WO2012008323A1 - ボール型等速ジョイント - Google Patents
ボール型等速ジョイント Download PDFInfo
- Publication number
- WO2012008323A1 WO2012008323A1 PCT/JP2011/065263 JP2011065263W WO2012008323A1 WO 2012008323 A1 WO2012008323 A1 WO 2012008323A1 JP 2011065263 W JP2011065263 W JP 2011065263W WO 2012008323 A1 WO2012008323 A1 WO 2012008323A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- ball
- inner ring
- cage
- outer ring
- contact
- 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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/2237—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22309—Details of grooves
Definitions
- the present invention relates to a ball type constant velocity joint that transmits a driving force to a steering wheel of an automobile and whose joint operating angle changes according to the steering angle of the steering wheel, that is, a ball type used for a front drive shaft of an automobile. It relates to constant velocity joints.
- JP-A-11-325094 discloses such a ball type constant velocity joint.
- the ball type constant velocity joint can allow the ball to move in the radial direction in the cage, and provide a protrusion on each window portion of the cage for the purpose of reducing the radial thickness of the cage. I have to.
- the radial contact range of the ball in the cage is increased. Therefore, in the ball type constant velocity joint, the radial thickness of the cage is formed so as to coincide with the radial contact range of the ball in the cage.
- the cage has a shape in which the annular portions on both sides in the axial direction of the cage are connected by a plurality of column portions.
- the vicinity of the pillar portion of the cage may be a portion having the lowest strength and rigidity in the ball type constant velocity joint. In such a case, the life of the ball-type constant velocity joint is improved by increasing the strength and rigidity of the cage.
- This invention is made in view of such a situation, and it aims at providing the ball type constant velocity joint which can improve the lifetime of a ball type constant velocity joint by raising the intensity
- An outer ring having a plurality of outer ring ball grooves formed on an inner peripheral surface thereof, and an inner ring having a plurality of inner ring ball grooves formed on an outer peripheral surface thereof.
- a plurality of balls that roll on the outer ring ball groove and the inner ring ball groove and transmit torque between the outer ring and the inner ring, are formed in an annular shape, and are arranged between the outer ring and the inner ring, and in the circumferential direction.
- a cage formed with a plurality of window portions for accommodating the balls respectively, and the radial thickness of the cage is such that the ball in the window portion of the cage is at a maximum joint operating angle. Radial contact It is set to be greater than the circumference.
- the radial thickness of the cage is made larger than the radial contact range of the ball in the window portion of the cage.
- the strength and rigidity of the cage can be increased, and the life of the ball type constant velocity joint can be improved.
- the contact angle between the outer ring and the inner ring and the ball is reduced, or the outer ring, the inner ring and the ball are It is necessary to reduce the major axis of the contact ellipse. Then, in any case, the surface pressure in the inner ring ball groove and the outer ring ball groove increases.
- the window portion of the cage has a radially outward direction and a radial direction of the cage with respect to the radial contact range of the ball in the window portion. It is good to set so that the non-contact area
- the radial thickness of the cage can be reliably increased while the contact ellipse in the inner ring ball groove and the outer ring ball groove is not chipped at all, or even if it is chipped, the chip is only slightly chipped. . Therefore, the strength and rigidity of the cage can be reliably increased, and the life of the ball type constant velocity joint can be improved.
- FIG. 1 is an axial cross-sectional view of the constant velocity joint 10 according to the present embodiment in a state where a predetermined joint operating angle ⁇ is taken.
- the opening side of the outer ring 20 means the left side of FIG. 1
- the back side of the outer ring 20 means the right side of FIG.
- the constant velocity joint 10 of the present embodiment transmits a driving force to a steering wheel of an automobile and, at the same time, a ball type constant velocity joint whose joint operating angle ⁇ changes according to the steering angle of the steering wheel.
- This is a ball-type constant velocity joint applied to the front drive shaft of an automobile.
