Gaming Machines

Abstract

To provide a game machine excellent in operation of a movable member.SOLUTION: A transmission member 640 which transmits a driving force of a first driving device 630 to a performance member 620 and rises the performance member 620 is pivotally supported by a second axis support hole 614 of a base member 610 and joined to the performance member 620, and a length from a joint position of the performance member 620 and the transmission member 640 to the second axis support hole 614 is formed shorter in comparison with a length from a joint position of the performance member 620 and the transmission member 640 to the second axis support hole 614. Thus, even when the performance member 620 is long in a radial direction of the second axis support hole 614, it is possible to suppress a travel amount of a center of gravity of the performance member 620 in the case that the first driving device 630 is operated by a minimum unit of resolution of control by the first driving device 630.SELECTED DRAWING: Figure 53

Description

[Technical field]

[0001] The present invention relates to gaming machines such as pachinko machines. [Background technology]

[0002] In gaming machines such as pachinko machines, Equipped with a movable means There is an amusement machine (Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2012-016623 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the conventional gaming machines described above, From the viewpoint of favoring the movement of the movable means There was a problem that there was room for improvement.

[0005] The present invention has been made to solve the above-mentioned problems, The movement of the movable means can be favorable. The object is to provide a gaming machine. [Means for solving the problem]

[0006] In order to achieve this object, the gaming machine according to claim 1 comprises: The device is provided with a first driving means, a movable means configured to be movable along a predetermined movement locus by the driving force of the first driving means, and a second driving means, and is capable of configuring a first situation in which the predetermined movement means, which is movable upward from a predetermined position by the driving force of the second driving means, abuts against a predetermined part of the movable means moving along the predetermined movement locus, thereby limiting the movement width of the movable means, and a second situation in which the predetermined movement means does not abut against the predetermined part of the movable means, and in the first situation, the predetermined movement means is capable of abutting against a plurality of positions including a first position in the predetermined part or a second position of the predetermined part different from the first position, the movement width of the movable means when the predetermined movement means abuts against the first position is different from the movement width of the movable means when the predetermined movement means abuts against the second position, and the driving mode of the first driving means is different between a case where the first situation is changed to the second situation and a case where the second situation is changed to the first situation. . Effect of the Invention

[0009] According to the gaming machine of claim 1, The movement of the movable means is preferable. It is possible. [Brief description of the drawings]

[0012] [Figure 1] FIG. 1 is a front view of a pachinko machine according to a first embodiment. [Diagram 2] FIG. 2 is a front view of the game board of a pachinko machine. [Diagram 3] FIG. 2 is a rear view of the pachinko machine. [Figure 4] FIG. 2 is a block diagram showing the electrical configuration of the pachinko machine. [Diagram 5] FIG. 2 is an exploded front perspective view of the game board and the operating unit. [Figure 6] FIG. [Figure 7] FIG. [Figure 8] FIG. [Figure 9] FIG. [Figure 10] FIG. [Figure 11] FIG. [Figure 12] FIG. [Figure 13] FIG. 2 is an exploded front perspective view of the panel and the panel lower unit. [Figure 14] FIG. 2 is an exploded front perspective view of the lower panel unit. [Figure 15] 15(a) is a front view of the base member, the first outlet, the second outlet, the left lower plate member and the right lower plate member, and (b) is a cross-sectional view of the base member and the left lower plate member taken along line XVb-XVb in FIG. 15(a). [Figure 16] FIG. 2 is a front perspective view of the vertical movement unit. [Figure 17] FIG. 4 is a rear perspective view of the vertical movement unit. [Figure 18] FIG. 2 is an exploded front perspective view of the vertical movement unit. [Figure 19] FIG. 4 is an exploded rear perspective view of the vertical movement unit. [Figure 20] FIG. [Figure 21] FIG. [Figure 22] FIG. 2 is a front perspective view of the combined action unit. [Figure 23] FIG. 2 is a rear perspective view of the combined action unit. [Figure 24] FIG. 2 is a front exploded perspective view of the combined action unit. [Diagram 25] FIG. 2 is an exploded rear perspective view of the composite action unit. [Figure 26] FIG. 2 is a front exploded perspective view of the telescopic performance device. [Figure 27] FIG. 2 is an exploded rear perspective view of the telescopic performance device. [Figure 28] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Figure 29] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 30] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 31] FIG. 4 is a front view of the pivot arm member and the pivot crank member. [Diagram 32] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 33] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 34] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 35] 4(a) and (b) are front views of a rotating arm member and a rotating crank member. [Diagram 36] 1 is a graph showing the distance of a protrusion from a reference horizontal line. [Figure 37] FIG. [Figure 38] FIG. [Figure 39] FIG. [Diagram 40] FIG. [Diagram 41] FIG. [Diagram 42] FIG. [Diagram 43] FIG. [Diagram 44] FIG. [Diagram 45] FIG. [Figure 46] FIG. 2 is a front perspective view of a tilting operation unit and a sliding operation unit. [Figure 47] FIG. 13 is a rear perspective view of the tilting operation unit and the sliding operation unit. [Figure 48] FIG. 2 is an exploded front perspective view of the slide operation unit. [Figure 49] FIG. 4 is an exploded rear perspective view of the slide operation unit. [Figure 50] FIG. 2 is an exploded front perspective view of the tilt operation unit; [Figure 51] FIG. 2 is an exploded rear perspective view of the tilting operation unit. [Figure 52] 1 is a front exploded perspective view of the performance member and the second drive device. FIG. [Figure 53] 4A and 4B are front views of a transmission member and a torsion spring. [Figure 54] 4(a) and (b) are front views of a transmission member and a torsion spring. [Figure 55] 13 is a schematic diagram showing the swing angle of the performance member relative to the swing angle of the transmission member; FIG. [Figure 56] FIG. 2 is a front view of the tilting motion unit and the sliding motion unit. [Figure 57] FIG. 2 is a front view of the tilting motion unit and the sliding motion unit. [Figure 58] 13(a) and 13(b) are front views of a transmission member and a torsion spring in a second embodiment. [Figure 59] FIG. [Figure 60] 13(a) and 13(b) are front views of a transmission member and a torsion spring in a third embodiment. [Figure 61] 13(a) is a rear perspective view of a transmission member in the fourth embodiment, and FIG. 13(b) is a rear perspective view of a moving contact member. [Figure 62]1A and 1B are rear perspective views of the transmission member, and 1C and 1D are top views of the transmission member. [Figure 63] This is a schematic front view showing the main body member of the performance component. [Figure 64] FIG. [Figure 65] FIG. 13 is a front view of a combined action unit according to a fifth embodiment. [Figure 66] FIG. [Figure 67] FIG. [Figure 68] FIG. [Figure 69] 69(a) is a partial front view of a rotating arm member in the sixth embodiment, (b) is a partial top view of the rotating arm member as viewed in the direction of arrow LXIXb in FIG. 69(a), and (c) is a partial front view of the rotating arm member. [Figure 70] 1A and 1B are front perspective views of a switching device. [Figure 71] 1A and 1B are front views of a composite action unit. [Figure 72] 13(a) and (b) are front views of a tilting action unit in the seventh embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] Hereinafter, an embodiment of the present invention will be described with reference to the attached drawings. First, with reference to Fig. 1 to Fig. 57, an embodiment in which the present invention is applied to a pachinko game machine (hereinafter, simply referred to as a "pachinko machine") 10 will be described as a first embodiment. Fig. 1 is a front view of the pachinko machine 10 in the first embodiment, Fig. 2 is a front view of a game board 13 of the pachinko machine 10, and Fig. 3 is a rear view of the pachinko machine 10.

[0014] As shown in Fig. 1, a pachinko machine 10 has an outer frame 11 in which an outer shell is formed by wooden frames assembled into a substantially rectangular shape, and an inner frame 12 formed in substantially the same external shape as the outer frame 11 and supported so as to be openable and closable relative to the outer frame 11. Metal hinges 18 are attached to the outer frame 11 at two locations, top and bottom, on the left side as viewed from the front (see Fig. 1) in order to support the inner frame 12, and the inner frame 12 is supported so as to be openable and closable toward the front side, with the side where the hinges 18 are provided serving as the axis for opening and closing.

[0015] A game board 13 (see FIG. 2) having a number of nails and winning holes 63, 64, etc., is detachably attached to the back side of the inner frame 12. A pinball game is played by balls (game balls) flowing down the front of the game board 13. The inner frame 12 is equipped with a ball launching unit 112a (see FIG. 4) that launches balls to the front area of ​​the game board 13, a launching rail (not shown) that guides the balls launched from the ball launching unit 112a to the front area of ​​the game board 13, and the like.

[0016] On the front side of the inner frame 12, there is provided a front frame 14 that covers the upper side of the front, and a lower plate unit 15 that covers the lower side. Metal hinges 19 are attached to two locations, top and bottom, on the left side when viewed from the front (see Figure 1), in order to support the front frame 14 and the lower plate unit 15, and the front frame 14 and the lower plate unit 15 are supported so that they can be opened and closed toward the front front side, with the side where the hinges 19 are provided serving as the axis for opening and closing. The locks on the inner frame 12 and the front frame 14 can be released by inserting a special key into the keyhole 21 of the cylinder lock 20 and performing a specified operation.

[0017] The front frame 14 is fitted with decorative resin parts, electrical parts, etc., and has a window 14c formed in a substantially elliptical shape at its approximate center. A glass unit 16 having two glass sheets is disposed on the rear side of the front frame 14, and the front of the game board 13 can be seen from the front side of the pachinko machine 10 through the glass unit 16.

[0018] In the front frame 14, the upper tray 17 for storing balls is formed in a roughly box-like shape with an open top that protrudes to the front side, and prize balls and loan balls are discharged into this upper tray 17. The bottom surface of the upper tray 17 is formed with a downward inclination to the right side when viewed from the front (see FIG. 1), and the balls inserted into the upper tray 17 are guided to the ball launching unit 112a (see FIG. 4) by this inclination. In addition, a frame button 22 is provided on the upper surface of the upper tray 17. This frame button 22 is operated by the player, for example, when changing the stage of the performance displayed on the third pattern display device 81 (see FIG. 2) or when changing the content of the performance of the super reach.

[0019] The front frame 14 is provided with various light-emitting means such as lamps around it (for example, at the corners). The light-emitting modes of these light-emitting means are changed and controlled by lighting or blinking in response to changes in the game state such as when a jackpot is hit or when a predetermined reach is reached, and they play a role in enhancing the presentation effect during the game. The periphery of the window portion 14c is provided with illumination units 29-33 incorporating light-emitting means such as LEDs. In the pachinko machine 10, these illumination units 29-33 function as presentation lamps such as jackpot lamps, and when a jackpot is hit or when a reach is reached, each illumination unit 29-33 lights up or blinks by lighting or blinking the built-in LEDs, thereby informing the player that a jackpot is being hit or that the player is in a reach just before a jackpot is being hit. In addition, the upper left part of the front frame 14 when viewed from the front (see FIG. 1) is provided with an indicator lamp 34 incorporating light-emitting means such as LEDs and capable of indicating that prize balls are being paid out and that an error has occurred.

[0020] Also, a small window 35 is formed by attaching transparent resin to the underside of the right-side illumination unit 32 from the back side so that the back side of the front frame 14 can be seen, and the certificate stamps and the like affixed to the attachment space K1 (see FIG. 2) on the front of the game board 13 can be seen from the front of the pachinko machine 10. Also, in the pachinko machine 10, a plated member 36 made of chrome-plated ABS resin is attached to the area around the illumination units 29-33 to create a more brilliant appearance.

[0021] A ball lending operation unit 40 is disposed below the window portion 14c. The ball lending operation unit 40 is provided with a number display unit 41, a ball lending button 42, and a return button 43. When the ball lending operation unit 40 is operated with bills, cards, etc. inserted into a card unit (ball lending unit) (not shown) arranged on the side of the pachinko machine 10, balls are lent out in response to the operation. Specifically, the number display unit 41 is an area where the remaining balance information of the card, etc. is displayed, and a built-in LED is lit to display the remaining balance in numbers as the remaining balance information. The ball lending button 42 is operated to obtain loan balls based on information recorded on a card, etc. (recording medium), and loan balls are supplied to the upper tray 17 as long as there is a remaining balance on the card, etc. The return button 43 is operated when requesting the return of a card, etc. inserted into the card unit. In addition, in pachinko machines where balls are directly dispensed from a ball dispenser to the upper tray 17 without going through a card unit, i.e., in so-called cash machines, the ball dispensing operation unit 40 is not necessary, but in this case, a decorative sticker or the like may be added to the installation part of the ball dispensing operation unit 40 to make the parts configuration common. It is possible to commonize pachinko machines using a card unit and cash machines.

[0022] The lower tray unit 15, located below the upper tray 17, has a lower tray 50 in the center formed in a roughly box-like shape with an open top for storing balls that cannot be stored in the upper tray 17. On the right side of the lower tray 50, an operating handle 51 is provided which is operated by the player to hit the ball into the front of the game board 13.

[0023] The operation handle 51 includes a touch sensor 51a for permitting the driving of the ball launching unit 112a, a launch stop switch 51b for stopping the launch of balls while the switch is being pressed, and a variable resistor (not shown) for detecting the rotation amount (rotation position) of the operation handle 51 by a change in electrical resistance. When the operation handle 51 is rotated clockwise by a player, the touch sensor 51a is turned on and the resistance value of the variable resistor changes corresponding to the rotation amount, and the ball is launched with a strength (launch strength) corresponding to the resistance value of the variable resistor, so that the ball is shot into the front of the game board 13 with a flight amount corresponding to the operation of the player. When the operation handle 51 is not being operated by the player, the touch sensor 51a and the launch stop switch 51b are turned off.

[0024] A ball removal lever 52 is provided on the lower front part of the lower tray 50 to be operated when discharging the balls stored in the lower tray 50 downward. This ball removal lever 52 is always biased to the right, and by sliding it to the left against this bias, a bottom opening formed on the bottom surface of the lower tray 50 opens, and the balls fall naturally from the bottom opening and are discharged. This ball removal lever 52 is usually operated with a box (commonly called a "senryo box") for receiving the balls discharged from the lower tray 50 placed below the lower tray 50. As described above, the operating handle 51 is disposed on the right side of the lower tray 50, and an ashtray 53 is attached to the left side of the lower tray 50.

[0025] As shown in FIG. 2, the game board 13 is configured by assembling a number of nails (not shown) for guiding balls, a windmill, rails 61, 62, a general winning opening 63, a first winning opening 64, a second winning opening 640, a first variable winning device 65, a second variable winning device 650, a through gate 67, a variable display unit 80, and the like, on a base plate 60 machined into a substantially square shape when viewed from the front, and the peripheral portion is attached to the back side of the inner frame 12 (see FIG. 1). The base plate 60 is made of a light-transmitting resin material, and is formed so that the player can visually recognize various structures arranged on the rear side of the base plate 60 from the front side. The general winning opening 63, the first winning opening 64, the second winning opening 640, the second variable winning device 650, and the variable display unit 80 are arranged in through holes formed in the base plate 60 by router processing, and are fixed from the front side of the game board 13 by tapping screws or the like.

[0026] The front central portion of the game board 13 can be seen from the front side of the inner frame 12 through the window portion 14c (see Fig. 1) of the front frame 14. The configuration of the game board 13 will be described below mainly with reference to Fig. 2. The first variable winning device 65 is disposed in a through hole formed in the base member 310 of the board lower unit 300 by router processing, and is fixed from the front side of the game board 13 by tapping screws or the like.

[0027] An outer rail 62 formed by bending a strip-shaped metal plate into a substantially arc shape is set up on the front of the game board 13, and an inner rail 61 formed of a strip-shaped metal plate similar to the outer rail 62 is set up on the inside of the outer rail 62. The outer rail 61 and the outer rail 62 surround the front outer periphery of the game board 13, and the game board 13 and the glass unit 16 (see FIG. 1) surround the front and rear, forming a game area in front of the game board 13 where games are played based on the behavior of the ball. The game area is an area (an area where winning holes and the like are arranged and where shot balls flow down) that is formed in front of the game board 13 and is partitioned by the two rails 61, 62 and the resin outer edge member 73 that connects the rails.

[0028] The two rails 61, 62 are provided to guide the ball launched from the ball launching unit 112a (see FIG. 4) to the upper part of the game board 13. A return ball prevention member 68 is attached to the tip part of the inner rail 61 (upper left part of FIG. 2) to prevent a ball once guided to the upper part of the game board 13 from returning back into the ball guide passage. A return rubber 69 is attached to the tip part of the outer rail 62 (upper right part of FIG. 2) at a position corresponding to the maximum flight part of the ball, and a ball launched with a certain amount of force or more hits the return rubber 69 and bounces back toward the center while its force is reduced.

[0029] The first symbol display devices 37A and 37B, which are equipped with a plurality of LEDs and a 7-segment display as light-emitting means, are arranged in the lower left side of the game area when viewed from the front (lower left side of FIG. 2). The first symbol display devices 37A and 37B are used to display information according to the controls performed by the main control device 110 (see FIG. 4), and mainly display the game status of the pachinko machine 10. In this embodiment, the first symbol display devices 37A and 37B are configured to be used differently depending on whether the ball has won the first winning hole 64 or the second winning hole 640. Specifically, when the ball has won the first winning hole 64, the first symbol display device 37A is activated, and when the ball has won the second winning hole 640, the first symbol display device 37B is activated.

[0030] The first symbol display devices 37A and 37B use LEDs to indicate whether the pachinko machine 10 is in a special probability, time-saving, or normal state, whether it is fluctuating, whether the stopped symbols correspond to a special probability jackpot, a normal jackpot, or a miss, and the number of reserved balls, while displaying the number of rounds during a jackpot and errors using a 7-segment display device. The LEDs are configured to have different light colors (e.g., red, green, and blue), and the combination of light colors can suggest various game states of the pachinko machine 10 with a small number of LEDs.

[0031] In this pachinko machine 10, a lottery is held when a prize is won in the first prize slot 64 and the second prize slot 640. In the lottery, the pachinko machine 10 judges whether or not a jackpot has been won (jackpot lottery), and if a jackpot has been determined, it also judges the type of jackpot. The types of jackpots that can be judged here include a 15R variable jackpot, a 4R variable jackpot, and a 15R normal jackpot. The first symbol display devices 37A and 37B not only show whether or not the result of the lottery is a jackpot as the stopped symbol after the variation ends, but also show a symbol according to the type of jackpot if a jackpot has been won.

[0032] Here, a "15R probability jackpot" refers to a probability jackpot that transitions to a high probability state after a jackpot with a maximum number of rounds of 15, and a "4R probability jackpot" refers to a probability jackpot that transitions to a high probability state after a jackpot with a maximum number of rounds of 4. Also, a "15R normal jackpot" refers to a jackpot that transitions to a low probability state after a jackpot with a maximum number of rounds of 15, and is in a time-saving state for a predetermined number of variations (for example, 100 variations).

[0033] In addition, the "high probability state" refers to a state in which the probability of a subsequent jackpot is increased as an added value after the jackpot is ended, that is, during a so-called probability fluctuation (during a probability change), in other words, a state of play in which it is easy to transition to a special game state. The high probability state (during a probability change) in this embodiment includes a game state in which the probability of a hit of the second symbol described later is increased and the ball is likely to enter the second winning hole 640. The "low probability state" refers to a time when the probability change is not in progress, and refers to a state in which the probability of a jackpot is in a normal state, that is, a state in which the probability of a jackpot is lower than that in a probability change. In addition, the time-saving state (during time-saving) in the "low probability state" refers to a game state in which the probability of a jackpot is in a normal state and the probability of a jackpot remains the same, only the probability of a hit of the second symbol is increased, and the ball is likely to enter the second winning hole 640. On the other hand, the normal state of the pachinko machine 10 refers to a game state in which the probability of a jackpot is not in a probability change state or a time-saving state (a state in which neither the probability of a jackpot nor the probability of a hit of the second symbol is increased).

[0034] During the probability variation or time reduction, not only does the probability of winning the second symbol increase, but the time for which the electric device 640a associated with the second winning port 640 is opened is also changed and set to a longer time than during normal play. When the electric device 640a is in an open state (open state), the ball is more likely to win the second winning port 640 than when the electric device 640a is in a closed state (closed state). Therefore, during the probability variation or time reduction, the ball is more likely to win the second winning port 640, and the number of times the jackpot lottery is held can be increased.

[0035] In addition, during the probability variation or time reduction, instead of changing the opening time of the electric role 640a associated with the second winning port 640, or in addition to changing the opening time, the number of times the electric role 640a opens with one win may be increased compared to normal. Also, during the probability variation or time reduction, the winning probability of the second symbol may not be changed, and at least one of the time when the electric role 640a associated with the second winning port 640 is opened and the number of times the electric role 640a opens with one win may be changed. Also, during the probability variation or time reduction, the time when the electric role 640a associated with the second winning port 640 is opened and the number of times the electric role 640a opens with one win may not be changed, and only the winning probability of the second symbol may be changed to be increased compared to normal.

[0036] In the game area, a plurality of general winning holes 63 are arranged, through which 5 to 15 balls are paid out as prize balls when a ball wins. In addition, a variable display unit 80 is arranged in the center of the game area. The variable display unit 80 is provided with a third pattern display device 81 consisting of a liquid crystal display (hereinafter simply abbreviated as "display device") that performs a variable display of a third pattern while synchronizing with the variable display in the first pattern display device 37A, 37B, triggered by winning (initial winning) in the first winning hole 64 and the second winning hole 640, and a second pattern display device (not shown) consisting of an LED that displays a variable display of a second pattern, triggered by the passage of a ball through the through gate 67. In addition, a center frame 86 is arranged in the variable display unit 80 so as to surround the outer periphery of the third pattern display device 81.

[0037] The third symbol display device 81 is composed of a large 9-inch liquid crystal display, and the display contents are controlled by the display control device 114 (see FIG. 4), so that, for example, three symbol rows, upper, middle, and lower, are displayed. Each symbol row is composed of a plurality of symbols (third symbols), and these third symbols are scrolled horizontally for each symbol row, so that the third symbols are variably displayed on the display screen of the third symbol display device 81. The third symbol display device 81 of this embodiment performs decorative display according to the display of the first symbol display devices 37A and 37B, while the display of the game state accompanying the control of the main control device 110 (see FIG. 4) is performed by the first symbol display devices 37A and 37B. Note that, instead of a display device, the third symbol display device 81 may be configured using, for example, a reel or the like.

[0038] The second symbol display device performs a variable display in which a "circle" symbol and an "x" symbol as display symbols (second symbol (not shown)) are alternately lit for a predetermined period of time each time the ball passes through the through gate 67. In the pachinko machine 10, when it is detected that the ball has passed through the through gate 67, a winning lottery is held. If the winning lottery results in a winning, the second symbol display device displays a static "circle" symbol after the second symbol is displayed in a variable manner. If the winning lottery results in a losing, the second symbol display device displays a static "x" symbol after the third symbol is displayed in a variable manner.

[0039] The pachinko machine 10 is configured such that when the varying display in the second pattern display device stops at a predetermined pattern (in this embodiment, a "circle" pattern), the electric device 640a attached to the second winning port 640 is activated (opened) for a predetermined period of time.

[0040] The time required for the second symbol to change is set to be shorter during the probability change or time reduction than during the normal game state. As a result, during the probability change and time reduction, the second symbol changes and is displayed in a short time, so that more winning lotteries can be held than during the normal game state. Therefore, since there are more chances to win in the winning lottery, the player can be given more chances to open the electric role 640a of the second winning hole 640. Therefore, during the probability change and time reduction, the second winning hole 640 can be easily entered.

[0041] In addition, if the state is made such that the ball is likely to enter the second winning slot 640 during the probability variation or time reduction by other methods such as increasing the probability of winning or increasing the opening time or number of openings of the electric device 640a for one win during the probability variation or time reduction, the time taken for the second symbol to be displayed may be constant regardless of the game state. On the other hand, if the time taken for the second symbol to be displayed is set shorter during the probability variation or time reduction than during normal play, the probability of winning may be constant regardless of the game state, and the opening time or number of openings of the electric device 640a for one win may be constant regardless of the game state.

[0042] The through gate 67 is attached to the game board on the right side of the lower area of ​​the variable display unit 80, and is configured to allow some of the balls that flow down the right side of the game board out of the balls that are shot to the game board to pass through. When a ball passes through the through gate 67, a lottery is held to determine whether a second symbol will win. After the lottery, a variable display is performed on the second symbol display device, and if the lottery results in a win, a "○" symbol is displayed as the stopping symbol of the variable display, and if the lottery results in a miss, a "X" symbol is displayed as the stopping symbol of the variable display.

[0043] The number of times that the balls pass through the through gate 67 is reserved up to a maximum of four times in total, and the number of reserved balls is displayed by the above-mentioned first symbol display device 37A, 37B, and is also displayed by lighting the second symbol reserved lamp (not shown). Four second symbol reserved lamps are provided, the maximum number of reserved balls, and are arranged symmetrically below the third symbol display device 81.

[0044] In addition, the variable display of the second pattern may be performed by switching on and off a plurality of lamps in the second pattern display device as in this embodiment, or may be performed using a part of the first pattern display device 37A, 37B and the third pattern display device 81. Similarly, the second pattern reserved lamp may be lit by a part of the third pattern display device 81. In addition, the maximum number of reserved balls for the passage of the ball through the through gate 67 is not limited to four times, and may be set to three times or less, or five times or more (e.g., eight times). In addition, the number of the through gates 67 to be assembled is not limited to one, and may be multiple (e.g., two). In addition, the assembly position of the through gate 67 is not limited to the right side of the variable display device unit 80, and may be, for example, the left side of the variable display device unit 80. In addition, since the number of reserved balls is indicated by the first pattern display device 37A, 37B, the second pattern reserved lamp may not be lit.

[0045] A first winning hole 64 into which a ball can win is disposed below the variable display unit 80. When a ball wins into this first winning hole 64, a first winning hole switch (not shown) provided on the back side of the game board 13 is turned on, and when the first winning hole switch is turned on, a lottery for a big win is performed by the main control device 110 (see FIG. 4), and a display according to the lottery result is shown on the first symbol display device 37A.

[0046] On the other hand, a second winning hole 640 into which a ball can win is disposed to the right of the first winning hole 64 as viewed from the front. When a ball wins into this second winning hole 640, a second winning hole switch (not shown) provided on the back side of the game board 13 turns on, and when the second winning hole switch turns on, a lottery for a big win is performed by the main control device 110 (see FIG. 4), and a display according to the lottery result is shown on the first symbol display device 37B.

[0047] In addition, each of the first winning port 64 and the second winning port 640 is also one of the winning ports into which five balls are paid out as prize balls when a ball enters the winning port. In this embodiment, the number of prize balls paid out when a ball enters the first winning port 64 is the same as the number of prize balls paid out when a ball enters the second winning port 640, but the number of prize balls paid out when a ball enters the first winning port 64 and the number of prize balls paid out when a ball enters the second winning port 640 may be different numbers, for example, the number of prize balls paid out when a ball enters the first winning port 64 may be three, and the number of prize balls paid out when a ball enters the second winning port 640 may be five.

[0048] The second winning port 640 is provided with an electric device 640a. This electric device 640a is configured to be openable and closable, and is usually in a closed state (reduced state), making it difficult for the ball to win the second winning port 640. On the other hand, when the second pattern display device displays a "○" pattern as a result of the variable display of the second pattern, which is performed in response to the passage of the ball through the through gate 67, the electric device 640a is in an open state (expanded state), making it easy for the ball to win the second winning port 640.

[0049] As described above, during the probability of winning and the time-saving period, the probability of winning the second symbol is higher than during normal play, and the time it takes for the second symbol to change is also shorter, so the symbol "○" is more likely to be displayed in the change display of the second symbol, and the number of times that the electric device 640a is in the open state (expanded state) increases. Furthermore, during the probability of winning and the time-saving period, the time that the electric device 640a is open is also longer than during normal play. Therefore, during the probability of winning and the time-saving period, it is possible to create a state in which the ball is more likely to win the second winning hole 640 than during normal play.

[0050] Here, the probability of winning a jackpot when a ball enters the first winning slot 64 and when a ball enters the second winning slot 640 is the same in both low and high probability states. However, the probability of a 15R variable jackpot being selected as the type of jackpot when a jackpot occurs is set higher when a ball enters the second winning slot 640 than when a ball enters the first winning slot 64. On the other hand, the first winning slot 64 does not have an electric device like the second winning slot 640, and the ball is always in a state where it can win a jackpot.

[0051] Therefore, under normal circumstances, the electric device associated with the second winning slot 640 is often in a closed state, making it difficult to win at the second winning slot 640. Therefore, it is more advantageous for the player to aim for a jackpot by shooting the ball toward the first winning slot 64, which has no electric device, so that the ball passes to the left of the variable display unit 80 (the so-called "left shot") and aiming for a jackpot by winning at the first winning slot 64, thereby gaining more opportunities to win the jackpot lottery.

[0052] On the other hand, during the special bonus period or the time-saving period, the electric device 640a associated with the second winning slot 640 is likely to be opened by passing the ball through the through gate 67, making it easier to win at the second winning slot 640. Therefore, it is more advantageous for the player to shoot the ball toward the second winning slot 640 so that it passes to the right of the variable display device 80 (the so-called "right hit"), passing through the through gate 67 to open the electric device, and aiming for the ball to win at the second winning slot 640, resulting in a 15R special bonus jackpot.

[0053] In this way, the pachinko machine 10 of this embodiment can allow the player to change the way the ball is shot to "left hit" or "right hit" depending on the game state of the pachinko machine 10 (whether it is in a probability change mode, a time-saving mode, or a normal mode). Therefore, the player can enjoy the game because the way the ball is shot can be changed.

