CN101493119A - Constant velocity joint - Google Patents
Constant velocity joint Download PDFInfo
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- CN101493119A CN101493119A CNA2009100080293A CN200910008029A CN101493119A CN 101493119 A CN101493119 A CN 101493119A CN A2009100080293 A CNA2009100080293 A CN A2009100080293A CN 200910008029 A CN200910008029 A CN 200910008029A CN 101493119 A CN101493119 A CN 101493119A
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Abstract
The invention relates to a constant velocity universal joint, which comprises an out cup, having first guide grooves extending axially defined in an inner wall surface thereof; an inner ring, having second guide grooves extending axially defined in an outer circumferential surface thereof; a ball configured between the first and second guide grooves; a retainer for receiving the ball; wherein transverse cross sections of the first and second guide grooves are in arcuate shape, curvature centers (H, R) of the first and second guide grooves are configured into positions offset from the spherical center in opposite directions by the same distance respectively, and the ratio V (T/N) of the distance (T) to the diameter (N) of the ball is set to satisfy the expression 0.12 <= V <= 0.14.
Description
The present invention is that application number is the dividing an application for the Chinese invention patent application of " constant velocity universal joint " that 200580002452.2 (PCT/JP2005/000317), the applying date be on January 13rd, 2005, denomination of invention.
Technical field
The present invention relates to a kind of constant velocity universal joint, it for example is used in the driving force transfer part of automobile a transmission shaft being connected with another transmission shaft.
Background technique
All the time, in the driving force transfer part of automobile, use a transmission shaft and another transmission shaft are coupled together rotating force is passed to the constant velocity universal joint of each axletree.In recent years, the lightweight requirements to constant velocity universal joint improves constantly the further miniaturization of the described constant velocity universal joint of hope realization.In this case, the intensity of constant velocity universal joint, durability, load capacity etc., base dimension according to each key element that constitutes constant velocity universal joint is set respectively, and need under the state of many characteristics such as the intensity that keeps described constant velocity universal joint respectively, durability, load capacity, set size corresponding to miniaturization.
As technological thought about the basic setting of this constant velocity universal joint, open the Japanese patent gazette spy and to disclose such content in 2001-330051 number: have in the fixed type constant velocity universal joint of lateral joint parts, inner contact parts, eight transmission of torque balls and retainer, the ratio Rw of the length (PCR) of the line segment at the center of axial width of described inner contact parts (W) and the guiding groove that is connected described inner contact parts and the center of described transmission of torque ball (=W/PCR) set 0.69≤Rw≤0.84 for.
In addition, open the Japanese patent gazette spy and to disclose such content in 2003-97590 number: having outer race (outer race), inner race (inner race), six transmission of torque balls and keep in the fixed type constant velocity universal joint of cage (cage), is that the diameter of d, transmission of torque ball is that the pitch diameter of DB, six transmission of torque balls is D at the diameter of establishing live axle
PSituation under, the diameter D of transmission of torque ball
BRatio D with respect to the diameter d of live axle
B/ d sets in 0.65～0.72 scope, pitch diameter D
PDiameter D with respect to the transmission of torque ball
BRatio D
P/ D
BSet in 3.4～3.8 scope.
In addition, as the constant velocity universal joint that relates to this prior art, for example at Charles E.Cooney, Jr compiles " UNIVERSALJOINT AND DRIVESHAFT DESIGNMANUAL ADVANCES IN ENGINEERING SERIES NO.7 " (U.S.) the 2nd edition, THE SOCIETY OF AUTOMOTIVE ENGINEERS, INC.1991, p.145-149, such rzeppa universal joint is disclosed in (hereinafter referred to as common document): have the ball groove center of outer race and the ball groove center of inner race on joint shaft (live axle and driven shaft), and the ball groove center of the ball groove center of described outer race and inner race is configured to leave in the both sides at joint center the distance that the joint center equates.
In this rzeppa universal joint, the relative action of ball groove with the ball groove of described inner race by described outer race, remain in six balls in the retainer on the equidistant point between isovelocity surface or the joint axis, thus, drive contact and remain on the isovelocity surface, thereby guaranteed constant speed.
Under this situation, in above-mentioned common document, put down in writing such content: the common normal of the ball groove (guiding groove) of outer race and the load side point of contact of ball, with the common normal angulation of the load side point of contact of the ball groove (guiding groove) of inner race and ball, be that the angle of wedge is set for and is approximately 15 degree～17 and spends.This be for: when rzeppa universal joint is that 0 degree carries out during the left and right sides preventing to cause the locked of ball because of friction under the situation of drift angle action at true joint angle.
And, also put down in writing such content in above-mentioned common document: the cross section of normally used ball groove (with the cross section on the direction of joint shaft quadrature) forms circular shape or elliptic arc shape, the contact angle of the ball groove of elliptic arc shape and ball wherein is set at 30 degree～45 degree, and the contact angle of normal employing is 45 degree.
In addition, open 2003-4062 number and special opening discloses such fixed type constant velocity universal joint in flat 9-317784 number the Japanese patent gazette spy, it is made of outer race, inner race, eight balls and retainer, center bottom land, that become curvilinear position of the guiding groove of outer race (rail slot) is with respect to the center of aperture surface, with center, center bottom land, that become curvilinear position of the guiding groove (rail slot) of inner race, be offset the distance (F) that equates vertically respectively in the opposite direction with respect to outer diametric plane.
Open above-mentioned Japanese patent gazette spy and to have put down in writing such content in 2003-4062 number, the ratio R1 of the length (PCR) of side-play amount (F), the line segment that couples together with center with the center of the guiding groove of the center of the guiding groove of outer race or inner race and ball (=F/PCR) be set in the scope of 0.069≤R1≤0.121.
And, open above-mentioned Japanese patent gazette spy and to have put down in writing such content in flat 9-317784 number: the ratio R1 of the length (PCR) of side-play amount (F), the line segment that couples together with center with the center of the guiding groove of the center of the guiding groove of outer race or inner race and ball (=F/PCR) be set in the scope of 0.069≤R1≤0.121, and the contact angle of each guiding groove and ball is set for smaller or equal to 37 and is spent.
In addition, open the Japanese patent gazette spy and to disclose such fixed type constant velocity universal joint in 2002-323061 number: by the lateral joint parts, the inner contact parts, eight transmission of torque balls and retainer constitute, and also put down in writing such content in this patent documentation: the center of the center of the ball groove (rail slot) of described lateral joint parts and the ball groove (rail slot) of inner contact parts has been offset the distance that equates towards opposition side vertically, and the PCD gap on the ball track (pitch diameter of the pitch diameter of the ball groove of lateral joint parts and the ball groove of inner contact parts poor) is 5～50 μ m.
Opening in 2002-323061 number above-mentioned Japanese patent gazette spy, is 5～50 μ m by making the PCD gap, and thus, in having the fixed type constant velocity universal joint of eight transmission of torque balls, the durability in the time of can promoting high capacity is also stablized the life-span deviation.
