WO2023188281A1 - Transmission à deux vitesses - Google Patents

Transmission à deux vitesses Download PDF

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Publication number
WO2023188281A1
WO2023188281A1 PCT/JP2022/016550 JP2022016550W WO2023188281A1 WO 2023188281 A1 WO2023188281 A1 WO 2023188281A1 JP 2022016550 W JP2022016550 W JP 2022016550W WO 2023188281 A1 WO2023188281 A1 WO 2023188281A1
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WO
WIPO (PCT)
Prior art keywords
state
engagement mechanism
frictional engagement
cam
hub
Prior art date
Application number
PCT/JP2022/016550
Other languages
English (en)
Japanese (ja)
Inventor
雅俊 佐藤
Original Assignee
株式会社ダイナックス
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 株式会社ダイナックス filed Critical 株式会社ダイナックス
Priority to PCT/JP2022/016550 priority Critical patent/WO2023188281A1/fr
Publication of WO2023188281A1 publication Critical patent/WO2023188281A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion

Definitions

  • the present invention relates to a two-stage transmission device that changes the rotational speed of an output shaft in two stages.
  • Patent Document 1 discloses a power transmission path switching device including a driving cam, a cam device having first and second driven cams, a first frictional engagement mechanism, and a second frictional engagement mechanism; A stepped transmission is disclosed.
  • the first driven cam is connected and disconnected by displacing the first driven cam in a direction that increases the axial distance from the drive cam, and the second driven cam is moved in a direction that reduces the axial distance from the drive cam. Since the second frictional engagement mechanism can be connected and disconnected by displacement, the first frictional engagement mechanism and the second frictional engagement mechanism can be switched by the electric actuator without using a hydraulic system. has been done.
  • an object of the present invention is to provide a two-stage transmission that has a small number of parts and can prevent malfunctions.
  • the present invention provides a case fixed in a non-rotatable manner, an input shaft disposed on the inner circumferential side of the case, a hub rotatably disposed on the input shaft, and a hub disposed between the case and the hub. a first frictional engagement mechanism arranged between the hub and the input shaft, a planetary gear mechanism arranged between the hub and the input shaft, an output shaft connected to the pinion carrier of the planetary gear mechanism, and between the hub and the pinion carrier.
  • a second frictional engagement mechanism disposed, a ball cam mechanism having a driving cam, a rolling element, and a driven cam, and a driving device configured to transmit torque to the driving cam
  • the first frictional engagement mechanism is configured to be brought into a fastened state by being biased by an elastic body
  • the planetary gear mechanism includes a sun gear provided on the input shaft, a ring gear provided on the hub, and a pinion gear that meshes with the sun gear and the ring gear and is rotatably provided on the pinion carrier.
  • the driven cam includes a piston that passes through the first frictional engagement mechanism, and a pressing portion for the second frictional engagement mechanism,
  • the driving cam rotates due to torque from the driving device from a first state in which the driving cam and the driven cam are closest to each other, the rolling element rolls to separate the driving cam and the driven cam.
  • the driving cam further rotates due to torque from the driving device, the rolling element rolls, and the driving cam and the driven cam are further separated from each other to reach a third state.
  • the first frictional engagement mechanism is biased by the elastic body and is in the engaged state, and the second frictional engagement mechanism is in the released state, and in the second state, the second frictional engagement mechanism is in the engaged state.
  • a two-stage transmission characterized in that the coupling mechanism is in a released state, and the second frictional engagement mechanism pressing portion engages with the second frictional engagement mechanism to bring the second frictional engagement mechanism into a fastened state.
  • the ring gear in the first state, the ring gear is fixed unrotatably, so the torque from the input shaft is transmitted from the sun gear to the pinion gear, and the torque due to the revolution of the pinion gear is transferred to the pinion carrier. Since the torque can be transmitted to the output shaft through the input shaft, the torque from the input shaft can be decelerated and transmitted to the output shaft.
  • the ring gear idles, so even if the input shaft rotates, the pinion gear rotates on its own axis without revolving, so the torque from the input shaft is not transmitted to the output shaft, making it possible to maintain a neutral state. can.
  • the ring gear and pinion carrier are engaged by the second frictional engagement mechanism, so that torque from the input shaft can be transmitted to the output shaft at a constant speed.
  • the rotational speed of the output shaft can be changed in two stages using a ball cam mechanism that uses one rolling element in the radial direction, and there is a neutral state between the first state and the third state. Since a certain second state is passed, the number of parts can be relatively reduced, and malfunctions can be easily prevented.
  • the second frictional engagement mechanism pressing section is a bearing, the second frictional engagement mechanism pressing section and the second frictional engagement mechanism will come into contact with each other, which can prevent wear when the hub is rotating. , can extend the life of the device.
  • FIG. 1 is a sectional view of the two-stage transmission of the present invention in a first state.
  • FIG. 2 is a sectional view of the second state in FIG. 1;
  • FIG. 2 is a sectional view of the third state in FIG. 1;
  • FIG. 3 is a front view of the groove portion of the ball cam mechanism.
  • FIG. 3 is an enlarged cross-sectional view of the ball cam mechanism in a first state.
  • FIG. 6 is an enlarged sectional view of the second state of FIG. 5;
  • FIG. 6 is an enlarged sectional view of the third state in FIG. 5;
