JP5020402B1 - Kinetic energy capture device - Google Patents

Abstract

[PROBLEMS] Generally known are automatic doors that automatically open and close using electric power, and door closers that automatically close using the energy stored when the door is opened manually and when the door is opened. When opening the door, it is necessary to store the energy for closing and the energy for resistance to close the door at an appropriate speed at the same time. Is not friendly to the environment or users.
A piston provided with a piston 223 having one rack 227 built in the mat 33 and a rack 229 installed on the other side by stepping over the mat 33 which is means for taking in kinetic energy without using electric power. By connecting 207 with gears 230 and 231, kinetic energy for work is obtained and the door is opened and closed.
[Selection] FIG. 30

Description

  The present invention relates to a door including a sliding door and a revolving door, and more particularly to a kinetic energy capturing device that operates an environmentally friendly door that automatically opens and closes by button operation without requiring electric power.

  Conventionally, automatic doors that are widely used require electric power, and there are door closers that automatically close manually opened doors, and a combination of a spring and a hydraulic damper is widely known. As for sliding doors, a combination of a spring and an air damper or a spring and a centrifugal brake is also known. Such a known closer is manually operated when the door is opened, and the door is opened against the resistance in the case of a damper type while compressing the spring, and the opened door is opened by the spring force of the spring. The door is gently closed against the resistance of the centrifugal brake. In addition, a door that opens by pressurizing a built-in airbag by traversing the mat and sending it to a cylinder device via a connecting pipe has been devised.

Japanese Patent Laid-Open No. 11-50736 JP-A-5-118180 Japanese Patent Laid-Open No. 11-159237 JP 2000-291326 A JP 2004-285792 A Japanese Patent No. 3906410 Japanese Patent Laid-Open No. 11-50736 Japanese Patent No. 2004-285792 JP-A-7-139594 JP-A-6-136780 Japanese Patent Laid-Open No. 58-054178 JP 2007-039997 A Japanese Patent No. 4567717 Japanese Patent No. 4687760

In realizing the above-mentioned known prior art document 14, the problems of increasing the size of the kinetic energy transmission member by design, lowering the transmission speed due to it, and not storing it in the mounting space due to the increase in the size of the device itself have been found.

In order to solve the above-mentioned problem, the common rack 228 used separately from the input rack 253 and the output rack 229 in order to increase the degree of freedom of the output position is omitted, the number of parts is reduced, and the input rack 253 and the output rack 229 are brought close to each other. Provided is a kinetic energy device that performs work by connecting the gears 251 and 231. Moreover, if this is applied to optimize the size of the gear, it is possible to connect with only the common gear 251 or to adjust the position and speed of the output with a plurality of gears, and to provide an automatic door similar to the conventional one. .

In order to use the kinetic energy generated by stepping through the mat, an input rack 253 for inputting the energy provided in the mat 33 into the apparatus and an output rack 229 for outputting the energy provided in the door 32 to the outside of the apparatus for work. Are connected to each other through a common gear 251, which provides a device that outputs kinetic energy for traversing a mat to the outside of the device and works, and is effective for all products that want to use kinetic energy.

That is, the present invention moves the output rack 229 from the input rack 253 provided in the mat 33 through the take-in gear 251 with the kinetic energy generated by the traffic of people. In the invention described in claim 1 of the present application, the following means may be further provided to reduce the thickness of the mat. The input gear 251a and the input rack 253, and the output gear 251b and the output rack 229 of the two-stage gear 251 having the integrated input gear 251a and output gear 251b in which the ratio of b to the gear diameter a is set to 1 or more are engaged. Provided is a device that captures kinetic energy that is set using a gear 231 and that is amplified by the ratio of diameter 251b / diameter 251a of the amount of movement of the input rack 253 when the mat 33 is stepped on.

The invention according to claim 1 of the present application can be transmitted only by a mechanism.

That is, the output rack 229 is moved using the gears 251 and 231 by simply moving the input rack 253 for energy transmission.