[0054] A first variable winning device 65 is disposed on the lower right side of the first winning hole 64, and a first specific winning hole 65a is disposed in the approximate center thereof. A second variable winning device 650 is disposed on the left side of the variable display device 80, and a second specific winning hole 650a having a circular shape of approximately the same size as the other winning holes 63, 64, 640 is disposed in the approximate center thereof. In the pachinko machine 10, when a jackpot lottery performed due to winning in the first winning hole 64 or the second winning hole 640 becomes a jackpot, after a predetermined time (variable time) has elapsed, the first pattern display device 37A or the first pattern display device 37B is turned on to become a jackpot stop pattern, and a stop pattern corresponding to the jackpot is displayed on the third pattern display device 81, thereby indicating the occurrence of a jackpot. After that, the game state transitions to a special game state (jackpot) in which the ball is likely to win. In this special game state, the specific winning holes 65a, 650a, which are normally closed, are opened for a predetermined time (for example, until 30 seconds have elapsed or until 10 balls have won).

[0055] The specific winning opening 65a, 650a is closed after a predetermined time has elapsed, and after the closing, the specific winning opening 65a, 650a is opened again for a predetermined time. The opening and closing operation of the specific winning opening 65a, 650a can be repeated up to, for example, 15 times (15 rounds). The state in which this opening and closing operation is being performed is one form of a special game state that is advantageous to the player, and the player is paid out a larger amount of prize balls than usual as an addition of game value (game value).

[0056] Specifically, the first variable winning device 65 includes a horizontally long rectangular opening plate that covers the first specific winning hole 65a, and a large opening solenoid 65b (see FIG. 15, only the outline is shown) for driving the opening and closing to the right side with the lower side of the opening and closing plate as an axis. The first specific winning hole 65a is normally in a closed state in which a ball cannot win or it is difficult to win. In the event of a big win, the large opening solenoid 65b is driven to tilt the opening and closing plate to the front side, temporarily forming an open state in which a ball can easily win the first specific winning hole 65a, and it operates to alternate between the open state and the normal closed state.

[0057] Specifically, the second variable winning device 650 includes a triangular opening plate arranged to the left of the second specific winning opening 650a when viewed from the front, and a large opening solenoid (not shown) for driving the opening and closing to the left with the lower side of the opening and closing plate as an axis. The second specific winning opening 650a is normally in a closed state in which the ball cannot win or is difficult to win. In the event of a big win, the small opening solenoid is driven to tilt the opening and closing plate to the left, temporarily forming an open state in which the ball is easy to win in the second specific winning opening 650a, and the open state and the normal closed state are alternately repeated.

[0058] In this embodiment, it is possible to make the ball enter the second variable winning device 650 by hitting it with the left hand, eliminating the hassle of having to switch between hitting with the left hand and hitting with the right hand every time the game state changes.

[0059] The special game state is not limited to the above-mentioned form. A large opening opening that is opened and closed separately from the specific winning opening 65a, 650a may be provided in the game area, and when an LED corresponding to a big win is lit in the first pattern display device 37A, 37B, the specific winning opening 65a, 650a is opened for a predetermined time, and a large opening opening provided separately from the specific winning opening 65a, 650a is opened for a predetermined time and a predetermined number of times when a ball enters the specific winning opening 65a, 650a while the specific winning opening 65a, 650a is open, forming a game state as a special game state. Also, the specific winning opening 65a, 650a is not limited to one, and one or more than two (for example, three) may be provided, and the location of the location is not limited to the lower right side of the first winning opening 64 or the left side of the variable display device 80, but may be, for example, below the first winning opening 64.

[0060] An attachment space K1 for attaching stamps, identification labels, etc. is provided in the right corner of the lower side of the game board 13, and the stamps, etc. attached to the attachment space K1 can be viewed through a small window 35 in the front frame 14 (see Figure 1).

[0061] The game board 13 is provided with a first outlet 314 and a second outlet 315. A ball that flows down the game area and does not win in any of the winning holes 63, 64, 65a, 640, 650a is guided to a ball discharge path (not shown) through the first outlet 314 or the second outlet 315. The first outlet 314 is disposed below the left side of the first winning hole 64, while the second outlet 315 is disposed below the right side of the first winning hole 64. That is, the second outlet 315 is disposed on the opposite side of the first outlet 314 across the first winning hole 64.

[0062] Therefore, balls flowing down the play area and reaching the lower end of the play area (inner rail 61 or outer edge member 73) to the right of the first winning opening 64 when viewed from the front (right side in Figure 2) flow down along the slope of the inner rail 61 or outer edge member 73 and are guided through the second outlet 315 to the ball discharge path, while balls that reach the lower end of the play area (inner rail 61) to the left of the first winning opening 64 when viewed from the front flow down along the slope (curve) of the inner rail 61 and are guided through the first outlet 314 to the ball discharge path.

[0063] A large number of nails are set on the game board 13 in order to appropriately distribute and adjust the direction in which the balls fall, and various components (gimmicks) such as windmills are also provided.

[0064] As shown in Fig. 3, the rear side of the pachinko machine 10 is mainly equipped with control board units 90, 91 and a back pack unit 94. The control board unit 90 is unitized with a main board (main control device 110), a voice lamp control board (voice lamp control device 113) and a display control board (display control device 114). The control board unit 91 is unitized with a payout control board (payout control device 111), a launch control board (launch control device 112), a power supply board (power supply device 115) and a card unit connection board 116.

[0065] The back pack unit 94 is a unit formed by the back pack 92 forming the protective cover and the payout unit 93. In addition, each control board is equipped with an MPU as a one-chip microcomputer that controls each part, a port for communicating with various devices, a random number generator used in various lotteries, a clock pulse generating circuit used for time counting and synchronization, etc. as necessary.

[0066] The main control device 110, the voice lamp control device 113 and the display control device 114, the payout control device 111 and the launch control device 112, the power supply device 115, and the card unit connection board 116 are each stored in the board boxes 100 to 104. The board boxes 100 to 104 each include a box base and a box cover that covers the opening of the box base, and the box base and the box cover are connected to each other to store the respective control devices and boards.

[0067] In addition, the board box 100 (main control device 110) and the board box 102 (dispensing control device 111 and launch control device 112) are connected (connected by a crimping structure) between the box base and the box cover by a sealing unit (not shown). In addition, a sealing seal (not shown) is affixed to the connection between the box base and the box cover, spanning the box base and the box cover. This sealing seal is made of a brittle material, and if an attempt is made to peel off the sealing seal to open the board box 100, 102 or to forcefully open the board box 100, 102, it will be cut into the box base side and the box cover side. Therefore, by checking the sealing unit or the sealing seal, it is possible to know whether the board box 100, 102 has been opened.

[0068] The payout unit 93 includes a tank 130 located at the top of the back pack unit 94 and opening upward, a tank rail 131 connected to the bottom of the tank 130 and gently inclined toward the downstream side, a case rail 132 connected vertically to the downstream side of the tank rail 131, and a payout device 133 provided at the most downstream part of the case rail 132 and paying out balls by a predetermined electrical configuration of a payout motor 216 (see FIG. 4). The tank 130 is successively replenished with balls supplied from the island equipment of the game hall, and the payout device 133 appropriately pays out the required number of balls. A vibrator 134 for applying vibration to the tank rail 131 is attached to the tank rail 131.

[0069] In addition, the payout control device 111 is provided with a state recovery switch 120, the launch control device 112 is provided with a variable resistor operation knob 121, and the power supply device 115 is provided with a RAM erase switch 122. The state recovery switch 120 is operated to resolve ball jams (return to normal state) when a payout error occurs, such as ball jamming in the payout motor 216 (see FIG. 4). The operation knob 121 is operated to adjust the launch force of the launch solenoid. The RAM erase switch 122 is operated when the power is turned on to return the pachinko machine 10 to its initial state.

[0070] Next, the electrical configuration of the pachinko machine 10 will be described with reference to Fig. 4. Fig. 4 is a block diagram showing the electrical configuration of the pachinko machine 10.

[0071] The main control device 110 is equipped with an MPU 201 as a one-chip microcomputer that is a calculation device. The MPU 201 has a ROM 202 that stores various control programs and fixed value data executed by the MPU 201, a RAM 203 that is a memory for temporarily storing various data when executing the control programs stored in the ROM 202, and various other circuits such as an interrupt circuit, a timer circuit, and a data transmission / reception circuit. In the main control device 110, the MPU 201 executes the main processes of the pachinko machine 10, such as a jackpot lottery, display settings in the first symbol display devices 37A and 37B and the third symbol display device 81, and a lottery for the display result in the second symbol display device.

[0072] In addition, in order to instruct sub-control devices such as the dispensing control device 111 and the voice lamp control device 113 to operate, various commands are sent from the main control device 110 to the sub-control devices via a data transmission / reception circuit, but such commands are sent only in one direction, from the main control device 110 to the sub-control devices.

[0073] The RAM 203 has various areas, counters, flags, a stack area in which the contents of the internal registers of the MPU 201 and the return addresses of the control programs executed by the MPU 201 are stored, and a work area (working region) in which various flags, counters, I / O values, etc. are stored. The RAM 203 is configured so that it can retain (back up) data by receiving a backup voltage from the power supply device 115 even after the power supply to the pachinko machine 10 is cut off, and all data stored in the RAM 203 is backed up.

[0074] When the power supply is cut off due to a power outage or the like, the stack pointer and the values ​​of each register at the time of the power outage (including the time of the power outage; the same applies below) are stored in the RAM 203. On the other hand, when the power supply is turned on (including the time of the power supply being turned on due to the power outage being resolved; the same applies below), the state of the pachinko machine 10 is restored to the state before the power supply was cut off based on the information stored in the RAM 203. Writing to the RAM 203 is executed by the main processing (not shown) when the power supply is cut off, and the restoration of each value written to the RAM 203 is executed in the start-up processing (not shown) when the power supply is turned on. Note that the NMI terminal (non-maskable interrupt terminal) of the MPU 201 is configured to receive a power outage signal SG1 from the power outage monitoring circuit 252 when the power supply is cut off due to a power outage or the like, and when the power outage signal SG1 is input to the MPU 201, an NMI interrupt processing (not shown) is immediately executed as a processing during a power outage.

[0075] An input / output port 205 is connected to the MPU 201 of the main control device 110 via a bus line 204 consisting of an address bus and a data bus. The input / output port 205 is connected to the payout control device 111, the voice lamp control device 113, the first symbol display device 37A, 37B, the second symbol display device, the second symbol reservation lamp, a large opening solenoid for driving the opening and closing of the specific winning port 65a to the front side with the lower side of the opening and closing plate as an axis, a solenoid for driving the electric role, and the like, and the MPU 201 transmits various commands and control signals to these via the input / output port 205.

[0076] In addition, the input / output port 205 is connected to various switches 208 consisting of a group of switches not shown and a group of sensors including a slide position detection sensor S and a rotation position detection sensor R, and a RAM erasure switch circuit 253 described below that is provided in the power supply device 115, and the MPU 201 performs various processes based on the signals output from the various switches 208 and the RAM erasure signal SG2 output from the RAM erasure switch circuit 253.

[0077] The payout control device 111 drives a payout motor 216 to control the payout of prize balls and loan balls. The MPU 211, which is a calculation device, has a ROM 212 that stores a control program executed by the MPU 211, fixed value data, etc., and a RAM 213 used as a work memory, etc.

[0078] The RAM 213 of the payout control device 111, like the RAM 203 of the main control device 110, has a stack area in which the contents of the internal registers of the MPU 211 and the return address of the control program executed by the MPU 211 are stored, and a work area (working area) in which the values ​​of various flags, counters, I / O, etc. are stored. The RAM 213 is configured to be able to hold (back up) data by being supplied with a backup voltage from the power supply device 115 even after the power supply of the pachinko machine 10 is cut off, and all data stored in the RAM 213 is backed up. In addition, like the MPU 201 of the main control device 110, the NMI terminal of the MPU 211 is configured to receive a power outage signal SG1 from the power outage monitoring circuit 252 when the power supply is cut off due to a power outage or the like, and when the power outage signal SG1 is input to the MPU 211, an NMI interrupt process (not shown) is immediately executed as a power outage process.

[0079] An input / output port 215 is connected to the MPU 211 of the payout control device 111 via a bus line 214 consisting of an address bus and a data bus. The input / output port 215 is connected to the main control device 110, the payout motor 216, the launch control device 112, and the like. Although not shown, the payout control device 111 is connected to a prize ball detection switch for detecting the paid-out prize balls. The prize ball detection switch is connected to the payout control device 111 but is not connected to the main control device 110.

[0080] The launch control device 112 controls the ball launch unit 112a so that the ball is launched with a strength corresponding to the amount of rotation of the operating handle 51 when the main control device 110 issues an instruction to launch a ball. The ball launch unit 112a is equipped with a launch solenoid and an electromagnet (not shown), and the launch solenoid and the electromagnet are permitted to be driven when a predetermined condition is met. Specifically, the touch sensor 51a detects that the player is touching the operating handle 51, and on condition that the launch stop switch 51b for stopping the launch of the ball is off (not operated), the launch solenoid is excited in response to the amount of rotation (rotation position) of the operating handle 51, and the ball is launched with a strength corresponding to the amount of operation of the operating handle 51.

[0081] The voice lamp control device 113 controls the output of voice in the voice output device (such as a speaker not shown) 226, the output of turning on and off the lamp display device (such as the illumination unit 29 to 33 and the display lamp 34) 227, and the setting of the display mode of the third pattern display device 81 performed by the display control device 114, such as variable performance (variable display) and advance notice performance. The MPU 221, which is a calculation device, has a ROM 222 that stores the control program executed by the MPU 221, fixed value data, etc., and a RAM 223 used as a work memory, etc.

[0082] An input / output port 225 is connected to the MPU 221 of the voice and lamp control device 113 via a bus line 224 consisting of an address bus and a data bus. The main control device 110, the display control device 114, the voice output device 226, the lamp display device 227, other devices 228, the frame button 22, etc. are connected to the input / output port 225. The other devices 228 include the drive motors 431, 466, 531, 561, 631, 661, and 751.

[0083] The voice lamp control device 113 determines the display mode of the third symbol display device 81 based on various commands (variation pattern command, stop type command, etc.) received from the main control device 110, and notifies the display control device 114 of the determined display mode by commands (display variation pattern command, display stop type command, etc.). In addition, the voice lamp control device 113 monitors input from the frame button 22, and when the frame button 22 is operated by the player, instructs the display control device 114 to change the stage displayed on the third symbol display device 81 or change the performance content at the time of super reach. When the stage is changed, a rear image change command including information on the changed stage is transmitted to the display control device 114 so that the third symbol display device 81 displays a rear image corresponding to the changed stage. Here, the rear image is an image displayed on the rear side of the third symbol, which is the main image to be displayed on the third symbol display device 81. The display control device 114 displays various images on the third symbol display device 81 according to the command transmitted from this voice lamp control device 113.

[0084] Also, the voice lamp control device 113 receives a command (display command) representing the display content of the third pattern display device 81 from the display control device 114. Based on the display command received from the display control device 114, the voice lamp control device 113 outputs a sound corresponding to the display content of the third pattern display device 81 from the voice output device 226 in accordance with the display content, and also controls the turning on and off of the lamp display device 227 in accordance with the display content.

[0085] The display control device 114 is connected to the voice lamp control device 113 and the third pattern display device 81, and controls the display of the third pattern display device 81, such as the variable performance of the third pattern, based on the command received from the voice lamp control device 113. The display control device 114 also transmits a display command to notify the display content of the third pattern display device 81 to the voice lamp control device 113 as appropriate. The voice lamp control device 113 can match the display of the third pattern display device 81 with the audio output from the audio output device 226 by outputting audio from the audio output device 226 in accordance with the display content indicated by the display command.

[0086] The power supply device 115 has a power supply unit 251 for supplying power to each unit of the pachinko machine 10, a power failure monitoring circuit 252 for monitoring power interruption due to a power failure or the like, and a RAM deletion switch circuit 253 provided with a RAM deletion switch 122 (see FIG. 3). The power supply unit 251 is a device that supplies the necessary operating voltage to each of the control devices 110-114, etc. through a power supply path not shown. In summary, the power supply unit 251 takes in an AC voltage of 24 volts supplied from the outside, generates a voltage of 12 volts for driving various switches such as the various switches 208, solenoids such as the solenoid 209, motors, etc., a voltage of 5 volts for logic, a backup voltage for RAM backup, etc., and supplies the necessary voltages to each of the control devices 110-114, etc.

[0087] The power failure monitoring circuit 252 is a circuit for outputting a power failure signal SG1 to each NMI terminal of the MPU 201 of the main control device 110 and the MPU 211 of the dispensing control device 111 when the power is cut off due to the occurrence of a power failure or the like. The power failure monitoring circuit 252 monitors the voltage of 24 volts DC, which is the maximum voltage output from the power supply unit 251, and when this voltage becomes less than 22 volts, it judges that a power failure (power failure, power cut) has occurred and outputs the power failure signal SG1 to the main control device 110 and the dispensing control device 111. By outputting the power failure signal SG1, the main control device 110 and the dispensing control device 111 recognize the occurrence of a power failure and execute NMI interrupt processing. Note that the power supply unit 251 is configured to maintain the output of the voltage of 5 volts, which is the drive voltage of the control system, at a normal value for a sufficient time to execute the NMI interrupt processing, even after the voltage of 24 volts DC becomes less than 22 volts. Therefore, the main control unit 110 and the dispensing control unit 111 can normally execute and complete the NMI interrupt processing (not shown).

[0088] The RAM clear switch circuit 253 is a circuit for outputting a RAM clear signal SG2 to the main control device 110 to clear the backup data when the RAM clear switch 122 (see FIG. 3) is pressed. When the main control device 110 inputs the RAM clear signal SG2 when the pachinko machine 10 is powered on, it clears the backup data and transmits a payout initialization command to the payout control device 111 to clear the backup data in the payout control device 111.

[0089] Next, the game board 13 and the operating unit 200 will be described with reference to Figures 5 to 12. First, the structure for housing the units 300 to 700 in the rear case 210 will be described with reference to Figures 5 to 7.

[0090] Fig. 5 is an exploded front perspective view of the game board 13 and the operation unit 200, and Fig. 6 and Fig. 7 are exploded front perspective views of the operation unit 200 viewed from the front. Note that Fig. 7 illustrates a state in which the composite operation unit 500 is attached to the rear case 210.

[0091] As shown in Fig. 5 to Fig. 7, the operating unit 200 includes a bottom wall portion 211 and an outer wall portion 212 erected from the outer edge of the bottom wall portion 211, and a rear case 210 formed in a box shape with one side (the front side of the paper surface of Fig. 6) open from the bottom wall portion 211. The rear case 210 is formed in a rectangular frame shape when viewed from the front by forming a rectangular opening 211a at the center of the bottom wall portion 211. The opening 211a is formed to a size corresponding to the outer shape of the third pattern display device 81 (see Fig. 2) (i.e., the third pattern display device 81 can be arranged).

[0092] The operation unit 200 is configured as one unit by accommodating a vertical operation unit 400, a composite operation unit 500, a tilt operation unit 600, and a sliding operation unit 700 in the internal space of a rear case 210.

[0093] Specifically, the composite action unit 500 is disposed in the upper right part of the area formed by the inner surface of the outer wall portion 212 of the rear case 210 (see FIG. 7). In contrast to the state shown in FIG. 7, the tilt action unit 600 and the slide action unit 700 are disposed in the lower part of the area formed by the inner surface of the outer wall portion 212 of the rear case 210. Also, in contrast to the state shown in FIG. 7, the up-down action unit 400 is disposed in a stacked state on the front side of the composite action unit 500, and is housed in the rear case 210 (see FIG. 5).

[0094] Thus, in this embodiment, a specified operational unit (e.g., composite operational unit 500) is arranged in a stacked state with other operational units (e.g., up / down operational unit 400) superimposed on the front side, so that the specified operational unit can be shielded by the other operational units when viewed from the front.

[0095] In other words, when the game board 13 (see FIG. 2) is made of a light-transmitting material and the operation units arranged on the back side of the game board 13 are visible to the player, it is possible to make only the necessary parts of a specific operation unit visible to the player, and to block the other parts from the player by the other operation units. This makes it possible to improve the freedom of design for the specific performance members that are blocked by the other operation units, since it is not necessary to design them on the premise that they will be entirely visible to the player.

[0096] Next, with reference to Figures 8 to 10, an outline of the operation modes of the vertical operation unit 400, the composite operation unit 500, the tilt operation unit 600, and the slide operation unit 700 will be described. In the explanation of Figures 8 to 10, Figures 5 to 7 will also be referred to as appropriate.

[0097] 8 to 10 are front views of the operation unit 200. Note that Fig. 8 shows a state in which the arm member 440 (see Fig. 18) of the up-down operation unit 400 is arranged in a projected position, Fig. 9 shows a state in which the extension and retraction performance device 540 (see Fig. 26) of the composite operation unit 500 is in an extended state, and Fig. 10 shows a state in which the tilt operation unit 600 is arranged in approximately the center in the width direction.

[0098] As shown in Fig. 8, the vertical movement unit 400 moves the arm member 440 (see Fig. 18) between the retracted position shown in Fig. 5 and the extended position shown in Fig. 8. In the retracted position shown in Fig. 5, the arm member 440 is retracted above the opening 211a of the rear case 210 and is not visible to the player (see Fig. 2). On the other hand, in the extended position shown in Fig. 8, the arm member 440 is lowered and the lens member 460 (see Fig. 18) is positioned in the center of the opening 211a of the rear case 210 (i.e., in front of the third pattern display device 81, see Fig. 2).

[0099] As shown in Fig. 9, the composite operation unit 500 can form an extended state in which the pivot arm member 550 (see Fig. 22) is disposed in a projecting position projecting downward and the front plate member 546 is disposed in the center of the opening 211a of the rear case 210 (i.e., in front of the third pattern display device 81, see Fig. 2), and a contracted state (see Fig. 5) in which the pivot arm member 550 is disposed in a retracted position retracted upward and the front plate member 546 is retracted above the opening 211a of the rear case 210. In the contracted state shown in Fig. 5, the front plate member 546 is retracted above the opening 211a of the rear case 210 and is not visible to the player (see Fig. 2).

[0100] As shown in Fig. 10, the tilting operation unit 600 can be moved between the retracted position shown in Fig. 5 and the extended position shown in Fig. 10 by sliding the support member 720 (see Fig. 47) of the sliding operation unit 700 left and right. In the retracted position shown in Fig. 5, the tilting operation unit 600 is retracted to the right outside of the opening 211a of the rear case 210 and is visible to the player inside the center frame 86 (see Fig. 2). On the other hand, in the extended position shown in Fig. 10, the tilting operation unit 600 is disposed in the center of the opening 211a of the rear case 210 (i.e., in front of the third pattern display device 81, see Fig. 2).

[0101] In addition, Fig. 10 illustrates a state in which the first curtain member 624 and the second curtain member 625 (see Fig. 46) are opened and the liquid crystal device inside is visible. That is, when the tilting operation unit 600 is arranged in the state of Fig. 10, the player can see both the performance displayed on the third pattern display device 81 (see Fig. 2) visible through the opening 211a and the performance displayed on the liquid crystal device inside the tilting operation unit 600.

[0102] These operation units 400-700 are formed so as to be able to operate independently, and are arranged in a state of being overlapped (stacked) as described above, so that operation units 400-700 arranged in different layers can be operated simultaneously even if the operation members protrude inwardly of the opening 211a of the rear case 210. That is, as illustrated in Figs. 8 to 10, not only can each of the operation units 400-700 be operated individually, but these operations can also be combined, thereby enhancing the presentation effect.

[0103] Fig. 11 is a front view of the operation unit 200. In Fig. 11, the telescopic performance device 540 (see Fig. 22) of the composite operation unit 500 is in an extended state, the arm member 440 and the lens member 460 of the vertical operation unit 400 are disposed in the extended position, and the door member 470 is in an open state.

[0104] 11, the front plate member 546 of the composite motion unit 500 is visible through the lens member 460 of the vertical motion unit 400. Since the lens member 460 is formed with a magnifying lens processing as described later, the front plate member 546 is viewed in a magnified manner.

[0105] That is, from the state shown in Fig. 11, when the rotating plate 520 (see Fig. 24) of the composite operation unit 500 is swung about the first shaft portion 512 (see Fig. 24) and the front plate member 546 is moved to a position (see Fig. 39) separated from the lens member 470 of the up-down operation unit 400 in a front view, the front plate member 546 is viewed at normal size. This makes it possible to switch between a state in which the front plate member 546 is viewed at normal size and a state in which it is viewed enlarged (see Fig. 11), thereby improving the presentation effect.

[0106] FIG. 12 is a front view of the motion unit 200. FIG. 12 illustrates a state in which the telescopic performance device 540 (see FIG. 22) of the composite motion unit 500 is in an extended state, the tilt motion unit 600 is placed at a retracted position and in a tilted state, and the tilt motion unit 600 and the front plate member 546 are immediately before coming into contact with each other. The tilt motion unit 600 is further tilted, so that the tilt motion unit 600 and the front plate member 546 come into contact with each other. In this case, by swinging the composite motion unit 500 clockwise as viewed from the front (see FIG. 39), it is possible to perform a performance in which it appears as if a force is applied from the tilt motion unit 600 to the composite motion unit 500 (the motions of the units can be associated with each other to perform a more complicated performance). This can improve the performance effect.

[0107] Next, the board lower unit 300 will be described with reference to Fig. 13 to Fig. 15. Fig. 13 is an exploded front perspective view of the board 13 and the board lower unit 300. As shown in Fig. 13, a receiving opening 13a is formed in the lower part of the game board 13, which is opened along the lower edge of the inner rail 61 and through which the board lower unit 300 is inserted.

[0108] Fig. 14 is an exploded front perspective view of the board lower unit 300. As shown in Fig. 14, the board lower unit 300 mainly includes a base member 310 that is fitted and fixed to the receiving opening 13a of the game board 13, a left lower plate member 320 that is disposed on the lower left side of the base member 310 when viewed from the front and guides balls to the first outlet 314, a right lower plate member 330 that is disposed on the lower right side of the base member 310 when viewed from the front and guides balls to the second outlet 315, and a front cover member 340 that is fastened and fixed to the base member 310 from the front and supports the left lower plate member 320 and the right lower plate member 330 with an insertion shaft 343.

[0109] The base member 310 mainly comprises a plate-shaped main body 311 which is formed with a cross-sectional shape that is approximately the same as the shape of the receiving opening 13a of the game board 13 and slightly smaller than the receiving opening 13a, a decorative front panel portion 312 which is formed in a thin plate shape so as to cover the front side of the main body portion 311, a movable performance member 313 which is attached to approximately the center of the width of the decorative front panel portion 312, a first outlet 314 which is a rectangular hole formed on the left side of the movable performance member 313 when viewed from the front, and a second outlet 315 which is a rectangular hole formed on the right side of the movable performance member 313 when viewed from the front.

[0110] The movable performance member 313 is provided at the lower edge of the widthwise center of the game board 13, and includes a rotating performance member 313a that is rotated by a drive device (not shown). If an outlet is provided at the lower edge of the widthwise center of the game board 13, the movable performance member 313 cannot be provided at the lower edge of the widthwise center of the game board 13. In this embodiment, an outlet is not provided at the lower edge of the widthwise center of the game board 13, and the first outlet 314 and the second outlet 315 are provided at positions spaced apart from the center of the game board 13 to the left and right, thereby ensuring space for providing the movable performance member 313 at the lower edge of the widthwise center of the game board 13.

[0111] The shapes of the first outlet 314, the second outlet 315, the left lower plate member 320, and the right lower plate member 330 will be described with reference to Fig. 15. Fig. 15(a) is a front view of the base member 310, the first outlet 314, the second outlet 315, the left lower plate member 320, and the right lower plate member 330, and Fig. 15(b) is a cross-sectional view of the base member 310 and the left lower plate member 320 taken along line XVb-XVb in Fig. 15(a). Fig. 15(a) also illustrates the outer shape of the front cover member 340 fastened and fixed to the base member 310, and nails formed above the first outlet 314 and the second outlet 315.

[0112] The first outlet 314 and the second outlet 315 are openings through which balls are discharged from the play area. The second outlet 315 is formed to have a shorter width than the first outlet 314. The reason for this will be described later. In addition, a guide rib 315a is formed on the upper inner surface of the second outlet 315, extending in the front-rear direction. The guide rib 315a can suppress the resistance applied to the ball when the ball flows into the second outlet 315 and bounces high and collides with the upper bottom surface of the second outlet 315. In addition, the flow of the balls discharged from the second outlet 315 can be adjusted in the front-rear direction, suppressing the variation in the direction of the discharged balls.

[0113] In addition, the buffer rib 322 of the left lower plate member 320 described later is formed higher toward the widthwise center of the game board 13 (see FIG. 13) (see FIG. 15(a)). As a result, even in this embodiment in which the vertical width of the play area increases toward the widthwise center of the game board 13, the effect of suppressing the rebound of a ball falling on the left lower plate member 320 is not lost. That is, the closer to the widthwise center of the game board 13, the higher the ball falls, so there is a risk of a large impact when the fallen ball collides with the left lower plate member 320. In contrast, the buffer rib 322 is formed higher toward the widthwise center of the game board 13, so that the degree of the cushioning effect that softens the impact of the fall can be increased by the buffer rib 322 bending closer to the widthwise center of the game board 13.

