WO2013108453A1 - 建設機械の軸受装置 - Google Patents
建設機械の軸受装置 Download PDFInfo
- Publication number
- WO2013108453A1 WO2013108453A1 PCT/JP2012/076907 JP2012076907W WO2013108453A1 WO 2013108453 A1 WO2013108453 A1 WO 2013108453A1 JP 2012076907 W JP2012076907 W JP 2012076907W WO 2013108453 A1 WO2013108453 A1 WO 2013108453A1
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- WO
- WIPO (PCT)
- Prior art keywords
- thrust plate
- bearing device
- construction machine
- bush
- right brackets
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/02—Sliding-contact bearings
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/006—Pivot joint assemblies
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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
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/045—Pivotal connections with at least a pair of arms pivoting relatively to at least one other arm, all arms being mounted on one pin
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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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
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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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/102—Construction relative to lubrication with grease as lubricant
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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
- F16C2350/00—Machines or articles related to building
- F16C2350/26—Excavators
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/74—Sealings of sliding-contact bearings
Definitions
- the present invention relates to a construction machine, and more particularly to a bearing device for a construction machine suitable for use in a connecting part such as a boom or an arm of the construction machine.
- a bearing device is provided in order to connect a boom, an arm, a bucket, and the like that constitute a front part for work so as to be rotatable.
- the bearing device provided in the front portion typically, one end of the boom or arm is a boss member fitted with a bush on the inner peripheral side, and the end of the arm or bucket connected thereto is used. It is a bracket. Then, a pair of left and right brackets are arranged outside the boss member, and these are rotatably connected by a connecting pin.
- Patent Document 1 An example of a connecting portion of a conventional construction machine having such a bearing device is described in Patent Document 1.
- the adjustment plate is composed of an elastic plate and a metal plate having adhesiveness.
- the adjustment plate has a flat shape without bending, and has a U-shaped notch extending from the central portion to the peripheral portion. Further, the gap in the axial direction is adjusted by passing the notch through the connecting pin.
- Patent Document 2 Another example of a bearing device for a construction machine is described in Patent Document 2.
- the bearing device described in this publication suppresses rattling caused by a radial gap between a hole formed in a bracket and a pin inserted into the hole in a connection portion such as an arm or a boom of a construction machine, and generates vibration. It aims at reducing. For this reason, the bearing device elastically supports the elastic cylinder by providing an elastic cylinder between a part of the bracket and the pin, and the radial gap between the bracket part where the elastic cylinder is not arranged and the pin is changed. It is smaller than the maximum elastic deformation.
- Patent Document 3 An example of a pin coupling portion of a construction machine is described in Patent Document 3.
- a pin coupling portion between an arm and a bucket is taken as an example, and a pin is inserted with a front end side of the arm on the inside and a bracket of the bucket on the outside, and the two members are coupled rotatably. At that time, the gap generated in the pin insertion direction is adjusted by the shim member.
- Patent Document 1 Japanese Utility Model Laid-Open No. 2-11852
- Patent Document 2 Japanese Patent Application Laid-Open No. 2001-330024
- Patent Document 3 Japanese Patent Application Laid-Open No. 2004-204650
- the gap formed as the difference between the distance between the left and right brackets and the axial length of the boss member is set as the thrust plate. It is adjusted by means such as a shim or the like to prevent intrusion of foreign matters such as earth and sand due to gap formation and frictional wear due to vibration noise.
- a U-shaped notch is formed in the gap adjusting plate, so that the gap is adjusted in the field after inserting the pin into the bracket and the boss member.
- the adjustment plate can be inserted.
- the gap adjusting plate described in this publication it is not sufficiently considered that the gap adjusting plate may fall off from the pin due to an impact force or the like generated at the construction site. That is, when the construction machine is used for a long time, it is expected that the axial clearance also increases at the pin coupling portion due to slight deformation of each portion.
- the gap adjustment plate may fall off the pin due to force such as gravity or impact.
- the gap formed between the bracket and the boss member can be absorbed by arranging and assembling the shim members in advance. Since the shim member used for the pin coupling portion described in this publication is configured to be deformable, it has an advantage that it can be assembled by inserting the pin together with the bracket and the boss member. However, the structure becomes complicated in order to make it deformable, the handling at the time of assembly becomes complicated, and the number of man-hours required for the assembly increases.
