WO2014203563A1 - 履帯式走行車両の転輪 - Google Patents
履帯式走行車両の転輪 Download PDFInfo
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- WO2014203563A1 WO2014203563A1 PCT/JP2014/054867 JP2014054867W WO2014203563A1 WO 2014203563 A1 WO2014203563 A1 WO 2014203563A1 JP 2014054867 W JP2014054867 W JP 2014054867W WO 2014203563 A1 WO2014203563 A1 WO 2014203563A1
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- WIPO (PCT)
- Prior art keywords
- thrust
- sliding bearing
- roller shell
- slide bearing
- shaft
- Prior art date
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D55/00—Endless track vehicles
- B62D55/08—Endless track units; Parts thereof
- B62D55/14—Arrangement, location, or adaptation of rollers
- B62D55/15—Mounting devices, e.g. bushings, axles, bearings, sealings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D55/00—Endless track vehicles
- B62D55/08—Endless track units; Parts thereof
- B62D55/14—Arrangement, location, or adaptation of rollers
Definitions
- the present invention relates to a wheel of a crawler type traveling vehicle.
- crawler type traveling vehicles such as excavators and bulldozers have been used for work on rough terrain.
- the crawler type traveling vehicle includes idle wheels and drive wheels disposed at front and rear positions on both the left and right sides of the traveling body, and endless crawler belts wound around the drive wheels and idle wheels.
- a plurality of wheels are arranged between the drive wheel and the idler wheel.
- a roller shell that comes into contact with the crawler belt link is rotatably provided on the outer periphery of a cylindrical shaft.
- a bush is provided between the roller shell and the shaft. The bush has a cylindrical portion that receives a load in the radial direction and a flange portion that receives a load in the thrust direction.
- the cylindrical portion and the flange portion are provided with an integral bush, and when the roller wheel rotates, the flange portion is against the boss portion. Slide. If this bush has a structure in which the cylindrical part and the collar part are provided separately, when the wheel rotates, the collar part rotates along with the rotation of the wheel, and the collar part and the wheel rotate. Will slide. Heat is generated by frictional resistance when the collar and the roller slide with high surface pressure. As a result of this heat generation, there is a problem that seizure occurs and the life of the bush is shortened.
- the present invention has been made in view of the above problems, and an object of the present invention is to provide a wheel for a crawler type traveling vehicle in which the sliding wear resistance of the bearing supporting the roller shell is improved.
- the wheel of the crawler type traveling vehicle of the present invention includes a shaft, a roller shell, a collar, a radial sliding bearing, and a thrust sliding bearing.
- the shaft has a cylindrical outer peripheral surface.
- the roller shell is disposed so as to surround a part of the outer peripheral surface in the circumferential direction.
- the roller shell has a cylindrical inner peripheral surface facing the outer peripheral surface and an annular end surface.
- the collar is fixed to the shaft.
- the collar has an annular facing surface facing the end surface.
- the radial plain bearing is disposed between the outer peripheral surface and the inner peripheral surface.
- the thrust slide bearing is disposed between the end surface and the facing surface.
- the thrust slide bearing is provided separately from the radial slide bearing.
- the wheel is provided with a detent structure. The detent structure prevents relative rotation of the thrust slide bearing with respect to the roller shell.
- the relative rotation of the thrust sliding bearing provided separately from the radial sliding bearing with respect to the roller shell is prevented. Therefore, when the roller shell rotates, the thrust slide bearing does not slide with respect to the roller shell but slides with respect to the collar. Since the area where the thrust sliding bearing contacts the collar is larger than the area where the thrust sliding bearing contacts the roller shell, the surface pressure generated when the thrust sliding bearing slides relative to the collar is increased. Get smaller. As a result, it is possible to reduce heat generation during sliding of the thrust slide bearing that supports the roller shell.
- the outer peripheral surface of the shaft has a cylindrical shape with the same diameter from the position where the end surface is disposed to the position where the opposing surface is disposed in the axial direction. In this way, at the position where the thrust slide bearing is provided, no step is formed on the outer peripheral surface of the shaft to receive the thrust load, and the shaft is a cylindrical straight with the same outer diameter. It has the shape of a shaft. By forming the shaft in such a shape, the shaft can be easily manufactured.
