WO2013014385A2 - Ensemble mobile lanceur - levier de commande pour engrenement avec une couronne de demarrage d'un moteur thermique et demarreur d'un moteur thermique comportant un tel ensemble - Google Patents
Ensemble mobile lanceur - levier de commande pour engrenement avec une couronne de demarrage d'un moteur thermique et demarreur d'un moteur thermique comportant un tel ensemble Download PDFInfo
- Publication number
- WO2013014385A2 WO2013014385A2 PCT/FR2012/051746 FR2012051746W WO2013014385A2 WO 2013014385 A2 WO2013014385 A2 WO 2013014385A2 FR 2012051746 W FR2012051746 W FR 2012051746W WO 2013014385 A2 WO2013014385 A2 WO 2013014385A2
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- WO
- WIPO (PCT)
- Prior art keywords
- assembly according
- lever
- reaction plate
- starter
- control lever
- Prior art date
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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
- F02N15/08—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing being of 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
- F02N15/022—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
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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
- F02N15/04—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
-
- 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
-
- 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
- F02N11/08—Circuits or control means specially adapted for starting of engines
- F02N11/0851—Circuits or control means specially adapted for starting of engines characterised by means for controlling the engagement or disengagement between engine and starter, e.g. meshing of pinion and engine gear
-
- 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
- F02N11/08—Circuits or control means specially adapted for starting of engines
- F02N11/0851—Circuits or control means specially adapted for starting of engines characterised by means for controlling the engagement or disengagement between engine and starter, e.g. meshing of pinion and engine gear
- F02N11/0855—Circuits or control means specially adapted for starting of engines characterised by means for controlling the engagement or disengagement between engine and starter, e.g. meshing of pinion and engine gear during engine shutdown or after engine stop before start command, e.g. pre-engagement of pinion
Definitions
- Mobile assembly launcher - control lever for meshing with a starter ring of a heat engine and starter of a heat engine comprising such a set
- the present invention relates to a mobile launcher - control lever for meshing with a ring gear for starting a heat engine, especially a motor vehicle.
- the present invention also relates to a starter and a thermal engine, including a motor vehicle, comprising such an assembly.
- a starter and a thermal engine including a motor vehicle, comprising such an assembly.
- a conventional thermal engine starter 4 in particular of a motor vehicle, comprises:
- a launcher 1 slidably mounted on the output shaft 24;
- a control lever 20 forming a movable assembly with the launcher 1 and configured to control the movement of the launcher 1 and meshing thereof with a starting ring gear C of the engine;
- an electric motor M housed in the casing 1 8 and provided with a drive shaft 26 of the launcher 1;
- the operating means may include a movable core 2b configured to act on the control lever 20 and rotate it to move the launcher 1 (See Figure 1).
- This mobile core 2b may belong to an electromagnetic contactor 2 provided with a body 2d carried by the housing 1 8 and provided with a movable control rod 3 -contact mobile 3a; this mobile core 2b being configured to act on the moving element and move the latter rearward towards fixed electrical contact terminal heads 3 e, 3 f to electrically power the electric motor M.
- the starter ring C may consist of a ring gear externally ( Figure 1) and integral with a plate connected rigidly or resiliently to the crankshaft of the engine as in FR 2 63 1 094 and GB 225 757.
- the starter ring C may consist of a internally toothed crown and secured to a pulley belonging to a belt movement transmission intervening between this pulley and a pulley secured to the crankshaft as described in the document FR 2 858 366.
- the output shaft 24 of the starter 4 may be confused with the drive shaft 26 of the electric motor M as described for example in GB 225 757, or be distinct from this shaft 26; at least one speed reducer 34 being interposed between the shafts 24, 26 as described in the documents FR 2 63 1 094 and FR 2 858 366.
- the speed reducers 34 make it possible to use a faster electric motor and to obtain a higher starting torque, while reducing the size and weight of the starter for a given power.
- These reducers 34 are most often gear reducers, either planetary gear, in which case the shafts 24, 26 are coaxial (see FIG. 1), either with internal gearing as described in the document FR 2 63 1 094, in which case the shafts 24, 26 are offset radially relative to one another.
- the housing 18, here metallic, comprises a front bearing configured for rotational mounting of the front end of the output shaft 24 and fixing the starter on a fixed part of the vehicle connected to the ground thereof, a rear bearing configured for rotational mounting of the rear end of the drive shaft 26 and a cylindrical intermediate yoke sandwiched between the bearings.
- the front bearing of FIG. 1 comprises an opening in its lower part for the passage of the starter ring C intended to be rotated by the launcher 1 when the electric motor M is electrically powered.
- the upper part of the front bearing carries the body 2d of the contactor 2 implanted here above the electric motor M provided with an inductor stator 30 surrounding an induced rotor 14 integral with the drive shaft 26 and having at the rear a collector (not referenced) with electrically conductive blades for friction of at least one pair of brushes (not referenced).
- the collector is here of the frontal type and the brushes are axially oriented with respect to the X axis of the shafts 24, 26.
- the collector may alternatively be oriented axially and the brushes radially oriented with respect to the X axis as in document FR 2 858 366.
- the cylinder head of the housing 1 8 internally carries the stator 30 comprising permanent magnets or alternatively an induction coil for example of the type described in EP 0 749 194.
- the rotor 14 comprises a body in the form of a sheet metal packet provided with slots for mounting a winding, the ends of which are connected to the conductive blades of the collector.
- One of the brushes is connected to ground and the other to the positive terminal of the vehicle battery as described below.
- several pairs of brushes are provided.
- the drive shaft 26 has here at the front the sun gear of the reducer 34 extended by a smooth portion engaged in a blind hole of the rear end of the output shaft 24 with the interposition of a sliding bearing and presence an axial locking ball.
- the planet carrier of the gearbox 34 is secured here by crimping the rear end of the output shaft 24, while the ring gear of the gearbox 34, made of rigid plastic material, is secured by overmolding a metal plate 55, so-called base plate.
- the control lever 20, advantageously made of plastic material for reducing noise, is pivotally mounted at an intermediate point on a rigid plastic support overmolded on the plate 55. This plate 55 serves to support the body 2d of the contactor 2.
- This 2d body is fitted into a circular hole in the upper part of the plate 55 interposed between the front bearing and the cylinder head of the housing 18.
- the fixing of the plate 55, the contactor 2 and the cylinder head to the front bearing housing 1 8 is performed here with the help of screw 56.
- screw 56 See document FR 2 725 758.
- the speed reducer 34 may be of the type described in FIGS. 2 to 5 of document FR 2 787 833. This reducer may have another shape and notably include a torque limiter as in document FR 2 63 1 094. .
- the contactor 2 is provided with ferromagnetic material parts namely the movable core 2b, a fixed core 2f and the body 2d, in which is arranged at least one coil 2a mounted on an insulating annular support 2c.
- the body 2d is closed at the rear by a second cover of electrically insulating material fixed here by crimping on the body 2d.
- This cover 2e also serves to fix the fixed core 2f, axially wedged between a shoulder of the 2nd cap and the body 2d.
- the cap 2e is provided with axial projections engaging in notches in the fixed core 2f for rotation locking and angular indexing of the cap 2e.
- the support 2c is engaged on a ring span (not referenced) of the fixed core 2f.
- This support 2c and the front end of the body 2d are centrally provided with a passage for the mobile core 2b.
- This coil 2a when it is activated electrically following for example the actuation of the ignition key, creates a magnetic field which controls the axial displacement of the movable core 2b in the direction of the fixed core 2f.
- the control rod 3 of the mobile assembly 3-3 a is here electrically insulating and stepped diameter, while the movable contact 3a is electrically conductive and may be in the form of a rectangular plate, for example copper, mounted sliding on the rod 3 through which to do a central opening of the contact 3a.
- the rod 3 may be electrically conductive, an electrically insulating sleeve being interposed between the rod 3 and the edge of the central opening of the contact 3 a.
- This contact 3a is intended to come into contact with the heads of the fixed electrical contact terminals 3 e, 3 f, arranged in a contact chamber formed in the cover 2e.
- the terminals are integral with the bottom of the 2nd cover.
- the terminal 3 e is intended to be connected to the positive terminal of the vehicle battery, while the terminal 3 f is connected by a cable to one of the brushes of the pair of brushes.
- the XI axis of the rod 3 coincides with the axis of the cores 2b, 2f. This axis XI constitutes the axis of the contactor 2, which is parallel to the axis X of the shafts 24, 26.
- the front end of the movable core 2b is connected to the upper end of the lever 20, which acts by its lower fork-shaped end on the launcher 1 and forms with it a moving assembly.
- the movable core 2b is blind for housing therein a connecting rod 5a to the lever 20.
- This rod 5 passes through the bottom of the core 2b and is configured to receive at its front end an upper hinge axis for mounting pivoting of the upper end of the lever 20 comprising here an intermediate axis of articulation on the plastic support overmolded on the plate 55.
- a spring 5, said spring tooth against tooth, here helical, is mounted in the movable core 2b around the rod 5a.
- This spring 5 is supported on the bottom of this core 2b and on the shouldered head of the rod 5.
- This head is locked in translation by a washer (not referenced) intended, after catching an axial j had, to act on the front end of the control rod 3 by pushing through a central hole of the fixed core 2f in which the front portion of the rod 3 is slidably mounted.
- the rod 3 carries at its rear end the contact 3 slidably mounted on the rod 3 against the force exerted by two axial-acting springs, here helical, namely a contact pressure spring 6b and a holding spring 6a disposed on either side of the contact 3a.
- the pressure spring 6b is mounted on an intermediate portion of the rod 3 of diameter greater than that of the front and rear ends of this rod 3 and this between a shoulder thereof housed in the fixed core 2d and the front face of the contact mobile 3 a.
- This spring 6b urges the rear face of the contact 3a towards a shoulder integral with the rod 3 in the form of a washer held in place by a Belleville washer (not referenced) with internal tabs engaged with the rear end 3.
- the retaining spring 6a is supported on the bottom of the bonnet 2e and on the Belleville washer. This spring 6a is mounted on the rear end of the rod 3 and is provided to maintain the movable contact 3a resting on the rear end of the fixed core 2f when the moving contact 3 year 'is not in contact with the terminal heads 3e, 3 f; the winding 2a is not then electrically powered.
- the contactor 2 comprises a return spring 6c, here helical, mounted around the front end of the movable core 2b and implanted between the front end of the cover 2d and a metal stop fixed on the front end of the movable core 2b for recall the movable core 2b and therefore the pivoting lever 20 to their retracted rest position ( Figure 1) when the coil 2a is not electrically powered. In this rest position, the rod 3 is at a distance from the mobile core 2b.
- a return spring 6c here helical
- the holding spring 6a also called breaking spring, has a stiffness lower than that of the contact pressure spring 6b.
- the coil (s) 2a when energized, create a magnetic field, which allows the axially backward drive of the mobile core 2b towards the fixed core 2f.
- the mobile core 2b after catching the axial clearance between the front end of the rod 3 and the movable core 2b, moves the rod 3 and the movable contact 3a, the latter compressing the holding spring 6a and being brought into contact with the terminal heads 3 e, 3 f for making an electrical contact and electrically supplying the electric motor M, which then rotates the output shaft 24 via the drive shaft 26 and the gearbox 34.
