CN1755154A - Constant speed universal coupling assembly - Google Patents

Constant speed universal coupling assembly Download PDF

Info

Publication number
CN1755154A
CN1755154A CN 200510078655 CN200510078655A CN1755154A CN 1755154 A CN1755154 A CN 1755154A CN 200510078655 CN200510078655 CN 200510078655 CN 200510078655 A CN200510078655 A CN 200510078655A CN 1755154 A CN1755154 A CN 1755154A
Authority
CN
China
Prior art keywords
coupling member
retainer
ball
inboard
torque transmitting
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.)
Pending
Application number
CN 200510078655
Other languages
Chinese (zh)
Inventor
曾根启助
穗积和彦
兼子佳久
杉山达朗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NTN Corp filed Critical NTN Corp
Publication of CN1755154A publication Critical patent/CN1755154A/en
Pending legal-status Critical Current

Links

Images

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
    • 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
    • F16D3/224—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 the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—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 the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • 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
    • F16D2003/22303—Details of ball cages
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/12—Mounting or assembling

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

The invention discloses a constant speed universal coupling joint, which is provided with 8 torque transmission balls (3). The ratio Gamma1 (which is equal to PCDBALL/DBALL) between the pitch diameter PCDBALL (PCDBALL is equal to 2*PCR) and the diameter DBALL of the torque transmission balls is set within the limit that Gamma1 is larger than or equal to 3.5 and is smaller than or equal to 5.0. The ratio Gamma2 (which is equal to DOUTER/PCDSERR) between the outer diameter DOUTER of a lateral coupling joint component 1 and the pitch diameter PCDSERR of the minute tooth (or spline) 2C of a medial coupling joint component 2 is set within the limit that the Gamma2 is larger than or equal to 2.5 and is smaller than 3.2.

