JP2015202846A - Drive mechanism - Google Patents

Abstract

A drive mechanism capable of ensuring the amount of power generated by a rotating machine and suppressing power consumption when starting an engine is provided. SOLUTION: An engine 2, a drive shaft 7a, a rotating machine MG, a first clutch 21 provided between the engine and the drive shaft, a transmission shaft 26, and a rotary shaft closer to the engine than the first clutch. 3a and the drive shaft side rotation shaft 7a, the connection mechanism 27 for connecting the rotation shaft having the higher rotational speed and the transmission shaft, the second clutch 22 provided between the engine and the rotating machine, and the transmission shaft And a one-way clutch 23 that allows transmission of power from the rotary machine to the transmission shaft and interrupts transmission of power from the rotary machine to the transmission shaft. When the engine is started, the second clutch is engaged to start the engine. The second clutch is released except when. [Selection] Figure 1

Description

  The present invention relates to a drive mechanism.

  Conventionally, there is a technique of selectively driving an auxiliary machine with a plurality of rotating shafts. For example, Patent Document 1 includes an output shaft provided so that power is output from a power transmission mechanism and power can be transmitted to and from a drive wheel of a vehicle. In a drive device that drives an accessory with power having a higher rotational speed, the power transmission mechanism includes a transmission control clutch and a transmission control brake that can limit power transmission between the turbine and the output shaft. A vehicle drive device technology is disclosed.

JP 2011-231844 A

  In a vehicle in which an auxiliary machine is selectively driven by a plurality of rotating shafts, a vehicle configuration in which a rotating machine is mounted as an auxiliary machine and an engine is started by the rotating machine can be considered. In this case, if the engine and the rotating machine are always connected, the engine is rotated when the inertial running is performed, and the running resistance increases. As a result, a sufficient amount of power generated by the rotating machine cannot be secured. If the rotating machine and the rotating shaft are connected so that torque can be transmitted in both directions, the torque of the rotating machine is transmitted not only to the engine but also to the rotating shaft when the engine is started by the rotating machine. There is a possibility that power consumption at the time of engine start increases.

  The objective of this invention is providing the drive mechanism which can implement | achieve securing of the electric power generation amount by a rotary machine, and suppression of the power consumption at the time of engine starting.

  The drive mechanism of the present invention includes an engine, a drive shaft, a rotating machine, a first clutch provided between the engine and the drive shaft, a transmission shaft, and the engine side of the first clutch. A connection mechanism that connects the rotation shaft and the rotation shaft on the drive shaft side to the transmission shaft having a higher rotational speed, and a second clutch provided between the engine and the rotating machine; A one-way clutch that allows transmission of power from the transmission shaft to the rotating machine and interrupts transmission of power from the rotating machine to the transmission shaft, and engages the second clutch when starting the engine. The second clutch is released except when the engine is started.

  A drive mechanism according to the present invention includes an engine, a drive shaft, a rotating machine, a first clutch provided between the engine and the drive shaft, a transmission shaft, a rotation shaft closer to the engine than the first clutch, A connection mechanism that connects the rotation shaft on the drive shaft side with the higher rotation speed to the transmission shaft, a second clutch provided between the engine and the rotation machine, and a transmission shaft to the rotation machine A one-way clutch that allows transmission of power and interrupts transmission of power from the rotating machine to the transmission shaft, and engages the second clutch when starting the engine, and the second clutch except when starting the engine To release. According to the drive mechanism of the present invention, there is an effect that it is possible to secure the amount of power generated by the rotating machine and to suppress the power consumption when starting the engine.

FIG. 1 is a diagram illustrating a schematic configuration of a vehicle according to the embodiment. FIG. 2 is a diagram illustrating a schematic configuration of a vehicle according to a first modification of the embodiment. Drawing 3 is a figure showing the schematic structure of the vehicles concerning the 2nd modification of an embodiment.

  Hereinafter, a drive mechanism according to an embodiment of the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or those that are substantially the same.

