Classifications

• • 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
  • F02N15/025—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the friction type
• • 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
  • F16D13/00—Friction clutches
  • F16D13/22—Friction clutches with axially-movable clutching members
  • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
  • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
• • 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
  • F16D13/00—Friction clutches
  • F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
• • 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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
  • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

• the invention relates to a pulley arrangement for a starter gear for starting an internal combustion engine of a motor vehicle, with the aid of which, for example, a crankshaft of an internal combustion engine with ancillaries, such as an alternator, a fuel pump or an engine oil pump can be connected and on the example using an electric starter torque in the crankshaft can be initiated to start the engine.
• a crankshaft of an internal combustion engine with ancillaries such as an alternator, a fuel pump or an engine oil pump can be connected and on the example using an electric starter torque in the crankshaft can be initiated to start the engine.
• a pulley arrangement may comprise a pulley and a planetary gear arranged radially inside the pulley, which is connected to a crankshaft of the internal combustion engine.
• the planetary gear can be operated outside via an actuator and causes a rotation of the crankshaft.
• a pulley arrangement for a starter transmission for starting an internal combustion engine of a motor vehicle with a pulley, a friction clutch, which is arranged radially inside the pulley and by means of which the pulley with a crankshaft of the starter gear can be brought into operative connection, wherein the friction clutch is an open position, in which the pulley is separated from the crankshaft, and has a closed position in which the pulley is operatively connected to the crankshaft, and actuating means for axially actuating the friction clutch between the open position and the closed position, wherein the friction clutch is actuated by means of a force acting on the pulley starter generator using the actuating means.
• the pulley arrangement according to the invention is therefore based on the principle that a crankshaft of a starter gearbox can be actuated by means of a friction clutch, which is arranged inside the belt pulley, during an engine standstill of the motor vehicle by means of a starter generator acting as an actuator.
• the pulley assembly may comprise actuating means which are adapted to actuate the friction clutch axially and to switch between an open position and a closed position of the friction clutch.
• the pulley assembly according to the invention is therefore based on a simple operating principle and allows easy operation of the crankshaft.
• the pulley assembly Since the pulley assembly has few components, it can be manufactured in particular inexpensively. In particular, additional manufacturing costs may be avoided based on providing an actuator for a planetary gear pulley assembly.
• the pulley assembly can be made particularly compact, since the friction clutch is disposed within the pulley and an axial force transfer of the actuating means can be used on the friction clutch for switching the friction clutch between its open position and its closed position.
• the pulley arrangement according to the invention can drive the crankshaft by means of the starter generator, the pulley arrangement and the starter gear can be operated particularly reliably, since in particular a failure of an external actuator can be avoided.
• the pulley assembly of the present invention may also provide a limited starting torque, for example, up to about 200 Newton-meters for the crankshaft so that the pulley assembly may enable a cost-effective start-stop system with stationary air conditioning, and is particularly useful for small engines and can perform a warm start on larger engines ,
• the actuating means may be formed as a one-piece or multi-piece link element, which may constitute a transmission element for transmitting a force.
• the actuating means and the pulley may be rotatable relative to each other, wherein the actuating means may be adapted to act in a first relative rotational position with respect to the pulley, the friction clutch with a first axial force for pressing the friction clutch in the closed position and in a second relative rotational position with respect to the pulley to apply the friction clutch with a second axial force for holding the friction clutch in the open position.
• the first relative rotational position can thus be the closed position of the friction clutch and the second relative rotational position can be assigned to the open position of the friction clutch.
• the first and second axial force can be the same or different.
• the pulley may be rotatable and the actuating means may be by means of a freewheel, which may be supported on a rotationally fixed and positionally fixed support member, in particular a housing of the pulley assembly, positionally stable and rotatably durable.
• a freewheel When rotating the pulley in the direction of rotation of the internal combustion engine of the freewheel can be formed in particular in the overtravel and the actuating means can rotate together with the pulley.
• the actuating means When driving the pulley by means of the starter generator, the actuating means can be held against rotation and positional stability, while the pulley can rotate relative to the actuating means according to a reverse direction of rotation of the starter generator against the predetermined by the internal combustion engine rotational direction of the pulley.
