CN1837632A

CN1837632A - Fixed-type constant-velocity universal joint

Info

Publication number: CN1837632A
Application number: CNA2006100717927A
Authority: CN
Inventors: 星野学; 中川亮; 登根宏; 菅沼和三郎
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2005-03-22
Filing date: 2006-03-22
Publication date: 2006-09-27
Anticipated expiration: 2026-03-22
Also published as: CN100526667C; JP2006266329A

Abstract

Internal dimensions for fixed-type constant velocity universal joints are defined to optimize the geometry of the components of the joints and to readily achieve a larger operating angle of the joints. In the joint, the track grooves of an outer ring and an inner ring are tapered by an angle not exceeding 12 DEG . The ratio (f/PCR) of the cage offset amount f to PCR is greater than 0 and smaller than or equal to 0.12. The ratio (Do/d) of the cage outer diameter (Do) to the ball diameter (d), the ratio (t/d) of the cage wall thickness (t) to the ball diameter (d), and the ratio (w/d) of the cage width (w) to the ball diameter (d) are such that 3.9<=Do/d<=4.1, 0.31<=t/d<=0.34, and 1.8<=w/d<=2.0, respectively. The end of the spherical outer surface of the cage adjacent to the open end is axially extended, and the end of the spherical inner surface of the cage adjacent to the open end is tapered so that the tapered surface has an increasing diameter toward the end of the spherical outer surface adjacent to the open end. Part of the spherical outer surface of the cage is cut on the open end side of pockets, and the outer diameter of the cage across the two opposing planer cut faces is smaller than the spigot diameter of the outer ring.

Description

Fixed-type constant-velocity universal joint

Technical field

The present invention relates to a kind of fixed-type constant-velocity universal joint.Constant velocity joint is used for the power transmission of automobile and various industrial machineries, and with Constant Angular Velocity moment of torsion is transferred to driven shaft from driving shaft.Known two types constant velocity joint: fixed, it only allows angular displacement; And slideable, it allows angular displacement and axial displacement.

Background technique

A kind of typical fixed-type constant-velocity universal joint comprises with lower member: the mode with transfer of torque is connected to initiatively or the socket member of driven shaft; Be connected to the spigot member of driven or driving shaft in the mode of transfer of torque; Place between the inside and outside joint member a plurality of balls with transfer of torque; And ball remained on initiatively and driven shaft between the bisection section at angle in cage ring.

Recently, owing to having been produced, the concern aspect vehicle safety the time is guaranteed in collision has the more design of the automobile of major axis distance.For preventing the increase of incident turning radius, need increase the steering angle of front-wheel by the operating angle that increases fixed-type constant-velocity universal joint, wherein said fixed-type constant-velocity universal joint is as the jointing in the automobile driving shaft.

In order to increase the operating angle of fixed-type constant-velocity universal joint, proposed in inside and outside joint member, to form rail slot with conical lower portion, thereby corresponding groove has formed the ball orbit that ball rolls therein together (for example referring to the open No.2001-153149 of Japan Patent, No.2001-304282, No.2001-349332).

In the trial of existing increase fixed-type constant-velocity universal joint operating angle, do not think that the cone angle of the rail slot of determining inside and outside joint member is a particular importance.

Although all having, each fixed-type constant-velocity universal joint of describing in the above-mentioned open file it is characterized in that the interior of taper rail slot and socket member, wherein said taper rail slot allows bigger joint operating angle, but the trend that present joint tends in light weight and compact structure has limited the external diameter of socket member, if the cone angle of rail slot increases, the wall thickness of socket member will reduce inevitably so, cause the intensity of socket member to reduce.The increase of rail slot cone angle also causes being increased by the load that the ball that is contained in the cage ring is applied on cage ring depression (cage pocket) sidewall.Be applied to the load on the cage ring depression and the cone angle of rail slot and increase (Figure 22) pro rata.

In the disclosed fixed-type constant-velocity universal joint, the cage ring side-play amount is enough big in the open No.2001-153149 of Japan Patent, thereby by being in its outermost locations or phase place (phase angle =0 °; The load that ball Fig. 3) is applied on the cage ring depression can keep less.But, in another traditional constant velocity universal, the load that ball applied that is in 0 ° of phase place generally increases along with the increase of joint operating angle.

Summary of the invention

An object of the present invention is to determine to be suitable for the best Inner Dimension of fixed-type constant-velocity universal joint, thereby make the geometrical construction optimization of each parts of joint, easily obtain bigger joint operating angle then.

(1) the present invention realizes this purpose by the upper limit of the optimum taper angle of the rail slot of joint member inside and outside determining in all Inner Dimensions of fixed-type constant-velocity universal joint.

Exactly, a kind of fixed-type constant-velocity universal joint of the present invention comprises:

Socket member with spherical inside surface, described socket member has opening end and a plurality of rail slots that are formed on this spherical inside surface, and each rail slot is equidistantly separated towards the opening end extension and along the circumference of spherical inside surface along axial direction;

The spigot member, described spigot member has spherical outer surface and is formed on a plurality of rail slots on the spherical outer surface corresponding to the rail slot of socket member, and each rail slot extends and equidistantly separates along the circumference of spherical outer surface along axial direction;

Be contained in each rail slot of inside and outside joint member so that a plurality of balls of transfer of torque; And

Be used to keep the cage ring of a plurality of balls, this cage ring is arranged between the spherical outer surface of the spherical inside surface of socket member and spigot member, and this cage ring has spherical inside surface and spherical outer surface,

Wherein:

The spherical outer surface center of cage ring oppositely is offset the distance that equates with the center of the spherical inside surface of cage ring along axial direction from the joint center;

Observe in the longitudinal section, the wall of cage ring is thicker in the zone of contiguous socket member opening end, and thinner in the zone away from opening end;

Each rail slot of socket member all have the regional neutral line of neighbouring open end be tapered so that the degree of depth of groove towards bottom that opening end increases;

Thereby each rail slot of spigot member all have away from the regional neutral line of opening end the degree of depth of the groove that is tapered towards bottom that the end of the spigot member relative with opening end reduces; And

The cone angle of the rail slot of inside and outside joint member is set at 12 ° or littler.

According to the present invention, each rail slot of inside and outside joint member is taper, thereby can easily increase the operating angle of fixed-type constant-velocity universal joint by making the attenuation of socket member, and do not increase the external diameter of socket member cause the intensity of socket member or workability impaired.In order to determine the best Inner Dimension of fixed-type constant-velocity universal joint, this application has has been studied effect and the effect that forms the taper rail slot at all Inner Dimensions of fixed-type constant-velocity universal joint, thereby the upper limit of having determined the optimum taper angle of rail slot is 12 °.

This application has is studied through utilizing static internal force analysis and Finite Element Method (FEM), to determine the optimum range of rail slot cone angle.The optimum range of cone angle must be determined like this: make that forming taper can not influence the required intensity of joint, serviceability and other material conditions.Whether evaluated and tested the sample with different cone angle, it is consistent with the determined best angle of analysis to understand the result thus.

The upper limit (that is, 12 °) of the optimum range of the rail slot by determining inside and outside joint member can easily increase the operating angle of fixed-type constant-velocity universal joint, and can not reduce the intensity and the workability of joint.This allows vehicle front that bigger steering angle is arranged, thereby helps the turning radius that keeps less, has satisfied for having the more demand of the automobile of major axis distance, and this automobile becomes more and more popular owing to the Security to crash-resistant of its improvement becomes.

