WO2001089649A1

WO2001089649A1 - Simulator for running animal

Info

Publication number: WO2001089649A1
Application number: PCT/KR2000/001262
Authority: WO
Inventors: Ho Sung Kim
Original assignee: Gaim Co., Ltd.
Priority date: 2000-05-24
Filing date: 2000-11-04
Publication date: 2001-11-29
Also published as: KR20010106908A; AU1177201A

Abstract

The present invention relates to a simulator for simulating animal motion. In case of using the conventional animal locomotion simulator, due to differences between motions of a real animal and the simulator, there are many problems in that the simulated motion of the simulator is unnatural or inconsistent with the motion of the real animal. In order to simulate such motion of a real animal, the present invention provides a simulator comprising an up and down rocking amplitude adjusting apparatus for reproducing an up and down rocking amplitude of a back portion of the real animal which is in inverse proportion to the running speed; an apparatus for shaking neck and head portions of the simulator up and down in inverse proportion to the running speed, and straightening or bending the neck and head portions of the simulator; an inclining apparatus for reproducing jump and uphill/downhill environments; a pressure sensor for implementing maintenance of the current running speed. Therefore, the simulator of the present invention makes motions similar to motion of a real animal, particularly motion of a horse in horse racing.

Description

SIMULATOR FOR RUNNING ANIMAL

Technical Field

The present invention relates to a simulator for simulating animal motion.

Background Art In general, there have been developed various apparatus for playing the game or practicing the riding by sitting astride a simulator for simulating motion of an animal such as a horse. One example of the apparatus is a horseback riding simulator for training a jockey. When beforehand practicing the horseback riding by using such horseback riding simulator, the jockey can easily adapt oneself to real horseback riding. Another example of the apparatus is a horse racing apparatus for a game. Such horse racing apparatus makes a simple rocking motion according to riding conditions displayed on a display device. In a case where an apparatus for simulating locomotion of a horse, tiger, lion or the like is installed at an ordinary home or playground, only the simple motion of the animal is simulated.

However, since such conventional animal simulating apparatus, particularly the horseback riding apparatus has a very simple function and thus cannot sufficiently reproduce the motion of a horse, it is merely a simulator that does not impart a sense of reality. A more specific example of conventional animal simulators will be explained below.

As shown in FIG. 1, in the conventional animal motion simulator, when a motor 7 rotates a hind leg shaft 5 along a path of A-B-C-D-A through a gear assembly (not shown) disposed in a hind leg post 3, a back frame 6 causes a foreleg shaft 4 to reciprocate along a path of E-F-E-G-E. Upon simulation of a horse's gallop, the motor 7 is rotated as a high speed to speed up the rotation of the hind leg shaft 5 and the reciprocating motion of the foreleg shaft 4 so that a rocking period is shortened. Upon simulation of a horse's canter, the motor 7 is rotated as a low speed to speed down the rotation of the hind leg shaft 5 and the reciprocating motion of the foreleg shaft 4 so that a rocking period is lengthened. In other words, such animal motion simulator can reproduce only a motion that always has a constant rocking amplitude. However, when sitting astride a saddle on a back of a real animal in practice, an up and down rocking amplitude of the saddle is in inverse proportion to the running speed, contrary to the conventional animal motion simulator. That is, if the speed increases, the rocking amplitude lessens, and if the motion speed decreases, the rocking amplitude becomes larger. In addition, as for real motion of an animal, there are a jump motion, uphill and downhill motions and the like which cannot be reproduced in the conventional simulator. In case of using the conventional animal motion simulator, due to differences between motions of a real animal and the simulator, there are many problems in that the simulated motion of the simulator is unnatural or inconsistent with the motion of the real animal.

Disclosure of Invention

The present invention is conceived to solve the aforementioned problems of the prior art. An object of the present invention is to provide a simulator with various functions by which motions of the simulator can be made to be very similar to the motion of a real animal such as a horse and a tiger.

More specifically, the present inventor found from continuous researches on the running of a real animal that contrary to a conventional simulator, an up and down rocking amplitude of a back portion of the animal becomes larger at low-speed running and it is very small at high-speed running, i.e. the up and down rocking amplitude is in inverse proportion to the running speed. The inventor also found that neck and head portions of the animal shake up and down inversely proportional to the running speed; that if the saddle was moved rearward with respect to a front shaft (in other words, the forelegs of the animal are off the ground and stretched out forward), the neck and head portions are straightened; and that if the saddle is moved forward with respect to the front shaft (in other words, the forelegs are bent inward in order to contact with the ground), the neck and head portions are bent. Furthermore, the inventor found that if the animal intends to jump an obstacle confronted in the course of the running, the real animal jumps the obstacle in postures as shown in FIG. 2. Moreover, the inventor found that upon uphill or downhill running, the real animal assumes postures similar to those of upward or downward motion during the jump. Additionally, the inventor found that although frequently seen in case of horse racing, a jockey exerts pressure upon the flank of a horse by his knees for signaling the horse to hold a current speed.

