JP6901144B2 - Drive mechanism using regenerative energy - Google Patents

Description

The present invention relates to a drive mechanism using regenerative energy, and more specifically, to a drive mechanism using regenerative energy including a regenerative energy storage unit and a speed change mechanism in its configuration.

A drive mechanism has been proposed in which regenerative energy is recovered by a drive mechanism, stored, and reused for output. For example, in Patent Document 1, a continuously variable transmission mechanism is arranged between an engine as a drive source and a drive wheel as an output, and the engine and the continuously variable transmission mechanism are connected to an elastic body that stores regenerative energy. ing.

The drive wheels and the continuously variable transmission mechanism, the continuously variable transmission mechanism and the engine, and the continuously variable transmission mechanism and the elastic body are connected by one or a plurality of clutch mechanisms, respectively, and perform power transmission, interruption thereof, switching of rotation direction, and the like. I am trying to do it.

Japanese Unexamined Patent Publication No. 2003-182399

In Patent Document 1, the clutch mechanism is switched by a central control unit (CPU), but since there are many clutch mechanisms, the mechanism becomes complicated, the control is difficult, and the maintainability is not sufficient. Absent.

An object of the present invention is to provide a drive mechanism capable of storing regenerative energy and reusing it for output by a simple structure.

The drive mechanism using the regenerative energy according to the present invention is
A drive source that rotates and drives a drive shaft that allows rotation in only one direction,
The storage has an input shaft connected to the drive source via the drive shaft, a storage means connected to the input shaft and capable of storing regenerative energy, and an input / output shaft connected to the storage means. A storage unit that stores regenerative energy in the means and can output the stored regenerative energy from the input / output shaft.
A transmission mechanism connected to the storage unit via the input / output shaft,
The driven member connected to the transmission mechanism and
To have.

The storage means can be exemplified by a mainspring.

The input shaft and the input / output shaft are arranged concentrically.
The mainspring is housed inside a casing that is concentrically and rotatably connected to the input shaft or the input / output shaft, and the outer end of the mainspring is connected to the casing.
The inner end of the mainspring is connected to the input shaft or the other of the input / output shafts.

Moreover, the storage means can exemplify a constant load spring.

An input side drum is attached to the tip of the input shaft so that it can rotate integrally.
An input / output side support plate is integrally rotatably attached to the input / output shaft 340, and an input / output side drum is rotatably attached to the input / output side support plate.
A configuration in which the constant load spring is wound around the input / output side drum in the rewinding direction and the other end of the constant load spring can be wound around the input side drum can be exemplified.

The speed change mechanism can switch between forward rotation, reverse rotation, and stop state, and the gear ratio is variable.

The speed change mechanism has a variable speed change ratio.

Further, the land-based mobile body of the present invention includes a drive mechanism utilizing the regenerative energy described above.

According to the drive mechanism using the regenerative energy of the present invention, the power from the drive source is stored in the storage unit as long as the energy can be stored in the storage unit. Further, the energy stored in the storage unit can be output to the transmission mechanism, and the driven member can be driven via the transmission mechanism.

On the other hand, since the drive shaft of the drive source is allowed to rotate in only one direction, the regenerative energy of the storage unit is not transmitted to the drive source or consumed by the drive source.

Further, the regenerative energy at the time of braking of the driven member or the like is transmitted to the storage unit via the transmission mechanism and stored.

According to the drive mechanism using the regenerative energy of the present invention, the energy for driving the driven member is generated from the drive source stored in the storage unit and when the driven member is braked. It is the regenerative energy stored in the storage part through.

Since the regenerative energy from the driven member can be stored in the storage unit via the transmission mechanism, for example, by adopting a continuously variable transmission mechanism for the transmission mechanism, a drive source or a mechanical brake is ultimately unnecessary. It is also possible.

Further, according to the drive mechanism using the regenerative energy of the present invention, the clutch mechanism is not required, or even if it is adopted, a small number is required, so that the configuration and control of the drive mechanism can be simplified. ..

Further, when a mainspring spring or a constant load spring is adopted as the storage unit, the regenerative energy is stored in the mainspring spring or the constant load spring, and the stored regenerative energy can be efficiently output to the transmission mechanism.

According to the drive mechanism using the regenerative energy of the present invention, the kinetic energy can be stored in the same physical system without being converted into another physical system such as electrical or chemical change, so that the energy can be stored with high efficiency. Can be realized.

FIG. 1 is a block diagram showing a schematic configuration of a drive mechanism using the regenerative energy of the present invention. FIG. 2 is a perspective view of a storage unit according to an embodiment of the present invention. FIG. 3 is a cross-sectional view taken along the axis of FIG. FIG. 4 is a perspective view of a transmission mechanism according to an embodiment of the present invention. FIG. 5 is a side view of the transmission mechanism. FIG. 6 is a cross-sectional view of the transmission mechanism as viewed from the first axis side, which is a cross section taken along the arrow AA of FIG. FIG. 7 is an explanatory diagram when the gear ratio of the second axis to the first axis is large and the rotation directions of the first axis and the second axis are opposite to each other. FIG. 8 is an explanatory diagram when the gear ratio of the second axis to the first axis is small and the rotation directions of the first axis and the second axis are opposite to each other. FIG. 9 is an explanatory diagram showing a neutral state in which the first axis and the first spherical rolling element are arranged side by side, and a state in which the second axis is stopped. FIG. 10 is an explanatory diagram when the gear ratio of the second axis to the first axis is small and the rotation directions of the first axis and the second axis are the same. FIG. 11 is an explanatory diagram when the gear ratio of the second axis to the first axis is large and the rotation directions of the first axis and the second axis are the same. FIG. 12 shows the relationship between the stroke of the actuator and acceleration / deceleration. FIG. 13 is an explanatory diagram showing the rotation speed and the gear ratio of each axis of the drive mechanism. FIG. 14 is a cross-sectional view taken along the axis of the storage portion according to another embodiment of the present invention, and shows an embodiment in which a constant load spring is adopted. FIG. 15 is a cross-sectional view taken along the line AA of FIG. FIG. 16 is an explanatory diagram showing an energy storage process of the constant load spring. FIG. 17 is an explanatory diagram of the stop mechanism of the second disc, showing a state in which the second spherical rolling element has not reached the center of the second disc. FIG. 18 is a cross-sectional view taken along the line AA of FIG. 17, showing a state in which the second spherical rolling element reaches the center of the second disc. FIG. 19 is a perspective view of a transmission mechanism according to a different embodiment of the present invention.

