EP1748181B1 - Mécanisme de transmission du couple de démarrage d'un moteur thermique - Google Patents

Mécanisme de transmission du couple de démarrage d'un moteur thermique Download PDF

Info

Publication number
EP1748181B1
EP1748181B1 EP20060015088 EP06015088A EP1748181B1 EP 1748181 B1 EP1748181 B1 EP 1748181B1 EP 20060015088 EP20060015088 EP 20060015088 EP 06015088 A EP06015088 A EP 06015088A EP 1748181 B1 EP1748181 B1 EP 1748181B1
Authority
EP
European Patent Office
Prior art keywords
combustion engine
internal combustion
ring gear
bearing
way clutch
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.)
Ceased
Application number
EP20060015088
Other languages
German (de)
English (en)
Other versions
EP1748181A2 (fr
EP1748181A3 (fr
Inventor
Kazuhito c/o Toyota Jidosha Kabushiki Kaisha Sakai
Toshiaki c/o Toyota Jidosha Kabushiki Kaisha Asada
Makoto c/o Toyota Jidosha Kabushiki Kaisha Ishikawa
Tomoaki c/o Toyota Jidosha Kabushiki Kaisha Suzuki
Toshimitsu c/o Toyota Jidosha Kabushiki Kaisha Shiba
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.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
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 Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP1748181A2 publication Critical patent/EP1748181A2/fr
Publication of EP1748181A3 publication Critical patent/EP1748181A3/fr
Application granted granted Critical
Publication of EP1748181B1 publication Critical patent/EP1748181B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02N2250/00—Problems related to engine starting or engine's starting apparatus
    • F02N2250/08—Lubrication of starters; Sealing means for starters