- the rotation preventing structure is a joint by engagement between a convex portion formed on one of the roller shell and the thrust slide bearing and a concave portion formed on the other.
- the radial sliding bearing and the thrust sliding bearing are formed of different materials.
- the thrust slide bearing that slides at a relatively high surface pressure can be formed of a material that can withstand the high surface pressure, so that the life of the thrust slide bearing can be further extended.
- the thrust slide bearing forming material has higher hardness than the radial slide bearing forming material. If it does in this way, a thrust slide bearing can be provided in the specification which can endure higher surface pressure.
- the thrust slide bearing has an annular plate-shaped main body portion having an annular main surface, and a convex portion that is formed integrally with the main body portion and protrudes from the main surface. In this way, the thrust slide bearing can be reliably prevented from rotating with respect to the roller shell by the engagement between the projection formed on the thrust slide bearing and the recess formed on the roller shell.
- the area where the thrust sliding bearing contacts the end face of the roller shell is smaller than the area where the thrust sliding bearing contacts the opposite surface of the collar. In this way, the surface pressure when the thrust slide bearing slides with respect to the collar as the roller shell rotates can be reliably reduced, and the heat generated during the sliding can be reliably reduced.
- the dimension of the portion where the thrust sliding bearing contacts the end surface of the roller shell is smaller than the dimension of the portion where the thrust sliding bearing contacts the facing surface of the collar.
- the sliding wear resistance of the bearing supporting the roller shell can be enhanced.
- FIG. 1 It is a schematic perspective view which shows the structure of the hydraulic shovel as an example of the crawler type traveling vehicle provided with the wheel in one embodiment of this invention. It is a schematic perspective view which shows the structure of the crawler belt apparatus contained in the crawler type traveling vehicle of FIG. It is sectional drawing which shows the outline of a structure of the underwheel of the crawler type traveling vehicle which concerns on one embodiment of this invention. It is sectional drawing which expands and shows the thrust slide bearing vicinity shown in FIG. It is a disassembled perspective view of the one part component of the downward roller shown in FIG. It is a perspective view of a thrust slide bearing. It is sectional drawing which shows the detail of arrangement
- a configuration of a hydraulic excavator will be described as an example of a crawler type traveling vehicle to which the idea of the present invention can be applied.
- the present invention can also be applied to a crawler type traveling vehicle such as a bulldozer other than the following hydraulic excavator.
- FIG. 1 is a schematic perspective view showing a configuration of a hydraulic excavator as an example of a crawler type traveling vehicle including a wheel in one embodiment of the present invention.
- a crawler type traveling vehicle for example, a hydraulic excavator 30 mainly includes a lower traveling body 20, an upper swing body 31, and a work implement 32.
- the lower traveling body 20 and the upper turning body 31 constitute a main body of the crawler traveling vehicle.
- the lower traveling body 20 has a pair of left and right crawler belt devices 10.
- the crawler type traveling vehicle 30 is configured to be able to self-run when the pair of left and right crawler belt devices 10 are rotationally driven.
- the lower traveling body 20 also has wheels that will be described in detail later.
- the upper turning body 31 is installed so as to be turnable with respect to the lower traveling body 20.
- the upper swing body 31 has a cab 31a on the front left side, an engine room 31b for housing the engine on the rear side, and a counterweight 31c.
- the front, rear, left and right of the upper swing body 31 are based on an operator seated in the cab 31a.
- the work machine 32 is pivotally supported on the front side of the upper swing body 31 and includes, for example, a boom, an arm, a bucket, a hydraulic cylinder, and the like.
- FIG. 2 is a schematic perspective view showing the configuration of the crawler belt device 10 included in the crawler-type traveling vehicle of FIG.
- the crawler belt device 10 mainly includes a crawler belt link 1, a bush 11, a connecting pin 12, and a crawler plate (shoe plate) 13.
- the crawler belt device 10 is configured in an annular shape by connecting a plurality of crawler belt links 1 to which a crawler plate 13 is attached in an endless manner.
