JP4243776B2 - Slewing bearing device for construction machinery - Google Patents

Slewing bearing device for construction machinery Download PDF

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JP4243776B2
JP4243776B2 JP2003281031A JP2003281031A JP4243776B2 JP 4243776 B2 JP4243776 B2 JP 4243776B2 JP 2003281031 A JP2003281031 A JP 2003281031A JP 2003281031 A JP2003281031 A JP 2003281031A JP 4243776 B2 JP4243776 B2 JP 4243776B2
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bearing device
end surface
race
slewing bearing
ring
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JP2005048863A (en
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慎一 関戸
信夫 鵜沢
裕二 井川
猛 栗原
壮史 渋川
智大 永田
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Hitachi Construction Machinery Co Ltd
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Hitachi Construction Machinery Co Ltd
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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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • 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
    • F16C19/163—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 with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Component Parts Of Construction Machinery (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、油圧ショベルやトラッククレーン等の建設機械において、その上部旋回体と下部走行体との間を接続する旋回軸受装置に関する。   The present invention relates to a slewing bearing device for connecting an upper swing body and a lower traveling body in a construction machine such as a hydraulic excavator or a truck crane.

この種の旋回軸受装置は、例えば特許文献１に開示されている。
特許文献１の旋回軸受装置は、油圧ショベルの上部旋回体と下部走行体との間の接続に使用され、上部旋回体のフレームに取付けられた外輪と、下部走行体のフレームに取り付けられた内輪とを有し、外輪は内輪に対して同心上に位置付けられている。これら外輪と内輪との間には、複数の転動体、例えばボールが介挿されており、外輪及び内輪の中心軸線を回転軸線とした上部旋回体は走行体に対して水平面内で旋回可能となっている。 This type of slewing bearing device is disclosed in Patent Document 1, for example.
The slewing bearing device of Patent Document 1 is used for connection between an upper swing body and a lower traveling body of a hydraulic excavator, and an outer ring attached to a frame of the upper swing body and an inner ring attached to a frame of the lower travel body. The outer ring is positioned concentrically with the inner ring. A plurality of rolling elements, for example, balls, are interposed between the outer ring and the inner ring, and the upper swinging body having the central axis of the outer ring and the inner ring as the rotation axis can turn in a horizontal plane with respect to the traveling body. It has become.

より詳しくは、外輪の内周面及び内輪の外周面には周溝からなるレース面が設けられ、これら外側及び内側のレース面間にて転動体を収容するための環状空間が形成されている。外輪には、転動体を環状空間内に挿入するために、蓋部材で閉塞可能な径方向孔が設けられている。転動体は、この径方向孔を通じて環状空間内に間座と交互に収容され、環状空間に沿い所定の間隔を存して配置され、転動体間の間隔は間座により確保される。   More specifically, a race surface including a circumferential groove is provided on the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, and an annular space for accommodating a rolling element is formed between the outer and inner race surfaces. . The outer ring is provided with a radial hole that can be closed by a lid member in order to insert the rolling element into the annular space. The rolling elements are alternately accommodated in the annular space with the spacers through the radial holes, and are arranged at predetermined intervals along the annular space, and the intervals between the rolling elements are secured by the spacers.

このように、旋回軸受装置の組立てに際しては、環状空間内にて転動体を移動させなければならないので、内外のレース面と転動体との間には適度なギャップが必要となる。
しかしながら、上述のギャップを有する旋回軸受装置は、下部走行体に対して上部旋回体をがたつかせてしまい、油圧ショベルの乗り心地を悪化させる。 Thus, when assembling the slewing bearing device, the rolling elements must be moved in the annular space, so that an appropriate gap is required between the inner and outer race surfaces and the rolling elements.
However, the slewing bearing device having the above-described gap causes the upper slewing body to rattle with respect to the lower traveling body, which deteriorates the riding comfort of the hydraulic excavator.

また、上部旋回体のがたつきは内外のレース面を早期に摩耗させて、上述のギャップを更に拡大させ、レース面の縁に転動体を衝突させて、レース面を剥離損傷させ、旋回軸受装置の寿命が短くなるという問題がある。   In addition, the rattling of the upper revolving body causes the inner and outer race surfaces to wear early, further widening the gap, causing the rolling elements to collide with the edges of the race surface, causing the race surface to peel and damage, There is a problem that the lifetime of the apparatus is shortened.