In addition, open the Japanese patent gazette spy and record such content in 2002-323061 number: making the radial clearance between lateral joint parts and the retainer is 20～100 μ m, and making the radial clearance between described retainer and the inner contact parts is 20～100 μ m.
In addition, relate to the constant velocity universal joint of this prior art, for example shown in Figure 24, have: exterior part (outer race parts) 1, it is formed with a plurality of curve-like guiding groove 1b vertically on the aperture surface 1a of spherical shape; And inner piece (inner race parts) 2, it is formed with a plurality of curve-like guiding groove 2b vertically on the external surface 2a of spherical shape, and is provided with spline 2c on aperture surface.By the curve-like guiding groove 1b of exterior part 1 and the curve-like guiding groove 2b of inner piece 2, integrally formed ball rolling groove, and configuration is used for the ball 3 that transmission of torque is used in this ball rolling groove.Ball 3 is kept by the maintenance window 4a on the retainer 4 that is formed at ring-type roughly.
Under this situation, the universal joint intensity when giving angle to exterior part 1 and inner piece 2 is by the intensity decision of retainer 4.Therefore, the universal joint intensity when giving angle in order to improve need to improve the intensity of retainer 4 self.
Here, in order to improve the intensity of retainer 4 self, can be corresponding by the sectional area that increases described retainer 4.As this method, for example can enumerate with inferior method: by reducing retainer inner ball surface diameter dimension, increasing the method (hereinafter referred to as first method) that the outer spherical surface diameter dimension increases the wall thickness of described retainer 4 on the other hand, ejection power at the ball 3 that to the universal joint additional angle time, produces, make the method (hereinafter referred to as second method) of the sectional area increase of bearing this ejection power one side of retainer 4, and increase method (hereinafter referred to as third party's method) at the sectional area that keeps the 4b of post portion between the window 4a.
But in above-mentioned first method and second method, exist with inferior problem: the weight of retainer 4 becomes big or width dimensions broadens, and ball 3 invades among the curve-like guiding groove 1b, causes the durability of exterior part 1 to reduce.And,, may cause and this retainer 4 can't be assembled in the exterior part 1 because retainer 4 width broaden.
On the other hand, in above-mentioned third party's method, but when the increase of the 4b of post portion length caused keeping the opening area of window 4a to reduce, ball 3 contacted with the described post 4b of portion easily, caused described ball 3 and produced the bad problem of assembling thereby exist.And, owing to keep window 4a too small, and have the problem that can't easily inner piece 2 be assembled in the retainer 4.
Therefore, for example open and disclose such constant velocity joint in 2002-13544 number: keeping on the window 4a 4c of angular radius portion being set, and the ratio R/D of the radius of curvature R of the 4c of this angular radius portion and the diameter D of ball 3 is 0.22≤R/D the Japanese patent gazette spy.
But in above-mentioned Japanese patent gazette spy opened 2001-330051 number disclosed technological thought, have such problem: number of spare parts was many, thereby causes manufacture cost higher, and technical difficulty is bigger during actual production.
In addition, in above-mentioned Japanese patent gazette spy opens 2003-97590 number disclosed technological thought, be that the size of carrying out for the intensity of the retainer that improves the holding torque transmission ball is set, thereby have the problem that can't make the constant velocity universal joint miniaturization.
In addition, the ball orbit-shaped that forms of the ball groove of ball groove by outer race and inner race becomes: the wedge-like that portion's side increases vertically gradually towards the opening portion side in the opening portion of outer race.Therefore, because each ball groove of bell shell-side and inner race side has been positioned at respect to the joint off-centring position of equidistance, therefore the degree of depth of two ball grooves is inhomogeneous in the axial direction.
In the disclosed structure of described common document, because the degree of depth of each ball groove of outer race and inner race is more shallow, therefore, when big angle of attachment or high capacity action, the contact ellipse of ball may and move on the shoulder (end) of this ball groove from described ball groove disengagement, perhaps may cause ball groove shoulder that destruction or wearing and tearing etc. take place, thereby reduce durability.In addition, also be susceptible to such situation: when applying high capacity, the contact position of ball groove and ball causes contact ellipse outstanding near the end of inner race, thereby the interface pressure to this ball groove is increased.
In addition, open 2003-4062 number and special opening discloses such content in flat 9-317784 number: side-play amount (F) above-mentioned Japanese patent gazette spy, the ratio R1 of the length (PCR) of the line segment that couples together with center with the center of the guiding groove of the center of the guiding groove of outer race or inner race and ball (=F/PCR) be set at predetermined value, but in this case, if will set the diameter of ball less, perhaps make constant velocity universal joint self miniaturization more, and guarantee as the intensity wall thickness of the retainer of weak parts, then must fully guarantee the guiding groove degree of depth of outer race and inner race, thereby can produce problems such as the destruction of guiding groove shoulder or wearing and tearing as described above.
In addition, open the Japanese patent gazette spy and to have put down in writing such content in 2002-323061 number, constant velocity joint with eight transmission of torque balls is different with the basic structure of the constant velocity joint with six transmission of torque balls, the former also has the intrinsic value that is fit to its structure at the setting value in PCD gap, and, then there is no and anyly mention or hint about the setting value in the PCD gap of constant velocity joint with six transmission of torque balls etc.
That is, in this constant velocity joint, the ball track is formed by one group of ball groove opposite each other of lateral joint parts and inner contact parts, and focuses on how setting PCD (pitch diameter) gap with respect to this ball track.This be because, if described PCD gap is too small, then the assembling operation of the ball when ball being inserted in the ball track is very difficult, in addition because bigger, thereby the scroll actions smoothly that can hinder described ball to the restraining force of ball.On the other hand, if the PCD excesssive gap then has again to produce the problem that collision noise or joint vibration increase between the maintenance window portion of retainer and ball.
In addition, open disclosed technological thought 2002-13544 number according to aforementioned Japanese patent communique spy, the ratio R/D of diameter D by ball that the radius of curvature R of the angular radius portion on the pocket hole (maintenance window) that is arranged at retainer and transmission of torque are used sets, improve durability and intensity, but have the problem that only can not fully improve the intensity of described retainer by above-mentioned condition enactment.
Summary of the invention
The object of the invention is to provide a kind of constant velocity universal joint, and it can reduce the surface pressure that guiding groove is produced owing to contacting with ball, to improve durability.
The object of the invention is to provide a kind of constant velocity universal joint, and destruction or wearing and tearing etc. take place its shoulder that can prevent guiding groove, can improve durability.
The object of the invention is to provide a kind of constant velocity universal joint, it is the constant velocity universal joint with six balls, be set at the best by side-play amount with the maintenance window of various gaps or retainer, can make between direct outside guiding groove that influences the universal joint life-span and the ball and the surface pressure between inboard guiding groove and the ball reduces, thereby can improve durability.
The object of the invention is to provide a kind of constant velocity universal joint, and it can keep each side characteristics such as intensity, durability, load capacity, and can carry out setting corresponding to the various sizes of miniaturization.
