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
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
  • F02N15/062—Starter drives
  • F02N15/063—Starter drives with resilient shock absorbers
• • 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
  • 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
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
  • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type
• • 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
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
  • F02N15/067—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement the starter comprising an electro-magnetically actuated lever

Definitions

• the invention relates to an improved pinion carrier assembly and to the corresponding starter and starter for a motor vehicle.
• the invention finds a particularly advantageous application for vehicles equipped with the stop and restart function of the engine (function called "stop and start” in English) depending on traffic conditions.
• the starter In order to start the engine of a vehicle, it is known to use a starter capable of transmitting mechanical energy to turn a crankshaft of the engine via gear wheels.
• the starter comprises a pinion installed on a drive shaft driven in rotation by a rotor of an electric motor.
• This pinion is provided with teeth capable of meshing with the teeth of a toothed wheel coupled to the crankshaft of the engine called starter ring.
• the drive gear belongs to a launcher mounted movably in translation on a drive shaft to move from a rest position in which the drive pinion is disengaged from the starter ring to a position active in which the drive pinion engages with the starter ring and vice versa.
• a starter starter assembly 1 shown in FIG. 1 comprises for this purpose the drive pinion 2 slidably mounted on a pinion carrier 4, a driver 3 mounted on a drive shaft via a helical link, and a friction clutch. 5 interposed between the pinion 2 and the driver 3.
• the pinion carrier 4 comprises a sleeve 7 on which is mounted the drive pinion 2 movable in translation, a plate 8 extending radially from a rear end of the sleeve, and an annular skirt 12 of axial orientation connected to the outer periphery of the reaction plate 8.
• the pinion 2 further comprises a cavity 13 for housing an elastic member 16, here a coil spring.
• This spring 16 is supported at one of its axial ends on the bottom of this cavity 13 constituted by an annular wall of radial orientation connected to the inner periphery of the pinion 2.
• the other axial end of the spring 16 is supported on the transverse front face of the reaction plate 8.
• a circlip 17 forming an axial stop is mounted in a groove machined in the front end of the sleeve 7.
• the friction clutch 5 further comprises a pressure element 6 constituted by a shoulder of the driver 3, a reaction element constituted by the plate 8 of the pinion carrier, as well as friction discs 9 located between the element pressure 6 and the reaction plate 8.
• the driver 3 is movable in translation relative to the reaction plate 8, in the limit of an axial play, between a disengaged position in which the driver 3 and the pinion 2 are uncoupled in rotation and a coupled position in which the pinion 2 and the driver 3 are coupled in rotation with each other.
• the discs 9 are housed in a housing 1 1 delimited by the reaction plate 8, the annular skirt 12 of axial orientation extending from the outer periphery of the reaction plate 8, as well as by a closure ring 14 crossed. centrally by the driver 3.
• the ring 14 is annularly hollowed at its outer periphery for mounting an assembly cap 15.
• An axially acting spring washer 18 is mounted in an annular groove 19 formed by a reduction in thickness that the plate 8 has at its inner periphery.
• This washer 18 is supported on the reaction plate 8 and on one end of the driver 3 for action on the driver 3 and push it backwards, that is to say in a direction opposite to the plateau 8.
• This washer 18 thus ensures a clearance between the disks 9 of the clutch in the rest position.
• the trainer 3 further comprises a groove 21 delimited by two transverse walls 22, 23 within which the lower part of a control lever of the starter is intended to be mounted.
• a wall 22 called pusher corresponds to the wall against which the lever is supported to push the driver 3 towards the starter ring.
• the other wall 23 called shooter is a wall against which the lever is supported to move the driver 3 from the starter ring.
• the spring 16 biases the pinion 2 in the direction of the axial stop 17, which corresponds to an initial position of the drive pinion 2.
• control lever of the starter which has a cam shape initially acts on the ring 14 of the housing 1 1 which then moves the pinion carrier 4 axially in the direction of the starter ring. along the drive shaft.