The drive mechanism 100 using the regenerative energy of the present invention will be described with reference to the drawings. The drive mechanism 100 of the present invention can be applied to, for example, a drive mechanism for a land moving body such as an automobile, a truck, a bus, a motorcycle, a bicycle, or a railroad.

FIG. 1 is a block diagram showing a schematic configuration of a drive mechanism 100 using regenerative energy according to an embodiment of the present invention. As shown in the figure, the drive mechanism 100 includes a drive source 200, a storage unit 300 that stores energy (including regenerative energy), a transmission mechanism 400 having a variable gear ratio, and a cover connected to the transmission mechanism 400. It includes a drive member 500.

The drive mechanism 100 of the present invention can store energy from the drive source 200 in the storage unit 300, and the energy (including regenerative energy) stored in the storage unit 300 is stored in the driven member 500 via the speed change mechanism 400. It can be supplied. Further, the energy generated when the driven member 500 is braked or the like can be stored in the storage unit 300 via the speed change mechanism 400. That is, energy can be stored in the storage unit 300 from both the drive source 200 and the driven member 500, and the driven member 500 can be driven by the stored energy.

Hereinafter, each configuration will be described in detail with reference to FIG. 1 and the like.

As shown in FIG. 1, the drive source 200 may exemplify a motor, an engine, or the like. For example, when the motor is used as the drive source 200, a battery, a commercial power source, or the like (not shown) is used as the power source. The drive source 200 includes a drive shaft 210 pivotally supported by a bearing or the like as an output shaft. The drive shaft 210 is configured to allow rotation in only one direction by a one-way bearing 220 or the like. It should be noted that "one direction" includes not only strictly one direction but also a configuration that allows some rotation in the opposite direction.

The storage unit 300 stores regenerative energy. As shown in FIGS. 2 and 3, the storage unit 300 illustrates the mainspring 310 as a storage means for storing energy. The storage unit 300 is not limited to the mainspring spring, and may be an elastic body such as a coil spring, rubber, or air. Further, as will be described later, constant load springs 360 and 361 can also be adopted for the storage unit 300.

The mainspring 310 can be formed by winding a steel plate, and is housed in a rotatably supported casing 320. In the illustrated embodiment, the casing 320 has a cylindrical shape, but a plurality of frames may be arranged concentrically as long as the spring 310 can be accommodated.

The inner end of the mainspring 310 is connected to an input shaft 330 pivotally supported by a bearing or the like. The input shaft 330 is integrally configured with the drive shaft 210 in the illustrated embodiment. The input shaft 330 and the drive shaft 210 may be connected via gears or the like.

The outer end of the mainspring 310 is connected to the casing 320. The casing 320 has a reduced diameter portion 322 at one end, and is connected to an input / output shaft 340 extending concentrically and in the opposite direction to the input shaft 330 at the center of the reduced diameter portion 322. The input / output shaft 340 is pivotally supported by a bearing or the like (not shown). The reduced diameter portion 322 may have a conical shape or a disk shape as shown in FIGS. 2 and 3. The diameter-reduced portion 322 does not need to completely close the casing 320, and may be configured by a frame or the like as long as the casing 320 and the input / output shaft 340 can rotate integrally.

Regarding the storage unit 300, in the present embodiment, as described above, the inner end of the mainspring 310 is connected to the input shaft 330 and the outer end is connected to the casing 320, but the inner end is connected to the casing 320 and the outer end is connected to the input / output shaft 340. It may be configured to be connected.

By rotating the drive source 200 in one direction, the storage unit 300 rotates in the direction in which the mainspring 310 is involved, and can store energy in the mainspring 310. Further, the storage unit 300 can output the stored energy (including regenerative energy) from the speed change mechanism 400 to the driven member 500 by deforming the mainspring 310 in the extending direction. On the other hand, when the driven member 500 is decelerated or the like, the regenerative energy can be stored in the mainspring 310 by rotating the speed change mechanism 400 in the direction in which the mainspring 310 is involved.

The transmission mechanism 400 can switch between the first shaft 420 connected to the input / output shaft 340 of the storage unit 300 and the second shaft 430 connected to the driven member 500 in any of forward rotation, reverse rotation, and stop states. Moreover, it is configured to be connected so that power can be transmitted.

The speed change mechanism 400 can adopt a stepped speed change mechanism capable of changing the speed change ratio in a stepped manner, but in the present embodiment, the speed change mechanism 400 is a stepless speed change mechanism in which the speed change ratio is steplessly variable. The mechanism is adopted. Thereby, the energy transfer from the storage unit 300 to the transmission mechanism 400 and the storage of the regenerative energy from the transmission mechanism 400 to the storage unit 300 can be controlled more finely.

