WO2003083287A1 - Montage de machine electrique tournante pour vehicule automobile - Google Patents
Montage de machine electrique tournante pour vehicule automobile Download PDFInfo
- Publication number
- WO2003083287A1 WO2003083287A1 PCT/FR2003/000866 FR0300866W WO03083287A1 WO 2003083287 A1 WO2003083287 A1 WO 2003083287A1 FR 0300866 W FR0300866 W FR 0300866W WO 03083287 A1 WO03083287 A1 WO 03083287A1
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- WO
- WIPO (PCT)
- Prior art keywords
- contour
- casing
- assembly according
- extension
- driver
- 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
- F02N11/00—Starting of engines by means of electric motors
- F02N11/04—Starting of engines by means of electric motors the motors being associated with current generators
Definitions
- the present invention relates to an assembly of a rotary electrical machine mounted in the movement transmission line between the internal combustion engine of a motor vehicle and a movement transmission box that this motor vehicle comprises.
- This machine comprises, in known manner, a fixed stator surrounding a rotor with the presence of an air gap between the internal periphery of the stator and the external periphery of the rotor as described in document FR-A-2 782 355.
- the rotor of the machine is carried by a drive wheel integral in rotation with the crankshaft of the internal combustion engine.
- This flywheel is integral with the reaction plate of a friction clutch comprising a friction disc, called clutch friction, provided with an internally grooved hub for rotational connection with the input shaft of a gearbox. with manual or robotic control.
- the friction clutch is a shutdown and starting member of the motor vehicle engine.
- a hydrokinetic coupling device 1 comprises a sealed annular casing 3 comprising two parts 300 and 301 connected together by a welding bead 303.
- One of these parts carries blades for formation of an impeller while the other part 301 carries, on the one hand, axially projecting and internally threaded sockets 31 for connection with a connecting flange in rotation with the crankshaft of the vehicle and, on the other hand , a centering nose 30 projecting for its centering relative to the crankshaft.
- a impeller turbine 210 fixed, here by ri stage, on a hub 211 internally fluted for its rotational connection with the input shaft 201 of the box automatic movement transmission, whose housing is seen in 340.
- a bell 14 is tightly fixed on this casing 340.
- the blades of the turbine wheel 210 face the blades of the impeller wheel 300 so that when the casing 3 is rotated by the crankshaft the wheel impeller 300 rotates the turbine wheel 210 and the shaft 201 by circulation of the oil between the blades. This circulation of oil causes the casing 3 to swell slightly.
- the wheels 210, 300 belong, in a known manner, to a torque converter so that the device 1 also includes a reaction wheel 220 connected to a reaction sleeve 222 by means of a free wheel 221.
- a locking clutch 200 called Lock-up.
- This clutch comprises a piston 203 carrying a friction lining 204 and is connected, by means of a torsion damper 205 or rigidly, to the hub 211.
- the clutch 200 is locked; the lining 204 then being clamped between the piston 203 and the transverse wall opposite the part 301 to eliminate the phenomenon of sliding between the wheels 300, 210 and thus reduce the consumption of the vehicle.
- the bell 14 is intended to be fixed on the casing of the internal combustion engine of the vehicle and has for this purpose a flange with passages 141 for the mounting of fixing members, such as fixing screws, to this casing with the more often the interposition of a spacer.
- the nose 30 is closed at its free end and cannot therefore be crossed by a driven shaft as described in FIG. 12 of document EP A 0 901 923.
- the assembly is axially bulky.
- the object of the present invention is to solve this problem in a simple and economical manner.
- an assembly of a rotating electric machine for a motor vehicle comprising a rotor surrounded by a stator integral with a spacer interposed between the casing of the internal combustion engine of the motor vehicle having a crankshaft and a bell
- the bell serves as a housing for the sealed casing of a hydrokinetic coupling device comprising a centering nose projecting axially and closed at its free end
- a first driver connects the crankshaft of the internal combustion engine of the motor vehicle to a rigid support carrying the rotor of the rotary electrical machine
- a second driver is connected to the casing of the hydrokinetic coupling device, in that the two drivers are connected to each other by a formally cooperating connection having a contour d axial orientation carried by the first coach cooperating in a complementary manner with a conto ur antagonist axially oriented carried by the second trainer, in that the rigid support is hollow in shape and in that the contour and the opposing contour penetrate inside the support.
- This assembly is also axially compact because the contour and the opposing contour penetrate into the rigid support. More precisely, the first trainer equipped with the rotor and the contour is first mounted on the vehicle crankshaft automobile and, on the other hand, the second trainer equipped with the opposing contour on the casing of the hydrokinetic coupling device. Then an assembly of the telescopic type is carried out between the contour and the opposing contour, one of these contours being of the male type and the other of the female type. This telescopic assembly is carried out by relative axial approximation of the casing of the hydrokinetic coupling device and of the bell relative to the casing of the vehicle engine. During this assembly, the male contour is quickly and simply threaded into the female contour.
- contours are for example of the multi-tooth or groove type; protrusions of one of the contours entering in a complementary manner into the hollows of the other contour.
- the projecting teeth or the hollow grooves advantageously having a trapezoidal contour.
- these contours are of the polygonal type.