[Embodiment]
An embodiment will be described with reference to FIG. The present embodiment relates to a drive mechanism. FIG. 1 is a diagram showing a schematic configuration of a vehicle according to an embodiment of the present invention.

  As shown in FIG. 1, the vehicle 100 has a drive mechanism 1. The drive mechanism 1 of the present embodiment includes an engine 2, a rotation shaft 7a (drive shaft), a rotating machine MG, a first clutch 21, a transmission shaft 26, a connection mechanism 27, a second clutch 22, and a one-way. The clutch 23 is included. The drive mechanism 1 may further include an ECU 20 as a control unit.

  The engine 2 converts the combustion energy of the fuel into a rotational motion and outputs it to the torque converter 3. The torque converter 3 includes a pump impeller 3a, a turbine runner 3b, a stator 3c, and a lockup clutch 3d. The pump impeller 3a is connected to the crankshaft 2a of the engine 2 and rotates integrally with the crankshaft 2a. The pump impeller 3a and the turbine runner 3b transmit torque via a fluid. The stator 3c amplifies and transmits torque from the pump impeller 3a to the turbine runner 3b. The lock-up clutch 3d is a friction clutch that connects the input shaft of the torque converter 3 and the turbine runner 3b.

  The turbine runner 3 b is connected to the input shaft 5 of the transmission 4. The transmission 4 of the present embodiment is a belt-type continuously variable transmission, and in addition to the input shaft 5, the first clutch 21, the planetary gear mechanism 10, the reverse brake 6, the primary pulley 7, the secondary pulley 8, the third The clutch 15 is configured. The planetary gear mechanism 10 is a double planetary type and includes a sun gear 11, a pinion gear 12, a ring gear 13, and a carrier 14. The first clutch 21 is provided between the input shaft 5 and the carrier 14. The first clutch 21 is a control clutch that can be arbitrarily engaged and released. The first clutch 21 is engaged by, for example, supplied hydraulic pressure. The sun gear 11 is connected to the input shaft 5 and rotates integrally with the input shaft 5. The reverse brake 6 regulates the rotation of the ring gear 13.

  The carrier 14 is connected to the rotation shaft 7 a of the primary pulley 7. In this specification, the rotation shaft 7a of the primary pulley 7 is also referred to as a “drive shaft”. An endless belt 9 is wound around the primary pulley 7 and the secondary pulley 8. The third clutch 15 is provided between the secondary pulley 8 and the counter drive gear 16. The third clutch 15 is a control clutch that can be arbitrarily engaged and released. The counter drive gear 16 meshes with the counter driven gear 17. The counter driven gear 17 is connected to the drive pinion gear 18. The drive pinion gear 18 meshes with the diff ring gear 19. The differential ring gear 19 is connected to the left and right drive wheels via a differential mechanism. In the transmission 4, when the first clutch 21 is engaged and the reverse brake 6 is released, the carrier 14 and the sun gear 11 are connected. Thereby, the input shaft 5 and the primary pulley 7 are connected so that rotation is integral. When the first clutch 21 is released and the reverse brake 6 is engaged, the planetary gear mechanism 10 converts the rotation of the input shaft 5 into the rotation in the reverse direction and transmits the rotation from the carrier 14 to the primary pulley 7. Is done.

  An oil pump 24 and an auxiliary machine 25 are mounted on the vehicle 100. The oil pump 24 is disposed on the radially outer side of the planetary gear mechanism 10. A transmission shaft 26 is disposed in parallel with the axial direction of the engine 2. The transmission shaft 26 faces the planetary gear mechanism 10, the first clutch 21, the torque converter 3, and the engine 2 in the radial direction. The oil pump 24 is disposed in a space portion between the transmission shaft 26 and the planetary gear mechanism 10. The oil pump 24 is connected to the transmission shaft 26 via a gear mechanism 24a. The gear ratio of the gear mechanism 24a of this embodiment is 1 or substantially 1. That is, the rotational speeds of the transmission shaft 26 and the oil pump 24 are substantially the same. The oil pump 24 supplies oil to each part of the drive mechanism 1 to perform lubrication, cooling, and the like.

