 3 and the suspension spring 2. The entry of foreign matter j such as is reliably prevented.
- the lip portion L is formed in a substantially cylindrical shape along the circular cross-sectional shape of the lower rising portion 2t of the suspension spring 2.
- the lip portion L of the slope portion 3s of the lower rubber pad 3 is brought into contact (close contact) with the lower rising portion 2t of the suspension spring 2, and no gap is formed between them. Therefore, it is possible to suppress or prevent foreign matter j such as sand or gravel from entering between the suspension spring 2 and the lower rubber pad 3.
- the lip portion L of the slope portion 3 s is also applied when the load of the suspension spring 2 becomes the smallest so that the lower rising portion 2 t of the suspension spring 2 is separated from the lower rubber pad 3.
- the lower rising portion 2t is kept in contact (contact) or in contact with the elastic force due to elastic deformation.
- the lip portion 10L of the lower rubber pad 3 has a tapered shape in which the width dimension b gradually decreases from the lip base end portion L2 to the tip end portion L1 in the axial direction of the suspension spring 2.
- the foreign matter j traveling in the winding direction of the suspension spring 2 where the foreign matter j such as gravel and pebbles is most likely to enter is repelled outward by the tapered shape of the tip portion L1 of the lip portion 10L (arrow in FIG. 2C). ⁇ 1). Therefore, foreign matter j such as gravel and pebbles is suppressed or prevented from entering between the suspension spring 2 and the lower rubber pad 3.
- the tip edge L0 of the lip portion 20L has a concave shape and covers the wrap portion 2 so as to be wrapped from the side of the lower rising portion 2t of the suspension spring 2. Therefore, foreign matter j such as gravel and pebbles is repelled against the front end side edges L01 and L02 of the lip portion 20L and is prevented from entering between the suspension spring 2 and the lower rubber pad 3.
- the surface coating of the lower rising portion 2t and the lower winding portion 2s of the suspension spring 2 is caused by the friction between the lower rising portion 2t and the lower winding portion 2s of the suspension spring 2 and the slope portion 3s of the lower rubber pad 3. It is possible to suppress abrasion and peeling. For this reason, wear, breakage, breakage, etc. of the suspension spring 2 are suppressed, the life of the suspension spring 2 can be extended, and durability and reliability are improved.
- the thickness of the slope portion 3s of the lower rubber pad 3 is changed to be thick in accordance with the shape of the lower rising portion 2t of the suspension spring 2 that is a compression coil spring, the followability of the lower rubber pad 3 to the suspension spring 2 is improved. be able to. Thereby, the gap
- the amount of deformation of the lower rising portion 2t of the suspension spring 2 increases as it approaches the central effective portion 2y, but the slope portion 3s of the lower rubber pad 3 has a thickness that matches the shape of the lower rising portion 2t of the suspension spring 2. Therefore, the slope portion 3s of the lower rubber pad 3 can be deformed in accordance with the deformation of the lower rising portion 2t. Therefore, it is possible to suppress an excessive stress from being generated in the slope portion 3 s of the lower rubber pad 3. As a result, the durability and life of the lower rubber pad 3 can be improved.
- the slope portion 3s of the lower rubber pad 3 is formed such that the width dimension w increases as the lower rising portion 2t of the suspension spring 2 approaches the effective portion 2y. Therefore, the volume of the lower rubber pad 3 increases along the lower rising portion 2 t of the suspension spring 2.
- the amount of deformation of the lower rising portion 2t of the suspension spring 2 increases as the central portion approaches the effective portion 2y, and the slope portion 3s of the lower rubber pad 3 increases along the lower rising portion 2t of the suspension spring 2.
- the volume of the slope portion 3 s of the lower rubber pad 3 increases along the lower rising portion 2 t of the suspension spring 2, it is possible to make the deformation amount per unit volume of the lower rubber pad 3 evenly close.
- the stress generated per unit volume of the lower rubber pad 3 is equalized, and deterioration of the lower rubber pad 3 with time can be suppressed. Therefore, the lifetime of the lower rubber pad 3 can be extended. As a result, the durability, reliability, and life of the suspension spring 2 and the lower rubber pad 3 as a unit are improved.
- FIG. 4A is a cross-sectional view corresponding to the AA cross section of FIG. 1 of the second embodiment
- FIG. 4B is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the second embodiment is minimized
- FIG. 4C is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the second embodiment is maximized.
- FIG. 4A shows the state of the suspension spring 2 and the lower rubber pad 13 in which the suspension spring 2 is fully rebounded, that is, only the load of the vehicle body is applied to the suspension spring 2 in the second embodiment.
- FIG. 4A shows the state of the suspension spring 2 and the lower rubber pad 13 in which the suspension spring 2 is fully rebounded, that is, only the load of the vehicle body is applied to the suspension spring 2 in the second embodiment.
- FIG. 4B shows the state of the suspension spring 2 and the lower rubber pad 13 when the load of the suspension spring 2 is minimized in the second embodiment.