[0114] Here, the relationship between the aspect ratio of the buffer ribs 322, 332 and the landing frequency of the falling ball will be explained. For example, if the falling height of the ball that lands on the buffer ribs 322, 332 is high, but the frequency of the ball reaching that position is extremely low, there are cases where the ejection of other balls is not hindered even if the rebound of the ball is not suppressed. If the aspect ratio of the buffer ribs 322, 332 is formed large even in this case, the space of the play area will be unnecessarily suppressed. Therefore, it is preferable that the aspect ratio of the buffer ribs 322, 332 is set not only based on the falling height of the ball, but also based on the relationship between the falling height and the frequency of the ball landing at that position.

[0115] As shown in Fig. 15, a ball flowing down above the buffer ribs 322, 332 starts on paths c1, c2, then passes through multiple branches b1-b10 and reaches the landing areas z0-z4. In the following explanation, we will assume that the probability of the ball flowing down is equal (1 / 2) for paths c1 and c2, and that the probability of branching to the left or right at branches b1-b10 is equal (1 / 2) for each. We will also assume that the ball will never flow down from the upper right.

[0116] The probability that the ball will reach the landing area z0 will be explained. In order to reach the landing area z0, it is necessary to flow down the left side at branch b5 and reach path c11. To reach branch b5, it is possible to reach it from path c1 via branch b1, or from path c2. Therefore, the probability that the ball will reach path c11 and reach the landing area z0 is expressed as the sum of the probability of the ball flowing down from path c1, 1 / 8 (= 1 / 2 × (1 / 2) ^ 2), and the probability of the ball flowing down from path c2, 1 / 4 (= 1 / 2 × 1 / 2), so it is 3 / 8 ("^" means exponentiation). In other words, each probability is expressed as the product of the probability 1 / 2 that the ball will flow down the paths c1 and c2, and the number of branches b1 to b10 through which the ball will pass before reaching the landing area z0, raised to the power of 1 / 2.

[0117] The probability that the ball will reach the landing area z1 will be explained. To reach the landing area z1, the ball must flow down the left side at branch b3 to reach path c15, or flow down the left side at branch b4 to reach path c16, or flow down the right side at branch b6 to reach path c14, or flow down the right side at branch b7 to reach path c13.

[0118] Up to branch b3, only the case where the ball flows down from path c1 is possible, and there are three branches before the ball reaches path c15, so the probability that the ball reaches path c15 is 1 / 16 (=1 / 2×(1×2)^3). Also, up to branch b4, only the case where the ball flows down from path c1 is possible, and there are four branches before the ball reaches path c16, so the probability that the ball reaches path c16 is 1 / 32 (=1 / 2×(1×2)^4). Also, up to branch b6, only the case where the ball flows down from path c1 is possible, and there are three branches before the ball reaches path c14, so the probability that the ball reaches path c14 is 1 / 16 (=1 / 2×(1×2)^3).

[0119] Up to branch b7, both the case where the ball flows down from path c1 and path c2 are possible, and there are cases where the ball flows down from path c1 and has four branches before it reaches path c13, and cases where there are three branches. There are two branches before the ball flows down from path c2 and reaches path c13. Therefore, the probability that the ball will reach path c13 is 7 / 32, which is the sum of the probability of the ball flowing down from path c1, 3 / 32 (=1 / 2×(1 / 2)^4+1 / 2×(1 / 2)^3), and the probability of the ball flowing down from path c2, 1 / 8 (=1 / 2×(1 / 2)^2).

[0120] Here, the probability that the ball will reach the landing area z1 is the sum of the probabilities that the ball will reach the above-mentioned paths c13 to c16, and is therefore 12 / 32.

[0121] The probability that the ball will reach the landing area z2 will be explained. The probability that the ball will reach the landing area z2 can be expressed as the probability that the ball will reach the path c12, which is equal to the probability that the ball that has reached the branch b7 will reach the path c13. Therefore, the probability that the ball will reach the landing area z2 is 7 / 32.

[0122] The probability that the ball will reach the landing area z3 will be described below. To reach the landing area z3, the ball needs to flow down the left side at branch b9 to reach path c17, or flow down the left side at branch b10 to reach path c18.

[0123] Up to branch b9, only the case where the ball flows down from path c1 is possible, and since there are six branches before the ball reaches path c17, the probability that the ball reaches path c17 is 1 / 128 (= 1 / 2 x (1 x 2) ^ 6). Also, up to branch b10, only the case where the ball flows down from path c1 is possible, and since there are seven branches before the ball reaches path c18, the probability that the ball reaches path c18 is 1 / 256 (= 1 / 2 x (1 x 2) ^ 7).

[0124] The probability that the ball will reach the landing area z3 is the sum of the probabilities that the ball will reach the above-mentioned paths c17 and c18, and is therefore 3 / 256.

[0125] The probability of a ball reaching landing area z4 will be explained. To reach landing area z4, the ball needs to flow down the right side of branch b10 and reach path c19. Note that all balls that flow down the right side of branch b10 will flow down path c19. The probability of a ball reaching path c19 is equal to the probability that a ball that has reached branch b10 will reach path c18. Therefore, the probability of a ball reaching landing area z4 is 1 / 256 (= 1 / 2 × (1 × 2)^7).

[0126] From these facts, the ratio of balls arriving at each landing zone z0 to z4 is (z0:z1:z2:z3:z4)=(96:96:56:3:1). This ratio is correlated with the cushioning ribs 322, 332.

[0127] For example, when comparing landing area z1 and landing area z3, the height of the balls falling in each landing area z1 and z3 is the same, but the aspect ratio of the buffer ribs 322, 332 in landing area z3 is smaller than that in landing area z1. This is because the rate at which balls reach landing area z3 is 1 / 32 of the rate at which balls reach landing area z1. In other words, even if the bounce of the falling ball is not suppressed as much as in landing area z1, there is little risk of the discharge of the ball being delayed in landing area z3. Therefore, by making the aspect ratio of the buffer rib 332 smaller in landing area z3 than in landing area z1, the position of the second outlet 315 can be lowered downward.

[0128] For example, when comparing landing area z2 and landing area z4, the falling distance of the ball into landing area z4 is longer than the falling distance into landing area z2, but the aspect ratio of the buffer ribs 322, 332 of landing area z2 is larger than that of landing area z4. This is because the rate at which the ball reaches landing area z4 is 1 / 56 of the rate at which the ball reaches landing area z2. In other words, even if the bounce of the falling ball is not suppressed as much as in landing area z2, there is little risk of the discharge of the ball being delayed in landing area z4. Therefore, by making the aspect ratio of the buffer rib 332 smaller in landing area z4 than in landing area z2, the position of the second outlet 315 can be lowered downward.

[0129] In the above explanation, the probability of the ball branching into branches b1 to b10 is equal (1 / 2) on both sides, but by changing the width of the nails, it is possible to adjust the probability of the ball branching into branches b1 to b10. For example, by reducing the spacing between the nails in the flow path through which the left arrow of branch b1 passes to approximately the same as the diameter of the ball, it is possible to increase the probability that the ball will flow down along the right arrow in branch b1 to more than 1 / 2. In the other branches b2 to b10, the probability of the ball branching can be adjusted in a similar manner.

[0130] This makes it possible to adjust the frequency with which the balls reach the paths c11 to c19, and improves the design freedom of the aspect ratio of the buffer rib 322.

[0131] In addition, the upper surface of the buffer rib 322 is formed to be inclined downward toward the rear (see FIG. 15(b)). This allows the ball flow to the first outlet 314 to be made faster.

[0132] Returning to Fig. 14, the left lower plate member 320 mainly comprises a long plate-like main body 321, buffer ribs 322 each formed of a thin plate connected in the left-right direction on the upper surface of the main body 321 and extending in the front-rear direction, a connecting front plate 323 formed in a manner connecting the front faces of the buffer ribs 322, a step 324 formed by protruding upward at the left end of the main body 321 as viewed from the front, a ball flow rail portion 325 extending from the step 324 to the left as viewed from the front, and a shaft support hole 326 drilled in the front-rear direction at the right end of the main body 321 as viewed from the front.

[0133] The buffer rib 322 is a portion through which a ball heading toward the first outlet 314 passes, and prevents the ball from bouncing up and down as it falls in the vertical direction. That is, the buffer rib 322 is formed from a thin plate connected in the left-right direction, and therefore, when it is hit by a falling ball, it bends in the thickness direction, thereby softening the impact of the collision. Also, when a ball moves left and right on the upper surface of the buffer rib 322, the ball gets stuck between the buffer ribs 322, and is braked. Also, the buffer rib 322 has a larger formation height and aspect ratio toward the right when viewed from the front (the inner side in the width direction of the game board 13 (see FIG. 2)).

[0134] The connecting front plate 323 connects the buffer ribs 322 together, thereby improving the strength of the buffer ribs 322 .

[0135] The step portion 324 is a raised portion for allowing the balls flowing down from the ball flow rail portion 325 to fall in the vertical direction. This makes it possible to suppress the load in the left-right direction from being applied to the buffer rib 322 by the balls flowing down the ball flow rail portion 325. This makes it possible to prevent the buffer rib 322 from bending in the left-right direction when subjected to the load in the left-right direction.

[0136] That is, since the buffer rib 322 is formed of a thin wall portion extending in the front-rear direction, there is a risk of it breaking when a load in the left-right direction is applied. On the other hand, in this embodiment, a ball that rolls on the upper surface of the ball flow rail 325, which has a left-right speed and may apply a left-right load to the buffer rib 322, is formed in such a manner that it falls in the vertical direction from the step portion 324 onto the buffer rib 322. As a result, the position where the ball lands on the buffer rib 322 can be shifted further to the right in the width direction as the ball's left-right speed increases.

[0137] Therefore, the load applied to the buffer rib 322 in the left-right direction when the ball lands on the buffer rib 322 can be made smaller toward the left (outside) in the width direction. Therefore, the risk of the buffer rib 322 breaking due to the left-right load of the ball decreases toward the left in the width direction of the buffer rib 322, and the aspect ratio of the buffer rib 322 can be made smaller than that toward the right in the width direction. In this case, the lower surface of the buffer rib 322 can be formed along the curved surface formed on the lower surface of the game board 13, so the position at which the buffer rib 322 is disposed can be made lower than when the buffer rib 322 has the same length in the width direction.

[0138] Here, it is also conceivable to form the lower surface of the buffer rib 322 along the curved surface formed on the lower surface of the game board 13 while keeping the aspect ratio of the buffer rib 322 constant in the left and right positions in the width direction (with the upper surface of the buffer rib 322 formed with the same curve as the lower surface of the buffer rib 322). However, in this case, the position of the step 324 becomes higher, and the position of the ball flow rail portion 325 formed with a downward incline toward the step 324 also becomes higher. In this case, the dead space between the ball flow rail portion 325 and the inner rail 61 (see FIG. 13) becomes larger, and the playing area is restricted.

[0139] On the other hand, the larger the aspect ratio of the buffer rib 322, the greater the effect of slowing down the momentum of the ball (deceleration effect). Therefore, the buffer rib 322 is formed in such a manner that the aspect ratio increases from the vicinity of the step portion 324 toward the center of the play area.

[0140] It is also possible to form the upper surface of the buffer rib 322 up to just before the step 324 with the same curve as the curve of the lower surface of the buffer rib 322 (so that the height is maximum halfway in the left-right direction of the buffer rib 322) so as not to affect the formation height of the step 324. However, in this case, the ball that reaches the landing area z1 is prevented from rolling to the left. Therefore, the ball is likely to remain in the landing area z1, making it difficult to discharge the ball smoothly.

[0141] In contrast, in this embodiment, the variation in height of the upper surface of the buffer rib 322 in the width direction of the buffer rib 322 is small, so that the ball that reaches the landing area z1 easily rolls to the left (toward the landing area z2). Therefore, the ball can flow into the landing area z2 before it accumulates in the landing area z1, so that the ball can be discharged smoothly.

[0142] In addition, the step 324 has the function of blocking the ball flowing down above the buffer rib 322 and to the left, thereby preventing the ball from bouncing back beyond the width of the first outlet 314 after colliding with the front cover member 340 (see FIG. 13).

[0143] The shaft support hole 326 is a portion through which the insertion shaft 343 of the front cover member 340 is inserted and supported.

[0144] The lower right plate member 330 mainly comprises a long, plate-shaped main body portion 331, a cushioning rib 332 which is formed by thin wall portions which are connected in the left-right direction on the upper surface of the main body portion 331 and extend in the front-to-rear direction, a connecting front plate 333 which is formed in a manner which connects the front faces of the cushioning rib 332, a recessed portion 324 which is recessed downwardly at the right end of the main body portion 331 when viewed from the front, a ball flow rail portion 335 which extends from the recessed portion 324 to the right when viewed from the front, and an axle support hole 336 which is drilled in the front-to-rear direction at the left end of the main body portion 331 when viewed from the front.

[0145] The configuration of the right lower plate member 330 and the configuration of the left lower plate member 320 are common in many parts. That is, the technical ideas of main body portion 331 are common to main body portion 321, buffer rib 332 to buffer rib 322, connecting front plate 333 to connecting front plate 323, ball flow rail portion 335 to ball flow rail portion 325, and shaft support hole 336 to shaft support hole 326 are common to each other, and therefore a description of the common parts will be omitted.

[0146] The buffer rib 332 is formed so that its width on the left and right is shorter than that of the buffer rib 322. This allows the width on the left and right of the second outlet 315 to be shorter, and the position of the second outlet 315 to be lowered lower than that of the first outlet 314, so that more space can be secured for the large opening solenoid 65b of the first variable winning device 65 (the position of the first variable winning device 65 can be lowered).

[0147] Here, the formation width of the buffer rib 332 can be made shorter than that of the buffer rib 322 because it regulates the flow path of the balls to the second outlet 315. That is, as shown in FIG. 14, the first variable winning device 65 is disposed at the upper right of the second outlet 315 when viewed from the front, so that when the opening and closing plate is opened, the balls flow into the first specific winning port 65a, and when the opening and closing plate is closed, the balls fall vertically downward on the front side of the first variable winning device 65. This makes it possible to prevent the balls from flowing down from the upper right to the second outlet 315 when viewed from the front. In other words, a non-flowing area in which the flow of the balls is regulated is formed at the upper right of the second outlet 315.

[0148] Therefore, the direction in which the balls flow down to the lower right plate member 330 is limited to vertical drop and widthwise flow (from the ball flow rail section 335) (flow from the diagonally upper right is restricted). Therefore, since there is no inflow of balls from the diagonally upper right, the direction in which the balls bounce can be restricted, and the width of the buffer rib 332 can be narrowed, and the width of the second outlet 315 can be narrowed. As a result, the installation space for the first variable winning device 65 can be secured.

[0149] The recessed portion 334 is a depression for bouncing the ball that flows down the ball flow rail portion 335. Therefore, the width of the recessed portion 334 is set to a width that allows a ball to be placed thereon without coming into contact with the adjacent buffer rib 332.

[0150] The balls that flow down ball flow rail section 335 drop into recessed section 334, bounce off when they come into contact with the upper surface of recessed section 334, and drop onto buffer rib 332. This prevents a load from being applied to buffer rib 332 in the width direction, and prevents buffer rib 332 from breaking.

[0151] The recessed portion 334 is formed in front of the fastening hole B through which the fastening screw for fastening the base member 310 to the game board 13 is inserted. This makes it easier to use a fastening tool such as a screwdriver when screwing the fastening screw into the fastening hole B to fasten the board lower unit 300 to the game board 13. In other words, the recessed portion 334 has both the effect of preventing the buffer rib 332 from breaking and the effect of making it easier to fasten the base member 310.

[0152] The front cover member 340 mainly comprises a plate-shaped main body 341 having the first winning opening 64 formed at the top, an opening 342 formed in the center of the main body 341 through which the rotating performance member 313a can be viewed, and a pair of insertion shafts 343 inserted into the shaft support holes 326, 336.

[0153] The main body 341 is formed in contact with the lower edge of the play area, and the side wall limits the direction in which the ball flows down. That is, a ball that hits the main body 341 from the right cannot penetrate to the left, and on the other hand, a ball that hits the main body 341 from the left cannot penetrate to the right.

[0154] The insertion shaft 343 is a portion that is inserted into the shaft support holes 326, 336. Therefore, the diameter of the insertion shaft 343 is formed to be slightly smaller than the shaft support holes 326, 336.

[0155] Next, the vertical operation unit 400 will be described with reference to Fig. 16 to Fig. 21. Fig. 16 is a front perspective view of the vertical operation unit 400, and Fig. 17 is a rear perspective view of the vertical operation unit 400. Note that Figs. 16 and 17 show a state in which the arm member 440 of the vertical operation unit 400 is arranged in the retracted position.

[0156] FIG. 18 is an exploded front perspective view of the vertical movement unit 400, and FIG. 19 is an exploded rear perspective view of the vertical movement unit 400. As shown in FIG. 18 and 19, the vertical operation unit 400 mainly comprises a base member 410 having an upper and lower groove portion 414 which is recessed from the rear side to the front side on the right side when viewed from the rear and which extends in the vertical direction, a rotating crank member 420 which rotates around a connecting hole 413 of the base member 410, a drive unit 430 which generates a driving force for the rotating crank member 420, an arm member 440 which receives the driving force from the rotating crank member 420 and is swung around an axle portion 412 of the base member 410, a slide member 450 which is disposed on the opposite side of the upper and lower groove portion 414 of the base member 410 and formed so as to be slidable in the vertical direction in conjunction with the swinging of the arm member 440, a lens member 460 which is suspended from a sliding hole 443 formed at the tip of the arm member 440 and formed so as to be slidable in the vertical direction in conjunction with the swinging of the arm member 440, and a pair of door members 470 which are each pivotally supported by the lens member 460.

[0157] The base member 410 mainly comprises a main body portion 411 formed in the shape of a long plate on the left and right sides, an axis portion 412 which protrudes cylindrically from the right end of the main body portion 411 toward the front side and supports the axis support hole 442 of the arm member 440, a connecting hole 413 which is drilled in a circular shape in the front-to-rear direction and connects the rotating crank member 420 and the transmission gear 432, an upper and lower groove portion 414 which is a recess formed from the rear side to the front side on the right side of the main body portion 411 when viewed from the rear and extends in the vertical direction, and recessed portions 415 which are recessed from the front side to the rear side on both the left and right outer sides of the upper and lower groove portion 414.

[0158] In the assembled state (see FIG. 2), the upper and lower grooves 414 are portions on the rear side where the telescopic performance device 540 of the composite operation unit 500 is housed. As described later, the more the telescopic performance device 540 approaches the contracted state, the more the swing angle of the telescopic performance device 540 is restricted, so that the telescopic performance device 540 is prevented from swinging and colliding with the left and right inner surfaces of the upper and lower grooves 414. The recessed portions 415 are portions where the slide guide portions 452 of the slide member 450 are guided.

[0159] The rotating crank member 420 mainly comprises a plate-shaped main body 421, a sliding protrusion 422 that protrudes cylindrically from one end of the main body 421 toward the front side and is inserted into an insertion portion 444 of the arm member 440, and an engagement portion 423 that engages with a fitting portion 432a of the transmission gear 432 to disable relative rotation between the transmission gear 432 and the rotating crank member 420.

[0160] When the sliding protrusion 422 is inserted into the insertion portion 444 of the arm member 440 and rotated, the driving force of the driving device 430 is transmitted to the arm member 440 , and the arm member 440 is swung about the shaft portion 412 .

[0161] The drive device 430 mainly comprises a drive motor 431 fastened to the base member 410, a drive gear 431a rotated and driven by the drive motor 431, a transmission gear 432 meshed with the drive gear 431a, and an engagement portion 432a formed on the front side of the transmission gear 432 with an outer diameter slightly smaller than the inner diameter of the connecting hole 413 and whose inner side surface is engaged with the engagement portion 423 of the rotating crank member 420.

[0162] The fitting portion 432a is a portion having a recess having a cross-sectional shape in which a circle is arranged at each apex of a triangle, and is inserted into the connecting hole 413 of the base member 410, and the engagement portion 423 of the rotating crank member 420 is fitted at the tip side thereof so as to be unable to rotate relative to the fitting portion 432a. As a result, the main body portion 411 of the base member 410 is sandwiched between the transmission gear 432 and the rotating crank member 420, and as described above, the transmission gear 432 and the rotating crank member 420 are unable to rotate relative to each other, so that the transmission gear 432 and the rotating crank member 420 rotate synchronously. That is, the driving force of the drive motor 431 is transmitted to the rotating crank member 420 via the transmission gear 432.

[0163] The arm member 440 mainly comprises a main body portion 441 formed in a long rod shape, a shaft support hole 442 drilled on the base end side (right side when viewed from the front) and supported by the shaft portion 412 so as to be able to swing, a sliding hole 443 drilled as a long hole on the swing end side which is the end opposite the base end side and through which the sliding protrusion portion 463 of the lens member 460 is inserted, and a bottomed hole-shaped insertion portion 444 through which the sliding protrusion portion 422 of the rotating crank member 420 is inserted.

[0164] The shape of the insertion portion 444 is set so that the rotating crank member 420 can rotate once with the sliding protrusion portion 422 inserted into the insertion portion 444. Therefore, the arm member 440 can perform a swinging motion regardless of the rotation direction of the rotating crank member 420.

[0165] The slide member 450 mainly comprises a rectangular plate-shaped main body 451, slide guide portions 452 extending rearward from both the left and right ends of the main body 451 and guided in the recessed portions 415 so as to be slidable up and down, a central guide recess 453 which is a recess formed on the front surface at the widthwise center of the main body 451 and extending in the vertical direction, through which the sliding protrusion 463 of the lens member 460 is inserted, and both end guide recesses 454 which are recesses formed on the front surface at both the left and right ends of the main body 451 and extending in the vertical direction, through which the stabilizing slide portion 464 of the lens member 460 is guided.

[0166] The lens member 460 mainly includes a plate-shaped main body portion 461 having a circular opening in the center, a magnifying lens 462 having a magnifying lens formed thereon and fitted into the opening of the main body portion 461, a sliding protrusion portion 463 that protrudes toward the rear side at the upper center end portion in the width direction of the main body portion 461 and is inserted into a sliding hole 443 of the arm member 440 so as to be slidable up and down, a stable slide portion 464 that protrudes toward the rear side at both ends in the width direction of the main body portion 461 and is inserted into both end guide recesses 454 of the slide member 450 so as to be slidable up and down, a pair of rotating cylinders 465 that are axially rotatably arranged on the lower left side of the main body portion 461 when viewed from the front, and through which a lower shaft portion 473 and an upper shaft portion 474 of the door member 470 are inserted, and a drive motor 466 that rotates the pair of rotating cylinders 465 in opposite directions by a transmission mechanism not shown.

[0167] The movement operation of the vertical operation unit 400 will be described with reference to Fig. 20. Fig. 20 is a front view of the vertical operation unit 400. Note that Fig. 20 illustrates a closed state of the door member 470 when the arm member 440 of the vertical operation unit 400 is placed in the extended position.

[0168] When arm member 440 is swung from the retracted position (see FIG. 16) to the extended position (see FIG. 20), slide protrusion 463 (see FIG. 18) of lens member 460 journaled in slide hole 443 on the swing end side of arm member 440 is slid along central guide recess 453 of slide member 450. Lens member 460 is guided in the vertical direction by guide recesses 454 at both ends of slide member 450, and slide member 450 is guided in the vertical direction by recess 415 of base member 410, so that lens member 460 is slid along the vertical direction by the swing of arm member 440.

[0169] 18 and 19. Door member 470 is configured by dividing a circular plate into upper and lower halves, and mainly includes a lower main body portion 471 formed on the lower side, an upper main body portion 472 formed on the upper side of lower main body portion 471, a lower shaft portion 473 provided at the lower end of lower main body portion 471 to protrude cylindrically toward the rear side and inserted into rotating cylinder 465 of lens member 460 so as not to rotate relatively thereto, and an upper shaft portion 474 provided at the lower end of upper main body portion 472 to protrude cylindrically toward the rear side and inserted into rotating cylinder 465 of lens member 460 so as not to rotate relatively thereto.

[0170] The lower main body portion 471 includes a guide protrusion 471a protruding from a side surface on the side that comes into contact with the upper main body portion 472, and the upper main body portion 472 includes a receiving recess 472a recessed into a side surface on the side that comes into contact with the lower main body portion 471. By fitting the guide protrusion 471a and the receiving recess 472a together, the lower main body portion 471 and the upper main body portion 472 can be relatively aligned in the closed state. In this embodiment, the guide protrusion 471a protrudes in a tapered shape, so that the guide protrusion 471a can be reliably fitted into the receiving recess 472a.

[0171] The operation of the door element 470 will be described with reference to Fig. 21. Fig. 21 is a front view of the vertical movement unit 400. Note that Fig. 21 illustrates the open state of the door element 470 when the arm element 440 of the vertical movement unit 400 is placed in the extended position.

[0172] The lower shaft portion 473 and the upper shaft portion 474 (see FIG. 19) are rotated by the rotation of the rotating cylinder 465 (see FIG. 18) of the lens member 460. The pair of rotating cylinders 465 are rotated in opposite directions by the driving force of a drive motor 466 (see FIG. 19), so that when the door member 470 is changed from the closed state (see FIG. 20) to the open state (see FIG. 21), the lower main body portion 471 and the upper main body portion 472 can be swung outward (in opposite directions) from each other. Also, when the door member 470 is changed from the open state (see FIG. 21) to the closed state (see FIG. 20), the lower main body portion 471 and the upper main body portion 472 can be swung inward from each other.

[0173] This allows the time required for lower main body portion 471 and upper main body portion 472 to be swung to half that required when compared to a case in which the front side of lens member 460 is covered by swinging a single cover member.

[0174] Next, the composite action unit 500 will be described with reference to Fig. 22 to Fig. 45. The composite action unit 500 is a unit that positions the telescopic performance device 540 on the front side of the third pattern display device 81 by swinging the rotating arm member 550 from the retracted position (see Fig. 22) to the extended position (see Fig. 9). In addition, the telescopic performance device 540 is formed to be capable of swinging around the first shaft portion 512 (see Fig. 24) of the base member 510.

[0175] Fig. 22 is a front perspective view of the composite action unit 500, and Fig. 23 is a rear perspective view of the composite action unit 500. In Fig. 22 and Fig. 23, the rotating arm member 550 is shown in a state in which it is disposed at a retreat position, which is a terminal position formed outside the third pattern display device 81 (see Fig. 2).

[0176] FIG. 24 is an exploded front perspective view of the combined action unit 500, and FIG. 25 is an exploded rear perspective view of the combined action unit 500. As shown in FIG.

[0177] As shown in FIG. 24 and FIG. 25, the composite operation unit 500 is a unit that performs a performance by sliding and swinging an extension performance device 540, and includes a base member 510 that forms a framework, a rotating plate 520 that is formed so as to be rotatable about a first shaft portion 512 of the base member 510, a first drive unit 530 that is fastened and fixed to the base member 510 and generates a drive force for the rotating plate 520, an extension performance device 540 that is fastened and fixed to the front surface of the rotating plate 520 and formed so as to be extendable and contractible in the radial direction of the rotating plate 520, and a first drive unit 530 that is fastened and fixed to the front surface of the rotating plate 520 and formed so as to be extendable and contractible in the radial direction of the rotating plate 520, and a second drive unit 530 that is fastened and fixed to the front surface of the rotating plate 520 and is fastened and fixed to the first drive unit 530. the other end of which is connected to a pivotable arm member 550 and which is journalled to the base member 510 and which swings to form the extension and retraction motion of the extension and retraction performance device 540; a second drive unit 560 which is fastened and fixed to the base member 510 and which generates a drive force for the pivotable arm member 550; a rotating crank member 570 which transmits the drive force of the second drive unit 560 to the pivotable arm member 550; and a front cover 580 which is fastened and fixed from the front of the base member 510 to conceal the mechanical parts on the rotation shaft side such as the pivotable arm member 550 and the pivotable crank member 570.

[0178] The base member 510 is mainly composed of a rectangular plate-shaped main body 511, a cylindrical first shaft portion 512 protruding forward from approximately the center lower part in the width direction of the main body 511, three rows of arc-shaped holes 513 drilled along an arc centered on the first shaft portion 512, a first through hole 514 drilled adjacent to a second arc-shaped hole 513b of the three rows of arc-shaped holes 513, a cylindrical second shaft portion 515 protruding forward from the main body 511 approximately midway between the shaft portion 512 and the right end portion of the main body 511, a second through hole 516 drilled adjacent to the second shaft portion 515, a cylindrical third shaft portion 517 protruding forward from the lower right end portion of the main body 511 when viewed from the front, and a folded wall portion 518 formed by bending forward from an edge of the main body 511.

[0179] The first shaft portion 512 is inserted into the shaft support hole 522 of the rotating plate 520 and serves as the rotation shaft of the rotating plate 520. Therefore, the diameter of the first shaft portion 512 is formed slightly smaller than the inner diameter of the shaft support hole 522 of the rotating plate 520.

[0180] The arc-shaped hole 513 includes, from the side closer to the first shaft portion 512, a first arc-shaped hole 513a, a second arc-shaped hole 513b, and a third arc-shaped hole 513c.

[0181] The first arc-shaped hole 513a and the third arc-shaped hole 513c are elongated holes through which the insertion shaft 525 of the rotating plate 520 is inserted and which guide the rotation of the rotating plate 520. This reduces the load on the first shaft portion 512 when the rotating plate 520 is rotated, and improves the durability of the rotating plate 520. Note that, although Figs. 24 and 25 show a state in which a collar is fastened to the tip of the insertion shaft 525, the first arc-shaped hole 513a and the third arc-shaped hole 513c are disposed between the collar and the main body portion 521 (they are inserted before the collar is fastened).

