WO2011152355A1 - スライド装置 - Google Patents
スライド装置 Download PDFInfo
- Publication number
- WO2011152355A1 WO2011152355A1 PCT/JP2011/062386 JP2011062386W WO2011152355A1 WO 2011152355 A1 WO2011152355 A1 WO 2011152355A1 JP 2011062386 W JP2011062386 W JP 2011062386W WO 2011152355 A1 WO2011152355 A1 WO 2011152355A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- bearing
- inner ring
- slider
- raceway groove
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller 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
- F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
- F16C13/006—Guiding rollers, wheels or the like, formed by or on the outer element of a single bearing or bearing unit, e.g. two adjacent bearings, whose ratio of length to diameter is generally less than one
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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
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller bearings
- F16C29/045—Ball or roller bearings having rolling elements journaled in one of the moving parts
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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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. clamping
- F16C2226/12—Force connections, e.g. clamping by press-fit, e.g. plug-in
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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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
- F16C2226/52—Positive connections with plastic deformation, e.g. caulking or staking
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/02—Wheel hubs or castors
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/31—Axle
Definitions
- the present invention relates to a slide device using a ball bearing, which can accurately move linearly with a low load, and more specifically to a slider of the slide device.
- this type of slide device is well known as a linear guide using balls as rolling elements.
- what is called the cross roller guide which used the roller for the rolling element is known by what supports a higher load.
- a linear guide using a slider in which a large number of ball bearings are arranged can be arranged in the same frame to achieve a reduction in size, and three ball bearings are used as one set for the frame.
- the guide in four directions is possible without adjustment even with the accuracy of the aluminum sash.
- Patent Document 2 a roller such as a resin is provided around the ball bearing, and the roller is disposed so as to contact the corresponding left and right track surfaces of the rail in the longitudinal direction of the rail between the corresponding sliders.
- Japanese Patent Laid-Open No. 11-37154 page 3, [0010], FIG. 1 and FIG. 3
- Japanese Laid-Open Patent Publication No. 8-2322952 page 3, [0007], FIG. 2, FIG. 3)
- the bearing is fixed by caulking to the slider plate with a stepped shaft having a flange. It is also disclosed that the caulking portion of the plate is recessed to escape the rest of the shaft caulking.
- the resin or rubber that is bonded, press-fitted or insert-molded around the bearing it is necessary to hold the resin or rubber that is bonded, press-fitted or insert-molded around the bearing, and these materials are soft and elastically deformed. There was a problem that it was difficult to correct, and the resin and rubber on the outer peripheral portion were likely to be damaged.
- the shaft provided on the slider and the bearing inner ring are fixed by press-fitting or the like, and the shaft has a straight shape.
- the dimensional relationship between the shaft and the inner ring is set as a tight fit, and the squeezing is set in consideration of the removal force and the radial clearance of the bearing.
- the inner ring inner diameter of the bearing is increased and the radial gap is decreased by press-fitting the bearing into the shaft.
- the shaft diameter is slightly increased by caulking the shaft, and so-called thickening of the shaft also reduces or eliminates the radial gap, resulting in heavy bearing rotation. Not only can it become smooth, but it also shortens its lifespan.
- the rigidity of the inner ring changes depending on the shape of the raceway groove and the thickness of the inner race, when a straight shaft is press-fitted, the raceway groove is deformed as a result.
- the deformation of the raceway groove is considered to be a decrease in the accuracy of the bearing, resulting in a variation in rotational torque, a variation in radial gap, and the like, resulting in a decrease in accuracy and reliability of the slide device.
- the present invention solves the above-described conventional problems, and a first object is to prevent the influence on the outer diameter of the shaft on which the bearing is mounted, to easily correct the inclination of the shaft, and to reduce the cost and accuracy.
- a good slide device is provided.
- the second purpose is to make it easy to manage the conventional shimoshiro and to reduce the change in radial gap and raceway groove that are reduced by press-fitting, thereby preventing an increase in bearing load and accuracy. Therefore, a highly reliable slide device is provided.
- a first invention includes a rail having a substantially C-shaped cross section, and a bearing that is arranged corresponding to an inner wall plane of the rail and rotates an outer ring, and this bearing.
- the shaft that holds the inner ring of the bearing of the slider is integral with the slider and has a through hole in the center. With this configuration, another shaft is inserted into the through hole, and by using this shaft, the shaft can be substantially held without grasping the outer diameter of the slider shaft.