- FIG. 4C shows the state of the suspension spring 2 and the lower rubber pad 13 when the load on the suspension spring 2 is maximized in the second embodiment.
- the lower rubber pad 13 according to the second embodiment is formed so that the distance that the lip portion 2L formed at the end edge of the slope portion 13s slides with the lower rising portion 2t of the suspension spring 2 is shortened. Since the other configuration is the same as that of the first embodiment, the same components are denoted by the same reference numerals, and detailed description thereof is omitted.
- the lip portion 2L of the lower rubber pad 13 extends from the center O1 of the lip function of the lip portion 2L to the tip of the lip portion 2L so that the sliding distance with the lower rising portion 2t of the suspension spring 2 is shortened.
- the distance radius r11 is formed small.
- the lip portion 2L continues to contact or abut on the lower rising portion 2t of the suspension spring 2 regardless of the load (spring load) of the suspension spring 2 due to the elastic force due to the elastic deformation thereof.
- the lip function of the lip portion 2L is such that the lip portion 2L follows or moves against the lower rising portion 2t of the suspension spring 2 as shown in FIGS. 4B and 4C. It refers to the action of turning or swinging.
- the center of the lip function is the center of the rotation or swinging motion of the lip portion 2L.
- the radius r11 is desirably set so that the sliding distance between the lip portion 2L and the suspension spring 2 approaches a minimum. Alternatively, it is desirable to set at least one of the length, width, thickness dimension, and shape of the lip 2L so that the sliding distance between the lip 2L and the suspension spring 2 is minimized.
- the end wall 13s1 of the slope portion 13s that forms the lip portion 2L of the slope portion 13s is formed in a C-shape.
- the end wall 13s1 is formed in a C shape in a side view, the lip 2L, the expansion / contraction deformation part 13H, and the thick support part are viewed from above in the axial direction of the suspension spring 2 (vertical direction in FIG. 4A). 13J is formed.
- the elastic deformation part 13H is thinner and thinner than the thick support part 13J.
- the elastic deformation part 13H is thinner than the thick support part 13J, and therefore has a smaller elastic coefficient than the thick support part 13J. Therefore, the expansion / contraction deformation portion 13H follows the movement of the lower rising portion 2t of the suspension spring 2 in the axial direction (see the white arrow in FIGS. 4B and 4C), so that the lip portion 2L is the lower rising portion of the suspension spring 2. It expands and contracts to contact or abut 2t. That is, the lip portion 2L assists so as to keep contacting or abutting the suspension spring 2 regardless of the load from the suspension spring 2.
- the shape of the expansion / contraction deformation portion 13H is determined in consideration of the lower space 13k formed in the lower portion of the lower rubber pad 13.
- the thick support portion 13J is thicker and thicker than the expansion / contraction deformation portion 13H. That is, the thick support portion 13J has a larger elastic coefficient than the expansion / contraction deformation portion 13H. Therefore, the thick support portion 13J mainly functions to receive a load applied from the lower rising portion 2t of the suspension spring 2. In other words, since the thick support portion 13J is thick and thick, it functions to distribute and receive the load applied from the lower rising portion 2t of the suspension spring 2. Therefore, the thick support portion 13J plays a role that contributes to the improvement of the durability of the lower rubber pad 13 by reducing the stress generated per unit volume as compared with the conventional case.
- the lip portion 2L of the second embodiment is formed on the lower rising portion 2t of the suspension spring 2 regardless of the deformation of the suspension spring 2, as shown by a two-dot chain line in FIG. 4A.
- the lower rubber pad 13 is attached to the suspension spring 2 in a state where it is pressed and brought into contact with or abuts in an elastically deformed state.
- the lip portion 2L of the lower rubber pad 13 is set in a state where the suspension spring 2 is set on the lower rubber pad 13 (see FIG. 4A) due to rotational deformation of the lip portion 2L and expansion / contraction deformation of the expansion / contraction deformation portion 13H (see FIG. 4A).
- the elastic spring is always elastically deformed through the case where the load on the suspension spring 2 of FIG. 4C becomes the largest, and comes into contact with and comes into contact with the lower rising portion 2t of the suspension spring 2.
- no gap is formed between the slope portion 13s of the lower rubber pad 13 and the lower rising portion 2t of the suspension spring 2.
- the lip portion 2L of the lower rubber pad 13 continues to contact or contact the lower rising portion 2t of the suspension spring 2 due to the rotational deformation of the lip portion 2L and the expansion / contraction deformation of the expansion / contraction deformation portion 13H. Therefore, foreign matter j such as gravel and pebbles is prevented from entering between the suspension spring 2 and the lower rubber pad 13 (see FIGS. 4B and 4C). Since the sliding distance between the lip 2L and the suspension spring 2 is set to be small, the coating of the suspension spring 2 is prevented from being peeled off or worn, and the coating of the suspension spring 2 is held and maintained as much as possible. can do. Therefore, the service life of the suspension spring 2 can be extended.
