JPH05179979A - Energy recovery device - Google Patents

Abstract

PURPOSE:To dispense with complicated control, secure durability and reliability, and recover energy efficiently, speedily and smoothly by connecting three rotational members to each other, and providing a rolling element which decelerates a fly wheel at the time of inputting a positive torque, and accelerates the fly wheel at the time of inputting a negative torque. CONSTITUTION:A first rotational member(c) is connected to a power source (a) through an input shaft (b). A second rotational member (f) is connected to a load (d) through an output shaft (e). A fly wheel (i) is connected to a third rotational member (g) through a reverse rotation preventive mechanism (h). The first rotational member (c), the second rotational member (f), and the third rotational member (g) are connected to each other. A rolling element (j) which is a gear or the like is provided for decelerating the fly wheel (i) when a positive torque is input from the power source (a), and accelerating the fly wheel (i) when a negative torque is input from the power source (a).

Description

Detailed Description of the Invention

[0001]

The present invention is applied to automobiles and the like,
The present invention relates to an energy regeneration device that effectively regenerates energy from a power source such as an engine by operating a flywheel.

[0002]

2. Description of the Related Art Conventionally, as this type of energy regenerator, for example, Japanese Utility Model Publication No. 57-150244 (conventional example 1), Japanese Utility Model Publication No. 1-136671 (conventional example 2),
The one described in JP-A-49-65433 (conventional example 3) is known.

In the above-mentioned conventional example 1, as shown in FIG. 1, a planetary system in which the flywheel 10 is driven by engaging the clutch 26 (reverse speed increasing function) and the flywheel 10 is made free by disengaging the clutch 26. Gears are shown.

When this system is used for energy regeneration, first, the clutch is engaged during engine braking,
After increasing the flywheel and engine speed, disengage the clutch. And when using the energy of the flywheel, engage the clutch according to the driver's request,
This is done by transmitting torque.

The above-mentioned conventional example 2 shows a system in which a clutch is used to select a flywheel or an engine as an input source of a continuously variable transmission.

During engine braking, the flywheel is selected by matching the input rotation of the continuously variable transmission with the rotation of the flywheel and engaging the flywheel clutch.
Apply the engine braking by changing the gear ratio of continuously variable transmission. Further, in order to output the stored energy, a flywheel is selected in the same manner, and the drive ratio is obtained by changing the gear ratio of the continuously variable transmission. When the engine is driven, the flywheel clutch is disengaged, the engine clutch is engaged according to the engine speed of the continuously variable transmission, and the engine is selected.

In the above-mentioned conventional example 3, FIG. 3 shows a system in which the output transmission is a fluid torque converter and only the rotation control of the flywheel is performed by a continuously variable transmission. The transmission system has a clutch that stores energy from the engine to the flywheel during idling and a clutch that stores energy from the drive shaft to the flywheel.

Also in the case of the conventional example 3, similarly to the conventional example 2, it is necessary to change the gear ratio of the continuously variable transmission for controlling the flywheel together with the switching of the clutch.

[0009]

However, in the above-mentioned conventional energy regenerating device, since each device has a clutch for engaging / disengaging from the outside, the engaging / disengaging timing of this clutch is controlled. There is a common problem that it must be done and requires complicated control. In addition, each conventional example has the problems listed below.

(1) The conventional example 1 cannot regenerate energy while stopping the engine.

Further, unless the ratio of flywheel rotation speed / transmission input rotation speed is larger than the gear transmission gear ratio, torque cannot be obtained, and torque is generated while sliding the clutch due to the difference in rotation speed. large.

(2) In the conventional example 2, when the engine and the flywheel are used as the power sources at the same time, both the flywheel clutch and the engine clutch are engaged.
As the rotation of the flywheel decreases, the engine speed also decreases, so all of the engine horsepower cannot be used during acceleration.

(3) In Conventional Example 3, the clutch is released → shifting →
The operation of clutch engagement is necessary and it takes time, and if a rotation difference occurs, a shock will occur when the clutch is engaged.