Therefore, in order to simulate such running of a real animal, the present invention provides a simulator comprising an up and down rocking amplitude varying or adjusting device for reproducing an up and down rocking amplitude of a back portion of the real animal which is in inverse proportion to the running speed; a device for shaking neck and head portions of the simulator up and down in inverse proportion to the running speed, and straightening or bending the neck and head portions of the simulator as a saddle is translated horizontally with respect to a foreleg of the simulator; an inclining device for reproducing jump and uphill/downhill environments; a pressure sensor for implementing maintenance of the current running speed. Therefore, the simulator of the present invention makes motions similar to locomotion of a real animal, particularly locomotion of a horse in horse racing. Brief Description of Drawings

FIG. 1 shows a conventional animal motion simulator. FIG. 2 shows sequential postures of a jump motion of an animal. FIG. 3 is a view showing the entire constitution of an animal motion simulator according to the present invention.

FIG. 4 shows a connecting structure of neck and head portions of the animal locomotion simulator according to the present invention.

FIG. 5 shows an electric-type up and down rocking amplitude varying device according to the present invention.

FIG. 6 illustrates a principle of an electric-type rotary connector applicable to the present invention.

FIG. 7 shows a mechanical-type up and down rocking amplitude varying device according to the present invention. FIG. 8 shows an inclining device for reproducing jump and uphill/downhill running according to the present invention.

^• FIG. 9 a view showing a position of the inclining device during the jump according to the present invention.

Best Mode for Carrying Out the Invention

Now, the schematic constitution of an animal motion simulator according to the present invention will be described in details with reference to FIG. 3 in which an outer frame and a supporting structure are omitted in order to clearly show the inner constitution thereof). Each of a front shaft 11 and a rear shaft 12 corresponding to forelegs and hind legs of an animal consists of two concentrically arranged shafts. An inner shaft 122 of the rear shaft 12 is fixedly coupled to a saddle 13 via a pin 14. An inner shaft 112 of the front shaft 11 is slidably coupled to the saddle 13 thereon so that the saddle 13 can be moved in a lateral direction. These inner shafts 112, 122 are shafts for vertically rocking the saddle 13 by an up and down rocking amplitude inversely proportional to a running speed which is determined by an up and down rocking amplitude varying or adjusting device (see FIGS. 5 and 7) to be explained later. Shock absorbers such as springs (not shown) are disposed between upper portions of the outer shafts 111, 121 and flanges of upper portions of the inner shafts 112, 122 to damp impact upon contact of the flange of the outer shafts 111, 121 with the upper portion of inner shafts 112, 122. The outer shafts 111, 121 define a tilt angle of the saddle 13, which is determined by the inclining device (see FIG. 8) in charge of the jump and uphill/downhill running. In addition, theses front shaft 11 and the rear shaft 12 can be slid in the lateral direction by means of a slide structure 42 coupled to a slide shaft 41. A neck portion 16 has a sliding groove 17 at a lower portion thereof, and a pin 15 fixed to a side surface of the saddle 13 is fitted into the sliding groove 17. The neck portion 16 is resiliently coupled to the upper portion of the inner shaft 112 of the front shaft 11 so as to take the shape at a normal condition as shown the figure. With such construction, as the simulator is operated to simulate the running of an animal, the pin 15 fixed to the saddle 13 pushes the sliding groove 17 in the lateral direction so that the neck portion 16 moves up and down. The degree of the up and down movement is proportional to the degree of sliding of the saddle 13 in the lateral direction. The degree of sliding of the saddle 13 in the lateral direction is proportional to the degree of up and down rocking by the up and down rocking amplitude adjusting device 20. Therefore, if the running speed decreases so that a period of the up and down rocking is lengthened and the up and down rocking amplitude increases, the saddle 13 is moved slowly but largely in the lateral direction. Thus, the neck portion 16 is moved slowly but greatly up and down. Otherwise, if the running speed increases so that a period of the up and down rocking is shortened and thus the up and down rocking amplitude decreases, the saddle 13 is moved quickly but slightly in the lateral direction. Thus, the neck portion 16 is moved quickly but slightly up and down. In such way, the simulator achieves the period and degree of the movement of the neck portion of a real animal upon the running thereof.

Next, the operation of the neck portion 16 and a head portion 18 of the simulator will be described with reference to FIGS. 3 and 4.

In FIG. 4, the head portion 18 is subject to downward force resulting from its own weight. The force is counteracted by a rope 19 of which one end is connected to the saddle 13 and the other end is connected to a lower end of a gear on the side of neck portion of two gears placed in vicinity of a connecting portion of the neck portion 16 and the head portion 18.