  The connection mechanism 27 connects the transmission shaft 26 and the rotation shaft on the higher rotation speed side of the pump impeller 3a and the rotation shaft 7a. The pump impeller 3 a is a rotating shaft closer to the engine 2 than the first clutch 21. The rotating shaft 7 a is a rotating shaft closer to the drive shaft than the first clutch 21. The connection mechanism 27 has two one-way clutches 28 and 29, and selectively connects the transmission shaft 26 and the pump impeller 3a or the transmission shaft 26 and the rotary shaft 7a.

  The input side one-way clutch 28 is disposed on the transmission shaft 26. The input-side one-way clutch 28 is disposed on the engine 2 side in the axial direction with respect to the oil pump 24. The input-side one-way clutch 28 has a sprocket 28a. The input-side one-way clutch 28 is released when the rotation speed of the transmission shaft 26 is higher than the rotation speed of the sprocket 28a, and the rotation speed of the sprocket 28a is lower than the rotation speed of the transmission shaft 26. Engage to regulate. That is, the input-side one-way clutch 28 allows torque transmission from the pump impeller 3a to the transmission shaft 26, and blocks torque transmission from the transmission shaft 26 to the pump impeller 3a.

  Here, the rotation direction of the sprockets 28a and 29a and the transmission shaft 26 is the same as the rotation direction of the pump impeller 3a when the engine 2 is operating. A sprocket 30 is connected to the pump impeller 3a. The sprocket 30 rotates integrally with the pump impeller 3a. An endless chain 31 is stretched between the sprocket 30 and the sprocket 28a. The gear ratio between the sprocket 30 and the sprocket 28a is 1 or substantially 1. That is, the rotation speed of the sprocket 28a and the rotation speed of the sprocket 30 are substantially the same.

  The output side one-way clutch 29 is disposed on the transmission shaft 26. The output side one-way clutch 29 is disposed on the opposite side of the oil pump 24 from the engine 2 side in the axial direction. The output-side one-way clutch 29 has a sprocket 29a. The output-side one-way clutch 29 is released when the rotation speed of the transmission shaft 26 is higher than the rotation speed of the sprocket 29a, and the rotation speed of the sprocket 29a is lower than the rotation speed of the transmission shaft 26. Engage to regulate. That is, the output-side one-way clutch 29 allows torque transmission from the rotation shaft 7a to the transmission shaft 26, and interrupts torque transmission from the transmission shaft 26 to the rotation shaft 7a. A sprocket 32 is connected to the rotating shaft 7a. The sprocket 32 rotates integrally with the rotating shaft 7a. An endless chain 33 is spanned between the sprocket 29 a and the sprocket 32. The gear ratio between the sprocket 29a and the sprocket 32 may be 1 or substantially 1. In this case, the rotation speed of the sprocket 29a and the rotation speed of the sprocket 32 are substantially the same.

  The one-way clutch 23 is disposed on the transmission shaft 26. The one-way clutch 23 has a sprocket 23a. The one-way clutch 23 is released when the rotational speed of the transmission shaft 26 is lower than the rotational speed of the sprocket 23a, and restricts that the rotational speed of the transmission shaft 26 is higher than the rotational speed of the sprocket 23a. Engage. That is, the one-way clutch 23 allows transmission of power from the transmission shaft 26 to the rotating machine MG, and blocks transmission of power from the rotating machine MG to the transmission shaft 26. A sprocket 34 is connected to the rotating shaft 37 of the rotating machine MG. The sprocket 34 rotates integrally with the rotating shaft 37 of the rotating machine MG. A sprocket 35 is connected to the rotation shaft of the auxiliary machine 25. The sprocket 35 rotates integrally with the rotating shaft of the auxiliary machine 25. The auxiliary machine 25 is, for example, a compressor of an air conditioner. An endless chain 36 is stretched around the sprockets 23a, 34, and 35. Instead of the chain 36, a belt may be used.