As the speed change mechanism 400, the configurations shown in FIGS. 4 to 11 can be exemplified. The transmission mechanism 400 can be applied to other than those shown in the present embodiment.

FIG. 4 is a perspective view showing a schematic configuration of the transmission mechanism 400, FIG. 5 is a side view, and FIG. 6 is a front view seen from the first shaft 420 side. As shown in the figure, in the transmission mechanism 400, the first shaft 420 connected to the storage unit 300 and the second shaft 430 connected to the driven member 500 are arranged in parallel and eccentrically. The first shaft 420 also serves as an output shaft for energy from the storage unit 300 to the transmission mechanism 400 and an input shaft for regenerative energy from the transmission mechanism 400 to the storage unit 300. Further, the second shaft 430 also serves as an output shaft of energy from the speed change mechanism 400 to the driven member 500 and an input shaft of regenerative energy from the driven member 500 to the speed change mechanism 400.

The first shaft 420 is pivotally supported by a bearing or the like, and the first disk 421 is connected to the tip thereof. In the illustrated embodiment, the first disk 421 is a disk body in which the first facing surface 422 facing the second axis 430 is perpendicular to the first axis 420. By setting the diameter of the first disk 421 to be equal to or greater than the eccentric distance between the first axis 420 and the second axis 430, the rotation directions of the first axis 420 and the second axis 430 can be switched.

The second shaft 430 is rotatably supported by a bearing or the like, and a second disc 431 is connected to the tip thereof. In the illustrated embodiment, the second disk 431 is also a disk body, the second facing surface 432 facing the first axis 420 is perpendicular to the second axis 430, and further, the second facing surface 432 is formed. Is at least partially opposed to the first facing surface 422. Desirably, the second facing surface 432 faces parallel to the first facing surface 422. By setting the diameter of the second disk 431 to be equal to or greater than the eccentric distance between the first axis 420 and the second axis 430, the rotation directions of the first axis 420 and the second axis 430 can be switched.

Between the first disk 421 and the second disk 431, a plurality of spherical rolling elements 440 and 450 that connect the first disk 421 and the second disk 431 so as to be able to transmit power are arranged. In the illustrated embodiment, there are two spherical rolling elements 440 and 450, the spherical rolling element 440 on the first disk 421 side is the first spherical rolling element, and the spherical rolling element 450 on the second disk 431 side is the second spherical rolling element. Called a moving body.

The first spherical rolling element 440 is in contact with the first facing surface 422, and the second spherical rolling element 450 is in contact with the second facing surface 432. Further, the first spherical rolling element 440 and the second spherical rolling element 450 are also in contact with each other. In the present embodiment, the first spherical rolling element 440 and the second spherical rolling element 450 have diameters (referred to as diameter lines L) arranged in a straight line, and the diameter lines L are the first axis 420 and the second axis. It is held in the holder 460 so as to be parallel to the 430 (the holder 460 is not shown in FIG. 4). The diameter line L is preferably parallel to the first axis 420 and the second axis 430, but may be non-parallel to these, and the first spherical rolling element 440 and the second spherical rolling element 440. The moving body 450 may be offset in diameter instead of being aligned in a straight line.

The holder 460 rotatably holds the first spherical rolling element 440 and the second spherical rolling element 450. More specifically, the illustrated holder 460 has bearings 461 such as thrust bearings arranged on the inner surfaces of the opposing plate-shaped pedestals. The pedestals are held so that the distance between them is constant. Then, the first spherical rolling element 440 protrudes from one end of the holder 460 toward the first facing surface 422, and the second spherical rolling element 450 protrudes from the other end toward the second facing surface 432.

The holder 460, together with the first spherical rolling element 440 and the second spherical rolling element 450, is located between the first disk 421 and the second disk 431 in a plane parallel to the first axis 420 and the second axis 430, and the first disk 421. Is connected to the holder moving means 464 so as to be movable in the opposite region of the second disc 431. The moving direction of the holder 460 is indicated by an arrow 6A in FIGS. 5 and 6. The holder moving means 464 can exemplify an actuator 465 such as a cylinder, and in this case, the piston rod 466 can be connected to the holder 460.

The first facing surface 422 and the first spherical rolling element 440 of the first disk 421 described above, the first spherical rolling element 440 and the second spherical rolling element 450, the second spherical rolling element 450 and the second facing surface of the second disk 431. The 432s are in frictional contact with each other. For example, the facing surfaces 422 and 432 and the spherical rolling elements 440 and 450 are preferably made of a metal such as steel, hard rubber, hard resin, or the like. In order to increase the efficiency of the transmission mechanism 400, it is desired to reduce the slippage between the facing surfaces 422 and 432 and the spherical rolling elements 440 and 450.

The operating principle of the above-mentioned transmission mechanism 400 will be described with reference to FIGS. 4 to 6. When the first shaft 420 rotates in the direction of arrow 2A in the drawing by receiving the power from the transmission mechanism 400, the first disk 421 also rotates together with the first shaft 420. Since the first spherical rolling element 440 is in frictional contact with the first facing surface 422 and is held by the holder 460, it rolls in the direction of arrow 4A in the drawing by the rotation of the first disk 421. The second spherical rolling element 450, which is in frictional contact with the first spherical rolling element 440, rolls in the direction of arrow 5A in the figure due to the rolling of the first spherical rolling element 440.