そこで、このような問題を解消するため、特許文献１の旋回軸受装置における内輪と外輪との間には、これら内輪及び外輪の軸線方向でみて転動体の両側にリング部材がそれぞれ配置されている。これらのリング部材は、転動体の両側において内輪と外輪との間に所定の隙間を確保するスペーサとして機能することから、上部旋回体のがたつきが低減され、これにより、旋回軸受装置の長寿命化が図られるものと考えられる。
実公平６−４９６４０号公報（図２等） Therefore, in order to solve such a problem, ring members are respectively arranged on both sides of the rolling element between the inner ring and the outer ring in the slewing bearing device of Patent Document 1 in the axial direction of the inner ring and the outer ring. . Since these ring members function as spacers that secure a predetermined gap between the inner ring and the outer ring on both sides of the rolling element, the rattling of the upper swing body is reduced, thereby reducing the length of the swing bearing device. It is thought that the lifetime is improved.
No. 6-49640 (Fig. 2 etc.)

しかしながら、特許文献１の旋回軸受装置にあっては、２つのリング部材を必要とすることから部品点数が多く、また、その製造工程においても、リング部材を固定するための溝を内輪及び外輪のレース面に形成しなければならない。その故、この旋回軸受装置は構成的に複雑となり、また、その製造コストもまた高くなってしまう。
この発明は、上記した問題を鑑みてなされたもので、その目的とするところは、簡単な構成にて、長寿命化を図ることができる旋回軸受装置を提供することにある。 However, in the slewing bearing device of Patent Document 1, since two ring members are required, the number of parts is large, and also in the manufacturing process, grooves for fixing the ring members are provided in the inner ring and the outer ring. Must be formed on the race surface. Therefore, this slewing bearing device is structurally complicated and its manufacturing cost is also increased.
The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a slewing bearing device that can achieve a long life with a simple configuration.

この発明の建設機械の旋回軸受装置は、建設機械における下部走行体と上部旋回体との間に設けられ、前記下部走行体に取付けられ、外周面に周溝を有する内輪と、前記上部旋回体の平坦な下端面にボルトを介して取付けられ、前記内輪を囲む内周面に周溝を有する外輪と、前記内輪及び前記外輪の周溝により形成された環状の空洞と、前記空洞内にその周方向に間隔を存して収容され、前記周溝との間にて所定のギャップが許容された転動体とを備えている。 A slewing bearing device for a construction machine according to the present invention is provided between a lower traveling body and an upper slewing body in a construction machine, is attached to the lower traveling body, has an inner ring having a circumferential groove on an outer peripheral surface, and the upper slewing body. attached via a flat lower end surface in bolt, an outer ring having a circumferential groove on the inner peripheral surface surrounding said inner ring, said inner ring and annular cavity formed by the circumferential groove of the outer ring, the said cavity And a rolling element that is accommodated in the circumferential direction with a gap therebetween and that allows a predetermined gap between the rolling groove and the circumferential groove.

そして、この旋回軸受装置においては、前記上部旋回体の下端面に密着させられる前記外輪の上端面は当該外輪の軸線との直交面に対して所定の勾配を有するテーパ面として形成され、前記内輪と前記外輪とが同心上に配置され且つ前記ボルトが締め付けられる前、前記雌テーパ面の外周縁は前記雌テーパ面の内周縁よりも前記上部旋回体の下端面に近く、前記ボルトの締め付けにより、前記雌テーパ面の勾配に対応して規定される前記雌テーパ面と前記上部旋回体の下端面とがなす角度が徐々に小さくなって前記雌テーパ面が前記上部旋回体の下端面に密着させられるとき、前記外輪は前記ギャップを解消すべく自身の内周面の下縁側が前記内輪の外周面に近づくように捻り変形を受け、前記内輪との間にて前記転動体を転動自在に保持する（請求項１）。 In this slewing bearing device, the upper end surface of the outer ring that is brought into close contact with the lower end surface of the upper swing body is formed as a tapered surface having a predetermined gradient with respect to a plane perpendicular to the axis of the outer ring, and the inner ring And the outer ring are arranged concentrically and before the bolt is tightened, the outer peripheral edge of the female tapered surface is closer to the lower end surface of the upper rotating body than the inner peripheral edge of the female tapered surface, and the bolt is tightened. The angle between the female taper surface defined corresponding to the gradient of the female taper surface and the lower end surface of the upper swing body gradually decreases, and the female taper surface closely contacts the lower end surface of the upper swing body When the outer ring is moved, the outer ring undergoes torsional deformation so that the lower edge side of its inner peripheral surface approaches the outer peripheral surface of the inner ring so as to eliminate the gap, and the rolling element can freely roll with the inner ring. Hold on (Claim 1).

本発明の旋回軸受装置によれば、その組立時に必要なギャップが確保されていても、下部走行体と上部旋回体との間に組付けられときには、ギャップが解消されているので、転動体と周溝との間には余分な遊びが存在せず、簡単な構成ながらも、内レースと外レースとの間におけるがたつきが防止される。   According to the slewing bearing device of the present invention, even when a gap required at the time of assembling is ensured, the gap is eliminated when assembled between the lower traveling body and the upper slewing body. There is no extra play between the circumferential groove and the ratchet between the inner race and the outer race is prevented with a simple configuration.