Definitions

  • the invention relates to a startup torque transmitting mechanism for an internal combustion engine, which, by means of a one-way clutch, both transmits torque generated by a starter motor to a crankshaft side in one direction and prevents the transmission of torque in the other direction.
  • Japanese Patent Application Publication No. JP-A-2003-83216 discloses a startup torque transmitting mechanism of an internal combustion engine in a startup apparatus of an internal combustion engine, in which a one-way clutch (i.e., a reverse input interruption clutch) is provided between a starter motor and a crankshaft such that the starter motor side can be in constant mesh with a ring gear.
  • a one-way clutch i.e., a reverse input interruption clutch
  • DE 103 43 400 A1 discloses a startup torque transmitting mechanism with a race connecting member, which rotates in conjunction with a crankshaft and is connected to one race of the one-way clutch and a ring gear which is connected to another race of the one-way clutch, mounted to a main body side of the internal combustion engine via a bearing at the most inside portion of the ring gear and rotates according to torque received from the starter motor.
  • the ring gear (a reduction gear) is provided on the crankshaft via a bearing. Furthermore, a one-way clutch is arranged on the side opposite the abutting surface of the bearing so the ring gear is connected to a drive gear that moves in conjunction with the crankshaft via this one-way clutch. Accordingly, when the starter motor is driven, the one-way clutch engages so that torque is transmitted from the ring gear to the drive gear, thus enabling the crankshaft to be rotated by the starter motor.
  • the ring gear can not be separated from the crankshaft so vibration from the crankshaft ends up acting on the ring gear via the bearing.
  • one aspect of the invention relates to a startup torque transmitting mechanism of an internal combustion engine, which, by means of a one-way clutch, both transmits torque generated by a starter motor to a crankshaft side in one direction and prevents the transmission of torque in the other direction, and which includes a race connecting member mounted on the crankshaft side, which rotates in conjunction with the crankshaft and is connected to one race of a one-way clutch; and a ring gear which is rotatably mounted to a main body side of the internal combustion engine via a bearing, and rotates according to torque received from the starter motor, and is connected to another race of the one-way clutch.
  • the ring gear is mounted via a bearing to the main body side of the internal combustion engine instead of to the crankshaft side. Therefore, the bearing operates only while the ring gear is being rotated by the starter motor at startup of the internal combustion engine, and stops rotating when the starter motor stops after startup. Accordingly, the bearing does not rotate while the internal combustion engine is operating. Since the bearing only needs to operate only for a short period of time during startup in this way, the bearing does not need to be supplied with a large amount of lubrication oil.
  • the ring gear is not directly connected to and supported by the crankshaft, but rather is mounted to the crankshaft via the one-way clutch. Therefore, the ring gear can be mounted away from the crankshaft which is advantageous in that it allows for a higher degree of freedom in terms of design layout.
  • the ring gear may also be provided in a state in which it does not contact the crankshaft side.
  • the ring gear can be completely separated from the crankshaft. As a result, it is possible to inhibit vibration from the crankshaft being transmitted to the ring gear while the internal combustion engine is operating.
  • the race connecting member may be connected to an outer race of the one-way clutch and the ring gear may be connected to an inner race of the one-way clutch.
  • the one-way clutch in particular can be completely covered when viewed from the outside by a structure in which the race connecting member and the outer race are connected.
  • a design is possible in which a high degree of sealability can easily be realized even if a large amount of lubrication oil is supplied to the one-way clutch during operation of the internal combustion engine because the one-way clutch, for which an oil seal is particularly necessary, can be completely covered.
  • the race connecting member may also be arranged on the opposite side of the ring gear from the main body of the internal combustion engine.
  • the ring gear is on the main body side of the internal combustion engine and the race connecting member is on the opposite side of the ring gear from the main body of the internal combustion engine.
  • the one-way clutch can be covered from the outside of the internal combustion engine, particularly from the transmission side, by the race connecting member and the outer race. Therefore, it is possible to both easily realize a high degree of sealability of the one-way clutch with respect to the outside of the internal combustion engine and provide an oil seal while the one-way clutch is completely separated from the transmission side. Accordingly, oil used to lubricate the internal combustion engine can also be used to lubricate the one-way clutch.
  • the bearing may be arranged so as to encircle the one-way clutch.
  • the ring gear can be mounted to the internal combustion engine by the one-way clutch and the bearing.
  • a first oil seal member may be arranged in a gap between the outer race of the one-way clutch and the ring gear, and a second oil seal member may be arranged in a gap between the ring gear and the main body of the internal combustion engine.
  • Arranging the first oil seal member and the second oil seal member in this way makes it possible to seal the inside of the startup torque transmitting mechanism of an internal combustion engine so that oil does not leak out both easily and with a high degree of sealability.