The object of the invention is to provide a kind of constant velocity universal joint, and it can guarantee the intensity of retainer well, and can improve assembling operation.
According to the present invention, the cross section of first guiding groove of exterior part forms circular shape, and be contacted with a bit with ball, and the cross section of second guiding groove of interior ring forms the elliptic arc shape, and is contacted with 2 points with ball, thus, compared with prior art, can reduce to improve durability owing to the surface pressure that produces with contacting of ball to first and second guiding grooves.
Under this situation, the ratio of the groove radius (P, Q) of the cross section of the groove radius (M) of the cross section of described first guiding groove and second guiding groove and the diameter (N) of ball is set in respectively in 0.51～0.55 the scope, and, the contact angle of first guiding groove and ball is that benchmark is made as zero degree with plumb line (L), and the contact angle of second guiding groove and ball (α) is that benchmark is set in the scope of 13 degree～22 degree with plumb line (L), surface pressure can be reduced thus, durability can be further improved.
In addition, better is that contact angle (α) with described second guiding groove and ball is that benchmark is set in the scopes of 15 degree～20 degree with plumb line (L).
In addition, according to the present invention, the PCD gap is set in the scope of 0 μ m～100 μ m, this be because: if the PCD gap is less than 0 μ m, then ball is with respect to the assembling variation in the hole portion of exterior part, and scroll actions stably that can stymy, causes durability to reduce.Be on the other hand because: if described PCD gap surpasses 100 μ m, then the contact ellipse of ball and first and second guiding grooves is outstanding from the shoulder as the groove end when high capacity, surface pressure is increased, and cause shoulder to destroy, and causes the durability reduction.
Under this situation, Spherical Clearance is by obtaining two following poor additions: the retainer outer spherical surface diameter of the exterior part inner ball surface diameter of the aperture surface of described exterior part and the outer surface of described retainer poor, poor with the interior ring outer spherical surface diameter of the outer surface of the retainer inner ball surface diameter of the internal surface of described retainer and interior ring, described Spherical Clearance [(exterior part inner ball surface diameter)-(retainer outer spherical surface diameter)]+[(retainer inner ball surface diameter)-(interior ring outer spherical surface diameter)] is set in the scope of 50～200 μ m.
This be because: if less than 50 μ m, then outside between the outer surface of the internal surface of parts and retainer and between the internal surface of interior ring outer surface and retainer, understand and cause ablation because of insufficient lubrication, thereby bring bad influence.Be on the other hand because: if described Spherical Clearance surpasses 200 μ m, then produce collision noise between parts and interior ring and the retainer outside, can influence commodity.
In addition, can will be formed at the maintenance window width center of the maintenance window of described retainer, be set in such position: the position of axially in the scope of 20～100 μ m, having carried out skew from the sphere centre of the outer surface of described retainer and internal surface along described retainer.
This be because: if the side-play amount of the maintenance window width center of retainer and sphere centre is less than 20 μ m,, thereby be difficult to guarantee constant speed then to the restraining force deficiency of ball, if described side-play amount is greater than 100 μ m, then binding force is excessive, and scroll actions smoothly that can stymy makes the durability variation.
In addition, according to the present invention, satisfy described relation (0.12≤V≤0.14) by the ratio V (T/N) that sets the diameter (N) that makes ball and the side-play amount T of the centre of curvature (H, R) of first and second guiding grooves for, therefore can prevent effectively that ball from moving on the shoulder that is formed at the described first and second guiding groove ends, or prevent described shoulder generation defective or wearing and tearing etc., thereby can improve the durability of constant velocity universal joint.
Under this situation, if the ratio V (T/N) of diameter of described ball (N) and side-play amount (T) is less than 0.12, then the angle of wedge that is formed by first guiding groove and second guiding groove is minimum state, when not being rotated action, the locking state of ball takes place easily, the operation reduction when making assembling.On the other hand, if the diameter of described ball (N) surpasses 0.14 with the ratio V (T/N) of side-play amount (T), then the degree of depth of first and second guiding grooves is more shallow, is difficult to stop ball to move to and is formed on the shoulder of the described first and second guiding groove ends, or stop described shoulder that destruction or wearing and tearing etc. take place.
In addition, according to the present invention, make described outer PCD with described in PCD identical and as outer/inner PCD, trepan tooth inside diameter in being formed with on the internal face of the hole portion of ring in described, the size of described outer/inner PCD (Dp) preferably sets in 1.9≤(Dp/D)≤2.2 scope with the ratio (Dp/D) of the diameter (D) of described interior trepan tooth inside diameter.If the size of described outer/inner PCD (Dp) with described in the size of diameter (D) of trepan tooth inside diameter than (Dp/D) less than 1.9, the wall thickness of ring is crossed thin and unfavorable condition that cause intensity to reduce in then existing, on the other hand, if described size surpasses 2.2 than (Dp/D), then can not make the constant velocity universal joint miniaturization.
In addition, make described outer PCD with described in PCD identical and as outer/inner PCD, the diameter of described ball (Db) preferably sets in 0.2≤(Db/Dp)≤0.5 scope with the ratio (Db/Dp) of the size (Dp) of described outer/inner PCD.Under this situation, if described size than (Db/Dp) less than 0.2, the too small and unfavorable condition that causes durability to reduce of the diameter that then has a ball, on the other hand, if described size surpasses 0.5 than (Db/Dp), then ball is big and the wall thickness of exterior part is thinner relatively, thereby causes intensity to reduce.
In addition, make described outer PCD with described in PCD identical and as outer/inner PCD, the external diameter of described exterior part (Do) preferably sets in 1.4≤(Do/Dp)≤1.8 scope with the ratio (Do/Dp) of the size (Dp) of described outer/inner PCD.Under this situation, if described size than (Do/Dp) less than 1.4, the thin and unfavorable condition that causes intensity to reduce of the wall thickness that then has an exterior part, on the other hand, if described size surpasses 1.8 than (Do/Dp), then the external diameter of exterior part can't be realized miniaturization greatly.
Make described outer PCD with described in PCD identical and as outer/inner PCD, trepan tooth inside diameter in described, being formed with on the internal face of the hole portion of ring, the size of described outer/inner PCD (Dp) preferably sets in 1.9≤(Dp/D)≤2.2 scope with the ratio (Dp/D) of the diameter (D) of described interior trepan tooth inside diameter, and, the diameter of described ball (Db) preferably sets in 0.2≤(Db/Dp)≤0.5 scope with the ratio (Db/Dp) of the size (Dp) of described outer/inner PCD, and the external diameter of described exterior part (Do) preferably sets in 1.4≤(Do/Dp)≤1.8 scope with the ratio (Do/Dp) of the size (Dp) of described outer/inner PCD.
In addition, according to the present invention, described maintenance window upwards has opening length (WL) in the week of described retainer, and described opening length (WL) preferably sets in 1.30≤(WL/N)≤1.42 scope with the ratio (WL/N) of the diameter (N) of described ball.Described maintenance window has the bight that radius of curvature is R, and the ratio (R/N) of the diameter (N) of described radius of curvature (R) and described ball preferably sets in 0.23≤(R/N)≤0.45 scope.
