JP3219016B2 - Gear device and power output device including the same - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a gear device and a power output device, and more particularly, to a gear device for transmitting power output to an output shaft to a drive shaft and a power output device for outputting power to a driving force.

[0002]

2. Description of the Related Art Conventionally, as a gear device of this type, an output shaft from which power is output, two bearings provided at both ends of the output shaft so that the output shaft does not shift in the axial direction, There has been proposed a device having a drive shaft disposed therein and a chain spanned between the output shaft and the drive shaft (for example, see Japanese Patent Application Laid-Open No.
-89061). The two bearings are axially positioned so that they can resist the axial component force.

[0003]

However, when such a gear device is to be installed in a place where space is limited, for example, to be mounted on a vehicle, two gears provided at both ends of the output shaft are required. Space is also needed,
There is a problem that the device becomes large and complicated.

[0004] A gear device according to the present invention solves the above-mentioned problems, and has an object to reduce the number of parts of the gear device by rotatably supporting the rotating shaft so as not to be displaced in the axial direction and to reduce the size of the device. One of

It is another object of the present invention to provide a power output device using a downsized gear device.

[0006]

Means for Solving the Problems and Their Functions and Effects The gear device of the present invention employs the following means in order to achieve at least a part of the above object.

[0007] A gear device according to the present invention is a gear device for transmitting power output to an output shaft to a drive shaft, wherein the output shaft and the drive shaft are different from the drive shaft, and attached to one end of the rotary shaft. Supporting means for rotatably supporting the rotating shaft while receiving a force from the rotating shaft; and when the output shaft is driven to rotate, the rotating shaft is driven to rotate by receiving a force in the direction of the supporting means. A helical gear attached to the output shaft and the rotating shaft; and a helical gear provided on the rotating shaft.
It has a rotation member which rotates together with the shaft, the rotational power of the rotating shaft via a pre-Symbol rotary member e Bei a power transmission means for transmitting to the drive shaft, there while the rotary shaft is rotating
Applies the force of the helical gear to the rotating shaft.
The gist is that the rotating shaft is pressed against the supporting means .

In the gear device of the present invention, when the output shaft is rotationally driven, the helical gear attached to the output shaft and the rotary shaft rotationally drives the rotary shaft while applying a force in the axial direction. Support means attached to one end of the rotary shaft, rotatably supports the rotary shaft while receiving this force, power transmission means, the drive shaft rotational power of the rotating shaft via a rotary member which rotates together with the rotating shaft To communicate . And the rotating shaft rotates
In the meantime, the helical gear rotates the axial force
The rotating shaft is pressed against the supporting means
And

According to such a gear device, by utilizing the axial force of the rotating shaft generated by the helical gear,
The axial displacement of the rotating shaft can be prevented only by providing the support means at one end of the rotating shaft. As a result, the number of parts of the gear device can be reduced to simplify the gear device, and the size of the device can be reduced.

[0010] In the gear apparatus of the present invention, the power transmission means, belts hung on the rotating member, rope, the rotational power of the rotating shaft with the deflection matter medium through a chain or the like driving
The power may be transmitted to a driving shaft, or the support means may be a thrust bearing.

A power output device according to the present invention is a power output device for outputting power to a driving force, comprising a prime mover having an output shaft, a first rotation shaft, and a motive power supplied to the first rotation shaft. An input / output motor, the output shaft, the first rotation shaft, and a second
Has three axes respectively coupled to the rotating shafts of the three axes. When power is input / output to any two of the three axes, the power determined based on the input / output power is transmitted to the remaining one axis. A three-axis gear that inputs and outputs, a support unit attached to one end of the second rotating shaft, and rotatably supporting the second rotating shaft while receiving a force from the second rotating shaft; On the 2 axis of rotation
A rotating member provided to rotate with the second rotating shaft.
And, through the pre-Symbol rotating member rotational power of the second rotary shaft
And a power transmission means for transmitting power to the drive shaft.
The shaft type gear is configured such that when the output shaft is driven to rotate by the motor while receiving the reaction force output to the first rotation shaft by the electric motor, the second rotation shaft exerts a force in the direction of the support means. The helical gear is configured to rotate while receiving the rotation , and the second rotation shaft rotates.
In the meantime, the force by the helical gear is
The second rotation axis and the support hand.
The gist is that it is pressed against a step .

