WO2023188281A1 - Two-speed transmission - Google Patents

Two-speed transmission 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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state
engagement mechanism
frictional engagement
cam
hub
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PCT/JP2022/016550
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French (fr)
Japanese (ja)
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雅俊 佐藤
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株式会社ダイナックス
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Priority to PCT/JP2022/016550 priority Critical patent/WO2023188281A1/en
Publication of WO2023188281A1 publication Critical patent/WO2023188281A1/en

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    • 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.

Abstract

The objective of the present invention is to provide a two-speed transmission with a small number of components, that can prevent a glitch. According to a two-speed transmission (100) of the present invention, in a first state of a ball cam mechanism, a first friction engagement mechanism (10) disposed between an unrotatably fixed case (50) and a hub (60) including a ring gear (36) is in a fastened state to unrotatably fix the ring gear (36), whereby torque from an input shaft (52) can be transmitted to an output shaft (62) as torque by revolution from a sun gear (32) to a pinion gear (34). In a second state, the first friction engagement mechanism (10) is in a released state to make the ring gear (36) run idle, and the pinion gear (34) rotates instead of revolving even when the input shaft (52) rotates, whereby the torque from the input shaft (52) is not transmitted to the output shaft (62). In a third state, a second friction engagement mechanism (20) is in a fastened state to fasten the ring gear (36) and a pinion carrier (35), permitting torque from the input shaft (52) to be transmitted to the output shaft (62) at constant velocity, whereby a ball cam mechanism (40) employing one rotating body (43) in a radial direction can shift the rotating speed of the output shaft (62) in two stages. Due to the second state as a neutral state being interposed between the first state and the third state, the number of components can be relatively reduced and a glitch can be easily prevented.

Description

２段変速装置2-speed transmission
　本発明は、出力軸の回転数を２段階で変速させる２段変速装置に関する。 The present invention relates to a two-stage transmission device that changes the rotational speed of an output shaft in two stages.
　近年、電気自動車やハイブリット車の開発が進んでいる。一般的に、電気自動車やハイブリット車は電池に充電された電気の力で、モータを作動させる仕組みであるから、モータに伝える電力を変化させることによって回転数を変えることができるので、変速装置を具えなくても車両を変速させることができる。 In recent years, the development of electric vehicles and hybrid vehicles has progressed. Generally, electric cars and hybrid cars operate the motor using the electric power charged in the battery, so the rotation speed can be changed by changing the electric power transmitted to the motor, so the transmission can be changed. You can shift your vehicle without it.
　しかし、変速装置を具えずに、発進時のトルクと、高速走行時の回転効率の良さを両立させようとすると、モータを大型化させる必要があるため、変速装置を具えた方がモータの小型化を図ることができ、全体としてコンパクトにすることができる。また、システムの簡略化によるコスト低減や電力消費を抑えるために油圧システムを不要とすることが望まれており、これを実現する変速装置として、以下のものが提案されている。 However, if you try to achieve both high starting torque and good rotational efficiency when driving at high speeds without a transmission, you will need to make the motor larger, so it is better to have a transmission and make the motor smaller. The overall design can be made more compact. Furthermore, it is desired to eliminate the need for a hydraulic system in order to reduce costs and reduce power consumption by simplifying the system, and the following transmission devices have been proposed to achieve this.
特開２０２０－１９０２８０号公報JP2020-190280A
　特許文献１には、駆動カムと、第一・第二被駆動カムを有するカム装置と、第一摩擦係合機構と、第二摩擦係合機構とが具えられた動力伝達経路切換装置及び２段変速機が開示されている。第一被駆動カムを駆動カムとの軸方向間隔が拡がる方向に変位させることで第一摩擦係合機構を接続・切断し、第二被駆動カムを駆動カムとの軸方向間隔が縮まる方向に変位させることで第二摩擦係合機構を接続・切断することができるので、油圧システムを用いずとも電動アクチュエータによって、第一摩擦係合機構と第二摩擦係合機構とを切り換えることができるとされている。 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.
