DE2749047B2 - Circulating friction gear - Google Patents

Description

' Cos λ j - Cos \\ , where /?.fdsr is the maximum value and RJ is the minimum value of the Radius R _{w of} the rotating roller path of the central body? and λ] is the maximum value and aj is the minimum value of the intersection angle between the first and second axes

4. Transmission according to one of claims 1 to 3, characterized in that the carrier (84) has a cylindrical part (112, 114) which extends between the rotary roller tracks (92, 95) of the central body (78) and the wobble body / 80 ) extends and has openings (120, 122) for a rolling friction engagement of the respective rotary roller tracks at the two contact points (P1, P2) in the plane containing the first and second axes (46, 82).

5. A transmission according to claim 4, characterized in that the between the carrier (84) and the wobble body (88) arranged at axially opposite ends of the wobble body bearing means (96, 98) are movable in diametrically opposite directions relative to the carrier and a pair of have radially acting piston / cylinder units (144, 134) which can be acted upon by fluid, in order to position the bearing devices symmetrically about the axis intersection (S).

6. Transmission according to claim 5, characterized in that the cylinder (134) of the piston / cylinder units (144, 134) with the cylindrical Part (112,114) of the carrier (84) and the piston (144) are firmly connected to the storage facilities (96,98).

7. Transmission according to one of claims 2 to 6, characterized in that the bearing surfaces (94) of the swash body (80) are outer surfaces.

8. Transmission according to claim 7, characterized in that the bearing devices (96,98) for the The wobble body (80) consists of roller bearings (142), each of which is the bearing surface (94) of the wobble body (80) surrounded.

9. Transmission according to claim 7, characterized in that the storage facilities for the Swash body (80) made of hydrostatic bearings (142 ') with semi-cylindrical bearing surfaces (148) exist, which with the bearing surfaces (94) of the wobble body at diametrically opposite Pages are engaged.

10. Transmission according to one of claims 1 to 3, characterized in that the between the Carrier (320) and the wobble body (316) arranged bearing devices a rotatable cylinder (352) with mutually inclined inner and outer cylindrical bearing surfaces, the inner bearing surfaces determine the axis of the bearing equipment.

11. Transmission according to claim 10, characterized in that actuatable by fluid Means for adjusting the rotation of the cylinder (352) are provided.

12. Transmission according to claim 5, 6 or 11, characterized by an actuating device (236) on the outside of the housing for Controlling a pump (202; 379) supplying the fluid.

In a known transmission (DIi-OS 24 33 685) according to the preamble of claim 1 is a free Pivotability or at least a radial play of the

The wobble body is provided in the plane containing the first and second axes, around which the plane emerges Forced precession movement of the wobble body resulting torque for mutual pressing insert the central body and the wobble body, ϊ However, this radial play has certain shortcomings. So the wobble body can be radial vibrate when it rolls on the central body These radial vibrations of the wobble body can Damage to the rotating roller tracks and fluctuations in the oil film in the contact area of the rotating roller tracks cause. In addition, these vibrations cause fluctuations in the contact pressure, which are detrimental to proper functioning and the efficiency of the transmission. aside from that are the mechanical connections between the wobble body and other elements of the transmission complicated by the requirement of radial play

The object of the present invention is to reduce the radial play between the rotary roller tracks the friction body and the inadequacies associated with this game of the confessed gear eliminate and create a transmission of the type in question, its gear ratio in simpler Way can be changed.

This object is achieved according to the invention in an epicyclic friction gear according to the preamble of Claim 1 solved by the features of the characterizing part of claim 1 by the constant, fixed set angle of intersection between the first and second axes can be those listed above, on the Radial play between the wobble body and the central body based inadequacies are avoided and uniaxial bearings are used throughout for the friction bodies, which means a considerable j Represents simplification. Due to the adjustability of the cutting angle according to the invention, on the other hand, is a simple change of the transmission ratio possible.