- Embodiment 1 the effect of Embodiment 1 is show
- Embodiment 3 is a cross-sectional view corresponding to the AA cross section of FIG. 1 of the third embodiment, and FIG. 5B is a cross-sectional view corresponding to the AA cross section of FIG. 1 when the load of the suspension spring of the third embodiment is reduced.
- FIG. 5C is a cross-sectional view corresponding to the AA cross-section of FIG.
- the lower rubber pad 23 of the third embodiment is formed so that the sliding distance of the lip portion 3L formed on the edge of the slope portion 23s with the lower rising portion 2t of the suspension spring 2 is small, and the suspension spring 2 A load receiving portion 23s1 that receives a load (spring load) is formed.
- FIG. 5A shows a state of the suspension spring 2 and the lower rubber pad 23 in which the suspension spring 2 is fully rebounded, that is, only the load of the vehicle body is applied to the suspension spring 2 in the third embodiment.
- FIG. 5B shows the state of the suspension spring 2 and the lower rubber pad 23 when the load of the suspension spring 2 becomes the smallest in the third embodiment.
- 5C shows the state of the suspension spring 2 and the lower rubber pad 23 when the load on the suspension spring 2 is maximized in the third embodiment. Since the other configuration is the same as that of the first embodiment, the same components are denoted by the same reference numerals, and detailed description thereof is omitted.
- the lip portion 3L of the lower rubber pad 23 of the third embodiment is separated from the center O2 of the lip function of the lip portion 3L in the same manner as in the second embodiment so that the sliding distance with the lower rising portion 2t of the suspension spring 2 is reduced.
- the radius r21 of the distance to the tip of the lip portion 2L is reduced.
- the lip portion 3L continues to contact or abut on the lower rising portion 2t of the suspension spring 2 regardless of the load (spring load) of the suspension spring 2 due to the elastic force due to the elastic deformation thereof.
- the lip function of the lip portion 3L is such that the lip portion 3L contacts or abuts the lower rising portion 2t following the movement of the lower rising portion 2t of the suspension spring 2, as shown in FIGS. 5B and 5C. It refers to the action of turning or swinging.
- the center of the lip function is the center of the rotation or swinging motion of the lip portion 3L.
- an end edge wall 23s1 of the slope portion 23s is formed to bulge outward along the shape of the lower rising portion 2t of the suspension spring 2 and formed. 23s2 is formed.
- the edge wall 23s1 in which the lip portion 3L and the lower rising portion 2t of the slope portion 23s are formed is formed in an S-shape.
- the radius r21 of the distance from the center O2 of the lip function of the lip 3L to the tip of the lip 2L so that the sliding distance between the lip 3L and the suspension spring 2 becomes smaller.
- the lip portion 3L of the lower rubber pad 23 is below the suspension spring 2 regardless of the load (spring load) of the suspension spring 2 as shown by the two-dot chain line in FIG.
- the lower rubber pad 23 is attached to the suspension spring 2 while being pressed against the rising portion 2t in a state of being elastically deformed and in contact with or in contact with the state of elastic deformation.
- the lip portion 3L of the lower rubber pad 23 is elastically deformed to come into contact with or abut against the lower rising portion 2t of the suspension spring 2, so that the gap between the slope portion 23s of the lower rubber pad 23 and the lower rising portion 2t of the suspension spring 2 is reached. In this configuration, no gap is formed.
- the expansion / contraction deformation portion 23H is thinner than the load receiving portion 23s2, the elastic coefficient is smaller than that of the load receiving portion 23s2. It fulfills the function of expanding and contracting according to the load from the suspension spring 2. As a result, the lip portion 3L assists so as to keep contacting or abutting against the suspension spring 2 regardless of the load from the suspension spring 2.
- the shape of the expansion / contraction deformation portion 23H is determined in consideration of the lower space 23k formed in the lower portion of the lower rubber pad 23.
- the load receiving portion 23s2 is formed in a shape in which the end wall 23s1 of the slope portion 23s bulges outward (in the winding direction of the suspension spring 2). Therefore, as shown in FIG. 5C, when a load (spring load) of the suspension spring 2 is applied to the lower rubber pad 23, the load is received by the load receiving portion 23s2 formed at the end portion of the slope portion 23s. Dispersed in the load receiving portion 23s2. Therefore, the stress generated in the lower rubber pad 23 is reduced, which can contribute to the improvement of the durability of the lower rubber pad 23.
- the load receiving portion 23s2 may be formed in a columnar shape having an axis in the axial direction of the suspension spring 2 or a direction perpendicular to the axial direction, as long as the load receiving portion 23s2 can receive the load (spring load) of the suspension spring 2. It may be formed in a spherical shape. Alternatively, it may be formed in a prismatic shape, and its form is not limited and can be arbitrarily selected.
- the sliding distance between the lip portion 3L and the suspension spring 2 is set to be small, it is possible to suppress or prevent the coating of the suspension spring 2 from being peeled off or worn out. Therefore, the suspension spring 2 can be prevented from being rusted or broken, and the life of the suspension spring 2 can be extended. Further, wear of the lip portion 3L is suppressed, and the life of the lip portion 3L can be extended. Therefore, maintenance work such as replacement of the lower rubber pad 23 is avoided.
