KR20130058433A - Energy recycling apparatus - Google Patents

Energy recycling apparatus Download PDF

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Publication number
KR20130058433A
KR20130058433A KR1020110124435A KR20110124435A KR20130058433A KR 20130058433 A KR20130058433 A KR 20130058433A KR 1020110124435 A KR1020110124435 A KR 1020110124435A KR 20110124435 A KR20110124435 A KR 20110124435A KR 20130058433 A KR20130058433 A KR 20130058433A
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KR
South Korea
Prior art keywords
sun gear
planetary gear
carrier
unit
driving force
Prior art date
Application number
KR1020110124435A
Other languages
Korean (ko)
Inventor
박지형
최남선
이한구
문덕수
Original Assignee
주식회사 인팩
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 주식회사 인팩 filed Critical 주식회사 인팩
Priority to KR1020110124435A priority Critical patent/KR20130058433A/en
Publication of KR20130058433A publication Critical patent/KR20130058433A/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/14—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers accumulating utilisable energy, e.g. compressing air
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/419—Gears
    • B60G2204/4191—Planetary or epicyclic gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2300/00—Indexing codes relating to the type of vehicle
    • B60G2300/60—Vehicles using regenerative power
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/30—Propulsion unit conditions
    • B60G2400/302—Selected gear ratio; Transmission function
    • B60G2400/306—Selected gear ratio; Transmission function overdrive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/30—Propulsion unit conditions
    • B60G2400/31—Clutch condition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N11/00—Generators or motors not provided for elsewhere; Alleged perpetua mobilia obtained by electric or magnetic means
    • H02N11/002—Generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02N—ELECTRIC MACHINES NOT OTHERWISE PROVIDED FOR
    • H02N11/00—Generators or motors not provided for elsewhere; Alleged perpetua mobilia obtained by electric or magnetic means
    • H02N11/006—Motors

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

PURPOSE: An energy regeneration device is provided to regenerate the kinetic energy generated by an impact or a vibration added on a pressure receiving portion of a vehicle from the outside into electrical energy, thereby improving the energy efficiency of the vehicle. CONSTITUTION: An energy regeneration device(1) comprises an input unit(3), a one-way motor(5), a speed increasing unit(7), and a power generating unit(9). The input unit is connected to a driving source identical to that of a driving disc and inputs a rotation-driving force generated by the driving source. The one-way motor transmits the rotation-driving force in one direction by a one-way clutch(13) mounted on the input unit. The speed increasing unit accelerates the speed of the rotation of an input shaft(21) caused by the rotation-driving force transmitted from the one-way motor. The power generating unit is joined to an output shaft of the speed increasing unit, thereby generating electrical energy using the accelerated rotation-driving force.

Description

Energy recycling apparatus

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an energy regeneration device, and more particularly, to various types of kinetic energy generated in a vehicle during operation and discarded as it is, such as a transmission device used for regenerative braking of an electric vehicle. The present invention relates to an energy regeneration device capable of increasing the rotational speed input from the driving source at a desired ratio in transferring the driving force to the power generation unit.

In general, the suspension is a shock absorber that absorbs the impact of the road surface through the wheels so as not to be transmitted to the vehicle body or the occupant, as shown by reference numeral 101 in Figure 1, the shock absorber 103, the suspension spring 105 , Upper and lower arms 107, 108 and the like as a basic element.

In particular, the shock absorber 103 is a portion that absorbs most of the shock applied to the vehicle body 111, and is not only applied to an electronically controlled suspension that electronically controls shock absorption characteristics in recent years, but also to a driving state through an ECU. It is also completely replaced by a hydraulic system that allows precise control of the shock absorbing performance.

However, the suspension 101 is developed by focusing only on the shock or vibration transmitted through the wheel 109 as an injurious element that adversely affects the vehicle performance and how to suppress and extinguish them as much as possible. come. Thus, the shock or vibration applied to the suspension 101 has been extinguished or discarded as far as possible through the shock absorber 103 or the suspension spring 105, but has not been recycled as a drive source.