The present invention has been made by paying attention to the above problems, and in an energy regeneration device having a flywheel that regenerates energy from a power source, does not require any complicated control and is durable and reliable. The first task is to achieve effective, swift and smooth energy regeneration while ensuring the above.

In addition to the above first problem, the second problem is to guarantee the device lubrication even when the rotation of the power source is stopped.

In addition to the above-mentioned first or second problem,
A third object is to prevent over-rotation of the flywheel and ensure generation of a power source braking torque during high-speed rotation of the flywheel.

[0017]

In order to solve the above first problem, in the energy regeneration device according to the first aspect, the power source, the load, and the reverse rotation prevention are provided to regenerate energy to each of the three rotating members of the rolling element. It is configured to connect the three elements with the flywheel having the mechanism.

That is, as shown in the claim correspondence diagram of FIG. 1, the power source a is connected to the first rotating member c via the input shaft b, and the load d is connected to the second rotating member c via the output shaft e. A rotary member f, a flywheel i connected to a third rotary member g through a reverse rotation preventing mechanism h, the first rotary member c, a second rotary member f, and a third rotary member g are connected to each other, and It has a gear or a rolling element j similar to a gear that decelerates the flywheel i when a positive rotational torque is input from the power source c and accelerates the flywheel i when a negative rotational torque is input from the power source c. And

In order to solve the above-mentioned second problem, in the energy regeneration device according to the second aspect, as shown in the claim correspondence diagram of FIG. 1, the load f is connected in the energy regeneration device according to the first aspect. A lubricating oil pump k is provided in the second rotary member system.

In order to solve the above-mentioned third problem, in the energy regeneration device according to claim 3, as shown in the claim correspondence diagram of FIG. 1, in the energy regeneration device according to claim 1 or 2, the flywheel. In the rotating system of i,
It is characterized in that a braking mechanism m for preventing excessive rotation of the flywheel i is provided.

[0021]

The operation of the present invention will be described.

When a positive rotational torque is input from the power source c,
When the flywheel i connected to the third rotation member g of the rolling element j via the reverse rotation prevention mechanism h is decelerated and the flywheel i is rotating, its rotational energy is released and the load d is the power. It is driven by the combined torque of the source c and the flywheel i. However, when the flywheel i is stopped, the reverse rotation prevention mechanism h operates and the stopped state of the flywheel i is maintained. Further, when the negative rotational torque is input from the power source c, the rolling element j
The flywheel i connected to is accelerated, and the deceleration energy of the power source c is converted into the rotational energy of the flywheel i and stored. And flywheel i
The rotational speed of is automatically controlled so that the torque of the rotating element connected to the rolling element j maintains a constant relationship.

The operation of the invention according to claim 2 will be described.

The second rotary member system to which the load f is connected is
Even if the power source c is stopped, the flywheel i keeps rotating as long as the flywheel i rotates.
Therefore, the lubricating oil pump k provided in the second rotary member system to which the load f is connected suppresses the generation of frictional heat of the rolling element j and the reverse rotation preventing mechanism h even when only the flywheel i is rotating. You can

The operation of the invention according to claim 3 will be described.

When the rotation speed of the flywheel i connected to the rolling element j becomes extremely high due to the input torque condition from the power source c, the braking mechanism m provided in the rotation system of the flywheel i operates. And flywheel i
Over rotation is prevented. Furthermore, when a negative rotation torque is input from the power source c in the flywheel high rotation range, generation of the power source braking torque by accelerating the flywheel i is guaranteed.

[0027]

【Example】

 (First Embodiment) The configuration will be described.

FIG. 2 is a schematic diagram showing a power train of a vehicle to which the energy recovery system of the first embodiment corresponding to the present invention described in claim 1 is applied.

