WO2002025134A1 - Device and method for modifying the speed of a shaft - Google Patents
Device and method for modifying the speed of a shaft Download PDFInfo
- Publication number
- WO2002025134A1 WO2002025134A1 PCT/DE2001/002780 DE0102780W WO0225134A1 WO 2002025134 A1 WO2002025134 A1 WO 2002025134A1 DE 0102780 W DE0102780 W DE 0102780W WO 0225134 A1 WO0225134 A1 WO 0225134A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- contact
- torque
- constraining means
- ring gear
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/22—Automatic clutches actuated entirely mechanically controlled by both speed and torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
- F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N11/00—Starting of engines by means of electric motors
- F02N11/04—Starting of engines by means of electric motors the motors being associated with current generators
Definitions
- the invention relates to a device for changing the rotational speed of a shaft with at least one constraining means, which can have an angular velocity that is different from the angular velocity of the shaft, and at least one contact means for establishing contact between the shaft and the constraining means.
- the invention further relates to a method for changing the rotational speed of a shaft, in which a contact is used to make contact between the shaft and a constraining means, which contact can have an angular speed that is different from the angular speed of the shaft.
- this active signal conveyed from the outside consists, for example, of depressing or releasing the clutch pedal.
- this active signal conveyed from the outside consists, for example, of depressing or releasing the clutch pedal.
- separate device components are therefore required, by means of which the arrangement as a whole is complex.
- the invention is based on the generic device in that the contact between the constraining means and the contact means depends on a torque of the shaft. There is therefore no need for any active elements which influence the contact between the constraining means and the contact means and thus the speed of the shaft from the outside. Rather, a torque of the shaft, which is naturally available during a rotational movement, is used to influence the rotational speed of the shaft, that is to say to lock or brake the shaft, for example.
- the contact between the constraining means and the contact means preferably depends on the magnitude of the torque. It it is therefore possible to allow an uninfluenced rotation of the shaft in a certain value range of the torque, while the speed of the shaft is influenced in another value range of the torque.
- the contact between the constraining means and the contact means depends on the direction of the torque of the shaft. Consequently, it can be achieved that the shaft rotates freely in one direction, while rotation in the other direction and a related torque reversal influence the rotational speed of the shaft, for example by locking the shaft.
- the constraining means is fixed in space.
- a device is thus available in which the shaft is blocked or braked by contact of the contact means with the fixed space constraining means, ⁇ so that overall a purely passive reduction in the speed of a shaft is possible.
- the device according to the invention is particularly advantageous in that at least one driver is arranged on the shaft, that the contact means has a radially displaceable contact element, that a force dependent on the torque of the shaft can be applied to the contact means by the driver, and that the contact element is dependent on the force dependent on the torque of the shaft changes its radial position.
- the driver which is arranged on the shaft, serves to transmit the torque to the contact means, so that the Konüaktmitt ⁇ l depending on this torque can make contact with the constraining means. This takes place in an advantageous manner in that a contact element of the contact means is shifted in its radial position so that it can come into contact with a radially external constraining means.
- the contact means comprises a knee lifting mechanism.
- the radial position of the contact element which is attached, for example, to one end of the knee lifting mechanism, can be changed.
- the knee joint is preferably flexed or stretched under the influence of an elastic restoring force.
- the device is particularly advantageous in that several drivers are provided on the shaft, that several contact means are provided on a rotatable inner ring, and that the axis of rotation of the shaft coincides with the axis of rotation of the inner ring. In this way, the resulting forces are evenly distributed on the shaft. Furthermore, * several contact means are available, so that a lower force when locking or braking the shaft has to be absorbed per contact means.
- the device is particularly advantageous in that the coercive means can cooperate with the contact means by closing. In this way, a reliable locking of the shaft is made possible.
- the constraining means is realized by a ring with an undulating inner profile and if the contact element is a pawl which can be snapped into the undulating inner profile. By extending the pawl in the radial direction, it can latch into a trough of the undulating inner profile, so that a reliable positive locking connection is created.