It has already been proposed to eliminate the radial play (DE-PS 26 34 244) that the carrier rotatably mounted in the housing about the first axis in turn the wobble body with a fixed cutting angle for its movement with a double conical path in the circumferential direction about the first axis with the apex of the double-conical path coinciding with the intersection of the axes. In this proposed transmission, the transmission ratio is changed by axially displacing annular rotary rolling paths of the friction bodies. The contact pressure between the friction elements at the contact points is generated at this proposed transmission through along one of the axes acting facilities that y to the corresponding rotation roller paths of the oscillatory body or Zentralkör- act pers permanently. Such devices are advantageously also used in the transmission according to the present invention for pressing the friction bodies against one another.

Advantageous embodiments of the _h n transmission of the invention, in particular the rotational rolling paths of the friction body, the simple radial bearing for the friction body enable (to claim 2, known per se, for. Example, DE-OS

25 33 475; Claim 3, proposed in DE-PS

26 34 244), the carrier (claim 4), the storage _{device h} -> lines for the wobble body and their adjustability (claims 5 to 12) are in the subclaims. cited.

Between the carrier and the wobble body at axially opposite ends of the wobble body arranged bearing devices in the form of roller bearings, the bearing surfaces of the wobble body outer Areas are proposed in DE-PS 26 34 244 (to claims 5,7,8),

From DE-OS 24 33 685 it is known, piston / Zy-Hnder units to shift the rotary roller tracks of the central body and thus to change the Gear ratio to be used (to claim 5).

The following is a description of exemplary embodiments with reference to the drawings. It shows

F i g. I a longitudinal section through a transmission according to of the present invention,

Fig. 2 is a section through a rotary member that is in Transmission of FIG. 1 is incorporated, illustrated,

F i g. 3 shows a partial section along the line 3-3 of FIG. 2, fig. 4 shows a partial section along the line 4-4 of FIG. 2.

F i g. 5 is a plan view showing a half part of the FIG. 2 represents the component shown

Fig. 6 is a perspective part; isicht of the in Fig. 5 shown part,

F i g. 7 shows a partial section of another embodiment of the bearing arrangement which is used in the transmission according to FIG the present invention is used,

Fi ^. 8 is a side view of one of the components of FIG Bearing arrangement according to FIG. 7,

F i g. 9 shows an enlarged partial section along the line 12-12 in FIG. 3;

Fig. 10 is a partial section along the line 13-13 of Fig. 1,

11 shows a section along the line 14-14 of FIG. 13,

12 shows a longitudinal section through a modified one Embodiment of the transmission according to the present invention,

13 shows a partial cross section through the transmission according to FIG. 15 and

Figure 14 is an enlarged broken away perspective View of the eccentric control cylinder of the in F i g. 15 shown transmission.

a preferred embodiment of the entire transmission is shown in FIG. 1 shown. This gear has a closed housing 10 which is provided with a peripheral mounting flange 12 at one end that is directly connected to the housing or block of a motor or other suitable source of drive torque indicated by the dash-dotted lines left in Fig. 1 is indicated, can be connected. At its opposite end is the housing 10 provided with an inwardly directed flange 14 which delimits one end of a gear 16. An im central area arranged, inwardly directed ^! ar.sth 18 on the housing 10 separates the opposite End of transmission housing 16 from torque converter 20. As described in detail below is, the torque converter is partially with the housing 10 by means of another inward directed flange 22 connected.

The torque input to the transmission takes place via a conventional centrifugal clutch 24, which in the vicinity of the peripheral mounting flange 12 on the Housing is arranged and which has a drive pulley 26 with a central recess 28 through which torque transmission pins 30 extend for engagement with and bearing by an input shaft (not shown) suitably adapted in

the energy source is stored with which the transmission is connected in practice. The drive pulley 26 carries a fixed annular friction lining 32 on one side of a driven disc 34. The disc 34 can be engaged between the fixed friction lining 32 and an annular lining 36 by an annular piston 38 which is movable by means of hydraulic fluid or oil from an annular chamber 40 to the outside through a conduit 42 and under the control of a probe 44. When the drive disk 26 is not rotating, oil is pumped past the sensor 44 and the disk 34 of the clutch is in an uncoupled state. When the drive disk 2G is subjected to rotation, the oil in the channel 42 is moved outward by centrifugal forces and moved against the annular piston 38 until the output disk 34 is in engagement with the friction linings 32 and 36.