• the driver 3 is in the uncoupled position so that the pinion 2 is free to rotate relative to the driver in both directions of rotation.
• the axial movement continues, the pinion 2 arrives in the vicinity of the starter ring.
• the free pinion 2 rotates slightly into the crown.
• the lever in contact with the pusher 22 axially moves the driver 3 and the shoulder 6 thereof towards the reaction plate 8.
• the spring washer 18 is then compressed and the clearance between the discs is canceled.
• the driver 3 then moves from the uncoupled position to the coupled position for transmitting the torque of the pinion 2 to the starter ring.
• a spring comprising at least two turns mounted in support on the one hand against one face of the pinion carrier and on the other hand against one face of the drive pinion facing one another, this spring being suitable for push the drive sprocket into the initial position
• one of the turns at least partially surrounds the other spring turn when the drive pinion is in the end position.
• the axial size of the spring being reduced in the final position of the drive pinion, it is possible to remove the cavity formed in the pinion so that the guide length of the pinion on the pinion carrier can be increased. This reduces the risk of bracing of the pinion drive relative to the pinion carrier in case of tooth-to-tooth position of the pinion with the starter ring.
• the spring is of frustoconical shape and in that the inner radius of the largest turn in a plane comprising the axis is greater than the inner radius of the next turn in the same plane.
• the first turn which is the largest turn surrounds the second turn being spaced from the first turn. This allows the two largest turns to retain their mechanical properties. Indeed, the turns are not in contact with each other and therefore are not compressed. There is therefore no more or much less deformation of the turns as in the prior art.
• the turns of the spring when the spring is in a compressed state, are spaced from each other.
• spacing is meant that in the same plane including the axis of rotation, each section of turns in this plane is spaced from other sections in this plane. This allows the spring to retain its mechanical properties. Indeed, the turns are not in contact with each other and therefore are not compressed. There is therefore no more or much less deformation of the turns as in the prior art.
• the spring so that the spring retains its mechanical properties when it is in a compressed state, the spring bears against at least a portion of the face of the pinion carrier, the portion of the face of the pinion carrier being inclined relative to a radial orientation plane.
• the face of the pinion carrier against which the spring bears is at least one shoulder of axial orientation.
• the face of the drive gear against which the spring bears is at least one shoulder.
• the face of the drive pinion against which the spring is supported is inclined relative to a radial orientation plane.
• the pinion carrier comprises a sleeve on which the drive pinion slides axially, a transverse plate having the face against which the spring is supported, the transverse plate being derived from an end of the sleeve as well as an annular skirt of axial orientation extending from an outer periphery of the plate.
• the sleeve, the plate and the skirt are made in one piece.
• the spring is of frustoconical shape, a last turn bearing against the face of the pinion carrier and is larger in diameter than a first turn bearing against the face of the drive pinion. This optimizes the return force compared to the axial size of the spring.
• the drive pinion abuts against the pinion carrier when the drive pinion is in the final position. This prevents the spring from being crushed and thus deformed during use.
• the invention also relates to a starter starter for a motor vehicle provided with a pinion carrier assembly according to the invention further comprising a friction clutch interposed between the pinion carrier and a driver.
• the friction clutch comprises a pressure member formed by a shoulder belonging to the driver, a reaction member formed by a plate of the pinion carrier, and a set of friction discs positioned between the element of pressure and the reaction element.
• the pinion carrier comprises a groove in which is positioned an elastic means adapted to exert a force separating the driver relative to the pinion carrier.
• the resilient means is a spring washer having a cylindrical helical shape, this washer being provided with corrugated profile turns.
• a retaining washer is positioned between one end of the driver and the elastic means, the retaining washer being rotatably connected with the pinion carrier.
• the invention further relates to a starter for a motor vehicle comprising a launcher according to the invention.
• the launcher is axially movable on a drive shaft between a rest position in which the drive pinion is disengaged from a starting ring of a heat engine to an active position in which the pinion of drive engages said starter ring, said starter having a control lever with a cam configured to act initially on the pinion carrier to move the drive gear towards the starter ring and in a second time on the trainer to ensure a closure of the friction clutch when the launcher moves from the rest position to the active position.
