CN116104864A - Thrust bearing device and macpherson suspension for vehicle - Google Patents

Thrust bearing device and macpherson suspension for vehicle Download PDF

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Publication number
CN116104864A
CN116104864A CN202211273228.9A CN202211273228A CN116104864A CN 116104864 A CN116104864 A CN 116104864A CN 202211273228 A CN202211273228 A CN 202211273228A CN 116104864 A CN116104864 A CN 116104864A
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CN
China
Prior art keywords
diameter side
concave portion
side concave
inner diameter
thrust bearing
Prior art date
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Pending
Application number
CN202211273228.9A
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Chinese (zh)
Inventor
池口昌吾
楢崎康弘
园田泰久
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Nakanishi Metal Works Co Ltd
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Nakanishi Metal Works Co Ltd
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Publication of CN116104864A publication Critical patent/CN116104864A/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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7806—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for spherical roller bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Fluid-Damping Devices (AREA)
  • Rolling Contact Bearings (AREA)
  • Vehicle Body Suspensions (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

The invention prevents the decrease of sealing performance and does not reduce the drainage performance of muddy water and the like which temporarily invade the inside. The thrust bearing device includes a thrust bearing and an upper spring seat. The thrust bearing includes upper and lower housings, upper and lower rail wheels, rolling elements rolling between the upper and lower rail wheels, and a seal located radially outward of the rolling elements. The upper spring seat is in contact with the lower housing. The radial inner side of the axial gap between the upper housing and the upper spring seat has an outer diameter side concave portion formed by the lower housing and the upper spring seat, and an inner diameter side concave portion formed by descending stepwise from the outer diameter side concave portion to the radial inner side. The inner diameter side concave portion blocks muddy water or the like which intrudes from the axial slit to the radial inner side.

Description

Thrust bearing device and macpherson suspension for vehicle
Technical Field
The present invention relates to a thrust bearing device for a macpherson suspension of a vehicle.
Background
As a suspension that supports a wheel with respect to a vehicle body by a coil spring and is provided with a damper for absorbing up-and-down vibration, there is a macpherson suspension (strut) that is formed by fixing a column (support rod) in which the damper is built to an axle.
As a thrust bearing (strut bearing) device for use in an upper portion of a macpherson suspension, there is a thrust bearing device having a synthetic resin upper side case (for example, an upper side cap 3 of patent document 1) that holds an upper side rail wheel, a synthetic resin lower side case (for example, a lower side cap 4 of patent document 1) that holds a lower side rail wheel, an inner diameter side seal material (for example, an inner diameter side seal 6 of patent document 1) that is provided in an elastic material of the lower side case, and an outer diameter side seal material (for example, an outer diameter side seal 7 of patent document 1) (for example, refer to patent document 1).
Patent document 1: U.S. Pat. No. 10,753,389 Specification
Such thrust bearing devices are used in a severe muddy water environment such as those directly receiving muddy water on a road surface on which wheels are splashed. When the high-pressure washer is used for washing a vehicle, the thrust bearing device receives high-pressure water discharged from the high-pressure washer during washing of the wheel shaft.
Therefore, in the thrust bearing device of patent document 1, for example, if high-speed water such as muddy water enters a gap between the upper cap 3 and the lower cap 4 from the outer diameter side, the water rises along the outer peripheral surface of the lower cap 4, and is not sufficiently decelerated, so that the outer seal 7 may be wet, and thus the sealability may be lowered.
In addition, in the case of adopting a labyrinth structure for decelerating the high-speed water entering from the gap, the structure becomes complicated, and the drainage of muddy water or the like temporarily entering the inside is lowered.
Disclosure of Invention
The invention aims to provide a thrust bearing device which can inhibit the reduction of sealing performance and can not reduce the drainage performance of an invaded object such as muddy water which temporarily invades the inside.
The gist of the present invention is as follows.