Description

Constant speed universal coupling assembly
The application is that Chinese patent application 02101533.3 (is divided an application and submitted to day: on January 4th, 2002; Denomination of invention: dividing an application constant-speed universal joint).
Technical field
The present invention relates to a kind of constant speed universal coupling assembly, it has the constant-speed universal joint that 8 torque transmitting balls are arranged.
Background technique
Constant-speed universal joint is divided into fixed (ball fixed type) of only allowing 2 interaxis angles generation displacement and the sliding-type (plunging type) of allowing angle and axial displacement substantially.Compare with sliding-type, a feature of fixed type constant velocity universal shaft coupling is to have big operating angle.For example, the used constant-speed universal joint of truck drive shaft needs for example maximum functional angle more than 45 °, and big like this operating angle has only fixed just can obtain.On the other hand, compare with the sliding-type constant-speed universal joint, the internal structure of fixed type constant velocity universal shaft coupling is had to complicated a little.
Figure 23 A and Figure 23 B are typical ball cage (Star エ パ) the formula constant-speed universal joints as the fixed type constant velocity universal shaft coupling.This constant speed universal shaft coupling is by outside coupling member 11.Inboard 12,6 torque transmitting balls 13 of coupling member and retainer 14 constitute.This outside coupling member 11 forms 6 curvilinear guiding groove 11b vertically on the aperture surface 11a of spherical shape; This inboard coupling member 12 forms 6 curve-like guiding groove 12b vertically on the outer diametric plane 12a of spherical shape, and is formed for connecting serration (spline) 12c of axial region on aperture surface; These 6 torque transmitting balls 13 are configured in the guiding groove 11b of outside coupling member 11 and the guiding groove 12b of inboard coupling member 12 works in coordination with in the ball track that forms; This retainer 14 is used to keep torque transmitting ball 13.
The center B of the center A of guiding groove 11b of outside coupling member 11 and the guiding groove 12b of inboard coupling member 12 respectively with respect to the sphere centre of the sphere centre of aperture surface 11a and outer diametric plane 12a only in the axial direction in opposition side (the center A of guiding groove 11b is in the opening side of shaft coupling, and the center B of guiding groove 12b is at the private side of shaft coupling) the identical distance of setovering.Therefore, the collaborative ball track that forms of guiding groove 11b and corresponding guiding groove 12b becomes towards the shape of shaft coupling opening side flare up wedge-like.Sphere centre as the outer diametric plane 12a of the aperture surface 11a of the outside coupling member 11 of the guide surface of retainer 14 and inboard coupling member 12 all is in the shaft coupling median plane O that comprises torque transmitting ball 13 centers.
If 12 angular displacements that produce angle θ of outside coupling member 11 and inboard coupling member, no matter then be which operating angle θ, torque transmitting ball 13 by retainer 14 guiding maintains in 2 faces such as branch such as grade (θ/2) of angle θ all the time, therefore guarantees the constant speed of shaft coupling.
Summary of the invention
The objective of the invention is to, in a kind of like this constant-speed universal joint, this further miniaturization of constant speed universal shaft coupling, and can guarantee to be equal to or surpass relatively intensity, load capacity and the durability of product (constant-speed universal joints of 6 balls as shown in Figure 23).
In order to achieve the above object, the invention provides a kind of constant speed universal coupling assembly that is used for vehicle, the sliding-type constant-speed universal joint that its other end with fixed type constant velocity universal shaft coupling that the end with the shaft portion of vehicle links and one and described shaft portion links, wherein, described fixed type constant velocity universal shaft coupling comprises: outside coupling member, and it has eight the curve-like guiding grooves that extend vertically that form on the aperture surface of spherical shape; Inboard coupling member, it has eight the curve-like guiding grooves that extend vertically that form on the outer diametric plane of spherical shape; Eight ball tracks, it forms between the described guiding groove of the described guiding groove of described outside coupling member and corresponding with it described inboard coupling member, and all described ball tracks are opened into wedge-like towards an axial side; Eight torque transmitting balls are configured in respectively in the described ball track; One retainer, it has eight covers that hold described torque transmitting ball; Wherein, a described end of described shaft portion is taken turns and is linked with one by described fixed type constant velocity universal shaft coupling, and the other end of described shaft portion links with a differential mechanism by described sliding-type constant-speed universal joint.
Pitch diameter (the PCD of torque transmitting ball BALL) and diameter (D BALL) ratio γ 1(=PCD BALL/ D BALL) can be at 3.3≤γ 1In≤5.0 the scope.Here, the pitch diameter (PCD of torque transmitting ball BALL) { coupling member guiding groove center and the line segment length at torque transmitting ball center equal to be connected the line segment length at inboard coupling member guiding groove center and torque transmitting ball center outside being connected, and guarantee the constant speed of shaft coupling thus to equal to connect the line segment length at center with the center of torque transmitting ball of the center of outside coupling member guiding groove or inboard coupling member guiding groove.Claim later on this to be of a size of (PCR) } 2 times of (PCD BALL=2 * PCR).
Make 3.3≤γ 1≤ 5.0 reason is the load capacity of intensity, shaft coupling in order to ensure outside coupling member etc. and durability is equal to or surpass relatively product (constant-speed universal joints of 6 balls).That is, in constant-speed universal joint, in limited space range, be difficult to change significantly the pitch diameter (PCD of torque transmitting ball BALL).Therefore, γ 1Value mainly rely on the diameter (D of torque transmitting ball BALL).If γ 1＜3.3 (mainly is diameter D BALLBig occasion), then the wall thickness of other parts (outside coupling member, inboard coupling member) becomes too thin, has problem aspect intensity.On the contrary, if γ 1＞5.0 (mainly is diameter D BALLLittle occasion), then load capacity diminishes, and has problem aspect durability.In addition, the face of the contact segment of torque transmitting ball and guiding groove presses a liter (because diameter D BALLDiminish, then the cause that also diminishes of the contact ellipse of contact segment), have the problems such as groove shoulder edge partial crushing of guiding groove.
By setting 3.3≤γ 1≤ 5.0, can guarantee outside coupling member etc. intensity, shaft coupling load capacity and durability is equal to or surpass relatively product (constant-speed universal joints of 6 balls).This part thing has been done confirmation to a certain extent by test.
(table 1 shows the evaluation according to comparative test) as shown in table 1 is at γ 1=3.2 occasion, the intensity of coupling member, inboard coupling member and retainer outside can not fully guaranteeing, the result who obtains is bad.At γ 1=3.3,3.4 occasion, the result who aspect intensity, obtains becoming better and better.Particularly, at γ 1〉=3.5 occasion can fully be guaranteed outside coupling member, inboard coupling member and the intensity of retainer and the durability of shaft coupling, the result who obtains.Also have, at γ 1Though also do not test in＞3.9 the scope, can infer to obtain and above-mentioned same good result.But, work as γ 1＞5.0 o'clock, as mentioned above, because having problem aspect the intensity of durability and outside coupling member, inboard coupling member, so can be made as γ 1≤ 5.0.
As known from the above, can be with γ 1Be set in 3.3≤γ 1In≤5.0 the scope, better be set in 3.5≤γ 1In≤5.0 the scope.
In addition, on above formation base, also can be with the external diameter (D of outside coupling member OUTER) with the flute profile pitch diameter (PCD of inner coupling member SERR) ratio γ 2(=D OUTER/ PCD SERR) be located at 2.5≤γ 2In≤3.5 the scope.
Be set at 2.5≤γ 2≤ 3.5 the reasons are as follows.That is pitch diameter (the PCD of the flute profile of inboard coupling member, SERR) for the reason of strength relationship of the axle that matches, can not change significantly.Therefore, γ 2The external diameter (D of the main and outside coupling member of value OUTER) relevant.γ 2＜2.5 o'clock (mainly is outer diameter D OUTERLittle occasion), the wall thickness of each parts (outside coupling member, inboard coupling member etc.) became thin, occurred the possibility of problem aspect intensity.On the other hand, work as γ 2＞3.5 o'clock (mainly is outer diameter D OUTERBig occasion), the problem in the practicality may be produced from the size aspect, in addition, the purpose of compactness can not be reached.By setting 2.5≤γ 2≤ 3.5, the durability that can guarantee the intensity of outside coupling member etc. and shaft coupling is equal to or surpasses relatively product (constant-speed universal joints of 6 balls), and can satisfy the requirement in the practicality.Particularly, by setting 2.5≤γ 2＜3.2, with respect to the relatively product (constant-speed universal joint of 6 balls: general γ of same nominal form 2〉=3.2), has the advantage that can make the outside dimension compactness.
As known from the above, can be with γ 2Be set in 2.5≤γ 2In≤3.5 the scope, better be set in 2.5≤γ 2In＜3.2 the scope.
The guiding groove center and the guiding groove center of inboard coupling member that can be by making outside coupling member towards the ball track of axial side's flare up wedge-like obtain with respect to the distance (F) that the sphere centre of the outer diametric plane of the sphere centre of the aperture surface of outside coupling member and inboard coupling member only equates in the opposition side biasing vertically respectively.The ratio R of Offset (F) and above-mentioned (PCR) 1(=F/PCR) can be set in the scope of 0.069≤R1≤0.121.
Set the reasons are as follows of 0.069≤R1≤0.121.The occasion of considering at fixing PCR, generally speaking, when operating angle is arranged, because it is many more that the big more then ball of Offset (F) track load (being added in the load of the contact segment of guiding groove and torque transmitting ball) reduces, so, on ball track load this point, we can say that Offset (F) is greatly favourable.
Yet, when Offset (F) is excessive:
(i) in big operating angle zone, the ball track shoals, and causes the safe load moment of torsion to reduce;