In the longitudinal direction of the transmission is located on one first transmission axis 46 a pair of concentric, torque transmitting shafts 48 and 50. The Central shaft 50 is toothed directly with the clutch drive disk 26 and can be attached to the clutch opposite end coupled to auxiliary engine components (not shown) or other devices that are in a direct drive relationship with the input torque to the transmission by means of the Drive pulley 26 are to be connected. The hollow shaft 48 is rotationally separate from the central shaft 50 independent and supported in the housing 10 on the axis 46 by bearings 52, 54 and 56. As from the The following description emerges, represents the hollow shaft 48 in the disclosed embodiment represents the output of torque converter 20 and the input of transmission 16. The torque output from the overall transmission takes place via a countershaft 58, which is connected to the hollow shaft 48 via the transmission 16 connected is.

As shown in Fig. 1, the transmission 16 in the form of a common gear train has a pair of gears 59 and 60 which are rotationally meshed with the hollow shaft 48 and are at all times in mesh with the gears 62 and 64, which on of the countershaft output 58 are freely rotatable. It should be noted that although the teeth of the respective gear sets 59, 62 and 60, 64 are shown disengaged, those gears are engaged by reverse idler gears (not shown) so that both gears of each set are in the same direction rotate. An engagement gear 66 is splined for common rotation with the countershaft 58 and is axially displaceable on that shaft. The gears 62, 66 and 64 are provided with mutually engageable axial gear sets 68 and 70 so that the gear 66 is in an intermediate position, as in FIG. 1, or held in positions in which it is engaged with one of the gears 62 and 64. Since the gears 62 and 64 are driven by the gears 59 and 60 in the same direction as the hollow shaft 48, a first forward gear ratio can be effected by meshing the coupling gear 66 with the gear 62. With this gear ratio, the torque is transmitted from the shaft 48 from the gear 59 via an intermediate gear (not shown) to the gear 62 and the coupling gear 66 to the output countershaft 58. A second forward gear ratio is achieved by only the coupling gear 66 in mesh with the gear 64 is brought so that the countershaft via the gear 60 and another intermediate gear (not shown) to the gear 64 and via the coupling gear 66 to the shaft 58. In this state, the coupling gear becomes

in 66 driven directly by a gear 72 which is normally freely rotatably mounted on the shaft 48 but is driven by the engagement of the axial teeth 74 with the gear 59.

An input torque that the clutch 24 with

π an angular speed is transmitted to the transmission 16 by rotating the hollow shaft 48 at an angular speed o) as a result of the operation of the torque converter 20 by continuously changing the speed ratio

in ω / «. Although the various components of the Torque converter that contributes to this operation, described in detail below, may be a Understanding of the basic operation can be achieved by noting that the

i-, torque converter 20 consists of three assemblies, which are movable as a unit or element; namely a first rotating body or central body 78, the is concentric about the first axis 46, a second Taumv.'körper 80, which is symmetrical about a second

) o axis 82 is arranged relative to the first Axis 46 is inclined by an angle λ and the first axis intersects at an axis intersection S, and a third body or carrier 84 which is concentric to the first axis and which is rotatable about the first axis 46. Of the

j-, third body 84 acts as a carrier with which the Angular position of the second axis 82 relative to the first axis 46 is maintained.

As shown in FIG. 1, the central body 78 of torque converter 20 from a pair of

4 (i conical parts 86 and 88 are formed which are serrated for direct rotation with the hollow shaft 48 and axially slidable thereon symmetrically to and away from the point S. The parts 86 and 88 are in the illustrated embodiment from each other

4-, biased away with the help of compression springs 90, wherein also other suitable devices such as a hydraulic system or a system of opposites helical keyways can be used for this purpose. The two conical parts