- the present invention has been made in view of the above-described problems of the prior art, and is intended to absorb an axial gap generated between a bracket and a boss member with a simple configuration in a pin coupling portion of a construction machine. Another object of the present invention is to allow the gap to be absorbed after the pins are fixed by inserting the pins into the bracket and the boss member. That is, an object of the present invention is to improve the assembly workability of the bearing device by allowing the gap to be absorbed on site with a simple configuration without measuring the assembly gap or the like in advance.
- a feature of the present invention that achieves the above object is a bearing device used in a connecting portion of a construction machine in which an upper swing body is mounted on a lower traveling body and a work device is attached to the upper swing body,
- a first member having a boss portion; a second member having left and right brackets sandwiching the boss portion from both left and right sides; a bush held on the inner peripheral side of the boss portion; and between the bush and the left and right brackets
- Sealing means arranged to prevent the lubricating medium from leaking from the bush, a thrust plate inserted between the left and right brackets and the boss portion, and a fastening pin inserted through the left and right brackets and the bush.
- the thrust plate has an annular cut-out shape so that the fastening pin can be inserted into the fastening pin after being inserted into the left and right brackets. Is formed, further the circumferential direction angles of the notch of the thrust plate is to have a less than 180 ° angle at the inner peripheral portion.
- the thrust plate is provided with a hole that allows the thrust plate to be elastically deformed in the vicinity of the incision point in the vicinity of the notch portion and in the vicinity of the curve of the notch portion from the inner arc portion.
- a hole that allows the thrust plate to be elastically deformed in the surface direction may be provided in the vicinity of the minimum gap portion of the thrust plate.
- a plurality of dimples be formed on at least one surface of the thrust plate, and at least one slit directed radially outward from the inner peripheral surface of the thrust plate may be formed.
- the axial gap generated between the bracket and the boss member is absorbed by the thrust plate made of a flat plate that can be elastically deformed in the plane direction.
- the gap can be absorbed even after the members are coupled with pins. Therefore, the assembly workability of the bearing device is improved.
- FIG. 1 is a side view of an embodiment of a construction machine according to the present invention. It is a longitudinal cross-sectional view of one Example of the bearing apparatus of the construction machine shown in FIG. It is a front view of the thrust plate used for the bearing apparatus shown in FIG. It is a front view of the other Example of the thrust plate used for the bearing apparatus shown in FIG. It is sectional drawing of the thrust plate shown in FIG.
- FIG. 1 is a side view of an embodiment of a construction machine 100 according to the present invention.
- the construction machine 100 is, for example, a hydraulic excavator for excavation, and includes a lower traveling body 1 to which an endless track is attached, and an upper revolving body 2 that is turnably mounted on the lower traveling body 1. Between the lower traveling body 1 and the upper swing body 2, a swing device for controlling the swing of the upper swing body 2 is provided.
- a cab 3 on which an operator gets on the front is operated, and a machine room 4 in which an engine and a hydraulic pump for driving and controlling the work machine are stored is disposed in the rear. .
- a working device 5 is attached in front of the upper swing body 2 so as to be able to move up and down.
- the working device 5 includes a boom 6 whose base end is pin-coupled to the upper swing body 2, an arm 8 that is also pin-coupled to the opposite end of the boom 6, and a pin at the tip of the arm 8. It is composed of an attachment 10 such as a bucket that is attached by coupling and used for excavation or the like.
- the boom 6, the arm 8, and the bucket 10 are provided with hydraulic actuators such as a boom cylinder 7, an arm cylinder 9, and a bucket cylinder 11, respectively.
- connection portion B between the base end portion of the boom 6 and the upper swing body 2, and the opposite end of the boom 6 and the end of the arm 8.
- a bearing device 31 is disposed at the connection part A on the part side and the attachment part of the bucket 10.
- FIG. 2 shows details of the bearing device 31 in a longitudinal sectional view.
- FIG. 2 is a detailed view of part A in FIG.
- the B part of the figure has the same configuration.