With such connection, if the simulator reproduces a condition that an animal jumps off the ground and stretches its forelegs forward, the saddle 13 is moved rearward with respect to the front shaft 11 so that the pin 15 pushes the sliding groove 17 rearward and thus the neck portion 16 is moved downward (straightened). Then, since the rope 19 is drawn, the head portion 18 is lifted (straightened). On the contrary, it the simulator reproduces a condition that the animal bends the forelegs inward in order to contact with the ground, the saddle 13 is moved forward with respect to the front shaft 11 so that the pin 15 moves toward the center of the sliding groove 17 and thus the neck portion 16 is moved upward (contracted). Then, since the rope 19 is loosened, the head portion 18 is lowered (contracted) due to its own weight. In other words, in case of simulating the jumping and landing motions of the animal, the neck portion 16 and the head portion 18 of the simulator repeat the straightening and contracting movements to perform the same motions as the real animal upon the running thereof.

Further, the degree of the straightening and contracting of the neck portion 16 and the head portion 18 is proportional to the degree of the sliding of the saddle with respect to the front shaft 11 which is in inverse proportion to the running speed. The period of the extension and contraction of the neck portion 16 and the head portion 18 is proportional to the period of the sliding of the saddle with respect to the front shaft 11 which is proportional to the running speed.

Next, the up and down rocking amplitude adjusting device 20 according to the present invention will be described.

The up and down rocking amplitude varying device 20 according to the present invention may be installed on both the sides of the front and rear shafts or on only the side of the rear shaft. Since the structures of the front and rear shaft portions are identical with each other, only the up and down rocking amplitude adjusting device 20 installed on one side of them will be specifically explained hereinafter. Incidentally, the maximum up and down rocking amplitude of the up and down rocking amplitude adjusting device 20 on the side of the front or rear shaft portion can be properly adjusted, if necessary. There exists electric type and mechanical type for the up and down rocking amplitude adjusting device 20.

The electric-type up and down rocking amplitude adjusting device 20 shown in FIG. 5 includes a sprocket 21 connected through a chain to an up and down rocking motor (not shown) which supplies power for vertically reciprocating the inner shaft according to a predetermined up and down rocking amplitude; a hollow, up and down rocking shaft 22 fixedly coupled to the sprocket 21; a terminal assembly 24 for supplying power and control signals to an up and down rocking amplitude adjusting motor 23 which is installed at one end of the up and down rocking shaft 22 and determines the up and down rocking amplitude; a screw 25 rotated by means of rotation of the up and down rocking amplitude adjusting motor 23 which receives the power and the control signals supplied through the terminal assembly 24; and a variable feeding carriage 26 threadedly engaged with the screw 25 and moved along the screw 25 to move toward and far away from the up and down rocking shaft 22 according to the rotation of the screw 25. The terminal assembly 24 has a plurality of annular metallic bands 27 on the side of the up and down rocking shaft 22. The metallic bands 27 are connected to electric wires 28 within the up and down rocking shaft 22. The metallic bands 27 are connected to bar-shaped metallic terminals 29 resiliently supported by springs. A supporting stand 40 supports the up and down rocking shaft 22 with a bearing (not shown) disposed therebetween.

With such construction, external power and control signals required for the up and down rocking amplitude adjusting motor 23 are transmitted to the up and down rocking amplitude adjusting motor 23 via the bar-shaped metallic terminals 29, the metallic bands 27 on the rotating up and down rocking shaft 22, and the electric wires 28. The up and down rocking amplitude adjusting motor 23 rotates the screw 25 in a forward or reverse direction in response to the external control signals so that the variable feeding carriage 26 moves toward and far away from the up and down rocking shaft 22 in response to the external control signals. Thus, the variable feeding carriage 26 adjusts the distance between central axes of the up and down rocking shaft 22 and the variable feeding carriage 26 to be set in inverse proportion to the running speed. Within a gap corresponding to the distance between the central axes of the up and down rocking shaft 22 and the variable feeding carriage 26 determined as such, an inner shaft 31 connected to the variable feeding carriage 26 is moved vertically and thus the saddle 13 is rocked as shown in FIG. 5. In addition, although only one array of the bar-shaped terminals 29 are shown in FIG. 5, a plurality of arrays of the terminals may be installed around the metallic band 27 in order to obtain more secure contact. In addition, as opposed to FIG. 5, resiliently supported terminals may be installed on the up and down rocking shaft 22, and a cylindrical body having the metallic band therein may be installed on the outside of the rocking shaft 22 so as to surround the rocking shaft 22.