- a bushing hole 6 and a pin hole 7 are formed in the crawler belt link 1.
- a plurality of crawler belt links 1 are arranged in two rows. One and the other crawler belt link 1 adjacent to each other in the same row are overlapped with each other so that the bushing hole 6 of the one crawler belt link 1 and the pin hole 7 of the other crawler belt link 1 are arranged concentrically. ing.
- the cylindrical bush 11 is press-fitted into the bush hole 6 of one of the crawler belt links 1.
- the connecting pin 12 is inserted into the bush 11 and is press-fitted into the pin hole 7 of the other crawler belt link 1. In this way, one and the other crawler belt links 1 arranged in the row direction are connected to each other.
- the bushing holes 6 of the crawler belt link 1 in the first row and the pin holes 7 of the crawler belt link 1 in the second row are arranged so as to be concentric with each other.
- the first row of crawler belt links 1 is installed on one end side of one bush 11 and the connecting pin 12, and the second row of crawler belt links 1 is installed on the other end side.
- the crawler belt links 1 in one row and the other row are connected to each other using the bush 11 and the connecting pin 12.
- the shoeboard 13 has a grounding surface 13a on the side in contact with the ground and a non-grounding surface 13b on the opposite side to the grounding surface 13a.
- Each of the ground contact surfaces 13 a of the plurality of crawler plates 13 constitutes a ground contact surface of the crawler belt device 10.
- Each of the non-grounding surfaces 13 b of the plurality of crawler plates 13 constitutes a non-grounding surface of the crawler belt device 10.
- the lower rolling wheel 21 as an example of the rolling wheel according to the present embodiment is disposed on the non-grounded surface side of the endless crawler belt device 10 and rotates while contacting the crawler belt link 1.
- the lower roller 21 is provided below the track frame 29 (see FIG. 1) of the lower traveling body 20 and guides the rotation of the crawler belt device 10 via the crawler belt link 1.
- the lower roller 21 includes a shaft 24 fixed to the track frame 29 and a roller shell 23 that contacts the crawler belt link 1.
- FIG. 3 is a cross-sectional view schematically showing the configuration of the lower roller 21 of the crawler type traveling vehicle according to the embodiment of the present invention.
- the shaft 24 is attached to the track frame 29.
- the shaft 24 is formed in a substantially solid columnar shape and has a cylindrical outer peripheral surface 24a.
- the roller shell 23 is disposed so as to surround a part of the outer peripheral surface 24a of the shaft 24 in the circumferential direction.
- the roller shell 23 is rotatably arranged on the outer peripheral side of the shaft 24 with the center line of the shaft 24 as the rotation center.
- the roller shell 23 has a cylindrical shape.
- the roller shell 23 is manufactured by welding two segments separated by a radial surface including the center in the center line direction.
- the shaft 24 is inserted into the cylindrical roller shell 23 and becomes the rotation center of the roller shell 23.
- the roller shell 23 has a cylindrical inner peripheral surface 23a facing the outer peripheral surface 24a of the shaft 24 along the rotation center direction (axial direction), and an annular end surface 23b along the radial direction.
- a pair of collars 22 are provided on both ends of the shaft 24 with respect to the roller shell 23.
- the collar 22 is disposed so as to sandwich the roller shell 23 in the axial direction.
- the collar 22 has a cylindrical shape, and is attached to the shaft 24 in a state where the shaft 24 is inserted into the center portion thereof.
- the collar 22 is fixed to the shaft 24 using a pin 28.
- a floating seal 27 is disposed between the collar 22 and the roller shell 23.
- the collar 22 has an annular facing surface 22b.
- the collar 22 and the roller shell 23 are arranged so that the facing surface 22 b of the collar 22 faces the end surface 23 b of the roller shell 23.
- a radial sliding bearing 25 is disposed between the outer peripheral surface 24 a of the shaft 24 and the inner peripheral surface 23 a of the roller shell 23.
- the radial sliding bearing 25 is provided to receive a load in the radial direction (the radial direction of the shaft 24) and to allow the roller shell 23 to rotate relative to the shaft 24.