(2) the present invention is by being evaluated at the internal force that puts on joint inside under the situation that has formed the taper rail slot, especially put on the load of depression, and consider the influence of load, and determine that at all Inner Dimensions of fixed-type constant-velocity universal joint the optimum geometry of cage ring realizes above-mentioned purpose for joint strength.

Wherein:

Each rail slot of socket member all have the regional neutral line of neighbouring open end be tapered so that the degree of depth of groove towards the bottom that opening end increases;

Cage ring external diameter (Do) with respect to the ratio (Do/d) of ball diameter (d) in 3.9 to 4.1 scope, cage ring wall thickness (t) with respect to the ratio (t/d) of ball diameter (d) in 0.31 to 0.34 scope, and cage ring width (w) with respect to the ratio (w/d) of ball diameter (d) in 1.8 to 2.0 scope.

Though for conventional fixed formula constant velocity joint, cage ring external diameter (Do) is 3.7≤Do/d≤3.8 with respect to the ratio (Do/d) of ball diameter (d), for joint according to the present invention, same ratio falls in the scope of 3.9≤Do/d≤4.1.This is owing to following reason: along with operating angle increases, the total amount that ball moves along the cage ring axis in depression also increases (referring to Fig. 3, wherein " m " represents the point of outermost radial outside, contact with cage ring at this some place ball, the radially the most inboard point of " n " expression contacts with cage ring at this some place ball).The lower limit of cage ring external diameter is automatically to determine, even because joint during with the operating angle work of maximum the point of contact of ball and cage ring also must remain in the cage ring scope.On the other hand, if the cage ring external diameter is too big, the degree of depth of the rail slot of socket member will be not enough, can reduce the serviceability of socket member in this case.Therefore, the upper limit of cage ring external diameter must be determined like this: make it possible to guarantee minimum serviceability.

Though for conventional fixed formula constant velocity joint, cage ring wall thickness (t) is 0.24≤t/d≤0.27 with respect to the ratio (t/d) of ball diameter (d), for joint according to the present invention, same ratio falls in the scope of 0.31≤t/d≤0.34.This is owing to following reason: cage ring wall thickness (t) is limited by cage ring external diameter (Do), with next definite the same by above-mentioned Do/d value.The cage ring internal diameter is determined by following principle: the same with the situation of above-mentioned Do/d value, the upper limit of cage ring internal diameter is determined the feasible point of contact that has ball and cage ring, and lower limit is determined and makes that the rail slot degree of depth of spigot member is enough dark, promptly guarantees serviceability.

Though for conventional fixed formula constant velocity joint, cage ring width (w) is 1.7≤w/d≤1.9 with respect to the ratio (w/d) of ball diameter (d), for joint according to the present invention, same ratio falls in the scope of 1.8≤w/d≤2.0.This is owing to following reason: the modulus of section of cage ring depression sidewall must be in particular range, so that make the stress that is applied to sidewall owing to the load that increases remain on the level that equates with conventional fixed formula constant velocity joint or be lower than stress in the conventional fixed formula constant velocity joint.Therefore, must adjust the modulus of section, because interior external diameter has been determined separately by the value of above-mentioned Do/d and t/d by the width that changes cage ring.

By selecting width as minimum cage ring width, the stress that is applied when wherein using this width become with conventional fixed formula constant velocity joint in observed stress suitable, the intensity of joint can maintain on the level suitable with conventional fixed formula constant velocity joint.The upper limit of cage ring width is definite like this: make that poor the scope of standard code (that is, by) between the upper limit of width and the lower limit is identical with the determined scope of corresponding conventional fixed formula constant velocity joint.Too big width can cause weight to increase and the cost of material improves.

(3) the present invention is by in the loss of the reduction of considering joint strength and serviceability and torque transfer, determine that at all Inner Dimensions of fixed-type constant-velocity universal joint the optimum geometry of cage ring realizes above-mentioned purpose so that cage ring can easily be assembled with the socket member.

Wherein:

Part cage ring spherical outer surface is cut in the open end side of two relative depressions at least, crosses the casing diameter of the cage ring external diameter of two relative cutting parts less than the socket member.

In the present invention, part cage ring spherical outer surface is cut in the open end side of two relative depressions at least.In this case, cage ring spherical outer surface in the open end side of depression can be cut like this: make the point of contact that has cage ring and ball when joint when the maximum functional angle is worked, in the rotating shaft of this point of contact place socket member and the rotating shaft angulation maximum of spigot member.

Exist the point of contact of cage ring and ball to be equivalent to phase place (phase angle =0 °) Shi Buhui that is in most possible disengaging cage ring depression when ball situation about breaking away from takes place.Although be that at least one pair of relative depression is carried out the part cutting, also can be to all relative depressions to cutting.

To the reasons are as follows that at least two relative depressions cut: in the assembly process of cage ring and socket member, cage ring at first keeps inserting in the socket member perpendicular to the mode of socket member axis with its axis.Insert after the socket member, cage ring turns over 90 °, thereby its axis is aimed at the socket member axis.If at least two relative depressions are cut and cross the casing diameter of the cage ring external diameter of these two cutting parts less than the socket member, it is possible cage ring being inserted the socket member so.

Said structure of the present invention, wherein a part of cage ring spherical outer surface at the open end side place of at least two relative depressions is cut, and cross the casing diameter of the cage ring external diameter of two relative cutting parts less than the socket member, make it possible to when guaranteeing cage ring intensity, thereby design the cage ring that casing diameter that a kind of external diameter reduces the socket member also reduces.This structure allows big relatively angle of contact (spherical angle), thereby helps the assembling of cage ring and socket member, and can not reduce intensity and the serviceability or the loss torque transfer of joint.Therefore, the quality of joint and the assembling of joint have been improved.

When being higher than the dynamic torsional torque when being applied to this joint of allowing level, the distortion of the rail slot of inside and outside joint member causes rising on the edge of rail slot.Have such coherence between the groove zone of pressurized and the lifting height that is caused, promptly rail slot is narrow more then rises highly more.

Therefore, along with the cone angle increase of rail slot, lifting height tends to higher.The sphere of this rising and cage ring has interfered and has limited moving of cage ring.This may cause stress to be applied on the edge of the depression that holds ball of cage ring circumference setting and cause splitting and cracked.

(4) the present invention realizes above-mentioned purpose by the optimum geometry of determining cage ring in all Inner Dimensions of fixed-type constant-velocity universal joint, and wherein this optimum geometry is considered rising and the interference between the cage ring sphere that forms along the rail slot edge and is applicable to and prevents that excessive stress is applied on the edge.

Exactly, fixed-type constant-velocity universal joint of the present invention comprises:

Wherein:

A plurality of depressions are along the circumference setting of cage ring and hold ball, and the depression edge is a fillet on the spherical inside surface side of cage ring and in the spherical outer surface side at least one.

In such fixed-type constant-velocity universal joint, preferably, the edge of the depression that holds ball of cage ring is a fillet on the spherical inside surface side of cage ring, mainly occurs between the rising and isolation channel spherical inside surface that forms along the rail slot of spigot member because interfere.But, the depression edge can be a fillet on the spherical outer surface side of cage ring also.Most preferably, the depression edge all is a fillet on the spherical inside surface side of cage ring and spherical outer surface side.

Terminology used here " fillet " is meant the spherical inside surface that connects cage ring smoothly or the continuous sphere of spherical outer surface and depression end face.Fillet can form like this: making its cross section is single circular arc or the combination circular arc be made up of level and smooth a plurality of circular arcs that link to each other each other.