The present invention has been made to solve the problems of the suspension of the conventional vehicle, such as the above, by mounting the energy regeneration device in the force receiving portion of the vehicle, such as the shock absorber or suspension spring of the suspension, the vehicle, The purpose of the present invention is to improve the energy efficiency of a vehicle by regenerating kinetic energy due to shock or vibration applied to a hydraulic pressure part such as a suspension from the outside into electrical energy through an energy regeneration device.

In order to achieve the above object, the present invention provides an input unit through which a rotational driving force is transmitted from a driving source; A one-way transmission unit configured to transmit the rotational driving force transmitted from the input unit only in one forward rotation direction by a one-way clutch mounted coaxially to the input unit; A speed increasing unit configured to increase the rotation speed by the rotation driving force transmitted from the one-way transmission unit; And a power generation unit coupled to the output shaft of the speed increasing unit to generate electricity by the rotational driving speed increased by the speed increasing unit.

In addition, the speed increasing unit is preferably configured by arranging one or more planetary gear trains in series.

The speed increasing unit may include: a first carrier having an input shaft protruding on one side axis; A first planetary gear pair rotatably mounted at regular angular intervals on the same radius from a center of the surface opposite the input shaft of the first carrier; A second sun gear carrier integrally formed on one side axis of the first sun gear meshed with the center of the first planetary gear pair; A second planetary gear pair rotatably mounted at a predetermined angle on the same radius from the center of the second sun gear carrier; A third sun gear carrier integrally formed on one side axis with a second sun gear meshed with the center of the second planetary gear pair; A third planetary gear pair rotatably mounted at a predetermined angle on the same radius from the center of the second sun gear carrier; A third sun gear meshed with and mounted to the center of the third planetary gear pair, the output shaft protruding on a surface axis opposite to the second sun gear carrier; And a ring gear in which the first, second, and third planetary gear pairs are externally externally engaged with each other.

Therefore, according to the energy regeneration device of the present invention, the impact or vibration applied to the vehicle body through the suspension from the vehicle wheel is regarded as kinetic energy, and all are extinguished by the shock absorber or the suspension spring. Since the conversion can be utilized, the energy efficiency of the vehicle can be further improved.

1 is a perspective view schematically showing a conventional general vehicle suspension.
2 is a schematic perspective view of a suspension to which an energy regeneration device according to an embodiment of the present invention is applied;
3 is an enlarged perspective view of the energy regeneration device shown in FIG.
Figure 4 is an exploded perspective view showing in detail the speed increase portion shown in FIG.
FIG. 5 is a partially cutaway perspective view illustrating the speed increasing unit of FIG. 4 in an assembled state; FIG.
FIG. 6 is a plan view showing the planetary gear train shown in FIG. 5; FIG.

Hereinafter, an energy regeneration device according to an embodiment of the present invention will be described with reference to the accompanying drawings.

In the energy regeneration device of the present invention, for example, as shown schematically by reference numeral 1 in FIG. It is mounted to interlock with one side of the absorber 83, as shown in the case of the hydraulic shock absorber 83, the plunger rod 84 to the plunger to reciprocate vertically in conjunction with a plunger (not shown) inside the shock absorber 83 , And one end of the drive link 86 through the connection link 85 to one end of the plunger rod 84, and then pin-couple the other end of the drive link 86 to the drive disk 87 as a whole. The drive disk 87 is rotated through a link structure consisting of three links.

In addition, the energy regeneration device 1 of the present invention can be applied to other shock absorbers in addition to the suspension shown in FIG. 2, and also applied to the suspension, depending on the type of suspension or drive type, It can be connected in such a way, and of course, it is possible to give a variety of changes to the link structure that delivers the shock or vibration applied to the hydraulic portion as kinetic energy.

On the other hand, the energy regeneration device 1 of the present invention, as shown by the reference numeral 1 in Figs. 9) consists of

Here, the input unit 3 is a part connected to a driving source such as the drive disk 87 of FIG. 2, and as shown in FIG. 3, various kinds of shaft joint means such as the rotating bush 11 may be used. The rotational driving force generated from the driving source is input to the energy regeneration device 1.