　しかし、径方向に並列した第一転動体と第二転動体の２つの転動体をコントロールする必要があるため、制御が容易でなく、インターロック状態などの予期せぬ誤作動に繋がる可能性もある。また、転動体、被駆動カム、弾性体を、それぞれ二つずつ設けなければならないので、部品点数が多くなる。 However, since it is necessary to control two rolling elements, the first rolling element and the second rolling element, which are parallel to each other in the radial direction, control is not easy and may lead to unexpected malfunctions such as interlock conditions. be. Furthermore, since two rolling elements, two driven cams, and two elastic bodies must be provided, the number of parts increases.
　そこで、本発明は、部品点数が少なく、誤作動を防止することができる２段変速装置を提供することをその目的とする。 Therefore, an object of the present invention is to provide a two-stage transmission that has a small number of parts and can prevent malfunctions.
　本発明は、回転不能に固定されたケース、前記ケースの内周側に配設されている入力軸、前記入力軸上に回転可能に設けられているハブ、前記ケースとハブの間に配設されている第一摩擦係合機構、前記ハブと入力軸の間に配設されている遊星歯車機構、前記遊星歯車機構のピニオンキャリアと連結されている出力軸、前記ハブとピニオンキャリアの間に配設されている第二摩擦係合機構、駆動カムと転動体と被駆動カムを有するボールカム機構、及び前記駆動カムにトルクを伝達する駆動装置を具え、
　前記第一摩擦係合機構は、弾性体によって付勢されることにより締結状態とされるように構成され、
　前記遊星歯車機構は、前記入力軸上に設けられたサンギアと、前記ハブ上に設けられたリングギアと、前記サンギアとリングギアに噛合い、前記ピニオンキャリア上に回転可能に設けられたピニオンギアを具え、
　前記被駆動カムは、前記第一摩擦係合機構を貫通するピストンと、前記第二摩擦係合機構押圧部を具え、
　前記駆動カムと被駆動カムが最も近接している第一状態から、前記駆動カムが前記駆動装置からのトルクにより回転すると、前記転動体が転動し、前記駆動カムと被駆動カムを離間させて第二状態とし、前記駆動カムが前記駆動装置からのトルクによりさらに回転すると、前記転動体が転動し、前記駆動カムと被駆動カムをさらに離間させて第三状態とするように構成され、
　前記第一状態では、前記第一摩擦係合機構が前記弾性体によって付勢されて締結状態で、前記第二摩擦係合機構は解放状態であり、前記第二状態では、前記第二摩擦係合機構は解放状態で、前記ピストンが前記弾性体を圧縮して前記第一摩擦係合機構を解放状態とし、前記第三状態では、前記ピストンが前記弾性体を圧縮して前記第一摩擦係合機構を解放状態とし、前記第二摩擦係合機構押圧部が前記第二摩擦係合機構と係合して該第二摩擦係合機構を締結状態にすることを特徴とする２段変速装置によって前記課題を解決した。 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. Equipped with
The driven cam includes a piston that passes through the first frictional engagement mechanism, and a pressing portion for the second frictional engagement mechanism,
When 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. When 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. ,
In the first 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. When the engagement mechanism is in a released state, the piston compresses the elastic body to bring the first frictional engagement mechanism into a released state, and in the third state, the piston compresses the elastic body and brings the first frictional engagement mechanism into the released 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 above problem was solved.
　本発明の２段変速装置によれば、第一状態において、リングギアが回転不能に固定されるため、入力軸からのトルクはサンギアからピニオンギアに伝達され、ピニオンギアの公転によるトルクをピニオンキャリアを通じて出力軸に伝達することができるので、入力軸からのトルクを減速して出力軸に伝達させることができる。第二状態においては、リングギアは空転するので、入力軸が回転してもピニオンギアは公転せずに自転するから、入力軸からのトルクは出力軸に伝達されず、ニュートラル状態とすることができる。第三状態においては、リングギアとピニオンキャリアが第二摩擦係合機構によって締結されるので、入力軸からのトルクを等速で出力軸に伝達させることができる。このように、本発明では、径方向に一つの転動体を使用したボールカム機構で、出力軸の回転数を２段階で変速させることができ、第一状態と第三状態の間にニュートラル状態である第二状態を介するから、部品点数を比較的少なくすることができ、誤作動を防止し易い。 According to the two-stage transmission of the present invention, 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. In the second state, 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. In the third state, 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. As described above, in the present invention, 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.