Since the second facing surface 432 is in frictional contact with the second spherical rolling element 450, the second disc 431 is rotated in the arrow 3A direction in the drawing by the rolling of the second spherical rolling element 450 in the arrow 5A direction. Then, the second axis 430 rotates in the direction opposite to that of the first axis 420.

Here, when the holder moving means 464 is operated, the gear ratios of the first shaft 420 and the second shaft 430 can be changed. When the diameters of the first spherical rolling element 440 and the second spherical rolling element 450 are the same, the gear ratio is the distance S1 from the first axis 420 to the diameter line L shown in FIG. 5 and the diameter line from the second axis 430. It can be expressed by the value (S1 / S2) divided by the distance S2 to L. The larger the gear ratio, the higher the rotation speed of the second shaft 430 with respect to the first shaft 420, but the smaller the torque of the second shaft 430, and the smaller the gear ratio, the larger the rotation speed of the second shaft 430 with respect to the first axis. The number is small, but the torque of the second shaft 430 is large.

Regarding the gear ratio, in FIG. 5, the distance S1 from the first axis 420 to the diameter line L and the distance S2 from the second axis 430 to the diameter line L are set to 1: 1. Therefore, the gear ratio (S1 / S2) of the first shaft 420 and the second shaft 430 is 1.

On the other hand, when the holder moving means 464 is shortened and the distance S1 from the first axis 420 to the diameter line L is made larger than the distance S2 from the second axis 430 to the diameter line L, as shown in FIG. 7, the gear ratio is increased. (S1 / S2) is larger than 1.

On the contrary, when the holder moving means 464 is extended and the distance S1 from the first axis 420 to the diameter line L is smaller than the distance S2 from the second axis 430 to the diameter line L, as shown in FIG. The ratio (S1 / S2) is less than 1.

As described above, according to the transmission mechanism 400 of the present embodiment, the position of the first spherical rolling element 440 and the second spherical rolling element 450 is set between the first axis 420 and the second axis 430 by the holder moving means 464. By moving, the rotation of the first shaft 420 can be transmitted to the second shaft 430 at a desired gear ratio.

As shown in FIG. 9, the first spherical rolling element 440 and the second spherical rolling element 450 are formed by expanding and contracting the holder moving means 464 so that the rotation center of the first axis 420 and the diameter line L coincide with each other. As shown by arrows 4B and 5B in the figure, the vehicle stops in a plane orthogonal to the first axis 420 and the second axis 430. As a result, the rotation of the first shaft 420 is not transmitted to the second shaft 430.

In the above case, as shown in FIG. 9, it is possible to exemplify a configuration in which an idling means 429 such as a bearing that makes the spherical rolling element 440 rollable is provided at the center of rotation of the first disc 421 and the second disc 431. .. In this case, when the first spherical rolling element 440 moves onto the idling means 429 of the first disk 421, the rotation of the first disk 421 is not transmitted to the first spherical rolling element 440, and the first spherical rolling element is in a free state. The 440, the second stadium transfer moving body 450, and the second disc 431 can realize the stopped state.

10 and 11 are examples of rotating the first axis 420 and the second axis 430 in the same direction. As shown in FIGS. 10 and 11, when the diameter line L is not between the first axis 420 and the second axis 430, the second axis 430 is the first axis as shown by the arrow 3B in the figure. It rotates in the same direction as the rotation direction of the shaft 420.

By combining the above, according to the transmission mechanism 400 of the present invention, the gear ratio from the first axis 420 to the second axis 430 can be changed, and of course, the rotation direction of the second axis 430 with respect to the first axis 420 is also changed. Can be controlled.

The speed change mechanism 400 has two spherical rolling elements, a first spherical rolling element 440 and a second spherical rolling element 450, but may have three or more spherical rolling elements. In this case, if the number of spherical rolling elements is an even number, the rotation directions of the first axis 420 and the second axis 430 are the same as described above. On the other hand, if the number of spherical rolling elements is odd, the rotation directions of the first axis 420 and the second axis 430 are opposite to those described above.

Further, in the above embodiment, the diameters of the first spherical rolling element 440 and the second spherical rolling element 450 are the same, but the diameters of the first spherical rolling element 440 and the second spherical rolling element 450 may be changed.

Further, in the above embodiment, the first facing surface 422 of the first disk 421 and the second facing surface 432 of the second disk 431 are each flat, but one of them has a concave shape such as a concave cone shape or a bowl shape. The other may have a convex shape corresponding to the concave shape. In this case, it is necessary to adjust the distance between the first facing surface 422 and the second facing surface 432 so that the frictional contact between the facing surfaces 422 and 432 and the spherical rolling elements 440, 450 or the spherical rolling bodies 440, 450 does not decrease. There is.

According to the above-mentioned speed change mechanism 400, the speed change ratio and the rotation direction of the power transmitted from the first shaft 420 to the second shaft 430 are simply adjusted by adjusting the contact positions of the spherical rolling elements 440 and 450 with the disks 421 and 431. Can be freely changed, and it can also be set to neutral without transmitting power.

Further, since the transmission mechanism 400 can be composed of the discs 421, 431, the spherical rolling elements 440, 450, the holder 460 for holding the spherical rolling elements, and the holder moving means 464, the transmission mechanism 400 is configured as compared with the conventional continuously variable transmission mechanism. Is simple and has excellent maintainability.