The edge of this its pocket has prevented that in the structure that on the spherical inside surface side of cage ring or the spherical outer surface side is fillet the depression edge splits and fragmentation when the sphere of the rising that forms along the rail slot edge and cage ring interferes.Therefore, guaranteed the intensity of cage ring.

(5) the present invention is by determining that at all Inner Dimensions of fixed-type constant-velocity universal joint the optimum geometry of cage ring realizes above-mentioned purpose, this optimum geometry is considered along the rising of rail slot edge formation and the interference between the cage ring sphere, and is suitable for preventing that excessive stress is applied on the depression in the depression corner away from the joint opening end.

Wherein:

Each rail slot of socket member have all that regional neutral line at neighbouring open end little by little attenuates so that the degree of depth of groove towards bottom that opening end increases;

Along the circumference setting of cage ring and a plurality of rectangular substantially depression that holds ball its away from the radius of curvature of the corner of socket member opening end greater than the corner radius at neighbouring open end place and less than the ball radius.

This wherein away from the radius of curvature of the depression corner of joint opening end greater than the radius of curvature of the corner of neighbouring open end and less than the structure of ball radius, can reduce when the rising that forms along the rail slot edge and cage ring sphere interfere being applied to away from the stress on the depression turning of joint opening end.Thereby, can optimize away from the stress equilibrium between the turning of the depression turning of joint opening end and adjacent joint opening end.This has guaranteed the intensity of cage ring.

If depression is equal to or less than radius of curvature in the corner of adjacent joint opening end in the radius of curvature away from the corner of joint opening end, just be difficult to reduce to be applied to overstress away from the turning of opening end.If be equal to or greater than the ball radius, then can interfere with depression turning when ball ball when column piece between the depression contacts away from the joint opening end in radius of curvature away from the depression corner of joint opening end.

(6) taper rail slot of the present invention can cause that load is applied on the depression of joint.When cage ring rubs the socket member when this load is applied on the depression, produced the heat that can cause serviceability reduction or torque transfer loss.Therefore, the present invention is by determining the optimum geometry of cage ring at all Inner Dimensions of fixed-type constant-velocity universal joint, and this optimum geometry has been considered the reduction of this serviceability that causes owing to heating or the loss of torque transfer.

Wherein:

Extend vertically the end of the cage ring spherical outer surface of adjacent joint opening end, and the end of the cage ring spherical inside surface of adjacent joint opening end forms such taper: make the diameter of the conical surface increase towards the end of the spherical outer surface of adjacent joint opening end.

According to the present invention, extend vertically the end of the cage ring spherical outer surface of adjacent joint opening end.Exactly, certain amount is extended in the end of the cage ring spherical outer surface of adjacent joint opening end, to prevent that the axle that is connected to the spigot member when joint when the maximum functional angle is worked from interfering with the cage ring end of adjacent joint opening end, the angle maximum of the rotating shaft of the rotating shaft of socket member and spigot member formation when being in the maximum functional angle.

When certain amount is extended in the end of the cage ring spherical outer surface of adjacent joint opening end, in the time of can preventing that the axle and the cage ring end of adjacent joint opening end from interfering, hope is apered to the end of the cage ring spherical inside surface of adjacent joint opening end to be equal to or greater than the socket member to become half cone angle of maximum functional angle with the spigot member.This cone angle preferably is equal to or greater than half of maximum functional angle of joint, because when joint during with bigger operating angle work, the spherical inside surface of the spherical outer surface of cage ring and socket member keeps in touch in abundant big area.If cone angle is less than half of joint maximum functional angle, then axle will interfere with the cage ring tapered end of adjacent joint opening end.

The fact that the spherical inside surface of the spherical outer surface of cage ring and socket member keeps in touch in fully big area has been guaranteed can force the opening end of cage ring towards joint when joint ball when the maximum functional angle is worked.The reduction of the serviceability that the thermal conductance that is produced in the time of therefore, can making the end of the cage ring spherical outer surface of adjacent joint opening end fiercely rub the spherical inside surface of socket member causes or the minimization of loss of torque transfer.This structure has also been guaranteed maximum cage ring rigidity, thereby has also improved the intensity of cage ring.

Therefore, can easily increase the operating angle of joint.Big steering angle allows vehicle front that bigger steering angle is arranged, thereby, help the turning radius that keeps little.This has satisfied for being combined with than major axis apart from the requirement with the recent emerging automobile of guaranteeing big passenger space.

(7) the present invention is directed to all Inner Dimensions of fixed-type constant-velocity universal joint and determine optimum range, realize above-mentioned purpose thus at rail slot that reduces to be applied to inside and outside joint member and the required factor of load that is on the cage ring of 0 degree phase state.This studies these factors by internal force analysis and finishes.

Wherein:

The distance that the centre of curvature of the rail slot of the centre of curvature of the rail slot of socket member and spigot member departs from the joint center is the cage ring side-play amount, the side-play amount at the center of the misalignment cage ring spherical inside surface that this cage ring side-play amount is the cage ring spherical outer surface, thus the orbit displacement amount is zero.

This structure has reduced outer loop orbit load, or is applied to load on the rail slot of socket member during in 0 ° of phase place when the joint.Also reduced interior loop orbit load, or be applied to load on the rail slot of spigot member during in 0 ° of phase place when the joint.When joint during, be applied to load on the cage ring depression end of adjacent joint open end for minimum in 0 ° of phase place.This means that such fixed-type constant-velocity universal joint height is applicable to bigger operating angle work.

If the centre of curvature of the spherical inside surface of socket member departs from the centre of curvature of the rail slot of socket member, if perhaps the centre of curvature of the spherical outer surface of spigot member departs from the centre of curvature of the rail slot of spigot member, the degree of depth of rail slot will reduce towards the dark side of socket member so.Thereby the ball that is arranged in the inner side of rail slot when joint during with the work of bigger operating angle can releasing slots.

Make that by constructing joint like this orbit displacement amount is zero, then the degree of depth of rail slot will can not reduce towards the dark side of socket member.Thereby, prevented to be in ball in the inner side of rail slot at joint releasing slots during with bigger operating angle work.

What wish is, in the fixed-type constant-velocity universal joint described in (1) to (7), suppose that the cage ring side-play amount between the center of the center of cage ring spherical outer surface and spherical inside surface is f, and the centre of curvature of the centre of curvature of the rail slot of connection socket member or the rail slot of spigot member and the line segment length at ball center are PCR, then the value of ratio f/PCR is greater than zero and be less than or equal to 0.12

Setting the cage ring side-play amount is favourable for bigger value, because can improve the intensity of cage ring by the thickness that increases the cage ring open end, wherein the spigot member inserts from this opening end.By increasing the thickness of cage ring open end, the cage ring depression can limit ball and will prevent that they break away from the socket member from opening end when joint is worked with big operating angle.

But, if the cage ring skew is too big, the circumferential displacement of the ball in the cage ring depression becomes big so, thereby must increase along the cage ring pocket sizes of cage ring circumference, so that guarantee the proper motion of ball.Therefore, the width of the column piece of cage ring is reduced, and causes cage ring intensity to reduce.In addition, reduce away from the cage ring thickness in the zone of its opening end.This also causes cage ring intensity to reduce.

Thereby, do not wish that the cage ring side-play amount is too big, and the optimum range that has the cage ring side-play amount according to the advantage and the balance between the cage ring intensity of cage ring side-play amount.Therefore but, the optimum range of cage ring side-play amount can change according to the size of joint, must determine by considering to have reflected the basic joint yardstick of joint size.