As shown in FIG. 2, the power train of the vehicle includes an engine 1 (corresponding to a power source), an energy regeneration device 2, a fluid coupling 3, and a forward / reverse switching device 4.
, Toroidal transmission 5, propeller shaft 6,
Differential gear 7 and drive shafts 8 and 9
And drive wheels 10 and 11 (a continuously variable transmission CVT composed of a fluid coupling 3, a forward / reverse switching device 4 and a toroidal transmission device 5 corresponds to a load).

The energy regenerating device 2 is the engine 1
A first rotating member 2d connected via a damper 2a, an engine flywheel 2b and an input shaft 2c, a second rotating member 2f connected to a load below the fluid coupling 3 via an output shaft 2e, A flywheel 2i connected to a three-rotation member 2g via a one-way clutch 2h (corresponding to a reverse rotation preventing mechanism), the first rotation member 2d, the second rotation member 2f, and a third rotation member 2g are connected to each other. It has a single pinion planetary gear 2j (corresponding to a rolling element) that decelerates the flywheel 2i when a positive rotational torque is input from the engine 1 and accelerates the flywheel 2i when a negative rotational torque is input from the engine 1. ing. The first rotating member 2d is a rotating member connected to the ring gear of the single pinion planetary gear 2j, and the second rotating member 2f is the single pinion planetary gear 2j.
Of the single pinion planetary gear 2j, and the third rotating member 2g is a rotating member corresponding to the sun gear of the single pinion planetary gear 2j.

The fluid coupling 3 includes a coupling cover 3a connected to the output shaft 2e, and a pump impeller 3b provided on the coupling cover 3a.
And a turbine runner 3c arranged at a position facing the pump impeller 3b, and a damper 3 attached to the turbine runner 3c.
It comprises an output shaft 3e connected via d, and a lockup clutch 3f capable of directly connecting the output shaft 3e and the coupling cover 3a. The lock-up clutch 3f is controlled to be engaged / disengaged according to traveling conditions and the like.

The forward / reverse switching device 4 includes a double planetary gear 4a, a forward clutch 4c capable of engaging the pinion carrier 4b of the double planetary gear 4a and the output shaft 3e, and the double pinion planetary gear 4a. This ring gear has a reverse brake 4e that can rest on the case 4d, and an output shaft 4f that is directly connected to the pinion carrier 4b. The output shaft 3e is directly connected to the sun gear of the double pinion planetary gear 4a.

In the toroidal transmission 5, the input disk 5a connected to the output shaft 4f, the output disk 5b connected to the propeller shaft 6, and the opposing surfaces of the disks 5a and 5b are frictionally contacted with each other. Power roller 5
and c. The power roller 5
As disclosed in Japanese Utility Model Laid-Open No. 63-92859, c is tilted in accordance with vehicle operating conditions such as vehicle speed and throttle opening via a control valve and a hydraulic actuator (not shown), so that the input disk The gear ratio between 5a and the output disk 5b is continuously changed.

The operation will be described.

FIG. 3 shows the energy recovery system 2 of the first embodiment.
4 is an operation explanatory diagram of FIG. 4, and FIG. 4 is an engine (DRIVE), C connected to the single pinion planetary gear 2j.
It is a collinear chart which shows the rotation speed relationship of each rotary element of VT (LOAD) and a flywheel (F / W).

For example, the specific specifications are set as follows.

Maximum engine speed 6000 rpm Maximum continuously variable transmission input speed 8000 rpm Maximum flywheel speed 12000 rpm Planetary gear ratio α = 0.5 Then, engine torque is TE and CVT input torque is T
When C and the flywheel torque are TF, the moment around the second rotating member 2f to which the CVT is connected is: TF = α · TE (1) The rotation around the third rotating member 2g to which the flywheel 3i is connected. The moment of is TC = (1 + α) TE (2), that is, α = 0.5, the flywheel torque TF is 0.5 times the engine torque TE, and the CVT input torque TC is , Always balance to be 1.5 times the engine torque TE.