- these contours have one or two flats.
- the casing of the hydrokinetic coupling device, in particular the closed nose thereof, and the crankshaft is not modified.
- the bell is also unchanged and the rotor can have the radial height required for good performance of the rotating electric machine.
- the second drive is axially flexible, in particular for filtering axial vibrations and absorbing deformations, in particular swelling, in operation of the casing of the hydrokinetic coupling device.
- the contour and the opposing contour are located at least for the most part inside the hollow-shaped support.
- the rigid support for reduction of the mass, of the axial bulk, in particular of the spacer, and formation of a housing for the contour and the opposing contour, the rigid support is hollow in shape and has at its outer periphery an annular skirt of axial orientation constituting a mounting surface for the rotor; for cost reduction and reduction in the number of parts, said support constitutes a first part of the first coach, being in one piece with the first coach; to better support the rigid support and the rotor, the first drive is rigid and has a second central portion of transverse orientation relative to the axis of axial symmetry that comprises said assembly; in a simple and economical manner, the contour belongs to an annular protuberance of axial orientation centrally secured to the second part of the first coach; in a simple and economical manner, the opposing contour belongs to an annular extension of axial orientation, which has a radially projecting collar for fixing to the central part of the second driver; to reduce the number of parts and the assembly time in the end, the second drive consists of a
- FIG. 1 is a partial axial sectional view of a conventional hydrokinetic coupling device
- - Figure 2 is an axial sectional view of an assembly of a rotary electric machine according to the invention before assembly of the bell of the hydrokinetic coupling device to the casing of the internal combustion engine of the motor vehicle;
- - Figure 3 is a view similar to Figure 2 after assembly of the bell of the hydrokinetic coupling device with the casing of the internal combustion engine of the motor vehicle;
- - Figures 4,5- 6,7- 8,9- are views similar to Figures 2 and 3 for respectively a second, a third and a fourth embodiment according to the invention.
- the rotary electrical machine 2 is here of the asynchronous type and comprises a stator 5 surrounding a rotor 6.
- the stator and the coaxial rotor are of annular shape and present in known manner a body or core in the form of a pack of sheets.
- the rotor body 6 is shaped for mounting a squirrel cage 60, while the stator body 5 has grooves, for example semi-closed, for mounting electrical conductors arranged to form the armature windings 8 of the machine.
- These conductors belong to conventional wire windings or consist of bars for example in U-shaped pins as visible in document US-A-2 928 963; the machine being of the polyphase type.
- the armature windings 8 pass through the body of the stator 5 and have protruding outside the body of the stator heads called updos.
- the squirrel cage 60 projects on either side of the body of the rotor 6.
- the stator 5 is carried internally by an annular spacer 61 internally provided with a cooling chamber 6002 for the circulation of a heat-transfer fluid, such as the coolant of the vehicle engine, making it possible to evacuate the heat and to cool the stator.
- the stator is fixed to the internal periphery of the spacer 61, for example, by hooping.
- This spacer 61 of axial orientation is located at the outer periphery of the bell 14 by being interposed axially between the casing 62 of the internal combustion engine of the motor vehicle and the housing bell 14 of the hydrokinetic coupling device.
- This bell 14, as visible in FIG. 1, is integral with the casing of the automatic movement transmission box.
- the engine of the vehicle comprises a shaft driving in the form of a crankshaft 11, the free end 111 of which is shaped to carry, outside the casing 62, a first driving drive 12 connecting the crankshaft 11 to a rigid support 13 carrying the rotor 6 of the machine 2.
- This support 13 has a hollow shape in order to reduce the axial size as described below.
- driver 12 is rigid and it is the same in all of Figures 2 to 9.
- This driver 12 carries, here at its outer periphery, the support 13 for the rotor 6.
- the driver 12 and the support 13 are of annular shape.
- the axial axis of symmetry of the crankshaft 11 is aligned with that of the input shaft, of the driven type, of the automatic movement transmission box visible in FIG. 1, so that an axis of symmetry is formed.
- axial XX constituting the axis of rotation of the crankshaft 11, the driven shaft of the automatic movement transmission box and the rotor 6.
- the bell 14 surrounds the casing 3, here metallic, of the hydrokinetic coupling device.
- Non-visible screws ensure the fixing of the spacer 61. These screws have a head bearing on a radial flange, which has the bell 14 at its free end. The screws pass through the edge of the bell 14 through the passages 141 in FIG. 1 and the spacer to be screwed into the threads of the housing 62 and tighten the spacer between the bell 14 and the housing 62.
- centering sleeves 161 of the spacer 61 carried in the figures illustrated by the spacer 61 or alternatively respectively by the bell 14 and by the housing 62 of the vehicle engine, here at the rate of two diametrically opposed sleeves 161 carried by the spacer or respectively by the casing 62 and the bell 14.
- the spacer 61 is in one piece with the casing 62 or the bell 14.
- the variant spacer has no cooling chamber.
- it is of the type described in FIG. 21 of document FR-A-2 782 355 to which reference will be made for more details.
- the cooling chamber 6002 of the spacer 61 is in the form of a channel inside which a heat transfer fluid circulates. This channel is connected to an inlet pipe and to an outlet pipe connected here to the coolant of the vehicle engine as described in the embodiment of FIGS. 14 and 15 of document FR-A-2 782 355 to which one is see for more details.