For this reason, adopted cage ring side-play amount f with respect to the centre of curvature of the rail slot of the centre of curvature of the rail slot that connects the socket member or spigot member and the ratio f/PCR of the length PCR of the line segment at ball center.

Thereby, suppose that the cage ring side-play amount is f, and the length of centre of curvature and the line segment at ball center that connects the rail slot of the centre of curvature of rail slot of socket member or spigot member is PCR, and the cage ring side-play amount in the said structure preferably is set at the value that makes ratio f/PCR greater than zero and be less than or equal to 0.12.Because cage ring side-play amount f is the function of seeing the cage ring wall thickness difference from the longitudinal section, so preferably by considering that this value determines.

If ratio f/PCR greater than 0.12, the problems referred to above about intensity can occur so.On the contrary, if ratio is less than or equal to 0, can lose the advantage of cage ring side-play amount so.When the value of cage ring side-play amount is equal to or less than zero, be used for when joint is worked with big operating angle, preventing that the ball cage ring skew of the point of contact disengaging cage ring depression of joint member open end outside from can not reach the purpose that it is wanted.Therefore, the optimum range of cage ring side-play amount f makes ratio f/PCR be equal to or less than 0.12, so that guarantee the intensity and the serviceability of cage ring.

To the fixed-type constant-velocity universal joint described in (7), the rail slot of inside and outside joint member is preferably finished by cold forging in above (1).Finish the taper rail slot in the cold forging mode and assist in removing mould.Thereby the application of cold forging has not only improved workability but also has reduced manufacture cost.

Description of drawings

Fig. 1 is the sectional arrangement drawing of expression according to an embodiment of fixed-type constant-velocity universal joint of the present invention.

Fig. 2 is the enlarged view of the critical piece of joint shown in Figure 1.

Fig. 3 is the sectional arrangement drawing of expression joint shown in Figure 1 when its maximum functional angle work.

Fig. 4 is the drawing in side sectional elevation of expression cage ring shown in Figure 1.

Fig. 5 is the sectional arrangement drawing of expression according to another embodiment of fixed-type constant-velocity universal joint of the present invention.

Fig. 6 is the expression sectional arrangement drawing of joint when the maximum functional angle is worked shown in Figure 5.

Fig. 7 is illustrated in the sectional arrangement drawing that has the cage ring of rounded edges on its spherical inside surface.

Fig. 8 is illustrated in the sectional arrangement drawing that has the cage ring of rounded edges on its spherical inside surface and the spherical outer surface.

Fig. 9 is the vertical figure that is illustrated in the cage ring that has rounded edges on its spherical inside surface and the spherical outer surface, its pocket in the radius of curvature of the corner of the thin side of cage ring greater than radius of curvature in the corner of the thicker side of cage ring.

Figure 10 is illustrated in the part amplification view that has the depression at turning on thin side and the thicker side.

Figure 11 is illustrated in the part amplification view that the corner that approaches a side has the depression of minimum profile curvature radius.

Figure 12 is illustrated in the part amplification view that the corner that approaches a side has the depression of maximum curvature radius.

Figure 13 is a side view of seeing the cage ring shown in Fig. 5 from a side relative with the outer ring opening end.

Figure 14 is the cross-sectional view of view shown in Figure 13.

Figure 15 is a side view of seeing outer shroud from open end side, illustrates the fit of cage ring and outer shroud.

Figure 16 a is the sectional arrangement drawing that expression is used for the cage ring of joint shown in Figure 5.

Figure 16 b is the sectional arrangement drawing that expression is used for the cage ring of joint shown in Figure 1.

Figure 17 is the plotted curve of the relation between the cone angle of expression joint strength and rail slot.

Figure 18 is the cone angle of expression rail slot and the plotted curve of the relation between the f/PCR.

Figure 19 is the plotted curve of expression load at 0 degree phase place place when applying rated torque.

Figure 20 is illustrated under the maximum depression load-up condition about the comparative example that is applied to the stress on the depression wall and the comparative graph between the example.

Figure 21 is the comparative graph of the depression load (maximum) between expression comparative example and the example.

Figure 22 is the plotted curve of the relation between expression cone angle and the depression load.

Embodiment

With reference to figure 1, fixed-type constant-velocity universal joint comprises outer shroud 10, interior ring 20, ball 30 and cage ring 20.Fixed-type constant-velocity universal joint connects needs connected two axles.For example, the driven shaft (not shown) is connected to outer shroud 10, and driving shaft is connected to this outer shroud, thus when two axles mutual when angled moment of torsion from the driving shaft constant speed transfer to driven shaft.State when Fig. 1 represents that operating angle θ that the rotating shaft X of outer shroud 10 is become with the rotating shaft Y of interior ring 20 is 0 °, and Fig. 3 represents the state of operating angle θ when its maximum value.

Form by mouth 16 with the stem portion (not shown) that the mode of transfer of torque is connected to driving shaft as the outer shroud 10 of socket member.Mouth 16 comes down to have the cup of opening end and has spherical inside surface, this spherical inside surface have formed thereon a plurality ofly extend vertically, the circumferential rail slot 14 opened of equi-spaced apart.Each rail slot 14 stretches to the opening end 18 of mouth 16.

Interior ring 20 as the spigot member has spherical outer surface 22, and this spherical outer surface comprises the rail slot 24 that a plurality of extensions vertically formed thereon, circumferential equi-spaced apart are opened.Each rail slot 24 is by ring 20 in axially cutting is passed.Interior ring 20 has the splined hole 26 that interior ring is connected to driving shaft in the mode of transfer of torque.

The rail slot 14 of outer shroud 10 forms corresponding to the rail slot 24 of interior ring 20.Each

groove

14,24 to correspondence has formed ball orbit, and ball 30 rollably is contained in this ball orbit so that transfer of torque.In other words, ball 30 is arranged between the rail slot 24 of the rail slot 14 of outer shroud 10 and interior ring 20, so that moment of torsion is transferred to outer shroud from interior ring.Ball 30 is contained in along in the corresponding depression 46 of the circle distribution of cage ring 40.The quantity of ball 30 and

rail slot

14,24 can be any suitable quantity, for example, and 6 or 8.

Cage ring 40 is arranged between outer shroud 10 and the interior ring 20 slidably, and have with the spherical inside surface 12 contacted spherical outer surfaces 42 of outer shroud 10 and with the spherical outer surface 22 contacted spherical inside surface 44 of interior ring 20.The curvature of the curvature of the spherical inside surface 12 of outer shroud 10 and the spherical outer surface 42 of cage ring 40 has identical center (among Fig. 2 with ' O ₄' expression).Similarly, the curvature of the spherical inside surface 44 of the curvature of the spherical outer surface 22 of interior ring 20 and cage ring 40 has identical center (among Fig. 2 with ' O ₃' expression).In institute's drawings attached, for clarity, the gap not to scale (NTS) between the spherical inside surface 12 of outer shroud 10 and the spherical outer surface 42 of cage ring 40 illustrates, and the gap between the spherical outer surface 22 of interior ring 20 and the spherical inside surface 44 of cage ring 40 also is like this.

Each rail slot 14 of outer shroud 10 comprises 14a of arc portion and the straight 14b of portion, and wherein the 14a of arc portion is formed on dark side, perhaps is formed on the side away from the opening end of mouth 16, and the straight 14b of portion is formed on a side of opening end.The bottom of each rail slot 14 in the zone of neighbouring open end 18 with the angle [alpha] linear tapered, thereby the degree of depth of groove increases towards opening end 18.