In the power output apparatus according to the present invention, a three-axis gear having three shafts respectively coupled to an output shaft of a prime mover and a first rotation shaft and a second rotation shaft of the electric motor is provided. When power is input / output to any two axes, power determined based on the input / output power is input / output to the remaining one axis, and the reaction force output to the first rotary shaft by the electric motor is determined. When the output shaft is rotationally driven by the prime mover while receiving, it functions as a helical gear that rotationally drives the second rotary shaft while applying an axial force to the second rotary shaft. The support means attached to one end of the second rotation shaft rotatably supports the second rotation shaft while receiving such a force, and the power transmission means rotates together with the second rotation shaft.
The rotation power of the second rotation shaft is transmitted to the drive shaft via the rotation member . Then, while the second rotating shaft is rotating,
In this case, the axial force of the helical gear is applied to the second rotating shaft.
The second rotating shaft is pressed against the supporting means.
And

According to the power output device of the present invention, by utilizing the axial force of the second rotating shaft generated by the triaxial gear functioning as a helical gear, one end of the second rotating shaft is provided. The axial displacement of the second rotating shaft can be prevented only by providing the support means. As a result, the number of parts of the three-shaft type gear, that is, the power output device can be reduced to simplify the device, and the size of the device can be reduced.

In the power output device of the present invention,
A second electric motor that inputs and outputs power to and from the second rotating shaft may be provided. In this way, the degree of freedom of the power that can be output to the drive shaft can be increased. For example,
If the electric power regenerated or consumed by receiving the reaction force output to the first rotating shaft by the electric motor is consumed or regenerated by the second electric motor, the power output from the prime mover is reduced to a desired power. It can be converted and output to the drive shaft.

Further, in the power output device of the present invention,
The triaxial gear is a planetary gear having a carrier coupled to the output shaft, a sun gear coupled to the first rotating shaft, and a ring gear coupled to the second rotating shaft. You can also.

[0016] In this addition, the power output apparatus of the present invention, the power transmission means, the rotation member hung bell <br/> DOO, rope, the second rotation by using a deflection quality medium through a chain or the like axis
Or shall transmit the rotational power to a drive shaft, the support means can also be assumed to be a thrust bearing.

[0017]

Next, embodiments of the present invention will be described based on examples. FIG. 1 is a configuration diagram schematically illustrating a configuration of a gear device 10 according to one embodiment of the present invention. As shown, the gear device 10 includes an output shaft 20 coupled to a power source, and a rotating shaft 30 to which a gear 32 forming a helical gear meshing with a gear 22 mounted on the output shaft 20 is mounted. A thrust bearing 40 attached to the end of the rotating shaft 30 where the gear 32 is not attached;
Chain 5 with sprocket 34 mounted on
6 and a drive shaft 50 to which a sprocket 54 erected by the motor 6 is attached. When rotational power in the direction indicated by the arrow is applied to the output shaft, the drive shaft 50 is Transmit rotational power.

FIG. 2 is an explanatory diagram for explaining the structure of the helical gear constituted by the gear 22 and the gear 32 and how the load component acts. As shown in the figure, both the gear 22 and the gear 32 constituting the helical gear have teeth cut obliquely with respect to the rotation axis. For this reason, the contact line between the gear 22 and the gear 32 has an inclination with respect to the axis, so that both gears 22 and 32 receive a load component in the axial direction.
In the helical gear with the cutting teeth shown in FIG. 2, when power is applied so that the gear 22 is driven to rotate in the direction of the dashed arrow in the figure, the gear 22 receives a load component directed leftward in the figure, and the gear 32 It receives a load component directed rightward in the figure.

FIG. 3 is a sectional view of the thrust bearing 40.
FIG. 4 is a sectional view taken along line 4-4 of the thrust bearing 40 of FIG. As shown in the drawing, the thrust bearing 40 is configured as a so-called thrust needle roller bearing, and has two flat races 4.
2 and 44, and a plurality of needle rollers 46 sandwiched between the planar races 42 and 44. Multiple needle rollers 46
Are radially arranged on the plane races 42, 44,
A recess (holding portion) 45 for holding the needle roller 46 is formed at a position where the needle roller 46 of the planar raceway rings 42 and 44 is disposed. Therefore, when a force for relatively rotating the two planar races 42 and 44 is applied in a state where the needle rollers 46 are sandwiched, the sandwiched needle rollers 46 rotate smoothly. The plane races 42 and 44 also rotate smoothly.