- the shaft is characterized in that the base portion close to the slider facilitates plastic deformation.
- the base portion close to the slider facilitates plastic deformation.
- the shaft is characterized in that the rigidity in the radial direction is made lower than that of the inner ring of the bearing to prevent deformation of the raceway groove of the bearing inner ring to be press-fitted.
- the shaft is formed by squeezing the slider.
- a second invention comprises a rail having a substantially C-shaped cross section, an outer ring rotating bearing disposed corresponding to an inner wall plane of the rail, and an inner ring of the bearing.
- the shaft that holds the inner ring of the bearing of the slider has a low rigidity of the portion corresponding to the raceway groove of the inner ring of the bearing. It is characterized by that.
- the shaft is characterized in that the portion corresponding to the raceway groove of the inner ring is thinned.
- the bearing corresponding to the raceway groove of the inner ring of the bearing is provided with a relief that does not contact the inner ring of the bearing.
- the width of the dengue or the thickness removal is equal to or larger than the width of the raceway groove of the inner ring of the bearing.
- the first invention by providing the through hole in the shaft of the slider to which the bearing is mounted, when correcting the inclination of the shaft, another shaft is inserted into the through hole.
- the shaft By using the shaft, it is possible to substantially hold the shaft without grasping the outer diameter of the slider shaft.
- the shaft outer diameter can be corrected without scratching, and an inexpensive and highly reliable slide device can be realized.
- the tilt of the shaft can be corrected without gripping the bearing.
- the rigidity of the portion of the slider corresponding to the inner ring of the bearing corresponding to the raceway groove of the bearing is reduced, thereby reducing the deformation of the raceway groove of the inner ring of the bearing. Therefore, it is possible to easily manage the white-eye and prevent an increase in load, and to realize a highly reliable slide device.
- the side view of the rail which concerns on the 1st Embodiment of this invention The top view of the slider which concerns on the 1st Embodiment of this invention XX sectional view of the slider in FIG. Sectional view of the slider shaft Enlarged view of part C in FIG.
- Conceptual diagram explaining axis tilt correction Sectional drawing of the slider which concerns on the 2nd Embodiment of this invention Sectional drawing of the principal part of the axis
- FIG. 1 is a perspective view showing a rail of a slide device according to a first embodiment of the present invention
- FIG. 2 is a side view of the rail of FIG. 1 viewed from the direction A
- FIG. 3 is a plan view of a slider
- FIG. 3 is a sectional view of the slider taken along line XX
- FIG. 5 is a sectional view of the shaft portion of the slider
- FIG. 6 is an enlarged view of FIG. 5, and FIG.
- the rail 1 has a substantially C-shaped cross section, and the first traveling surface 2 at the bottom as an inner wall plane on which the outer ring 18 of the bearing travels while rotating, and this traveling surface. 2 has a second running surface 3 provided above 2.
- fixing holes 4 for fixing the rail 1 to a base (not shown) with screws or the like are arranged in the rail 1 at substantially equal intervals in the longitudinal direction.
- the rail 1 of this embodiment is made of ferritic stainless steel (SUS430) with a good balance of strength, hardness, and workability. Used. In order to make the required shape, it is made by cold working with a press.
- the outer dimensions of the rail are about 20 mm in width, about 10 mm in height, and about 250 mm in length.
- the length direction is the travel direction of the slider, which will be described later, and the travel direction is indicated by an arrow in the figure.
- the first traveling surfaces 2a and 2b are provided on the left and right at the bottom on the inner surface side of the rail 1.
- a wall perpendicular to the first traveling surfaces 2a and 2b is provided parallel to the traveling direction and above the first traveling surfaces 2a and 2b at an angle with the first traveling surfaces 2a and 2b.
- the left and right paired second running surfaces 3a and 3b are provided.
- the portion indicated by the dotted line in the figure is the surface of the portion that contacts the outer ring 18 of the bearing, and is hardened by cold working, and the hardness increases toward the surface.
- a required shape is created by pressing, it is work hardened by sufficiently pressing with a mold or performing bending R-collision.
- the surface is given an inclination so that the hardness decreases in the thickness direction from the running surface.
- FIG. 3 is a plan view of the slider 10.
- the slider 10 has six bearings 11a, 11b, 11b, 12a, 12a, and 12b attached to a base 15 having a metal sheet in a required shape.
- a fixing hole 16 for fixing the slider 10 to a base of a moving body (not shown) with a screw or the like is appropriately provided.