(A) When the vehicle starts When the engine 1 is started with the forward clutch 4c in the released state, the flywheel 2i attempts to decelerate in the reverse rotation direction because the rotational torque of the engine 1 is positive. For the reverse rotation of the third rotating member 2g, the one-way clutch 2h mechanically drives the flywheel 2
i remains stopped.

Thereafter, when the forward clutch 4c is engaged, the single pinion planetary gear 2j acts as a reduction gear (ring gear input, carrier output, sun gear fixed), and the reduction ratio becomes 1.5 according to the equation (2). As a result, a torque that is 1.5 times the torque of the engine 1 is input to the continuously variable transmission CVT as a starting torque.

(B) When the vehicle is traveling When the vehicle is traveling while appropriately operating the accelerator while the forward clutch 4c is engaged, the energy regeneration action is exerted as follows.

First, when a negative rotational torque is input from the engine 1 to the energy regenerator 2 by absorbing torque by the engine 1 by releasing the accelerator pedal or shifting gears in the downshift direction, the flywheel 2i is accelerated and rotated. (Fig. 4), the deceleration energy of the load is the flywheel 2i.
Stored as rotational energy. That is, (1) above
According to the formula (2), the flywheel 2i is accelerated and rotated at a torque 0.5 times the engine torque, and the formula (2) allows the continuously variable transmission CVT to reach 1.5 times the engine torque. Double negative rotation torque (engine brake torque) will be applied.

First, when a positive rotational torque is input from the engine 1 to the energy regenerator 2 by increasing the output torque of the engine 1 by depressing the accelerator or shifting in the upshift direction, the flywheel 2i is decelerated. It rotates (FIG. 4), and the rotational energy stored in the flywheel 2i is released. That is, according to the equation (1), the flywheel 2i is decelerated and rotated with a torque that is 0.5 times the engine torque, and according to the equation (2), the flywheel 2i is reduced with respect to the continuously variable transmission CVT. A positive rotation torque (driving torque) that is 1.5 times the engine torque is applied.

As described above, during traveling, the rotational energy is accumulated in the flywheel 2i and the flywheel 2i depending on whether the direction of the rotational torque of the engine 1 is negative or positive.
And rotational energy release from the.

The rotational speed of the flywheel 2i during running is automatically controlled so that the output torque to the continuously variable transmission CVT is always 1.5 times the engine torque without any external control. The rotation will be controlled.

The maximum output to the continuously variable transmission CVT is as follows: engine speed = 6000 rpm, flywheel speed = 12000 rpm, CVT input speed = 8000 rp.
At m, you can get twice the engine horsepower.

(C) When the engine is stopped Immediately after the engine is stopped and the flywheel 2i is rotating, the single pinion planetary gear 2j is used.
Since the reduction gear has a fixed ring gear (reduction ratio is 3), the rotational energy from the flywheel 2i can be used to perform energy regeneration traveling by the flywheel 2i alone. When the number of revolutions of the flywheel 2i is maximum, the characteristic A shown in FIG. 4 is obtained.

(D) When the flywheel rotation system is locked When the flywheel 2i and the one-way clutch 2h are locked due to seizure, the single pinion planetary gear 2j is a reduction gear with a fixed sun gear (reduction ratio of 1.5). ), The vehicle can be driven only by the engine 1, and the fail safe is established when the flywheel rotation system is locked. Incidentally, when the rotation speed of the engine 1 is maximum, the characteristic B in FIG. 4 is obtained.

The effect will be described.

(1) Energy regeneration device 2 having a flywheel 3i for regenerating energy from the engine 1
At 3 in the single pinion planetary gear 2j
In order to regenerate energy to each of the two rotating members 2d, 2f, 2g, the configuration is such that the engine 1, the continuously variable transmission CVT as a load, and the flywheel 2i having the one-way clutch 2h are connected to each other. Since the rotation speed of 2i is automatically controlled so that a predetermined torque relationship is always obtained between the rotating elements, there is no need for complicated control as in the prior art, and the clutch It is possible to effectively accumulate energy when a negative rotation torque is input from the engine 1 and quickly and smoothly release energy when a positive rotation torque is input from the engine 1 while generating heat and ensuring durability reliability.