The invention according to claim 1 of the present application is an input gear of a two-stage gear 251 having an integrated input gear 251a and output gear 251b in which the ratio of the gear b to the gear diameter a is set to 1 or more for the purpose of thinning the mat. 251a and rack 227, output gear 251b and gear 231 and output rack 229 are set to mesh with each other, and the amount of movement of output rack 229 is amplified by the ratio of diameter 251b / diameter 251a of the amount of movement of input rack 253 by stepping on mat 33. A device for capturing kinetic energy is provided.

Further, the invention according to claim 2 of the present application has two sets of one-way clutches 213 and 214, and a gear 211 that are provided so as to rotate integrally only in opposite directions in order to efficiently incorporate kinetic energy with respect to claim 1. 212, an output piston 207 having racks 215, 216, a device for capturing kinetic energy from both directions of piston reciprocation.

Further, the invention of claim 3, wherein the have connected to that gear 211 or 212 meshes with the rack 215 or 216 is a shaft 208 which is connected to the output piston 205 to claim 2, the reciprocating motion is converted to rotary motion The motor 250 connected to the shaft 208 provides a kinetic energy capturing device characterized in that its rotational motion can be converted into electric power and used. The greater the inertia, the more effective it is because it only turns in one direction.

Further, the invention according to claim 4 of the present application has a gear that rotates integrally with a pulley meshing with a belt-like power transmission material in order to increase the degree of freedom of the output installation position without increasing the size of the invention. A device for capturing the characteristic kinetic energy is provided.
When a conventional rack is used, a separate space is required at a position where it meshes with the gears, and a guide is necessary for further smooth movement, which is not necessary for a belt-shaped power transmission member.
That is, by the movement of the input rack 253, the output rack 229 moves through the gear 251a, the integrated pulley 251b, the belt 256, the pulley 251b, the integrated pulley 254, the belt 257, the pulley 255, and the integrated gear 231. .
The invention according to claim 5 of the present application is an input gear of a two-stage gear 251 having an integrated input gear 251a and an output pulley 251b in which the ratio of the pulley b to the gear diameter a is set to 1 or more in order to reduce the mat thickness. 251a and rack 227, and output pulley 251b and belt 256 are set to mesh with each other, and the kinetic energy is amplified by the ratio of the diameter 251b / diameter 251a of the movement amount of the input rack 253 by stepping over the mat 33. Provide a device for
Also, by applying this, the two-stage pulley 254 connected to the two types of belts 256 and 257 is similarly amplified at the ratio of the output pulley diameter 254 / input pulley diameter 251b.
Although a belt is used as an example of the belt-shaped power transmission material, the same effect can be achieved with a chain.
From the above description, the mat device as an energy capturing means efficiently captures kinetic energy without requiring electric power.