- the constant velocity joint 10 will be described by taking a joint center fixed ball type constant velocity joint (also referred to as “Zepper type constant velocity joint”) as an example.
- UF undercut free type
- BF Barfield type
- BF Barfield type
- the constant velocity joint 10 includes an outer ring 20 having a plurality of outer ring ball grooves 23, an inner ring 30 having a plurality of inner ring ball grooves 32, a plurality of balls 40, a cage 50, and a shaft 60. ing.
- an outer ring 20 having a plurality of outer ring ball grooves 23
- an inner ring 30 having a plurality of inner ring ball grooves 32
- a plurality of balls 40 a cage 50
- a shaft 60 a shaft 60.
- the outer ring 20 is formed in a cup shape (bottomed tubular shape) having an opening on the left side of FIG. 1 (corresponding to “one side in the axial direction” of the present invention).
- a connecting shaft 21 is integrally formed on the outer side (right side in FIG. 1) of the cup of the outer ring 20 so as to extend in the direction of the outer ring axis.
- the connecting shaft 21 is connected to another power transmission shaft.
- the inner peripheral surface of the outer ring 20 is formed in a concave spherical shape.
- the concave spherical inner peripheral surface 22 of the outer ring 20 is formed by a part of a spherical surface having an intersection O between the outer ring axis L1 and the inner ring axis L2 as a center of curvature, and is cut in the outer ring axis direction. When viewed in cross section, it is formed in a concave arc shape.
- outer ring ball grooves 23 having a concave arc-shaped cross section in the outer ring axis orthogonal direction are formed on the inner peripheral surface of the outer ring 20 so as to extend substantially in the outer ring axis direction.
- These outer ring ball grooves 23 (six in this embodiment) are formed at equal intervals in the circumferential direction (60-degree intervals in this embodiment) when viewed in a cross section cut in the radial direction.
- the outer ring axial direction means a direction passing through the central axis of the outer ring 20, that is, a rotation axis direction of the outer ring 20.
- the inner ring 30 is formed in an annular shape and is arranged inside the outer ring 20.
- the outer peripheral surface 31 of the inner ring 30 is formed in a convex spherical shape.
- the convex spherical outer peripheral surface 31 of the inner ring 30 is formed by a part of a spherical surface drawn with the intersection O between the outer ring axis L1 and the inner ring axis L2 as the center of curvature, and is a cross section cut in the direction of the inner ring axis. Is formed in a convex arc shape.
- a plurality of inner ring ball grooves 32 having a substantially arc-shaped cross section in the direction orthogonal to the inner ring axis are formed on the outer peripheral surface of the inner ring 30 so as to extend in the direction of the inner ring axis.
- the plurality of (six in this embodiment) inner ring ball grooves 32 are equally spaced in the circumferential direction (60 degrees in the present embodiment) and viewed from the outer ring 20 when viewed in a cross section cut in the radial direction.
- the same number of outer ring ball grooves 23 are formed. That is, each inner ring ball groove 32 is positioned so as to face each outer ring ball groove 23 of the outer ring 20.
- An inner spline 35 extending in the inner ring axial direction is formed on the inner circumferential surface of the inner ring 30.
- the internal spline 35 is fitted (engaged) with the external spline of the shaft 60.
- the inner ring axial direction means a direction passing through the central axis of the inner ring 30, that is, a rotation axis direction of the inner ring 30.
- the plurality of balls 40 are disposed so as to be sandwiched between the outer ring ball groove 23 of the outer ring 20 and the inner ring ball groove 32 of the inner ring 30 facing the outer ring ball groove 23, respectively.
- Each ball 40 is rotatable with respect to each outer ring ball groove 23 and each inner ring ball groove 32 and is engaged in a circumferential direction (around the outer ring axis or around the inner ring axis). Therefore, the ball 40 transmits torque between the outer ring 20 and the inner ring 30.
- the cage 50 is formed in an annular shape.