  • the startup torque transmitting mechanism of an internal combustion engine can be lubricated using the oil that is used to lubricate the internal combustion engine.
  • a cylindrical portion may be formed around the crankshaft on a portion of the ring gear, the first oil seal member may be arranged on an inner peripheral side of this cylindrical portion, and the second oil seal member may be arranged on an outer peripheral side of the cylindrical portion.
  • the oil seals can be easily arranged by insertion. Also, a reliable seal can be provided for the lubrication oil supplied to the bearing by arranging the second seal member and the bearing in this manner.
  • the second oil seal member and the bearing may be arranged parallel to each other in the gap between the ring gear and the main body of the internal combustion engine, with the bearing being toward the inside of the main body of the internal combustion engine.
  • Arranging the second seal member and the bearing in this manner enables a reliable seal to be provided for the lubrication oil supplied to the bearing.
  • the second oil seal member may be integrally incorporated into the inner peripheral side of the outer race of the bearing. Forming the second oil seal member so that it is integrated with the bearing as an assembled body enables the work of assembling it to the internal combustion engine to be done efficiently.
  • the ring gear may be a disc in which a curved portion is formed in the radial direction thereof. This structure makes the ring gear itself more rigid, which enables the ring gear to have a high mechanical strength as well as improves the suppression function against vibration.
  • a bearing mounting portion to which the bearing mounts and a clutch mounting portion to which the one-way clutch mounts may be formed in the curved portion. Accordingly, this structure makes it possible to effectively utilize space for mounting the bearing and the one-way clutch using the curved portion, in turn enabling the overall structure of the startup torque transmitting mechanism of the internal combustion engine to be made more compact.
  • the startup torque transmitting mechanism of an internal combustion engine may also be structured such that the ring gear is formed as a separate structure that is separated from the flywheel, while a middle portion of the ring gear is supported by an outer wall of the internal combustion engine via the bearing and a center open portion of the ring gear is supported by the crankshaft via the one-way clutch.
  • the one-way clutch releases.
  • less lubrication oil can be supplied to the bearing.
  • the ring gear is supported by the outer wall of the internal combustion engine via the bearing, as well as by the crankshaft via the one-way clutch.
  • the ring gear is supported in suspension from the crankshaft. Therefore, when the internal combustion engine is in a steady running mode, such that the one-way clutch is released, drive vibration of the internal combustion engine transmitted from the crankshaft is largely suppressed by the one-way clutch. As a result, the vibration characteristics of the ring gear can be improved, which in turn enables the characteristics of noise produced by the ring gear to be improved.
  • the one-way clutch may be supported by the crankshaft via the race connecting member.
  • FIG. 1 is an enlarged longitudinal sectional view of the upper half, with respect to the axial center of a crankshaft, of a main portion of a startup torque transmitting mechanism of an internal combustion engine for a vehicle, at an area on the rear side of the internal combustion engine where power is output to the transmission side.
  • a ring gear 10 is mounted to the cylinder block 2.
  • the flywheel 6, the upper half of which is shown in FIG. 1 , is substantially disc-shaped, with the center portion being open in the shape of a circle.
  • a ring-shaped clutch disc 6a which serves as a portion of a clutch mechanism for transmitting torque to and from a transmission, is mounted to the flywheel 6 on the side opposite the side that contacts the outer race support plate 8.
  • the clutch mechanism may also be formed separately.
  • the outer race support plate 8 the upper portion of which is shown in FIG 1 , is formed in a flat circular shape with the center portion open.
  • the outer race support plate 8 is fixed by a bolt both to the flywheel 6 and to a rear end surface 4a of the crankshaft 4 at a portion around the center opening. As a result, the outer race support plate 8 rotates in conjunction with both the flywheel 6 and the crankshaft 4.
  • the ring gear 10 is a circular disc in which the center portion is largely open and which has bent portions (i.e., a flange portion 10a, a cylindrical portion 10c, and a curved portion 10f) in the radial direction.
  • the flange portion 10a functions as a mounting portion for a one-way clutch 12 and the cylindrical portion 10c functions as a mounting portion for a bearing 16.
  • the flange portion 10a is formed at the center open portion of the ring gear 10 and an inner race of a one-way clutch 12 is mounted to that flange portion 10a.
  • the reference character 10a will also be used to denote the inner race portion because the inner race of the one-way clutch is mounted to the flange portion 10a.
  • a ring-shaped groove portion which has a cross-section in the shape of the letter C is formed in the ring gear 10 by the flange portion 10a and the cylindrical portion 10c. In this groove portion are housed the one-way clutch 12, the outer race 18, and a second oil seal 20.
  • a ring-shaped gear portion 10b with which a starter motor, not shown, can engage is provided on an outer peripheral portion of the ring gear 10.
  • This ring gear 10 is such that the portion with the inner race 10a (i.e., the flange portion) is positioned closest to the center of the crankshaft.
  • the ring gear 10 is not supported by crankshaft 4 via the inner race 10a, however, but rather is suspended from a peripheral surface 4b of the crankshaft 4.