86 and 88 are identically shaped to define an outer rolling surface or rotary rolling path 92 having a variable radius /? ". with respect to the first axis 46. It is noted that the generatrix of each surface 92 is a curve with a large radius R _c which follows the minimum value (|) and the maximum value (I) of the radius R _w and the angle α, respectively Equation is related:

Cos xl - Cos 4 '

The torque converter wobble body 80 is essentially tubular in structure with concentric bearing and rolling surfaces 94 and 95 about the second axis 82, as shown in FIG. 1 shows These areas are doubled on opposite sides of the intersection point 5 noted that the rolling surfaces or rotary rolling path

nen 95 have the same radius R _b with respect to the axis 82 and that the surfaces 93 are in engagement with the surfaces 92 of the conical parts 86 and 88 at two contact points P 1 and Pl arranged at the same distance from the point S opposite.

The bearing surfaces 94 on the wobble body 80 are rotationally detected by bearing devices 96 and 98 which are carried as a unit by the third body 84 in a manner described below is described. Extends between the flange 22 on the housing 10 and the wobble body 80 in addition, a universal joint system .; 100 to the To prevent wobble bodies from rotating about the second axis 82 without in any way the nutation or To affect wobbling of the body 80, so 1 - that the second axis 82 is on a double conical The path about the first axis 46 can move symmetrically to the axis intersection S.

In the illustrated embodiment, the drives

u ~ i (iC rvGrpCr xrr uCri u / rCumGniCriiiVantjiCr & v an ümu Ϊ3ί * 't therefore rotationally connected to the output disk 34 of the clutch 24 by spline teeth 102. In addition, it can be seen from FIG Adjacent to the spline teeth 102 is rotatably supported independently of the shaft 48 by the aforementioned bearing 56 and also independently of the clutch drive pulley 26 by the bearing 104. At its opposite end, the body 84 is rotatably supported on the shaft 48 by a bearing 106 In addition, a central bearing bushing 108 is provided between the shaft 48 and a connecting ring or collar HO which is part of the body 84. An understanding of the manner in which the torque from the third body 84 acts on the wobble body 80 can be obtained by referring to Figures 2-6, in which the construction of the body 84 is fully illustrated.

As shown in FIG. 2, the body 84 is comprised of a pair of generally similar elongated ones Half parts 112 and 114, face to face on opposite sides of the connecting ring 110 by a series of thrust bolts 116 or other equivalent means are attached. Each half-part extends from the ring 110 as a cylindrical arrangement to bearing hubs 118. A middle portion of half parts 112 and 114 is broken away to provide diametrically opposed openings 120 and 122 in the assembled body create. It is noted that openings 120 and 122 expose the tapered portions 86 and 88 so that the rolling surfaces 92 on these portions pass through the body 84 are presented.

The bearing hubs 118 are similarly shaped to a set one-story fork section 124, the clear in fig. 5 and 6 and a pair of outwardly spaced, longitudinally extending having extending leg plates 126, each of which has an inclined screwing surface 128. At the two leg plates 126 of each fork ab- ω Section 124 a cylinder head bracket 130 is attached with the aid of screws 132. Each bracket 130 delimits one inwardly directed cylinder 134, the oil or other suitable hydraulic fluid a through channel 136 is supplied, which in the Bracket 130 is formed and with through channels 138 and 140 in each fork portion 124 in connection stands (Fig. 3).

In the exemplary embodiment of FIGS. 1 to 6, the bearing devices 96 and 98 each contain a series of rollers which are in engagement with the bearing surfaces 94 on the wobble body 80 and which are carried by an outer race 142. The outer race 142 is formed with a piston 144 that can be received in the cylinder 134. The race 142 is also provided with outer flats 146 which are slidable on the inner surfaces of the leg plates 126 of each fork section 124. It is noted that the pistons 144 of the outer races in the respective bearing assemblies 14 and 98 are diametrically opposed at opposite ends of the body 84. In view of this arrangement, the tubular swash body 80 can be adjusted by tilting it about the axis intersection 5, while oil is introduced into or emptied from the cylinders 134 of each bearing device 96 and 98. Such a rvippCinSiCnUng Crgiui, of course, CiHC EifiStCilüng \ jCT second axis 82, where the angle λ is between a minimum value «| and a maximum value «f changed. Such a change in the angle λ results in a simultaneous displacement of the points of contact Pi and Pl in the direction of the axis intersection point S or away from it. As a result of this movement of the points of contact, the radius R _{w of} the surfaces 92 on the conical parts 86 and 88 changes between a minimum value for <x \ and a maximum value for ot \. Since the radius Rb of the rolling surfaces 95 on the wobble body 80 remains constant, the ratio RbIRw or ρ changes directly with the angle <x.