- the outer peripheral surface 51 of the cage 50 is formed in a partial spherical shape substantially corresponding to the concave spherical inner peripheral surface 22 of the outer ring 20, that is, a convex spherical shape.
- the inner peripheral surface 52 of the cage 50 is formed in a partial spherical shape that substantially corresponds to the convex spherical outer peripheral surface 31 of the inner ring 30, that is, a concave spherical shape.
- the cage 50 is disposed between the concave spherical inner peripheral surface 22 of the outer ring 20 and the convex spherical outer peripheral surface 31 of the inner ring 30.
- the cage 50 includes a plurality of window portions 53 that are substantially rectangular through holes arranged at equal intervals in the circumferential direction (the circumferential direction of the cage axis).
- the number of window portions 53 of the cage 50 is the same as the number of balls 40.
- One ball 40 is accommodated in each window 53.
- the outer ring ball groove 23 has a cross section in a direction orthogonal to the outer ring axis, which is formed in a so-called gothic arc shape in which two concave arcs having different centers are connected.
- the inner ring ball groove 32 has a so-called gothic arc shape in which the cross section of the inner ring ball groove 32 in the direction orthogonal to the inner ring axis is formed by connecting two concave arcs having different centers.
- the radius of curvature of the concave arc of the inner ring ball groove 32 in this embodiment is R1. Therefore, in the state where the joint operating angle ⁇ is taken, during torque transmission, as shown in FIG. 2, the outer ring ball groove 23 and the ball 40 are in contact with each other in an elliptical range centering on the outer ring contact point Po1, and the inner ring ball groove 32 and the ball 40 are in contact with each other in an elliptical range centered on the inner ring contact point Pi1.
- the contact ellipse Ei1 at the inner ring contact point Pi1 has a size as shown in FIG.
- the size of the contact ellipse Ei1 differs according to the radius of curvature R1 of the concave arc shape of the inner ring ball groove 32. That is, the larger the concave arc-shaped radius of curvature R1 of the inner ring ball groove 32, the smaller the major and minor diameters of the contact ellipse Ei1 between the ball 40 and the inner ring ball groove 32. Conversely, the smaller the concave arc-shaped radius of curvature R1 of the inner ring ball groove 32 is, the longer diameter (long axis length) and the shorter diameter (short axis length) of the contact ellipse Ei1 between the ball 40 and the inner ring ball groove 32 are. Becomes larger.
- the contact angle in this embodiment is ⁇ 1.
- the contact angle ⁇ 1 is a method at the radial line La of the inner ring 30 passing through the center Oa of the ball 40 and the inner ring contact point Pi1 that is the center of the contact ellipse Ei1 between the inner ring ball groove 32 and the ball 40.
- the size of the contact ellipse Ei1 varies depending on the contact angle ⁇ 1. That is, the longer the contact angle ⁇ 1, the smaller the major axis and the minor axis of the contact ellipse Ei1 between the ball 40 and the inner ring ball groove 32.
- the contact angle ⁇ 1 is smaller, the major axis and minor axis of the contact ellipse Ei1 between the ball 40 and the inner ring ball groove 32 become larger.
- the ball 40 rolls in the outer ring ball groove 23 and the inner ring ball groove 32 with the joint operating angle ⁇ , the ball 40 is located on the opening side of the outer ring 20 in the window 53 of the cage 50. Touch the surface. This is because a force for pushing the ball 40 toward the opening side of the outer ring 20 is generated by the wedge effect of the outer ring ball groove 23 and the inner ring ball groove 32. And the position where the ball
- the contact position of the ball 40 in the window 53 is the radially outward position in the “8” shape.
- the contact position of the ball 40 in the window 53 is the radially inner position in the “8” shape.
- the radial contact range of the cage 50 in the “8” -shaped contact locus G is W1.
