JPS62274116A - Torque transmission gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention 3. Detailed Description of the Invention Industrial Application Field The present invention relates to a torque transmission device provided in a drive shaft system of a vehicle, particularly between an internal combustion engine and a transmission, Two spring masses are provided which are rotatable relative to each other, one spring mass being connectable to the internal combustion engine, and the other spring mass being able to be connected and disconnected from the engine via a clutch. relating to a certain form of thing.

2. Description of the Prior Art A torque transmission device of the above type is known, for example, from DE 34 40 927 A1. This known device has a circumferentially acting force accumulator, such as a helical spring, and also an axially acting force accumulator, which ensures a damping effect between the two elastic masses. For this purpose, the axially and circumferentially acting force accumulator is supported on disc-shaped components of the two bouncy masses, which have a limited relative movement or rotation relative to each other. This relative movement between the supported disk-shaped components of the force accumulator causes a tightening or compression of the circumferentially acting force accumulator and an axially acting force accumulator which is compressed by at least one disk. Friction along the shaped component is guaranteed.

OBJECTS OF THE INVENTION It is an object of the invention to improve a device of the type described above to increase its wear resistance and thus its service life, and to improve its function, in particular its damping effect, and in particular to improve the torque of this type. It is possible to make the damping characteristics of the transmission variable in relation to the specific speed range and thus to enable maximum damping of the vibrations occurring between the internal combustion engine and the transmission over the entire speed range of the internal combustion engine. Knowledge also ensures simple construction and inexpensive manufacture.

Means for Solving the Problems The structural means of the present invention for solving the above-mentioned problems resides in that both bouncy masses are connected to each other via a hydraulic device that transmits power by means of a pressurized hydraulic medium. .

Effect If a hydraulic device is used as in the invention between two resilient masses, by setting and adjusting the medium pressure, and/or
Or, set the volume of hydraulic medium discharged by the hydraulic device.
By adjusting it, it is possible to obtain a specific characteristic curve in relation to a given operating parameter, such as, for example, the engine speed or the power transmitted from one spring mass to the other. . Furthermore, by determining the volume of hydraulic medium discharged by the hydraulic system, it is possible to obtain a slip between the two resilient bodies, which can be adjusted or limited to a defined value for the given operating conditions.

Through this limited or defined slip, the hydraulic system can act as an hydrostatic damper between the two elastic bodies.

Embodiments The hydraulic system acting between the two bouncing masses can include or form a hydraulic clutch. In this case, it is advantageous if the clutch is a hydrostatic clutch. In constructing the torque transmission device, both bouncing masses operate on the principle of rotation. It is advantageous if they are connected to one another by a positive displacement pump, in particular a gear pump. Lubricants are particularly suitable as hydraulic or viscous media, and for most applications it is advantageous to use pasty media such as greases. Moreover, the pasty medium in this case is such that its state is not or only slightly changed over the entire temperature range occurring, i.e. the consistency of the one-stripe medium is not subject to at least a substantial change. It is a medium. Such a grease or pasty medium avoids the disadvantageous situation in which liquid grease collects at the lowest point and forms an imbalance after the internal combustion engine has been shut down. However, in the case of a filtration application, the viscosity is as uniform as possible over the temperature range encountered.
It is also advantageous to use liquid media such as oil.

Particularly advantageous in terms of structure and function of the torque transmission device are:
When torque is transmitted from the internal combustion engine to the transmission, the power passes from the crankshaft to one of the spring masses and from there via the input part of the hydraulic system, the output part of the hydraulic system and the other spring mass to the friction clutch. This is the case when trying to reach .

It is advantageous in terms of function and construction of the torque transmission device if the hydraulic device acting between the two bouncing masses has a plurality of gears arranged in a planetary manner over the entire circumference around the axis of rotation of the hydraulic device. be. Advantageously, these gears mesh with a drive gear, which drive gear is arranged radially inside the planetary gears.

In the delivery course of positive displacement pumps, the planetary gears are arranged over the entire circumference of the drive gear in order to reduce the pressure pulses caused by the gears, which are due to non-uniform delivery due to the tooth pitch. It is arranged as follows. That is, the meshing of at least some of the teeth of the planetary gears and the teeth of the driving gear are shifted from each other. In other words, this means that the teeth of at least the individual gears arranged in a planetary manner have the same position with respect to the imaginary joining line between the axis of rotation of the drive gear and the axis of rotation of the gears arranged in a planetary manner. It means you haven't. With this arrangement, the pressures caused by the individual gears arranged in a planetary manner occur offset from each other, so that the total pressure of the pump becomes more constant.

In order to reduce leakage losses in the pump and, in turn, to minimize the slippage that occurs between the two bouncing masses due to these losses, a packing plate is provided on at least one side of the planetary gear. It is advantageous to provide a gear pump, in which case the side of the gear/plate facing away from the gear can be connected to the hydraulic system or to the delivery side of the gear pump. In order to ensure an impeccable seal, it is advantageous for the force storage to act on the side of the packing plate facing away from the gear. The gearwheel is axially tensioned by pressure, possibly by means of a force accumulator, so that when the gearwheel rotates, a frictional damping effect is additionally produced as a result of the pressure occurring in the pump.

A particularly advantageous and simple construction of the torque transmission device is obtained if all gear wheels arranged in a planetary manner are provided with at least one common packing plate forming a toroidal component.

In order to improve the functioning of the torque transmission device, a plurality of gear wheels arranged in a planetary manner are each rotatably mounted on a shaft. It is advantageous in terms of the construction of the torque transmission device if a plurality of planetary gears are supported by a first resilient mass and the drive gear is provided on a second resilient mass.