The principal part front view of one Example at the time of the sliding door opening direction movement which removed the case of this invention AA arrow view of FIG. The principal part front view of one Example at the time of the sliding door closing direction movement which removed the gear which is not used with the case of the present invention The front view of the main part of one embodiment of the present invention when moving in the sliding door closing direction with the gears not used with the case of the present invention removed and the gears 23 made transparent AA arrow view of FIG. The principal part front view of one Example at the time of movement of the revolving door opening direction which removed the case of this invention The front view of the main part of one embodiment of the present invention when moving in the direction of opening the revolving door, using a weight instead of a spring for the driving force of the present invention and removing the case Schematic diagram of one embodiment of a sliding door equipped with the mechanism of the present invention BB button cross section and rod schematic diagram in the unconstrained state of the gear 3 when the door is automatically opened by pressing the button and automatically closed after being fully opened. 9 is a cross-sectional view of the button and the rod in a state where the gear 3 is switched from non-restraint to restraint when the door opening button 31 is pressed. FIG. 9 is a cross-sectional view of the button and the rod in a restrained state of the gear 3 when the door is opened In FIG. 9, when the stopper taper portion 17b collides, the button cross section and the rod schematic diagram in a state where the gear 3 is switched from restraint to non-restraint. The button cross section and the rod in the unconstrained state of the gear 3 when the door that automatically opens to the fully open state by pressing the open button 31a and automatically closes to the fully closed state by pressing the close button 31b is closed. Overview 13 is a cross-sectional view of the button and the rod in a state where the gear 3 is switched from non-restraint to restraint when the door opening button 31 is pressed. FIG. 13 is a cross-sectional view of the button and the rod in a restrained state of the gear 3 when the door is opened FIG. 13 is a cross-sectional view of the button and the rod in a state where the gear 3 is switched from restraint to non-restraint when the door closing button 31b is pressed. The front view which shows the structure of the spiral gear apparatus of one Example of this invention. The front view which shows the structure of one Example provided with the rack in FIG. CC sectional view of FIG. External view of FIG. FIG. 17 is a characteristic diagram showing the operation of the embodiment shown in FIG. FIG. 18 is a characteristic diagram showing the operation of the embodiment shown in FIG. 19 is an enlarged view of part D of FIG. 19 using a bush. EE arrow cross-sectional view of FIG. Example of enlarged view of part D in FIG. 19 using a self-aligning ball bearing FF arrow view of Fig. 2 in the closed state FF arrow view of Fig. 2 with the door open GG arrow sectional view of FIG. HH cross section and schematic diagram of FIG. Schematic diagram of an example of a sliding door using only a fluid mat device FIG. 30 is an enlarged view of part I. JJ cross section of FIG. Part I enlarged view of FIG. 30 using a rack type mat device. JJ sectional view of Fig. 8 using rack type mat device FIG. 30 is an enlarged view of a portion K of the embodiment. LL sectional view of FIG. MM cross section of FIG. FIG. 30 is an enlarged view of a portion K of the embodiment. NN cross section of FIG. FIG. 30 is an enlarged view of part I. FIG. 30 is an enlarged view of part I. Sectional drawing which shows the structure of one Example provided with the two-step gear in FIG. FIG. 34 is a cross-sectional view showing a configuration of one embodiment provided with a two-stage gear. JJ sectional view of FIG. 8 using only the gear type mat device of the present invention 44 is a cross-sectional view showing a configuration of one embodiment provided with a two-stage gear. JJ sectional view of FIG. 8 using the gear + belt type mat device of the present invention Enlarged view of part I in Fig. 30 using a gear + belt type mat device JJ sectional view of FIG. 8 using a mat device in which two gears + belt type mechanisms of the present invention are connected.

Hereinafter, embodiments of the present invention will be described with reference to FIGS.
In FIG. 1, it is shown that a driving force with a small change due to the degree of winding is transmitted to the helical gear 3 by rotating the spiral gear 2 that is the adjusting means by the spiral spring 1 that is the driving means.

The spiral gear 2 shown here is input from the spiral gear 103 on the side surface via a bevel gear 102 which can restrain the rotational direction by the splines 115 and 116 and can move freely in the axial direction. The output is made to the helical gear 21 of the outer diameter surface via the one-way clutch 20.

FIG. 1 shows an outline of a door that automatically opens and automatically closes after being fully opened, and when operated, the rod 12 having the cam 5 is lifted by pressing a button 31 connected to a built-in switch 4 serving as switching means. The leaf spring 15 and the groove 12a are engaged and restrained. Next, the cams 6 and 7 connected to the rod are also lifted and restrained. Accordingly, the helical gear 3 having the holder 19 is restrained so as to engage with the gear 13 by fitting the cam 7.
As a result, the gear serving as the transmission means is switched from the gear 23 composed of an odd number to the gears 13 and 14 composed of an odd number, and the direction of the driving force transmitted to the rack is changed. As a material selection, the button 31 is preferably made of rubber or polyurethane which is a low-hardness elastic body, and the built-in switch 4 is preferably made of polypropylene or polyamide which is a high-hardness elastic body.

As a result, the driving force is transmitted to the rack 16 through the gears 13 and 14 serving as transmission means via the helical gear 3, and the sliding door 32 having the main body case 30 is moved in the door opening direction.

When the sliding door 32 moving in the opening direction collides with the stopper 17, the cam 6 is pushed down by the taper 17 b and is engaged and restrained by the leaf spring 15 and the groove 12 b. As a result, the cam 7 and the holder 19 are disengaged, and the constraint on the helical gear 3 is released.