そして、本発明の旋回軸受装置は、がたつきが防止されたことで、早期に周溝が摩耗することが防止される。このため、この旋回軸受装置においては、空洞の拡大が抑制され、転動体と内レース又は外レースとの面圧が局所的に高くなることが抑制されるので、内レース及び外レースの周溝、すなわち摺動面に剥離損傷が生じることが長期に亘り防止される。従って、この旋回軸受装置は寿命が長い。   In the slewing bearing device of the present invention, since the rattling is prevented, the circumferential groove is prevented from being worn out at an early stage. For this reason, in this slewing bearing device, since the expansion of the cavity is suppressed and the surface pressure between the rolling element and the inner race or the outer race is suppressed from being locally increased, the circumferential grooves of the inner race and the outer race are suppressed. That is, it is prevented for a long time that peeling damage occurs on the sliding surface. Therefore, this slewing bearing device has a long life.

更に、本発明の旋回軸受装置は、従来の旋回軸受装置に比べ、スペーサ等の部品点数が少なく且つ構成が簡単で安価である。
また、本発明の旋回軸受装置を備えた建設機械は、旋回軸受装置のがたつきが防止されていることから、走行時に下部走行体に対して上部旋回体ががたつかず、作業員の乗り心地が良いことに加え、長寿命且つ安価である。 Furthermore, the slewing bearing device of the present invention has fewer parts such as spacers and is simple and inexpensive compared to conventional slewing bearing devices.
In addition, since the construction machine provided with the slewing bearing device of the present invention prevents the slewing bearing device from rattling, the upper slewing body does not rattle against the lower traveling body during traveling, and the In addition to being comfortable, it is long-lived and inexpensive.

図１は、本発明の一実施例に係る旋回軸受装置を備えた油圧ショベルの概略側面図である。
油圧ショベルは下部走行体１０を備えている。この下部走行体１０上には、後述する旋回軸受装置１２を介して上部旋回体１４が旋回自在に設けられている。
上部旋回体１４は旋回フレーム１６を含み、旋回フレーム１６には旋回軸受装置１２を駆動する油圧モータ１８が固定して取付けられている。油圧モータ１８は旋回軸受装置１２を駆動し、この駆動により、上部旋回体１４が下部走行体１０上にて旋回される。 FIG. 1 is a schematic side view of a hydraulic excavator provided with a slewing bearing device according to an embodiment of the present invention.
The hydraulic excavator includes a lower traveling body 10. On the lower traveling body 10, an upper swing body 14 is turnably provided via a swing bearing device 12 described later.
The upper swing body 14 includes a swing frame 16, and a hydraulic motor 18 that drives the swing bearing device 12 is fixedly attached to the swing frame 16. The hydraulic motor 18 drives the swing bearing device 12, and the upper swing body 14 is swung on the lower traveling body 10 by this drive.

旋回フレーム１６上にはその前部から後部に向けて順に、運転室２０、機械室２２およびカウンタウェイト２４等が設置されている。また、旋回フレーム１６上には作業装置２６が搭載され、この作業装置２６は運転室２０の側方にてその基端が旋回フレーム１６に枢支された起伏ブーム、この起伏ブームの先端に回動可能に連結されたアーム、そして、このアームの先端に回動可能に連結されたバケット２８を有する。   On the revolving frame 16, an operator cab 20, a machine cab 22, a counterweight 24, and the like are installed in order from the front to the rear. Further, a work device 26 is mounted on the swing frame 16, and the work device 26 is turned around the swing boom 16, the base end of which is pivotally supported by the swing frame 16 at the side of the cab 20. It has a movably connected arm and a bucket 28 pivotally connected to the tip of this arm.

図２は、旋回軸受装置１２の一部を示す断面図である。旋回軸受装置１２は旋回フレーム１６と下部走行体１０におけるトラックフレーム３０のベース３２との間に設けられている。   FIG. 2 is a cross-sectional view showing a part of the slewing bearing device 12. The swing bearing device 12 is provided between the swing frame 16 and the base 32 of the track frame 30 in the lower traveling body 10.

旋回軸受装置１２は、互いに同心にして配置されたそれぞれリング状の内レース３６及び外レース３８を有し、内レース３６は下部走行体１０のベース３２の上面に固定され、外レース３８は旋回フレーム１６の下面に固定されている。   The slewing bearing device 12 includes a ring-shaped inner race 36 and an outer race 38 arranged concentrically with each other. The inner race 36 is fixed to the upper surface of the base 32 of the lower traveling body 10, and the outer race 38 is turned. It is fixed to the lower surface of the frame 16.