In an embodiment of the invention, different types of components are provided between the delivery side and the suction side of the hydraulic system or pump, which influence the torque transmitted by the torque transmission device and thus also the slip occurring between the two resilient masses. It is possible to provide valves or throttles. For example, it is possible to provide at least one throttle valve and/or check valve between the discharge side and the suction side of the hydraulic system.

In a preferred embodiment, a throttle valve is used as the throttle, which is integrated in one of the resilient masses and is connected via channels to the delivery and suction sides of the hydraulic system. In order to simplify the construction of the torque transmission device, if not only a throttle but also a check valve is required, it is advantageous to use at least one throttle valve which is simultaneously designed as a check valve. It is also advantageous to provide one throttle in each case between the discharge side and the suction side of each planetary gear.

Depending on the design of these valves, it is possible to provide a clutch formed by a hydraulic device, such as a gear pump, with different properties, in particular with different torque properties or with different slip properties. These valves are actuated in relation to the rotational speed of the internal combustion engine or the rotational speed of one and/or the other elastic mass or the rotational speed of the transmission input shaft, thereby changing the characteristics of the hydraulic system and thus also between the two elastic masses. It is particularly advantageous if the slip of the motor can also be varied as a function of the rotational speed.

It is also advantageous for the valve to be actuated in conjunction with other /4' parameters which depend on the operating conditions occurring between the internal combustion engine and the transmission. For example, the throttling effect between the discharge side and the suction side of the hydraulic system may be variable as a function of the temperature of the discharged medium.

In an embodiment of the invention, a tonion damper is provided between the hydraulic device and the at least one resilient mass, which is formed by a rotationally elastic damper. It is also possible to additionally provide a friction damping device between the two elastic blanks, for example forming a friction clutch with play. Advantageously, the friction clutch with play is a so-called loaded friction device.

A torsionally elastic shock absorber disposed between the hydraulic system and one of the resilient masses has at least one input section and at least one output section, the input section and the output section being connected to each other. A particularly advantageous configuration for the functioning of the torque transmission device is obtained if a circumferentially acting force store is provided in between.

In this case, it is advantageous if the hydraulic system and the torsionally elastic damper are arranged in series.

By supporting or forming the drive gear by the input or output part of a torsionally elastic damper, a particularly simple construction of the torque transmission device is also ensured. A torsionally elastic damper also connects the hydraulic device in the power transmission path from the first bouncy mass to the second bouncy mass and a second bouncy mass connectable to the transmission input shaft via a clutch. It is advantageous for the construction of the torque transmission device to be provided between the two. It is also advantageous for the torsionally elastic damper to be arranged radially inside the hydraulic device and for the torsionally elastic damper and the hydraulic device to be arranged at least approximately the same axial height.

A rotating elastic damper has two discs axially spaced from each other forming an output part, between which an input part of the torsionally elastic damper is arranged. A particularly advantageous configuration of the torque transmission device is obtained if a flank is provided which simultaneously forms the drive gear of the hydraulic device.

In this case, a flange extends radially beyond the disks on both sides, and on the outer periphery of the flange the drive gear for a plurality of planetary gears of the hydraulic system or pump is molded. It is advantageous to have

One of the bouncy masses has a chamber at least partially filled with a viscous medium, in which a torsionally elastic damper and a hydraulic system are optionally also installed to prevent the friction acting between the two bouncy masses. Advantageously, a damping device is accommodated. By configuring the torque transmission device in this way, lubrication takes place between the areas of the device components that are in contact with each other and are in relative motion, which significantly reduces wear due to contact friction and thus increases the service life and functional reliability. is significantly increased. The invention provides in particular the individual windings of the circumferentially acting helical spring of a torsionally elastic damper and the various disc-shaped components forming the input and/or output part of the torsionally elastic damper. It also becomes possible to reduce the friction between the radially outer edge of the window receiving the coil spring. Advantageously, the chamber for the viscous medium essentially consists of an annular chamber formed by a component of one of the resilient masses. The annular chamber is formed by an outer circumferential wall that axially surrounds the torsionally resilient damper, and opposing Ill walls that extend radially inwardly from the outer circumferential wall and receive the torsionally resilient damper therebetween. ing. Advantageously, the first resilient mass connectable to the internal combustion engine has the annular chamber. In that case, one side wall of the annular chamber extends radially between the torsionally elastic damper and the second bouncing mass, and the radially inner extent of the side wall and the second bouncing mass extend radially. A seal member is provided between the mass body and the mass body.

Furthermore, the first resilient mass has a ring-shaped axial extension, which forms the outer circumferential wall of the annular chamber, and is connected to the torsionally elastic damper and the second resilient mass. It is advantageous for the construction of the torque transmission device that the side wall of the annular chamber extending radially between the two is fixed to the annular axial extension.

In order to configure the torque transmission device of the present invention even more simply,
An axially recessed portion is provided radially inwardly of the axially attached portion of the first resilient element, and within the axially recessed portion (in the
A plurality of gears arranged in a planetary manner are accommodated and rotatably supported. Advantageously, the side wall fixed to the axial extension axially closes off the axial recess. For this purpose, the side walls are fastened to the end faces of the axial extensions.

In order to prevent the viscous medium filled in the chamber from flowing out, a seal is installed at the radial outer edge of the planetary gear and between the end face of the joint and the fill I wall fixed to the end face in the axial direction. It is advantageous to provide an OIJ pump on the component side.

In order to make the purchase of torque transmission devices particularly compact, when torque is transferred from an internal combustion engine to a transmission, the power travels from the crankshaft to a first bouncy mass and from there to a hydraulic clutch such as a hydraulic clutch. input part of hydraulic system,
Advantageously, the clutch is reached via the output part of the hydraulic system, the damper and the second resilient mass.