- the contact pressure spring 6b makes it possible during a last phase to the mobile core 2b to continue its movement to come into contact with the fixed core 2f and the rod 3 to move relative to the contact 3a.
- the contact 3 has finally occupies a retracted active position.
- the displacement of the movable core 2b also causes the control lever 20 to move at its upper end and pivot it at its intermediate axis of articulation on the support integral with the plate 55.
- the lower end of the lever 20 then axially moves the driver, which the launcher 1 comprises, forwardly along the output shaft 24 of the starter 4 towards a stop 25 secured to the front end of the starter.
- the output shaft 24 rotatably mounted in the front bearing here via a plain bearing.
- metal cladding means can be permanently attached to the control lever at the friction zones with the coach as described in the document FR 2 862 721 to which we refer. report to.
- the coil 2a is de-energized, the movable core 2b is no longer driven backwards, the pressure spring 6b expands and the holding spring 6a pushes the control rod 3 forward until the movable contact 3a is in abutment with the fixed core 2f.
- the return spring 6c is also used to bring the movable core 2b and the lever 20 back to their retracted rest position, which can be seen in FIG.
- the contact 3a is therefore slidably mounted on the rod 3 between an advanced rest position and an active retracted position.
- the lever 20 is pivotally mounted on the rod 5a and on the support secured to the plate 55 to axially move the launcher 1 between a retracted rest position and an active forward position defined by the abutment 25.
- the switch 2 thus has two functions, namely moving the moving element 3 - 3 a and moving in the opposite direction of the mobile assembly control lever 20 - launcher 1.
- the launcher 1 has at the front a pinion 1 1 and back the coach 1 1 8 provided with a drive bushing traversed by the output shaft 24 of the starter and a receiving groove of the fork - shaped lower end of the lever 20.
- the references 20a and 20b designate respectively the upper hinge axis and the axis of intermediate articulation of the lever 20.
- the axis 20b is received axially in an oblong hole of the support 36 of plastic secured by overmolding the plate 55.
- the reference 1 16 denotes a bearing, here a needle bearing, interposed radially between the outer periphery of the front end of the shaft 24 and the inner periphery of a hollow cylindrical nose that presents the front bearing of the bearing 1 8.
- the bearing 1 16 allows the rotation of the shaft 24, which has at the front a smooth section 22, delimited by the stop 25, and at the rear a section 1 10 of larger diameter.
- This section 1 10 is provided at its outer periphery with helical splines 28 for co-operation with complementary helical splines 29 belonging to the inner periphery of the rear end of the driving sleeve of the driver 1 1 8.
- the splines 29 surround the grooves 28.
- the launcher 1 is thus animated by a movement of rotation and translation along the output shaft 24 when moved by the lower end of the lever 20.
- the driver 118 is axially coupled to the pinion 11 by a freewheel with rollers 126 subjected to the action of springs.
- the freewheel allows the driving sleeve 118 of the driver to drive, when starting the engine, the pinion 11 and the ring C in a direction of rotation corresponding to that of the shaft 26 of the motor M As soon as the rotational speed of the thermal engine exceeds a threshold, the freewheel disengages the rotational drive of the pinion 11 relative to the shaft 26 to preserve the constituents of the starter, in particular the electric motor thereof.
- the teeth of the pinion 11 belong to a sleeve 111 extended at the rear to form, by means of an excess thickness, the cylindrical external track of the freewheel roller 126.
- This sleeve 111 is guided axially on the smooth section 22 by via a bearing 124 interposed radially between the outer periphery of the section 22 and the inner periphery of the sleeve integral with the bearing 124.
- the sleeve of the driver 118 is extended at the front by a flange of transverse orientation relative to to the axis X of the shaft 24. This flange is extended at its outer periphery by a cylindrical skirt of axial orientation extending forwardly.
- This skirt is internally configured to form housing for the rollers 126 and their associated springs. These housings delimit the external track of the rollers 126 and are closed by a washer 130.
- the rollers 126 are trapped axially between the flange of the driver 118 and the washer 130 bearing axially on the free end of the skirt of the coach .
- This washer 130 is held in place by the bottom of a cover 131, here metallic.
- This hood 131 in the form of a cup, envelopes the skirt of the coach 118 and is axially locked by folding of material from its free end to the chamfered outer periphery of the flange of the coach 118.
- the housing groove of the lower fork-shaped end of the lever 20 is delimited by the flange of the driver 118 and a washer integral with the rear end of the sleeve of the driver 118.
- the pinion 11 of the launcher 1 in the retracted position of rest is at a distance from the ring gear C.
- the teeth of the pinion 1 1 buttent on the teeth of the crown C.
- the spring 5 tooth against tooth is compressed and the pinion rotates, especially when starting the electric motor, to mesh with the crown C.
- the tooth against tooth spring 5 may be implanted at the inner end of the control lever as described in document GB 225 757 to which reference will be made, FIGS. 1 to 3 thereof showing the positions of the pinion relative to the ring gear start.
- the freewheel comprises friction discs under pressure via a cup and a locking ring.
- the friction clutch is frustoconical type as in WO 2006/100353 according to the preamble of claim 1.
- the rotation of the crown C can mill the pinion January 1 when it is in position tooth against tooth with the crown C because the launcher because of its configuration and the kinematic chain that goes from the launcher to the electric motor oppose this rotation.
- the starter 4 must therefore, when starting or stopping the heat engine, overcoming, in addition to the internal friction forces of the heat engine, the resistant compressive forces in the cylinders.
- the angular acceleration of the starter is lower than that of the heat engine and the free wheel intervenes to make a disengagement.
- the engine slows down while the the starter continues to accelerate until the freewheel clutch reclocks; the starter again transmitting energy to the heat engine.
- Curve A (number of revolutions per minute of the engine as a function of time) of FIG. 15 illustrates the aforementioned phenomena; the vibration spectrum being different at the end of the engine stop.
- the mobile launcher - control lever assembly is movable between a retracted rest position and an advanced position for meshing with a ring gear for starting a heat engine, of the type comprising:
- a launcher equipped with a meshing gear in advanced position with the starting ring gear and an axis of axial symmetry
- a friction clutch intervening between the driver and the pinion said clutch being provided with a reaction plate, a pressure element integral with the driver and at least one friction element able to be clamped between the reaction plate and the pressure element;
- the pressure element is implanted at least partly inside a housing, on the one hand, integral in rotation with the pinion and on the other hand, comprising a plate constituting the reaction plate of the clutch. friction;
- a pivoting control lever comprising, on the one hand, an upper end adapted to be displaced by maneuvering means belonging to a starter and, on the other hand, a lower end in the form of a fork comprising two arms for action on the launcher;
- control lever is associated with means for closing the friction clutch
- the closing means act in a second phase delayed with respect to the control lever. These closure means are distinct from the lever being mounted to articulation in favor of the means
- the pinion can rotate freely in both directions (clockwise and counterclockwise) to mesh with the start ring still rotating.
- the clutch In the second phase, the clutch is closed to transmit the torque.
- the closing means of the clutch therefore act in a delayed manner.
- a mechanical synchronizer is thus produced, the speed of rotation of the pinion being adapted to that of the starter ring.
- the time between two restarts of the engine can be shortened.
- an internal combustion engine combustion engine starter in particular a motor vehicle, is characterized in that it comprises such a mobile assembly.
- each arm of the lever carries a configured salient pad
- the casing carries externally cam-shaped pads which are each adapted to come into contact with an associated arm of the lower end of the lever for axial displacement of the casing towards the advanced meshing position with the starting ring gear;
- the closing means of the friction clutch are connected to the lever and are configured to act later on the coach and urge it towards the reaction plate for clamping the clutch;
- the friction clutch closing means comprise a friction clutch closing piece, which is hingedly coupled to the lower end of the lever and which is configured to act on the coach and request in the direction of the reaction plate for clamping the clutch;
- the mobile assembly comprises a double lever
- the friction clutch closing means comprise an additional pivoting lever, which is configured to allow a pivotal mounting of the control lever between the upper and lower ends thereof;
- the additional lever comprises an upper end that can be moved by the operating means of the control lever after catching a jute;
- the additional lever carries, between its upper and lower ends, a mounting strut with articulation of the lever of
- control lever is mounted to nest in the lever
- the friction clutch closing means comprise a friction clutch closure piece, which is hingedly coupled to the lower end of the additional lever and is configured to act in a delayed manner on the driver and to engage the latter in the direction of the reaction plate for clamping the clutch;
- the housing comprises a closing ring and a skirt for connecting the reaction plate to the closure ring, each cam-shaped projecting pad being configured to come into contact with the closure ring of the casing;
- the housing comprises a connecting skirt extending axially at the outer periphery of the reaction plate, being directed in the opposite direction to the pinion, each cam-shaped projecting pad being configured to come into contact with the connecting skirt of the housing;
- the housing comprises a connecting skirt, on the one hand, extending
- each cam-shaped protruding pad being configured to engage the relevant arm of the control lever
- the housing comprises a closure ring provided with cam-shaped projecting pads and a skirt for connecting the reaction plate to the closure ring, each cam-shaped projecting pad being configured to come into contact with an arm of interest. control lever;
- the housing comprises a connecting skirt extending axially at the outer periphery of the reaction plate while being directed in the opposite direction to the pinion, each cam-shaped projecting pad being configured to come into contact with the connecting skirt of the housing; each cam-shaped projecting pad has a generally flat top portion able to come into contact with the closure ring or with the connecting skirt of the box or with one of the associated arms of the control lever;
- each arm of the lever comprises a rounded area, each top portion of a pad being extended at its inner periphery by an inclined portion of clearance extending in the direction of a flat portion, which is connected to the rounded area;
- the pads are intended, via their upper portion, to come into contact, that is to say, in support, on the closure ring or on the connecting skirt of the housing in two diametrically opposite zones thereof;
- the closing part of the clutch is hingedly mounted on the lower end in the form of a fork of the control lever between the arms of this lower end;
- the closing part of the clutch is hingedly mounted on the forked lower end of the additional lever between the arms of this lower end;
- the closing part consists of a hinge mounted hinge on the fork-shaped lower end of the additional lever between the arms of the lower end; the hoop comprises at each of its ends an axle each rotatably mounted in a hole of an associated arm which comprises the lower part of the additional lever;
- the arch is semicircular in shape
- the closing part of the clutch is mounted in a groove secured to the coach;
- the closure part consists of a closure washer mounted in a groove secured to the trainer;
- the closure washer is open at its inner periphery for mounting in the groove of the coach;
- the closing washer is closed by being mounted in the integral groove of the driver by a mounting bayonet type
- the opening of the closure washer is oblong to allow a radial displacement of the closure washer relative to the groove;
- the washer has two branches interconnected at least by an outer portion
- the branches are spaced from each other by a distance which corresponds generally to the outer diameter of the bottom of the groove;
- the washer bears in two diametrically opposite zones on one of the sides of the annular groove
- each branch is hingedly mounted on the lower end of an associated arm of the lever;
- one of the associated arm / branch elements carries a pivot penetrating into a hole belonging to the other of the associated arm arm members;
- each branch laterally carries a pivot adapted to penetrate in a complementary manner into a cylindrical hole, which each lever arm has at its lower end.