(ii) since the torque transmitting ball in retainer cover to move radially quantitative change big, so, come off in order to prevent torque transmitting ball, need the wall thickness (radial dimension) of increase retainer.For this reason, the ball track shoals, and causes the safe load moment of torsion to reduce;
(iii) the circumferential mobile quantitative change owing to the torque transmitting ball in the retainer cover is big, so, in order to ensure the proper exercise of torque transmitting ball, need to increase the circumferential size of retainer cover.For this reason, the intermediate portion stenosis of retainer has problems aspect intensity.
On the other hand, when Offset (F) is too small,
(iv) when operating angle is arranged, the ball track load of the ball track load (P1) of load side and non-load side (P2: in 1 changes, on non-load side ball track, load generation work phase place) peak value increases (P1, P2 illustrate honeybee value in certain phase angle), causes durability decline;
(V) reduce at the maximum functional angle.
By above content as can be known, Offset is excessive or too small all bad, and it has an optimum range, can balanced above-mentioned (i) in this optimum range, (ii), problem (iii) and above-mentioned (iv), (problem v).But, owing to the optimum range of Offset (F) size along with shaft coupling changes, so be necessary evaluation under the relation of the base dimension of expression shaft coupling size.Utilization than R1 (=F/PCR) be exactly this reason.When R1＞0.121, above-mentioned (i), (ii), (iii) become problem, when R1＜0.069, above-mentioned (iv), (v) become problem.From guaranteeing the safe load moment of torsion, guarantee retainer intensity, guaranteeing the reduction of ball track load, the angle of guaranteeing durability and guaranteeing the maximum functional angle, 0.069≤R1≤0.121st, the optimum range of Offset (F).Here, frequently the general value (being generally 0.14) of the R1 of product (constant-speed universal joints of 6 balls) is much smaller for the CLV ceiling limit value of above-mentioned R1 (0.121).Because R1 is little,, more can considers to improve the safe load moment of torsion, guarantee retainer intensity so the present invention's product are compared with product relatively.R1 can be set in the above-mentioned scope, be because the present invention's product have 8 torque transmitting balls, product more favourable (being confirmed by theory analysis) frequently aspect ball track load, the temperature rising is compared be reduced (by experimental verification, with reference to Figure 11, Figure 12) with product relatively.In product (constant-speed universal joints of 6 balls) relatively, as R1 being set in the above-mentioned scope, then can cause ball rail load excessive, durability reduces.
On above formation base, also can be further with the sphere centre of the sphere centre of the outer diametric plane of retainer and aperture surface with respect to the shaft coupling median plane that comprises the torque transmitting ball center only vertically in the identical distance (f) of opposition side biasing.In this occasion, can with the ratio R2 of Offset (f) and PCR (=f/PCr) be set in the scope of 0＜R2≤0.052.
R2 is set in interior the reasons are as follows of scope of 0＜R2≤0.052.Generally speaking, by Offset (f) is set, its advantage is, can increase the area of the aperture surface of retainer, reduced by heating and can improve durability.In addition, the wall thickness of the entrance part of the retainer that inboard coupling member packs into is increased, can improve intensity.
Yet, when Offset (f) is excessive:
(i) because the circumferential mobile quantitative change of the torque transmitting ball in the retainer cover is big, so, in order to ensure the proper exercise of torque transmitting ball, need to increase the circumferential size of retainer cover, for this reason, the intermediate portion stenosis of retainer, existing problems aspect intensity;
Wall thickness with the part entrance part opposition side (ii) retainer reduces, intensity aspect existing problems.
From the above, Offset (f) is excessive bad, and it has an optimum range, can be in addition balanced to meaning that Offset (f) is set and above-mentioned (i), (ii) problem at this optimum range.But, owing to the optimum range of Offset (f) size along with shaft coupling changes, so be necessary fastening evaluation with the pass of the base dimension of expression shaft coupling size.Employing than R2 (=f/PCR) be exactly this reason.When R1＞0.052, above-mentioned (i), (ii) become problem.From guaranteeing retainer intensity, guaranteeing the angle of durability, 0＜R2≤0.052nd, the optimum range of Offset (f).
Description of drawings
Figure 1A is the longitudinal sectional view of the present invention the 1st embodiment's constant-speed universal joint, and Figure 1B is its transverse sectional view.
Fig. 2 A is the front view of outer shroud, and Fig. 2 B is the local longitudinal sectional view of outer shroud, and Fig. 2 C is the local amplification front elevation of guiding groove, and Fig. 2 D is the longitudinal sectional view of amplification of the end of outer shroud.
Fig. 3 A is the front view of interior ring, and Fig. 3 B is the longitudinal sectional view of interior ring.
Fig. 4 A is the drawing in side sectional elevation of retainer, and Fig. 4 B is the sectional arrangement drawing of retainer.
Fig. 5 is for being assembled into interior ring the state of retainer.
Fig. 6 A, 6B are for being assembled into interior ring the state of retainer.
Fig. 7 A is the longitudinal sectional view that other form of retainer is shown, and Fig. 7 B is for being assembled into interior ring the state in this retainer.
Fig. 8 A, Fig. 8 B are the state in the cover that ball is assembled into retainer.
Fig. 9 A, Fig. 9 B are the figure that is positioned at the motion of the ball that overlaps when operating angle is shown for α.Fig. 9 is corresponding to the formation that is not provided with biasing on retainer, and Fig. 9 B is corresponding to the formation that is provided with biasing on retainer.
Figure 10 is that transverse sectional view is amplified in the cover part on every side that retainer is shown.
Figure 11 A, Figure 11 B, Figure 11 C are the figure that the relation of rotating speed and temperature rising value is shown.
Figure 12 is for illustrating the time dependent figure of temperature rising value.
Figure 13 is the figure that the relation of operating angle and loss of machine of torque rate is shown.
Figure 14 is the figure of relation of the abrasion degree of depth that the cover portion of working time and retainer is shown.
Figure 15 A is the longitudinal sectional view that the present invention the 2nd embodiment's constant-speed universal joint is shown, and Figure 15 B is its transverse sectional view.
Figure 16 illustrates the figure that interior ring is assembled into the state of retainer.
Figure 17 A, Figure 17 B illustrate the figure that interior ring is assembled into the state of retainer.
Figure 18 A is the longitudinal sectional view that another form of retainer is shown, and Figure 18 B is the figure that the state in this retainer that interior ring is assembled into is shown.
Figure 19 A, Figure 19 B are that transverse sectional view is amplified in the cover part on every side that retainer is shown.
Figure 20 A is the longitudinal sectional view of the present invention the 3rd embodiment's constant-speed universal joint, and Figure 20 B is its transverse sectional view.
Figure 21 is the figure that an example (transmission shaft) of automobile power transfer unit is shown.
Figure 22 is the figure of position relation change of sphere centre (sphere centre of the aperture surface of retainer) of outer diametric plane of sphere centre (sphere centre of the outer diametric plane of retainer), inboard shaft coupling of aperture surface of guiding groove center, the outside coupling member of the guiding groove center that the outside coupling member in the fixed type constant velocity universal shaft coupling is shown, inboard coupling member.
Figure 23 A is the longitudinal sectional view that an example of the fixed type constant velocity universal shaft coupling with 6 torque transmitting balls is shown, and Figure 23 B is its transverse sectional view.
Embodiment
Embodiments of the invention are described below with reference to the accompanying drawings.
Shown in Figure 1A and Figure 1B, this embodiment's constant-speed universal joint is made of outside coupling member 1,2,8 torque transmitting balls 3 of inboard coupling member and retainer 4.This outside coupling member 1 forms 8 curvilinear guiding groove 1b vertically on spherical shape aperture surface 1a; This inboard coupling member 2 forms 8 curvilinear guiding groove 2b vertically on the diametric plane 2a outside spherical shape, and be formed for connecting serration (or spline) 2c of axial region 5 on aperture surface; These 8 torque transmitting balls 3 are placed in by in the collaborative ball track that forms of the guiding groove 2b of the guiding groove 1b of outside coupling member 1 and inboard coupling member 2; This retainer 4 is used to keep torque transmitting ball 3.
In this embodiment, the center O 2 of the center O 1 of guiding groove 1b of outside coupling member 1 and the guiding groove 2b of inboard coupling member 2 respectively with respect to the sphere centre of the sphere centre of aperture surface 1a and outer diametric plane 2a only vertically in opposition side (center O 1 is in the opening side of shaft coupling, and center O 2 is in the private side of shaft coupling) the identical distance (F) of setovering.Therefore, the collaborative ball track that forms of guiding groove 1b and corresponding with it guiding groove 2b forms the shape towards shaft coupling opening side flare up wedge-like.
The sphere centre of the outer diametric plane 4a of retainer 4 and as the sphere centre of the aperture surface 1a of the outside coupling member 1 of the guide surface of the outer diametric plane 4a of retainer 4 all in the shaft coupling median plane O that comprises torque transmitting ball 3 center O 3.In addition, the sphere centre of the aperture surface 4b of retainer 4 and as the sphere centre of the outer diametric plane 2a of the inboard coupling member 2 of the guide surface of the aperture surface 4b of retainer 4 all in shaft coupling median plane O.Therefore, under this formation, the above-mentioned Offset (F) of outside coupling member 1 is the center O 1 of guiding groove 1b and the axial distance between the shaft coupling median plane O, the above-mentioned Offset (F) of inboard coupling member 2 is the center O 2 of guiding groove 2b and the axial distance between the shaft coupling median plane O, and both equate.The center O 1 of the guiding groove 1b of outside coupling member 1 is positioned at respect to shaft coupling median plane O vertically in the position of opposition side (center O 1 of guiding groove 1b is positioned at the opening side of shaft coupling, and the center O 2 of guiding groove 2b is positioned at the private side of shaft coupling) equidistant (F) biasing with the center O 2 of the guiding groove 2b of inboard coupling member 2.Connecting the line segment length of center O 1 and the center O 3 of torque transmitting ball 3 of guiding groove 1b of outside coupling member 1 and the line segment length of center O 2 and the center O 3 of torque transmitting ball 3 that is connected the guiding groove 2b of inboard coupling member 2 all is PCR respectively, and both are equal.