By operating the actuator 465, the above-mentioned transmission mechanism 400 applies the driving force input from the first shaft 420 to the maximum speed, high speed, medium speed, low speed, and slow speed on the forward rotation side, as shown in FIG. It is possible to output to the second shaft 430 in the state of stop, reverse slowing on the reverse side, reverse low speed, and reverse medium speed. By further expanding and contracting the actuator 465, it is possible to adjust the reverse high speed and the reverse maximum speed. In the explanation, it is shown in stages such as high speed and medium speed, but since the gear ratio can be set steplessly, the speed change can also be adjusted steplessly. In addition, fine adjustment is possible, and a large variable width with a gear ratio from extremely small to maximum can be obtained.

The driven member 500 is a member driven by the drive mechanism 100, and in the case of a land-moving body, a drive wheel (see FIG. 1) can be exemplified.

Then, the operation of the drive mechanism 100 is performed by the operation unit 600 (see FIG. 1) that accepts human operations such as the accelerator and the brake.

As shown in FIG. 1, the drive mechanism 100 utilizing the regenerative energy having the above configuration is controlled by a central control device (consisting mainly of the CPU 700). A storage means (not shown) such as a ROM or RAM for storing programs and settings for all control of the drive mechanism 100 is connected to the CPU 700.

The CPU 700 is electrically connected to the operation unit 600, and controls the output and the rotation speed of the drive source 200 and controls the expansion and contraction of the actuator 465 of the transmission mechanism 400 based on the operation from the operation unit 600. , Controls the gear ratio and power transmission direction of the speed change mechanism 400. Further, a detector 710 for detecting the rotation speed and torque is provided on the first shaft 420 of the transmission mechanism 400, and the detected value is transmitted to the CPU 700.

Further, the storage unit 300 is provided with a sensor 720 that detects the energy (including regenerative energy) stored in the storage unit 300, and the detected value is transmitted to the CPU 700.

Then, the CPU 700 grasps the rotation speed, torque, and the amount of stored energy of the storage unit 300 of each axis, and compares the operation from the operation unit 600 and the energy storage status of the storage unit 300 from the sensor 720 with the comparison unit 730. It controls the actuator 465 and the drive source 200. The details will be described later.

The basic operation of the drive mechanism 100 using the regenerative energy of the above configuration is as follows.

By operating the drive source 200, the drive shaft 210 and the input shaft 330 rotate integrally, the mainspring 310 connected to the input shaft 330 is wound in the winding direction from the inner end side, and energy is applied to the storage unit 300. Accumulate. When the sensor 720 detects that the energy stored in the storage unit 300 has reached the maximum, the CPU 700 controls to stop the drive source 200. This control is the same in any of the following cases.

Then, the energy (including regenerative energy) stored in the storage unit 300 drives the driven member 500 through the transmission mechanism 400. For example, when it is desired to drive the driven member 500, the operation unit 600 is operated (accelerator), so that the CPU 700 compares the energy stored in the storage unit 300 detected by the sensor 720 with the required power. The actuator 465 is expanded and contracted so that the optimum driving force can be supplied to the driven member 500 while the detector 710 detects the rotation speed and torque of the transmission mechanism 400, which is calculated by the unit 730. As a result, the rotational force is transmitted from the storage unit 300 to the driven member 500 via the transmission mechanism 400, and the driven member 500 is driven.

By operating the drive source 200 while the driven member 500 is being driven, if the rotation speed of the input shaft 330 is larger than the rotation speed of the input / output shaft 340, additional energy is added to the storage unit 300. Is accumulated. Further, if the rotation speeds of the input shaft 330 and the input / output shaft 340 are the same, the storage unit 300 is held constant without accumulating additional energy. Further, if the rotation speed of the input shaft 330 is smaller than the rotation speed of the input / output shaft 340, a part of the power of the drive source 200 and the energy of the storage unit 300 will be consumed by the driven member 500 and stored. The energy stored in the unit 300 will be reduced.

On the other hand, when the driven member 500 is decelerated, the operating unit 600 is operated (brake) to operate the actuator 465 to store the braking force of the driven member 500 via the speed change mechanism 400. The spring 310 is wound in the winding direction, and the regenerative energy is stored in the storage unit 300. At this time, the CPU 700 detects the rotation speed and torque of the transmission mechanism 400 with the detector 710, and also refers to the amount of energy already stored in the storage unit 300 with the sensor 720 to optimally store the regenerative energy. It is controlled so that it can be accumulated in the unit 300.

Hereinafter, an embodiment of the operation of the drive mechanism 100 of the present invention during constant speed traveling and deceleration will be specifically described with reference to FIG. The drive mechanism 100 is mounted on the vehicle, and the driven member 500 exemplifies the drive wheels of the vehicle.

FIG. 13 is a schematic view of the drive mechanism 100. In the figure, the rotation speed of the second shaft 430 for driving the driven member 500 is A, the rotation speed of the input / output shaft 340 (first shaft 420) is B, and the rotation speed of the drive shaft 210 (input shaft 330) is C. To do. Further, in the following description, the gear ratio of the transmission mechanism 400 is expressed by X: Y = second axis 430 (driven member side): first axis 420 (accumulation unit side).

<1. Constant speed running at 50km / h>
For example, when the gear ratio of the transmission mechanism 400 is set to 1: 1 in a state where the vehicle is traveling at a speed of 50 km / h, the rotation speed becomes A = B ≦ C. At this time, since the input repulsive torque of the storage unit 300 (energy stored in the storage unit 300) is smaller than the output torque of the drive source 200 (energy input from the drive source 200 to the storage unit 300), the storage unit 300 The energy from the drive source 200 is gradually accumulated in the.