The mode of operation of the torque converter 20 for transmitting a torque, which drives the third body 84 at a speed λ, to an output torque at infinitely changing speed ratios in the hollow shaft 48 at speeds ώ will now be explained. The rotation of the body 84 and consequently the coordinated orbital movement of the outer races 142 of the two bearing devices 96 and 98 cause a wobbling or nutation movement of the body 80, so that the axis 82 is guided on a double-conical path about the first axis 46, the Surfaces 95 and 92 are in frictional engagement with one another at the two points P 1 and P2. Since the wobble body 80 is prevented from rotating about the axis 82 by the universal joint system 100, the conical parts 86 and 88 as well as the shaft 48 with which they are splined at a speed ω corresponding to the equation ώ = <x (1 - ) driven. Since the radium Rb is always greater than the radium A ₁ ^, the function ρ always has a value greater than 1. As a result, ω is a direct reversal of oL

With reference to Figures 2 to 6, it is noted that the screwing surfaces 128 on the leg plates 126 of the fork sections 124 are inclined so that the axis of each cylinder 134 forms an angle with the axis 46 of the body 84. This angle is selected such that it corresponds approximately to half the value of the change in angle cc or an average value between λ j and <x. \ The pistons 144 are also designed to facilitate one degree of axial misalignment with the axis of the cylinder 134 in order to accommodate changes in the angle γ .

A modified one is shown in FIGS Embodiment of the storage devices 96 and 98 shown, wherein corresponding elements have the same reference numerals with a '. With the modified Embodiment of FIG. 7 and 8, the piston 144 'is therefore on a bearing body 142' with outer Flats 146 'arranged for sliding movement with respect to fork 124 in the same manner as that outer race 142 of the previously described bearing assemblies 96 and 98. In this embodiment however, the inner surface of the body 142 'is provided with a semi-cylindrical bearing surface 148 which directly can be brought into engagement with the bearing surface 94 on the tubular wobble body 80. the Surface 48 is provided with oil grooves 150 to provide a π hydrostatic bearing between body 142 'and to form the bearing surfaces 94 on the wobble body. The piston 144 'is modified and has a sliding sealing nipple 132, which is received in a central chamber i54, softer öi in the _> n is supplied in the same manner as the cylinder 134 'for actuating the piston 144'. The oil grooves 150 are in communication with the nipple 152 via through openings 156.

Although the modified embodiment of the FIGS . 7 and 8 in every respect like the storage devices 96 and 98 of the embodiment according to FIG. 1 to 6 works, the modified embodiment has, at least in some applications of the overall transmission, an improved mode of operation in that the friction between the bearings and the tubular wobble body 80 is reduced. Assuming that the friction losses of a hydrostatic bearing are comparable to that of a roller bearing, the r> friction is reduced by keeping the surface contact in the bearing as small as possible.

In the F i g. 1 to 4 and 9 to 11 show a fluid system both for lubricating the transmission and for controlling the actuation of the pistons 144 to change the intersection angle <x of the axes 46 and 82. As in Fig. 1, the inwardly directed flange 18 of the housing 10 supports a hub 189 which carries the bearing 54 and additionally delimits an annular chamber 190 to which oil is supplied via a through-channel 192 which is connected to an external oil supply, represented by a hose connector 194 The chamber 190 extends through the hollow shaft 48 with the aid of the through openings 1%, so that oil can flow from the chamber 190 through the annulus which extends along the entire length of the concentric shafts 48 and 50. The shaft 48 is also provided with radial through openings, such as. B. a through opening 198, provided through which oil, which is located between the shafts 50 and 48, due to the centrifugal force alone or combined with system pressure, under which the oil is pressed into the annular chamber 190, is thrown to the outside. Although various additional lubrication channels are shown in FIG. 1, a further description of these channels should be superfluous for an understanding of the present transmission.