FIG. 2 is a view taken in the direction of arrows A-A. The driving force is detachable, and the spiral gear 2 and the spiral spring 1 are rotated by rotating a rotary lever 22 having a shaft directly connected to the spiral gear 2. Let it accumulate. The direction of rotation of the spiral gear 2 is opposite to that during driving, and the one-way clutch 20 is set not to be engaged during the accumulation, so that the sliding door 32 does not move and accumulates, and the spiral spring 1 Reverse rotation is prevented even when there is no accumulation of driving force.

In FIG. 3, the helical gear 3 whose restraint has been released shows that it receives a thrust force and meshes with the gear 23. FIG. 4 shows a transparent gear 23 therein.

As a result, the driving force is transmitted through the helical gear 3 through the gear 23 serving as a transmission means, and is inverted when it is changed from an even number to an odd number and output to the rack 16 to complete the closing of the sliding door 32 having the case body 30. Move in the direction of closing the door. FIG. 5 is an AA arrow view.

Further, the gear 13 has two types of input gear 13a and output gear 13b having different diameters, and the gear 23 is also a two-stage gear having 23a and 23b. Since meshing with the helical gear 3, the diameters 13a and 23a are the same, and the diameter of 23b is larger than 13b.

Further, by setting the ratio of b to the gear diameter a to 1 or more, the sliding door can be displaced more than the displacement of the spiral spring.

In FIG. 6, the principal part at the time of door opening direction movement in a revolving door is shown. The driving force is the same as that shown in FIG. 1 up to the gear 14 as means, and is transmitted to the worm wheel 24 instead of the rack 16 and is transmitted to the rotating worm 25 and rotated by the reaction force.

In FIG. 7, the principal part at the time of moving in the sliding door opening direction which uses the weight 29 instead of the spring for driving force is shown. The load of the weight 29 is guided to the guide rollers 27 and 28, and the driving rope 26 wound around the holder 19 rotates the helical gear 3.

In FIG. 8, the outline of the door frame provided with the sliding door provided with the mechanism of this invention and the rack is shown. By pressing the button 31, it opens and closes as the user intends.

9-12, the button cross section of the door which opens automatically by pressing the button and automatically closes after fully opening is shown. A door that automatically opens when the button 31 is pressed and the cam 6 collides with the stopper taper portion 17b when the door is fully opened corresponds to the BB portion in FIG.

13-16, the button cross section of the door which opens automatically to a fully opened state by pressing a door open button and automatically closes to a fully closed state by pressing a door close button is shown. In FIG. 1, this system has two types of internal buttons 31a and 31b of the switch 4 and is different in that the tapered portion 17b of the stopper 17 is not provided. A door that automatically opens when the door opening button 31a is pressed, and that does not have the stopper taper portion 17b, maintains the door in a fully open state, and automatically closes when the door closing button 31b is pressed. Corresponds to part B.

In FIG. 17, the input shaft shaft 104 rotated by the spiral spring 110 serving as the driving means is automatically aligned with the spiral gear 103 serving as the adjusting means via the bevel gear 102 and meshed with an appropriate angle, and is transmitted to the output shaft 117. To output torque.

18 shows that the rack 109 is meshed with the gear 108 in FIG. 17, and torque is converted into a load and output. Thereby, the load change by the displacement of a spring can be adjusted with a load. 19 shows a cross-sectional view of FIG. 17, which is a common part, and FIG. 20 shows an external view of FIG. 21 shows the relationship between displacement and torque in the embodiment of FIG. 17, and FIG. 22 shows the relationship between displacement and load in the embodiment of FIG. In FIG. 21, a specific example shows that MAX torque = 2 × MIN torque in the conventional apparatus is MAX torque = 1.2 × MIN torque in the present invention example, and the rate of change is 1/10.