- the contact element changes its radial position dynamically up to an upper limit torque of the shaft in a first direction of the torque, and if the upper limit torque of the shaft exceeds the contact element changes its position abruptly to a contact position and with the constraining means cooperates and the contact element maintains its contact position when the shaft falls below the upper limit torque.
- the shaft can therefore rotate unaffected by the constraining means until the upper limit torque is reached. Only when the upper limit torque is exceeded does the interaction between the contact means and the constraining means occur, so that the shaft is blocked. This sudden switching is also referred to as "snap-through behavior".
- the contact means After the sudden switching, the contact means reaches a stable position, so that the contact element maintains its contact position even if the torque is reduced as desired, that is to say in particular if the upper limit torque is undershot.
- the contact element In a second direction of the torque of the shaft, which is opposite to the first direction of the torque of the shaft, the contact element can preferably be guided out of its contact position.
- the drivers of the shaft can thus cause the contact means to give up their position locked with the constraining means, so that the rotation of the shaft is released again.
- the constraining means can interact with the contact means by frictional force. There is therefore no need to completely lock the shaft rotation. Rather, the friction can also gradually reduce the rotational speed.
- the constraining means can interact with the contact means by frictional engagement.
- the frictional force can thus be increased to such an extent that the shaft rotation can also be completely locked.
- the constraining means is realized by a ring with an essentially smooth inside and in that the contact element is a brake shoe which can interact with the inside of the ring.
- the braking force can thus be gradually increased by radially displacing the brake shoes of the contact means. If the brake shoes are part of a knee lifting mechanism in this case, this is designed so that that the toggle lever mechanisms cannot penetrate even with maximum braking forces.
- the invention shows its particular advantages in that the shaft is the ring gear shaft of a planetary gear, that the crankshaft of an engine is connected to the planet gear carrier, that the sun gear shaft of the planetary gear carries a pulley, and that a sprag clutch is integrated between the sun gear shaft and the ring gear shaft.
- three different operating conditions can advantageously be generated with a combination of internal combustion engine and starter-generator.
- the internal combustion engine can be started with a large gear ratio between the crankshaft and the starter generator, which drives a belt pulley via a belt drive.
- generator operation with a low gear ratio can take place between the crankshaft and the starter generator.
- the device is have advantageous that locks with the crankshaft as the drive of the sprag and the forcing means no influence on the ring gear shaft especially as ⁇ . In this Be ⁇ the planetary gear drive blocked, and crankshaft pulley and gear rotate at the same speed.
- the starter generator works in generator mode.
- the sprag freewheel is free with the pulley as the drive Force means up to an upper limit torque of the ring gear shaft have no influence on the ring gear shaft and the force means from an upper limit torque of the ring gear shaft have an influence on the ring gear shaft.
- the system can be used for air conditioning in a stand.
- the starter generator can always be used to operate a compressor for an air conditioning system when the crankshaft is stationary.
- the arrangement can also be used to start the internal combustion engine, namely by increasing the torque of the ring gear shaft, so that it applies a torque above the upper limit torque. Due to the presence of a torque above the upper limit torque, the ring gear shaft is braked or locked, and consequently the power of the starter generator is transmitted to the crankshaft of the internal combustion engine via the pulley so that it starts,
- the invention builds on the generic method in that the contact is established between the constraining means and the contact means as a function of a torque of the shaft. No active elements are therefore required which influence the contact between the coercive means and the contact means and thus the speed of the shaft from the outside. Rather, a torque of the shaft, which is naturally available during a rotational movement, is used to influence the rotational speed of the shaft, that is to say to lock or brake the shaft, for example.
- the contact between the constraining means and the contact means is preferably established as a function of the magnitude of the torque. It is therefore possible to allow an uninfluenced rotation of the shaft in a certain value range of the torque, while the speed of the shaft is influenced in another value range of the torque.