- the spacer 61, the stator 5 and the rotor 6 are of annular shape while being mounted coaxially.
- An annular radial air gap 7 exists between the internal periphery of the stator 5 and the external periphery of the rotor 6.
- This machine 2 is interposed axially between the casing 62 of the vehicle engine and the casing 3 of the hydrokinetic coupling device, that is to say between the engine block of the motor vehicle and the casing 3, here in stamped sheet metal.
- the rigid support 13 has externally in Figures 2 to 9 an annular skirt of axial orientation.
- the support 13 is in this embodiment in one piece with the driver 12.
- the support 13 is rigidly fixed, for example by welding, to the first driver 12 of the driving type.
- the support 13 is rigidly secured to the coach 12 and constitutes, at the external periphery of the coach 12, a first annular part of axial orientation thereof directed axially projecting towards the casing 3.
- the external periphery of the support 13 constitutes, by virtue of its skirt, an axial orientation mounting surface for the rotor 6, here mounted by hooping on said surface.
- the external periphery of the support 13 advantageously has, as visible in the embodiment of FIGS. 6 to 9, an abutment shoulder for the sheet metal package of the rotor 6 at its axial end closest to the casing 62 of the engine of the vehicle.
- the fixing of the sheet metal package of the rotor 6 to the mounting surface of the support 13 is carried out by a spline mounting with axial locking by crimping at the other end of the sheet metal package.
- this mounting is carried out by welding or by mounting using screws mounted between leather and flesh as for example in FIG.
- the driver 12 has a second annular part of transverse orientation in the form of a fixing disc 140 provided with holes (not referenced) for the passage of fixing members 145 from the driver 12 to the crankshaft 11.
- the disc 140 rigidly connects the crankshaft 11 to the support 13 and is directed radially towards the axis XX.
- This disc 140 extends perpendicularly to the axis XX and is connected at its external periphery to the axial end of the support 13, at external periphery overall in the form of a skirt, the closest to the motor 62.
- the fixing disc 140 is thicker than the support 13.
- This support 13 extends cantilevered from the disc 140 and is therefore directed axially towards the casing 3.
- the second axial end of the sleeve 13 is free.
- the fixing members 145 consist of screws.
- the support 13 has a constant thickness outside the disc 140 and is therefore generally of tubular shape.
- the thickness of the support 13 is not constant as described below.
- ribs can be provided to reinforce the connection between the support 13 and the disc 140.
- the squirrel cage 60 is located radially outside the driver 12 while being adjacent to the casing 62.
- the coach 12 carries the third part 240 provided with a contour 241, here of axial orientation, for connection by cooperation of shapes with an antagonistic contour 341, here of axial orientation, belonging to a part 4 mounted centering on the periphery external of the centering nose 30 with free closed end of the casing 3.
- the part 4 is annular and of axial orientation.
- the piece 4 axially extends the nose 30 projecting axially to use a casing 3 of the standard type and therefore consists of an axial extension mounted centering on the nose 30 of the casing 3.
- the extension 4 is here of cylindrical shape, while the support 13 hollow delimits a housing into which the opposing contour 341 penetrates.
- the third part 240 is a solid protuberance of axial orientation and of annular shape, the axis of axial symmetry of which is axis XX.
- the protrusion 240 is directed axially towards the casing 3, being taken centrally from the disc 140.
- the protrusion 240 has at its external periphery grooves 241, that is to say an external profile with multiple teeth, constituting the abovementioned contour; alternating teeth and grooves being produced.
- the contour 241 is a contour with a hexagonal profile, a profile with external lobes, such as a profile sold under the brand "TORX". The same is true of the antagonistic internal contour 341.
- the contour 241 and the opposing contour 341 are of axial orientation and consist of grooves or a toothing with multiple teeth.
- One of the contours 241, 341 has projections (the teeth) which penetrate in a complementary manner into hollows (the grooves) of the other contour 341, 241.
- the protrusions and hollows here have a trapezoidal shape.
- the hollow support delimits a housing inside which the contour 241 and the opposing contour 341 penetrate in order to reduce the axial size of the assembly according to the invention.
- the support 13 delimits with the second part 140 of the driver a cavity into which the contours 241, 341 penetrate.
- the rigid driver 12 is here in one piece; its parts 140, 240, 13 being obtained economically, for example by molding.
- the first trainer is here metallic.
- the support 13 and / or the protrusion 240 are attached to rigid attachment to the attachment disc 140, for example by welding or riveting.
- the protrusion 240 is provided centrally with a blind hole.
- the central hole of the protrusion 240 is through so that the second part 140 of the driver 12 consists of a centrally perforated ring.
- the support 13 is axially longer than the rotor 6 and that the protrusion 240.
- the support 13 is longer than the rotor 6 and shorter than the axial protrusion 240 .
- the contour 241 and the antagonistic contour 341 are implanted advantageously at least in major part inside the rotor 6 under it.
- the internal periphery of the support 13 is not machined.
- the driver 12 extends radially inside the air gap 7 of the electric machine 2, which is favorable for reducing the axial size of the assembly of the machine.
