DE102005037940A1 - Flexible drive transmission for motor vehicle has shaft with longitudinal borehole and oblique hole with exit covered by movable pulley - Google Patents

Abstract

The conical-pulley flexible drive transmission (1) has a shaft on the pinion end and a shaft (3) on the power take-off end. The shaft has at least one borehole (20) extending longitudinally through the shaft, and starting from it, and oblique or cross hole, the exit of which is arranged on the peripheral surface in an area covered by a movable pulley (5), irrespective of its axial position.

Description

The invention relates to an automatic transmission in the form of a conical-pulley, as it is for example from the DE 10 2004 015 215 and other publications, as well as a method for its production and a vehicle equipped therewith.

automatic transmission in the broader sense, identifier converters whose instantaneous translation is itself independent dependent on from current or expected operating conditions, such as partial load, Thrust and environmental parameters, such as temperature, air pressure, Humidity, gradually or continuously changed. They include such Identification transformers operating on an electric, pneumatic, hydrodynamic, hydrostatic Principle or on a principle mixed from these principles based.

The Automation refers to a variety of functions, such as the approach, the translation choice, the nature of the translation change in different operating situations, where under type of translation change to For example switching one step at a time, skipping be understood by switching stages and the speed of adjustment can.

Of the Desired for comfort, safety and reasonable construction costs the degree of automation d. H. how many functions run independently.

In As a rule, the driver can intervene manually in the automatic sequence or him for limit individual functions.

Automatic transmissions in the narrower sense, as they are used today mainly in vehicle construction, usually have the following structure:
On the drive side of the transmission there is a starting unit in the form of a controllable clutch, for example a wet or dry friction clutch, a hydrodynamic clutch or a hydrodynamic converter.

To A hydrodynamic converter often uses a lock-up clutch in parallel with the pump and turbine part connected by direct power transmission increases the efficiency and by defined slip at critical Speeds dampening the vibration.

The Starting unit drives a mechanical, stepless or stepped Change gearbox having a forward / reverse drive unit, a main, range, Split group and / or a variator may contain. Gear transmission groups depending on the requirements of smoothness, space and transmission options, in countershaft or planetary design with straight or helical gearing designed.

The Output element of the mechanical transmission, a shaft or a Gear, drives directly or indirectly via intermediate shafts or a Intermediate stage with a constant gear ratio to a differential gear, which can be designed as a separate transmission or an integrated Part of the automatic transmission is. Basically, the gear is suitable for longitudinal and Cross installation in the vehicle.

to Adjustment of the translation In the mechanical transmission are hydrostatic, pneumatic and / or provided electrical actuators. A hydraulic pump after works the principle of repression, supplies pressure oil for the Starting unit, in particular the hydrodynamic unit, for the hydrostatic Control elements of the mechanical transmission and for the lubrication and cooling of the System. Depending on the required pressure and delivery volume gear pumps, Screw pumps, vane pumps and piston pumps, the latter mostly in radial design, in question. In practice, gear pumps and radial piston pumps have for this Purpose enforced, the gear pumps because of their low Construction costs and the radial piston pump because of the higher pressure levels and provide better controllability benefits.

The Hydraulic pump can be anywhere on the gearbox one constantly arranged by the drive unit driven main or secondary shaft be.

It Are stepless automatic transmissions known, consisting of a starting unit, a planetary reversing gear as a forward / reverse drive unit, a hydraulic pump, a variator, an intermediate shaft and a differential. Of the Variator in turn consists of two conical disk pairs and one Encircling. Each conical disk pair consists of one in axially displaceable second conical disk. Between these Conical pulley pairs running the belt, for example a push belt, a pull chain or a belt. about the adjustment of the second conical disk changes the running radius of the Umschlingungsorgans and thus the translation of the stepless Automatic transmission.

Infinitely variable automatic transmissions require a high pressure level to the conical disks of the variator in all operating points with the desired To be able to adjust speed and also with a sufficient base pressure largely wear-free to transmit the torque.

A The invention is based subtask is that by means of To improve a power transmission shown hydraulic fluid. A Another sub-task is to simplify parts production and also to influence the production costs low. A Another subtask of the invention is the durability of components and thus extend the life of such an automatic transmission. A further sub-task of the invention is based, which Torque capacity To increase such a transmission or greater forces through the components of the Transmission transmitted to be able to.