- an expansion / contraction deformation portion 23H is formed below the lip portion 3L, and is elastically deformed according to a load from the suspension spring 2. This assists the operation in which the lip portion 3L continues to contact or abut against the suspension spring 2 regardless of the load from the suspension spring 2, and can be made more reliable. Therefore, as shown in FIGS. 5B and 5C, the lip 3 ⁇ / b> L can continue to contact or abut on the suspension spring 2 more reliably regardless of the load from the suspension spring 2.
- a load (spring load) of the suspension spring 2 is applied to the lower rubber pad 23, it is reliably received by the load receiving portion 23s2 having a large volume formed in the slope portion 23s.
- the load applied to the lower rubber pad 23 is dispersed by the load receiving portion 23s2 having a large volume. Therefore, the stress generated in the lower rubber pad 23 is reduced by the dispersion of the load, the durability of the lower rubber pad 23 can be improved, and the life of the lower rubber pad 23 can be extended. As a result, the durability and reliability of the lower rubber pad 23 as a unit on the market is improved.
- the load receiving portion 23s2 is formed in a shape in which the end wall 23s1 of the slope portion 23s bulges outwardly, it is impossible to load the load of the suspension spring 2 without the load receiving portion 23s2 leaning. You can receive without. Further, the load receiving portion 23s2 is formed so as to protrude in the winding direction of the suspension spring 2 from the lip portion 3L. Therefore, even when the lip portion 3L is pressed downward by the suspension spring 2, it strikes the load receiving portion 23s2 and is elastically received, and the lip portion 3L is prevented from being damaged. As a result, it is possible to reduce labor and man-hours for replacement and maintenance by service personnel in the market.
- the durability of the suspension spring 2 can be improved, and the reliability of the suspension spring 2 can be improved. Further, the durability of the lower rubber pad 23 can be improved, and the reliability of the lower rubber pad 23 can be improved. In addition, the effect of Embodiment 1 is show
- the lip portions L, 2L, and 3L described in the first to third embodiments are adjusted by adjusting the shape of the lip portions L, 2L, and 3L extending from the slope portion 3s in order to suppress wear due to sliding. It is desirable that L, 2L, and 3L always contact or contact the lower rising portion 2t of the suspension spring 2 and that the sliding distance is as small and short as possible.
- the lip portions L, 2L, 3L, 10L, and 20L are formed by extending in the extending direction of the lower rising portion 2t of the suspension spring 2, and deformed up and down (moving up and down) into the lower rising portion 2t while being in contact with each other. Alternatively, the sliding distance is shortened by abutting.
- the lip portions L, 2L, 3L, 10L, and 20L are formed so as to be in contact with or abut against substantially the same portion of the lower rising portion 2t when the lower rising portion 2t of the suspension spring 2 is deformed. It is preferable to shorten the sliding distance with respect to the portion 2t.
- the load receiving portion 23s2 described in the third embodiment may be applied to the configuration of the first and second embodiments.
- the lip portions L, 2L, 3L, 10L, and 20L of the first, second, and third embodiments may be configured independently.
- the lip portions L, 2L, 3L, 10L, and 20L described in the first to third embodiments may be applied to the lower rubber pads 3, 13, and 23 that do not have the slope portions 3s, 13s, and 23s.
- the lower rubber pads 3, 13, and 23 described in the first to third embodiments may be applied as a spring receiving member for a compression spring without a suspension device.
- the present invention is applied to the suspension device S of an automobile.
- MTB mountain bike
- tricycle automatic
- four-wheeled vehicle railway vehicle and other industrial machines, aircraft, snowplows and other industrial machines, agricultural machinery, and the like.
- the present invention may be applied to a compression coil spring that does not have a suspension device.
- Embodiments 1 to 3 various configurations have been described. However, the configurations may be appropriately selected and combined, or may be used alone.