- each arm of the lever comprises a pivot penetrating in a complementary manner in a hole each belonging to an arm of the washer;
- one of the sides of the annular groove is thicker
- the branches of the closure piece are mounted axially in the groove
- the thickest sidewall of the receiving groove of the closing part of the clutch has a thickness greater than that of the axial junction; an elastic washer axial action is interposed between the reaction plate and the driver to push back the coach to the rest position;
- the spring washer is mounted in an annular groove formed at the inner periphery of the reaction plate;
- the throat is open towards the coach
- the groove is formed by means of a reduction in thickness which the reaction plate has at its inner periphery
- the elastic washer consists of a corrugated washer
- the friction clutch is a frustoconical type friction clutch comprising at least one friction element in the form of a friction lining anchored in a housing of the front part of the driver constituting the pressure element;
- This lining has at its outer periphery a convex frustoconical friction surface cooperating in a complementary manner with a concave frustoconical friction surface formed at the outer periphery of the integral reaction plate at least in rotation of the pinion;
- the friction clutch comprises at least one friction element in the form of a friction disk interposed between a pressure element in the form of a pressure plate integral with the driver and the reaction plate;
- the pressure plate consists of a flange secured to the coach;
- the retaining ring of the housing is hollowed at its inner periphery for forming a shoulder adapted to cooperate with the rear face of the flange;
- the friction clutch comprises two integral friction discs in rotation of a front section of the coach with axial mobility; - The clutch has three friction discs integral in rotation of the reaction plate;
- the three friction discs are integral in rotation of the reaction plate with axial mobility via the skirt of the housing;
- Each disc secured to rotation of the front section of the driver is interposed between two friction discs integral in rotation of the skirt so that there is alternating friction discs;
- the inner diameter of the retaining ring of the housing is greater than the outer diameter of the thickest side of the receiving groove of the closing part of the clutch;
- the inner diameter of the skirt of the housing is greater than the outer diameter of the thickest side of the receiving groove of the closing part of the clutch;
- the gear of the trainer is secured to a sleeve of the reaction plate;
- the pinion is integral in rotation with axial mobility of a sleeve integral with the reaction plate;
- an elastic member is interposed between the reaction plate and the axially movable pinion on a sleeve integral with the reaction plate.
- FIG. 1 is an axial sectional view of a motor vehicle engine starter of the prior art which is illustrated in the rest position;
- FIG. 2 is a view of the front portion of Figure 1 with the rear portion of the launcher cut;
- FIG. 3 is an axial sectional view of the mobile assembly launcher control lever closure washer belonging to means for closing the friction clutch according to a first embodiment of the invention for the retracted rest position of this moving assembly - the launcher pinion then being at a distance from the ring gear -;
- FIG. 4 is a view in axial section of the launcher of FIG.
- Figure 5 is a perspective view of the trainer of Figures 3 and 4;
- FIG. 6 is a perspective view of the control lever of Figure 3 equipped with cams for action on a casing integral in rotation with the starter pinion;
- FIG. 7 is a front view of the control lever equipped with its closing part of the friction clutch
- FIG. 8 is a view similar to Figure 3, without the output shaft of the starter, at the beginning of the engagement of the starter gear in the ring gear start;
- Figure 9 is a view similar to Figure 8 for a position in which the pinion penetrates part into the starter ring with contacting the closing part of the friction clutch with the launcher driver;
- Figure 10 is a partial view similar to Figure 4 in which the friction clutch is closed;
- Figure 1 1 is a view similar to Figures 8 and 9 for an advanced position of the movable assembly in which the pinion penetrates fully into the starter ring; the friction clutch being closed;
- FIG. 12 is a partial sectional view of the launcher for a second embodiment of the invention.
- FIG. 13 is a view similar to Figure 8, the pinion of Figure 12 being in position tooth against tooth relative to the starter ring;
- FIG. 14 is a partial view in axial section of the front of the launcher equipped with needle bearings for sliding along the output shaft of the starter;
- FIG. 15 is a view of the intervention windows of the mobile assembly according to the invention with ordinate the speed of rotation N (number of revolutions per minute) of the heat engine and abscissa time;
- FIG. 16 is a perspective view of a double lever assembly intended to act on the launcher of FIG. 4 for a third embodiment of the invention.
- FIG. 17 is an exploded view of the double lever of FIG. 16.
- a forward-to-back orientation corresponds to a left-to-right orientation in Figures 1, 3 and 4.
- the launcher 1 is mounted instead of the launcher 1 of Figures 1 and 2. It comprises an axis of symmetry coinciding with the axis of symmetry X of the output shaft 24 of the starter.
- This launcher 1 comprises a pinion 11 adapted to mesh with a ring gear C for starting the engine, a driver 118 and a friction clutch 300 acting between the driver 118 and the pinion 11.
- This clutch 300 is configured to constitute a freewheel mechanical connection between the pinion 11 and the driver 118. It comprises for this purpose a pressure element, a reaction plate 112 and at least one friction element 301 interposed between the plate 112 and the pressure element. It is able to come into frictional contact, directly or indirectly, with the reaction plate 112 under the clamping action exerted by the pressure element for transmission of the torque from the shaft 24 to the crown C via the pinion 11.
- the teeth of the pinion 11 and the crown C may be axially oriented relative to the X axis.
- the clutch 300 is engaged (engaged).
- the torque is then transmitted from the shaft 24 to the crown C.
- the pinion 11 is then rotatably connected to the driver 118.
- the clutch 300 In the retracted rest position of the launcher 1 (see FIGS. 3 and 4), the clutch 300 is, according to one characteristic, disengaged (disengaged) so that the pinion 11 can rotate freely.
- the clutch 300 may be a frustoconical type friction clutch as described in document WO 2006/100353 to which reference will be made. It will therefore comprise (see FIGS. 2 to 5 of this document WO 2006/100353) at least one friction element in the form of a friction lining anchored in a housing of the front part of the driver 118 constituting the element of pressure.
- This lining has at its outer periphery a convex frustoconical friction surface cooperating in a complementary manner with a concave frustoconical friction surface formed at the outer periphery of a reaction plate integral at least in rotation with the pinion.
- This reaction plate has at its outer periphery a protuberance for fixing a cover having at its rear end a ring traversed centrally by the driver.
- This cover has an annular skirt fixed on the protuberance of the reaction plate.
- the friction lining is thus housed inside a housing comprising the reaction plate, the ring and the skirt connecting the reaction plate to the ring constituting the closing ring of the housing through which the trainer passes. 118 constituting the pressure element implanted partly in the housing.
- the friction clutch 300 may comprise at least one friction element in the form of a friction disc 301 interposed between a pressure element in the form of a friction plate. pressure 120 secured to the driver 118 and a reaction plate 112.
- the disc 301 is also housed in a housing 112, 113, 114 having a closure ring 114 traversed centrally by the driver 118. It is of transverse orientation. These front and rear faces are in Figures 3 to 13 parallel to each other.
- the pressure plate is implanted in the housing.
- the invention generally takes advantage of the presence of the housing within which is implanted at least in part the pressure element.
- the pressure element 118, 120 is axially movable with respect to the reaction plate 112 in the limit of axial play. Preferably this axial clearance is guaranteed by an elastic washer with axial action 400 bearing on the reaction plate 112 for action on the coach 118 and pushing it backwards.
- the invention can take advantage of the closure ring 114 of the housing.
- the invention can take advantage of the skirt 113 of the housing.
- the friction disc 301 may be rotatably connected to the driver 118 by a form-coaxial connection permitting axial mobility of the disc 301 with respect to the driver 118.
- the disk 301 may be integral with the pressure plate 120 and come into direct or indirect contact with the reaction plate 112.
- the disk 301 may be integral with the reaction plate and come into direct or indirect contact with the pressure plate 120.
- This game can advantageously be guaranteed by an elastic washer with axial action 400 interposed between the reaction plate 112 and the driver 118.
- This washer 400 bears on the rear face of the reaction plate 112 and acts on the front face of the coach 118 to push it backwards and thus to the retreated position of rest.
- This arrangement promotes a better rotation of the pinion 11 relative to the driver, as well as a better separation of the disc 301 compared to the pressure plate 120 or the friction lining with respect to the reaction plate 112.
- This washer 400 increases the detachment speed of the driver 118 with helical splines 29 in engagement with the complementary helical splines 28 of the shaft 24. This washer 400 thus favors the unscrewing of the driver 118 and thus reduces the reaction time. peeling off.
- This arrangement also reduces noise because it avoids contact between the driver 118 and the reaction plate 112 when the clutch 300 is not engaged.
- the pressure plate 120 is integral with the driver 118, while the reaction plate 112 (FIGS. 4 and 10) is integral in rotation with the pinion 11 and belongs to the housing 112, 113, 114.
- the plates 120 and 112 are transverse orientation and parallel to each other.
- the pinion 11 may be worn, as in Figures 1 and 2 and as visible for example in Figures 3 and 4, by a sleeve 111 of axial orientation.
- This sleeve 111 is extended at its rear end by the reaction plate 112.
- This plate 112 is itself extended at its outer periphery by an annular skirt 113 of axial orientation. This skirt 113 is directed rearward towards the trainer 118.
- the skirt 113 thus extends axially to the outer periphery of the reaction plate 112 while being directed in the opposite direction to the pinion 11.
- the length of the sleeve 111 depends on the applications
- the reaction plate 112 may be in one piece with the sleeve 111.
- the reaction plate 112 is distinct from the sleeve 111 by being assembled thereto, for example by screwing, riveting, using parts fixing, such as screws, or welding.
- the sleeve 1 1 1 is extended at the rear by a sail of transverse orientation. This web may be perforated for assembly with the reaction plate 1 12, for example cast iron, overmolded on the web. In these variants one can choose the material of the tray 1 12 so that it has an adequate coefficient of friction.
- the skirt 1 13 may be in one piece with the reaction plate
- the skirt 1 13 may be distinct from the reaction plate 1 12 being assembled thereto for example by screwing, riveting, using fasteners, such as screws, or welding.
- the web extending in the above-mentioned manner the sleeve 11, is itself extended by an axially oriented sleeve with holes for assembly by overmolding the skirt with this axially oriented sleeve. In these two cases one can choose the material of the skirt 1 13 so that it has the qualities required for its function to achieve.
- the skirt 1 13 is assembled to the reaction plate by means of a cover 230.
- This skirt may belong to the hood as in WO 2006/100353.
- the pinion 1 1 may be integral with the sleeve 1 1 1, as in Figures 3, 4 and 8 to 1 1,
- the pinion 11 may be distinct from the sleeve 11 by being rotationally integral therewith with the possibility of axial movement as can be seen in FIGS. 12 and 13.
- the pinion 11 is attached to attachment, in particular by crimping or welding, to the sleeve 11 1.
- the material of the pinion 11, such as steel with mechanical resistance, the material of the reaction plate 1 12 and the skirt 1 13 can be chosen optimally depending on the function to be performed.