(2) Energy regeneration device 2 of the first embodiment
Since this is applied in combination with the continuously variable transmission CVT of the vehicle, energy regenerative traveling can be performed by the flywheel 2i alone, and fail-safe that engine driven traveling is secured when the flywheel rotation system is locked can also be achieved. ..

(3) Energy regeneration device having a flywheel 2i whose rotation speed is automatically controlled so that the output torque to the continuously variable transmission CVT is always 1.5 times the engine torque. Since No. 2 is applied in combination with the continuously variable transmission CVT of the vehicle, when continuously variable transmission of the toroidal transmission 5 is performed, shift control can be easily performed.

By the way, the flow chart of the shift control operation is shown in FIG. 5, in which the flywheel rotational speed NF is read in step 50, and the target engine rotational speed NE at that time is read from the throttle opening degree in step 51. Then, in step 52, the target CVT input rotational speed NC is calculated by the formula described in the step frame, and in step 53, the target CVT is input.
The gear ratio can be controlled by determining the gear ratio based on the VT input rotational speed NC and outputting a gear control command for obtaining the gear ratio determined in step 54.

A modified example of the first embodiment will be described below.

FIG. 6 is a schematic view showing an energy regenerator with a built-in coupling. In FIG. 2, the energy regeneration device 2 and the fluid coupling 3 are arranged independently, whereas in FIG. 6, the energy regeneration device 2 is built in the fluid coupling 3, and in this case, the axial dimension It can be shortened.

FIG. 7 is a schematic view showing a double pinion planetary gear type energy regenerator. In this example, the double pinion planetary gear 2k is used as the rolling element, the first rotating member 2d is the rotating member corresponding to the pinion carrier, and the second rotating member 2f is the rotating member connected to the ring gear.

Functionally, it is exactly the same as that of the first embodiment, and when α = 0.5, the CVT input torque is twice the engine torque.

FIG. 8 is a schematic view showing a differential gear type energy regeneration device. In this example, the differential gear 2m is used as the rolling element, the input shaft 2c is also used as the first rotating member and is coupled to one side gear, and the second rotating member 2f corresponds to the differential case, and is connected via the output gear 2n. It corresponds to the shaft that is connected to the output shaft 2e and the third rotating member 2g is connected to the other side gear. In this case, the alignment chart is as shown in FIG. 9, and the CVT input torque is twice the engine torque. Also, NFmax = 12000 rpm, NEmax = 60
At 00 rpm and NCmax = 9000 rpm, three times the engine horsepower can be obtained.

(Second Embodiment) The configuration will be described.

FIG. 10 is a schematic diagram showing an energy regeneration device of a second embodiment corresponding to the present invention described in claims 1 and 2.

As shown in FIG. 10, the energy regeneration device 2 of the second embodiment has a lubricating oil pump 21 on the output shaft 2e to which the continuously variable transmission CVT is connected in addition to the device of the first embodiment.
And a one-way clutch 22 for ensuring the rotation of the lubricating oil pump 21 is provided on the input shaft 2c to which the engine 1 is connected. In addition, by the device cover 23,
Engine flywheel chamber 23a and gear train chamber 2
3b, flywheel chamber 23c, and oil pump chamber 2
It is defined as 3d.

The operation will be described.

Output shaft 2e to which continuously variable transmission CVT is connected
The flywheel 2i even if the engine 1 is stopped
The rotation is maintained by the flywheel 2i as long as is rotating.

Therefore, by the lubricating oil pump 21 provided on the output shaft 2e to which the continuously variable transmission CVT is connected, not only when the engine 1 is rotationally driven but also when only the flywheel 2i is rotating. Oil pump chamber 23
By supplying oil from d to the gear train chamber 23b, it is possible to suppress the generation of frictional heat of the single pinion planetary gear 2j and the one-way clutches 2h, 22.