  • Embodiments of the present invention will be described below with reference to FIGS. 1 to 7. However, the present invention is not limited to this embodiment. Note that the configuration of the two-stage transmission 100 is basically symmetrical with respect to the axis X, so in FIGS. 1 to 3, only one side in the radial direction with respect to the axis X is shown.
  • the two-stage transmission 100 includes a first frictional engagement mechanism 10, a second frictional engagement mechanism 20, a planetary gear mechanism 30, a ball cam mechanism 40, a drive device 42, a case 50, an input shaft 52, It includes a hub 60 and an output shaft 62.
  • the planetary gear mechanism 30, the second friction engagement mechanism 20, and the ball cam mechanism 40 are arranged in parallel in the axial direction in this order.
  • the case 50 is fixed unrotatably.
  • the input shaft 52 and the output shaft 62 are rotatably disposed on the inner peripheral side of the case 50.
  • the hub 60 is rotatably provided on the input shaft 52.
  • a first friction engagement mechanism 10 is disposed between the case 50 and the hub 60.
  • a planetary gear mechanism 30 is disposed between the hub 60 and the input shaft 52.
  • the pinion carrier 35 of the planetary gear mechanism 30 is connected to the output shaft 62.
  • a second friction engagement mechanism 20 is disposed between the hub 60 and the pinion carrier 35.
  • the ball cam mechanism 40 includes a driving cam 45, a rolling element 43, and a driven cam 44, and is disposed on the inner peripheral side of the case 50. Torque is transmitted to the drive cam 45 from the drive device 42 .
  • the first frictional engagement mechanism 10 and the second frictional engagement mechanism 20 are each composed of a combination of a first friction plate 12 and a first plate 14, and a combination of a second friction plate 22 and a second plate 24.
  • the first friction plate 12 is spline-fitted onto the outer peripheral surface of the hub 60
  • the second friction plate 22 is spline-fitted onto the pinion carrier 35.
  • the first plate 14 is spline-fitted onto the inner peripheral surface of the case 50
  • the second plate 24 is spline-fitted onto the inner peripheral surface of the hub 60.
  • the first friction plate 12 is placed on the inner peripheral surface of the case 50, the first plate 14 is placed on the outer peripheral surface of the hub 60, the second friction plate 22 is placed on the inner peripheral surface of the hub 60, and the second plate 24 is placed on the inner peripheral surface of the hub 60. It may also be configured such that they are spline-fitted onto the pinion carrier 35, respectively.
  • the end plate 14a of the first frictional engagement mechanism 10 is engaged with the elastic body 16, and is urged toward the friction plate 12 by the elastic body 16.
  • a coil spring or a disc spring may be used.
  • the planetary gear mechanism 30 includes a sun gear 32, a ring gear 36, a pinion carrier 35, and a pinion gear 34.
  • Sun gear 32 is provided on input shaft 52 .
  • the ring gear 36 is provided on the hub 60 by spline fitting onto the inner peripheral surface of the hub 60.
  • the pinion gear 34 is rotatably provided on the pinion carrier 35 and meshes with the sun gear 32 and the ring gear 36. Note that a plurality of pinion gears 34 can be provided in the circumferential direction.
  • the ball cam mechanism 40 is composed of a drive device 42, a rolling element 43, a driven cam 44, and a drive cam 45.
  • the rolling element 43 is held between a driving cam 45 and a driven cam.
  • the driven cam 44 includes a piston 47 and a second frictional engagement mechanism pressing portion 46 on the opposite side from the driving cam 45 side.
  • the piston 47 is rod-shaped, and passes through the first frictional engagement mechanism 10 by passing through holes (not shown) provided in the first plate 14 and the end plate 14a.
  • a plurality of pistons 47 may be provided in the circumferential direction, and may be a comb-shaped piston.
  • a hole may be provided in the first friction plate 12 and the piston 47 may be passed through the hole.
  • the drive cam 45 is configured to rotate by torque from the drive device 42.
  • the drive device 42 is a worm gear, but it may be any other gear mechanism, belt mechanism, etc. as long as it can rotate the drive cam 45.
  • a driven cam inclined groove 44a is formed on the surface of the driven cam 44 on the driving cam 45 side.
  • a driving cam inclined groove 45a symmetrical to the driven cam inclined groove 44a is also provided on the surface of the driving cam 45 on the driven cam 44 side (see also FIGS. 5 to 7).
  • Three driven cam inclined grooves 44a are provided in the circumferential direction, and rolling elements 43 corresponding to each are provided. Note that an arbitrary number of driven cam inclined grooves 44a, drive cam inclined grooves 45a, and rolling elements 43 may be provided in the circumferential direction.
  • FIG. 5 shows a first state in which the driving cam 45 and the driven cam 44 are closest to each other. At this time, since the rolling element 43 is at the deepest position of the driven cam inclined groove 44a and the driven cam inclined groove 45a, the driving cam 45 and the driven cam 44 are closest to each other.
  • the rolling element 43 rolls in a shallow direction on the inclined surfaces of the driven cam inclined groove 44a and the driving cam inclined groove 45a, resulting in the second state shown in FIG. 6. .
  • the distance between the driving cam 45 and the driven cam 44 is smaller than that in the first state. spaced apart.
  • the rolling element 43 When the driving cam 45 further rotates in one direction from the second state, the rolling element 43 further rolls in a shallow direction on the inclined surfaces of the driven cam inclined groove 44a and the driving cam inclined groove 45a, and the third state shown in FIG. becomes.
  • the rolling elements 43 are at a shallower position between the driven cam inclined groove 44a and the driving cam inclined groove 45a than in the second state, so the distance between the driving cam 45 and the driven cam 44 is the same as in the second state. spaced apart. In this way, the ball cam mechanism 40 can convert the torque transmitted to the drive cam 45 into axial force.
  • the rolling element 43 rolls in a deeper direction on the slopes of the driven cam slope groove 44a and the drive cam slope groove 45a, and the second state shown in FIG. 6 is reached.
  • the driving cam 45 further rotates in the other direction