- the shade of the material of the pinion 1 1 can be adapted to the needs of the gear with the crown C (mechanical strength, wear resistance, low noise emission ..), while the grade of the material of the reaction plate 1 12 can be specially adapted to the needs of the clutch and the passage of torque (wear resistance, value of the coefficient of friction, mechanical resistance, etc.).
- the pinion 11 and the reaction plate 1 12 may be obtained by machining and heat treatment being for example metal.
- the pinion 11 and the reaction plate 112 are obtained by molding, in particular by sintering.
- the sintering can be bi material when the reaction plate 1 12 is monobloc with pinion January 1. This also applies to the skirt 11, which can be obtained by molding with the reaction plate 1 12.
- the plate 1 12 may be alternatively provided with a layer whose coefficient of friction is compatible with that of the friction disc 301. With this arrangement the material of the tray 1 12 may be the same as that of the pinion 11 metal. This layer is for example glued on the rear face of the reaction plate 1 12.
- the layer is replaced by a friction disc 302 rotatably connected to the skirt 1 integral with the reaction plate 1 12 by a shape-engaging connection permitting axial movement of the disc 302 by
- the friction disk 302 may be bonded to the reaction plate by gluing or otherwise.
- the pressure plate 120 of the clutch which can be attached to the attachment to the drive sleeve 1 19 that includes the coach 1 1 8, or alternatively overmolded on a transverse web integral of the sleeve 1 19, or be in one piece with this socket 1 19.
- the pressure plate 120 belongs to the coach 1 18. This plate 120 is integral with the coach 1 18 being worn secured to the socket 1 19.
- Trays 1 12 and 120 may therefore be in a cast iron embodiment.
- the plate 120 may therefore be alternatively provided with a layer whose coefficient of friction is compatible with that of the friction disc 301.
- the launcher 1 belongs to a mobile assembly 500 comprising, as in FIGS. 1 and 2, the control lever 20.
- This assembly 500 is movable between a retracted rest position (FIG. 3), in which the pinion 11 is at a distance the ring gear C, and an advanced position ( Figure 1 1) meshing with this starter ring C; the pinion then being in abutment on the abutment 25 of FIG.
- This assembly 500 is, according to the invention, configured, as described below, to constitute a synchronizer for meshing of the pinion January 1 with the ring C before stopping in rotation thereof. It is thus possible to restart the engine more quickly before the complete stop in rotation of the crown C and this with a minimum noise and reduced shocks between teeth of the pinion 1 1 and the crown C. The time between two successive restarts of the engine can be reduced.
- the lever 20 is mounted in place of that of Figures 1 and 2 so that the upper end of the lever 20 is adapted to be moved by the electromagnetic contactor 2 of Figures 1 and 2.
- this movable assembly 500 comprises means 200A, 200A, 120A for closing the friction clutch 300.
- These closing means 200-200A, 120A are associated with the control lever 20 and are configured to act offline on the control device. 1 1 8 drive and urge it towards the reaction plate 1 12 for clamping the friction clutch 300. This is achieved when the moving assembly moves from the rest position to the advanced meshing position with the starter crown, ie during the engagement and training phase with the crown C.
- closing means 200-200A, 120A are connected to the lever 20. According to a characteristic of the articulation means intervene between the lever 20 and these closing means 200-200A, 120A.
- the lever 20 is configured so as to enable the casing 1 12, 1 13, 1 14 to be displaced axially along the axis of axial symmetry X towards the advanced meshing position with the start crown C, while that the means of closing
- the friction clutch are configured to, in a second step, axially move the driver 1 1 8 towards the reaction plate 1 12 for clamping the friction clutch 300.
- the friction clutch 300 closing means may comprise a closing piece 200, 200A of the friction clutch 300.
- This piece 200 may be coupled to the lower end 240, 241, 242 of the lever 20 as best seen in Figures 6 and 7.
- This piece 200A may be coupled to the lower end of an additional lever 120A as best seen in Figures 16 and 17.
- the coupling of the closing piece 200, 200A respectively to the control lever 20 and to the additional lever 120A is a hinge hinge, means of articulation intervening between the closure piece and its associated lever.
- This closing piece is configured to act offline on the trainer 1 1 8 and urge it towards the reaction plate 1 12 for clamping the clutch 300.
- the lever 20 is configured, as above, to act on the housing 1 12, 1 13, 1 14 supra and move it axially to the advanced position meshing with the crown C.
- the housing is moved axially along the X axis and the shaft 24.
- the lever 20 acts in the aforementioned manner on the housing first, before the clamping action exerted by the closing part 200, 200A on the coach 1 1 8.
- this closing piece consists of a closing washer 200 of the clutch 300.
- the washer 200 is hingedly mounted on the forked lower end 240, 241, 242 (FIGS. 6 and 7) of the lever 20. It is mounted in the fork of the lower end of this lever 20.
- This washer 200 may be open at its inner periphery
- the washer 200 may be closed and be mounted in the groove 223 by a mounting bayonet type.
- the opening of the washer 200 is oblong and transverse to the X axis to allow a radial displacement of the washer 200 relative to the groove 223.
- the groove 223 is delimited by two transversely oriented flanks. Its section is generally U-shaped. One of the flanks of the groove 223 may be thicker than the other flank as can be seen for example in FIGS. 4, 5 and 10. In these figures it is the front flank 224 of the groove 223, which is the thicker.
- the groove 223 may be formed by means of an annular piece 123, generally U-shaped section, attached to the driver 118, more precisely on the outer periphery of the sleeve 119.
- the piece 123 and the closure washer 200 may be plastic for noise reduction.
- the washer 200 is configured to act on the front flank 224 of the groove 223. It is able to bear in two diametrically opposite zones on the front flank 224, which is the thickest.
- flank 224 partly penetrates inside the ring 114. Its outer diameter is smaller than the internal diameter of the ring. This reduces the axial size of the launcher 1.
- the launcher 1 thus comprises (see FIGS. 3 to 5) the centrally hollow driver 118 for the passage of the output shaft 24 with a section 110 having helical splines 28.
- This driver 118 comprises at the rear the driving bush 119 internally provided with helicoidal grooves 29 of complementary shape to the helical grooves 28 of the shaft 24 at its inner periphery.
- the aforementioned washer 400 increases the unscrewing speed of the splines 29 with respect to the splines 28.
- the sleeve 119 is defined at the front by a flange 120 transversely oriented relative to the axis X of the output shaft 24 of the starter shown in part in Figure 3.
- This shaft 24 comprises at the front a smooth section 22 having a recess (not referenced) for receiving the mounting ring of the abutment 25 of FIG. 1.
- a bearing 124 is integral with the metal gear 11 of the centrally hollow launcher. This pad 124 intervenes between the outer periphery of the section 22 and the inner periphery of the pinion 11 delimiting a cylindrical central bore through which the section 22 passes.
- the annular piece 123 dedicated to the reception of the washer 200 closing the clutch 300, is force-fitted on the outer periphery of the sleeve 119.
- This piece 123 to section U-shaped, comprises an annular bottom axially oriented relative to the axis X (not referenced in Figures 4 and 10) in contact with its inner periphery with the outer periphery of the sleeve 119 and two sidewalls transverse orientation with respect to this axis X.
- the leading edge is in contact by its front face with the rear face of the flange 120.
- This front flank constitutes the thickest flank 224 of the groove 223.
- the piece 123 is chamfered to the flange 120.
- FIGS. 4 and 10 a slot (not referenced) exists between the rear end of the section 121 and the front face of the flange 120 to be able to machine the grooves 122.
- the flange 120 is here ring-shaped. Its diameter is smaller than that of the coach 118 of Figures 1 and 2.
- the outer diameter of the flange 120 is, according to one characteristic, greater than the outer diameter of the piece 123 constituted by the outer diameter of its flanks.
- the piece 123 is axially supported on the flange 120.
- this puddle 120 constitutes in this embodiment the above-mentioned pressure plate of the friction clutch 300 provided with at least one friction disk 301.
- This flange 120 integral with the driver 118, is implanted in the housing 112, 113, 114
- This friction clutch 300 replaces the freewheel roller of FIGS. 1 and 2. It constitutes a disengageable coupling means for the driver 118 to the pinion 11. It allows a rotation in both directions of the pinion 11 when the launcher is in position. advanced rest position.
- the driver presents here at the front a section 121 with grooves 122 of axial orientation.
- This section 121 penetrates inside the cavity defined by the reaction plate 112 and the skirt 113. It is therefore implanted in this cavity.
- the disk 301 has, at its inner periphery, tabs which penetrate in a complementary way in the grooves 122.
- the disk 301 is rotatably connected to the driver 118 by cooperation of shapes with the possibility of axial movement.
- the reaction plate 112 extends parallel to the flange 120.
- the outer diameter of the reaction plate 112 is greater than the outer diameter of the flange 120.
- the pinion 11 is of outer diameter greater than that of the sleeve 11 January.
- the pinion 1 1 is integral with the sleeve 1 1 1, itself integral with the reaction plate 1 12 extended at its outer periphery by the skirt 1 13 cylindrical.
- the skirt 1 13 is directed axially towards the rear in the direction of the flange
- the inner periphery of the skirt 1 13 extends parallel to the section 121 of the coach 1 1 8 and this radial distance from the section 121.
- the outer diameter of the disc 301 is smaller than the internal diameter of the skirt 11, while the internal diameter of the disc 301 is generally equal to the external diameter of the section 121.
- the size of the inner tabs of the disc 301 depends on the depth of the grooves 122.
- a friction disc 302 is rotatably connected to the reaction plate 1 12 while being adjacent to the rear face of this plate 1 12.
- skirt 1 13 internally has an extra thickness (not referenced).
- Axially oriented grooves 322 are formed at the inner periphery of this extra thickness.
- the disk 302 has at its outer periphery tabs (not referenced) penetrating in a complementary manner in the grooves 322 for rotational connection to the reaction plate 1 12 by cooperation of shapes with axial mobility.
- the outer diameter of the disc 302 is generally equal to the internal diameter of the extra thickness of the skirt 1 13, while the internal diameter of the disc 302 is generally equal to the external diameter of the section
- the size of the outer tabs of the disc 302 depends on the depth of the grooves 322.
- the number of tabs of the discs 301, 302 may be equal to the number of complementary grooves respectively 122, 322 for maximum torque transmission. In a variant, the number of tabs may be smaller than the number of complementary grooves 122, 322 when the torque to be transmitted is smaller.
- the tabs of the discs 301, 302 and the complementary grooves 122, 322 may be of generally trapezoidal shape (FIG. 5).
- the lugs of the disks 301, 302 and the complementary grooves 122, 322 may be in the form of globally semicircular section globules.
- the tabs of the discs 301, 302 and the complementary grooves 122, 322 may be of generally rectangular shape.
- the number of disks 301, 302 can be increased to transmit a larger torque without increasing the diameter of the launcher 1.
- two friction discs 301 are provided.
- a greater number of friction discs 301, 302 are provided.
- the disks 301, 302 may be of the organic type being obtained for example from a binder comprising at least one thermosetting resin, fillers, such as graphite-silica metal powders, and fibers, such as aramid fibers, for example Kevlar ⁇ .
- the discs 301, 302 may be of the sintered type composed of metal powders, such as copper and iron, agglomerated at high temperature and under pressure.
