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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
  • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type

Definitions

• the present invention relates to an electrical machine which can be switched as a starter and generator for an internal combustion engine, in particular an internal combustion engine of a motor vehicle.
• Such machines have been developed because they enable the two functions of starting the internal combustion engine and generating electric current that are required for the on-board systems of a vehicle, such as ignition, lighting, etc., to be carried out in a single electric machine unite and thus save weight and costs.
• a two-stage planetary gear is known from DE 36 04 395 AI. This document teaches the use of such a transmission in an automatic transmission of a motor vehicle for setting different transmission ratios which correspond to the different gears of a gear shift and act on the chassis of the motor vehicle.
• the power transmission takes place constantly in one direction, namely from the internal combustion engine to the chassis. The document does not provide information on the starter or alternator of the vehicle.
• a two-stage planetary gear is known from DE 19 531 043 AI.
• the planetary gear dealt with in this document is provided in order to be driven by a motor, in particular a motor of an electrically operated tool such as a drilling machine, and to drive a tool with an adjustable translation. Only one of the two stages is assigned a locking device which can prevent any rotation of the ring gear of this stage.
• the present invention creates an electrical machine for use as a starter or generator for an internal combustion engine, which can be switched over easily with gear ratios optimally adapted to the operation of the electrical machine as a starter or as a generator Funds allowed.
• Desirable gear ratios are for
• Machine a gear ratio range from 1.6 to 4 for generator operation or from 4 to 60 in starter operation.
• the spread that is to say the ratio of the gear ratios to one another, should be at least 2.
• the braking force can be exerted in a simple manner, in particular by engaging a braking device on a ring gear of the planetary gear.
• Brake devices in particular include shoe brakes, multi-disk brakes or friction band brakes.
• the planetary gear comprises two fixedly connected to the internal combustion engine shaft. dene sun gears and two sets of each meshing with one of the sun gears and a ring gear planet gears, and the planet gears of both sets are rotatably mounted on a planet carrier, which in turn is fixedly connected to a starter or generator shaft to a rotational movement on the generator shaft or of the Transfer generator shaft to the planet carrier.
• a rotational force can be transmitted between the sun gear of the braked stage of the two-stage transmission and the planet carrier, while the other stage rotates freely.
• This construction enables a particularly compact structure in which the dimensions of the two ring gears are identical. This reduces the number of different components of the gearbox required and enables more efficient and cost-effective production.
• the planetary gear comprises two sun gears, one of which is permanently connected to the internal combustion engine shaft or the starter or generator shaft, and two sets of planet gears meshing with one of the sun gears and one ring gear.
• the planetary wheels of the two sets connected in pairs on a common axis in a rotationally fixed manner.
• the ring gear of a step can be omitted.
• the two-stage planetary gear comprises two sun gears, one of which is permanently connected to the internal combustion engine shaft or a starter or generator shaft, and two sets of planet gears meshing with one of the sun gears, the planet gears of the two sets in pairs comb together.
• Such a planetary gear requires only a ring gear.
• the second brake device preferably does not engage a ring gear, but is designed to block the planetary movement of the planet gears, that is to say their rotation around the shafts.
• the planet gears of both sets are preferably rotatably mounted on a common planet carrier, and the second braking device acts on this planet carrier.
• a common actuating device is preferably Direction for actuating both braking devices is provided, which has at least one working position in which the first braking device is open and the second is closed, a working position in which the second braking device is open and the first is closed, and an idle position in which both are open.
• These positions can be set by a control element that can be moved with one degree of freedom.
• This degree of freedom is preferably a rotation, so that the actuating device can be actuated easily, for example with the aid of any conventional electric motor.
• the adjusting device can preferably be moved from one working position to the other via the idle position.