By setting 0.23≤(R/N) relation for, can reduce the major principal stress load that keeps the post portion between the window, can improve the intensity of retainer.On the other hand, by setting the relation of (R/N)≤0.45 for, it is excessive to prevent to keep the bight of window effectively, thereby avoids the assembling of ball and interior ring bad.
In addition, described first guiding groove and described second guiding groove can form and alongst have curved shape portion and rectilinear form portion (S1, S2).And described first guiding groove and described second guiding groove are preferably formed to alongst only having curved shape portion.
Description of drawings
Fig. 1 is the longitudinal section vertically of the constant velocity universal joint of embodiment of the present invention.
Fig. 2 is that longitudinal section is amplified in the part of constant velocity universal joint shown in Figure 1.
Fig. 3 be constant velocity universal joint shown in Figure 1 from axial (arrow directions X) observed partial side view in cross section.
Fig. 4 is that cross-sectional view is amplified in constant velocity universal joint and axially vertical part shown in Figure 1.
Fig. 5 is that longitudinal section is amplified in the part of the degree of depth of first guiding groove of the constant velocity universal joint of expression present embodiment.
Fig. 6 is that longitudinal section is amplified in the part of the degree of depth of first guiding groove of the constant velocity universal joint of expression comparative example.
Fig. 7 is expression second guiding groove and the contact angle of ball and the explanatory drawing of the relation between the durability.
Fig. 8 A is the longitudinal section of expression as the outer PCD of the pitch diameter of first guiding groove that is formed at outer cup (outer cup), and Fig. 8 B is the longitudinal section of expression as the interior PCD of the pitch diameter of second guiding groove that is formed at interior ring (inner ring).
Fig. 9 A is the longitudinal section of outer glass of inner ball surface diameter of the aperture surface of cup outside representing, Fig. 9 B is the longitudinal section of interior ring outer spherical surface diameter of the outer surface of ring in the expression, and Fig. 9 C is the longitudinal section of retainer inner ball surface diameter of representing the internal surface of the retainer outer spherical surface diameter of outer surface of retainer and retainer respectively.
Figure 10 is the longitudinal section of the side-play amount between the sphere centre of the outer surface of the maintenance window width center of maintenance window of expression retainer and retainer and internal surface.
Figure 11 is the explanatory drawing of the relation between expression PCD gap and the durability.
Figure 12 is the explanatory drawing of the relation between expression Spherical Clearance and the durability.
Figure 13 is the explanatory drawing that expression keeps the relation between window skew and the durability.
Figure 14 be constant velocity universal joint shown in Figure 1 from axial (arrow directions X) observed partial side view in cross section.
Figure 15 is the local amplification sectional view of the constant velocity universal joint of expression axle serrations diameter (D), outer/inner PCD (Dp), the external diameter (Do) of outer cup and the diameter (Db) of ball etc.
Figure 16 is the performance plot of the characteristic straight line L of the diameter of trepan tooth inside diameter and the relation between the outer/inner PCD in the expression.
Figure 17 be the outer/inner PCD of expression with outer glass external diameter between the performance plot of characteristic straight line M of relation.
Figure 18 is the performance plot of the characteristic straight line N of the relation between the inner ring width of expression outer/inner PCD and interior ring.
Figure 19 is the performance plot of the characteristic straight line Q of the relation between the diameter of expression outer/inner PCD and ball.
Figure 20 is the longitudinal section vertically that is used to illustrate the constant velocity universal joint of the maintenance window that is formed at retainer and the relation between the ball.
Figure 21 constitutes the retainer of constant velocity universal joint shown in Figure 20 and the exploded perspective view of ball.
Figure 22 be used to illustrate described retainer shown in Figure 21 and described ball each size from circumferential observed side view.
Figure 23 is the longitudinal section vertically that is used to illustrate the constant velocity universal joint of first guiding groove that alongst only has curved shape portion and second guiding groove.
Figure 24 is the exploded perspective view of the constant velocity universal joint of prior art.
Embodiment
In Fig. 1, with reference to the constant velocity universal joint of label 10 expression embodiment of the present invention.In addition, in the following description, the longitudinal section is meant along first 12 and second 18 axial cross section, and cross section is meant the cross section with described axial quadrature.
These constant speed universal joint 10 basic comprisings are to comprise: outer cup (exterior part) 16 of round-ended cylinder shape arranged, and itself and first 12 a end connects as one, and has opening portion 14; And inner piece 22, it is anchored on an end of second 18, and is contained in the hole portion of outer cup 16.
As shown in figures 1 and 3, outside described, has the aperture surface 24 that constitutes by sphere on the inwall of cup 16, on described aperture surface 24, be formed with six first guiding groove 26a～26f that extend vertically, and described six first guiding groove 26a～26f separate configuration with the interval of 60 degree respectively around the axle center.
As shown in Figure 2, being formed at a described outer cup longitudinal section 16, vertically is the curvilinear first guiding groove 26a (26b～26f), be centre of curvature with a H.Under this situation, described some H is disposed at such position: from the sphere centre K of aperture surface 24 (intersection point of imaginary plane (median plane of ball) and universal joint axis 27 quadratures that connects the central point O of ball 28) vertically outwardly opening portion 14 lateral deviations of cup 16 moved position apart from T1.
As shown in Figure 4, be formed at the cross section of first guiding groove 26a～26f of described outer cup 16, constitute respectively have the single circular-arc of centre of curvature A on the plumb line L of the center O by ball 28, the outer surface that described first guiding groove 26a～26f forms on drawing with ball 28 described later is contacted with 1 B.
In addition, in fact, when applying load transmitting rotating torques, the outer surface of ball 28 and first guiding groove 26a～26f contact but face contacts.
The both sides of first guiding groove 26a～26f in described cross section are formed with described aperture surface 24 continuously, in the end of described first guiding groove 26a～26f and the boundary part of aperture surface 24, are formed with one group of first shoulder 30a, 30b having passed through chamfering.
Ring is 34 chimeric with second 18 end spline by the hole portion at the center of being formed in described, perhaps is fixed in second 18 end integratedly by the fastening parts 40 that are installed on the ring-type in second 18 the annular slot.Be formed with a plurality of second guiding groove 32a～32f along the circumferentially spaced equal angles in this on the outer diametric plane 35 of ring 34, described a plurality of second guiding groove 32a～32f and first guiding groove 26a～26f of outer cup 16 are configured accordingly.
As shown in Figure 2, being formed at described interior ring 34 and longitudinal section vertically and forming curvilinear described second guiding groove 32a～32f, is centre of curvature with a R.Under this situation, described some R is disposed at such position: be offset the position apart from T2 vertically from the sphere centre K (imaginary plane (median plane of ball) of the central point O of connection ball 28 and the intersection point of universal joint axis 27 quadratures) of aperture surface 24.
