JP2975903B2 - Swivel bearing - Google Patents
Swivel bearingInfo
- Publication number
- JP2975903B2 JP2975903B2 JP9020231A JP2023197A JP2975903B2 JP 2975903 B2 JP2975903 B2 JP 2975903B2 JP 9020231 A JP9020231 A JP 9020231A JP 2023197 A JP2023197 A JP 2023197A JP 2975903 B2 JP2975903 B2 JP 2975903B2
- Authority
- JP
- Japan
- Prior art keywords
- ring portion
- peripheral surface
- outer ring
- inclined surface
- inner ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- 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
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
- F16C19/362—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/30—Angles, e.g. inclinations
- F16C2240/34—Contact angles
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、外輪部および内輪
部間に略円柱状の転動体を有する単列複式スラスト軸受
を備えた旋回座軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swivel bearing provided with a single-row double-type thrust bearing having a substantially cylindrical rolling element between an outer ring portion and an inner ring portion.
【０００２】[0002]
【従来の技術】従来、例えばクレーンなどの物揚機械や
油圧ショベルなどの建設機械等の旋回する作業装置を回
転自在に支持する軸受として、例えば図９および図１０
に示すように、単列複式スラスト軸受を備えたクロスロ
ーラ形の旋回座軸受41が知られている。2. Description of the Related Art Conventionally, as a bearing for rotatably supporting a swinging working device such as a lifting machine such as a crane or a construction machine such as a hydraulic shovel, for example, FIGS.
As shown in FIG. 1, there is known a cross roller type swivel seat bearing 41 provided with a single-row double-type thrust bearing.
【０００３】この図９および図１０に示す旋回座軸受41
は、作業装置が取り付けられる環状の外輪部42と、この
外輪部42の内周側に同軸上に配設される環状の内輪部43
と、外輪部42の内周面および内輪部43の外周面との間に
回転自在に外周面が挟持され軸方向が直交するように交
互に複数配設され外輪部42および内輪部43を相対的に回
転自在に連結する転動体である円柱状のコロ44a ，44b
とを備えている。そして、外輪部42には作業装置と連結
する図示しないボルトが取り付けられるボルト孔45が設
けられ、内輪部43には作業装置を保持する本体と連結す
る図示しないボルトが取り付けられるボルト孔46が設け
られている。また、内輪部43の内周面には、図示しない
作業装置の駆動手段の歯車が係合するギア47が設けられ
ている。[0003] The swivel bearing 41 shown in FIGS.
A ring-shaped outer ring portion 42 to which the working device is attached, and a ring-shaped inner ring portion 43 coaxially arranged on the inner peripheral side of the outer ring portion 42
The outer ring portion is rotatably held between the inner peripheral surface of the outer ring portion 42 and the outer peripheral surface of the inner ring portion 43, and a plurality of the outer ring portions are alternately arranged so that the axial directions are orthogonal to each other. Cylindrical rollers 44a, 44b, which are rolling elements that are rotatably connected to each other
And The outer ring portion 42 is provided with a bolt hole 45 to which a bolt (not shown) connected to the working device is attached, and the inner ring portion 43 is provided with a bolt hole 46 to which a bolt (not shown) to be connected to the main body holding the working device is attached. Have been. Further, a gear 47 is provided on the inner peripheral surface of the inner ring portion 43 to be engaged with a gear of driving means of a working device (not shown).
【０００４】また、外輪部42の内周面および内輪部43の
外周面には、コロ44a ，44b の外周面が当接する一対の
軌道面48，48が拡開するＶ字状の溝部49，49がそれぞれ
対向するように設けられている。そして、これら溝部4
9，49間に、コロ44a ，44b が軸方向を外輪部42および
内輪部43の径方向に対して４５°傾斜して互いに直交さ
れ、コロ44a ，44b 間の距離を保持するプラスチックな
どの図示しないセパレータを介在させて交互に複数配設
されている。On the inner peripheral surface of the outer ring portion 42 and the outer peripheral surface of the inner ring portion 43, a pair of raceway surfaces 48, 48 with which the outer peripheral surfaces of the rollers 44a, 44b abut, are expanded in a V-shaped groove portion 49, 49 are provided to face each other. And these grooves 4
Between rollers 9 and 49, rollers 44a and 44b are inclined at an angle of 45 ° with respect to the radial direction of outer ring portion 42 and inner ring portion 43 so that the rollers 44a and 44b are orthogonal to each other, and are made of plastic or the like that maintains the distance between rollers 44a and 44b. A plurality of separators are alternately arranged with separators not provided.
【０００５】[0005]
【発明が解決しようとする課題】ところで、上記図９お
よび図１０に示す旋回座軸受41は、コロ44a ，44b が軸
方向を外輪部42および内輪部43の径方向に対して４５°
傾斜して互いに直交されて配設されている。このため、
例えば作業装置が取り付けられる外輪部42に掛かる作業
装置の重量や作業装置の作業の際に加わる重力方向の外
力Ｆ1 は、回転軸ａが一方に傾いたコロ44a にのみ掛か
る。すなわち、全コロ44a ，44b の半数のみで重力方向
の荷重を受け、回転軸ｂが他方に傾いたコロ44b は外周
面が当接せずに荷重が掛からず無負荷状態となる。同様
に、作業装置の作業の際に加わる反重力方向の外力Ｆ2
は、回転軸ｂが他方に傾いたコロ44b にのみ掛かる。そ
して、外力Ｆ1 と外力Ｆ2 とを比較すると、作業装置の
重力による負荷の分および作業装置の転倒などを防止す
るために、外力Ｆ1 の負荷の方が外力Ｆ2 の負荷より大
きい。In the above-described swivel bearing 41 shown in FIGS. 9 and 10, the rollers 44a and 44b are arranged so that the axial direction is 45 ° with respect to the radial direction of the outer ring portion 42 and the inner ring portion 43.
They are arranged inclined and orthogonal to each other. For this reason,
For example the external force F 1 in the direction of gravity acting upon the work of the working device weight and working devices of the working apparatus according to the outer ring 42 attached is is applied only to the rollers 44a of the rotary shaft a is inclined in one. In other words, only half of all the rollers 44a and 44b receive a load in the direction of gravity, and the roller 44b with the rotating shaft b inclined to the other side is not in contact with the outer peripheral surface, so that no load is applied and no load is applied. Similarly, the external force F 2 applied in the antigravity direction during the operation of the working device
Hangs only on the roller 44b whose rotation axis b is inclined to the other side. The larger when comparing the external force F 1 and force F 2, in order to prevent a fall of the minute and the working device of the load due to gravity of the working device, the load towards the load of the external force F 1 is an external force F 2.
【０００６】このため、回転軸ａのコロ44a に掛かる負
荷が回転軸ｂのコロ44b に掛かる負荷より大きくなり、
例えば溝部49，49の一方の軌道面48，48の摩耗速度が早
くなるなどにより、円滑な作業装置の旋回が損なわれる
おそれがある。Therefore, the load applied to the roller 44a of the rotating shaft a becomes larger than the load applied to the roller 44b of the rotating shaft b,
For example, a smooth turning of the working device may be impaired due to an increase in the wear speed of one of the raceway surfaces 48, 48 of the groove portions 49, 49.
【０００７】本発明は、上記問題点に鑑みなされたもの
で、軸方向が異なる各転動体に掛かる負荷を均等化し、
円滑な旋回が得られる旋回座軸受を提供することを目的
とする。SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has an object to equalize loads applied to rolling elements having different axial directions.
It is an object of the present invention to provide a swivel seat bearing capable of smoothly turning.
【０００８】[0008]
【課題を解決するための手段】請求項１記載の旋回座軸
受は、内周面が円筒状の外輪部と、この外輪部の内周側
に位置し外周面が前記外輪部の内周面に対向する内輪部
と、前記外輪部および前記内輪部間にこれら外輪部およ
び内輪部の径方向に対して軸方向が交差しかつ互いに軸
方向が交差して交互に複数配設された略円柱状の転動体
を有する単列複式スラスト軸受とを備え、前記軸方向が
一方向の転動体の前記外輪部および前記内輪部の軸方向
に沿って掛かる荷重に対する荷重容量が、前記軸方向が
他方向の転動体に掛かる荷重に対する荷重容量より大き
いものである。そして、外輪部および内輪部の径方向に
対して軸方向が一方向に傾斜する略円柱状の転動体の外
輪部および内輪部に掛かる軸方向に沿った荷重に対する
荷重容量を、軸方向が他方向に傾いた転動体に掛かる荷
重に対する荷重容量より大きくなるように、外輪部およ
び内輪部間に位置して外輪部および内輪部の径方向に対
して軸方向が交差しかつ互いに軸方向が交差して交互に
略円柱状の転動体を複数配設して単列複式スラスト軸受
を構成したため、軸方向が異なる各転動体に外輪部およ
び内輪部の軸方向に沿って異なる大きさの反対方向の荷
重が掛かっても各転動体に掛かる負荷が均等化し、円滑
な旋回が得られる。According to a first aspect of the present invention, there is provided a swivel bearing including an outer ring portion having a cylindrical inner peripheral surface and an inner peripheral surface of the outer ring portion located on the inner peripheral side of the outer ring portion. And a plurality of substantially circular circles in which the axial direction intersects the radial direction of the outer ring portion and the inner ring portion and the axial direction intersects each other between the outer ring portion and the inner ring portion. A single row double-type thrust bearing having a columnar rolling element, wherein the axial direction is different from the axial direction in that the load capacity with respect to the load applied along the axial direction of the outer ring portion and the inner ring portion of the rolling element is one direction. It is larger than the load capacity for the load applied to the rolling element in the direction. The load capacity with respect to the axial load applied to the outer ring and the inner ring of the substantially cylindrical rolling element whose axial direction is inclined in one direction with respect to the radial direction of the outer ring and the inner ring, The axial direction intersects the radial direction of the outer ring portion and the inner ring portion, and the axial direction intersects with the radial direction of the outer ring portion and the inner ring portion so as to be larger than the load capacity for the load applied to the rolling element inclined in the direction. A plurality of substantially cylindrical rolling elements are alternately arranged to form a single-row double-type thrust bearing, so that each rolling element having a different axial direction has a different size along the axial direction of the outer ring portion and the inner ring portion in each of the rolling elements having different axial directions. Even if the load is applied, the load applied to each rolling element is equalized, and smooth turning is obtained.