The effect will be described.

The following effects are added to the effects of the first embodiment device.

(4) Since the lubricating oil pump 21 is provided on the output shaft 2e to which the continuously variable transmission CVT is connected, the engine 1
The device lubrication can be guaranteed even when the rotation of the device is stopped.

(5) Energy regeneration device 2 of the second embodiment
When combined with the continuously variable transmission CVT, the oil pump provided in the continuously variable transmission CVT can be replaced with the lubricating oil pump 21 provided in the output shaft 2e.

A modification of the second embodiment will be described below.

FIG. 11 is a schematic view showing an energy regenerator in which a lubricating oil pump 21 is provided on the side portion of the single pinion planetary gear 2j so as to be connected to the second rotating member 2f. In this case, the axial dimension of the device can be shortened compared to the example of FIG.

FIG. 12 is a schematic diagram showing an energy regeneration device of the second embodiment in which a lubricating oil pump 21 and a one-way clutch 22 are provided on the output shaft 2e of the energy regeneration device shown in FIG.

FIG. 13 is a schematic diagram showing an energy regeneration device of the second embodiment in which a lubricating oil pump 21 and a one-way clutch 22 are provided on the output shaft 2e of the energy regeneration device shown in FIG.

(Third Embodiment) The configuration will be described.

FIG. 14 shows claims 1, 2, and 3.
FIG. 6 is a schematic view showing an energy regeneration device of a third embodiment corresponding to the described invention.

The energy recovery system of the third embodiment is shown in FIG.
As shown in FIG. 4, a hydraulic brake 24 (corresponding to a braking mechanism) is provided between the flywheel rotation system of the device shown in FIG. 11 and the device cover 23.

The operation will be described.

When the flywheel 2i rotates at high speed,
The pressure generated in the pitot tube 24a close to the flywheel 2i is introduced into the brake piston chamber 24b, overcomes the return spring 24c, and the piston 24d strokes to engage the multi-plate brake 24e to brake the flywheel 2i. , To prevent excessive rotation of the flywheel 2i.

The effect will be described.

The following effects are added to the effects of the first and second embodiment devices.

(6) Since the hydraulic brake 24 for restricting the high speed rotation of the flywheel 2i is provided, the flywheel 2
i is prevented from over-rotating, and when a negative rotation torque is input from the engine 1 during high-speed rotation of the flywheel 2i, torque absorption by the flywheel 2i is allowed, which causes engine brake torque to be generated. Can be guaranteed.

A modification of the third embodiment will be described below.

FIG. 15 is a schematic view showing an energy regenerating device in which a centrifugal brake 25 (corresponding to a braking mechanism) is provided between the flywheel 2i and the device cover 23 of the device shown in FIG. When the flywheel 2i rotates at high speed,
The centrifugal force applied to the weight 25a overcomes the spring force of the spring 25b, and the weight 25a is brought into pressure contact with the friction material 25c attached to the inner surface of the device cover 23, thereby exerting a braking force that suppresses excessive rotation of the flywheel 2i. ..

FIG. 16 is a schematic diagram showing an energy regeneration device in which an electric brake 26 (corresponding to a braking mechanism) is provided on a third rotating member 2g to which the flywheel 2i of the device shown in FIG. 11 is connected. In FIG. 16, 26a is a generator rotor,
Reference numeral 26b is a generator coil, and 26c is a rotary pickup. An electric circuit is shown in FIG. 17. The output of the rotary pickup 26c is connected to the F / V converter 26d. When the output voltage becomes higher than the reference voltage, the comparator 26
The exciting current of the generator flows from e, and the braking force acts by generating power.

Although the embodiments have been described above with reference to the drawings, the specific configuration is not limited to the embodiments, and modifications and additions within the scope of the present invention are included in the present invention. Be done.

For example, in the embodiment, the example of application in combination with the toroidal type continuously variable transmission CVT is shown, but it can be applied in combination with the V belt type continuously variable transmission or automatic multi-stage transmission.