　また、第二摩擦係合機構押圧部をベアリングとすれば、第二摩擦係合機構押圧部と第二摩擦係合機構が接触し、ハブが回転しているときの摩耗を防ぐことができるので、装置の寿命を延ばすことができる。 Furthermore, if 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.
本発明の２段変速装置の第一状態の断面図。FIG. 1 is a sectional view of the two-stage transmission of the present invention in a first state. 図１の第二状態の断面図。FIG. 2 is a sectional view of the second state in FIG. 1; 図１の第三状態の断面図。FIG. 2 is a sectional view of the third state in FIG. 1; ボールカム機構の溝部の正面図。FIG. 3 is a front view of the groove portion of the ball cam mechanism. ボールカム機構の第一状態の拡大断面図。FIG. 3 is an enlarged cross-sectional view of the ball cam mechanism in a first state. 図５の第二状態の拡大断面図。FIG. 6 is an enlarged sectional view of the second state of FIG. 5; 図５の第三状態の拡大断面図。FIG. 6 is an enlarged sectional view of the third state in FIG. 5;
　以下、本発明の実施形態を図１～７を参照して説明する。但し、本発明はこの実施形態に限定されるものではない。なお、２段変速装置１００の構成は、軸心Ｘに対して基本的に対称なので、図１～３では、軸心Ｘに対する径方向片側のみを示している。 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.
　図１に示すように、２段変速装置１００は、第一摩擦係合機構１０、第二摩擦係合機構２０、遊星歯車機構３０、ボールカム機構４０、駆動装置４２、ケース５０、入力軸５２、ハブ６０、及び出力軸６２を具えている。遊星歯車機構３０、第二摩擦係合機構２０、ボールカム機構４０は、この順で軸方向に並列するように配設されている。 As shown in FIG. 1, 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.
　まず、ケース５０は回転不能に固定される。入力軸５２及び出力軸６２は、ケース５０の内周側に回転可能に配設されている。ハブ６０は、入力軸５２上に回転可能に設けられている。ケース５０とハブ６０の間には、第一摩擦係合機構１０が配設されている。ハブ６０と入力軸５２の間には、遊星歯車機構３０が配設されている。遊星歯車機構３０のピニオンキャリア３５は、出力軸６２と連結されている。ハブ６０とピニオンキャリア３５の間には、第二摩擦係合機構２０が配設されている。ボールカム機構４０は、駆動カム４５、転動体４３、被駆動カム４４を具え、ケース５０の内周側に配設されている。駆動カム４５には、駆動装置４２からトルクが伝達される。 First, 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 .
　第一摩擦係合機構１０及び第二摩擦係合機構２０は、それぞれ、第一摩擦板１２と第一プレート１４の組合せ、第二摩擦板２２と第二プレート２４の組合せから構成されている。第一摩擦板１２は、ハブ６０の外周面上にスプライン嵌合しており、第二摩擦板２２は、ピニオンキャリア３５上にスプライン嵌合している。第一プレート１４は、ケース５０の内周面上にスプライン嵌合しており、第二プレート２４は、ハブ６０の内周面上にスプライン嵌合している。なお、第一摩擦板１２をケース５０の内周面上に、第一プレート１４をハブ６０の外周面上に、第二摩擦板２２をハブ６０の内周面上に、第二プレート２４をピニオンキャリア３５上にそれぞれスプライン嵌合させた構成としてもよい。第一摩擦係合機構１０のエンドプレート１４ａは、弾性体１６と係合しており、弾性体１６により摩擦板１２方向に付勢されている。弾性体１６としては、コイルばねや皿ばねを適用すればよい。第一摩擦係合機構１０が締結状態になると、ケース５０とハブ６０が締結され、ハブ６０は回転不能に固定される。第二摩擦係合機構２０が締結状態になると、ハブ６０とピニオンキャリア３５が締結される。 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, and 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, and 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. As the elastic body 16, a coil spring or a disc spring may be used. When the first frictional engagement mechanism 10 enters the engaged state, the case 50 and the hub 60 are engaged, and the hub 60 is fixed non-rotatably. When the second frictional engagement mechanism 20 enters the engaged state, the hub 60 and pinion carrier 35 are engaged.