[0182] The second arc-shaped hole 513b is an elongated hole in which the arc-shaped rack 526 of the rotating plate 520 is disposed and moved. The upper side of the approximate center is opened, and the drive gear 532 of the first driving device 530 is disposed in the opened portion. This allows the meshing portion between the drive motor 531 of the first driving device 530 and the arc-shaped rack 526 of the rotating plate 520 to be disposed in the plate thickness portion of the main body 511, thereby making it possible to reduce the dimension in the thickness direction of the composite action unit 500 (the dimension in the front-rear direction in FIG. 22).

[0183] The first through hole 514 and the second through hole 516 are through holes through which the drive gear 532 of the first drive device 530 and the drive gear 562 of the second drive device 560 are inserted, respectively.

[0184] The second shaft portion 515 is a columnar portion to which the cover portion 575 of the rotating crank member 570 is fastened and fixed on the front side, and which serves as the central axis of rotation of the main body portion 571. Therefore, the diameter of the second shaft portion 515 is formed to be slightly smaller than the inner diameter of the main body portion 571 of the rotating crank member 570.

[0185] Third shaft portion 517 is inserted into shaft support hole 552 of rotating arm member 550, and serves as a central shaft for rotation of rotating arm member 550. Therefore, the diameter of third shaft portion 517 is formed to be slightly smaller than the inner diameter of shaft support hole 552 of rotating arm member 550. Torsion spring 517a is wound around third shaft portion 517 to generate a biasing force that moves rotating arm member 550 toward the retracted position.

[0186] Torsion spring 517a is formed in such a manner that arms extend from both ends of a coil portion wound around third shaft portion 517. One arm is fixed to the lower right portion (near first stopper portion 518a) of bent wall portion 518 in front view, and the other arm opposite to the one arm is locked to lock portion 555 of rotating arm member 550.

[0187] The folded wall portion 518 mainly comprises a first stopper portion 518a adjacent to the third shaft portion 517, a second stopper portion 518b formed to the right of the first shaft portion 512, and a third stopper portion 518c formed to the left of the first shaft portion 512.

[0188] The first stopper portion 518a is a portion that restricts the rotation of the rotating arm member 550. That is, when the rotating arm member 550 is lowered to the extended position (see FIG. 9), it comes into contact with the first stopper portion 518a, and the descent is stopped.

[0189] As shown in Fig. 24, the second stopper portion 518b is disposed lower than the third stopper portion 518c. Since the lower surface of the rotating plate 520 is formed symmetrically with respect to the shaft support hole 522 (see Fig. 37), the rotating plate 520 can rotate at a larger rotation angle in the direction toward the second stopper portion 512b. That is, the telescopic performance device 540 described later is formed so that the maximum angle of swinging clockwise when viewed from the front is larger than the maximum angle of swinging counterclockwise when viewed from the front.

[0190] The rotating plate 520 mainly comprises a sector-shaped main body 521, an axle support hole 522 drilled circularly in the thickness direction at the base of the main body 521, a rail receiving groove 523 linearly recessed in the front surface of the main body 521 with a width slightly larger than the inner diameter of the axle support hole 522, a pair of expandable stoppers 524 formed by protruding forward on both sides of the lower end of the rail receiving groove 523, multiple insertion shafts 525 (three in this embodiment) protruding from the rear surface of the main body 521, and an arc-shaped rack 526 protruding in an arc shape centered on the axle support hole 522 from the rear surface of the main body 521 and having gear teeth engraved on its outer periphery.

[0191] The first shaft portion 512 of the base member 510 is inserted into the shaft support hole 522. Therefore, the rotating plate 520 swings around the first shaft portion 512.

[0192] The rail receiving groove 523 is a portion to which the slide rail 545 of the telescopic performance device 540 is fastened and fixed, and the telescopic performance device 540 telescopically moves along the extending direction of the rail receiving groove 523. Therefore, the moving direction of the telescopic performance device 540 is changed depending on the posture of the rotating plate 520.

[0193] The telescopic stopper 524 is a part that comes into contact with the inner surface of the slide plate 544 of the telescopic performance device 540 in the vertical direction and restricts the movement width of the slide plate 544. It is formed on both sides of the rail receiving groove 523 and comes into contact with the inner surface of the slide plate 544 on both sides, thereby suppressing the slide rail 545 from receiving a load in a direction perpendicular to the telescopic direction, and improving durability.

[0194] The insertion shaft 525 is a portion that is inserted into the first arc-shaped hole 513a and the third arc-shaped hole 513c of the base member 510 to guide the rotation of the rotating plate 520, and is formed with a diameter that is slightly smaller than the width dimensions of the first arc-shaped hole 513a and the third arc-shaped hole 513c. In addition, a collar member having a diameter larger than the width dimensions of the first arc-shaped hole 513a and the third arc-shaped hole 513c is fastened and fixed to the tip, thereby connecting the rotating plate 520 to the base member 510 so that it cannot be pulled out.

[0195] The arc-shaped rack 526 is inserted into the second arc-shaped hole 513b of the base member 510, and meshes with the drive gear 532 of the first drive device 530. Since the meshing portion between the arc-shaped rack 526 and the first drive device 530 is formed in an area including the thickness portion of the base member 510, the dimension in the thickness direction of the composite action unit 500 can be reduced.

[0196] The first driving device 530 mainly includes a driving motor 531 fastened and fixed to the base member 510 , and a driving gear 532 that is inserted into a first through-hole 514 of the base member 510 and axially rotated by the driving motor 531 .

[0197] Next, the telescopic performance device 540 will be described with reference to Fig. 26 and Fig. 27. Fig. 26 is an exploded front perspective view of the telescopic performance device 540, and Fig. 27 is an exploded rear perspective view of the telescopic performance device 540.

[0198] As shown in FIG. 26 and FIG. 27, the telescopic performance device 540 includes a main body member 541 forming a skeleton, a first guide member 542 and a second guide member 543 which are fastened to the back surface of the main body member 541 and through which a main body part 551 of a rotating arm member 550 is inserted between the first guide member 542 and the second guide member 543, a slide plate 544 which is arranged to be axially slidable along the extending direction of the insertion holes 542d, 543d of the first guide member 542 and the second guide member 543, and a slide plate 544 which is arranged to be axially slidable along the extending direction of the insertion holes 542d, 543d of the first guide member 542 and the second guide member 543. 4 and the rotating plate 520, and one end of which is fitted into the rail receiving groove 523 and fastened thereto; a front plate member 546 which is raised on the front side of the main body member 541 and fastened thereto; a connecting sliding member 547 which is slidably supported by the support portion 546c of the front plate member 546; and a decorative member 548 which is fastened to the connecting sliding member 547 and has a front hanging portion 548b formed so as to be movable in front of the main body member 541.

[0199] The main body member 541 mainly comprises a plate-shaped main body portion 541a forming the skeleton, a cylindrical protrusion portion 541b protruding toward the rear side at the widthwise center of the main body portion 541a, a first raised fastening portion 541c protruding in an upper and lower pair on the left side of the protrusion portion 541b when viewed from behind, a second raised fastening portion 541d protruding in an upper and lower pair on the right side of the protrusion portion 541b when viewed from behind, a guide fastening portion 541e protruding from the upper left part of the main body portion 541a when viewed from behind, and fastening holes 541f formed on the front side of the main body portion 541a (three in this embodiment) to which the front plate member 546 is fastened and fixed.

[0200] The protrusion 541b is a portion that is inserted into the arc-shaped hole 554 of the rotating arm member 550. Therefore, the diameter of the protrusion 541b is formed to be slightly smaller than the width dimension of the inner circumferential surface of the arc-shaped hole 554. In addition, since the protrusion 541b is inserted into the arc-shaped hole 554, when the rotating arm member 550 is swung, the main body member 541 can be moved in conjunction with the protrusion 541b.

[0201] The first raising fastening portion 541c is a portion for fastening and fixing the first guide member 542, and the second raising fastening portion 541d is a portion for fastening and fixing the second guide member 543. The reason why the second raising fastening portion 541d is longer in the vertical direction than the first raising fastening portion 541c is that it is arranged at a position that does not interfere with the rotating arm member 550. Here, in this embodiment, the rotating arm member does not pass through the lower left of the main body member 541 in the front view in its rotation trajectory (see Figures 37, 40, and 44). Therefore, it is possible to widen the arrangement interval of the pair of second raising fastening portions 541d compared to the first raising fastening portion 541c, and the rigidity of the second raising fastening portion 541d can be improved.

[0202] The guide fastening portion 541e is a portion to which the auxiliary fastening portion 542e of the first guide member 542 is fastened and fixed, and is a portion to which the upper surface of the rotating arm member 550 is guided when the telescopic performance device 540 is in the extended state. That is, even if the protrusion 541b is not guided by the arc-shaped hole 554 of the rotating arm member 550, the guide fastening portion 541e is guided by the upper surface of the rotating arm member 550 when the rotating arm member 550 rotates upward, so that the rotating arm member 550 and the telescopic performance member 540 operate in conjunction with each other.

[0203] The fastening hole 541f is a through hole to which the fastening portion 546b of the front plate member 546 is fastened and fixed.

[0204] The first guide member 542 mainly comprises a fastening plate portion 542a fastened to the first raising fastening portion 541c, a rear regulating portion 542b extending upward from a position one step higher on the upper surface of the fastening plate portion 542a toward the rear surface side, a guide rail portion 542c protruding in a wall-like manner toward the rear surface from both the left and right sides of the rear regulating portion 542b, an insertion hole 542d formed in the upper end portion of the rear regulating portion 542b protruding toward the rear surface side in the vertical direction, and an auxiliary fastening portion 542e extending from the rear regulating portion 542b and fastened to the guide fastening portion 541e.

[0205] The rear surface regulating portion 542b is a portion disposed on the rear surface of the rotating arm member 550, and prevents the protruding portion 541b from falling off from the arc-shaped hole 554 when the rotating arm member 550 moves rearward.

[0206] The guide rail portion 542c is a portion that guides the movement of the rail receiving portion 544d of the sliding plate 544 when the telescopic performance device 540 telescopically operates, and suppresses deviation of the posture of the sliding plate 544 relative to the first guide member 542.

[0207] The insertion hole 542d is a hole through which the slide rod 544e of the slide plate 544 is inserted. The inner diameter of the insertion hole 542d is formed slightly larger than the diameter of the slide rod 544e, so that the slide plate 544 is formed to be slidable relative to the first guide member 542.

[0208] The second guide member 543 mainly comprises a fastening plate portion 543a fastened to the second raising fastening portion 541d, a rear regulating portion 543b extending upward from a position one step above the upper surface of the fastening plate portion 543a toward the rear side, guide rail portions 543c protruding in a wall-like manner toward the rear side from both the left and right sides of the rear regulating portion 543b, and an insertion hole 543d formed in the upper end portion of the rear regulating portion 543b so as to penetrate in the vertical direction in the portion protruding toward the rear side.

[0209] The rear surface regulating portion 543b is a portion disposed on the rear surface of the rotating arm member 550, and prevents the protruding portion 541b from falling off from the arc-shaped hole 554 when the rotating arm member 550 moves rearward.

[0210] The guide rail portion 543c is a portion that guides the movement of the rail receiving portion 544d of the sliding plate 544 when the telescopic performance device 540 telescopically operates, and suppresses deviation of the posture of the sliding plate 544 relative to the first guide member 543.

[0211] The insertion hole 543d is a hole through which the slide rod 544e of the slide plate 544 is inserted. The inner diameter of the insertion hole 543d is formed slightly larger than the diameter of the slide rod 544e, so that the slide plate 544 is formed to be slidable relative to the first guide member 543.

[0212] The slide plate 544 mainly comprises a main body portion 544a formed in a rectangular plate shape, a recessed portion 544b in which a wide recess extending in the vertical direction is formed on the back surface of the main body portion 544a, end recessed portions 544c in which recesses extending in the vertical direction are formed on the front surfaces on both the left and right sides of the recessed portion 544b, rail receiving portions 544d protruding in a semicircular shape toward the front side at the upper and lower ends of the end recessed portions 544c, a cylindrical slide rod 544e extending in the vertical direction inside the end recessed portions 544c, a performance support wall 544f protruding toward the front approximately at the center in the vertical direction of the main body portion 544a, and stopper portions 544g protruding toward the back surface at both the left and right ends of the upper and lower ends of the recessed portion 544b.

[0213] The recessed portion 544b is a portion that guides the slide plate 544 relative to the expansion and contraction stopper 524 of the rotation plate 520. Therefore, the width of the inner surface of the recessed portion 544b is formed slightly larger than the width dimension of the expansion and contraction stopper 524.

[0214] The recesses 544c at both ends are portions that accommodate the protrusions through which the insertion holes 542d, 543d of the guide members 542, 543 are formed. This makes it possible to guide the protrusions through which the insertion holes 542d, 543d of the guide members 542, 543 are formed from the outside.

[0215] The rail receiving portion 544d is a portion that is accommodated in the guide rail portions 542c, 543c of the guide members 542, 543. This makes it possible to suppress wobbling of the guide members 542, 543 with respect to the slide plate 544.

[0216] The slide bar 544e is a columnar bar inserted into the insertion holes 542d, 543d of the guide members 542, 543. This allows the guide members 542, 543 to be slidable in the extending direction of the slide bar 544e (the up-down direction in FIG. 26).

[0217] The performance assisting portion 544f is a portion that comes into contact with the hanging portion 548c of the decorative member 548 when the telescopic performance device 540 is in the extended state, and moves the decorative member 548. This allows the appearance of the telescopic performance device 540 to be changed.

[0218] The stopper portion 544g is a portion that comes into contact with the expandable stopper 524 of the rotating plate 520 and defines the upper and lower movement ends of the slide plate 544.

[0219] The slide rail 545 is a commercially available mini rail member. One end is fastened and fixed along the rail receiving groove 523 of the rotating plate 520, and the other end opposite to the one end is fastened and fixed to the recessed portion 544b of the slide plate 544.

[0220] The front plate member 546 is a presentation part visible to the player, and mainly comprises a plate-shaped main body portion 546a formed in approximately the same shape as the main body member 541 when viewed from the front, a fastening portion 546b protruding from the main body portion 546a toward the rear side in accordance with the position at which the fastening hole 541f is formed, and a pair of support portions 546c protruding from the upper end of the main body portion 546a toward the rear side.

[0221] The fastening portion 546b is a portion that fixes the front plate member 546 to the main body member 541, and is fastened and fixed by screws passing through the fastening holes 541f.

[0222] The pivot support portion 546c is a portion that slidably supports the connecting sliding member 547. Therefore, the diameter of the pivot support portion 546c is formed slightly smaller than the width of the inner circumferential surface of the sliding elongated hole 547b of the connecting sliding member 547.

[0223] The connecting sliding member 547 mainly comprises a main body portion 547a formed in a plate shape, a pair of sliding long holes 547b formed as long holes extending vertically and drilled in the front-rear direction, and a pair of insertion holes 547c drilled in the vertical direction.

[0224] The long sliding hole 547b is a portion through which the pivot support portion 546c of the front plate member 546 is inserted. Therefore, the width of the inner peripheral surface of the long sliding hole 547b is formed slightly larger than that of the pivot support portion 546c. A collar member having an outer diameter larger than the width of the inner peripheral surface of the long sliding hole 547b is fastened and fixed to the tip of the pivot support portion 546c, so that the connecting sliding member 547 is pivotally supported by the front plate member 546 so as not to be pulled out. The insertion hole 547c is a circular hole through which a fastening screw for fastening and fixing the decorative member 548 is inserted.

[0225] Decorative member 548 mainly comprises a main body portion 548a formed in a plate shape to which connecting sliding member 547 is fastened and fixed from below, a front hanging portion 548b formed and hanging downward from the front side of main body portion 548a, and a rear hanging portion 548c formed and hanging downward from the rear side of main body portion 548a.

[0226] When the connecting sliding member 547 moves relative to the front plate member 546, the front hanging portion 548b can be in a state where it covers the front plate member 546 (see FIG. 43) or in a state where it is separated from the front plate member 546 (see FIG. 37). This makes it possible to change the appearance of the extendable performance member 540, thereby improving the performance effect.

[0227] The hanging portion 548c is a part that comes into contact with the performance support wall 544f of the sliding plate 544 due to the extension and retraction operation of the telescopic performance device 540, and the decorative member 548 is moved relative to the front plate member 546 when the hanging portion 548c comes into contact with the performance support wall 544f.

[0228] 24 and 25, the rotating arm member 550 mainly includes a main body 551 formed in a long rod shape, a shaft support hole 552 drilled in the front-rear direction at one end of the main body 551, an irregularly shaped long hole 553 which is a bottomed long hole of a special shape formed on the back side of the main body 551 close to the shaft support hole 552, an arc-shaped hole 554 which is a bottomed long hole of an arc shape formed on the front side of the other end which is the end opposite to the one end, and a locking portion 555 which protrudes toward the back side near the shaft support hole 552 of the main body 551, has a tip which is bent into a hook shape, and with which the other arm of the torsion spring 517a is locked.

[0229] The shaft support hole 552 is a circular hole through which the third shaft portion 517 of the base member 510 is inserted. Therefore, the inner diameter of the shaft support hole 552 is formed slightly larger than the diameter of the third shaft portion 517, so that the rotating arm member 550 is formed to be rotatable around the third shaft portion 517.

[0230] The irregularly shaped long hole 553 is a portion through which the sliding protrusion 574 of the rotating crank member 570 is inserted. The shape of the irregularly shaped long hole 553 will be described later.

[0231] The arc-shaped hole 554 is an elongated hole through which the protrusion 541b of the telescopic performance device 540 is inserted. Therefore, the width dimension of the arc-shaped hole 554 is formed slightly larger than the diameter of the protrusion 541b. Also, the arc formed by the arc-shaped hole 554 coincides with the arc formed by the protrusion 541b when the telescopic performance device 540 is swung around the first shaft portion 512 in the extended state (see FIGS. 37 to 39).

[0232] The arc-shaped hole 554 is open at the tip of the other end of the rotating arm member 550 and has a tip portion 554a that widens at the tip.

[0233] The second driving device 560 is a device that generates a driving force to rotate the rotating crank member 570, and mainly comprises a driving motor 561 fastened to the base member 510, and a driving gear 562 that is inserted into the second through hole 516 of the base member 510 and rotated about its axis by the driving motor 561.

[0234] The drive gear 562 is meshed with the transmission gear teeth 572 of the rotating crank member 570. As a result, when the drive gear 562 is rotated, the rotating crank member 570 is rotated accordingly.

[0235] The rotating crank member 570 is a member that transmits a driving force to the rotating arm member 550, and mainly comprises a ring-shaped main body portion 571 journaled on the second shaft portion 515, transmission gear teeth 572 engraved on the outer peripheral surface of the main body portion 571, a regulating umbrella portion 573 formed in a manner to cover the front side of the transmission gear teeth 572, a sliding protrusion portion 574 protruding toward the front side at a position eccentric to the center of the main body portion 571, and a cover portion 575 formed with a diameter larger than the inner peripheral diameter of the main body portion 571 and fastened to the front side of the second shaft portion 515.

[0236] The transmission gear teeth 572 are meshed with the drive gear 562 of the second drive device 560. As a result, the drive force of the drive motor 561 is transmitted to the rotating crank member 570.

[0237] The restricting umbrella portion 573 prevents the drive gear 532 from being misaligned to the front side of the transmission gear teeth 572. This makes it possible to optimize the meshing relationship between the drive gear 532 and the transmission gear teeth 572.

[0238] The sliding protrusion 574 is a portion that is inserted into the irregularly shaped elongated hole 553 of the rotating arm member 550. In other words, the relationship between the shape of the sliding protrusion 574 and the rotating arm member 550 determines whether or not the transmission of driving force is established.

[0239] The lid portion 575 is a portion for mounting the main body portion 571 to the base member 510 so that the main body portion 571 cannot be pulled out.

[0240] 28 to 31, a description will be given of the relationship between the swing of the rotating arm member 550 and the rotation of the rotating crank member 570. First, a description will be given of the shape of the irregular elongated hole 553 of the rotating arm member 550 with reference to Figures 28(a) and 29(a).

[0241] 28(a) and 29(a) are front views of the rotating arm member 550 and the rotating crank member 570. Note that Fig. 28(a) illustrates a state in which the rotating arm member 550 is arranged in the retracted position, and Fig. 29(a) illustrates a state in which the rotating arm member 550 is arranged in the extended position, and in Fig. 28(a) and 29(a), the irregular elongated hole 553 and the sliding protrusion 574 are illustrated with hidden lines, and the front plate member 546 and the protrusion 541b of the extendable performance device 540 are illustrated with imaginary lines.

[0242] As shown in FIG. 28(a), when the pivot arm member 550 is positioned in the retracted position, an upward orthogonal state is formed in which a straight line connecting the rotation axis of the pivot crank member 570 and the sliding protrusion portion 574 and a straight line connecting the rotation axis of the pivot crank member 570 and the shaft support hole 552 are perpendicular to each other.

[0243] As shown in Fig. 29(a), when the rotating arm member 550 is disposed at the extended position, a downward orthogonal state can be formed in which a straight line connecting the rotation axis of the rotating crank member 570 and the sliding protrusion 574 is perpendicular to a straight line connecting the rotation axis of the rotating crank member 570 and the shaft support hole 552. Note that Fig. 29(a) illustrates a state in which the rotating crank member 570 is rotated a predetermined angle counterclockwise as viewed from the front from the downward orthogonal state described above.

[0244] The irregularly shaped elongated hole 553 mainly comprises a transmission groove portion 553a in which the driving force is transmitted to the pivot arm member 550 by movement of the sliding protrusion portion 574, a first non-transmission wall portion 553b connected to the upper end of the transmission groove portion 553a, a second non-transmission wall portion 553c connected to the lower end of the transmission groove portion 553a, and a selection wall portion 553d connecting the first non-transmission wall portion 553b and the second non-transmission wall portion 553c.

[0245] 28(a), the transmission groove 553a is a recessed groove extending linearly to the left from the sliding protrusion 574 of the rotating crank member 570 in the upward orthogonal state. The transmission groove 553a is formed with a length that allows the sliding protrusion 574 of the rotating crank member 570 to move from the upward orthogonal state to the downward orthogonal state, and the width of the inner circumferential surface thereof is formed slightly larger than the diameter of the sliding protrusion 574. Therefore, while the sliding protrusion 574 moves through the transmission groove 553a, the driving force is transmitted from the rotating crank member 570 to the rotating arm member 550.

[0246] 28(a), in the upward orthogonal state, the first non-transmitting wall portion 553b is a wall portion formed from the upper wall surface at the right end portion of the transmission groove portion 553a along a circumscribing circle of the sliding protrusion portion 574 centered on the rotation axis of the rotating crank member 570. In other words, when the rotating crank member 570 is rotated clockwise as viewed from the front from the upward orthogonal state, the rotating crank member 570 rotates freely relative to the rotating arm member 550, and the driving force is not transmitted from the rotating crank member 570 to the rotating arm member 550.

[0247] When the rotating arm member 550 is rotated counterclockwise as viewed from the front from a state in which the rotating arm member 550 is disposed at the retracted position (see FIG. 28(a)), the movement direction of the first non-transmitting wall portion 553b is directed toward the rotation axis of the rotating crank member 570. Therefore, when the sliding protrusion portion 574 is disposed opposite the first non-transmitting wall portion 553b, the load applied to the sliding protrusion portion 574 by the rotation of the rotating arm member 550 is directed toward the rotation axis of the rotating crank member 570. Therefore, when the sliding protrusion portion 574 is disposed opposite the first non-transmitting wall portion 553b, rotation of the rotating arm member 550 is prevented.

[0248] 29(a), when the rotating arm member 550 is disposed in the extended position, the second non-transmitting wall portion 553c is a wall portion formed from the lower wall surface of the right end portion of the transmission groove portion 553a along a circumscribing circle of the sliding protrusion portion 574 centered on the rotation axis of the rotating crank member 570. That is, when the rotating crank member 570 is rotated counterclockwise as viewed from the front from the downward orthogonal state (a state in which the rotating crank member 570 is rotated a predetermined amount clockwise as viewed from the state of FIG. 29(a)), the rotating crank member 570 rotates freely relative to the rotating arm member 550, and the driving force is not transmitted from the rotating crank member 570 to the rotating arm member 550.

[0249] 29(a), the direction of movement of the second non-transmitting wall portion 553b is directed toward the rotation axis of the rotating crank member 570. Therefore, when the sliding protrusion portion 574 is disposed opposite the second non-transmitting wall portion 553c (see FIG. 29(b)), the load applied to the sliding protrusion portion 574 by the rotation of the rotating arm member 550 is directed toward the rotation axis of the rotating crank member 570. Therefore, when the sliding protrusion portion 574 is disposed opposite the second non-transmitting wall portion 553c, the rotation of the rotating arm member 550 is prevented.

[0250] The selection wall portion 553d is a wall portion formed from a smooth curved surface connecting the right end portion of the first non-transmitting wall portion 553b when viewed from the front and the right end portion of the second non-transmitting wall portion 553c when viewed from the front, and is formed above the curve extended from the first non-transmitting wall portion 553b.

[0251] The selection wall portion 553d is disposed opposite to the right side portion of the second non-transmission wall portion 553c, and is formed in such a manner that the distance from the second non-transmission wall portion 553c increases toward the left end portion of the selection wall portion 553d. Therefore, for example, when the rotating crank member 570 is rotated clockwise as viewed from the front from the upward orthogonal state (see FIG. 28(a)), in the clearance portion D (see FIG. 32(b)) between the sliding protrusion portion 574 passing over the first non-transmission wall portion 553b and reaching the second non-transmission wall portion 553c, the driving force is not transmitted to the rotating arm member 550, and the rotation is not restricted. That is, the driving force is not transmitted from the rotating crank member 570 to the rotating arm member 550, and the sliding protrusion portion 574 does not restrict the rotation of the rotating arm member 550.

[0252] The right end of the second non-transmission wall portion 553c is formed along an arc S1 centered on the pivot hole 552 (the angle formed with the arc S1 is small), while the right end of the selection wall portion 553d is formed in a manner that intersects with an arc S2 centered on the pivot hole 552 at an angle larger than the angle formed between the right end of the second non-transmission wall portion 553c and the arc S1.

[0253] In this case, when the distance between the sliding protrusion 574 and the pivot hole 552 changes, the amount of swing of the rotating arm member 550 required to correspond to the amount of change changes. That is, the amount of swing of the rotating arm member 550 when the distance between the sliding protrusion 574 and the pivot hole 552 changes by a predetermined amount in a state in which the right end of the sliding protrusion 574 and the selection wall portion 553d abuts is smaller than the amount of swing of the rotating arm member 550 when the distance changes by a predetermined amount in a state in which the right end of the sliding protrusion 574 and the second non-transmission wall portion 553c abuts. Therefore, the swing speed of the rotating arm member 550 relative to the speed of the rotating crank member 570 can be changed depending on whether the sliding protrusion 574 rotates along the second non-transmission wall portion 553c or along the selection wall portion 553d.

[0254] Returning to Fig. 28 to Fig. 31, Fig. 28 to Fig. 31 are front views of the rotating arm member 550 and the rotating crank member 570, illustrating the swing of the rotating arm member 550 and the rotation of the rotating crank member 570 in time series. Note that Fig. 28(a) shows the above-mentioned upward orthogonal state (the rotating arm member 550 is disposed in the retracted position), and Fig. 28 to Fig. 31 sequentially show the state in which the rotating crank member 570 is rotated counterclockwise as viewed from the front, with the irregular elongated hole 553 and a part of the rotating crank member 570 shown by hidden lines, and the front plate member 546 and the protrusion 541b of the telescopic performance device 540 shown by imaginary lines.

[0255] 28 to 31, the position of the telescopic performance device 540, which is telescopic in the vertical direction, is detected by a position detection sensor (not shown), and the swinging is stopped in that position. That is, in Fig. 28 to 31, the protrusion 541b moves only in the vertical direction. In this case, the swinging of the telescopic performance device 540 is prevented by the resistance between it and the drive gear 532 of the first drive device 530 (see Fig. 25).

[0256] 28(a), the rotating crank member 570 is in an upward orthogonal state. In this case, the reference horizontal line O is set at a position vertically downward by a distance h1 from the protrusion 541b. In other words, when the rotating crank member 570 is in an upward orthogonal state, the protrusion 541b is disposed at a position vertically upwardly spaced by a distance h1 from the reference horizontal line O.

[0257] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state shown in FIG. 28(a) (rotated counterclockwise from the upward orthogonal state (see FIG. 28(a)) by an angle T1), the sliding protrusion 574 is moved along the transmission groove portion 553a of the irregular elongated hole 553, and the protrusion 541 is moved vertically upward from the reference horizontal line O by a distance h2 (h2 ​

[0258] From the state of FIG. 28(b), when the rotating crank member 570 is rotated counterclockwise in a front view (rotated counterclockwise by an angle T2 (T2 ≒ 180 degrees > T1) from the upward orthogonal state (see FIG. 28(a))), the sliding protrusion 574 is moved in the transmission groove portion 553a of the irregular long hole 553 (transmission region), enters the region facing the second non-transmission wall portion 553c, and the protrusion 541 is disposed at a position separated from the reference horizontal line O by a distance h3 (h3 < h2) vertically upward (see FIG. 29(a)). That is, the rotating arm member 550 is swung.