Particularly, when a structure comprising the resiliently supported bar- shaped terminals 29 and the metallic band 27 is used for a long time, contact elements may be worn away, leading to reduced lifetime and poor contact due to foreign matter such as dust. Meanwhile, according to the present invention, as shown in FIG. 6 (showing the operating principle of the structure), two cylindrical non-conductive shafts 90, 91 are faced to each other and are stuck to each other by a nut 92 having threads on the outside thereof and a bearing 93 so as to be rotatably engaged to each other. At a portion of the shafts faced to each other, the rotatable shaft 91 (fixedly engaged with the up and down rocking shaft 22) has concentric grooves 94 (four concentric grooves in FIG. 6), and metallic contact elements 95 are formed on the bottom walls of the concentric grooves 94 along the concentric grooves 94. The fixed shaft 90 has a plurality of recesses 96 (although it is sufficient that four recesses are installed on one side of the fixed shaft in the radial direction, as shown in FIG. 6, additional four recesses are installed on the other side of the non-rotating shaft in the radial direction in order to obtain excellent contact performance) to face with the concentric grooves in the radial direction, and metallic contact elements 97 are installed on the bottom wall of the recesses 96. Two electric wires 98, 99 are connected to the metallic grooves and recesses 94, 96, respectively. In an electric-type rotary connector (for example, M20 model manufactured by Rotocon Co. Ltd.) having the above constitution, the grooves and recesses 94, 96 are filled with conductive liquid such as mercury. Therefore, since contact between the contact elements is formed by the conductive liquid, there is no wear on the contact elements and no poor contact due to foreign matter. In addition, the contact becomes secured. In case of this connector, it is important that the conductive liquid should be prevented from flowing from one pair of grooves to the other pair of recesses and from forming unwanted conductive paths. Thus, it is preferable that the conductive liquid does not tend to flow. For example, mercury is representative material having this property. When power and control signals from the outside are transmitted to the terminals A, B, C and D of the fixed shaft 90, the power and control signals are transmitted via the wire 99, the contact element 97 and the conductive liquid (gauze pattern) to the contact element 95, the wire 98 and the terminals A', B', C and D' of the rotatable shaft 91. Then, when the wire 28 in the up and down rocking shaft 22 is connected to the terminals A', B', C and D', the terminals A, B, C and D in the fixed shaft 90 are connected to the wire 28 in the up and down rocking shaft 22, allowing the signals to be transmitted.

FIG. 6 explains the principle of the electric-type rotary connector. Various kinds of electric-type rotary connectors principle of which are the same but structures of which are different may be used. For example, a plurality of concentric grooves may be on the circumference of the rotatable shaft, corresponding recesses may be on the bottom of a cylinder surrounding the rotatable shaft, and this cylinder may be hermetically fitted to the rotatable shaft.

Next, a mechanical up and down rocking amplitude adjusting device will be explained with reference to FIG. 7.

The mechanical up and down rocking amplitude adjusting device is in principle the same as the electric-type up and down rocking amplitude adjusting device. However, in order to move a mechanical variable feeding carriage 56 in an up and down direction, in the electric-type up and down rocking amplitude adjusting device, the up and down rocking amplitude adjusting motor 23 is installed on the top of a screw 25. On the other hand, in the mechanical up and down rocking amplitude adjusting device, a screw 55 is turned by the up and down rocking amplitude adjusting shaft 51 and a plurality of gears. Therefore, hereinafter, it will be explained how the up and down rocking amplitude adjusting shaft 51 moves the variable feeding carriage 56.

The mechanical up and down rocking amplitude adjusting device comprises the adjusting shaft 51 connected to the up and down rocking amplitude adjusting motor (not shown) for supplying power to move the variable feeding carriage 56; a gear assembly 52 installed on the variable feeding carriage 56 of the adjusting shaft 51 for transmitting power to a bevel gear 53 connected to the screw 55 for moving the variable feeding carriage 56 in an up and down direction; a brake/clutch assembly 59 for braking rotation of the adjusting shaft 51 and blocking power of the up and down rocking amplitude adjusting motor to the adjusting shaft 51 at a first state, releasing the brake so that the adjusting shaft 51 can rotate, transmitting power of the up and down rocking amplitude varying motor to the adjusting shaft 51 at a second state, separating the adjusting shaft 51 from the up and down rocking amplitude motor and fixedly engaging the adjusting shaft 51 and the up and down rocking shaft 54 at a third state so as to rotate the adjusting shaft 51 and the up and down rocking shaft 54 together by the rotation of the motor for the up and down rocking shaft 54.

In order to move the variable feeding carriage 56 toward the central axis of the up and down rocking shaft 54 when the running speed increases, the brake/clutch assembly 59 is brought into a first state so that the adjusting shaft 51 cannot move by operating the brake, and that the power from the varying motor is not transmitted to the adjusting shaft 51 by releasing the clutch. In other words, the up and down rocking shaft 54 is brought into a rotating state, and the adjusting shaft 51 is brought into a stopping state. It is considered that the up and down rocking amplitude varying shaft 51 rotates in the direction opposed to the rotation direction of the up and down rocking shaft 54, and that the up and down rocking shaft 54 stops. In FIG. 7, when the up and down rocking shaft 54 rotates in the shown direction (clockwise), the bevel gear 53 also rotates clockwise. Then, the variable feeding carriage 56 moves upward, resulting in decreasing the up and down rocking amplitude. When the distance of the variable feeding carriage 56 to be moved from the current position is determined, revolution or angular displacement are determined depending on the diameters of the bevel gear 53 and the gear assembly 52. As a detector for accurately detecting whether the up and down rocking shaft 54 has rotated by the determined revolution or angular displacement of the up and down rocking shaft 54, for example, as shown in FIG. 7, a disc 60 having wings around the circumference thereof and a sensor 61 for detecting the number of passing the wings are preferably disposed.