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Springs (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
- Connector Housings Or Holding Contact Members (AREA)
- Bridges Or Land Bridges (AREA)
Abstract
Description
従来のロアラバーパッド103は、懸架スプリング102の下立ち上がり部102tに沿った傾斜を有さず、懸架スプリング102の下座巻き部102sを受ける平坦形状であるとともに、リップ部もない。
加えて、ロアラバーパッド103と懸架スプリング102の下立ち上がり部102tとの隙間から、砂、砂利等の異物jが侵入する。
そのため、圧縮スプリングの塗膜が異物により磨滅、剥離し、圧縮スプリングが折損、破損、破壊することが回避される。従って、圧縮スプリングの長寿命化が図れる。
従って、圧縮スプリングと下側ばね受け部材との間に異物が入ることが抑制または阻止され、圧縮スプリングの経時劣化が抑制され、長寿命化が可能である。
図1は、本発明の実施形態に係わるロアラバーパッドが装着されるサスペンション装置の縦断面図である。
実施形態1に係わるロアラバーパッド3が装着されるサスペンション装置Sは、不図示の車体と車輪Tとの間に介在され、車輪Tの変動や車輪Tが受ける衝撃等を減衰、吸収する装置である。
サスペンション装置Sは、懸架スプリング2の上端の座巻部2uおよび下端の座巻部2sにそれぞれ、ロアラバーパッド3、アッパラバーパッド4を備えている。
ロアラバーパッド3、アッパラバーパッド4は、懸架スプリング2の圧縮変形で発生する弾性力Fを、弾性的性質をもつ柔軟構造で受けている(詳細は後記)。
ショックアブソーバ1は、車輪Tが路面から衝撃力や衝撃エネルギを受ける際にその荷重に伴って伸縮動作する。この際、ショックアブソーバ1は、封入される流体の粘性減衰力により、衝撃力や衝撃エネルギを減衰させる。同時に、懸架スプリング2は、圧縮変形による弾性力や弾性エネルギ、内部摩擦によって該衝撃力を吸収する。
下方の太径部1a2は、上方の細径部1a1より径が大きい。
環状段部1a3には、鋼製の円板状の下側スプリングシート5が係止されて固定されている。下側スプリングシート5は、中心孔5a1を有する円環状の支持板部5aと、平板部5aの周囲に形成される低い高さの側壁部5bとを有している。なお、下側スプリングシート5は有底円筒状の場合を例示しているが、皿状やすり鉢状でもよい。
平板部5aの中心孔5a1には、アウタチューブ1aの細径部1a1が挿通される。
一方、ピストンロッド1bに挿通して略円環状の上側スプリングシート6が備えられている。上側スプリングシート6は不図示の車体に固定されている。下側スプリングシート5、上側スプリングシート6は、プレス成形品である。
下側スプリングシート5と上側スプリングシート6との間には、懸架スプリング2が懸架されている。懸架スプリング2は、圧縮変形することで伸長方向に弾性力を発生させる圧縮コイルばねである。
懸架スプリング2の下端部には、ばねとして機能(弾性変形)しない下座巻き部2sが形成される。同様に、懸架スプリング2の上端部には、ばねとして機能(弾性変形)しない上座巻き部2uが形成されている。
懸架スプリング2の上座巻き部2uと中央部の有効部2yとの間には、上立ち上がり部2vが形成されている。上立ち上がり部2vは、下立ち上がり部2tと同様、上座巻き部2uからスパイラル形状に所定の勾配で立ち上がって形成され、印加される圧縮荷重により弾性変形をする。
図1に示すように、下側スプリングシート5と懸架スプリング2の下端部との間には、ロアラバーパッド3が介装されている。同様に、上側スプリングシート6と懸架スプリング2の上端部との間には、アッパラバーパッド4が介装されている。
ロアラバーパッド3は、NR(天然ゴム)などのゴムで成形されている。
ロアラバーパッド3は、図2Aに示すように、懸架スプリング2を軸方向から見た形状に沿う円環状の一部を成す形状を有し、かつ、懸架スプリング2の下座巻き部2sおよび下立ち上がり部2t(図1参照)との隙間をなくす(埋める)ように立ち上がる形状を有している。
そして、基端部3aとスロープ部3sの間には、懸架スプリング2を保持するスプリング保持部3oを有している。基端部3aは、懸架スプリング2の終端部が挿入され装着される。
図1に示すように、懸架スプリング2はスパイラル状に所定の勾配で立ち上がる下立ち上がり部2tを有している。ロアラバーパッド3は、懸架スプリング2の下座巻き部2sおよび下立ち上がり部2tの一部を保持する略0.6巻~0.9巻分に相当する長さとしているので、ロアラバーパッド3の材料費などの製造コストを低減することができる。なお、ロアラバーパッド3の長さは、下座巻き部2sおよび下立ち上がり部2tの一部または全部を保持する長さに設定してもよい。
そのため、図2Aに示すように、ロアラバーパッド3は、懸架スプリング2の下座巻き部2sから下立ち上がり部2t(図1参照)の一部を受ける形状を有している。
ここで、図1のA-A断面とは、ロアラバーパッド3に懸架スプリング2を装着した際に、懸架スプリング2の巻線方向に沿った断面である。