  • the rolling element 43 further rolls in the deeper direction on the inclined surfaces of the driven cam inclined groove 44a and the driving cam inclined groove 45a, resulting in the first state shown in FIG. 5.
  • the distance between the driving cam 45 and the driven cam 44 can be made to be apart or close to each other depending on the direction of rotation of the driving cam 45.
  • a structure in which either the driving cam 45 or the driven cam 44 is provided with an inclined groove may be adopted.
  • the two-stage transmission 100 shown in FIG. 1 shows a state in which the ball cam mechanism 40 is in the first state.
  • the end plate 14a is urged toward the first friction plate 12 and the first plate 14 by the elastic body 16, and the first frictional engagement mechanism 10 is in a fastened state.
  • the second frictional engagement mechanism 20 is in a released state.
  • the first frictional engagement mechanism 10 is in the engaged state, the case 50 and the hub 60, which are fixed in a non-rotatable manner, are fastened, so the hub 60 and the ring gear 36 are fixed in a non-rotatable manner.
  • the torque from the input shaft 52 is transmitted from the sun gear 32 to the pinion gear 34, and the torque due to the revolution of the pinion gear 34 is transmitted to the output shaft through the pinion carrier 35, so the torque from the input shaft 52 is decelerated and output. It can be transmitted to the shaft 62.
  • the two-stage transmission 100 shown in FIG. 2 shows a state in which the ball cam mechanism 40 is in the second state.
  • the piston 47 connected to the driven cam 44 presses the elastic body 16 in a direction to separate it from the end plate 14a, compressing the elastic body 16, so that the first frictional engagement mechanism 10 is in the released state. becomes.
  • a configuration may be adopted in which the piston 47 presses the end plate 14a toward the elastic body 16 and compresses the elastic body 16.
  • the second frictional engagement mechanism 20 is in a released state.
  • pinion gear 34 rotates and transmits the torque to ring gear 36 .
  • the pinion gear 34 does not revolve but rotates.
  • the torque from the input shaft 52 is not transmitted to the output shaft 62, and a neutral state can be achieved.
  • the two-stage transmission 100 shown in FIG. 3 shows the ball cam mechanism 40 in the third state.
  • the piston 47 connected to the driven cam 44 further presses the elastic body 16 in the direction of separating it from the end plate 14a, further compressing the elastic body 16, so that the second state One frictional engagement mechanism 10 is in a released state.
  • the second frictional engagement mechanism pressing portion 46 presses the second plate 24 in the direction of the second friction plate 22 and frictionally engages the second plate 24 and the second friction plate 22, so that the second frictional engagement mechanism 20 is in a fastened state.
  • the ring gear 36 and the pinion carrier 35 are engaged by the second friction engagement mechanism 20, when the torque from the sun gear 32 is transmitted to the pinion gear 34, the pinion gear 34 can neither rotate nor revolve. Therefore, the torque is transmitted to the ring gear 36 and pinion carrier 35. Therefore, the torque from the input shaft 52 can be transmitted to the output shaft 62 at a constant speed.
  • the second frictional engagement mechanism pressing section 46 is a bearing such as a ball bearing or a thrust bearing, the second frictional engagement mechanism pressing section 46 and the second plate 24 of the second frictional engagement mechanism 20 will come into contact with each other. Since the hub 60 can be prevented from being worn out during rotation, the life of the device can be extended.
  • first plates 14 and/or between the first plate 14 and the end plate 14a there is a direction in which the first plates 14 are spaced apart from each other and/or the first plate 14 and the end plate 14a.
  • An auxiliary elastic body for urging may be provided.
  • the number of rotations of the output shaft 62 can be changed in two stages using the ball cam mechanism 40 that uses one rolling element 43 in the radial direction, so the number of parts is relatively small. can do.
  • the input shaft Since the torque from 52 is passed through the second neutral state in which it is not transmitted to the output shaft 62, the possibility of an interlock state can be reduced and malfunctions can be easily prevented.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'objectif de la présente invention consiste à fournir une transmission à deux vitesses avec un petit nombre de composants, qui peut empêcher un régime transitoire. Selon une transmission à deux vitesses (100) de la présente invention, dans un premier état d'un mécanisme de came à billes, un premier mécanisme de mise en prise par frottement (10) disposé entre un boîtier fixé de manière non rotative (50) et un moyeu (60) comportant une couronne dentée (36) est dans un état fixé pour fixer de manière non rotative la couronne dentée (36), moyennant quoi un couple provenant d'un arbre d'entrée (52) peut être transmis à un arbre de sortie (62) en tant que couple par révolution d'un planétaire (32) à un pignon (34). Dans un deuxième état, le premier mécanisme de mise en prise par frottement (10) est dans un état libéré pour mettre la couronne dentée (36) au ralenti, et le pignon (34) tourne au lieu de réaliser une révolution même lorsque l'arbre d'entrée (52) tourne, moyennant quoi le couple provenant de l'arbre d'entrée (52) n'est pas transmis à l'arbre de sortie (62). Dans un troisième état, un second mécanisme de mise en prise par frottement (20) est dans un état fixé pour fixer la couronne dentée (36) et un support de pignon (35), permettant à un couple provenant de l'arbre d'entrée (52) d'être transmis à l'arbre de sortie (62) à une vitesse constante, moyennant quoi un mécanisme de came à billes (40) utilisant un corps rotatif (43) dans une direction radiale peut décaler la vitesse de rotation de l'arbre de sortie (62) en deux étapes. En raison du deuxième état en tant qu'état neutre interposé entre le premier état et le troisième état, le nombre de composants peut être relativement réduit et un régime transitoire peut être facilement empêché.
PCT/JP2022/016550 2022-03-31 2022-03-31 Transmission à deux vitesses WO2023188281A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/016550 WO2023188281A1 (fr) 2022-03-31 2022-03-31 Transmission à deux vitesses