　遊星歯車機構３０は、サンギア３２，リングギア３６、ピニオンキャリア３５、及びピニオンギア３４から構成されている。サンギア３２は、入力軸５２上に設けられている。リングギア３６は、ハブ６０の内周面上にスプライン嵌合することによりハブ６０上に設けられている。ピニオンギア３４は、ピニオンキャリア３５上に回転可能に設けられており、サンギア３２及びリングギア３６に噛合っている。なお、ピニオンギア３４は周方向に複数設けることができる。 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.
　ボールカム機構４０は、駆動装置４２、転動体４３、被駆動カム４４、及び駆動カム４５から構成されている。転動体４３は、駆動カム４５及び被駆動カムによって挟持されている。被駆動カム４４は、駆動カム４５側の反対側にピストン４７と第二摩擦係合機構押圧部４６を具えている。ピストン４７は棒状のものであり、第一プレート１４及びエンドプレート１４ａに設けられている孔（図示省略）を貫通することにより、第一摩擦係合機構１０を貫通している。ピストン４７は、周方向に複数設けることができ、櫛状のピストンとしてもよい。なお、ケース５０の内周面上に第一摩擦板１２が設けられている構成の場合は、第一摩擦板１２に孔を設け、ピストン４７を貫通させればよい。駆動カム４５は、駆動装置４２からのトルクにより回転するように構成されている。２段変速装置１００では、駆動装置４２は、ウォームギアであるが、他のギア機構やベルト機構など、駆動カム４５を回転させることができるものであればよい。 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. In addition, in the case of the structure in which the first friction plate 12 is provided on the inner peripheral surface of the case 50, 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. In the two-stage transmission 100, 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.
　図４に示すように、被駆動カム４４の駆動カム４５側の面には、被駆動カム傾斜溝４４ａが形成されている。一方、被駆動カム傾斜溝４４ａと対称的な駆動カム傾斜溝４５ａが駆動カム４５の被駆動カム４４側の面にも設けられている（図５～７も参照。）。被駆動カム傾斜溝４４ａは、周方向に３つ設けられており、それぞれに対応する転動体４３が配設されている。なお、被駆動カム傾斜溝４４ａ、駆動カム傾斜溝４５ａ、及び転動体４３は、周方向に任意の数で設ければよい。 As shown in FIG. 4, a driven cam inclined groove 44a is formed on the surface of the driven cam 44 on the driving cam 45 side. On the other hand, 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.
　図５は、駆動カム４５と被駆動カム４４が最も近接している第一状態を示している。このとき、転動体４３は、被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの最も深い位置にあるため、駆動カム４５と被駆動カム４４は最も近接する。 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.
　第一状態から駆動カム４５が一方向に回転すると、転動体４３が被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの傾斜面を浅い方向に転動し、図６に示す第二状態となる。第二状態では、転動体４３が第一状態に比べて被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの浅い位置にあるため、駆動カム４５と被駆動カム４４の間隔は第一状態のときよりも離間する。 When the driving cam 45 rotates in one direction from the first state, 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. . In the second state, since the rolling element 43 is at a shallower position between the driven cam inclined groove 44a and the driving cam inclined groove 45a than in the first state, the distance between the driving cam 45 and the driven cam 44 is smaller than that in the first state. spaced apart.
　第二状態から駆動カム４５が一方向にさらに回転すると、転動体４３が被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの傾斜面を浅い方向にさらに転動し、図７に示す第三状態となる。第三状態では、転動体４３が第二状態に比べて被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの浅い位置にあるため、駆動カム４５と被駆動カム４４の間隔は第二状態のときよりも離間する。このようにして、ボールカム機構４０によれば、駆動カム４５に伝達されたトルクを軸方向の力に変換することができる。 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. In the third state, 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.