  The rotating machine MG has a function as a motor (electric motor) and a function as a generator. The rotating machine MG is connected to a battery via an inverter. The rotating machine MG can convert electric power supplied from the battery into mechanical power and output it, and can be driven by the input power to convert mechanical power into electric power. The electric power generated by the rotating machine MG can be stored in the battery. As the rotating machine MG, for example, an AC synchronous motor generator can be used.

  A sprocket 38 that is rotatable relative to the rotation shaft 37 is disposed coaxially with the rotation shaft 37 of the rotating machine MG. The second clutch 22 engages or releases the rotating shaft 37 and the sprocket 38. The engaged second clutch 22 connects the rotary shaft 37 and the sprocket 38 so as to be integrally rotatable. Further, the released second clutch 22 allows relative rotation between the rotating shaft 37 and the sprocket 38. A sprocket 39 is connected to the crankshaft 2 a of the engine 2. The sprocket 39 rotates integrally with the crankshaft 2a. An endless chain 40 is stretched between the sprocket 38 and the sprocket 39. Instead of the chain 40, a belt may be used.

  When the rotational speed of the pump impeller 3a is higher than the rotational speed of the rotary shaft 7a of the transmission 4, the input side one-way clutch 28 is engaged and the output side one-way clutch 29 is released in the connection mechanism 27. In this case, the transmission shaft 26 is rotationally driven by torque transmitted from the pump impeller 3a via the sprocket 30, the chain 31, and the sprocket 28a.

  On the other hand, when the rotational speed of the rotating shaft 7a of the transmission 4 is higher than the rotational speed of the pump impeller 3a, the output-side one-way clutch 29 is engaged and the input-side one-way clutch 28 is released in the connection mechanism 27. . In this case, the transmission shaft 26 is rotationally driven by torque transmitted from the rotary shaft 7a via the sprocket 32, the chain 33, and the sprocket 29a.

  That is, the connection mechanism 27 is engaged with either the input-side one-way clutch 28 or the output-side one-way clutch 29 in accordance with the magnitude relationship between the rotation speed of the pump impeller 3a and the rotation speed of the rotation shaft 7a. Torque is input to. Torque input from the connection mechanism 27 to the transmission shaft 26 is transmitted to the oil pump 24 via the gear mechanism 24a, and the oil pump 24 is rotationally driven. The torque input from the connection mechanism 27 to the transmission shaft 26 is transmitted from the one-way clutch 23 to the sprockets 34 and 35 via the chain 36.

The rotating machine MG generates power using torque transmitted from the sprocket 34 to the rotating shaft 37. The rotating machine MG converts the torque input to the rotating shaft 37 into electric energy and stores it in the battery. In addition, the auxiliary machine 25 is rotationally driven by the torque transmitted to the sprocket 35. The gear ratio γ2 between the sprocket 23a and the sprocket 34 of the present embodiment is about 1/3. Here, assuming that the rotational speed of the transmission shaft 26 is Ns and the rotational speed of the rotating machine MG is Nmg, the gear ratio γ2 is expressed by the following equation (1). That is, in the present embodiment, the MG rotation speed Nmg is about three times the rotation speed Ns of the transmission shaft 26.
γ2 = Ns / Nmg (1)

  In the present embodiment, when the input-side one-way clutch 28 is engaged, the rotational speed Ns of the transmission shaft 26 is substantially equal to the rotational speed of the pump impeller 3a, in other words, the engine rotational speed Ne. Therefore, when the input-side one-way clutch 28 is engaged, the rotating machine MG rotates at a rotational speed approximately three times the engine rotational speed Ne.

  The engine 2 is provided with a starter 41. The starter 41 is a starter motor and consumes electric power to generate torque. The torque generated by the starter 41 is transmitted to the crankshaft 2a of the engine 2 to rotate the engine 2. The starter 41 is selectively connected to the crankshaft 2a by a clutch or the like.