Be disposed at such position as the some H of the centre of curvature of first guiding groove 26a～26f of outer cup 16 with as the some R of the centre of curvature of second guiding groove 32a～32f of interior ring 34: from the sphere centre K (intersection points of the median plane of ball and universal joint axis 27 quadratures) of aperture surface 24 along the position that has been offset equidistance (T1=T2) week towards each other in the opposite direction.Described some H is opening portion 14 sides of baseline configuration in outer cup 16 with sphere centre K, and described R point is positioned at depth portion 46 sides of outer cup 16, and the radius of curvature of the radius of curvature of described some H and some R is set at cross-like (with reference to Fig. 2).
Under this situation, if the diameter of ball 28 is N, if the side-play amount of the centre of curvature of first guiding groove 26a～26f of outer cup 16 and second guiding groove 32a～32f of interior ring 34 (some H, some R) (distance of leaving vertically from sphere centre K) is made as T respectively, if the ratio of described diameter N and described side-play amount T is made as V, at this moment, the diameter N of described ball 28 and side-play amount T preferably set become to make described than V (=T/N) satisfy the relation of 0.12≤V≤0.14.
As shown in Figure 4, the cross section of described second guiding groove 32a～32f forms: have along substantially horizontal at a distance of a pair of center C of intended distance, the elliptic arc shape of D, the outer surface that described second guiding groove 32a～32f forms on drawing with ball 28 is contacted with E, F at 2.In addition, in fact, when applying load when transmitting rotating torques, the outer surface of ball 28 and second guiding groove 32a～32f contact but face contacts.
The both sides of second guiding groove 32a～32f in described cross section are formed with outer diametric plane 35 continuously, the end of described second guiding groove 32a～32f with outside the boundary part of diametric plane 35, be formed with one group of second shoulder 42a, 42b having passed through chamfering.
The contact angle α of ball 28 and second guiding groove 32a～32f is to leave angle same α about benchmark is set at plumb line L.Under this situation, as shown in Figure 7, when the contact angle α of ball 28 and described second guiding groove 32a～32f is set in the scopes of 13 degree～22 degree, durability is good, if the contact angle α of ball 28 with described second guiding groove 32a～32f is set in the scope of 15 degree～20 degree, then can obtain extraordinary durability in addition.In addition, groove radius P, the Q in the cross section of described second guiding groove 32a～32f can be set at 0.51～0.55 (with reference to Fig. 4) with the ratio (P/N, Q/N) of the diameter N of ball 28.
Described ball 28 is for example made by steel ball, and is configured to: respectively dispose one between second guiding groove 32a～32f of first guiding groove 26a～26f of cup 16 and interior ring 34 outside, and can be along circumferential rolling.This ball 28 is passed to first 12 with second 18 rotating torques by interior ring 34 and outer cup 16, and, can make second 18 and on the angle direction that intersects, relative displacement take place between (interior ring 34) and first 12 (outer glass 16) by rolling along first guiding groove 26a～26f and second guiding groove 32a～32f.In addition, rotating torques can transmit to any direction between first 12 and second 18 well.
Shown in Fig. 8 A and Fig. 8 B, six balls 28 respectively with the first guiding groove 26a～26f point state of contact of outer cup 16 under, if the pitch diameter of described first guiding groove 26a～26f is outer PCD, six balls 28 respectively with the second guiding groove 32a～32f point state of contact of interior ring 34 under, if the pitch diameter of described second guiding groove 32a～32f is interior PCD, in this case, according to described outer PCD and described in PCD poor, the PCD gap is determined (PCD in the outer PCD-).
In addition, shown in Fig. 9 A～9C, by with following two poor additions, Spherical Clearance is determined: the retainer outer spherical surface diameter of the outer diametric plane of outer cup inner ball surface diameter on the aperture surface 24 of cup 16 and retainer 38 is poor outward, and the interior ring outer spherical surface diameter of the outer diametric plane of the retainer inner ball surface diameter of retainer 38 aperture surfaces and interior ring 34 is poor.
In other words, set according to following formula: Spherical Clearance=[(outer cup inner ball surface diameter)-(retainer outer spherical surface diameter)]+[(retainer inner ball surface diameter)-(interior ring outer spherical surface diameter)].
In addition, as shown in figure 10, the maintenance window width center of the maintenance window 36 of retainer 38 (with retainer 38 axially as width direction), with the outer surface 38a of described retainer 38 and the sphere centre of internal surface 38b, be configured in along the axial dipole field of retainer 38 on the position of intended distance.
The basic structure of the constant velocity universal joint 10 of present embodiment describes its action and action effect as mentioned above below.
When second 18 rotation, its rotating torques 16, the first 12 in cup outside interior ring 34 is passed to by each ball 28 keeps and described second 18 constant speed, and rotates to predetermined direction simultaneously.
At this moment, under the situation that first 12 and second 18 intersecting angles (operating angle) change, by the effect of the ball 28 that between first guiding groove 26a～26f and second guiding groove 32a～32f, rolls, retainer 38 predetermined angle that fascinates, thus allow that described angle changes.
In this case, remain in six balls 28 in the maintenance window 36 of retainer 38 on isovelocity surface or first, equidistant point between second spool 12,18, thus, drive contact and remain on the isovelocity surface, can guarantee constant speed.Like this, when keeping first 12 and second 18 constant speed, also allow angle variation suitable between them.
In the present embodiment, the diameter N of ball 28, with the ratio V of the side-play amount of the centre of curvature (some H, some R) of second guiding groove 32a～32f of first guiding groove 26a～26f of outer cup 16 and interior ring 34 (distance of leaving vertically from sphere centre K) T (=T/N), set for satisfied: the relation of 0.12≤V≤0.14 (with reference to Fig. 2).
Under this situation, if the ratio V of the diameter N of described ball 28 and side-play amount T is less than 0.12, then the angle of wedge that is formed by first guiding groove 26a～26f and second guiding groove 32a～32f is minimum state, when not being rotated action, the locking state of ball 28 takes place easily, the unfavorable condition of the operation reduction when having assembling.
On the other hand, if the diameter N of described ball 28 and the ratio V of side-play amount T surpass 0.14, then because the degree of depth of first guiding groove 26a～26f and second guiding groove 32a～32f is more shallow, and be difficult to avoid ball 28 to move to and be formed at the end of first and second guiding groove 26a～26f, 32a～32f the first and second shoulder 30a, 30b, 42a, 42b is last or be difficult to avoid destroy or the generation of the situations such as the first and second shoulder 30a, 30b, 42a, 42b of wearing and tearing.
Like this, the side-play amount T of the centre of curvature (some H, some R) by setting the diameter N that makes ball 28 and first and second guiding groove 26a～26f, 32a～32f for satisfies described relation (0.12≤V≤0.14), can prevent effectively that ball 28 from moving to the first and second shoulder 30a of the end that is formed at first and second guiding groove 26a～26f, 32a～32f, 30b, 42a, 42b is last or the generation of the destruction or the situations such as the first and second shoulder 30a, 30b, 42a, 42b of wearing and tearing, thereby can further improve the durability of constant velocity universal joint 10.