<2. Decelerate from 50km / h to 40km / h>
The operation unit 600 is operated (the accelerator is weakened), and the gear ratio of the transmission mechanism 400 is set to, for example, 1.2: 1. As a result, the output torque from the transmission mechanism 400 becomes larger than the torque of the storage unit 300, the rotation speed becomes A <B ≦ C, and the energy on the driven member 500 side moves to the storage unit 300. Since the drive source 200 is rotating, energy is stored in the storage unit 300 from both the driven member 500 and the drive source 200. That is, as the energy moves from the driven member 500 to the storage unit 300 as regenerative energy, the rotation speed of the driven member 500 gradually decreases, and the vehicle starts decelerating.

Then, the speed gradually approaches 40 km / h and becomes constant speed. At this time, the rotation speed becomes A = B ≦ C, and the regenerative energy of the storage unit 300 increases by the deceleration energy corresponding to 50 km-40 km = 10 km. Then, when the speed approaches the set speed of 40 km / h, the gear ratio of the transmission mechanism 400 is gradually returned to the original 1: 1 to bring the vehicle into a constant speed state. Due to this deceleration, the above 1. Similarly, energy is stored in the storage unit 300.

<3. Constant speed running at 40km / h>
When the gear ratio of the transmission mechanism 400 is 1: 1 (A = B) and the stored energy of the storage unit 300 reaches the maximum energy that can be stored in the storage unit 300, the drive source 200 is stopped (C = 0). ). As a result, the driven member 500 can be driven only by the stored energy of the storage unit 300. Then, when the stored energy of the storage unit 300 decreases, the drive source 200 is operated again, and the reduced energy is added to the storage unit 300 and stored.

<4. Sudden braking from 50km / h>
Above 1. When the operation unit 600 is operated (brake) to suddenly brake while traveling at a constant speed of 50 km / h, the gear ratio of the transmission mechanism 400 is rapidly changed to, for example, 2: 1. As a result, the ratio of the rotation speeds of the second axis 430 and the first axis 420 becomes A << B. Further, in the case of sudden braking, the regenerative energy suddenly flows into the storage unit 300, so that C = 0 may be set in order to prevent the energy transfer from the drive source 200 to the storage unit 300. However, the one-way bearing 220 does not reverse the drive source 200.

When the gear ratio is 2: 1 and the rotation speed ratio is A << B, the torque transmitted from the driven member 500 to the transmission mechanism 400 sharply increases. Then, a large amount of regenerative energy is rapidly accumulated in the storage unit 300, the number of rotations of the driven member 500 is reduced, and the speed of the vehicle is rapidly reduced.

If you want to drive at low speed after sudden braking, please refer to 3. above. The same control as in the above may be performed.

As described above, when the brake is operated, the braking force is converted into regenerative energy and stored in the storage unit 300, so that the kinetic energy is ultimately converted into heat energy in the driven member 500. Therefore, it is possible to eliminate the need for a general brake that is released to the outside, and to achieve simplification of the drive mechanism 100.

According to the present invention, the drive mechanism 100 can be configured by the simple mechanism as described above, and the clutch mechanism is not required, or even if it is adopted, a small number is required.

Further, since energy (including regenerative energy) is stored in the storage unit 300, it is not necessary to rely on the energy of only the drive source 200 even when sudden acceleration is performed, so that the drive source 200 has a small output. The drive mechanism 100 can be made smaller and lighter.

The above description is for explaining the present invention, and should not be construed as limiting or limiting the scope of the invention described in the claims. In addition, each part of the present invention is not limited to the above embodiment, and it goes without saying that various modifications can be made within the technical scope described in the claims.

14 and 15 show an embodiment in which a pair of constant load springs 360 and 361 are used as the accumulator 300 instead of the mainspring 310. The same members as those in the above embodiment are designated by the same reference numerals, and the description thereof will be omitted as appropriate.

The input shaft 330 and the input / output shaft 340 are pivotally supported by the bearings 331 and 341 and are arranged concentrically. An input side drum 362 is integrally rotatably attached to the tip of the input shaft 330. Further, a disk-shaped input / output side support plate 363 is integrally rotatably attached to the input / output shaft 340.

In the input / output side support plate 363, a pair of input / output side drums 364 and 364 are attached symmetrically and rotatably with the input side drum 362 interposed therebetween toward the input shaft 330 side.

Constant load springs 360 and 361 are wound around the input / output side drums 364 and 365, respectively. The constant load springs 360 and 361 are strip-shaped springs whose rewinding direction is the winding direction to the input / output side drums 364 and 365, and the ends of these constant load springs 360 and 361 in the rewinding direction are inserted respectively. It is fixed to the output side drums 364 and 365.

The other ends of the constant load springs 360 and 361 are fixed to the central input side drum 362, and the constant load springs 360 and 361 are wound around the input side drum 362 in a warped state by reversing the winding direction. It is possible to turn.

The constant load springs 360 and 361 have an urging force acting on the input / output side drums 364 and 365 in the rewinding direction, and store energy by bending back and winding the input side drum 362, while storing energy. Energy is released by rewinding the constant load springs 360 and 361 around the input / output drums 364 and 365.

That is, as shown in FIG. 16 (in FIG. 16, only the constant load spring 360, the input side drum 362, and the input / output side drum 364 are shown), the input side drum 362 is rotated as shown by the arrow 2A. As shown from the left to the right side of FIG. 16, the constant load spring 360 is sent out from the input / output side drum 364, and the constant load spring 360 is wound around the input side drum 362. As a result, energy is stored in the storage unit 300.

The energy storage is similar to rotating the input / output side support plate 363 in the direction of arrow 3A in FIG. That is, the rotation of the input / output side support plate 363 with respect to the input side drum 362 in the direction of arrow 3A means that the input side drum 362 rotates relatively in the direction of arrow 2A.

