EP1524430B1 - Démarreur-générateur muni d'une roue libre auto-inverseuse - Google Patents

Démarreur-générateur muni d'une roue libre auto-inverseuse Download PDF

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Publication number
EP1524430B1
EP1524430B1 EP20040022895 EP04022895A EP1524430B1 EP 1524430 B1 EP1524430 B1 EP 1524430B1 EP 20040022895 EP20040022895 EP 20040022895 EP 04022895 A EP04022895 A EP 04022895A EP 1524430 B1 EP1524430 B1 EP 1524430B1
Authority
EP
European Patent Office
Prior art keywords
hub
shaft
pulley
springs
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20040022895
Other languages
German (de)
English (en)
Other versions
EP1524430A3 (fr
EP1524430A2 (fr
Inventor
Manfred Ahner
Manfred Ackermann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1524430A2 publication Critical patent/EP1524430A2/fr
Publication of EP1524430A3 publication Critical patent/EP1524430A3/fr
Application granted granted Critical
Publication of EP1524430B1 publication Critical patent/EP1524430B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
    • F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning 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
    • 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 invention relates to a starter with pulley, arranged inside the pulley shaft and a freewheel which has loaded by means of a spring device clamping body, with the features mentioned in the preamble of claim 1.
  • Belt-driven starter generators for internal combustion engines of the generic type are known. They are a favored variant for a low-leakage start system, which is used in vehicles with automatic start-stop, because the occurring here tenfold the startup operations of the conventional single-track starter can not be used.
  • WO 01/77520 A1 and WO 01/88369 A1 discloses devices for coupling a belt-driven starter generator with an internal combustion engine. These have a planetary gear with a sun gear, wherein the switching takes place at torque reversal active by coupling elements.
  • Pulleys with freewheel, shortly belt freewheel disks are also described in the prior art. They have a free-running ring and clamping body with a spring device. These pulleys with freewheel described in the prior art can but are not used for the belt-driven starter generator, since when using the belt-driven starter generator in starter mode, ie as a motor to start an internal combustion engine, the torque in the opposite direction to the torque in generator mode, ie when the engine is running occurs.
  • the starter generator according to the invention with the features mentioned in claim 1 offers the advantage over that the function of the known freewheeling pulley is fulfilled in the generator mode and opposite torques are transmitted in the starter operation.
  • This is achieved by using a double freewheel in the belt-driven starter generator.
  • the double freewheel has pairs of mutually associated clamping body, between which the spring device is arranged.
  • the clamping body cooperate with different clamping gaps.
  • the clamping bodies between the hub and the pulley are arranged with a control cage, which is coupled to the pulley.
  • the coupling of the control cage takes place with the pulley by means of friction elements. Through this coupling, the switching of the double freewheel with torque reversal takes place.
  • the advantage of a coupling by means of friction elements is that the coupling is not rigid, but is operatively connected. On the other hand, it is so rigid that with a movement of the pulley, the control cage performs the same movement as the pulley. When the direction of the pulley turns, so does the direction of movement of the control cage around.
  • the springs of the spring coupling between shaft and hub have different stiffnesses.
  • an angle range is connected upstream, which can transmit only small torques.
  • This difference angle arises in particular at the start of the internal combustion engine and results from the non-uniform rotational speed of the internal combustion engine and from the, under its inertial mass uniformly rotating, starter generator. This nonuniformity is considerable only at the beginning of the starting process and decreases with increasing speed of the internal combustion engine.
  • the springs are designed as spiral springs. The advantage here is that despite a small space, a large impact force is achieved.
  • damping chambers which are filled with at least one medium may also be present. These damping chambers are formed between the driver of the shaft and the inner contour of the hub. They act like throttles. As a medium here gases with different compressibility properties or liquids with different viscosities can be used.
  • the clearance angle of the spring coupling can be adjusted, namely by connecting in series of at least two hubs with drivers and associated springs.
  • the geometric series connection of the hubs with drivers and associated springs can take place both on the axis of the shaft one behind the other, ie axially, as well as coaxially.
  • Coaxial here means annularly arranged around the shaft scars.
  • each of the inner hub represents the shaft for the next hub, so that multiple pairs of hub and shaft are realized with springs arranged therebetween. It is possible to increase the clearance angle by using different springs with different stiffness
  • FIG. 1 shows an arrangement of a starter generator 1 with a shaft 3, which has a shaft axis 4 and is connected to the starter generator 1.
  • the shaft 3 is part of a device 5, of which only a pulley 7 is shown in this figure.
  • the pulley 7 is connected by means of a belt 9 with a pulley 11 of an internal combustion engine 15.
  • the pulley 11 is connected to the engine 15 through a shaft 13.
  • FIG. 2 is the starter generator 1 according to the invention with the device 5 along the line II of FIG FIG. 1 shown arrangement shown. Identical parts are designated by the same reference numerals. It is going to the description too FIG. 1 directed to avoid repetition.
  • the device 5 comprises the pulley 7, the shaft 3 of the starter generator 1 and a hub 19 arranged between the shaft 3 and the pulley 7.
  • the shaft 3 has on an outer circumference 21 a driver 23 which is integrally connected to the shaft 3.
  • the driver 23 has an almost rectangular base 25, which has almost vertical side surfaces 26 and 26 '. In the figure, only the rectangular base 25 is shown. A geometric dimension of the driver 23 in the direction of the shaft axis 4 can not be seen in the sectional view.
  • the hub 19 has an inner contour 29. On the inner contour 29, a driver 31 is formed integrally with the hub 19. Of the driver 31 is also a base 33 shown in the figure.