The thrust bearing device of [ 1] comprises: a thrust bearing; and an upper spring seat which is a spring support member for supporting an upper end of the coil spring,
wherein,,
the thrust bearing includes:
an upper case and a lower case;
an upper side rail wheel held by the upper side housing;
a lower side rail wheel held by the lower side housing; ,
a rolling element rolling between the upper side rail wheel and the lower side rail wheel; and
a seal member located radially outward of the rolling element,
the upper spring seat contacts the lower housing,
an outer diameter side concave portion and an inner diameter side concave portion are formed on the radial inner side of the axial gap between the upper housing and the upper spring seat, the outer diameter side concave portion and the inner diameter side concave portion are formed by the lower housing and the upper spring seat, the inner diameter side concave portion is formed to descend stepwise from the outer diameter side concave portion to the radial inner side,
the inner diameter side concave portion blocks an intrusion such as muddy water which intrudes from the axial slit to the radially inner side.
[ 2] A thrust bearing device is provided with:
an upper case and a lower case;
an upper side rail wheel held by the upper side housing;
a lower side rail wheel held by the lower side housing;
a rolling element rolling between the upper side rail wheel and the lower side rail wheel; and
a seal member located radially outward of the rolling element,
wherein,,
the lower case is mainly made of synthetic resin with a core bar, and has a cylindrical portion and a circular ring portion extending radially outward from an upper portion of the cylindrical portion, and functions as a spring supporting member for supporting an upper end of the coil spring,
an outer diameter side concave portion and an inner diameter side concave portion formed in the lower case are provided on a radial inner side of an axial gap between the upper case and the lower case, and the inner diameter side concave portion is formed so as to be stepped down from the outer diameter side concave portion to the radial inner side,
the inner diameter side concave portion blocks an intrusion such as muddy water which intrudes from the axial slit to the radially inner side.
The thrust bearing device according to [ 1] or [ 2], wherein,
the radial length of the inner diameter side concave part is larger than or equal to the axial gap,
the position of the upper end of the inlet of the inner diameter side concave part is higher than the position of the upper end of the axial gap.
[ 4 ] A Macpherson suspension for a vehicle comprising the thrust bearing device according to any one of [ 1] to [ 3 ]
According to the thrust bearing device and the macpherson suspension for a vehicle of the present invention described above, the radially inner side of the axial gap between the upper housing and the upper spring seat or the radially inner side of the axial gap between the upper housing and the lower housing has the outer diameter side concave portion and the inner diameter side concave portion that is stepped down from the outer diameter side concave portion to the radially inner side. The inner diameter side concave portion blocks penetration of muddy water and the like penetrating from the axial slit to the radially inner side.
When high-speed water such as muddy water enters the axial gap, the high-speed water first enters the inner diameter side concave portion located radially inward of the axial gap, passes through the outer diameter side concave portion, and approaches the outer diameter side seal. Therefore, the high-speed water is temporarily stopped by the inner diameter side concave portion and greatly decelerated, and further decelerated by the outer diameter side concave portion and approaches the outer diameter side seal, so that the decrease in the sealability of the outer diameter side seal can be suppressed.
Further, since the labyrinth structure is not provided, but only the outer diameter side concave portion and the inner diameter side concave portion are provided, the structure is not complicated, the structure can be simplified, and the drainage of an intruding object such as muddy water temporarily intruding into the inside is not reduced.
Drawings
Fig. 1 is a schematic view, partly in section, of a macpherson suspension for a vehicle provided with a thrust bearing device according to embodiment 1 of the present invention.
Fig. 2 is an enlarged longitudinal sectional view showing a main portion of the thrust bearing device and the spring spacer.
Fig. 3 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing modification 1.
Fig. 4 is an enlarged longitudinal sectional view of the same main part as fig. 2, showing modification 2.
Fig. 5 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing modification 3.
Fig. 6 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing a modification 4.
Fig. 7 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing a modification 5.
Fig. 8 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing modification 6.
Fig. 9 is an enlarged longitudinal sectional view of the same main part as fig. 2 showing a modification 7.
Fig. 10 is an enlarged longitudinal cross-sectional view of a main part of an example showing a change in the flow rate of water entering from an axial gap in a thrust bearing device having an outer diameter side recess and an inner diameter side recess.
Fig. 11 is an enlarged longitudinal cross-sectional view of a main part of an example showing a change in the flow rate of water entering through an axial gap in a conventional thrust bearing device.