• a circuit of the friction clutch between its open position and its closed position by means of the actuating means can be effected particularly easily.
• the pulley assembly may further comprise at least one locking element for non-rotatably locking the actuating means relative to the pulley or the friction clutch, wherein the actuating means a, in particular circular, closed track for the at least one locking element with at least a first locking point, the open position of the Friction clutch may be assigned, and may have at least a second detent point, which may be associated with the closed position of the friction clutch.
• the at least first latching point and the at least second latching point of the track of the actuating means can in particular represent stable latching positions, ie self-locking latching positions, for the at least one latching element.
• This measure can cause the friction clutch can be held particularly safe in its open position or in its closed position, since the actuating means by means of the locking element relative to the pulley or friction clutch can be held against rotation.
• a solution of the latching of the latching element from the at least first or the at least second latching point can be effected particularly easily by means of the starter generator, whose low torque for driving the pulley and thus for releasing the latching element can be sufficient. Since the actuating means have a closed track for the at least one latching element, switching of the friction clutch between its open position and its closed position can be carried out alternately. Therefore, an inadvertently incorrect shift of the friction clutch can always be corrected, in particular when the internal combustion engine is at a standstill.
• the actuating means may be ramp-shaped on their side facing the at least one latching element and have at least one first ramp section between the at least first latching point and the at least second latching point and at least one second ramp section between the at least second latching point and the at least first latching point, wherein a pitch of at least first ramp portion may have a positive value and wherein a slope of the at least second ramp portion may have a negative value.
• the pitch with respect to an end face of the actuating means which may be facing the at least one locking element and / or run approximately perpendicular to a rotational axis of the pulley assembly, are measured.
• a positive value of the gradient of the first ramp section may correspond to an at least first ramp section rising in the direction of the at least one latching element between the first latching point and the second latching point.
• a negative value of the slope of the second ramp section may correspond to a sloping in the direction of at least one locking element at least second ramp section between the second detent point and the first detent point.
• a length, measured in particular along the track, of the at least first ramp section may be smaller than a corresponding length of the at least second ramp section, and / or the gradient of the at least first ramp section may be greater in magnitude than the slope of the at least second ramp section.
• the shorter length of the at least first ramp section compared to the length of the at least second ramp section can enable a particularly fast switching of the friction clutch from its open position to its closed position. At the same time accidental switching of the friction clutch can be avoided from its closed position to its open position, since the locking element has to cover a relatively long path along the at least the second ramp section.
• the magnitude greater slope of the at least first ramp portion compared to the slope of the at least second ramp portion can prevent accidental actuation of the friction clutch in the closed position, since a large stroke of the at least one latching portion must be overcome.
• an undesired shifting of the friction clutch from its closed position to the open position is prevented in comparison with the gradient of the at least first ramp section.
• Both the longer path of the at least second ramp section and the lower slope of the at least second ramp section make it possible for the crankshaft to rotate slowly when the active connection between the crankshaft and the friction clutch is released, and thus a slight counter-rotation of the crankshaft in the just released state can be small. Thereby, a material stress of the pulley assembly can be reduced.
• the track may be formed substantially concentric with respect to a rotational axis of the pulley, so that the actuating means may have a structurally particularly simple construction.
• the track may have a multiplicity of first latching points and a plurality of second latching points, wherein a first latching point of the plurality of first latching points can be arranged along the track, adjacent to a second latching point of the plurality of second latching points.
• the pulley assembly may further comprise a plurality of locking elements, and it may be provided for each locking element of the plurality of locking elements, a first locking point and a second locking point of the raceway.
• the pulley arrangement may have three latching elements, three first latching points and three second latching points and optionally corresponding first and second ramp sections.
• one or more latching elements can be moved endlessly between a first latching point and a second latching point, so that the open position and the closed position of the friction clutch can alternate continuously.
• Providing the pulley assembly with the plurality of detents may increase safety in holding the friction clutch in its closed position or in its open position.
• the track may have an at least partially along the track extending receptacle for partially receiving the at least one locking element or the plurality of locking elements in which the at least one locking element or the plurality of locking elements can be performed safely.