These Task parts are characterized by those set forth in the claims as well as in the Description also in connection with the figures explained invention solved with their training, in particular by a conical-pulley transmission with drive-side and output side cone pulley pairs, each a solid disk and a Wegscheibe, each on a drive side and a driven-side shaft and arranged via a belt for torque transmission are connectable, wherein at least one of the waves at least one in the longitudinal direction of Has wave extending bore, of the at least one to the lateral surface the shaft extending bore, such as oblique or transverse bore, goes out, their exit on the lateral surface is arranged in an area independent of the windscreen whose axial position is covered.

Thereby for example, a shortening the feed hole for the achieved hydraulic medium, the more economical and with increased process safety can be made.

Generally it can be in a conical-pulley transmission according to the invention be advantageous if at least one fixed disk in one piece with connected to the shaft.

Farther It may be advantageous, the distance disc rotatably, but axially relocatable over to connect a toothing with the shaft.

Especially It may be advantageous if the outlet of the bore from the lateral surface is arranged in the region of the toothing.

By this arrangement of the bore forms in the middle of the spline this practically a kind of ribs around the highly stressed holes, thereby a significant increase in strength is achievable as the tensions in the critical area around the hole exit from the lateral surface of the shaft between the teeth be significantly reduced.

It may prove appropriate if the tooth is omitted in the area of the hole exit, and it is furthermore advantageous may be two adjacent hole exit teeth on the inner diameter the distance disc omitted.

Generally it can be in a conical-pulley transmission according to the invention be advantageous to provide multiple bore exits on the circumference, wherein the bore exits are preferably arranged distributed uniformly over the circumference can.

at a conical-pulley transmission according to the invention are preferred the travel disc and the fixed disc of a cone pulley pair arranged in the circumferential direction associated with each other.

For this It may be advantageous if in the region of the internal toothing of the Take away an increase is provided, which is at the location of the lost tooth of the shaft engages, and / or in the region of the outer diameter of the shaft at least an increase is intended to lie in the area of the missing teeth of the travel plate comes, which constructively excluded incorrect assembly can.

Farther The invention relates to a method for producing a cone pulley transmission according to the invention, the tool for producing the external toothing of the shaft and / or the internal toothing of the spacer - viewed in the circumferential direction - only one Part of the profile generated and to manufacture another part angularly twisted becomes.

Of Furthermore, the invention relates to a vehicle with a transmission according to the invention.

The Invention will be described below with reference to schematic drawings, for example explained in more detail.

It represent:

1 a partial view of a belt pulley,

2 a substantially the 1 corresponding representation of an embodiment of the invention,

3 a partial section along the line III-III of 2 .

4 the detail IV of 3 .

5 the detail V of 3

6 Other possible embodiments according to section III-III

1 shows only a portion of a conical pulley, namely the driven by a drive motor, such as an internal combustion engine drive or input side of the conical-pulley belt drive 1 , In a fully executed conical-pulley transmission, this input-side part is assigned a complementarily designed output-side part of the continuously variable conical-pulley belt transmission, both parts being connected via a belt in the form of a link chain, for example 2 are connected to each other for torque transmission. The conical-pulley transmission 1 has a wave on the input side 3 on, in the illustrated embodiment in one piece with a fixed conical disk or fixed disk 4 is trained. This axially fixed conical disk 4 located in the axial longitudinal direction of the shaft 3 an axially displaceable cone pulley or spacer disc 5 neighboring.

In the presentation after 1 is the link chain 2 on the drive side cone pulley pair 4 . 5 shown in a radially outer position, which results from the fact that the axially displaceable cone pulley 5 is shifted in the drawing in the direction to the right and this displacement movement of the axially displaceable cone pulley 5 to a movement of the link chain 2 leads radially outward, resulting in a ratio change of the transmission in the fast.

The axially displaceable cone pulley 5 can be moved in a conventional manner in the plane of the drawing to the left, in which position the link chain 2 is located in a radially inner position (denoted by the reference numeral 2a is provided), in which a translation of the conical-pulley transmission 1 slow down.

