CN101349338A - Toroidal continuously variable transmission - Google Patents
Toroidal continuously variable transmission Download PDFInfo
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- CN101349338A CN101349338A CNA200810110621XA CN200810110621A CN101349338A CN 101349338 A CN101349338 A CN 101349338A CN A200810110621X A CNA200810110621X A CN A200810110621XA CN 200810110621 A CN200810110621 A CN 200810110621A CN 101349338 A CN101349338 A CN 101349338A
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Abstract
Power roller-side concave grooves are opposed to disk-side concave grooves 19, 19 so as to have angles therebetween in a rolling contact area between a peripheral surface of the power roller and a one-side surface 17 of a disk 16 in an axial direction regardless of a transmission gear ratio of a toroidal continuously variable transmission. Accordingly, the disk-side concave grooves 19, 19 are formed so as to have angles with respect to a circumferential direction of the disk 16 when viewed from a normal direction relative to the one-side surface 17 in the axial direction. Meanwhile, the power roller-side concave grooves are formed into a concentric shape (or a spiral shape) about a central shaft of the power roller. As a result, it is possible to prevent a decrease of a contact area in the rolling contact area regardless of the transmission gear ratio.
Description
Technical field
The present invention relates to the improvement of transmission device of the continuous variable of toroidal (toroidal), the transmission device of the continuous variable of this toroidal is as the variable-speed unit of automatic transimission that is configured for vehicle, or with the transmission device of the motion speed of the various industrial machines that act on adjusting such as pump.Specifically, the invention provides a kind of structure, wherein a plurality of grooves (concave groove) (meticulous groove) not only had been formed on the periphery of power drum (power roller) but also had been formed on a side surface of axial disk (disk), so that improve the traction coeficient of the rolling contact area between the outer surface of this axial side surface and power drum, guarantee the durability of disk and power drum simultaneously.And the present invention also provides this groove with low cost.
Background technique
In some fields, the transmission device of the continuous variable of toroidal is used as the speed change gear of vehicle usually.Fig. 9 and Figure 10 illustrate the basic structure of transmission device of continuous variable of the toroidal of current practical application.The transmission device of the continuous variable of this toroidal is called concave-concave chamber type, wherein a pair of input side disk 1 and 1 is supported in input turning axle 2 in rotatable mode, while, corresponding to the state also interlocking concentrically with respect to one another along an axial side surface, this input side internal surface 3 and 3 formed toroidal curved surfaces (being arc-shaped concave) and positioned opposite to each other on section with input side internal surface 3 and 3.
In addition, the output cylinder 5 with external gear 4 of the external peripheral surface that is fixedly connected to its core is supported on around the position of the core of input turning axle 2, so that be rotatable around this input turning axle 2. Outlet side disk 6 and 6 is supported in the two end part of output cylinder 5 by spline engagement, so that rotate with output cylinder 5.In this state, corresponding to along the outlet side disk 6 of an axial side surface with 6 both outlet side internal surface 7 with 7 with input side internal surface 3 with 3 both are relative, this outlet side internal surface 7 and 7 forms the toroidal curved surface.
Two power drums 8 and 8 with spherical convex surface are arranged between input side internal surface 3 and the outlet side internal surface 7 around input turning axle 2.This power drum 8 and 8 is supported in the internal surface of pivot (trunnion) 9 and 9 by back shaft 10 and 10, each described back shaft 10 has the eccentric each other end half one and first half, with a plurality of roller bearings, so that be rotatable and can swing a little around the end half of back shaft 10 and 10 one along the first half of back shaft 10 and 10. Pivot 9 and 9 can be swung around sloping shaft 11 and 11, so that concentrically with respect to one another, sloping shaft 11 and 11 (inboard among Fig. 9 and lateral direction, the Vertical direction among Figure 10) along the longitudinal is arranged on the two end part of pivot 9 and 9.
Wherein the operation of pivot 9 and 9 swings is undertaken by the pivot 9 and 9 that moves axially along sloping shaft 11 and 11 by hydraulic actuator 12 and 12.That is to say, when needs change speed, by putting on the hydraulic oil of actuator 12 and 2, pivot 9 and 9 moving axially along sloping shaft 11 and 11.As a result, act on along direction and change (sideslip) perpendicular to the power of the direction of the outer surface of power drum 8 and 8 and the rolling contact area between input side and outlet side internal surface 3 and 7, then pivot 9 and 9 move, simultaneously around sloping shaft 11 and 11 swings.
In the transmission device of the continuous variable that moves above-mentioned toroidal, driven shaft 13 drives with rotation the input side disk 1 in (on the left side among Fig. 9) by loading cam pressure unit 14 on a side.As a result, this of two end part that is supported in input turning axle 2 rotate together to input side disk 1 and 1, and the while is compacted along direction close to each other.So, by power drum 8 and 8 rotation is passed to two outlet side disks 6 and 6, and draws from output gear 4 then.
With the running of explanation when changing the rotating ratio of importing between turning axle 2 and the output gear 4.
When between input turning axle 2 and output gear 4, slowing down, pivot 9 and 9 swings to position shown in Figure 9, then, power drum 8 and 8 outer surface and input side disk 1 and 1 input side internal surface 3 and 3 core and two outlet side disks 6 and 6 outlet side internal surface 7 partly directly contact respectively with 7 excircle.
On the contrary, when quickening, pivot 9 and 9 along with opposite direction swing shown in Figure 9, so power drum 8 and 8 outer surface and input side disk 1 with 1 both input side internal surface 3 and 3 excircle partly and outlet side disk 6 directly contact with 7 core with 6 both outlet side internal surfaces 7.
