JPH0579551A - Conical belt pulley winding transmission device which is adjustable without step - Google Patents

Abstract

(57) [Abstract] [Purpose] Two mutually adjustable conical belt wheel pairs arranged on a driving side and a driven side are provided, and at least one conical belt wheel pair is loaded with a pressure medium by a torque sensor. By improving the steplessly adjustable conical belt wheel winding transmission of the type loaded to tension the winding member by means of an adjusting member such as a piston / cylinder unit, the loss efficiency is reduced at the same time. To increase the service life of the transmission and to provide a simple and inexpensive adjusting and control device, in particular by reducing the tension or the application force between the winding member and the conical belt wheel to the minimum necessary. The adjusting member 6 is based on the adjusted transmission ratio of the transmission and the pressure supplied by the torque sensor 24.
Means 25 are provided for defining the pressure that loads the.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable conical belt wheel winding transmission, which is provided with two mutually adjustable conical belt wheel wheels arranged on a driving side and a driven side. And at least one conical belt wheel pair is loaded to tension the wrapping member by a piston / cylinder unit or similar adjusting member which is pressure-medium loaded by a torque sensor. Regarding the type of

[0002]

Devices of this type are disclosed, for example, in DE-A-2828347 and DE-A-3538884. In order to generate a torque-based clamping pressure in this known device, a torque sensor is provided, at least between the drive and the drive-side conical belt wheel pair, which is designed as a torque-controlled valve. Has been. This valve is supplied by a pump and is at least partially closed when a torque shock occurs, whereby the pressure in the adjusting member (consisting of piston and cylinder) of the conical belt wheel pair is correspondingly increased. As a result, the tension of the wrapping member is increased correspondingly to the torque shock. In order to adjust the valve, the torque sensor has mutually facing discs with press cams between which there are rolling elements which are clamped together by the pressure created by the pump in the valve chamber. Has been done. When there is a torque shock from the drive side, the two disks are expanded and the axially moving disk shrinks or closes the outflow opening in response to the torque shock. Further, the drive moment is mechanically transmitted through the disc provided with the press cam, the valve is also closed in accordance with the transmitted torque, and the pressing force of the winding member (for example, the chain) is adjusted. This valve is always in the flow-through state except when the torque shock is extremely strong, and in addition to the pressure to sufficiently tighten the press cam to transmit the torque, a force corresponding to the medium flowing through the valve under pressure is applied. This force becomes permanent loss efficiency.

The same pump is also used to regulate the transmission ratio. This creates a pressure differential in the pressure chamber of the adjusting member (controlled, for example, via a control valve in the form of a square slider), so that in the pressure chamber of the adjusting member the higher pressure is created. A corresponding pressure medium is supplied,
This is done by drawing out the pressure medium from the other pressure chamber.

On the one hand, this pump produces a significantly higher pressure (the required pressure as a function of torque is several times the amount required to adjust the transmission ratio), and on the other hand
In order to ensure the required adjusting speed of the transmission ratio at this high pressure, it must be arranged to provide a significantly higher conveying force. With this known device, a high permanent loss efficiency occurs in proportion to the volume conveyed at a correspondingly high pressure. Moreover, in this known device or drive unit, relatively complex and expensive means are required for adjusting or controlling.

[0005]

SUMMARY OF THE INVENTION The object of the present invention is therefore to reduce the loss efficiency in a transmission of this type, and at the same time, in particular, to provide a tension or an application force between the winding member and the conical belt wheel. The minimum reduction is to increase the service life of the transmission. In addition, it must be cheap and provide optimal functions. Another object of the invention is to make the adjustment and control device necessary for adjusting the variable drive or the conical belt wheel drive transmission particularly simple and inexpensive.

[0006]

According to the invention, which has solved this problem, an adjustment is made for tensioning a conical belt wheel on the basis of the adjusted transmission ratio of the transmission and the pressure supplied by the torque sensor. Means are provided to define the pressure loading on the member. The transmission ratio of the transmission or the spacing between the conical belt wheels of at least one of the conical belt wheel pair and the pressure supplied by the torque sensor for adjusting the pressure on the adjusting member of the at least one conical belt wheel pair. Used for. According to the configuration of the present invention, the tension of the winding transmission or the pressing force between the winding transmission and the conical belt wheel cooperating with the winding transmission is minimized even in the partial load range. Therefore, the loss caused by the tension of the winding member and the conical belt wheel can be minimized. According to the present invention, the pressing force can be reduced to a necessary degree. The means for adjusting or adjusting the pressure for the adjusting member are in this case arranged to change, in particular multiply, the pressure supplied by the torque sensor by a predetermined factor, depending on this pressure and the adjusted transmission ratio. ing. This factor is based on the adjusted transfer ratio. That is, this factor changes with the transmission ratio. According to the invention, the pressure supplied or regulated by the torque sensor is modified by a predetermined percentage in response to this pressure, and then at least one regulating member of the conical belt wheel transmission is loaded with the modified pressure. To be done. This ensures that the pressure supplied by the torque sensor remains unchanged, for example when the chain is located radially inward on the drive side (i.e. when transmission is delayed). That is, the factor between the pressure supplied by the torque sensor and the pressure loading the adjusting member is one. Also, if the chain is located radially outward on the drive side (that is, transmission is premature),
The pressure supplied by the torque sensor for loading the adjusting member is reduced by 50%. That is, the factor 0.5 is multiplied.