Therefore, the energy can be stored in the storage unit 300 by the rotation of the input shaft 330 or the reverse rotation of the input / output shaft 340.

On the other hand, the energy stored in the storage unit 300 is released by rewinding the constant load springs 360 and 361 around the input / output side drums 364 and 365. Since the input / output side drums 364 and 365 are connected to the input / output side support plate 363, the input / output drums 364 and 365 rotate when the input / output side drums 364 and 365 rewind the constant load springs 360 and 361. At the same time, the input / output side support plate 363 also rotates in the direction opposite to the arrow 3A. As a result, the energy stored in the storage unit 300 can rotate the input / output side support plate 363, that is, the input / output shaft 340.

Therefore, similarly to the above-described embodiment, the energy from the drive source 200 is stored in the storage unit 300 and released to the driven member 500, and the regenerative energy from the driven member 500 is stored in the storage unit 300. be able to.

By adopting the constant load springs 360 and 361 for the storage unit 300, energy can be stored and released by a constant torque regardless of the winding amount of the constant load springs 360 and 361 around the input side drum 362. The spring of the storage unit 300 does not necessarily have to be a constant load spring.

17 and 18 show a stop mechanism for the second disc 431 on the driven member 500 side. As shown in the figure, the second disc 431 has a through hole 433 formed at the center of rotation thereof, and a tubular protrusion is formed on the surface opposite to the second facing surface 432. A drive shaft transmission gear 434 is engraved on the outer peripheral side of the protrusion, and a gear-shaped brake wear portion 435 is engraved on the inner peripheral side. The drive shaft transmission gear 434 meshes with a gear 436 formed at the base end of the second shaft 430.

The second disc 431 is rotatably supported by a shaft 471 projecting from the housing 470 on the fixed side via a bearing 472. A recess is formed in the center of the shaft 471, and the Oldham shaft joint 474 is housed in the recess. At the tip of the Oldham shaft joint 474, a sensing shaft 475, which has a smaller diameter than the through hole 433 of the second disc 431 and is slidable in a plane parallel to the rotating surface of the second disc 431, protrudes from the Oldham shaft joint 474. It is installed. On the tip side of the Oldham shaft joint 474, a brake wear portion that abuts or meshes with the brake wear portion 435 of the second disc 431 when the sensing shaft 475 abuts or approaches the inner surface of the through hole 433 of the second disc 431. 476 are formed. The Oldham shaft joint 474 is supported by an urging means (not shown) so that the sensing shaft 475 is located at the center of the through hole 433 in the no-load state.

In the stop mechanism having the above configuration, as shown in FIG. 17, when the second spherical rolling element 450 moves to the center of the second disk 431, the sensing shaft 475 comes into contact with the second spherical rolling element 450, and the sensing shaft 475 comes into contact with the second spherical rolling element 450. The brake wear portions 435 and 476 are brought into contact with each other or mesh with each other, so that the second disc 431 is non-rotatably engaged with the housing 470. As a result, the rotation of the second disc 431 can be stopped.

On the other hand, in the state where the second spherical rolling element 450 is not in contact with the sensing shaft 475, the Oldham shaft joint 474 is located at the center of the through hole 433 of the second disc 431 by the urging means, so that the brake wear portions 435 and 476 Since they are separated from each other, the rotation of the second disc 431 is allowed.

By adopting the stop mechanism having the above configuration, the rotation of the second disc 431 can be stopped only by operating the second spherical rolling element 450, that is, the actuator 465.

On the other hand, when the second spherical rolling element 450 is located at the center of the second disk 431, it can be detected based on the position information of the actuator 465, and the driven member 500 can be stopped or in a neutral state at the discretion of the CPU 700. it can.

<Embodiments with different transmission mechanisms>
FIG. 19 shows different embodiments of the transmission mechanism 400 in the drive mechanism of the present invention. The transmission mechanism 400 of FIG. 19 can be arranged in the drive mechanism instead of the transmission mechanism described with reference to FIG. 4 and the like. Since the configuration of the storage unit 300 and the like is the same as that of the above embodiment, the description thereof will be omitted. Further, the members having the same reference numerals as those in the above embodiment have the same or equivalent configurations, and the description thereof will be omitted as appropriate.

In the transmission mechanism 400 of FIG. 19, in addition to the first disk 421 arranged in the storage unit so as to be able to transmit power via the first shaft 420 and the second disk 431 connected to the output side via the second shaft 430. , An auxiliary disk 480 driven by the first disk 421 is arranged on the first disk 421 side. The auxiliary disk 480 can be a disk body circumscribing the first disk 421, and the auxiliary disk 480 is arranged in a plane parallel to the first disk 421 and supported by a bearing 482 to rotate the first disk 421. It is driven and rotates in the direction opposite to that of the first disk 421.

For example, the first disc 421 and the auxiliary disc 480 are gears having teeth engraved on the peripheral surface, and the rotation of the first disc 421 can be transmitted to the auxiliary disc 480 by meshing the gears. Further, the peripheral surfaces of the first disk 421 and the auxiliary disk 480 may be roughly formed so that the peripheral surfaces are brought into contact with each other.

That is, the power transmission mechanism is not particularly limited as long as the first disk 421 and the auxiliary disk 480 are both rotated by driving the first shaft 420.

In the illustrated embodiment, the auxiliary disc 480 has the same diameter as the first disc 421 but may have a different diameter.