The one-way transmission unit 5 is a means for transmitting the rotational force in one direction only from the drive disk 87 toward the power generation unit 9, for example, the drive motor to use the rotational force of the wheel for power generation when regenerative braking in the electric vehicle When transmitting to the drive force transmission is made, on the contrary, when the drive motor is operated to rotate the wheels so as not to transmit power to the wheels from the drive motor.

To this end, the one-way transmission part 5 increases the rotational driving force transmitted to the input part 3 when the one-way clutch 13 coaxially mounted to the input part 3 and this one-way clutch 13 are connected. It consists of an electric gear (15) or a series of electric gear to transmit to.

Here, the one-way clutch 13 again has a form similar to that of a conventional one-way clutch as schematically shown in FIG. 3, and includes a bush hub at the center side integrally formed with or integrally coupled with the rotary bush 11. 17) and the outer gear 19 of the outer gear. For example, in the case of the sprag type, the bush hub (from the rotating bush 11 by the wedge action of the sprag during the forward rotation according to the shape characteristic of the sprag) 17) transmits the rotational force transmitted through the external gear 19. On the contrary, when the external gear 19 rotates faster than the bush hub 17, that is, when the power transmission from the external gear 19 toward the bush hub 17 occurs, the wedge action of the sprag does not occur. This prevents the rotational force of the external gear 19 from being transmitted to the bush hub 17.

In addition, the electric gear 15 meshed with the external gear 19 is a spur-type spur gear as shown in FIG. 3, and the external gear 18 and the external gear 18 mounted on the input shaft 21 of the speed increasing unit 7 are shown. (19) is connected so that the rotational driving force of the external gear 19 is accurately transmitted to the speed increasing unit (7) through the driven gear (18).

The speed increasing portion 7 is a portion for increasing the rotational speed of the input shaft 21 by the rotational driving force transmitted from the one-way transmission portion 5, as shown in Figures 3 to 5, one or preferably The planetary gear trains 30, 50, and 70 are arranged in series.

In particular, the speed increase unit 7 may be configured by combining three planetary gear trains 30, 50, and 70, as shown in FIGS. 3 to 5, wherein the speed increase unit 7 is illustrated. As shown, the first carrier 31, the first planetary gear pair 33, the second sun gear carrier 51, the second planetary gear pair 53, the third sun gear carrier 71, and the third planetary gear pair 73 , And the third sun gear 75.

Here, the first carrier 31 is a disk-shaped support plate material to which the rotational driving force transmitted from the one-way transmission part 5 to the speed increasing part 7 is input first, as shown in FIGS. 4 to 6. The input shaft 21 protrudes and forms on the axis line of the center of an upper surface so that it may be directly connected to the speed increasing part 7 input shaft 21. In addition, like the carriers of the general planetary gear train, the first carrier 31 has a plurality of fixing pins 34 protruding at regular angular intervals at equal angular intervals from the center on the opposite surface of the input shaft 21, that is, the bottom surface. Each of the first planetary gear pairs 33 is rotatably supported.

The first planetary gear pair 33 is a means for increasing the rotational speed of the first carrier 31 by rotating and rotating about the first sun gear 35 as shown in FIGS. 4 to 6. As shown above, it is rotatably mounted on the bottom surface of the first carrier 31 through the fixing pin as above, and is fixed on the same radius from the surface opposite the input shaft 21 of the first carrier 31, that is, the center of the bottom surface. It is arranged at an angular interval, preferably three are provided in pairs as shown, when rotating around the fixing pin while revolving around the first sun gear 35 by the rotational force of the first carrier 31 At the same time, each is matched around the first sun gear 35 so as to rotate the first sun gear 35 at an increased speed. In this manner, the first carrier 31, the first planetary gear pair 33, and the first sun gear 35 together with the ring gear 25 form the first planetary gear train 30.

