WO2018230799A1

WO2018230799A1 - Caterpillar vehicle capable of changing direction

Info

Publication number: WO2018230799A1
Application number: PCT/KR2018/000710
Authority: WO
Inventors: 이충철
Original assignee: 이충철
Priority date: 2017-06-16
Filing date: 2018-01-16
Publication date: 2018-12-20
Also published as: KR101954729B1; KR20180137233A

Abstract

The present invention relates to a caterpillar vehicle capable of very quickly and effectively changing the direction thereof since when the driving power transmission toward any one side thereof is blocked, the driving speed of the other side thereof is increased by means of a planetary gear of a driving force transmission device.

Description

Endless tracked vehicles

The present invention relates to a caterpillar vehicle, and more particularly, to a caterpillar vehicle capable of changing the direction so that the direction can be changed intuitively by individually controlling the driving force transmitted to the caterpillar.

Applicant has registered Korean Patent No. 10-1034354 "Infinite Track Vehicle" (registered on May 3, 2011), and Korean Registered Patent No. 10-1105783 "Manual Infinite Track Vehicle capable of directional manipulation" (January 6, 2012) Day registration), Korean Patent No. 10-1375635 "manual tracked vehicle capable of directional control" (registered on March 12, 2014) has been proposed.

The present invention is proposed to improve the conventional technique proposed by the applicant.

Korean Patent No. 10-1034354 is manufactured in the form of a dumbbell is provided with a driving sprocket and a driven sprocket is generated buoyancy, and also buoyancy is generated is equipped with an endless track divided into a plurality of track shoes structurally in the water The present invention relates to a tracked vehicle having high stability and excellent durability.

Korean Patent No. 10-1105783 and Korean Patent No. 10-1375638 are related to the endless track vehicle that can be intuitively manipulated by the same gripping structure as the bicycle, more specifically by driving both endless tracks separately It relates to a driving force transmission structure that makes it possible to manipulate the direction.

The prior art controlled both endless tracks individually by transmitting or blocking a driving force using a clutch member, thereby enabling a change of direction. In addition, a brake member was separately provided to brake the rotation of the endless track by inertia after the transmission of the driving force.

However, in this form, a brake member for braking an endless track together with a clutch member for transmitting and blocking driving force must be separately provided, and a structure for operating them simultaneously must be provided so that the structure is complicated and difficult to manufacture. there is a problem.

On the other hand, in the water, due to the lack of friction, the turn does not change as quickly as on the ground. Therefore, in order to smoothly change the direction, the endless orbit opposite to the direction to be converted should be rotated faster than when driving in a straight line.

In the conventional crawler vehicle, even if one of the driving force blocks the transmission of the driving force by the clutch member, the crawler on the other side rotates at a constant speed. When operating the clutch member to block the transmission of the driving force of one side, the driving load is reduced by half, and the other side has the ability to increase the driving speed.

However, there is a problem that the drive speed must be adjusted separately by the occupant, despite the driving power. That is, the conventional tracked vehicle as described above does not utilize the driving force effectively when the direction change, so the direction change is also not made quickly.

The present invention has been made to solve the above problems of the prior art, and has a new power transmission structure to replace the conventional power transmission structure for controlling the driving force transmission and braking the track using the clutch member and the brake member. In this paper, we will propose an endless tracked vehicle that can be turned around.

In particular, the structural complexity of the method using the clutch member and the brake member is greatly reduced, and the drive force transmission can be controlled by simply operating the brake member without using the clutch member so that the direction can be changed more intuitively than before. I would like to.

In addition, the driving force due to the reduction of the driving load during the change of direction can be used for the change of direction, so that the change of direction can be made quickly and effectively.

The present invention to solve the above problems, the main body is provided with a drive unit for generating a driving force; A pair of driving sprockets and a pair of driven sprockets respectively provided on both front and rear sides of the main body; A pair of endless tracks mounted between the drive sprocket and the driven sprocket to generate buoyancy; First and second drive shafts rotatably supported by the main body such that the other ends thereof face each other with one end connected to each driving sprocket; A sun gear connected to the other end of the first drive shaft, a ring gear connected to the other end of the second drive shaft and arranged concentrically on a radially outer side of the sun gear, between the sun gear and the ring gear A plurality of planetary gears meshed with and coupled to the planetary gears so that the plurality of planetary gears revolve and rotate on the same plane as the sun gear and the ring gear, but the drive force of the driving unit is transmitted to the planetary gears. A driving force transmission device including a carrier for revolving gears; A pair of brake devices for individually braking the first and second drive shafts; When the driving force is input through the carrier and the planetary gear is revolving around the sun gear while transmitting the driving force to both the sun gear and the ring gear, the sun by the pair of brake devices When one of the gears and the ring gear is braked, the planetary gear rotates about the sun gear and rotates at the same time to transmit driving force to only the other of the sun gear and the ring gear.

In the above, the carrier is in the form of a disk with a first through-hole is formed in the center, the driving force input unit for receiving the driving force from the drive unit on one side is provided; A second through-hole is formed in the center and is coupled to the other side of the carrier further comprises a housing for forming a gear chamber between the carrier; The sun gear is disposed in the center of the gear chamber with the first driving shaft penetrating the first through hole, and the ring gear is radially formed in the gear chamber with the second driving shaft penetrating the second through hole. A plurality of planetary gears rotatably fixed to the other side of the carrier to be engaged on the same plane as the sun gear and the planetary gear; This is preferred.