Fig. 5 represents that the part of longitudinal section of the constant velocity universal joint 10 of present embodiment amplifies, because the relation of the side-play amount T of the diameter N of ball 28 and the centre of curvature of first and second guiding groove 26a～26f, 32a～32f (some H, some R) satisfies described relation, so side-play amount T1 sets lessly.On the other hand, Fig. 6 represents that the part of longitudinal section of the constant velocity universal joint 10 of comparative example amplifies, and side-play amount T2 compares and set greatly (T1＜T2) with present embodiment.
In this case, at positions with respect to straight line S (this straight line S and joint axis 27 quadratures also pass through the center of ball 28) about 15 degree that tilt, externally the degree of depth of first guiding groove 26a～26f of cup 16 compares, at this moment, the depth D P1 of first guiding groove 26a～26f of present embodiment can form (DP1＞DP2), the first and second shoulder 30a of the end that therefore can effectively avoid ball 28 to move to being formed at first guiding groove 26a～26f greater than the depth D P2 of first guiding groove of comparative example, 30b, 42a, on the 42b, perhaps destroy or the first and second shoulder 30a that wear and tear, 30b, 42a, the generation of situations such as 42b.
In addition, in the present embodiment, the cross section of first guiding groove 26a～26f of outer cup 16 forms circular shape, and is contacted with a bit with ball 28, and, the cross section of second guiding groove 32a～32f of interior ring 34 forms elliptical shape, and be contacted with 2 points with ball 28, thus, compared with prior art, reduced the surface pressure that produces owing to contacting, can improve durability first guiding groove 26a～26f and second guiding groove 32a～32f with ball 28.
Under this situation, in the present embodiment, the ratio (M/N, P/N, Q/N) of groove radius on the cross section of first guiding groove 26a～26f and second guiding groove 32a～32f (M, P, Q) and the diameter N of ball 28 is set in respectively in 0.51～0.55 the scope, and, the contact angle of first guiding groove 26a～26f and ball 28 is that benchmark is made as zero degree with plumb line L, and the contact angle α of second guiding groove 32a～32f and ball 28 is that benchmark is set in the scope of 13 degree～22 degree with plumb line L, surface pressure can be reduced thus, durability can be further improved.
Why make the groove radius (M on the cross section of described first guiding groove 26a～26f and second guiding groove 32a～32f, P, Q) ratio with the diameter N of ball 28 is 0.51～0.55, be because: when this than less than 0.51 the time, groove radius (M, P, Q) too approaching with the diameter N of ball 28, and become approximate all states of contact (contact on whole), therefore be unfavorable for the rolling of ball 28, so cause durability to reduce, on the other hand, if surpass 0.55, then on the contrary, because the contact ellipse of ball 28 reduces, thereby cause interface pressure to increase, thereby influence durability.
In addition, the ratio V (T/N) of the side-play amount T of the centre of curvature of first and second guiding groove 26a～26f, 32a～32f on the diameter N of described ball 28 and the longitudinal section (some H, some R), the contact angle α of second guiding groove 32a～32f and ball 28, and the ratio of the groove radius (M, P, Q) on the cross section of described first guiding groove 26a～26f and second guiding groove 32a～32f and the diameter N of ball 28, be respectively the optimum value that the result according to simulation of carrying out repeatedly and test tries to achieve.
In addition, why the contact angle α with second guiding groove 32a～32f and ball 28 is set in the scopes of 13 degree～22 degree, be because: if described contact angle α less than 13 the degree, then the load to ball 28 increases, make surface pressure increase, thereby make the durability variation, on the other hand, if described contact angle α surpasses 22 degree, then the end of second guiding groove 32a～32f (the second shoulder 42a, 42b) and the contact position of ball 28 are approaching, cause that contact ellipse is outstanding, has increased surface pressure, thereby has made the durability variation.
In addition, in the present embodiment, the PCD gap (with reference to Fig. 8 A and Fig. 8 B) that poor (the outer PCD-in PCD) by outer PCD and interior PCD forms is set at 0～100 μ m, and preferably can be set at 0～60 μ m.Making described PCD gap is 0～100 μ m, be because: if less than 0 μ m then can reduce the assembling performance of ball 28, and the scroll actions smoothly of stymy 28, make the durability variation.Be on the other hand because: if described PCD gap surpasses 100 μ m, then when high capacity, make the contact ellipse of ball 28 and first and second guiding groove 26a～26f, 32a～32f outstanding from the first and second shoulder 30a, 30b, 42a, 42b as the groove end, surface pressure is increased, and cause the first and second shoulder 30a, 30b, 42a, 42b to destroy, cause the durability variation.At this moment, shown in the test result of Figure 11, be 0～60 μ m by the setting range that makes described PCD, can obtain extraordinary durability.
In addition, in the present embodiment, shown in Fig. 9 A～Fig. 9 C, making the Spherical Clearance by [(outer cup inner ball surface diameter)-(retainer outer spherical surface diameter)]+[(retainer inner ball surface diameter)-(interior ring outer spherical surface diameter)] set is 50～200 μ m, preferably can be set at 50～150 μ m.This be because: if less than 50 μ m, then outside between the outer surface 38a of cup 16 internal surface and retainer 38 and between the internal surface 38b of interior ring 34 outer surfaces and retainer 38, understand and cause ablation because of insufficient lubrication, thereby bring bad influence.Be on the other hand because: if surpass 200 μ m, then outside cup 16 and interior ring 34, and retainer 38 between produce collision noise, can influence commodity.At this moment, shown in the test result of Figure 12, be 50～150 μ m by the setting range that makes described Spherical Clearance, can obtain extraordinary durability.
In addition, in the present embodiment, as shown in figure 10, the maintenance window width center of the maintenance window 36 of retainer 38 (axially is width direction with retainer 38) is disposed at such position: the axial dipole field from the sphere centre of the outer surface 38a of described retainer 38 and internal surface 38b along retainer 38 position of 20～100 μ m.This be because: if the side-play amount of the maintenance window width center of the maintenance window 36 of retainer 38 and sphere centre is less than 20 μ m, then to the restraining force deficiency of ball 28, thereby be difficult to guarantee constant speed, if and described side-play amount is greater than 100 μ m, then binding force is excessive, the scroll actions smoothly of meeting stymy 28 reduces durability.At this moment, shown in the test result of Figure 13, the setting range of the maintenance window width center by making described retainer 38 and the side-play amount of sphere centre is 40～80 μ m, can obtain extraordinary durability.
As a result, in the present embodiment, in constant velocity universal joint 10,, also can suppress contact ellipse outstanding of ball 28, thereby can improve durability even under the situation of high capacity with six balls 28.
Below, the setting of the various sizes of constant velocity universal joint 10 is elaborated.
Under this situation, described outer PCD shown in Fig. 8 A and Fig. 8 B and described interior PCD are set at equal (PCD in the outer PCD=), thereby the difference of outer PCD and interior PCD is set to zero.In addition, in the following description, outer PCD and interior PCD are called " outer/inner PCD " in the lump.