When the angle of oscillation of pivot 9 and 9 is set to intermediate value, can between input turning axle 2 and output gear 4, obtain medium velocity ratio.
When the transmission device of the continuous variable that moves above-mentioned toroidal, in the input side and the rolling contact area (towing area) between outlet side internal surface 3 and 7 of the outer surface of power drum 8 and 8 and input side and outlet side disk 1 and 6, by the traction transferring power.Here, the friction factor of traction (traction coeficient) is normal value, and must impose severe pressure so that in the big torque of rolling contact area transmission to the rolling contact area.
But, when applying this big pressure, input side and outlet side disk 1 and 6 or the serviceability possible deviation of power drum 8 and 8.In addition, in order to ensure disk 1 and 6 or the intensity of power drum 8 and 8, parts 1,6 and 8 size may increase, this for the implement device size to reduce be undesirable.
Simultaneously, in order to prevent the problems referred to above, for example, Japanese patent unexamined is looked into open JP-A-2002-39306, JP-A-2003-207009, JP-A-2003-278869 and JP-A-2003-343675 and is disclosed a kind of technology, wherein having the degree of depth and be a plurality of grooves in 0.1 μ m to 8 mu m range is formed on the whole side surface of disk 1 and 6 or on the outer surface (traction surface) of power drum 8, so that intersect each other.When adopting this technology, can improve the traction coeficient of rolling contact area, and therefore, think and compare, can be by little propagation of pressure big torque with the structure that does not have this groove.
In this case, when traction coeficient is improved when obtaining high-energy (admissible driving torque increase) with this structure widely, for example, the degree of depth of groove can be set to (deeply) greatly.
But, when the degree of depth of groove is configured to greatly (deeply), is difficult to guarantee be used to form the serviceability of the machining tool of groove, and therefore, may increases manufacture cost.In addition, when groove forms by rolling mill practice for example, may be damaged corresponding to the traction surface of surface to be machined, perhaps its flexural fatigue possible deviation.On the contrary, for example, when groove is formed on when the outer surface of side surface of axial disk 1 and 6 and power drum 8 is gone up, promptly the degree of depth of convenient groove especially when big (deeply), can not improved traction coeficient significantly yet.But, when groove be formed on disk 1 and 6 and both surfaces of power drum 8 on the time, disk 1 and 6 or the serviceability of power drum 8 can not only guarantee by on surface (traction surface), forming groove simply.Will be described below about this point.
That is to say, in JP-A-2002-39306, JP-A-2003-207009, JP-A--2003-278869 and JP-A-2003-343675 in the disclosed structure, a plurality of grooves are formed on the outer surface of power drum 8 or on a side surface of axial disk 1 and 6, so that have the spiral-shaped or concentric shape of the central shaft (running shaft) around parts.For example, as shown in figure 11, can suppose that the groove 15 and 15 with concentric shape is formed on the side surface 3 and 7 of the outer surface 18 of power drum 8 and disk 1 and 6 here.In addition, Figure 11 is a schematic representation, wherein is exaggerated for the ease of formation state (relation between the groove width of groove 15 and the groove depth P is greater than the relation of the reality) groove 15 and 15 of understanding groove 15 and 15.In fact, in groove 15 and 15 the scope of the degree of depth about 0.1 to 8 μ m, and in the scope of its well width about 10 to 500 μ m, in the scope of its pitch of grooves about 25 to 500 μ m.So, groove 15 and 15 is formed in the structure of concentric shape therein, according to the pinion ratio between disk 1 and 6 (transmission gear ratio), can not guarantee fully disk 1 and 6 a side surface 3 and 7 and the outer surface 18 of power drum 8 between the area of contact of rolling contact area, that is to say, can not guarantee the tilt angle of power drum 8 and 8 fully.
Just, as mentioned above, groove 15 and 15 forms in the structure of concentric shape therein, groove 15 and 15 in the rolling contact area abreast toward each other.Here, shown in Figure 12 A of contact condition that the rolling contact area schematically is shown, when the contact groove 15 and 15 with mutually the same position relation toward each other the time, the main area of contact of the contact area that can not roll (summation of the surface of contact knot of the rolling contact area except groove 15 and 15) becomes the problem less than essential area.
But shown in Figure 12 B, because the relation of the position between the groove 15 and 15 departs from according to the pinion ratio between disk 1 and 6, the main rolling area of contact of rolling contact area may reduce.In addition, though do not illustrate in the accompanying drawings, be that box lunch has spiral groove and is formed on the traction surface, because abreast toward each other at the groove of rolling contact area, also may take place and have the groove 15 of concentric shape and 15 essentially identical problems (because groove with the same toward each other reason of slightly different parallelism, main area of contact may reduce).
So when area of contact diminished by this way, the surface pressure of rolling contact area increased, and therefore, with significant state, between the traction surface of rolling contact area Metal Contact may take place.Pinion ratio between the disk 1 and 6 changes according to running state.But, for example, during constant-speed operation, under the constant state of pinion ratio, move.So, in this state, when the area of contact of rolling contact area diminishes, disk 1 and 5 or the serviceability possible deviation of power drum 8 and 8, this is undesirable.
Summary of the invention
Consider the problems referred to above and design the present invention, and one of purpose of the present invention provides a kind of structure, wherein a plurality of grooves (meticulous groove) are formed on the outer surface of power drum and on a side surface of axial disk, so that improve the traction coeficient of the rolling contact area between the outer surface of an axial side surface and power drum, guarantee the serviceability of disk and power drum simultaneously.And the invention still further relates to provides a kind of structure, is used for realizing a plurality of grooves with low cost, and relates to the method for making a plurality of grooves with low cost.