- the base 15 in this embodiment is a cold rolled steel plate (SPCC) with a thickness of 1.6 mm, and the surface is electroless nickel plated.
- the bearing is a deep groove ball bearing having an inner diameter (d) of ⁇ 4 mm, an outer diameter (D) of ⁇ 7 mm, and a width (B) of 2 mm.
- the inner ring 17 and the outer ring 18 and the ball 19 of the rolling element are quenched and tempered with martensitic stainless steel (SUS440C equivalent) to a required hardness.
- SUS440C equivalent martensitic stainless steel
- bowl it is also possible to use suitably the thing of a high carbon chromium steel (SUJ2) or a ceramic with a low density.
- the three bearings 11a, 11b and 11b correspond to the running surfaces 2a and 2b at the bottom of the rail 1, and the other three bearings 12a, 12a and 12b correspond to the second running surfaces 3a and 3b.
- the bearings of the slider 10 are guided to the inner surface of the inner wall of the rail 1 and can stably travel with respect to the corresponding traveling surface.
- the base 15 is integrally provided with a shaft 20 press-fitted into the inner ring 17 of the bearing 11b in a required dimension and direction by drawing.
- the shaft 20 is cylindrical, has an outer diameter of 4 mm, and a through hole 21 having a diameter of about 3.2 mm is provided in the center.
- the length of the straight portion of the shaft 20 is about 2.3 mm, which is closer to the base 15 than the tip portion.
- the shaft 20 has a smaller thickness than the inner ring 17 of the bearing 11b, the rigidity in the radial direction is lowered. Therefore, even if the shaft 20 is press-fitted into the inner ring 17 of the bearing 11b, the inner ring of the bearing 11b. It is possible to prevent deformation of the raceway groove 17a provided in 17. As a result, the raceway groove 17a of the inner ring 17 of the bearing 11b is maintained and assembled with high accuracy, so that it can be stably rotated with a low load (torque). Thereby, a highly reliable slide device can be realized.
- the other bearings and shafts of the slider 10 have the same configuration.
- a shaft 20 provided by drawing on the slider 10 holds the slider 10 so as to be slidable with respect to the rail 1 with a required accuracy via a bearing, and the angular accuracy with respect to the rail 1 is particularly important.
- a shaft 26 that can be inserted is provided at one end with respect to the through hole 21 of the shaft 20 provided in the base 15, and a shaft having a shape similar to that of a screwdriver having a handle 25 is used at the other end.
- a shaft 26 that can be inserted through the 20 through holes 21 is inserted.
- a stress capable of plastic deformation can be applied to the root portion 22 of the shaft 20.
- the base portion 22 of the shaft 20 is reduced in thickness so that plastic deformation occurs more easily than the tip portion.
- a large stress is generated in the root portion 22 and plastic deformation is given, so that the inclination of the shaft 20 can be easily corrected.
- the shaft 20 is designed to be easily plastically deformed, strain and residual stress with respect to other portions of the slider 10 can be reduced.
- the direction to be corrected is not limited to the direction of B, and it can be easily understood that the direction can be corrected to a direction perpendicular to B or an arbitrary direction to be corrected.
- this inclination correction since the inclination correction can be performed without grasping the outer diameter portion of the shaft 20 press-fitted into the inner ring 17 of the bearing, the outer diameter of the shaft is not damaged. As a result, it is possible to prevent the bearing from being influenced. Further, it can be easily understood that the correction jig 24 can be inserted from the base 15 side, contrary to FIG.
- the shaft is integrally formed by drawing, the number of parts can be reduced, and reliability can be improved.
- the relationship between the shaft and the bearing can be applied to a configuration in which the outer ring is rotated with a slight gap and a configuration in which the inner ring and the shaft are bonded and fixed.
- the inner ring raceway groove is not deformed, and it is possible to prevent the adhesion from coming off.
- the present invention can be applied to prevent the bearing from being detached in the thrust direction by crushing or pushing the tip of the through hole.
- the thinned portion 23 is formed by removing the outer diameter portion of the straight portion of the shaft 20 corresponding to the raceway groove 17a of the inner ring 17 of the bearing 11b. Since the rigidity of the shaft 20 in the radial direction is lower than that of the inner ring 17 of the bearing 11b, even if the shaft 20 is press-fitted into the inner ring 17 of the bearing 11b, the deformation of the raceway groove 17a provided in the inner ring of the bearing 11b. Can be prevented. As a result, the raceway groove 17a of the bearing 11b can be reduced in deformation, and can stably rotate with a low load (torque). Thereby, a highly reliable slide device can be realized.