- a thrust slide bearing 26 is disposed between the end surface 23 b of the roller shell 23 and the facing surface 22 b of the collar 22.
- the thrust slide bearing 26 is provided to receive a load in the thrust direction (axial direction of the shaft 24) and to allow the roller shell 23 to rotate relative to the collar 22.
- the radial sliding bearing 25 and the thrust sliding bearing 26 support the roller shell 23 in the radial direction and the axial direction, respectively, so as to be rotatable relative to the shaft 24 and the collar 22.
- the radial sliding bearing 25 is press-fitted into the inner peripheral surface 23 a of the roller shell 23 and is provided so as to be rotatable integrally with the roller shell 23.
- the thrust slide bearing 26 is disposed on the side facing the collar 22 in the axial direction with respect to the roller shell 23.
- FIG. 4 is an enlarged sectional view showing the vicinity of the thrust slide bearing 26 shown in FIG.
- one of the thrust surfaces of the thrust slide bearing 26 is disposed at substantially the same position as the end surface 23 b of the roller shell 23 in the axial direction of the shaft 24 (left and right direction in the drawing).
- the other of the thrust surfaces of the thrust slide bearing 26 is disposed at substantially the same position as the facing surface 22 b of the collar 22 in the axial direction of the shaft 24.
- a gap G is formed between the thrust slide bearing 26 and the radial slide bearing 25.
- the radial sliding bearing 25 and the thrust sliding bearing 26 are arranged in non-contact with each other.
- the radial sliding bearing 25 and the thrust sliding bearing 26 are provided as separate members that are completely separated by the gap G.
- the hollow cylindrical radial sliding bearing 25 is disposed between the outer peripheral surface 24 a of the shaft 24 and the inner peripheral surface 23 a of the roller shell 23.
- the annular plate-like thrust slide bearing 26 has an inner peripheral end face with a diameter substantially equal to the outer diameter of the shaft 24.
- the outer peripheral end surface of the thrust slide bearing 26 is located on the outer side in the radial direction with respect to the outer peripheral surface 24a of the shaft 24 and away from the outer peripheral surface 24a.
- the collar 22 is disposed from the outer peripheral surface 24a of the shaft 24 to the outer peripheral end surface of the thrust slide bearing 26 in the radial direction of the shaft 24.
- the facing surface 22b of the collar 22 is provided so as to face substantially the entire surface of one thrust surface (left side in FIG. 4) of the thrust sliding bearing 26. Since the radial sliding bearing 25 is disposed between the shaft 24 and the roller shell 23, the end surface 23 b of the roller shell 23 faces only a part of the other thrust surface of the thrust sliding bearing 26 on the radially outer side. Is provided. That is, a part of the other thrust surface (the right side in FIG. 4) of the thrust slide bearing 26 in the vicinity of the inner peripheral end surface of the thrust slide bearing 26 is disposed at a position not facing the end surface 23 b of the roller shell 23.
- the outer peripheral surface 24a of the shaft 24 has a cylindrical shape with the same diameter in the axial direction of the shaft 24 from the position where the end surface 23b of the roller shell 23 is disposed to the position where the facing surface 22b of the collar 22 is disposed. have.
- the shaft 24 is not provided with a step for receiving a thrust load on the outer peripheral surface 24a in a portion straddling the thrust slide bearing 26 in the axial direction, and the outer peripheral surface 24a has a cylindrical straight shaft shape. .
- the radial slide bearing 25 and the thrust slide bearing 26 provided separately are formed of different materials.
- the material forming the thrust slide bearing 26 has a higher hardness than the material forming the radial slide bearing 25.
- a material for forming the thrust slide bearing 26 a material having a Brinell hardness of twice or more that of the material for forming the radial slide bearing 25 may be applied.
- a material having a Brinell hardness of 200 or more may be selected as the forming material of the thrust sliding bearing 26.
- a lead bronze casting such as CAC603 defined in JIS (Japanese Industrial Standard) H 5120 may be applied as a material for forming the radial sliding bearing 25.