- the contact between the constraining means and the contact means is established as a function of the direction of the torque. Consequently, it can be achieved that the shaft rotates freely in one direction, while rotation in the other direction and a related torque reversal influence the rotational speed of the shaft, for example by locking the shaft.
- the constraining means is spatially fixed.
- a method is available, in which the shaft by contact 'of the contact means will be locked with the spatially fixed coercion or braked, so that is possible for a total shaft a purely passive reduction of the speed.
- the method is particularly advantageous if at least one driver is arranged on the shaft, if the contact means has a radially displaceable contact element, if a force dependent on the torque of the shaft is applied to the contact means by the driver and if the contact element is a function of the radial force dependent on the torque of the shaft Position changed.
- the driver which is arranged on the shaft, serves to transmit the torque to the contact means, so that the contact means can make contact with the constraining means as a function of this torque. This takes place in an advantageous manner in that a contact element of the contact means is displaced in its radial position, so that it can come into contact with a radially outer constraining means.
- the constraining means interacts with the contact means by positive locking. In this way, a reliable blocking of the shaft is made possible.
- the constraining means is realized by a ring with an undulating inner profile and if the contact element is a pawl which engages in the undulating inner profile. By extending the pawl in the radial direction, it can latch into a trough of the undulating inner profile, so that a reliable positive locking connection is created.
- the contact element dynamically changes its radial position up to an upper limit torque of the shaft in a first direction of the torque, and if the upper limit torque of the shaft is exceeded, the contact element suddenly changes its radial position to a contact position and with it Coercive agents work together and exceed the upper limit torque of the shaft, the contact element maintains its contact position. Until the upper limit torque is reached, the shaft can therefore rotate unaffected by the constraining means. Only when the upper limit torque is exceeded does the interaction between the contact means and the constraining means occur, so that the shaft is locked. This sudden switching is also referred to as "snap-through behavior".
- the contact means After the sudden switching, the contact means reaches a stable position, so that the contact element maintains its contact position even if the torque is reduced as desired, that is to say in particular if the upper limit torque is undershot. Any mechanisms with “snap-through behavior" can advantageously be used in the context of the invention.
- the contact element In the case of a second direction of the torque of the shaft, which is opposite to the first direction of the torque of the shaft, the contact element is preferably guided out of its contact position.
- the drivers of the shaft can thus cause the contact means to give up their position locked with the constraining means, so that the rotation of the shaft is released again.
- the constraining means cooperates with the contact means by frictional force. There is therefore no need to completely lock the shaft rotation. Rather, the friction can also gradually reduce the rotational speed. It is particularly preferred if the constraining means interacts with the contact means by frictional engagement. The frictional force can thus be increased to such an extent that the shaft rotation can also be completely locked.
- the constraining means is realized by a ring with an essentially smooth inside and if the contact element is a brake shoe which is braked by the inside of the ring.
- the braking force can be gradually increased by radially displacing the brake shoes of the contact means.
- the brake shoes are part of a knee lifting mechanism, this is designed so that the knee lever mechanisms cannot penetrate even with the maximum braking force.
- the method of the invention is' particularly when the shaft is the ring gear of a planetary gear, when the crankshaft of an engine is connected to the gear rack when the sun gear of the planetary gear carries a pulley and when a sprag clutch is integrated between the sun gear and ring gear.
- three different operating states can advantageously be generated with a combination of an internal combustion engine and a starter-generator.
- the internal combustion engine can be started with a large gear ratio between the crankshaft and the starter generator, which drives a belt pulley via a belt drive.
- generator operation with a low gear ratio can take place between the crankshaft and the starter generator.
- stationary air conditioning is possible in which the pulley is uncoupled from the crankshaft.
- the clamping body freewheel locks with the crankshaft as the drive and the constraining means have no influence on the ring gear shaft.
- the planetary gear is locked and the crankshaft, pulley and ring gear rotate at the same speed.
- the starter generator works in generator mode.
- the constraining means have no influence on the ring gear shaft up to an upper limit torque of the ring gear shaft and the constraining means have an influence on the ring gear shaft from an upper limit torque of the ring gear shaft.