When outside coupling member 1 produced the angular displacement of angle θ with inboard coupling member 2, no matter be what kind of operating angle θ, the torque transmitting ball 3 that is led by retainer 4 maintained in 2 faces such as branch such as grade (θ/2) of angle θ all the time, guarantees the constant speed of shaft coupling.
In this embodiment, except above-mentioned formation, also the key dimension with shaft coupling is set at following numerical value.As preceding as state,
1. from the intensity of guaranteeing outside coupling member etc., guarantee load capacity, guarantee the angle of durability, wish pitch diameter PCD with torque transmitting ball 3 BALL(PCD BALL=2 * PCR) with diameter D BALLRatio γ 1(=PCD BALL/ D BALL) be located at 3.3≤γ 1In≤5.0 the scope, and better be set in 3.5≤γ 1≤ 5.0 (or 3.5＜γ 1≤ 5.0) in the scope, in the present embodiment, be set at γ 1=3.83.In addition, 2. with the outer diameter D of outside coupling member 1 OUTERPitch diameter PCD with serration (or spline) 2C of inboard coupling member 2 SERRRatio γ 2(=D OUTER/ PCD SERR) be located at 2.5≤γ 2In≤3.5 the scope, for example be located at 2.5≤γ 2In＜3.2 the scope.Above-mentioned formation 1. also can adopt separately.
About above-mentioned 1., 2. formation, compare with the relatively product (constant-speed universal joints of 6 balls as shown in Figure 23) of identical nominal form, as shown in table 2.
The number of the torque transmitting ball 3 of this embodiment's constant-speed universal joint is 8, compare with product (constant-speed universal joints of 6 balls) relatively, the load proportion shared owing to each torque transmitting ball in the shaft coupling full load capacity is few, so, with respect to the relatively product (constant-speed universal joints of 6 balls) of identical nominal form, can reduce the diameter D of torque transmitting ball 3 BALL, and can guarantee the wall thickness of outside coupling member and the wall thickness of inboard coupling member 2 with the degree that relatively product (constant-speed universal joints of 6 balls) are identical.
In addition, the relatively product (constant-speed universal joints of 6 balls) with respect to identical nominal form can reduce and compare γ 2(=D OUTER/ PCD SERR) (2.5≤γ 2＜3.2), one side is guaranteed to be equal to or is surpassed relatively intensity, load capacity and the durability of product (constant-speed universal joints of 6 balls), further makes its miniaturization on the one hand.
The Offset of guiding groove 1b, 2b (F) can be set at following numerical value.As previously mentioned,
3. from guaranteeing the safe load moment of torsion, guarantee retainer intensity, reduce ball track load, guarantee durability, guaranteeing the angle at maximum functional angle, wish by the Offset (F) of setting guiding groove 1b, 2b make than R1 (=F/PCR) in the scope of 0.069≤R1≤0.121, in the present embodiment, be set at R1=0.104 (or 0.1038).Relatively the R1 of product (constant-speed universal joints of 6 balls) is generally 0.14, and frequently product are much smaller for the R1 of present embodiment.
Fig. 2 A-Fig. 2 D illustrates outside coupling member 1.In the opening side field of the aperture surface 1a of outside coupling member 1, be provided with and be used for pack into the cylindric notch portion 1a1 of aperture surface 1a of retainer 4.When retainer 4 is installed, shown in Fig. 2 A, under the orthogonal state of axis, with the cover 4C of retainer 4 (with pack into assembly behind the aperture surface 4b of retainer 4 of inboard coupling member 2) the cylindric notch 1a1 that packs into.Under this state, 4 insertions sphere centre of diametric plane 4a outside it is consistent with the sphere centre of the aperture surface 1a of outside coupling member 1 with keeping.From this state, retainer 4 is rotated 90 degree, make the axis of retainer 4 consistent with the axis of outside coupling member 1.Like this, retainer 4 (and inboard coupling member 2) is encased on the aperture surface 1a of outside coupling member 1 fully.
In addition, as Fig. 2 C, Fig. 2 D illustrate enlargedly, be provided with chamfering 1b1 in the opening side zone of the guiding groove 1b of outside coupling member 1.Chamfering 1b1 has prevent the effect (open end at outside coupling member 1 does not quench) of softening when heat treatment guiding groove 1b (the regional W among Fig. 2 D is heat-treated), also can be used as the targeting part when packing into torque transmitting ball 3 among the cover 4c of retainer 4.
Fig. 3 A, Fig. 3 B illustrate inboard coupling member 2.The diameter of the outer diametric plane 2a of inboard coupling member 2 is A, and largest interval in the longitudinal cross-section parallel with the planar S of the bottom land that comprises 180 degree 2 guiding groove 2b in opposite directions, between outer diametric plane 2a is C.
Fig. 4 A and Fig. 4 B illustrate retainer 4.In retainer 4, be provided with on circumference, be spacedly distributed, be used to accommodate 8 windows cover 4C that keep 8 torque transmitting balls 3.In 8 cover 4C, 4 is the big long cover 4C1 of circumferential lengths, and remaining 4 is the little short cover 4C2 of circumferential lengths, long cover 4C1 and short cover 4C arranged alternate.Under this formation, mutual 90 degree that are spaced apart of 4 short cover 4C2.In addition, also can make 6 among 8 cover 4C to be long cover 4C1, remaining 2 are short cover 4C2.In this occasion, 2 short 180 degree that are spaced apart that overlap between the 4C2.The circumferential lengths of short cover 4C2 is set to such degree, promptly this constant speed universal shaft coupling is got maximum angle (with the maximum functional angle that can get on the shaft coupling function is that " maximum functional angle " is benchmark, perhaps with in the scope at this " maximum functional angle ", the maximum functional angle that can get on using is benchmark) during transmitting torque, torque transmitting ball 3 does not interfere with the circumferential wall of short cover 4C2.In addition, the circumferential lengths of long cover 4C1 is set to such degree, promptly, make the outside coupling member 1 and inboard coupling member 2 relative tilts, from the opening portion of outside joint member 1 with 1 short cover 4C2 facing to outside when packing torque transmitting ball 3 into, the circumferential wall that does not make the torque transmitting ball 3 of packing into earlier interfere long cover 4C1.In addition, pack into the setting of diameter (B) of entrance part 4d of retainer 4 wherein of inboard coupling member 2 will make external diameter (A) and largest interval (C) with respect to the inboard coupling member 2 shown in Fig. 3 A, has the relation of C≤B＜A.Step 4e is made in the inboard of entrance part 4d (boundary part of aperture surface 4b and entrance part 4d).But, also can make the shape that does not have step 4e.
The diameter (B) of entrance part 4d is set at the relation of C≤B＜A, is durability and the intensity in order to ensure retainer 4, and has further considered the installation when packing inboard coupling member 2 the aperture surface 4b of retainer 4 into.As shown in Figure 5, when inboard coupling member 2 is installed, under the orthogonal state of axis, one side leans against a guiding groove of inboard coupling member 2 on the entrance part 4d of retainer 4, and one side is inserted in inboard coupling member 2 on the aperture surface 4b of retainer 4.Under this state, when being inserted into inboard coupling member 2 to a certain degree, as shown in Figure 6A, the largest interval (c) of the outer diametric plane 2a of inboard coupling member 2 rests on the step 4e, can not further insert inboard coupling member 2.At this moment, the sphere centre O of the aperture surface 4b of the sphere centre O ' of the outer diametric plane 2a of inboard coupling member 2 and retainer 4 " depart from certain distance.Afterwards, utilize the sidepiece T of the step 4e of retainer 4 shown in Fig. 6 B that inboard coupling member 2 is rotated 90 degree, make the axis of inboard coupling member 2 consistent with the axis of retainer 4.Like this, inboard coupling member 2 is encased on the aperture surface 4b of retainer 4 fully.And, shown in Fig. 7 A and Fig. 7 B, like that,, also can assemble as described above even there is not the occasion of the retainer 4 of step 4e.In this occasion, can under the state of the axis that makes inboard coupling member 2 and the axis normal of retainer 4, assemble up to the sphere centre O ' of the outer diametric plane 2a of inboard coupling member 2 and the sphere centre O of the aperture surface 4b of retainer 4 " consistent.After this, though will inboard coupling member 2 be rotated 90 degree so that both axis unanimities have the advantage that operation is carried out easily this moment with respect to retainer 4.
Generally speaking, in this constant-speed universal joint, for inboard coupling member is assembled on the aperture surface of retainer, and 1 in a plurality of covers of retainer or locational in opposite directions 2 circumferential lengths of 180 degree are set for axial length greater than inboard coupling member.And, both assemblings are performed such, promptly, under the state of the axis normal of the axis of inboard coupling member and retainer, one side is encased in 1 external diameter face portion of inboard coupling member (the circumferentially part of adjacent guiding groove face) in the above-mentioned cover that circumferential lengths establishes greatly, one side is further rotated 90 degree with respect to retainer with inboard coupling member with the aperture surface of inboard coupling member insertion retainer.Yet, structure and assembling method according to such retainer, owing to the circumferential lengths of 1 cover in the retainer must be established at least greater than the axial length of inboard coupling member, so, make the area of the aperture surface of retainer and outer diametric plane reduce, make the circumferential wall thickness minimizing of intermediate portion of inner room.This is not a good thing for the durability of retainer and intensity.Structure and assembling method according to the retainer of above-mentioned present embodiment, owing to there is no need to be provided with the cover of circumferential lengths greater than inboard coupling member axial length, so, the aperture surface that can retainer and the area of outer diametric plane, guarantee the circumferential wall thickness of inner room intermediate portion, can improve the durability and the intensity of retainer.Particularly, resemble under the formation the constant-speed universal joint of the present invention with 8 torque transmitting balls 3 since the number of the cover 4C of retainer 4 frequently product (constant-speed universal joints of 6 balls) are many, so guarantee that the durability of retainer and intensity are very important.