In the above, the seating portion and the grip handle is provided on the main body; The driving unit is a passive driving unit for generating a rotational driving force by a passenger seated in the seating unit; The brake device includes a pair of brake members provided on the first and second drive shafts, respectively, and a pair of brake levers provided on the grip handle to individually operate the brake members; This is preferred.

As described above, the caterpillar vehicle capable of changing the direction of the present invention has a very simple structure compared to the conventional caterpillar vehicle that transmits a driving force and switches the direction by using a clutch member and a brake member, and thus is easy to manufacture and maintain. Is simple.

In addition, since the driving force is blocked and the direction is changed using only the brake device without a separate clutch member, the operation is very easy and intuitive.

In particular, when the transmission of the driving force to one side is blocked, the driving speed of the other side is increased by the planetary gear of the driving force transmission device, and thus the direction change is made very quickly and effectively.

1 is a plan view of a crawler vehicle capable of changing the direction according to an embodiment of the present invention,

2 is an exploded perspective view of FIG. 1;

3 is a perspective view of the driving sprocket of FIG.

4 is a plan view of FIG.

5 is a cross-sectional view taken along line A-A of FIG. 4;

6 is a cross-sectional view of the split drive sprocket,

7 is a modified form of FIG. 5,

8 is a perspective view of the driven sprocket of FIG.

9 is a perspective view of the track shoe of FIG.

FIG. 10 is a perspective view of FIG. 9 viewed from below;

11 is an exploded perspective view of FIG. 9;

12 is an exploded perspective view of FIG. 10;

FIG. 13 is a plan view of FIG. 9;

14 is a sectional view taken along line B-B in FIG. 13;

15 is an exploded cross-sectional view of FIG. 14;

16 is a perspective view of the caterpillar of FIG.

17 is a sectional view of the caterpillar of FIG. 16;

18 is a side conceptual view for showing a coupling state between the endless track and the sprocket,

19 is a plane conceptual view for showing a coupling state between the endless track and the sprocket,

20 is a cross-sectional view showing a coupling state of the lower track of the caterpillar according to another embodiment;

21 is a conceptual diagram illustrating a power transmission and direction change structure of FIG. 1;

22 is a cross-sectional view showing the interior of the driving force transmission device of FIG.

23 is an exploded cross-sectional view of the driving force transmission device of FIG. 22;

24 is an exploded perspective view of the driving force transmission device of FIG. 21;

25 is a conceptual cross-sectional view in the C-C direction of the driving force transmission device of FIG. 22;

26 is a view showing an operating state of the driving force transmission device of FIG.

DETAILED DESCRIPTION Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art may easily implement the present invention. As those skilled in the art would realize, the described embodiments may be modified in various different ways, all without departing from the spirit or scope of the present invention. In the drawings, parts irrelevant to the description are omitted for simplicity of explanation, and like reference numerals designate like parts throughout the specification. When any part of the specification is to "include" any component, this means that it may further include other components, except to exclude other components unless otherwise stated.

1 is a plan view of a crawler vehicle capable of changing the direction according to an embodiment of the present invention, Figure 2 is an exploded perspective view of Figure 1, Figure 3 is a perspective view of the driving sprocket of Figure 2, Figure 4 is a 5 is a cross-sectional view taken along line AA of FIG. 4, FIG. 6 is a cross-sectional view of the split drive sprocket, FIG. 7 is a modified form of FIG. 5, FIG. 8 is a perspective view of the driven sprocket of FIG. 2, and FIG. 9 is 1 is a perspective view of the track shoe of FIG. 1, FIG. 10 is a perspective view of FIG. 9 viewed from below, FIG. 11 is an exploded perspective view of FIG. 9, FIG. 12 is an exploded perspective view of FIG. 10, FIG. 13 is a plan view of FIG. 9, FIG. 14 is a sectional view taken along line BB of FIG. 13, FIG. 15 is an exploded sectional view of FIG. 14, FIG. 16 is a perspective view of the caterpillar of FIG. 1, FIG. 17 is a sectional view of the caterpillar of FIG. 16, and FIG. 18 is a caterpillar. Is a side conceptual view for showing a coupling state between the sprocket and FIG. 19. A plan schematic view for showing the coupling state between the sprockets.

According to one embodiment of the present invention, the caterpillar vehicle capable of changing directions may be rotatably provided in the main body 100 having the seating unit 110 and the driving unit 120 and the front and rear sides of the main body 100. Drive sprocket 200 and the driven sprocket 300, a plurality of buoyancy generating track shoes 500 are connected in a chain form includes an endless track 400 mounted between the drive sprocket 200 and the driven sprocket 300 It is done by

First, the structure of the driving sprocket 200 will be described with reference to FIGS. 3 to 6.

The drive sprocket 200 is manufactured as a plastic buoyancy material of the hollow form. Therefore, the driving sprocket 200 also generates buoyancy.

The driving sprocket 200 includes

large buoyancy parts

210 and 230 on both sides and small buoyancy parts 220 formed between the large buoyancy parts 210 and 230 (see FIG. 5).

In addition, the large buoyancy portion (210, 230) is a large cylindrical shape, and the small buoyancy portion 220 is a small cylindrical shape.