The second sun gear carrier 51 is a disc-shaped support plate formed integrally with the first sun gear 35 and is inscribed in the center of the first planetary gear pair 33 as shown in FIGS. 4 and 5. The first sun gear 35 to be engaged so as to be integrally formed on the top axis. In addition, the second sun gear carrier 51 has a plurality of fixing pins 34 at regular angular intervals with the same radius from the center on the opposite surface of the first sun gear 35, that is, like the first carrier 31. As it protrudes, the plurality of second planetary gear pairs 53 are rotatably supported as follows.

The second planetary gear pair 53 revolves and rotates about the second sun gear 55 to be described below, thereby increasing the rotational speed of the second sun gear carrier 51 again. As shown, since it is rotatably mounted on the bottom of the second sun gear carrier 51 through the fixing pin, at a constant angular interval on the same radius from the center at the bottom of the second sun gear carrier 51 preferably Like the first planetary gear pair 33, three are arranged in a pair in the circumferential direction. Accordingly, each of the planetary gears of the second planetary gear pair 53 is matched around the second sun gear 55, thereby revolving around the second sun gear 55 by the rotational force of the second sun gear carrier 51. At the same time, the second sun gear 55 can be rotated at an increased speed when rotating about the center. In this way, the second sun gear carrier 51, the second planetary gear pair 53, and the second sun gear 55 together with the ring gear 25 form a second planetary gear train 50.

The third sun gear carrier 71 is a disk-shaped support plate formed integrally with the second sun gear 55 like the second sun gear carrier 51. As shown in FIGS. 4 and 5, the second planetary carrier The second sun gear 55 meshed with the center of the gear pair 53 is integrally formed on the upper surface axis line, and the plurality of second sun gears 55 are integrally formed on the bottom surface of the second sun gear 55 at regular angle intervals with the same radius from the center. As the fixing pin 34 protrudes, the plurality of third planetary gear pairs 73 are rotatably supported as follows.

The third planetary gear pair 73 rotates about the third sun gear 75 to be described below and rotates at the same time to further increase the rotational speed of the output shaft 23 as shown in FIGS. 4 and 5. As can be seen, the bottom surface of the third sun gear carrier 71 is rotatably mounted via a fixing pin. Accordingly, the third planetary gear pair 73 is preferably spaced at the same radius from the center by the same radius at the bottom of the third sun gear carrier 71 like the first and second planetary gear pairs 33 and 53. Three are arranged in pairs in the circumferential direction. Accordingly, the respective planetary gears of the third planetary gear pair 73 are matched around the third sun gear 75, thereby being fixed while revolving around the third sun gear 75 by the rotational force of the third sun gear carrier 71. When rotating around the pin, the third sun gear 75 can be rotated at an increased speed at the same time.

The third sun gear 75 is a final portion that transmits the rotational force increased from the speed increase unit 7 to the power generation unit 9, as shown in FIGS. 4 and 5, of the first planetary gear pair 33. As it is engaged to be inscribed in the center, the output shaft 23 protrudes along the axis on the surface opposite to the third sun gear carrier 71, that is, at the center of the bottom surface. Accordingly, the third sun gear carrier 71, the third planetary gear pair 73, and the third sun gear 75 together with the ring gear 25 form a third planetary gear train 70.

Finally, the ring gear 25 is a ring gear commonly used for the first, second, and third planetary gear trains 30, 50, and 70 as mentioned above, and has three planetary gears directly connected up and down. Although the length is longer than the ring gear of the general planetary gear train so as to cover all the rows 30, 50, and 70, each of the first, second, and third planetary gear pairs 33,53,73 on the inner circumference. ) And other configurations are similar to general planetary gear trains.

On the other hand, the power generation unit 9 is a portion for producing electrical energy through the rotational driving force increased several times by the plurality of planetary gear train (30, 50, 70) in the speed increase unit (7), the speed increase unit (7) It is possible to use any form as long as it is directly connected to the output shaft 23 of the generator to produce electric energy according to the principle of the generator.

Now, the operation of the energy regeneration device 1 of the present invention configured as described above is as follows.