Fig. 12 is a graph showing the analysis results of the flow rate of water entering from the axial slit in one example of an analysis model of the thrust bearing device having the outer diameter side concave portion and the inner diameter side concave portion.
Fig. 13 is an enlarged longitudinal sectional view showing a main part of a thrust bearing device according to embodiment 2 of the present invention.
Description of the reference numerals
1 thrust bearing 2 upper side housing 3 lower side housing
Upper side rail wheel of 3A cylindrical part 3B annular part 4
5 lower side rail wheel 6 rolling element 7 retainer
8 inner diameter side seal 9 outer diameter side seal 10 support rod
11 coil spring 12 dust cover 13 spring support member
14 upper spring seat 15 spring spacer 16 upper fixing piece
A. B thrust bearing device C1, C2 axial gap
D recess DO outer diameter side recess
DI inner diameter side concave E core bar
F position G of the inlet upper end of the inner diameter side concave portion is the position of the upper end of the axial slit
Depth (radial length) of H inner diameter side concave part J axial direction
Axial length of entrance of inner diameter side concave part of K inner side protruding piece L
Radial length of M outer diameter side recess N radial length of recess
O rotary shaft
Axial distance between the outer diameter side seal side end of the P outer diameter side concave portion and the upper spring seat
Axial distance between outer diameter side seal side end of Q recess and upper spring seat
R radial RI radial inner side
RO radial outside S McPherson suspension
Detailed Description
Embodiments according to the present invention will be described below with reference to the drawings.
In the present specification, a direction parallel to the rotation axis O (see fig. 1) of the thrust bearing 1 is referred to as an "axial direction" (see, for example, arrow J of fig. 1), a direction orthogonal to the rotation axis O is referred to as a "radial direction" (see, for example, arrow R of fig. 1), a radial direction approaching the rotation axis O is referred to as a "radial inner side" (see, for example, arrow RI of fig. 1), and a radial direction away from the rotation axis O is referred to as a "radial outer side" (see, for example, arrow RO of fig. 1).
Embodiment 1
Macpherson suspension
The macpherson suspension S of the vehicle shown in the partially cut-away schematic view of fig. 1 is used in a state in which the telescopic support rod 10 having a damper incorporated therein is fixed to an unillustrated axle and the upper mount 16 is fixed to the vehicle body.
A thrust bearing 1 is provided at an upper portion of the macpherson suspension S, and the thrust bearing 1 swings while supporting the vehicle body, and the amount of swing rotation corresponds to the amount by which the steering wheel changes direction in accordance with the steering operation. The pivot angle of the thrust bearing 1 is determined in accordance with the allowable steering angle of the wheel, and is set in a range of 40 ° to 50 °.
A coil spring 11 as a suspension spring and a dust cover 12 for protecting an oil seal of the damper from foreign matter such as sand are provided on the radial outside RO of the support rod 10. The macpherson suspension S includes a spring support member 13 that supports an upper end of the coil spring 11. As shown in an enlarged longitudinal sectional view of the main part of fig. 2, the spring support member 13 is composed of an upper spring seat 14 and a spring spacer 15.
< thrust bearing device >)
As shown in the schematic view of fig. 1 and the longitudinal cross-sectional view of fig. 2, the thrust bearing device a according to embodiment 1 of the present invention includes a thrust bearing 1 and an upper spring seat 14, and the upper spring seat 14 is a spring support member 13 that supports the upper end of the coil spring 11.
The thrust bearing 1 includes upper and lower housings 2 and 3, upper and lower rail wheels 4 and 5, rolling elements 6, a retainer 7, an inner diameter side seal 8, an outer diameter side seal 9, and the like.
The upper housing 2 is fixed to the upper end of the support rod 10, and the lower housing 3 receives the upper spring seat 14 from above. The upper side rail wheel 4 is held by the upper side housing 2, and the lower side rail wheel 5 is held by the lower side housing 3. The rolling elements 6 roll between the upper rail wheel 4 and the lower rail wheel 5, and the retainer 7 holds such that the adjacent rolling elements 6 do not contact each other.
The inner diameter side seal 8 is located on the radially inner side RI of the rolling elements 6, and the outer diameter side seal 9 is located on the radially outer side RO of the rolling elements 6.