  • a semicircular peripheral surface portion 2a is formed protruding on the rear portion side of the cylinder block 2. Similarly, a semicircular surface portion that continues on from this semicircular surface portion 2a on the cylinder block 2 side is also provided on the rear portion side of an oil pan arranged below the cylinder block 2.
  • the oil pan not shown, is assembled to the cylinder block 2, the semicircular surface portion 2a on the cylinder block 2 side and the semicircular surface portion on the oil pan side connect, forming a short circumferential surface portion 14 which encloses the entire periphery of the crankshaft 4 and is short in axial direction of the crankshaft.
  • the bearing (a roller bearing is used in this embodiment) 16 is fitted to an inner peripheral surface 14a of the short circumferential surface portion 14 in the space formed between that inner peripheral surface 14a and the cylindrical portion 10c. Accordingly, the ring gear 10 is supported by the main body side of the internal combustion engine via the bearing 16. Therefore, when the one-way clutch 12 is released, the ring gear 10 can rotate freely, independently of the rotation of the crankshaft 4.
  • the gear portion 10b of the ring gear 10 is in constant mesh with a pinion gear of the starter motor that is arranged below the crankshaft 4.
  • this gear portion 10b receives torque from the starter motor via the pinion gear, the entire ring gear 10 rotates, thus driving the crankshaft 4 via the one-way clutch 12, which will be described later.
  • An outer race 18 is mounted to the outer peripheral portion of the outer race support plate 8, opposite the inner race 10a (i.e., the flange portion) formed on the center open portion of the ring gear 10 such that the one-way clutch 12 is formed between the ring gear 10 and the outer race support plate 8.
  • the one-way clutch 12 engages the outer race support plate 8 with the ring gear 10 when the starter motor rotates the ring gear 10 via the pinion gear during startup of the internal combustion engine, i.e., when the ring gear 10 is rotated in the direction that will enable torque to be transmitted to the outer race support plate 8 during startup of the internal combustion engine.
  • the starter motor can rotate the crankshaft 4.
  • Engine oil is supplied as lubrication oil to the bearing 16 and the one-way clutch 12 via oil passages in the cylinder block 2 or the crankshaft 4, as shown by the arrow A in the FIG.1 .
  • the one-way clutch 12 is arranged between the outer race support plate 8 and the ring gear 10 so it is necessary to prevent oil from leaking out.
  • a ring-shaped first oil seal member 20 is arranged between the outer race 18 that is integrally mounted to the outer race support plate 8 and the cylindrical portion 10c of the ring gear 10. This first oil seal member 20 is fixed to the ring gear 10 side by being fitted to the inner peripheral surface 10d of the cylindrical portion 10c.
  • a seal lip 20a which is formed on the inner peripheral side of the first oil seal member 20 is urged to slidably contact the outer peripheral surface of the outer race 18 by spring force of a spring provided in the seal lip 20a, thus providing an oil seal.
  • a second oil seal member 22 which has a larger diameter than the first oil seal member 20 is arranged parallel with the bearing 16 described above on the side of the cylindrical portion 10c opposite the inner peripheral side where the first oil seal member 20 is arranged (i.e., the second oil seal member 22 is arranged on the outer peripheral side of the cylinder portion 10c).
  • the bearing 16 is arranged on the inside in the axial direction with respect to the short circumferential surface portion 14 and the second oil seal member 22 is arranged on the outside in the axial direction with respect to the short circumferential surface portion 14.
  • This second oil seal member 22 is fixed the position shown in the drawing by being fitted to the inner peripheral surface 14a of the short circumferential surface portion 14, similar to the bearing 16. Accordingly, a seal lip 22a which is formed on the inner peripheral side of the second oil seal member 22 slidably contacts an outer peripheral surface 10e of the cylindrical portion 10c, similar to the first oil seal member 20, thus providing an oil seal.
  • the embodiment described above can achieve the following effects.
  • (I) The ring gear 10 is mounted via the bearing 16 to the main body side of the internal combustion engine (the cylinder block 2 and the oil pan in this embodiment), not the crankshaft 4 side.
  • the bearing 16 only actually functions (i.e., rotates) while the ring gear 10 is being rotated by the starter motor during startup of the internal combustion engine. It is therefore possible to have the bearing 16 not rotate while the internal combustion engine is operating because the bearing 16 stops rotating when the starter motor stops after the internal combustion engine has started.
  • the bearing 16 Since the bearing 16 only rotates for a short period of time at startup in this way, a large amount of lubrication oil does not need to be supplied to the bearing 16. Moreover, the bearing 16 itself does not need to be large from providing a plurality of rows of balls or rollers or the like which is another reason why a large amount of lubrication oil does not need to be supplied. Therefore, as shown in FIG. 1 , the bearing 16 can be sufficiently lubricated with the lubrication oil that is supplied only through a gap 24 between the cylinder block 2 and the ring gear 10. As a result, special consideration does not have to be given to providing a lubrication oil passage for the bearing 16, which enables the lubrication oil passages to be simplified, as well as contributes to an overall reduction in size of the internal combustion engine.