Next, in order to move the variable feeding carriage 56 far away from the central axis of the up and down rocking shaft 54 when the running speed decreases, the brake/clutch assembly 59 is brought into the second state so as to release the brake of the adjusting shaft 51 and to operate the clutch. Then, the power from the up and down rocking amplitude adjusting motor is transmitted to the adjusting shaft 51. In other words, the up and down rocking shaft 54 and the adjusting shaft 51 rotate. At this time, the adjusting shaft 51 should rotate faster than the up and down rocking shaft 54 in the same direction. This is because it is considered that in the same speed, the adjusting shaft 51 does not rotate relative to the up and down rocking shaft 54, and that the gear assembly 52 and the bevel gear 53 do not rotate.

For example, as shown in FIG. 7, when the adjusting shaft 51 and the up and down rocking shaft 54 rotate in the same direction (clockwise), it is considered that the up and down rocking shaft 54 stops, and that the adjusting shaft 51 rotates clockwise. Then, the bevel gear 53 rotates counterclockwise, and accordingly, the variable feeding carriage 56 moves downward, resulting in increasing the up and down rocking amplitude. At this time, when the distance of the variable feeding carriage 56 to be moved from the current position is determined, revolution and angular displacement are determined depending on the diameters of the bevel gear 53 and the gear assembly 52. As a detector for accurately detecting whether the adjusting shaft 51 has rotated by the determined revolution or angular displacement of the up and down rocking amplitude varying shaft 51, for example, in the same way as a case where the running speed increases, a disc 62 having a wing around the circumference thereof and a sensor 63 are preferably disposed.

In a case where the current speed is maintained, the adjusting shaft 51 and the up and down rocking shaft 54 should have the same speed. However, since it is difficult to render the shafts to have substantially the same velocity, the brake/clutch assembly 59 is brought into the third state of fixedly engaging the two shafts and separating the adjusting shaft 51 from the varying motor. Then, the up and down rocking amplitude varying shaft 51 and the up and down rocking shaft 54 are rotated together by the rotational force of the motor for the up and down rocking shaft 54. In addition, in order to accurately control the mechanical or electric- type variable feeding carriage 26 or 56, when a sensor 64 for detecting whether the variable feeding carriage 26 or 56 is at a position farthest from the central axis of the rocking shaft 22 or 54 as shown in FIGS. 5 and 7 is disposed, the variable feeding carriage 26 or 56 can be moved to this position when converted into an initial stage or other operating mode, resulting in initializing the position of the variable feeding carriage. Next, a jump function will be explained.

In order to jump over a hurdle, a real animal takes a jump posture as shown in FIG. 2. In other words, a saddle portion is horizontal at first (initial posture), is directed to an upward direction at a time of starting to jump toward the hurdle (uphill posture), becomes horizontal at a time of reaching the top of the hurdle (horizontal posture), is directed to an downward direction at a time of starting to pass the top of the hurdle (descending posture), and becomes horizontal again at a time of arriving at the ground (initial posture).

Now, a method of mechanically realizing jump motion will be explained.

As shown in FIG. 8a, a device for jump motion comprises a motor 70 for supplying power for jump motion; a clutch 80 for transmitting power from the motor 70; a brake 81 for stopping a rotational shaft of the motor 70 from rotating; a gear 72 driven by a chain 71 (a belt may be used) connected to the rotational shaft of the motor 70; a gear 73 connected to the gear 72 by the chain in the form of pulley and having the same rotating velocity as the gear 72; first connecting rods 74, 75 two one ends of which are connected to shafts of the gear 72, 73, respectively; second connecting rods 76, 77 two one ends of which are connected to the two other ends of the first connecting rods 74, 75, respectively; and shafts 78, 79 for jump motion connected to the two other ends of the second connecting rods 76, 77, respectively so as to perform an up and down motion as the gear 72, 73 rotate. The shafts 78, 79 correspond to the outer shafts 111, 121 of the front shaft 11 and the rear shaft 12 as shown in FIG. 3, respectively.

FIG. 8b is a side view of only the first connecting rods 74, 75 and the shafts 78, 79 in FIG. 8a. Referring to FIG. 8b, the gears 72, 73 in the form of pulley shown in FIG. 8b are connected by the chain so that the first connecting rod 74 connected to the shaft of the gear 72 advances the first connecting rod 75 connected to the shaft of the gear 73 in phase by about 90°.