- the disks 301, 302 may be of the metal type and include an alloy, for example copper or iron.
- the discs 301, 302 may be metallic and be covered on each of their face with a friction lining for example of the aforementioned type that is to say organic or sintered.
- the tabs 301, 302 of the disks are in this case metal.
- the disks 301 are each interposed between two disks 302, one of which is adjacent to the rear face of the reaction plate 122.
- the disk 302 farthest from the plate 122 called the extreme disk, has a rear face which faces the front face of the flange 120.
- the skirt 113 is extended, at its axial end farthest from the plate 112, by a closure ring 114, of transverse orientation relative to the axis X.
- the control lever 20 is configured to come into contact with the closing ring 114.
- the pads 100 described below intervene between the housing 112, 113, 114 and the lower part of the control lever 20.
- the shoes 100 may belong to the housing.
- the pads 100 belong to the control lever 20 being integral with the lever. They are carried by the lever 20. In these figures the pads 100 are configured to act on the closure ring 114.
- the ring 114 belongs to the housing comprising the reaction plate 112 integral with the sleeve 111 and the skirt 113.
- This casing is integral in rotation with the pinion 11, which may also be axially integral with the sleeve 111 and this housing or alternatively be movable axially with respect to this housing as described below.
- the ring 114 is a closing ring of this housing and is itself centrally closed by the flange 120.
- the flange 120, the discs 301, 302 and the washer 400 are introduced into the casing before closing it by the ring 114.
- the rear face of the flange 120 may come into contact with the front face of the ring 114.
- the outer diameter of the flange 120 is greater than the internal diameter of the ring 114.
- this ring 114 is annularly hollowed at its inner periphery. A change in thickness of the ring 114 is thus made at its inner periphery with the formation of a shoulder 115 of transverse orientation relative to the axis X.
- This shoulder 115 (FIG. 4) is delimited at its outer periphery. by an annular bearing surface 215 of axial orientation with respect to the X axis with presence of a rounded connection of the shoulder 115 to the bearing surface 215.
- the front face of the shoulder 115 is adapted to cooperate with the rear face of the flange 120.
- the outer diameter of the flange 120 is smaller than the internal diameter of the bearing surface 215 and greater than the internal diameter of the ring 114.
- the shoulder 115 is therefore configured to cooperate with the outer periphery of the rear face of the flange 120.
- the ring 114 is annularly hollowed at its outer periphery for mounting an assembly cap 230 of the ring 114 and the skirt 113 to the reaction plate 112.
- the extra thickness of the skirt 113 made for forming the grooves 322 of axial orientation, constitutes an axial spacer between the ring 114 and the reaction plate 112.
- This cover 230 is here made of sheet metal and has a bottom with a central hole. This bottom (not referenced) is in contact with the front face of the plate 112 and is extended at its outer periphery, by means of a chamfer, by an annular skirt of axial orientation in intimate contact with the outer periphery of the skirt 113.
- the hood 230 of annular shape, thus wraps the skirt 113.
- the internal diameter of the bottom of the cover 230 is preferably equal to greater than the external diameter of the pinion 11 for mounting by axial threading of the cover 230 on the skirt 113 with abutment of the bottom of the cover 230 on the plate 112. The free end the cover 230 is then folded radially inwards to penetrate into the recess of the outer periphery of the ring and attachment of the skirt 113 to the plate 122.
- the ring 114 is attached to fastening, for example by riveting-screwing-crimping, or welding such as a laser welding by transparency, on the free end of the skirt 113, which in the aforementioned manner, can be reported on the outer periphery of the plate 112 or be in one piece with this plate 112.
- a bayonet type assembly may be formed between the ring 114 and the skirt 113. The presence of the hood 230 is not required.
- the outer periphery of the skirt 113 is cylindrical.
- the outer periphery of the skirt 113 may not be cylindrical, for example being of frustoconical shape.
- the outer diameter of the piece 123 is smaller than the internal diameter of the ring 114 of the housing.
- the outer diameter of the flanks of the groove 223 is therefore smaller than the internal diameter of the ring 114.
- the thickest flank 224 of the part 123 is of axial thickness greater than that of the shoulder 115.
- This thickness is in this embodiment greater than the clearance J as better visible in the figures. 4 and 10.
- the thickness of the flank 224 depends on the applications. This thickness is determined to avoid any interference of the clutch closure washer 200 with the ring 114, in particular in the position of FIG. 11.
- the flank 224 is allowed to move axially with respect to the ring 114. the direction of the reaction plate 112 during the transition from the position of Figure 3 to the position of Figure 11. It penetrates in part in the ring 114 in the aforementioned manner.
- the thickness of the flank 224 is in this example less than that of the ring 114. It all depends on the applications.
- the groove 223 may comprise alternatively two sidewalls, one of which is constituted by the flange 120 constituting the pressure plate of the clutch 300 and the other by a washer attached to the rear end of the coach as in FIGS. 1 and 2.
- the flange 120 is thicker at the rear. This extra thickness and the diameter thereof will then correspond to those of the branch 224.
- the sleeve 111 is integral with a housing comprising the reaction plate 112, the skirt 113 and the ring 114.
- This housing houses the clutch 300 and the flange 120 therein.
- This washer 400 pushes the coach 118 backwards and promotes the detachment and the speed of detachment of the driver 118 screwed onto the splines 28 of the shaft 24.
- This washer 400 reduces noise because it avoids any contact between the coach 118 and the reaction plate 112 when the moving assembly 500 is in the retracted rest position. It is compressed in the advanced position of the moving assembly 500.
- the setting of the washer 400 is low. It develops a minimal force compared to that developed by the spring tooth against tooth 5.
- the washer 400 here consists of a wave washer of the onduflex type, which is housed in an annular groove 401 formed in the rear face of the reaction plate 1 12 at the inner periphery of this plate 1 12, which is of reduced thickness at the of this groove 401 open towards the coach 1 1 8.
- This washer 400 is compact axially and exerts a generally constant force on the flange 120.
- the section 121 has at its front end an annular projection (not referenced) able to penetrate inside the washer 400 for a good positioning thereof.
- the washer 400 is replaced by a Belleville washer or a diaphragm in the form of a Belleville washer comprising tabs at its inner periphery, or even a coil spring.
- the lever 20 ( Figures 6 and 7) has at its upper end two tabs 244, 245 separated from each other by a slot 246 for passage of the front end of the rod 5a of Figure 1.
- Each tab 244, 245 comprises a recess 247 for receiving the upper hinge axis 20a of FIG. 2, this axis passing through the rod 5a.
- the rod 5a and the axis 20a belong to the contactor 2 and thus to means for maneuvering the upper end of the lever 20.
- This lever 20 also comprises a fork-shaped lower end 240, 241, 242 and a connecting portion 243 connecting the upper end to the lower end of the lever 20.
- the connecting portion 243 is generally of constant width between the ends of the lever. This portion 243 carries laterally on each of its faces a cylindrical pivot 20b. These pivots 20b are each intended to penetrate each into the oblong hole formed in the branches that comprises the support 36 of Figure 2. The pivots 20b constitute the axis of intermediate articulation of the lever 20. The width of the portion 243 is function the distance between the branches of the support 36.
- the lower end of the lever 20 comprises two arms 240,
- the lever 20 is thus a pivoting control lever comprising, on the one hand, an upper end adapted to be displaced by maneuvering means belonging to the starter and, on the other hand, a fork-shaped lower end comprising two arms 240, 241.
- the closure washer 200 of the clutch 300 is housed in the lower end of the lever 20, between the arms 240, 241.
- the washer 200 is pivotally mounted between the arms 240, 241.
- This washer 200 is open at its lower end for forming two branches 201, 202 interconnected by an outer portion 203 extending at a distance from the rounded portion 242.
- Portion 203 is rounded in this embodiment. It may be trapezoidal or other shape.
- the washer 200 when the washer 200 is closed, the latter comprises two branches 201, 202 connected by a rounded outer portion and also by a rounded internal portion.
- the edges of the branches are parallel.
- the branches 201, 202 are separated from each other by a distance which corresponds generally to the external diameter of the bottom of the groove 223.
- this bottom of the groove 223 corresponds to that of the part 123 for mounting on it and support in two diametrically opposite zones on the side 224 of this piece 123 annular groove 223.
- the branches 201, 202 are mounted axially in the groove 223 of the part 123 for delayed intervention on the trainer 1 1 8.
- Each branch 201, 202 carries laterally a pivot 204 salient adapted to penetrate in a complementary manner in a cylindrical hole 261 that each arm 240, 241 has at its lower end.
- One of the associated arm-arm members carries a pivot 204 penetrating into a hole 261 belonging to the other of the associated arm-branch elements.
- a small radial clearance may exist between the pivot 204 and its associated hole 261 for better decoupling of the action exerted by the lever 20 on the ring 114 relative to the action exerted by the washer 200 on the leading edge 224 of the groove 223 of the actuator 118.
- the articulation is performed for each branch 201, 202 at the lower end of the arm 240, 241 associated.
- each arm 240, 241 has a rounded zone 262 extended outwardly, according to a characteristic by a protruding pad 100, configured according to a characteristic for externally forming a cam adapted to come into contact with the casing 112, 113 , 114 to move it towards the meshing position of the pinion 11 with the crown C and this along the axis of axial symmetry X of the launcher 1.
- each shoe 100 is in this embodiment integral with the arm 240, 241 of the lever 20 and is configured to come into contact with the closure ring 114, more precisely with the rear face of this ring 114.
- the pads 100 extend in axial projection with respect to the front face of the lever 20.
- These cam-shaped pads 100 each comprise, as can be seen in FIGS. 3-6, a top portion 101 extended to its inner periphery by an inclined portion 102 of relief extending towards a flat portion 104, which is connected to the rounded area 262.
- This portion 101 is generally flat.
- This flat portion 1001 may be parallel to the rear face of the arm 240, 241 concerned and be delimited at its outer periphery by a portion 103 generally perpendicular to the arm 240, 241 concerned.
- the holes 261 and the pivots 204 are located at the portions 104 and 262 areas as visible in Figures 3, 8, 8, 11. Each cam thus has the portions 101, 102, 103.
- the pads 100 carried by the lever 20 are, via their top portion 101, able to come into contact, that is to say, in abutment, on the closure ring 114 in two diametrically opposite zones thereof.
- the spacing between the arms 240, 241 is therefore a function of the internal diameter of the ring 1 14.
- lever 20 and the washer 200 may be plastic for noise reduction and ease of assembly.
- the pads 100 may be monobloc with the lever 20.
- the lever 20 and the washer 200 may be made of metal, for example based on aluminum.
- the piece 123 is advantageously metallic
- pivots 204 may be reported. They may be different material than the lever 20 or the closure part 200.
- the pads 100 may be reported on the lower end of the lever 20. They may be of different material from that of the lever 20.
- the plastic material may be reinforced with fibers.
- pads 100 may be reported on the arms 240, 241.
- the moving assembly 500 allows meshing of the pinion 1 1 with the crown C before stopping in complete rotation thereof.
- This mobile assembly 500 is equipped above with a pinion 1 1, which can rotate clockwise and counterclockwise.
- the moving assembly 500 operates as follows.