  • the ring gear 10 is not supported by the crankshaft 4, but rather is mounted via the one-way clutch 12 so it is separated from and does not contact the crankshaft 4. That is, the ring gear 10 can be arranged across a gap 26 from the peripheral surface 4b of the crankshaft 4, as shown in FIG. 1 . Therefore, vibration from the crankshaft 4 when the internal combustion engine is operating is not transmitted to the ring gear 10 so wear due to vibration at the point of contact between the gear portion 10b and the pinion gear can be reduced and noise from sound radiation from the ring gear 10 can be suppressed. Also, this gap 26 makes it easier to supply lubrication oil to the one-way clutch 12. In particular, sufficient lubrication oil can be supplied to the one-way clutch 12 which slides when the internal combustion engine is operating, thereby increasing the durability of the one-way clutch 12.
  • the outer race support plate 8 as the race connecting member is connected to the outer race 18 which forms part of the one-way clutch 12, and the ring gear 10 is connected to the inner race 10a which also forms part of the one-way clutch 12.
  • the connecting body of the outer race support plate 8 and the outer race 18 when viewed from one direction, e.g., when viewed from the transmission side.
  • a high degree of sealability can easily be realized even when a large amount of lubrication oil is supplied to the one-way clutch 12 during operation of the internal combustion engine because the one-way clutch 12 for which an oil seal is particularly necessary can be completely covered.
  • an oil seal can be provided by the first oil seal member 20 while the one-way clutch 12 is completely separated from the transmission side. Accordingly, the oil used to lubricate the internal combustion engine can also be introduced through the gap 26 and used to lubricate the one-way clutch 12.
  • the first oil seal member 20 is arranged as described above, and the second oil seal member 22 is arranged in the gap between the ring gear 10 and the main body side of the internal combustion engine, while the bearing 16 is arranged parallel with and to the inside, in the axial direction, of this second oil seal member 22 in the same gap. Therefore, the inside of the startup torque transmitting mechanism of an internal combustion engine can be easily sealed with a high degree of sealability.
  • the first oil seal member 20 is arranged on the inner peripheral surface 10d side of the cylindrical portion 10c formed in the ring gear 10 and the second oil seal member 22 and the bearing 16 are arranged on the outer peripheral surface 10e of that cylindrical portion 10c. Therefore, the oil seal members 20 and 22 and the bearing 16 can be arranged easily by being fitted into place, making it possible to reliably form the bearing and oil seals.
  • the outer race 18 of the one-way clutch 12 is arranged, via the first oil seal member 20, on the inner peripheral surface 10d of the cylindrical portion 10c of the ring gear 10, which is on the opposite side of the cylindrical portion 10c than the outer peripheral surface 10e on which the bearing 16 is arranged. Therefore, the cylindrical portion 10c does not directly contact the one-way clutch 12. Also, the inner race 10a (i.e., the flange portion) of the one-way clutch 12 is formed on the inner peripheral side of the ring gear 10, but shock force on the inner race 10a generated when the one-way clutch 12 engages is applied in the direction which reduces the holding force on the bearing 16 by the cylindrical portion 10c and the short circumferential surface portion 14.
  • the bearing 16 is arranged in the position shown in FIG. 1 , which alleviates the problem of shock force being applied to the bearing 16 when the one-way clutch 12 engages. Accordingly, an excessive load is not applied to the bearing 16 even when the one-way clutch 12 engages. Hence, this embodiment makes it possible to prevent damage to the bearing 16.
  • the ring gear is provided with the curved portion which increases the rigidity of the ring gear itself and thus enables the ring gear to have a high mechanical strength.
  • the vibration characteristics i.e., the vibration suppression function, can be improved such that noise from the ring gear can be suppressed, enabling quieter operation of the internal combustion engine itself.
  • the bearing mounting portion and the clutch mounting portion are formed on the curved portion which makes it possible to ensure space for mounting the bearing and the one-way clutch using the curved portion. As a result, the overall structure of the startup torque transmitting mechanism of the internal combustion engine can be made more compact.
  • FIG. 2 a bearing 52 and a second oil seal member 54 are unitized as an assembly 50. All other structure is the same as it is in the foregoing embodiment. Thus, portions shown in FIG. 2 that are the same as portions shown in FIG 1 will be denoted by like reference characters and redundant descriptions thereof will be omitted.
  • An outer race 52a of the bearing 52 is formed wider than an inner race 52b, and the assembly 50 is formed with the second oil seal member 54 being fit beforehand to the inner peripheral side of this outer race 52a. Therefore, during assembly of the internal combustion engine, both the bearing 52 and the second oil seal member 54 can be mounted at one time by fitting the assembly 50 to the inner peripheral surface 14a of the short circumferential surface portion 14. In order to more completely seal the area between the outer race 52a and the inner peripheral surface 14a of the short circumferential surface portion 14, an O-ring 56 may be provided therebetween, as shown in FIG 2 .
  • the outer race support plate 8 is fastened by a bolt to the flywheel 6, as shown in FIG. 1 .
  • the outer race support plate 8 may be fastened to a drive plate that is connected to a cover of a torque converter, instead of being fastened to the flywheel 6.
  • the inner race of the one-way clutch 12 is mounted to the outside of the flange portion 10a that is at the center open portion of the ring gear 10.
  • the outer race 18 may be mounted to the inside of the flange portion 10a, i.e., the one-way clutch may be arranged farther toward the rotational center side.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Gear Transmission (AREA)