The cover 4C of retainer 4 is set as two kinds of long cover 4C1 and short cover 4C2, is durability and the intensity in order to guarantee retainer 4 as described above, also is in order to consider the assembling performance when packing torque transmitting ball 3 the cover 4C of retainer 4 into.This constant-speed universal joint is an assembling torque transmission ball 3 under such state, promptly, in with the assembly of retainer 4 and inboard coupling member 2 dress on the aperture surface 1a of outside coupling member 1 after (Fig. 2 A), make wind side coupling member 2 (and retainer 4) with respect to the 1 generation angular displacement of outside coupling member as shown in Figure 8.
At this moment, in this constant-speed universal joint, generally speaking, at outside coupling member and inboard coupling member during with the mutual transmitting torque of operating angle θ, torque transmitting ball is along with the phase change of sense of rotation, in the cover of retainer along circumferentially and move radially.And the amount of movement of this torque transmitting ball and operating angle θ increase pro rata, this operating angle θ when packing torque transmitting ball into maximum (operating angle of this moment is " ball pack into angle α ".Should " ball pack into angle α " be " maximum functional angle " greater than operating angle in the following obtainable maximum of prerequisite that guarantees the shaft coupling function).Therefore, because the particularly circumferential amount of movement of the amount of movement of torque transmitting ball is maximum when ball is packed angle α into, when setting the circumferential lengths of retainer cover, need consider the circumferential amount of movement of torque transmitting ball at this moment.
Fig. 8 B with label 31,32 ..., 38 torque transmitting balls 3 that each phase place that is in sense of rotation is shown. Torque transmitting ball 31,33,35,37 is housed among the short cover 4C2 of retainer 4, and ball 32,34,36,38 is housed among the long cover 4C1.The mobile position that is in torque transmitting ball 3 each phase place, that be positioned at cover 4C when shaft coupling is got operating angle α is shown in Fig. 9 A.Also has the mobile status of the torque transmitting ball of Fig. 9 A during for the formation (two sphere centre are positioned at shaft coupling median plane O) of with have as the retainer 4 of present embodiment the sphere centre of the sphere centre of outer diametric plane 4a and aperture surface 4a not being setovered; Fig. 9 B is the aperture surface and the mobile status of outer diametric plane with respect to the torque transmitting ball of shaft coupling median plane O when axial equidistant biasing constitutes of retainer.
Torque transmitting ball 3 is assembled at first respectively among 4 long cover 4C1, is assembled into respectively then among 4 short cover 4C2.For example when the weak point of like that torque drive ball 31 being packed into shown in Fig. 8 A overlapped among the 4C2, the circumferential amount of movement of torque transmitting ball 3 was many in 32,34,36,38 phase place, the phase place 33,35,37 few (Fig. 9 A).As described above, the circumferential lengths of long cover 4C1 (being in 32,34,36,38 phase place in Fig. 8 B) is set at the size of degree like this, promptly when torque transmitting ball 3 being packed into 1 short cover 4C2 (being positioned at 31 phase place in Fig. 8 B), the torque transmitting ball 3 of packing into earlier can not interfered the circumferential wall of long cover 4C1; In addition, the circumferential amount of movement at the phase place at short cover 4C2 place (among Fig. 8 B 33,35,37) torque transmitting ball 3 is few.Therefore, torque transmitting ball 31 can be assembled among the short cover 4C2.Equally, for example when torque transmitting ball 33 assemblings were entered, long cover 4C1 was positioned at 32,34,36,38 phase place, and on 31,35,37 phase place, the circumferential amount of movement of torque transmitting ball 3 is few.Therefore, the short cover 4C2 that torque transmitting ball 33 can be packed into.Like this, (in long cover 4C1 that torque transmitting ball 3 is packed into earlier) among all short 4C2 of overlapping that torque transmitting ball 3 can be packed into so among the cover 4C that the result can pack into torque transmitting ball 3 all.Also have when ball 3 being packed into cover 4C1, the chamfering 1b1 of outside coupling member 1 plays the effect (with reference to Fig. 8 A) to ball 3 guiding.
Generally speaking, in this constant-speed universal joint, be to be (as previously mentioned, the making the axial dimension of the circumferential lengths of 1 cover wherein at least) that benchmark is set circumferential lengths that retainer overlaps greater than inboard coupling member with the circumferential maximum amount of movement of the torque transmitting ball of assembling during ball in cover.Therefore, because the area of the aperture surface of retainer and outer diametric plane reduces and the circumferential wall thickness of the intermediate portion of inner room reduces, so this durability and intensity for retainer is not a good thing.Consider from this point, in the constant-speed universal joint of present embodiment, set the circumferential lengths of the long cover 4C1 of retainer 4 with said reference; For the circumferential lengths of short cover 4C2, be with this constant speed universal shaft coupling during with maximum angle (this angle is littler than " ball pack into angle α ") transmitting torque the circumferential maximum amount of movement of torque transmitting ball 3 in cover be the benchmark setting.By such constituting, can guarantee the aperture surface of retainer and the area of outer diametric plane, the circumferential wall thickness of inner room intermediate portion, guarantee the durability and the intensity of retainer.
In addition, in the formation that does not have as the retainer 4 of present embodiment the sphere centre biasing of the sphere centre of outer diametric plane 4a and aperture surface 4b, shown in Fig. 9 A, because moving at the internal side diameter of shaft coupling of the torque transmitting ball 3 in the cover is all the same with outside diameter, forms the tabular surface (Figure 10) that is parallel to each other or form concave curved surface corresponding to torque transmitting ball 3 surface curvatures so will overlap two circumferential wall 4C11 of 4C.
Under above-mentioned state, assemble outside coupling member 1, inboard coupling member 2, retainer 4, torque transmitting ball 3, then finish the constant-speed universal joint of present embodiment shown in Figure 1A and Figure 1B.Serration (also can be spline) the last connection of 2C axial region 5 at inboard coupling member 2.Also have, form axial region 5 with boron steel in this embodiment, (make the maximum functional angle and the diameter of the part of outside coupling member 1 opening end interference little with the minor diameterization that realizes axial region 5.The diameter of serration with relatively product are identical).Making axial region 5 minor diameterizations is to consider the increase operating angle.In preproduction, can fully reach for example angle of the desired maximum functional of used for vehicle transmission shaft shaft coupling angle more than 45 °.
Figure 11 A-Figure 11 C illustrate embodiment's product and relatively rotating speed (rpm) and the temperature rise amount of product (constant-speed universal joints of 6 balls) (both for same nominal form) (℃) the comparative test result of relation.X among the figure (broken-line white o) is embodiment's product, and Y (solid line is deceived o) is product relatively, the temperature ascending amount (℃) data for beginning from operation after 30 minutes, to measure.In addition, θ is the shaft coupling operating angle, and T is the input moment of rotation.
By this figure test result as can be known, frequently product (Y) are little for the temperature ascending amount of embodiment's product (X), also become big along with rotating speed increases its difference.The reduction that temperature rises improves relevant with durability.In addition, can think how operating angle (θ) and input moment of rotation (T) all can obtain the reduction that such temperature rises.
Figure 12 illustrate embodiment's product and product (constant-speed universal joints of 6 balls) relatively (both are identical nominal form) the temperature ascending amount (℃) time dependent comparative test result.X among the figure (broken-line white o) is embodiment's product, and Y (solid line is deceived o) is product relatively, and θ is the shaft coupling operating angle, and T is the input moment of rotation.
By test result shown in this figure as can be known, the temperature ascending amount of embodiment's product (X) is less than product (Y) relatively, even working time, elongated its difference did not have too big variation yet.
Figure 13 illustrates embodiment's product and the operating angle θ (deg) of product (the constant velocity universal homokinetic joints of 6 balls) relatively (both are identical nominal form) and the comparative test result of the relation of loss of machine of torque rate (%).X among the figure (broken-line white o) is embodiment's product, and Y (solid line is deceived o) is product relatively, does not import moment of rotation T=196N.m when θ=10deg, establishes T=98N.m when θ=30deg, measures the loss of machine of torque rate.
As known in the figure, the loss of machine of torque rate of embodiment's product (X) also becomes big less than product relatively along with operating angle θ increases its difference.The reduction of loss of machine of torque is saved the energy except that but fuel saving takes, and also can make temperature rising reduction and then durability is improved.
Table 3 illustrates embodiment's product and product (constant-speed universal joints of 6 balls) relatively (both the are identical nominal form) observation result through the damage status of outside coupling member, inboard coupling member, retainer and torque transmitting ball after 300 hours.The cover portion wearing depth measurement result of retainer as shown in figure 14.Test conditions is operating angle θ=6deg, input moment of rotation T=1078N.m, rotating speed=200rpm, total winding number=3.60 * 10 6(rev).Also have, in experiment, embodiment's product and relatively product adopt 2 trial targets (embodiment's product are NO1,2, and relatively product are NO3,4) respectively, wearing depth shown in Figure 14 is the mean value of 2 trial targets.