Said means for reducing the pressure supplied by the torque sensor are connected on the one hand to the torque sensor and on the other hand to the adjusting member, the pressure supplied by said torque sensor and the transmission ratio of the transmission being It is particularly advantageous to have a pressure regulating valve (in particular a pressure reducing valve) which regulates the pressure applied to the regulating member of the at least one conical belt wheel pair which is regulated on the basis of The use of a pressure valve or a pressure regulating valve as the control member for regulating the pressure applied to the regulating member makes possible a particularly simple and inexpensive construction of the invention. This is because the pressure supplied by the torque sensor can be used directly through a transmission ratio mechanism to adjust such a type of valve. It is also possible with particular advantage to use pressure valves which are designed as piston or slider valves. A piston valve of this type is able to compensate for the static pressure produced, ie the force produced by the pressure difference across the valve, so that only a flow force is produced. This allows a particularly precise adjustment of the valve.

Said means for varying the pressure supplied by the torque sensor comprises an adjusting member, such as a piston / cylinder unit, which is loaded by the torque sensor and, in response to this applied pressure, It is adapted to define a pressure which loads said adjusting member of at least one conical belt wheel pair. In this case, the adjusting member for adjusting or varying the pressure supplied by the torque sensor is directly loaded by this pressure. This means that
This means that the pressure supplied by the torque sensor is formed on this adjusting member.

If the pressure regulating valve and the piston / cylinder unit that influences this pressure regulating valve constitute one component unit, that is, if the piston or the slider is provided in one common casing. , Because of the function and construction of the device according to the invention.

It is particularly advantageous if the pressure regulating valve is arranged such that it can be operated by means of a piston / cylinder unit which cooperates with the pressure regulating valve with a transmission element interposed. A transmission member of this type preferably has a lever, which pivots in dependence on the transmission ratio of the transmission (that is to say in dependence on the relative position of the at least one slider pair). It is possible to turn around. A pivot point of this type can be provided in a particularly simple manner on an axially displaceable component (eg rod or slide). The axially displaceable component is, for example, axially displaceable on the basis of at least one axially displaceable disc of the transmission. Such components are for this purpose connected directly to one of the axially displaceable disks of the transmission, for example in a form connection.

According to the invention, each conical belt wheel pair can be loaded for tensioning the winding transmission by means of an adjusting member (for example a piston / cylinder unit) which is pressure-mechanically loaded by a torque sensor. In this case, the two adjusting members are not directly loaded with the pressure provided by the torque sensor, as described above, but this pressure is in the form according to the invention, by the pressure supplied by the torque sensor and by the conical belt. It is corrected on the basis of the transmission ratio of the transmission, which is adjusted according to the desired or required pressing force between the vehicle and the winding member.

In order to be able to regulate the pressure supplied by the torque sensor by means of the pressure regulating valve, it is necessary to produce the desired leakage on the regulated pressure side, that is to say behind the pressure regulating valve. is there. This leak is regulated, for example by means of a valve, or it occurs in an adjusting element provided for tensioning the conical belt wheel pair. It would be advantageous if there were about 200 ccm / min of leak flow for each conical belt wheel pair.

Particularly when the device according to the invention is used in motor vehicles, it is particularly advantageous if the transmission ratio change of the transmission is controlled by the pressure medium. To this end, at least one moment-based circulation circuit, which is provided for controlling the transmission ratio, can be supplied by at least one pump and is axially displaceable in at least one conical belt wheel pair. Conical belt car
It is connected to an adjusting member which applies a force based at least on the moment and the transmission ratio. For a possible arrangement and configuration of the adjusting elements provided on the pair of conical belt wheels, see German Patent DE 4036683.9. It is particularly advantageous if a pressure-regulating valve is provided at least in the moment-based circulation circuit, at least when using an adjusting element for applying a force that is at least moment-dependent and that is based on the transmission ratio.

A pressure based on at least the moment and the transmission ratio is applied to the axially movable conical belt wheels of the drive side and driven side conical belt wheel pairs, respectively.
A particularly advantageous configuration for the functioning of the device according to the invention is obtained if the adjusting members are connected in parallel. In this possible configuration, two circulation circuits are provided, one circulation circuit being provided only for adjusting the transmission ratio, and the other via the conical belt wheel and the winding member. The pressing force between and is defined or adjusted. In such a configuration, the pressure medium is supplied to the two pressure medium circulation circuits by one pump having different pressure outlets, but each of the two pressure medium circuits is provided by one pump. Is particularly advantageous. Thereby, at least the pump provided for producing the pressure according to the moment can be configured to carry a volume in which the leakage loss is compensated in any case. However,
The hydraulic energy for the pressure portion, which is proportional to the moment (excluding leakage), virtually does not have to occur.
This is because the pressure medium, e.g. oil, only needs to be pumped back and forth, i.e., exchanged, between the adjusting members, as the volume contained in the adjusting member changes at each moment, at least in accordance with the moment, with the adjustment based on the transmission ratio. Because it is good.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction of the present invention will be described in detail with reference to the embodiments shown in the drawings.