In this case, the second resilient mass connectable to the transmission input shaft via a clutch, for example a friction clutch, is
Advantageously, it has a friction surface for a clutch disc which is clamped between the second spring mass and a pressure plate that is non-rotatable and axially displaceable relative to the spring mass. .

In order to dampen the vibrations occurring between the internal combustion engine and the transmission, the slip between the two resilient masses is between 20 and 200 revolutions, particularly preferably between 20 and 100 revolutions.

In order to reduce the losses caused by the presence of slips to a replaceable extent, it is advantageous to reduce said slips to a minimum at relatively high engine speeds of the internal combustion engine. Already begins in the number range.

Example Next, embodiments of the present invention will be explained in detail with reference to the drawings.

In order to compensate for rotational shocks, the torque transmission device 1 shown in FIG.
have. The bouncy mass body 3 is fixed to the crankshaft 5 of an internal combustion engine (not shown) via a plurality of fixing screws 6.
is fixed. A clutch disc 9 is provided between the pressure plate 8 and the resilient mass body of the friction clutch 7, and the clutch disc is attached to an input shaft 10 of a transmission (not shown). Friction clutch 7
The pressure plate 8 is loaded in the direction of the spring mass by a disk spring 12 which is pivotably supported on the clutch clutch 11. By actuation of the friction clutch 7, the bouncy mass, and thus also the flywheel 2 and the internal combustion engine, are coupled and disengaged from the input shaft 10 of the transmission. Between the bouncy mass 3 and the cow, there is a first hydraulic shock absorber 13 and a second mechanical shock absorber 14 arranged in series with the shock absorber.
is provided, the hydraulic and mechanical shock absorbers permitting relative rotation of both bouncing masses 3 and the hand.

Both bouncy masses 3 and the cow are mounted on a support device 1 so as to be rotatable relative to each other.
It is supported through 5. The bearing device 15 has rolling bearings in the form of single-row ball bearings 16. ball bearing 1
The outer race 17 of the ball bearing 16 is arranged in the recess 18 of the bouncy mass body 3, and the inner race 19 of the ball bearing 16 is arranged in the center of the bouncy mass body 3 and is located on the axis remote from the crankshaft 5. It is arranged on the outer periphery of a cylindrical bottle 20 that extends in the direction and enters the recessed portion 18 .

The inner race 19 is attached to the outer circumference of the bottle 20 in a press fit and is tightened between the shoulder 21 of the bottle 20 of the bouncy mass 3 and a securing disc 22, which secures the bottle 20 with a press fit. It is fixed on the end face.

The ball bearing 16 is secured in the axial direction with respect to the bouncy mass body.
In this case, the ball shaft stack 6 is fixedly connected to the shoulder 25 of the bouncy mass Φ through a spacer pin 26 by inserting two rings 23 and 24 having a cross-sectional shape. It is tightened in the axial direction between the disc 27 and the disc 27.

On the radially outer side, the resilient mass 3 has a ring-shaped axial extension 28 which accommodates the mechanical damper 14 and delimits a chamber 29 .

The chamber 29 is substantially formed by an annular chamber 30 . The annular chamber 30 is radially outwardly connected to the aforementioned axial extension 2.
8, and on both sides, a side wall 3 extending radially inward from the axial extension and interposing a °C buffer 14.
It is limited by 1 and 32°C. The side wall 31 is
A resilient mass 30 extending radially from 0 is formed by a radial turning flank 33. The side wall 32 is also formed by a substantially inelastic, i.e. rigid, cover, the cup ζ- extending radially inwardly between the damper 14 and the bouncy mass, and On the radially outer side, the resilient mass 30 is fixed to a radial turning flange 33.

In order to ensure the functioning of the hydraulic shock absorber 13, a viscous damping and lubricating agent is provided in the chamber 29, which consists, for example, of oil, grease or a pasty medium. In this case, the level of buffering and lubricant, such as silicone oil, is determined as follows depending on the application or as required. That is, when the torque transmission device rotates, both bouncy masses 3 and 4 are moved under the action of centrifugal force.
The radially supinated range of the coil spring as the force storage 34 of the damper 14 acting between the damper 14 or the entire radial range of the coil spring is immersed in the viscous damping/lubricant.

Furthermore, as can be seen from FIG. 1 together with FIG. 2, the radially outer hydraulic shock absorber 13 is distributed evenly over the entire circumference of the ring-shaped axial addition 28. It has a plurality of gears 35 arranged in a planetary manner. Each gear 35
are arranged in respective axial recesses 1 36 , in which the ring-shaped axial extensions 2 of the bouncy mass 3 are arranged.
It is provided in a radial range of δ. The gears 35 arranged in a planetary manner are each rotatably supported by a shaft 37 in a ring-shaped axial recess 36 . The shaft 37 is
A large-diameter central portion 3δ equipped with a gear 35 and journal-shaped portions 39 extending in the axial direction on both sides of the central portion 380.
．． It has 40. In order to hold the shaft 37 in the radial direction, the journal-shaped parts 39, 40 have axial holes drilled in the bottom of the axial recess 36 as well as in the axially opposite regions of the side walls 32. It extends into Cow 2.

9111 The wall 32 is fastened to the 7 radial flange 33 via 43 rivet joints. As can be seen in FIG. 2, the rivet joint 43 is arranged in the middle of the gearwheel 35 when viewed in the circumferential direction of the torque transmission device.