For example, the energy regeneration device 1 of the present invention is applied to the shock absorber 83 of the suspension 80 shown in FIG. 2 so that the kinetic energy transmitted in the form of rotational driving force can be converted into electrical energy and utilized. First, the driving shock or vibration applied to the suspension 80 is partially dissipated and removed by the shock absorber 83 and the suspension spring 91, and the remaining energy causes the plunger rod 84 to reciprocate up and down in the direction of the arrow. Accordingly, the link link 85 swings around the point, and the drive link 87 rotates in a crank form while the drive link 86 is locked up and down by the link link 85.

In this way, the rotational driving force transmitted to the energy regeneration device 1 is input to the energy regeneration device 1 through the input unit 3 member, such as the rotary bush 11, as shown in FIG. The one-way transmission part 5 is rotated from the bush hub 17 to the external gear 19 through the one-way clutch 13 by the bush hub 17 coupled to the tip. Transmit driving force. At this time, the one-way clutch 13 is a soup that causes wedge action between the inner ring of the one-way clutch 13 attached to the outer peripheral surface of the bush hub 17 and the outer ring of the one-way clutch 13 attached to the inner peripheral surface of the outer gear 19. Synchronous rotation by the lag (not shown) allows the rotational driving force of the bush hub 17 to be transmitted to the external gear 19. However, when the external gear 19 turns earlier or rotates faster than the bush hub 17, the wedge action of the sprag does not occur, so that only the outer ring of the one-way clutch 13 turns out, and thus The rotational driving force of the external gear 19 is not transmitted to the bush hub 17. As a result, the one-way clutch 13 causes the driving force transmission to occur only in one direction, that is, from the bush hub 17 toward the outer gear 19, depending on whether or not the inner sprag is wedge action.

In this way, the rotational drive force transmitted to the outer gear 19 of the one-way transmission part 5 is transmitted through the electric gear 15 and the driven gear 18 consisting of the electric gear 15 meshed with the outer gear 19 or a plurality of gears. Or it is transmitted to the speed increasing unit 7 through other transmission means such as a transmission belt.

When the rotational driving force is transmitted from the one-way transmission part 5 via the input shaft 21 coupled to the driven gear 18, the speed increasing part 7 is the first, second, and first, as shown in FIG. 3 planetary gear trains (30, 50, 70) in order to increase the driving force at the same time while transmitting the drive force, first carrier 31 of the first planetary gear train 30 is integrally connected to the input shaft 21 is the input shaft ( 21) and synchronous rotation. As described above, when the first carrier 31 rotates, the respective planetary gears of the first planetary gear pair 33 which are rotatably positioned in the first carrier 31 are moved along the first carrier 31. At the same time as it revolves around the first sun gear 35 between the sun gear 35 and the ring gear 25, it rotates about the fixing pin 34. Therefore, the rotational speed of the input shaft 21 turning the first carrier 31 is equal to the number of teeth of the first carrier 31 relative to the number of teeth of the first sun gear 35 (the number of teeth of the first sun gear 35 and the number of ring gears 25). Is increased by the gear transmission ratio indicated by the ratio of

As such, the rotation driving force accelerated by the first planetary gear train 30 rotates the second sun gear carrier 51 integrated with the first sun gear 35 at an increased speed, and thus the second planetary gear. The column 50 operates to increase the rotational driving force again. That is, the rotational driving force of the second sun gear carrier 51 is similar to the first planetary gear pair 33, so that the second planetary gear pair 53 is formed between the second sun gear 55 and the ring gear 25. 55) Rotate and rotate around. Accordingly, the second sun gear 55 rotated by the second planetary gear pair 53 has the number of teeth of the second sun gear 55 and the number of teeth of the second sun gear carrier 51 (the number of teeth of the second sun gear 55 and the ring gear ( 25) The speed is increased again by the gear transmission ratio according to the sum of the number of teeth).

Similarly, the third planetary gear train 70 rotated by the third sun gear carrier 71 formed integrally with the second sun gear 55 also has the third sun gear 75 teeth and the third according to the same mechanism. The gear is increased once again by the gear shift ratio represented by the ratio of the number of teeth of the sun gear carrier 71 (the sum of the number of teeth of the third sun gear 75 and the number of ring gears 25 teeth).