In FIG. 1, a conical belt wheel pair 1 on the drive side fixed to a drive shaft I driven by an engine so as to rotate together with the drive shaft I, and a driven shaft II on the driven shaft II. 2 is a schematic illustration of a conical belt winder transmission with a conical belt wheel pair 2 fixed for rotation with II. Each conical belt wheel pair has a conical belt wheel 1a or 2a that is movable in the axial direction, and one conical belt wheel 1b and 2b that are fixed in the axial direction. Two
A winding member configured as a chain 3 for transmitting torque is provided between the pair of conical belt wheels.

The conical belt wheel 2a, which is movable in the axial direction, is provided with a force related to the transmission ratio by the disc spring packet 4. This force exerts a strong force on the chain 3 when the chain 3 is within the radial inner range of the drive side conical belt wheel pair 1, and the chain 3 is within the radial outer range of the drive side conical belt wheel pair 1. The chain 3 is configured to exert a weak force at one time.

The disc spring packet 4 is supported in its radially outer region by a disc 2a which is movable in the axial direction.
The radially inner region is supported by the axially fixed component (piston 5) of the piston / cylinder unit 6. The axially movable and rotatable cylinder part 7 of this piston / cylinder unit 6 is rigidly connected to the axially movable conical belt wheel 2a.

In the conical belt wheel pair 1 on the drive side as well, the axially displaceable disc 1a is connected to the axially displaceable annular cylinder part 8 of the piston / cylinder unit 9. .. The co-rotating but axially fixed piston part of the piston / cylinder unit 9 is designed here as a ring piston 10.

A piston / cylinder unit 11 is connected to the inside of the piston / cylinder unit 9 in the radial direction, mechanically parallel to the piston / cylinder unit 9. Of the piston / cylinder unit 11,
A cylinder part 12 which is axially fixed and rotatable with the drive shaft I is rigidly connected to the piston part 10 of the outer piston / cylinder unit 9 and moves axially of the outer piston / cylinder unit 9. The piston part 13, which is possible but rotatable with the drive shaft I, is rigidly connected to the cylinder part 8 of the outer piston / cylinder unit 9.

The pump 14 is driven via a drive shaft I,
The pump 14 interposes a pressure regulating valve 15 (which may be configured as a slider with one angled edge), which is controlled or regulated in relation to the desired or required transmission ratio, through which a pressure medium is pumped via a conduit 16. Supply into the pressure chamber 11a of the inner piston / cylinder unit 11. Pressure control valve 1
Depending on the position of 5, the pressure medium is supplied via the conduit 16 into the pressure chamber 11a, which causes the chain 3 to move outwards in the conical belt wheel pair 1 against the spring force of the disc spring packet 4. The pressure medium is guided through conduit 17 back to the sump by a corresponding position or control of valve 5. The pump 14 is a pressure medium (eg oil)
Is sucked up through the filter. A safety valve 19 for limiting the maximum allowable pressure is arranged between the pump 14 and the pressure regulating valve 15.

The pump 14 provided for adjusting the transmission ratio requires a very low power output, which results in a higher efficiency than in the prior art. This is because the pump 14 has only a small pressure chamber 11a, and therefore only needs to pump about 1/4 of the volume required here.

A pump 20 is provided for producing a pressure according to the transmitted or generated torque,
The pump 20 includes a pressure chamber 6 of a piston / cylinder unit 6 of a driven conical belt wheel pair 2 via a conduit 21.
a, and into the pressure chamber 9a of the piston / cylinder unit 9 provided radially outside of the drive-side conical belt wheel pair 1. From the conduit 21, a conduit 22 communicates with the pressure chamber 24a of the torque sensor 24. The torque sensor 24 is configured as a torque-controlled valve, and is a conical belt wheel pair 1 from the drive unit or the engine to the drive side.
Torque is transmitted directly to. The torque sensor 24 has a known type (see German Patent DE 28347), an axially stationary cam 24b and an axially movable cam 24c. These cams 24b, 24c
Each has an inclined surface. Between these cams 24b and 24c there is provided an expansion body configured as a ball 24d. Depending on the torque generated between the two cams 24b and 24c, the outflow opening 24e is correspondingly closed or opened via the cam 24c, which acts as a control piston, whereby in the pressure chamber 24a and in the conduits 21,22. Then, a pressure corresponding to the torque generated in the torque sensor 24 is formed.

A safety valve 20a is connected downstream of the pump 20 in order to limit the maximum pressure. The pressure supplied from the torque sensor 9 does not directly load the pressure chambers 6a and 9a of the piston / cylinder units 6 and 9 but
It is adjusted by the device 25 according to the adjusted transmission ratio of the transmission. The device 25 has a pressure regulating valve 26, which is connected to the pressure chamber 24a of the torque sensor 24 via conduits 21 and 22. The pressure regulating valve 26 is configured as a piston valve, the piston 27 of which moves or regulates in accordance with the pressure supplied to the torque sensor 24 in order to regulate the pressure loading the piston / cylinder units 6, 9. Be done. On the output side or the discharge side, the pressure adjusting valve 26 is connected to the pressure chambers 6a and 9a via conduits 28 and 29. The discharge side and the suction side of the pressure regulating valve 26 are connected to each other via a check valve 30. The check valve 30 is arranged so as to be closed in the direction from the suction side to the discharge side.
In the illustrated embodiment, the check valve 30 includes the torque sensor 2
Conduit 22 and conduits 28,2 directly pressure loaded by
It is provided between 9 and.