- the disc 140 has a centrally located annular recess 212 at its face facing the casing 62 of the vehicle engine. There is thus defined an annular shoulder 213 of axial orientation externally delimiting the recess 212 and making it possible to center the driver 12 on the crankshaft 11. The same is true in all the figures because the crankshaft is not modified.
- the free end 111 of the crankshaft 11 is in the form of a radially projecting ring with a diameter greater than the current part of the crankshaft and has tapped holes for mounting the screws 145.
- This ring 111 is notched at its free end for formation on the one hand, of an annular axial centering surface for the shoulder 213 of the driver 12 and, on the other hand, of a transverse support shoulder for the disc 140 of the driver 12 generally transverse in orientation with respect to the axis XX.
- the driver 12, equipped with the support 13 on which the rotor 6 is fixed, is simply fixed in advance on the crankshaft, that is to say before assembly of the bell 14 to the casing 62.
- the crankshaft 11 is here of the standard type so that its end 111 has a blind cavity centrally centering 112 to receive the nose 30 of the casing 3 in a mounting of the conventional type without an electric machine 2. It will be noted that the centering cavity 112 is delimited by an inlet chamfer to facilitate in a conventional mounting the threading of the nose 30 in the cavity 112.
- the extension 4 is in Figures 2 to 7 of tubular shape and has at one of its ends closest to the casing 62, called the free end, a chamfer 43 to avoid any interference with the heads of the screws 145 and therefore reduce the axial dimension of the assembly comprising the machine 2 interposed axially between the housings 62, 3.
- the other axial end of the extension 4 has, on the one hand, internally a reduction in diameter to form a cylindrical centering surface 42 on the outer periphery of the annular centering nose 30 of the hydrokinetic coupling device and, on the other hand, an annular flange 41 radially projecting outwardly provided with tapped holes for fixing screws 245 with interposition of the central part transverse orientation of a second driver 15 between the head of the screws 245 and the flange 41.
- the internal periphery, that is to say the central part, of the driver 15 is in contact with the face of the flange facing 41 towards the casing of the vehicle; the heads of the screws 245 also being turned towards the casing 62.
- the extension 4 is therefore secured to the second driver 15 by means of the screws 245, which pass through the driver 15 provided with holes for this purpose.
- the internal bore of the extension 4 here has an intermediate portion of smaller diameter for forming the bearing 42 as well as a first portion and a third portion disposed axially on either side of the intermediate portion 42.
- the first portion has the aforementioned contour 341 and extends axially between the free end of the extension 4 and the intermediate portion 42.
- the third portion extends at the level of the collar 41 below the latter.
- the central nose 30 has come from stamping of the casing 3 and has a change in diameter at its free end to form a centering surface for the surface 42 of the extension.
- the nose is cylindrical in shape, being axially oriented and closed at its free end.
- the nose 30 is attached for example by welding to the casing 3. In all cases the casing 3 is sealed.
- the extension 4 has at its outer periphery three portions of increasing diameter, namely a portion of smaller diameter extending above (outside) the contour 341, an intermediate portion of larger diameter extending above the bearing surface 42 and finally a portion of greater diameter constituted by the external periphery of the flange 41.
- the intermediate portion is delimited by the flange 41 of transverse orientation and serves as a centering surface at the internal periphery of the second driver 15 perforated centrally at this effect .
- the second driver 15 is thin and here consists of a disc-shaped plate fixed at its outer periphery to the casing 3.
- the driver 15 has at its outer periphery an outer ring offset axially in the direction of the casing 3 relative to the central part of the driver 15 and in this embodiment have taken advantage of the axial offset of the external ring to fix the latter directly by welding on the metal casing 3 so that the presence of sockets 31 of figure 1 is not compulsory.
- the outer ring is fixed by welding to the sockets 31 so that they are not necessarily threaded and that the driver is in one embodiment of flat shape.
- the axial offset of the external ring of the driver 15 makes it possible to avoid interference with the bun 8 of the stator 5 and therefore to reduce the axial size.
- the sockets 31 are threaded and the attachment of the external ring of the driver 15 to the casing 3 is carried out, in a manner analogous to the embodiments of FIGS. 6 to 9, using fixing members referenced at 45 in these FIGS. 6 to 9, here screws, fixed by screwing onto the threaded bushings 31 that the axially protruding casing 3 carries over the casing 3 above.
- the driver 15, of transverse orientation in this case therefore has holes at its external and internal periphery for the passage of the screws 45 and 245 respectively.
- the external periphery of the second driver 15 is offset axially in the direction of the casing 62 relative to the central part of the driver.
- the second drive 15 is in all cases axially flexible to absorb the axial vibrations and the deformations of the casing 3 due in particular to the swelling of the latter in operation.
- the diameter of the cylindrical centering surface 42 of the extension has an inlet chamfer for the nose 30, the external periphery of which is in intimate contact with the diameter of the surface 42 of the centering device.
- the 4 multifunction extension is an economical and simple to manufacture piece.
- the extension 4 on the one hand, contributes to obtaining a precise air gap 7 and, on the other hand, makes it possible, in combination with the protuberance 240 and the hollow support 13 with an outer periphery in the form of a skirt, to occupy as best as possible the space available at the center of the assembly and of the casing 3.