According to the present invention, a kind of transmission device of continuous variable of toroidal is provided, comprising:
Pair of discs, it has sectional shape respectively is a bell-mouthed axial side surface, this disk is with corresponding axial side surface state respect to one another rotatably and supported concentrically with respect to one another; With
The a plurality of power drums that are provided with along the circumferencial direction of disk between a corresponding axial side surface, corresponding power drum have and are made into the outer surface that contacts with an axial side surface of disk, wherein
A plurality of disk side grooves are formed on the axial side surface of disk,
A plurality of cylinder side grooves be formed on the outer surface of power drum and
No matter velocity ratio is (no matter the true dip direction of power drum how) how, the rolling contact area between disk and power drum, disk side groove and power drum side groove are deflection relationship (distortional relation).
Notice that being formed on the outer surface of power drum or the degree of depth of the groove on the axial side surface is that for example, 8 μ m or following are preferably 5 μ m or following, more preferably 0.5 to 3.0 μ m.More preferably, groove is set to intersect each other.
According to the present invention, preferably, the disk side groove only is formed on the radial component of an axial side surface of disk, makes the disk side groove not meet continuously with power drum side groove.Specifically, when velocity ratio was desired certain value of certain traction coeficient, the part of an axial side surface contacted with the outer surface of power drum.
According to the present invention, more preferably, in the rolling contact area, when when observing with respect to the normal direction of rolling contact area, disk side groove and power drum side groove are with the angle of intersection of 5 to 90 degree, preferably with 5 to 45 angle of intersection of spending.More preferably, angle is set to 10 to 45 degree, 20 to 45 degree, the angle of 30 to 45 degree.
According to the present invention, a kind of transmission device of continuous variable of toroidal is provided, comprising:
Pair of discs, it has the axial side surface that sectional shape is a toroidal respectively, and this disk is with corresponding axial side surface state respect to one another rotatably and supported concentrically with respect to one another; With
The a plurality of power drums that are provided with along the circumferencial direction of disk between a corresponding axial side surface, corresponding power drum have and are made into the outer surface that contacts with an axial side surface of disk, wherein
A plurality of disk side grooves are formed on the axial side surface of disk,
A plurality of cylinder side grooves are formed on the outer surface of power drum,
When the normal direction that forms surface thereon with respect to corresponding grooves is observed, the circumferencial direction of the circumferencial direction of one of them of disk side groove and power drum side groove and disk or power drum is with certain angle of intersection at least, and
This groove is configured such that formed angle between formed angle between the groove of radially inner side and the circumferencial direction is greater than the groove at radial outside.
And, according to the present invention, providing a kind of manufacture method of transmission device of continuous variable of toroidal, this transmission device comprises:
Pair of discs, it has the axial side surface that sectional shape is a toroidal respectively, and this disk is with corresponding axial side surface state respect to one another rotatably and supported concentrically with respect to one another; With
The a plurality of power drums that are provided with along the circumferencial direction of disk between a corresponding axial side surface, corresponding power drum have and are made into the outer surface that contacts with an axial side surface of disk, wherein
A plurality of disk side grooves are formed on the axial side surface of disk,
A plurality of cylinder side grooves are formed on the outer surface of power drum,
When the normal direction that forms surface thereon with respect to corresponding grooves is observed, the circumferencial direction of one of them and the disk at least of disk side groove and power drum side groove or the circumferencial direction of power drum be with certain angle of intersection, and
This groove is arranged so that the angle that forms between the angle that forms between the groove of radially inner side and the circumferencial direction is greater than the groove at radial outside,
This manufacture method comprises:
With constant speed rotational workpieces, groove shaped is formed on this workpiece;
The instrument (cutting tool or the emery wheel that are used for machining) that is used to form groove is taken to the surface to be machined of workpiece; And
In the contact of rolling with constant rotating speed rotational workpieces and maintenance between described instrument and the workpiece, move (swing or displacement) described instrument along radially (also along the longitudinal) of workpiece with constant speed.
Transmission device according to the continuous variable of above-mentioned toroidal can provide a kind of structure with a plurality of grooves, has improved traction coeficient, guarantees the serviceability of disk and power drum simultaneously.
That is to say because groove is formed on the axial side surface and the outer surface of power drum on (two traction surface) on both, promptly during the degree of depth of convenient groove very little (not being dark especially), also can guarantee enough traction coeficients.Therefore, the serviceability of the machining tool of groove can be guaranteed to be used to form easily, and therefore manufacture cost can be reduced.In addition, when forming groove, can prevent that the finished surface that groove forms thereon is damaged, and prevent the flexural fatigue variation by rolling mill practice.
In addition, as mentioned above, no matter the velocity ratio between the disk how, in the outer surface and the rolling contact area between the axial side surface of power drum, the power drum side groove that is formed on the power drum outer surface is relative with disk side groove on being formed on an axial side surface.Therefore, for example, under certain gear ratio, the problem that the main area of contact of the contact area that can not roll (summation of the area of contact of the rolling contact area except that groove) diminishes.Therefore, when running gear under the especially little state of area of contact, can prevent the excessive surface pressure in the rolling contact area or the generation of Metal Contact, and therefore can guarantee the serviceability of disk and power drum.
In addition, as mentioned above, in order to make the disk side groove become deflection relationship with power drum side groove, when when the normal direction that forms surface (concave surface the sectional view or convex surface) thereon with respect to corresponding recesses is observed, at least one groove of power drum side and disk side groove are with certain angle of intersection.So in this case, this angle forms and make the angle that is limited between the groove of angle greater than radial outside that is limited between radially inner side groove and the circumferencial direction.