より詳しくは、内レース３６の下端面４０には複数のねじ孔４６が形成され（図３参照）、これらねじ孔４６は内レース３６の周方向に等間隔に配置され、これらねじ孔４６にベース３２の貫通孔を通してボルトがねじ込まれることで、内レース３６はベース３２上に固定されている。また、内レース３６はその内周面にギア４８が形成された内歯のリングギヤであり、内レース３６のギア４８は、油圧モータ１８のモータ軸に取付けられた駆動ギヤと噛み合っている。   More specifically, a plurality of screw holes 46 are formed in the lower end surface 40 of the inner race 36 (see FIG. 3), and these screw holes 46 are arranged at equal intervals in the circumferential direction of the inner race 36. The inner race 36 is fixed on the base 32 by screwing a bolt through the through hole of the base 32. The inner race 36 is an internal ring gear having a gear 48 formed on the inner peripheral surface thereof. The gear 48 of the inner race 36 meshes with a drive gear attached to the motor shaft of the hydraulic motor 18.

一方、外レース３８には、軸線方向に貫通する複数のボルト孔５４が形成され（図３参照）、これらボルト孔５４もまた外レース３８の周方向に等間隔に配置されている。各ボルト孔５４と旋回フレーム１６の取付孔（図示しない）とを位置合わせした状態で、これらボルト孔５４及び取付孔にボルト５６を挿通し、ボルト５６の突出端にナットをねじ込むことで、外レース３８は旋回フレーム１６の下面に押圧された状態で固定されている。なお、図２はボルト５６を単に１点鎖線で示している。   On the other hand, a plurality of bolt holes 54 penetrating in the axial direction are formed in the outer race 38 (see FIG. 3), and these bolt holes 54 are also arranged at equal intervals in the circumferential direction of the outer race 38. With the bolt holes 54 and the mounting holes (not shown) of the revolving frame 16 aligned, the bolts 56 are inserted into the bolt holes 54 and the mounting holes, and nuts are screwed into the projecting ends of the bolts 56. The race 38 is fixed to the lower surface of the turning frame 16 while being pressed. In FIG. 2, the bolt 56 is simply indicated by a one-dot chain line.

内レース３６の外周面４４及び外レース３８の内周面５２には、断面形状が半円状の周溝５８，６０がそれぞれ形成されている。
これら周溝５８，６０は互いに対向してドーナツ状の空洞を形成し、この空洞内には転動体３４としての複数のボールと、ボール間に所定の間隔を付与する複数の間座（図示せず）とが周方向に交互に配置されている。 On the outer peripheral surface 44 of the inner race 36 and the inner peripheral surface 52 of the outer race 38, circumferential grooves 58 and 60 having a semicircular cross section are formed, respectively.
These circumferential grooves 58 and 60 form a donut-shaped cavity facing each other, and a plurality of balls as the rolling elements 34 and a plurality of spacers (not shown) that give a predetermined interval between the balls. Are alternately arranged in the circumferential direction.

従って、油圧モータ１８を駆動すると、その駆動ギヤと内レース３６のギヤ４８との噛み合いにより内レース３６に対して外レース３８が回転し、これにより、上部旋回体１４は下部走行体１０に対して旋回する。
なお、外レース３８には、転動体３４及び間座を空洞内に収容するための径方向孔（図示せず）が形成され、この径方向孔は、一端が空洞に臨んで開口する一方、他端が外レース３８の外周面にて開口し、蓋材で閉塞可能である。転動体３４及び間座は、この径方向孔を通じて交互に空洞内に収容され、そして、所定の配置となるように空洞内を周方向に移動させられる。 Accordingly, when the hydraulic motor 18 is driven, the outer race 38 rotates with respect to the inner race 36 due to the meshing of the drive gear with the gear 48 of the inner race 36, whereby the upper swing body 14 moves relative to the lower traveling body 10. Turn.
The outer race 38 is formed with a radial hole (not shown) for accommodating the rolling element 34 and the spacer in the cavity, and the radial hole is opened with one end facing the cavity, The other end opens at the outer peripheral surface of the outer race 38 and can be closed with a lid. The rolling elements 34 and the spacers are alternately accommodated in the cavity through the radial holes, and are moved in the circumferential direction so as to have a predetermined arrangement.