The planetary gears 35 mesh with a common drive gear 44 arranged radially inwardly of these gears. In the ring-shaped axial addition 28 of the resilient mass 3 in the radial meshing region between the tooth row 35a of the gear wheel 35 and the tooth row 44a of the drive gear wheel 44, a borehole forming a toroidal chamber 45 is provided. A section is provided. III also faced gear 35.
A cutout starting from the end face of the wall 32 is also provided in the side wall 32 in a similar manner, which cutout forms an annular chamber 46 . During the relative rotation between both bouncy mass bodies 3 and the cow,
A viscous buffer/lubricant discharged from the hydraulic shock absorber 13, ie, the gear pump, is press-fitted into one of the annular chambers 45.46 and sucked into the other annular chamber 46.45. On both sides of the gear wheel 35 there are provided .xi. disks 47, 48 which are axially displaceable and are pressed onto the gear 35. room 45 this one time
．． 46 has a communication portion between the gear 35 for pushing away the medium to be discharged and the meshing teeth of the driving gear 4. “Illustrated”
f value 511 4 + bi stone set 9 ko W 斂 ko flood l
stomach ,? -Nokoshi Soloko ga L 74
Hole 49.50 made in δ (see Figure 3 and raw diagram)
is formed by. Depending on the direction of the relative rotation of the two resilient masses 3, 4, these boreholes 49, 50 lead the pressure medium to the . It is sucked in from the ξtsukin disk side. This operation will be described later.

As can be seen from FIG. 2, holes 49 and 5 belonging to gear 35
0 are mutually shifted in the circumferential direction with respect to the virtual connecting straight line 51 extending through the rotational axis of the torque transmission device 1 and the rotational axis of the gear 35, and are located on both sides of the virtual connecting straight line 51. It is arranged so that In the embodiment shown, the perforation 49
．． 50 is provided symmetrically with respect to the virtual connection 6 straight line 51 of 1 square.

As can be seen from FIG. 3, the ξ-nokin disc 7 has an annular inner range 52, and the inner range has a plurality of ring-shaped or disc-shaped radial lines on the outer circumference when viewed in the radial direction. Bracket 5
The three to one radial brackets are evenly distributed over the entire circumference of the annular inner region 52. The radial bracket 53 is received in an axial recess 36 of the ring-shaped axial extension 28 of the resilient mass 3.

The outer diameter of the disc-shaped radial bracket 53 is adapted to the diameter of the axial recess 36 . A borehole 54 is provided in the central region of the disc-shaped radial bracket 53, into which the central part 38 of the shaft 37 is inserted.

As can be seen from FIG. 4, in addition to the connecting bore 50, the .xi. cylinder 48 has a further bore 55 into which the central part 38 of the shaft 37 is also inserted. Packing disc 48 also has a plurality of radially extending slots 56 that extend radially outward from the inner peripheral edge of packing disc 48 into the radial extent of chambers 4-6. Thus, the chamber 46 is connected to the central annular chamber 30 via a radial slot 56.

Furthermore, a through hole 43a is provided between the perforations 55 to allow the rivet of the rivet joint 43 to escape.

As can be seen in FIGS. 1 and 2, the flange-shaped drive gear 44 simultaneously forms the input part for the circumferentially rotating elastic inner shock absorber 14. As can be seen in FIGS. The rotary elastic shock absorber 14 also has a group of disks, namely two disks 27 and 57 arranged on either side of the drive gear 44, which rotate relative to each other at an axial distance via a spacer pin 26. The bouncing mass is fixedly coupled and pivotally mounted to the bouncing mass. Disc 27.57
and an axially aligned cutout 58 within the drive gear 44.
．． 59 and 60 are formed, and within the cutout,
A circumferentially acting force accumulator 34 in the form of a coil spring is accommodated.

The force accumulator 34 acts against the relative rotation between the drive gear 44 and the two disks 27.57. The range of action of the inner shock absorber 14 is defined by the length of the cutout 44b for the spacer pin 26 which extends in the circumferential direction and is formed in the drive gear 44.

Furthermore, a friction device 61 is provided between the two bouncing masses 3 and the cow, which acts in parallel to the rotating elastic shock absorber 14. The friction disc 61a is controlled by the spacer bin 26.For this purpose, the friction disc 61a
has a notch 61b with which the rivet head of the spacer bin 26 engages in the axial direction. In that case, the notch 61
Advantageously, there is circumferential play between b and the rivet head.

In order to seal the chamber 29 and thereby prevent the outflow of the buffer/lubricant, there is a gap between the end face of the axial extension 28 and the side wall 32, as well as between the circumferential surface of the center hole 620 of the side wall 32 and the inside of the center hole 62. Seal rings 64, 648 are provided between the axial rotation addition portion 63 of the bouncy mass body that engages in the axial direction, and in the example shown in FIG. It is formed by a fitted Q l) ring. The sole ring 64 is arranged radially outside the gear 35 or the axial recess 36 . Further, a seal ring 65 is provided between the inner race 19 and the outer circumferential surface of the pin 20 to seal the chamber 29, and a recessed portion 18 for the ball bearing 16 and a ring having an angular cross section are provided. A sealing ring 66 is arranged in the area between the two shafts, which also consists of an O-ring fitted in a suitable groove.

The radially extending legs 23a, 24a of the cross-sectional rings 23, 2+ also serve to seal the chamber 29 from the outside, so that no leakage of damping and lubricant through the ball bearings 16 is possible. do not have.

The functional aspect of the hydraulic shock absorber 14, that is, the gear pump will be explained next.

During tension operation, i.e. by the internal combustion engine, the crankshaft 5
When the input shaft 10 of the transmission is driven via the drive gear 35 and the torque transmission l, the viscous medium is drawn out of the chamber 46, which in this case serves as a suction or supply chamber for the gearwheel 35 and the drive gearwheel 44. through the gears,
In this case, it is press-fitted into a chamber Φδ that serves as a pressure chamber.