  • the base 33 of the hub 19 has a nearly perpendicular to the inner contour 29 of the hub 19 aligned side surfaces 35 and a nearly parallel to this side surface 35 '.
  • a spring 37 is arranged between the side surface 35 'of the driver 31 and the side surface 26 of the driver 23.
  • a spring 39 is arranged between the side surface 26 'of the driver 23 and the side surface 35 of the driver 33.
  • the springs 37 and 39 have different stiffnesses. Rotates the shaft 3 clockwise, the spring 39 is compressed, the shaft 3 rotates counterclockwise, the spring 37 is compressed. If, however, the hub 19 rotates clockwise, the spring 37 is compressed and when the hub 19 is moved counterclockwise, the spring 39 is compressed.
  • the shaft 3 and the hub 19 are thus rotatable relative to each other in accordance with the spring travel 37 and 39. It can be transmitted from the hub 19 on the shaft 3 torques and vice versa.
  • Stiffnesses of the springs 37 and 39 is the necessary to transmit the same torque torsional angle of different sizes.
  • the distance between the driver 23 and driver 31, which is adjustable by the springs 37 and 39, is referred to as clearance angle 41.
  • the hub 19 has an outer contour 43. Between the outer contour 43 of the hub 19 and the pulley 7, a double freewheel 47 is arranged.
  • the double freewheel 47 has at least two clamping elements 49 and 51 and a spring device 53 and a control cage 55 arranged between two clamping elements 49 and 51.
  • the double freewheel has six of the at least two clamping elements 49 and 51, ie a total of twelve, each pairwise cooperating , Clamping elements.
  • the control cage 55 is operatively connected to the pulley 7 via friction elements, not shown here, so that a torque is transmitted. This means that upon rotation of the pulley 7 in one direction, the control cage 55 is rotated in the same direction.
  • the clamping elements 49 and 51 of the double freewheel 47 can be used in various embodiments, for example as a roller clamp or balls.
  • hubs and shafts with springs in a row.
  • the series connection of hubs and shafts can have axially successively connected shafts and hubs. It is also conceivable for hubs and shafts to be switched coaxially, that is to say onion-shaped, one behind the other, wherein an inner hub serves as a shaft for the outer hub.
  • the driver 23 of the shaft 3 and the driver 31 of the hub 19 of the clearance angle 41 is formed. It is, as already described, also possible to switch hubs and shafts in succession, so that the resulting clearance angle is composed of the sum of the individual clearance angles between in each case a pair consisting of a hub and a shaft.
  • the device 5 is shown in starter mode. Introduced by the shaft 3 right-handed torque, which is symbolized by the arrow 59 is on the soft spring 39, which is shown here in the block pressed state, from the driver 23 of the shaft 3 via the driver 31 of the hub 19 finally on the Hub 19 transferred. If the spring 39 is designed as a soft spring, that is to say with low spring rigidity, large shaft rotation angles and thus large difference angles to the hub 19 are produced even at low torques. The hub 19 begins to rotate, and thus the control cage 55, which is coupled via not shown friction elements with the pulley 7, through the pulley 7 withheld.
  • a clamping gap 63 is released and the clamping body 49 transmits the clockwise torques, shown as arrow 59, from the hub 19 to the pulley 7.
  • the clamping body 51 now form a self-releasing freewheel. That is, the clamp bodies 51, which are urged by the centrifugal force against the inner wall of the pulley 7, rotate with the pulley 7 as a rigid body, do not transmit moments, and do not make relative movement to the pulley 7. Rotates due to the nonuniformity of the internal combustion engine 15, the torque direction, the hub 19 is accelerated by the spring 39 due to the freewheel closed with clamping body 49.
  • the freewheel 41 formed via the clamping bodies 49 opens.
  • the freewheel 41 formed via the clamping bodies 51 can now close. It would have been transmitted at this time torques from the pulley 7 via the hub 19 to the shaft 3, which would have led to damage to the shaft 3, if the reversal of the freewheel of the clamping body would not have occurred. Therefore, the clearance angle 41 between the driver 23 and the driver 31 must be selected so that before the closing of the clamp body 51 of the torque input, which was caused by the reversal of the direction of the torque must be completed. It is particularly advantageous if this results in a compensatable by the spring 39 and the clearance angle 41 angular difference, which is greater than / equal to the largest difference angle during the startup process.
  • the clearance angle 41 and thus the compensatable angular difference can be increased by hubs with drivers and springs are connected in series.
  • series connection can be understood both an axial series connection of hubs and shafts, as well as a coaxial series connection analogous to a onion-like structure.
  • coaxial series connection of hubs and shafts each of the outer side of a hub acts as a shaft for the next overlying hub.
  • FIG. 4 the device 5 is shown in the generator mode, ie with the internal combustion engine 15 running.
  • a clockwise torque shown as arrow 65, moves the pulley 7 clockwise and tows by means of the friction elements, not shown, the control cage 55 with clockwise rotation.
  • clamping gaps 61 are released for the clamping elements 51.
  • the clamping elements 51 are moved by the springs 53 in clamping gaps 61 and thus transmit the clockwise torques 65 from the pulley 7 to the hub 19.
  • the driver 31 transmits by the spring 37, the clockwise torque on the driver 23 on the shaft 3.
  • the clamping body 49 are prevented by the control cage 55 from falling into the nip 63 and are forced outward by the centrifugal force, so that they rotate with the pulley 7 as a rigid body, so transmit no torque. They thus form a low-wear self-lifting freewheel.
  • the shaft 3 rotates counterclockwise and the Driver 23 is moved to the driver 31 of the hub 19 and thus transmits the left-handed torque 69 to the hub 19.
  • the rotation of the hub 19 in the counterclockwise direction of the clamping body 51 is moved to the clamping body 49 to. Since the pulley 7 is not in motion, the control cages 55 remain at rest and the nip 61 is released.
  • the springs 53 press the clamping bodies 49 located in front of the springs 53 into the clamping gaps 63 and thus transmit the torque 69 from the hub 19 to the pulley 7.
  • the pulley 7 is thus rotated and tensions the belt 9 between the pulley 7 of the starter generator 1 and pulley 11 of the engine 15 against the negative drag torque of the engine 15, since the pulley 11 is at rest.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (7)