【０００９】請求項２記載の旋回座軸受は、請求項１記
載の旋回座軸受において、軸方向が一方向の転動体の外
輪部および内輪部に掛かる軸方向に沿った最大荷重の方
向への外周面の投影長さが、軸方向が他方向の転動体の
前記最大荷重の方向と反対方向への外周面の投影長さよ
り大きいものである。そして、外輪部および内輪部に掛
かる軸方向に沿った最大荷重の方向への軸方向が一方向
へ傾いた転動体の外周面の投影長さを、軸方向が他方向
に傾いた転動体の最大荷重の方向と反対方向への外周面
の投影長さより大きくしたため、外輪部および内輪部に
掛かる軸方向に沿った異なる大きさの反対方向の荷重に
対する軸方向の異なる各転動体の荷重容量が異なるの
で、異なる大きさの反対方向の荷重が掛かっても簡単な
構成で各転動体に掛かる負荷が均等化する。According to a second aspect of the present invention, there is provided a swivel bearing according to the first aspect, in which a maximum load is applied along the axial direction applied to the outer ring portion and the inner ring portion of the rolling element having one axial direction. The projected length of the outer peripheral surface is larger than the projected length of the outer peripheral surface in the direction opposite to the direction of the maximum load of the rolling element in the axial direction in the other direction. Then, the projected length of the outer peripheral surface of the rolling element whose axial direction in the direction of the maximum load along the axial direction applied to the outer ring part and the inner ring part is tilted in one direction is the same as that of the rolling element whose axial direction is tilted in the other direction. Because the projection length of the outer peripheral surface in the direction opposite to the direction of the maximum load was made larger, the load capacity of each rolling element in the axial direction with respect to the load in the opposite direction of different size along the axial direction applied to the outer ring and the inner ring was Since the load is different, the load applied to each rolling element is equalized with a simple configuration even when loads of different sizes in opposite directions are applied.
【００１０】請求項３記載の旋回座軸受は、請求項１ま
たは２記載の旋回座軸受において、外輪部は、内周面に
転動体の外周面が当接する第１の傾斜面および第２の傾
斜面を有し内輪部側に向けて拡開する外輪溝部を有し、
前記内輪部は、外周面に前記第２の傾斜面に平行に対向
し前記転動体の外周面が当接する第３の傾斜面および前
記第１の傾斜面に平行に対向し前記転動体の外周面が当
接する第４の傾斜面を有し前記外輪部に向けて拡開する
内輪溝部を有し、前記第１の傾斜面および前記第４の傾
斜面の前記外輪部および前記内輪部の軸方向に沿って掛
かる最大荷重の方向への投影長さが、前記第２の傾斜面
および前記第３の傾斜面の前記最大荷重の方向と反対方
向への投影長さより大きいものである。そして、外輪部
の内周面に内輪部に向けて拡開する外輪溝部の第１の傾
斜面と内輪部の外周面に外輪部に向けて拡開する内輪溝
部の第１の傾斜面に平行に対向する第４の傾斜面との外
輪部および内輪部の軸方向に沿って掛かる最大荷重の方
向への投影長さを、外輪溝部の第２の傾斜面および内輪
部の第２の傾斜面に平行に対向する第３の傾斜面の最大
荷重の方向と反対方向への投影長さより大きくしたた
め、外輪部および内輪部に掛かる軸方向に沿った異なる
大きさの反対方向の荷重に対する軸方向の異なる各転動
体の荷重容量が異なるので、異なる大きさの反対方向の
荷重が掛かっても簡単な構成で各転動体に掛かる負荷が
均等化する。According to a third aspect of the present invention, in the slewing bearing according to the first or second aspect, the outer ring portion has a first inclined surface and a second inclined surface in which the outer peripheral surface of the rolling element contacts the inner peripheral surface. An outer ring groove having an inclined surface and expanding toward the inner ring,
The inner ring portion is opposed to an outer peripheral surface in parallel with the second inclined surface, and is opposed in parallel to the third inclined surface and the first inclined surface with which the outer peripheral surface of the rolling element is in contact, and the outer periphery of the rolling element. A fourth inclined surface having an abutting surface, an inner ring groove extending toward the outer ring portion, and an axis of the outer ring portion and the inner ring portion of the first inclined surface and the fourth inclined surface; The projection length in the direction of the maximum load applied along the direction is larger than the projection length of the second inclined surface and the third inclined surface in the direction opposite to the direction of the maximum load. The first inclined surface of the outer ring groove portion expanding toward the inner ring portion on the inner peripheral surface of the outer ring portion is parallel to the first inclined surface of the inner ring groove portion expanding toward the outer ring portion on the outer peripheral surface of the inner ring portion. The projected length of the outer ring portion and the inner ring portion in the direction of the maximum load applied along the axial direction of the outer ring portion and the inner ring portion with the fourth inclined surface facing the second inclined surface of the outer ring groove portion and the second inclined surface of the inner ring portion. Because the length of the third inclined surface facing in parallel to the third inclined surface is larger than the projected length in the direction opposite to the direction of the maximum load, the third inclined surface has an axial direction with respect to a load of a different size in the opposite direction along the axial direction applied to the outer ring portion and the inner ring portion. Since the load capacities of the different rolling elements are different, the loads applied to the rolling elements are equalized with a simple configuration even when loads of different magnitudes are applied in opposite directions.
【００１１】請求項４記載の旋回座軸受は、請求項１な
いし３いずれか一記載の旋回座軸受において、外輪部
は、内周面に外輪溝部の第１の傾斜面の縁側に設けられ
た径小内周面と、前記外輪溝部の第２の傾斜面の縁側に
前記径小内周面より径大に略同軸上に設けられた径大内
周面とを有し、内輪部は、外周面に内輪溝部の第３の傾
斜面の縁側に設けられ前記外輪部の径小内周面に対向す
る径小外周面と、前記内輪溝部の第４の傾斜面の縁側に
前記径小外周面より径大に略同軸上に設けられた径大外
周面とを有したものである。そして、外輪部の内周面の
外輪溝部の第１の傾斜面の縁側に径小内周面を設けると
ともに、外輪溝部の第２の傾斜面の縁側に径小内周面よ
り径大に略同軸上に径大内周面を設け、内輪部の外周面
の内輪溝部の第３の傾斜面の縁側に外輪部の径小内周面
に対向する径小外周面を設けるとともに、内輪溝部の第
４の傾斜面の縁側に径小外周面より径大に略同軸上に径
大外周面を設けたため、外輪部および内輪部の径方向に
沿った荷重に対して異なる荷重容量となる各転動体が、
簡単な構成で内輪部および外輪部が干渉せず容易に配設
され小型化する。According to a fourth aspect of the present invention, in the slewing bearing according to any one of the first to third aspects, the outer ring portion is provided on the inner peripheral surface of the outer ring groove portion on the edge side of the first inclined surface. A small-diameter inner peripheral surface, and a large-diameter inner peripheral surface provided substantially coaxially with a diameter larger than the small-diameter inner peripheral surface on the edge side of the second inclined surface of the outer-ring groove portion; A small-diameter outer peripheral surface provided on the outer peripheral surface on the edge side of the third inclined surface of the inner ring groove portion and facing the small-diameter inner peripheral surface of the outer ring portion; and the small-diameter outer periphery on the edge side of the fourth inclined surface of the inner ring groove portion; And a large-diameter outer peripheral surface provided substantially coaxially with a diameter larger than the surface. In addition, a small-diameter inner peripheral surface is provided on the inner peripheral surface of the outer ring portion on the edge side of the first inclined surface of the outer ring groove portion, and the diameter is substantially larger than the small-diameter inner peripheral surface on the edge side of the second inclined surface of the outer ring groove portion. A large-diameter inner peripheral surface is provided coaxially, and a small-diameter outer peripheral surface facing the small-diameter inner peripheral surface of the outer ring portion is provided on the edge side of the third inclined surface of the inner ring groove portion on the outer peripheral surface of the inner ring portion. Since the large-diameter outer peripheral surface is provided substantially coaxially on the edge side of the fourth inclined surface with a diameter larger than that of the small-diameter outer peripheral surface, each rolling element having a different load capacity with respect to the radial load of the outer ring portion and the inner ring portion. The moving body is
With a simple configuration, the inner ring portion and the outer ring portion do not interfere with each other, and are easily arranged and downsized.