Now, the device can realize the jump motion as shown in FIG. 2. The jump motion will be explained with reference to FIGS. 9a to 9g. The power from the motor 70 is transmitted via the chain 71 to the gear 72, 73 by the clutch 80. At this time, a brake 81 is at a releasing state. Now, the device is brought into an initial state as shown in FIG. 9a. In order to sense the initial state, a sensor is attached. When the jump motion starts, if the current state sensed by the sensor is not the initial state, the gears 72, 73 are rotated so that the device is brought into the initial state. In the initial state, the saddle 13 is horizontal and at the lowermost position. Then, when the gears 72, 73 rotate and the first connecting rods 74, 75 are brought into a state of FIG. 9b, the front side of the saddle is raised. When the gears 72, 73 further rotate and the first connecting rods 74, 75 are brought into a state of FIG. 9c, the front side of the saddle 13 is further raised. When the rods are brought into a state of FIG. 9d, the saddle 13 becomes horizontal at a higher position. When the rods are brought into a state of FIG. 9e and FIG. 9b, the saddle is dropped. Finally, the rods are brought into a landing state of FIG. 9g. Thus, the actual jump motion of the animal as shown in FIG. 2 can be mechanically realized.

Now, a method of mechanically realizing uphill and downhill motions will be explained.

The uphill and downhill motions are achieved by maintaining any state of jump functions. A sensor for detecting the state of the rods is attached. When the sensor senses any desired state of the rods, the power from the motor 70 is cut in the clutch 80. In order to maintain the state, the brake 81 is operated so as to stop the gears 72, 73. Then, the shafts 78, 79 (corresponding to the outer shafts in FIG. 3) are maintained. For example, in order to become the state of FIG. 9b, when a sensor for detecting the state of the rods senses the state of FIG. 9b, the clutch 80 is released, and the brake 81 is operated. Thus, when the gears 72, 73 stop, the saddle 13 lies in a slight uphill configuration as shown in FIG. 9b.

Therefore, since the simulator is brought into a flat state (FIG. 9a), a slight uphill state (FIG. 9b), an uphill state (FIG. 9c), a downhill state (FIG. 9e), a slight downhill state (FIG. 9f), sensors for detecting the states (the positions of the first connecting rods as shown in FIG. 9a, FIG. 9b, FIG. 9c, FIG. 9e and FIG. 9f) should be installed.

Now, how the up and down rocking function, the jump function, and the uphill/downhill function described above are combined with one another will be explained with reference to FIGS. 5 and 9.

When observing the motion of a real animal, it can be noted that there are three modes, i.e. a flat ground running mode, a jump mode after temporary stop of flat ground running motion, and an uphill/downhill running mode. Although there is also a possibility of jumping during the uphill/downhill running, considering it is not likely that such case occurs and considering safety of the simulator, the present invention may omits the jump function during the uphill/downhill running. The electric or mechanical type up and down rocking amplitude adjusting device shown in FIG. 5 and 7 has a coupling structure 30, 65 for connecting the imier shaft 31 or 57 to the variable feeding carriage 26. The coupling structure 30 or 65 is constructed such that when the control signals are turned off, the coupling structure 30 or 65 allows the inner shaft 31 or 57 to be freely slid up and down so that the inner shaft 31 or 57 is slid downward due to the weight of the saddle 13. It is also constructed such that when the control signals are turned on, it holds the inner shaft 31 or 57. The other end of the coupling structure is rotatably connected to the variable feeding carriage 26 or 56. With such construction, when the control signals are turned on, the inner shaft 31 or 57 is coupled to the variable feeding carriage 26 or 56. When the control signals are turned off, the inner shaft 31 or 57 is lowered due to its own weight until the flange of the inner shaft 31 or 57 is caught by the upper portion of the outer shaft (111 or 121 of FIG. 3; 78 or 79 of FIG. 8). First, when the simulator is turned on, it is brought into an initial state.

The initial state means that the inclining device for the jump motion and the uphill/downhill environments is fixed to be horizontal as shown in FIG. 9a; the variable feeding carriage 26 is moved toward a lowermost position, which is farthest from the up and down rocking shaft 22, by means of the rotation of the up and down rocking shaft 22 as shown in FIG. 5; and the coupling structure 30 is released to lower the inner shaft 31 so that the flange of the inner shaft 31 is caught by the upper portion of the outer shaft 111 or 121. In other words, in the initial state, the saddle 13 is brought into a lowest horizontal position and the rocking amplitude is maximized.

When the simulator starts to perform flat ground running and goes into a flat ground running mode, the inclining device is fixed in a state shown in

FIG. 9a. Thereafter, the control signals for the coupling structure 30 are turned on, and the variable feeding carriage 26 and the inner shaft 31 are engaged with each other. In a case where a running speed of the simulator is increased during the flat ground running mode, the rotational speed of the up and down rocking shaft 22 is increased, and then the number of times the simulator rocks is increased. Further, the variable feeding carriage 26 is controlled to move toward a central axis of the up and down rocking shaft 22, and thus, the rocking amplitude is decreased. In a case where the running speed of the simulator is decreased during the flat ground running mode, the rotational speed of the up and down rocking shaft 22 is decreased, and then the number of times the simulator rocks is decreased. Further, the variable feeding carriage 26 is controlled to move far away from the central axis of the up and down rocking shaft 22, and thus, the rocking amplitude is increased.