The upper rail 4, the lower rail 5, and the upper spring seat 14 are made of steel, and are formed from a steel plate by press working, and are quench-hardened after working. The upper case 2 and the lower case 3 are made of synthetic resin, and the inner diameter side seal 8 and the outer diameter side seal 9 are made of an elastic material.
The synthetic resin used for the upper case 2 and the lower case 3 is, for example, polyamides (PA 66, PA46, PA612, PA6, PA9T, PA T, etc.), and the reinforcing fibers contain, for example, 20 to 60 wt% Glass Fibers (GF).
The elastic material used for the inner diameter side seal 8 and the outer diameter side seal 9 is TPS (styrenes), TPOs (olefins), TPU (urethanes), TPA (amines), TPEE (esters) or the like as a thermoplastic elastic material (TPE), and nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), acrylate rubber (ACM), ethylene acrylate rubber (AEM), fluororubber (FKM, FPM), silicone rubber (VQM) or the like as a rubber material. The rubber material may be used by mixing one or two or more kinds of rubber as appropriate.
< outer diameter side concave portion and inner diameter side concave portion >)
As shown in the enlarged longitudinal sectional view of the main part of fig. 2, the thrust bearing device a has an outer diameter side concave portion DO formed by the lower housing 3 and the upper spring seat 14 and an inner diameter side concave portion DI formed by descending stepwise from the outer diameter side concave portion DO to the radially inner side in a radial direction inside of an axial gap C1 between the upper housing 2 and the upper spring seat 14. The inner diameter side concave portion DI blocks intrusion of muddy water or the like from the axial slit C1 toward the radially inner side RI.
The inner diameter side concave portion DI in fig. 2 has a circular ring shape, and a longitudinal section of the inner diameter side concave portion DI along the radial direction R has a substantially triangular shape. The upper surface of the inner diameter side concave portion DI is a substantially horizontal surface formed by the lower housing 3, and the lower surface of the inner diameter side concave portion DI is an inclined surface formed by the upper spring seat 14 that rises as it moves toward the radial inner side RI.
The inside diameter side concave portion DI may be the shape of the 1 st modification shown in the enlarged longitudinal section of fig. 3, the 2 nd modification shown in the enlarged longitudinal section of fig. 4, the 3 rd modification shown in the enlarged longitudinal section of fig. 5, the 4 th modification shown in the enlarged longitudinal section of fig. 6, the 5 th modification shown in the enlarged longitudinal section of fig. 7, the 6 th modification shown in the enlarged longitudinal section of fig. 8, or the like. The inner diameter side concave portions DI shown in fig. 3 to 8 are all connected in an annular shape as in the inner diameter side concave portion DI shown in fig. 2.
As in the inner diameter side concave portion DI of fig. 2, the inner diameter side concave portion DI of modification 1 of fig. 3 has a substantially triangular shape in longitudinal section along the radial direction R, but the upper surface of the inner diameter side concave portion DI is an inclined surface which decreases as going inward in the radial direction RI, and the lower surface of the inner diameter side concave portion DI is a substantially horizontal surface. In the inner diameter side concave portion DI of fig. 4 as modification 2, a longitudinal section of the inner diameter side concave portion DI along the radial direction R is substantially rectangular, and an upper surface and a lower surface of the inner diameter side concave portion DI are substantially horizontal surfaces. In the inner diameter side concave portion DI of fig. 5 as modification 3, a vertical section of the inner diameter side concave portion DI along the radial direction R is substantially trapezoidal, an outer diameter side portion of an upper surface of the inner diameter side concave portion DI is substantially horizontal, an inner diameter side portion of the upper surface of the inner diameter side concave portion DI is an inclined surface which descends as proceeding toward the radial direction inner side RI, and a lower surface of the inner diameter side concave portion DI is substantially horizontal.