The bearing hub 118 on the half-part 112 is provided with an inner oil collecting groove 200, which acts as a reservoir serves to supply oil to an oil pump 202 which is carried directly by the body 84. Although the Details of this pump below with respect to FIG. 9 to 11 can be described from FIGS. 1 to 4 sn that a through passage 204 extends from the pump 202, and with a annular through channel 206 in the connecting ring 110 is in communication. The ring-shaped one Through-channel 206 is also in communication with an axial through-channel 208, which connects to the Bearing hub 118 and fork 124 of the other half-part 114 extends. The connection with the cylinders 134 opposite ends of the body 84 takes place as described above in connection with FIGS and includes passageways 136, 138 and 140.

As is particularly clear from FIG. 9, the pump 202 is provided with a reciprocating Pump piston 210 provided, which is guided in a cylindrical bore 212, which has an inlet check valve 214 and a one-way outlet check valve? 16. The valve 214 stands with the annular groove 20G iiuci cmc Düi'CMgäiigäuiinüMg 218 and a slot

220 in connection, which serves as a small oil storage reservoir for the pump. The outlet check valve 216 communicates with the passage 204 in communication such that after reciprocating movement of the piston 210 pressure oil is conveyed to the passage 204 and finally to the piston cylinders 134 in one Way that the inclination of the wobble body 80 with respect to the axis 46 or the angle α is increased.

A drain valve assembly is located near the pump. As shown in Fig.9, this has Arrangement a piston 222, which can be moved against the check ball 224 to the Connection of the passage 204 to a drain valve 226 to open. It is noted that, when the check ball 224 is moved to an open position, oil from both the bore 212 ais also from the passage cana! 204 can be led directly to the drain valve 226.

The manner in which the FIG. 9 is actuated and controlled pump and drain valve assembly, goes from the F i g. 1, 10 and 11. Both the drain valve piston 21? as well as the piston 210 carry rollers 228, in a position in which they are in engagement with an annular track 230 which is pivotably mounted in the hub 189 by pins 232. On the side of the ring delimiting the path 230 opposite the pin 232, an arm 234 extends which is connected to an operating linkage 236 for a pivoting movement between three in FIG. 11 positions shown in engagement. If the path 230 is therefore held in a plane running exactly perpendicular to the axis 46, there is neither a pumping action nor the drain valve 224 is opened. The state of the pistons 144 will therefore be stable in this position of the path 230. A pivoting movement of the path 230 to the direction indicated by the line A in FIG. 11 causes the piston to move to pump oil into the cylinders 134. The drain valve piston 222! is withdrawn from the non-return ball 224 in this position of the track 230. When the track is pivoted to position B , the piston 222 will remove the check ball 224 from its seat, thereby removing fluid from the cylinders 134 and accordingly causing the pistons to move in the other direction.

12 and 13 show a modified embodiment of the present transmission

The transmission contains a housing 310 in which a central body 312 is mounted rotatably about a longitudinal axis 314. A wobble body 316 symmetrical to the longitudinal axis 318 is supported in the housing 310 with the aid of a carrier 320 which is rotatably supported about the axis 314 with the aid of the bearings 322 and 324. As shown, the carrier includes an outer cylindrical shell. One end of the support extends in one piece as a sleeve portion 328 that is supported by the bearings 324 and extends over the housing 310 hinauserstreckt It is noted that although the bearing 324 are not directly supported by the gear housing 310, the housing 310 rigidly in operation with a motor housing 311 is connected through which the corresponding storage for the · "> bearings 324 takes place.