In other words, when considering that common center is the concentric circle of rotating center disk or power drum, also between groove and concentric circle, limit this angle.In this case, groove is configured such that in the crossing angle that limits between groove and the inner concentric circle greater than the crossing angle that limits between groove and outer concentric circle.
When as mentioned above groove being set, can form groove with low cost.Its reason is because groove can form like this, promptly by need to form the parts of groove with the constant speed rotation, simultaneously be used to form the machining tool of groove (such as the groove form-cutting instrument of superfinish blade or such as the grinding tool of superfinish emery wheel) and surface that will be processed directly under the state of contact, moving (swing) machining tool with constant speed along the diametric(al) (and vertically) of the parts of needs formation groove.In addition, why can be by moving the reason that machining tool forms groove with constant speed simultaneously with the constant speed rotating disk, the peripheral velocity of the parts that processed instrument is processed changes, and makes peripheral velocity on the diameter outside faster than the peripheral velocity on the diameter inboard.Therefore, accelerate along with peripheral velocity with respect to the angle of circumferencial direction and diminish.
For this reason, do not form the rotational speed of parts of groove or the travelling speed of change machining tool, so do not need to be provided for to change the mechanism of the rotational speed of processing device owing to when machined grooves, do not need to change needs.In addition because the cost of processing device can be reduced to and do not need for its cost that mechanism is provided as many, therefore can reduce the cost that is used to form groove.
Description of drawings
Figure 1A is the top view of first embodiment's disk, and its further groove is exaggerated;
Figure 1B is the side view of first embodiment's disk, and its further groove is exaggerated;
Fig. 2 illustrates that disk is formed and the schematic representation of the state that a part of groove is removed;
Fig. 3 A is the top view of first embodiment's power drum, and its further groove is exaggerated;
Fig. 3 B is the side view of first embodiment's power drum, and its further groove is exaggerated;
Fig. 4 A is the top view of second embodiment's disk, and its further groove is exaggerated;
Fig. 4 B is the side view of second embodiment's disk, and its further groove is exaggerated;
Fig. 5 A is the top view of second embodiment's power drum, and its further groove is exaggerated;
Fig. 5 B is the side view of second embodiment's power drum, and its further groove is exaggerated;
Fig. 6 A is the top view of the 3rd embodiment's input side disk, and its further groove is exaggerated;
Fig. 6 B is the side view of the 3rd embodiment's input side disk, and its further groove is exaggerated;
Fig. 7 A is the top view of the 3rd embodiment's outlet side disk, and its further groove is exaggerated;
Fig. 7 B is the side view of the 3rd embodiment's outlet side disk, and its further groove is exaggerated;
Fig. 8 A is the top view of the 3rd embodiment's power drum, and its further groove is exaggerated;
Fig. 8 B is the side view of the 3rd embodiment's power drum, and its further groove is exaggerated;
Fig. 9 is the sectional view that the example of known structure 1 is shown;
Figure 10 is the view that the X-X line along Fig. 9 is intercepted;
Figure 11 is illustrated in the schematic representation that the possibility of problem takes place in the structure with groove;
Figure 12 A is the sectional view of the amplification of the rolling contact area between disk and the power drum, and it illustrates the big contact condition between disk and the power drum;
Figure 12 B is the sectional view of the amplification of the rolling contact area between disk and the power drum, and it illustrates little contact condition;
Figure 13 is the schematic representation of the setting of power drum and disk, and an example of the present invention is shown; And
Figure 14 is the schematic representation of the setting of power drum and disk, and another example of the present invention is shown.
Embodiment
First embodiment
Fig. 1 to Fig. 3 illustrates the first embodiment of the present invention.In addition, this embodiment's feature is 19,20 a principle of research groove, so that the structure with a plurality of grooves 19,20 is provided, it has improved traction coeficient, has guaranteed the serviceability of disk 16 (it is corresponding to input side disk 1 shown in Figure 9 and outlet side disk 6) and power drum 8 simultaneously.Because the structure and the effect of the known example described in other structures and effect and Fig. 9 and Figure 10 are same, so its corresponding accompanying drawing will be removed or describe simply with describing.Hereinafter, will this embodiment's characteristic be described mainly.
In this embodiment, as depicted in figs. 1 and 2, a plurality of grooves 19,19 are formed on the whole side surface 17 of disk 16, and (it is corresponding to the surface shown in Figure 1A and 2, upper surface shown in Figure 1B, input side internal surface 3 shown in Figure 9 and outlet side internal surface 7) on, this disk 16 is along the transmission device of axial formation according to the continuous variable of this embodiment's toroidal.At this moment, for example, groove 19,19 has the 8 μ m or the following degree of depth, and hope is the 5 μ m or the following degree of depth, and even more wishes scope at 0.5 to 3.0 μ m.In addition, on the outer surface 18 of the power drum shown in Fig. 3 A and the 3B 8, a plurality of power drum side grooves 20,20 are formed on the whole outer surface 18.At this moment, for example, power drum side groove has the 8 μ m or the following degree of depth, and hope is 5 μ m or following, and even more wishes in the scope of 0.5 to 3.0 μ m.
In addition, in Figure 1A to 3B (and Fig. 4 A to Fig. 8 B that describes below), similar above-described Figure 11, understand the formation state of groove 19,20 for convenience, groove 19,20 is exaggerated, and is schematically illustrated, and makes the recess width and the flute pitch P of groove 19,20
19And P
20Relation between the (see figure 2) is greater than the relation of its reality.Under truth, as mentioned above, the degree of depth of groove 19,20 is the 8 μ m or the following degree of depth, is 5 μ m or following with wishing, and even wishes more that in the scope of 0.5 to 3.0 μ m groove width is in the scope of 10 to 500 μ m, and pitch of grooves P
19And P
20In the scope of 25 to 500 μ m.So, utilize the precision machining blade by milling process, groove 19,20 is formed on the outer surface 18 of side surface 17 of disk 16 and power drum 8.At this moment, by superfinish, a side surface 17 is formed smooth surface.In addition, as described below, the groove width of disk side groove 19,19 can be identical or inequality with the groove width of power drum side groove 20,20.