• the at least one latching element or the plurality of latching elements can be spherical, that is to say in the form of a ball, or in the form of a roller, that is to say as a roller with preferably a spherically shaped cylinder jacket surface.
• This measure can cause a frictional force between the actuating means and the latching element can be reduced due to a relative movement of the latching element and the actuating means, so that a lifetime of the latching element and the actuating means can be increased.
• the pulley assembly may further comprise a counter-pressure element for the at least one latching element, wherein the counter-pressure element may be arranged on a side facing away from the actuating means of the at least one latching element. Consequently, the actuating means together with the latching element and the counter-pressure element can form a bearing in which the counter-pressure element and the actuating means can rotate relative to one another. This allows a simple rotatably holding the locking element between the actuating means and the counter-pressure element.
• the counter-pressure element and the pulley may be rotatable relative to each other, wherein the actuating means may be adapted to act in a first relative rotational position of the counter-pressure element with respect to the pulley, the friction clutch with a first axial force for pressing the friction clutch in the closed position and in a second relative rotational position of the counter-pressure element with respect to the pulley to act on the friction clutch with a second axial force for holding the friction clutch in the open position.
• the first relative rotational position may be the closed position of the friction clutch and the second relative rotational position may be the open position be assigned to the friction clutch.
• the first axial force may be equal to or different from the second axial force.
• the principle of "mechanical center release" can also be used with pulley rotating actuators. This can also be a particularly compact and inexpensive construction of the pulley assembly can be effected.
• the pulley and the actuating means to each other rotatably and rotatably formed and the counter-pressure element can be by means of a freewheel, which may be supported on a rotationally fixed and positionally fixed support member, in particular a housing of the pulley assembly, positionally stable and rotatably durable.
• the freewheel When rotating the pulley in the direction of rotation of the internal combustion engine, the freewheel can be designed in particular in the overtaking direction, so that the counter-pressure element can rotate together with the pulley and the actuating means.
• the counter-pressure element When driving the pulley by means of the starter generator, the counter-pressure element can be rotationally fixed and held position while the pulley can rotate together with the actuating means relative to the counter-pressure element according to the remindheftcardrich- direction of the starter generator against the predetermined direction of rotation of the pulley by the internal combustion engine.
• a circuit of the friction clutch between its open position and its closed position by means of the actuating means can be effected particularly easily by the friction clutch can be acted upon in response to a relative rotational position of the reaction element with respect to the pulley with an axial force of the actuating means.
• the counterpressure element can be formed substantially free of ramps on its side facing the at least one latching element. This measure can be realized in particular when substantially not against a rotational axis of the actuating means tiltable actuating means and / or at a substantially not tiltable against a rotational axis of the counter-pressure element counter-pressure element, since the at least one locking element does not slip off a surface of the flat counter-pressure element and the at least one Locking element can be performed safely on the surface of the counter-pressure element.
• the counter-pressure element may be counter-ramped in relation to the ramp-shaped actuating element on its side facing the at least one latching element. be formed, so that a distance between the actuating means and the counter-pressure element along the raceway can be substantially contant. As a result, slippage or release of the at least one latching element between the counter-pressure element and the ramp-shaped actuating element can be prevented.
• a maximum lift of corresponding first and second ramp sections of the counterpressure element and of the at least first ramp section and the at least second ramp section of the actuating means can amount to half of a stroke of the at least first and second ramp sections of the actuating means in the case of a ramp-free counterpressure element.
• Actuation of the friction clutch between its closed position and its open position may require a double relative rotation angle of the pulley and the actuating means.
• an axial space of the pulley arrangement can be particularly low.
• the counter-pressure element on its the spherical, at least one locking element side facing at least partially along a track extending receptacle for partially receiving the at least one locking element, so that the security can be increased in a guide of the at least one locking element.
• the counter-pressure element may have at least one holding element for rotatably holding the at least one latching element.
• the at least one retaining element can be designed, for example, as a needle sleeve or as an radially inwardly arranged, angular extension of the counterpressure element.
• the pulley assembly may further comprise a Belleville spring which may be disposed radially inside the pulley and at least partially adjacent to the friction clutch and may have a radially inner edge region, the radially inner edge region of the Belleville spring being axially displaceable along the raceway by means of a movement of the at least one detent element can.