[0085]

As described above, according to the present invention as set forth in claim 1, in the energy regeneration device having the flywheel that regenerates energy from the power source,
Since the three elements of the power source, the load, and the flywheel with the reverse rotation prevention mechanism are connected to regenerate energy to each of the three rotating members of the rolling element, no complicated control is required at all, and durability is reliable. The effect of being able to achieve effective, swift and smooth energy regeneration while securing the property is obtained.

Further, in the present invention according to claim 2,
Since the second rotating member system is provided with the lubricating oil pump, in addition to the above-described effects, it is possible to ensure the device lubrication even when the rotation of the power source is stopped.

Further, in the present invention according to claim 3,
Since the rotation system of the flywheel is provided with the braking mechanism, in addition to the above effects, it is possible to prevent the flywheel from over-rotating and to ensure that the power source braking torque is generated during high-speed rotation of the flywheel.

The energy regenerator of the present invention, in particular when applied in combination with a continuously variable transmission or an automatic transmission of a vehicle, can obtain a torque increasing action without using a torque converter and can easily perform shift control. Moreover, in terms of layout, it is a technique that is useful in various respects, such as simply inserting this unit between the engine and the transmission.

[Brief description of drawings]

FIG. 1 is a claim correspondence diagram showing an energy regeneration device of the present invention.

FIG. 2 is a schematic diagram showing a power train of a vehicle to which the energy regeneration device of the first embodiment is applied.

FIG. 3 is an operation explanatory view of the energy regeneration device of the first embodiment.

FIG. 4 is a collinear diagram showing the rotational relationship of each rotary member in the energy regeneration system of the first embodiment.

FIG. 5 is a flowchart showing a flow of a shift control operation of the continuously variable transmission to which the device of the first embodiment is applied.

FIG. 6 is a schematic diagram showing a modified example of the energy regeneration device of the first embodiment.

FIG. 7 is a schematic view showing another modified example of the energy regeneration device of the first embodiment.

FIG. 8 is a schematic view showing another modified example of the energy regeneration device of the first embodiment.

9 is a collinear chart showing the rotational relationship of each rotary member in the device shown in FIG.

FIG. 10 is a schematic diagram showing an energy regeneration device according to a second embodiment.

FIG. 11 is a schematic view showing a modified example of the energy regeneration device of the second embodiment.

FIG. 12 is a schematic view showing an energy regeneration device of a second embodiment based on the device shown in FIG. 7.

FIG. 13 is a schematic view showing an energy regeneration device of a second embodiment based on the device shown in FIG.

FIG. 14 is a schematic view showing an energy regeneration device of a third embodiment based on the device shown in FIG.

FIG. 15 is a schematic view showing an energy regeneration device of a third embodiment based on the device shown in FIG.

FIG. 16 is a schematic view showing another example of the energy regeneration system of the third embodiment based on the system shown in FIG.

17 is an electric circuit diagram of an electric brake of the apparatus shown in FIG.

[Explanation of symbols]

 a power source b input shaft c first rotating member d load e output shaft f second rotating member g third rotating member h reverse rotation preventing mechanism i flywheel j rolling element k lubricating oil pump m braking mechanism

Claims (3)

[Claims] 1. A first power source is connected via an input shaft.
A rotating member, a second rotating member whose load is connected via an output shaft, a flywheel connected to a third rotating member via a reverse rotation preventing mechanism, the first rotating member, the second rotating member, Three rotating members are respectively connected, and a gear or a rolling element similar to a gear that accelerates the flywheel when a positive rotational torque is input from the power source and accelerates the flywheel when a negative rotational torque is input from the power source, Energy regeneration device characterized in that. 2. The energy regeneration device according to claim 1, wherein a lubricating oil pump is provided in the second rotating member system to which the load is connected. 3. The energy regeneration device according to claim 1, wherein the rotation system of the flywheel is provided with a braking mechanism that prevents excessive rotation of the flywheel.