Under any circumstance, in this embodiment, power drum side groove 20,20 and disk side groove 19,19 are deflection relationship.That is to say, no matter the pinion ratio between the disk 16 (between input side disk 1 and the outlet side disk 6) how, when when observing with respect to the normal direction of the rolling contact area between the side surface 17 of the outer surface 18 of power drum 8 and disk 16, power drum side groove 20,20 is relative with disk side groove 19,19, and the while is angulation relative to each other.For example, this angle is in 5 to 90 degree scopes, and more wishes in 5 to 45 degree scopes.
As for the concrete structure of above-mentioned notion, Figure 13 and embodiment shown in Figure 14 are exemplary.That is to say that as shown in figure 13, disk side groove 19 is made into the circumferencial direction and the power drum side groove 20 that are parallel to disk 16 and is applicable to the present invention with the structure that constant angle and circumferencial direction intersect.As one of other embodiments, as shown in figure 14, the structure that the disk side groove 19 shown in Figure 1B is applied to disk side and power drum side groove 19 also is suitable for.
That is to say that when only observing the small contact area be limited between disk 15 and the power drum 8 partly, within this local Microcell, disk side groove 19 is not parallel to power drum side groove 20, and these grooves 19,20 are deflection relationship.According to this structure, when disk 15 and power drum 8 rotate together, there is not the situation that they contact with each other continuously with this small contact area shown in Figure 12 B.
Say in detail, though shown in Figure 12 B, the contact area between disk 15 and the power drum 8 is less at a time ratio, has served as certain hour, and when disk 15 and power drum 8 rotated together, the position of groove 19,20 relation was changed into the big state of the area of contact shown in Figure 12 A.Therefore, the situation that does not have disk 15 and power drum 8 to contact continuously each other with small area of contact.
Therefore, because during the rotation of disk 15 and power drum 8, the situation that does not have disk 15 and power drum 8 to contact continuously each other with small area of contact, and therefore, big contact pressure is put on disk 15 and power drum 8 discontinuously.Therefore, can avoid having only the specific part of disk 15 and power drum 8 to be subjected to the situation of king-sized damage.
It should be noted that to need not many speeches, the invention is not restricted to the embodiment shown in Figure 13 and 14.As long as when local small area of contact of observing between disk 15 and power drum 8 only, disk side groove 19 and power drum side groove are deflection relationship, and they do not contact with each other continuously with small area of contact in during their rotations, and this structure just comprises within the scope of the invention.
In order to realize said structure, particularly be made into uneven each other disk side and power drum side groove 19,20, below with an example of description architecture and method in order to form.
In this embodiment, power drum side groove 20,20 is formed around the concentric shape (or spiral-shaped) of the central shaft (running shaft) of power drum 8.Simultaneously, when from respect to when the normal direction of an axial side surface 17 is observed (seeing the observation line shown in Figure 1B), disk side groove 19,19 is formed with respect to the circumferencial direction angulation α of disk 16 and β (see figure 2).In other words, disk side groove 19,19 is with respect to becoming (having) angle [alpha] and β along the imaginary concentric circle X-shaped shown in the axial side surface 17, and this imagination concentric circle X forms around the central shaft of disk 16.So, angle [alpha] and β formed make in the angle on the diametric inboard (on the inner diameter side) of disk 16 greater than the angle on its diametric(al) outside (in the outer diameter side).
That is to say, as wherein being formed with the shown in Figure 2 of disk 16, being formed on disk side groove 19,19 and being formed and make at the angle beta of diameter inboard greater than the angle [alpha] in the diameter outside (α＜β) corresponding to the angle [alpha] between the imaginary concentric circle X of the circumferencial direction of disk 16 and β.In addition, formation figure shown in Fig. 2 is the view that wherein is formed planimetric map as the concave curvatures of a side surface 17 of disk 16, and its generation type is with identical with the situation that earth surface is shown world's plane map by mercator's projection (Mercatorprojection).The horizontal direction parallel (imaginary concentric circle X is corresponding to the parallel of world map) of the paper of imagination concentric circle X and Fig. 2.So angle [alpha] shown in the formation figure of Fig. 2 and β be corresponding to as angle [alpha] and β when observing with respect to the normal direction of a side surface 17, and angle [alpha] and β are adjusted to and satisfy relation α＜β.
In addition, Figure 1A illustrates from observe the state of disk 16 along axial smaller diameter side.Angle [alpha] shown in Figure 1A
aAnd β
aIt is the outward appearance angle when along end on observation disk 16.In addition, Figure 1B illustrates from observe the state (side view) of disk 16 along the diametric outside.Angle [alpha] shown in Figure 1B
bAnd β
bIt is the outward appearance angle when along diametric(al) observation disk 16.So, angle [alpha], α
aAnd α
bAnd angle beta, β
aAnd β
bCorrespond respectively to diametric same position (angle θ with respect to disk 16
aAnd θ
βBe formed on the position between the imaginary plane that intersects perpendicular to the straight line of a side surface 17 with the central shaft of right angle and disk 16).