[0259] From the state of FIG. 28(c), when the rotating crank member 570 is rotated counterclockwise in a front view (rotated counterclockwise by an angle T3 (T3 > T2) from the upward orthogonal state (see FIG. 28(a))), the sliding protrusion 574 is slid on the second non-transmission wall portion 553c of the irregular long hole 553, and the state of FIG. 29(b) is reached. During this period, since the inner peripheral surface of the irregular long hole 553 is not arranged in the moving direction of the sliding protrusion 574, the sliding protrusion 574 idles with respect to the rotating arm member 550, and the driving force is not transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmission region), and the protrusion 541 is maintained at a position separated from the reference horizontal line O by a distance h3 vertically upward.

[0260] When the rotating arm member 550 is rotated clockwise in a front view from the states of FIGS. 29(a) and 29(b), the sliding protrusion 574 is pushed by the second non-transmission wall portion 553c toward the rotation axis of the rotating crank member 570. In this case, the movement of the sliding protrusion 574 is restricted, and thereby, the swinging of the rotating arm member 550 is restricted. Therefore, the rotating arm member 550 is prevented from rotating clockwise in a front view from the states of FIGS. 29(a) and 29(b).

[0261] 29(a), stopping the rotating crank member 570 is considered. However, if the performance speed of the rotating arm member 550 is kept high until just before it reaches the extended position and the rotating crank member 570 is suddenly stopped, a load is applied to the second drive device 560, and if the speed reduction of the rotating crank member 570 is made gradual, the performance effect cannot be improved.

[0262] On the other hand, in this embodiment, as shown in Figs. 28 and 29, the rotation of the rotating arm member 550 can be stopped in the state of Fig. 29(a) by rotating the rotating crank member 570 to the state of Fig. 29(b) without stopping it in the state of Fig. 29(a) (the protrusion 541 can be stopped at a position vertically upwardly spaced by a distance h3 from the reference horizontal line O). This allows the speed of the rotating crank member 570 to be maintained until the rotating arm member 550 reaches the extended position, and then the rotating crank member 570 can be decelerated from the state of Fig. 29(a) to the state of Fig. 29(b). Therefore, it is not necessary to suddenly stop the rotating crank member 570. Therefore, it is possible to achieve both an improvement in the performance effect of the rotating arm member 550 and an improvement in the durability of the second drive device 560.

[0263] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state of FIG. 29(b) (rotated counterclockwise from the upward orthogonal state (see FIG. 28(a)) by an angle T4 (T4 ≈ 270 degrees > T3)), the sliding protrusion 574 slides on the second non-transmitting wall portion 553c of the irregular elongated hole 553, and the state of FIG. 30(a) is reached. During this time, since the inner circumferential surface of the irregular elongated hole 553 is not disposed in the moving direction of the sliding protrusion 574, the sliding protrusion 574 rotates freely with respect to the rotating arm member 550, and no driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmitting region), and the protrusion 541 is maintained at a position spaced vertically upward from the reference horizontal line O by a distance h3.

[0264] That is, while the rotating crank member 570 rotates 1 / 4 revolution counterclockwise from the state shown in FIG. 29(a), the rotating arm member 550 is maintained in the same posture, and the protrusion 541b is maintained in the same position. In the present embodiment, the length during which the rotating arm member 550 is maintained in the same posture and the protrusion 541b is maintained in the same position is set to the length during which the rotating crank member 570 rotates 1 / 4 revolution, but it is not necessary to be limited thereto. The length during which the front plate member 546 continues to be positioned in the lower position can be changed by changing the length of the second non-transmitting wall portion 553c (see FIG. 28(a)) of the irregular elongated hole 553. For example, by making the second non-transmitting wall portion 553c longer than in the present embodiment, the length during which the front plate member 546 continues to be positioned in the lower position can be made longer than in the present embodiment.

[0265] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state shown in FIG. 30(a) (rotated counterclockwise by an angle T5 (T5>T4) from the upward orthogonal state (see FIG. 28(a))), the sliding protrusion 574 pushes up the selected wall portion 553d of the irregular elongated hole 553, and the protrusion 541 reaches a state (see FIG. 30(b)) in which it is positioned at a position spaced a distance h2 (h2>h3) vertically upward from the reference horizontal line O. During this time, the inner circumferential surface of the irregular elongated hole 553 is positioned in the moving direction of the sliding protrusion 574 and they come into contact with each other, so that a driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (transmission region).

[0266] That is, when the rotating arm member 550 and the rotating crank member 570 are rotated counterclockwise in a front view, the selective wall portion 553d and the sliding protrusion portion 574 come into contact with each other, whereby the driving force is transmitted to the rotating arm member 550 (transmission region).

[0267] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state of FIG. 30(b) (rotated counterclockwise from the upward orthogonal state (see FIG. 28(a)) by an angle T6 (T6>T5)), the sliding protrusion 574 enters the region facing the first non-transmitting wall portion 553b of the irregular elongated hole 553, and the protrusion 541 reaches a state (see FIG. 31) in which it is disposed at a position spaced vertically upward from the reference horizontal line O by a distance h1 (h1>h2). During this period, the inner circumferential surface of the irregular elongated hole 553 is disposed in the moving direction of the sliding protrusion 574 and they come into contact with each other, so that the driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (transmission region).

[0268] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state in Fig. 31, the sliding protrusion 574 is moved through a region facing the first non-transmitting wall portion 553b of the irregular elongated hole 553, and reaches the state in Fig. 28(a). During this time, since the inner circumferential surface of the irregular elongated hole 553 is not disposed in the moving direction of the sliding protrusion 574, the sliding protrusion 574 rotates freely with respect to the rotating arm member 550, and no driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmitting region).

[0269] 31, the sliding protrusion 574 is pressed by the second non-transmitting wall portion 553c toward the rotation axis of the rotating crank member 570. In this case, the movement of the sliding protrusion 574 is restricted, thereby restricting the swing of the rotating arm member 550. Therefore, the rotating arm member 550 is prevented from rotating counterclockwise as viewed from the front from the state of FIG.

[0270] Here, stopping the rotating crank member 570 is considered as a method for stopping the rotation of the rotating arm member 550 in the state shown in Fig. 31. However, if the performance speed of the rotating arm member 550 is kept high until just before it reaches the retracted position and the rotating crank member 570 is suddenly stopped, a load is applied to the second drive device 560, and if the speed reduction of the rotating crank member 570 is made gradual, it becomes impossible to improve the performance effect.

[0271] On the other hand, in this embodiment, the rotation of the rotating arm member 550 can be stopped in the state of FIG. 31 by rotating the rotating crank member 570 to the state of FIG. 28(a) without stopping it in the state of FIG. 31. This allows the speed of the rotating crank member 570 to be maintained until the rotating arm member 550 reaches the extended position, and then the rotating crank member 570 can be decelerated from the state of FIG. 31 to the state of FIG. 28(a). Therefore, it is not necessary to suddenly stop the rotating crank member 570. Therefore, it is possible to improve both the performance effect of the telescopic performance device 540 linked to the rotating arm member 550 and the durability of the second drive device 560.

[0272] As shown in Figures 28 to 31, by rotating the rotating crank members 570 once in the same direction, the rotating arm members 550 can be swung back and forth between the retracted position and the extended position.

[0273] From these facts, when the rotating crank member 570 is rotated counterclockwise at a uniform speed as shown in FIG. 28 to FIG. 31, in a period half the rotation period of the rotating crank member 570, the protrusion 541b moves from a position separated vertically upward from the reference horizontal line O by a distance h1 to a position separated vertically upward by a distance h3 (h3 h3) to a position spaced apart from the rotating crank member 570. This makes it possible to double the moving speed of the protrusion 541b (the moving speed of the extension / contraction performance device 540 in the extension / contraction direction) even when the rotating crank member 570 moves at a constant speed.<h1>

[0274] Here, when the rotating arm member 550 is in the retracted position, the rotating arm member 550 and the rotating crank member 570 can form an upward orthogonal state (see FIG. 28(a)), and when the rotating arm member 550 is in the extended position, the rotating arm member 550 and the rotating crank member 570 can form a downward orthogonal state (see FIG. 29(a)). Note that the downward orthogonal state can be formed by rotating the rotating crank member 570 a predetermined amount clockwise when viewed from the front from the state of FIG. 29(a).

[0275] Therefore, in this embodiment, the rotating crank member 570 is rotated half a revolution (180 degrees) to swing the rotating arm member 550 from the retracted position to the extended position. Therefore, when the rotating crank member 570 is rotated at a constant speed, the time required for the rotating arm member 550 to be swung from the retracted position to the extended position (see FIG. 28(a) to FIG. 29(a)) can be made equal to the time required for the rotating arm member 550 to be swung from the retracted position to the extended position (see FIG. 29(a) to FIG. 31 to FIG. 28(a)).

[0276] The relationship between the swing of the rotating arm member 550 and the rotation of the rotating crank member 570 will be described with reference to Fig. 32 to Fig. 35. Fig. 32 to Fig. 35 are front views of the rotating arm member 550 and the rotating crank member 570, illustrating the swing of the rotating arm member 550 and the rotation of the rotating crank member 570 in chronological order. Note that Fig. 32 to Fig. 35 illustrate a state in which the rotating crank member 570 is rotated clockwise when viewed from the front, with the irregular elongated hole 553 and a part of the rotating crank member 570 being illustrated with hidden lines, and the front plate member 546 and the protrusion 541b of the extension and retraction performance device 540 being illustrated with imaginary lines.

[0277] In addition, in Figure 32(a), the above-mentioned upward orthogonal state is formed (the pivot arm member 550 is placed in the retracted position), and in Figures 32(b) to 35, the states in which the pivot arm member 550 and the pivot crank member 570 have been rotated a predetermined amount from Figure 32(a) are shown in chronological order.

[0278] 32(a), the rotating crank member 570 is in an upward orthogonal state. In this case, the protrusion 541b is disposed at a position spaced vertically above the reference horizontal line O by a distance h1.

[0279] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state of FIG. 32(a) (rotated clockwise by an angle T11 from the upward orthogonal state (see FIG. 32(a))), the sliding protrusion 574 is moved through a region facing the first non-transmitting wall portion 553b of the irregular elongated hole 553, and the state of FIG. 32(b) is reached. During this time, since the inner circumferential surface of the irregular elongated hole 553 is not disposed in the moving direction of the sliding protrusion 574, the sliding protrusion 574 rotates freely with respect to the rotating arm member 550, and no driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmitting region), and the protrusion 541 is maintained at a position spaced vertically upward from the reference horizontal line O by a distance h1.

[0280] 32(b), the movement of the sliding protrusion 574 is restricted, thereby restricting the swing of the rotating arm member 550. Therefore, the rotating arm member 550 is prevented from rotating counterclockwise when viewed from the front from the state of FIG.

[0281] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state shown in FIG. 32(b) (rotated clockwise by an angle T12 (T12>T11) from the upward orthogonal state (see FIG. 32(a))), the sliding protrusion 574 is slightly separated from the inner peripheral surface of the irregular elongated hole 553, and the rotating arm member 550 is swung downward by the action of gravity, as shown in FIG. 33(a). In this case, in a clearance portion D between the state shown in FIG. 32(b) and the time when the sliding protrusion 574 passes over the first non-transmitting wall portion 553b and reaches the second non-transmitting wall portion 553c, no driving force is transmitted to the rotating arm member 550 (non-transmitting region), and the protrusion 541 moves vertically upward from the reference horizontal line O by a distance h4 (h4

[0282] ​From the state of FIG. 33(a), when the rotating crank member 570 is rotated clockwise in a front view (rotated clockwise by an angle T13 (T13 > T12) from the upward orthogonal state (see FIG. 32(a))), as shown in FIG. 33(b), the sliding projection 574 abuts against the second non-transmission wall portion 553c of the deformed long hole 553 of the rotating arm member 550 that swings downward under the action of gravity. That is, from the state of FIG. 33(b) to the state of FIG. 34(a), a driving force is transmitted to the rotating arm member 550 (transmission region). In the state of FIG. 33(b), the protrusion 541 is disposed at a position separated from the reference horizontal line O by a distance h5 (h5 < h4) vertically upward.

[0283] From the state of FIG. 33(b), when the rotating crank member 570 is rotated clockwise in a front view (rotated clockwise by an angle T14 (T14 ≒ 90 degrees > T13) from the upward orthogonal state (see FIG. 32(a))), the sliding projection 574 is received in the right end portion of the second non-transmission wall portion 553c of the deformed long hole 553, and the protrusion 541 reaches a state where it is disposed at a position separated from the reference horizontal line O by a distance h3 vertically upward (see FIG. 34(a)). During this period, the inner peripheral surface of the deformed long hole 553 abuts against the moving direction of the sliding projection 574, and a driving force is transmitted to the rotating arm member 550 (transmission region).

[0284] Here, the rotation of the rotating crank member 570 shown from FIG. 32(b) to FIG. 34(a) and the rotation of the rotating crank member 570 shown from FIG. 30(a) to FIG. 31 have different rotation directions of the rotating crank member 570, but the rotation regions (phases) of the rotating crank member 570 are the same.

[0285] In this case, in the rotation of the rotating crank member 570 shown from FIG. 32(b) to FIG. 34(a), a driving force is not transmitted to the rotating arm member 550 while the inner peripheral surface of the deformed long hole 553 does not abut against the moving direction of the sliding projection 574 of the rotating crank member 570 (non-transmission region), while in the rotation of the rotating crank member 570 shown from FIG. 30(a) to FIG. 31, a driving force is always transmitted to the rotating arm member 550 (transmission region).

[0286] Therefore, the manner in which the driving force is transmitted to the rotating arm member 550 can be changed depending on the rotation direction of the rotating crank member 570. As a result, by reversing the rotation direction of the rotating crank member 570, two different performance modes of the rotating arm member 550 can be formed.

[0287] That is, in this embodiment, when the sliding protrusion 574 of the rotating crank member 570 rotates between Figures 32(a) and 34(a), if the rotating crank member 570 rotates clockwise as viewed from the front, the rotating arm member 550 is swung by free fall depending on the acceleration of gravity until the sliding protrusion 574 abuts against the inner circumferential surface of the irregular elongated hole 553 (non-transmission region). On the other hand, if the rotating crank member 570 rotates counterclockwise as viewed from the front, the rotating arm member 550 is swung at a speed depending on the rotation speed of the rotating crank member 570 (transmission region).

[0288] As a result, even if the rotational speed of the rotating crank member 570 is constant, by reversing the rotational direction of the rotating crank member 570, the variation in the swing speed of the rotating arm member 550 can be increased when the rotating crank member 570 is arranged in the same phase.

[0289] Furthermore, since the increase in the variation in the swing speed of the rotating arm member 550 is achieved by the shape of the irregular elongated hole 553 (the formation of the margin D), other components such as a change-over switch for changing the manner in which the driving force is transmitted to the rotating arm member 550 are not required, and the cost of components can be reduced.

[0290] In this embodiment, the clearance portion D is formed on the pivot hole 552 side of the rotating arm member 550. Therefore, it is possible to lengthen the distance that the protrusion 541b moves downward while the sliding protrusion 574 passes a predetermined distance through the clearance portion D, compared to the case where the clearance portion D is formed on the opposite side of the pivot hole 552 with respect to the rotation axis of the rotating crank member 570. Therefore, it is possible to make the change in the operation of the rotating arm member 550 when the rotation direction of the rotating crank member 570 is changed noticeable, while restricting the formation range of the clearance portion D of the rotating crank member 570.

[0291] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state of Fig. 34(a) (rotated clockwise by an angle T15 (T15>T14) from the upward orthogonal state (see Fig. 32(a))), the sliding protrusion 574 slides on the second non-transmitting wall portion 553c of the irregular elongated hole 553, and the state of Fig. 34(b) is reached. During this time, since the inner circumferential surface of the irregular elongated hole 553 is not disposed in the moving direction of the sliding protrusion 574, the sliding protrusion 574 rotates freely with respect to the rotating arm member 550, and no driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmitting region), and the protrusion 541 is maintained at a position spaced vertically upward from the reference horizontal line O by a distance h3.

[0292] When the rotating arm member 550 is rotated clockwise as viewed from the front from the state shown in Fig. 34(b), the sliding protrusion 574 is pushed by the second non-transmitting wall portion 553c toward the rotation axis of the rotating crank member 570. In this case, the movement of the sliding protrusion 574 is restricted, and therefore the swing of the rotating arm member 550 is restricted. Therefore, the rotating arm member 550 is prevented from rotating clockwise as viewed from the front from the state shown in Fig. 34(b).

[0293] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state of FIG. 34(b) (rotated clockwise by an angle T16 (T16 ≈ 180 degrees > T15) from the upward orthogonal state (see FIG. 32(a))), the sliding protrusion 574 slides on the second non-transmitting wall portion 553c of the irregular elongated hole 553, and the state of FIG. 35(a) is reached. During this time, since the inner circumferential surface of the irregular elongated hole 553 is not disposed in the moving direction of the sliding protrusion 574, the sliding protrusion 574 rotates freely with respect to the rotating arm member 550, and no driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (non-transmitting region), and the protrusion 541 is maintained at a position spaced vertically upward from the reference horizontal line O by a distance h3.

[0294] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state in FIG. 35(a) (rotated clockwise by angle T17 (T17>T16) from the upward orthogonal state (see FIG. 32(a))), the sliding protrusion 574 is moved in the transmission groove portion 553a (transmission area), and the protrusion 541 reaches a state (see FIG. 35(b)) where it is positioned vertically upward from the reference horizontal line O by a distance h2 (h2>h3). That is, the rotating arm member 550 is swung.

[0295] Here, when the rotation of the rotating crank member 570 and the swing of the rotating arm member 550 are always linked, it is difficult to shift the timing of starting the rotating crank member 570 and the rotating arm member 550. Therefore, when starting the rotating crank member 570 and the rotating arm member 550, it is necessary to generate a large force that is the rigidity of the force that overcomes the inertia of each member. Therefore, a driving device with a large driving force is required, and there is a risk that the driving device will become large in size.

[0296] On the other hand, in this embodiment, it is possible to shift the timing of starting the rotating crank member 570 and the rotating arm member 550. That is, for example, only the rotating crank member 570 is rotated from the state of Fig. 34(b) to the state of Fig. 35(a), and the rotating arm member 550 can be started by being linked to the rotating crank member 570 when it reaches the state of Fig. 35(b) from the state of Fig. 35(a).

[0297] As a result, the momentum of the rotating crank member 570 can be used to start the rotating arm member 550, making it possible to reduce the driving force required for the second driving device 560. Therefore, the second driving device 560 can be made smaller in size.

[0298] When the rotating crank member 570 is rotated clockwise as viewed from the front from the state shown in Fig. 35(b), the sliding protrusion 574 is moved along the transmission groove 553a, and reaches the state shown in Fig. 32(a). During this time, the inner circumferential surface of the irregular elongated hole 553 is disposed in the moving direction of the sliding protrusion 574 and they come into contact with each other, so that the driving force is transmitted from the sliding protrusion 574 to the rotating arm member 550 (transmission region). That is, the rotating arm member 550 is swung.

[0299] From these facts, when the rotating crank member 570 is rotated clockwise at a uniform speed as shown in FIG. 32 to FIG. 35, in a period of 1 / 4 of the rotation period of the rotating crank member 570, the protrusion 541b moves from a position that is separated vertically upward from the reference horizontal line O by a distance h1 to a position that is separated by a distance h3 (h3 h3) to a position spaced apart from the rotating crank member 570. This makes it possible to double the moving speed of the protrusion 541b (the moving speed of the extension / contraction performance device 540 in the extension / contraction direction) even when the rotating crank member 570 moves at a constant speed.<h1>

[0300] Also, the moving speed of the rotating arm member 550 is partially accelerated by the gravitational acceleration when moving downward, while on the other hand, when moving upward, the speed is always set to the rotation speed of the rotating crank member 570. This makes it possible to change the manner of the speed change of the protrusion 541b (the telescopic performance device 540) depending on the direction of movement of the protrusion 541b (the telescopic performance device 540).

[0301] With reference to FIG. 36, a change in the distance of the protrusion 541b (the extension and retraction performance device 540) from the reference horizontal line O when the rotating crank member 570 is rotated clockwise or counterclockwise will be described.

[0302] Fig. 36 is a graph showing the distance of the protrusion 541b (see Fig. 28(a)) from the reference horizontal line O. In the graph shown in Fig. 36, the horizontal axis shows the swing angle increasing from the upper orthogonal state (see Fig. 28(a)) of the rotating crank member 570 at the left end toward the right, and the vertical axis shows the distance of the protrusion 541b from the reference horizontal line O.

[0303] In Fig. 36, the distance of the protrusion 541b from the reference horizontal line O when the rotating crank member 570 is rotated counterclockwise is shown by a curve CC1, and the distance of the protrusion 541b from the reference horizontal line O when the rotating crank member 570 is rotated clockwise is shown by a curve CW1. The curves CC1 and CW1 correspond to the states of the protrusion 541b in Figs. 28 to 35, respectively, and a curve obtained by inverting the curve CC1 from left to right is shown by an imaginary line as a curve CC2 for comparison of the respective curves when the rotating crank member 570 is disposed in the same phase. By comparing the curves CC1 and CW1, as described above, the rotation direction of the rotating crank member 570 is inverted, and the rising speed and the falling speed of the protrusion 541b moved up and down by the rotating arm member 550 can be changed.

[0304] As a comparison object with curve CW1, a case where the rotating arm member 550 (see FIG. 28(a)) is placed in the retracted position until the sliding protrusion 574 abuts against the second non-transmitting wall portion 553c (see FIG. 28(a)) when the rotating crank member 570 rotates clockwise is shown by a dashed line as curve CW2. This corresponds to a case where the biasing force of the torsion spring 517a (see FIG. 23) for swinging the rotating arm member 550 upward is set large. In this case, the period during which the rotating arm member 550 is placed in the retracted position can be made longer.

[0305] In curves CC1 and CW1, in angle range N1 where the distance of protrusion 541b (see FIG. 28(a)) from horizontal reference line O is maintained unchanged, a non-transmission region is formed where no driving force is transmitted between rotating crank member 570 and rotating arm member 550 (see FIG. 28(a)). Note that the width of this angle range N1 can be adjusted by the formation width of second non-transmission wall portion 553c (see FIG. 28(a)).

[0306] In addition, in the curve CW1, in an angle range N2 until the sliding protrusion 574 of the rotating crank member 570 (see FIG. 28(a)) abuts against the irregular elongated hole 553 (see FIG. 28(a)) of the rotating arm member 550, a non-transmission region is formed in which no driving force is transmitted between the rotating crank member 570 and the rotating arm member 550. The width of this angle range N2 can be adjusted by the formation width of the first non-transmission wall portion 553b (see FIG. 28(a)).

[0307] As shown in FIG. 36, between angles T11 to T14, which is the case when the rotating crank member 570 (see FIG. 28(a)) is arranged in the same phase, and between angles T4 to T6, the shapes of the curves CW1 and CC1 are different (the curve CW1 does not overlap with the curve CC2, which is the left-right mirror image of the curve CC1).

[0308] In other words, when the rotating crank member 570 (see FIG. 28(a)) rotates in a manner lifting the rotating arm member 550 (see FIG. 28(a)) between angles T4 and T6, the curve is gentler than when the rotating crank member 570 rotates in a manner pushing down the rotating arm member 550 between angles 11 and T14.

[0309] This is because, on curve CW1, the sliding protrusion 574 (see Figure 28(a)) abuts against the second non-transmitting wall portion 553c (see Figure 28(a)) of the irregular elongated hole 553, causing the pivot arm member 550 (see Figure 28(a)) to rotate, and on curve CC1, the sliding protrusion 574 abuts against the selected wall portion 553d (see Figure 28(a)) of the irregular elongated hole 553, causing the pivot arm member 550 to rotate.

[0310] 28(a) will be explained again. As described above, in the irregular elongated hole 553, the right end of the second non-transmitting wall portion 553c is formed along an arc S1 centered on the shaft support hole 552 (the angle formed with the arc S1 is small), while the right end of the selection wall portion 553d is formed in a manner to intersect with an arc S2 centered on the shaft support hole 552 at an angle larger than the angle formed with the right end of the second non-transmitting wall portion 553c and the arc S1.

[0311] In this case, when the distance between the sliding protrusion 574 and the pivot hole 552 changes, the amount of swing of the rotating arm member 550 required to accommodate the amount of change also changes. That is, the amount of swing of the rotating arm member 550 when the distance between the sliding protrusion 574 and the pivot hole 552 changes by a predetermined amount in a state in which the sliding protrusion 574 and the right end of the selection wall portion 553d are in contact with each other is smaller than the amount of swing of the rotating arm member 550 when the distance changes by a predetermined amount in a state in which the sliding protrusion 574 and the right end of the second non-transmission wall portion 553c are in contact with each other.

[0312] Therefore, as shown in FIG. 36, even when the rotating crank member 570 is rotated at a constant speed, the moving speed of the protrusion 541b when the rotating crank member 570 is arranged in the same phase can be changed depending on the rotation direction of the rotating crank member 570.

[0313] 28 to 35, the case where the rotating crank member 570 rotates in one direction has been described, but it is also possible to reverse the rotation direction of the rotating crank member 570 midway. As the timing for reversing the rotation direction of the rotating crank member 570, a state in which the sliding protrusion 574 is arranged opposite the first non-transmitting wall portion 553b (for example, see Figs. 28(a), 31, 32(a) and 32(b), the rotating arm member 550 is arranged in the retracted position) or a state in which the sliding protrusion 574 is arranged opposite the second non-transmitting wall portion 553c (for example, see Figs. 29(a), 29(b), 34(b) and 35(a), the rotating arm member 550 is arranged in the extended position) is preferable.

[0314] In this case, since the rotating arm member 550 is not abutted against the rotational direction of the rotating crank member 570, it is possible to suppress the resistance that is applied from the rotating arm member 550 to the rotating crank member 570 when the rotational direction of the rotating crank member 570 is reversed. Also, in this embodiment, a position detection sensor (not shown) is provided that detects whether the rotating arm member 550 is disposed at the retracted position or the extended position, so that it is possible to easily control the reversal of the rotational direction of the rotating crank member 570 when the rotating arm member 550 is disposed at the retracted position or the extended position.

[0315] By reversing the rotation direction of the rotating crank member 570, the variety of reciprocating motions of the extension and retraction performance device 540 in the up and down directions can be increased.

[0316] For example, from a state in which the rotating arm member 550 is disposed at the retracted position (see FIG. 28(a)), the rotating crank member 570 is rotated counterclockwise a half turn (see FIG. 29(a)), and then the direction of rotation of the rotating crank member 570 is reversed and rotated clockwise a half turn, so that the rotating arm member 550 is disposed at the retracted position (see FIG. 28(a)). That is, this is the case in which the sliding protrusion 574 is moved on the opposite side of the shaft support hole 552.

[0317] In this case, the protrusion 541b of the telescopic performance device 540 moves from a position that is vertically upwardly spaced a distance h1 from the reference horizontal line O to a position that is a distance h3 (h3 In this case, the protrusion 541b moves upward along a curve CW1 (see FIG. 36) that extends from 180 degrees to 360 degrees on the horizontal axis.<h1>

[0318] As a result, when the rotating crank member 570 rotates at a constant speed, the period during which the protrusion 541b of the extension / retraction performance device 540 moves downward a predetermined distance (h1-h3) can be made the same as the period during which it moves upward a predetermined distance (h1-h3).

[0319] Also, for example, from a state in which the rotating arm member 550 is disposed at the retracted position (see FIG. 32(a)), the rotating crank member 570 is rotated 1 / 4 turn clockwise (see FIG. 34(a)), and then the direction of rotation of the rotating crank member 570 is reversed and rotated 1 / 4 turn counterclockwise, thereby disposing the rotating arm member 550 at the retracted position (see FIG. 32(a)). That is, this is the case in which the sliding protrusion 574 moves on the side close to the shaft support hole 552.

[0320] In this case, the protrusion 541b of the telescopic performance device 540 moves from a position that is vertically upwardly spaced a distance h1 from the reference horizontal line O to a position that is a distance h3 (h3 In this case, the protrusion 541b moves upward along a curve CC1 (see FIG. 36) that extends from 270 degrees to 360 degrees on the horizontal axis.<h1>

[0321] As a result, when the rotating crank member 570 rotates at a constant speed, the period during which the protrusion 541b of the telescopic performance device 540 moves downward a predetermined distance (h1-h3) can be made the same as the period during which it moves upward a predetermined distance (h1-h3), and the predetermined period can be made shorter than when the sliding protrusion 574 moves on the opposite side of the shaft support hole 552.

[0322] In addition, when the protrusion 541b of the telescopic performance device 540 moves downward, it can be partially made to fall freely (from angle T11 to angle T13), while when the protrusion 541b of the telescopic performance device 540 moves upward, it is always moved at a speed according to the rotation speed of the rotating crank member 570. Therefore, even if the rotation speed of the rotating crank member 570 is the same, the movement mode (degree of speed change) of the telescopic performance device 540 when the rotating crank member 570 is arranged in the same phase can be changed depending on the movement direction of the protrusion 541b of the telescopic performance device 540. In other words, the curve CW1 and the curve CC2 in the range from angle T11 to angle T13 in FIG. 36 can be made different.

[0323] Next, a description will be given of the difference in the swing angle due to the difference in the stretching state of the stretching performance device 540. First, a description will be given of the swing angle when the stretching performance device 540 forms the stretched state.