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Application Number Priority Date Filing Date Title
PCT/JP2022/016550 WO2023188281A1 (fr) 2022-03-31 2022-03-31 Transmission à deux vitesses

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WO2023188281A1 true WO2023188281A1 (fr) 2023-10-05

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62200844U (fr) * 1986-06-12 1987-12-21
CN108443434A (zh) * 2018-05-21 2018-08-24 福建中青集团有限公司 电动汽车变速器用单作动器换档执行机构及变速器
WO2020084913A1 (fr) * 2018-10-22 2020-04-30 ジヤトコ株式会社 Mécanisme de commutation vers l'avant/vers l'arrière
JP2021014198A (ja) * 2019-07-12 2021-02-12 Ｎｓｋワーナー株式会社 インホイールモータ型駆動ユニット

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62200844U (fr) * 1986-06-12 1987-12-21
CN108443434A (zh) * 2018-05-21 2018-08-24 福建中青集团有限公司 电动汽车变速器用单作动器换档执行机构及变速器
WO2020084913A1 (fr) * 2018-10-22 2020-04-30 ジヤトコ株式会社 Mécanisme de commutation vers l'avant/vers l'arrière
JP2021014198A (ja) * 2019-07-12 2021-02-12 Ｎｓｋワーナー株式会社 インホイールモータ型駆動ユニット

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