- a high-strength brass casting (Cu—Zn—Mn—) having superior mechanical properties such as CAC301, CAC302, CAC303 or CAC304 specified in JIS H5120. (Fe-Al alloy) may be applied.
- FIG. 5 is an exploded perspective view of some components of the downwheel 21 shown in FIG.
- FIG. 6 is a perspective view of the thrust slide bearing 26.
- the thrust slide bearing 26 is provided separately from the radial slide bearing 25.
- the thrust slide bearing 26 has an annular plate-shaped main body portion 26m.
- the main body 26m has an annular main surface 26t on one and the other side in the direction of the rotation center.
- One side of the main surface 26 t faces the end surface 23 b of the roller shell 23, and the other side faces the facing surface 22 b of the collar 22.
- the main surface 26t has a function as a thrust surface that receives a thrust force between the roller shell 23 and the collar 22.
- the thrust slide bearing 26 further has a convex portion 26p protruding from the main surface 26t on one side of the main body portion 26m.
- the convex portions 26p are provided at two locations on the main surface 26t.
- the convex portion 26 p extends in the radial direction of the annular main surface 26 t and is formed from the inner peripheral end surface to the outer peripheral end surface of the thrust slide bearing 26.
- the two convex portions 26p are formed so that their extending directions are on the same straight line passing through the center of the annular main surface 26t.
- the convex portion 26p is formed integrally with the main body portion 26m.
- a thrust sliding bearing 26 can be easily formed by molding a material by casting and further cutting and molding the material.
- the convex portion 26p may be formed to protrude from the main surface 26t to the same extent as the thickness of the main body portion 26m.
- the distance between the tip of the convex portion 26p in the thickness direction of the thrust slide bearing 26 and the main surface 26t on which the convex portion 26p protrudes may also be 3.5 mm. Good.
- the 5 is formed with a recess 23c in which a part of the end surface 23b is recessed.
- the concave portion 23c is configured to accommodate the convex portion 26p therein.
- the recesses 23c are formed at two locations on the annular end surface 23b of the roller shell 23, and are formed to extend in the radial direction of the end surface 23b.
- the two recessed portions 23c are formed so that the extending direction is on the same straight line passing through the center of the annular end surface 23b.
- the shape of the recess 23c is determined corresponding to the shape of the protrusion 26p.
- the convex portion 26p and the concave portion 23c are fitted so that the convex portion 26p fits inside the concave portion 23c without a gap or between the surface of the convex portion 26p and the inner surface of the concave portion 23c through a minute gap. Is formed.
- the thrust sliding bearing 26 rotates together with the roller shell 23 when the roller shell 23 rotates.
- the engagement between the convex portion 26p and the concave portion 23c has a function as a detent structure for preventing relative rotation of the thrust slide bearing 26 with respect to the roller shell 23.
- the number of convex portions 26p and concave portions 23c may be an arbitrary number. From the viewpoint of reducing the material for forming the thrust sliding bearing 26 and from the viewpoint of sufficiently exerting the function of preventing the rotation of the thrust sliding bearing 26 with respect to the roller shell 23, two protrusions 26p and two recesses 23c are formed as described above. Is desirable.
- FIG. 7 is a cross-sectional view showing details of the arrangement of the thrust slide bearing 26 with respect to the roller shell 23 and the collar 22.
- One of the main surfaces 26t (the right side in FIG. 7) of the thrust sliding bearing 26 that functions as a thrust surface is disposed to face the end surface 23b of the roller shell 23.
- a radial dimension R1 shown in FIG. 7 indicates a dimension in the radial direction of a portion of the main surface 26t that contacts the end surface 23b of the roller shell 23.
- the other main surface 26t (the left side in FIG. 7) is disposed to face the facing surface 22b of the collar 22.
- a radial dimension R2 shown in FIG. 7 indicates a dimension in the radial direction of a portion of the main surface 26t that contacts the facing surface 22b of the collar 22.