Therefore, the driving sprocket 200 has a form such as a dumbbell.

In addition, in the large buoyancy portion (210, 230), the track shoe engaging projections (211, 231) coupled to the connection between the track shoe 500 on the outer peripheral surface adjacent to the small buoyancy portion 220 is formed to protrude in the radial direction. The track 400 is rotated by the driving sprocket 200 by the track

shoe coupling protrusions

211 and 231.

In addition,

seating portions

212 and 232 having a flat plate shape are formed between the track

shoe coupling protrusions

211 and 231. The

seating parts

212 and 232 are formed in consideration of the fact that the caterpillar 400 is a form in which the rigid connecting plate 520 is connected in a chain form.

Meanwhile, the driving sprocket 200 of this type may be manufactured by a blow molding method of plastic.

However, if such a large drive sprocket 200 is manufactured in one mold, the volume of the mold is very large, and a large cost is required to manufacture the mold apparatus.

Therefore, the present inventors manufactured the drive sprocket 200 in a form in which a pair of split

type drive sprockets

200a and 200b are assembled with each other.

That is, each of the divided driving

sprockets

200a and 200b includes one of the

large buoyancy parts

210 and 230 and the divided

small buoyancy parts

220a and 220b having half the width of the small buoyancy parts 220. . 6 is a cross-sectional view of the small buoyancy portion 220a.

Therefore, each of the divided

drive sprockets

200a and 200b has a shape in which the drive sprocket 200 having a dumbbell shape is cut about its center in the width direction.

As such, if the

split drive sprockets

200a and 200b are manufactured and then assembled to each other to produce one drive sprocket 200, the size of the manufacturing mold can be reduced to half, and thus the volume of the manufacturing apparatus can be reduced to half. .

In addition, since the divided driving

sprockets

200a and 200b are in contact with each other, the portion of the driving sprocket 200 may function as a reinforcing material for increasing the strength of the driving sprocket 200.

The split drive

sprockets

200a and 200b may be assembled to each other by a bolt and a nut to form the drive sprocket 200, and the assembly method may be any one of known assembly methods.

Thus, if the drive sprocket 200 is manufactured by assembling the divided

drive sprockets

200a and 200b with each other, the shape of the drive sprocket 200 may be modified and implemented as shown in FIG. 7. FIG. 7 is a modified form of FIG. 5.

On the other hand, the driven sprocket 300, as shown in Figure 8, the portion corresponding to the track shoe engaging projections (211, 231) and the mounting portion (212, 232) of the driving sprocket 200 is not formed. Except, it is manufactured in the same form as the drive sprocket 200, the production and assembly methods thereof are also the same.

Of course, according to the exemplary embodiment, the driven sprocket 300 may also have a track shoe coupling protrusion similarly to the driving sprocket 200.

Hereinafter, the detailed structure of each track shoe 500 constituting the crawler 400 will be described with reference to FIGS. 9 to 15.

The track shoe 500 is a buoyancy-producing track shoe capable of generating buoyancy.

In addition, the track shoe 500 is connected to the other track shoe 500 in a chain form to form an endless track 400, all the track shoes 500 are manufactured in the same form.

The track shoe 500 includes a first buoyancy material 530, a foam pad 540, a connecting plate 520, and a second buoyancy material 510.

The first buoyancy material 530 is a plastic buoyancy material of a hollow cylindrical shape, and has a long width direction and a short length direction.

Coupling portions 531 for pads are formed on the lower and outer surfaces of the first buoyancy material 530 in the width direction.

Pad coupling portion 531 is a groove shape recessed inward.

In addition, the coupling portion 532 for the first connecting plate protrudes from an upper surface of the first buoyancy material 530.

The first connecting plate coupling part 532 includes a front first connecting plate coupling part 532a and a rear first connecting plate coupling part 532b which are spaced apart from each other in the longitudinal direction.

Therefore, a space in the form of a groove is generated between the coupling part 532a for the front first connection plate and the coupling part 532b for the rear first connection plate.

Foam pad 540 is made of a foam material that can absorb the external impact.

The foam pad 540 is disposed while surrounding the width direction of the first buoyancy material 530.

At this time, the upper portion of the foam pad 540 is disposed while passing between the coupling portion 532a for the front first connecting plate and the coupling portion 532b for the rear first connecting plate.

In addition, the foam pad 540 has a lower coupling portion 541 coupled to the pad coupling portion 531.

The lower coupling part 541 is a rail-shaped protrusion that protrudes upward (specifically, the inner direction of the first buoyancy material 530) and is inserted into the pad coupling part 531.

As such, the foam pad 540 is provided to surround the width direction of the first buoyancy material 530 to be in direct contact with the ground, and the first buoyancy material 530 may be damaged by the shock by absorbing the impact received from the ground. Will be prevented.

In addition, the foam pad 540 is separated from the first buoyancy member 530 by an assembly form of the lower coupling part 541 and the pad coupling part 531 and the coupling structure of the

coupling parts

532a and 532b for the first connection plate. Is prevented.

The connecting plate 520 is provided on the first buoyancy material 530.

The connecting plate 520 has a connecting bracket 521 formed at the front and the rear thereof, and a lower coupling part 522 is formed at the lower surface thereof to be coupled to the coupling part 532 for the first connecting plate. An upper surface coupling part 523 coupled to the buoyancy material 510 is formed.