- the radial thickness of the cage 50 is T1. That is, the radial thickness T1 of the cage 50 is set to be larger than the radial contact range W1 of the ball 40 in the window portion 53. More specifically, the window 53 of the cage 50 has a radial outer direction and radial direction of the cage 50 with respect to the radial contact range W1 of the ball 40 in the window 53 when the joint operating angle ⁇ is maximum. A non-contact area of the ball 40 is set inward.
- a comparative example As a comparative example, the one shown in FIG. 4 is used.
- the outer ring ball groove 223, the inner ring ball groove 232, and the retainer 250 in the comparative example are different from the outer ring ball groove 23, the inner ring ball groove 32, and the retainer 50 in the present embodiment in the following points.
- the radial contact range W3 of the ball 40 in the window 253 of the cage 250 and the radial thickness T3 of the cage 250 are the same.
- the radial contact range W3 in the comparative example is the same as the radial contact range W1 in the present embodiment.
- the radial thickness T3 of the cage 250 in the comparative example is smaller than the radial thickness T1 of the cage 50 in the present embodiment.
- the contact angle ⁇ 3 in the comparative example is the same as the contact angle ⁇ 1 in the present embodiment.
- the radius of curvature of the concave arc of the inner ring ball groove 232 in the comparative example is R3, which is smaller than the radius of curvature R1 in the present embodiment. Therefore, the major axis and minor axis of the contact ellipse Ei3 in the comparative example are larger than the major axis and minor axis of the contact ellipse Ei1 in the present embodiment.
- the present embodiment shown in FIG. 2 and the comparative example shown in FIG. 4 are compared and considered.
- the chipping of the contact ellipses Ei1 and Ei3 causes a decrease in life due to stress concentration. For this reason, it is required that the contact ellipses Ei1 and Ei3 are absent at all, or if they are present, they are only slightly present. That is, the difference between the long diameter of the contact ellipse Ei1 and the length from the inner ring contact point Pi1 which is the center of the contact ellipse Ei1 to the shoulder (opening edge) of the inner ring ball groove 32 is the long diameter of the contact ellipse Ei3 and the contact ellipse Ei3.
- the difference from the center inner ring contact point Pi1 to the length of the inner ring ball groove 232 from the shoulder is set to the same extent.
- the radial contact ranges W1 and W3 are the same, but the radial thickness T1 of the cage 50 in this embodiment is different from the radial thickness T3 of the cage 250 in the comparative example. Furthermore, the contact angles ⁇ 1 and ⁇ 3 are the same. In this case, in order to make the chip in the contact ellipse Ei1 in this embodiment the same as the chip in the contact ellipse Ei3 in the comparative example, the major axis of the contact ellipse Ei1 in the present embodiment is larger than the major axis of the contact ellipse Ei3 in the comparative example. Need to be smaller.
- the concave arc-shaped curvature radius R1 of the inner ring ball groove 32 in the present embodiment is set larger than the concave arc-shaped curvature radius R3 of the inner ring ball groove 232 in the comparative example.
- the major axis and minor axis of contact ellipse Ei1 in this embodiment can be made smaller than the major axis and minor axis of contact ellipse Ei3 in a comparative example.
- the radial thickness T1 of the cage 50 can be made larger than the radial thickness T3 of the cage 250 in the comparative example.
- the life of the cage 50 can be improved as a result. Since the life of the cage 50 is the shortest among the components of the constant velocity joint 10, the life of the constant velocity joint 10 can be improved as a result by improving the life of the cage 50.
- the major axis and minor axis of the contact ellipse Ei1 in the present embodiment are made smaller than the major axis and minor axis of the contact ellipse Ei3 in the comparative example.
- the surface pressure (pressure) received by the inner ring ball groove 32 from the ball 40 in the present embodiment is higher than the surface pressure received by the inner ring ball groove 232 from the ball 40 in the comparative example.
- it can be achieved by using a grease corresponding to high surface pressure, making the inner ring ball groove 32 harder by improving quenching, improving the material used for the inner ring 30, or the like.