The bevel gear 102 and the spiral gear 103 will be described using specific examples. Based on a bevel gear using face gears, immediate teeth, helical teeth, or curved teeth, the minimum radius r0 is set to increase from the starting point (θ = 0) to the radius r by a pitch p every round. Therefore, the radius at the arbitrary angle θ: r = r0 + θ × p / (2π), and the circumference: Σr × Δθ, the circumference of the present gear: l = r0 + θ ^ 2 × p / (4π). For example, when r0 = 14.5 mm, p = 13 mm, total rotation angle θt = 2.5 laps (5π), module: m = 1, total rotation distance: lt = 483 mm, total number of teeth: nt = 483 teeth . Table 1 shows an example of a specification table for the Bleeson beveled bevel gear.


A specific structure will be described below.

For the tooth profile (module), the reference pitch circle diameter at the starting point which is the minimum gear diameter: d02 = 2 × r02 is used. The bevel gear is considered to be a virtual equivalent spur gear in design, and an equivalent pitch circle radius: r02f = r02 / cosΦ (Φ: apex angle of pitch cone × 1/2) is used. Here, the spur gears mesh with each other if the tooth profile is the same and the distance between the axes and the angle between the axes (normally right angle) are appropriate. Therefore, even if the radius changes in a spiral shape, it can mesh. However, it is necessary to align the shaft 104 and rotate integrally with the shaft 104 in order to cope with the angle change (inclination) between the shafts due to the radius change. For alignment, it is desirable to provide self-aligning bearings (self-aligning roller bearings, self-aligning ball bearings 129, self-aligning bushes 120 to 123). In FIG. 23, the bushes 120 to 123 described here are obtained by making a conventional cylindrical bush into a spherical shape and dividing it into four parts for the purpose of downsizing and material reduction. The basic structure is such that a spherical portion 132 is provided on the shaft 104 and a spherical recess is provided on the inner surface of the main body so as to come into contact with the bush so that it can freely rotate on the spherical surface with relatively low resistance. To describe the detailed structure, a pinion provided with a spherical recess on the inner surface, which is the main body, is divided by an axis perpendicular passing through the center of the sphere. A copper alloy, which is a bush material, is sprayed on the inner surface, and a sintered or spherical bush is divided into four parts and press-fitted into the pinion as usual. In FIG. 24, the bevel gear 102 is fitted into the spline 124 of the shaft 104 at the time of assembling the gear and is fitted into a cover having a bush divided into four spheres 132, and bolts 127 and 128 are passed through the through holes that have been previously opened. Fix to the gear 102. The cover side spline should be sufficiently larger than the shaft side so that it can be moved during use. FIG. 25 shows an embodiment using an existing self-aligning ball bearing.

In FIG. 32, when the seat 218 provided on the mat 33 installed at a place where traffic is expected, the input piston 223 that divides the input cylinder 220 up and down falls, the internal pressure rises, and the fluid 225 Moves the output piston 207 that divides the output cylinder 205 of FIG. 29 into the right and left via the hydraulic hose 34 to the right. The fluid 225 is preferably hydraulic fluid. After stepping over, the hydraulic oil 225 is returned to the input cylinder 220 by the springs 204 and 221, the input piston 223 is raised, and the output piston 207 is moved to the left and returned to a predetermined position. At this time, energy is extracted by the reciprocating motion of the output piston 207. At this time, it is desirable that the material of the O-ring or U packing for sealing the hydraulic oil is NBR, and the steel ball having reduced frictional resistance is SUJ.

In FIG. 26, when the door is closed, the claw 210 is disengaged from the claw wheel 209 and can be rotated, and the gear 202 is engaged with the gear 201. At this time, when the mat 33 is stepped over, the output cylinder 205 connected to the input cylinder 220 reciprocates, and the shaft 208 rotates clockwise to extract kinetic energy, which is transmitted to the gear 201 via the gear 202 and can be used as drive means. FIG. 28 is a cross-sectional view taken along the line G-G in FIG. 2, and in order to efficiently store kinetic energy, when the output piston 207 moves to the right, the one-way clutch 213 operates to integrate with the shaft 208 clockwise. The rack 215 rotates the rotating gear 211 clockwise. When the output piston 207 moves to the left, the one-way clutch 214 is operated and the rack 216 rotates the gear 212 that rotates integrally with the shaft 208 in the clockwise direction.
In FIG. 27, when the door is opened, the claw 210 is engaged with the claw wheel 209 to lock the rotation, and the output cylinder 205 in the mat 33 is restricted.