• Figure 1 already described, shows a perspective view of a friction launcher according to the state of the art
• FIG. 2 shows a longitudinal sectional view of a thermal engine starter according to the invention in the rest position
• Figures 3a and 3b show longitudinal sectional views of the friction launcher according to the invention provided with a drive pinion respectively in the initial position and in the end position;
• Figure 4a shows a longitudinal sectional view of the starter gear carrier of Figures 3a and 3b
• Figures 4b and 4c are perspective representations of the starter gear carrier of Figures 3a and 3b according to different viewing angles;
• Figure 5 shows a sectional view of the drive gear belonging to the launcher of Figures 3a and 3b;
• Figures 6a and 6b are respectively side and top views of the frustoconical spring used with the launcher of Figures 3a and 3b;
• Figures 7a and 7b show respectively perspective and side views of a spring washer used with the launcher of Figures 3a and 3b.
• the starter 30 comprises a friction launcher 31 provided with a driving pinion 32 described in more detail below, mounted movably in translation on a drive shaft 33.
• the launcher 31 can move from a rest position (that of Figure 2) in which the drive pinion 32 is disengaged from a starting ring of a heat engine to an active position (not shown) in which the drive pinion 32 engages with a starter ring 35, and vice versa.
• the starter 30 comprises an electric motor 37 composed of a stator 38 and a rotor 39 mounted coaxially.
• the stator 38 surrounds the rotor 39, which is mounted on a shaft 42 of axis X said rotor shaft inside a yoke 43. The latter is secured to a support 45 of the starter to be fixed on a fixed part of the motor vehicle.
• the stator 38 comprises for example an inductor winding having two pairs of windings, which are each wound around a pole mass integral with the yoke. The axis of each winding is radial with respect to the X axis of the rotor.
• the stator 38 comprises a plurality of permanent magnets.
• the rotor 39 mounted on the rotor shaft 42 comprises a bundle of plates provided with grooves for mounting electrical conductors in the form of pins. These conductors are interconnected to form a rotor winding in connection with conductive blades belonging to a collector 48 integral with the rotor shaft 42 cooperating with brushes 49a, 49b described below.
• the X axis of the rotor shaft 42 coincides with the axis of the drive shaft 33.
• the drive shaft 33 has its front end rotatably mounted in a bearing, said front bearing 50, via a bearing 51.
• the rotor shaft 42 has its rear end mounted in a bearing 52 of a bearing 53 at the rear of the starter, called the rear bearing, and which is secured to a brush holder 54.
• a front-to-back orientation corresponds to a left-to-right orientation in FIGS. 2, 3a, 3b and 4a.
• a front face of an organ is the face facing towards the front bearing 50 and the rear face is the face looking towards the rear bearing 53.
• the starter 30 further comprises a reduction system 58 mounted between the rotor shaft 42 and the drive shaft 33, one end of which is connected to the rotor shaft 42 and the other end is connected to the shaft 33.
• the reducing system 58 is in this case an epicyclic gear comprising a cylindrical ring gear 59 immobilized in rotation toothed internally.
• the teeth of the ring gear 59 mesh with planet wheels mounted to rotate about axes carried by a transverse plate 60 integral with the rear end of the drive shaft 33.
• the sun gear 61 is connected to the front end of The rotor shaft 42.
• transverse an orientation inclined by a few degrees with respect to a plane orthogonal vis-à-vis the X or X 'axis.
• the reducing system 58 may be any other type of reducer.
• the reduction system 58 could comprise two gears, one of which is secured to the rotor shaft 42 and the other of the drive shaft 33.
• the two axes of the rotor shaft 42 and the drive shaft 33 are offset parallel to each other relative to the other.
• the reduction system 58 may be geared left or gear concurrent.
• the starter 30 further comprises a system for moving the launcher 31 from its rest position to its active position and vice versa.