【００１２】請求項５記載の旋回座軸受は、請求項１な
いし４いずれか一記載の旋回座軸受において、軸方向が
一方向の転動体は、外輪部および内輪部に当接する外周
面の垂線が前記外輪部および前記内輪部に掛かる軸方向
に沿った最大荷重の方向に対して１６．７°以上４２°
以下の角度で配設されたものである。そして、外周面の
垂線が外輪部および内輪部に掛かる軸方向に沿った最大
荷重の方向に対して１６．７°以上４２°以下の角度と
なるように軸方向を傾斜させて転動体を配設して単列複
式スラスト軸受を構成したため、各転動体に掛かる負荷
がほぼ均等化して、円滑な旋回が得られる。なお、角度
が１６．７°より小さくなると一方向の荷重容量は大き
くなるが、異なる大きさの反対方向の荷重が掛かった際
の各転動体に掛かる負荷の均等化が図れず、円滑な旋回
が得られにくくなり、角度が４２°より大きくなると、
外輪部および内輪部に掛かる軸方向に沿った荷重に対す
る荷重容量が小さくなり、荷重が支持しきれなくなるお
それがあるため、１６．７°以上４２°以下の角度に設
定する。According to a fifth aspect of the present invention, there is provided a swivel bearing according to any one of the first to fourth aspects, wherein the rolling element having one axial direction is perpendicular to an outer peripheral surface abutting the outer ring portion and the inner ring portion. Is 16.7 ° or more and 42 ° with respect to the direction of the maximum load along the axial direction applied to the outer ring portion and the inner ring portion.
They are arranged at the following angles. The rolling elements are arranged by inclining the axial direction such that the perpendicular of the outer peripheral surface is at an angle of 16.7 ° or more and 42 ° or less with respect to the direction of the maximum load along the axial direction applied to the outer ring portion and the inner ring portion. In this case, the load applied to each rolling element is substantially equalized, and smooth turning is obtained. When the angle is smaller than 16.7 °, the load capacity in one direction increases, but the load applied to each rolling element when a load of a different size is applied in the opposite direction cannot be equalized, and a smooth turning is performed. Is difficult to obtain, and when the angle is greater than 42 °,
Since the load capacity with respect to the load applied to the outer ring portion and the inner ring portion along the axial direction becomes small and there is a possibility that the load cannot be completely supported, the angle is set to 16.7 ° or more and 42 ° or less.
【００１３】[0013]
【発明の実施の形態】以下、本発明の旋回座軸受の実施
の一形態を図面を参照して説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a swivel bearing according to the present invention will be described below with reference to the drawings.
【００１４】図１および図２において、１は旋回座軸受
で、この旋回座軸受１は、例えばクレーンなどの物揚機
械や油圧ショベルなどの建設機械である図示しない作業
装置を車両や船舶などの本体に回転自在に取り付け作業
装置を旋回可能に軸支するように作業装置および本体間
に介在して取り付けられる。In FIGS. 1 and 2, reference numeral 1 denotes a swivel seat bearing. The swivel seat bearing 1 is provided with a working device (not shown) such as a lifting machine such as a crane or a construction machine such as a hydraulic shovel, such as a vehicle or a ship. The work device is rotatably mounted on the main body and is interposed between the work device and the main body so as to pivotally support the work device.
【００１５】そして、旋回座軸受１は、略環状の外輪部
２と、この外輪部２の内周側に外輪部２の内周面に外周
面が対向して位置して配設された略環状の内輪部３と、
外輪部２および内輪部３間に挟持され外輪部２および内
輪部３を相対的に回転自在に連結保持する複数の円柱状
の転動体であるコロ4a，4bとを備えている。The swivel seat bearing 1 has a substantially annular outer ring portion 2 and an inner ring surface of the outer ring portion 2. The inner ring surface of the outer ring portion 2 is opposed to the outer circumferential surface of the outer ring portion 2. An annular inner ring 3,
Rollers 4a and 4b, which are a plurality of cylindrical rolling elements, sandwiched between the outer ring portion 2 and the inner ring portion 3 and rotatably connect and hold the outer ring portion 2 and the inner ring portion 3 relatively rotatably.
【００１６】また、外輪部２は、例えば硬質鋼材にて内
周面が円筒状である略環状に形成され、作業装置を取り
付ける図示しないボルトなどの取付部材が挿通される軸
方向に沿った挿通孔６が複数設けられている。さらに、
外輪部２の内周面には、略中央に周方向に沿って内輪部
３の外周面に向けて拡開する略Ｖ字溝状の外輪溝部７が
設けられている。The outer ring portion 2 is formed of, for example, a hard steel material and is formed in a substantially annular shape having a cylindrical inner peripheral surface, and is inserted along an axial direction through which a mounting member such as a bolt (not shown) for mounting a working device is inserted. A plurality of holes 6 are provided. further,
On the inner peripheral surface of the outer ring portion 2, there is provided an outer ring groove portion 7 having a substantially V-shaped groove shape that expands toward the outer peripheral surface of the inner ring portion 3 along the circumferential direction substantially at the center.
【００１７】そして、外輪溝部７は、第１の傾斜面８お
よび第２の傾斜面９にて内方に拡開するように略Ｖ字溝
状に形成されている。なお、第１の傾斜面８は、垂線が
上下方向である軸方向に対して所定の角度θ1 、例えば
１６．７°以上４２°以下の角度θ1 となるように傾斜
して形成されている。また、第２の傾斜面９は、垂線が
上下方向である軸方向に対して所定の角度θ2 、例えば
４８°以上７３．３°以下の角度θ2 、すなわち９０°
−θ1 の角度θ2 となるように傾斜して形成されてい
る。さらに、外輪溝部７の第１の傾斜面８および第２の
傾斜面９との間には、略円弧状の逃げ部10が設けられて
いる。The outer ring groove 7 is formed in a substantially V-shaped groove so as to expand inward at the first inclined surface 8 and the second inclined surface 9. The first inclined plane 8, perpendicular line vertical predetermined angle theta 1 with respect to the axial direction which is the direction, for example, 16.7 ° or 42 ° are formed to be inclined such that the angle theta 1 below I have. Further, the second inclined surface 9 forms a predetermined angle θ 2 with respect to the axial direction in which the vertical line is the vertical direction, for example, an angle θ 2 of not less than 48 ° and not more than 73.3 °, that is, 90 °.
It is formed to be inclined so as to have an angle θ 2 of −θ 1 . Further, between the first inclined surface 8 and the second inclined surface 9 of the outer ring groove portion 7, a substantially arc-shaped relief portion 10 is provided.
【００１８】さらに、外輪部２は、第１の傾斜面８の縁
に連続する内周面が径小に形成された径小内周面12とな
り、第２の傾斜面９の縁に連続する内周面が径小内周面
12より径大で略同軸上に形成された径大内周面13とな
り、径小内周面12の部分が径大内周面13の部分に比して
肉厚に形成されている。Further, the outer ring portion 2 becomes a small-diameter inner peripheral surface 12 in which an inner peripheral surface continuous with the edge of the first inclined surface 8 is formed to have a small diameter, and is continuous with the edge of the second inclined surface 9. Inner surface is small diameter inner surface
A large-diameter inner peripheral surface 13 larger than 12 and formed substantially coaxially is formed, and the portion of the small-diameter inner peripheral surface 12 is formed thicker than the portion of the large-diameter inner peripheral surface 13.
【００１９】また、外輪部２には、外周面から内周面に
貫通する円形の投入口14が開口形成され、この投入口14
を閉塞して図示しないボルトまたはノックピンなどで固
定される蓋体15が設けられている。The outer race portion 2 is formed with a circular inlet 14 which penetrates from the outer peripheral surface to the inner peripheral surface.
A cover 15 is provided, which is closed and fixed with a bolt or a knock pin (not shown).
【００２０】一方、内輪部３は、外輪部２と同様に例え
ば硬質鋼材にて外周面が円筒状である略環状に形成さ
れ、車両や船舶などの本体に取り付ける図示しないボル
トなどの取付部材が挿通される軸方向に沿った挿通孔20
が複数設けられている。さらに、内輪部３の外周面に
は、略中央に周方向に沿って外輪部２の外輪溝部７に対
向する外輪部２の内周面に向けて拡開する略Ｖ字溝状の
内輪溝部21が設けられている。On the other hand, the inner race portion 3 is formed in a substantially annular shape having a cylindrical outer peripheral surface, for example, of a hard steel material similarly to the outer race portion 2, and has an attachment member such as a bolt (not shown) attached to a main body of a vehicle or a ship. Insertion hole 20 along the axial direction to be inserted
Are provided. Further, on the outer peripheral surface of the inner ring portion 3, a substantially V-shaped groove-shaped inner ring groove portion which is opened toward the inner peripheral surface of the outer ring portion 2 facing the outer ring groove portion 7 of the outer ring portion 2 substantially in the center along the circumferential direction. 21 are provided.