- the radial dimension R1 is smaller than the radial dimension R2. That is, the relational expression R1 ⁇ R2 is established. Therefore, the area where one main surface 26 t of the thrust sliding bearing 26 contacts the end surface 23 b of the roller shell 23 is smaller than the area where the other main surface 26 t contacts the facing surface 22 b of the collar 22.
- the thrust sliding bearing 26 disposed between the end surface 23 b of the roller shell 23 and the facing surface 22 b of the collar 22 is separated from the radial sliding bearing 25.
- the lower roller 21 is provided with a detent structure for preventing the relative rotation of the thrust slide bearing 26 with respect to the roller shell 23.
- the thrust slide bearing 26 When the thrust slide bearing 26 is provided as a separate member from the radial slide bearing 25, the thrust slide bearing 26 is provided on either the end face 23 b or the opposed face 22 b in order to support the roller shell 23 relative to the collar 22. It will slide against. As described with reference to FIG. 7, the area where the thrust slide bearing 26 contacts the collar 22 is larger than the area where the thrust slide bearing 26 contacts the roller shell 23. By sliding, it is possible to reduce the surface pressure generated when sliding.
- the thrust slide bearing 26 does not slide on the roller shell 23 but slides on the collar 22. To move. As a result, the surface pressure acting when the thrust slide bearing 26 slides is reduced, and as a result, the heat generation during sliding can be reduced. Therefore, the occurrence of seizure of the thrust slide bearing 26 can be suppressed.
- the diameter of the downwheel 21 is reduced for the purpose of avoiding interference between the downwheel 21 and the track frame 29.
- the diameter of the lower roller 21 is reduced, the area in which the thrust slide bearing 26 contacts the collar 22 is reduced, so that the surface pressure acting on the thrust slide bearing 26 increases.
- the outer peripheral surface 24 a of the shaft 24 extends from the position where the end surface 23 b of the roller shell 23 is disposed to the position where the facing surface 22 b of the collar 22 is disposed in the axial direction of the shaft 24. And has a cylindrical shape with the same diameter. In this way, at the position where the thrust slide bearing 26 is provided in the axial direction of the shaft 24, a step for receiving the thrust load is not formed on the outer peripheral surface 24a of the shaft 24, and the shaft 24
- the outer peripheral surface has the shape of a cylindrical straight shaft having the same diameter.
- an anti-rotation structure is formed by engagement of the concave portion 23 c formed in the roller shell 23 and the convex portion 26 p formed in the thrust slide bearing 26.
- a detent structure can be formed with a simple structure.
- the radial slide bearing 25 and the thrust slide bearing 26 provided separately are formed of different materials.
- the thrust slide bearing 26 that slides at a relatively high surface pressure can be formed of a material that can withstand a high surface pressure, such as a high-strength brass casting, thereby further extending the life of the thrust slide bearing 26. be able to.
- the forming material of the thrust slide bearing 26 has higher hardness than the forming material of the radial slide bearing 25.
- the thrust slide bearing 26 may be formed of a high strength brass casting, and the radial slide bearing 25 may be formed of a lead bronze casting. In this way, the thrust slide bearing 26 can be provided with specifications that can withstand higher surface pressure.
- the thrust slide bearing 26 includes an annular plate-shaped main body portion 26m having an annular main surface 26t, and a convex portion 26p formed integrally with the main body portion 26m and protruding from the main surface 26t. Have. In this way, the thrust sliding bearing 26 is reliably prevented from rotating with respect to the roller shell 23 by the engagement between the convex portion 26p formed on the thrust sliding bearing 26 and the concave portion 23c formed on the roller shell 23. It becomes possible.
- the area where the thrust sliding bearing 26 contacts the end surface 23 b of the roller shell 23 is smaller than the area where the thrust sliding bearing 26 contacts the facing surface 22 b of the collar 22. In this way, the surface pressure when the thrust slide bearing 26 slides with respect to the collar 22 as the roller shell 23 rotates can be reliably reduced, and the heat generated during the sliding can be reliably reduced. it can.