Of course, the coupling part 522 is formed to correspond to the shape of the coupling part 532 for the first connection plate, and the connection plate 520 is coupled to the first buoyancy material 530 in such a structure to further increase the foam pad 540. Departure is prevented. That is, the separation to the upper portion of the foam pad 540 by the connecting plate 520 is prevented.

The connecting bracket 521 of the connecting plate 520 is assembled with the connecting bracket 521 of the other connecting plate 520 by the connecting pin 524, and the track shoe 500 by the assembly of the connecting bracket 521 as described above. ) Are connected to each other in a chain form to form a caterpillar (400).

On the other hand, the front and rear edges of the connecting plate 520 is formed with an arc-shaped guide portion 525 forming a convex arc downward.

Therefore, when the connecting plate 520 is connected to the other connecting plate 520, the arc-shaped guide portion 525 of any one of the connecting plate 520 is in contact with the arc-shaped guide portion 525 of another neighboring connecting plate 520. The arc-shaped guides 525 adjacent to each other may form a semicircle by contacting each other.

The structure of the arc-shaped guide portion 525 is formed so that the lower track 420 of the caterpillar 400 can maintain the straightness. The straightness of the crawler 400 will be described later. If the arc shaped guide 525 is not present, the track shoe 500 will be able to rotate in any direction with respect to the neighboring track shoe 500.

The second buoyancy material 510 is provided on the connection plate 520.

Like the first buoyancy material 530, the second buoyancy material 510 is a plastic buoyancy material having a hollow shape.

However, the width of the second buoyancy material 510 is shorter than the width of the first buoyancy material 530.

In addition, a second coupling plate coupling part 511 coupled to the top coupling part 523 of the connection plate 520 is formed on the bottom surface of the second buoyancy material 510.

After the second buoyancy material 510, the connecting plate 520, the first buoyancy material 530, and the foam pad 540 are assembled to each other in this manner, the fixing member 550 such as a rivet or bolt is formed as a second buoyancy material ( The unit track shoe 500 is completed by fixedly coupling through the 510, the connecting plate 520, and the first buoyancy material 530.

At this time, the second buoyancy member 510, the connecting plate 520, the first buoyancy member 530 is withstanding the horizontal force because the respective sliding portions are prevented from sliding each other by the coupling portion (511 and 523, 522 and 532) The holding member 550 may be prevented from being overloaded by the holding member 550 because only the fixing member 550 needs to be separated from each other in the vertical direction.

Such a track shoe 500 is connected in a chain form to form an endless track 400 of the type shown in FIGS. 16 to 17.

In addition, the crawler 400 is mounted between the driving sprocket 200 and the driven sprocket 300 as shown in FIGS.

At this time, the portion coupled to the track shoe coupling protrusion 231 formed on the outer circumferential surface of the driving sprocket 200 in the endless track 400 is a space formed by the arc-shaped guide portion 525 of the connecting plate 540. That is, the coupling protrusion insertion space 526 into which the track shoe coupling protrusion 231 is inserted between the adjacent track shoes 500 is formed by the arc-shaped guide part 525 (see FIGS. 17 to 19).

Of course, even when the arc-shaped guide portion 525 is simply deleted, the portion where the arc-shaped guide portion 525 is located may be used as the coupling protrusion insertion space 526.

In addition, the components of the track shoe 500, the outer track shoe and the outer track shoe depending on whether it is located outside the large buoyancy portion (210, 230) or the space between the large buoyancy portion (210, 230) of the drive sprocket 200 It may be divided into an inner track shoe.

That is, the connecting plate 520, the first buoyancy material 530, the foam pad 540 form an outer track shoe, and the outer track shoe has a width similar to that of the driving sprocket 200 while having a large buoyancy portion 210. It comes in contact with the outer circumferential surface of 230).

The outer track shoe not only generates a relatively large buoyancy but also has a structure whose outer side is surrounded by the foam pad 540, thereby protecting the driving sprocket 200 and the driven sprocket 300.

The second buoyancy material 510 forms an inner track shoe, and the width of the inner track shoe 510 is positioned between the

large buoyancy parts

210 and 230 while having a width corresponding to that of the small buoyancy part 220. do.

The inner track shoe not only generates buoyancy but also passes between the

large buoyancy portions

210 and 230, thereby preventing the caterpillar 400 from being separated from the driving sprocket 200 to the driven sprocket 300.

Meanwhile, the caterpillar 400 has been described under the premise that the connecting plates 520 of the respective unit track shoes 500 are connected in a chain form.

However, according to the exemplary embodiment, the belt may be modified and implemented as a caterpillar.

In other words, by modifying the chain form formed by the connecting plate 520 is connected to each other, the belt plate for the endless track of the belt shape is designed, and the engaging track insertion space is formed in the endless belt for every predetermined length, and the endless track The second buoyancy material 510, the first buoyancy material 530, and the foam pad 540 may be provided by the fixing member 550 for each predetermined length of the belt.

In this case, the second buoyancy material 510 will be provided as the inner track shoe, and the first buoyancy material 530 and the foam pad 540 will be provided as the outer track shoe.