Each rail slot 24 of interior ring 20 comprises 24a of arc portion and the straight 24b of portion, and wherein the 24a of arc portion is formed on the open end side of outer shroud 10, and the straight 24b of portion is formed on the side away from opening end.The bottom of each rail slot 24 in away from the zone of opening end with the angle [alpha] linear tapered, thereby the degree of depth of groove increases towards the end relative with opening end.

This joint has as shown in Figure 2 structure to guarantee the big operating angle θ of joint.Exactly, as shown in Figure 2, the centre of curvature O of the rail slot 14 of outer shroud 10 ₁The center O that departs from spherical inside surface 12 ₃Distance be F, and the centre of curvature O of the rail slot 24 of interior ring 20 ₂The center O that departs from spherical outer surface 22 ₄Identical apart from F (that is orbit displacement amount).Centre of curvature O ₁With centre of curvature O ₂On the direction of axial opposed, depart from corresponding sphere centre.

Similarly, the centre of curvature O of the spherical outer surface 42 of cage ring 40 ₃Centre of curvature O with the spherical inside surface 44 of cage ring 40 ₄Depart from axial direction that the center O of joint equates apart from f (that is cage ring side-play amount).

As shown in Figure 3, when the rotating shaft X of outer shroud 10 becomes operating angle θ (being different from 0 °) with the rotating shaft Y of interior ring 20, and all balls 30 all are in the midplane P of joint, in the time of promptly and in the perpendicular plane of the bisector of the angle θ between two rotating shaft X and the Y, the centre distance two rotating shaft X of each ball and the distance of Y equate, thereby rotation is transferred to rotating shaft X by constant speed ground from rotating shaft Y.The intersection point of joint midplane P and rotating shaft X and Y is represented by the joint center O.In fixed-type constant-velocity universal joint, the joint center O is fixed on random working angle θ.

Each the bar ball orbit that is formed by the corresponding rail slot in

pairs

12,24 of outer shroud 10 and interior ring 20 has the shape of wedge like, and wherein the mouth 16 of outer shroud 10 relatively broadens gradually near the opening end of inboard narrow end towards outer shroud 10.When joint during with transfer of torque, impels ball to be applied on the ball 30 to the power of wide end motion (representing with blank arrow among Fig. 2) from the narrow end of wedge shape ball orbit in operating angle θ work.Below, the load that is applied to by this compressing power on the depression wall of cage ring 40 is called " depression load ".

Joint design one-tenth of the present invention is compared with traditional universal joint has bigger cage ring side-play amount f, thereby cage ring 40 is used for limiting ball 30 and prevents that they break away from the mouth 16 of outer shrouds 10 from opening end 18 when the maximum functional angle is worked when joint.Exactly, suppose orbital radius (the centre of curvature O that perhaps connects the rail slot 14 of outer shroud 10 at the center of ball 30 ₁Or the centre of curvature O of the rail slot 24 of interior ring 20 ₂Center O with ball 30 ₅Line segment length) be PCR, come so like this to determine cage ring side-play amount f so that ratio f/PCR greater than 0 and be less than or equal to 0.12.

The structure that the rail slot 14 of outer shroud 10 and the rail slot 24 of interior ring 20 have a conical lower portion makes that not only joint can be in bigger maximum functional angle work, but also guarantees that ball 30 is keeping in touch with outer shroud 10 in respective track groove 14 scopes on the length fully.Thereby, realized the stable torque transfer between outer shroud 10 and the interior ring 20.

When joint this structure when bigger operating angle θ works also is favourable, because track load and depression load minimum that the ball 30 in the phase place that is in most probable and breaks away from the cage ring depression (phase angle =0 °, referring to Fig. 3 and Fig. 4) is applied.Here employed term " track load " is meant by just contiguous ball 30 and is applied to load on the wall of

rail slot

14,24.

Because the spherical outer surface 42 of cage ring 40 is by spherical inside surface 12 guiding of outer shroud 10, and the spherical inside surface 44 of cage ring 40 is by spherical outer surface 22 guiding of interior ring 20, so sphere power in the torque transfer process (that is, act between the sphere power) acts between cage ring 40 and interior ring 10 or the outer shroud 20.Said structure has reduced the maximum value of sphere power, thereby has reduced the heat that produces in the joint.In addition, this structure helps to remove mould, has guaranteed workability high in the cold forging process and has reduced manufacture cost.

When the operating angle of joint increased in the course of the work, ball 30 forced cage ring 40 also to increase (representing with blank arrow in Fig. 2) towards the power (that is depression load) of opening end motion.When ball be in or during near its inner side (phase angle =180 °) this Z-TEK not remarkable.Therefore, the spherical inside surface 12 of the spherical outer surface 42 of cage ring 40 friction outer shroud 10 in the zone (in Fig. 3, representing) of contiguous outer ring opening end by " A ".At this some place, if cage ring 40 only contacts with outer shroud 10, can produce considerable heat so in the zonule, cause the reduction of serviceability and the loss of torque transfer.

For the generation that prevents this heat in the process of cage ring 40 friction outer shrouds 10 and follow-up serviceability reduces and the loss of torque transfer, the physical dimension of cage ring is optimised, in the joint as shown in fig. 5.In Fig. 5, identical among the reference character of the parts except cage ring and Fig. 1, identical description no longer repeats: two joints are only variant aspect the physical dimension of cage ring.Fig. 5 has described such state, and wherein the rotating shaft X of outer shroud 10 is 0 ° with the operating angle θ that the rotating shaft Y of interior ring 20 is become, and Fig. 6 has described such state, wherein operating angle θ maximum.

In the cage ring 140 of joint shown in Figure 5, opposite with the cage ring 40 of joint shown in Figure 1, be close to the end of the spherical outer surface 142 of outer ring opening end and extend vertically, and formed the conical surface 148 at the place, end of the spherical inside surface 144 of being close to the outer ring opening end.Surface 148 is convergent by this way: the diameter of conical surface increases (Fig. 1 and Fig. 5) towards the end of the spherical outer surface 142 of contiguous outer ring opening end.As shown in Figure 6, certain amount is extended in the end of the spherical outer surface 142 of the cage ring 140 of the opening end of contiguous outer shroud 10, with prevent to encircle outside 10 be connected to by splined joint with 20 one-tenths maximum functional angles of interior ring the time in the end of cage ring 140 of the axle 50 of ring 20 and vicinity outer ring opening end interfere.

When certain amount is extended in the end of the spherical outer surface 142 of the cage ring 140 of contiguous outer ring opening end, when thereby the end that can prevent the cage ring 140 of axle 50 and contiguous outer ring opening end interferes, wish to make the conical surface 148 to be tapered, make angle θ/2 be equal to or greater than half of maximum angle θ that outer shroud 10 become with interior ring 20 at the place, end of the spherical inside surface 144 of the cage ring 140 of contiguous outer ring opening end.

If the taper angle theta of the conical surface 148/2nd, half of maximum functional angle θ or bigger keeps in touch with the spherical inside surface 12 of outer shroud 10 in fully big area when the spherical outer surface 142 of joint cage ring 140 during in big operating angle work so.If taper angle theta/2 are less than half of maximum functional angle θ, axle 50 will interfere with the end of the cage ring 140 of contiguous outer ring opening end so.