- the casing 3 has an annular depression 36 at the external periphery of its nose 30.
- the central part of the driver 15 is in contact with the face of the flange 41 facing the casing 3 and more precisely towards the bottom of the annular depression 36.
- the heads of the screws 245 come as close as possible to the bottom of the depression 36.
- the flange 41 of the extension is fixed directly to the outer edge 37 of the depression 36 for example by welding intervening between this edge 37 and the outer periphery of the collar 41.
- the collar 41 locally comes into contact with the bottom of the depression 36.
- the collar 41 is then the drive for the extension 4 which reduces the number of parts.
- the extension 4 is housed in the annular cavity delimited by the support 13, the disc 140 constituting the bottom of the cavity, and the central protuberance 240.
- the mounting is easy because during the assembly of the bell 14 with the casing 62, the female grooves 341 of axial orientation of the extension 4 are threaded onto the male splines of axial orientation complementary to the protuberance 240 so that the extension 4 is linked in rotation by a form-fitting connection to the first driver 12 of the driving type and is connected to the casing 3 via the second driver 15 of the driven type.
- the grooves 341 are of the male type being formed at the external periphery of the extension 4, while the grooves 241 are of the female type being formed in a central cylindrical hole, blind or through, of the protrusion 240 of axial orientation.
- This type of embodiment is visible in Figures 8 and 9.
- the extension 4 is full and has at its axial end adjacent to the flange 41 a blind annular recess 400 for forming the annular bearing surface 42 of axial orientation cooperating with centering with the outer periphery of the nose 30.
- the grooves 241 belong to a torsion damper as described below.
- the diametrical size of the machine 2 depends on the applications and in particular on the power thereof.
- an air gap 7 is obtained which is precise and as small as possible, as well as good mechanical strength of the crankshaft.
- the performance of the machine 2 is increased, the axial vibrations generated by the crankshaft and the deformations in operation of the casing 3 are well filtered.
- an oil sump 163 is located in the lower part of the engine sump 62.
- This oil sump 163 is provided with a projecting transverse flange 164 provided with an opening 165 for in a conventional assembly without a rotating machine 2, access to the elements for fixing the connection plate of the casing 3 to the crankshaft 11.
- the assembly time is reduced in the end because the opposing contour 341 of the extension 4 is threaded integral in rotation with the casing 3 on the contour 241 of the protrusion secured to the driver 12 itself secured to the crankshaft so that the opening 163 is no longer used.
- Machine 2 has several functions. It constitutes a current generator in the form of an alternator for consumers of the vehicle and also a starter for the vehicle. It makes it possible to stop the vehicle engine at red light and then restart it. It also avoids stalling the vehicle engine by providing additional energy for this purpose.
- the machine in one embodiment operates as an auxiliary electric motor for for example driving the compressor of the air conditioning device in rotation when the vehicle is at red light with internal combustion engine stopped.
- the armature windings 8 are therefore connected to an electronic management and control unit receiving information relating in particular to the speed of rotation of the crankshaft 11 or of the casing 3 and that of the input shaft of the gearbox. automatic. All the functions of the machine are described for example in documents FR-A-2 782 355 and WO 98/05882 to which reference may be made.
- the assembly of the rotary electric machine 2 of FIGS. 5 2 and 3 calls for the formation in advance of two assemblies, namely, on the one hand, the assembly on the end 111 of the crankshaft 11 of the first trainer 12 equipped with the protuberance 240 with a contour 241 and of the rotor 6 at the external periphery of the support 13 and, on the other hand, the mounting of the extension 10 4 with a contiguous contour 341 on the casing 3.
- This latter mounting comprising the following steps: a) mounting the extension 4 on the nose 30 by axial threading of the bearing surface 42 on the external periphery of the nose 30 and fixing of the internal periphery of the second driver 15 on the
- Figures 2 to 9 is mounted, on the one hand, the spacer 61 on the housing 62 using the sleeves 161, carried by the spacer 61 or alternatively by the housing 62, and, on the other hand , the driver 12, equipped with the rotor 6 and the protrusion 30 240, on the crankshaft 11 which makes assembly easier later on because the spacer is carried by the casing 62 so that the bell 14 is less heavy.
- the spacer 61 is fixed to the bell 14 and the casing 62 using screws or bolts, not shown.
- the spacer 61-stator 5 assembly is mounted on the bell 14 by axial threading of the spacer 61 on the centering sleeves 161, preferably diametrically opposite, carried by the bell 14 or the spacer 61. It will be noted that advantage is taken of the axial clearances within the hydrokinetic coupling device so that the casing 3 can move axially.
- centering sleeves 161 are carried by the casing 62, 3 or the spacer 61.
- a series of the sleeves is carried by the spacer and the other series by one of the casing elements 62-bell 14. All combinations are possible; the sockets 161 entering a complementary calibrated passage preferably provided with an inlet chamfer.
- the flange 41 has at least one centering pin penetrating a complementary hole in the driver 15 for the positioning of this driver 15 on the extension 4 and then facilitating the fixing of the screws 245.