In order to adjust or change (in particular reduce) the pressure supplied by the torque sensor 24 to the required or desired pressure (which loads the piston / cylinder units 6 and 9) by means of the pressure regulating valve 27, Said device 25 has an adjusting member configured as a piston / cylinder unit 31. The pressure chamber of this adjusting member is directly loaded by the pressure supplied by the torque sensor 24. The piston / cylinder unit 31 acts on the pressure regulating valve 26 via a transmission mechanism configured as a lever mechanism 32.

The lever mechanism 32 has a lever 33, one side of which is loaded by a piston 31a of a piston / cylinder unit 31, and the other side of which is movable and a member for adjusting pressure, that is, a pressure regulating valve. It is supported by a piston 27 of 26. The lever 33 acts as a transmission lever. For this reason, the lever 33 is supported so as to be pivotable about the pivot center point 34. The turning center point 34 is movable between the contact point 33a having the piston 31a and the support point 36 of the piston 27. Pivot center point 34 for lever 33
Moves in accordance with a change in the transmission ratio of the transmission, the transmission ratio acting via the lever 33 is also the conical belt wheel pair 1 provided on the drive shaft I and the conical belt wheel provided on the driven shaft II. It is based on the transmission ratio adjusted between pair 2.
In the illustrated embodiment, the pivot point 34 is provided on another lever 35, which is axially displaceable,
The conical belt wheel 2a on the side of the driven shaft II can be formally connected, whereby the conical belt wheel 2a can be moved in the same direction as the axial movement.

By means of the pressure adjusting device 25, the pressure supplied by the torque sensor 24 is adjusted, in particular reduced, according to the adjusted transmission ratio.

The factor for correcting the pressure regulated or supplied by the torque sensor, which loads the regulating member (piston / cylinder unit 6, 9), is based on the transmission ratio regulated by the lever mechanisms 33 and 35. The reference numeral 34a indicates an extreme position that the turning center point 34 can occupy. At the position 34a of the turning center point 34 (or lever 35), the chain 3 exists on the innermost side (that is, the smallest radius) in the radial direction of the conical belt wheel pair 1, and the outer side in the radial direction of the conical belt wheel pair 2 (that is, the smallest radius). It corresponds to the transmission ratio of the transmission, which is present in the largest radius). This transmission ratio of the transmission corresponds to the maximum possible reduction of the rotational speed from the drive shaft I to the driven shaft II. That is,
This means that the driven shaft II has a lower rotational speed than the driving shaft I. In this transmission ratio adjustment, in order to be able to transmit the generated torque,
It is necessary to maximize the application force between the conical belt wheel pair 1, 2 and the chain 3. As can be seen from the drawing, in this transmission ratio adjustment, the pivot point 34a lies on the load transmission point (abutment point 33a), so that the force exerted by the piston 31a practically affects the pressure regulating valve 37. Don't give. This is because the lever 33 does not transmit at this position of the turning center point 34a. As a result, the pressure chambers 6a and 9a are connected to the torque sensor 2
It is loaded virtually directly by the pressure supplied by 4.

The other extreme position of the turning center point 34 is indicated by reference numeral 34b. This position 34 of the turning center point 34
b corresponds to the transmission ratio adjusting position of the transmission in which the chain 3 is present at the maximum radius of the conical belt wheel pair 1 and at the minimum radius of the conical belt wheel pair 2. At this transmission ratio adjusting position, torque is transmitted from the drive shaft I to the driven shaft II. That is, the driven shaft II rotates faster than the driving shaft I. At the position 34b of the turning center point 34, the lever 33 moves to 2
Acting as an arm-shaped lever, the turning force applied to the lever 33 by the piston 31a acts strongly on the piston 27 of the pressure regulating valve 26. At this transmission ratio of the levers 33, 35, i.e. after the pressure regulating valve 26, the weakest pressure is produced. By means of the pressure adjusting device 25, the pressures which load the pressure chambers 6a, 9a of the piston / cylinder units 6, 9 are additionally adjusted on the basis of the transmission ratio, the pressure also being based on this transmission ratio. The pressure provided by the torque sensor 24 is utilized to adjust the. That is, this pressure supplied by the torque sensor 24 acts on the piston 27 of the pressure regulating valve 26 via the piston / cylinder unit 31 and the lever mechanism (lever 33 + lever 35). The pressure supplied by the torque sensor 24 and the piston / cylinder unit 6,
The pressures and ratios that are actually created in 9, as well as the changes in this ratio, are influenced by correspondingly configuring the piston / cylinder unit 31 of the lever 33 and the lever 35.

Since the piston / cylinder units 11 and 9 are connected in parallel, the force exerted on the conical belt wheel 1a by the pressure adjusted by the pressure adjusting device 25 is the piston portion 13 by the pressure based on the transmission ratio.
Added to the force that is formed on.