【００２１】そして、内輪溝部21は、第３の傾斜面22お
よび第４の傾斜面23にて外方に拡開するように略Ｖ字溝
状に形成されている。なお、第４の傾斜面23は、外輪溝
部７の第１の傾斜面８に平行に対向、すなわち垂線が上
下方向である軸方向に対して所定の角度θ1 、例えば１
６．７°以上４２°以下の角度θ1 となるように傾斜し
て形成されている。また、第３の傾斜面22は、第２の傾
斜面９に平行に対向、すなわち垂線が上下方向である軸
方向に対して９０°−θ1 の所定の角度θ2 、例えば４
８°以上７３．３°以下の角度θ2 となるように傾斜し
て形成されている。さらに、内輪溝部21の第３の傾斜面
22および第４の傾斜面23との間には、外輪溝部７と同様
に略円弧状の逃げ部24が設けられている。The inner ring groove 21 is formed in a substantially V-shaped groove so as to expand outward on the third inclined surface 22 and the fourth inclined surface 23. The fourth inclined surface 23 is opposed to the first inclined surface 8 of the outer ring groove 7 in parallel with the first inclined surface 8, that is, a predetermined angle θ 1 , for example, 1 with respect to the axial direction whose vertical line is the vertical direction.
It is formed to be inclined so as to have an angle θ 1 of 6.7 ° or more and 42 ° or less. Further, the third inclined surface 22 faces in parallel with the second inclined surface 9, that is, a predetermined angle θ 2 of 90 ° −θ 1 with respect to the axial direction whose vertical line is the vertical direction, for example, 4 °.
It is formed to be inclined so as to have an angle θ 2 of 8 ° or more and 73.3 ° or less. Furthermore, the third inclined surface of the inner ring groove 21
A substantially arc-shaped relief portion 24 is provided between the outer peripheral groove 22 and the fourth inclined surface 23, similarly to the outer ring groove portion 7.
【００２２】さらに、内輪部３は、第３の傾斜面22の縁
に連続する外周面が径小に形成された径小外周面26とな
り、第４の傾斜面23の縁に連続する外周面が径小外周面
26より径大で略同軸上に形成された径大外周面27とな
り、径小外周面26の部分が径大外周面27の部分に比して
肉薄に形成されている。Further, the inner race portion 3 is a small-diameter outer peripheral surface 26 having an outer peripheral surface continuous with the edge of the third inclined surface 22 formed into a small diameter, and an outer peripheral surface continuous with the edge of the fourth inclined surface 23. Has a small diameter outer peripheral surface
The outer peripheral surface 27 has a larger diameter and is formed substantially coaxially with the outer peripheral surface 27. The portion of the outer peripheral surface 26 having a smaller diameter is formed thinner than the outer peripheral surface 27 of the larger diameter.
【００２３】また、内輪部３の内周面には、作業装置に
設けられた図示しない駆動手段の歯車が噛み合うギヤ29
が形成されている。On the inner peripheral surface of the inner ring portion 3, a gear 29 meshed with a gear of driving means (not shown) provided in the working device is provided.
Are formed.
【００２４】一方、コロ4a，4bは、外輪部２および内輪
部３と同様に例えば硬質鋼材にて端部縁が面取りされて
略円柱状に形成されている。そして、コロ4a，4bは、外
周面が外輪溝部７の第１の傾斜面８および内輪溝部21の
第４の傾斜面23に当接する回転軸ａの状態と、外周面が
外輪溝部７の第２の傾斜面９および内輪溝部21の第３の
傾斜面22に当接する回転軸ｂの状態とが、回転軸ａおよ
び回転軸ｂを直交するように交互に位置して、対向する
外輪溝部７および内輪溝部21間に挟持されるように配設
されている。そして、これら外輪溝部７、内輪溝部21お
よびコロ4a，4bにて単列複式スラスト軸受30が構成され
ている。On the other hand, the rollers 4a and 4b, like the outer ring 2 and the inner ring 3, are formed in a substantially columnar shape with a chamfered end edge made of, for example, a hard steel material. The rollers 4a and 4b have a state in which the outer peripheral surface is in contact with the first inclined surface 8 of the outer ring groove 7 and the fourth inclined surface 23 of the inner ring groove 21, and the outer peripheral surface is the third surface of the outer ring groove 7. The rotation axis b and the state of the rotating shaft b contacting the third inclined surface 22 of the inner ring groove 21 are alternately positioned so that the rotation axis a and the rotation axis b are orthogonal to each other. And it is arranged so as to be sandwiched between the inner ring grooves 21. The outer ring groove 7, the inner ring groove 21, and the rollers 4a, 4b constitute a single-row double-type thrust bearing 30.
【００２５】また、回転軸ａの状態のコロ4aは、外周面
が当接する第１の傾斜面８および第４の傾斜面23と同様
に傾斜、すなわち外周面の垂線が第１の傾斜面８および
第４の傾斜面23の垂線と平行で上下方向である外輪部２
および内輪部３の軸方向に対して例えば１６．７°以上
４２°以下の角度θ1 となるように傾斜して形成されて
いる。さらに、回転軸ｂの状態のコロ4bも同様に、外周
面が当接する第２の傾斜面９および第３の傾斜面22と同
様に傾斜、すなわち外周面の垂線が第２の傾斜面９およ
び第３の傾斜面22の垂線と平行で上下方向である外輪部
２および内輪部３の軸方向に対して９０°−θ1 の角度
θ2 である例えば４８°以上７３．３°以下の角度θ2
となるように傾斜して形成されている。The roller 4a in the state of the rotation axis a is inclined in the same manner as the first inclined surface 8 and the fourth inclined surface 23 with which the outer peripheral surface abuts, that is, the perpendicular of the outer peripheral surface is the first inclined surface 8 And the outer ring portion 2 that is parallel to the vertical line of the fourth inclined surface 23 and that is in the vertical direction.
And it is formed so as to be inclined at an angle θ 1 of , for example, 16.7 ° or more and 42 ° or less with respect to the axial direction of the inner ring portion 3. Further, the roller 4b in the state of the rotation axis b is similarly inclined in the same manner as the second inclined surface 9 and the third inclined surface 22 with which the outer peripheral surface is in contact, that is, the perpendicular of the outer peripheral surface is the second inclined surface 9 and An angle θ 2 of 90 ° −θ 1 with respect to the axial direction of the outer ring portion 2 and the inner ring portion 3 that is parallel to the vertical line of the third inclined surface 22 and is vertical, for example, an angle of 48 ° or more and 73.3 ° or less. θ 2
It is formed so as to be inclined.
【００２６】なお、各コロ4a，4bの軸方向の端面は、外
輪溝部７および内輪溝部21に負荷が掛かった状態で当接
しないように若干の間隙が設けられて配設されている。The axial end faces of the rollers 4a and 4b are provided with a slight gap so that they do not come into contact with the outer ring groove 7 and the inner ring groove 21 under a load.
【００２７】また、各コロ4a，4b間には、コロ4a，4b間
の間隔を保持してコロ4a，4bをがたつきなく外輪溝部７
および内輪溝部21間に配設するプラスチックなどにて形
成された間隙保持部材である図示しないセパレータが配
設されている。Also, between the rollers 4a, 4b, the gap between the rollers 4a, 4b is maintained so that the rollers 4a, 4b do not rattle and the outer ring groove portion 7 is formed.
A separator (not shown), which is a gap holding member formed of plastic or the like, provided between the inner ring grooves 21 is provided.
【００２８】そして、コロ4a，4bの配設により、外輪部
２および内輪部３が相対的に回転自在に連結保持されて
いる。The outer race 2 and the inner race 3 are rotatably connected and held by the arrangement of the rollers 4a and 4b.
【００２９】また、作業装置の駆動手段の駆動により、
内輪部３のギヤ29に噛み合う駆動手段の歯車が内輪部３
の内周側を転動して、本体に取り付け固定された内輪部
３に対して外輪部２とともに作業装置が回転して旋回す
る。Also, by driving the driving means of the working device,
The gear of the driving means meshing with the gear 29 of the inner race 3 is the inner race 3
The working device rotates together with the outer ring portion 2 with respect to the inner ring portion 3 attached and fixed to the main body, and turns.
【００３０】次に、上記実施の一形態の旋回座軸受の組
み立て動作を説明する。Next, the assembling operation of the swivel bearing of the above embodiment will be described.
【００３１】まず、あらかじめ外輪部２の内周側に内輪
部３を同軸上に位置させ、外輪部２の投入口14からコロ
4a，4bおよびセパレータを外輪溝部７および内輪溝部21
間に交互に投入する。なお、コロ4a，4bは、回転軸ａの
状態および回転軸ｂの状態が交互に位置するように投入
する。そして、外輪溝部７および内輪溝部21内にコロ4
a，4bおよびセパレータを配設後、蓋体15を図示しない
ボルトまたはノックピンなどにて投入口14を閉塞のため
外輪部２に取り付け、旋回座軸受１を組み立てる。First, the inner ring portion 3 is positioned coaxially on the inner peripheral side of the outer ring portion 2 in advance, and the
4a, 4b and the separator are connected to the outer ring groove 7 and the inner ring groove 21.
Feed alternately in between. The rollers 4a and 4b are loaded so that the state of the rotating shaft a and the state of the rotating shaft b are alternately located. Then, the rollers 4 are inserted into the outer ring groove 7 and the inner ring groove 21.
After disposing the separators a and 4b and the separator, the cover 15 is attached to the outer ring portion 2 with a bolt or a knock pin (not shown) so as to close the inlet port 14 and the swivel bearing 1 is assembled.
【００３２】次に、上記実施の一形態の旋回座軸受１の
作用を説明する。Next, the operation of the swivel bearing 1 according to the embodiment will be described.