- the left and right brackets 17A and 17B extend in the form of a fork to connect the front end of the boom 6 to the arm 8, and the left and right brackets 17A and 17B are provided on the front end side of the arm 8. 32 is sandwiched.
- the left and right brackets 17A and 17B are formed with through holes 17C and 17D in order to connect the boss 32 of the arm 8 to the boom 6 so as to be rotatable.
- the left and right through holes 17C and 17D are connected to the connecting pins. 20 is inserted.
- the connecting pin 20 also penetrates the arm 8 and is slidably inserted into the inner peripheral surface of a boss-side bush 16 described below.
- a bush 18 having a hole into which the connecting pin 20 is fitted is attached to the outside of one bracket 17B by welding. .
- the bush 18 and the connecting pin 20 are formed with a through hole 19 and a retaining hole 20a that penetrate in a direction perpendicular to the axial direction.
- Bolts 14 are inserted into these through holes 19 and retaining holes 20 a and are bolted by nuts 15. Thereby, the connecting pin 20 is fixed to the brackets 17A and 17B in a state of retaining and preventing rotation.
- the boss 32 of the arm 8 is formed in a substantially cylindrical shape.
- the inner peripheral surface of the boss portion 32 of the arm 8 is a fitting hole 33A, and two boss-side bushes 16 made of a hard material such as chromium molybdenum steel or oil-impregnated sintered metal are fitted.
- the boss-side bush 16 has an axial length L, and is arranged at intervals in the axial direction.
- a gap in the axial direction between the boss-side bushes 16 and 16 is a grease reservoir 34, and grease is supplied from the outside through a grease supply path (not shown).
- the inner peripheral surface of the boss-side bush 16 forms a sliding surface with the connecting pin 20.
- a seal member 38 is disposed between the opposing surface sides of the left and right brackets 17A and 17B of the boom 6 and the end surfaces of the boss-side bushes 16 and 16.
- the seal member 38 is configured by a contact-type seal such as an oil seal, and grease that has entered the sliding portion between the boss-side bush 16 and the connecting pin 20 from the oil reservoir 34 flows out from the sliding portion. To prevent.
- the distance between the opposing surfaces of the left and right brackets 17A and 17B is slightly larger than the axial length of the boss portion 32 of the arm 8, and there is a gap 35 between the left and right brackets 17A and 17B and the boss portion 32. Is formed. That is, the clearance 35 is formed for improving the assembly of the connecting portion and for the burden of the thrust force (force acting in the axial direction of the connecting pin 20) acting on the work device 5 including the arm 8 and the boom 6.
- a thrust plate 36 that is a feature of the present invention, which will be described in detail later, is inserted into the gap 35.
- a thrust bearing acts between both surfaces of the thrust plate 36, the axial end surfaces 32a and 32b of the boss portion 32 of the arm 8, and the left and right brackets 17A and 17B.
- a thrust plate made of urethane rubber or polyethylene is formed in an annular shape, and after a bush is accommodated in the boss part of the arm, a connecting pin is inserted into the inside together with the boss part of the arm and the bracket to be connected. It was. For this reason, it is difficult to adjust the axial gap formed between the bracket and the boss portion of the arm or between the bracket and the bush, and the axial gap or frictional wear is caused by the excessive gap.
- the thrust plate 36 is configured as follows in the present invention. That is, as shown in FIGS. 3 to 5, the thrust plate 36 disposed on the inner side in the axial direction of the left and right brackets 17 ⁇ / b> A and 17 ⁇ / b> B is formed in a shape in which a part in the circumferential direction is cut away from an annular material. Yes.
- the thrust plate 36 formed in this way is pushed first from the notch portion with a hammer or the like after the left and right brackets 17A, 17B and the boss portion 32 of the arm 8 are connected by the connecting pin 20. Therefore, chamfers 21 are provided on the outer peripheral corners of the left and right brackets 17A and 17B and the boss portion 32 of the arm 8, so that the thrust plate 36 can be smoothly inserted and the workability of the hammer operation can be improved.
- the thrust plate 36 shown in FIG. 3 is formed by heat-treating a steel material having a thickness t and then subjecting the surface to a surface treatment such as nitriding.