In this embodiment, form disk side groove 19,19 as follows.That is, in constant speed rotating disk 16, the machining tool (forming cutting tool such as the groove of fine finishing blade) that is used to form disk groove 19,19 perhaps such as the abrasive tool of superfinish emery wheel with a processed side surface 17 is directly contacted.In this state, machining tool with constant speed along the diametric(al) of disk 16 (and axially) swing (or move along surface to be machined).So, by this way, machining tool is with constant speed swing or when mobile in constant speed rotating disk 16, disk side groove 19,19 is formed on the side surface 17, so that the circumferencial direction with respect to disk 16 has angle (being formed on the angle between imaginary concentric circle X and the disk side groove 19,19), make when when observing with respect to the normal direction of a side surface 17, in the angle of the diameter inboard of disk 16 greater than the angle outside its diameter.
Rotational speed by regulating disk 16, the axial velocity of machining tool with and radial velocity, the spacing or the angular dimension of groove 19,20 can be adjusted within the desired value.Cubic boron nitride) or ceramic tip in addition, when forming groove 19,20 by cutting tool, can use the CBN emery wheel (CBN: of its front end R (radius of curvature) very little (for example, about R0.1 or R0.2).When forming groove 19,20 with the superfinish emery wheel, concave portions is that coarse plain emery wheel in #80 to the #200 scope forms by granularity, subsequently, for the convex part of finishing in the surface to be machined forms groove with concave portions simultaneously, carry out one or more superfinish, abrasive machining and shot-peening (peening) processing.
Rotational speed by regulating disk 16, the axial velocity of machining tool with and radial velocity, can be with the spacing P of disk side groove 19,19
19Or the size of angle [alpha] and β is adjusted within the desired value.In addition, if necessary, can change the rotational speed of disk 16 or the travelling speed of change machining tool.At this moment, when adding man-hour, do not need to be provided for to change the mechanism of the rotational speed of processing device with constant speed.Therefore, the structure of this device can be simplified, therefore the cost that is used to form groove can be reduced.In addition, can form disk side groove 19,19 or power drum side groove 20,20 by rolling mill practice.When from respect to when the normal direction of an axial side surface 17 is observed, disk side groove 19,19 can have angle with respect to the circumferencial direction of disk 16, but is not limited to the principle shown in Fig. 1 and Fig. 2.When forming disk side groove 19,19 and power drum side groove 20,20 by cutting, remove the tiny burr that on surface to be machined, forms if desired, then after cutting, carry out grinding.
According to this embodiment recited above, the structure with a plurality of grooves 19,20 can be provided, this groove has improved traction coeficient, guarantees the serviceability of disk 16 and power drum 8 simultaneously.
Just, because groove 19,20 is formed on a side surface 17 and power drum 8 the two (both traction surface) of axial disk 16, during the degree of depth that is convenient groove 19,20 very little (degree of depth is not big especially), can guarantee traction coeficient fully.Therefore, can easily guarantee to be used to form the serviceability of the machining tool of groove 19,20, and therefore reduce manufacture cost.In addition, when forming groove 19,20 by rolling mill practice, can prevent that the finished surface that groove 19,20 forms thereon is damaged, and prevent the flexural fatigue variation.
In addition, in this embodiment, as mentioned above, power drum side groove 20,20 and disk side groove 19,19 are deflection relationship.Therefore, for example, the problem that the main area of contact of the contact area that can not roll (summation of the area of contact of the rolling contact area outside the groove 19,20) diminishes under certain pinion ratio.Therefore,, can prevent the excessive surface pressure in the rolling contact area or the generation of Metal Contact, and therefore can guarantee the serviceability of disk 16 and power drum 8 when operation this when device under the very little state of area of contact.
According to the foregoing description, can form the groove 19,20 that improves traction coeficient with low cost.That is to say, as mentioned above, when when observing with respect to the normal direction of a side surface (concave curvatures) 17 that forms groove 19,20, groove 19,20 with respect to the circumferencial direction angulation α of disk 16 and β (be formed on groove 19 or 20 and imaginary concentric circle X between angle), make and (satisfy relation α＜β) greater than the angle on its outer diameter side in the angle on the inner diameter side of disk 16.As mentioned above, groove 19,20 can form by this way, promptly under machining tool that is used to form groove 19,20 and a side surface 17 direct state of contact, in with constant speed rotating disk 16, machining tool is swung or is moved with constant speed along the diametric(al) (with axially) of disk 16.
Reason is because the peripheral velocity of the parts of being processed by machining tool is from becoming faster laterally along diametric inboard, and therefore, and is faster and become littler along with becoming of peripheral velocity with respect to the angle of circumferencial direction.Therefore, can reduce the number of operation, wherein machining tool directly directly contacts with surface to be machined or moves away from surface to be machined.And, do not need to change the amount of feed (feed speed) (for example, when it is mobile laterally along diametric(al), need feed speed is not adjusted to slack-off) of machining tool along diametric(al) according to along diametric processed position component.
Therefore, can carry out the processing work of groove 19,20 easily and form groove 19,20, and need not invalidly to increase the price of the device that is used to form groove 19,20 with low cost.In addition, when forming groove 19,20 with milling process, remove the tiny burr that is formed on the surface to be machined if desired, then after cutting, carry out grinding.
In addition, disk side groove 19,19 can have identical groove depth, groove width and pitch of grooves P with power drum side groove 20,20
19, P
20(P
19=P
20) or have the size (P that differs from one another
19≠ P
20).In this case, for example, wish to form one of them in disk 16 and the power drum 8, its serviceability is littler, so that have little groove depth.In addition, can form one of them in disk side groove 19,19 and the power drum side groove 20,20, its groove can form easily, so that have big groove depth.For example, can form power drum side groove 20,20,, maybe can form the disk side groove 19,19 that is formed in the concave curvatures, so that have big groove depth so that have big groove depth with concentrically ringed shape (or spiral-shaped).In any case, groove depth, groove width, the pitch of grooves P of (adjustment) disk side groove 19,19 and power drum side groove 20,20 are set according to needed traction coeficient, serviceability, processing cost etc.