- this assembly 500 is in the retracted rest position corresponding to that of FIGS. 1 and 2.
- An axial jue exists between the branches 201, 202 and the flank 224.
- the one or more coils 2a are electrically powered by the actuator 2 of FIGS. 1 and 2.
- the power supply of the actuator 2 creates a magnetic field and an axial displacement of the movable core 2b in the direction of the fixed core 2f, said movable core 2b acting on the upper end 244, 245 of the lever 20 via the engaged axis 20a in the hollows 247.
- the upper end 244, 245 of the lever 20 is then moved generally axially along the arrow f1 of FIG. 8 with pivoting of the lever 20 in the support 36, via the pivot pins 20 constituting the intermediate hinge axis of the lever 20 in the support 36, in a clockwise direction.
- the shoes 100 act, via their summit portion 101, on the ring 114 of the casing 112, 113, 114, which then moves the sleeve 111 and the pinion 11 axially towards the crown C along the shaft 24 along the arrow f3 of FIG. 8.
- the bearing 124 slides on the shaft 24.
- the washer 200 is moved axially towards the flange 224 to come into contact therewith and axially move the driver 118 and the flange 120 thereof towards the reaction plate 112.
- the washer 400 is then compressed. and the game J between the extreme disk 302 is canceled.
- the clutch is then progressively engaged for transmitting the torque of the pinion 11 to the ring gear C.
- the pivots 204 and the holes 261 are moved axially towards the flank 224 during the transition from the position of FIG. 8 to the position of FIG. 9. During this passage, the radial clearances between the holes 261 and the pivots 204 are caught up.
- This radial clearance is present in the position of Figure 9 between the inner periphery of the pivot and the inner periphery of the associated opening 261. In the position of Figure 8 this game is present between the outer periphery of the pivot and the outer periphery of the associated hole 261.
- the radial clearance is for example less than 0.5 mm. It is in the figures overall of 0.35 mm.
- a third step moving from the position of FIG. 9 to the advanced meshing position of FIG. 11
- the axial movement of the pinion 11 and the pivoting of the lever 20 continues, the shoes 100 are retracted, the clutch 300 is engaged and the torque is transmitted from the pinion 11 to the crown C.
- the pinion 11 penetrates fully into the crown C to mesh with it ( Figure 11) and the washer 200 moves radially outwardly while remaining in position. sliding along the flank 224 and without contact with the ring 114 taking into account the thickness of the flank 224.
- the pivots 204 and the holes 261 also move radially outwards.
- the washer 400 is compressed.
- the length of the branches 201, 202 is dimensioned according to the applications so that these branches 201, 202 remain in contact with the flank 224 in two diametrically opposite zones.
- a complementary spline mounting 422 occurs between the outer periphery of the sleeve 111 and the inner periphery of the pinion 11 distinct from the sleeve 11.
- This assembly creates a rotational connection between the pinion 11 and the sleeve 111 secured to the housing 112, 113, 114.
- the grooves 422 here are of axial orientation, unlike the complementary helical grooves 28, 29.
- the pinion 11 is extended at the rear by a cylindrical wall of axial orientation 452, which delimits with the outer periphery of the sleeve 111 a housing cavity of an elastic member 451, here a coil spring 451.
- This spring 451 takes support at one of its axial ends on the bottom of this cavity constituted by the zone of connection of the wall 452 to the inner periphery of the pinion 11.
- the other axial end of the spring 451 bears on the front face of the plate of reaction 112.
- the wall 452 guides the spring 451.
- a groove 453 is provided at the rear axial end of the sleeve 111 adjacent to the plate 112 so as to be able to machine the grooves at the outer periphery of the sleeve 111, here in one piece with the plate 112.
- the inner periphery of the front end of the pinion 11 is hollowed to form a housing 456 of a circlip ⁇ 452 axial retaining the pinion 11.
- This circlip is mounted in a groove 454 machined in the front end of the sleeve 111
- the spring 451 urges the pinion 11 towards the circlip 450 constituting an axial abutment then bears against the shoulder formed by the bottom of the housing 456.
- the spring 5 of FIG. 1 is then compressed until it comes into contact with the movable contact 3a with the heads of the terminals 3e, 3f and set rotation of the electric motor M allowing, in a known manner, penetration of the pinion 11 in the crown.
- the stiffness of the spring 45 1 is greater than that of the spring washer 400 being lower than that of the spring 5.
- the spring washer 400 is mounted in an annular groove formed in favor of a reduction in thickness that the reaction plate 1 has at its internal periphery. .
- This shoulder is delimited at its outer periphery by an annular bearing axially oriented relative to the axis X.
- This scope is a range centering for the outer periphery of the elastic washer 400 of corrugated shape in these figures.
- the groove is centrally open for passage of the output shaft 24.
- FIGS. 4 and 10 there is shown a variant of the groove 401 for housing the washer 400.
- This groove 401 is open axially in the direction of the driver 1 1 8 and has a bottom of transverse orientation and two parallel flanks. axial orientation.
- the reaction plate 1 12 is hollowed at its inner periphery for housing the washer 400 which reduces the axial size.
- reaction plate 1 12 is of constant thickness and has a cylindrical wall of axial orientation for the housing of the washer 400.
- the pinion 11 can rotate in both directions so that it constitutes a crazy gear.
- a mechanical synchronizer is produced; the pinion 1 1 crazy can penetrate the crown C when it rotates so that the speed of rotation of the pinion 1 1 is adapted and synchronizes with that of the crown C. This penetration into the crown can be achieved even if it turns in the opposite direction.
- Operation is carried out in two phases.
- the cam-shaped shoes 100 act on the ring 14, which is connected at least in rotation to the then-free pinion 11, because it is crazy during this first phase.
- the gear 1 1 is moved axially via the ring 1 14 and can therefore mesh with the crown C without resistance knowing that the clutch 300 is then disengaged.
- the pads 100 stop pushing on the ring 1 14 and the washer 200 acts on the side 224 of the groove 223 and moves the driver 1 18 and the flange 120 thereof towards the reaction plate 1 12 which makes it possible to gradually close the clutch 300 and thus gradually tighten the friction disk (s) 301, 302 between the reaction plates 1 12 and the pressure plate constituted by the flange 120 to transmit the torque of the electric motor of the starter to the crown C of starting the engine.
- the progressivity of the clutch is favored by the washer 400, which guarantees a clearance between the extreme disc 302 and the flange 120.
- the washer 200 moves radially. It acts in a delayed manner on the coach 1 1 8 of the launcher 1 relative to the action exerted by the shoes 100 on the casing of the launcher 1.
- the closing of the clutch 300 occurs much faster than in conventional friction clutch launchers.
- the disks 301, 302 are held together during their compression.
- the clutch can not open; the pressure within the clutch being maintained by the washer 200.
- the washer is mounted in the groove 223 the clutch 300 closes more quickly.
- the reference R corresponds to the idling speed of the engine, generally of the order of 750 revolutions per minute for a diesel engine
- the reference M corresponds to the speed of minimum rotation of the engine restart (Auto rotation speed)
- Curve A corresponds to the aforementioned conventional curve of a heat engine when it is stopped.
- the engine can be restarted according to the curve B after switching to a positive rotation speed in the window E.
- This curve B is shifted in time with respect to the curve F. It precedes in time the curve F.
- the pinion 11 can penetrate into the crown C in this window E. It can also penetrate into the ring C which is still rotating in the window D.
- bearing 124 is replaced by two needle bearings 124 'as shown in Figure 14.
- bearing 124 is replaced by a lubricated bearing and another bearing, such as a needle bearing.
- the presence of the sleeve 1 1 1 is not mandatory.
- the flange 120 may abut directly on the front face of the ring 1 14 so that the presence of the inner recess 1 15, 215 of the ring 1 14 is not mandatory.
- the skirt 1 13 is alternatively extended axially rearward in the opposite direction to the pinion 11.
- This skirt 1 13 internally carries a ring, such as a circlip or other component ⁇ stop shoulder for the flange 120.
- the projecting pads 100 are intended to bear with the free end of the skirt 1 13.
- This extension of axial length is for example at least equal to the thickness of the closure ring 1 14 of the preceding figures, whose outer diameter is reduced.
- the axial extension of the skirt 1 13 can be further increased as well as the thickness of the flank 224.
- the axial extension of the skirt 1 13 can be further increased as well as the thickness of the flank 224.
- the lever 20 can therefore be supported by its shoes 100 on an annular shoulder offset axially in the direction of the pinion 1 1 relative to the free end of the skirt 1 13 internally with a closing shoulder.
- the closing means of the clutch comprise a closure piece 200A associated with an additional lever 120A.
- the mobile assembly 500 is provided in this case with a double lever comprising the control lever 20 and an additional lever 120 A as visible in Figures 16 and 17.
- the lever 20 is dedicated to the displacement of the housing as in FIGS. 3 to 13, whereas the additional lever 120 A is dedicated to the displacement of the clutch pressure element via the closing piece 200 A hinged to the hinge. lower end of the additional lever 120A.
- This additional lever 120A is configured, as will be described hereinafter, to allow hinge mounting of the control lever 20 between the upper and lower ends thereof.
- the cylindrical pivots 20b belong to the additional lever 120A.
- This additional lever 120A comprises two parts 1210, 1220, each carrying a pivot 20b.
- the spacer 1200 is located in the extension of the pivots 20b indirectly constituting the intermediate pivot axis of the control lever 20.
- the lever 20 for controlling the displacement of the housing has, as in FIGS. 6 and 7, an upper end 244 to 246, a lower fork-shaped end 240 to 242 and a connecting portion 243 connecting the upper end to the end. lower lever.
- This lever 20 is not modified with respect to that of FIG. 6 and therefore comprises two tabs 244, 245 separated from each other by a slot 246 for the passage of the rod 5a of FIG. 1.
- Each tab 244, 245 comprises a recess 247 for receiving the axis 20a.
- the lower part of the lever is similar to that of Figure 6 and therefore comprises two arms 240, 241 connected by a rounded portion 242 connecting to the connecting portion 243.
- Each arm carries a pad 100.
- This lower end 240 to 242 has no holes since the closing part 200 A of the clutch is hinged to the lower end of the additional lever 120A.
- the connecting portion 243 is similar to that of Figure 6. The difference relates to the fact that this part has a notch 1200A for its hinge assembly on the cylindrical spacer 1200.
- the 1200A notch is opened for its snap fit on the spacer 1200.
- the size of the notch 1200A is adapted to the outer diameter of the spacer 1200 for hinge mounting of the portion 243 and therefore the lever 20 on the spacer 1200.
- the two parts 1210, 1220 of the lever 120A consist of flanges. Each flange 1210, 1220 has a lower end, an upper end and a connecting portion 1243 between the lower end and the upper end.
- the additional lever 120A comprises a connecting portion 1243 in two parts separated by the cylindrical hinge spacer 1200 determining the distance between these two parts.
- the connecting portion 243 of the lever 20 is interposed between the two parts of the connecting portion 1243 of the additional lever 120A so that the distance between the two connecting portions of the lever 120A at the spacer 1200 is a function of of the thickness of the connecting portion 243 of the lever 20.