【００３３】例えばクレーンなどの物揚機械や油圧ショ
ベルなどの建設機械である図示しない作業装置を、旋回
座軸受１の径方向が水平方向となるように配設して旋回
可能に取り付けた場合について説明する。A case in which a working device (not shown) such as a lifting machine such as a crane or a construction machine such as a hydraulic shovel is arranged so that the radial direction of the swivel bearing 1 is horizontal and pivotally mounted. explain.
【００３４】まず、作業装置が駆動していない状態にお
いて、作業装置の重心が外輪部２の中心上方に位置する
場合には、旋回座軸受１にはこの旋回座軸受１の軸方向
である重力方向に沿った鉛直方向の荷重である図２に示
す矢印Ｆのアキシアル荷重Ｆが軸受荷重として掛かる。
また、作業装置の重心が外輪部２の外側上方に位置する
場合には、アキシアル荷重Ｆの他に図２に示す矢印Ｍの
モーメント荷重Ｍが軸受荷重として掛かる。なお、歯車
の噛み合いで生じるラジアル荷重は小さい。First, when the center of gravity of the working device is located above the center of the outer ring portion 2 in a state where the working device is not driven, the slewing bearing 1 has gravity acting in the axial direction of the slewing bearing 1. An axial load F indicated by an arrow F in FIG. 2, which is a load in a vertical direction along the direction, is applied as a bearing load.
In addition, when the center of gravity of the working device is located outside and above the outer race portion 2, a moment load M indicated by an arrow M shown in FIG. The radial load generated by the meshing of the gears is small.
【００３５】また、作業装置が駆動した際には大きなモ
ーメント荷重Ｍが軸受荷重として掛かる。そして、これ
らアキシアル荷重Ｆやモーメント荷重Ｍにより、旋回座
軸受１の軸方向に沿って下向きである重力方向に掛かる
アキシアル荷重Ｆおよびモーメント荷重Ｍの一部である
軸受荷重Ｆ1 は、旋回座軸受１の軸方向に沿って上向き
である反重力方向に掛かるモーメント荷重Ｍの一部であ
る軸受荷重Ｆ2 より大きく、一般に、図３に示すよう
に、Ｆ2 はＦ1 の略０．３〜０．９倍の大きさの荷重で
あることが知られている。When the working device is driven, a large moment load M is applied as a bearing load. Due to the axial load F and the moment load M, the axial load F and the bearing load F1, which is a part of the moment load M, applied in the gravitational direction which is downward along the axial direction of the swivel seat bearing 1, are changed. greater than bearing load F 2 is part of a moment load M applied to the anti-gravity direction is upward along the first axis direction, generally, as shown in FIG. 3, F 2 is substantially 0.3 of the F 1 It is known that the load is 0.9 times as large.
【００３６】そして、図１３に示すように、コロ4aの外
周面の垂線が旋回座軸受１の軸方向に対して平行な状態
（旋回座軸受１の中心軸に垂直な平面と外輪部２および
内輪部３によってコロ4aに与えられる作用線とのなす角
である接触角が９０°）の場合における軸受荷重の掛か
る方向への外周面の投影長さＬは最大長となる。また、
図１１に示すように、従来のコロ44a の外周面の垂線が
旋回座軸受41の軸方向に対して４５°傾斜した場合（接
触角が４５°）には、軸受荷重の掛かる方向への外周面
の投影長さＬ1 は、回転軸ａ，ｂの傾斜する方向にかか
わらず、 Ｌ1 ＝Ｌ2 ＝Ｌ×ｃｏｓ４５°＝0.7071Ｌ となり、図１２に示すように、軸受荷重に対するコロ44
a ，44b で支えられる荷重容量Ｑ1 ，Ｑ2 も同一とな
る。As shown in FIG. 13, the perpendicular of the outer peripheral surface of the roller 4a is parallel to the axial direction of the swivel bearing 1 (a plane perpendicular to the center axis of the swivel bearing 1 and the outer ring 2 and The projected length L of the outer peripheral surface in the direction in which the bearing load is applied when the contact angle, which is the angle formed by the inner ring portion 3 with the action line given to the roller 4a, is 90 °, is the maximum length. Also,
As shown in FIG. 11, when the perpendicular of the outer peripheral surface of the conventional roller 44a is inclined by 45 ° with respect to the axial direction of the swivel bearing 41 (contact angle is 45 °), the outer periphery in the direction in which the bearing load is applied The projection length L 1 of the surface is L 1 = L 2 = L × cos 45 ° = 0.7071L regardless of the direction in which the rotation axes a and b are inclined. As shown in FIG.
The load capacities Q 1 and Q 2 supported by a and 44b are also the same.
【００３７】一方、図４に示すように、回転軸ａの状態
のコロ4aの外周面の垂線が旋回座軸受１の軸方向に対し
て３５°傾斜した場合（接触角は、５５°）には、軸受
荷重の掛かる方向への外周面の投影長さＬ1 は、 Ｌ1 ＝Ｌ×ｃｏｓ３５°＝0.8192Ｌ で、回転軸ｂの状態のコロ4bにおける外周面の投影長さ
Ｌ2 は、 Ｌ2 ＝Ｌ×ｃｏｓ（９０°−３５°）＝Ｌ×ｃｏｓ５５
°＝0.5736Ｌ となる。On the other hand, as shown in FIG. 4, when the perpendicular of the outer peripheral surface of the roller 4a in the state of the rotating shaft a is inclined by 35 ° with respect to the axial direction of the swivel bearing 1 (the contact angle is 55 °). Is the projected length L 1 of the outer peripheral surface in the direction in which the bearing load is applied, L 1 = L × cos 35 ° = 0.8192L, and the projected length L 2 of the outer peripheral surface of the roller 4b in the state of the rotating shaft b is L 2 = L × cos (90 ° −35 °) = L × cos55
° = 0.5736L.
【００３８】また、図１に示すように、コロ4a，4bの外
周面に当接する外輪溝部７および内輪部３の溝深さ
ｌ1 ，ｌ2 、すなわち第１の傾斜面８および第４の傾斜
面23の旋回座軸受１の軸方向に沿った方向への投影長さ
ｌ1 および第２の傾斜面９および第３の傾斜面22の旋回
座軸受１の軸方向に沿った方向への投影長さｌ2 を、ほ
ぼ ｌ1 ＝Ｌ1 ，ｌ 2 ＝Ｌ2 となるように形成して、コロ4a，4bの外周面のほぼ全長
が外輪溝部７および内輪溝部21のほぼ全長に当接するよ
うにする。Further, as shown in FIG. 1, the groove depths l 1 and l 2 of the outer ring groove portion 7 and the inner ring portion 3 which are in contact with the outer peripheral surfaces of the rollers 4a and 4b, ie, the first inclined surface 8 and the fourth inclined surface The projection length l 1 of the inclined surface 23 in the direction along the axial direction of the swivel bearing 1, and the projection of the second inclined surface 9 and the third inclined surface 22 in the direction along the axial direction of the swivel bearing 1. The projection length l 2 is formed so as to be approximately l 1 = L 1 , l 2 = L 2, and substantially the entire length of the outer peripheral surface of the rollers 4a, 4b corresponds to substantially the entire length of the outer ring groove 7 and the inner ring groove 21. Make contact.
【００３９】このため、軸受荷重に対するコロ4a，4bで
支えられる荷重容量も異なり、回転軸ａの状態のコロ4a
の方が大きくなる。すなわち、コロ4a，4bの回転軸ａ，
ｂの傾斜状態となる外周面の垂線が旋回座軸受１の軸方
向である鉛直方向に対して傾斜する度合により、回転軸
ａの状態のコロ4aと回転軸ｂの状態のコロ4bとの荷重容
量Ｑ1 ，Ｑ2 が反比例に可変することとなる。For this reason, the load capacity supported by the rollers 4a and 4b with respect to the bearing load is also different, and the roller 4a in the state of the rotating shaft a is different.
Is larger. That is, the rotation axes a of the rollers 4a and 4b,
The load between the roller 4a in the state of the rotating shaft a and the roller 4b in the state of the rotating shaft b depends on the degree of inclination of the perpendicular of the outer peripheral surface in the inclined state of b with respect to the vertical direction which is the axial direction of the swivel bearing 1. The capacitances Q 1 and Q 2 vary in inverse proportion.
【００４０】そして、図１２に示す回転軸が４５°傾斜
した場合のコロに掛かる転動体荷重Ｆ1 を支持する荷重
容量Ｑに対して、図４に示す回転軸ａの状態のコロ4aの
荷重容量Ｑ1 は、 Ｑ1 ＝（ｃｏｓ３５°／ｃｏｓ４５°）Ｑ＝ 1.158Ｑ で、図５に示す回転軸ｂの状態のコロの荷重容量Ｑ
2 は、 Ｑ2 ＝（ｃｏｓ５５°／ｃｏｓ４５°）Ｑ＝ 0.811Ｑ となる。[0040] Then, the load capacity Q for supporting the rolling element load F 1 applied to the rollers when the rotary shaft shown in FIG. 12 is inclined by 45 °, the load of the rollers 4a of the state of the rotary axis a illustrated in FIG. 4 The capacity Q 1 is: Q 1 = (cos 35 ° / cos 45 °) Q = 1.158Q, and the load capacity Q of the roller in the state of the rotating shaft b shown in FIG.