The provided by a drive motor not shown torque is in the in 1 shown drive-side part of the belt pulley belt transmission via a on the shaft 3 stored gear 6 initiated, which on the shaft 3 via a rolling bearing in the form of an axial and radial forces receiving ball bearing 7 is stored, which is on the shaft 3 over a disc 8th and a shaft nut 9 is determined. Between the gear 6 and the axially displaceable cone pulley 5 there is a torque sensor 10 arranged, the one with an axially fixed expanding disc 11 and an axially displaceable expansion disc 12 provided Spreizscheibenkonfiguration 13 assigned. Between the two spreader discs 11 . 12 For example, rolling elements are in the form of the illustrated balls 14 arranged.

One over the gear 6 initiated torque leads to the formation of a rotation angle between the axially fixed expansion disc 11 and the axially displaceable expanding disc 12 , resulting in an axial displacement of the expanding disc 12 leads, and because of this arranged on ramps on which the balls 14 accumulate and so provide an axial displacement of the expansion discs to each other.

The torque sensor 10 has two pressure chambers 15 . 16 of which the first pressure chamber 15 is provided for an application of pressure medium as a function of the introduced torque and the second pressure chamber 16 is supplied with pressure medium, depending on the ratio of the transmission.

For generating the contact force with which the link chain 2 between the axially fixed conical disk 4 and the axially displaceable cone pulley 5 with a normal force beauf beat is a piston / cylinder unit 17 provided the two pressure chambers 18 . 19 has. The first pressure room 18 serves the translation-dependent change of the loading of the link chain 2 and the second pressure chamber 19 serves in conjunction with the torque-dependent controlled pressure chamber 15 of the torque sensor 10 to increase or decrease the contact force with which the link chain 2 between the conical disks 4 . 5 is charged.

The wave 3 has three channels for supplying pressure medium to the pressure chambers 20 , via which pressure medium is fed into the pressure chambers from a pump, not shown. Via an outlet-side channel 21 can the pressure fluid from the shaft 3 drain and recycled the cycle.

The admission of pressure chambers 15 . 16 . 18 . 19 leads to a torque and translation-dependent displacement of the axially displaceable conical disk 5 on the wave 3 , The wave 3 has to accommodate the displaceable cone pulley 5 centering 22 acting as a sliding seat for the displaceable cone pulley 5 serve.

As it is based on the 1 is easily apparent possesses the conical-pulley 1 in the area of the bearing points of the conical disk 5 on the wave 3 in each case a noise damping device 23 , For this purpose, the noise damping device may comprise a ring body and a damping insert or consist only of a damping insert.

In the 1 Reference numerals used also refer to the substantially comparable features of 2 , The figures are therefore to be regarded as a unit. For the sake of clarity, in 2 only those reference numerals are used which are above those of 1 go out.

In 2 is now the middle of the three channels 20 designed according to the invention. It can be seen that these are the central channel 20 forming hole 24 as a blind hole from the 1 and 2 is made on the right side, is significantly shorter than in 1 , Such blind holes are expensive to manufacture and require a very high degree of accuracy in manufacturing. The manufacturing effort and the requirements with regard to process reliability increase disproportionately with the length. The shortening of such a hole thus has a favorable z. B. on the manufacturing costs.

In the area of the bottom of this hole 24 branches the cross hole 25 from which several can be arranged distributed around the circumference. In the case shown, this transverse bore 25 shown as a radial bore; However, it can also be manufactured at a different angle than inclined bore. The hole 25 penetrates the lateral surface of the shaft 3 at a location that is independent of the operating state, ie z. B. of the set ratio, in an area that is always on the path plate 5 is covered.

By laying the cross hole 25 in the overlap area of the path plate 5 can the wave 3 be made shorter axially, which space can be saved. Also, by shortening the shaft 3 also result in a load reduction.

The mouth of the channel or the transverse bore 25 can, for example, in the area of the recess 26 , the centering surface 22 the shaft is adjacent to be arranged. This can be particularly advantageous when the teeth 27 that the way-plate 5 axially displaceable but non-rotatable with the shaft 3 connects, for example, is highly stressed by the torque transmission.