• This displacement system comprises an electromagnetic contactor 64 extending parallel to the electric motor 37 being implanted radially above it and a control lever 65 in the form of a fork.
• the brush group 49a and 49b is provided for the power supply of the rotor winding 39. At least one of the brushes 49b is electrically connected to the ground of the starter, for example the support 45, and at least one other of the brushes 49a is electrically connected to an electrical terminal 66a of the contactor, for example via a wire. The brushes 49a and 49b rub against the blades of the collector 48 when the rotor 39 is rotating.
• the starter 30 may comprise a plurality of brushes.
• the contactor 64 comprises, in addition to the terminal 66a connected to the brush, a terminal 66b intended to be connected via an electrical connection element to a positive power supply V + of the vehicle, in particular a battery, not shown.
• a normally open contact (not shown), located between a terminal V + of the power supply and the terminal 66b controls the power supply of the contactor 64 to start the electric motor.
• the contactor 64 comprises a movable contact plate 69 for electrically connecting the terminals 66a and 66b in order to supply the electric motor 37.
• the contactor 64 is also able to actuate the control lever 65 to move the launcher 31 along the X axis of the drive shaft 33 from the rest position to the active position and vice versa.
• the switch 64 also comprises a movable core 71, a fixed core 72, a fixed coil 73, a control rod 74 and a movable rod 75.
• the control rod 74 passes through the fixed core 72 which serves as a guide.
• This control rod 74 has its front end bearing on the fixed core 72 and its rear end attached to the contact plate 69.
• the control rod 74 is subjected to the action of a compressed contact spring (not referenced) between a shoulder of the control rod 74 and the plate contact 69 to ensure electrical contact of the contact plate 69 with the terminals 66a and 66b when the movable core 71 is in a so-called magnetized position.
• the movable rod 75 is fixed at its front end to the control lever 65. When the coil 73 is energized, the movable core 71 is attracted to the fixed core 72 until it is in a magnetized position.
• the movable rod 75 is further subjected to a tooth against tooth spring 78 housed inside the movable core 71 and surrounding the movable rod 75.
• This tooth against tooth spring 78 bears on a front shoulder of the movable rod 75 and a rear shoulder of the movable core 71.
• This spring tooth against tooth 78 is compressed when the contact plate 69 moves towards the terminals 66a and 66b and the control lever 65 can not advance the pinion 32.
• the lever 65 can not advance when the pinion 32 is blocked in translation along the axis X in the direction of the ring 35 by one or more teeth of the ring 35.
• tooth against tooth position This blocked state is called "tooth against tooth position".
• the compression of the tooth against tooth spring 78 absorbs shocks while applying a force on the control lever 65 transmitted to the pinion 32 to the active position.
• the contactor 64 further comprises a return spring 80, bearing on the fixed coil 73 and the movable core 71 to urge it forward to its rest position and simultaneously move the control lever 65 until that the pinion 32 is in the rest position.
• the friction launcher 31 comprises the driving pinion 32 slidably mounted on a pinion carrier 83, a driver 81 actuated by the control lever 65, and a friction clutch 82 interposed axially between the driver 81 and the pinion 32.
• the axes of the pinion carrier 83 and the driver 81 are merged into an axis X 'corresponding to the axis of the launcher 31.
• the launcher is mounted on the starter, the X 'axis of the pinion carrier 83 is coincident with the X axis of the rotor shaft 42 and the drive shaft 33.
• the driver 81 is internally endowed helical grooves 84 in complementary engagement with external helical gears 85 carried by drive shaft 33 (see Fig. 2).
• the launcher 31 is thus animated by a helical movement when it is moved by the lever 65 against the stop 88 to come, through the pinion 32, engaged with the ring 35 in the active position.
• the pinion carrier 83 comprises a sleeve 100 of axial orientation having a bore 101 for its mounting on the drive shaft 33.
• the sleeve 100 thus makes it possible to axially guide the pinion 32 on a smooth section of the drive shaft 33.