  The ECU 20 is an electronic control unit having a computer. The ECU 20 has a function of controlling each part of the vehicle 100. The ECU 20 is connected to the engine 2, the first clutch 21, the second clutch 22, the rotating machine MG, and the starter 41, respectively. ECU20 performs injection control of the engine 2, throttle control, ignition control, etc. Further, the ECU 20 controls the transmission 4. For example, the ECU 20 commands the engagement and release of the first clutch 21 and the reverse brake 6. Further, the ECU 20 controls the transmission ratio of the transmission 4 by adjusting the belt clamping pressure with respect to the primary pulley 7 and the secondary pulley 8.

  Further, the ECU 20 controls the operating state of the rotating machine MG. The ECU 20 instructs to execute regenerative power generation by the rotating machine MG, to generate torque by powering the rotating machine MG, to idle the rotating machine MG, etc. according to the state of charge of the battery, traveling conditions, and the like. . The ECU 20 commands the engagement and release of the second clutch 22. Further, the ECU 20 can cause the starter 41 to perform cranking when the engine is started.

  The ECU 20 according to the present embodiment has an inertia traveling mode in which the vehicle 100 is subjected to inertia traveling while the engine 2 side is separated from the wheel side during traveling. In the inertia traveling mode, the first clutch 21 and the reverse brake 6 are released. Thereby, in the inertia traveling mode, transmission of torque between the input shaft 5 and the rotating shaft 7a is interrupted. Therefore, the mechanical load (friction) of the engine 2 or the like that becomes a running resistance is reduced. In the inertial running mode, the engine 2 is in an idle state or a stopped state. In the following description, the inertial running mode executed with the engine 2 stopped is referred to as a first inertial running mode, and the inertial running mode executed with the engine 2 operated is referred to as a second inertial running mode.

  The fuel consumption can be reduced by the first inertia traveling mode. In the first inertia traveling mode, since the engine 2 is stopped, the pump impeller 3a also stops rotating. Accordingly, the output-side one-way clutch 29 is engaged, and the transmission shaft 26 is rotated by the torque transmitted from the rotary shaft 7a. Torque input to the transmission shaft 26 is transmitted to the oil pump 24 via the gear mechanism 24a, and the oil pump 24 is rotationally driven. The torque input to the transmission shaft 26 is transmitted to the rotary machine MG and the auxiliary machine 25 via the one-way clutch 23. The ECU 20 may cause the rotating machine MG to perform regenerative power generation in the first inertia traveling mode.

  The ECU 20 of the present embodiment releases the second clutch 22 except when the engine 2 is started. Accordingly, in the first inertia traveling mode, the second clutch 22 is released except when the engine 2 is started. When the second clutch 22 is disengaged, torque transmission between the rotating shaft 37 of the rotating machine MG and the crankshaft 2a is interrupted. Therefore, the engine 2 is suppressed from being rotated by the rotation of the rotating machine MG.

  In the second inertia traveling mode, the engine 2 is operating. Accordingly, the crankshaft 2a and the pump impeller 3a rotate. When the rotational speed of the rotary shaft 7a is relatively high with respect to the engine rotational speed Ne, the output-side one-way clutch 29 is engaged and the input-side one-way clutch 28 is released. In this case, torque is input from the drive wheel to the transmission shaft 26 via the rotary shaft 7a. When the engine speed Ne is higher than the rotational speed of the rotary shaft 7a, the input side one-way clutch 28 is engaged and the output side one-way clutch 29 is released. In this case, the engine torque is input to the transmission shaft 26 via the pump impeller 3a. Torque input to the transmission shaft 26 is transmitted to the oil pump 24, the rotary machine MG, and the auxiliary machine 25.

  The ECU 20 restarts the engine 2 and engages the first clutch 21 when shifting from the first inertia traveling mode to a mode for traveling using the engine 2 as a power source. The cranking of the engine 2 can be performed by the rotating machine MG or by the starter 41. The ECU 20 of the present embodiment basically rotates the engine 2 by the rotating machine MG when starting the engine. The ECU 20 engages the second clutch 22 when starting the engine 2. Thereby, the rotating shaft 37 of the rotating machine MG and the crankshaft 2a are connected.