• the actuating device can be moved beyond a working position into a braking position in which the braking device which is open in the working position is braked.
• "Braked” is understood to mean a state of the braking device in which the braking torque is different from zero, but is limited to such an extent that the transmission and the drive are overloaded. strand is excluded.
• the actuating device should only allow the complete closing of a braking device if the other braking device is not also closed at the same time.
• the adjusting device in which the braking devices can be actuated by adjusting movements parallel to an axis of the transmission, the adjusting device comprises two ramps which can be rotated about this axis for converting a rotary movement into an adjusting movement of the braking devices.
• the two ramps are connected in a rotationally fixed manner.
• Such an adjusting device is particularly suitable for use with multi-disc brakes as braking devices.
• the actuating device in which the braking devices can be actuated by an actuating movement perpendicular to an axis of the transmission, has at least one cam disk and levers interacting with the cam disk for converting a rotation of the cam disk into an actuating movement of the braking devices.
• each lever and thus each braking device can also be assigned its own cam disk. These outcomes staltung is particularly suitable for use in conjunction with shoe brakes as braking devices.
• 1, 2, 2a and 3 show schemes of configurations of planetary gears of the machine according to the invention
• Figure 4 shows a longitudinal section through a transmission according to the first embodiment
• FIG. 5 shows a section along the line V-V in FIG. 4.
• FIG. 6 shows an axial section through a transmission of the machine according to the invention with two multi-disc brakes and a common adjusting device for the two multi-disc brakes
• FIG. 7 shows a perspective view of an adjusting ring of the adjusting device from FIG. 6, which has two ramps for adjusting a multi-disc brake in different operating positions;
• FIG. 8 shows a graphical representation of the axial displacement of the multi-disc brakes as a function of the orientation of the adjusting ring
• FIGS. 9 and 10 each show views of an adjusting device for jointly setting two multi-disc brakes
• FIG. 11 shows a perspective view of a shoe brake
• Figure 12 is a schematic representation of the interaction of the shoe brake with a control element
• FIG. 13 shows a side view of a transmission which is equipped with two shoe brakes according to FIG. 11 and an adjusting device according to FIG. 12;
• FIG. 14 shows a schematic illustration of the arrangement of the machine according to the invention in the drive train of a motor vehicle. Description of the embodiments
• FIG. 14 the arrangement of an electrical machine according to the invention in the drive train of a motor vehicle is first briefly illustrated using FIG. 14.
• This drive train comprises an internal combustion engine 30 which can be connected via a main clutch 31 to a manual transmission 32 which drives 37 wheels of the motor vehicle with various adjustable transmission ratios via an output shaft.
• An internal combustion engine machine shaft 4 passes through the manual transmission 32 and is connected to the transmission 33 of the electrical machine according to the invention.
• the gear 33 has two stages, each gear stage 34 i , 34 ii is a separate braking device 35 i; 35 1L assigned. With the aid of the braking devices, the transmission ratio between the shaft 4 and a shaft 6, which is connected to an electrical machine 36, can be set.
• One of the two transmission ratios of the transmission 33 is provided for the operation of the electrical machine 36 as a starter of the internal combustion engine 30 and the other for the operation as an alternator.
• Different configurations of gears 33 are now dealt with on the basis of FIGS. 1, 2, 2A and 3.
• Figures 1 to 3 show highly schematic axial sections through gears.
• Short horizontal lines 10 each represent the toothing of a gearwheel. Two such lines are connected by a vertical line 11, which symbolizes the disk of the gearwheel.
• An open circle 12 in the middle of line 11 indicates that the gear in question is freely rotatable about an axis, which is symbolized by a horizontal line running through circle 12.
• a closed round point 13 represents a fixed connection between the gear in question and its axis.
• the internal combustion engine is coupled via a shaft 4 to a planet carrier 5, which rotatably holds planet wheels 2 1 , 2 2 of the two stages of the planetary gear.
• These planet gears each mesh with a sun gear 1 or 1 X1 and a ring gear 3 or 3 x ⁇ .
• the sun gears are on one fixed to the (not shown) electrical machine shaft 6 mounted.
• a braking device (not shown in FIG. 1) engages on an outer surface 8 i; B i one of the ring gears 3 ⁇ 3 ⁇ and prevents this from rotating while the other ring gear is freely movable.