Claims (13)

  1. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne, qui, au moyen d'un embrayage unidirectionnel (12), transmet un couple généré par un démarreur côté vilebrequin (4) dans une seule direction et empêche la transmission de couple dans l'autre direction, comprenant :
    un élément (8) de raccordement de cage monté côté vilebrequin (4), qui tourne avec le vilebrequin (4) et qui est relié à une cage (18) de l'embrayage unidirectionnel (12) ; et
    une couronne dentée (10) qui est montée en rotation côté corps principal du moteur à combustion interne à travers un roulement (16), et qui tourne selon un couple reçu du démarreur, et est reliée à une autre cage (10a) de l'embrayage unidirectionnel (12),
    caractérisé en ce que le roulement (16) est agencé de manière à encercler l'embrayage unidirectionnel (12).
  2. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 1, dans lequel la couronne dentée (10) est pourvue dans un état dans lequel elle ne rentre pas en contact avec le côté vilebrequin.
  3. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 1 ou 2, dans lequel l'élément (8) de raccordement de cage est relié à une cage externe de l'embrayage unidirectionnel (12) et la couronne dentée (10) est reliée à une cage interne de l'embrayage unidirectionnel (12).
  4. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 3, dans lequel l'élément (8) de raccordement de cage est agencé sur le côté opposé de la couronne dentée (10) à partir du corps principal du moteur à combustion interne.
  5. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon l'une quelconque des revendications 1 à 4, dans lequel un premier élément (20) étanche à l'huile est agencé dans un espace entre la cage externe de l'embrayage unidirectionnel (12) et la couronne dentée (10), et un deuxième élément (22) étanche à l'huile est agencé dans un espace entre la couronne dentée (10) et le corps principal du moteur à combustion interne.
  6. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 5, dans lequel une partie cylindrique est formée autour du vilebrequin (4) sur une partie de la couronne dentée (10), le premier élément (20) étanche à l'huile est agencé sur un côté périphérique interne de cette partie cylindrique, et le deuxième élément (22) étanche à l'huile est agencé sur un côté périphérique externe de la partie cylindrique.
  7. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 5 ou 6, dans lequel le deuxième élément (22) étanche à l'huile et le roulement (16) sont agencés l'un parallèle à l'autre dans un espace entre la couronne dentée (10) et le corps principal du moteur à combustion interne, avec le roulement (16) étant vers l'intérieur du corps principal du moteur à combustion interne.
  8. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 7, dans lequel le deuxième élément (22) étanche à l'huile est intégralement incorporé dans le côté périphérique interne de la cage externe du roulement (16).
  9. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon l'une quelconque des revendications 1 à 8, dans lequel la couronne dentée (10) est un disque dans lequel une partie courbée est formée dans la direction radiale de celui-ci.
  10. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon l'une quelconque des revendications 1 à 9, dans lequel une partie (2a, 10c) de montage de roulement à laquelle le roulement est monté et une partie (2a, 10c) de montage d'embrayage à laquelle l'embrayage unidirectionnel est monté sont formées dans la partie courbée.
  11. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 1, dans lequel la couronne dentée (10) est formée comme une structure séparée qui est séparée du volant (6), tandis qu'une partie ouverte centrale de la couronne dentée est soutenue par le vilebrequin (4) à travers l'embrayage unidirectionnel (12) et la couronne dentée (10) est soutenue par une paroi externe du moteur à combustion interne à travers le roulement (16) à l'extérieur de la partie de la partie ouverte centrale de la couronne dentée.
  12. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 11, dans lequel une partie médiane de la couronne dentée (10) est soutenue par une paroi externe du moteur à combustion interne à travers le roulement (16).
  13. Mécanisme de transmission de couple de démarrage d'un moteur à combustion interne selon la revendication 12, dans lequel l'embrayage unidirectionnel (12) est soutenu par le vilebrequin (4) à travers l'élément (8) de raccordement de cage.
EP20060015088 2005-07-29 2006-07-19 Mécanisme de transmission du couple de démarrage d'un moteur thermique Ceased EP1748181B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005220105A JP4218667B2 (ja) 2005-07-29 2005-07-29 内燃機関始動回転力伝達機構