2 is: Q 2 = (cos 55 ° / cos 45 °) Q = 0.111Q
【００４１】ここで、反重力方向に掛かる軸受荷重Ｆ2
は、重力方向に掛かる軸受荷重Ｆ1の略０．３〜０．９
倍の大きさの荷重であることから、回転軸ｂの状態のコ
ロ4bの荷重容量Ｑ2 も回転軸ａの状態のコロ4aの荷重容
量Ｑ1 の略０．３〜０．９倍の容量があれば十分に軸受
荷重Ｆ2 を支持できる。Here, the bearing load F 2 applied in the anti-gravity direction
Is approximately the bearing load F 1 acting in the direction of gravity 0.3-0.9
Since multiple of a size load of approximately 0.3 to 0.9 times the capacity of the load capacitance to Q 1 roller 4a of the state of the load capacitance Q 2 the rotation axis a of the roller 4b of the state of the rotating shaft b I can fully support the bearing load F 2, if any.
【００４２】このため、 Ｑ2 ＝０．３Ｑ1 またはＱ2 ＝０．９Ｑ1 ， Ｑ2 ／Ｑ1 ＝ｃｏｓ（９０°−θ1 ）／ｃｏｓθ1 上式から求める角度θ1 は、それぞれ約１６．７°およ
び約４２°（接触角で約７３．３°および約４８°）と
なる。[0042] Therefore, Q 2 = 0.3Q 1 or Q 2 = 0.9Q 1, Q 2 / Q 1 = cos (90 ° -θ 1) / cosθ 1 angle theta 1 determined from the above equation is about respectively 16.7 ° and about 42 ° (about 73.3 ° and about 48 ° in contact angle).
【００４３】そして、重力方向に向けて掛かる軸受荷重
Ｆ1 を支持する回転軸ａの状態のコロ4aを、外周面の垂
線が旋回座軸受の軸方向である鉛直方向に対して約１
６．７°以上約４２°以下の角度θ1 （接触角で４８°
以上７３．３°以下）に傾斜し、反重力方向に向けて掛
かる軸受荷重Ｆ2 を支持する回転軸ｂの状態のコロ4b
を、９０°−θ1 の式から４８°以上７３．３°以下の
角度θ2 （接触角で１６．７°以上４２°以下）に傾斜
する状態に外輪溝部７および内輪溝部21を設計形成して
配設する。この軸受荷重Ｆ1 ，Ｆ2 の大きさに対応して
角度を適宜設定して配設することにより、図６および図
７に示すように、大きい負荷である重力方向に掛かる軸
受荷重Ｆ1 を支持する回転軸ａの状態のコロ4aの荷重容
量Ｑ1 が増大する一方、小さい負荷である反重力方向に
掛かる軸受荷重Ｆ2 を支持する回転軸ｂの状態のコロ4b
の荷重容量Ｑ2 が減少するので、重力方向に掛かる軸受
荷重Ｆ1 と反重力方向に掛かる軸受荷重Ｆ2 との大きさ
が異なる場合でも、回転軸ａの状態のコロ4aと回転軸ｂ
の状態のコロ4bとで受ける軸受荷重Ｆ1 ，Ｆ2 による負
荷はほぼ均等化する。[0043] Then, the roller 4a of the state of the rotating shaft a which supports the bearing load F 1 acting toward the direction of gravity about the vertical direction is perpendicular to the outer peripheral surface is an axial direction of the slewing rim bearing 1
Angle θ 1 between 6.7 ° and about 42 ° (48 ° in contact angle)
Above 73.3 angled ° or less), the state of the rotating shaft b which supports the bearing load F 2 applied toward the antigravity direction roller 4b
The outer ring groove portion 7 and the inner ring groove portion 21 are designed and formed in such a manner that the outer ring groove portion 7 and the inner ring groove portion 21 are inclined at an angle θ 2 of 48 ° to 73.3 ° (contact angle of 16.7 ° to 42 °) from the equation of 90 ° −θ 1. And arrange them. By arranging the angle appropriately in accordance with the magnitude of the bearing loads F 1 and F 2 , the bearing load F 1 acting in the direction of gravity, which is a large load, is reduced as shown in FIGS. while loading capacity to Q 1 roller 4a of the state of the rotary shaft a supporting increases, the state of the rotating shaft b which supports the bearing load F 2 applied to the anti-gravity direction with a small load rollers 4b
Since the load capacity Q 2 of decreases, even if the magnitude of the bearing load F 1 acting in the gravitational direction and bearing load F 2 applied to the anti-gravity direction is different, the rotary shaft and the roller 4a of the state of the rotating shaft a b
The loads due to the bearing loads F 1 and F 2 received by the rollers 4b in the state of ( 1) are almost equalized.
【００４４】このため、例えば回転軸ａの状態のコロ4a
の摩耗が回転軸ｂの状態のコロ4bの摩耗より早くなるこ
とにより、片減りした状態となって作業装置が円滑に旋
回しなくなるなどを防止でき、円滑な作業装置の旋回が
得られて、作業性を向上できる。For this reason, for example, the roller 4a in the state of the rotating shaft a
The wear of the roller 4b in the state of the rotating shaft b is faster than that of the roller 4b, thereby preventing the working device from turning smoothly due to a reduced state, and a smooth turning of the working device can be obtained. Workability can be improved.
【００４５】また、回転軸ａの状態のコロ4aと回転軸ｂ
の状態のコロ4bとの荷重容量Ｑ1 ，Ｑ2 を可変させる構
成として、コロ4a，4bを第１の傾斜面８および第２の傾
斜面９を有した外輪溝部７と第３の傾斜面22および第４
の傾斜面23を有した内輪溝部21間に挟持し、大きな軸受
荷重を支持するコロ4aの軸方向に沿った大きな軸受荷重
が掛かる方向への投影長さが、小さい軸受荷重である反
対方向の軸受荷重を支持するコロ4bの軸方向に沿った反
対方向への投影長さより大きくなるように、コロ4aの外
周面に当接する第１の傾斜面８および第４の傾斜面23の
大きな軸受荷重が掛かる方向への投影長さが、コロ4bの
外周面に当接する第２の傾斜面９および第３の傾斜面22
の反対方向への投影長さより大きくなるように形成した
ため、簡単な構成で容易にコロ4a，4bに掛かる負荷を均
等化できる。The roller 4a in the state of the rotating shaft a and the rotating shaft b
In order to change the load capacities Q 1 and Q 2 with the roller 4b in the state of ( 1) , the rollers 4a and 4b are provided with an outer ring groove 7 having a first inclined surface 8 and a second inclined surface 9 and a third inclined surface. 22nd and 4th
The projection length in the direction in which a large bearing load is applied along the axial direction of the roller 4a that is sandwiched between the inner ring groove portions 21 having the inclined surfaces 23, and supports a large bearing load, is opposite to the small bearing load. A large bearing load on the first inclined surface 8 and the fourth inclined surface 23 abutting on the outer peripheral surface of the roller 4a so as to be larger than the projected length of the roller 4b supporting the bearing load in the opposite direction along the axial direction. The projection length in the direction in which is applied is the second inclined surface 9 and the third inclined surface 22 that are in contact with the outer peripheral surface of the roller 4b.
Is formed so as to be longer than the projection length in the opposite direction, the load applied to the rollers 4a and 4b can be easily equalized with a simple configuration.
【００４６】さらに、外輪部２の第１の傾斜面８の縁側
に連続する内周面に径小内周面12を設け、第２の傾斜面
９の縁側に連続する内周面に径大内周面13を設けるとと
もに、内輪部３の第３の傾斜面22の縁側に連続する外周
面に径小外周面26を設け、第４の傾斜面23の縁側に連続
する外周面に径大外周面27を設けたため、簡単な構成で
容易に内輪部３および外輪部２が干渉せずに、コロ4aの
外周面に当接する第１の傾斜面８および第４の傾斜面23
の大きな軸受荷重が掛かる方向への投影長さが、コロ4b
の外周面に当接する第２の傾斜面９および第３の傾斜面
22の反対方向への投影長さより大きくなるように形成で
きる。Further, a small-diameter inner peripheral surface 12 is provided on an inner peripheral surface of the outer ring portion 2 that is continuous with the edge of the first inclined surface 8, and a large-diameter inner peripheral surface that is continuous with the edge of the second inclined surface 9 is provided. An inner peripheral surface 13 is provided, a small-diameter outer peripheral surface 26 is provided on an outer peripheral surface of the inner ring portion 3 that is continuous with the edge of the third inclined surface 22, and a large-diameter outer peripheral surface that is continuous with the edge of the fourth inclined surface 23 is provided with a large diameter. Since the outer peripheral surface 27 is provided, the first and fourth inclined surfaces 8 and 23 which come into contact with the outer peripheral surface of the roller 4a without interference between the inner ring portion 3 and the outer ring portion 2 easily with a simple configuration.
The projected length in the direction in which the large bearing load is
2nd slope 9 and 3rd slope which contact the peripheral face of
22 can be formed to be larger than the projection length in the opposite direction.
【００４７】なお、上記実施の一形態において、旋回座
軸受１の径方向が水平方向となるように配設して説明し
たが、例えば径方向を鉛直方向に配設し常時は軸方向に
荷重が掛かる状態で使用するなど、軸方向に沿った一方
側の荷重が反対方向の荷重より大きくなるようないずれ
の場合でも軸受として利用できる。In the above embodiment, the swivel bearing 1 is arranged so that the radial direction is horizontal, but, for example, the swivel bearing 1 is arranged vertically in the radial direction, and the load is always applied in the axial direction. It can be used as a bearing in any case where the load on one side along the axial direction is larger than the load in the opposite direction, such as when used in a state where the load is applied.