- the cage 150 in the second embodiment has the same configuration as the cage 50 of the first embodiment.
- the radial thickness T2 of the cage 150 in the second embodiment is the same as the radial thickness T1 of the cage 50 in the first embodiment, and the radial contact range W2 of the ball 40 in the window 153 of the cage 150 is This is the same as the radial contact range W1 in the first embodiment. That is, the radial thickness T2 in the second embodiment is set to be larger than the radial contact range W2.
- the contact angle ⁇ 2 in the second embodiment is set smaller than the contact angle ⁇ 1 in the first embodiment. That is, the inner ring contact point Pi2 that is the center of the contact ellipse Ei2 in the second embodiment is the groove bottom of the inner ring ball groove 132 from the inner ring contact point Pi1 that is the center of the contact ellipse Ei1 and Ei3 in the first embodiment and the comparative example. It is located on the side (lower side in FIG. 3). Further, the radius of curvature of the concave arc shape of the inner ring ball groove 132 in the second embodiment is R2, which is the same as the curvature radius R3 in the comparative example, and is smaller than the curvature radius R1 in the first embodiment. Therefore, the major axis and minor axis of the contact ellipse Ei2 in the second embodiment are the same as the major axis and minor axis of the contact ellipse Ei3 in the comparative example.
- the second embodiment shown in FIG. 3 and the comparative example shown in FIG. 4 will be compared and considered.
- the chipping of the contact ellipses Ei2 and Ei3 causes a decrease in life due to stress concentration. Therefore, it is required that the lack of contact ellipses Ei2 and Ei3 is not present at all, or is small even if present. That is, the difference between the long diameter of the contact ellipse Ei2 and the length from the inner ring contact point Pi2 which is the center of the contact ellipse Ei2 to the shoulder (opening edge) of the inner ring ball groove 132 is the long diameter of the contact ellipse Ei3 and the contact ellipse Ei3.
- the difference from the center inner ring contact point Pi1 to the length of the inner ring ball groove 232 from the shoulder is set to the same level.
- the radial contact ranges W2 and W3 are the same, but the radial thickness T2 of the cage 150 in the second embodiment is different from the radial thickness T3 of the cage 250 in the comparative example. Furthermore, the concave arc-shaped curvature radius R2 of the inner ring ball groove 232 in the second embodiment is the same as the concave arc-shaped curvature radius R3 of the inner ring ball groove 232 in the comparative example.
- the inner ring contact point Pi2 that is the center of the contact ellipse Ei2 in the second embodiment is It is necessary to set the inner ring ball groove 232 on the groove bottom side with respect to the inner ring contact point Pi1 which is the center of the contact ellipse Ei3 in the comparative example.
- the concave arc-shaped contact angle ⁇ 2 of the inner ring ball groove 132 in the second embodiment is set smaller than the concave arc-shaped contact angle ⁇ 3 of the inner ring ball groove 232 in the comparative example. Accordingly, the inner ring contact point Pi2 that is the center of the contact ellipse Ei2 in the second embodiment needs to be set on the groove bottom side of the inner ring ball groove 132 with respect to the inner ring contact point Pi1 that is the center of the contact ellipse Ei3 in the comparative example. There is.
- the radial thickness T2 of the cage 150 can be made larger than the radial thickness T3 of the cage 250 in the comparative example.
- the life of the cage 150 can be improved as a result. Since the life of the cage 150 is the shortest among the components of the constant velocity joint 10, the life of the constant velocity joint 10 can be improved as a result by improving the life of the cage 150.
- the contact angle ⁇ 2 in the second embodiment is made smaller than the contact angle ⁇ 3 in the comparative example.
- the surface pressure (pressure) that the inner ring ball groove 132 receives from the ball 40 in the second embodiment is higher than the surface pressure that the inner ring ball groove 232 receives from the ball 40 in the comparative example.