Publications (3)

Publication Number Publication Date
EP1748181A2 EP1748181A2 (fr) 2007-01-31
EP1748181A3 EP1748181A3 (fr) 2007-11-14
EP1748181B1 true EP1748181B1 (fr) 2011-03-02

Family

ID=37204129

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060015088 Ceased EP1748181B1 (fr) 2005-07-29 2006-07-19 Mécanisme de transmission du couple de démarrage d'un moteur thermique

Country Status (3)

Country Link
EP (1) EP1748181B1 (fr)
JP (1) JP4218667B2 (fr)
DE (1) DE602006020375D1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4127289B2 (ja) 2006-04-21 2008-07-30 トヨタ自動車株式会社 内燃機関の始動装置
JP2008184988A (ja) * 2007-01-31 2008-08-14 Denso Corp エンジン始動装置
JP2009047075A (ja) * 2007-08-20 2009-03-05 Denso Corp エンジン始動装置
FR2922605B1 (fr) * 2007-10-22 2010-05-21 Skf Ab Module debrayable pour systeme de transmission d'un couple de demarrage a un moteur a combustion interne
CA2761906A1 (fr) * 2009-05-15 2010-11-18 Litens Automotive Partnership Demarreur de moteur
JP5306103B2 (ja) * 2009-08-04 2013-10-02 株式会社オティックス 内燃機関の始動装置
WO2012079558A2 (fr) 2010-12-15 2012-06-21 Schaeffler Technologies AG & Co. KG Dispositif de transmission d'un couple
DE112012005001A5 (de) * 2011-11-30 2014-09-11 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung
EP2824349A1 (fr) * 2013-07-09 2015-01-14 Aktiebolaget SKF Procédé de fabrication d'un mécanisme de transmission de couple
EP2886850A1 (fr) * 2013-12-23 2015-06-24 Aktiebolaget SKF Mécanisme de transmission de couple pour moteur à combustion interne
EP2886849A1 (fr) * 2013-12-23 2015-06-24 Aktiebolaget SKF Mécanisme de transmission de couple