The diameter (D) of interior trepan tooth inside diameter 39 is set arbitrarily, according to the diameter (D) of trepan tooth inside diameter 39 in described, sets the size (with reference to Figure 14 and Figure 15) as the outer/inner PCD of the minimum wall thickness (MINI W.) of interior ring 34.
In addition, the diameter (D) of trepan tooth inside diameter 39 is meant in described: the bottom of paddy portion on the direction at the center of the hole portion by interior ring 34, an interior trepan tooth inside diameter 39 and the size (maximum diameter) (with reference to Figure 15) between the bottom of the paddy portion of trepan tooth inside diameter 39 in another.Guarantee the bond strength be scheduled to by the minimum wall thickness (MINI W.) of ring 34 in described.As shown in figure 16, the value of described outer/inner PCD is tried to achieve according to the diameter of interior trepan tooth inside diameter 39 and the characteristic straight line L of the relation between the outer/inner PCD.
Under this situation, if the diameter of interior trepan tooth inside diameter 39 is D, if outer/inner PCD is Dp (with reference to Figure 14 and Figure 15), then described outer/inner PCD (Dp) preferably sets in 1.9≤(Dp/D)≤2.2 scope than (Dp/D) with the size of the diameter (D) of described interior trepan tooth inside diameter 39.
This be because: if described size than (Dp/D) less than 1.9, then exist because of the wall thickness of interior ring 34 and cross the thin unfavorable condition that causes intensity to reduce, on the other hand,, then can't make constant velocity universal joint 10 miniaturizations if described size surpasses 2.2 than (Dp/D).
In addition, as shown in figure 17,, set the external diameter of described outer cup 16 according to the external diameter of outer glass 16 cup portion and the characteristic straight line M of the relation between the outer/inner PCD.Under this situation, as Figure 14 and shown in Figure 15, the external diameter of establishing outer cup 16 is Do, and the external diameter (Do) of then described outer cup 16 preferably sets in 1.4≤(Do/Dp)≤1.8 scope than (Do/Dp) with the size of outer/inner PCD (Dp).
This be because: if described size than (Do/Dp) less than 1.4, then existence is crossed the thin rough sledding that causes intensity to reduce because of the wall thickness of outer cup 16, on the other hand, if described size surpasses 1.8 than (Do/Dp), then the external diameter of outer cup 16 can't be realized miniaturization greatly.
In addition, as shown in figure 18, according to interior ring 34 along second 18 the axial ring width and the characteristic straight line of the relation between the outer/inner PCD, set described in ring 34 inner ring width.Under this situation, the inner ring width of ring 34 is W in establishing, and then the inner ring width (W) of interior ring 34 preferably sets in 0.38≤(W/Dp)≤0.42 scope than (W/Dp) with the size of outer/inner PCD (Dp).
In addition, as shown in figure 19,, set the diameter of ball 28 according to the diameter of ball 28 and the characteristic straight line Q of the relation between the outer/inner PCD.Under this situation, as Figure 14 and shown in Figure 15, the diameter of establishing ball 28 is Db, and the diameter of then described ball 28 (Db) preferably sets in 0.2≤(Db/Dp)≤0.5 scope than (Db/Dp) with the size of outer/inner PCD (Dp).
This be because: if described size than (Db/Dp) less than 0.2, too small and the unfavorable condition that causes durability to reduce of the diameter that then has a ball 28, on the other hand, if described size surpasses 0.5 than (Db/Dp), then ball 28 is big and wall thickness outer cup 16 is thinner relatively, thereby causes intensity to reduce.In addition, keep the inner ball surface diameter and the outer spherical surface diameter of the retainer 38 of described ball 28 to set arbitrarily according to design separately.
Like this, by setting each size respectively, can keep each side characteristics such as intensity, durability, load capacity, the while can be carried out the setting corresponding to the various sizes of the constant velocity universal joint 10 of miniaturization.
Below, according to Figure 20～Figure 23, the relation of maintenance window 36 between the diameter (N) of opening length (WL) that makes progress in week and ball 28 that forms on the retainer 38 is elaborated.
As shown in figure 20, be formed with six first guiding groove 26a～26f on the aperture surface 24 of cup 16 outside, described six first guiding groove 26a～26f (arrow directions X) vertically extend, and the intervals of 60 degree that separate each other around the axle center are provided with, and described first guiding groove 26a～26f alongst (arrow directions X) has the S1 of rectilinear form portion that is made as one with curved shape portion.
On the outer diametric plane 35 of interior ring 34, be formed with and extend vertically and the second guiding groove 32a～32f identical with described first guiding groove 26a～26f quantity.Described each second guiding groove 32a～32f alongst (arrow directions X) has the S2 of rectilinear form portion that is made as one with curved shape portion, and described each S1 of rectilinear form portion, S2 are arranged on opposite direction along the arrow directions X.
As Figure 21 and shown in Figure 22, retainer 38 is a general toroidal, keeps six of each ball 28 to keep window 36 to form along the circumferentially spaced equal angles compartment of terrain of retainer 38.
As shown in figure 22, each keeps window 36 upwards to have opening length (WL) in the week of retainer 38, and the ratio (WL/N) of the diameter (N) of described opening length (WL) and ball 28 is set the relation of 1.30≤WL/N≤1.42 for.Each keeps window 36 to have the bight 36a that radius of curvature is R, and described radius of curvature R and the ratio R/N of the diameter N of described ball 28 are set at the relation of 0.23≤R/N≤0.45.
As shown in figure 22, in constant velocity universal joint 10, in respectively keeping in the window 36 of retainer 38, the opening length (WL) that the week of described retainer 38 makes progress and the diameter (N) of ball 28 are set at the relation of WL/N≤1.42.Therefore, retainer 38 can effectively be kept the circumferential lengths that keeps the post portion 136 between the window 36, does not need to set the wall thickness of described retainer 38 bigger, can increase the sectional area of described post portion 136.
Therefore, retainer 38 for example, does not need to set the inner ball surface diameter dimension less and set the outer spherical surface diameter dimension bigger, or axial width dimensions is increased, and just can improve the intensity of described retainer 38 effectively.
And in constant velocity universal joint 10, the opening length (WL) of maintenance window 36 and the diameter (N) of ball 28 are set the relation of 1.30≤WL/N for.Thus, can increase the opening area that respectively keeps window 36, can prevent effectively that the assembling of the bad and interior ring 34 of assembling of ball 28 is bad etc.Therefore, in constant velocity universal joint 10, can use simple structure easily to improve the operation of assembling operation.
In addition, the radius of curvature R of the bight 36a by will keeping window 36 and the diameter (N) of ball 28 are set the relation of 0.23≤R/N for, can reduce the major principal stress load of the post portion 136 between the described maintenance window 36, can improve the intensity of retainer 38.
On the other hand, by setting the relation of R/N≤0.45 for, can stop such situation to take place effectively: excessive because of the bight 36a that keeps window 36, and it is bad to cause ball 28 and interior ring 34 to produce assembling.