  The rotating machine MG generates torque according to a command from the ECU 20, and rotates the crankshaft 2a. When the engine speed Ne becomes equal to or higher than the predetermined speed, the ECU 20 starts the firing of the engine 2 and shifts the engine 2 to a self-sustaining operation state. When the complete explosion determination of the engine 2 is made based on the engine speed Ne or the like, the start control of the engine 2 ends. The ECU 20 releases the second clutch 22 when the start of the engine 2 is completed. Note that the cranking of the engine 2 is executed by the starter 41 when the temperature is low or the rotating machine MG is abnormal.

  As described above, the drive mechanism 1 of the present embodiment includes the pump impeller 3a (rotary shaft closer to the engine 2 than the first clutch 21) and the rotational shaft 7a (rotary shaft closer to the drive shaft than the first clutch 21). A connection mechanism 27 for connecting the rotation shaft on the higher rotation speed side to the transmission shaft 26. Thereby, the supply of the lubricating oil by the oil pump 24 can be performed smoothly. For example, even if the engine 2 is stopped during traveling, the oil pump 24 is rotationally driven by torque input from the rotary shaft 7a to the transmission shaft 26. Therefore, the occurrence of insufficient lubricating oil in the lubricated part is suppressed.

  Further, in the drive mechanism 1 of the present embodiment, cranking is performed by the rotating machine MG when the engine is started. Therefore, it is possible to ensure re-acceleration responsiveness when returning from the first inertia traveling mode. Further, by adopting a configuration in which the engine 2 is started by the rotating machine MG, the restriction on the number of times of durability of the starter 41 and the drive plate is relaxed.

  The drive mechanism 1 has a second clutch 22 provided between the engine 2 and the rotating machine MG, and releases the second clutch 22 except when the engine 2 is started. Therefore, the oil pump 24 can be driven to rotate without rotating the engine 2. The drive mechanism 1 engages the second clutch 22 when starting the engine 2. Therefore, the engine 2 can be cranked by the torque of the rotating machine MG when the engine is started.

Here, the rotating machine MG has performance required for each of power generation and engine start. In the drive mechanism 1 of this embodiment, the gear ratio γ2 during power generation is different from the gear ratio γ3 during engine start. Here, the gear ratio γ3 at the time of starting the engine is a gear ratio between the sprocket 39 of the crankshaft 2a and the sprocket 38 of the second clutch 22. The gear ratio γ3 is expressed by the following formula (2). In the present embodiment, the gear ratio γ3> 1/3 is set. That is, when the second clutch 22 is engaged, the MG rotational speed Nmg is less than three times the engine rotational speed Ne.
γ3 = Ne / Nmg (2)

  As described above, the ratio of the MG rotation speed Nmg to the engine rotation speed Ne at the time of power generation is different from the ratio of the MG rotation speed Nmg to the engine rotation speed Ne at the time of starting the engine, so that the design freedom of the rotating machine MG is widened. . The relationship between the gear ratio γ2 and the gear ratio γ3 is determined so that the MG rotational speed Nmg falls within an appropriate rotational speed range during power generation and when the engine is started.

[First Modification of Embodiment]
A first modification of the embodiment will be described. FIG. 2 is a diagram illustrating a schematic configuration of a vehicle according to a first modification of the embodiment. In the drive mechanism 1 of the first modification, the difference from the drive mechanism 1 of the above embodiment is the arrangement of the second clutch 50. In the drive mechanism 1 of the first modified example, a second clutch 50 is provided on the crankshaft 2a instead of the rotating shaft 37 of the rotating machine MG.

  A sprocket 51 that is rotatable relative to the crankshaft 2a is disposed on the crankshaft 2a. The second clutch 50 engages or releases the crankshaft 2a and the sprocket 51. A sprocket 52 is connected to the rotating shaft 37 of the rotating machine MG. The sprocket 52 rotates integrally with the rotating shaft 37. An endless chain 40 is spanned between the sprocket 51 and the sprocket 52. The gear ratio γ4 between the sprocket 51 and the sprocket 52 may be set to the same value as the gear ratio γ3 of the above-described embodiment, for example.