In this way, the rotary driving force increased in the last three times is output to the power generation unit 9 through the output shaft 23 to produce electrical energy, and the produced electrical energy is stored and used in a battery or the like.

At this time, of course, increasing the number of planetary gear trains coupled in series can provide a higher speed ratio, and decreasing the number decreases the speed ratio, so that the speed ratio can be changed by adjusting the number of planetary gear trains according to a designer's choice.

1: energy regeneration device 3: input unit
5: one-way transmission part 7: speed increasing part
9: power generation unit 11: rotating bush
13: one-way clutch 15: electric gear
17: bush hub 21: input shaft
23: output shaft 25: ring gear
27: internal gear 30: first planetary gear train
31: first carrier 33: first planetary gear pair
35: first sun gear 50: second planetary gear train
51: second sun gear carrier 53: second planetary gear pair
55: second sun gear 70: third planetary gear train
71: third sun gear carrier 73: third planetary gear pair
75: third sun gear 83: shock absorber
87: drive disk

Claims (3)

An input unit through which rotational driving force is transmitted from a driving source;
A one-way transmission unit configured to transmit the rotational driving force transmitted from the input unit only in one forward rotation direction by a one-way clutch mounted coaxially to the input unit;
A speed increasing unit configured to increase the rotation speed by the rotation driving force transmitted from the one-way transmission unit; And
And a power generation unit coupled to the output shaft of the speed increasing unit to generate electricity with the rotational driving speed increased in the speed increasing unit. The method according to claim 1,
And said speed increasing unit is configured by arranging one or more planetary gear trains in series. 3. The method according to claim 1 or 2,
The speed-
A first carrier on which the input shaft protrudes on one side axis;
A first planetary gear pair rotatably mounted at regular angular intervals on the same radius from a center of the surface opposite the input shaft of the first carrier;
A second sun gear carrier integrally formed on one side axis of the first sun gear meshed with the center of the first planetary gear pair;
A second planetary gear pair rotatably mounted at a predetermined angle on the same radius from the center of the second sun gear carrier;
A third sun gear carrier integrally formed on one side axis with a second sun gear meshed with the center of the second planetary gear pair;
A third planetary gear pair rotatably mounted at a predetermined angle on the same radius from the center of the second sun gear carrier;
A third sun gear meshed with and mounted to the center of the third planetary gear pair, the output shaft protruding on a surface axis opposite to the second sun gear carrier; And
And a ring gear in which the first, second, and third planetary gear pairs are externally externally engaged with each other.
KR1020110124435A 2011-11-25 2011-11-25 Energy recycling apparatus KR20130058433A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101448783B1 (en) * 2013-07-25 2014-10-13 현대자동차 주식회사 Energy regeneration device of suspension system for vehicle
CN107061607A (en) * 2017-03-29 2017-08-18 西北农林科技大学 A kind of automobile vibrational energy recycles damper
WO2020057322A1 (en) * 2018-09-21 2020-03-26 张朝刚 Electromagnetic shock absorber employing enhanced electric motor using planetary gear
WO2020198127A1 (en) * 2019-03-25 2020-10-01 Transcend Energy Ev, Llc Energy conversion devices and related systems
US11967884B2 (en) 2021-06-08 2024-04-23 Gig Energy LLC Energy conversion device, associated systems and methods

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101448783B1 (en) * 2013-07-25 2014-10-13 현대자동차 주식회사 Energy regeneration device of suspension system for vehicle
CN107061607A (en) * 2017-03-29 2017-08-18 西北农林科技大学 A kind of automobile vibrational energy recycles damper
WO2020057322A1 (en) * 2018-09-21 2020-03-26 张朝刚 Electromagnetic shock absorber employing enhanced electric motor using planetary gear
WO2020198127A1 (en) * 2019-03-25 2020-10-01 Transcend Energy Ev, Llc Energy conversion devices and related systems
CN113661647A (en) * 2019-03-25 2021-11-16 吉格能源有限责任公司 Energy conversion device and related system
US11967884B2 (en) 2021-06-08 2024-04-23 Gig Energy LLC Energy conversion device, associated systems and methods

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