- the system can be used for air conditioning in a stand.
- the starter generator can always be used to operate a compressor for an air conditioning system when the crankshaft is stationary.
- the arrangement can also be used to start the internal combustion engine, namely by increasing the torque of the ring gear shaft, so that it applies a torque above the upper limit torque. Due to the presence of a torque above the upper limit torque, the ring gear shaft is braked or locked, and consequently the force of the starter generator is transmitted via the belt disc is transferred to the crankshaft of the internal combustion engine so that it starts.
- the invention is based on the surprising finding that a passively switching locking element or braking element can be made available by using the torque of the shaft to be locked or braked as a controlling variable.
- a passively switching locking element or braking element can be made available by using the torque of the shaft to be locked or braked as a controlling variable.
- Figure 1 shows a first embodiment of a device according to the invention in a first operating state
- Figure 2 shows the embodiment of Figure 1 in a second operating state
- Figure 3 shows the embodiment of Figure 1 in a third operating state
- FIG. 4 shows a second embodiment of a device according to the invention in a first operating state
- FIG. 5 shows the embodiment according to FIG. 4 in a second operating state
- FIG. 6 shows the embodiment according to FIG. 4 in a third operating state
- Figure 7 is an illustration for explaining a contact means
- FIG. 8 shows an illustration to explain a “snap-through behavior”
- FIG. 9 shows a planetary gear transmission in a first operating state
- FIG. 10 shows the planetary gear according to FIG. 9 in a second operating state
- FIG. 11 shows the planetary gear according to FIG. 9 in a third operating state.
- FIG. 1 shows a first embodiment of a device according to the invention in a sectional view.
- Downtown a shaft 10 is provided in the arrangement.
- Carriers 16 are arranged on this shaft 10.
- the axis of the shaft 10 coincides with the axis of an inner ring 40.
- This inner ring 40 carries contact means 14.
- stops 38 are arranged on the inner ring, which together with the contact means . can work.
- An outer ring 12 with an inner profile 42 is arranged around the inner ring 40.
- the axis of the outer ring 12 also coincides with the axes of the shaft 10 and the inner ring 40.
- the outer ring 12 is fixed in space, while the inner ring 40 and the shaft 10 are rotatably mounted.
- the contact means 14 are each equipped with a knee lifting mechanism 22.
- This comprises two levers 24, 26 and three joints 28, 30, 32.
- a spring 56 is arranged between the two joints 28, 32 on the outside.
- a sliding block 34 is provided on the outer joint 32 of the knee lifting mechanism 22 and is guided in a guide 36. On the outside of the sliding block 34, a pawl 18 is arranged as a contact element. The mode of operation of the toggle lever mechanism 22 is explained in detail below with reference to FIGS. 7 and 8.
- FIG. 1 shows the device according to the invention in a first operating state.
- the shaft 10 rotates clockwise.
- the drivers 16 of the shaft 10 exert a force on the central joints 30 of the toggle lever mechanisms 22, which depends on the torque applied by the shaft 10.
- the springs 56 are tensioned by the force applied to the toggle lever mechanisms 22.
- the torque of the shaft 10 has an amount, so that in the state shown, the mass of the knee lifting mechanism is neglected 22 there is a balance of forces between the force applied by the torque and the spring force. Therefore, the inner ring with the shaft 10 can rotate clockwise.
- the pawls 18 do not engage in the inner profile of the outer ring 12, so that an unimpeded joint rotation of the shaft 10 and the inner ring 40 can take place.
- FIG. 2 shows a second operating state of the device according to FIG. 1.
- This operating state is achieved in that the shaft 10 exceeds an upper limit torque, which depends on the design of the contact means 14 and the springs 56. If one starts from the state in FIG. 1, the pawl 18 is displaced more and more radially outwards as the torque of the shaft 10 increases. At a certain limit torque, the toggle mechanism 22 strikes through and against the stop 38. This situation is shown in Figure 2. It is also clear that the locking pawl 18 is engaged in the inner profile 42 of the outer ring 12 in this state. Since the outer ring is fixed in space 12, the rotation of the shaft 10 is blocked in the example shown in Figure 2 'condition.