• splines 139 formed in the outer periphery of the sleeve 100 clearly visible in Figures 4b and 4c cooperate with complementary grooves 140 formed in the inner periphery of the pinion 32 clearly visible on the Figure 5.
• the grooves 139, 140 are here of axial orientation.
• This assembly creates a connection in rotation between the pinion 32 and the sleeve 100.
• At least one pad 102 is preferably interposed between the smooth portion of the drive shaft 33 and the sleeve 100. In this case, two pad 102, as shown in Figures 3a and 3b.
• the pinion carrier 83 also comprises a plate 91 of transverse orientation located in the extension of a rear end of the sleeve 100.
• This plate 91 is itself extended at its outer periphery by an annular skirt 105 of axial orientation.
• This skirt 105 is directed rearward towards the coach 81.
• the sleeve 100, the plate 91 and the skirt 105 are made in one piece.
• the plate 91 and the skirt 105 are inserts which are assembled with the sleeve 100.
• a spring 141 in this case a frustoconical helical shaped spring, has a first turn bearing against a transverse rear face 322 of the pinion 32.
• This face of the pinion 32 comprises an axially oriented shoulder 321 situated at the level of the internal periphery of said pinion for centering the spring 141 on the drive gear 32.
• This annular shoulder 321 extends continuously over the corresponding circumference of the rear face 322 of the pinion.
• this shoulder 321 could be formed of several parts annular circumferences for example three parts regularly spaced from each other by 120 degrees or two diametrically opposite parts.
• the last turn of the spring 141 having a larger diameter than the first turn bears on the transverse front face 912 of the plate 91.
• the inner radius of the largest turn (the last turn) in a plane including the axis is larger than the inner radius of the next turn in the same plane.
• the first turn which is the largest turn surrounds the second turn being spaced from the first turn. This allows the two largest turns to retain their mechanical properties. Indeed, the turns are not in contact with each other and therefore are not compressed. There is therefore no more or much less deformation of the turns as in the prior art.
• the turns of the spring are spaced from each other.
• spacing is meant that in the same plane including the axis of rotation, each section of turns in this plane is spaced from other sections in this plane. This allows the spring to retain its mechanical properties. Indeed, the turns are not in contact with each other and therefore are not compressed. There is therefore no more or much less deformation of the turns as in the prior art.
• this front face 912 has at least one portion inclined at an angle A in a direction opposite to the drive pinion 32.
• This inclination is a few degrees with respect to a plane P of FIG. radial orientation vis-à-vis the X 'axis of the pinion carrier 83.
• Such inclination of the face 912 allows the spring 141 to maintain its mechanical properties when in a compressed state.
• the face 322 of the pinion 32 has a corresponding inclination towards the pinion carrier 83 of an angle B (see Figure 5) so that the two faces of the plate 91 and the pinion 32 facing one of the other define a substantially frustoconical space in which the spring can be housed 141 in the compressed position.
• the rear face of pinion 32 could be devoid of inclination and extend parallel to the front radial face of pinion 32.
• the front face 912 of the plate 91 has a shoulder 91 1 of axial orientation for the radial retention of the spring 141 when the latter is subjected to a centrifugal force.
• This shoulder 91 1 is located at the outer periphery of the plate 91.
• this shoulder 91 1 of annular shape extends continuously over the corresponding circumference of the front face of the plate 91.
• this shoulder 91 1 could be formed of several annular circumferential parts, for example three parts regularly spaced from each other by 120 degrees or two diametrically opposite parts.
• the inclined portion of the front face 912 extends between a radially oriented portion located at the inner periphery of the plate 91 and the shoulder 91 1. This inclined portion of the plate 91 extends over a distance corresponding to a radial distance between the first and the last turn of the spring 141.
• the directions of the inclinations of the faces 912 and 322 could be in the other direction, the mounting of the spring 141 then being reversed.
• the pinion carrier 83 comprises an axial stop 142 formed in this case by a circlip mounted in a groove 143 machined in the front end of the sleeve 100 (see Figure 4a).