- the thickness t is determined in accordance with the gap 35 formed after the coupling pin 20 is assembled, but is about 1 mm.
- the inner diameter of the thrust plate 36 is slightly major 2r than the outer diameter d 0 of the connecting pin 20.
- the size of the cutout portion 24 has a width W at the minimum gap portion is slightly smaller than the inner diameter 2r of the thrust plate 36, the width smaller than the diameter d 0 of the further connecting pin. Therefore, the entire circumferential angle ⁇ excluding the notch 24 is ⁇ > 180 °. Note that the minimum gap portion changes from an arc to a straight portion, and therefore constitutes an inflection point.
- the corner portion of the minimum gap portion does not plastically deform but is within the range of elastic deformation.
- the corner portion of the minimum gap portion is elastically deformed.
- the corner portion of the minimum gap portion (width W portion) is elastically deformed. It is effective if it is made easier. Therefore, in order to promote the elastic deformation of the thrust plate 36, a small hole 22 having a diameter d is formed in the vicinity of the minimum gap portion (width W portion).
- the shape of the cutout portion 24 is a fan shape, and is a shape that opens from the rectangular cutout to the outer diameter side by an angle ⁇ on one side.
- the notch shape is not limited to a fan shape, and may be a rectangular shape when the bearing performance is important.
- the fan shape has the advantage that it can be inserted with less resistance when the thrust plate 36 is inserted by a hammer operation.
- the shape of the small hole 22 is a round hole, this is not limited to a round hole and may be an oval or the like.
- the position of the small hole 22 is limited to the vicinity of the minimum gap portion (width W portion), but it is necessary to be separated from the end portion by a distance that is not destroyed when the thrust plate 36 is inserted into the connecting pin 20 portion. As a result obtained experimentally, it is desirable that the position is slightly above the minimum gap (width W) in FIG.
- FIGS. differs from the above embodiment in that minute depressions (dimples) 40 (40a to 40c) are provided almost uniformly on one or both surfaces of the thrust plates 36a to 36c.
- the shape of the dimple 40 is, for example, a shape in which a sphere is pressed, and may be arranged regularly and vertically as shown in the drawing, or may be arranged in a staggered manner.
- the diameter and depth of the dimple 40 are about 2 mm and 0.2 mm, respectively.
- FIG. 5A is an example in which the dimple 40 is formed on only one side
- FIGS. 5B and 5C are examples in which the dimple 40 is formed on both sides.
- the position of the dimple 40 is changed on the front and back surfaces
- FIG. 5D the position of the dimple 40 is the same on the front and back surfaces.
- the dimples 40 can be processed simultaneously by a press or the like.
- the dimple 40 is formed in order to hold the grease supplied from the grease reservoir 34 or previously applied to the surface on the thrust plates 36a to 36c for a long period of time.
- the bearing device 31 in addition to the effects of the above embodiment, there is an effect that the bearing device 31 can hold the grease for a long time.
- the shape and position of the small hole 22 and the shape of the notch 24 can be changed as in the above embodiment.
- the thrust plate it is essential that the thrust plate be elastically deformed at the minimum gap.
- FIGS. 4A differs from the above embodiments in that a slit 42 is provided instead of a small hole.
- a slit 42 having a width p and a length q is formed on the side opposite to the notch 24. Since the slit 42 is formed, when the thrust plates 36a to 36c are inserted into the connecting pin 20 portion, the notches of the thrust plates 36a to 36c are first expanded with the slit 42 as the center. When the minimum gap portion of the thrust plates 36a to 36c passes through the connecting pin 20 portion, the slit 42 is restored by the elastic force.
- the thrust plates 36a to 36c can be prevented from falling off the connecting pin 20.
- the shape of the notch 24 and the arrangement of the dimples 40 can be changed in the same manner as in the embodiment shown in FIG.
- the position of the slit 42 can be changed, it is easier to generate a uniform stress if the symmetry is maintained, and it is easier to avoid the destruction of the thrust plates 36a to 36c.
- Lubrication is improved by heat treatment and surface treatment of the reservoir and thrust plate, ensuring the same level of lubricity as a conventional resin thrust plate and reducing the axial clearance of the bearing device Thus, friction and wear can be reduced.