In the inner diameter side concave portion DI of fig. 6 as modification 4, a longitudinal section of the inner diameter side concave portion DI along the radial direction R is substantially in a parallelogram shape, and an upper surface and a lower surface of the inner diameter side concave portion DI are inclined surfaces that rise as they move toward the radial direction inner side RI. In the inner diameter side concave portion DI of fig. 7 as the 5 th modification, the outer diameter side portion of the inner diameter side concave portion DI is substantially parallelogram shaped as in the 4 th modification (fig. 6), and the inner diameter side portion of the inner diameter side concave portion DI is substantially rectangular shaped as in the 2 nd modification (fig. 4). The inner diameter side concave portion DI of fig. 8, which is a modification 6, is formed in a shape in which an inner diameter side portion of the inner diameter side concave portion DI of a modification 4 (fig. 6) extends upward so that a longitudinal section along the radial direction R is formed in a substantially rectangular shape.
The inner diameter side concave portion DI may be a shape different from the shape shown in the enlarged longitudinal sectional view of the main part of fig. 2 to 8, or may be a shape not connected in the circumferential direction in a circular shape.
The depth (length in the radial direction R) H of the inner diameter side concave portion DI shown in fig. 2 to 8 is equal to or greater than the axial slit C1 (h≡c1), and the position F of the inlet upper end of the inner diameter side concave portion DI is higher than the position G of the upper end of the axial slit C1. Accordingly, high-speed water entering from the axial slit C1 easily enters the inner diameter side concave portion DI, and the high-speed water easily decelerates.
By making the position F of the upper end of the inlet of the inner diameter side concave portion DI higher than the position G, the axial length L of the inlet of the inner diameter side concave portion DI becomes equal to or greater than the axial gap C1 (l≡c1) in the examples of fig. 2, 6 to 8, and the axial length L is greater than the axial gap C1 (L > C1) in the examples of fig. 3 to 5. Further, according to the analysis results shown below, L.ltoreq.2.0X1 is more preferable. Further, based on the analysis results shown below, the radial length H of the inner diameter side concave portion DI is more preferably H.gtoreq.2.5XC1. The inner diameter side end of the inner diameter side concave portion DI is located radially outward RO of the pitch diameter of the rolling elements 6 in order to suppress deformation of the lower case 3 due to the load received from the rolling elements 6.
In fig. 2 to 8 as embodiment 1, the upper case 2 has an annular inner protruding piece K protruding toward the radial inner RI at the lower end of the radial outer RO. The inner tabs K are intermittently arranged and are arranged at one or more places on the circumference. The inner protrusion K engages with the outer diameter side recess DO to prevent the separation of the upper case 2 and the lower case 3. In the thrust bearing device a according to embodiment 1, the inner protruding piece K may be omitted as in the 7 th modification shown in the enlarged longitudinal cross-sectional view of the main part of fig. 9, and in this case, a separation preventing structure, not shown, may be provided on the inner diameter side.
Comparison of flow Rate of muddy water etc. based on the presence or absence of intrusion of inner diameter side concave portion
(analytical model)
Based on the presence or absence of the inner diameter side concave portion DI in the shape of fig. 2, a comparison is made of the flow velocity of water entering from the axial slit C1 below the outer diameter side seal 9. That is, an analysis model is created and compared based on fluid analysis. The analytical model having the outer diameter side concave portion DO and the inner diameter side concave portion DI is a model that mimics the shape of fig. 2. The analysis model without the inner diameter side concave portion DI mimics the shape of fig. 2, and the outer peripheral surface of the lower case 3 of fig. 2 is set to the position of the virtual line I, and has the concave portion D having the shape shown in fig. 11.
(analysis conditions)
The environment in water is set for easy analysis. The radial direction R of the injected water is set at a position where the injection port is in contact with the outer diameter (see fig. 1) of the upper spring seat 14, and the axial direction J of the injected water is set at a position where the lower end of the injection port is in contact with the upper end of the outer diameter of the upper spring seat 14. The analysis was performed under the condition that the diameter of the jet port was set to 2mm and high-speed water having a flow rate of 8m/s was jetted from the jet port.
In the analysis model having the outer diameter side concave portion DO and the inner diameter side concave portion DI, the radial length h=2.5 mm (h=2.5×c1) of the inner diameter side concave portion DI is set to 1.0mm in the axial slit c1=1.0 mm shown in fig. 2 and 10, the axial length l=2.0 mm (l=2.0×c1) of the inlet of the inner diameter side concave portion DI is set to 2.0mm in the radial length m=2.0 mm of the outer diameter side concave portion DO shown in fig. 10, and the axial distance p=3.0 mm between the outer diameter side seal 9 side end portion of the outer diameter side concave portion DO and the upper spring seat 14.