A pump 20 for producing a moment-based pressure, which is modified on the basis of the transmission ratio by means of a pressure regulating device 25, is in each case arranged in the conduit and in the adjusting member (piston / cylinder unit 6, 9). It is only necessary to pump out a volume that is compensated for the leakage losses that occur and the volume expansion caused by the widening of the conduit or the adjustment member. However, except for leakage losses, it is not necessary to generate hydraulic energy proportional to this moment or after the pressure regulator 25 for the pressure part based on moment and transmission ratio. This is because the pressure medium need only be reciprocally transported, that is, exchanged, in order to compensate for the volume change in the pressure chambers 9a and 6a at the same time as the change in the transmission ratio. The output required for the pump 20 is
It is within 1/6 of the total output required in the conventionally known device. Therefore, the total output required by pumps 14 and 20 is significantly smaller.

The drive unit or transmission is the first for driving the output shaft III in one direction (for example, forward direction) behind the conical belt wheel pair 2 when viewed from the driven side, that is, the direction in which the force flows from the engine. The first friction clutch 38 and the second clutch 37 for driving the output shaft III in the other direction (for example, the backward direction) are provided.

The second friction clutch 37 includes a driven portion 37a having a friction surface, which is fixed to the drive shaft II.
It comprises a pressure plate 37b configured as a piston with an anti-friction surface, which is axially displaceable on the part 37a, but which rotates with this part 37A. Further, the second friction clutch 37 has a clutch disc 37c fixed to the shaft III so as to rotate together with the shaft III, and the friction range of the clutch disc 37c opposes the friction surface. Axial tightening is possible between the surfaces. Driven part 37a and pressure plate 37
A pressure chamber 37d is formed between it and b.

The first friction clutch 38 is, for example, axially fixed to the transmission casing and has a non-rotatable counter pressure plate 38a having a counter surface, and moves axially with respect to the counter pressure plate 38a. However, it also comprises a pressure plate 38b with a friction surface 38c configured as a piston, which rotates with it against the pressure plate 38a. The first friction clutch 38 further has a clutch disc 37c, and the friction range of the clutch disc 37c can be tightened in the axial direction between the counter pressure plate 38a and the pressure plate 38b. Clutch disc 38c
Has an outer gear 39a of the planetary gear transmission 39, and the sun gear 39b of the planetary gear 39a has an output shaft II.
It is fixed to rotate with I. The planetary gears 39c, which are divided and arranged in different types, are supported by or driven by the drive side portion 37a of the friction clutch 37. The piston 38b limits the pressure chamber 38d.

Pressure plate or piston 37
Since b and 38b are urged in the releasing direction by a force accumulator (for example, a disc spring) as is known, when the pressure in the pressure chambers 37d and 38d is small, the corresponding clutches 37 and 38 are completely opened. However, this results in virtually no transmission of torque and tensile moment to the corresponding clutch discs 37c, 38c.

In order to supply pressure to the two pressure chambers 37d and 38d, the pressure regulating valve 15 and the two clutches 37 and 3 are provided.
The first switching valve 40 and the second switching valve 41 are disposed between the first switching valve 40 and the second switching valve 41. The first switching valve 40 is connected via a conduit 40a to the pressure medium circulation circuit supplied by the pump 20, and via a conduit 40b to the pump 14
Is connected to a pressure medium circulation circuit supplied by. On the outlet side, the switching valve 40 is connected on the one hand to the second switching valve 41 via a conduit 42 and on the other hand to the conduit 16
pressure chamber 1 of piston / cylinder unit 11 via a
It is connected to 1a. This piston / cylinder unit 11 influences the transmission ratio of the conical belt wheel transmission. In the illustrated embodiment, the switching valve 40 is a so-called 5 /
It consists of a two-stroke valve. Two clutches 3
Switching valve 41 provided between the switching valves 40 and 40
Is constituted by a so-called 4/2 stroke valve. The clutches 37, 38 are connected via a switching valve 40 to a pressure-medium circulation circuit having a torque-based pressure or to a pressure-regulating valve, depending on predetermined operating parameters (for example, in a motor vehicle with a transmission of this type). It is connected to a pump 14 which creates a pressure based on 15. In addition, this switching valve acts such that either one of the friction clutches 37, 38 can be selectively engaged, that is to say loaded by the pressure medium. As a result, through the switching valve 41, it is possible to select between forward traveling in which the clutch 37 is connected and reverse traveling in which the clutch 37 is disengaged and the clutch 38 is connected. Switching of the valve 41 can be done directly by a manual,
Alternatively, it is done indirectly via an adjusting device which detects the corresponding position of the select lever for adjusting the driving module of the motor vehicle.

In the drawing, the switching valves 40 and 41 are the same as the switching valve 4
0,41, in relation to the conduits connected to 0,41, the position for starting the drive unit or the conical belt wheel transmission, i.e. the drive shaft I required for producing the effect of the torque on the output shaft III. In position (for introducing torque transmission). When starting the forward drive during this torque-forming stage, the pressure chamber 37d is connected to the pump 14 via valves 41, 40, which is based on the regulation or control of the pressure regulating valve 15. Form pressure. In this starting process, the pressure regulating valve is regulated via the regulating device 43. This adjustment can be carried out on the basis of the fuel supply adjusting element, and furthermore, the slip formed by the corresponding clutches, and possibly other parameters such as engine temperature, drive module (e.g. normal driving, sports driving, forward driving). The travel can be performed based on the position of the select lever that defines travel (reverse travel). The coordinator may have a processor with a memory in which the only value for the starting phase is read. In this case, this only value is, as is known,
It can always be realized during driving. In this case, this value is
It corresponds to a predetermined position or a corresponding operation of a member that influences the fuel supply (for example, an accelerator pedal).