The spherical outer surface 142 of cage ring 140 keeps in touch with the spherical inside surface 12 of outer shroud 10 in fully big area have been guaranteed to move towards opening end when joint ball 30 when maximum functional angle θ works forces cage ring 140.Therefore, the serviceability that heat caused that produces in the time of can making the spherical inside surface 12 of the fierce friction of spherical outer surface 142 outer shrouds 10 of cage ring 140 of contiguous outer ring opening end reduces and torque transfer loss reduces to minimum.This structure has also been guaranteed the maximum rigidity of cage ring 140, thereby has improved the intensity of cage ring 140.

In the cage ring 140 of joint shown in Figure 5, the edge 143 of depression 146 that cage ring spherical inside surface 144 is connected to the end face 141 of depression 146 can fall into fillet to form for example spherical R curved surface, as shown in Figure 7.Spherical R curved surface is the continuous sphere that is connected smoothly between the end face 141 of the spherical inside surface 144 of cage ring 140 and depression 146.Edge 143 on the cage ring spherical inside surface side forms along the whole circumference of depression 146.

Fig. 8 represents an embodiment, and the edge 143 on the cage ring inner surface side of its pocket 146 forms spherical R curved surface, and is the same with edge 145 on the cage ring spherical outer surface side.The spherical R curved surface at the edge 145 on the cage ring spherical outer surface side also is the continuous sphere that is connected smoothly between the end face 141 of the spherical outer surface 142 of cage ring 140 and depression 146.Edge 145 also forms along the whole circumference of depression 146.

The edge 143 of its pocket 146,145 structures that form the spherical R curved surface on cage ring spherical inside surface side or the spherical outer surface side have prevented to be applied to joint when being higher than the dynamic torsional torque of allowing level, and the spherical inside surface 144 of rising that forms along the edge of the rail slot of outer shroud 10 and interior ring 20 and cage ring 140 and spherical outer surface 142 are when interfering, the edge 143,145 of depression 146 splits and is broken.

Although in the above-described embodiments, wherein work as on the cage ring spherical inside surface side of the depression 146 or edge 143 on the cage ring spherical outer surface side, 145 structures that form spherical R curved surface are to be applied on the cage ring 140 of joint shown in Figure 5, but same structure also may be used on the cage ring 40 of joint shown in Figure 1.

Because the cause of cage ring skew, the wall of cage ring 140 is thicker in the zone of contiguous outer shroud 10 opening ends, and thinner in the zone away from opening end.Cage ring 140 comprises a plurality of rectangular substantially depressions 146 along its circle distribution, and wherein each depression 146 has four turnings: two " thin district side " turning 147 and two " thick district side " turnings 149.

Fig. 9 represents an embodiment, and wherein each depression 146 of cage ring 140 is in the radius of curvature at its 147 places, side turning, the thin district radius of curvature greater than 149 places, side turning, thick district, and less than the radius of ball 30.The planimetric map of single depression 146 as shown in figure 10 so that easily relatively the side turning, thin district 147 of depression 146 and the radius of curvature between the side turning, thick district 149.

Figure 11 represents another embodiment, and the side turning, thin district 146 of its pocket 146 has minimum radius of curvature (R _Min), it equals the radius of curvature at side turning, thick district 149.Figure 12 represents another embodiment, and the side turning, thin district 147 of its pocket 146 has maximum radius of curvature (R _Max), it equals the radius of ball 30.

Its pocket 146 can reduce to be applied to the stress on the side turning, thin district 147 of depression 146 when the spherical inside surface 144 of the rising that forms along the rail slot edge and cage ring 140 and spherical outer surface 142 interfere greater than the radius of curvature at 149 places, side turning, thick district and less than the structure of the radius of ball 30 in the radius of curvature at its 147 places, side turning, thin district, and limit the motion of cage ring 140.Thereby, can the thin stress equilibrium of distinguishing between side turning 147 and the side turning, thick district 149 of optimization.This has guaranteed the intensity of cage ring 140.

FEM analyzes and has represented the stress that the radius of curvature that increases 147 places, side turning, thin district of depression 146 can reduce to be applied to the there, therefore the stress that is applied to 147 places, side turning, thin district is approaching mutually with the stress that is applied to 149 places, side turning, thick district, has obtained best stress equilibrium.Thereby, under the spherical inside surface 144 of the rising that forms along the rail slot edge and the cage ring 140 that is used for defining cage ring 140 and the situation that spherical outer surface 142 interferes, increased the tolerance limits that cage ring 140 breaks and guaranteed joint strength at big operating angle duration of work.

Although illustrated in the radius of curvature at 147 places, side turning, thin district of depression 146 greater than the radius of curvature at 149 places, side turning, thick district and less than the structure of the radius of ball 30, same structure also can be applicable to the cage ring 40 of joint shown in Figure 1 with reference to the cage ring 140 of joint shown in Figure 5.

In joint shown in Figure 1, orbit displacement is less relatively, and is to guarantee joint in bigger operating angle work, and the cage ring skew is relatively large.Because the cause of little orbit displacement, the rail slot 14 of outer shroud 10 can be configured to have enough degree of depth in the zone of dark side.This helps to prevent to be in ball 30 releasing slots at the inner side place of rail slot 14.

But, little orbit displacement has caused little encirclement angle (spherical angle) γ, and outer shroud 10 surrounds cage ring 40 (referring to Fig. 2) with this angle.Exactly, term " surround angle (spherical angle) γ " is meant the end and the joint midplane P angulation of spherical inside surface 12 of the outer shroud 10 of neighbouring open end.For the ease of the assembling of the cage ring in this type fittings 40, make the casing diameter Ф D of outer shroud 10 with outer shroud 10 ₁(Fig. 1) be equal to or greater than the outmost diameter Ф D of cage ring 40 ₂(Fig. 4).But, this makes that encirclement angle (spherical angle) γ of outer shroud 10 is littler.Therefore, may reduce the intensity and the serviceability of joint and lose torque transfer.

Can not reduce intensity or the serviceability or the loss torque transfer of joint with the assembling of outer shroud 10 for the ease of cage ring 40, the physical dimension optimum of cage ring 140 turns to the cage ring physical dimension in the joint as shown in Figure 5.The cage ring of seeing from the opposite side of the opening end of outer shroud 10 shown in Figure 5 140 is illustrated in Figure 13, and the sectional view of Figure 13 is illustrated among Figure 14.

Exactly, a part of spherical outer surface 142 in the open end side of each depression 146 of the cage ring 140 of joint shown in Figure 5 is cut to form side grain 150.In addition, cross the external diameter Ф D of the cage ring 140 of two relative side grains 150 ₄Casing diameter Ф D less than outer shroud 10 ₃(referring to Fig. 5 and Fig. 6).As shown in Figure 6, be cut, thereby have the point of contact of cage ring and ball 30 during in the maximum functional angle θ work that the rotating shaft X of outer shroud 10 is become with the rotating shaft Y of interior ring 20 when joint at a part of spherical outer surface 142 of the open end side of depression 146.

Exist the point of contact of cage ring and ball 30 to be equivalent to: with in the maximum functional angle θ work, when ball is in the phase place that most probable breaks away from the depression 146 of cage ring 140 (phase angle =0 °), to make ball not break away from depression at joint.

Although in this embodiment, at the depression 146 formation tangent planes 150 of each circumferential equidistant separation, shown in Figure 13 and 14, tangent plane can not form at each depression 146: can form tangent planes at least one pair of relative depression 146.