  1. Démarreur-générateur comprenant une poulie à courroie, un arbre disposé à l'intérieur de la poulie à courroie et une roue libre, qui présente un corps de serrage sollicité au moyen d'un dispositif à ressort, la roue libre étant réalisée sous forme de double roue libre, caractérisé en ce que celle-ci présente des corps de serrage (49, 51) disposés par paires, entre lesquels le dispositif de ressort (53) est disposé, et qui coopèrent avec des fentes de serrage différentes (61, 63), en ce qu'au moins un moyeu (19) entourant l'arbre (3) est prévu, en ce que les corps de serrage (49, 51) sont disposés entre le moyeu (19) et la poulie à courroie (7) avec une cage de commande (55) accouplée à la poulie à courroie (7), et en ce qu'entre le moyeu (19) et l'arbre (3) est prévu un accouplement à ressort avec au moins deux ressorts (37, 39).
  2. Démarreur-générateur selon la revendication 1, caractérisé en ce que l'accouplement entre la cage de commande (55) et la poulie à courroie (7) s'effectue au moyen d'un élément de friction.
  3. Démarreur-générateur selon les revendications 1 et 2, caractérisé en ce que les au moins deux ressorts (37, 39) de l'accouplement à ressort présentent des rigidités différentes, au moins un premier ressort (37), dans le cas d'un mouvement relatif entre le moyeu (19) et l'arbre (3), et au moins un deuxième ressort (39), dans le cas d'un mouvement relatif entre le moyeu (19) et l'arbre (3), agissant dans une direction opposée.
  4. Démarreur-générateur selon l'une quelconque des revendications précédentes, caractérisé en ce que les ressorts (37, 39) sont réalisés sous forme de ressorts spirale.
  5. Démarreur-générateur selon l'une quelconque des revendications précédentes, caractérisé en ce que des espaces d'amortissement remplis avec au moins un milieu sont prévus entre les dispositifs d'entraînement (23, 31).
  6. Démarreur-générateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un angle de dépouille (41) entre le dispositif d'entraînement (23) de l'arbre (3) et le dispositif d'entraînement (31) du moyeu (19) est défini par la rigidité des ressorts (37, 39) de l'accouplement à ressort.
  7. Démarreur-générateur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'angle de dépouille (41) peut être ajusté par un montage l'un derrière l'autre d'au moins deux moyeux (19) avec un dispositif d'entraînement (31) et des ressorts associés (37, 39).
EP20040022895 2003-10-13 2004-09-25 Démarreur-générateur muni d'une roue libre auto-inverseuse Expired - Lifetime EP1524430B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10347422 2003-10-13
DE2003147422 DE10347422A1 (de) 2003-10-13 2003-10-13 Startergenerator mit selbsttätig umschaltendem Freilauf