19And P
20In addition, the angle that (adjustment) is formed on the rolling contact area between disk side groove 19,19 and the power drum side groove 20,20 is set in the same way.
Second embodiment
Fig. 4 and Fig. 5 illustrate the second embodiment of the present invention.In this embodiment, as shown in Figure 4, disk side groove 19,19 is formed around the concentric shape (or spiral-shaped) of the central shaft (running shaft) of disk 16.Simultaneously, as shown in Figure 5, when when observing with respect to the normal direction of the peripheral direction 18 of power drum 8, the circumferencial direction that power drum side groove 20,20 forms with respect to power drum 8 has angle.So in this embodiment, this angle forms and makes in the angle on the inner diameter side of this power drum 8 greater than the angle on its outer diameter side.
Except the groove with angle is that the surface of power drum side groove 20,20 and 20,20 formation place of power drum side groove is the spherical male surface (convex surface), form power drum side groove 20,20 other structures, effect is identical with method with top described first embodiment.
The 3rd embodiment
Fig. 6 to Fig. 8 illustrates the 3rd embodiment.In this embodiment, with the identical mode of above-mentioned second embodiment, disk side groove 19,19 is formed around the concentric shape (or spiral-shaped) of the central shaft (running shaft) of disk 16a and 16b.But, in this embodiment, need guarantee especially in pinion ratio under the state of traction coeficient ( disk side groove 19,19 is not formed on the whole side surface 17), 19,19 of disk side grooves are formed in the axial direction, and the outer surface 18 of power drum 8 rolls with the side surface 17 of disk 16a and 16b on that part that contacts.Specifically, as shown in Figure 9, when input side disk 1 and 1 and outlet side disk 6 and 6 between pinion ratio when being deceleration regime, on the outer surface 18 that 19,19 of disk side grooves are formed on power drum 8 and disk 1 and 6 input side and that part that outlet side internal surface 3 and 7 directly contacts.
Therefore, in this embodiment, as shown in Figure 6, be formed on corresponding to the disk side groove on the disk 16a of input side disk 1 19,19 only be formed on from along diametric inside part to inner end portion along the part of the side surface (input side internal surface) 17 (3) of axial disk 16a (1).On the contrary, as shown in Figure 7, be formed on corresponding to the disk side groove among the disk 16b of output disk 6 19,19 only be formed on from along the diametric outside to outer end portion axially the part of a side surface (outside internal surface) 17 (7) of disk 16b (6) in.
In addition, in this embodiment, as shown in Figure 8, when when observing with respect to the normal direction of the outer surface 18 of this power drum 8, the circumferencial direction that power drum side groove 20,20 is formed with respect to power drum 8 has angle.So in this embodiment, this angle forms and makes in the angle on the diameter inboard of power drum 8 greater than the angle on its diameter outside.But, in this embodiment, the number of power drum side groove 20,20 still less, and pitch of grooves and groove width are greater than the pitch of grooves and the groove width (see figure 5) of described power drum side groove 20,20 in a second embodiment.
In this embodiment, in the rolling contact area (towing area) in the whole transmission range of the transmission device of the continuous variable of toroidal, disk side groove 19,19 and power drum side groove 20,20 are not toward each other.But, between deceleration period, just at power drum side groove 20,20 and disk side groove 19,19 under rolling contact area state respect to one another, angulation between power drum side groove 20,20 and disk side groove 19,19.Under this deceleration regime, therein under the situation that disk side groove 19,19 is formed on corresponding to this embodiment in the part of rolling contact area, can reduce being applied to pivot 9 (seeing Fig. 9 and Figure 10), input turning axle 2 or the maximum load on the thrust ball bearing of supporting motive force cylinder 8 rotatably, thereby realize this device compactedness dimensionally.About this point, be applied to first and second embodiments equally.
Because other structures are identical with effect with first and second embodiments, will save the description of its repetition.
In addition,, be in pinion ratio under the situation of state of acceleration, on the input side that the disk side groove can only be formed on input side and outlet side disk and outlet side internal surface and the part that the outer surface of power drum directly contacts though do not illustrate.In addition, be under the state of " 1 " in pinion ratio, the disk side groove can only be formed in contacted that part of outer surface of direct and power drum.
In the above-described embodiments, wherein a kind of groove of disk side groove and power drum side groove has angle with respect to circumferencial direction, and another groove shaped becomes concentric shape (or spiral-shaped) (not having angle).But, can be configured such that disk side groove and power drum side groove have angle with respect to circumferencial direction.Under any circumstance, no matter how the pinion ratio of the transmission device of the continuous variable of toroidal allows, power drum side groove and disk side groove are deflection relationship in the rolling contact area.For example, when when observing with respect to the normal direction of rolling contact area, the angle between disk side and the power drum side groove and is more wished in the scopes of 5 to 45 degree in the scopes of 5 to 90 degree.
Though the present invention has described relevant exemplary embodiment, but can carry out variations and modifications without departing from the invention obviously for a person skilled in the art, so its purpose is to contain all such changes and modifications that belong in connotation of the present invention and the scope in accessory claim.