- the pawl 18 nevertheless remains in the locked state, since the distance between the stop 38 and the axis of the adjacent spring 56 is chosen to be so large that the spring 56 prevents the knee lifting mechanism 22 from snapping back. On the other hand, the distance between the stop 38 and the axis of the adjacent spring 56 is chosen so small that in the struck state the pawl 18 remains locked in the inner profile 42 of the outer ring 12.
- FIG. 3 if the shaft 10 continues to rotate counterclockwise, the state shown in FIG. 3 is reached at a certain point.
- the device according to the invention is shown in a third operating state.
- a selection of the toggle lever mechanisms 22 and a selection of the drivers 16 were marked by capital letters in FIGS. 1 to 3.
- shaft 10 is in clockwise rotation in contact with toggle mechanism 22A via driver 16A, while shaft 10 is in contact with toggle mechanism 22B via driver 16B.
- This assignment of driver 16 and knee lifting mechanism 22 does not change in FIG. 2 either.
- the shaft has rotated counterclockwise, so that, for example, the driver 16A is now in contact with the contact element 22B.
- the movement of the shaft 10 is blocked asc only if, on the one hand, the torque of the shaft 10 has a certain direction and, on the other hand, it exceeds a certain size.
- the drivers 16 and the contact means 14 are arranged such that the drivers 16 can come into contact with adjacent toggle lever mechanisms 22 from both sides. However, the construction is carried out in such a way that there are no other possible collisions between the drivers and any components of the arrangement.
- a positive connection to the inner profile 42 of the outer ring 12 is established via the pawls 18.
- the shaft 10 initially runs freely without a driver 16 interacting with the inner ring 40.
- the driver 16A then comes into contact with the knee lifting mechanism 22B.
- a freewheel has been implemented when the torque is reversed.
- the knee lever mechanisms snap back and the pawls 18 release the inner ring 40.
- the magnitude of the force required for the toggle mechanisms 22 to snap back depends on the position of the stops 38. The force can be chosen arbitrarily small depending on the amount.
- Schulz, M. and Pellegrino, S. (2000) ⁇ guilibrium paths of mechanical systems with unilateral constraints, part I: theory, to apear in: The Royal Society Proceedings: Mathematical, Physical and Engineering Sciences.
- a theory about equilibrium paths of systems with one-sided bonds is derived.
- the diameters of the inner ring 40 and the outer ring 12 are smaller. can be selected if the drivers 16 are aligned axially rather than radially. In this way, an overall more compact arrangement can be achieved.
- Figure 4 shows a second embodiment of a device according to the invention in a sectional view. This embodiment is similar in many details to the embodiment according to FIGS. 1 to 3.
- the contact elements on the contact means 14 are designed here as brake shoes 20.
- the outer ring 12 in the embodiment according to FIG. 4 has an essentially smooth inside.
- FIG. 4 shows a first operating state in which the shaft 10 exerts a comparatively low torque on the central joints 30 of the toggle lever mechanisms 22. Consequently, the force of the springs 56 is sufficient to prevent the brake shoes from contacting the inside of the outer ring 12.
- the diameters of the inner ring 40 and the outer ring 12 can be selected to be smaller if the drivers 16 are directed axially rather than radially.
- FIG. 7 serves to explain the contact means 14 in more detail.
- the contact means which form a knee lifting mechanism 22, comprise two levers 24, 26, each of which has a ne length L.
- the levers are connected to one another via a joint 30.
- Further joints 28, 32 are arranged on the ends of the levers 24, 26 facing away from the connection point. These joints 28, 32 are connected to a linearly elastic spring 56, which has a spring constant c.
- the left lever 24 is fixed in space via the joint 25.
- the right lever 26 is horizontally displaceably mounted on a sliding block 34 via a further joint 32.