In FIG. 30, when the output cylinder 205 is directly integrated with the door 32 and the mat 33 is installed in front of the door 32, a simple automatic door that automatically opens when the user stands in front of the door 32 and automatically closes when the user passes is shown. Show. FIG. 31 is an enlarged view of the output cylinder I.

In FIG. 34, by traversing the seat 218, the input piston 223 having the rack 227 is lowered and the common rack 228 that is also fitted through the gear 230 that is fitted with the input piston 223 is raised. In FIG. 33, this operation shows that the gear 231 engaged with the rack 228 at the other end rotates clockwise to move the output piston 207 including the rack 229 to the right.

FIGS. 35 and 38 show a state in which the operating oil 225 at the time of opening and closing moves via the in-flow path regulating valve 233. 36 and 37 are LL and MM sectional views of FIG. 35, and FIG. 39 is an NN sectional view of FIG.

In FIG. 35, when the door is opened, the hydraulic oil 225 moves from the left input piston 223 to the right output piston 207, and the sphere 234 flows to the right side, but is larger than the holes 240 to 243 and secures the flow path by the tapered portion of the hole 239. Although the flow rate is fast, the hydraulic oil 225 moves from the output piston 207 on the right side to the input piston 223 on the left side when the door is closed, the ball 234 flows to the left side, travels along the taper portion, and clogs the hole 239. It is adjusted and slowed down.

Similarly, in FIG. 38, the hydraulic oil 225 when the door is opened moves from the left input piston 223 to the right output piston 207, and the lid 244 is inclined to the right with the node 245 as an axis and the flow velocity is fast. The movement from the output piston 207 on the right side to the input piston 223 on the left side causes the lid 244 to incline to the left side and close the hole 246, so that the flow rate is adjusted by the holes 247 to 249 and slows.

In FIG. 40, the output piston 207 reciprocates and the shaft 208 can rotate the connected motor 250 clockwise to convert it into electric power.

Similarly, FIG. 41 shows that the output piston 207 reciprocates and the shaft 208 can rotate the connected motor 250 clockwise and counterclockwise to convert it into electric power.

FIG. 42 shows that the input piston 223 coupled to the rack 253 via the two-stage gear 251 is amplified by the ratio of the gear diameter 251b / diameter 251a and moved to the right by traversing the seat 218.

Similarly, in FIG. 43, it is shown that the input piston 228 connected to the rack 227 provided in the input piston 223 via the two-stage gear 251 is amplified to a gear diameter 251b / diameter 251a ratio by lifting the seat 218. .

Next, an embodiment of a gear type kinetic energy capturing device will be described.
44, the input rack 253 is lowered by stepping over the seat 218 and the gear 231 is rotated clockwise via the gear 251 engaged with the input rack 253, so that the output rack 229 moves to the right.

Next, an embodiment of a two-stage gear type kinetic energy capturing device will be described.
In FIG. 45, when the seat 218 is traversed, the input rack 253 is lowered and the gear 231 is engaged with the input rack 253, and the gear 231 is rotated clockwise via the integrated gear 251b, so that the output rack 229 moves to the right. Indicates to do.

Next, an embodiment of a belt type kinetic energy capturing device will be shown.
In FIG. 46, when the seat 218 is traversed, the input rack 253 is lowered, and the belt 256 is rotated counterclockwise via the gear 251a and the gear 251b integrated with the input rack 253. The belt 257 is rotated counterclockwise. In FIG. 47, this operation shows that the pulley 255 and the gear 231 that rotate integrally with the other end of the belt 257 rotate counterclockwise and the output piston 207 including the rack 229 moves to the left.

Similarly, in FIG. 46, the belt 256 is amplified to a ratio of pulley diameter 251b / gear diameter 251a through the input rack 227 and the two-stage gear 251 having the input gear 251a and the output pulley 251b by rotating through the seat 218 and rotating. Indicates to do.
Similarly, the two-stage pulley 254 connected to the two types of belts 256 and 257 is similarly amplified and rotated with the ratio of the output pulley diameter 254 / input pulley diameter 251b.