　第三状態から駆動カム４５が他方向に回転すると、転動体４３が被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの傾斜面を深い方向に転動し、図６に示す第二状態となり、駆動カム４５が他方向にさらに回転すると、転動体４３が被駆動カム傾斜溝４４ａと駆動カム傾斜溝４５ａの傾斜面を深い方向にさらに転動し、図５に示す第一状態となる。かくして、ボールカム機構４０では、駆動カム４５の回転方向により、駆動カム４５と被駆動カム４４の間隔を離間及び近接させることができる。なお、上記では、駆動カム４５と被駆動カム４４のいずれもが傾斜溝を具える構成を説明したが、駆動カム４５と被駆動カム４４のいずれかが傾斜溝を具える構成としてもよい。 When the drive cam 45 rotates in the other direction from the third state, 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. When 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. Thus, in the ball cam mechanism 40, 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. In addition, although the structure in which both the driving cam 45 and the driven cam 44 are provided with an inclined groove has been described above, a structure in which either the driving cam 45 or the driven cam 44 is provided with an inclined groove may be adopted.
　図１に示す２段変速装置１００は、ボールカム機構４０が第一状態にあるときを示している。第一状態では、弾性体１６によってエンドプレート１４ａが第一摩擦板１２及び第一プレート１４方向に付勢されており、第一摩擦係合機構１０が締結状態にある。このとき、第二摩擦係合機構２０は、解放状態である。第一摩擦係合機構１０が締結状態であると、回転不能に固定されているケース５０とハブ６０が締結されているため、ハブ６０とリングギア３６が回転不能に固定される。そうすると、入力軸５２からのトルクはサンギア３２からピニオンギア３４に伝達され、ピニオンギア３４の公転によるトルクがピニオンキャリア３５を通じて出力軸に伝達されるので、入力軸５２からのトルクを減速して出力軸６２に伝達させることができる。 The two-stage transmission 100 shown in FIG. 1 shows a state in which the ball cam mechanism 40 is in the first state. 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. At this time, the second frictional engagement mechanism 20 is in a released state. When 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. Then, 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.
　図２に示す２段変速装置１００は、ボールカム機構４０が第二状態にあるときを示している。第二状態では、被駆動カム４４に連結されているピストン４７が弾性体１６をエンドプレート１４ａと離間させる方向に押圧し、弾性体１６を圧縮させるので、第一摩擦係合機構１０は解放状態となる。なお、ピストン４７がエンドプレート１４ａを弾性体１６方向に押圧し、弾性体１６を圧縮する構成としてもよい。また、第二摩擦係合機構２０は解放状態である。第二状態において、入力軸５２からサンギア３２にトルクが伝達されると、ピニオンギア３４が回転し、そのトルクをリングギア３６へ伝達する。このとき、リングギア３６は入力軸５２上を空転するので、ピニオンギア３４は公転せずに自転する。かくして、入力軸５２からのトルクは出力軸６２に伝達されず、ニュートラル状態とすることができる。 The two-stage transmission 100 shown in FIG. 2 shows a state in which the ball cam mechanism 40 is in the second state. 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. Note that 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. Further, the second frictional engagement mechanism 20 is in a released state. In the second state, when torque is transmitted from input shaft 52 to sun gear 32 , pinion gear 34 rotates and transmits the torque to ring gear 36 . At this time, since the ring gear 36 idles on the input shaft 52, the pinion gear 34 does not revolve but rotates. Thus, the torque from the input shaft 52 is not transmitted to the output shaft 62, and a neutral state can be achieved.