図3Cは、懸架スプリング2の負荷が突発的に最も小さくなった際の懸架スプリング2およびロアラバーパッド3の状態である。
図3Dは、懸架スプリング2への負荷が最も大きくなった際の懸架スプリング2およびロアラバーパッド3の状態である。
図3Aに示すように、ロアラバーパッド3は、懸架スプリング2の下座巻き部2sを受ける部分の基端部3aを含む平坦部3hは、懸架スプリング2の下座巻き部2sの形状に応じて厚みを変化させて形成されている。つまり、平坦部3hは、懸架スプリング2の下座巻き部2sに当接または接触するように厚みが変化されている。
ここで、懸架スプリング2が変形した場合、下立ち上がり部2tは、下座巻き部2sから離膈するにつれて変形量が次第に大きくなる。そのため、懸架スプリング2の下立ち上がり部2tが当接するスロープ部3sは、平坦部3hから離膈するにつれて変形量が大きくなる。
図2A、図3Aに示すように、スロープ部3sの端縁には、スロープ部3sの上部から外方に延びて懸架スプリング2の下立ち上がり部2tに接触または当接して延びるリップ部Lが設けられている。
リップ部Lは、懸架スプリング2の軸方向視でリップ基端部L2から先端部L1にかけて幅寸法bは、ほぼ同じ寸法である。
リップ部Lが懸架スプリング2に接触または当接し続けることで、図3C、図3Dに示すように、砂利、小石などの異物jが、外側にはじかれ、ロアラバーパッド3と懸架スプリング2との間に入ることが抑制される。
1.懸架スプリング2の下端部を受けるロアラバーパッド3のスロープ部3sの端部に、懸架スプリング2の変形に拘わらず、懸架スプリング2の下立ち上がり部2tに、弾性変形による弾性力によって接触し続けるリップ部Lを形成したので、ロアラバーパッド3が懸架スプリング2の変形に追従することができる。
そのため、懸架スプリング2とロアラバーパッド3のスロープ部3sの端部との間に空隙ができない。
従って、懸架スプリング2とロアラバーパッド3のスロープ部3sとの間に、砂、砂利等の異物jが侵入せず(図3C、図3D参照)、懸架スプリング2が傷付き毀損することが抑制される。
なお、懸架スプリング2の巻線方向以外の方向からロアラバーパッド3と懸架スプリング2との間に入ろうとする異物jはロアラバーパッド3の側壁3iに衝突または当接し、間に入ることが抑制される。
懸架スプリング2の下立ち上がり部2tの変形量は、中央部の有効部2yに近付くに従って大きくなり、ロアラバーパッド3のスロープ部3sが、懸架スプリング2の下立ち上がり部2tに沿って変形量が増加する。しかしながら、ロアラバーパッド3のスロープ部3sが、懸架スプリング2の下立ち上がり部2tに沿って容積が大きくなるため、ロアラバーパッド3の単位容積当たりの変形量を均等に近付けることが可能である。
そのため、ロアラバーパッド3の単位容積当たりに発生する応力が均等化され、ロアラバーパッド3の経時劣化を抑制することができる。従って、ロアラバーパッド3の長寿命化を図れる。結果、懸架スプリング2とロアラバーパッド3のユニットとして市場での耐久性、信頼性、寿命が向上する。
図4Aは、実施形態2の図1のA-A断面相当図であり、 図4Bは、実施形態2の懸架スプリングの負荷が最も小さくなった場合の図1のA-A断面相当図であり、図4Cは、実施形態2の懸架スプリングの負荷が最も大きくなった場合の図1のA-A断面相当図である。
図4Aは、実施形態2において、懸架スプリング2がフルリバウンド、つまり懸架スプリング2に車体の荷重のみが加わった懸架スプリング2およびロアラバーパッド13の状態である。
図4Bは、実施形態2において、懸架スプリング2の負荷が最も小さくなった際の懸架スプリング2およびロアラバーパッド13の状態である。
図4Cは、実施形態2において、懸架スプリング2への負荷が最も大きくなった際の懸架スプリング2およびロアラバーパッド13の状態である。
これ以外の構成は、実施形態1と同様であるので、同一の構成要素には、同一の符号を付して示し、詳細な説明は省略する。
リップ部2Lのリップ機能とは、リップ部2Lが、図4B、図4Cに示すように、懸架スプリング2の下立ち上がり部2tの動きに追随して該下立ち上がり部2tに接触または当接するように回動または揺動する動作をいう。リップ機能の中心とは、リップ部2Lの当該回動または揺動動作の中心である。
半径r11は、リップ部2Lと懸架スプリング2との摺動距離が最小に近付くように設定するのが望ましい。
または、リップ部2Lと懸架スプリング2との摺動距離が最小となるように、リップ部2Lの長さ、幅、厚さ寸法、形状の少なくとも何れかを設定することが望ましい。
側面視で、端縁壁13s1を、あたかもCの字形状に形成することで、懸架スプリング2の軸方向(図4Aの上下方向)に、上からリップ部2Lと伸縮変形部13Hと太支持部13Jとが形成される。
なお、伸縮変形部13Hは、ロアラバーパッド13の下部に形成される下部空間13kとの兼ね合いで形状が決定される。
そして、リップ部2Lと懸架スプリング2との摺動距離が小さくなるように設定するので、懸架スプリング2の塗装の剥がれ、損耗等を阻止し、懸架スプリング2の塗装を可及的に保持、維持することができる。従って、懸架スプリング2の塗装の長寿命化を図れる。
また、リップ部2Lの摩耗が抑えられ、リップ部2Lの長寿命化を図れる。