また、内レース３６の外周面４４の下部及び外レース３８の内周面５２の上部にはシールリング６６がそれぞれ取付けられており、これらシールリング６６は転動体３４を挟むようにして互いに軸線方向に離間している。より詳しくは、上側のシールリング６６はその先端が内レース３６の上端面６２に摺接し、これに対し、下側のシールリング６６はその先端が外レース３８の下端面６４に相対的に摺接する。これらシールリング６６は、内レース３６と外レース３８との間の隙間及び空洞内に注入されたグリースを保持する。なお、内レース３６及び外レース３８の周溝５８，６０には底面に油溝６８，６８が形成され、油溝６８，６８内にもグリースが注入されている。   Further, seal rings 66 are respectively attached to the lower portion of the outer peripheral surface 44 of the inner race 36 and the upper portion of the inner peripheral surface 52 of the outer race 38, and these seal rings 66 are separated from each other in the axial direction so as to sandwich the rolling elements 34 therebetween. is doing. More specifically, the tip of the upper seal ring 66 is in sliding contact with the upper end surface 62 of the inner race 36, whereas the lower seal ring 66 has its tip sliding relative to the lower end surface 64 of the outer race 38. Touch. These seal rings 66 hold the grease injected into the gap and cavity between the inner race 36 and the outer race 38. Oil grooves 68 and 68 are formed on the bottom surfaces of the circumferential grooves 58 and 60 of the inner race 36 and the outer race 38, and grease is also injected into the oil grooves 68 and 68.

そして、外レース３８の上端面５０はその軸線と直交しておらず、軸線との直交面に対して所定の角度θを存した緩やかな雌テーパ面として形成されている。
以下、上記した旋回軸受装置１２自体の組立、並びに、下部走行体１０と上部旋回体１４との間への旋回軸受装置１２への組付けについて順次説明する。 The upper end surface 50 of the outer race 38 is not perpendicular to its axis, but is formed as a gentle female taper surface having a predetermined angle θ with respect to the plane perpendicular to the axis.
Hereinafter, the assembly of the slewing bearing device 12 itself and the assembly of the slewing bearing device 12 between the lower traveling body 10 and the upper slewing body 14 will be sequentially described.

図３に示したように、内レース３６及び外レース３８を互いに同心上に位置付けて支持する。この支持状態のとき、内レース３６の外周面４４及び外レース３８の内周面５２は互いに平行であるが、外レース３８の上端面５０は内レース３６の上下の端面とは平行ではない。すなわち、外レース３８の上端面５０は前述したように雌テーパ面として形成されているから、その内周縁は外周縁よりも内レース３６の上端面６２により近接した状態にある。またこのとき、これら内外レース３６，３８の周溝５８，６０は互いに合致するように対向してドーナツ状の空洞を形成し、そして、上下のシールリング６６は対応する内外レース３６，３８の端面に当接している。   As shown in FIG. 3, the inner race 36 and the outer race 38 are positioned concentrically and supported. In this supported state, the outer peripheral surface 44 of the inner race 36 and the inner peripheral surface 52 of the outer race 38 are parallel to each other, but the upper end surface 50 of the outer race 38 is not parallel to the upper and lower end surfaces of the inner race 36. That is, since the upper end surface 50 of the outer race 38 is formed as a female tapered surface as described above, the inner peripheral edge thereof is closer to the upper end surface 62 of the inner race 36 than the outer peripheral edge. At this time, the peripheral grooves 58 and 60 of the inner and outer races 36 and 38 are opposed to each other to form a donut-shaped cavity, and the upper and lower seal rings 66 are end faces of the corresponding inner and outer races 36 and 38. Abut.

次に、この支持状態下で、外レース３８の径方向孔を通じて外部から空洞内に転動体３４及び間座を交互に収容し、収容した転動体３４及び間座を空洞に沿って移動させることで、空洞の全周に亘って転動体３４を間隔を存して配置し、この後、径方向孔を蓋材で閉塞する一方、外レースに形成された注油口を通じて空洞内にグリースを封入し、旋回軸受装置１２の組立を完了する。   Next, under this supporting state, the rolling elements 34 and the spacers are alternately accommodated in the cavity from the outside through the radial holes of the outer race 38, and the accommodated rolling elements 34 and the spacer are moved along the cavity. Then, the rolling elements 34 are arranged at intervals over the entire circumference of the cavity, and thereafter, the radial holes are closed with a lid member, and grease is sealed in the cavity through the oil filling port formed in the outer race. Then, the assembly of the slewing bearing device 12 is completed.

空洞の断面は転動体３４の断面よりも若干大きく、内外レース３６，３８の周溝５８，６０が形成する内又は外のレース面と転動体３４との間に適度なギャップが確保されている。したがって、空洞内での転動体３４及び間座の移動時、前記ギャップの存在は、転動体３４及び間座の移動を円滑にする。   The cross section of the cavity is slightly larger than the cross section of the rolling element 34, and an appropriate gap is secured between the inner or outer race surface formed by the circumferential grooves 58 and 60 of the inner and outer races 36 and 38 and the rolling element 34. . Therefore, when the rolling elements 34 and spacers move in the cavity, the existence of the gap facilitates the movement of the rolling elements 34 and spacers.