- it can be achieved by using a grease compatible with high surface pressure, making the inner ring ball groove 132 harder by improving the quenching, or improving the material used for the inner ring 30.
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- Engineering & Computer Science (AREA)
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- Power Steering Mechanism (AREA)
Abstract
Description
(ボール型等速ジョイントの全体構成)
本実施形態のボール型等速ジョイント10(以下、単に「等速ジョイント」と称す)の構成について、図1を参照して説明する。図1は、本実施形態に係る等速ジョイント10の所定角度のジョイント作動角θをとった状態の軸方向断面図である。なお、以下の説明において、外輪20の開口側とは、図1の左側を意味し、外輪20の奥側とは、図1の右側を意味する。
次に、外輪ボール溝23、内輪ボール溝32、保持器50の詳細形状について図2を参照して説明する。ここで、外輪ボール溝23の外輪軸直交方向断面は、中心の異なる二つの凹円弧状を接続した、いわゆるゴシックアーク形状に形成される。また、内輪ボール溝32の内輪軸直交方向断面は、図2に示すように、中心の異なる二つの凹円弧状を接続した、いわゆるゴシックアーク形状に形成される。本実施形態における内輪ボール溝32の凹円弧状の曲率半径はR1としている。従って、ジョイント作動角θをとった状態において、トルク伝達時には、図2に示すように、外輪ボール溝23とボール40とは外輪接触点Po1を中心とした楕円範囲にて接触し、内輪ボール溝32とボール40とは内輪接触点Pi1を中心とした楕円範囲にて接触する。この内輪接触点Pi1における接触楕円Ei1は、図2に示すような大きさとなる。
次に、第二実施形態における外輪ボール溝123、内輪ボール溝132、保持器150の詳細形状について図3を参照して説明する。なお、第二実施形態における外輪ボール溝123、内輪ボール溝132および保持器150は、以下に説明する点について、第一実施形態および比較例のものと相違する。
Claims (2)
- 自動車の舵取用車輪に駆動力を伝達すると共に、前記舵取用車輪の舵角に応じてジョイント作動角が変化するボール型等速ジョイントにおいて、
少なくとも軸方向一方に開口部を備える筒状に形成され、内周面に外輪ボール溝が複数形成された外輪と、
前記外輪の内側に配置され、外周面に内輪ボール溝が複数形成された内輪と、
それぞれの前記外輪ボール溝および前記内輪ボール溝を転動し、前記外輪と前記内輪との間でトルクを伝達する複数のボールと、
環状に形成され、前記外輪と前記内輪との間に配置され、周方向に前記ボールをそれぞれ収容する複数の窓部が形成された保持器と、
を備え、
前記保持器の径方向厚は、前記ジョイント作動角が最大の場合に前記保持器の前記窓部における前記ボールの径方向接触範囲より大きくなるように設定されているボール型等速ジョイント。 - 請求項1において、
前記保持器の前記窓部は、前記ジョイント作動角が最大の場合に、前記窓部における前記ボールの前記径方向接触範囲に対して前記保持器の径方向外方および径方向内方に、前記ボールの非接触領域を形成するように設定されているボール型等速ジョイント。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180034222XA CN102985713A (zh) | 2010-07-15 | 2011-07-04 | 等速球型接头 |
EP11806653.9A EP2594820A4 (en) | 2010-07-15 | 2011-07-04 | TRACKING BALL JOINT |
US13/704,062 US20130095932A1 (en) | 2010-07-15 | 2011-07-04 | Constant-velocity ball joint |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010-160739 | 2010-07-15 | ||
JP2010160739A JP2012021608A (ja) | 2010-07-15 | 2010-07-15 | ボール型等速ジョイント |
Publications (1)
Publication Number | Publication Date |
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WO2012008323A1 true WO2012008323A1 (ja) | 2012-01-19 |
Family
ID=45469326
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/065263 WO2012008323A1 (ja) | 2010-07-15 | 2011-07-04 | ボール型等速ジョイント |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130095932A1 (ja) |
EP (1) | EP2594820A4 (ja) |
JP (1) | JP2012021608A (ja) |
CN (1) | CN102985713A (ja) |