For example, based on leakage loss due to gaps (due to manufacturing errors or intentionally designed) that exist between the tooth surfaces of the ear pump and between the discharge side and the suction side, Since the viscous medium escapes, the gear 35 is moved by the drive gear 4 to the shaft 37. This causes a relative rotation or slip between the bouncing masses 3 and the bottle. The speed of this unrestricted relative rotation is related to the transmitted moment and to the transmitted moment which is small (and approximately proportional) to this moment. In short, this means that if the impact moment is This means that the slip velocity between the body 3 and the body is constant, thereby absorbing or dampening this shock.The viscous medium volume sucked out of the annular chamber 16 due to leakage losses is From 30 a radial slot 56 can follow into the annular chamber 46.

in the radial direction to avoid large leakage losses during tensioning operation. At the same level in the annular chamber 45 and in the axial direction between the contact surface of the bouncy mass 3 for the ξ-disk 7 and said axially displaceable ξ-disc 47, In the illustrated embodiment, a seal consisting of a ring 67 is provided.

A fitting groove is formed in the bouncy mass body 3 to attach this OIJ song 7. Due to the axial deformation of the O-ring 67, the axial force is applied to the packing disk divided by 7, so that the packing disk is pressed against the gear δ5.

Due to the pressure generated in the annular chamber 5, the axially displaceable .xi. discs 47 are pressed against the gears 35, so that these gears 35 and the .xi. The bouncy mass is tightened between the packing disk 48 supported by the cow.

In addition, the radial supination range of the drive gear 4÷, which is inserted in the radial direction between the two ξ-skin discs 47 and the cow 8, is also tightened between the two ξ-skin discs 47 and the middle δ. be included. By tightening or tightening the gear 35 and the drive gear 4/+ in the axial direction, the gear 35 and the drive gear 44 are rotated relative to each other.
Additional frictional damping is generated between and the .xi. disks 47, 48. Friction damping is annular (pressure)
It is related to the pressure prevailing within chamber 45.

During engine braking operation, that is, when torque is transmitted from the driving wheels to the internal combustion engine via the transmission l1llll (10) torque transmission l, a viscous medium is present in the gear 35 and the drive gear 4+. It is taken out from an annular chamber 45, which serves as a suction or supply chamber for the water, and is forced into an annular chamber 46, which in turn serves as a pressure chamber, by means of the gear. Due to the leakage losses already mentioned and also due to the passage formed between the chamber 46 and the annular chamber 30 by the radial slots 56 of the locking disk 48, the viscous medium is forced out of the chamber 46. Ru. Based on this leakage loss or a predetermined discharge amount of the gear pump (13), the plurality of gears 35 are rotated by the drive gear 44 by degrees Celsius. An arrow tension line occurs, and this 0) Sl:,/
is related to the moment created between the bouncing masses 3 and the cow.

It is possible to define the slip as desired by a deliberately designed radial slot 56 which acts like a diaphragm. Due to this slot 56, the slip between the two bouncing masses 3 and the cow in the direction of engine braking is greater than the slip in the direction of pulling.

When the torque transmission device 1 is activated in the direction of engine braking operation, the viscous medium is sucked out of the chamber 45 by means of the gear pump (13).

This is because, ignoring any possible leakage, said chamber 45 serves as a storage chamber for the viscous medium (since it does not communicate with the annular chamber 30). After a period of time, the gear pump (13) acts like an afreewheel, since after a certain operating time in the engine braking direction, the gear pump (13) is no longer supplied with viscous medium from the chamber 45. During this operating period, a negative pressure is generated in the chamber 45, but this negative pressure is no more than 1 part.

As long as there is pressure in the chamber 46 during the engine braking period, the pressure disc 48 will be able to move the gear 35 and the drive gear 44.
Since they are also loaded axially, the gear 35 and the drive gear 44 are axially clamped between the two ξ sliding discs 47 and 48.

Due to this tightening, when the gear 35 and the drive gear 44 are rotated, these gears 35, 44 and the two rubber discs 47.
48, frictional damping occurs. However, the friction damping that occurs during engine braking operation is smaller than during traction operation. This is because the pressure that builds up in (pressure) chamber 46 is less than the pressure that builds up in chamber 45 during the tensioning phase.

During engine braking operation, the gear pump (13) is parallel to the buffering action of the
It is advantageous for many applications to minimize frictional damping effects with 5.44. This is ensured by the axial fixation of the .degree. C. rotation disk 48 to the side wall 32. This fixation in the axial direction is achieved by: - matching the perforation 55 (see Fig. 2) of the ξ-thickening disk 48 to the outer diameter of the journal-shaped partial protrusion ○ of the shaft 37; This can be done by axially tightening between 38 and the side wall 32 or by axially supporting the central portion 38 of the shaft 37. As a result, when pressure is generated in the chamber 46, the packing disk 48 is supported on the radial flange 33 via the shaft 37, thereby supporting the gear 35 and the driving gear 44 between the packing disk 4-
This makes it possible to avoid tightening between 7 and 48.

The force accumulator 34 of the rotary elastic shock absorber 14 connected in series with the gear pump (13) is adapted to correspond to the moment occurring between the two elastic masses 3 and the spacer pin 26 and the circumferential direction. Cutout 44 of drive gear 44 extending to
b is compressed until there is no rotational play between it and b. The radially inner rotational elastic damper 14 is then locked and only the radially supinated gear pump (hydraulic damper 13) remains active.

In particular, as can be seen from the cross-sectional view shown in FIG.
When actuated, the axial forces required for this are applied to the bearing device 15.
, so that the gear pump (13) is not adversely affected. This simply means that the gear pump (13) is unrelated to the operation of the friction clutch (7), and in other words, the characteristics of the gear pump are not affected by the operating force of the friction clutch 70. There is.