- a mounting jau exists between the two portions of the connecting portion 1243 of the lever 120A and the intermediate portion of the connecting portion 243 of the control lever 20 .
- each flange 1210, 1220 comprises a tab 1244, 1245 offset from the connecting portion 1243 carrying the pivot 20b.
- the tabs 1244, 1245 each have an oblong hole 1247 into which the relevant end of the axis 20a penetrates.
- each flange comprises respectively an arm 1240, 1241.
- Each arm 1240, 1241 comprises a hole (not referenced) for receiving an axis 200B of the closing part 200A of the clutch 300.
- This piece 200a is in the form of a bow mounted to be articulated between the arms 1240, 1241 in favor of an axis 200B that includes the hoop at each of its ends.
- the arch 200A is of semicircular shape and therefore extends circumferentially globally over 1 80 °.
- the shoes 100 and the arms 240, 241 extend above the axes 200B. It will be noted that the additional lever 120A is devoid at its lower end of connection portion between the arms 1240, 1241.
- the lever 20 is implanted into the additional lever
- the control lever 20 is thus mounted to nest in the additional lever 120 A and this pivotally between its lower and upper ends, with the aid of the spacer 1200.
- the rod 5 has moved the axis 20a and the lever 20 pivots around the spacer 1200A to act, via the shoes 100, on the housing to move the pinion 11 as in FIGS. 3 to 13.
- the closing piece 200A then acts on the flank 224 and moves the driver 1 18 to tighten the clutch 300 as in FIGS. 3 to 13.
- the closing piece 200A acts in a delayed manner via the lever 120A after catching the jut between the axis 20a and the front edges of the holes 1247. This piece 200A is therefore hinged to the lower end of the additional lever 120 A configured to act offline after the lever 20.
- the means for closing the clutch comprise an additional lever 120A pivoting with the aid of the pivots 20b having, on the one hand, an upper end 1244, 1245 capable of being displaced, after catching up on a second. by operating means 20a, 5a belonging to a starter and on the other hand, a lower end comprising two arms 1240, 1241 configured for hinge mounting of a closure piece 200A adapted to act in a delayed manner on the trainer 1 1 8 to axially move the clutch pressure member via the driver 1 18 and urge the trainer 1 1 8 towards the reaction plate for clamping the clutch 300.
- the operating means of the additional lever 120 A are constituted by the operating means of the control lever 20.
- this additional lever 120A comprises two flanges 1210, 1220 which follow the shape of the control lever 20 implanted between the two flanges 1210, 1220. These two flanges 1210, 1220 are separated from each other between their lower and upper ends by a cylindrical spacer 1200 for pivoting mounting of the control lever 20
- the levers 20, 120 A may be plastic.
- the flanges 1220, 1210 may be monoblock with the spacer 1200 and pivots 20b.
- the lever 20 may be metal and the lever 120A plastic.
- the spacer 1200 may be integral with the flanges 1220, 1210 or be attached to the flanges 1210, 1220.
- pads 100 may be integral with the lever 20 or be reported thereon.
- shoes 100 may be carried by the casing of the launcher 1. These pads 100 then each cooperate with the relevant arm of the control lever 20.
- the pads belong to the closure ring 1 14 or to the skirt 1 13 as appropriate.
- the friction clutch 300 is, as mentioned above, alternatively of the frustoconical type as described in the document WO 2006/100353.
- the friction disk (s) are alternatively replaced by a frustoconical external periphery friction lining, constituting the friction element, anchored in the front part of the driver, constituting the pressure element, passing through the ring. closure, secured to a skirt belonging to a cover fixed on a protuberance of the frustoconical shaped inner periphery reaction plate to cooperate with the outer periphery of the friction lining.
- the retaining ring integral with this skirt is advantageously ribbed to be stiffened.
- the outer protuberance of the reaction plate is alternatively extended axially rearwards to form the skirt on the free end of which is fixed the closing ring of the clutch.
- the spring washer 400 then mounted in an annular groove formed in the transverse part of the reaction plate, allows to detach the friction lining abutting in the rest state against the retaining ring.
- the coach may be made of plastic and include the receiving groove of the closure washer, the retaining ring.
- the friction element may be of plastic material loaded and reinforced by fibers
- the friction element is thus housed in all cases at least partly in the housing delimited by the closing ring.
- the friction disc may therefore be of transverse orientation relative to the X axis with a front face parallel to its rear face as in FIGS. 3 to 13.
- at least one of these front and rear faces constitutes a friction face of the clutch 300.
- the friction face may be constituted by the outer periphery of the friction lining.
- the invention applies to all types of conventional engine starters.
- starter gear can pass through the front bearing and extend to the outside of the housing as described in documents FR 2 677 710, US 4,895,035 and FR 2 738599.
- the sleeve 1 1 1 is extended and bearing means, such as a ball bearing, are interposed radially between the outer periphery of the sleeve and the housing 1 8 as visible in these documents.
- the abutment 25 may be attached to the free end of the shaft 24 or may be implanted in the vicinity of this free end of the shaft 24.
- the starter pinion may, in the aforementioned manner, meshing with an externally toothed starting ring gear as in FIG. 1 or internally toothed as in document FR 2 858 366.
- the transmission of motion described in the document FR 2 858 366 may be be replaced by a chain transmission intervening between a toothed wheel secured to the crankshaft and a toothed wheel belonging to the starter and secured to the internally toothed starter ring.
- a gear transmission may intervene between a toothed wheel secured to the crankshaft and a toothed wheel belonging to the starter and secured to the starter ring adapted to mesh with the launcher.
- the starter ring C is connected directly or indirectly to the crankshaft of this engine.
- the output shaft of the starter can be confused with the output shaft of the electric motor or be distinct from this so that the two output shafts can be coaxial or offset.
- Two gear reducers, in particular of the epicyclic gear type can be provided as described in the document FR 2 858 366.
- a torque limiter and / or a torsion damper may be associated with the speed reducer as described for example in document FR 2 803 345.
- the control lever may be pivotally mounted on a bearing, preferably made of plastic, having a first bearing portion carried by the front bearing housing and a second complementary portion formed vis-a-vis in a bearing part of the lever comprising a transverse annular ring which cooperates with a front portion of the actuator as described in the WO 01/3115.
- the lever may be pivotally mounted on an extension of the ring gear of the shaped gear to provide a function of articulation of the lever as described in WO 2005/054664.
- Tie rods can assemble the rear bearing to the front bearing of the housing with clamping of the cylinder head between these bearings as in the documents WO 2005/054664, FR 263 1 094 and FR 2 858 366 above.
- the stator of the electric motor may comprise a winding as in the document WO 98/329966 or permanent magnets.
- the number of brushes can be increased as described for example in the document FR 2 934 434, especially when the starter must perform the function stop and start (Stop & Start in English), which stops the engine because of conditions such as stopping at traffic lights or traffic jams, and then restarting the engine to reduce fuel consumption.
- the contactor can be installed above the electric motor of the starter as in Figure 1 or be deported being for example implanted transversely to the rear of the starter motor electric motor. via a return mechanism as described in document FR A 2,843,427.
- the contactor may comprise a holding coil and a call coil.
- the contactor comprises a coil as described in document FR A 2 795 884.
- the bearing shoulder of the rear face of the movable contact 3a may have another shape and belong, for example, to a bayonet type mounting as described in the document FR 2 895 143, in particular when the starter must perform the function " Stop & Start "or a snap fit between the central opening of the contact 3a and the rod 3 as described in the document FR 2 767 960.
- the mounting bayonet type may be applied to the lock washer 200.
- the other side of the groove 223 opposite the flank 224 may include two flats for passage of the washer 200 having two complementary flats and then rotation of the washer. in the bottom of the groove 23, the distance between the two flats of the washer being a function of the outer diameter of the bottom of the groove. This is also applicable to the flank 224.
- control lever of the operating means may comprise a movable core electromagnetic switch for operating the control lever and another electromagnetic contactor for operating the control rod and the moving assembly.
- the operating means of the control lever may consist of an actuator with an electric motor acting, for example by a mechanical connection of the rack type, on a movable core comprising inside it the spring against the tooth coupled to a rod as Figure 1.
- the heat engine may be stationary or belong to a motor vehicle, such as a passenger vehicle or a boat.