- it since it has a simple configuration, it is easy to match on-site, and the number of processing steps and assembly steps can be reduced.
- the bearing device of the joint portion between the arm and the boom has been described as an example.
- the present invention is not limited to the above portion, and can be applied to a bearing device that is pin-coupled like the boom base portion.
- the hydraulic excavator has been described as an example in the above embodiment, it can be applied to other construction machines such as a crane.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
- Component Parts Of Construction Machinery (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
特許文献2:特開2001-330024号公報
特許文献3:特開2004-204650号公報
以上述べた各実施例によれば、グリース溜りおよびスラストプレートの熱処理や表面処理により、潤滑性を向上させているので、従来用いられている樹脂製のスラストプレートと同程度の潤滑性が確保できる上に、軸受装置の軸方向隙間を低減して摩擦や摩耗を低減できる。また簡単な構成であるので現場合わせも容易であり、加工工数および組み立て工数を低減できる。
Claims (6)
- 下部走行体上に上部旋回体を搭載し、この上部旋回体に作業装置を取り付けた建設機械の連結部に用いる軸受装置であって、前記軸受装置はボス部を有する第1の部材と、このボス部を左右両側から挟む左右ブラケットを有する第2の部材と、前記ボス部の内周側に保持されるブッシュと、このブッシュと前記左右ブラケット間に配置され前記ブッシュから潤滑媒体が漏れるのを防止するシール手段と、前記左右ブラケットと前記ボス部間に挿入されるスラストプレートと、前記左右ブラケットと前記ブッシュとを貫通して挿入される締結ピンを有し、前記スラストプレートは環状の一部を切り欠いた形状とすることにより前記締結ピンを前記左右ブラケットに貫挿した後に前記締結ピンに挿入可能に形成されており、さらに前記スラストプレートの前記切り欠き部の周方向角度はその内周部で180°より小さい角度であることを特徴とする建設機械の軸受装置。
- 前記スラストプレートは前記切り欠き部の近傍であって内周の円弧部分から切り欠き部の曲線に移り変わる変曲点の近傍に、このスラストプレートを弾性変形可能にする孔を設けたことを特徴とする請求項1に記載の建設機械の軸受装置。
- 前記スラストプレートの内周面から半径方向外側に向かう少なくとも1個のスリットを形成したことを特徴とする請求項2に記載の建設機械の軸受装置。
- 前記スラストプレートの少なくとも一方の表面に複数のディンプルを形成したことを特徴とする請求項1に記載の建設機械の軸受装置。
- 前記スラストプレートの少なくとも一方の表面に複数のディンプルを形成したことを特徴とする請求項2に記載の建設機械の軸受装置。
- 前記スラストプレートの少なくとも一方の表面に複数のディンプルを形成したことを特徴とする請求項3に記載の建設機械の軸受装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201280067103.9A CN104053840A (zh) | 2012-01-17 | 2012-10-18 | 工程机械的轴承装置 |
US14/372,311 US20150016761A1 (en) | 2012-01-17 | 2012-10-18 | Bearing device for construction machine |
KR1020147019701A KR20140112026A (ko) | 2012-01-17 | 2012-10-18 | 건설기계의 베어링 장치 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2012-006873 | 2012-01-17 | ||
JP2012006873A JP5789524B2 (ja) | 2012-01-17 | 2012-01-17 | 建設機械の軸受装置 |
Publications (1)
Publication Number | Publication Date |
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WO2013108453A1 true WO2013108453A1 (ja) | 2013-07-25 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2012/076907 WO2013108453A1 (ja) | 2012-01-17 | 2012-10-18 | 建設機械の軸受装置 |
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US (1) | US20150016761A1 (ja) |
JP (1) | JP5789524B2 (ja) |
KR (1) | KR20140112026A (ja) |
CN (1) | CN104053840A (ja) |
WO (1) | WO2013108453A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2016023672A (ja) * | 2014-07-17 | 2016-02-08 | 日本ピラー工業株式会社 | 滑り材及び支承装置 |
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WO2014065320A1 (ja) * | 2012-10-25 | 2014-05-01 | Ntn株式会社 | プーリアームの支点軸受装置 |
JP6211334B2 (ja) * | 2013-07-26 | 2017-10-11 | コベルコ建機株式会社 | 作業アタッチメント及びこれを備えた建設機械 |