次に、下部走行体１０のベース３２と上部旋回体１４の旋回フレーム１６との間に組立が完了した旋回軸受装置を配置し、その内レース３６及び外レース３８を下部走行体１０のベース３２及び旋回フレーム１６にそれぞれボルトを介して固定する。   Next, the swivel bearing device that has been assembled is disposed between the base 32 of the lower traveling body 10 and the swivel frame 16 of the upper revolving body 14, and the inner race 36 and the outer race 38 are connected to the base 32 of the lower traveling body 10. And it fixes to the revolving frame 16 via a volt | bolt, respectively.

旋回フレーム１６への外レース３８の固定時、旋回フレーム１６の下面が平坦であるのに対し、外レース３８の上端面５０は雌テーパ面であるので、ボルトの締付けにより、外レース３８の上端面５０がその旋回フレーム１６の下面に密着されると、外レース３８はその全周に亘って捻り変形を受ける。このため、外レース３８の内周面５２はその下縁側が内レース３６の外周面４４に向かって近づくよう傾斜する。   When the outer race 38 is fixed to the revolving frame 16, the lower surface of the revolving frame 16 is flat, whereas the upper end surface 50 of the outer race 38 is a female tapered surface. When the end surface 50 is brought into close contact with the lower surface of the revolving frame 16, the outer race 38 undergoes torsional deformation over the entire circumference. For this reason, the inner peripheral surface 52 of the outer race 38 is inclined so that the lower edge side approaches the outer peripheral surface 44 of the inner race 36.

したがって、内レース３６の内レース面に対して外レース３８の外レース面が近づくので、これら内外のレース面にて形成される空洞の断面領域が減少し、転動体３４は内外のレース面間に遊びを存することなく保持される。   Accordingly, since the outer race surface of the outer race 38 approaches the inner race surface of the inner race 36, the cross-sectional area of the cavity formed by these inner and outer race surfaces is reduced, and the rolling element 34 is located between the inner and outer race surfaces. Is kept without play.

従って、外レース３８が捻り変形を受ける前には、内又は外のレース面と転動体３４との間に転動体３４を円滑に移動させるためのギャップが存在していたが、外レース３８の捻り変形後には、このギャップが無くなり、内レース３６及び外レース３８のレース面に対して、転動体３４は安定して保持される。つまり、ボルト５６を締め付けにより、下部走行体１０に対して上部旋回体１４が旋回軸受装置を介してがたつくことなく旋回自在に支持される。   Therefore, before the outer race 38 is subjected to torsional deformation, there is a gap for smoothly moving the rolling element 34 between the inner or outer race surface and the rolling element 34. After the twist deformation, the gap disappears, and the rolling elements 34 are stably held against the race surfaces of the inner race 36 and the outer race 38. That is, by tightening the bolt 56, the upper swing body 14 is supported by the lower traveling body 10 so as to be rotatable without rattling through the swing bearing device.

より具体的には、外レース３８の捻り変形は、図４を参照して以下の３つの式を用いて定量的に表すことができる。   More specifically, the torsional deformation of the outer race 38 can be quantitatively expressed using the following three equations with reference to FIG.

Figure 0004243776
Figure 0004243776

ただし式中、ｘは、外レース３８が捻り変形を受け、その周溝６０の曲率中心７０が移動した径方向の距離を、Ａは外レース３８の外周面側における上端面５０と下端面６４との距離を、Ｂは外レース３８の内周面５２側における上端面５０と下端面６４との距離を、Ｃは外レース３８の下端面６４から周溝６０の曲率中心７０までの距離を、Ｄは外レース３８の外周面から周溝６０の曲率中心７０までの距離を、Ｅ1は捻り変形前における外レース３８の上端面外縁から周溝６０の曲率中心７０までの距離を、Ｅ2は捻り変形後における外レース３８の上端面外縁から周溝６０の曲率中心７０までの距離を、ＦはＥ2の径方向への余弦を、αは外レース３８の上端面外縁と周溝６０の曲率中心７０とを結ぶ線分と、外レース３８の外周面、すなわち軸線とがなす角度を、そして、θは上端面５０の傾斜角度を表している。 In the equation, x is a radial distance in which the outer race 38 is subjected to torsional deformation and the center of curvature 70 of the peripheral groove 60 is moved, and A is an upper end surface 50 and a lower end surface 64 on the outer peripheral surface side of the outer race 38. , B is the distance between the upper end surface 50 and the lower end surface 64 on the inner peripheral surface 52 side of the outer race 38, and C is the distance from the lower end surface 64 of the outer race 38 to the center of curvature 70 of the circumferential groove 60. , D is the distance from the outer circumferential surface of the outer race 38 to the center of curvature 70 of the circumferential groove 60, E 1 is the distance from the outer edge of the outer race 38 to the center of curvature 70 of the circumferential groove 60 before torsional deformation, E 2 is the distance from the outer edge of the upper end surface of the outer race 38 to the center of curvature 70 of the circumferential groove 60 after torsional deformation, F is the cosine of E 2 in the radial direction, and α is the outer edge of the upper end surface of the outer race 38 and the circumferential groove. The line segment connecting the center of curvature 70 of 60 and the outer peripheral surface of the outer race 38, The angle formed KazuSatoshi and the axis is, and, theta represents the angle of inclination of the upper end face 50.