In the torque transmission device 101, which is partially shown in FIG.
6, a pressure limiting valve 170 is disposed between the pressure limiting valve 170 and the pressure limiting valve 170. The pressure limiting valve 170 has an axial hole 171, a plastic ball 172 as a closing body, and a coil spring 1 as a closing spring.
The axial hole 171 is formed in the ring-shaped axial extension 128 in the area between the gears 35 (see FIG. 2) when viewed in the circumferential direction. The coil spring 173 is attached to the conical seat 1 formed by the axial hole 171.
Ball 172 is loaded against 74. The axial bore 171 is connected on the one hand with the pressure chamber 145 via a radial passage 175 and on the other hand with the suction chamber 146 via a radial slot 176 formed in the knob disk 1+8. ing. By designing the preload of the coil spring 173 accordingly, it is possible to define the pressure-limiting valve 1700 opening pressure in a targeted manner. As soon as the pressure limiting valve 170 opens at a predetermined pressure, which corresponds to a predetermined moment occurring between the two bouncy masses 3 and the cow, a relatively large slip occurs between the two bouncy masses 3 and 4. This is because the viscous medium can escape from the pressure chamber 145 into the suction chamber 146 via the radial passage 175, the pressure limiting valve 170 and the radial slot 176. In short, the use of the pressure limiting valve 170 makes it possible to buffer or attenuate undesired impact torque within the output system of the internal combustion engine.

Also in the torque transmission device shown in FIGS. 1 to 4, a plurality of pressure limiting valves 170 are evenly distributed over the entire circumference.
Of course, it is possible to provide the following.

In a further embodiment of the torque transmission device 201 of the invention, partially shown in FIG. 6, a centrifugal force-related throttle valve 270 is provided. The throttle valve 270 consists of a cylindrical roller 272 as a valve body accommodated in a radially extending receiving recess 271. The cylindrical roller 272 moves radially outward under the action of centrifugal force, thereby closing the throttle boat 277, which closes the throttle boat 277 in the radial passage 27.
5, a chamber 2 which forms a pressure chamber during tension operation Pj,j
It is connected to 45. The receiving recess 271 also serves as a suction chamber (connected to the chamber 246 during tension operation) via a radial slot 276 formed in the packing disk 248. When a high pressure develops, the viscous medium leaves the pressure chamber 245 in the radial passage 27.
5, throttle valve 270 and radial slot 276 into suction chamber 246 by gear pump 213.

The discharged viscous medium volume determines the slip occurring between the two bouncing masses 3 and the cow or the relative rotation speed between the two bouncing masses 3 and the cow. This media capacity is
It is related to the moment occurring between the two bouncing masses 3 and the cow as well as to the centrifugal force acting on the cylindrical rollers 272. The weight of the cylindrical roller 272 closes the throttle boat 277 in a predetermined rotational speed range of the internal combustion engine exceeding the idling rotational speed and under normal operating conditions, so that no slip occurs between the bouncy mass bodies 3 and Φ. , if any, are selected to minimize the slippage and to minimize the extent to which leakage in the hydraulic shock absorber or hydraulic clutch occurs. For example, in a low rotational speed range below or close to the idling speed, the throttle valve can be opened if the pressure increase in the pressure chamber 245 is relatively small.

Depending on the usage conditions and desired characteristics of the gear pump 213, hydraulic shock absorber, or hydraulic clutch, the characteristics or characteristic curved edge of the throttle valve 270 related to centrifugal force may be determined by the accumulation acting on the cylindrical roller 272 as a valve body. Affected by power tools. Thus, for example, as schematically illustrated in FIG. 6, the cylindrical rollers 272 can be pressed radially outwardly onto the throttle boat 277, so that the throttle boat 277 can be closed even when the torque transmission device does not rotate. A pressure accumulator 278 like this is provided (
It is also possible. Only when a sufficiently high overpressure exists in the pressure chamber 2 and 5 can the throttle valve 270 open against the force of the pressure accumulator 27 δ and, if necessary, against the centrifugal force acting on the cylindrical roller 272. You can do it.

In addition, according to an embodiment not shown, it is possible to provide a force accumulator that loads the cylindrical roller 272 as a valve body in radial pronation, and in this case, when the torque transmission device rotates, the cylindrical roller The distance force acting on 272 is the aperture bow 1
In order to close 277, the force of the energy storage device must be overcome.

The throttle valve 270 shown in FIG. 6 is arranged, like the pressure limiting valve of FIG. 5, between the gear wheels 35 (FIG. 1) when viewed in the circumferential direction. The combination of pressure limiting valve 170 and centrifugal throttle valve 270 is advantageous for many pressure applications.

The valve 370 shown in FIG.
It has a valve body 372 which is loaded in radial pronation via 8. The force accumulator 378 and the valve body 372 are the elastic body 3
The radial hole 371 is closed radially outwardly by a screw 379, against which a force accumulator 378 is abutted. The preload of the energy accumulator 378 is set via a screw 379. Two passages 375 and 376 branch off from said radial bore 371 and form the chamber 45.4 in FIG.
It communicates with chambers 345 and 346 corresponding to 6. Valve body 3
72 is a hole 3 that communicates both the passages 375 and 376.
72a. The arrangement of the hole 372a and the energy storage device 3
The design of 78 is as follows. In the low rotational speed range of the internal combustion engine, for example in the rotational speed range below idling speed, the hole 372a is radially offset from the passages 375 and 376, so that there is no communication between the passages 375 and 376. It is designed not to occur.