Claims (7)
1. the transmission device of the continuous variable of a toroidal comprises:
Pair of discs, it has sectional shape respectively is a bell-mouthed axial side surface, described disk with corresponding axial side surface state respect to one another, rotatably and supported concentrically with respect to one another; With
A plurality of power drums, along the circumferencial direction setting of described disk, each power drum has the contacted outer surface of an axial side surface that is made into described disk to these a plurality of power drums, wherein between a corresponding axial side surface
On an axial side surface of described disk, form a plurality of disk side grooves,
On the outer surface of described power drum, form a plurality of power drum side grooves, and
No matter velocity ratio is how, the rolling contact area between described disk and power drum, described disk side groove and power drum side groove are deflection relationship.
2. according to the transmission device of the continuous variable of the toroidal of claim 1, wherein
Described disk side groove only is formed on the radial component of an axial side surface of described disk, makes described disk side groove and power drum side groove meet discontinuously.
3. according to the transmission device of the continuous variable of the toroidal of claim 1, wherein
In the rolling contact area, when when observing with respect to the normal direction of described rolling contact area, described disk side groove and power drum side groove are with 5 to 90 angle of intersection of spending.
4. according to the transmission device of the continuous variable of the toroidal of claim 3, wherein
In the rolling contact area, when when observing with respect to the normal direction of described rolling contact area, described disk side groove and power drum side groove are with 5 to 45 angle of intersection of spending.
5. according to the transmission device of the continuous variable of the toroidal of claim 1, wherein
When the normal direction that forms surface thereon with respect to described each groove is observed, the circumferencial direction of one of them and the described disk or the power drum at least of described disk side groove and power drum side groove is with certain angle of intersection, and
Described groove is arranged so that the angle that limits between the angle that limits between the groove of radially inner side and the circumferencial direction is greater than the groove at radial outside.
6. the moving transmission device of the continuous variable of a toroidal comprises:
Pair of discs, it has the axial side surface that sectional shape is a toroidal respectively, described disk with corresponding axial side surface state respect to one another, rotatably and supported concentrically with respect to one another; With
Along the circumferencial direction setting of described disk, corresponding power drum has the contacted outer surface of an axial side surface that is made into described disk, wherein between a corresponding axial side surface for a plurality of power drums, these a plurality of power drums
A plurality of disk side grooves are formed on the axial side surface of described disk,
On the outer surface of described power drum, form a plurality of cylinder side grooves,
When the normal direction that forms surface thereon with respect to corresponding groove is observed, the circumferencial direction of one of them and the described disk or the described power drum at least of described disk side groove and described power drum side groove is with certain angle of intersection, and
Described groove is arranged so that formed angle between formed angle between the groove of radially inner side and the circumferencial direction is greater than the groove at radial outside.
7. the manufacture method of the transmission device of the continuous variable of a toroidal, this transmission transmission device comprises:
Pair of discs, it has the axial side surface that sectional shape is a toroidal respectively, described disk with corresponding axial side surface state respect to one another, rotatably and supported concentrically with respect to one another; With
Along the circumferencial direction setting of described disk, corresponding power drum has the contacted outer surface of an axial side surface with described disk, wherein between a corresponding axial side surface for a plurality of power drums, these a plurality of power drums
A plurality of disk side grooves are formed on the axial side surface of described disk,
A plurality of cylinder side grooves are formed on the outer surface of described power drum,
When the normal direction that forms surface thereon with respect to corresponding groove is observed, the circumferencial direction of one of them and the described disk or the described power drum at least of described disk side groove and described power drum side groove is with certain angle of intersection, and
Described groove is arranged so that the angle that is limited between the angle that is limited between the groove of radially inner side and the circumferencial direction is greater than the groove at radial outside,
Described manufacture method comprises:
Rotate a workpiece with constant speed, groove shaped is formed on this workpiece;
The instrument that is used to form groove is taken to the surface to be machined of described workpiece; And
Rotate described workpiece with constant rotating speed and keep described instrument and described workpiece between contact in, with constant speed along the described instrument of moving radially of described workpiece.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007-149923 | 2007-06-06 | ||
| JP2007149923A JP4915287B2 (en) | 2007-06-06 | 2007-06-06 | Toroidal continuously variable transmission |
| JP2007149923 | 2007-06-06 | ||
| JP2007151251 | 2007-06-07 | ||
| JP2007-151251 | 2007-06-07 | ||
| JP2007151251A JP4915288B2 (en) | 2007-06-07 | 2007-06-07 | Toroidal continuously variable transmission and manufacturing method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101349338A true CN101349338A (en) | 2009-01-21 |
| CN101349338B CN101349338B (en) | 2015-05-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200810110621.XA Active CN101349338B (en) | 2007-06-06 | 2008-06-06 | Production method of toroidal continuously variable transmission |
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|---|---|
| JP (1) | JP4915287B2 (en) |
| CN (1) | CN101349338B (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001254795A (en) * | 2000-03-08 | 2001-09-21 | Koyo Seiko Co Ltd | Toroidal type continuously variable transmission |
| JP2002039303A (en) * | 2000-07-28 | 2002-02-06 | Nissan Motor Co Ltd | Traction drive and method for grooving rolling element for power transmission |
| JP2003065409A (en) * | 2001-08-29 | 2003-03-05 | Toyota Central Res & Dev Lab Inc | Power transmission device |
| JP4196636B2 (en) * | 2002-10-17 | 2008-12-17 | 日産自動車株式会社 | Method for manufacturing rolling element for traction drive |
| JP4374225B2 (en) * | 2003-09-17 | 2009-12-02 | 株式会社ジェイテクト | Toroidal continuously variable transmission |
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- 2007-06-06 JP JP2007149923A patent/JP4915287B2/en active Active
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Also Published As
| Publication number | Publication date |
|---|---|
| JP4915287B2 (en) | 2012-04-11 |
| JP2008303922A (en) | 2008-12-18 |
| CN101349338B (en) | 2015-05-13 |
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