In the analysis model without the inner diameter side concave portion DI, the axial gap c1=1.0 mm shown in fig. 11 is set, the radial length n=2.0 mm of the concave portion D, and the axial distance q=3.0 mm between the outer diameter side seal 9 side end portion of the concave portion D and the upper spring seat 14.
(analysis results)
In an example of a change in the flow velocity of water entering through the axial slit C1 (see fig. 2, 10, and 11) in the thrust bearing device a, the flow velocity is set to the length of an arrow, and the case where the outer diameter side concave portion DO and the inner diameter side concave portion DI are provided is shown in an enlarged longitudinal sectional view of a main portion in fig. 10, and the case where the inner diameter side concave portion DI is not provided and only the concave portion D is shown in an enlarged longitudinal sectional view of a main portion in fig. 11. Fig. 12 shows the analysis result of the flow rate of water entering from the "axial slit" in an example of an analysis model of the thrust bearing device having the "outer diameter side concave portion DO and the" inner diameter side concave portion DI ", wherein the flow rate is set to the length of the arrow.
When the flow velocity along the inner surface of the upper case 2 below the outer diameter side seal 9 is 1, the flow velocity of the analysis model having the outer diameter side concave portion DO and the inner diameter side concave portion DI is about 0.1 to about 0.3, and it is found that the deceleration effect by the outer diameter side concave portion DO and the inner diameter side concave portion DI is large. The reason for this is that, when high-speed water enters from the axial slit C1 of the thrust bearing device a having the outer diameter side concave portion DO and the inner diameter side concave portion DI, the high-speed water first enters the inner diameter side concave portion DI located at the position of the radial inner side RI of the axial slit C1, passes through the outer diameter side concave portion DO, and then approaches the outer diameter side seal 9. Therefore, it is considered that this is because the high-speed water is temporarily blocked by the inner diameter side concave portion DI and greatly decelerated, and further decelerated by the outer diameter side concave portion DO.
Embodiment 2
< thrust bearing device >)
In the thrust bearing device B according to embodiment 2 of the present invention shown in an enlarged longitudinal cross-sectional view of a main portion of fig. 13, the same reference numerals as those in fig. 1 to 9 of embodiment 1 denote the same or corresponding parts, portions, or the like.
The lower housing 3 of the thrust bearing 1 as the thrust bearing device B is made of synthetic resin having the core E built therein. The core E is made of steel, and is formed from a steel plate by press working, and is quench-hardened after working as necessary. The lower housing 3 is molded by injection molding with the core E as an insert.
The lower case 3 has a cylindrical portion 3A and an annular portion 3B extending radially outward RO from an upper portion of the cylindrical portion 3A, and has a function as an upper spring seat of a spring support member 13 for supporting an upper end of a coil spring 11 (see fig. 1) by incorporating a core E.
< outer diameter side concave portion and inner diameter side concave portion >)
The thrust bearing device B has an outer diameter side recess DO formed in the lower housing 3 and an inner diameter side recess DI formed by stepwise lowering from the outer diameter side recess DO to the inner diameter side RI between the upper housing 2 and the lower housing 3. The inner diameter side concave portion DI blocks intrusion of muddy water or the like from the axial slit C2 toward the radially inner side RI.
The depth (length in the radial direction R) H of the inner diameter side concave portion DI shown in fig. 13 is equal to or greater than the axial slit C2 (h≡c2), and the position F of the inlet upper end of the inner diameter side concave portion DI is higher than the position G of the upper end of the axial slit C2. Accordingly, high-speed water entering from the axial slit C2 easily enters the inner diameter side concave portion DI, and the high-speed water easily decelerates.
By making the position F of the inlet upper end of the inner diameter side concave portion DI higher than the position G, the axial length L is greater than the axial slit C2 (L > C2). Further, based on the analysis result, L.ltoreq.2.0XC2 is more preferable. Further, based on the analysis result, the radial length H of the inner diameter side concave portion DI is more preferably h.gtoreq.2.5×c2. The inner diameter side end of the inner diameter side concave portion DI is located radially outward RO of the pitch diameter of the rolling elements 6 in order to suppress deformation of the lower casing 3 due to the load received by the rolling elements 6.