- the rigidity of the portion corresponding to the raceway groove 17a need only be low without reducing the rigidity of the shaft 20 as compared with the inner ring 17 of the bearing 11b.
- the other bearings and shafts of the slider 10 have the same configuration.
- the portion corresponding to the raceway groove 17a since the portion corresponding to the raceway groove 17a has a lower rigidity than the other portions due to the rigidity of the shaft 20 in the radial direction, the inner ring 17 of the inner ring 17 is pressed into the inner ring 17 of the bearing. Deformation of the raceway groove 17a can be reduced. Furthermore, in the control of the squeeze between the shaft 20 and the inner ring 17, the influence of deformation on the raceway groove 17a of the inner ring 17 can be reduced, so that the management can be facilitated, thereby reducing the reliability with low load. A high slide device can be realized.
- FIG. 10 is a characteristic diagram showing the characteristics of the sliding load at each temperature of the sliding device in the present embodiment. Compared with the characteristics of the conventional slide device, the sliding load can be reduced at each temperature. It can also be seen that the magnitude of the change in sliding load due to temperature is small. This is because the change due to the difference in temperature expansion coefficient between the shaft 20 and the bearing inner ring 17 lowers the rigidity of the shaft 20 in the radial direction, so that the raceway groove 17a is more reliably compared to the conventional slide device. This is thought to be due to the reduction in deformation.
- a plurality of annular grooves 23 a are provided on the outer peripheral side of the shaft at a portion corresponding to the raceway groove 17 a of the inner ring 17 of the bearing.
- the annular groove 23a can be configured in one or a plurality of spiral shapes. Since the operation is the same as that of the second embodiment, the description thereof will be omitted.
- the effect of the metal removal is partially changed as appropriate by changing the interval, width, and depth of the groove 23a. Can be done easily. That is, it is possible to change the rigidity appropriately and easily according to the longitudinal direction of the shaft 20. Further, according to the second and third embodiments, it is possible to further strengthen the fixation of the bearing with the inner ring 17 by applying an adhesive to the thinned portion and the groove portion of the shaft 20.
- the thinned portion 23b is formed by thinning the inner diameter portion of the shaft 20 in the straight portion of the shaft 20. According to this embodiment, there are the same effects as the second and third embodiments. Furthermore, in the present embodiment, since the outer diameter of the shaft 20 becomes uniform, handling in the case of finishing the outer diameter later is convenient because it can be handled as a normal shaft.
- the straight portion of the shaft 20 is provided with a protrusion 23c having a width Ws that does not contact the inner ring 17 at the outer diameter portion of the shaft 20 with respect to the width dimension Wb of the raceway groove 17a of the inner ring 17 of the bearing 11b.
- the relationship between the width dimension Wb of the track groove 17a and the width dimension Ws of the protrusion 23c that does not contact the inner ring 17 is Wb ⁇ Ws, and the deformation of the track groove 17a is reliably prevented. Further, it is also possible to configure the relief 23c that does not contact the inner ring 17 as in the third embodiment.
- the slide device of the first invention by providing a through hole in the shaft of the slider to which the bearing is mounted, the tilt of the shaft can be corrected without grasping the outer diameter of the shaft.
- a slide device can be provided, and is useful for application to an expensive linear guide or the like.