[0324] 37 to 39 are front views of the composite motion unit 500. Note that, in FIG. 37 to FIG. 39, the case where the telescopic performance device 540 forms an extended state (the case where the rotating arm member 550 is disposed at the extended position) is illustrated. Also, in FIG. 37, the state where the protrusion 541b of the telescopic performance device 540 is disposed on the vertical line of the first shaft portion 512 of the base member 510 is illustrated, in FIG. 38, the state where the protrusion 541 is moved counterclockwise in front view from the state of FIG. 37, and in FIG. 39, the state where the protrusion 541 is moved clockwise in front view from the state of FIG. 37. Note that the posture of the rotating arm member 550 illustrated in FIG. 37 to FIG. 39 is the same as the posture of the rotating arm member 550 illustrated in FIG. 29(a). Therefore, in FIG. 37 to FIG. 39, the front plate member 546 is disposed at a position spaced upward from the reference horizontal line O by a distance h3.

[0325] As shown in Fig. 37 to Fig. 39, when the telescopic performance device 540 forms the extended state, the swing trajectory of the protrusion 541b is formed in an arc shape centered on the first shaft portion 512 and is along the extension direction of the arc hole 554 of the rotating arm member 550. In other words, the arc hole 554 is extended along the swing trajectory of the protrusion 541b. Therefore, the inner surface of the arc hole 554 is not disposed facing the swing direction of the protrusion 541b, and the arc hole 554 does not act as a stopper that stops the swing of the protrusion 541b. Therefore, the swing angle of the protrusion 541b depends on the manner in which the swing of the rotating plate 520 is regulated. That is, the rotating plate 520 can swing until it abuts against the third stopper portion 518c, and the protrusion portion 541b can swing counterclockwise when viewed from the front up to a swing angle θ1, and the rotating plate 520 can swing until it abuts against the second stopper portion 518b, and the protrusion portion 541b can swing clockwise when viewed from the front up to a swing angle θ2.

[0326] 39, when the protrusion 541b is swung to the left side when viewed from the front at a swing angle θ2, the protrusion 541b moves away from the arc-shaped hole 554 of the rotating arm member 550. In this case, the telescopic performance device 540 moves in the telescopic direction independently of the rotating arm member 550, and the protrusion 541b cannot return to the arc-shaped hole 554, which may cause malfunction.

[0327] In contrast, in this embodiment, even when the protrusion 541b is separated from the arc-shaped hole 554 of the rotating arm member 550, the first raising fastening part 541c and the guide fastening part 541e of the telescopic performance device 540 are disposed so as to be engageable with the rotating arm member 550, so that the protrusion 541b can be aligned with the arc-shaped hole 554. That is, the telescopic performance device 540 can be prevented from moving in the telescopic direction independently of the rotating arm member 550.

[0328] This makes it possible to shorten the length of the rotating arm member 550 while eliminating the defect that the protrusion 541b cannot return to the arc-shaped hole 554. This makes it possible to reduce the arrangement area of ​​the rotating arm member 550 and thereby ensure an arrangement area for other movable members. In addition, the material cost of the rotating arm member 550 can be reduced.

[0329] Furthermore, if the rotating arm member 550 swings with the protrusion 541b spaced away from the arc-shaped hole 554 (see FIG. 39), the positional relationship between the protrusion 541b and the arc-shaped hole 554 will be shifted, making it difficult for the protrusion 541b to return to the arc-shaped hole 554, which may result in malfunction. In contrast, in this embodiment, the sliding protrusion 574 comes into contact with the irregular elongated hole 553, thereby preventing the rotating arm member 550 from swinging (see FIG. 39).

[0330] In addition, the movement trajectory of the point on the side farthest from the rotation axis of the sliding protrusion 574 (the point farthest from the rotation axis) is formed along the side of the irregularly shaped long hole 553 that abuts against the sliding protrusion 574 (see Figure 39), so that the rotating crank member 570 can be rotated counterclockwise from the state in Figure 39 while maintaining the posture of the rotating arm member 550.

[0331] 28 to 31, for example, consider a case in which the protrusion 541b moves away from the arc-shaped hole 554 immediately after the rotating arm member 550 is placed in the extended position (see FIG. 29(a)), and then the protrusion 541b returns to the arc-shaped hole 554 before the rotating crank member 570 is placed in the state shown in FIG. 30(a). If the protrusion 541b has returned to the arc-shaped hole 554, even if the rotating crank member 570 is further rotated and the rotating arm member 550 swings to the state shown in FIG. 30(b), no operational malfunction occurs in which the protrusion 541b cannot return to the arc-shaped hole 554.

[0332] In this case, when the rotating arm member 550 and the telescopic performance device 540 are caused to swing, there is no need to control the stop or start of the rotating crank member 570 in accordance with the positional relationship between the protrusion 541b and the arc-shaped hole 554, and the rotating crank member 570 can continue to rotate. In other words, it is only necessary to control the timing of the swing of the telescopic performance device 540, and there is no need to control the rotating crank member 570, which can be allowed to continue to rotate. Therefore, it is possible to reduce the control burden of the complicated operation of swinging the telescopic performance device 540 and the rotating arm member 550 at different timings.

[0333] In this embodiment, a mouth portion 554a is formed that widens the width of the arc-shaped hole 554 toward the opening end (left end in FIG. 39) of the arc-shaped hole 554. This allows a large tolerance for positional deviation (positional deviation in the extension / retraction direction of the extension / retraction performance device 540) when the protrusion 541b returns to the arc-shaped hole 554, and ensures a large clearance between the first raising fastening portion 541c and the guide fastening portion 541e and the rotating arm member 550.

[0334] Next, a swing angle when the telescopic performance device 540 forms an intermediate state between the extended state and the contracted state will be described. By swinging the rotating arm member 550 clockwise from the extended state (see FIG. 37), the protrusion 541b moves in correspondence with the arc-shaped hole 554, and the telescopic performance device 540 forms the intermediate state.

[0335] 40 to 42 are front views of the composite action unit 500. Note that Fig. 40 to 42 show the case where the telescopic performance device 540 forms an intermediate state (the case where the rotating arm member 550 is disposed halfway between the extended position and the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541b is shorter than that when the telescopic performance device 540 forms an extended state (see Figs. 37 to 39). That is, the swinging trajectory of the protrusion 541b changes depending on the state of the telescopic performance device 540 in the telescopic direction.

[0336] In addition, Figure 40 illustrates a state in which protrusion 541b of extension / retraction performance device 540 is positioned on the vertical line of first axis portion 512 of base member 510, Figure 41 illustrates a state in which protrusion 541 is moved counterclockwise when viewed from the front from the state of Figure 40, and Figure 42 illustrates a state in which protrusion 541 is moved clockwise when viewed from the front from the state of Figure 40.

[0337] 40 to 42 is the same as the posture of the rotating arm member 550 shown in Fig. 28(b). Therefore, in Fig. 40 to 42, the front plate member 546 is disposed at a position spaced upward from the reference horizontal line O by a distance h2.

[0338] At this time, the front plate member 546 moves in conjunction with the upward movement of the arc-shaped hole 554 due to the swinging of the rotating arm member 550. Therefore, the arc-shaped hole 554 has both a function of changing the swing angle of the protrusion 541b as described below and a function of linking the rotating arm member 550 and the front plate member 546. This allows for integration of functions.

[0339] 40 to 42, when telescopic performance device 540 forms an intermediate state, the swing trajectory of protrusion 541b and the shape of arc-shaped hole 554 of rotating arm member 550 have different radii of curvature and postures, although the central axes of the radii of curvature of both coincide at the upper side. Since the swing trajectory of protrusion 541b and arc-shaped hole 554 intersect at angle α1 (see FIG. 42), arc-shaped hole 554 acts as a stopper that stops the swing of protrusion 541b (see FIG. 42).

[0340] 41, when the rotating plate 520 is rotated counterclockwise as viewed from the front, the protrusion 541b does not come into contact with the arc-shaped hole 554. That is, since the rotating plate 520 is allowed to swing until it comes into contact with the third stopper portion 518c, the protrusion 541b is allowed to swing counterclockwise as viewed from the front up to a swing angle θ3 (angle θ3=angle θ1).

[0341] 42, when the rotating plate 520 is rotated clockwise as viewed from the front, the protrusion 541b abuts against the first stopper surface 554b of the arc-shaped hole 554. In this state, the guide fastening portion 541e abuts against the upper side surface of the rotating arm member 550, and the state change in the extension / retraction direction of the extension / retraction performance device 540 is prevented, so that the swing of the extension / retraction performance device 540 is stopped in the state of FIG.

[0342] That is, the rotating plate 520 does not swing until it abuts against the third stopper portion 518c, and the protrusion portion 541b can swing clockwise in a front view up to a swing angle θ4 (angle θ4<angle θ2). Therefore, the swing angle of the protrusion portion 541b can be changed depending on the state of the telescopic performance device 540 in the telescopic direction. This makes it possible to increase the variation of the swing angle of the telescopic performance device 540 by varying the telescopic state of the telescopic performance device 540. Note that in the state of FIG. 42, the guide fastening portion 541e abuts against the main body portion 551 of the rotating arm member 550.

[0343] Next, a description will be given of the swing angle when the telescopic performance device 540 forms the contracted state. By swinging the rotating arm member 550 clockwise from the state where the telescopic performance device 540 is in the intermediate state (see FIG. 40), the protrusion 541b moves in correspondence with the arc-shaped hole 554, and the telescopic performance device 540 forms the contracted state.

[0344] 43 to 45 are front views of the composite action unit 500. Note that Fig. 43 to 45 show the case where the telescopic performance device 540 forms a contracted state (the case where the rotating arm member 550 is disposed at the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541b is shorter than that when the telescopic performance device 540 forms an intermediate state (see Figs. 40 to 42). That is, the swinging trajectory of the protrusion 541b changes depending on the state of the telescopic performance device 540 in the telescopic direction.

[0345] 43 illustrates a state in which the protrusion 541b of the telescopic performance device 540 is disposed on the vertical line of the first shaft portion 512 of the base member 510, FIG. 44 illustrates a state in which the protrusion 541 is moved counterclockwise in front view from the state of FIG. 43, and FIG. 45 illustrates a state in which the protrusion 541 is moved clockwise in front view from the state of FIG. 43. The posture of the rotating arm member 550 illustrated in FIG. 43 to FIG. 45 is the same as the posture of the rotating arm member 550 illustrated in FIG. 28(a). Therefore, in FIG. 43 to FIG. 45, the front plate member 546 is disposed at a position spaced upward from the reference horizontal line O by a distance h1.

[0346] At this time, the front plate member 546 moves in conjunction with the upward movement of the arc-shaped hole 554 due to the swinging of the rotating arm member 550. Therefore, the arc-shaped hole 554 has both a function of changing the swing angle of the protrusion 541b and a function of linking the rotating arm member 550 and the front plate member 546. This allows for integration of functions.

[0347] 43 to 45, when the telescopic performance device 540 forms the contracted state, the shape of the swing trajectory of the protrusion 541b and the shape of the arc-shaped hole 554 of the rotating arm member 550 are different from each other, and the central axis of the curvature radius is reversed. That is, the central axis of the curvature radius of the swing trajectory of the protrusion 541b is below the protrusion 541b, and the central axis of the curvature radius of the arc-shaped hole 554 is disposed above the arc-shaped hole 554. In this case, the swing trajectory of the protrusion 541b and the arc-shaped hole 554 intersect at a formation angle α2 (angle α2>angle α1), and the arc-shaped hole 554 acts as a stopper that stops the swing of the protrusion 541b (see FIGS. 44 and 45).

[0348] 44, when the rotating plate 520 is rotated counterclockwise as viewed from the front, the protrusion 541b abuts against the second stopper surface 554c of the arc-shaped hole 554. In this case, the rotating plate 520 is not swung until it abuts against the third stopper portion 518c (see FIG. 41), and the protrusion 541b is allowed to swung counterclockwise as viewed from the front up to a swing angle θ5 (angle θ5<angle θ1=angle θ3).

[0349] As shown in Fig. 45, when the rotating plate 520 rotates clockwise as viewed from the front, the protrusion 541b abuts against the third stopper surface 554d of the arc-shaped hole 554. In this case, the rotating plate 520 does not swing until it abuts against the third stopper portion 518c, and the protrusion 541b can swing up to a swing angle θ6 in the clockwise direction as viewed from the front (angle θ6<angle θ4<angle θ2). Therefore, the swing angle of the protrusion 541b can be changed depending on the state of the telescopic performance device 540 in the telescopic direction. This allows the variation in the swing width of the telescopic performance device 540 to be increased.

[0350] Here, the angle α2 formed between the movement path of the protrusion 541b and the arc-shaped hole 554 in the contracted state is greater than the angle α1 formed between the movement path of the protrusion 541b and the arc-shaped hole 554 in the intermediate state.

[0351] In the relationship between the swing locus of the protrusion 541b and the arc-shaped hole 554, if the angle is 90 degrees, the protrusion 541b swings in a manner that crosses the arc-shaped hole 554, and the swing angle of the protrusion 541b is minimized. On the other hand, in the relationship between the swing locus of the protrusion 541b and the arc-shaped hole 554, if the angle is 0 degrees (see FIGS. 37 to 39), the protrusion 541b swings along the extension direction of the arc-shaped hole 554, and the swing angle of the protrusion 541b is maximized. Therefore, the swing angle of the protrusion 541b in the contracted state (angle of formation α2) can be made smaller than the swing angle of the protrusion 541b in the intermediate state (angle of formation α1) (angle of formation α1<angle of formation α2).

[0352] As described above, the swing angle of the protrusion 541b is changed by changing the extension / retraction state of the telescopic performance device 540, and at that time, the inner circumferential surface of the arc-shaped hole 554 (the first stopper surface 554b, the second stopper surface 554c, and the third stopper surface 554d) functions as a stopper that regulates the swing angle of the telescopic performance device 540. As a result, the inner circumferential surface of the arc-shaped hole 554 can also be used as a part that regulates the swing angle of the protrusion 541b in each case where the extension / retraction state of the telescopic performance device 540 is different. Therefore, the space required for arranging the stopper that regulates the swing angle of the protrusion 541b can be reduced.

[0353] In addition, the stopper that regulates the swing angle of the telescopic performance device 540 is retracted from the front side of the third pattern display device 81 by placing the rotating arm member 550 in the retracted position. Therefore, unlike the case where a fixed stopper is disposed on the front side of the third pattern display device 81, it is possible to prevent the stopper from remaining on the front side of the third pattern display device 81 even when the rotating arm member 550 is placed in the retracted position. As a result, when the rotating arm member 550 is placed in the retracted position, other members can be placed in front of the third pattern display device 81, so that protruding space for other movable members (for example, the support member 720 of the slide operation unit 700) can be secured.

[0354] In addition, the arc-shaped hole 554 of the rotating arm member 550 has a function as a stopper that restricts the swing angle of the telescopic performance device 540, and a function as a transmission device that transmits the driving force of the second drive device 560 to the telescopic performance device 540 by swinging the rotating arm member 550, thereby causing the telescopic performance device 540 to perform a telescopic operation. This makes it possible to consolidate functions and reduce the number of parts.

[0355] The tilting motion unit 600 and the sliding motion unit 700 will be described with reference to Fig. 46 to Fig. 57. The tilting motion unit 600 is a unit that causes the performance member 620 to perform a swinging motion (tilting motion) (see Fig. 12), and the sliding motion unit 700 is a unit that causes the tilting motion unit 600 to slide in the left-right direction. Fig. 46 is a front perspective view of the tilting motion unit 600 and the sliding motion unit 700, and Fig. 47 is a rear perspective view of the tilting motion unit 600 and the sliding motion unit 700. Note that Figs. 46 and 47 show a state in which the support member 720 (see Fig. 47) of the tilting motion unit 600 and the sliding motion unit 700 is arranged in the retracted position.

[0356] Fig. 48 is an exploded front perspective view of the slide operation unit 700, and Fig. 49 is an exploded rear perspective view of the slide operation unit 700. In Figs. 48 and 49, the tilt operation unit 600 is illustrated without being disassembled in order to facilitate understanding.

[0357] The sliding operation unit 700 mainly comprises a base member 710 formed in the shape of a long plate in the left-right direction, a support member 720 having one end fastened to a slide plate 711 of the base member 710 and formed so as to be able to slide in the left-right direction, a slide rail 730 having one end fastened to the support member 720 and the other end to which the base member 610 of the tilting operation unit 600 is fastened and formed so as to be able to expand and contract in the up-down direction, a connecting member 740 formed so as to be able to slide on the rear rail portion 716 of the main body 710 and pivoted to the pivot support protrusion 612 of the tilting operation unit 600, a driving device 750 that generates a driving force for moving the support member 720 in the left-right direction, and a rear cover member 760 formed on the rear side of the driving device 750 and fastened to the base member 710.

[0358] The base member 710 is a member forming the framework of the sliding operation unit 700, and includes a slide plate 711 formed so as to be slidable in the left-right direction and to which a support member 720 is fastened and fixed from the rear side, a shaft support hole 712 recessed in a circular cross section at the lower left side of the base member 710 as viewed from the rear and supporting a fixed shaft portion 753a, and a long hole recessed in the lower right side of the base member 710 as viewed from the rear, which is aligned with the shaft support hole 712 in the vertical direction and supports the moving shaft portion 754a so as to be slidable. a lever member 714 formed to be swingable up and down by a solenoid and regulating left-right movement of an engaging portion 725 of the support member 720; a front rail portion 715 which protrudes from the upper end of the base member 710 to the front side in a cross-sectionally downward arc shape and on which an upper rolling member 742 of a connecting member 740 rolls; and a rear rail portion 716 which is recessed into the front rail portion 715 from the rear side in a cross-sectionally arc shape and through which an insertion plate portion 741b of the connecting member 740 is inserted.

[0359] Since the lever member 714 restricts the left-right sliding movement of the support member 720 fastened to the slide plate 711, the driving force of the drive device 750 is not required when maintaining the tilting motion unit 600 in the retracted position.

[0360] Here, in this embodiment, since the tilting motion unit 600 is moved along the forming direction (arc track) of the front rail portion 715 and the back rail portion 716, the support member 720 connected to the tilting motion unit 600 may slide left and right due to the action of gravity applied to the tilting motion unit 600. For example, when the tilting motion unit 600 is placed at the retracted position (see FIG. 46), the movement direction of the tilting motion unit 600 is directed obliquely downward along the shape of the front rail portion 715. Therefore, even if the movement direction of the support member 720 connected to the tilting motion unit 600 is the left and right direction along the movement direction of the slide plate 711, there is a risk that the support member 720 may be moved by gravity. In this embodiment, the lever member 714 is swung downward to engage with the locking portion 725 of the support member 720, and the movement of the support member 720 in the left-right direction is restricted, so that the support member 720 can be maintained in the retracted position even if the driving force of the drive device 750 is not required. Therefore, the durability of the drive device 750 can be improved.

[0361] The support member 720 includes a main body portion 721 formed in a plate shape long in the vertical direction, a first fastening portion 722 connected in the left-right direction to the lower end of the main body portion 721, drilled in the front-rear direction, and through which a screw is inserted to be fastened to the slide plate 711 of the base member 710, a second fastening portion 723 connected in the vertical direction to the left end of the main body portion 721 as viewed from the front, drilled in the front-rear direction, and through which a slide rail 730 is fastened, a slide hole 724 formed in the right side of the main body portion 721 as viewed from the front, which is an elongated hole extending in a direction parallel to the connecting direction of the second fastening portion 723, and 7. The rear cover member 760 has a hook-shaped engaging portion 725 which protrudes upward from the lower right end of the main body portion 721 and engages with the lever member 714, a lower cover portion 726 which is fastened to the underside of the main body portion 721 and through which a belt 755 of the drive unit 750 is sandwiched between the main body portion 721 and a rolling portion 727 which protrudes from the rear side of the lower end of the main body portion 721 and is formed so as to be able to roll on the inner circumferential surface of a slide recessed portion 764 of a rear cover member 760, and a coil spring 728 which is suspended downward and forward from the upper end of the main body portion 721 and whose lower end is connected to the hook-shaped portion 617 of the base member 610.

[0362] The slide rail 730 is fastened and fixed to the support member 720 in a position that allows it to expand and contract in the direction in which the second fastening portion 723 is connected.

[0363] The slide hole 724 is an elongated hole extending in a direction parallel to the direction in which the second fastening portion 723 is connected, and is an elongated hole through which the auxiliary member 615 of the tilt motion unit 600 is inserted. Therefore, the slide hole 724 can suppress deviation in the left-right posture of the tilt motion unit 600 that moves up and down (relative rotation of the tilt motion unit 600 with respect to the support member 720).

[0364] The lower cover portion 726 has a toothed shape extending in the front-rear direction formed on the upper surface side. The toothed shape is shaped to mesh with a toothed shape formed on the inner peripheral surface of the belt 755 of the driving device 750. This makes it possible to prevent the support member 720 from slipping on the belt 755 of the driving device 750.

[0365] The rolling portion 727 is rotatably inserted into the slide recess 764 of the rear cover 760, thereby suppressing frictional resistance and suppressing tilt in the front-rear direction around the lower end of the support member 720 as an axis.

[0366] Coil spring 728 provides a biasing force that moves upward tilt motion unit 600. Since the biasing force from coil spring 728 is constantly applied to tilt motion unit 600, tilt motion unit 600 is prevented from falling downward due to gravity.

[0367] The connecting member 740 mainly comprises a triangular plate-shaped main body member 741 rotatably supported on the pivot support protrusion 612 of the tilting operation unit 600, a pair of cylindrical upper rolling members 742 supported on rolling shafts 741c protruding from the main body member 741 and rolling on the upper surface of the front rail portion 715 of the base member 710, a front cover member 743 fastened and fixed to the rolling shafts 741c of the main body member 741 from the front side and arranged in a manner covering the front side of the front rail portion 715, and a cylindrical lower rolling member 744 arranged on the lower back side of the front cover member 743, with its lower half fitted and held by the front cover member 743 and its upper half rolling on the underside of the front rail portion 715.

[0368] The main body member 741 is a member formed in a triangular plate shape and mainly comprises a support portion 741a, which is a circular recess recessed from the back surface at the upper end and is rotatably supported by the support protrusion 612 of the tilting operation unit 600, an insertion plate portion 741b, which is a plate-shaped member protruding toward the front side at the lower end and is slidably inserted into the rear rail portion 716 of the base member 710, and a pair of rolling shafts 741c, which protrude cylindrically toward the front side from positions linearly symmetrical with respect to the perpendicular line drawn from the support portion 741a to the insertion plate portion 741b and on which the upper rolling member 742 is rotatably supported.

[0369] Since the insertion plate portion 741b is inserted into the rear rail portion 716 of the base member 710, the connecting member 740 is formed to be movable along the rear rail portion 716. Therefore, the tilting operation unit 600 pivotally supported by the pivot support portion 741a is also formed to be movable along the rear rail portion 716.

[0370] The rolling shafts 741c are formed in a pair at positions that are symmetrical with respect to a perpendicular line drawn from the pivot support portion 741a to the insertion plate portion 741b. Therefore, when the pair of rolling shafts 741c abut against the front rail portion 715 formed in an arc shape via the upper rolling portion 742, the load (force in the normal direction of the arc) applied to the connecting member 740 from the upper surface of the front rail portion 715 passes through the pivot support portion 741a. Therefore, the pivot support protrusion 612 of the tilting motion unit 600 can be stably held by the connecting member 740.

[0371] The upper rolling member 742 is rotatably supported by the pivot support portion 741a, and abuts against the upper surface of the front rail portion 715. That is, when the connecting member 740 slides along the front rail portion 715, the upper rolling portion 742 rolls on the upper surface of the front rail portion 715. This reduces the frictional resistance generated when the connecting member 740 slides, and makes it possible to suppress the driving force required for the sliding movement.

[0372] The lower half of the lower rolling member 744 is rotatably fitted onto the lower part of the front cover member 743, and the upper end part abuts against the lower surface of the front rail portion 715. That is, when the connecting member 740 slides along the front rail portion 715, the lower rolling part 744 rolls on the lower surface of the front rail portion 715. This reduces the frictional resistance generated between the connecting member 740 and the front rail portion 715 when the connecting member 740 slides, and makes it possible to suppress the driving force required for the sliding movement.

[0373] Thus, in this embodiment, the upper rolling member 742 rolls on the upper surface of the front rail portion 715, and the lower rolling member 744 rolls on the lower surface of the front rail portion 715. This makes it possible to maintain the upper and lower surfaces of the front rail portion 715 sandwiched between the upper rolling member 742 and the lower rolling member 744 of the connecting member 740 while suppressing frictional resistance.

[0374] Here, the tilting motion unit 600 has a center of gravity formed upward as described below, so there is a risk of it tilting in the front-rear direction. In this case, the connecting member 740 sandwiches the upper and lower surfaces of the front rail portion 715 between the upper rolling member 742 and the lower rolling member 744, so it is possible to generate resistance to the tilting motion unit 600 tilting in both the front and rear directions. This makes it easier to maintain the posture of the tilting motion unit 600.

[0375] The front cover member 743 is pivotally supported from the front side of the rolling shaft 741c of the connecting member 740, thereby pivotally supporting the upper rolling member 742 so that it cannot be pulled out.

[0376] The drive device 750 mainly comprises a drive motor 751 which is fastened to the base member 710 and generates a drive force for sliding the support member 720, a drive gear 752 which is axially supported by the drive motor 751, a fixed shaft gear 753 which is meshed with the drive gear 752 and has a belt 755 wound around it, a shaft moving gear 754 which is disposed at a distance from the fixed shaft gear 753 and has the belt 755 wound around it and has a rotating shaft 754a which is slidably moved, the belt 755 which is wound around the fixed shaft gear 753 and the moving shaft gear 754 which is moved by the rotation of the fixed shaft gear 753, and a coil spring 756 which generates a biasing force for moving the moving shaft gear 754 in a direction away from the fixed shaft gear 753.

[0377] The shaft fixed gear 753 is a cylindrical member serving as a rotating shaft and includes a fixed shaft portion 753a that is inserted into the shaft support hole 712 of the base member 710. The shaft moving gear 754 is a cylindrical member serving as a rotating shaft and includes a moving shaft portion 754a that is inserted into the slide shaft support hole 713 of the base member 710.

[0378] The fixed shaft gear 753 and the movable shaft gear 754 are formed as gears of the same shape. The inner circumferential surface of the belt 755 is formed with teeth that mesh with the gear teeth of the fixed shaft gear 753 and the movable shaft gear 754. This makes it possible to suppress slippage between the belt 755 and the fixed shaft gear 753 and between the belt 755 and the fixed shaft gear 753 and the movable shaft gear 754, and to reliably transmit the amount of rotation of the fixed shaft gear 753 to the belt 755.

[0379] One end of the coil spring 756 is fixed to a hook-shaped portion formed on the right side of the slide shaft support hole 713n of the base member 710 when viewed from behind, and the other end is fixed to a case covering the shaft moving gear 754. This makes it possible to generate a biasing force that moves the shaft moving gear 754 to the opposite side of the shaft support hole 712, and to provide an appropriate tension to the belt 755, thereby preventing the belt 755 from falling off the shaft fixed gear 753 and the shaft moving gear 754.

[0380] The rear cover member 760 is a member that covers the drive unit 750 on the rear side of the base member 710, and mainly comprises a main body portion 761 formed in a box shape with an open front side, a recessed portion 762 which is a recess on the bottom surface of the main body portion 761 to receive the fixed shaft portion 753a, a moving recessed portion 763 which is an recess that extends in the same shape as the slide shaft support hole 713 and receives the moving shaft portion 754a, and a slide recessed portion 764 which is an recess that extends in the left-right direction and receives the rolling portion 727.

[0381] The slide recessed portion 764 is a recess in which the rolling portion 727 rolls on its upper and lower inner surfaces. It suppresses the frictional resistance of the sliding movement of the support member 720 and also suppresses the support member 720 from tilting in the front-rear direction. In other words, when the support member 720 tilts in the front-rear direction, the rolling portion 727 abuts against either the upper inner surface or the lower inner surface of the slide recessed portion 764. This makes it possible to suppress the tilt of the support member 720 in the front-rear direction.

[0382] Next, the tilt action unit 600 will be described with reference to Figures 50 and 51. Figure 50 is an exploded front perspective view of the tilt action unit 600, and Figure 51 is an exploded rear perspective view of the tilt action unit 600.

[0383] The tilting operation unit 600 mainly comprises a plate-shaped base member 610 fastened to the other end of the slide rail 730, a box-shaped performance member 620 whose lower end is pivotally supported on the base member 610 for swinging motion, a first drive unit 630 that generates a driving force for swinging the performance member 620, a transmission member 640 that transmits the driving force of the first drive unit 630 to the performance member 620, a torsion spring 650 that abuts against the transmission member 640 and generates a biasing force that moves the transmission member 640, and a second drive unit 660 that generates a driving force for opening and closing the first curtain member 624 and second curtain member 625 of the performance member 620.

[0384] The base member 610 includes a main body 611 to which the slide rail 730 is fastened and which is formed in a vertically long plate shape, a support protrusion 612 which is cylindrically protrudes from the front side of the main body 611 and supports the support part 741a of the connecting member 740, a first support hole 613 which is a circular hole drilled in the front-rear direction vertically above the support protrusion 612 and supports the swing shaft part 626 of the performance member 620 so as to be swingable, and a support hole 613 between the first support hole 613 and the support part 612. The main component includes a second shaft support hole 614 which is a circular hole drilled vertically upward in the front-to-rear direction and in which the tubular portion 642 of the transmission member 640 is pivotally supported so as to be capable of swinging, an auxiliary member 615 which is formed on the rear surface of the main body portion 611 and which is inserted into the slide hole 724 of the support member 720 so as to be able to slide up and down, an insertion hole 616 through which the drive shaft of the first drive device 630 is inserted, and a hook-shaped portion 617 which extends from the lower end of the main body portion 611 towards the rear surface side.