In addition, in constant velocity universal joint 10, first guiding groove 26a～26f alongst has the S1 of rectilinear form portion, and simultaneously, second guiding groove 32a～32f alongst has the S2 of rectilinear form portion.Therefore can be effectively must be bigger with the maximum actuation angular setting of constant velocity universal joint 10.
And as shown in figure 23, described first guiding groove 26a～26f and second guiding groove 32a～32f also can form alongst only has curved shape portion.
Claims (4)
1. constant velocity universal joint, it comprises:
Exterior part (16), one is open-ended, and this exterior part (16) is connected with a side in two axles that intersect, and has the aperture surface that is made of sphere, and, be formed with a plurality of first guiding grooves (26a～26f) of extension vertically at this exterior part (16);
In ring (34), it is connected with the opposing party in described two axles, and be formed with extension vertically, with described first guiding groove (second guiding groove that 26a～26f) quantity is identical (32a～32f);
Ball (28), (26a～26f) and described second guiding groove (between the 32a～32f), are used at described first guiding groove (26a～26f) and described second guiding groove (transmitting torque between the 32a～32f) rollably to be disposed at described first guiding groove; And
Retainer (38), it is formed with the maintenance window that is used to take in described ball (28),
Wherein,
(26a～26f) is formed at described exterior part (16) to first guiding groove, and (26a's～26f) is curve-like along axial longitudinal section to described first guiding groove, second guiding groove (32a～32f) be formed at described in ring (34), and (32a's～32f) is curve-like along axial longitudinal section to described second guiding groove, the described first guiding groove (centre of curvature (H) of 26a～26f) and the described second guiding groove (centre of curvature (R) of 32a～32f), be disposed at such position: the position that has been offset the distance (T) that equates from described sphere centre (K) vertically respectively in the opposite direction
((side-play amount (T) of 32a～32f) is set for: making their ratio (T/N) is V, and satisfies relation: 0.12≤V≤0.14 for 26a～26f) for the diameter (N) of described ball (28) and described first and second guiding grooves.
2. constant velocity universal joint according to claim 1 is characterized in that,
Be formed at described exterior part (16) first guiding groove (26a～26f) form: it forms single circular shape with axial cross section of quadrature, and described first guiding groove (26a～26f) be contacted with a bit with described ball (28),
Be formed at described in second guiding groove of ring (34) (32a～32f) form: it forms the elliptic arc shape with axial cross section of quadrature, and described second guiding groove (32a～32f) be contacted with 2 points with described ball (28).
3. constant velocity universal joint according to claim 2 is characterized in that,
(groove radius (M) on the cross section of 26a～26f) and second guiding groove (groove radius (P, Q) on the cross section of 32a～32f), are set in respectively in 0.51～0.55 the scope with the ratio of the diameter (N) of ball (28) described first guiding groove, and, first guiding groove (26a～26f) is that benchmark is made as zero degree with the contact angle of ball (28) with plumb line (L), and second guiding groove (contact angle (α) of 32a～32f) and ball (28) be that benchmark is set in the scopes that 13 degree～22 spend with plumb line (L).
4. constant velocity universal joint according to claim 3 is characterized in that,
(32a～32f) contact angle (α) with ball (28) is that benchmark is set in the scope of 15 degree～20 degree with plumb line (L) to described second guiding groove.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004008524 | 2004-01-15 | ||
| JP2004008524A JP4681235B2 (en) | 2004-01-15 | 2004-01-15 | Constant velocity joint |
| JP2004194274 | 2004-06-30 | ||
| JP2004192637 | 2004-06-30 | ||
| JP2004194230 | 2004-06-30 | ||
| JP2004358176 | 2004-12-10 | ||
| JP2005003787 | 2005-01-11 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800024522A Division CN100476227C (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101493119A true CN101493119A (en) | 2009-07-29 |
Family
ID=34821827
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009100080293A Pending CN101493119A (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
| CNA2009100080306A Pending CN101493120A (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
| CNB2005800024522A Expired - Fee Related CN100476227C (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
Family Applications After (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009100080306A Pending CN101493120A (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
| CNB2005800024522A Expired - Fee Related CN100476227C (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4681235B2 (en) |
| CN (3) | CN101493119A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103453032A (en) * | 2012-06-04 | 2013-12-18 | 现代自动车株式会社 | Constant velocity joint for vehicle |
| US11493092B2 (en) | 2017-08-02 | 2022-11-08 | Thk Co., Ltd. | Speed-reducing or -increasing apparatus |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007023354B4 (en) * | 2007-05-18 | 2009-10-01 | Gkn Driveline Deutschland Gmbh | Ball synchronized sliding joint with low displacement forces |
| JP5130121B2 (en) * | 2008-06-05 | 2013-01-30 | サンデン株式会社 | Swing plate type variable capacity compressor |
| JP5420369B2 (en) * | 2009-10-08 | 2014-02-19 | Ｎｔｎ株式会社 | Fixed constant velocity universal joint |
| US8684850B2 (en) * | 2010-04-02 | 2014-04-01 | Ntn Corporation | Constant velocity universal joint |
| DE112013007324B4 (en) * | 2013-08-09 | 2019-07-18 | Hyundai Wia Corporation | Ball constant velocity joint for vehicles |
| CN104455055B (en) * | 2014-10-09 | 2017-02-22 | 上海纳铁福传动系统有限公司 | Ball cage type constant velocity universal joint |
| CN117128251B (en) * | 2023-10-27 | 2024-01-30 | 万向钱潮股份公司 | Ball cage universal joint for vehicle rear drive and vehicle |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19808029C1 (en) * | 1998-02-26 | 1999-12-30 | Gkn Automotive Ag | Ball joint for motor vehicle wheel drive |
| DE19941142C2 (en) * | 1999-08-30 | 2002-05-02 | Gkn Automotive Gmbh | Ball constant velocity joint |
| JP4834921B2 (en) * | 2001-01-30 | 2011-12-14 | 日本精工株式会社 | Rotation support device for pulley for compressor |
| JP2002372067A (en) * | 2001-06-18 | 2002-12-26 | Ntn Corp | Constant velocity universal coupling for propeller shaft |
-
2004
- 2004-01-15 JP JP2004008524A patent/JP4681235B2/en not_active Expired - Fee Related
-
2005
- 2005-01-13 CN CNA2009100080293A patent/CN101493119A/en active Pending
- 2005-01-13 CN CNA2009100080306A patent/CN101493120A/en active Pending
- 2005-01-13 CN CNB2005800024522A patent/CN100476227C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103453032A (en) * | 2012-06-04 | 2013-12-18 | 现代自动车株式会社 | Constant velocity joint for vehicle |
| US11493092B2 (en) | 2017-08-02 | 2022-11-08 | Thk Co., Ltd. | Speed-reducing or -increasing apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1910380A (en) | 2007-02-07 |
| JP2005201371A (en) | 2005-07-28 |
| CN101493120A (en) | 2009-07-29 |
| JP4681235B2 (en) | 2011-05-11 |
| CN100476227C (en) | 2009-04-08 |
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Application publication date: 20090729 |