On the other hand, the endless track 400 is located between the portion in contact with the drive sprocket 200, the portion in contact with the driven sprocket 300, and the drive sprocket 200 and the driven sprocket 300 to advance the tracked vehicle It may be divided into an upper track 410 moving forward from the top, and a lower track 420 located between the driving sprocket 200 and the driven sprocket 300 and moving backward from the bottom to advance the crawler vehicle. (See FIG. 17).

In this structure, when the endless track vehicle is positioned on the water surface without a separate device, since the lower track 420 is composed of the track shoes 500 for buoyancy, the track shoe 500 receives the buoyancy and the lower track 420. Is transformed into a convex shape upwards.

However, as described above, the lower track 420 of the upper convex shape generates excessive power loss, and in particular, the passive tracked vehicle becomes a problem.

Therefore, the structure that can maintain the straightness of the lower track 420 in the water should be proposed.

In the caterpillar vehicle of the present embodiment, the straightness maintaining device such as the support roller is not separately provided in the main body 100 in consideration of problems such as maintenance and forward force.

However, in this embodiment, the arc-shaped guide portion 525 of the connecting plate 520 interferes with the arc-shaped guide portion 525 of the neighboring connecting plate 520 (that is, the arc-shaped guide portions 525 meet each other and thus have a semicircular structure. It is possible to deform the lower track 420 into a convex shape downward, but it is impossible to deform the lower track 420 into a convex shape upward (see FIG. 16).

Therefore, the caterpillar vehicle of the present embodiment has almost no power loss since the force of rotation of the lower track is used only to advance the caterpillar vehicle when the caterpillar is rotated.

On the other hand, when maintaining the straightness of the lower track 420 in the form as described above is not a problem in the water phase, but there is a problem that the shape of the lower track 420 can not be deformed according to the shape of the ground. If the lower track 420 is deformed upwardly convex in the ground, it means that the arc-shaped guide 525 is broken.

That is, it is advantageous that the lower track does not deform upwardly convex in the water phase, but in the ground, the lower track 420 moves upward in order to widen the contact area with the ground and to prevent the specific track shoe 500 from being overloaded. It is advantageous to be able to deform into a convex form.

In order to develop this technique, the inventors have focused on the fact that the rigid plastic resins are not in contact with each other and interfere with each other, but if the foamed foams in the lower track 420 are in contact with each other as shown in FIG. 20, this problem can be solved.

FIG. 20 is a view illustrating a connection state of the lower track as a modified view of FIG. 17.

According to FIG. 20, when the lower track 420 is deformed upwardly, the foam pad 540 may interfere with each other with the adjacent foam pad 540 to maintain the straightness of the lower track 420. have.

In FIG. 20, the foam pads 540 in contact with each other are slightly compressed while in contact with the other foam pads 540. That is, if the foam pad 540 is in contact with another foam pad 540 without being compressed at all, the lower raceway 420 may be convex downward. However, as the foam pad 540 is slightly compressed due to the buoyancy of the track shoe 500, the lower track 420 maintains its straightness.

At this time, the force that the lower track 420 is deformed to the upper convex shape is a relatively weak force due to the buoyancy of the track shoe 500. Accordingly, if the material of the foam pad 540 is selected only to withstand the buoyancy of the track shoe 500, the straightness of the lower track 420 may be maintained by the interference between the foam pads 540 in the water phase.

In this case, the foam pad 540 is located on the outermost side of the track shoe 500, the lower track 420 is located at the bottom.

Deformation of the lower track 420 into a convex shape upward means that the track shoes 500 rotate in each other in a connection structure between the tracks 500.

At this time, if the support of the rotation of the track shoe 500 at a distance away from the rotation axis (in this embodiment, the connection bracket 521 is applicable.), A strong torque can be generated even by the same bearing force, so that a relatively soft foam pad 540 may also maintain the straightness of the lower track 420.

On the other hand, when the caterpillar vehicle having such a structure meets a convex shape when the ground moves, the foam pad 540 is compressed to withstand the strong pressure received from the ground and the lower track 420 is deformed to be convex upward. Will be allowed.

The foam pad 540 contracted as described above is restored to its original shape while being separated from the ground of the convex shape.

By applying this design technique, not only the straightness of the lower track in the water can be maintained, but also the lower track is freely deformed to some extent on land, so that the movement on the ground is smooth.

20 is only illustrated as a modified form of FIG. 17, the straightness maintaining manner by the foam pad may be applied in various forms.

On the other hand, the drive sprocket 200, the driven sprocket 300, the first buoyancy member 530, the second buoyancy member 510 has been described as having a hollow cylinder shape, but this means that the interior is necessarily empty It is not.

For example, it may be desirable in some cases for the foam to be injected and foamed into various cylindrical buoyancy materials. This will be able to inject and foam a very light foam in the interior in order to maintain the buoyancy for the purpose of preventing water accidents in advance even when some of the cylindrical buoyancy material is damaged.

However, the foam thus injected foam has a disadvantage that increases the weight of the various buoyancy materials.

However, unlike the foam pad 540, the foam that is injected and foamed into the cylindrical buoyancy material does not need any strength to withstand external shocks or its shape retention ability (that is, is protected from external impact by the cylindrical buoyancy material). Can be relatively light weight.

In addition, the driving sprocket 200, the driven sprocket 300, the first buoyancy material 530, the second buoyancy material 510 may be adopted as a buoyancy material itself. That is, the drive sprocket 200, the driven sprocket 300, the first buoyancy material 530, and the second buoyancy material 510 may be implemented by manufacturing parts having buoyancy as foams and assembling these parts.