- the end 111 of the crankshaft 11 has in one embodiment at least one centering pin penetrating in a complementary manner into a hole in the disc 140 of the driver 12 for. mounting this coach 12 on the end 111 and facilitating the mounting of the screws 145.
- the pins engage in associated holes for formation of polarizers. Any other form of polarizing device, forming angular indexing means between the parts concerned, is conceivable.
- the screws 245 and 145 are installed here on an average circumference of the same diameter. It will be noted that the lock washers can be associated with the screws 145 and 345 as visible for example in FIGS. 6 to. 9. As a variant, instead of screws 45, 145, 245, nuts can be used which are screwed onto threaded rods carried in axial projection respectively by the sockets 31, the free end 111 of the crankshaft and the flange 41. The above-mentioned fixings are removable . As a variant, the screws 145 and / or 245 are replaced by non-removable fasteners, for example by riveting or welding.
- one of the fasteners 45, 145, 245 is removable and all the others cannot be dismantled.
- all the fixings are removable.
- the attachment of the driver 12 to the end 111 is carried out using a single central screw.
- the external periphery of the rotor 6 extends over a circumference of diameter generally equal to the mean diameter of the implantation circumference of the screws 45 and of the sockets 31.
- the external periphery of the rotor 6 extends over a circumference of diameter less than the average diameter of the implantation circumference of the screws 45 and of the sockets 31.
- the external periphery of the rotor 6 extends over a circumference of diameter less than the average diameter of one external peripheral ring of the second driver 15.
- the rotor 6 is implanted at least for the most part radially below (inside) the average diameter of the circumference of implantation of the screws 45 and of the sockets 31 or of the external peripheral ring of the second driver 15 so that the inertia of the rotor is reduced as well as the mass of the support 13.
- the casing 3 carries a target 32 for example for sensing the speed of rotation of the casing 3 and therefore of the crankshaft 11 or for adjusting the ignition of the vehicle or for controlling the engine of the motor vehicle.
- the target 32 is associated with a sensor sending information to the electronic control and management unit of the windings 8 of the stator 5. It can be the same in the other figures.
- the spacer 61 is mounted for centering on a centering web 600 extending transversely with respect to the axis XX of axial symmetry of the assembly according to the invention.
- This veil 600 is perforated centrally for passage of the extension 4 and has at its outer periphery calibrated holes 601 for mounting the centering sleeves 161 secured to the spacer 61.
- the sleeves are carried by the bell 14 or by the bell 14 and the spacer 61.
- the veil also has other holes not visible for the passage of the fastening members of the spacer 61 to the bell 14.
- this web 600 has a cylindrical hub 602 of axial orientation directed towards the casing 62 and therefore towards the free end of the extension 4.
- the hub 602 is axially shorter than the extension 4.
- the internal periphery of the hub 602 serves as a mounting surface for a bearing 603 acting radially, that is to say radially interposed, between the external periphery of the extension 4 and the internal periphery of hub 602.
- the bearing 603 is in one embodiment a smooth bearing.
- it is a ball bearing with a row of balls; alternatively with two rows of balls.
- the extension 4 has an abutment shoulder (not referenced) at its outer periphery for axial setting in one direction of the inner ring of the bearing 603.
- the abutment shoulder is formed by means of a variation in diameter at the periphery external of the extension 4. The position of this shoulder is determined to avoid any interference between the internal periphery of the centering web 600 and the flange 41 of the extension 4.
- a circlip (not referenced) is mounted in a groove made at the periphery outer of the extension 4 for axial setting in the other direction of the inner ring of the bearing 603.
- the hub 602 has at its end furthest from the flange 41 a transverse flange 604 directed towards the axis XX and forming a stop shoulder for axially wedging in one direction the outer ring of the ball bearing 603. In the other axial direction the outer ring of the bearing 603 is wedged by a circlip (not referenced) mount in a groove made at the periphery internal hub 602.
- circlips it is possible to use circlips to wedge the rings of the bearing 603 axially in both directions.
- the flange 604 is attached by welding to the hub 602.
- the outer ring of the bearing 603 is in one piece with the hub 602.
- the spacer 61 and the extension 4 are well positioned so that the air gap 7 is even more precise.
- the assembly is carried out in the aforementioned manner by mounting in advance the spacer 61 on the casing 62 and the rotor 6 - support 13 - driver 12 assembly on the crankshaft.
- the driver 15 is mounted on the flange 41 using the screws 245, then the outer periphery of the driver 15 is fixed to the sockets 31 using the screws 45.
- angular indexing means such as pins coming from one of the sail 600-bell 14 elements penetrating into calibrated holes of the other of the 14-sail 600 bell elements , intervene between the bell 14 and the web 600 so that the sockets 161 can penetrate the holes of the web 600.
- the free end of the extension 4 has in FIGS. 6 and 7 an external diameter smaller than the external diameter of the extension 4 defining a mounting range for the external ring of the bearing 603. It is the same in FIGS. 8 and 9 In these figures the free end of the extension 4 has at its outer periphery grooves of the male type 341 penetrating into grooves 241 of the female type formed at the inner periphery of a protuberance 200.
- the protuberance 2400 here consists of a hub internally having the grooves 241.
- the hub 2400 is located inside the support 13 and therefore of the rotor 6. This hub 2400 is axially oriented and constitutes the outlet part of the torsional damper 700.