The gear device 10 according to the embodiment having the above-described structure is described.
In this embodiment, the gear 22 and the gear 32 constitute a helical gear, and are arranged so that the thrust bearing 40 receives an axial load component acting on the rotary shaft 30 via the gear 32. Therefore, as long as the output shaft 20 is rotationally driven in the direction of the arrow in FIG. 1, the rotating shaft 30 exerts an axial load component acting on the gear 32 (the load component of the helical gear).
And the reaction force from the thrust bearing 40, the rotating shaft 30 can rotate without shifting in the axial direction without providing a bearing at the end of the rotating shaft 30 on the side where the gear 32 is attached. .

As described above, the gear device 1 according to the embodiment is described.
According to 0, the gear 22 and the gear 32 constitute a helical gear, and are arranged so that the axial load component acting on the rotating shaft 30 via the gear 32 is received by the thrust bearing 40. There is no need to attach bearings to both ends of the rotating shaft 30. As a result, the gear device 10 can be simplified with a small number of components and can be reduced in size.

Since the gear 22 and the gear 32 constitute a helical gear having a long meshing length of teeth, vibration and noise can be reduced, and the gear can be suitable for high-speed rotation.

In the gear device 10 of the embodiment, the thrust needle roller bearing is used as the bearing of the rotating shaft 30, but if the thrust force, that is, the axial force can be received, and the rotating shaft 30 can be rotatably supported. Any bearing or member may be used. Therefore, as long as the end of the rotating shaft 30 and the wall surface abutting on the rotating shaft 30 can rotate sufficiently smoothly, a special bearing does not need to be used.

In the gear device 10 of the embodiment, a thrust bearing 40 disposed at an end of the rotating shaft 30 opposite to the gear 32 is provided.
, The thrust force (pressing force) of the rotating shaft 30 is received, but a member capable of supporting the pulling force and capable of rotating and supporting the rotating shaft 30 may be provided at the end of the rotating shaft on the gear 32 side.

Next, a power output device 110 as one embodiment of the present invention will be described. FIG. 5 is a configuration diagram illustrating a schematic configuration of the power output device 110 according to the embodiment. As shown in the figure, the power output device 110 of the embodiment mainly includes an engine 112, a planetary gear 120 in which a planetary carrier 124 is coupled to a crankshaft 114 of the engine 112, and a motor MG <b> 1 coupled to a sun gear 121 of the planetary gear 120. And a motor MG2 coupled to the ring gear 122 of the planetary gear 120.

The planetary gear 120 is a hollow sun gear shaft 125 penetrating the crankshaft 114 through the center of the shaft.
Sun gear 121 connected to the crankshaft 11
4, a plurality of planetary pinion gears 123 disposed between the sun gear 121 and the ring gear 122 and revolving around the outer periphery of the sun gear 121 while rotating. And a planetary carrier 124 that is connected to support the rotation shaft of each planetary pinion gear 123. In this planetary gear 120,
A sun gear shaft 125 coupled to a sun gear 121, a ring gear 122, and a planetary carrier 124;
3 of the ring gear shaft 126 and the crankshaft 114
The shaft is used as a power input / output shaft, and when the power input / output to any two of the three axes is determined, the power determined based on the determined power input / output to / from the two axes is the remaining one. Input and output to the axis.

The sun gear 121 of the planetary gear 120,
Planetary pinion gear 123 and ring gear 122
Are cut diagonally to the axial direction.
21 and the planetary pinion gear 123, and the planetary pinion gear 123 and the ring gear 122 each constitute a helical gear. Therefore, the planetary carrier 124 from the engine 112 via the crankshaft 114
When the rotational power is output to the gears 121, 122, 12
3 will receive a load component. Each gear 121, 12
The direction of the load component received by 2, 2123 and the operation at that time will be described later.