Hereinafter, the power transmission and direction switching structure of the crawler vehicle according to the present embodiment will be described with reference to the drawings.

FIG. 21 is a conceptual diagram illustrating a power transmission and direction change structure of FIG. 1, FIG. 22 is a cross-sectional view illustrating the inside of the driving force transmission device of FIG. 21, and FIG. 23 is an exploded cross-sectional view of the driving force transmission device of FIG. 22. 24 is an exploded perspective view of the driving force transmission device of FIG. 21, FIG. 25 is a conceptual cross-sectional view of the driving force transmission device of FIG. 22, and FIG. 26 is a view illustrating an operating state of the driving force transmission device of FIG. 22.

The main body 100 of the crawler vehicle according to the present embodiment is provided with a driving unit for generating a driving force. The driving unit may be a power generating device such as a motor or an engine. However, since the exemplary embodiment describes the caterpillar vehicle used for leisure, the passive driving unit 120 is provided to directly generate the driving force. In addition, the grip handle 130 is provided to allow the occupant to grip by hand while operating the passive drive unit 120.

Passive drive unit 120 is a bicycle pedal structure that is widely used in the bicycle as shown in the figure. The grip handle 130 is similar in shape to a bicycle handle and is fixed so as not to rotate left and right unlike a conventional bicycle handle. The grip handle 130 is provided with a pair of grip portions 131 to allow the occupant to grip. Since the structure of the passive drive unit 120 and the grip handle 130 as described above is widely known in the prior art, a detailed description thereof will be omitted.

The driving force generated by the passive driving unit 120 is input to the driving force transmission device 600 via the chain 140, and the driving force input to the driving force transmission device 600 is paired through the first and

second driving shafts

710 and 720. The driving sprocket 200 is delivered to.

The first and

second driving shafts

710 and 720 are rotatably supported by the main body 100 and connected to the driving sprockets 200 on both sides, respectively. More specifically, one end of the first and

second drive shafts

710 and 720 is connected to each driving sprocket 200 and the other ends are disposed in a straight line to face each other.

The driving force transmitting device 600 is a device for transmitting the driving force input from the passive driving unit 120 to the first and

second driving shafts

710 and 720. The sun gear 610, the ring gear 620, and the plurality of planetary gears 630 are provided. And a carrier 640.

The sun gear 610 is provided to rotate together with the first driving shaft 710 while being fixed to the other end of the first driving shaft 710. The ring gear 620 is fixed to the other end of the second driving shaft 720 by the disk-shaped connecting portion 621 provided on one side, and is provided to rotate together with the second driving shaft 720. The sun gear 610 and the ring gear 620 are arranged concentrically, and a plurality of planetary gears 630 are engaged therebetween.

The plurality of planetary gears 630 are arranged to maintain a constant distance by the carrier 640 interconnecting each of the planetary gears 630. The carrier 640 rotates by a driving force input from the passive driving unit 120 and revolves the planetary gears 630 around the sun gear 610, thereby being engaged with the planetary gears 630. The driving force is transmitted to the 610 and the ring gear 620.

That is, the carrier 640 and the planetary gear 630 coupled thereto are where the driving force is input, and the sun gear 610 and the ring gear 620 engaged with the planetary gear 630 are respectively the driving force. to be.

The carrier 640 has a disc shape in which a first through hole 641 is formed at a center thereof, and a driving force input unit 642 is provided on one side of the carrier 640 to receive a driving force from the passive driving unit 120. The passive driving unit 120 of the present embodiment is the same as the driving unit of the bicycle, and since the driving force is transmitted through the chain 140, the driving force input unit 642 of the carrier 640 is in the form of a corresponding chain sprocket.

However, the driving force is transmitted by the chain 140 and the chain sprocket-type driving force input unit 642 as an example, and according to the embodiment, the driving force is transmitted by the belt and the pulley-type driving force input unit or by two gears engaged with each other. The driving force may be implemented to be transmitted.

The other side of the carrier 640 is provided with a housing 650 to form a gear chamber 654 between the carrier 640. The housing 650 is provided in the shape of a disc such as the carrier 640, but is inserted between the carrier 640 and the cover part 651, and a cover part 651 having a second through hole 651-1 at the center thereof. It comprises a ring shaped spacer 652. The spacer 652 may be provided integrally with the cover part 651 or the carrier 640.

When the spacer 652 and the cover 651 are coupled to the other side of the carrier 640 through the screw member 653, a gear chamber 654 is formed between the carrier 640 and the cover 651. .

The sun gear 610 is disposed in the center of the gear chamber 654 with the first driving shaft 710 passing through the first through hole 641 of the carrier 640. The first through hole 641 is provided with a bearing (not shown) to allow the first drive shaft 710 to smoothly rotate.

The ring gear 620 is disposed in the radially outer portion of the gear chamber 654 with the second driving shaft 720 passing through the second through hole 651-1 of the housing 650. A bearing (not shown) is also provided in the second through hole 651-1 to allow the second driving shaft 720 to smoothly rotate.

The plurality of planetary gears 630 are disposed to be located on the same plane as the sun gear 610 and the ring gear 620 in the gear chamber 654. In this embodiment, four planetary gears 630 are provided, and each planetary gear 630 is rotatably fixed to a planetary gear support shaft 644 provided on the other side of the carrier 640.