- the inlet part of the damper torsion 700 consists of two guide washers 702 disposed on either side of a hub web 701 secured to the hub 2400.
- the guide washers 702 surround the hub 2400, so that a relative rotational movement is allowed between the hub and the guide washers.
- the web 701 is in one piece with the hub 2400.
- the web 701 is fixed to its internal periphery by welding or crimping on the hub 2400.
- annular centering bearing acts radially between the hub and a first of the guide washers.
- This bearing also advantageously intervenes axially between this first guide washer and the web 701 and has for this purpose an annular part of transverse orientation.
- elastic means with axial action such as a Belleville washer or a wavy washer, intervene between the second guide washer and the web 701 to urge a friction washer in contact with the web 701 and tighten the transverse part of the bearing. between the first guide washer and the web.
- a distribution washer linked in rotation to the second guide washer for example using axial tabs penetrating holes in the second guide washer are provided; said elastic axial action means being axially interposed between the second guide washer and the distribution washer, which in one embodiment serves as a support for the friction washer or constitutes the friction washer. Friction and / or centering means can therefore intervene between the web 701-hub 2400 assembly and the guide washers 702.
- the veil 701 and the guide washers 702 have opposite openings, here windows, for the accommodation of elastic members 705 with circumferential action.
- the windows are located tangentially; the internal edges of the windows being located tangentially with respect to the same internal circumference.
- the elastic members 705 here consist of coil springs. As a variant, at least some of these members 705 consist of blocks of elastic material.
- the windows of the guide washers 702 and of the web 701 have in one embodiment the same size.
- the elastic members 705 are mounted without play in the windows of the guide washers 702, without play in certain windows of the web 701 and with play in other windows of the web 701 for a staggered intervention of the elastic bodies 705.
- the openings for housing the members 705 are open towards the outside and the elastic members 705 are curved springs.
- the rigid support 13 has internally thickeners 706 connecting at one of their axial ends to the disc 140 of the driver 12.
- the thickeners define at their other free axial end a transverse shoulder for support of the outer periphery of a first guide washer 702 integral with the second guide washer.
- axial spacers 704 in the form of a bushing are interposed axially between the two guide washers 702. These spacers are located at the periphery. outer of the guide washers 702 and are each traversed by a screw 703.
- the head of the screw 703 bears on the second guide washer 702; its threaded part passing through the second guide washer 702, the spacer concerned 704 and the first guide washer 702 to be screwed into a thread made in the extra thickness 706 concerned.
- the screws 703 thus ensure the fixing of the guide washers on the extra thicknesses 706, the first guide washer 702 being in abutment on the shoulders of the extra thicknesses 706.
- the protuberance 2400 is connected elastically to the rigid support 13.
- the damper 700 is mounted inside the support 13 and the rotor 6 while being located axially between the axial end faces of the rotor 6.
- the first coach 12 is simplified; the disc 140 consisting of a simple ring carrying the support 13 at its external periphery.
- the guide washers 702 are secured to the hub 2400 and the web 701 is secured to the extra thicknesses 706, for example by screwing using screws 703.
- the elastic members 705 are eliminated and the web 701, secured to the hub 2400 , is fixed directly to the extra thicknesses 706 using screws 703.
- the protuberance 2400 in the form of a hub is therefore rigidly or resiliently connected, via a torsional damper with circumferential action, to the rigid support 13. This protuberance is installed radially inside the rotor 6 and axially advantageously between the axial end faces of the rotor.
- protuberance 240, 2400 is therefore rigidly or resiliently linked to the first driver 12, namely to the disc 140 or to the support 13.
- cooperation link 241, 341 extends axially more distant from the disc 140.
- this link extends mainly outside the support 13.