• the spring 141 biases the pinion 32 in the direction of the axial stop 142, which corresponds to a position, called the initial position of the drive pinion shown in FIG. 3a.
• the spring 141 is compressed and the pinion 32 moves back towards the reaction plate 91 in a position called final position shown in Figure 3b.
• the pinion 32 abuts against the pinion carrier 83 when the pinion 32 is in the final position. This prevents the spring 141 is crushed and thus deformed during use. In this case, the pinion 32 abuts against the transverse plate 91 of the pinion carrier 83 via the shoulder 321.
• the turns of the spring 141 have a configuration such that a given turn at least partially surrounds an adjacent turn when the drive pinion 32 is in the final position, as can be seen in FIG. 3b.
• a turn is a turn of the spring following a spiral path.
• the fact that a turn, so-called surrounding turn, partially surrounds an adjacent turn, called the circled turn, is due to the fact that the diameter of the surrounding turn extending over a given turn of the spring is in every point greater than the diameter. of the surrounded turn extending on the next turn of the spring 141.
• the orthogonal projection of the surrounding turn on the axis X ' is superimposed at least partially with the corresponding orthogonal projection of the adjacent enclosed turn on the axis X' when the drive pinion 32 is in the final position.
• the frustoconical spring 141 shown in Figures 6a and 6b has three turns but could alternatively have a different number of turns in any case at least equal to two turns.
• the spring 141 has a smaller diameter D1, said internal diameter of the order of 20 mm and a larger diameter D2, called external diameter, of the order of 40mm and a height D3 of the order of 15mm when the spring is at the uncompressed free state.
• the angles of inclination A and B respectively of the face of the pinion carrier 83 and the face of the pinion 32 are of the order of ten degrees.
• the spring 141 could have an axial helical portion formed by turns which do not overlap radially with respect to each other in a compressed state and a portion comprising at least two turns capable of radially overlapping one another. relative to each other so that one of the two turns at least partially surrounds the other turn in a compressed state of the spring 141.
• the friction clutch 82 comprises a reaction member constituted by the plate 91 of the pinion carrier 83, a pressure element 92 constituted by a shoulder of the driver 81, as well as friction disks 93, 94 situated between the pressure element 92 and the reaction plate 91.
• the driver 81 is movable in translation relative to the reaction plate 91 in the limit of an axial play. Thus, the driver 81 can move from an uncoupled position in which the driver 81 and the pinion 32 are uncoupled in rotation to a coupled position in which the pinion 32 and the driver 81 are coupled in rotation with each other. at least in the direction of starting rotation at pinion 32, and vice versa.
• the disks 93, 94 are housed in a housing 108 delimited by the reaction plate 91 connected to the pinion, the annular skirt 105 of axial orientation connected to the outer periphery of the reaction plate, as well as by a closure ring 106. elsewhere, the ring 106 is annularly hollowed at its outer periphery for mounting an assembly cap 151 of the ring to the pinion carrier 83.
• the shoulder 92 is implanted inside the housing 108.
• the disks 93 and 94 are alternately rotatably connected to the drive pinion 32 and to the driver 81.
• first disks 93 called internal disks
• first disks 93 have at their inner periphery a plurality of lugs inserted inside corresponding notches 109 located in the outer periphery of the driver 81.
• These notches 109 are for example grooves whose depth extends radially in an outer wall of the driver 81 and whose length extends along the axis X '.
• Second disks 94 called external disks, comprise at their outer periphery a a plurality of lugs inserted inside corresponding notches 1 10 located in the inner periphery of the annular skirt 105. These notches 1 10 clearly visible in FIGS.
• 4a and 4b are, for example, grooves whose depth extends radially in the annular skirt 105 and whose length extends along the axis X '.
• the internal disks 93 are thus linked in rotation with the driver 81 and the external disks 94 are connected in rotation with the drive pinion 32 via the annular skirt 105.