The central body 312 has a hollow shaft 332 which is rotatably supported in the housing 310 by bearings 334 and 336 about the first axis 314 . the

WJ H 'l'jÄ, »· * 11» Λ ** * DI 1 / "* -λ

ττ ν »ιιν> ^ - * ^ # * i τι ugt im vi jCiLj \ .in ■ ΰΰΓ νΟΓϊ ivtrg ^ ii vsi * iTi! gCm - '* parts 338 and 340, which rotatably with the shaft 332 by Kt.i ^ Teeth 341 are connected, but are axially movable on this shaft symmetrically to the point 5 and away from this point due to an axial force supplied by a helical compression spring 342. While the magnitude of the mechanical force provided by coil spring 342 is substantially constant, other means of generating a variable axial force may be envisaged, such as, e.g. B. eir · fluid system j <> or a system of helical ramps or the like.

The wobble body 316 of the embodiment according to FIGS. 12-14 is a substantially cylindrical body 344 having a cylindrical inner surface 346 with a constant radius about the axis 318 over its entire length. The body 344 is rotatable with respect to an eccentric cylinder 352 mounted in bearings 348 and 350, the cylinder in turn being rotatably mounted in bearings 354 and 356 with respect to the carrier 320. Although embodiments of the present transmission are contemplated in which the cylindrical body 344, which forms the wobble body 316 , can rotate freely about the axis 318 and relative to the housing 310 , the cylindrical body 344 in the disclosed embodiment is adapted to rotate about the Axis 318 hindered in relation to housing 310 by arm 358. One end of the arm 358 is non-rotatably connected to the cylindrical body 344 and the

rf rrarran Y \ r exVtt * ryrt ■ rt wedge irr

Housing 310 secured by Oldham hinge 364.

The operation of the pumps 379 is the same as that described with respect to the embodiment according to FIGS. That is, fluid is pumped into and withdrawn from the passageway 376 to effect a rotational adjustment of the cylinder 352 and an adjustment of the angle <x. In other respects, the embodiment shown in Figures 12-14 is similar to the embodiment first described.

For this 7 sheets of drawings

Claims (3)

Claims; 1. Epicyclic friction gear with a housing, a central body on a first to the housing Fixed axis with rotating roller tracks around the first axis, both sides of a first perpendicular to the first axis arranged axially displaceable through an axis intersection plane are, with a wobble body held by a carrier on a second axis, which the to first axis at the axis intersection intersects, with rotary roller tracks arranged on a single component around the second axis, which is on both sides of a second arranged perpendicular to the second axis through the axis intersection plane are, the respective rotary rolling tracks of the central body and the wobble body in one third plane containing the first and second axes by means of mutual means Pressing the central body and the wobble body at two points of contact in rolling friction engagement stand, the> on both sides of the axis intersection are arranged, and wherein the rotary roller tracks of at least one of the two bodies are determined by generators that are opposite in the Inclined and symmetrical in relation to its axis are arranged in relation to the axis intersection and the generating d -_- r rotary roller paths of the two bodies are shaped such that the ratio of the radii of the rotary roller paths of the jo wobble body and the central body at the two points of contact in relation to their respective axes when the angle of inclination changes between the axes and with anial displacement of the rotary roller tracks of the central body symmetrically to the axis intersection, characterized in that the carrier (84; 320 ) in turn the wobble body (80; 316) with a fixed angle of intersection (<%) for its movement with a double-conical path in the circumferential direction around the first axis, the apex of the double-conical path coinciding with the intersection point (S) , and that the between bearing means (96, 98, 144, 134; 348, 350, 352) arranged on the carrier and the wobble body for the Ta surrounding body (80; 316) are designed to be adjustable for changing the angle of intersection between the first and second axes (46, 82; 314, 318). 2. Transmission according to claim 1, characterized in that the rotary roller tracks (95; 346) of the Swash body (80; 316) closed inner rotating surfaces and the rotating roller tracks (92; -) of the Central body (78; 312) are continuous outer rotating surfaces. 3. Transmission according to claim 2, characterized in that the rotary roller tracks (95; 346) of the wobble body (80; 316) are inner cylindrical surfaces and the rotary roller tracks (92; -) of the central body (78; 312) by oppositely inclined, convex generatrices are determined which have a radius of curvature R _c according to the equation