- This solution is less advantageous because it increases the axial size, in particular of the spacer 61.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)
- Motor Or Generator Frames (AREA)
- Manufacture Of Motors, Generators (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2004-7015226A KR20040098024A (ko) | 2002-03-28 | 2003-03-19 | 차량용 전기회전기계 조립체 |
JP2003580703A JP2005521831A (ja) | 2002-03-28 | 2003-03-19 | 自動車用の回転電気機械の取付方法 |
DE60322204T DE60322204D1 (de) | 2002-03-28 | 2003-03-19 | Montage einer rotierenden elektrischen maschine für ein automobil-fahrzeug |
EP03725305A EP1497554B1 (fr) | 2002-03-28 | 2003-03-19 | Montage de machine electrique tournante pour vehicule automobile |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR02/03890 | 2002-03-28 | ||
FR0203890A FR2837755B1 (fr) | 2002-03-28 | 2002-03-28 | Montage de machine electrique tournante pour vehicule automobile |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003083287A1 true WO2003083287A1 (fr) | 2003-10-09 |
Family
ID=27839272
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2003/000866 WO2003083287A1 (fr) | 2002-03-28 | 2003-03-19 | Montage de machine electrique tournante pour vehicule automobile |
Country Status (8)
Country | Link |
---|---|
EP (1) | EP1497554B1 (fr) |
JP (1) | JP2005521831A (fr) |
KR (1) | KR20040098024A (fr) |
AT (1) | ATE401499T1 (fr) |
DE (1) | DE60322204D1 (fr) |
ES (1) | ES2310657T3 (fr) |
FR (1) | FR2837755B1 (fr) |
WO (1) | WO2003083287A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015172918A1 (fr) * | 2014-05-14 | 2015-11-19 | Robert Bosch Gmbh | Système d'entraînement pour un véhicule automobile hybride |
EP2662957B1 (fr) * | 2012-02-22 | 2022-01-26 | MAN Truck & Bus SE | Agencement comprenant un moteur à combustion |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2881587A1 (fr) * | 2005-02-01 | 2006-08-04 | Peugeot Citroen Automobiles Sa | Dispositif permettant le refroidissement d'une machine electrique tournante par circulation d'un fluide de refroidissement |
DE102005040647A1 (de) * | 2005-08-27 | 2007-03-08 | Valeo Systèmes d`Essuyage | Elektromotorischer Hilfsantrieb für Fahrzeuge |
JP6493250B2 (ja) * | 2016-02-25 | 2019-04-03 | 株式会社豊田自動織機 | モータ組み付け治具及びモータ組み付け方法 |
KR101765645B1 (ko) | 2016-10-24 | 2017-08-07 | 현대자동차 주식회사 | 하이브리드 변속기용 엔진 클러치의 모터 연결구조 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB456039A (en) * | 1934-12-21 | 1936-11-02 | Porsche Gmbh | An improved arrangement of the lighting dynamo or starting motor, more especially for automobiles |
JPS63309768A (ja) * | 1987-06-10 | 1988-12-16 | Mazda Motor Corp | エンジンの始動充電装置 |
EP0901923A2 (fr) * | 1997-09-12 | 1999-03-17 | Honda Giken Kogyo Kabushiki Kaisha | Dispositif de propulsion pour véhicule hybride |
FR2782355A1 (fr) | 1998-07-28 | 2000-02-18 | Valeo Equip Electr Moteur | Embrayage a friction portant le rotor d'une machine electrique, notamment pour vehicule automobile |
US20010015586A1 (en) * | 1999-12-29 | 2001-08-23 | Francois Honorio | Attachment device for electrical equipment, such as an alternator/starter motor, in a clutch housing of an automobile |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19631384C1 (de) | 1996-08-02 | 1997-10-16 | Clouth Gummiwerke Ag | Elektrische Maschine in einem Antriebsstrang, z. B. eines Kraftfahrzeuges |
-
2002
- 2002-03-28 FR FR0203890A patent/FR2837755B1/fr not_active Expired - Fee Related
-
2003
- 2003-03-19 ES ES03725305T patent/ES2310657T3/es not_active Expired - Lifetime
- 2003-03-19 JP JP2003580703A patent/JP2005521831A/ja active Pending
- 2003-03-19 KR KR10-2004-7015226A patent/KR20040098024A/ko not_active Application Discontinuation
- 2003-03-19 WO PCT/FR2003/000866 patent/WO2003083287A1/fr active IP Right Grant
- 2003-03-19 DE DE60322204T patent/DE60322204D1/de not_active Expired - Lifetime
- 2003-03-19 EP EP03725305A patent/EP1497554B1/fr not_active Expired - Lifetime
- 2003-03-19 AT AT03725305T patent/ATE401499T1/de not_active IP Right Cessation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB456039A (en) * | 1934-12-21 | 1936-11-02 | Porsche Gmbh | An improved arrangement of the lighting dynamo or starting motor, more especially for automobiles |
JPS63309768A (ja) * | 1987-06-10 | 1988-12-16 | Mazda Motor Corp | エンジンの始動充電装置 |
EP0901923A2 (fr) * | 1997-09-12 | 1999-03-17 | Honda Giken Kogyo Kabushiki Kaisha | Dispositif de propulsion pour véhicule hybride |
FR2782355A1 (fr) | 1998-07-28 | 2000-02-18 | Valeo Equip Electr Moteur | Embrayage a friction portant le rotor d'une machine electrique, notamment pour vehicule automobile |
US20010015586A1 (en) * | 1999-12-29 | 2001-08-23 | Francois Honorio | Attachment device for electrical equipment, such as an alternator/starter motor, in a clutch housing of an automobile |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 013, no. 148 (M - 812) 11 April 1989 (1989-04-11) * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2662957B1 (fr) * | 2012-02-22 | 2022-01-26 | MAN Truck & Bus SE | Agencement comprenant un moteur à combustion |
WO2015172918A1 (fr) * | 2014-05-14 | 2015-11-19 | Robert Bosch Gmbh | Système d'entraînement pour un véhicule automobile hybride |
Also Published As
Publication number | Publication date |
---|---|
KR20040098024A (ko) | 2004-11-18 |
ATE401499T1 (de) | 2008-08-15 |
JP2005521831A (ja) | 2005-07-21 |
ES2310657T3 (es) | 2009-01-16 |
DE60322204D1 (de) | 2008-08-28 |
FR2837755B1 (fr) | 2004-08-27 |
EP1497554B1 (fr) | 2008-07-16 |
EP1497554A1 (fr) | 2005-01-19 |
FR2837755A1 (fr) | 2003-10-03 |
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