  The ECU 20 engages the second clutch 50 when starting the engine 2 and releases the second clutch 50 except when starting the engine 2. Therefore, the drive mechanism 1 of this modification can have the same effects as the drive mechanism 1 of the above embodiment.

[Second Modification of Embodiment]
A second modification of the embodiment will be described. Drawing 3 is a figure showing the schematic structure of the vehicles concerning the 2nd modification of an embodiment. The drive mechanism 1 of the second modification differs from the drive mechanism 1 of the above embodiment in the arrangement of the one-way clutch 61 and the configuration of the second clutch 62.

  The one-way clutch 61 is disposed on the rotating shaft 37 of the rotating machine MG instead of the transmission shaft 26. The one-way clutch 61 has a sprocket 63. The one-way clutch 61 is released when the rotation speed of the rotation shaft 37 is higher than the rotation speed of the sprocket 63, and restricts the rotation speed of the rotation shaft 37 from being lower than the rotation speed of the sprocket 63. Engage with. That is, the one-way clutch 61 allows transmission of power from the transmission shaft 26 to the rotating machine MG, and interrupts transmission of power from the rotating machine MG to the transmission shaft 26. A sprocket 56 is connected to the transmission shaft 26. The sprocket 56 rotates integrally with the transmission shaft 26. An endless chain 36 is stretched around the sprockets 56, 63 and 35. Instead of the chain 36, a belt may be used.

  The second clutch 62 is disposed on the rotating shaft 37 of the rotating machine MG. The second clutch 62 is a selectable one-way clutch. The second clutch 62 can be selectively switched between an engaged state that functions as a one-way clutch and a released state that does not transmit rotation. The second clutch 62 has a sprocket 64. An endless chain 40 is spanned between the sprocket 64 and the sprocket 39. Instead of the chain 40, a belt may be used. When the torque from the rotating machine MG toward the crankshaft 2a is input, the engaged second clutch 62 connects the rotating shaft 37 and the sprocket 64 to allow torque transmission. On the other hand, when the torque from the crankshaft 2a toward the rotating machine MG is input to the engaged second clutch 62, the sprocket 64 is idled to interrupt transmission of torque.

  The ECU 20 engages the second clutch 62 when starting the engine 2 and releases the second clutch 62 except when starting the engine 2. Therefore, the drive mechanism 1 of this modification can have the same effects as the drive mechanism 1 of the above embodiment.

[Third Modification of Embodiment]
A third modification of the embodiment will be described. In the embodiment and each modification, the transmission 4 is not limited to a continuously variable transmission (CVT). The transmission 4 may be, for example, a multistage automatic transmission (AT).

  The contents disclosed in the above embodiments and modifications can be executed in appropriate combination.

DESCRIPTION OF SYMBOLS 1 Drive mechanism 2 Engine 3 Torque converter 3a Pump impeller 4 Transmission 5 Input shaft 7 Primary pulley 7a Rotation shaft (drive shaft)
20 ECU
21 First clutch 22 Second clutch 23 One-way clutch 24 Oil pump 25 Auxiliary machine 26 Transmission shaft 27 Connection mechanism 37 Rotating shaft MG Rotating machine

Claims (1)

Engine,
A drive shaft;
A rotating machine,
A first clutch provided between the engine and the drive shaft;
A transmission shaft;
A connection mechanism for connecting the transmission shaft and the rotation shaft on the higher rotation side of the rotation shaft on the engine side and the rotation shaft on the drive shaft side than the first clutch;
A second clutch provided between the engine and the rotating machine;
A one-way clutch that allows transmission of power from the transmission shaft to the rotating machine and cuts off transmission of power from the rotating machine to the transmission shaft;
Engaging the second clutch when starting the engine;
The drive mechanism, wherein the second clutch is released except when the engine is started.

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