- the radial dimension R1 of the portion where the thrust slide bearing 26 contacts the end surface 23b of the roller shell 23 is equal to the thrust slide bearing 26 contacts the facing surface 22b of the collar 22. It is smaller than the radial dimension R2 of the portion to be. In this way, the surface pressure when the thrust slide bearing 26 slides with respect to the collar 22 as the roller shell 23 rotates can be reliably reduced, and the heat generated during the sliding can be reliably reduced. it can.
- the rotation preventing structure for preventing the relative rotation of the thrust slide bearing 26 with respect to the roller shell 23 has the protrusion 26p formed on the thrust slide bearing 26 and the recess 23c formed on the roller shell 23.
- the example comprised by this engagement was demonstrated.
- the anti-rotation structure is not limited to this.
- the anti-rotation structure may be configured by joining the roller shell 23 and the thrust slide bearing 26 by brazing, bonding, or welding.
- the joining by welding nickel may be deposited on the end surface 23b of the roller shell 23, and an annular plate material of high strength brass casting may be joined to the end surface 23b by gas tungsten arc welding to form the thrust slide bearing 26. .
- the end surface 23b of the roller shell 23 is treated with zinc phosphate / chromic acid
- the annular plate material of high-strength brass casting is treated with a nitric acid aqueous solution
- the plate material is joined to the roller shell 23 with an epoxy adhesive to perform thrust sliding.
- the bearing 26 may be used.
- a groove for brazing may be provided on the end surface 23b of the roller shell 23, and an annular plate material of high strength brass casting may be brazed with brass brazing.
- the arrangement of the recesses and the projections may be interchanged to form the recesses in the thrust slide bearing 26 and the projections in the roller shell 23.
- a recess that receives the projection 26p is formed in the radial slide bearing 25. It doesn't matter.
- the recess may be formed on the extension of the recess 23 c formed in the roller shell 23 in the radial direction of the shaft 24.
- the shaft 24 is not limited to a cylindrical straight shaft as shown in FIG. 3, and a stepped shaft having a step having a shape whose diameter decreases toward the end can also be applied.
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Abstract
Description
まず本発明の思想を適用可能な履帯式走行車両の一例として油圧ショベルの構成について説明する。なお本発明は以下の油圧ショベル以外のブルドーザなどの履帯式走行車両にも適用可能である。
本実施の形態によれば、図5に示すように、ローラシェル23の端面23bとカラー22の対向面22bとの間に配置されるスラスト滑り軸受26は、ラジアル滑り軸受25とは別体に設けられている。下転輪21には、ローラシェル23に対するスラスト滑り軸受26の相対回転を防止する回り止め構造が設けられている。
Claims (8)
- 円筒状の外周面を有するシャフトと、
前記外周面の一部を周方向に取り囲んで配置され、前記外周面に対向する円筒状の内周面および環状の端面を有するローラシェルと、
前記シャフトに固定され、前記端面に対向する環状の対向面を有するカラーと、
前記外周面と前記内周面との間に配置されたラジアル滑り軸受と、
前記端面と前記対向面との間に配置され、前記ラジアル滑り軸受とは別体に設けられたスラスト滑り軸受とを備え、
前記ローラシェルに対する前記スラスト滑り軸受の相対回転を防止する回り止め構造が設けられている、履帯式走行車両の転輪。 - 前記外周面は、前記シャフトの軸方向において、前記端面の配置されている位置から前記対向面の配置されている位置に亘って、同径の円筒形状を有する、請求項1に記載の履帯式走行車両の転輪。
- 前記回り止め構造は、前記ローラシェルと前記スラスト滑り軸受との一方に形成された凸部および他方に形成された凹部の係合である、請求項1に記載の履帯式走行車両の転輪。
- 前記ラジアル滑り軸受と前記スラスト滑り軸受とは、互いに異なる材料で形成されている、請求項1に記載の履帯式走行車両の転輪。