• the disks 93, 94 can slide along the axis X 'by through the notches 109, 1 10 and their corresponding legs.
• the discs 93, 94 for example made of a friction material, such as bronze and steel, for transmitting frictional torque between the driver 81 and the pinion 32.
• the number of internal disks 93 is two and the number of external disks 94 is three.
• this number of disks 93, 94 is likely to vary according to the intended application and the torque to be transmitted. It will thus be possible to increase the number of disks 93, 94 in order to transmit more torque without having to increase the diameter of the driver 81.
• the launcher 31 also has a resilient means 1 exerting a force away from the driver 81 of the reaction plate 91 towards the disengaged position.
• the elastic means 1 15 is mounted in compression between a radial face of the reaction plate 91 and an end of the driver 81.
• the elastic means 1 15 is positioned inside a groove 1 17 closed by a washer 1 18, said retaining washer, connected in rotation with the reaction plate 91.
• the groove 1 17 is formed by a circular groove around the axis X '.
• the groove 1 17 thus corresponds to a reduction in thickness at the inner periphery of the reaction plate 91.
• the groove 1 17 is open axially on the rear side and radially closed by two annular walls 120, 121 of axial orientation, an inner annular wall 120 which is closest to the axis X 'and an outer annular wall 121 which is the further from the X 'axis.
• the inner annular wall 120 corresponds to the axial extension of the sleeve 100 rearwardly beyond the reaction plate 91.
• the groove 1 17 comprises at its outer periphery a set of three notches 124 spaced angularly in a regular manner for receiving three lugs 130 of corresponding shape located at the outer periphery of the retaining washer 1 18.
• the retaining washer 1 18 closes the open axial end of the groove 1 17 inside which is positioned the elastic means 1 15.
• This washer 1 18 has the form of a flat annular plate of radial orientation having a internal diameter substantially equal to the internal diameter of the groove 1 17 and an outer diameter substantially equal to the outer diameter of the groove 17.
• the retaining washer 1 18 comprises at its outer periphery a set of three lugs 130 spaced angularly from in a regular manner intended to cooperate with the three notches 124 of corresponding shape located at the outer periphery of the groove 1 17.
• the retaining washer 1 18 is connected in rotation with the reaction plate 91 and is movable in translation relative to this plate 91 to the extent that the lugs 130 of the retaining washer 1 18 can slide inside the notches 124 corresponding formed in the tray of reaction 91.
• the number of lugs 130 and notches 124 depends on the application and may be greater than or less than three. In all cases, this number is at least one.
• the elastic means 1 15 is in this case a spring washer positioned inside the groove 1 17. As shown in Figures 7a and 7b, the washer 1 15 has a cylindrical helical shape. This washer is provided with corrugated turns. The spring washer 1 15 is mounted compressed between the bottom 1 19 of the groove 1 17 and the retaining washer 1 18 bears on the end of the driver 81 to separate the driver 81 from the reaction plate 91. The spring washer 1 15 is thus preserved from wear by the retaining washer 1 18 which closes the groove 1 17. The walls of the groove 1 17 and the retaining washer 1 18 thus form a protective casing of the spring washer 1 15.
• the spring washer 1 15 has a free height D4 of the order of 5mm, an internal diameter D5 of the order of 17mm and an outer diameter of about 25mm.
• the driver 81 further comprises a groove 135 delimited by two walls 136, 137 of transverse orientation within which the lower portion of the control lever 65 is intended to be mounted.
• the section of the groove 135 is generally U-shaped.
• the wall 136 called the pusher is the wall against which the lever 65 bears to push the driver 81 towards the crown 35.
• the other wall 137 called the shooter is the wall against which the lever 65 is supported to move the driver 81 away from the crown 35.
• the groove 135 can be obtained by making a groove at the outer periphery of the driver 81 or can be formed from an annular piece, generally U-shaped section, attached to the outer periphery of the driver 81 as shown in Figures 3a and 3b.