• a radially outer edge region of the disc spring can be arranged in a rotationally fixed manner between an axial extension of the belt pulley and the friction clutch with respect to the pulley or a radially outer edge region of the counterpressure element arranged adjacent to the friction clutch.
• the diaphragm spring can serve simultaneously as an axial suspension of the friction clutch on the axial extension of the pulley and as an axial suspension of the counter-pressure element and / or the actuating means. Overall, an axial force of the actuating means is transmitted to the friction clutch by this measure.
• the at least one latching element which is preferably designed as a roller, directly on the radially inner edge region of the plate spring, which may preferably have the tongues attached, whereby a costly mounting of the at least one latching element by means of the counter-pressure element omitted can.
• the actuating means may be arranged at least partially axially adjacent to the pulley and on one side of the pulley assembly, which may face away from the crankshaft, wherein the actuating means may be axially mounted on its side facing away from the at least one latching element and wherein the counter-pressure element at a radially inner Edge region of the plate spring can be arranged axially sprung.
• the radially inner edge region of the disc spring may have one or more tongues pointing radially inward.
• the axial bearing of the actuating means in particular on a housing or an axial extension of the pulley may allow a relative rotation of the actuating means and the pulley.
• the axial springing of the counter-pressure element may allow an axial displacement of the at least one latching element and the counter-pressure element and thus the plate spring corresponding to the raceway of the actuating means to act on the friction clutch with an axial force.
• This embodiment of the pulley assembly can effect a small outer diameter of the pulley assembly.
• the actuating means may be arranged radially inside the pulley, wherein the radially inner edge region of the plate spring adjacent to the at least one detent element side facing away from the counter-pressure element and axially sprung on its side facing away from the counter-pressure element, wherein the actuating means on a side facing away from the counter-pressure element the plate spring can be clamped axially.
• the counter-pressure element can be designed to be rotatable with respect to the pulley.
• the axial clamping of the actuating means can be accomplished by means of a slotted locking ring disposed adjacent to the axial springing of the disc spring, and an axial portion of the actuating means can pass through the disc spring and be secured in the locking ring.
• the radially inner edge region of the disk spring can be annular and thus a complicated configuration of the plate spring can be avoided with tongues that can claim a relatively large axial space.
• This measure can allow a particularly compact design of the pulley arrangement.
• An outer diameter of the belts Disc arrangement may be greater in particular compared to the previously described embodiment.
• the actuating means may be arranged radially inside the pulley, wherein the actuating means may be axially mounted on its side facing away from the locking element, wherein a radially outer portion of the counter-pressure element rotatably connected to the friction clutch and may be disposed adjacent to the radially outer edge region of the plate spring ,
• the radially inner edge region of the disk spring can be annular and thus a complicated configuration of the plate spring can be avoided with tongues that can claim a relatively large axial space.
• the installation space of the pulley arrangement can be reduced in the axial direction, in particular in comparison to the aforementioned configurations of the pulley arrangement. An axial reduction of the installation space can be in particular about 15 percent.
• the actuation of the friction clutch can take place directly on the counterpressure element, since the at least one latching element can be accommodated in the at least one holding element of the counterpressure element.
• the counter-pressure element can receive the at least one latching element directly and be axially movable by means of the actuating means.
• the counter-pressure element can be configured as a substantially disk-annular pressure plate which has a radially inner annular portion, on which at least one holding element for the at least one latching element can be arranged.
• the holding element may, for example, have an angled body, which extends in a continuation of the pressure plate radially inwardly and may be open in the direction of the at least one latching element.
• the three aforementioned embodiments of the pulley arrangement may depend on a field of application of the pulley arrangement.
• the invention further relates to a starter gearbox for a drive train for starting an internal combustion engine of a motor vehicle, with a pulley assembly, which is described above, a crankshaft, which is rotatably connected to a friction clutch of the pulley assembly and engageable with a pulley of the pulley assembly and a starter generator that attacks the pulley.
• the invention further relates to a drive train for starting an internal combustion engine of a motor vehicle, with a starter gear, which is described above.