そのため、懸架スプリング2の損壊、ロアラバーパッド13の損耗等が阻止できる。
従って、懸架スプリング2、ロアラバーパッド13の取り換え等のメンテナンス作業が回避され、懸架スプリング2とロアラバーパッド13の耐久性、信頼性を高めることができる。
なお、実施形態1の作用効果は同様に奏する。
図5Aは、実施形態3の図1のA-A断面相当図であり、 図5Bは、実施形態3の懸架スプリングの負荷が小さくなった場合の図1のA-A断面相当図であり、図5Cは、実施形態3の懸架スプリングの負荷が最も大きくなった場合の図1のA-A断面相当図である。
図5Aは、実施形態3において、懸架スプリング2がフルリバウンド、つまり懸架スプリング2に車体の荷重のみが加わった懸架スプリング2およびロアラバーパッド23の状態である。
図5Bは、実施形態3において、懸架スプリング2の負荷が最も小さくなった際の懸架スプリング2およびロアラバーパッド23の状態である。
図5Cは、実施形態3において、懸架スプリング2への負荷が最も大きくなった際の懸架スプリング2およびロアラバーパッド23の状態である。
これ以外の構成は、実施形態1と同様であるので、同一の構成要素には、同一の符号を付して示し、詳細な説明は省略する。
リップ部3Lのリップ機能とは、リップ部3Lが、図5B、図5Cに示すように、懸架スプリング2の下立ち上がり部2tの動きに追随して該下立ち上がり部2tに接触または当接するように回動または揺動する動作をいう。リップ機能の中心とは、リップ部3Lの当該回動または揺動動作の中心である。
この構成により、図5A、図5Bの側面視で示すように、スロープ部23sのリップ部3Lおよび下立ち上がり部2tが形成される端縁壁23s1の形状はあたかもSの字形状に形成される。
または、リップ部3Lと懸架スプリング2との摺動距離が最小となるように、リップ部3Lの長さ、幅、厚さ寸法の少なくとも何れかを設定することが望ましい。
一方、リップ部3Lの下方に、伸縮変形部23Hと、荷重受け部23s2とが形成されている。
なお、伸縮変形部23Hは、ロアラバーパッド23の下部に形成される下部空間23kとの兼ね合いで形状が決定される。
そのため、図5Cに示すように、懸架スプリング2の負荷(ばね荷重)がロアラバーパッド23に印加された場合に、スロープ部23sの端部に形成される荷重受け部23s2で受けられ、負荷が荷重受け部23s2に分散される。そのため、ロアラバーパッド23での発生する応力が低減され、ロアラバーパッド23の耐久性の向上に資することができる。
なお、荷重受け部23s2は、懸架スプリング2の負荷(ばね荷重)を受けられる形状であれば、懸架スプリング2の軸方向または該軸方向に垂直な方向に軸をもつ円柱状に形成してもよいし、球状に形成してもよい。或いは、角柱状に形成してもよいし、その形態は限定されず任意に選択できる。
また、リップ部3Lの摩耗が抑えられ、リップ部3Lの長寿命化を図れる。そのため、ロアラバーパッド23の取り換え等のメンテナンス作業が回避される。
そのため、図5B、図5Cに示すように、懸架スプリング2からの負荷に拘わらず、より確実にリップ部3Lが懸架スプリング2に接触または当接し続けることができる。
加えて、懸架スプリング2の負荷(ばね荷重)がロアラバーパッド23に印加された場合、スロープ部23sに形成される容積が大きい荷重受け部23s2で確実に受けられる。そのため、ロアラバーパッド23に加わる負荷が、容積が大きい荷重受け部23s2で分散される。従って、ロアラバーパッド23に発生する応力が負荷の分散により低減され、ロアラバーパッド23の耐久性を向上でき、ロアラバーパッド23の長寿命化を図れる。
その結果、市場でのユニットとしてのロアラバーパッド23の耐久性、信頼性が向上する。
さらに、荷重受け部23s2がリップ部3Lよりも懸架スプリング2の巻線方向に突出して形成される。そのため、リップ部3Lが懸架スプリング2により下方に押圧された場合にも荷重受け部23s2に当たって弾力性をもって受け止められ、リップ部3Lが傷付くことが防止される。結果、市場でのサービスマンによる交換、メンテナンス等による作業、工数低減が図れる。
また、本実施形態3と異なり、リップ部3Lの基端部3L2が側面視で直角または凹状の鋭角の角部で形成される場合には、該角部の応力集中による破断、損耗が懸念される。
なお、実施形態1の作用効果は同様に奏する。
例えば、リップ部L、2L、3L、10L、20Lを、懸架スプリング2の下立ち上がり部2tの延在方向に延ばして形成し、下立ち上がり部2tに上下変形しつつ(上下動しつつ)、接触または当接するようにして、摺動距離を短くする。
或いは、リップ部L、2L、3L、10L、20Lを、懸架スプリング2の下立ち上がり部2tの変形に際して、下立ち上がり部2tのほぼ同じ箇所に弾性力をもって接触または当接するに形成して、下立ち上がり部2tに対する摺動距離を短くなるようにするとよい。
13J 太支持部(荷重受け部)
2s 下座巻き部(座巻き部)
2t 立ち上がり部(下立ち上がり部)
2u 上座巻き部
2v 上立ち上がり部
2y 有効部
3 ロアラバーパッド(下側ばね受け部材)
3h、13h、23h 平坦部
3s、13s、23s スロープ部
4 アッパラバーパッド(上側ばね受け部材)
23s2 荷重受け部
h2 厚さ
L、2L、3L、10L、20L リップ部(接触部)