By result shown in the table 3 as can be known, embodiment's product and relatively product all do not have to find damage at each parts.In addition, by result shown in Figure 14 as can be known, the wearing depth of the retainer of embodiment's product (X) cover is less than product (Y) relatively.
As described above,, both can make compact shape, and can have and be equal to or surpass the relatively load capacity and the durability of product (constant-speed universal joints of 6 balls) according to the constant-speed universal joint of present embodiment.
Figure 15 A and Figure 15 B illustrate the constant-speed universal joint of other embodiments of the invention.The center O 2 of the center O 1 of guiding groove 1b of outside coupling member 1 and the guiding groove 2b of inboard coupling member 2 respectively with respect to the sphere centre O5 of the sphere centre O4 of aperture surface 1a and outer diametric plane 2a vertically in the opposition side equidistance (F) of setovering.In addition, in this embodiment, the sphere centre of the aperture surface 4b ' of the sphere centre of the outer diametric plane 4a ' of retainer 4 ' (identical) and retainer 4 ' (identical) with the sphere centre O5 of the outer diametric plane 2a of inboard coupling member 2 with the sphere centre O4 of the aperture surface 1a of outside coupling member 1 with respect to shaft coupling median plane O vertically in opposition side biasing equidistance (f).The above-mentioned Offset (F) of outside coupling member 1 is the axial distance between the sphere centre O4 of the center O 1 of guiding groove 1b and aperture surface 1a, the above-mentioned Offset (F) of inboard coupling member 2 be the axial distance between the sphere centre O5 of the center O 2 of guiding groove 2b and outer diametric plane 2a, and both are equal.Connecting the line segment length of center O 1 and the center O 3 of torque transmitting ball 3 of guiding groove 1b of outside coupling member 1 and the line segment length of center O 2 and the center O 3 of torque transmitting ball 3 that is connected the guiding groove 2b of inboard coupling member 2 all is PCR respectively, and both are equal.
The Offset (f) of outer diametric plane 4a ', the aperture surface 4b ' of retainer 4 ' can be set at following value.As previously mentioned,
4. from guaranteeing retainer intensity, guarantee the viewpoint of durability, the Offset (f) of preferably setting outer diametric plane 4a ', aperture surface 4b ' make than R2 (=f/PCR) in the scope of 0＜R2≤0.052, set R2=0.035 in this embodiment.Since with the foregoing description in, 1., 2., formation 3. identical (but in formation 3., setting R1=0.1003), so save its explanation.In addition, the Offset of retainer 4 ' (f) towards also can on the contrary.That is, the sphere centre of the O4 among Figure 15 A as aperture surface 4b ' will be able to be put the sphere centre of O5 as outer diametric plane 4a '.
In this embodiment's retainer 4 ', also similarly set the diameter (B) of the entrance part 4d ' of the inboard coupling member 2 of packing into, the feasible relation (Figure 17 A) that has C≤B＜A with respect to the external diameter (A) and the largest interval (C) of inboard coupling member 2 with the retainer 4 of the foregoing description.Step 4e ' is made in the inboard of entrance part 4d ' (boundary part of aperture surface 4b ' and entrance part 4d ').But, also can make the shape that does not have step 4e '.When packing inboard coupling member 2 into, as shown in figure 16, under the mutually perpendicular state of axis, a guiding groove 2b of inboard coupling member 2 is leaned against on the entrance part 4d ' of retainer 4 ', simultaneously inboard coupling member 2 is inserted the aperture surface 4b ' of retainers 4 '.Under this state, when inboard coupling member 2 was inserted a certain degree, like that, the largest interval (C) of the outer diametric plane 2a of inboard coupling member 2 was stuck on the step 4e ' shown in Figure 17 A, can not further inboard coupling member 2 be inserted again.At this moment, the sphere centre O of the aperture surface 4b ' of the sphere centre O ' of the outer diametric plane 2a of inboard coupling member 2 and retainer 4 " depart from some distances.Subsequently, utilize the side part T of the step 4e ' of retainer 4 shown in Figure 17 B that inboard coupling member 2 is rotated 90 degree, make the axis of inboard coupling member 2 consistent with the axis of retainer 4 '.Like this, inboard coupling member 2 is encased on the aperture surface 4b ' of retainer 4 ' fully.And, shown in Figure 18 A and Figure 18 B,, also can assemble as described above in occasion even without the retainer 4 ' of step 4e '.
In addition, this embodiment's retainer 4 ' also has 8 covers that are used to accommodate 8 torque transmitting balls 3, and these 8 covers are made of the long cover of setting its circumferential lengths by benchmark same as the previously described embodiments and two kinds of covers of short cover.The number of long cover and short cover and layout with and the wall shape also the formation with the foregoing description is identical.Also have, the assembling of torque transmitting ball 3 in cover is also same as the previously described embodiments, carries out with state shown in Fig. 8 A and Fig. 8 B.But, in this embodiment's formation, because the sphere centre O5 of the sphere centre O4 of the outer diametric plane 4a ' of retainer 4 ' and aperture surface 4b ' is offset to shown in Figure 15 A on the position, so, when the assembling ball, torque transmitting ball 3 moving shown in Fig. 9 B in cover becomes big at outside diameter like that.In such occasion, shown in Figure 19 A and Figure 19 B like that, also can with cover 4c ' two circumferential wall 4c11 ' have the plane of inclination of inclination towards the expansion of retainer 4 ' outside diameter.Figure 19 A illustrates the formation that two wall 4c11 ' make tabular surface, and Figure 19 B illustrates the formation that two wall 4c11 ' make the concave curved surface corresponding with the surface curvature of torque transmitting ball 3.The occasion that becomes the face (with reference to Figure 10) that is parallel to each other with circumferential two walls that will overlap is compared, because the increase of the area (the internal side diameter area of intermediate portion) of the aperture surface 4b ' of retainer 4 ', so favourable aspect the intensity of guaranteeing retainer and durability.
Figure 20 A, Figure 20 B illustrated embodiment form straight line shape with the regulation zone U2 of the guiding groove 2b of the regulation zone U1 of the guiding groove 1b of outside coupling member 1 and inboard coupling member 2 respectively.Zone beyond the U1 of guiding groove 1b is for being the curve-like at center to put 01, and the zone beyond the U2 of guiding groove 2b is for being the curve-like at center with an O2.Because other formation is identical with Figure 15 B illustrated embodiment with Figure 15 A, the Therefore, omited explanation.
, the constant-speed universal joint of the foregoing description can be widely used as the power transmitting elements of automobile, various industrial machines, particularly is suitable for being used for the automobile power transfer unit, for example uses shaft coupling as the live axle of automobile with being connected of propeller shaft.
The constant-speed universal joint that is connected normally fixed and sliding-type of automobile driving axle and propeller shaft is used as a pair of.For example, with the car engine mechanomotive force to the actuating unit of wheel transmission because angular displacement that variation produced and axial displacement by the relative position relation of motor and wheel are arranged, so, such as shown in figure 21, an end that is installed on the live axle 20 that starts between pusher side and the wheel side is connected in differential mechanism 22 by sliding-type constant-speed universal joint 21, the other end is connected in wheel 24 by fixed type constant velocity universal shaft coupling 23.With the constant-speed universal joint of the foregoing description when connecting the fixed type constant velocity universal shaft coupling 23 of this live axle 20, owing on the one hand can guarantee to be equal to or surpass relatively intensity, load capacity and the durability of product (the fixed type constant velocity universal shaft couplings of 6 balls), reduce on the one hand the size of shaft coupling, so be extremely beneficial to the lightweight of tare and the low fuel expensed that brings thus.
Also have, in this constant-speed universal joint, the position relation of the sphere centre (sphere centre of the aperture surface of retainer) of the sphere centre (sphere centre of the outer diametric plane of retainer) of the guiding groove center of guiding groove center, the inboard coupling member of outside coupling member, the aperture surface of outside coupling member, the outer diametric plane of inboard coupling member has 8 kinds of variations shown in Figure 22 { (a)～(h) }, and the present invention is applicable to any formation wherein.The formation of Figure 1A, Figure 1B is corresponding to Figure 22 (b), Figure 15 A, and the formation of Figure 15 B and Figure 20 A, Figure 20 B is corresponding to Figure 22 (a).Also have, torque transmitting ball 3 moving at outside diameter in cover becomes big, is because the formation of Figure 22 (a), (d), (e), (f), (g).
More than Shuo Ming embodiment's formation 1., 2., 3., 4. can be used alone or in combination as (1.), (1.+2.), (3.), (4.), (1.+3.), (1.+4.), (1.+2.+3.), (1.+2.+4.), (3.+4.), (1.+3.+4.), (1.+2.+3.+4.).Wherein, (1.) (claim 2), (1.+2.) (claim 3), (3.) (claim 4), 1.+3. the formation of (claim 4), (1.+2.+3.) (claim 4), (4.) (claim 6), (1.+4.) (claim 6), (1.+2.+4.) (claim 6), (3.+4.) (claim 7), (1.+3.+4.) (claim 7), (1.+2.+3.+4.) (claim 7) is better.
Also have, the invention is not restricted to have the constant-speed universal joint that connects the formation of inboard coupling member and axial region with flute profile (serration or spline), and be applicable to constant-speed universal joint inboard coupling member and the incorporate formation of axial region.For example, behind the outside coupling member of also inboard coupling member, retainer and torque transmitting ball can being packed into, integratedly axial region is engaged (welding, for example laser beam welding, pressure welding etc.) in the end face of inboard coupling member.
Table 1
r1 3.2 3.3 3.4 3.5 3.6 3.7 3.8 3.9
Durability ○ ○ ○ ○ ○ ○ ○ ○
The intensity of outside coupling member × △ △ ○ ○ ○ ○ ○
The intensity of inboard coupling member × △ △ ○ ○ ○ ○ ○
The intensity of protector × △ △ ○ ○ ○ ○ ○
Zero: good △: can *: can not (8 balls)
Table 2
r1(＝PCD BALL/D BALL) r2(＝D OUTER/PCD SERR)
Embodiment's product (8 balls) Product (6 balls) relatively Embodiment's product (8 balls) Product (6 balls) relatively
3.3≤r1≤5.0 3.0≤r1≤3.5 2.5≤r2≤3.5 3.2≤r2
Table 3
Through the situation after 300 hours
Outside coupling member Inboard coupling member Retainer Ball
Embodiment's product (8 balls) NO1 ○ ○ ○ ○
NO2 ○ ○ ○ ○
Product (6 balls) relatively NO3 ○ ○ ○ ○
NO4 ○ ○ ○ ○
Zero: not damage