When the carrier 640 is rotated, the plurality of planetary gears 630 whose positions are fixed to the planetary gear support shaft 644 are revolved about the sun gear 610. When the planetary gear 630 revolves, the sun gear 610 and the ring gear 620 engaged with the planetary gear 630 also rotate together to transmit driving force to the first and

second driving shafts

710 and 720.

That is, when the carrier 640 is rotated, the first and

second drive shafts

710 and 720 rotate in the same direction as the carrier 640, and each driving sprocket 200 connected thereto is also rotated in the same direction.

The driving force transmitting device 600 may individually transmit the driving force to any one of the first and

second driving shafts

710 and 720.

When a braking force is applied to any one of the first and

second driving shafts

710 and 720, the sun gear 610 or the ring gear 620 connected to the first and

second driving shafts

710 and 720, respectively, stops without rotation.

Since the sun gear 610 and the ring gear 620 can be rotated individually even when the sun gear 610 is engaged with the planet gear 630 by the rotation of the planet gear 630, the sun gear 610 and the ring gear 620 are rotated. Regardless of which one stops, the driving force by the rotation of the carrier 640 is transmitted to the other.

A detailed example will be described with reference to FIG. 26 to easily understand such an operation state.

(A), (b) and (c) of FIG. 26, the driving force input through the carrier 640 rotates the planetary gear 630 counterclockwise. That is, the planetary gear 630 revolves around the sun gear 610 in the counterclockwise direction.

FIG. 26A illustrates a state in which braking force is not applied to the first and

second driving shafts

710 and 720. The driving force input through the carrier 640 is simultaneously output to the first and

second driving shafts

710 and 720 through the sun gear 610 and the ring gear 620.

The planetary gear 630 is fixed to the carrier 640 without rotating about the planetary gear support shaft 644, and the sun gear 610 and the ring gear 620 engaged therewith are also fixed to the carrier 640. It is in a state.

In this state, since the

gears

610, 620, 630 do not rotate in engagement with each other, the

entire gears

610, 620, 630 rotate in one mass at the same angular velocity as the input driving force.

FIG. 26B illustrates a state in which braking force is applied to the first driving shaft 710 to prevent rotation of the sun gear 610. In this state, the driving force input through the carrier 640 is output only to the second driving shaft 720 through the ring gear 620.

Since the sun gear 610 connected to the first drive shaft 710 is fixed, the planetary gear 630 revolving around the sun gear 610 rotates in a counterclockwise direction while being engaged with the sun gear 610.

The ring gear 620 meshed with the planetary gear 630 is increased in speed by the revolution and rotation of the planetary gear 630 and rotates in the same counterclockwise direction as the revolution direction of the planetary gear 630. The rotation of the ring gear 620 is output through the second drive shaft 720 connected to the ring gear 620.

That is, when a driving force is applied to the carrier 640 and the planetary gear 630 connected thereto while the first driving shaft 710 is braked, the second driving shaft 720 is faster than the input driving speed. It rotates in the same direction as the direction of the input driving force.

FIG. 26C illustrates a state in which braking force is applied to the second driving shaft 720 to prevent rotation of the ring gear 620. In this state, the driving force input through the carrier 640 is output only to the first driving shaft 720 through the sun gear 610.

Since the ring gear 620 which is connected to the second drive shaft 720 is fixed, the planetary gear 630 revolving around it rotates clockwise while being engaged with the ring gear 620.

The sun gear 610 meshed with the planetary gear 630 is increased in speed by the revolution and rotation of the planetary gear 630 and rotates in the same counterclockwise direction as the revolution direction of the planetary gear 630. The rotation of the sun gear 610 is output through the first drive shaft 710 connected to the sun gear 610.

That is, when the driving force is applied to the carrier 640 and the planetary gear 630 connected thereto while the second driving shaft 720 is braked, the first driving shaft 710 is faster than the input driving speed. It rotates in the same direction as the direction of the input driving force.

The tracked vehicle according to the present embodiment is to change the direction through the individual braking of the first and second drive shafts (710,720). That is, the direction is switched by stopping one of the first and

second driving shafts

710 and 720 to stop the rotation of the crawler 200 that is operated by the brake.

A pair of brake devices for individually braking the first and

second drive shafts

710 and 720 is provided.

The brake device includes a pair of brake members 810 provided on the first and

second driving shafts

710 and 720 and a brake lever 820 for individually operating the brake members 810, respectively.

The brake member 810 may be applied in various forms, but in this embodiment, the brake member 810 having a disk shape widely applied to a bicycle is used.

The brake member 810 is provided on the first and

second driving shafts

710 and 720, respectively, and the brake disk 811 is rotated together with the first and

second driving shafts

710 and 720, and the respective brake disks are fixed to the main body 100. The brake caliper 812 allows or prevents rotation of the 811.

The brake levers 820 are provided around the pair of grip portions 131 so that the passenger can operate the grip portion 131 of the grip handle 130 while the brake levers 820 are brake cables. It is connected to each of the brake caliper 812 located in the same direction (left, right) through 821.

When a pull force is applied to the brake cable 821 by operating the brake lever 820, the pull force of the brake cable 821 tightens the brake caliper 812 to prevent rotation of the brake disc 811.