ここで、ｘは前述した解消されるべきギャップの大きさを示して表していることから、転動体３４の大きさ及び周溝６０の曲率等を考慮して、ｘの値が設定されれば、このｘの値を上記した式に代入して外レース３８における上端面５０の傾斜角度θを求め、そして、傾斜角度θを外レース３８の上端面５０に付与することで、外レース３８と内レース３６との間におけるがたつきを容易に防止することができる。   Here, since x represents the size of the gap to be eliminated as described above, if the value of x is set in consideration of the size of the rolling element 34, the curvature of the circumferential groove 60, and the like. Then, by substituting the value of x into the above equation, the inclination angle θ of the upper end surface 50 in the outer race 38 is obtained, and the inclination angle θ is given to the upper end surface 50 of the outer race 38 to obtain the outer race 38 Shaking between the inner race 36 and the inner race 36 can be easily prevented.

上記した旋回軸受装置１２を介して、下部走行体１０上に上部旋回体１４が旋回可能に搭載された油圧ショベルにおいては、油圧モータ１８が駆動されると、上部旋回体１４は下部走行体１０に対し、旋回軸受装置１２を介して円滑に旋回する。
この旋回軸受装置１２は、その組立時に必要なギャップが確保されていても、下部走行体１０と上部旋回体１４との間に組付けられときには、前記ギャップが解消されているので、転動体３４と周溝（レース面）５８，６０との間には余分な遊びが存在せず、内レース３６と外レース３８との間におけるがたつきが防止されている。 In the hydraulic excavator in which the upper swing body 14 is rotatably mounted on the lower traveling body 10 via the swing bearing device 12 described above, when the hydraulic motor 18 is driven, the upper swing body 14 is moved to the lower traveling body 10. On the other hand, it smoothly turns through the swing bearing device 12.
Even if the slewing bearing device 12 is secured between the lower traveling body 10 and the upper slewing body 14 even if a gap required at the time of assembling is secured, the gap is eliminated. There is no extra play between the inner race 36 and the outer race 38 between the inner race 36 and the outer race 38.

そして、旋回軸受装置１２のがたつきが防止されていることから、この油圧ショベルは、走行時に下部走行体１０に対して上部旋回体１４ががたつかず、作業員の乗り心地が良い。
また、旋回軸受装置１２は、がたつきが防止されたことで、早期にレース面が摩耗することが防止される。このため、旋回軸受装置１２においては、空洞断面の拡大が抑制され、転動体３４と内レース３６又は外レース３８との面圧が局所的に高くなることが抑制されるので、内レース３６及び外レース３８の周溝５８，６０、すなわち摺動面に剥離損傷が生じることが長期に亘り防止される。従って、旋回軸受装置及びこの旋回軸受装置１２を用いた油圧ショベルは寿命が長い。 Since the swing bearing device 12 is prevented from rattling, the excavator does not rattle the upper swing body 14 with respect to the lower travel body 10 during traveling, and the ride comfort of the worker is good.
Further, since the swing bearing device 12 is prevented from rattling, the race surface is prevented from being worn out at an early stage. For this reason, in the slewing bearing device 12, the expansion of the cavity cross section is suppressed, and the surface pressure between the rolling element 34 and the inner race 36 or the outer race 38 is suppressed from being locally increased. It is prevented for a long time that peeling damage occurs in the circumferential grooves 58 and 60 of the outer race 38, that is, the sliding surface. Therefore, the slewing bearing device and the hydraulic excavator using the slewing bearing device 12 have a long life.

更に、旋回軸受装置１２は、従来の旋回軸受装置に比べ、スペーサ等の部品点数が少なく且つ構成が簡単で安価であり、この旋回軸受装置１２を用いた油圧ショベル自体も安価にすることができる。
なお、本発明は上記した一実施例に限定されることはなく、種々変形が可能であって、例えば、本発明の建設機械の旋回軸受装置は、油圧ショベルの他、トラッククレーン等の建設機械にも好適する。 Further, the slewing bearing device 12 has fewer parts such as spacers and is simple and inexpensive compared to the conventional slewing bearing device, and the hydraulic excavator using the slewing bearing device 12 can also be made inexpensive. .
The present invention is not limited to the above-described embodiment, and various modifications are possible. For example, the slewing bearing device for a construction machine according to the present invention includes a construction machine such as a truck crane in addition to a hydraulic excavator. Also suitable.