- 前記スラスト滑り軸受の形成材料は、前記ラジアル滑り軸受の形成材料よりも高い硬度を有する、請求項4に記載の履帯式走行車両の転輪。
- 前記スラスト滑り軸受は、環状の主表面を有する円環板状の本体部と、前記本体部と一体に形成され前記主表面から突起する凸部とを有する、請求項1~5のいずれか1項に記載の履帯式走行車両の転輪。
- 前記スラスト滑り軸受が前記端面に接触する面積は、前記スラスト滑り軸受が前記対向面に接触する面積よりも小さい、請求項1~5のいずれか1項に記載の履帯式走行車両の転輪。
- 前記シャフトの径方向において、前記スラスト滑り軸受が前記端面に接触する部分の寸法は、前記スラスト滑り軸受が前記対向面に接触する部分の寸法よりも小さい、請求項7に記載の履帯式走行車両の転輪。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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CN201480000238.2A CN104024096B (zh) | 2013-06-17 | 2014-02-27 | 履带式行驶车辆的滚轮 |
US14/362,649 US9764785B2 (en) | 2013-06-17 | 2014-02-27 | Roller of track-type traveling vehicle |
KR1020157012322A KR101750637B1 (ko) | 2013-06-17 | 2014-02-27 | 무한궤도식 주행 차량의 롤러 휠 |
DE112014000234.8T DE112014000234B4 (de) | 2013-06-17 | 2014-02-27 | Rolle eines Raupenketten-Fahrzeugs |
IN4014DEN2015 IN2015DN04014A (ja) | 2013-06-17 | 2015-05-12 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2013-126347 | 2013-06-17 | ||
JP2013126347A JP5552558B1 (ja) | 2013-06-17 | 2013-06-17 | 履帯式走行車両の転輪 |
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WO2014203563A1 true WO2014203563A1 (ja) | 2014-12-24 |
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PCT/JP2014/054867 WO2014203563A1 (ja) | 2013-06-17 | 2014-02-27 | 履帯式走行車両の転輪 |
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US (1) | US9764785B2 (ja) |
JP (1) | JP5552558B1 (ja) |
KR (1) | KR101750637B1 (ja) |
DE (1) | DE112014000234B4 (ja) |
IN (1) | IN2015DN04014A (ja) |
WO (1) | WO2014203563A1 (ja) |
Families Citing this family (7)
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WO2019198111A1 (en) * | 2018-04-13 | 2019-10-17 | Italtractor Itm S.P.A. | Element of a crawler-track movement assembly for works vehicles |
US11654983B2 (en) * | 2019-06-10 | 2023-05-23 | Caterpillar Inc. | Rotatable element in machine track having thrust washer stack for stepping down relative speeds |
KR20220032742A (ko) | 2020-09-08 | 2022-03-15 | 엘지디스플레이 주식회사 | 표시 장치 |
US11724757B2 (en) * | 2020-10-29 | 2023-08-15 | Caterpillar Inc. | Roller frame assembly in ground-engaging track system having anti-backbending rollers and method |
US12049266B2 (en) | 2020-12-22 | 2024-07-30 | Caterpillar Inc. | Press fit roller collar |
US11987302B2 (en) * | 2021-01-21 | 2024-05-21 | Caterpillar Inc. | Rim for a track roller |
JP7494763B2 (ja) * | 2021-02-26 | 2024-06-04 | 株式会社豊田自動織機 | 流体機械 |
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- 2014-02-27 DE DE112014000234.8T patent/DE112014000234B4/de active Active
- 2014-02-27 WO PCT/JP2014/054867 patent/WO2014203563A1/ja active Application Filing
- 2014-02-27 KR KR1020157012322A patent/KR101750637B1/ko active IP Right Grant
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JP2001080550A (ja) * | 1999-09-09 | 2001-03-27 | Hitachi Constr Mach Co Ltd | 装軌式車両の案内ローラ装置 |
Also Published As
Publication number | Publication date |
---|---|
US20150274228A1 (en) | 2015-10-01 |
KR101750637B1 (ko) | 2017-06-23 |
DE112014000234T5 (de) | 2015-08-06 |
IN2015DN04014A (ja) | 2015-06-26 |
JP5552558B1 (ja) | 2014-07-16 |
JP2015000666A (ja) | 2015-01-05 |
KR20150068467A (ko) | 2015-06-19 |
DE112014000234B4 (de) | 2018-11-08 |
US9764785B2 (en) | 2017-09-19 |
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