Therefore, the viscous medium does not reach the suction side from the discharge side of the gear pump 313 via the passages 375 and 376. In the medium speed range, the hole 372a is connected to the passages 375 and 376.
, so that the viscous medium can circulate through valve 370.

As the rotational speed increases, the centrifugal force acting on the valve body 372 increases, and the force accumulator 378 also becomes more constricted, with the result that the hole 372a moves radially outward relative to the passage 375, 376. However, as a result, communication with both passages 375 and 376 is interrupted in the high rotational speed range. Therefore, when the rotational speed of the internal combustion engine becomes relatively high, the viscous medium no longer flows through the valve 3.
Words circulate through 70.

The characteristic curve of the valve 370 shown in FIG. 7 can be adapted to the particular application by configuring the shape of the energy storage device 378 and the bore 372a accordingly.

The energy accumulator 378 advantageously does not have a linear characteristic curve.

According to a variant not shown, the valve body 372 of the valve 370 shown in FIG. 7 may have a plurality of holes communicating the passages 375 and 376. In this case, the arrangement form in which the plurality of holes are provided in the valve body 372 is as follows. In the low rotational speed range of the internal combustion engine, the passages 375 and 376 communicate with each other, and in the middle rotational speed range, this communication is interrupted, and in the relatively high rotational speed range, the passages 375 and 376 communicate with each other in the radial direction in the valve body 372. Both passages 375.376
The space is now reconnected.

In the torque transmission device of the embodiment shown in FIG. 1, the clutch disc 9 is constructed as a rigid disc. However, in most applications it is advantageous to use clutch discs with Q et al. In that case, the torsion force ξ of the clutch disc is configured in a multistage manner, and at least one stage is configured for the idling range.
Also, at least one stage is provided for the load range. However, in many applications it may be advantageous for the clutch disc to have only one torsion damper designed for the idling range. It is also possible for the clutch disk to have a low torsion damp ξ (and also to include one friction device, in which case the friction device has a plurality of successively acting friction stages, the friction stages being so-called loaded friction devices or A stretching friction device is formed.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of the torque transmission device according to the invention, Fig. 2 is a partially cutaway partial view seen in the direction of the arrow ■ in Fig. 1, and Fig. 3 is a sectional view of the torque transmission device according to the invention. FIG. 4 shows a seal plate according to a different embodiment of a gear pump located between both bouncing masses. Figure 5 is a detailed sectional view of a throttle valve that can be used in the torque transmission device shown in Figures 1 and 2;
The figure is a detailed sectional view of a centrifugal force-responsive valve that can also be used in the torque transmission devices shown in Figures 1 and 2, and Figure 7 is a detailed cross-sectional view of the
FIG. 3 is a detailed sectional view of a different embodiment of a centrifugally responsive valve which can also be used in the torque transmission device shown in FIGS.

Claims (1)