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE409374C (de) * 1923-08-14 1925-02-05 Maybach Motorenbau G M B H Freilaufkupplung, insbesondere fuer Anlassgetriebe von Kraftfahrzeugen
JP3293971B2 (ja) * 1993-08-30 2002-06-17 本田技研工業株式会社 内燃機関の始動用ドリブンギア軸受給油構造
DE10343400A1 (de) * 2003-09-19 2005-04-14 Daimlerchrysler Ag Kraftfahrzeugantrieb mit Starter-Anlage

Also Published As

Publication number Publication date
JP2007032497A (ja) 2007-02-08
JP4218667B2 (ja) 2009-02-04
EP1748181A2 (fr) 2007-01-31
EP1748181A3 (fr) 2007-11-14
DE602006020375D1 (de) 2011-04-14

Similar Documents

Publication Publication Date Title
EP1748181B1 (fr) Mécanisme de transmission du couple de démarrage d'un moteur thermique
US7559303B2 (en) Startup torque transmitting mechanism of an internal combustion engine
EP1910668B1 (fr) Mécanisme de transmission de couple de démarrage d un moteur à combustion interne
US8029400B2 (en) Center crank eccentrically oscillating speed reducer
US7147095B2 (en) Gearshift transmission for a motor vehicle with hydraulically actuated multiple clutch
EP1776524B1 (fr) Dispositif de démarrage
JP5418173B2 (ja) 乾式クラッチ
KR20060048439A (ko) 토크 전달 장치
KR20060048440A (ko) 토크 전달 장치 시스템
JP4306641B2 (ja) スタータ用トルク伝達装置
JP2013007432A (ja) 可変慣性質量フライホイール及びそれを搭載する車両
JP5425696B2 (ja) ワンウェイクラッチを用いたエンジンスタータ機構
WO2010140425A1 (fr) Dispositif de transmission d'énergie pour démarrer un moteur
JP2006258249A (ja) クラッチ内蔵型プーリユニット
JP2008031900A (ja) エンジン用オイルポンプ
JP4006187B2 (ja) 変速機ユニット
JP3577658B2 (ja) トルクコンバータ
JP2002192967A (ja) 車両の動力伝達装置
JP2012007528A (ja) ラチェット型ワンウェイクラッチを用いたエンジンスタータ機構
JPH11351331A (ja) 内燃機関の振動低減装置
JP2002364573A (ja) 流体機械
JPH05141447A (ja) 自動変速機
JPH10325332A (ja) 過給機
JP2012117385A (ja) 内燃機関
JPH0914401A (ja) 変速機のメインドライブギヤの支持装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20060719

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

AKX Designation fees paid

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RIN1 Information on inventor provided before grant (corrected)

Inventor name: SAKAI, KAZUHITOC/O TOYOTA JIDOSHA KABUSHIKI KAISHA

Inventor name: SHIBA, TOSHIMITSUC/O TOYOTA JIDOSHA KABUSHIKI KAIS

Inventor name: SUZUKI, TOMOAKIC/O TOYOTA JIDOSHA KABUSHIKI KAISHA

Inventor name: ISHIKAWA, MAKOTOC/O TOYOTA JIDOSHA KABUSHIKI KAISH

Inventor name: ASADA, TOSHIAKIC/O TOYOTA JIDOSHA KABUSHIKI KAISHA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 602006020375

Country of ref document: DE

Date of ref document: 20110414

Kind code of ref document: P

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602006020375

Country of ref document: DE

Effective date: 20110414

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20111205

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006020375

Country of ref document: DE

Effective date: 20111205

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20130412

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602006020375

Country of ref document: DE

Effective date: 20130410

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180612

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180703

Year of fee payment: 13

Ref country code: IT

Payment date: 20180713

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20180718

Year of fee payment: 13

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602006020375

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200201

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190719