Publications (3)

Publication Number Publication Date
EP1524430A2 EP1524430A2 (fr) 2005-04-20
EP1524430A3 EP1524430A3 (fr) 2006-10-25
EP1524430B1 true EP1524430B1 (fr) 2009-12-02

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EP20040022895 Expired - Lifetime EP1524430B1 (fr) 2003-10-13 2004-09-25 Démarreur-générateur muni d'une roue libre auto-inverseuse

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EP (1) EP1524430B1 (fr)
DE (2) DE10347422A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009034339A1 (de) * 2009-07-23 2011-01-27 Bayerische Motoren Werke Aktiengesellschaft Nebenaggregateantrieb
DE102009035178A1 (de) 2009-07-29 2011-02-10 Daimler Ag Freilauf für einen Starter einer Verbrennungskraftmaschine sowie Verbrennungskraftmaschine
DE102010000999B4 (de) * 2010-01-19 2018-03-01 Siemens Aktiengesellschaft Dynamoelektrische Maschine mit Läuferblockiereinrichtung
DE112012000738A5 (de) * 2011-02-09 2013-11-14 Schaeffler Technologies AG & Co. KG Verfahren und Vorrichtung zum Start einer Brennkraftmaschine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR609501A (fr) * 1926-01-18 1926-08-16 Perfectionnements aux accouplements élastiques
DE635474C (de) * 1932-12-13 1936-09-18 Zahnradfabrik Friedrichshafen Kupplungsvorrichtung, insbesondere fuer Kraftfahrzeuge, mit in der Vorwaerts-bzw. Rueckwaertstriebrichtung benuetzbaren Klemmkoerpern
US2209459A (en) * 1938-03-03 1940-07-30 Gen Motors Corp Overrunning clutch
DE19919449B4 (de) * 1998-05-04 2015-10-15 Schaeffler Technologies AG & Co. KG Triebscheibe
DE19852085C1 (de) * 1998-11-12 2000-02-17 Daimler Chrysler Ag Starteinrichtung für eine Brennkraftmaschine und Verfahren zum Starten der Brennkraftmaschine
DE10253495A1 (de) * 2001-12-14 2003-09-11 Ina Schaeffler Kg Generatorfreilauf für einen riemengetriebenen Startergenerator

Also Published As

Publication number Publication date
DE10347422A1 (de) 2005-06-02
EP1524430A3 (fr) 2006-10-25
EP1524430A2 (fr) 2005-04-20
DE502004010439D1 (de) 2010-01-14

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