【００４８】そして、外輪部２および内輪部３を略環状
に形成したが、外輪部２の外周側および内輪部の内周側
の構成は、利用態様により適宜設定される。The outer ring portion 2 and the inner ring portion 3 are formed in a substantially annular shape. However, the configuration of the outer ring portion of the outer ring portion 2 and the inner ring side of the inner ring portion are appropriately set according to the usage.
【００４９】また、転動体として、円柱状のコロ4a，4b
を用いて説明したが、円筒状に近い樽状でも異なる荷重
に対する容量が異なるようないずれの形状のものでもで
きる。As rolling elements, cylindrical rollers 4a and 4b are used.
Although the description has been made with reference to the above, any barrel shape having a different capacity with respect to a different load can be used even in a barrel shape close to a cylindrical shape.
【００５０】さらに、コロ4a，4bを配設する構成とし
て、蓋体15にて閉塞される投入口14から投入する場合に
限らず、例えば図８に示す構成の旋回座軸受31のよう
に、外輪部32を２分割し、２分割された第１の外輪部33
および第２の外輪部34を合わせつつコロ4a，4bを配設す
るなど、いずれの構成でもよい。Further, the configuration in which the rollers 4a and 4b are provided is not limited to the case where the rollers 4a and 4b are inserted through the insertion port 14 closed by the lid 15, and may be, for example, a swivel seat bearing 31 having a configuration shown in FIG. The outer ring part 32 is divided into two parts, and the first outer ring part 33 is divided into two parts.
Either configuration may be adopted, such as disposing the rollers 4a and 4b while aligning the second outer ring portion 34 with the outer ring portion 34.
【００５１】[0051]
【発明の効果】請求項１記載の旋回座軸受によれば、外
輪部および内輪部の径方向に対して軸方向が一方向に傾
斜する転動体の外輪部および内輪部に掛かる軸方向に沿
った荷重に対する荷重容量を、軸方向が他方向に傾いた
転動体に掛かる荷重に対する荷重容量より大きくなるよ
うに単列複式スラスト軸受を構成したため、軸方向が異
なる各転動体に外輪部および内輪部の軸方向に沿って異
なる大きさの反対方向の荷重が掛かっても、各転動体に
掛かる負荷を均等化でき、円滑な旋回が得られる。According to the turning seat bearing of the first aspect, the axial direction of the rolling element whose axial direction is inclined in one direction with respect to the radial direction of the outer ring portion and the inner ring portion extends along the axial direction of the outer ring portion and the inner ring portion. Single-row double-type thrust bearings are designed so that the load capacity for the applied load is greater than the load capacity for the load applied to the rolling element whose axial direction is inclined in the other direction. Even if loads of different magnitudes in opposite directions are applied along the axial direction, the loads applied to the rolling elements can be equalized, and smooth turning can be obtained.
【００５２】請求項２記載の旋回座軸受によれば、請求
項１記載の旋回座軸受の効果に加え、外輪部および内輪
部に掛かる軸方向に沿った最大荷重の方向への軸方向が
一方向へ傾いた転動体の外周面の投影長さを、軸方向が
他方向に傾いた転動体の最大荷重の方向と反対方向への
外周面の投影長さより大きくしたため、外輪部および内
輪部に掛かる軸方向に沿った異なる大きさの反対方向の
荷重に対する軸方向の異なる各転動体の荷重容量が異な
り、異なる大きさの反対方向の荷重が掛かっても簡単な
構成で各転動体に掛かる負荷を均等化できる。According to the slewing bearing of the second aspect, in addition to the effect of the slewing bearing of the first aspect, the maximum load applied along the axial direction on the outer ring portion and the inner ring portion is one. Because the projected length of the outer peripheral surface of the rolling element inclined in the direction is larger than the projected length of the outer peripheral surface in the direction opposite to the direction of the maximum load of the rolling element whose axial direction is inclined in the other direction, the outer ring part and the inner ring part The load capacity of each different rolling element in the axial direction is different for the opposite load of different size along the applied axial direction, and the load applied to each rolling element with a simple configuration even if a different size of the load in the opposite direction is applied. Can be equalized.
【００５３】請求項３記載の旋回座軸受によれば、請求
項１または２記載の旋回座軸受の効果に加え、外輪部の
内周面に設けた外輪溝部の第１の傾斜面と内輪部の外周
面に設けた内輪溝部の第１の傾斜面に対向する第４の傾
斜面との外輪部および内輪部の軸方向に沿って掛かる最
大荷重の方向への投影長さを、外輪溝部の第２の傾斜面
および内輪部の第２の傾斜面に対向する第３の傾斜面の
最大荷重の方向と反対方向への投影長さより大きくした
ため、外輪部および内輪部に掛かる軸方向に沿った異な
る大きさの反対方向の荷重に対する軸方向の異なる各転
動体の荷重容量が異なり、異なる大きさの反対方向の荷
重が掛かっても簡単な構成で各転動体に掛かる負荷を均
等化できる。According to the third aspect of the present invention, in addition to the effects of the first or second aspect, the first inclined surface of the outer ring groove provided on the inner peripheral surface of the outer ring and the inner ring portion. The projection length of the inner ring groove portion provided on the outer peripheral surface of the outer ring groove portion with the fourth inclined surface facing the first inclined surface in the direction of the maximum load applied along the axial direction of the outer ring portion and the inner ring portion, Since the projection length of the third inclined surface facing the second inclined surface and the second inclined surface of the inner ring portion in the direction opposite to the direction of the maximum load was larger than that of the second inclined surface, the axial direction applied to the outer ring portion and the inner ring portion was extended. The load capacities of the different rolling elements in the axial direction with respect to the different loads of the opposite directions are different, and even if loads of different sizes in the opposite directions are applied, the loads applied to the respective rolling elements can be equalized with a simple configuration.
【００５４】請求項４記載の旋回座軸受によれば、請求
項１ないし３いずれか一記載の旋回座軸受の効果に加
え、外輪部の外輪溝部の第１の傾斜面の縁側に径小内周
面を設け、外輪溝部の第２の傾斜面の縁側に径小内周面
より径大に略同軸上の径大内周面を設けるとともに、内
輪部の内輪溝部の第３の傾斜面の縁側に外輪部の径小内
周面に対向する径小外周面を設け、内輪溝部の第４の傾
斜面の縁側に径小外周面より径大に略同軸上の径大外周
面を設けたため、外輪部および内輪部の径方向に沿った
荷重に対して異なる荷重容量となる各転動体が、簡単な
構成で内輪部および外輪部が干渉せず容易に配設でき、
小型化できる。According to the fourth aspect of the present invention, in addition to the effect of the first aspect of the present invention, in addition to the effect of the first aspect of the present invention, the outer ring portion has a small inner diameter at the edge of the first inclined surface of the outer ring groove. A peripheral surface is provided, and a large-diameter inner peripheral surface that is substantially coaxial with a diameter larger than the small-diameter inner peripheral surface is provided on the edge side of the second inclined surface of the outer ring groove portion, and a third inclined surface of the inner ring groove portion of the inner ring portion is provided. A small-diameter outer peripheral surface facing the small-diameter inner peripheral surface of the outer ring portion is provided on the edge side, and a large-diameter outer peripheral surface that is substantially coaxial with the diameter of the fourth inclined surface of the inner ring groove portion and is larger in diameter than the small-diameter outer peripheral surface is provided. , Each rolling element having a different load capacity with respect to the radial load of the outer ring part and the inner ring part can be easily arranged with a simple configuration without interference between the inner ring part and the outer ring part,
Can be downsized.
【００５５】請求項５記載の旋回座軸受によれば、請求
項１ないし４いずれか一記載の旋回座軸受の効果に加
え、外周面の垂線が外輪部および内輪部に掛かる軸方向
に沿った最大荷重の方向に対して１６．７°以上４２°
以下の角度となるように軸方向を傾斜させて転動体を配
設したため、簡単な構造で容易に各転動体に掛かる負荷
をほぼ均等化でき、円滑な旋回が容易に得られる。According to the fifth aspect of the present invention, in addition to the effects of the first to fourth aspects of the present invention, the vertical line of the outer peripheral surface extends along the axial direction of the outer ring portion and the inner ring portion. 16.7 degrees or more and 42 degrees with respect to the direction of the maximum load
Since the rolling elements are arranged so as to be inclined in the axial direction so as to have the following angles, the load applied to each rolling element can be easily and substantially equalized with a simple structure, and smooth turning can be easily obtained.
【図１】本発明の旋回座軸受の実施の一形態を示す一部
を切り欠いた断面図である。FIG. 1 is a partially cutaway sectional view showing an embodiment of a swivel bearing according to the present invention.
【図２】同上旋回座軸受の断面図である。FIG. 2 is a sectional view of the pivot seat bearing.
【図３】同上旋回座軸受に掛かる軸受荷重の状況を示す
説明図である。FIG. 3 is an explanatory diagram showing a state of a bearing load applied to the swivel seat bearing.
【図４】同上一方のコロの傾斜状態を示す説明図であ
る。FIG. 4 is an explanatory diagram showing an inclined state of one of the rollers.