[0385] The second shaft support hole 614 is provided with a lower support plate portion 614a that protrudes from the lower edge of the second shaft support hole 614 toward the front side and has an arc-shaped cross section. The lower support plate portion 614a guides the rotation of the cylindrical portion 642 of the transmission member 640. The lower support plate portion 614a is formed with a left-right width and a length that is approximately equal to the outer diameter of the cylindrical portion 642 (see FIG. 53(a)).

[0386] By inserting the auxiliary member 615 through the slide hole 724, tilt of the base member 610 in the left-right direction can be suppressed, so that the base member 610 can be smoothly slid in the up-down direction.

[0387] The hook-shaped portion 617 is a portion to which one end of a coil spring 728 is hooked and to which a biasing force is applied.

[0388] With reference to Fig. 52, the performance member 620 and the second drive unit 660 will be described. Fig. 52 is a front exploded perspective view of the performance member 620 and the second drive unit 660. Note that the liquid crystal device disposed inside the performance member 620 is illustrated by imaginary lines, and Figs. 50 and 51 will be referred to as appropriate for the description of the performance member 620 and the second drive unit 660.

[0389] The performance member 620 is a box-shaped member in which a liquid crystal device is arranged, and mainly comprises a rectangular plate-shaped main body member 621, upper and lower cover members 622 which extend forward from the top and bottom of the main body member 621 and are bent so as to cover the main body member 621, left and right cover members 623 which are plate-shaped members attached to both sides of the upper and lower cover members 622 and which form a rectangular box shape with an opening at the front together with the upper and lower cover members 622, a first curtain member 624 which is a member that opens and closes the front opening and is connected to a fitting hole 665a of the second drive device 660 and moved, a second curtain member 625 which is a member that opens and closes the front opening together with the first curtain member 624 and is moved by being pulled by the first curtain member 624, and a cylindrical oscillating shaft portion 626 which protrudes from the lower part of the back surface of the main body member 621, and the center of gravity position G (see Figure 53) is formed above (at a higher position) than the oscillating shaft portion 626. The center of gravity G is formed on a straight line passing through the sliding shaft portion 621a and the swinging shaft portion 626 (see FIG. 53) in the inverted state (see FIG. 53).

[0390] The main body member 621 includes a cylindrical sliding shaft portion 621a (see FIG. 51) that protrudes from the rear surface side vertically above the swinging shaft portion 626. The sliding shaft portion 621a is slidably inserted into a sliding hole 643 of a transmission member 640 (see FIG. 51).

[0391] The upper and lower cover members 622 are members that house the first curtain member 624 and the second curtain member 625 inside when the first curtain member 624 and the second curtain member 625 are in a state in which they are opened by the driving force of the driving device 660.

[0392] The left and right cover members 623 are provided with slide grooves 623a formed in the inner surfaces thereof in a groove shape, in which the slide protrusions 625c of the second curtain member 625 can slide.

[0393] The slide groove 623a is a linear groove extending vertically, and curved grooves formed in an arc shape are connected to the upper and lower ends of the linear groove. This allows the second curtain member 625 to slide in a manner in which linear movement and curved movement occur in sequence along the shape of the slide groove 623a.

[0394] The first curtain member 624 is a member that is swung in the vertical direction around the opening / closing axis 664 of the second drive unit 660, and mainly comprises a main body portion 624a having a shape of a plate material bent into a C-shape in cross section, an engagement portion 624b that protrudes in the left-right direction from the end of the main body portion 624a and is engaged with an engagement hole 665a of the second drive unit 660 so that it cannot rotate relative to the main body portion 624, and a connecting member 624c having one end that is axially supported by the main body portion 624 for swinging near the engagement portion 624b and the other end that is connected to a connecting protrusion 625b of the second curtain member 625.

[0395] The second curtain member 625 is a member that is pulled by the first curtain member 624 and moved in the vertical direction, and mainly comprises a main body portion 625a formed in a plate shape with a C-shaped cross section, a connecting protrusion 625b that protrudes in the left-right direction from the end of the C-shaped cross section of the main body portion 625a and is connected to the other end of the connecting member 624c, and a slide protrusion 625c that protrudes outward in the left-right direction from near the bent portion of the main body portion 625a and is inserted into the slide groove 623a of the left and right cover members 623.

[0396] The second drive unit 660 mainly comprises a drive motor 661 fastened to the back side of the performance member 620, a drive gear 662 journalled to the drive motor 661, a pair of transmission gears 663, one of which is meshed with the drive gear 662 and rotates in opposite directions, an opening / closing shaft 664 which is inserted through the transmission gear 663 so as not to rotate relative to one another and is rotatably supported on the front side of the main body member 621 of the performance member 620 by a journal mechanism not shown, and transmission members 665 which are fixed to both ends of the pair of opening / closing shafts 664 so as not to rotate relative to one another.

[0397] The transmission member 665 has a fitting hole 665a into which the fitting portion 624b of the first curtain member 624 is fitted so as not to rotate relative to the transmission member 665. This allows the first curtain member 624 to swing up and down around the opening / closing shaft 664 as an axis.

[0398] 50 and 51. The first driving device 630 mainly includes a driving motor 631 whose driving shaft is inserted into the insertion hole 616 of the base member 610 and fastened to the base member, a worm 632 in the form of a screw gear fixed to the driving shaft of the driving motor 631, and a worm wheel 633 in the form of a helical gear meshing with the worm 632.

[0399] The worm 632 is formed with a double thread. In this embodiment, the number of teeth of the worm wheel 633 that meshes with the worm 632 is about 20, so that the worm wheel 633 rotates once for every 10 rotations of the worm 632. This makes it possible to significantly reduce the rotation angle of the worm wheel 633 and the transmission member 640 when the drive motor 631 is operated at the minimum unit of control resolution.

[0400] The worm wheel 633 includes a locking projection 633a that protrudes from the center of the rotation axis, is inserted into the second shaft support hole 614 of the base member 610, and is locked to the cylindrical portion 643 of the transmission member 640 so as not to rotate relative to the worm wheel 632. The transmission of the driving force between the worm 632 and the worm wheel 633 is limited to one direction from the worm 632 to the worm wheel 633 due to the structure (when the worm wheel 633 actively rotates, the force is applied in the axial direction of the worm 632). This can reduce the load that the drive motor 631 receives when the worm wheel 633 is stopped. In addition, the worm wheel 633 and the transmission member 640 can be stopped when the power of the drive motor 631 is cut off, and the power consumption of the drive motor 631 can be suppressed.

[0401] The transmission member 640 and the torsion spring 650 will be described with reference to FIG. 53. FIG. 53(a) and FIG. 53(b) are front views of the transmission member 640 and the torsion spring 650. In FIG. 53(a) and FIG. 53(b), the outer shapes of the base member 610 and the performance member 620 are illustrated by imaginary lines, and FIG. 50 and FIG. 51 are appropriately referred to for the explanation of the transmission member 640 and the torsion spring 650. In addition, FIG. 53(a) illustrates an inverted state in which the slide hole 643 of the transmission member 640 is disposed vertically above the cylindrical portion 642, and in this state, the biasing force of the torsion spring 650 is balanced in the swing direction of the transmission member 640. FIG. 53(b) illustrates a state in which the transmission member 640 is swung a predetermined amount counterclockwise when viewed from the front from the inverted state of FIG. 53(a), and the performance member 620 is swung a predetermined amount.

[0402] The transmission member 640 is a member that is oscillated by the rotation of the worm wheel 633 (see Figure 50), and mainly comprises a main body portion 641 formed in the shape of a long rectangular rod, a tubular portion 642 extending in the front-to-rear direction at one end of the main body portion 641 and engaging with a locking protrusion 633a of the first driving device 630, a sliding hole 643 drilled as a long hole extending in the axial radial direction of the tubular portion 642 at the other end of the main body portion 641, abutment portions 644 arranged spaced apart on both sides of the oscillating direction of the main body portion 641, a front arc plate portion 645 having a certain arc shape connecting the abutment portion 644 and the front side surface of the main body portion 641, and a rear arc plate portion 646 having a certain arc shape connecting the abutment portion 644 and the rear side surface of the main body portion 641.

[0403] 53, the contact portion 644, the front arc plate portion 645 and the rear arc plate portion 646 are disposed in a manner to surround the biasing arm portion 652 of the torsion spring 650. This makes it possible to prevent the torsion spring 650 from falling off (disengaging) from the transmission member 640.

[0404] The cylindrical portion 642 is pivotally supported in a second pivot hole 614 (see FIG. 50) of the base member 610, and is locked to a locking projection 633a (see FIG. 50) of the first driving device 630 so as not to rotate relative to the first driving device 630.

[0405] The sliding shaft portion 621a of the performance member 620 is inserted into the sliding hole 643. As a result, when the transmission member 640 is swung about the second shaft support hole 614 (see FIG. 50) by the driving force of the first driving device 630 (see FIG. 50), the performance member 620 is swung about the first shaft support hole 613 while the sliding shaft portion 621a of the performance member 620 is slid in the sliding hole 643 (slid in the shaft diameter direction).

[0406] By swinging the performance member 620 in this way, the swing angle of the performance member 620 when the drive motor 631 is rotated in the smallest unit of the control resolution of the drive device can be suppressed. For example, as a method of swinging the performance member 620, a method of directly connecting a gear to the swing shaft part 626 of the performance member 620 and transmitting the driving force of the drive motor to the gear can be considered. However, in this case, when the drive motor is rotated at an angle P0 (see FIG. 53(a) (for ease of understanding, the angle is illustrated several times larger than the actual angle P0) which is the smallest unit of the control resolution, the amount of movement X1 by which the center of gravity of the performance member 620 shifts left and right from the inverted state becomes larger as the center of gravity of the performance member 620 is farther away from the swing shaft part 626. Therefore, the farther the center of gravity of the performance member 620 is from the oscillating axis portion 626, the more difficult it becomes to adjust the position of the center of gravity of the performance member 620, and the more difficult it becomes to keep the performance member 620 stationary in an inverted state where the center of gravity of the performance member 620 is positioned directly above the oscillating axis portion 626.

[0407] In contrast, in this embodiment, a transmission member 640 that transmits the driving force of a drive motor 631 to a performance member 620 is connected to a sliding shaft portion 621a of the performance member 620. The length from this sliding shaft portion 621a to a cylindrical portion 642 that is the swing shaft of the transmission member 640 is formed shorter than the length from the sliding shaft portion 621a to a swing shaft portion 626 that is the swing shaft of the performance member 620.

[0408] Therefore, even if the performance member 620 is long in the radial direction of the oscillating shaft portion 626, it is possible to suppress the amount of movement X2 of the center of gravity of the performance member 620 when the drive unit is operated at angle P0, the smallest unit of the control resolution of the drive unit (see FIG. 53(a) (for ease of understanding, the angle is illustrated as being several times larger than the actual angle P0). This makes it easy to stop the movable member in an inverted state where the center of gravity of the movable member is located directly above the first axis.

[0409] As a method for swinging the performance member 620, a method is considered in which gear teeth are formed on the performance member 620 on an arc centered on the swing shaft portion 626, and a gear meshing with the gear teeth is rotated by a drive motor to swing the performance member 620. However, in this case, the larger the swing range of the performance member 620, the larger the range required to form the gear teeth on the arc in the left-right direction of the performance member 620 becomes. Therefore, if the performance member 620 is formed with a narrow shape in the swing direction, the gear teeth on the arc will protrude from the performance member 620, hindering the performance effect. Therefore, the design freedom of the performance member 620 is reduced.

[0410] On the other hand, in this embodiment, the transmission member 640 that transmits the driving force of the drive motor 631 to the performance member 620 has a cylindrical portion 642 that is a swing shaft disposed vertically above the swing shaft portion 626 that is the swing shaft of the performance member 620, and is connected to the swing shaft portion 621a at the left-right center of the performance member 620. Since the performance member 620 swings following the transmission member 640, the formation range of the transmission member 640 relative to the swing range of the performance member 620 can be suppressed to the vicinity of the left-right center of the performance member 620. As a result, even if the performance member 620 is made thin in the left-right direction, it is possible to suppress the transmission member 640 from protruding from the performance member 620, and the design freedom of the performance member 620 can be improved.

[0411] The lower surface of the sliding shaft portion 621a of the performance member 620 abuts against the inner peripheral surface of the sliding hole 643 of the transmission member 640. As a result, the weight of the performance member 620 is loaded not only on the oscillating shaft portion 626 but also on the transmission member 640. That is, a force opposing the weight of the performance member 620 can be generated not only from the oscillating shaft portion 626 but also from the cylindrical portion 642 of the transmission member 640. Therefore, the performance member 640 can be supported at two points, the oscillating shaft portion 626 and the cylindrical portion 642, and the radial force loaded on the oscillating shaft portion 626 and the cylindrical portion 642 can be suppressed.

[0412] Here, since the inverted state shown in Figure 53 (a) is considered to be the normal state of the performance member 620, it is desirable that the transmission member 640 can be swung a predetermined amount from the inverted state and then quickly return to the inverted state.

[0413] In this embodiment, as shown in Figure 53(b), when the transmission member 640 is swung counterclockwise when viewed from the front from the state shown in Figure 53(a) at a swing angle φ1, the performance member 620 is swung at a swing angle φ2 (φ2<φ1).

[0414] That is, the swing angle of the performance member 620 is made smaller than the swing angle of the transmission member 640 that is swung by the driving force of the first driving device 630 (see FIG. 50). Therefore, it is possible to easily return the performance member 620 to the inverted state (see FIG. 53(a)).

[0415] In this embodiment, a long-hole-shaped sliding hole 643 is formed in the axial direction of the transmission member 640, and the sliding shaft portion 621a of the performance member 620 is inserted into the sliding hole 643. The transmission member 640 and the performance member 620 have different swing axes, and the sliding hole 643 of the transmission member 640 has a shorter swing radius than the sliding shaft portion 621a of the performance member 620. Therefore, the more the transmission member 640 swings, the farther the sliding shaft portion 621a moves from the swing axis of the transmission member 640. Therefore, the arm length R1 from the sliding shaft portion 621a of the performance member 620 to the tubular portion 642 of the transmission member 640 in the inverted state (see Figure 53 (a)) is shorter than the arm length R2 from the sliding shaft portion 621a of the performance member 620 to the tubular portion 642 of the transmission member 640 in a state swung a predetermined amount from the inverted state (see Figure 54 (b)).

[0416] That is, the closer to the inverted state, the shorter the arm length of the transmission member 640 becomes, and the swing angle of the performance member 620 when the transmission member 640 swings at a predetermined angle can be made smaller as the performance member 620 approaches the inverted state, compared to when the arm length of the transmission member 640 is constant. Therefore, even without changing the rotation speed of the drive motor 631, the operating speed of the performance member 620 can be increased near a predetermined stop position, while the operating speed of the performance member 620 can be decreased near the inverted state, making it easier to stop the performance member 620 in the inverted state (it is easier to stop and control the performance member 620 when the center of gravity of the performance member 620 is located vertically above the first shaft support hole 613).

[0417] Referring to Figure 55, a change in the swing angle of performance member 620 relative to the swing angle of transmission member 640 by changing the arm length from sliding shaft portion 621a of performance member 620 to cylindrical portion 642 of transmission member 640 will be described.

[0418] FIG. 55 is a schematic diagram showing the swing angle of the performance member 620 (see FIG. 53(a)) relative to the swing angle of the transmission member 640 (see FIG. 53(a)). In FIG. 55, the rotation axis M1 corresponds to the swing axis portion 626 (see FIG. 53(a)), which is the rotation axis of the performance member 620, and the rotation axis M2 corresponds to the cylindrical portion 642 (see FIG. 53(a)), which is the swing axis of the transmission member 640. The straight lines a1 to a4 are schematic diagrams showing the arrangement of the transmission member 640, and are straight lines drawn radially from the rotation axis M2, with the straight line a1 passing through the rotation axis M1, and the straight lines a2 to a4 being formed in such a manner that the angles formed with the straight line a1 are added in sequence by 15 degrees each. In other words, the angles formed between adjacent straight lines a1 to a4 are 15 degrees each.

[0419] An arc drawn with a radius equal to arm length R1 (see FIG. 53(a)) centered on rotation axis M2 is illustrated as arc SR1, and an arc drawn with a radius equal to arm length R2 (see FIG. 54(b)) centered on rotation axis M2 is illustrated as arc SR2. Note that arc SR0 is an arc drawn with rotation axis M1 as its center, and has a radius equal to arm length R1 plus the distance between rotation axis M1 and rotation axis M2.

[0420] These arcs are assumed to be the trajectory of the connection position between performance member 620 and transmission member 640 (see FIG. 53(a)). In this embodiment, sliding shaft portion 621a (see FIG. 53(a)) as the connection position protrudes from performance member 620, and the connection position between performance member 620 and transmission member 640 moves along arc SR0. Note that, when the connection position between performance member 620 and transmission member 640 moves along arc SR1 or SR2, it is assumed that a long hole is formed in performance member 620 in the axial direction, and an axis is protruded from transmission member 640 to be inserted into the long hole.

[0421] As shown in FIG. 55, the intersection of the straight line a1 and the arc SR0 is illustrated as intersection P10, the intersection of the straight line a1 and the arc SR1 is illustrated as intersection P11, and the intersection of the straight line a1 and the arc SR2 is illustrated as intersection P12.

[0422] Similarly, the intersection of the straight line a2 and the arc SR0 is illustrated as an intersection point P20, the intersection of the straight line a2 and the arc SR1 is illustrated as an intersection point P21, and the intersection of the straight line a2 and the arc SR2 is illustrated as an intersection point P22. The intersection of the straight line a3 and the arc SR0 is illustrated as an intersection point P30, the intersection of the straight line a3 and the arc SR1 is illustrated as an intersection point P31, and the intersection of the straight line a3 and the arc SR2 is illustrated as an intersection point P32. The intersection of the straight line a4 and the arc SR0 is illustrated as an intersection point P40, the intersection of the straight line a4 and the arc SR1 is illustrated as an intersection point P41, and the intersection of the straight line a4 and the arc SR2 is illustrated as an intersection point P42. Note that the intersection points P10 and P11 are located at the same position, and the intersection points P40 and P42 are located at the same position.

[0423] Also, as shown in FIG. 55, the angle formed by a line passing through the rotation axis M1 and intersection point P10 and a line passing through the rotation axis M1 and intersection point P20 is illustrated as angle A10, the angle formed by a line passing through the rotation axis M1 and intersection point P11 and a line passing through the rotation axis M1 and intersection point P21 is illustrated as angle A11, and the angle formed by a line passing through the rotation axis M1 and intersection point P12 and a line passing through the rotation axis M1 and intersection point P22 is illustrated as angle A12.

[0424] Similarly, the angle formed by the line passing through the rotation axis M1 and the intersection point P20 and the line passing through the rotation axis M1 and the intersection point P30 is illustrated as angle A20, the angle formed by the line passing through the rotation axis M1 and the intersection point P21 and the line passing through the rotation axis M1 and the intersection point P31 is illustrated as angle A21, the angle formed by the line passing through the rotation axis M1 and the intersection point P22 and the line passing through the rotation axis M1 and the intersection point P32 is illustrated as angle A22, the angle formed by the line passing through the rotation axis M1 and the intersection point P30 and the line passing through the rotation axis M1 and the intersection point P40 is illustrated as angle A30, the angle formed by the line passing through the rotation axis M1 and the intersection point P31 and the line passing through the rotation axis M1 and the intersection point P41 is illustrated as angle A31, and the angle formed by the line passing through the rotation axis M1 and the intersection point P32 and the line passing through the rotation axis M1 and the intersection point P42 is illustrated as angle A32. These angles correspond to the swing angles of the performance component 620.

[0425] Here, in this embodiment, the ratio of (distance between rotation axis M1 and rotation axis M2: arm length R1: arm length R2) is (1:2.32:2.54). When the angles are actually measured, angle A32 is 11.07 degrees, angle A31 is 10.77 degrees, and angle A30 is 11.37 degrees. That is, when transmitting member 640 is swung between line a4 and line a3, the swing angle of transmitting member 640 is the largest when transmitting member 640 and performance member 620 are connected along arc SR0, and is formed by the case where transmitting member 640 and performance member 620 are connected along arc SR2 or more (angle A30 is closer to angle A32 than angle A31).

[0426] Angle A22 is 10.87 degrees, angle A21 is 10.59 degrees, and angle A20 is 10.82 degrees. That is, when transmitting member 640 is swung between straight line a3 and straight line a2, the swing angle when transmitting member 640 and performance member 620 are connected along arc SR0 is smaller than the swing angle when transmitting member 640 and performance member 620 are connected along arc SR2. In this case, the difference between angle A22 and angle A20 is smaller than the difference between angle A20 and angle A21 (angle A20 is closer to angle A22 than angle A21).

[0427] Angle A12 is 10.78 degrees, angle A11 is 10.50 degrees, and angle A10 is 10.53 degrees. That is, when transmitting member 640 is swung between line a2 and line a1, the swing angle when transmitting member 640 and performance member 620 are connected along arc SR0 exceeds the swing angle when transmitting member 640 and performance member 620 are connected along arc SR1. In this case, the difference between angle A12 and angle A10 is greater than the difference between angle A10 and angle A11 (angle A10 is closer to angle A11 than angle A12).

[0428] From this, it can be seen that by making the trajectory of the connection position between transmission member 640 and performance member 620 (see FIG. 53(a)) a circular arc SR0, for example, when transmission member 640 swings at a constant speed, the degree of freedom in adjusting the angular velocity of performance member 620 can be improved. That is, the angular velocity when transmission member 640 is arranged on straight line a4 can be made to approach the angular velocity (higher speed side) when the trajectory of the connection position between transmission member 640 and performance member 620 is a circular arc SR2, and the angular velocity when transmission member 640 is arranged on straight line a1 can be made to approach the angular velocity (lower speed side) when the trajectory of the connection position between transmission member 640 and performance member 620 is an arc SR1.

[0429] Furthermore, when the ratio of each angle is calculated, angle A22 / angle A32 is 0.98, and angle A12 / angle A22 is 0.99. Angle A21 / angle A31 is 0.98, and angle A11 / angle A21 is 0.99. In other words, when the path of the connection position between transmission member 640 and performance member 620 (see FIG. 53(a)) is the arc SR1, SR2, the deceleration ratio of the angular velocity of performance member 620 when transmission member 640 is swung toward the inverted state at a constant speed is small at 1 to 2%.

[0430] On the other hand, angle A20 / angle A30 is 0.95, and angle A10 / angle A20 is 0.97. That is, when the trajectory of the connection position between transmission member 640 and performance member 620 (see FIG. 53(a)) is arc SR0 (arc centered on rotation axis M1), the deceleration ratio of the angular velocity of performance member 620 when transmission member 640 is swung toward the inverted state at a constant speed can be set to 3 to 5%. That is, compared to the case where the trajectory of the connection position is arc SR1, SR2 (arc centered on rotation axis M2), the deceleration ratio of the angular velocity of performance member 620 can be made larger.

[0431] As shown in FIG. 53(a), in the inverted state, the sliding shaft portion 621a of the performance member 620 abuts against the lower end of the sliding hole 643 of the transmission member 640. In the inverted state, the center of gravity G of the performance member 620 is formed vertically above the swinging shaft portion 626 of the performance member 620 and the cylindrical portion 642 of the transmission member 640, so that the force of gravity G of the performance member 620 is applied vertically downward to the swinging shaft portion 626 and the cylindrical portion 642. Therefore, since the force component in the direction in which the performance member 620 is swung due to the gravity of the performance member 620 is not generated, the posture of the performance member 620 can be maintained in the inverted state even if the power of the first drive device 630 is cut off. This can improve the durability of the first drive device 630.

[0432] In addition, since the force of gravity G of the performance member 620 is applied vertically downward to the oscillating shaft portion 626 and the cylindrical portion 642, the rotational resistance of the oscillating shaft portion 626 and the cylindrical portion 642 can be increased, making it easier for the performance member 620 to maintain its position in an inverted state.

[0433] The torsion spring 650 is an elastic spring that generates a biasing force in the direction of rewinding the coil portion 651 (in the direction of pushing the transmission member 640 back) as the transmission member 640 oscillates, and mainly comprises a coil portion 651 wound around the oscillating shaft portion 626 of the performance member 620, a biasing arm portion 652 extending along both side surfaces in the oscillating direction of the main body portion 641 of the transmission member 640, and a connecting arm portion 653 that connects the end of the coil portion 651 and the end of the biasing arm portion 652 by passing between the tubular portion 642 and the oscillating shaft portion 626.

[0434] Coil portion 651 is formed with an inner diameter approximately three times the diameter of swing shaft portion 626 of performance member 620. Therefore, when biasing arm portion 652 is swung and a load that causes coil portion 651 to undergo diameter-reducing deformation is generated, the amount of deformation of coil portion 651 can be secured, and deformation can be prevented from concentrating on biasing arm portion 652 and connecting arm portion 653.

[0435] The urging arm portion 652 is surrounded by the main body portion 641, the abutment portion 644, the front arc plate portion 645, and the rear arc plate portion 646 of the transmission member 640. This makes it possible to prevent the urging arm portion 652 from falling off (disengaging) from the transmission member 640.

[0436] Moreover, the biasing arm 652 is formed so as to be able to come into contact with the lower receiving plate 614a on the plane on which the transmission member 640 swings. Therefore, a biasing force that pushes back the transmission member 640 is generated from the biasing arm 652 arranged in the swing direction of the transmission member 640, and the biasing arm 652 arranged on the opposite side of the swing direction of the transmission member 640 is prevented from moving to the lower receiving plate 614a. Thus, the torsion spring 650 is formed so as to be able to generate a biasing force in a direction that pushes back the transmission member 640 regardless of the swing direction of the transmission member 640.

[0437] At the connecting portion between the biasing arm portion 652 and the connecting arm portion 653, a bent portion 653a is formed that is bent toward the opposite side of the transmission member 640. In this case, as described below, the abutting portion 644 of the transmission member 640 is pressed against the bent portion 653a of the torsion spring 650, thereby stretching the bent portion 653a (see FIG. 54(b)). As a result, the abutting position between the biasing arm portion 652 of the torsion spring 650 and the main body portion 641 of the transmission member 640 becomes farther from the cylindrical portion 642, and the moment loaded from the torsion spring 650 to the transmission member 640 can be increased.

[0438] With reference to Fig. 54, a description will be given of changes in the biasing force generated from torsion spring 650 and pushing back transmission member 640. Fig. 54(a) and Fig. 54(b) are front views of transmission member 640 and torsion spring 650. Note that in Fig. 54(a) and Fig. 54(b), the outlines of base member 610 and performance member 620 are shown by imaginary lines, and Fig. 53 will be referred to as appropriate for an explanation of changes in the biasing force generated from torsion spring 650.

[0439] In addition, Figure 54(a) illustrates a state in which transmission member 640 is further rotated counterclockwise when viewed from the front from the state in Figure 53(b) and the left-side biasing arm 652 when viewed from the front begins to be pressed against the inner surface of the abutment portion 644 of transmission member 640, and Figure 54(b) illustrates a state in which transmission member 640 is further rotated counterclockwise when viewed from the front from the state in Figure 54(a) and the bent portion 653a of torsion spring 650 is stretched.

[0440] 54(a), a biasing force that pushes back the transmission member 640 is generated in the biasing arm 652 on the left side as viewed from the front of the torsion spring 650. This biasing force is the sum of the biasing force generated with the coil portion 651 as the starting point and the biasing force generated with the bent portion 653a as the starting point.

[0441] That is, in the state of Figure 53 (b), the transmission member 640 is not pressed against the bent portion 653a that is located on the left side when viewed from the front, of the pair of bent portions 653a, so that only the biasing force originating from the coil portion 651 is generated in the biasing arm portion 652 on the left side when viewed from the front of the torsion spring 650 as a biasing force that pushes back the transmission member 640.

[0442] 54(a), in addition to the biasing force originating from coil portion 651, a biasing force is generated by deformation of biasing arm portion 652 originating from bent portion 653a. This makes it possible to increase the spring constant of biasing arm portion 652. Note that, in the deformation of biasing arm portion 652 originating from bent portion 653a, the length of the portion subjected to deformation is shorter than that in the deformation originating from coil portion 651, so that the biasing force generated per unit deformation of transmission member 640 can be made larger.

[0443] In the state of FIG. 54(b), the bent portion 653a of the torsion spring 650 is pushed by the abutment portion 644 of the transmission member 640, so that the angle formed by the urging arm portion 652 and the connecting arm portion 653 is widened. As a result, compared with the abutment position length L1, which is the distance between the abutment position of the main body portion 641 of the transmission member 640 and the urging arm portion 652 of the torsion spring 650 and the cylindrical portion 642 in the state of FIG. 54(a), the similar abutment position length L2 in the state of FIG. 54(b) is moved away from the cylindrical portion 642 of the transmission member 640. That is, the abutment position length is extended. As a result, the arm length of the torsion spring 650 that pushes back the transmission member 640 is lengthened, so that the moment loaded from the torsion spring 650 to the transmission member 640 can be increased.

[0444] Therefore, for example, if the biasing force generated by torsion spring 650 is approximately the same in the state of Fig. 54(a) and the state of Fig. 54(b), the moment loaded on transmission member 640 can be made larger in Fig. 54(b). Therefore, it is possible to make it easier to push back transmission member 640 and performance member 620.