On the side of the ring gear 122 opposite to the ring gear shaft 126, a comb-shaped ring gear-side engaging portion 122a is formed, and the ring gear-side engaging portion 122a is formed at the end of the rotary shaft 127. Rotary shaft side engaging portion 128
Are fitted so as to be slidable in the axial direction. Therefore, the rotation shaft 127 is driven to rotate integrally with the ring gear shaft 126. The ring gear side engaging portion 122
The comb tooth a is formed slightly longer than the rotary shaft side engaging portion 128 so that the tip of the comb tooth of the ring gear side engaging portion 122a contacts the stem of the comb tooth of the rotary shaft side engaging portion 128. It has become. At the other end of the rotary shaft 127, a thrust bearing 130 having the same configuration as the above-described thrust bearing 40 is provided. A sprocket 129 is attached to the rotating shaft 127, and a chain 154 is hung between the sprocket 129 and the sprocket 152 attached to the drive shaft 150. Therefore, the rotation shaft 1 is connected via the planetary gear 120.
The power output to 27 is transmitted to drive shaft 150.

The motor MG1 is configured as a synchronous motor generator, and includes a rotor 132 having a plurality of permanent magnets 135 on its outer peripheral surface, and a stator 133 around which a three-phase coil 134 for forming a rotating magnetic field is wound. The rotor 132 is
The planetary gear 120 is connected to a sun gear shaft 125 which is connected to a sun gear 121. The stator 133 is
It is formed by laminating thin sheets of non-oriented electrical steel sheets, and is fixed to the case 119. The motor MG1 operates as an electric motor that rotationally drives the rotor 132 by the interaction between the magnetic field of the permanent magnet 135 and the magnetic field formed by the three-phase coil 134, and the interaction between the magnetic field of the permanent magnet 135 and the rotation of the rotor 132. By three-phase coil 1
It operates as a generator that generates an electromotive force at both ends of 34.

The motor MG2 is also configured as a synchronous motor generator like the motor MG1, and has a rotor 142 having a plurality of permanent magnets 145 on its outer peripheral surface and a stator around which a three-phase coil 144 for forming a rotating magnetic field is wound. 143. The rotor 142 is connected to a ring gear shaft 126 connected to the ring gear 122 of the planetary gear 120, and the stator 143 is fixed to the case 119. The stator 143 of the motor MG2 is also formed by laminating thin non-oriented electrical steel sheets. This motor MG2 also operates as a motor or a generator similarly to the motor MG1.

Next, the manner in which power is output from the power output device 110 of this embodiment to the drive shaft 150 will be described. Now, the engine 112 is operated at the operating point P1 of the rotation speed Ne and the torque Te, and the engine 1
12 that is the same energy as the energy Pe output from the motor 12 but is different from the operating point P2 of the rotational speed Nr and the torque Tr.
, The case where the power output from the engine 112 is torque-converted and applied to the ring gear shaft 126 will be considered. FIG. 6 shows the relationship between the rotation speed and torque of the engine 112 and the ring gear shaft 126 at this time.

According to the teaching of the mechanics, the relationship between the rotational speed and the torque of the three shafts (the sun gear shaft 125, the ring gear shaft 126, and the planetary carrier 124 (crank shaft 114)) of the planetary gear 120 is shown in FIG.
And can be represented as a diagram called an alignment chart illustrated in FIG. 8 and can be solved geometrically. Note that the relationship between the rotational speed and the torque of the three axes in the planetary gear 120 can be mathematically analyzed by calculating the energy of each axis without using the above-mentioned alignment chart. In this embodiment, a description will be given using a collinear chart for ease of description.

In FIG. 7, the vertical axis is the three rotation speed axes, and the horizontal axis is the ratio of the positions of the three coordinate axes. That is, when the coordinate axes S and R of the sun gear shaft 125 and the ring gear shaft 126 are set at both ends, the planetary carrier 124
Is defined as an axis that internally divides the axis S and the axis R into 1: ρ. Here, ρ is a ratio of the number of teeth of the sun gear 121 to the number of teeth of the ring gear 122, and is represented by the following equation (1).

[0034]

(Equation 1)

Now, it is assumed that the engine 112 is operating at the rotation speed Ne and the ring gear shaft 126 is operating at the rotation speed Nr. Therefore, the planetary carrier 124 to which the crankshaft 114 of the engine 112 is coupled is considered. The rotation speed Ne of the engine 112 on the coordinate axis C of
The rotation speed Nr can be plotted on the coordinate axis R of the ring gear shaft 126. By drawing a straight line passing through these two points, the rotation speed Ns of the sun gear shaft 125 can be obtained as the rotation speed represented by the intersection of the straight line and the coordinate axis S. Hereinafter, this straight line is referred to as an operation collinear line. The rotation speed Ns is
The rotation speed Ne and the rotation speed Nr can be determined by a proportional calculation formula (formula (2)). Thus, in the planetary gear 120, the sun gear 121, the ring gear 12
2 and the rotation of any two of the planetary carriers 124, the remaining one rotation is determined by the determined 2
Is determined based on one rotation.