WO (1) | WO2012008323A1 (ja) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010011175A1 (de) * | 2009-03-13 | 2010-10-14 | GM Global Technology Operations, Inc., Detroit | Gleichlaufgelenk und Herstellverfahren |
US9926985B2 (en) * | 2013-08-09 | 2018-03-27 | Hyundai Wia Corporation | Sliding ball type constant velocity joint for vehicles |
KR101467913B1 (ko) * | 2013-09-11 | 2014-12-02 | 한국델파이주식회사 | 등속 유니버설 조인트 |
US11187273B2 (en) | 2016-04-22 | 2021-11-30 | Dana Automotive Systems Group, Llc | Propeller shaft assembly |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11325094A (ja) | 1998-03-18 | 1999-11-26 | Kenji Mimura | 等速自在継手及びそのケージ製造方法並びにそのケージ製造装置 |
JP2007024106A (ja) * | 2005-07-13 | 2007-02-01 | Ntn Corp | 固定型等速自在継手 |
JP2007032648A (ja) * | 2005-07-25 | 2007-02-08 | Ntn Corp | 高角固定式等速自在継手 |
JP2009036253A (ja) * | 2007-07-31 | 2009-02-19 | Ntn Corp | 固定式等速自在継手 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2837301C3 (de) * | 1978-08-26 | 1983-01-13 | Uni-Cardan Ag, 5200 Siegburg | Gleichlaufdrehgelenk |
DE4215218C2 (de) * | 1992-05-09 | 1994-06-16 | Gkn Automotive Ag | Kugelgleichlaufdrehgelenk mit geräuschmindernden Käfiganschlagsflächen |
US6120382A (en) * | 1995-12-26 | 2000-09-19 | Ntn Corporation | Constant velocity joint |
JP4076818B2 (ja) * | 2002-08-12 | 2008-04-16 | Ntn株式会社 | 等速自在継手 |
JP4223358B2 (ja) * | 2003-09-04 | 2009-02-12 | Ntn株式会社 | 固定式等速自在継手 |
JP2006266329A (ja) * | 2005-03-22 | 2006-10-05 | Ntn Corp | 固定型等速自在継手 |
JP4812376B2 (ja) * | 2005-09-09 | 2011-11-09 | Ntn株式会社 | 車輪用軸受装置の製造方法 |
-
2010
- 2010-07-15 JP JP2010160739A patent/JP2012021608A/ja active Pending
-
2011
- 2011-07-04 CN CN201180034222XA patent/CN102985713A/zh active Pending
- 2011-07-04 US US13/704,062 patent/US20130095932A1/en not_active Abandoned
- 2011-07-04 EP EP11806653.9A patent/EP2594820A4/en not_active Withdrawn
- 2011-07-04 WO PCT/JP2011/065263 patent/WO2012008323A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11325094A (ja) | 1998-03-18 | 1999-11-26 | Kenji Mimura | 等速自在継手及びそのケージ製造方法並びにそのケージ製造装置 |
JP2007024106A (ja) * | 2005-07-13 | 2007-02-01 | Ntn Corp | 固定型等速自在継手 |
JP2007032648A (ja) * | 2005-07-25 | 2007-02-08 | Ntn Corp | 高角固定式等速自在継手 |
JP2009036253A (ja) * | 2007-07-31 | 2009-02-19 | Ntn Corp | 固定式等速自在継手 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2594820A4 |
Also Published As
Publication number | Publication date |
---|---|
EP2594820A1 (en) | 2013-05-22 |
JP2012021608A (ja) | 2012-02-02 |
CN102985713A (zh) | 2013-03-20 |
EP2594820A4 (en) | 2014-06-18 |
US20130095932A1 (en) | 2013-04-18 |
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