また、上記した一実施例の軸受装置は単列ボール式であったが、本発明の軸受装置は、ころ式、クロスローラ式、又は複列式等であってもよい。   In addition, although the bearing device of the above-described embodiment is a single row ball type, the bearing device of the present invention may be a roller type, a cross roller type, or a double row type.

本発明の一実施例に係る油圧ショベルの概略構成を示す側面図である。1 is a side view showing a schematic configuration of a hydraulic excavator according to an embodiment of the present invention. 図１の油圧ショベルにおける旋回軸受装置周辺の断面図である。FIG. 2 is a cross-sectional view around a slewing bearing device in the hydraulic excavator of FIG. 図２の旋回軸受装置の組立て方法及び上部旋回体と下部走行体との間への組付け方法を説明するための断面図である。It is sectional drawing for demonstrating the assembly method of the slewing bearing apparatus of FIG. 2, and the assembly | attachment method between an upper revolving body and a lower traveling body. 図２の軸受装置におけるがたつき防止作用の説明図である。It is explanatory drawing of the rattling prevention effect in the bearing apparatus of FIG.

符号の説明Explanation of symbols

３４ 転動体
３６ 内レース（内輪）
３８ 外レース（外輪）
４４ 内レースの外周面
５０ 外レースの上端面（固定面）
５２ 外レースの内周面
５８ 内レースの周溝
６０ 外レースの周溝 34 Rolling elements 36 Inner race (inner ring)
38 Outer race (outer ring)
44 Inner race outer peripheral surface 50 Outer race upper end surface (fixed surface)
52 Inner circumferential surface of outer race 58 Circumferential groove of inner race 60 Circumferential groove of outer race

Claims (1)

建設機械における下部走行体と上部旋回体との間に設けられた旋回軸受装置において、
前記下部走行体に取付けられ、外周面に周溝を有する内輪と、
前記上部旋回体の平坦な下端面にボルトを介して取付けられ、前記内輪を囲む内周面に周溝を有する外輪と、
前記内輪及び前記外輪の周溝により形成された環状の空洞と、
前記空洞内にその周方向に間隔を存して収容され、前記周溝との間にて所定のギャップが許容された転動体と
を備え、
前記上部旋回体の下端面に密着させられる前記外輪の上端面は、当該外輪の軸線との直交面に対して所定の勾配を有する雌テーパ面として形成され、
前記内輪と前記外輪とが同心上に配置され且つ前記ボルトが締め付けられる前、前記雌テーパ面の外周縁は前記雌テーパ面の内周縁よりも前記上部旋回体の下端面に近接し、前記ボルトの締め付けにより、前記雌テーパ面の勾配に対応して規定される前記雌テーパ面と前記上部旋回体の下端面とがなす角度が徐々に小さくなって前記雌テーパ面が前記上部旋回体の下端面に密着させられるとき、前記外輪は前記ギャップを解消すべく自身の内周面の下縁側が前記内輪の外周面に近づくように捻り変形を受け、前記内輪との間にて前記転動体を転動自在に保持することを特徴とする建設機械の旋回軸受装置。 In the slewing bearing device provided between the lower traveling body and the upper swing body in the construction machine,
An inner ring attached to the lower traveling body and having a circumferential groove on the outer peripheral surface;
An outer ring attached to a flat lower end surface of the upper swing body via a bolt, and having a circumferential groove on an inner circumferential surface surrounding the inner ring;
An annular cavity formed by circumferential grooves of the inner ring and the outer ring;
A rolling element that is accommodated in the cavity with a space in the circumferential direction and that allows a predetermined gap between the circumferential groove,
The upper end surface of the outer ring that is brought into close contact with the lower end surface of the upper swing body is formed as a female tapered surface having a predetermined gradient with respect to a plane orthogonal to the axis of the outer ring ,
Before the inner ring and the outer ring are arranged concentrically and the bolt is tightened, the outer peripheral edge of the female tapered surface is closer to the lower end surface of the upper rotating body than the inner peripheral edge of the female tapered surface, and the bolt By tightening, the angle formed by the female taper surface defined corresponding to the gradient of the female taper surface and the lower end surface of the upper swing body is gradually reduced, so that the female taper surface is below the upper swing body . When the outer ring is brought into close contact with the end surface , the outer ring undergoes torsional deformation so that the lower edge side of its inner peripheral surface approaches the outer peripheral surface of the inner ring in order to eliminate the gap, and the rolling element is interposed between the inner ring and the inner ring. A slewing bearing device for a construction machine, wherein the slewing bearing device is held freely.
JP2003281031A 2003-07-28 2003-07-28 Slewing bearing device for construction machinery Expired - Fee Related JP4243776B2 (en)

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