• FIG. 3 is a schematic sectional view in plan view of a pulley arrangement according to a third embodiment
• FIG. 5 is a schematic sectional view in plan view of a pulley arrangement according to a fourth embodiment
• FIG. 6 is a schematic sectional view in plan view of a pulley arrangement according to a fifth embodiment
• FIG. 7 is a schematic sectional view in plan view of a pulley arrangement according to a sixth embodiment
• FIG. 8 is a schematic cross-sectional view of the pulley assembly in FIG.
• FIG. 9 is a schematic sectional view in plan view of a pulley assembly according to a seventh embodiment
• FIG. 10 is a schematic cross-sectional view of the pulley assembly in FIG. 9;
• FIG. 1 1 is a perspective view of a counter-pressure element of the pulley assembly in Fig. 10, Fig. 12 is a perspective view of the counter-pressure element in Fig. 1 1 and of
• FIG. 13 is a schematic sectional view in plan view of the counter-pressure element and the actuating means in FIG. 12.
• Drive train for starting an internal combustion engine of a motor vehicle has a pulley 12 and a friction clutch 14 which is arranged radially inside the pulley 12 and by means of which the pulley 12 can be brought into operative connection with a crankshaft 16.
• the pulley 12 is mounted on the crankshaft 16 by means of a bearing 18. In an open position of the friction clutch 14, the pulley 12 is separated from the crankshaft 16, i. the pulley 12 is not in operative connection with the crankshaft 16, and in a closed position of the friction clutch 14, the pulley 12 is in operative connection with the crankshaft 16.
• the pulley arrangement 10 has actuating means 20 for axially actuating the friction clutch 14 between the open position and the closed position of the friction clutch 14.
• the actuating means 20 are drivable by means of an attacking on the pulley 12 starter generator of the starter gear.
• the actuating means 20 are supported by means of a freewheel 22 on a housing 24 of the pulley assembly 10 or a housing of the pulley assembly 10 receiving the starter gear.
• the actuating means 20 are formed as a one-piece link element, which has a closed track 26 for a along the raceway 26 movably formed locking element 28.
• the raceway 26 is provided with a stable first latching point 30 and a stable, second latching point 32.
• the first latching point 30 is assigned to the open position of the friction clutch 14, and the second latching point 32 is assigned to the closed position of the friction clutch 14.
• the actuating means 20 have a first ramp section 34 between the first latching point 30 and the second latching point 32 and a second ramp section 36 between the second latching point 32 and the first latching point 30.
• a slope of the first ramp portion 34 is positive with respect to an end surface of the actuating means 20 which is perpendicular to a rotation axis of the pulley assembly 10 defined by the crankshaft 16 and faces the friction clutch 14, and a pitch of the second ramp portion 36 is negative with respect to this end surface.
• the first ramp section 34 rises in the direction of the friction clutch 14 and the second ramp section 36 drops as viewed in the direction of the friction clutch 14.
• the pulley 12 is driven by means of an internal combustion engine connected to the pulley 12.
• the direction of rotation of the internal combustion engine corresponds to the direction of rotation of the pulley 12.
• the freewheel 22 is in the overhauling direction, so that the actuating means 20 rotate with the pulley 12 with.
• the friction clutch 14 is in its closed position.
• the latching element 28 is thus located at the stable latching point 32.
• the freewheel 22 holds the actuating means 20 positionally fixed and rotationally fixed, so that the actuating means 20 and the pulley 12 rotate relative to each other.
• the latching element 28 travels along the track 26 of the actuating means 20 from the second latching point 32 to the first latching point 30.
• the actuating means 20 and the latching element 28 act on the friction clutch 14 with an axial force , which is indicated by means of a two-sided end arrow 38, and the friction clutch 14 is in its open position.
• the crankshaft 16 is rotated with the pulley 12, for example, by about 50 degrees and only remains rotationally fixed with respect to the housing of the starter gear when the friction clutch 14 begins to solve.
• a stationary air conditioning of the starter gear can be performed.
• the pulley 12 is further rotated during the engine standstill relative to the actuating means 20, which are again held stationary and stable position over the freewheel 22, the locking element 28 moves along the track 26 to the second detent point 32.