　図３に示す２段変速装置１００は、ボールカム機構４０が第三状態にあるときを示している。第三状態では、第二状態と比べて、被駆動カム４４に連結されているピストン４７が弾性体１６をエンドプレート１４ａと離間させる方向にさらに押圧し、弾性体１６をさらに圧縮させるので、第一摩擦係合機構１０は解放状態でなる。一方、第二摩擦係合機構押圧部４６が第二プレート２４を第二摩擦板２２方向に押圧し、第二プレート２４と第二摩擦板２２を摩擦係合させるので、第二摩擦係合機構２０は締結状態となる。このとき、リングギア３６とピニオンキャリア３５が第二摩擦係合機構２０によって締結されるので、サンギア３２からのトルクがピニオンギア３４に伝達されると、ピニオンギア３４は自転も公転もすることができず、そのトルクをリングギア３６とピニオンキャリア３５に伝達する。よって、入力軸５２からのトルクを等速で出力軸６２に伝達させることができる。なお、第二摩擦係合機構押圧部４６をボールベアリングやスラストベアリング等のベアリングとすれば、第二摩擦係合機構押圧部４６と第二摩擦係合機構２０の第二プレート２４が接触し、ハブ６０が回転しているときの摩耗を防ぐことができるので、装置の寿命を延ばすことができる。 The two-stage transmission 100 shown in FIG. 3 shows the ball cam mechanism 40 in the third state. In the third state, compared to the second 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. On the other hand, 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. At this time, since 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. Note that if 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.
　ここで、図示は省略するが、第一プレート１４同士及び／又は第一プレート１４とエンドプレート１４ａの間に、第一プレート１４同士及び／又は第一プレート１４とエンドプレート１４ａを離間させる方向に付勢する補助用弾性体を設けることができる。本構成とすれば、第一摩擦係合機構１０が解放状態のとき、第一プレート１４と第一摩擦板１２が貼付くことや引摺りトルクの発生を防止することができ、２段変速装置１００の誤作動を防止することができる。 Here, although not shown in the drawings, between the 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. With this configuration, when the first friction engagement mechanism 10 is in the released state, it is possible to prevent the first plate 14 and the first friction plate 12 from sticking together and to prevent the generation of dragging torque, and it is possible to prevent the two-stage transmission 100 malfunctions can be prevented.
　このように、２段変速装置１００では、径方向に一つの転動体４３を使用したボールカム機構４０で、出力軸６２の回転数を２段階で変速させることができるので、部品点数を比較的少なくすることができる。また、入力軸５２からのトルクを減速して出力軸６２に伝達する第一状態と、入力軸５２からのトルクを等速で出力軸６２に伝達する第三状態が切換る際に、入力軸５２からのトルクが出力軸６２に伝達されないニュートラル状態の第二状態を介するので、インターロック状態になる可能性を低減させることができ、誤作動を防止し易い。 In this way, in the two-stage transmission 100, 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. Further, when switching between the first state in which the torque from the input shaft 52 is decelerated and transmitted to the output shaft 62 and the third state in which the torque from the input shaft 52 is transmitted at a constant speed to the output shaft 62, 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.
　以上に説明したとおり、本発明によれば、部品点数が少なく、誤作動を防止することができる２段変速装置を提供することができる。 As explained above, according to the present invention, it is possible to provide a two-stage transmission that has a small number of parts and can prevent malfunctions.
　１０　　第一摩擦係合機構
　１６　　弾性体
　２０　　第二摩擦係合機構
　３０　　遊星歯車機構
　３２　　サンギア
　３４　　ピニオンギア
　３５　　ピニオンキャリア
　３６　　リングギア
　４０　　ボールカム機構
　４２　　駆動装置
　４３　　転動体
　４４　　被駆動カム
　４５　　駆動カム
　４６　　第二摩擦係合機構押圧部（ベアリング）
　４７　　ピストン
　５０　　ケース
　５２　　入力軸
　６０　　ハブ
　６２　　出力軸
　１００　２段変速装置 10 First friction engagement mechanism 16 Elastic body 20 Second friction engagement mechanism 30 Planetary gear mechanism 32 Sun gear 34 Pinion gear 35 Pinion carrier 36 Ring gear 40 Ball cam mechanism 42 Drive device 43 Rolling element 44 Driven cam 45 Drive cam 46 No. Two-friction engagement mechanism pressing part (bearing)
47 Piston 50 Case 52 Input shaft 60 Hub 62 Output shaft 100 Two-stage transmission

Claims (2)