r11 半径(曲率半径)
r12 摺動半径(摺動する際の半径)
w1、w2、w3 幅寸法(幅)
13H、23H 伸縮変形部
Claims (9)
- 有効部、弾性変形しない端部の座巻き部、および前記有効部と前記座巻き部との間の立ち上がり部を有する圧縮スプリングを、下側で受ける下側ばね受け部材であって、
その延在方向の一方側の端部から外方に突出して形成されて前記立ち上がり部との間に空隙ができないように前記立ち上がり部に接触する接触部を有し、
前記接触部は、
前記圧縮スプリングによる負荷に拘わらず、その弾性変形による弾性力によって前記立ち上がり部に接触する
ことを特徴とする下側ばね受け部材。 - 請求項1に記載の下側ばね受け部材において、
その延在方向の一方側の端部の前記接触部の反対側に外方に突出する形状に形成され、前記圧縮スプリングのばね荷重を受ける荷重受け部を備える
ことを特徴とする下側ばね受け部材。 - 請求項1または請求項2に記載の下側ばね受け部材において、
前記一方側の端部の前記接触部と荷重受け部との間に設けられ、前記圧縮スプリングの負荷に応じて伸縮変形する伸縮変形部を備え、
前記伸縮変形部は、前記荷重受け部より細い形状を有する
ことを特徴とする下側ばね受け部材。 - 請求項2に記載の下側ばね受け部材において、
前記荷重受け部は、凸形状の曲率を有して外方に膨出した形状に形成されている
ことを特徴とする下側ばね受け部材。 - 請求項2または請求項4に記載の下側ばね受け部材において、
前記荷重受け部は、
前記圧縮スプリングの軸方向視で、前記接触部より、前記圧縮スプリングの巻線方向に外方に突出して形成されている
ことを特徴とする下側ばね受け部材。 - 請求項1に記載の下側ばね受け部材において、
前記平坦部に連続して形成され、前記立ち上がり部に沿って厚さが次第に厚くなり、前記立ち上がり部を受けるスロープ部とを備える
ことを特徴とする下側ばね受け部材。 - 請求項6に記載の下側ばね受け部材において、
前記圧縮スプリングの延在方向に見た前記スロープ部の幅は、前記座巻き部から遠ざかるに従って広くなる
ことを特徴とする下側ばね受け部材。 - 請求項1または請求項2または請求項4または請求項6または請求項7の何れか一項に記載の下側ばね受け部材において、
前記接触部は、
前記立ち上がり部の変形に際して、前記立ち上がり部のほぼ同じ箇所に接触または当接している
ことを特徴とする下側ばね受け部材。 - 請求項1または請求項2または請求項4または請求項6または請求項7のうちの何れか一項に記載の下側ばね受け部材において、
前記圧縮スプリングを一方側の前記下側ばね受け部材とともに受ける他方側の上側ばね受け部材は、前記下側ばね受け部材と対称的な同様な構成である
ことを特徴とする下側ばね受け部材。
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DE102016206891B3 (de) * | 2016-04-22 | 2017-04-27 | Zf Friedrichshafen Ag | Hydropneumatisches Federbein |
CN108263158B (zh) * | 2018-02-02 | 2023-06-02 | 中国北方车辆研究所 | 一种减小螺旋弹簧上绞座自由度的专用限位块及其安装结构 |
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JP2019157945A (ja) * | 2018-03-09 | 2019-09-19 | 中央発條株式会社 | 懸架装置用スプリング |
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JP7010733B2 (ja) | 2018-03-09 | 2022-01-26 | 中央発條株式会社 | 懸架装置用スプリング |
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CN107250597B (zh) | 2022-04-01 |
EP3260729B1 (en) | 2021-03-31 |
JP6615857B2 (ja) | 2019-12-04 |
US10704634B2 (en) | 2020-07-07 |
EP3260729A1 (en) | 2017-12-27 |
CN107250597A (zh) | 2017-10-13 |
CA2976751C (en) | 2019-04-02 |
HUE054294T2 (hu) | 2021-08-30 |
US20180038437A1 (en) | 2018-02-08 |
BR112017017577B1 (pt) | 2022-10-18 |
JPWO2016132926A1 (ja) | 2017-11-24 |
MX2017010585A (es) | 2018-06-27 |
CA2976751A1 (en) | 2016-08-25 |
BR112017017577A2 (ja) | 2018-05-08 |
EP3260729A4 (en) | 2018-11-14 |
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