- the joints 28, 30, 32 are preferably designed as cylindrical joints, the axes of which are all parallel and perpendicular to the plane of representation.
- the entire knee lifting mechanism 22 moves in the representation plane with a degree of freedom of 1.
- FIG. 3 shows the equilibrium positions ⁇ as a function of a control parameter ⁇ .
- the graph in FIG. 8 is also called the equilibrium path, since all points of the curve correspond to equilibrium positions of the mechanism, in each case for different angles ⁇ .
- the course of the equilibrium path is shown qualitatively in FIG. Points of the thickly drawn curves correspond to stable equilibrium positions, and points of the thinly drawn curve correspond to unstable equilibrium positions.
- the points with horizontal tangents A and B are also unstable and are called limit points.
- a method for computing equilibrium paths of mechanical systems is discussed in the following publication: Thompson, JMT and Hunt, GW ('1973), A general theory of elastic stability, J. Wiley, London.
- the behavior of the system can be described if the force in a model is increased quasi-statically from zero.
- F the system is in the stable equilibrium position ⁇ o.
- F growing quasi-statically one moves on the right stable part of the equilibrium path until the limit point A is reached.
- the path becomes unstable.
- F is further enlarged, an equilibrium position is no longer reached in the vicinity of the limit point.
- the mechanism strikes dynamically in the direction of the arrow. This behavior is referred to as "snap-through behavior".
- the system carries out vibrations. After the vibrations have subsided, the system follows the force from point C upwards from the left part of the stable equilibrium path.
- the dynamic penetration is associated with a very rapid movement of the cylinder joint 30 from the half-plane above the spring axis into the half-plane below, the spring axis in FIG. 7.
- This instability phenomenon is used in the embodiments of the invention according to FIGS. 1 to 3 in order to lock the shaft 10 in one direction, specifically when a torque exceeds a critical value.
- the device is preferably used in connection with a planetary gear, the functioning of which can be seen from FIGS. 9 to 11.
- the planetary gear is integrated into the device according to the invention such that, for example, a crankshaft is connected to the planet gear carrier 50.
- a pulley which is connected to a starter generator via a belt, is connected to the sun gear 54 via the sun gear shaft.
- a conventional sprag freewheel is integrated between the sun gear shaft and the ring gear shaft connected to the ring gear 48.
- a ring is located between the ring gear shaft and a spatially fixed constraining means, for example the motor housing .
- Connection with the figures 1 to 8 explained mechanism, which the ring gear 48 depending on the size and direction of the acting on the ring gear. Torque locks or releases. To prevent the mechanism from locking due to centrifugal forces alone, a centrifugal lock can be used.
- FIG. 1 A further operating state of the planetary gear is shown in FIG.
- the pulley connected to the sun gear 54 acts as a drive; the starter generator consequently provides the drive energy.
- the ring gear 48 rotates counter to the direction of rotation of the sun gear. Because of the low torque of the ring gear and thus the ring gear shaft, operating states according to FIGS. 1 and 4 exist, ie the ring gear shaft and the ring gear are not affected by the interaction of the Contact means and the coercive means blocked. As a result, the energy of the starter generator can be used to drive a compressor of a parking cooler.