< Effect >
In the thrust bearing device a of embodiment 1 and the thrust bearing device B of embodiment 2, when high-speed water such as muddy water enters the axial slits C1 and C2, the high-speed water first enters the inner diameter side concave portion DI located on the radially inner side RI than the axial slits C1 and C2, passes through the outer diameter side concave portion DO, and then approaches the outer diameter side seal 9. Therefore, the high-speed water is temporarily stopped by the inner diameter side concave portion DI and greatly decelerated, and further decelerated by the outer diameter side concave portion DO to approach the outer diameter side seal 9, so that the decrease in the sealability of the outer diameter side seal 9 can be suppressed.
Further, since the labyrinth structure is not provided, but only the outer diameter side concave portion DO and the inner diameter side concave portion DI are provided, the structure is not complicated, the structure can be simplified, and the drainage of an intruding object such as muddy water which temporarily intrudes into the inside is not reduced.
The description of the above embodiments is merely exemplary, and is not limited thereto. Various modifications and alterations can be made without departing from the scope of the invention.
Description of the drawings
Fig. 12: an outer diameter side seal, an inner diameter side recess, an outer diameter side recess, and an axial slit.

Claims (4)

1. A thrust bearing device, comprising:
a thrust bearing; and
an upper spring seat which is a spring support member for supporting an upper end of the coil spring,
the thrust bearing device is characterized in that,
the thrust bearing includes:
an upper case and a lower case;
an upper side rail wheel held by the upper side housing;
a lower side rail wheel held by the lower side housing; ,
a rolling element rolling between the upper side rail wheel and the lower side rail wheel; and
a seal member located radially outward of the rolling element,
the upper spring seat contacts the lower housing,
an outer diameter side concave portion and an inner diameter side concave portion are formed on the radial inner side of the axial gap between the upper housing and the upper spring seat, the outer diameter side concave portion and the inner diameter side concave portion are formed by the lower housing and the upper spring seat, the inner diameter side concave portion is formed to descend stepwise from the outer diameter side concave portion to the radial inner side,
the inner-diameter-side concave portion blocks an intrusion into the radial direction from the axial slit.
2. A thrust bearing device is provided with:
an upper case and a lower case;
an upper side rail wheel held by the upper side housing;
a lower side rail wheel held by the lower side housing;
a rolling element rolling between the upper side rail wheel and the lower side rail wheel; and
a seal member located radially outward of the rolling element,
the thrust bearing is characterized in that,
the lower case is mainly made of synthetic resin with a core bar, and has a cylindrical portion and a circular ring portion extending radially outward from an upper portion of the cylindrical portion, and functions as a spring supporting member for supporting an upper end of the coil spring,
an outer diameter side concave portion and an inner diameter side concave portion formed in the lower case are provided on a radial inner side of an axial gap between the upper case and the lower case, and the inner diameter side concave portion is formed so as to be stepped down from the outer diameter side concave portion to the radial inner side,
the inner-diameter-side concave portion blocks an intrusion into the radial direction from the axial slit.
3. The thrust bearing device according to claim 1 or 2, wherein,
the radial length of the inner diameter side concave part is larger than or equal to the axial gap,
the position of the upper end of the inlet of the inner diameter side concave part is higher than the position of the upper end of the axial gap.
4. A Macpherson suspension for a vehicle, characterized in that,
a thrust bearing device according to any one of claims 1 to 3.
CN202211273228.9A 2021-11-11 2022-10-18 Thrust bearing device and macpherson suspension for vehicle Pending CN116104864A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021-183853 2021-11-11
JP2021183853A JP2023071229A (en) 2021-11-11 2021-11-11 Strut bearing device and strut-type suspension of vehicle

Publications (1)

Publication Number Publication Date
CN116104864A true CN116104864A (en) 2023-05-12

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202211273228.9A Pending CN116104864A (en) 2021-11-11 2022-10-18 Thrust bearing device and macpherson suspension for vehicle

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JP (1) JP2023071229A (en)
CN (1) CN116104864A (en)

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