- the slide device of the second invention can reduce deformation of the inner ring raceway groove by reducing the rigidity of the portion of the bearing of the slider on which the bearing is mounted with respect to the inner ring raceway groove. It is possible to provide a slide device with high dynamic reliability.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Bearings For Parts Moving Linearly (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
また、軸にベアリングを組立てた後であっても、ベアリングを掴むことなく軸の傾きなどの修正が可能となる。
また、第2の発明によれば、ベアリングの内輪が装着されるスライダーの軸をベアリングの内輪の軌道溝に対応する部分の剛性を低くしたことにより、ベアリングの内輪の軌道溝の変形を低減することができ、シメシロの管理を容易にすると共に、負荷の増加を防止しでき、信頼性の高いスライド装置を実現できる。
本発明の実施の形態について、図面を参照しながら説明する。図1は本発明の第1の実施形態に係るスライド装置のレールを示す斜視図、図2は図1のレールをAの方向から見た側面図、図3はスライダーの平面図、図4は図3におけるスライダーのX-X断面図、図5はスライダーの軸部分の断面図、図6は図5の拡大図、図7は軸の傾き修正を説明する概念図である。先ずスライド装置の概要について説明する。
次に本発明における第2の実施形態について図8を参照して説明する。本実施形態では、軸20の構成のみが第1の実施形態と異なるため、軸20の構成について詳細に説明し、第1の実施形態と同一部分については同一の符号を付して説明を省略する。
次に本発明の第3実施形態について、図9Aを参照して説明する。本実施形態では、軸20の構成のみが第1の実施形態と異なるため、軸20の構成について詳細に説明し、第1の実施形態と同一部分については同一の符号を付して説明を省略する。
また、第2及び第3実施形態によれば、軸20の除肉部分や溝部分に接着剤を塗布させることによって、ベアリングの内輪17との固定をより強固にすることも可能である。
次に本発明の第4実施形態について、図9Bを参照して説明する。本実施形態では、軸20の構成のみが第1の実施形態と異なるため、軸20の構成について詳細に説明し、第1の実施形態と同一部分については同一の符号を付して説明を省略する。
次に本発明の第5実施形態について、図9Cを参照して説明する。本実施形態では、軸20の構成のみが第1の実施形態と異なるため、軸20の構成について詳細に説明し、第1の実施形態と同一部分については同一の符号を付して説明を省略する。
以上説明した除肉、溝、ニゲなどは、単独でも、組み合わせて実施することは可能なことは明らかである。また、本発明はこれらの実施の形態に限定されることなく、適宜変更は可能であることは明らかである。
また、第2の発明のスライド装置は、ベアリングが装着されるスライダーの軸のベアリングの内輪軌道溝に対する部分の剛性を低くしたことにより、内輪軌道溝の変形を低減することができるので、低摺動負荷で信頼性の高いスライド装置が提供できるものである。
2、2a、2b 第1の走行面
3、3a、3b 第2の走行面
4 固定穴
10 スライダー
11a、11b ベアリング
12a、12b ベアリング
15 ベース
16 固定穴
17 内輪
17a 軌道溝
18 外輪
19 ボール
20 軸
21 貫通穴
22 根元部分
22a 応力集中部
23 除肉部
23a 溝
23b 除肉部
23c ニゲ
24 修正冶具
25 ハンドル
26 軸
Claims (8)
- 概略Cの字型断面を有するレールと、レールの内壁平面に対応して配置され、外輪回転するベアリングと、を備え、このベアリングの内輪を保持するスライダーが前記レールに案内されて直線運動をするスライド装置において、前記スライダーの前記ベアリングの内輪を保持する軸は前記スライダーと一体で中央に貫通穴を有することを特徴とするスライド装置。
- 前記軸は、スライダーに近い根元部分が塑性変形を容易としたことを特徴とする請求項1記載のスライド装置。
- 前記軸は、前記ベアリングの内輪より半径方向の剛性を低くし、圧入される内輪の軌道溝の変形を防止することを特徴とする請求項1又は2記載のスライド装置。
- 前記軸は前記スライダーを絞り出すことで作られることを特徴とする請求項1ないし3のいずれか1項記載のスライド装置。
- 概略Cの字型断面を有するレールと、レールの内壁平面に対応して配置される外輪回転するベアリングと、このベアリングの内輪を保持するスライダーが、前記レールの内壁平面に案内されて直線運動をするスライド装置において、前記スライダーの前記ベアリングの内輪を保持する軸は、前記ベアリングの内輪の軌道溝に対応する部分の剛性を低くしたことを特徴とするスライド装置。
- 前記軸は、内輪の軌道溝に対応する部分を除肉したことを特徴とする請求項5記載のスライド装置。
- 前記軸は、前記ベアリングの内輪の軌道溝に対応する部分と当接しないニゲを設けたことを特徴とする請求項5記載のスライド装置。
- 前記ニゲまたは除肉の幅は前記ベアリングの内輪の軌道溝の幅と同じか幅より大きいことを特徴とする請求項6又は7記載のスライド装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11789758.7A EP2578893B1 (en) | 2010-06-01 | 2011-05-30 | Sliding device |
US13/634,267 US8827560B2 (en) | 2010-06-01 | 2011-05-30 | Slide device |
CN201180001562.2A CN102369365B (zh) | 2010-06-01 | 2011-05-30 | 滑动装置 |
JP2012518382A JP5747914B2 (ja) | 2010-06-01 | 2011-05-30 | スライド装置 |
Applications Claiming Priority (2)
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JP2010126012 | 2010-06-01 | ||
JP2010-126012 | 2010-06-01 |
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WO2011152355A1 true WO2011152355A1 (ja) | 2011-12-08 |
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/062386 WO2011152355A1 (ja) | 2010-06-01 | 2011-05-30 | スライド装置 |