• the lever 65 is configured to push the pinion carrier 83 firstly through the ring 106 and in a second step the driver 81 through the pusher 136.
• the lever of control 65 comprises for example a cam positioned between the pusher 136 and the shooter 137. Reference is made to document FR2978500 for more details concerning such a control lever.
• the disks 93, 94 are not tightened so that there is an axial clearance distributed between the pressure element 92, the internal disks 93 and external 94 and the reaction plate 91.
• the movable core 71 is attracted to the fixed core 72 until it is in a magnetized position. Its displacement simultaneously drives the movable rod 75, the movable contact 69 and the control rod 74 towards the rear.
• the lever 65 moved by the movable rod 75 then acts initially on the ring 106 of the housing 108 which then moves the pinion carrier 83 and the pinion 32 axially in the direction of the ring 35 along the shaft 33.
• the driver 81 is in the uncoupled position so that the pinion 32 is free to rotate in both directions of rotation relative to the driver 81.
• the axial movement continues, the pinion 32 arrives in the vicinity of the ring 35.
• the pinion 32 free in rotation penetrates slightly into the crown 35.
• the control lever 65 comes into contact with the pusher 136 so as to axially move the driver 81 and the shoulder 92.
• the movable core 71 being in abutment against the fixed core 72, the movable contact 69 makes contact between the two terminals for supplying the electric motor.
• the electric motor 37 With the electric motor 37 energized, the rotation of the drive shaft 33 drives the driver 81 to the coupled position through the helical splines 84, 85.
• the forward end of the driver 81 moves to the tray 91 so that the spring washer 1 15 is compressed and the clearance between the disks 93, 94 is canceled.
• the clutch 82 is then locked for transmission of the torque of the pinion 32 to the crown 35.
• the control lever 65 continues to move the driver to put in place.
• the displacement is made possible by the compression of the spring 141 when the pinion 83 is moved relative to the pinion carrier 83 in the final position of Figure 3a.
• the tooth against tooth spring 78 located between the movable rod 75 and the bottom of the movable core 71 may also be compressed to absorb shock while applying a force on the lever 65 transmitted to the pinion 32 to the active position.
• the friction clutch 82 is released because the driver 81 makes an axial backward movement due to the helical connection between the 81 and the shaft 33.
• the coach 81 unscrews to move from the coupled position to the uncoupled position.
• This action is amplified by the spring washer 1 15 which relaxes and pushes the driver 81 backwards via the retaining washer 1 18 resting on the end of the driver 81 which slides inside the groove 1 17.
• the return spring 80 acts to bring the movable core 71 and the control lever 65 to their rest position shown in Figure 2. The lever 65 thus moves the thrower 31 backwards by pushing on the shooter 137.
• the spring washer 1 15 is protected by the retaining washer 1 18. Indeed, it is the washer of holding 1 18 linked in rotation with the reaction plate 91 which rubs against the end of the driver 81.
• the friction clutch 82 comprises only a pressure element 92 and a reaction element 91 having two frustoconical surfaces of complementary shape in contact with each other.
• a starting torque can be transmitted to the crown when a bearing force allowing the coupling in rotation of these two surfaces will be applied by a displacement of the driver 81.
• the clutch 82 is devoid of intermediate friction elements located between the pressure element 92 and the reaction element 91.
• the spring 141 may also be used with a starter provided with a freewheel in place of the friction clutch 82 in the case where the drive pinion is distinct from the pinion carrier. Such a configuration essentially minimizes shocks and noises.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Operated Clutches (AREA)
• Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

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• 2013
  • 2013-04-08 FR FR1353115A patent/FR3004222B1/fr active Active
• 2014
  • 2014-04-08 CN CN201490000540.3U patent/CN205297814U/zh not_active Expired - Lifetime
  • 2014-04-08 EP EP14723097.3A patent/EP2984330A1/de not_active Withdrawn
  • 2014-04-08 WO PCT/FR2014/050835 patent/WO2014167236A1/fr active Application Filing

Non-Patent Citations (1)

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