Applying this, FIG. 48 shows an embodiment of an installation having a plurality of input racks. It shows that the output pulley 254 rotates at the two input racks 253.

It can be applied to doors for welfare facilities, mainly for disabled people, elderly people, or children, doors that are infrequently used and may be forgotten to be closed, and household doors that do not want to use power but want to open and close automatically.

Reference Signs List 1 spiral spring device 2 spiral gear 3 helical gear 4 switch 5 cam 6 cam 7 cam 8 guide pin 9 guide pin 10 guide pin 11 guide pin 12 rod 13 gear 14 gear 23 gear 15 leaf spring 16 rack 17 stopper 18 Rubber 19 Holder 20 One-way clutch 21 Helical gear 22 Rotating lever 24 Worm wheel 25 Worm 26 Driving rope 27 Guide roller 28 Guide roller 29 Weight 30 Case body 31 Button 32 Door 33 Mat 34 Hydraulic hose 101 Spring case body 102 Cap Gear 103 Spiral gear 104 Shaft (input shaft)
105 Shaft 106 Gear case body 107 Bearing case 108 Teeth 109 Rack 110 Spiral spring 111 Spring hook 112 Bearing 113 Bearing 114 Bearing 115 Spline 116 Spline 117 Output shaft 118 Cover 119 Cover 120 Bush (bearing)
121 Bush (bearing)
122 Bush (bearing)
123 Bush (bearing)
124 Spline 125 Cover 126 Cover 127 Bolt 128 Bolt 129 Self-aligning ball bearing 130 E ring 131 E ring 132 Spherical body part 201 Gear wheel 202 Gear wheel 203 Pin 204 Spring 205 Cylinder 206 O-ring (U packing)
207 Piston 208 Shaft 209 Claw wheel 210 Claw 211 Gear 212 Gear 213 One-way clutch 214 One-way clutch 215 Rack 216 Rack 217 Bearing 218 Seat 219 O-ring (U packing)
220 Cylinder 221 Spring 222 Flow path (oil path)
223 Input piston 224 Steel ball 225 Fluid (hydraulic oil)
226 Bush 227 Rack 228 Rack 229 Rack 230 Gear 231 Gear 232 Person 233 Adjusting valve 234 Ball 235 Hole 236 Hole 237 Hole 238 Hole 239 Hole 240 Hole 241 Hole 242 Hole 243 Hole 244 Lid 245 Node 246 Hole 247 Hole 248 Hole 249 Hole 250 Motor 251 Gear 252 Rack 253 Rack 254 Pulley
255 pulley
256 belt
257 belt

Claims (3)

A kinetic energy capturing device for utilizing kinetic energy generated by traversing a mat,
It has two rack parts consisting of one and the other,
Only one input rack part to be traversed to make the mat compact is built into the mat,
The straight line connecting the rack teeth of the input rack is installed parallel to the sliding direction.
The input rack part is interlocked with the mat stepping part, and the sliding direction of the mat stepping part is installed in the direction of gravity load.
The other output rack part is installed outside the mat, the straight line connecting the rack teeth of the output rack part is installed parallel to the sliding direction, and the input rack part and the output rack part are connected via a common two-stage gear. A kinetic energy capturing device that takes in the energy of sliding movement of the input rack and outputs it as the energy of sliding movement of the output rack. In order to efficiently convert the reciprocating motion of the output rack section having two racks composed of one and the other into rotary motion and take in kinetic energy, the straight lines connecting the rack teeth of the two racks are parallel to the sliding direction. Installed in
Two independent gears meshing with two racks,
The two gears rotate on the same shaft,
There is a one-way clutch that operates in the opposite direction between the two gears and the shaft, one one-way clutch is activated during the forward path, and the other one-way clutch is activated during the return path.
The kinetic energy capturing device according to claim 1, wherein the shaft is rotated in the same direction. The kinetic energy capturing device according to claim 2, wherein the shaft is connected to a motor that generates electric power by rotation.