Country Status (5)
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---|---|
US (1) | US8827560B2 (ja) |
EP (1) | EP2578893B1 (ja) |
JP (1) | JP5747914B2 (ja) |
CN (2) | CN102369365B (ja) |
WO (1) | WO2011152355A1 (ja) |
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JPH08232952A (ja) | 1995-03-01 | 1996-09-10 | Purutonchien Kk | ローラー型直線案内装置 |
JPH1137154A (ja) | 1997-07-24 | 1999-02-09 | Oki Electric Ind Co Ltd | 直線ガイド機構 |
JP2002089577A (ja) * | 2000-09-19 | 2002-03-27 | Nsk Ltd | 軸受装置 |
JP2006322579A (ja) * | 2005-05-20 | 2006-11-30 | Jtekt Corp | 転がり軸受 |
JP2007331457A (ja) * | 2006-06-13 | 2007-12-27 | Ntn Corp | 車輪用軸受装置 |
JP2010126012A (ja) | 2008-11-28 | 2010-06-10 | Hitachi Automotive Systems Ltd | 車両制御用マルチコアシステムまたは内燃機関の制御装置 |
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GB8529940D0 (en) * | 1985-12-04 | 1986-01-15 | Jackson P A S | Ball slide system |
GB8707244D0 (en) * | 1987-03-26 | 1987-04-29 | Hepco Slide Systems Ltd | Slide systems |
CH673137A5 (en) * | 1987-10-30 | 1990-02-15 | Fernand Moser | Precision linear guide with ball bearing rollers - has spigots for rollers projecting from slider, with rollers fitting into tracks along rail |
US4914712A (en) * | 1988-04-08 | 1990-04-03 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Device for supporting lift roll for fork lift truck |
DE3829276C2 (de) | 1988-08-30 | 1998-02-19 | Skf Linearsysteme Gmbh | Anordnung zum Anstellen von auf einem Tragkörper angeordneten Laufrollen |
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JP2750821B2 (ja) * | 1994-10-17 | 1998-05-13 | プルトンチエン株式会社 | ローラー型直線案内装置 |
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2011
- 2011-05-30 WO PCT/JP2011/062386 patent/WO2011152355A1/ja active Application Filing
- 2011-05-30 JP JP2012518382A patent/JP5747914B2/ja active Active
- 2011-05-30 CN CN201180001562.2A patent/CN102369365B/zh active Active
- 2011-05-30 CN CN201110454376.6A patent/CN102562798B/zh active Active
- 2011-05-30 US US13/634,267 patent/US8827560B2/en active Active
- 2011-05-30 EP EP11789758.7A patent/EP2578893B1/en active Active
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JPS445475Y1 (ja) * | 1964-09-01 | 1969-02-27 | ||
JPH08232952A (ja) | 1995-03-01 | 1996-09-10 | Purutonchien Kk | ローラー型直線案内装置 |
JPH1137154A (ja) | 1997-07-24 | 1999-02-09 | Oki Electric Ind Co Ltd | 直線ガイド機構 |
JP2002089577A (ja) * | 2000-09-19 | 2002-03-27 | Nsk Ltd | 軸受装置 |
JP2006322579A (ja) * | 2005-05-20 | 2006-11-30 | Jtekt Corp | 転がり軸受 |
JP2007331457A (ja) * | 2006-06-13 | 2007-12-27 | Ntn Corp | 車輪用軸受装置 |
JP2010126012A (ja) | 2008-11-28 | 2010-06-10 | Hitachi Automotive Systems Ltd | 車両制御用マルチコアシステムまたは内燃機関の制御装置 |
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See also references of EP2578893A4 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2011152355A1 (ja) | 2013-08-01 |
US20120328223A1 (en) | 2012-12-27 |
CN102369365A (zh) | 2012-03-07 |
EP2578893B1 (en) | 2018-08-15 |
CN102369365B (zh) | 2016-01-20 |
CN102562798A (zh) | 2012-07-11 |
EP2578893A1 (en) | 2013-04-10 |
JP5747914B2 (ja) | 2015-07-15 |
CN102562798B (zh) | 2016-08-03 |
EP2578893A4 (en) | 2014-02-12 |
US8827560B2 (en) | 2014-09-09 |
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