• the friction clutch 14 is acted upon by the actuating means 20 and the locking element 28 with an axial force which is greater than the axial force acting in the above-described relative rotational position 38 and which presses the friction clutch 14 in its closed position.
• the starter generator is first rotated back briefly again, and the pulley 12 and the actuating means 20 rotate relative to each other until the locking element 28 in the second detent position 32 and the friction clutch 28 in their Closed position is.
• the friction clutch 14 In a normal operation of the starter gear, the friction clutch 14 is in its closed position, and it can be arbitrarily between a generator mode in which the starter generator is charged, and a Boost- Operation, in which the starter generator supports the combustion engine to be changed.
• a decoupling of ancillaries, such as an alternator, a fuel pump or an engine oil pump, is not possible in normal operation of the pulley assembly, since a circuit of the friction clutch 14 between its closed position and its open position can only be done with the internal combustion engine.
• the pulley arrangement according to a second embodiment illustrated in FIG. 2 differs from the pulley arrangement 10 shown in FIG. 1 in that the actuating means 20 are arranged on the side facing the crankshaft 16.
• the pulley assembly 10 of a starter gear shown in FIG. 3 is similar to the pulley assembly in FIG. 1.
• the pulley assembly 10 is formed substantially concentrically about a rotation axis M of a crankshaft 16.
• a friction clutch 14 of the pulley assembly 10 is a normally closed friction clutch in which an inner disc carrier 40 and an outer disc carrier 42 against lamellae of a disk set 44, which form seven friction surfaces are always pressed.
• the outer plate carrier 42 is rotatably connected to the crankshaft 16.
• the inner disk carrier 40 is mounted on the hub 46 of the pulley assembly 10 by means of a double row ball bearing 18.
• the inner disk carrier 40 is also non-rotatably connected to the pulley 12 and centered the pulley 12.
• the freewheel 22 is designed as a sleeve free run and has a support sleeve 48 which is surrounded by a freewheel sleeve 50.
• the support sleeve 48 is fixedly mounted with an engine block of a housing of the starter gear.
• the actuating element 20 is designed as a link element and largely aaxially adjacent to the pulley 12 and disposed on one side of the pulley assembly 10, which faces away from the crankshaft 16.
• the actuating means 20 are mounted by means of a sliding bearing 52 axially and radially on a cup-shaped extension 54 of the pulley 12. Alternatively, a rolling bearing between the actuating means 20 and the axial extension 54 may be provided.
• the actuating means 20 have a sleeve-shaped or annular portion 56, on which a disc-annular portion 58 of the actuating means 20, for example a Kur- venusionnring, is arranged.
• a disc-annular portion 58 of the actuating means 20 for example a Kur- venusionnring.
• Each three first and second ramp sections 34, 36 of the actuating means 20 project from the disc-annular portion 58 in the direction of the crankshaft 18.
• a raceway 26 on the ramped portions 34, 36 of the actuating means 20 is formed flat.
• the pulley assembly 10 further comprises three locking elements 28, which are each formed as rollers and are held in a roller carrier serving as a counter-pressure element 60 of the pulley assembly 10.
• the disk-ring-shaped counter-pressure element 60 has three retaining elements 61 protruding axially in the direction of the actuating means 20.
• the counter-pressure element 60 is arranged on a side facing away from the actuating means 20 of the three latching elements 28 and axially spring-loaded via an annular Vorlasttellerfeder 62 on a rotatably connected to a plate spring 64 plastic disc 66.
• the plate spring 64 is arranged radially inside the pulley 12, and a radially inner edge region 68 of the plate spring 64 is axially displaceable by means of the relative rotation of the actuating means 20 and the pulley 12.
• the plastic disk 66 is applied to the radially inner edge region 68 of the plate spring 64 formed as tongues, and nose-shaped extensions of the plastic disk 66 engage between the tongues 68 of the disk spring 64, so that an anti-rotation lock is formed between the disk spring 64 and the plastic disk 66 ,
• the Vorlasttellerfeder 62 has circumferentially a toothing to ensure a rotation with respect to the plastic disc 66.
• the attached to the plastic disc 66 Vorlasttellerfeder 62 serves as a tolerance compensation with closed friction clutch 14.