【図５】同上他方のコロの傾斜状態を示す説明図であ
る。FIG. 5 is an explanatory view showing an inclined state of the other roller of the above.
【図６】同上軸受荷重の大きさの異なる割合が小さい際
の各コロの荷重容量の状況を示す説明図である。FIG. 6 is an explanatory diagram showing the state of the load capacity of each roller when the different ratios of the bearing loads are small.
【図７】同上軸受荷重の大きさの異なる割合が大きい際
の各コロの荷重容量の状況を示す説明図である。FIG. 7 is an explanatory diagram showing the state of the load capacity of each roller when the ratio of the magnitude of the bearing load is large.
【図８】本発明の旋回座軸受の他の実施の形態を示す一
部を切り欠いた断面図である。FIG. 8 is a partially cutaway sectional view showing another embodiment of the swivel seat bearing of the present invention.
【図９】従来例の旋回座軸受の一部を切り欠いた断面図
である。FIG. 9 is a sectional view of a conventional swivel seat bearing with a part cut away.
【図１０】同上旋回座軸受の断面図である。FIG. 10 is a cross-sectional view of the pivot seat bearing.
【図１１】同上コロの傾斜状態を示す説明図である。FIG. 11 is an explanatory view showing an inclined state of the roller.
【図１２】同上各コロの荷重容量の状況を示す説明図で
ある。FIG. 12 is an explanatory diagram showing a state of a load capacity of each roller in the same.
【図１３】従来の他の旋回座軸受のコロの傾斜状態を示
す説明図である。FIG. 13 is an explanatory view showing an inclined state of rollers of another conventional swivel seat bearing.
１，31 旋回座軸受 ２，32 外輪部 ３ 内輪部 4a，4b 転動体としてのコロ ７ 外輪溝部 ８ 第１の傾斜面 ９ 第２の傾斜面 12 径小内周面 13 径大内周面 21 内輪溝部 22 第３の傾斜面 23 第４の傾斜面 26 径小外周面 27 径大外周面 30 単列複式スラスト軸受 1, 31 Swivel seat bearing 2, 32 Outer ring part 3 Inner ring part 4a, 4b Roller as rolling element 7 Outer ring groove part 8 First inclined surface 9 Second inclined surface 12 Small inner peripheral surface 13 Large inner peripheral surface 21 Inner ring groove 22 Third inclined surface 23 Fourth inclined surface 26 Small outer diameter surface 27 Large outer diameter surface 30 Single row double thrust bearing
Claims (5)
面に対向する内輪部と、 前記外輪部および前記内輪部間にこれら外輪部および内
輪部の径方向に対して軸方向が交差しかつ互いに軸方向
が交差して交互に複数配設された略円柱状の転動体を有
する単列複式スラスト軸受とを備え、 前記軸方向が一方向の転動体の前記外輪部および前記内
輪部の軸方向に沿って掛かる荷重に対する荷重容量が、
前記軸方向が他方向の転動体に掛かる荷重に対する荷重
容量より大きいことを特徴とした旋回座軸受。1. An outer ring portion having an inner peripheral surface having a cylindrical shape, an inner ring portion located on an inner peripheral side of the outer ring portion and an outer peripheral surface facing an inner peripheral surface of the outer ring portion, the outer ring portion and the inner ring portion A single-row double-type thrust bearing having a plurality of substantially cylindrical rolling elements alternately arranged in such a manner that the axial direction intersects the radial direction of the outer ring portion and the inner ring portion and the axial direction intersects with each other. The load capacity with respect to the load applied along the axial direction of the outer ring portion and the inner ring portion of the rolling element whose axial direction is one direction,
A swivel seat bearing characterized in that the axial direction is larger than a load capacity for a load applied to a rolling element in another direction.
内輪部に掛かる軸方向に沿った最大荷重の方向への外周
面の投影長さが、軸方向が他方向の転動体の前記最大荷
重の方向と反対方向への外周面の投影長さより大きいこ
とを特徴とする請求項１記載の旋回座軸受。2. The projection length of the outer peripheral surface in the direction of the maximum load along the axial direction applied to the outer ring portion and the inner ring portion of the rolling element whose axial direction is one direction is the same as that of the rolling element whose axial direction is the other direction. The swivel bearing according to claim 1, wherein the length is greater than a projection length of the outer peripheral surface in a direction opposite to a direction of the maximum load.
接する第１の傾斜面および第２の傾斜面を有し内輪部側
に向けて拡開する外輪溝部を有し、 前記内輪部は、外周面に前記第２の傾斜面に平行に対向
し前記転動体の外周面が当接する第３の傾斜面および前
記第１の傾斜面に平行に対向し前記転動体の外周面が当
接する第４の傾斜面を有し前記外輪部に向けて拡開する
内輪溝部を有し、 前記第１の傾斜面および前記第４の傾斜面の前記外輪部
および前記内輪部の軸方向に沿って掛かる最大荷重の方
向への投影長さが、前記第２の傾斜面および前記第３の
傾斜面の前記最大荷重の方向と反対方向への投影長さよ
り大きいことを特徴とした請求項１または２記載の旋回
座軸受。3. The outer ring portion has a first inclined surface and a second inclined surface with which the outer peripheral surface of the rolling element abuts on the inner peripheral surface, and has an outer ring groove portion that expands toward the inner ring portion, The inner ring portion is opposed to an outer peripheral surface in parallel with the second inclined surface, and is opposed in parallel to the third inclined surface and the first inclined surface with which the outer peripheral surface of the rolling element is in contact, and the outer periphery of the rolling element. An inner ring groove having a fourth inclined surface with which a surface abuts and expanding toward the outer ring portion; axes of the outer ring portion and the inner ring portion of the first inclined surface and the fourth inclined surface; The projection length in the direction of the maximum load applied along the direction is larger than the projection length of the second inclined surface and the third inclined surface in the direction opposite to the direction of the maximum load. Item 3. A swivel bearing according to item 1 or 2.
斜面の縁側に設けられた径小内周面と、前記外輪溝部の
第２の傾斜面の縁側に前記径小内周面より径大に略同軸
上に設けられた径大内周面とを有し、 内輪部は、外周面に内輪溝部の第３の傾斜面の縁側に設
けられ前記外輪部の径小内周面に対向する径小外周面
と、前記内輪溝部の第４の傾斜面の縁側に前記径小外周
面より径大に略同軸上に設けられた径大外周面とを有し
たことを特徴とする請求項１ないし３いずれか一記載の
旋回座軸受。4. The outer ring portion has a small-diameter inner peripheral surface provided on the inner peripheral surface on the edge side of the first inclined surface of the outer ring groove portion, and the small-diameter inner peripheral surface provided on the edge side of the second inclined surface of the outer ring groove portion. A large-diameter inner peripheral surface provided substantially coaxially with a diameter larger than the peripheral surface, and an inner ring portion is provided on the outer peripheral surface on the edge side of the third inclined surface of the inner ring groove portion, and the inner ring portion has a smaller diameter. A small-diameter outer peripheral surface facing the peripheral surface; and a large-diameter outer peripheral surface provided substantially coaxially on the edge side of the fourth inclined surface of the inner race groove portion with a diameter larger than the small-diameter outer peripheral surface. The swivel bearing according to any one of claims 1 to 3.
び内輪部に当接する外周面の垂線が前記外輪部および前
記内輪部に掛かる軸方向に沿った最大荷重の方向に対し
て１６．７°以上４２°以下の角度で配設されたことを
特徴とする請求項１ないし４いずれか一記載の旋回座軸
受。5. A rolling element having an axial direction in one direction, wherein a perpendicular of an outer peripheral surface abutting on an outer ring portion and an inner ring portion has a perpendicular to a direction of a maximum load along the axial direction applied to the outer ring portion and the inner ring portion. The swivel seat bearing according to any one of claims 1 to 4, wherein the swivel bearing is arranged at an angle of not less than 0.7 ° and not more than 42 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9020231A JP2975903B2 (en) | 1997-02-03 | 1997-02-03 | Swivel bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9020231A JP2975903B2 (en) | 1997-02-03 | 1997-02-03 | Swivel bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10220466A JPH10220466A (en) | 1998-08-21 |
| JP2975903B2 true JP2975903B2 (en) | 1999-11-10 |
Family
ID=12021412
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9020231A Expired - Lifetime JP2975903B2 (en) | 1997-02-03 | 1997-02-03 | Swivel bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2975903B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5011025B2 (en) * | 2007-08-16 | 2012-08-29 | 株式会社アンテックス | Double row 4-point contact ball bearing |
| JP2010127319A (en) * | 2008-11-25 | 2010-06-10 | Antex Corp | Revolving seat bearing |
| JP2010151152A (en) * | 2008-12-24 | 2010-07-08 | Antex Corp | Revolving seat bearing |
| CN102312918B (en) * | 2011-06-14 | 2014-07-16 | 安徽枞晨回转支承有限公司 | Double row oblique cylinder type slewing bearing |
| JP2014059025A (en) * | 2012-09-19 | 2014-04-03 | Ntn Corp | Bearing for wind power/tidal power generation |
| CN112128227B (en) * | 2020-08-20 | 2022-06-17 | 北京特种机械研究所 | Articulated slewing bearing device |
-
1997
- 1997-02-03 JP JP9020231A patent/JP2975903B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10220466A (en) | 1998-08-21 |
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