In many cases, however, the burden of toothing 27 not the most critical design criterion, leaving the mouth of the hole 25 can be placed in the field of this gearing, as in 2 is shown. Due to the arrangement of the transverse bore 25 in the teeth 27 instead of in the turn 26 , there is an advantage in that there is a larger moment of resistance, whereby the bending stress is reduced in the edge fiber. In addition, the moment of inertia is greater at this point, while the critical fiber through the cross hole 25 is disturbed, remains at about the same radius. This results in a significant reduction of the stresses in the critical area around the mouth of the transverse bore 25 between the teeth of the gearing 27 , The supply of hydraulic fluid is at the 1 and 2 identical, because the pressure chambers 15 and 19 communicate with each other and the path plate 5 connecting bores 28 which has the area of gearing 27 with the pressure room 19 connect. In the figures is the path plate 5 in its extreme left position corresponding to the Anfahrübersetzung or the Underdrive shown. Becomes the path plate 5 Now turn right towards the hard disk 4 shifted, so there is always a part of the cavity or the chamber 29 above the mouth of the transverse bore or the channel 25 so that the required fluid supply as well as in 1 is always guaranteed. As well as in 1 is there for the pressure room 16 two switching states, that of the axial position of the spacer plate 5 hang out. In the illustrated position are the control bores 30 exposed so that it is related, with a stopper 31 axially closed channel 20 and the pressure chamber connected to it via a channel, not shown 16 are depressurized or have only ambient pressure. Will now be the path plate 5 on the hard disk 4 To move, it passes over the tax holes 30 , where from a certain way the chamber 29 over the mouths of the tax holes 30 to come to rest. In the chamber 29 However, there is a dependent on the moment high pressure, which then on the tax holes 30 and the channel 20 also in the pressure chamber 16 is brought so that there is also high pressure. In this way, two switching states are realized, which control the contact force translation-dependent.

Furthermore, in 2 a plate spring 32 provided in the unpressurized state of the transmission 1 the path plate 5 brings in a predetermined axial position, whereby a translation of the transmission 1 can be set, which prevents excessive load, for example when towing the vehicle.

3 shows a section along the line III-III of 2 , wherein in the upper and lower half of the figure each have a different embodiment of the transverse bore or the channel 25 is shown.

In the lower part, the detail IV in 4 is shown enlarged again, is in the area of the mouth of the channel 25 in the lateral surface of the shaft 3 the tooth lying there is removed or not executed, so that - viewed in the axial direction of the shaft - a channel 33 arises, which can be traversed by the hydraulic fluid.

If such a cross section of the channel 33 is not sufficient, in addition, the two adjacent radially inwardly projecting teeth of the spacer 5 omitted, as in the area V and magnified in 5 is shown.

The elimination of each per channel 33 Up to three teeth can be made several times around the circumference in order to represent the required total flow area. Advantageously, this is done z. B. three times on the circumference with a uniform angular pitch and a divisible by three teeth z. B. at 30 teeth.

When mounting the travel plate 5 on the wave 3 It should be noted that the path plate 5 in the correct angular position to the fixed disk 4 is assigned to the required cross-section of the channel 33 to make sure.

In 6 Again, three different channel arrangements are shown, at A must be paid to the correct installation, while at B and C by design measures incorrect assembly can be prevented.

At A again the arrangement according to 5 as described above, this embodiment can be distributed several times around the circumference in order to obtain the required flow cross section, as well as the arrangements according to B and C.

At B, a constructive solution is shown, which excludes an incorrect assignment during assembly. For this purpose, according to the invention in the internal toothing of the spacer 5 an increase 34 provided exactly at the point between two originally existing teeth, at the wrong case a tooth of the shaft 3 to come to rest.

At C, a solution is shown on the shaft 3 one or two raises 35 be provided in the double gap at the points where in attempted false installation teeth of the spacer 5 to come to rest.

According to the invention, said expression can be produced particularly economically by virtue of the tool for rolling off the internal toothing of the spacer disk 5 only 10 teeth plus the tool design for the two attributable teeth and a correspondingly small diameter, so that the tool during manufacture analogous to a planetary three times in the bore of the path plate 5 rotates and thereby brings the total originally 30 teeth minus the three times formed on the circumference special design (the number of teeth is only an example).