The pressure regulating valve 15 is constituted by a proportional valve which, as mentioned above, is assigned to different parameters which are stored in the regulating device or which can be detected, for example, even at start-up. It is loaded by the electronic regulator 43 (processor) with the voltage obtained. As a result, a predetermined engine speed for starting can be adjusted according to the position of the accelerator pedal, for example. If the actual speed of the engine or drive shaft 1 is lower than the target speed, the pressure in the conduits 16, 42 is increased via the pressure regulating valve 15 (proportional valve). This is an electric adjustment member 1
This is done by a corresponding change in the voltage at 5a, which causes the clutch 37 to be further engaged.

During the starting stage or torque forming stage,
By the torque sensor 24, the conical belt wheels 1a, 1b; 2a, 2 are subjected to torque impact or torque change.
The pressure or tension exerted on the chain 3 by b is adjusted accordingly in order to prevent the chain 3 from spinning. The pressure medium circulation path based on the generated torque is automatically adjusted mechanically during the start-up phase without the influence of electronics or external influences. This self-regulation of the circulation path supplied by the pump 20 (which creates a pressure based on the generated torque) allows the valve 15 which is expensive compared to the valves 40, 41 to be moved during the torque generation phase or It can be used for forward and reverse clutches during the start-up phase.

In the configuration of the illustrated embodiment, it is premised that the conical belt wheel winding transmission does not require adjustment of the transmission ratio at startup. Because, at the time of start-up and during the start-up phase, correct transmission by means of a disc spring packet (two conical belt wheels 2a, 2b clamped together axially) provided on the secondary or driven side conical belt wheel pair 2. This is because it is compensated that the ratio is obtained.
At this transmission ratio, the chain 3 is wound around a primary conical belt wheel pair 1 having a small diameter and a secondary conical belt wheel pair 2 having a large diameter. This means that there is a maximum speed reduction between the drive shaft 1 and the driven shaft 2.

After the start-up phase, ie after the clutch 37 has been engaged (which means that there is no slip in the friction clutch, or a predetermined slip, for example for vibration isolation), the pressure chamber of the clutch 37. 37d is valve 40
Is switched by the pump 20 and is connected to a pressure medium circulation path that forms a pressure based on the generated torque. Furthermore, the pressure part or circulation path based on the transmission ratio is connected to the piston / cylinder unit 11.
In this case the valve 40 is in the position indicated by the square.

The mode of action or the mode of adjustment described in connection with the clutch 37 is also connected to the clutch 38 when the valve 41 is switched. However, other known rotational direction reversing devices can be used instead of the reverse traveling friction clutch 38 (first friction clutch), so that the clutch 38 and thus the valve 41 can be omitted.

The task of switching the valve 40 from the left position to the right position is at the latest when the transmission ratio of the transmission can be changed to a smaller or larger direction, ie a higher rotation of the driven shaft II. A number of directions, or higher speeds of the vehicle, must be made when changing directions.

The pressure for adjusting the corresponding transmission ratio via the pressure regulating valve (proportional valve 15) after start-up is, as mentioned above, adjusted according to the vehicle parameters, in particular the engine parameters and the fuel supply member parameters. It

In the illustrated embodiment, the torque sensor 2
4 or a valve 44 (pressure limiting valve) is provided in the outlet circuit of the torque sensor 24. The valve 44 has a minimum pressure of, for example, 2 bar even when the torque is small in the circulation circuit having a pressure based on the torque. Guarantee to be maintained. This minimum pressure is based on the return force of an energy accumulator such as a disc spring that loads the piston or the pressure plate 37b of the clutch 37 or the piston 38b of the clutch 38 in the releasing direction. The minimum pressure regulated by the valve 44 keeps the start- or reverse-start clutch 37, 38 in its sliding or slipping position at moment = 0, thereby transmitting a predetermined moment or virtually no moment. It must be high enough to prevent transmission. That is, some valves 44 must ensure that the friction surface of the corresponding pressure plate and the counter plate of the clutch with the lining of the clutch disc remain engaged when the torque is practically zero. I have to. This valve 44 has the advantage of preventing the corresponding clutches 37, 38 from opening during load exchange, i.e. when transitioning from the positive torque range to the negative torque range. This is because the pump 20 bushes the valve 44 which regulates the minimum pressure, and thus there is a pressure high enough to partially engage the correspondingly engaged clutch. When torque = 0, the closing force formed on the clutch 37 or 38 is small enough to moderate the torque or vibration peaks by idling the connection between the engine and the output shaft III, which is of a medium magnitude. It can be chosen such that torque or very little torque is transmitted, or no torque is transmitted at all.