[0036]

(Equation 2)

Next, the engine 11
2 is applied to the coordinate axis C of the planetary carrier 124.
Is applied from the bottom to the top in the figure as a line of action. At this time, since the motion collinear can be treated as a rigid body when a force as a vector is applied to the torque, the torque Te applied on the coordinate axis C is applied to two different action lines in parallel. By the method of separating the force, the torque can be separated into the torque Tes on the coordinate axis S and the torque Ter on the coordinate axis R. At this time, the magnitudes of the torques Tes and Ter are expressed by the following equations (3) and (4).

[0038]

(Equation 3)

In order for the operating collinear to be stable in this state, the forces of the operating collinear may be balanced. That is,
On the coordinate axis S, a torque Tm1 having the same magnitude and opposite direction as the torque Tes is applied. The torque Tm2 of the same magnitude and opposite direction acts on the resultant force with Ter. This torque Tm1 is controlled by the motor MG1 to
m2 can be actuated by the motor MG2. At this time, since the motor MG1 applies a torque in the direction opposite to the direction of rotation, the motor MG1 operates as a generator, and the electric energy Pm1 represented by the product of the torque Tm1 and the number of revolutions Ns is converted into the sun gear shaft 125. Regenerate from. Since the direction of rotation and the direction of torque of motor MG2 are the same, motor MG2 operates as an electric motor and outputs electric energy Pm2 represented by the product of torque Tm2 and rotational speed Nr to ring gear shaft 126 as power. .

Here, if the electric energy Pm1 is made equal to the electric energy Pm2, all of the electric power consumed by the motor MG2 can be regenerated and supplied by the motor MG1. In order to achieve this, it is sufficient to output all of the input energy. Therefore, the energy Pe output from the engine 112 and the energy Pr output to the ring gear shaft 126 may be made equal. That is, energy Pe represented by the product of torque Te and rotation speed Ne,
Energy P represented by the product of torque Tr and rotational speed Nr
That is, r is made equal. Referring to FIG. 6, the power expressed by the torque Te and the rotation speed Ne output from the engine 112 operated at the operation point P1 is torque-converted, and the torque Tr and the rotation speed Nr are converted with the same energy.
Is output to the ring gear shaft 126 as power expressed by As described above, the power output to the ring gear shaft 126 is transmitted to the rotating shaft 127 via the ring gear side engaging portion 122a and the rotating shaft side engaging portion 128,
Further, the power is transmitted to the drive shaft 150 via the chain 154. Therefore, since the power output to the ring gear shaft 126 and the power transmitted to the drive shaft 150 have a linear relationship, the power transmitted to the drive shaft 150 controls the power output to the ring gear shaft 126. Can be controlled by

Although the rotational speed Ns of the sun gear shaft 125 is positive in the alignment chart shown in FIG.
Depending on e and the rotation speed Nr of the ring gear shaft 126, the value may be negative as shown in the alignment chart of FIG. At this time, in the motor MG1, the direction of rotation and the direction in which the torque acts are the same, so that the motor MG1 operates as an electric motor and consumes electric energy Pm1 represented by the product of the torque Tm1 and the number of revolutions Ns. On the other hand, the motor MG2
In this case, the direction of rotation and the direction in which the torque acts are opposite, so that the motor MG2 operates as a generator and the torque Tm
Electric energy Pm2 represented by the product of 2 and rotation speed Nr
Is regenerated from the ring gear shaft 126. In this case, if the electric energy Pm1 consumed by the motor MG1 is made equal to the electric energy Pm2 regenerated by the motor MG2, the electric energy Pm1 consumed by the motor MG1 can be exactly covered by the motor MG2.

Although the basic torque conversion in the power output device 110 according to the embodiment has been described above, the power output device 110 according to the embodiment converts all of the power output from the engine 112 into a torque, and
In addition to the operation for outputting to the motor 6, the battery (not shown) is provided, so that the power output from the engine 112 (the product of the torque Te and the rotation speed Ne) and the electric energy Pm1 regenerated or consumed by the motor MG1 are obtained. Motor MG
By adjusting the electric energy Pm2 consumed or regenerated by the battery 2, the operation for finding the surplus electric energy and charging the battery or the operation for supplementing the insufficient electric energy by discharging from the battery is performed in various operations. be able to.