• the biased in its normal state plate spring 64 is supported on the back pressure element 60 from.
• a radially outer edge region 70 of the disk spring 64 is clamped in a rotationally fixed manner between an axial extension 72 of the belt pulley 12 and the inner disk carrier 40 of the friction clutch 14 with respect to the belt pulley 12.
• An elastomeric lifter 74 which serves as a spring and damping element, is directly connected to an outer region of the crankshaft 16 and arranged axially adjacent to the pulley 12 on the crankshaft 16 side facing the pulley assembly 10.
• the rollers 28 rotatably received in the holding members 61 pass over the disc-annular portion 58 of the actuating means 20 and transmit the axial path defined by the raceway 26 of the actuating means 20 to the tongues 68 of the disc spring 64.
• the radially outer peripheral portion 70 of the plate spring 64 pressed against the inner disk carrier 40 of the friction clutch 14.
• the lamellae of the disk pack 44 are rotated by the axial application of force, depending on the relative rotational position of the actuating means 20 and the pulley 12, rotative mit- connected or separated from each other.
• the axial power flow is thereby closed via the hub 46 and the double-row ball bearing 18 and transmitted to the crankshaft 16.
• the actuating means 20 shown in FIG. 4 have a concentric design and are arranged concentrically with respect to the axis of rotation M.
• the raceway 26 has the first latching point 30, the second latching point 32, the first ramp section 34 and the second ramp section 36, which are each arranged as a group three times along the track 26.
• the first ramp portion 34 has a greater pitch than the second ramp portion 36 as measured with respect to the radial extent of an end face of the actuating means 20, while, measured along the circumferential direction of the actuating means 20, a length of the first ramp portion 34 is shorter than a length of the second ramp portion 36 is.
• the pulley assembly 10 shown in Fig. 5 is similar to the pulley assembly 10 formed in Fig. 3, but has, instead of the three formed as rollers locking elements 28 three formed as balls locking elements 28.
• a raceway 26 of actuating means 20 has a receptacle 76 for partially receiving the locking elements 28.
• the counter-pressure element 60 is formed as an angular bearing ring and has a receptacle 78 for partially receiving the locking elements 28.
• an axial needle bearing 52 or roller bearing between the disc-annular portion 58 of the actuating means 20 and the axial extension 54 of the pulley 12 is arranged.
• the actuating means 20 are disposed radially inside the pulley 12.
• the actuating means 20 have an angled body which is open in a direction away from the crankshaft 18.
• a disk-ring-shaped portion 58 of the actuating means 20 is formed similar to the disc-annular portion 58 in Fig. 5 and facing in the direction away from the crankshaft 18 direction.
• An annular portion 56 of the actuating means 20 is arranged radially outside of the disc-annular portion 58.
• a projecting end portion of the annular portion 56 rotatably extends with respect to the plate spring 64 through the plate spring 64 and is held under tension by means of a locking ring 80 axially.
• the plate spring 64 has an annular radially inner edge region 68, which is arranged adjacent to a side of a counterpressure element 60, which faces away from the latching element 28.
• the counterpressure element 60 is also connected to the circlip 80 by means of a preload plate spring 62 sprung.
• the counter-pressure element 60 has a sleeve-shaped radially inner portion 82, which is arranged on the freewheel sleeve 50 of the freewheel 22 and is surrounded by a radially outer, radially outwardly projecting disc-ring-shaped portion 84.
• the disk-ring-shaped portion 84 of the counter-pressure element 60 is formed in opposite directions rampenformig to the ramp-shaped disc-annular portion 58 of the actuating means 20 and has a receptacle 78 for the locking elements 28. This results in a centric force application to the spherical locking elements 28.
• a stroke of the actuating means 20 which corresponds to a height of the disc-ring-shaped portion 58 with respect to a latching element 38 facing end face of the actuating means 20 which Half.
• a total stroke of the actuating means 20 and the counter-pressure element 60 results as the sum of the stroke of the disc-annular portions 58, 64 and corresponds to the stroke of the actuating means 20 in Fig. 5.