JP6211335B2 (ja) * | 2013-07-26 | 2017-10-11 | コベルコ建機株式会社 | 作業アタッチメント及びこれを備えた建設機械 |
US9556902B2 (en) * | 2013-11-07 | 2017-01-31 | Cnh Industrial America Llc | Agricultural tandem pivot assembly |
EP3135934B1 (en) * | 2015-08-25 | 2019-07-31 | Aktiebolaget SKF | Bearing having a shim between two ring parts |
US10189470B2 (en) * | 2016-08-17 | 2019-01-29 | GM Global Technology Operations LLC | Hybrid vehicle propulsion systems and methods |
CA2989756A1 (en) * | 2016-12-22 | 2018-06-22 | Harnischfeger Technologies, Inc. | Equalizer with lubrication |
CN108643273B (zh) * | 2018-07-09 | 2023-11-28 | 三一重机有限公司 | 定位销、配重定位结构及装配方法、挖掘机 |
JP6712622B2 (ja) * | 2018-08-06 | 2020-06-24 | キャタピラー エス エー アール エル | 軸受装置および建設機械 |
JP6813250B2 (ja) * | 2018-08-06 | 2021-01-13 | キャタピラー エス エー アール エル | 軸受装置および建設機械 |
US20200094619A1 (en) * | 2018-09-26 | 2020-03-26 | Bowman International Limited | Hub Bearing System |
JP7148433B2 (ja) * | 2019-02-18 | 2022-10-05 | キャタピラー エス エー アール エル | 隙間調整部材 |
DE102020105781A1 (de) * | 2020-03-04 | 2021-09-09 | Nidec Gpm Gmbh | Wasserpumpenlagereinheit mit Dichtungsanordnung sowie damit ausgerüstete Wasserpumpe |
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JPH10122235A (ja) * | 1996-10-21 | 1998-05-12 | Hitachi Constr Mach Co Ltd | 軸受装置 |
JP2009041659A (ja) * | 2007-08-08 | 2009-02-26 | Hitachi Constr Mach Co Ltd | 軸受装置 |
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JPS60159417A (ja) * | 1984-01-31 | 1985-08-20 | Matsushita Electric Ind Co Ltd | 流体軸受装置 |
US5110223A (en) * | 1990-03-27 | 1992-05-05 | Ina Bearing Company, Inc. | Shim thrust bearing apparatus |
JP2002349571A (ja) * | 2002-04-12 | 2002-12-04 | Hitachi Constr Mach Co Ltd | 軸受装置 |
CN100427776C (zh) * | 2003-08-25 | 2008-10-22 | 日立建机株式会社 | 滑动轴承组件及滑动轴承 |
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2012
- 2012-01-17 JP JP2012006873A patent/JP5789524B2/ja not_active Expired - Fee Related
- 2012-10-18 KR KR1020147019701A patent/KR20140112026A/ko not_active Application Discontinuation
- 2012-10-18 US US14/372,311 patent/US20150016761A1/en not_active Abandoned
- 2012-10-18 WO PCT/JP2012/076907 patent/WO2013108453A1/ja active Application Filing
- 2012-10-18 CN CN201280067103.9A patent/CN104053840A/zh active Pending
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JPH10122235A (ja) * | 1996-10-21 | 1998-05-12 | Hitachi Constr Mach Co Ltd | 軸受装置 |
JP2009041659A (ja) * | 2007-08-08 | 2009-02-26 | Hitachi Constr Mach Co Ltd | 軸受装置 |
Cited By (1)
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JP2016023672A (ja) * | 2014-07-17 | 2016-02-08 | 日本ピラー工業株式会社 | 滑り材及び支承装置 |
Also Published As
Publication number | Publication date |
---|---|
JP2013147792A (ja) | 2013-08-01 |
JP5789524B2 (ja) | 2015-10-07 |
KR20140112026A (ko) | 2014-09-22 |
CN104053840A (zh) | 2014-09-17 |
US20150016761A1 (en) | 2015-01-15 |
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