As shown in FIG. 19, the second disc 431 is arranged at a position facing both the first disc 421 and the auxiliary disc 480. More specifically, the second disc 431 is arranged so that the diameter is arranged on the line Lm connecting the rotation center of the first disk 421 and the auxiliary disk 480, that is, the extension line of the second axis 430 is orthogonal to the Lm. Will be done. It is desirable that the second disk 431 has a diameter equal to or larger than the distance between the rotation centers of the first disk 421 and the auxiliary disk 480, and the rotation center of the second shaft 430 is located at the contact point between the first disk 421 and the auxiliary disk 480.

Then, the first spherical rolling element 440 is in contact with the first disk 421 and the auxiliary disk 480 side, and the second spherical rolling element 450 is in contact with the second disk 431. The first spherical rolling element 440 and the second spherical rolling element 450 are in contact with each other in the same manner as in the above embodiment, are held by the holder (not shown), and can be moved in the line Lm direction by the holder moving means (not shown). ing.

However, by moving the spherical rolling elements 440, 450 on the disks 421, 480, 431 by operating the holder moving means, the rotation direction, the rotation speed, and the rotation torque output from the first axis 420 to the second axis 430. Can be adjusted as appropriate.

Specifically, when the first axis 420 is rotated, the first disk 421 is rotated (direction 2A), and the auxiliary disk 480 is driven in the direction opposite to that of the first disk 421 (direction 8A).

The first spherical rolling element 440 is driven and rotated in a vertical plane orthogonal to the rotation direction of the disks 421 and 480 by frictional contact with the first disk 421 or the auxiliary disk 480. In the example of FIG. 19, since the first spherical rolling element 440 is on the first disk 421, it rotates in the direction indicated by the arrow 4A in the figure.

Since the second spherical rolling element 450 is in frictional contact with the first spherical rolling element 440, the rotation of the first spherical rolling element 440 causes the first spherical rolling element 440 to be in the same plane as the first spherical rolling element 440. Drives in the opposite direction (direction 5A).

Then, the second disc 431, which is in frictional contact with the second spherical rolling element 450, is driven to rotate by the rotation of the second spherical rolling element 450. In the illustrated embodiment, the second disc 431 rotates in the direction indicated by arrow 3A. As a result, the second shaft 430 connected to the second disc 431 can rotate in the same 3A direction as the second disc 431 to drive a load (not shown).

The rotation direction, rotation speed, and rotation torque of the second disc 431 are determined by the positions of the first spherical rolling element 440 and the second spherical rolling element 450. For example, when the spherical rolling elements 440 and 450 are moved from the state of FIG. 19 to the outer peripheral side of the first disk 421 and the center side of the second disk 431, the rotation direction is the same as above, but the first axis 420 If the rotation speeds are the same, the rotation speed of the second shaft 430 increases and the rotation torque decreases.

On the other hand, even if the first spherical rolling element 440 moves to the auxiliary disk 480 side, the rotation directions of the first spherical rolling element 440 and the second spherical rolling element 450 remain the same as in FIG. However, since the second spherical rolling element 450 crosses the rotation center of the second disc 431, the rotation directions of the second disc 431 and the second shaft 430 are opposite to those of the arrow 3A in FIG. That is, if the arrow 3A is considered as the forward direction of the load, the driving force is transmitted in the backward direction of the load. Further, the load is powered by the rotation speed and the rotation torque according to the ratio of the distance between the rotation center of the auxiliary disc 480 and the first spherical rolling element 440 and the distance between the rotation center of the second disk 431 and the second spherical rolling element 450. Can be transmitted.

On the contrary, when the load is in the decelerated state, the rotational force transmitted from the load to the second shaft 430 is transmitted via the second disk 431, the spherical rolling elements 450, 440, the first disk 421 or the auxiliary disk 480. It can also be transmitted to one disk 421 and stored as regenerative energy from the first shaft 420 to the storage unit.

The release of energy required to drive the load from the storage unit or the storage of regenerative energy is achieved by the control by the CPU 700 described with reference to FIG.

100 Drive mechanism 200 Drive source 210 Drive shaft 220 One-way bearing 300 Storage unit 310 Casing 330 Input shaft 340 Input / output shaft 360 Constant torque spring 370 Casing 400 Transmission mechanism 420 First shaft 430 Second shaft 500 Driven member

Claims (4)

It is a drive mechanism that uses regenerative energy.
A drive source that rotates and drives a drive shaft that allows rotation in only one direction,
The storage has an input shaft connected to the drive source via the drive shaft, a storage means connected to the input shaft and capable of storing regenerative energy, and an input / output shaft connected to the storage means. A storage unit that stores regenerative energy in the means and can output the stored regenerative energy from the input / output shaft.
A transmission mechanism connected to the storage unit via the input / output shaft,
With a driven member connected to the transmission mechanism ,
The storage means is a constant load spring.
An input side drum is attached to the tip of the input shaft so that it can rotate integrally.
An input / output side support plate is integrally rotatably attached to the input / output shaft, and an input / output side drum is rotatably attached to the input / output side support plate.
The constant load spring is wound around the input / output side drum in the rewinding direction, and the other end of the constant load spring can be wound around the input side drum.
A drive mechanism that uses regenerative energy. The speed change mechanism can switch between forward rotation, reverse rotation, and stop state, and the gear ratio is variable.
The drive mechanism using the regenerative energy according to claim 1. The speed change mechanism has a variable speed change ratio.
The drive mechanism using the regenerative energy according to claim 2. A land-based mobile body including a drive mechanism using the regenerative energy according to any one of claims 1 to 3.

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