• For moving the friction clutch 14 in its closed position and in its open position is therefore the double relative rotation the pulley 12 and the actuating means 20 required while the necessary torsional forces are half.
• an annular serving as a crankshaft damper Elastomertilger 74 is attached on an outer diameter of a hub 46.
• the flange of the elastomeric spider 74 is secured to the crankshaft 16 by a central screw.
• an axial toothing between the Elastomertilger 74 and the hub 46 is used, so that an additional positive engagement is achieved to the frictional engagement by the central screw.
• Operation of the pulley assembly 10 is similar to operation of the pulley assembly 10 in Figs. 1 and 2.
• the back pressure member 60 is rotationally held by a freewheel 22 of the pulley assembly 10 and the actuators 20 rotate with the pulley 12 and the inner disc carrier 40 with.
• actuating means 20 as the counter-pressure element 60 and the counter-pressure element 60 can be regarded as the actuating means 20.
• the pulley assembly 10 shown in FIGS. 7, 8 is similar to the pulley assembly in FIG. 6.
• the illustrations of the pulley assemblies 10 in FIGS. 6 and 7 are mirror images of each other.
• the counterpressure element 60 is configured as a roller carrier for the latching elements 28 configured as rollers and has three holding elements 61 on a disc-shaped portion 84 of the counterpressure element 60, so that instead of the ramp-shaped, disk-shaped portion 84, a roller bearing for the locking elements 28 is formed.
• the pulley assembly 10 shown in FIG. 9 is similar to the pulley assembly in FIGS. 7, 8. Slats of a disk set 44 of a friction clutch 14 define nine friction surfaces.
• the actuating means 20 are configured similarly to the actuating means 20 in FIG. 3 and arranged radially inside the pulley 12.
• a disk-ring-shaped portion 58 of the actuating means 20 is mounted by means of a Axialnadellagers 52 axially on a bearing ring 86 which is spring-biased by means of a Vorlasttellerfeder 62 against an inner disc carrier 40 of the friction clutch 14.
• the axial needle bearing 52 allows a small friction and thus small actuation torques upon rotation of the actuating element 20 relative to the pulley 12.
• the counter-pressure element 60 is formed as a pressure plate and has three radially inwardly arranged holding elements 61 for the locking elements 28 designed as rollers.
• a radially outer edge region 88 of the counter-pressure element 60 is connected in a rotationally fixed manner to the inner disk carrier 40 of the friction clutch 14.
• the radially outer edge region 88 of the counter-pressure element 60 is sprung by means of a disk spring 64 against an axial extension 72 of the belt pulley 12.
• the Vorlasttellerfeder 62 prevents lifting of the locking elements 28 of the actuating means 20, since the radially outer edge portion 88 of the counter-pressure element 60 is axially movable only to a concern with the slats and this position of the back pressure element 60 can also vary production-related. If the counter-pressure element 60 can no longer be closed to the friction clutch 14, the actuating means 20 are pressed against the locking elements 28 by means of the preload disc spring 62. As a result, tolerances are compensated and disturbing rattling noises are avoided.
• the angled retaining members 61 are arranged for the locking elements 28 radially within the plate-shaped reaction element 60 and point in the direction of the actuating means 20.
• Through holes 90 of the counter-pressure element 60 are provided radially adjacent to the holding elements 61 through which the inner plate carrier 40 and the counter-pressure element 60 are attached.
• Operation of the pulley assembly 10 is similar to operation of the pulley assembly 10 in FIGS. 1, 3.
• the actuators 20 are rotationally held by a freewheel 22 of the pulley assembly 10, and the counterpressure member 60 rotates with the pulley 12 and inner disc carrier 40 ,

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Pulleys (AREA)

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Citations (4)

• 2013
  • 2013-04-18 DE DE112013002359.8T patent/DE112013002359A5/de not_active Withdrawn
  • 2013-04-18 WO PCT/EP2013/058125 patent/WO2013167361A1/fr not_active Ceased
  • 2013-04-18 EP EP13721926.7A patent/EP2847455A1/fr not_active Withdrawn
  • 2013-04-18 DE DE201310207055 patent/DE102013207055A1/de not_active Withdrawn

Patent Citations (4)

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