Analog is for the production of the external teeth of the shaft 3 a tool originally used with 10, 20, 30 or correspondingly more teeth including the decaying teeth. In addition to the one-off tooling costs, this results in virtually no additional unit costs.

The invention is advantageously applicable to all CVT disc sets with oil guide to the piston / cylinder unit 17 through the path plate 5 in the field of gearing 27 , especially at high transmission torque.

The The invention is also applicable to the corresponding part of not shown output side cone pulley set.

1

cone pulley

2

link chain

2a

radial inner position of the link chain

3

wave

4

hard disk

5

movable disk

6

gear

7

ball-bearing

8th

disc

9

shaft nut

10

torque sensor

11

axial fixed spreading disc

12

axial movable spreading disc

13

Spreizscheibenkonfiguration

14

roll

15

first pressure chamber

16

second pressure chamber

17

Piston / cylinder unit

18

first pressure chamber

19

second pressure chamber

20

(three) channels (Feed)

21

Channel (the outlet side)

22

centering

23

Silencing device

24

(Central) drilling

25

Cross holes)

26

recess

27

gearing

28

connecting bores

29

Cavity / chamber

30

drillings

31

Plug

32

Belleville spring

33

channel

34

increase

35

increase

Claims (13)

Conical pulley belt transmission ( 1 ) with drive-side and output-side cone pulley pairs, each having a fixed disk ( 4 ) and a path plate ( 5 ), each on a drive-side and a driven-side shaft ( 3 ) and via a belt ( 2 ) are connectable to the torque transmission, wherein at least one of the shafts ( 3 ) at least one in the longitudinal direction of the shaft ( 3 ) extending bore ( 20 ), of which at least one to the lateral surface of the shaft ( 3 ) extending bore ( 25 ), such as oblique or transverse bore, whose outlet is arranged on the lateral surface in an area which is separated from the spacer plate (FIG. 5 ) is covered regardless of their axial position. Conical pulley belt transmission ( 1 ) according to claim 1, characterized in that at least one fixed disk ( 4 ) integral with the shaft ( 3 ) connected is. Conical pulley belt transmission ( 1 ) according to one of the preceding claims, characterized in that the travel disc ( 5 ) rotatably, but axially displaceable via a toothing ( 27 ) with the wave ( 3 ) connected is. Conical pulley belt transmission ( 1 ) according to claim 3, characterized in that the outlet of the bore ( 25 ) from the lateral surface in the region of the toothing ( 27 ) is arranged. Conical pulley belt transmission ( 1 ) according to one of the preceding claims, characterized in that the tooth is omitted in the region of the bore exit. Conical pulley belt transmission ( 1 ) according to one of the preceding claims, characterized in that two teeth adjacent to the bore exit on the inner diameter of the spacer disc ( 5 ) accounted for. Conical pulley belt transmission ( 1 ) according to one of the preceding claims, characterized in that a plurality of bore exits are provided on the circumference. Conical pulley belt transmission ( 1 ) according to claim 7, characterized in that the bore exits are distributed uniformly over the circumference. Conical pulley belt transmission ( 1 ) according to one of the preceding claims, characterized in that the travel disc ( 5 ) and the hard disk ( 4 ) of a cone pulley pair are arranged in the circumferential direction associated with each other. Conical pulley belt transmission ( 1 ) according to claim 9, characterized in that in the region of the internal toothing of the spacer disk an increase ( 34 ) provided at the location of the lost tooth of the shaft ( 3 ) intervenes. Conical pulley belt transmission ( 1 ) according to one of claims 9 or 10, characterized in that in the region of the outer diameter of the shaft ( 3 ) at least one increase ( 35 ) is provided, which in the area of the missing teeth of the washer ( 5 ) comes to rest. Method for producing a conical-pulley transmission ( 1 ) according to one of the preceding claims, characterized in that the tool for producing the external toothing of the shaft ( 3 ) and / or the internal toothing of the washer ( 5 ) - viewed in the circumferential direction - generates only part of the profile and is angularly rotated to produce another part. Vehicle characterized by a gearbox after one of the preceding claims.