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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)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
RU2014107016/06A RU2014107016A (ru) | 2011-07-26 | 2012-07-23 | Подвижный узел обгонная муфта/приводной рычаг для зацепления с маховиком двигателя внутреннего сгорания и стартер двигателя внутреннего сгорания, содержащий такой узел |
BR112013033469A BR112013033469A2 (pt) | 2011-07-26 | 2012-07-23 | Conjunto móvel lançador alavanca de comando para engrenagem com uma coroa de partida de um motor térmico e motor de arranque de um motor térmico que compreende um tal conjunto |
JP2014522140A JP2014521893A (ja) | 2011-07-26 | 2012-07-23 | ヒートエンジンのスターターリングギアと噛み合うための、スターター駆動ユニットと制御レバーとを備える移動アセンブリ、および、そのようなアセンブリを備えるヒートエンジンスターター |
CN201280037104.9A CN103717879A (zh) | 2011-07-26 | 2012-07-23 | 包括起动器驱动单元和控制杆的用于热机起动器的移动组件 |
EP12750446.2A EP2737199A2 (fr) | 2011-07-26 | 2012-07-23 | Ensemble mobile avec lanceur et levier de commande pour un demarreur d'un moteur thermique |
KR1020147002118A KR20140051916A (ko) | 2011-07-26 | 2012-07-23 | 열기관 시동기를 위한, 시동기 구동 유닛과 제어 레버를 포함하는 이동 조립체 |
US14/235,395 US20140245984A1 (en) | 2011-07-26 | 2012-07-23 | Mobile assembly comprising a starter drive unit and a control lever, for meshing with a starter ring gear of a heat engine, and a heat engine starter comprising such an assembly |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1156805A FR2978500B1 (fr) | 2011-07-26 | 2011-07-26 | Ensemble mobile lanceur - levier de commande pour engrenement avec une couronne de demarrage d'un moteur thermique et demarreur d'un moteur thermique comportant un tel ensemble |
FR1156805 | 2011-07-26 |
Publications (2)
Publication Number | Publication Date |
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WO2013014385A2 true WO2013014385A2 (fr) | 2013-01-31 |
WO2013014385A3 WO2013014385A3 (fr) | 2013-08-08 |
Family
ID=46724511
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2012/051746 WO2013014385A2 (fr) | 2011-07-26 | 2012-07-23 | Ensemble mobile lanceur - levier de commande pour engrenement avec une couronne de demarrage d'un moteur thermique et demarreur d'un moteur thermique comportant un tel ensemble |
Country Status (9)
Country | Link |
---|---|
US (1) | US20140245984A1 (fr) |
EP (1) | EP2737199A2 (fr) |
JP (1) | JP2014521893A (fr) |
KR (1) | KR20140051916A (fr) |
CN (1) | CN103717879A (fr) |
BR (1) | BR112013033469A2 (fr) |
FR (1) | FR2978500B1 (fr) |
RU (1) | RU2014107016A (fr) |
WO (1) | WO2013014385A2 (fr) |
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WO2015075400A1 (fr) | 2013-11-21 | 2015-05-28 | Valeo Equipements Electriques Moteur | Lanceur et demarreur pour moteur thermique |
US20150204297A1 (en) * | 2014-01-23 | 2015-07-23 | Denso Corporation | Starter |
WO2015145087A1 (fr) * | 2014-03-28 | 2015-10-01 | Valeo Equipements Electriques Moteur | Lanceur de demarreur pour moteur à combustion interne |
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EP0749194A1 (fr) | 1995-06-12 | 1996-12-18 | Valeo Equipements Electriques Moteur | Démarreur de véhicule automobile muni d'un bobinage inducteur d'épaisseur réduite |
FR2738599A1 (fr) | 1995-09-12 | 1997-03-14 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile comportant un lanceur perfectionne et lanceur pour un tel demarreur |
WO1998032966A1 (fr) | 1997-01-28 | 1998-07-30 | Robert Bosch Gmbh | Circuit pour un relais d'enclenchement |
FR2767960A1 (fr) | 1997-09-01 | 1999-03-05 | Valeo Equip Electr Moteur | Contacteur de demarreur de vehicule |
FR2787833A1 (fr) | 1998-12-23 | 2000-06-30 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile a reducteur a engrenages comportant des moyens formant amortisseur de torsion |
FR2795884A1 (fr) | 1999-06-30 | 2001-01-05 | Valeo Equip Electr Moteur | Procede d'entrainement progressif d'un contacteur du demarreur de vehicule |
WO2001031195A1 (fr) | 1999-10-29 | 2001-05-03 | Valeo Equipements Electriques Moteur | Demarreur equipe d'une piece d'appui de levier perfectionnee |
FR2803345A1 (fr) | 1999-12-30 | 2001-07-06 | Valeo Equip Electr Moteur | Demarreur equipe d'un dispositif amortisseur et limiteur de couple |
WO2003006824A1 (fr) | 2001-07-10 | 2003-01-23 | Valeo Equipements Electriques Moteur | Demarreur pour vehicule automobile |
FR2843427A1 (fr) | 2002-07-03 | 2004-02-13 | Valeo Equip Electr Moteur | Demarreur a contacteur deporte sur le palier arriere du moteur electrique |
EP1462645A1 (fr) | 2003-03-28 | 2004-09-29 | Valeo Electronique et Systemes de Liaison | Dispositif de commande d'un démarreur d'un véhicules automobiles |
FR2858366A1 (fr) | 2003-07-28 | 2005-02-04 | Valeo Equip Electr Moteur | Systeme de demarrage a poulie et courroie pour un moteur thermique de vehicule automobile |
FR2862721A1 (fr) | 2003-10-31 | 2005-05-27 | Valeo Equip Electr Moteur | Dispositif de commande d'un lanceur de demarreur electrique |
WO2005054664A1 (fr) | 2003-11-28 | 2005-06-16 | Valeo Equipements Electriques Moteur | Demarreur de moteur a combustion interne equipe de moyens de centrage du reducteur et de culasse sur le boitier |
WO2006100353A1 (fr) | 2005-03-24 | 2006-09-28 | Valeo Equipements Electriques Moteur | Demarreur de moteur a combustion equipe d’un lanceur a roue libre par friction |
FR2895143A1 (fr) | 2005-12-15 | 2007-06-22 | Valeo Equip Electr Moteur | Equipage mobile pour contacteur electromagnetique et contacteur comportant un tel equipage |
FR2934434A1 (fr) | 2008-07-24 | 2010-01-29 | Valeo Equip Electr Moteur | Dispositif porte-balais pour demarreur d'un vehicule automobile |
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IT1249933B (it) * | 1991-06-25 | 1995-03-30 | Magneti Marelli Spa | Dispostitivo di avviamento per un motore a combustione interna per autoveicolo. |
FR2772433B1 (fr) * | 1997-12-17 | 2000-02-04 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile comportant un lanceur perfectionne |
FR2827915B1 (fr) * | 2001-06-29 | 2003-12-19 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile a lanceur perfectionne |
FR2871532B1 (fr) * | 2004-06-09 | 2006-08-04 | Valeo Equip Electr Moteur | Demarreur, notamment de vehicule automobile, equipe d'un lanceur a roue libre par friction |
-
2011
- 2011-07-26 FR FR1156805A patent/FR2978500B1/fr not_active Expired - Fee Related
-
2012
- 2012-07-23 CN CN201280037104.9A patent/CN103717879A/zh active Pending
- 2012-07-23 RU RU2014107016/06A patent/RU2014107016A/ru not_active Application Discontinuation
- 2012-07-23 JP JP2014522140A patent/JP2014521893A/ja active Pending
- 2012-07-23 KR KR1020147002118A patent/KR20140051916A/ko not_active Application Discontinuation
- 2012-07-23 BR BR112013033469A patent/BR112013033469A2/pt not_active IP Right Cessation
- 2012-07-23 EP EP12750446.2A patent/EP2737199A2/fr not_active Withdrawn
- 2012-07-23 WO PCT/FR2012/051746 patent/WO2013014385A2/fr active Application Filing
- 2012-07-23 US US14/235,395 patent/US20140245984A1/en not_active Abandoned
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GB225757A (en) | 1924-03-17 | 1924-12-11 | Eclipse Machine Co | Improvements in engine starters |
US4895035A (en) | 1987-03-26 | 1990-01-23 | Mitsubishi Denki Kabushiki Kaisha | Device for supporting pinion shaft of electric motor for starting engine |
FR2631094A1 (fr) | 1988-05-04 | 1989-11-10 | Equip Electr Moteur | Reducteur de vitesse a limiteur de couple, notamment pour demarreur de moteur a combustion interne |
FR2677710A1 (fr) | 1991-06-13 | 1992-12-18 | Valeo Equip Electr Moteur | Dispositif d'etancheite pour lanceur de demarreur d'un moteur a combustion interne, notamment pour vehicule automobile. |
FR2725758A1 (fr) | 1994-10-18 | 1996-04-19 | Valeo Equip Electr Moteur | Demarreur electrique pour un moteur a combustion de vehicule automobile |
EP0749194A1 (fr) | 1995-06-12 | 1996-12-18 | Valeo Equipements Electriques Moteur | Démarreur de véhicule automobile muni d'un bobinage inducteur d'épaisseur réduite |
FR2738599A1 (fr) | 1995-09-12 | 1997-03-14 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile comportant un lanceur perfectionne et lanceur pour un tel demarreur |
WO1998032966A1 (fr) | 1997-01-28 | 1998-07-30 | Robert Bosch Gmbh | Circuit pour un relais d'enclenchement |
FR2767960A1 (fr) | 1997-09-01 | 1999-03-05 | Valeo Equip Electr Moteur | Contacteur de demarreur de vehicule |
FR2787833A1 (fr) | 1998-12-23 | 2000-06-30 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile a reducteur a engrenages comportant des moyens formant amortisseur de torsion |
FR2795884A1 (fr) | 1999-06-30 | 2001-01-05 | Valeo Equip Electr Moteur | Procede d'entrainement progressif d'un contacteur du demarreur de vehicule |
WO2001031195A1 (fr) | 1999-10-29 | 2001-05-03 | Valeo Equipements Electriques Moteur | Demarreur equipe d'une piece d'appui de levier perfectionnee |
FR2803345A1 (fr) | 1999-12-30 | 2001-07-06 | Valeo Equip Electr Moteur | Demarreur equipe d'un dispositif amortisseur et limiteur de couple |
WO2003006824A1 (fr) | 2001-07-10 | 2003-01-23 | Valeo Equipements Electriques Moteur | Demarreur pour vehicule automobile |
FR2843427A1 (fr) | 2002-07-03 | 2004-02-13 | Valeo Equip Electr Moteur | Demarreur a contacteur deporte sur le palier arriere du moteur electrique |
EP1462645A1 (fr) | 2003-03-28 | 2004-09-29 | Valeo Electronique et Systemes de Liaison | Dispositif de commande d'un démarreur d'un véhicules automobiles |
FR2858366A1 (fr) | 2003-07-28 | 2005-02-04 | Valeo Equip Electr Moteur | Systeme de demarrage a poulie et courroie pour un moteur thermique de vehicule automobile |
FR2862721A1 (fr) | 2003-10-31 | 2005-05-27 | Valeo Equip Electr Moteur | Dispositif de commande d'un lanceur de demarreur electrique |
WO2005054664A1 (fr) | 2003-11-28 | 2005-06-16 | Valeo Equipements Electriques Moteur | Demarreur de moteur a combustion interne equipe de moyens de centrage du reducteur et de culasse sur le boitier |
WO2006100353A1 (fr) | 2005-03-24 | 2006-09-28 | Valeo Equipements Electriques Moteur | Demarreur de moteur a combustion equipe d’un lanceur a roue libre par friction |
FR2895143A1 (fr) | 2005-12-15 | 2007-06-22 | Valeo Equip Electr Moteur | Equipage mobile pour contacteur electromagnetique et contacteur comportant un tel equipage |
FR2934434A1 (fr) | 2008-07-24 | 2010-01-29 | Valeo Equip Electr Moteur | Dispositif porte-balais pour demarreur d'un vehicule automobile |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3003307A1 (fr) * | 2013-03-13 | 2014-09-19 | Valeo Equip Electr Moteur | Demarreur a lanceur muni d'un embrayage a friction a double leviers de commande |
WO2015075400A1 (fr) | 2013-11-21 | 2015-05-28 | Valeo Equipements Electriques Moteur | Lanceur et demarreur pour moteur thermique |
US20150204297A1 (en) * | 2014-01-23 | 2015-07-23 | Denso Corporation | Starter |
WO2015145087A1 (fr) * | 2014-03-28 | 2015-10-01 | Valeo Equipements Electriques Moteur | Lanceur de demarreur pour moteur à combustion interne |
FR3022594A1 (fr) * | 2014-06-24 | 2015-12-25 | Valeo Equip Electr Moteur | Demarreur de vehicule automobile |
WO2015197931A1 (fr) * | 2014-06-24 | 2015-12-30 | Valeo Equipements Electriques Moteur | Démarreur de véhicule automobile |
FR3038157A1 (fr) * | 2015-06-26 | 2016-12-30 | Valeo Equip Electr Moteur | Demarreur de moteur thermique de vehicule automobile muni d'un embrayage a configuration amelioree |
DE102018009455A1 (de) | 2017-12-11 | 2019-06-13 | Valeo Equipements Electriques Moteur | Elektromotor für einen Anlasser eines Verbrennungsmotors und Anlasser, der mit einem solchen Elektromotor ausgestattet ist |
Also Published As
Publication number | Publication date |
---|---|
FR2978500B1 (fr) | 2015-03-13 |
BR112013033469A2 (pt) | 2017-03-14 |
WO2013014385A3 (fr) | 2013-08-08 |
CN103717879A (zh) | 2014-04-09 |
EP2737199A2 (fr) | 2014-06-04 |
US20140245984A1 (en) | 2014-09-04 |
KR20140051916A (ko) | 2014-05-02 |
FR2978500A1 (fr) | 2013-02-01 |
JP2014521893A (ja) | 2014-08-28 |
RU2014107016A (ru) | 2015-09-10 |
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