Claims (1)

1. constant speed universal coupling assembly that is used for vehicle, the sliding-type constant-speed universal joint that its other end with fixed type constant velocity universal shaft coupling that the end with the shaft portion of vehicle links and one and described shaft portion links, wherein, described fixed type constant velocity universal shaft coupling comprises:
Outside coupling member, it has eight the curve-like guiding grooves that extend vertically that form on the aperture surface of spherical shape;
Inboard coupling member, it has eight the curve-like guiding grooves that extend vertically that form on the outer diametric plane of spherical shape;
Eight ball tracks, its described guiding groove by the described guiding groove of described outside coupling member and corresponding with it described inboard coupling member forms jointly, and all described ball tracks are opened into wedge-like towards an axial side;
Eight torque transmitting balls are configured in respectively in the described ball track;
One retainer, it has eight covers that hold described torque transmitting ball;
It is characterized in that the external diameter (D of described outside coupling member OUTER) be formed at the pitch diameter (PCD of the flute profile in the inboard coupling member aperture surface SERR) ratio R 2(=D OUTER/ PCD SERR) be 2.5≤R 2≤ 3.5.
CN 200510078655 1995-12-26 1996-12-19 Constant speed universal coupling assembly Pending CN1755154A (en)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP339345/1995 1995-12-26
JP33934595A JP3702019B2 (en) 1995-12-26 1995-12-26 Fixed constant velocity joint
JP343519/1995 1995-12-28
JP107316/1996 1996-04-26
JP157594/1996 1996-05-28
JP133999/1996 1996-05-28
JP133998/1996 1996-05-28
JP259484/1996 1996-09-30