Form the reasons are as follows of tangent planes at least one pair of relative depression 146: in the assembly process of as shown in figure 15 cage ring 140 and outer shroud 10, cage ring 140 at first keeps inserting in the outer shroud 10 perpendicular to the mode of outer shroud 10 axis with its axis.Insert after the outer shroud 10, cage ring 140 turns over 90 ° so that the axis alignment of its axis and outer shroud 10.If at least one pair of relative depression 146 is carried out the part excision and crosses the external diameter Ф D of the cage ring 140 of two side grains 150 ₄Casing diameter Ф D less than outer shroud 10 ₃, cage ring 140 insertion outer shrouds 10 are exactly possible so.

In this embodiment, be cut forming side grain 150 at a part of spherical outer surface 142 of the cage ring 140 of the open end side of depression 146, and cross the external diameter Ф D of the cage ring 140 of two side grains 150 ₄Casing diameter Ф D less than outer shroud 10 ₃This structure can be guaranteed the intensity of cage ring 140, and meanwhile constructs diameter Ф D ₄The described diameter Ф of the cage ring 140[that is reduced D ₄Outmost diameter Ф D less than the cage ring 40 of joint shown in Figure 1 ₂(Figure 16 b)], shown in Figure 16 a, thereby, structure casing diameter Ф D ₃The outer shroud 10 that is reduced (described casing diameter Ф D ₃Casing diameter Ф D less than the outer shroud 10 of joint shown in Figure 1 ₁).Therefore, do not reduce encirclement angle (spherical angle) γ (referring to Fig. 6) of outer shroud 10, can not lose torque transfer yet thereby can be convenient to cage ring 140 can not reduce joint with the assembling of outer shroud 10 intensity or serviceability.

Although in this embodiment, wherein a part of spherical outer surface 142 is cut in the open end side of depression 146, and crosses the external diameter Ф D of the cage ring 140 of two relative side grains 150 ₄Casing diameter Ф D less than outer shroud 10 ₃Structure applications on the cage ring 140 of joint shown in Figure 5, but same structure also can be applied on the cage ring 40 of joint shown in Figure 1.

Up to the present, we have discussed the taper rail slot 14 of outer shroud in Fig. 1 and the joint shown in Figure 5 10 and interior ring 20 about internal force, 24 effect and effect, wherein said internal force comprises above-mentioned track load, depression load and sphere power, and has utilized Finite Element Method (FEM) to carry out analyzing to determine the optimum range of cone angle.Learn that increasing cone angle can influence internal force in the mode shown in the table 1.

Table 1 is expressed as determines that ball 30 most probables break away from the analysis result that the phase place of cage ring depression (phase angle =0 °) and internal force are in its peaked phase place.About sphere power, term " change amount " is meant poor between the maximum value of sphere power and the minimum value.

(table 1)

Track load	Phase angle =0 °	Reduce
	Phase angle =0 °	Reduce	Maximum value	Reduce
	Depression load	Phase angle =0 °	Maximum value	Reduce	Reduce
Maximum value		Phase angle =0 °	Increase		Reduce
Maximum value		Sphere power	Increase	Phase angle =0 °	Reduce
The change amount	Reduce			Phase angle =0 °	Reduce

Can find out from table 1, increase cone angle and cause the maximum value of depression load to increase.But, this can not throw into question, because outer shroud 10 and cage ring 40 form thicklyer (phase angle =180 °) in ball 30 position that is arrived of moving in outer shroud 10 inside as far as possible far, thereby can guarantee the intensity of outer shroud 10 and cage ring 40.Cage ring 40 can be made thicklyer by increasing cage ring side-play amount f.

Then, utilize Finite Element Method (FEM) to analyze to determine the upper limit of cone angle.When cone angle increases, be in the internal force (track load and depression load) that the ball 30 at the phase place place that most probable breaks away from the cage ring depression (phase angle =0 °) applied and reduce.Although this looks for joint strength is favourable, outer shroud 10 must be made thinlyyer at opening end 18 places.In order in depth to verify this point, the stress that is applied on the rail slot 14 is converted into joint strength.

The result as shown in figure 17, the relation between its expression cone angle (degree) and joint strength.The result shows, joint strength is reduced to below the required intensity during in cone angle=12.9 °.Like this, the upper limit of optimum taper angle degree α is defined as 12 °.

Although combine orbit displacement in the foregoing description, also can eliminate orbit displacement, the 14a of arc portion of the rail slot 14 of the outer shroud 10 of the inside forms like this because provide orbit displacement need be arranged in the mouth 16 more: make its degree of depth inwardly increase.This has brought the risk that ball 30 in the inner side of the rail slot 14 that is in it may releasing slots.

By eliminating orbit displacement (orbit displacement amount=0), being arranged in the mouth 16 more, the 14a of arc portion of the rail slot 14 of the outer shroud 10 of the inside can form with uniform depth.Thereby at joint during with big operating angle work, the ball 30 that is in the rail slot 14 of outer shroud 10 inner side place has been avoided releasing slots.

We illustrate the result of internal force analysis now, and wherein orbit displacement amount F, cage ring side-play amount f and cone angle change.In analysis, consider the performance of the fixed-type constant-velocity universal joint of superelevation operating angle, wherein the load-torque of allowing when high operating angle is worked when joint according to this performance can not reduce, and the orbit displacement amount is fixed as zero (not having orbit displacement).Although the cage ring skew preferably keeps as far as possible little with regard to internal force, but still need minimum cage ring skew so that guarantee the normal function of joint.Therefore, the cage ring skew changes in following scope: 0≤f/PCR≤0.150.Cone angle changes between 0 degree and 12 degree.

If f=0 (f/PCR=0) is when cone angle is 1.1 degree or all becomes 0 in 0 degree phase place lower railway load and depression load when bigger.

As a comparison, if cone angle=12 degree, when f is 3.94 (f/PCR=0.114) or becomes 0 in 0 degree phase place lower railway load and depression load when following.

Like this, if the relation between cage ring side-play amount f and the cone angle falls into by the zone shown in the oblique line of Figure 18, all be zero in 0 degree phase place lower railway load and depression load so.Figure 18 makes up on the basis of the data that obtain at internal force analysis, and wherein transverse axis is represented cone angle (degree) and the longitudinal axis is represented f/PCR.

Analyze according to these, can make the internal technology specification of load minimum that under 0 degree phase place, applies and the joint that in process, has advantage following definite with big operating angle work:

Orbit displacement: zero;

Cage ring side-play amount f:0＜f/PCR≤0.15; And

Cone angle: 1 degree≤α≤12 degree.

In the present embodiment, cage ring 40 preferably places outer shroud 10 with its thick portion towards the mode of opening end 18.This layout of cage ring can be guaranteed joint strength, because compare with traditional constant velocity joint, has reduced although peak load increases the load that applies under 0 degree phase place.

Utilize the have joint (example) of determined yardstick on the basis of above-mentioned technical specification and traditional joint (comparative example) of the present invention, the track load and the depression load that experimentize and under 0 degree phase place, apply to determine.The result as shown in figure 19.As shown in the figure, in example observed track load and depression load each all than observed low more than 80% in comparative example.The EWS internal force that calculates (T=T100 (462.6Nm), θ=46.5 degree) as shown in table 2.