• FIG. 4 shows the structure of the two-stage planetary gear from FIG. 1 in one for illustration detailed axial section.
• the shaft 4 connected to the internal combustion engine carries a planet carrier 20 in the form of a plate-like flange, on the outer edge of which three pins 21 x (see also FIG. 5) are let in at an angular distance of 120 °, which are the axes of rotation of the planet wheels 2 X of the first gear stage define.
• the disks 22 ⁇ of the planet gears 2 have only a fraction of the axial dimension of the teeth and are also broken through in order to keep the moment of inertia of the wheels as low as possible.
• the ring gear 3 X is screwed to a flange 23, which has a cylindrical projection 24 as an engagement surface for a braking device.
• the planet carrier 20 has an arm 27 projecting over the axial width of the first geurium stage, at the end of which a further pin 21 1 is anchored, each of which carries a planet gear 2 X1 of the second gear stage.
• a flange 25 fixedly connected to the ring gear 3 X1 forms a carrier for plates 26 of a plate brake.
• FIG. 5 shows a simplified cross section along the line VV from FIG. 4.
• the gearwheels 1 x , 2 L , 3 X of the first stage are shown in section, the sun gear 1 , is partially covered.
• the arms 27 of the planet carrier 20 which hold the planet gears 2 1X of the second stage.
• the dimensions of the ring gear 3 xl of the second stage are identical to those of the ring gear 3 X of the first.
• the suns are in Figure 5 with 1. and 1 ,. designated.
• Figure 2 shows the diagram of a second embodiment of a two-stage planetary gear for an electrical machine according to the invention.
• the shafts 4 and 6 connected to the internal combustion engine and the electrical machine are each firmly connected to a sun gear l x and l lx .
• Planet gears 2 1 and 2 1X of the two stages are firmly coupled to one another by a common axis 7.
• basically three different transmission ratios can be set, two of them by locking a ring gear each and the third by locking the planetary movement, that is to say holding the axes 7 of the pairs of planet gears.
• the gear ratios are given by the formulas
• a braking device can be used which exerts a force in the axial direction on the ends of the axes 7, as indicated by the arrows 9 in FIG. 2, and so on the axes a planetary movement, but does not prevent the planet wheels from rotating about the axes.
• FIG. 2a A modification is shown in FIG. 2a.
• braking devices of the same type can be used to brake the movement of the axes 7 as well as the rotation of the ring gear 3 X , which simplifies the construction.
• the shaft 4 of the internal combustion engine is firmly connected to a large sun gear 1, which meshes with the planet gears 2 1 .
• a large sun gear 1 which meshes with the planet gears 2 1 .
• These are rotatably mounted on a planet carrier 20 ′′ and mesh with planet gears 2 X of the second stage, which are mounted on the same carrier 20 ′′.
• the latter are in engagement with a small sun gear l 1 which is coupled via a shaft 6 to an electrical machine provided as a starter or generator of the motor vehicle.
• the gearbox has two gear ratios. In the first, the ring gear 3 XX of the second stage is fixed, in the second it is the planet carrier 20 ′′.
• the planet carrier 20 ′′ holds the planet gears 2 XX of the second stage with the aid of arms which are partially cranked outside the sectional plane of the figure in the direction of the planetary movement, which is indicated in the figure by a broken line.
• the planet carrier 20 ′′ can be locked by a brake acting on a cylindrical outer surface 8.
• the following table shows gear ratios ü ⁇ ü j of the two gear ratios for different numbers of teeth Z of the different wheels.
• gear ratios in the appropriate range and spreads of 2 or significantly higher with moderate number of teeth and consequently with an overall compact gear can be achieved.
• FIG. 6 shows in axial section a gear 33 with two multi-disc brakes 35 ⁇ , 35 ⁇ ; L and an actuating device for actuating the two multi-disc brakes together.
• the structure of the transmission corresponds to that of Figure 1 and will not be described again in detail.
• the disk brakes 35 ⁇ 35 ⁇ each comprise a disk set connected to a ring gear 3 1 , 3 ll and a disk set connected to an axially displaceable carrier 40.
• the displaceable plate set is pressed by a spring (not shown) against an adjusting ring 41, which FIG. 7 shows in a perspective view.
• the adjusting ring 41 is axially clamped between the lamellae and a set of fixed rollers 42 by the force of the spring.
• the adjusting ring 41 carries two ramps 43 extending in the circumferential direction, on the surface of which a roller 42 runs when the adjusting ring 41 is rotated about the shaft 4 or 6.
• the disk carriers 40 are axially displaced to different extents, that is to say the brake is applied to different extents.
• the two adjusting rings 41 are connected via a bridge 44 to a telescopic mechanism in a rotationally fixed but axially displaceable manner.