As described above, since the brake device including the brake member 810 and the brake lever 820 is widely used in the related art, a detailed description of the detailed structure and operating principle thereof will be omitted.

On the other hand, the pulling force of the brake cable 821 is not necessarily applied through the brake lever 820. The grip handle 130 is rotatably provided to the left and right to allow more intuitive direction manipulation, and the grip handle 130 is applied to each brake cable 821 when the grip handle 130 is rotated left and right. Left and right rotation of may be implemented to replace the function of the brake lever 820.

Next, the direction change structure by the drive force transmission apparatus 600 and a brake apparatus is demonstrated.

The occupant generates a driving force in the passive drive unit 120. The generated driving force is input to the carrier 640 of the driving force transmission device 600 through the chain 140 and the driving force input unit 642, and the input driving force is respectively driven through the first and

second driving shafts

710 and 720. 200 and the crawler 400 coupled thereto.

In order to switch the caterpillar vehicle to the right based on FIG. 21, the right caterpillar 400 of the pair of caterpillars 400 rotating in the traveling direction should be braked. Braking of the crawler 400 is performed through the brake member 810 provided on the first driving shaft 710, and the brake member 810 is operated by operating the brake lever 820 provided in the same direction (right side).

When the brake lever 820 is operated to brake the first driving shaft 710, the rotation of the sun gear 610 connected to the first driving shaft 710 is stopped, and the ring is rotated by the revolution and rotation of the planetary gear 630. The driving force is transmitted only to the second driving shaft 720 connected to the gear 620. In addition, the speed of the second drive shaft 720 is increased, so that the left caterpillar 400 rotates at a faster speed than when driving in a straight line, and the direction is quickly changed.

In order to reverse the caterpillar vehicle according to the present embodiment to the left, the left brake member 810 may be operated by operating the left brake lever 820 as opposed to the above description. When the left brake member 810 is operated, the rotation of the left caterpillar 400 is stopped and the right caterpillar 400 is rotated in an increased speed to quickly change direction to the left.

The speed increase may be controlled by changing gear ratios of the sun gear 610, the ring gear 620, and the planetary gear 630 in the driving force transmission device 600.

In addition, the tracked vehicle according to the prior art requires a precise setting for the brake member to operate after the clutch member is operated and the transmission of the driving force is interrupted. However, the tracked vehicle of the present embodiment does not require such a precise setting. Easy to manufacture and easy to maintain

The foregoing description of the present invention is intended for illustration, and it will be understood by those skilled in the art that the present invention may be easily modified in other specific forms without changing the technical spirit or essential features of the present invention. .

Therefore, the embodiments described above are to be understood in all respects as illustrative and not restrictive. For example, each component described as a single type may be implemented in a distributed manner, and similarly, components described as distributed may be implemented in a combined form.

The scope of the present invention is shown by the following claims rather than the above description, and all changes or modifications derived from the meaning and scope of the claims and their equivalents should be construed as being included in the scope of the present invention. do.

The present invention can be used as a crawler vehicle.

Claims

A main body provided with a driving unit for generating a driving force;

A pair of driving sprockets and a pair of driven sprockets respectively provided on both front and rear sides of the main body;

A pair of endless tracks mounted between the drive sprocket and the driven sprocket to generate buoyancy;

First and second drive shafts rotatably supported by the main body such that the other ends thereof face each other with one end connected to each driving sprocket;

A sun gear connected to the other end of the first drive shaft, a ring gear connected to the other end of the second drive shaft and arranged concentrically on a radially outer side of the sun gear, between the sun gear and the ring gear A plurality of planetary gears meshed with and coupled to the planetary gears so that the plurality of planetary gears revolve and rotate on the same plane as the sun gear and the ring gear, but the drive force of the driving unit is transmitted to the planetary gears. A driving force transmission device including a carrier for revolving gears;

A pair of brake devices for individually braking the first and second drive shafts;

It is made, including

When the driving force is input through the carrier, the planetary gear transfers driving force to both the sun gear and the ring gear while revolving around the sun gear, wherein the pair of brake devices are used to control the sun gear and the ring gear. When any one of the braking, the planetary gear is revolving around the solar gear and at the same time rotates to transfer the driving force to only the other of the sun gear and the ring gear, the infinitely variable tracked vehicle.
The method of claim 1,

The carrier is in the form of a disk having a first through-hole is formed in the center, the driving force input unit for receiving the driving force from the drive unit on one side is provided;

A second through-hole is formed in the center and is coupled to the other side of the carrier further comprises a housing for forming a gear chamber between the carrier;

The sun gear is disposed in the center of the gear chamber with the first driving shaft penetrating the first through hole, and the ring gear is radially formed in the gear chamber with the second driving shaft penetrating the second through hole. A plurality of planetary gears rotatably fixed to the other side of the carrier to be engaged on the same plane as the sun gear and the planetary gear;

A caterpillar vehicle capable of changing direction, characterized in that.
The method of claim 1,

The seating part and the grip handle are provided in the main body;

The driving unit is a passive driving unit for generating a rotational driving force by a passenger seated in the seating unit;

The brake device includes a pair of brake members provided on the first and second drive shafts, respectively, and a pair of brake levers provided on the grip handle to individually operate the brake members;

A caterpillar vehicle capable of changing direction, characterized in that.