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
CNB021015333A Division CN1260487C (en) 1995-12-26 2002-01-04 Constant speed universal coupling assembly

Publications (1)

Publication Number Publication Date
CN1755154A true CN1755154A (en) 2006-04-05

Family

ID=18326576

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 200510078655 Pending CN1755154A (en) 1995-12-26 1996-12-19 Constant speed universal coupling assembly

Country Status (2)

Country Link
JP (1) JP3702019B2 (en)
CN (1) CN1755154A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106741780A (en) * 2017-01-15 2017-05-31 佛山市佛禅健康管理有限公司 A kind of mechanical agriculture drive mechanism peculiar to vessel

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69828467T2 (en) 1997-07-16 2006-02-16 Nsk Ltd. Constant velocity joint for wheels
DE10304156B4 (en) * 2003-02-03 2011-10-20 Gkn Driveline International Gmbh Anti-ball joint with improved cage
DE10337919B4 (en) * 2003-08-18 2008-01-24 Gkn Driveline International Gmbh Counter track joint with improved ball cage
DE10337918B4 (en) * 2003-08-18 2010-01-07 Gkn Driveline Deutschland Gmbh Twin ball joint with improved ball cage
JP2006258170A (en) 2005-03-16 2006-09-28 Ntn Corp Fixed type constant velocity universal joint
JP2006283830A (en) * 2005-03-31 2006-10-19 Ntn Corp Constant velocity universal joint
JP5241078B2 (en) 2006-03-31 2013-07-17 Ｎｔｎ株式会社 Fixed constant velocity universal joint
JP4850154B2 (en) * 2007-09-07 2012-01-11 Ｎｔｎ株式会社 Working angle sensor for constant velocity universal joint
JP5355876B2 (en) 2007-10-24 2013-11-27 Ｎｔｎ株式会社 Constant velocity universal joint
JP5734742B2 (en) * 2011-05-25 2015-06-17 Ntn株式会社 Constant velocity universal joint

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106741780A (en) * 2017-01-15 2017-05-31 佛山市佛禅健康管理有限公司 A kind of mechanical agriculture drive mechanism peculiar to vessel

Also Published As

Publication number Publication date
JPH09177814A (en) 1997-07-11
JP3702019B2 (en) 2005-10-05

Similar Documents

Publication Publication Date Title
CN1260487C (en) Constant speed universal coupling assembly
US10207536B2 (en) Drive wheel bearing and method of manufacturing the same
JP5507061B2 (en) Fixed type constant velocity universal joint
EP2908019B1 (en) Manufacturing method for bearing device for wheel
CN1755154A (en) Constant speed universal coupling assembly
US9255611B2 (en) Constant velocity universal joint
EP2101072B1 (en) Constant velocity universal joint
EP2592292A1 (en) Fixed-type constant velocity universal joint
CN1644946A (en) Sliding type constant velocity universal joint
WO2014057781A1 (en) Fixed-type constant-velocity universal joint
JP6468694B2 (en) Wheel bearing device
CN100343543C (en) Fixed constant-velocity universal joint body and its manufacturing method
CN1834490A (en) Fixed constant velocity universal joint
EP2505863B1 (en) Fixed type constant velocity universal joint
KR101405073B1 (en) Fixed uniform motion universal joint
EP2202422B1 (en) Constant velocity universal joint
EP2749783B1 (en) Constant velocity universal joint and method for producing same
CN1918394A (en) Constant velocity universal joint
EP2133582B1 (en) Constant velocity universal joint
JP2012087847A (en) Fixed type constant velocity universal joint
JP5461329B2 (en) Fixed constant velocity universal joint
JP2007064265A (en) Constant velocity universal joint and its inner member
JP2003206948A (en) Bearing device for driving wheel
JP2009287711A (en) Fixed-type, constant-velocity universal joint

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C12 Rejection of a patent application after its publication
RJ01 Rejection of invention patent application after publication