As described with reference to FIGS. 7 and 8,
The power output from the engine 112 is transferred to the ring gear shaft 12
6, the rotation direction of the ring gear shaft 126 does not change. In the embodiment, when such rotational power is applied, the ring gear 122 and the planetary pinion gear so that the ring gear 122 of the gears constituting the helical gear receives a load component in the right direction (the direction of the arrow) in FIG. 123 teeth have been cut. For this reason, the rotation shaft 127
Are connected to the ring gear 12 via the tip of the comb teeth of the ring gear side engaging portion 122a and the stem of the comb teeth of the rotating shaft side engaging portion 128.
2 and a reaction force from the thrust bearing 130. Since the manner of operation of the load component and the arrangement of the thrust bearing 130 are the same as those of the above-described gear device 10, even if the bearing is not provided on the ring gear 122 side of the rotating shaft 127 as described in the gear device 10, The rotating shaft 127 can be driven to rotate without shifting in the axial direction.

Incidentally, the power output device 11 of this embodiment
At 0, the motor MG2 may be used to rotate the ring gear shaft 126 in the reverse direction to rotate the drive shaft 150 in the reverse direction. In this case, a leftward load component in FIG. 5 acts on the ring gear 122, but the ring gear-side engaging portion 122a and the rotary shaft-side engaging portion 128, both formed in a comb shape, slide in the axial direction. Since they are movably fitted, no load component acts on the rotating shaft 127. Therefore, the rotating shaft 127 is driven to rotate integrally with the ring gear 122 without receiving an axial stress.

The power output device 110 of the embodiment described above
According to this, by forming a helical gear by the planetary pinion gear 123 and the ring gear 122, and by arranging the thrust bearing 130 to receive an axial load component acting on the rotating shaft 127 via the ring gear 122, It is not necessary to attach bearings to both ends of the rotating shaft 127. As a result, the power output device 110 can be simplified with a small number of components and can be reduced in size.

Of course, the planetary pinion gear 123
Since the helical gear having a long meshing length between the teeth and the ring gear 122 is formed, vibration and noise can be reduced, and the gear can be suitable for high-speed rotation.

In the power output device 110 of the embodiment, the thrust needle roller bearing is used as the bearing of the rotary shaft 127.
Any bearing or member may be used as long as it can receive a thrust force, that is, an axial force and can rotatably support the rotating shaft 127. Therefore, the rotating shaft 12
As long as the end of 7 and the wall surface in contact with it can rotate sufficiently smoothly, a special bearing does not need to be used.

In the power output device 110 of the embodiment, the motor MG2 is attached to the ring gear shaft 126,
G2 may not be provided. Even in this case, the torque MG output from the engine 112 to the sun gear shaft 125 via the planetary gear 120 is received by the motor MG1 so that the torque Ter can be output to the rotary shaft 127 via the ring gear 122. However, in this case, it is necessary to provide a power storage means such as a battery capable of charging and discharging the power consumed or regenerated when the motor MG1 receives the torque Tes as a reaction force.

Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments at all, and can be implemented in various forms without departing from the gist of the present invention. Of course.

[Brief description of the drawings]

FIG. 1 is a configuration diagram illustrating a schematic configuration of a gear device 10 as one embodiment of the present invention.

FIG. 2 is an explanatory diagram for explaining a structure of a helical gear constituted by a gear 22 and a gear 32 and a state in which a load component acts.

FIG. 3 is a cross-sectional view of the thrust bearing 40.

FIG. 4 is a sectional view taken along line 4-4 of the thrust bearing 40 of FIG. 3;

FIG. 5 is a configuration diagram illustrating a schematic configuration of a power output device 110 according to the embodiment.

FIG. 6 is a graph for explaining the operation principle of the power output apparatus 110 according to the embodiment.

FIG. 7 is a collinear diagram showing a relationship between a rotation speed and a torque of three shafts coupled to the planetary gear 120.

FIG. 8 is a nomographic chart showing a relationship between a rotation speed and a torque of three shafts coupled to the planetary gear 120.