  1. 　回転不能に固定されたケース、前記ケースの内周側に配設されている入力軸、前記入力軸上に回転可能に設けられているハブ、前記ケースとハブの間に配設されている第一摩擦係合機構、前記ハブと入力軸の間に配設されている遊星歯車機構、前記遊星歯車機構のピニオンキャリアと連結されている出力軸、前記ハブとピニオンキャリアの間に配設されている第二摩擦係合機構、駆動カムと転動体と被駆動カムを有するボールカム機構、及び前記駆動カムにトルクを伝達する駆動装置を具え、
    　前記第一摩擦係合機構は、弾性体によって付勢されることにより締結状態とされるように構成され、
    　前記遊星歯車機構は、前記入力軸上に設けられたサンギアと、前記ハブ上に設けられたリングギアと、前記サンギアとリングギアに噛合い、前記ピニオンキャリア上に回転可能に設けられたピニオンギアを具え、
    　前記被駆動カムは、前記第一摩擦係合機構を貫通するピストンと、前記第二摩擦係合機構押圧部を具え、
    　前記駆動カムと被駆動カムが最も近接している第一状態から、前記駆動カムが前記駆動装置からのトルクにより回転すると、前記転動体が転動し、前記駆動カムと被駆動カムを離間させて第二状態とし、前記駆動カムが前記駆動装置からのトルクによりさらに回転すると、前記転動体が転動し、前記駆動カムと被駆動カムをさらに離間させて第三状態とするように構成され、
    　前記第一状態では、前記第一摩擦係合機構が前記弾性体によって付勢されて締結状態で、前記第二摩擦係合機構は解放状態であり、前記第二状態では、前記第二摩擦係合機構は解放状態で、前記ピストンが前記弾性体を圧縮して前記第一摩擦係合機構を解放状態とし、前記第三状態では、前記ピストンが前記弾性体を圧縮して前記第一摩擦係合機構を解放状態とし、前記第二摩擦係合機構押圧部が前記第二摩擦係合機構と係合して該第二摩擦係合機構を締結状態にすることを特徴とする、
    　２段変速装置。     a case fixed to be non-rotatable; 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 friction engagement mechanism, a planetary gear mechanism disposed between the hub and the input shaft, an output shaft coupled to a pinion carrier of the planetary gear mechanism, and a friction engagement mechanism disposed between the hub and the pinion carrier; a ball cam mechanism having a drive cam, a rolling element, and a driven cam, and a drive device that transmits torque to the drive 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. Equipped with
    The driven cam includes a piston that passes through the first frictional engagement mechanism, and a pressing portion for the second frictional engagement mechanism,
    When 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. When 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. ,
    In the first 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. When the engagement mechanism is in a released state, the piston compresses the elastic body to bring the first frictional engagement mechanism into a released state, and in the third state, the piston compresses the elastic body and brings the first frictional engagement mechanism into the released state. The engaging 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.
    2-speed transmission.
  2. 　前記第二摩擦係合機構押圧部がベアリングである、請求項１の２段変速装置。 The two-stage transmission according to claim 1, wherein the second frictional engagement mechanism pressing portion is a bearing.
PCT/JP2022/016550 2022-03-31 2022-03-31 Two-speed transmission WO2023188281A1 (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62200844U (en) * 1986-06-12 1987-12-21
CN108443434A (en) * 2018-05-21 2018-08-24 福建中青集团有限公司 Electric automobile gear device single actuator gear-shifting actuating mechanism and speed changer
WO2020084913A1 (en) * 2018-10-22 2020-04-30 ジヤトコ株式会社 Forward/reverse switching mechanism
JP2021014198A (en) * 2019-07-12 2021-02-12 Ｎｓｋワーナー株式会社 In-wheel motor type drive unit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62200844U (en) * 1986-06-12 1987-12-21
CN108443434A (en) * 2018-05-21 2018-08-24 福建中青集团有限公司 Electric automobile gear device single actuator gear-shifting actuating mechanism and speed changer
WO2020084913A1 (en) * 2018-10-22 2020-04-30 ジヤトコ株式会社 Forward/reverse switching mechanism
JP2021014198A (en) * 2019-07-12 2021-02-12 Ｎｓｋワーナー株式会社 In-wheel motor type drive unit

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