(table 2)

Parameter		Example	Comparative example
Parameter		Example	Comparative example	θ _max		52	50
Cone angle: α (degree)		5.233	0	θ _max		52	50
Cone angle: α (degree)		5.233	0	Ball quantity		6	6
Ball diameter (mm)		19.844	20.638	Ball quantity		6	6
Ball diameter (mm)		19.844	20.638	PCD(mm)		69.32	68.02
The contact gear ratio of ring in the %		1.04	1.04	PCD(mm)		69.32	68.02
The contact gear ratio of ring in the %		1.04	1.04	The contact gear ratio of % outer shroud		1.08	1.08
Orbit displacement: F (mm)		0	4.53	The contact gear ratio of % outer shroud		1.08	1.08
Orbit displacement: F (mm)		0	4.53	Cage ring skew: f (mm)		3.11	0.57
Wrapping angle (degree)		35	40	Cage ring skew: f (mm)		3.11	0.57
Wrapping angle (degree)		35	40	Sphere radial clearance (mm) between interior ring and the cage ring		0.0288	0.0263
Sphere radial clearance (mm) between outer shroud and the cage ring		0.0288	0.0288			0.0288	0.0263
		0.0288	0.0288	PCD gap (mm)		0.04	0.0175
The depression gap (mm) of neighbouring open end		-0.01025	-0.00825	PCD gap (mm)		0.04	0.0175
The depression gap (mm) of neighbouring open end		-0.01025	-0.00825	The cage ring depression gap (mm) of joint inside		-0.01025	-0.00825
Track load ^*	Phase angle=0 degree	582	4458	The cage ring depression gap (mm) of joint inside		-0.01025	-0.00825
	Phase angle=0 degree	582	4458	Maximum value	15156	13747
	Depression load ^*	Phase angle=0 degree	455	Maximum value	15156	13747	2696
Maximum value		Phase angle=0 degree	455	5091	4466		2696

^*Load is to be 462.6Nm (T100)/θ at load torque _MaxCondition under measure.

Utilize the have joint (example) of determined yardstick on the basis of above-mentioned technical specification and traditional universal joint (comparative example) of the present invention, carry out another experiment with determine when apply 0 spend under the phase place maximum depression load the time be applied to stress on the cage ring sidewall.The result as shown in figure 20.

The joint of example is in operating angle (56 °) the down work bigger than the operating angle (50 °) of comparative example.Percentage is with respect to observed stress (=100) in the comparative example.Shown in the result, the stress that applies in the joint of example is lower than the stress of comparative example middle joint, expression when joint when working greater than the operating angle of the joint of comparative example, the intensity with cage ring of the present invention of above technical specification is comparable to or is higher than the cage ring of comparative example.

Below, the joint that comes comparative example about the effect and the effect of internal force (especially depression load) at the taper rail slot and the joint of comparative example.Proved that in example the depression load that ball was applied that is under the phase place (phase angle=0 degree) that most probable breaks away from the cage ring depression significantly reduces in the process with the work of maximum functional angle.But, the analysis showed that of the depression load that under other phase places, applies by ball, the 5939N (maximum value) in the example, observed depression load is 4671N (maximum value) in comparative example.

Therefore, the maximum depression load in the example is compared with comparative example and is exceeded 30% (referring to Figure 21).In this experiment, applied identical load torque, but joint is to work under different operating angles: the joint of example is in operating angle (56 °) the down work higher than the operating angle (50 °) of comparative example joint.The technical specification of the joint of comparative example and example is as shown in table 3.

(table 3)

Parameter	Comparative example	Example
Parameter	Comparative example	Example	Do/d	3.7	4.1
t/d	0.26	0.32	Do/d	3.7	4.1
t/d	0.26	0.32	w/d	1.8	1.9
A	0	5.15°	w/d	1.8	1.9
A	0	5.15°	f/PCR	0.017	0.09

The increase of maximum depression load is considered to that the increase of the convergent of rail slot and operating angle causes in the example.Therefore, adopt following cage ring technical specification so that joint can withstand the early damage that the depression load of increase also can be avoided joint.Parenthetic numeral is the technical specification of traditional fixed-type constant-velocity universal joint (BJ) or fixed-type constant-velocity universal joint (UJ).Outer diameter D o, inside diameter D i and width w are as shown in Figure 2.The cage ring thickness t is the thickness that records in the center of cage ring along central axis.

Cage ring external diameter (Do) is with respect to the ratio (Do/d) of ball diameter (d): 3.9≤Do/d≤4.1 (3.7≤Do/d≤3.8)

Cage ring thickness (t) is with respect to the ratio (t/d) of ball diameter (d): 0.31≤t/d≤0.34 (0.24≤t/d≤0.27)

Cage ring width (w) is with respect to the ratio (w/d) of ball diameter (d): 1.8≤w/d≤2.0 (1.8≤w/d≤1.9)

Cage ring internal diameter (Di) is determined by cage ring external diameter and cage ring thickness with respect to the ratio (Di/d) of ball diameter (d).As a reference, this ratio is as follows:

3.25≤Di/d≤3.45(3.10≤Di/d≤3.25)。

Because depression load is in that the direction towards the outer ring opening end works from the inside of outer shroud mouth, thus cage ring be arranged on like this in the outer shroud so that the thicker end neighbouring open end of cage ring and thin end in the inside of outer shroud mouth.This is because need to form appropriate casing diameter so that the assembling of interior ring.Less relatively in the depression load that the direction towards outer shroud mouth inside from the outer ring opening end works, thus can not cause special problem.

Claims

1. fixed-type constant-velocity universal joint comprises:

Socket member with spherical inside surface, described socket member have opening end and a plurality of rail slots that are formed on the spherical inside surface, and each rail slot is equidistantly separated towards the opening end extension and along the circumference of spherical inside surface along axial direction;

Wherein:

2. a fixed-type constant-velocity universal joint comprises:

Wherein:

3. a fixed-type constant-velocity universal joint comprises:

Wherein:

A part of spherical outer surface of cage ring is cut in the open end side of two relative depressions at least, crosses the casing diameter of the cage ring external diameter of two relative cutting parts less than the socket member.

4. a fixed-type constant-velocity universal joint comprises:

Wherein:

A plurality of depressions are along the circumference setting of cage ring and hold ball, and the depression edge is rounded angle on the spherical inside surface side of cage ring and in the spherical outer surface side at least one.

5. a fixed-type constant-velocity universal joint comprises:

Wherein:

Have radius of curvature along the circumference setting of cage ring and a plurality of rectangular substantially depression that holds ball in its corner away from socket member opening end, this radius of curvature is greater than the radius of curvature of the corner of neighbouring open end and less than the ball radius.

6. a fixed-type constant-velocity universal joint comprises:

Wherein:

7. fixed-type constant-velocity universal joint as claimed in claim 6, wherein the end convergent of the cage ring spherical inside surface of adjacent joint opening end forms and is equal to or greater than the socket member becomes the maximum functional angle with the spigot member half angle.

8. a fixed-type constant-velocity universal joint comprises:

Wherein:

The distance that the centre of curvature of the centre of curvature of socket member rail slot and spigot member rail slot departs from the joint center is the cage ring side-play amount, the side-play amount at the center of the misalignment cage ring spherical inside surface that this cage ring side-play amount is the cage ring spherical outer surface, thus the orbit displacement amount is zero.

9. one kind as any described fixed-type constant-velocity universal joint in the claim 1 to 8, suppose that wherein the cage ring side-play amount between the center of the center of cage ring spherical outer surface and spherical inside surface is f, and the rail slot centre of curvature that connects the rail slot centre of curvature of socket member or spigot member is PCR with the length of the line segment at ball center, and then the value of ratio f/PCR is greater than zero and be less than or equal to 0.12.

10. one kind as any described fixed-type constant-velocity universal joint in the claim 1 to 8, and wherein the rail slot of inside and outside joint member is finished by Cold Forging.

11. a fixed-type constant-velocity universal joint as claimed in claim 9, wherein the rail slot of inside and outside joint member is finished by Cold Forging.