[Claims] 1. A torque transmission device provided in a drive shaft system of a vehicle, particularly between an internal combustion engine and a transmission, which is provided with at least two resilient mass bodies that are rotatable relative to each other. In a type in which one of the bouncy mass bodies can be connected to the internal combustion engine, and the other bouncy mass body can be connected to and disconnected from the transmission via a clutch,
Torque transmission device, characterized in that both resilient masses are connected to each other via a hydraulic device which transmits the power by means of a pressurized hydraulic medium. 2. The torque transmission device according to claim 1, wherein a hydraulic clutch is provided between both bouncing masses. 3. The clutch is a hydrostatic clutch.
A torque transmission device according to claim 1 or 2. 4. Torque transmission device according to any one of claims 1 to 3, characterized in that both resilient masses are connected to each other by a positive displacement pump operating on the principle of rotation. 5. The torque transmission device according to any one of claims 1 to 4, wherein a gear pump is provided between both bouncing masses. 6. The torque transmission device according to any one of claims 1 to 5, wherein the hydraulic device functions as a hydrostatic shock absorber through a limited slip range. 7. The torque transmission device according to any one of claims 1 to 6, wherein a pasty medium such as grease or paste is used as the hydraulic medium. 8. When torque is transmitted from the internal combustion engine to the transmission, the power reaches one of the resilient masses from the crankshaft, and from there passes through the input part of the hydraulic system, the output part of the hydraulic system and the other resilient mass. A torque transmission device according to any one of claims 1 to 7, which reaches a friction clutch. 9. Any one of claims 1 to 8, wherein the hydraulic device has a plurality of gears arranged in a planetary manner around the entire circumference of the hydraulic device. Torque transmission device as described in . 10. Claim 1, wherein the hydraulic device has one drive gear that meshes with a plurality of gears arranged in a planetary manner.
9. The torque transmission device according to any one of items 9 to 9. 11. The torque transmission device according to claim 10, wherein the drive gear is provided radially inside a plurality of gears arranged in a planetary manner. 12. The torque transmission device according to any one of claims 9 to 11, wherein a packing plate is provided on at least one side surface of a plurality of gears arranged in a planetary manner. 13. The torque transmission device according to any one of claims 9 to 12, wherein the packing plate side remote from the gear is connected to the discharge side of the hydraulic device. 14. The torque transmission device according to claim 12 or 13, wherein the power accumulator acts on the side of one packing plate that is remote from the gear. 15. Torque transmission device according to any one of claims 12 to 14, characterized in that the individual gear packing plates are connected to each other and form an annular component. 16. Any one of claims 9 to 15, wherein a plurality of gears are rotatably supported on respective shafts.
Torque transmission device as described in . 17. a plurality of gears are supported by the first bouncing mass and a drive gear is provided on the second bouncing mass;
A torque transmission device according to any one of claims 9 to 16. 18. The torque transmission device according to any one of claims 1 to 17, wherein a throttle is provided between the discharge side and the suction side of the hydraulic device. 19. The torque transmission device according to any one of claims 1 to 18, wherein a check valve is provided between the discharge side and the suction side of the hydraulic device. 20. The torque transmission device according to claim 18, wherein the throttle is formed by a throttle valve. 21. Torque transmission device according to any one of claims 18 to 20, wherein the throttle valve is also configured as a check valve. 22. The torque transmission device according to any one of claims 18 to 21, wherein a throttle is provided between the discharge side and the suction side of each gear. 23. Torque transmission device according to one of claims 18 to 22, wherein the throttling effect caused by the throttle is variable in dependence on the predetermined operating conditions. 24. Torque transmission device according to claim 23, wherein the throttling action is variable in relation to the rotational speed of the one and/or the other resilient mass. 25. Torque transmission device according to claim 23 or 24, wherein the throttling effect is variable in relation to the temperature of the medium delivered or displaced by the hydraulic device. 26. Torque transmission device according to one of claims 1 to 25, characterized in that a rotational elastic damper is provided between the hydraulic device and at least one resilient mass. 27. Any one of claims 1 to 26, wherein a friction damping device is provided between both bouncing mass bodies.
Torque transmission device as described in . 28. Claim 2, wherein the rotary elastic shock absorber has an input part and an output part, between which a circumferentially acting force accumulator is provided.
The torque transmission device according to item 6 or item 27. 29. Torque transmission device according to any one of claims 26 to 28, wherein the hydraulic device and the rotary elastic shock absorber are arranged in series. 30. Torque transmission device according to any one of claims 10 to 29, wherein the drive gear is supported by an input part or an output part of a rotary elastic shock absorber. 31. A rotating elastic damper is provided between the hydraulic device and the second resilient mass in the power transmission path from the first resilient mass to the second resilient mass. The torque transmission device according to any one of the ranges 26 to 30. 32. Torque transmission device according to any one of claims 26 to 31, characterized in that a rotationally elastic damper is provided radially inside the hydraulic device. 33. Torque transmission device according to any one of claims 26 to 32, characterized in that the rotary elastic shock absorber and the hydraulic system are arranged at at least approximately equal axial heights. 34. Torque transmission device according to any one of claims 10 to 33, characterized in that the drive gear is constructed integrally with the input part of the rotary elastic shock absorber. 35. A rotary elastic shock absorber has two discs arranged axially spaced from each other forming an output part, between which a flange forming an input part of said rotary elastic shock absorber. Torque transmission device according to any one of claims 26 to 34, wherein the torque transmission device is provided. 36. A flange extends radially beyond the discs on both sides, and a drive gear for a plurality of planetary gears of the hydraulic system is integrally molded on the outer periphery of the flange, A torque transmission device according to claim 35. 37. One of the resilient masses has a chamber at least partially filled with a viscous medium, in which a rotary elastic shock absorber and a hydraulic system are received. 37. The torque transmission device according to any one of items 36 to 36. 38. Torque transmission device according to claim 37, wherein the chamber consists essentially of an annular chamber formed by a component of one of the resilient masses. 39. The annular chamber is defined by an outer circumferential wall axially surrounding the rotating elastic damper and opposing side walls extending radially inwardly from the outer circumferential wall and receiving the rotating elastic damper therebetween. 39. A torque transmission device according to claim 37 or 38, wherein the torque transmission device is formed. 40. Torque transmission device according to any one of claims 37 to 39, wherein the first resilient mass has an annular chamber. 41, one side wall of the annular chamber extends radially between the rotational elastic damper and the second resilient mass, and the radially inner extent of the side wall and the second resilient mass 41. The torque transmission device according to any one of claims 37 to 40, wherein a sealing member is provided between. 42. The first resilient mass has a ring-shaped axial extension, which forms the outer circumferential wall of the annular chamber, and the rotational elastic damper and the second resilient mass Claim 37, wherein a side wall of said annular chamber extending radially between is fixed to said ring-shaped axial addition.
42. The torque transmission device according to any one of items 41 to 41. 43. An axial recess is provided in the radially inner position of the axial appendage of the first bouncy mass, and a plurality of gears arranged in a planetary manner are housed in the axial recess. has been,
A torque transmission device according to any one of claims 9 to 42. 44. Any of claims 9 to 43, wherein the side wall fixed to the axially extending portion axially closes the axially recessed portion for accommodating the planetary gear. or1
Torque transmission device as described in . 45. The torque transmission device according to any one of claims 42 to 44, wherein the side wall is fixed to the end face of the axially extending portion. 46. Claim 42, wherein a sealing member is provided between the end face of the axially extending portion and the side wall fixed to the end face at a radially outer position of the gears arranged in a planetary manner. 45. The torque transmission device according to any one of items 45 to 45. 47. Torque transmission device according to any one of claims 37 to 46, wherein the chamber is only partially filled. 48. When torque is transmitted from the internal combustion engine to the transmission, the power passes from the crankshaft to the first bouncing mass, from where it passes through the input part of a hydraulic device, such as a hydraulic clutch, the output part of the hydraulic device, a shock absorber. 48. Torque transmission device according to any one of claims 1 to 47, which reaches the clutch via the second resilient mass and the second resilient mass. 49. A second bouncy mass connectable to the transmission input shaft via a clutch such as a friction clutch is non-rotatable and axially displaceable relative to the second bouncy mass and the bouncy mass. 49. Torque transmission device according to claim 1, further comprising a friction surface for a clutch disc which is clamped between the clutch disc and a pressure plate. 50. The torque transmission device according to any one of claims 1 to 49, wherein the slip between both bouncing masses is 20 to 200 revolutions.