According to an embodiment which is not shown, a valve which can be regulated or controlled can be used instead of the valve 44 (pressure control valve) which is constantly adjusted, so that vehicle parameters, in particular fueling parameters, can be used. And / or based on predetermined operating parameters such as oil temperature or similar engine parameters, the minimum pressure regulated by valve 44 can be varied accordingly. As a result, when the generated torque is 0, the moment transmitted by the clutch 37 or 38 can be changed according to the operating parameter.

The friction clutch 37 for starting and optionally the clutch 38 for reversing are also adjusted in the same manner, for example or in order to adjust this clutch, German patent application DE 40 11850.9. Similar or the same parameters may be utilized as described in the specification. In this known case, it is necessary to generate a hydraulic pressure in order to release the clutch, whereas in the embodiment of the invention the clutch is connected via hydraulic pressure. Must be taken into consideration.

The pumps 14 and 20 are driven by an engine that drives the drive shaft 1, for example, an internal combustion engine. However, in many uses, the pumps 14, 20
It is advantageous if at least one of these has its own drive motor (eg electric motor). In this case, the electric motor is controlled or adjusted on the basis of a predetermined operating parameter, for example, an operating parameter of the automobile or the internal combustion engine, so that the operating time of the pump can be changed. That is, it is possible to affect the transfer volume or the transfer pressure of the pump.

In the variant embodiment shown in FIG. 1, an energy store configured as a disc spring packet 4 is provided for producing a force according to the transmission ratio on the driven conical belt wheel pair 2. ing. The disc spring packet 4 can also be replaced by a piston / cylinder unit arranged in the conical belt wheel pair 2 with a structure similar to the piston / cylinder unit 11 of the conical belt wheel pair 1 provided on the drive shaft I. Its construction is described in connection with FIG. 2 of the German patent application DE 4036683.9. The valve (36) described in this known specification
Must be provided in the exemplary embodiment of the invention behind the switching valve 40, i.e. in the area of the conduit 16a, and starting from this additional valve, the conical belt wheel pair 2 on the driven side.
A second connecting conduit to the piston / cylinder unit for adjusting the transmission ratio is required.

In the embodiment shown in FIG. 1, the clutches 37, 38 are loaded virtually directly by the pressure provided by the torque sensor 24. However, the conduit 40a connected to the valve 40 is also connected to the rear of the pressure regulator 25, for example to the conduit 28 or 29, so that the clutches 37, 38 are connected to the piston / cylinder units 6, 9 respectively.
Can be loaded with the same pressure as.

Different oil return circuits are shown in FIG. This return circuit opens into a common oil receiving container or sump.

Instead of the adjusting member adjusted by the piston / cylinder unit 31 and the lever mechanism 32 shown in FIG. 1, the adjusting member or the pressure adjusting valve 126 shown in FIG. 2 can be used. This pressure regulating valve 12
6 can be adjusted or operated via an adjusting device configured as a solenoid 131 to adjust the desired pressure by changing the pressure provided by the torque sensor 24. The pressure adjusting valve 126 is connected to the conduit 21 on the inflow side and to the conduits 28 and 29 on the outflow side in the same manner as the pressure adjusting valve 26 shown in FIG. In the illustrated pressure regulating valve 126, resetting is via springs 132, but combined or other resetting devices, such as hydraulic resetting devices, may be used. It is advantageous to use the pressure regulating valve 126 configured as a piston valve or a slider valve.

The pressure regulating valve 126 can be constructed as a proportional valve, in which case the solenoid 131 is regulated, for example by adjusting the voltage, in order to regulate the required or desired pressure at the outlet side of the pressure regulating valve 126. Loaded by value. This adjustment value can be different parameters or adjustments-
And / or associated with disturbance values, these parameters can be electronic control units or regulators (processor 4
3) detected and processed. Pressure control valve 126
Affect the electronic control unit or processor 4
The values or parameters processed by 3 include, among other things, the transmission ratio adjusted by the conical belt wheel transmission. The oil temperature of the engine and / or the transmission and / or the two hydraulic circulation paths (supplied by the pumps 14 and 20 of FIG. 1) is used as another parameter. Other parameters include the fuel supply quantity or position of the fuel supply member, the engine speed, the drive speed of the transmission, the operating module of a motor vehicle with a conical belt wheel winding transmission according to the invention, and in some cases, Another parameter is used which influences the torque supplied by the engine or to be transmitted by the conical belt wheel transmission.

Since the pressure adjusting valve 126 is designed so that the pressure adjusting valve 126 is opened when the solenoid 131 is not controlled, the conical belt wheel winding transmission device can be used even when the control device of the solenoid 131 fails. It is possible to get nervous. In other words, two conical belt wheels 1 and 2
The total pressure transmitted by the torque sensor 24 is built up in the corresponding pressure chamber of This reduces the work efficiency of the transmission, but maintains the torque transmission function.

The solenoid 131 is connected to the adjusting device 43 via a conductor 131.

In order to detect the transmission ratio adjusted by the transmission, a sensor or a detection element is used which cooperates with at least one axially movable conical belt wheel 1a, 1b. The sensor may be formed by an inductive stroke detector, such as a linear potentiometer.
The stroke detector is connected via a corresponding conductor 131 to an electronic adjustment device 43, which is used to inform the adjustment device 43 of the position of at least one movable disc relative to the stationary disc. Is becoming

[Brief description of drawings]

FIG. 1 is a schematic view showing a conical belt wheel winding transmission device and a circuit thereof according to an embodiment of the present invention.