[Description of Signs] 10 ... Gear device 20 ... Output shaft 22 ... Gear 30 ... Rotating shaft 32 ... Gear 34 ... Sprocket 40 ... Thrust bearing 42,44 ... Flat raceway ring 50 ... Drive shaft 54 ... Sprocket 56 ... Chain 110 ... Power Output device 112 ... Engine 114 ... Crankshaft 119 ... Case 120 ... Planetary gear 121 ... Sun gear 122 ... Ring gear 122a ... Ring gear side engaging part 123 ... Planetary pinion gear 124 ... Planetary carrier 125 ... Sun gear shaft 126 ... Ring gear shaft 127 ... Rotating shaft 128 ... Rotary shaft side engaging portion 129 ... Sprocket 130 ... Thrust bearing 132 ... Rotor 133 ... Stator 134 ... Three-phase coil 135 ... Permanent magnet 142 ... Rotor 143 ... Stator 144 ... Three-phase coil 145 ... Permanent magnet 150 ... Drive 152 ... sprocket 154 ... chain

Continuation of the front page (72) Inventor Masatoshi Adachi 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (56) References JP-A-8-183347 (JP, A) JP-A-2-154837 (JP, A) JP-A-9-24743 (JP, A) JP-A-7-135701 (JP, A) JP-A-10-281239 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) ) F16H 37/02 B60K 6/02 B60K 17/04 B60L 11/00-11/14 F16H 57/02

Claims (8)

(57) [Claims] 1. A gear device for transmitting power output to an output shaft to a drive shaft, comprising: a rotation shaft different from the output shaft and the drive shaft; and a rotation shaft attached to one end of the rotation shaft. Supporting means for rotatably supporting the rotation shaft while receiving a force from the output shaft, wherein the output shaft is rotatably driven by receiving a force in the direction of the support means when the output shaft is rotationally driven. A helical gear attached to the rotating shaft; and a rotating unit provided on the rotating shaft and rotating together with the rotating shaft.
It has a timber, through a pre-Symbol rotating member rotational power of the rotating shaft
Bei example a power transmission means for transmitting to the drive shaft Te, In the while said rotary shaft is rotating, said Subaha
Applying the force by the car to the rotation axis, the rotation axis
Teeth wheel device comprising pressed against the support means. 2. The power transmission means is mounted on the rotating member.
Using kicked the belts, rope, a deflection quality medium through the chain, etc.
請 Motomeko 1 for transmitting the rotational power of the rotating shaft to the drive shaft
A gear device as described. 3. The gear device according to claim 1, wherein said support means is a thrust bearing. 4. A power output device for outputting power to a driving force, comprising: a prime mover having an output shaft; a motor having a first rotating shaft, for inputting and outputting power to and from the first rotating shaft; It has three shafts respectively coupled to the output shaft, the first rotation shaft, and the second rotation shaft. When power is input / output to any two of the three shafts, the power is input / output. A three-axis gear for inputting and outputting power determined based on the received power to the remaining one shaft; and a second rotation attached to one end of the second rotation shaft while receiving a force from the second rotation shaft. Supporting means for rotatably supporting a shaft; and rotating means provided on the second rotating shaft to rotate together with the second rotating shaft.
Has a rotating member that rolling, the second rotational power of the rotating shaft via the <br/> before Symbol rotary member and a power transmission means for transmitting to said drive shaft, said three shaft-type gear, the When the motor drives the output shaft to rotate while receiving the reaction force output to the first rotation shaft by the electric motor, the second rotation shaft rotates while receiving a force in the direction of the support means. It is configured as a helical gear, and while the second rotating shaft is rotating, the
Applying the force by the helical gear to the second rotating shaft,
Dynamic force output device comprising pressing said second rotary shaft to said support means. 5. The power output device according to claim 4, further comprising a second electric motor that inputs and outputs power to and from the second rotation shaft. 6. The planetary gear having a carrier coupled to the output shaft, a sun gear coupled to the first rotation shaft, and a ring gear coupled to the second rotation shaft. The power output device according to claim 4 or 5, wherein 7. The power transmission means is mounted on the rotating member.
Using kicked the belts, rope, a deflection quality medium through the chain, etc.
The power output device according to any one of claims 4 to 6 , wherein the rotation power of the second rotation shaft is transmitted to the drive shaft . 8. The power output device according to claim 4, wherein said support means is a thrust bearing.