• One of the adjusting rings 41 has on its outer periphery a ring gear which meshes with a pinion 45 which is driven by a motor 46 via a reduction gear 47.
• the ring gear extends over an angular segment, the size of which corresponds at least to the angle spanned by each ramp 43.
• FIG. 9 shows a perspective view of the adjusting device from FIG. 6 and the geared motor arrangement 46, 47.
• the ring gear has the shape of a segment 48 fixedly mounted on an adjusting ring 41, from which the bridge 44 to the second adjusting ring 41 also extends.
• the bridge 44 consists of two interlocking, axially rail-guided elements.
• the components 41 to 45 and 48 can be regarded as a single adjusting device which, by simply rotating the pinion 45, allows the braking devices 35 ⁇ 35 ⁇ to be brought into different positions in a coupled manner.
• FIG. 8 shows an example of a possible height profile of the ramps 43 of the two adjusting rings 41 from FIG. 6 along their circumference.
• the lower curve corresponds to the collar shown in FIG. 7.
• Corresponding positions of the adjusting ring 41 in FIGS. 7 and 8 are each identified by letters a to e.
• the circles on the curves in positions a to e each symbolize the roller 42 assigned to the ramp in different positions of its path.
• the ramp from FIG. 7 has a height h a (see lower curve in FIG. 8) at which the assigned braking device brakes but does not block completely.
• the braking device is open.
• Figure 10 shows schematically a variant of an actuating device.
• the adjusting rings 41 are both serrated on at least part of their outer circumference and mesh with pinions 45, which, mounted on a common shaft 49, are driven by the motor 46.
• the width of the pinion or the teeth of the adjusting wheels 42 is dimensioned such that the adjusting wheels are selectively move the ramps (not shown in this figure) with the braking devices axially, without coming out of engagement with the pinions 45.
• FIG. 50 A second embodiment of a braking device, in the form of a shoe brake, is shown in FIG.
• This shoe brake designated by the reference numeral 50, comprises two arms 51 which can be pivoted about axes 52 which are stationary in relation to the gear 33 (not shown here).
• Each arm 51 carries a brake shoe 53.
• a tension spring 49 exerts a force on the arms 51 which acts to open the brake.
• the arms 51 have at their ends opposite, tapering triangular lugs 54.
• An adjusting lever 55 is about a stationary axis 58 pivotable and carries on a first arm 57 a rider 59 with a recess in which the lugs 54 engage.
• the rider 59 can be moved in the direction of arrow A by a pivoting movement of the actuating lever 55 perpendicular to the axis of the transmission.
• the second arm 56 of the actuating lever 55 interacts, as shown in FIG. 12, with a cam disk 60 and thus determines the height of the rider 59 on the lugs 54.
• the cam disk 60 In order to make the profile of the cam disk more recognizable, it is about its center of rotation dash-dotted circle, the radius of which is equal to the maximum radius of the cam disk. The further the rider 59 in FIG. 11 is pressed down, the more the brake shoes 53 press against the (not shown) ring gear of the transmission arranged between them.
• the cam disk 60 can (like the adjusting ring of the previously described embodiments) assume positions which are denoted by letters a to e in FIG. 12 and correspond to the open, closed or braked states of the shoe brake 50 in the same way as the above-described states.
• Figure 13 shows a side view of a transmission 33 with two shoe brakes 50 ⁇ 50 ⁇ with the structure described above, which are each assigned to the two stages 34 i , 35 ii of the transmission.
• Two cam disks are on a common shaft 49 connected to an actuator 46.
• the two cam disks are identically shaped, but arranged in mirror image to one another, so that in the position shown in FIG. 13 a second lever 56 is lowered, the associated shoe brake 50. thus open, and the other second lever arm 56 lx raised, the shoe brake 50 1X is closed accordingly.
• each control lever is assigned its own cam disk ⁇ ü ⁇ öO ⁇ .
• the two actuating levers engage on a common cam disk with an offset angle.

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

Priority Applications (5)

Applications Claiming Priority (4)

Publications (1)

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Families Citing this family (42)

Citations (6)

Family Cites Families (12)

• 1999
  • 1999-11-04 BR BR9906923-7A patent/BR9906923A/pt not_active IP Right Cessation
  • 1999-11-04 JP JP2000582709A patent/JP4582607B2/ja not_active Expired - Fee Related
  • 1999-11-04 WO PCT/DE1999/003522 patent/WO2000029744A1/de not_active Ceased
  • 1999-11-04 US US09/600,089 patent/US6409622B1/en not_active Expired - Fee Related
  • 1999-11-04 EP EP99963199A patent/EP1047874B1/de not_active Expired - Lifetime

Patent Citations (6)

Non-Patent Citations (1)

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