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Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10194007T DE10194007D2 (en) | 2000-09-18 | 2001-07-21 | Device and method for changing the speed of a shaft |
AU2001278397A AU2001278397A1 (en) | 2000-09-18 | 2001-07-21 | Device and method for modifying the speed of a shaft |
EP01956364A EP1322870A1 (en) | 2000-09-18 | 2001-07-21 | Device and method for modifying the speed of a shaft |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE10046035.6 | 2000-09-18 | ||
DE2000146035 DE10046035A1 (en) | 2000-09-18 | 2000-09-18 | Device and method for changing the speed of a shaft |
Publications (1)
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WO2002025134A1 true WO2002025134A1 (en) | 2002-03-28 |
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PCT/DE2001/002780 WO2002025134A1 (en) | 2000-09-18 | 2001-07-21 | Device and method for modifying the speed of a shaft |
Country Status (4)
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EP (1) | EP1322870A1 (en) |
AU (1) | AU2001278397A1 (en) |
DE (2) | DE10046035A1 (en) |
WO (1) | WO2002025134A1 (en) |
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DE102008031527B4 (en) * | 2008-07-03 | 2015-02-05 | Audi Ag | centrifugal clutch |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0384808A1 (en) * | 1989-02-21 | 1990-08-29 | Valeo Equipements Electriques Moteur | Alternator-starter with automatic coupling device |
US5040643A (en) * | 1990-08-13 | 1991-08-20 | Sundstrand Corporation | Radial torque limiter |
DE4128112A1 (en) * | 1991-08-24 | 1993-02-25 | Swf Auto Electric Gmbh | Locking device between engine shaft and gearbox shaft - has locking pawl engaging with locking ring to block displacement in adverse conditions |
DE19927521A1 (en) * | 1998-11-14 | 2000-06-08 | Bosch Gmbh Robert | Electrical machine |
EP1038719A1 (en) * | 1999-03-17 | 2000-09-27 | MAN Nutzfahrzeuge Aktiengesellschaft | Starter/generator drive arrangement and attachment to an internal combustion engine |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE189967C (en) * | ||||
US1306513A (en) * | 1919-06-10 | aurand | ||
DE458809C (en) * | 1925-02-03 | 1928-10-16 | Heinrich Horn Soehne | Automatic mechanical brake |
DE1000646B (en) * | 1952-05-02 | 1957-01-10 | Eickhoff Geb | Shaft coupling disengages automatically in the event of overload |
US2829749A (en) * | 1952-08-25 | 1958-04-08 | Thomson Edward | Shock load clutch with automatic reset |
DE1300744B (en) * | 1967-07-29 | 1969-08-07 | Welger Maschinenfabrik Geb | Overload safety clutch, especially for ratchet jacks |
US4641735A (en) * | 1985-05-30 | 1987-02-10 | Gerard Couture | Overload clutch with automatic reset |
DE19650039A1 (en) * | 1995-12-21 | 1997-06-26 | Gkn Viscodrive Gmbh | Coupling unit with at least one viscous coupling and one friction clutch |
DE19824457C2 (en) * | 1998-05-30 | 2000-06-08 | Gkn Viscodrive Gmbh | Shaft coupling with damping device |
-
2000
- 2000-09-18 DE DE2000146035 patent/DE10046035A1/en not_active Withdrawn
-
2001
- 2001-07-21 DE DE10194007T patent/DE10194007D2/en not_active Expired - Fee Related
- 2001-07-21 EP EP01956364A patent/EP1322870A1/en not_active Withdrawn
- 2001-07-21 WO PCT/DE2001/002780 patent/WO2002025134A1/en not_active Application Discontinuation
- 2001-07-21 AU AU2001278397A patent/AU2001278397A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0384808A1 (en) * | 1989-02-21 | 1990-08-29 | Valeo Equipements Electriques Moteur | Alternator-starter with automatic coupling device |
US5040643A (en) * | 1990-08-13 | 1991-08-20 | Sundstrand Corporation | Radial torque limiter |
DE4128112A1 (en) * | 1991-08-24 | 1993-02-25 | Swf Auto Electric Gmbh | Locking device between engine shaft and gearbox shaft - has locking pawl engaging with locking ring to block displacement in adverse conditions |
DE19927521A1 (en) * | 1998-11-14 | 2000-06-08 | Bosch Gmbh Robert | Electrical machine |
EP1038719A1 (en) * | 1999-03-17 | 2000-09-27 | MAN Nutzfahrzeuge Aktiengesellschaft | Starter/generator drive arrangement and attachment to an internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
EP1322870A1 (en) | 2003-07-02 |
DE10194007D2 (en) | 2003-08-21 |
DE10046035A1 (en) | 2002-04-04 |
AU2001278397A1 (en) | 2002-04-02 |
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