If the flat ground running mode is to be changed to a mode for performing a jump motion, the simulator should be immediately shifted into the aforementioned initial state (i.e., a state where the saddle 13 is set to be horizontal and the rocking amplitude is maximized). After the simulator has become in the initial state, the aforementioned jump motion begins.

After the jump motion has been completed, it goes into the initial state, and then, the flat ground running mode begins again.

Now, uphill and downhill running motion will be explained.

Similarly to the jump motion, if it would go into an uphill or downhill mode during the flat ground running mode, the simulator should be shifted into the aforementioned initial state and take a horizontal posture. Thereafter, the simulator is shifted into an uphill or downhill posture. Alternatively, it may be performed in such a manner that the inclining device takes first an uphill or downhill posture and then both the variable feeding carriage 26 and the inner shaft 31 become the initial state. Thus, if the saddle 13 takes a lowest uphill and downhill posture, i.e. it becomes the same state as the aforementioned flat ground running, the saddle 13 rocks up and down in inverse proportion to the running speed in a state where the saddle 13 is inclined uphill or downhill. Therefore, it is possible to perform the uphill and downhill running.

Finally, a function of maintaining a current running speed will be explained.

In case of real horse racing, a jockey pushes the flank of a horse with jockey's knees at a predetermined pressure in order to maintain the current running speed of the horse during the running. In order to implement the function of maintaining the current running speed, the present invention is constructed in such a manner that the pressure sensors are attached and user can push a flank portion of a horse simulator at a predetermined pressure, and thus, the current running speed of the horse simulator can be kept by detecting the pressure.

As described above, the animal motion simulator of the present invention has a variety of functions such as a up and down rocking amplitude adjusting function, a jump function, an uphill and downhill function and a current speed maintaining function. However, all the functions may be implemented or some of the functions may be omitted since degree of skill of the user can be set by means of a controller of the animal motion simulator. For example, all the functions can be performed when an expert mode is set. Further, a maximum up and down rocking amplitude, a maximum jump amplitude, an uphill and downhill degree, etc. can be set higher. In case of a beginner or children mode, some dangerous functions can be omitted or the degree of the difficulty of the functions can be lowered.

The preferred embodiments of the present invention have been described herein. These preferred embodiments have been described for illustrative purposes only, and are not limited thereto. Other embodiments are possible and are covered by the invention. Such other embodiments will be apparent to persons skilled in the art based on the teachings contained herein. Thus, the breadth and scope of the present invention should not be limited by any of the above-described exemplary embodiments, but should be defined only in accordance with the following claims and their equivalents.

Industrial Applicability

According to the present invention, the animal motion simulator has a variable rocking function, a jump function, an uphill and downhill function, a current motion speed maintaining function, etc. Thus, the animal motion simulator can operate similarly to the motion of real animals. Accordingly, a realistic animal motion simulator can be obtained.

Claims

1. An animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle, the apparatus comprising: a shaft 31 connected to a saddle 13 at an upper portion thereof for up and down rocking the saddle; a up and down rocking shaft 22 which provides the shaft 31 with up and down rocking force, of which axial direction is perpendicular to an axial direction of the shaft 31 , and in which wires for supplying electric power and control signals for controlling a up and down rocking amplitude of the shaft 31 are included; a device 24, 27 mounted to an end of the up and down rocking shaft 22 far away from the shaft 31 for supplying the electric power and the control signals to the rotating shaft 22; a cylindrical screw 25 which is supported by a supporting structure fixed to an end of the up and down rocking shaft 22 close to the shaft 31 and of which axial direction is peφendicular to the axial direction of the up and down rocking shaft 22; a motor 23 which provides electric power for rotating the screw 25 and to which the electric power and control signals are supplied by the wires within the up and down rocking shaft 22; a variable feeding carriage 26 threadedly engaged with the screw 25 for moving toward an axial direction of the screw 25 by means of rotation of the screw 25; and a coupling structure of which an end is rotatably engaged with the variable feeding carriage 26 and of which the other end is coupled with the shaft 31.

2. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 1, wherein the device 24, 27 for supplying the control signals and electric power to the up and down rocking shaft 22 includes a plurality of metallic bands 27 mounted to the up and down rocking shaft 22, and at least an array of metallic terminals 29 electrically contacted with the metallic bands 27 and resiliently supported.

3. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 1, wherein the device 24, 27 for supplying the control signals and electric power to the up and down rocking shaft 22 includes at least an array of metallic terminals mounted to the up and down rocking shaft 22 and resiliently supported, and a cylindrical body in which annular metallic bands electrically connected with the metallic terminals are included and by which a part of the up and down rocking shaft 22 is surrounded.

4. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 1 or 2, wherein the multiple arrays of the metallic terminals are mounted around a circumferential periphery of the up and down rocking shaft 22 to have redundancy.

5. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 1, wherein the device 24, 27 for supplying the control signals and electric power to the up and down rocking shaft 22 is an electric-type rotary connector.

6. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in any one of claims 1, 2, 3 and 5, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting revolution and angular displacement of the up and down rocking shaft 22.

7. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 4, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting revolution and angular displacement of the up and down rocking shaft 22.

8. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in any one of claims 1, 2, 3 and 5, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting a state where the variable feeding carriage 26 is located at a lowest position farthest away from the up and down rocking shaft 22.

9. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 4, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting a state where the variable feeding carriage 26 is located at a lowest position farthest away from the up and down rocking shaft 22.

10. An animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle, the apparatus comprising: a shaft 57 connected to a saddle 13 at an upper portion thereof for up and down rocking the saddle; a up and down rocking shaft 54 which provides the shaft 57 with up and down rocking force, of which axial direction is perpendicular to an axial direction of the shaft 57, and in which an axially cylindrical space is included; an adjusting shaft 51 for varying a up and down rocking amplitude, which is mounted into the cylindrical space of the up and down rocking shaft 54 to be disposed concentrically with the up and down rocking shaft 54; a brake/clutch assembly 59 which is mounted to an end of the adjusting shaft 51 far away from the shaft 57 so that the assembly can operate in a first state where power supplied to the adjusting shaft 51 is cut off and the adjusting shaft 51 is caused to be immobilized, in a second state where power supplied to the adjusting shaft 51 is transmitted and the adjusting shaft 51 is caused to be freely mobilized, and in a third state where power supplied to the adjusting shaft 51 is cut off and the adjusting shaft 51 is caused to be fixedly engaged with the up and down rocking shaft 54; a supporting structure which is fixed at an end of the up and down rocking shaft 54 close to the shaft 57 and through which the adjusting shaft 51 pass; a cylindrical screw 55 which is supported by the supporting structure and of which axial direction is perpendicular to the axial direction of the up and down rocking shaft 54; gear assemblies 52, 53 for enabling the screw 55 to rotate by means of the power of the adjusting shaft 51; a variable feeding carriage 56 threadedly engaged with the screw 55 for moving toward an axial direction of the screw 55 by means of rotation of the screw 55; and a coupling structure 65 of which an end is rotatably engaged with the variable feeding carriage 56 and of which the other end is engaged with the shaft 57.

11. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 10, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting revolution and angular displacement of the up and down rocking shaft 54.

12. The animal motion simulator having up and down rocking amplitude adjusting apparatus of saddle as claimed in claim 10 or 11, wherein the up and down rocking amplitude adjusting apparatus further comprises a detecting device for detecting a state where the variable feeding carriage 56 is located at a lowest position farthest away from the up and down rocking shaft 54.

13. An animal motion simulator having jump apparatus, the apparatus comprising: gears 72, 73 connected with and driven by a motor 70 to rotate at the same rotational speed; first connecting rods 74, 75 fixedly connected with one side ends of shafts of the gears 72, 73, respectively; second connecting rods 76, 77 of which one side ends are rotatably connected with the other side ends of the. first connecting rods 74, 75, respectively; and shafts 78, 79 corresponding to front and rear shafts 121, 111, respectively, which are rotatably connected with the other side ends of the second connecting rods 76, 77 to support a saddle 13, wherein the first connecting rod 74 is set and fixed such that the first connecting rod 74 advances to 90 degrees than the first connecting rod 76.

14. The animal motion simulator having jump apparatus as claimed in claim 13, wherein the jump apparatus further comprises a clutch 80 mounted between the motor 70 and the gears 72, 73 for transmitting or cutting off power of the motor 70, and a brake 81 for immobilizing the gears 72, 73 when the power of the motor is cut off by the clutch 80.

15. The animal motion simulator having jump apparatus as claimed in claim 13 or 14, wherein the jump apparatus further comprises detecting devices for detecting various positional relationships between the shafts 78, 79.

16. The animal motion simulator having jump apparatus as claimed in claim 15, wherein a specific condition of the shafts 78, 79 is maintained when the condition is detected by any one of the detecting devices.

17. An animal motion simulator, characterized in that the shafts 31, 57 of the adjusting apparatus according to claim 1 or 10 correspond to inner shafts

112, 122 and the shafts 78, 79 of the jump apparatus according to claim 14 correspond to outer shafts 111, 121, whereby the inner shafts 112, 122 and the outer shafts 111, 121 are formed to be concentric with each other, and that upper flanges of the inner shafts 112, 122 are caught in upper portions of the outer shafts 111, 121.

18. The animal motion simulator as claimed in claim 17, wherein the inner shafts 112, 122 are engaged with the variable feeding carriage 26, 56 by means of external control signals after the upper flanges of the inner shafts 112, 122 are caused to have been caught in the upper portions of the outer shafts 111, 121, whereby the coupling structures 30, 65 start to run.