FIG. 2 is a schematic view of a pressure regulating valve according to another embodiment of the present invention.

[Explanation of symbols]

1, 2 conical belt wheel pair, 1a, 2a, 1b, 2b
Conical belt wheel, 3 chains, 4 disc spring packets,
5 pistons, 6 piston / cylinder units,
6a Pressure chamber, 7,8 Cylinder part, 9 Piston / cylinder unit, 10 Ring piston,
11 piston / cylinder unit, 11a pressure chamber,
12 cylinder chamber, 13 piston part, 14
Pump, 15 Pressure regulating valve, 16, 16a, 17
Conduit, 19 Safety valve, 21, 22 Pump, 24
Torque sensor, 24a pressure chamber, 24b stationary cam, 24c axially movable cam, 24d
Sphere, 24e outflow opening, 25 pressure component, 26
Pressure regulating valve, 27 piston, 28, 29 conduit, 30 check valve, 31 piston / cylinder unit, 31a piston, 32 lever mechanism, 33
Lever, 33a contact point, 34 turning center point, 34a position, 35 lever, 36 support point, 37 friction clutch, 37a part, 37
b pressure plate, 37c clutch disc,
37d pressure chamber, 38 friction clutch, 38a counter pressure plate, 38b pressure plate, 38c clutch disc, 38d pressure chamber, 39
Planetary gear transmission, 39a Outer gear, 39b
Sun gear, 39c planetary gear, 40, 41 switching valve, 40a, 40b conduit, 41 switching valve, 42
Conduit, 43 regulator (processor), 44 valve,
126 pressure regulating valve, 131 solenoid, 13
2 springs, 133 conductors

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Norbert Indre Koufah, Federal Republic of Germany Bjühl-Altshjüvía am Biakeller 8 (72) Inventor Osvald Friedman, Federal Republic of Germany Richtenau Moser Schitraße 59

Claims (13)

[Claims] 1. A continuously variable conical belt wheel winding transmission, comprising two mutually adjustable conical belt wheel pairs arranged on a driving side and a driven side, and at least 1. In a form in which two conical belt wheel pairs are adapted to be tensioned by a torque sensor by a piston / cylinder unit or similar adjusting member to tension the winding member, Steplessly adjustable conical belt, characterized in that means are provided for defining the pressure loading on the adjusting member based on the adjusted transmission ratio of the transmission and the pressure supplied by the torque sensor. Vehicle winding transmission device. 2. A pressure adjustment, wherein said means is connected on the one hand to a torque sensor and on the other hand to an adjusting member and is adjusted on the basis of the pressure supplied by said torque sensor and the transmission ratio of the transmission. The conical belt wheel winding transmission according to claim 1, further comprising a valve. 3. The means for varying the pressure supplied by the torque sensor comprises a piston / cylinder unit or similar adjusting member, which is loaded by the torque sensor and is loaded by the torque sensor. 3. A conical belt wheel winding transmission according to claim 1 or 2, wherein a pressure is applied to the adjusting member of at least one conical belt wheel pair in response to the pressure. 4. A pressure regulating valve and a piston / cylinder unit which influences this pressure regulating valve constitute one component unit.
The conical belt wheel winding transmission device according to the item. 5. The conical belt wheel winding transmission device according to claim 4, wherein the pressure regulating valve is operable by the adjusting member with the transmission member interposed. 6. The conical belt wheel winding transmission device according to claim 5, wherein the transmission member has a lever which can be swung around a turning center point which moves based on a transmission ratio of the transmission device. 7. The pivot point is provided on an axially movable component, which is connected to an axially movable disc of the transmission. 6
The conical belt wheel winding transmission device described. 8. Each of the conical belt wheel pairs is loadable by a piston / cylinder unit or similar adjusting member which is pressure-medium loaded by a torque sensor. Conical belt wheel winding transmission device. 9. The conical belt wheel transmission according to claim 1, wherein changes in the transmission ratio are controlled by the pressure medium. 10. Provided to control the transmission ratio,
At least one circulation circuit based on moments can be supplied by at least one pump, and in at least one conical belt wheel pair, an axially movable conical belt wheel exerts a force based at least on the moment and the transmission ratio A member connected to a member.
The conical belt wheel winding transmission device according to any one of 1 to 6 above. 11. A conical belt wheel winding transmission according to claim 10, wherein a pressure regulating valve is provided at least in the moment-based circulation circuit. 12. A parallel-connected adjusting member for applying a pressure based on at least a moment and a transmission ratio to each of the axially movable conical belt wheels of the driving-side and driven-side conical belt wheel pairs. The conical belt wheel winding transmission device according to any one of claims 1 to 12. 13. The means for defining the pressure loading on at least one adjusting member of the conical belt wheel pair comprises a pressure adjusting valve, which pressure adjusting valve is provided via a solenoid or similar adjusting device. 13. Conical belt wheel winding transmission according to any one of claims 1 to 12, which is adapted to be controlled and wherein said adjusting device is adjusted in response to operating parameters processed by a processor.