[0445] 53 and 54, the biasing force of torsion spring 650 pushing back transmission member 640 is small while the swing angle from the retracted position of transmission member 640 (performance member 620) is small, and increases elastically as the swing angle increases, increasing beyond the elastic increase at the border of the state of Fig. 54(a). Therefore, when the biasing force of torsion spring 650 required when performance member 620 is at the maximum swing angle (see Fig. 54(b)) is determined, the biasing force when the swing angle is small can be set smaller (a softer spring can be used) compared to when the torsion spring only increases elastically.

[0446] This reduces the degree to which the movement speed of performance member 620 when it starts to swing is slowed down by the biasing force of torsion spring 650, and makes it possible to increase the movement speed of performance member 620 when it starts to move.

[0447] 54(a), the biasing force is increased beyond the elastic increase, so that the deceleration acceleration of the performance member 620 can be increased when the swing angle of the performance member 620 is set to be equal to or greater than the state of FIG. 54(a). This makes it possible to delay the timing at which the performance member 620 starts to decelerate during the swinging motion of the performance member 620. Therefore, the swing angle at which the performance member 620 can be swung at high speed can be expanded, and the performance effect of the tilting motion unit 600 can be improved.

[0448] Next, the sliding motion of the tilting motion unit 600 and the sliding motion unit 700 will be described with reference to Fig. 56. Fig. 56 is a front view of the tilting motion unit 600 and the sliding motion unit 700. Note that in Fig. 56, the state in which the tilting motion unit 600 is placed in the retracted position is illustrated by an imaginary line, and the state in which the tilting motion unit 600 has been slid a predetermined amount from the retracted position is illustrated by a solid line.

[0449] 56, the connecting member 740 that connects the tilting motion unit 600 formed to be slidable in the up-down direction and the sliding motion unit 700 is formed to be movable in the extension direction of the front rail portion 715. Here, the weight of the tilting motion unit 600 is loaded on the connecting member 740, so when the tilting motion unit 600 is placed in the retracted position, the tilting motion unit 600 is urged by gravity to the left in front view along the front rail portion 715. Therefore, in order to maintain the tilting motion unit 600 in the retracted position, it is considered to fix the driving device 750.

[0450] In contrast, in this embodiment, the lever member 714 is formed to be able to swing up and down, and when the lever member 714 is swung downward, it engages with the locking portion 725 of the support member 720, restricting the sliding movement of the support member 720 in the left-right direction.

[0451] This makes it possible to mechanically maintain the tilt motion unit 600 in the retracted position, so that when the tilt motion unit 600 is disposed in the retracted position, the tilt motion unit 600 can be maintained in the retracted position with the drive device 750 stopped. Therefore, the durability of the drive device 750 can be improved.

[0452] Furthermore, when the tilting operation unit 600 is placed in the retracted position, the lever member 714 can be swung upward and the drive device 750 can be operated to move the support member 720, thereby allowing the tilting operation unit 600 to slide left and right.

[0453] As shown in FIG. 56, when the tilting motion unit 600 is placed in the retracted position in an inverted state, the pivot support portion 741a of the connecting member 740 is placed vertically below the center of gravity G of the tilting motion unit 600.

[0454] Here, since the direction of sliding movement of the tilting motion unit 600 is along the front rail portion 715, in FIG. 56, the movement of the tilting motion unit 600 while it is slid a predetermined amount from the retracted position (see imaginary line in FIG. 56) always has an upward and downward component.

[0455] Therefore, if the center of gravity G of the tilt motion unit 600 and the pivot support 741a of the connecting member 740 are misaligned in the vertical direction, a load may be applied from the connecting member 740 in a direction that rotates the tilt motion unit 600. This also applies when the tilt motion unit 600 slides in the opposite direction.

[0456] In contrast, in this embodiment, the pivot support 741a of the connecting member 740 is disposed vertically below the center of gravity G, so that the vertical component of the force applied from the connecting member 740 to the tilting motion unit 600 is formed on the same line as the center of gravity G. This makes it possible to prevent the connecting member 740 from applying a load in a direction that rotates the tilting motion unit 600, and to stabilize the posture of the tilting motion unit 600.

[0457] Next, with reference to Fig. 57, an effect that the tilting motion (swinging motion) of the tilting motion unit 600 has on the sliding motion of the sliding motion unit 700 will be described. Fig. 57 is a front view of the tilting motion unit 600 and the sliding motion unit 700. Note that Fig. 57 illustrates a state in which the performance member 620 of the tilting motion unit 600 has been swung to the state of Fig. 54(b).

[0458] 57, when the performance member 620 is swung counterclockwise as viewed from the front, the center of gravity G of the performance member 620 is located to the left as viewed from the front of the connecting member 740. Therefore, the acceleration to the left as viewed from the front that is applied to the connecting member 740 is increased.

[0459] In this case, the driving force required for sliding the tilting motion unit 600 from the retracted position can be reduced, so that the driving motor 751 of the driving device 750 can be made smaller.

[0460] Next, a tilting action unit 2600 in the second embodiment will be described with reference to FIGS.

[0461] In the first embodiment, the case has been described where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 is a flat surface, but in the tilting motion unit 2600 in the second embodiment, the main body 2641 of the transmission member 2640 includes an abutment portion 2641a that contacts the tip of the biasing arm 652 of the torsion spring 650. Note that the same parts as those in the above-mentioned embodiments are given the same reference numerals and their description will be omitted.

[0462] 58(a), 58(b) and 59 are front views of the transmission member 2640 and the torsion spring 650 in the second embodiment. In addition, in FIG. 58(a), 58(b) and 59, the outer shapes of the base member 610 and the performance member 620 are illustrated by imaginary lines. Also, FIG. 58(a) illustrates an inverted state in which the slide hole 643 of the transmission member 2640 is disposed vertically above the cylindrical portion 642, FIG. 58(b) illustrates a state in which the transmission member 2640 is swung a predetermined amount counterclockwise from the inverted state of FIG. 58(a) and the lower surface of the abutment portion 2641a is abutted against the tip of the biasing arm portion 652 of the torsion spring 650, and FIG. 59 illustrates a state in which the transmission member 2640 is further swung counterclockwise from the state of FIG. 58(b) in the front view.

[0463] 58, when the transmission member 2640 is swung from the inverted state (see FIG. 58(a)), the main body 2641 is pressed against the biasing arm 652 of the torsion spring 650, and the torsion spring 650 generates a biasing force that swings the main body 2641 in a direction returning it to the inverted state. When the transmission member 2640 is swung and the biasing arm 652 is deformed, the coil 651 is deformed by reducing its diameter by the connecting arm 653 that is connected to the biasing arm 652 on the deformed side. In other words, the more the coil 651 is reduced in diameter, the greater the biasing force that swings the transmission member 2640 in a direction returning it to the inverted state.

[0464] 58, due to the difference in the swing angle between the biasing arm 652 of the torsion spring 650 and the transmission member 2640, the contact position between the main body 2641 of the transmission member 2640 and the biasing arm 652 (the tip position of the biasing arm 652) is changed by the swing of the transmission member 2640. That is, the more the transmission member 2640 is swung, the more the tip of the biasing arm 652 is moved toward the tip side of the main body 2641 (the side closer to the sliding hole 643).

[0465] Therefore, as shown in FIG. 58(b), when the lower surface of the abutting portion 2641a abuts against the tip portion of the urging arm 642, if the transmission member 2640 is further rotated counterclockwise when viewed from the front, the movement of the urging arm 642 toward the tip side of the main body portion 2641 is restricted by the abutting portion 2641a.

[0466] 59, when the transmission member 2640 is swung in a state in which the movement of the attachment arm portion 642 is restricted by the abutting portion 2641a, the torsion spring 650 is deformed as a whole. That is, the base side (the side of the bent portion 653a) of the urging arm portion 642 is moved downward by the amount that the movement of the urging arm portion 642 toward the tip side of the main body portion 2641 is restricted. As a result, the connecting arm portion 653 is moved in a direction that reduces the diameter of the coil portion 651 (a direction in which the urging force of the torsion spring 650 increases).

[0467] That is, the biasing force of the torsion spring 650 can be increased when the transmission member 2640 is swung to the state shown in Fig. 59, compared to when there is no abutting portion 2641a. This makes it possible to increase the degree of change in the biasing force generated by the torsion spring 650 (the rate of increase in the biasing force relative to the swing angle of the transmission member 2640) in the state shown in Fig. 59, compared to the state shown in Fig. 58. Therefore, when the swing angle of the transmission member 2640 is small, the biasing force of the torsion spring 650 is suppressed, and the starting speed of the transmission member 2640 is increased, while when the swing angle is large (see Fig. 59), the biasing force of the torsion spring 650 is increased nonlinearly (more than elastic change), and a biasing force sufficient to return the transmission member 2640 to the inverted state can be obtained.

[0468] Next, a tilting action unit 3600 in the third embodiment will be described with reference to FIG.

[0469] In the first embodiment, the case was described where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 has a constant width, but in the tilting motion unit 3600 in the third embodiment, the main body 3641 of the transmission member 3640 has an inclined side surface 3641a that is inclined so that the width becomes wider as it approaches the tip side, on the side surface that contacts the tip of the torsion spring 650. Note that the same parts as in the above-mentioned embodiments are given the same reference numerals, and their description will be omitted.

[0470] Fig. 60(a) and Fig. 60(b) are front views of the transmission member 3640 and torsion spring 650 in the third embodiment. In Fig. 60(a) and Fig. 60(b), the outlines of the base member 610 and the performance member 620 are shown by imaginary lines. Fig. 60(a) illustrates an inverted state in which the sliding hole 643 of the transmission member 3640 is disposed vertically above the cylindrical portion 642, and Fig. 60(b) illustrates a state in which the transmission member 3640 has been swung a predetermined amount counterclockwise when viewed from the front from the inverted state of Fig. 60(a).

[0471] As shown in Figure 60, when the transmission member 3640 is swung from the inverted state (see Figure 60 (a)), the main body portion 3641 is pressed against the biasing arm portion 652 of the torsion spring 650, and the torsion spring 650 generates a biasing force that swings the main body portion 3641 in a direction returning it to the inverted state.

[0472] 60(b) from the state shown in Fig. 60(a) to the state shown in Fig. 60(b), due to the difference in the swing angle between the biasing arm 652 of the torsion spring 650 and the transmission member 3640, the contact position between the main body 3641 of the transmission member 3640 and the biasing arm 652 (the tip position of the biasing arm 652) is changed by the swing of the transmission member 3640. That is, the larger the swing angle from the inverted state of the transmission member 3640 (see Fig. 60(a)), the more the tip of the biasing arm 652 moves toward the tip side of the main body 3641 (the side closer to the sliding hole 643).

[0473] Therefore, the tip of the biasing arm 652 slides along the inclined side surface 3641a of the main body 3641. That is, when the transmission member 3640 is swung, the torsion spring 650 is deformed due to the swing angle of the transmission member 3640, and also due to the width of the transmission member 3640 being expanded by the inclined side surface 3641a. In this case, the width of the transmission member 3640 is expanded more toward the tip of the transmission member 3640, so that the deformation of the torsion spring 650 due to the width of the transmission member 3640 being expanded by the inclined side surface 3641a increases as the swing angle of the transmission member 3640 from the inverted state (see FIG. 60(a)) increases. Therefore, as the swing angle of the transmission member 3640 increases, the rate of increase in the biasing force generated by the torsion spring 650 (change in the biasing force of the torsion spring 650 relative to the swing angle of the transmission member 3640) can be increased.

[0474] Next, a tilting operation unit 4600 in the fourth embodiment will be described with reference to FIGS.

[0475] In the first embodiment, the case where the contact portion 644 of the transmission member 640 is fixed has been described, but in the tilting motion unit 4600 in the fourth embodiment, the transmission member 4640 includes, in addition to the contact portion 644, a moving contact member 4647 having a width shorter than that of the contact portion 644. Note that the same parts as those in the above-mentioned embodiments are given the same reference numerals, and the description thereof will be omitted.

[0476] Figure 61(a) is a rear perspective view of a transmission member 4640 in the fourth embodiment, and Figure 61(b) is a rear perspective view of a moving contact member 4647. Note that in Figure 61(a), illustration of the moving contact member 4647 is omitted.

[0477] 61(a), the front arc plate portion 4645 of the transmission member 4640 has guide holes 4645a that are bored in the front-rear direction and symmetrically arranged at intervals shorter than the intervals between the contact portions 644. The guide holes 4645a are through holes that guide the pair of rear projections 4647b of the moving contact member 4647 to be movable in the front-rear direction.

[0478] As shown in Figure 61 (b), the movable abutment member 4647 mainly comprises a main body portion 4647a formed in the shape of a long plate, a pair of rear protrusions 4647b protruding from both ends of the main body portion 4647a toward the rear side, and a front protrusion portion 4647c protruding from approximately the center of the main body portion 4647 toward the front side with a hemispherical tip.

[0479] One end of the coil spring 4648 is fixed to the side opposite the front protrusion 4647c of the main body 4647a, and the other end of the coil spring 4648 is fixed to the main body 641b (see Figs. 62(c) and 62(d)). For ease of understanding, the coil spring 4648 is omitted from Figs. 61(a), 61(b), 62(a) and 62(b).

[0480] The rear projection 4647b is a portion that is inserted from the front side into the guide hole 4645a of the transmission member 4640, and is formed in such a manner that a sufficient length (a length that can abut against the biasing arm 652 of the torsion spring 650) protrudes from the front arc plate portion 4645 when the projection 4647b is inserted. The rear projection 4647b is formed at an inclination angle that abuts against the biasing arm 652 of the torsion spring 650 at a surface (line) (see FIG. 64(b)). This reduces the load applied to the biasing arm 652 (suppresses stress concentration) compared to when the biasing arm 652 and the rear projection 4647b abut at a point, and the durability of the biasing arm 652 can be improved.

[0481] The front protrusion 4647c is a portion that comes into contact with the main body member 4621 (see FIG. 63) of the performance member 4620, and the moving contact member 4647 is moved away from the front arc plate portion 4645 (see FIG. 62(c)) or moved close to the front arc plate portion 4645 (see FIG. 62(d)) due to its relationship with the escape opening 4621a formed in the main body member 4621. Note that, since the tip of the front protrusion 4647c is formed in a hemispherical shape, it is possible to easily make the front protrusion 4647c ride up onto the surface of the main body member 4621 from the escape opening 4621a.

[0482] Figures 62(a) and 62(b) are rear perspective views of the transmitting member 4640, and Figures 62(c) and 62(d) are top views of the transmitting member 4640. Note that Figures 62(a) and 62(c) show a state in which the moving abutment member 4647 is separated from the front arc plate portion 4645, and Figures 62(b) and 62(d) show a state in which the moving abutment member 4647 is brought close to the front arc plate portion 4645.

[0483] 63 is a front schematic diagram showing the main body member 4621 of the performance member 4620. The transmission member 4640 that forms an inverted state with respect to the main body member 4621 is shown by imaginary lines as a center state 4640C, a state in which the transmission member 4640 is swung counterclockwise when viewed from the front as a counterclockwise swing state 4640L, and a state in which the transmission member 4640 is swung clockwise when viewed from the front as a clockwise swing state 4640R. In addition, in the center state 4640C, the counterclockwise swing state 4640L, and the clockwise swing state 4640R, the abutment portion 644, the front arc plate portion 4645, and the back arc plate portion 646 are omitted from illustration in order to facilitate understanding.

[0484] The main body member 4621 has an escape opening 4621a formed in the front-rear direction. As shown in Fig. 63, the escape opening 4621a is formed in a region (between the center state 4640C and the counterclockwise swing state 4640L) through which the front protrusion 4647c (see Fig. 62) moves when the transmission member 4640 is swung counterclockwise as viewed from the front.

[0485] When the front projection 4647c of the transmission member 4640 overlaps with the escape opening 4621a in a front view, the front projection 4647c is inserted into the escape opening 4621a, and the moving contact member 4647 is moved away from the main body 641 of the transmission member 4640 by the elastic force of the coil spring 4648 (see FIG. 62(c)). On the other hand, when the front projection 4647c does not overlap with the escape opening 4621a (overlaps with the main body member 4621), the front projection 4647c abuts against the side surface on the rear side of the main body member 4621 of the performance member 4620, and the moving contact member 4647 is brought close to the main body 641 of the transmission member 4640 (see FIG. 62(d)).

[0486] That is, the rear projection 4647b of the moving contact member 4647 is extended to a position where it can come into contact with the biasing arm 652 of the torsion spring 650 when the transmission member 4640 is swung clockwise from the inverted state as viewed from the front. Therefore, the rate of increase in the biasing force generated by the biasing arm 652 of the torsion spring 650 (the degree of increase in the biasing force relative to the swing angle) can be increased when the transmission member 4640 is swung clockwise from the inverted state as viewed from the front, compared to when it is swung counterclockwise as viewed from the front.

[0487] 64(a) and 64(b) are front views of the transmission member 4640 and the torsion spring 650. In addition, in FIG. 64(a) and FIG. 64(b), the outer shapes of the base member 610 and the performance member 4620 are illustrated by imaginary lines, and the main body portion 4647a of the moving contact member 4647 is omitted for ease of understanding. Also, FIG. 64(a) illustrates an inverted state in which the sliding hole 643 of the transmission member 4640 is disposed vertically above the cylindrical portion 642, and FIG. 64(b) illustrates a state in which the transmission member 4640 is swung a predetermined amount clockwise from the inverted state of FIG. 64(a) and the biasing arm portion 652 on the left side in front view is in contact with the rear projection portion 4647b.

[0488] As shown in FIG. 64(b), by making it possible for the biasing arm 652 to abut from the opposite side (the abutment portion 644 side) of the main body 641 of the transmission member 4640 while the swing angle of the transmission member 4640 is small, the biasing force generated by the torsion spring 650 when the transmission member 4640 is rotated clockwise when viewed from the front can be increased.

[0489] This makes it possible to increase the biasing force when the transmission member 4640 is swung clockwise when viewed from the front while increasing the starting speed when the transmission member 4640 is swung counterclockwise when viewed from the front. Therefore, it is possible to prevent the performance member 4620 from colliding with the inner surface of the rear case 210.

[0490] That is, when the tilting operation unit 4600 is disposed in the retracted position and the performance member 4620 is in an inverted state, the inner surface of the rear case 210 is brought into close proximity with the performance member 4620 (see FIG. 5). Here, if the performance member 4620 is swung from a state in which it is swung counterclockwise as viewed from the front (see FIG. 57) to an inverted state with force, the performance member 4620 cannot be decelerated sufficiently, and there is a risk that the performance member 4620 will collide with the inner surface of the rear case 210.

[0491] In contrast, in this embodiment, the rear projection 4647b is protruded (see FIG. 62(d)) at the timing when the performance member 4620 is swung clockwise as viewed from the front from the inverted state, and the biasing force of the torsion spring 650 can be increased. This allows the performance member 4620 to be sufficiently decelerated when tilting clockwise from the inverted state while maintaining a high operating speed when tilting counterclockwise as viewed from the front from the inverted state.

[0492] Also, a biasing force is generated in a direction to push back the rear protrusion 4647b (counterclockwise in front view in FIG. 64(b)) at the contact point between the rear protrusion 4647b and the biasing arm 652, which are disposed on the opposite side of the swing direction of the transmitting member 4640. This makes it possible to push back the transmitting member 4640 with a larger biasing force than when the transmitting member 4640 is pushed back only by the biasing arm 652 disposed on the side approaching the transmitting member 4640 (right side in FIG. 64(b)). On the other hand, it is also possible to improve the biasing force generated by the biasing arm 652 disposed on the side approaching the transmitting member 4640.

[0493] 64, the distance from the lower support plate portion 614a to the bent portion 653a is shorter than the distance from the position where the abutment portion 644, which is arranged on the opposite side to the side approached by the transmission member 4640, and the biasing arm portion 652 abut against the lower support plate portion 614a. In this case, it is easy to move the bent portion 653a by the force from the abutment portion 644, with the lower support plate portion 614 as the fulcrum, but the reverse is difficult (because there is a difference in the distance from the fulcrum to the point of action).

[0494] Therefore, the urging force generated by the deformation of the urging arm 652 on the left side as viewed from the front, which occurs when the abutment portion 644 and the urging arm 652 come into contact with each other, is generated by the deformation of the entire torsion spring 650. That is, the deformation in which the bent portion 653a on the left side as viewed from the front is moved to the left as viewed from the front (in the direction narrowing the inner diameter of the coil portion 651) with the lower receiving plate portion 641a as a fulcrum, causes the deformation of the connecting arm 653, the coil portion 651, and the urging arm 652 on the right side as viewed from the front. In this case, since the coil portion 651 is deformed to reduce its inner diameter, the coil portion 651 and the connecting arm 653 generate a urging force in the direction to increase the inner diameter of the coil portion 651, and the urging force of the urging arm 652 on the right side as viewed from the front (the swing direction side of the transmission member 4640) pushing back the transmission member 640 can be improved.

[0495] Next, a composite action unit 5500 in the fifth embodiment will be described with reference to FIGS.

[0496] In the first embodiment, a case has been described in which when the rotating arm member 550 is disposed in the extended position, the second non-transmitting wall portion 553c has a shape along a circle centered on the rotation axis of the rotating crank member 570, but in the fifth embodiment, the rotating arm member 5550 has a recessed portion 5556 in which the non-transmitting wall portion 5553c is recessed in a direction away from the rotating crank member 570. Note that the same parts as those in the above-mentioned embodiments are denoted by the same reference numerals, and description thereof will be omitted.

[0497] 65 to 68 are front views of a composite action unit 5500 in the fifth embodiment. In addition, Figure 65 shows a state in which the rotating arm member 5550 is positioned in the extended position and the sliding protrusion portion 574 of the rotating crank member 570 is positioned near the left end portion of the second non-transmitting wall portion 5553c, Figure 66 shows a state in which the rotating crank member 570 is rotated counterclockwise when viewed from the front from the state in Figure 65 and the sliding protrusion portion 574 is accommodated in the first recessed portion 5556 from the left end of the second non-transmitting wall portion 5553c, Figure 67 shows a state in which the rotating crank member 570 is rotated counterclockwise when viewed from the front from the state in Figure 66 to a position where the sliding protrusion portion 574 is removed from the recessed portion 5556, and Figure 68 shows a state in which the rotating crank member 570 is rotated counterclockwise when viewed from the front from the state in Figure 67 and the sliding protrusion portion 574 is accommodated in two recessed portions 5556 from the left end of the second non-transmitting wall portion 5553c.

[0498] As shown in FIGS. 65 to 68, the second non-transmitting wall portion 5553c of the composite action unit 5550 is provided with a recessed portion 5556 recessed in a direction away from the rotating crank member 570.

[0499] The recessed portion 5556 mainly includes a first wall portion 5556a having an arc shape (about 1 / 4 of a circle) formed on the left side as viewed from the front, and a second wall portion 5556b having an arc shape (about 1 / 4 of a circle) formed on the right side as viewed from the front, and is shaped to enable sliding of the sliding protrusion portion 574 of the rotating crank member 570. That is, the recessed depth of the recessed portion 5556 from the second non-transmitting wall portion 5553c is set to be equal to or less than the radius of the sliding protrusion portion 574, and the connecting portion between the recessed portion 5556 and the second non-transmitting wall portion 5553c is formed of a smooth curved surface.

[0500] 66, a gap is generated between the sliding protrusion 574 and the second non-transmitting wall portion 5553c, and the rotating arm member 5550 is swung by the biasing force generated by the torsion spring 517a until it abuts against the sliding protrusion 574. In this case, as the rotating crank member 570 is rotated, the first wall portion 5556a of the first recessed portion 5556 from the left end of the second non-transmitting wall portion 5553c is slid by the sliding protrusion 574, and the rotating arm member 5550 is swung.

[0501] That is, between the state shown in Fig. 65 and the state shown in Fig. 66, the rotating arm member 5550 is merely swung by the biasing force of the torsion spring 517a, and is not swung by the driving force of the second driving device 560. Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view and the sliding protrusion portion 574 of the rotating crank member 570 is disposed opposite to the first wall portion 5556a, the rotating arm member 5550 and the rotating crank member 570 form a non-transmitting state.

[0502] 67, the sliding protrusion 574 is pressed against the second wall portion 5556b of the first recessed portion 5556 from the left end of the second non-transmitting wall portion 5553c, and the rotating arm member 5550 is swung (pushed down) to the extended position again. That is, from the state shown in FIG. 66 to the state shown in FIG. 67, the second wall portion 5556b is pushed forward and moved by the sliding protrusion 574, thereby causing the rotating arm member 5550 to swing, and the driving force of the second driving device 560 is transmitted to the rotating arm member 5550 via the rotating crank member 570.

[0503] Therefore, when the rotating crank member 570 is rotated counterclockwise when viewed from the front and the sliding protrusion portion 574 of the rotating crank member 570 is disposed opposite to the second wall portion 5556b, the rotating arm member 5550 and the rotating crank member 570 form a transmission state.

[0504] When the rotating crank member 570 is rotated counterclockwise as viewed from the front from the state shown in Fig. 67 to the state shown in Fig. 68, a gap is generated between the sliding protrusion 574 and the second non-transmitting wall portion 5553c, and the rotating arm member 5550 is swung by the biasing force generated by the torsion spring 517a until it abuts against the sliding protrusion 574. In this case, as the rotating crank member 570 is rotated, the first wall portion 5556a of the second recessed portion 5556 from the left end of the second non-transmitting wall portion 5553c is slid by the sliding protrusion 574, and the rotating arm member 5550 is swung.

[0505] That is, between the state shown in Fig. 67 and the state shown in Fig. 68, the rotating arm member 5550 is merely swung by the biasing force of the torsion spring 517a, and the rotating arm member 5550 is not swung by the driving force of the second driving device 560. Therefore, when the rotating crank member 570 is rotated counterclockwise when viewed from the front and the sliding protrusion portion 574 of the rotating crank member 570 is disposed opposite to the first wall portion 5556a, the rotating arm member 5550 and the rotating crank member 570 form a non-transmitting state.

[0506] As shown in Figures 65 to 68, when the rotating crank member 570 is rotated counterclockwise when viewed from the front, a non-transmitting state is formed between the rotating crank member 570 and the rotating arm member 5550 when the sliding protrusion 574 is positioned opposite the first wall portion 5556a, and a transmitting state is formed between the rotating crank member 570 and the rotating arm member 5550 when the sliding protrusion 574 is positioned opposite the second wall portion 5556b.

[0507] It should be noted that if the rotation direction of the rotating crank member 570 is reversed, the relationship between the first wall portion 5556a and the second wall portion 5556b is reversed. That is, when the rotating crank member 570 is rotated clockwise as viewed from the front, a transmitted state is formed between the rotating crank member 570 and the rotating arm member 5550 when the sliding protrusion portion 574 is disposed opposite to the first wall portion 5556a, and a non-transmitted state is formed between the rotating crank member 570 and the rotating arm member 5550 when the sliding protrusion portion 574 is disposed opposite to the second wall portion 5556b.

[0508] As shown in Figures 65 to 68, in this embodiment, in addition to the swinging motion in which the rotating arm member 5550 is swung between the retracted position (see Figure 22) and the extended position, it is possible to form a swinging motion in which the rotating arm member 5550 is swung in a narrow width manner near the extended position (a manner in which the lower end of the front plate member 546 is moved between positions U1 and U2) without switching the swing direction of the rotating crank member 570.

[0509] This allows the rotating arm member 5550 to perform a swinging motion that is difficult to achieve by switching the drive direction of the drive device 560. That is, it is possible to cause the rotating arm member 5550 to perform a swinging motion with a small width near the extended position by repeatedly switching the drive direction of the drive device 560 at short intervals. However, in this case, the width of the swinging motion depends on the switching speed of the drive direction of the drive device 560. Also, even if the drive direction of the drive device 560 is switched when the swinging motion speed of the rotating arm member 5550 is high, the inertia of the drive device 560 and the rotating arm member 5550 is large and the drive direction cannot be switched instantly, and there is a risk that it takes a long time to switch the drive direction.

[0510] In contrast to this, in the present embodiment, the swinging operation of the rotating arm member 5550 near the extended position does not require switching the rotation direction of the rotating crank member 570, and therefore the time required for switching the drive direction can be eliminated.

[0511] Furthermore, the speed of the action of the rotating arm member 5550 swinging clockwise when viewed from the front (upward swinging action) depends on the biasing force generated by the torsion spring 517a, and the speed of the action of the rotating arm member 5550 swinging counterclockwise when viewed from the front (downward swinging action) depends on the rotation speed of the rotating crank member 570. Therefore, by increasing the biasing force of the torsion spring 517a and increasing the rotation speed of the rotating crank member 570, the swing speed of the rotating arm member 5550 in the vicinity of the extended position can be increased.

[0512] This makes it possible to achieve both an increase in the speed of the swinging action of the rotating arm member 5550 near the extended position and a reduction in the time required to switch the swinging direction.

[0513] Next, a composite action unit 6500 in the sixth embodiment will be described with reference to FIGS.

[0514] In the first embodiment, the rotating arm member 550 of the composite action unit 500 is integrally molded, but in the sixth embodiment, the rotating arm member 6550 is formed by connecting two members. The posture of the arc-shaped hole 554 formed at the other end is...

Claims

[Claim 1] A first driving means; a movable means configured to be movable along a predetermined movement trajectory by the driving force of the first driving means; and a second drive means, a first situation in which a predetermined moving means that can move upward from a predetermined position by a driving force of the second driving means abuts against a predetermined portion of the movable means that moves along the predetermined movement trajectory, thereby limiting the movement range of the movable means; a second state in which the predetermined moving means does not abut on a predetermined portion of the movable means; In the first situation, the predetermined moving means is capable of contacting a plurality of positions including a first position in the predetermined portion or a second position in the predetermined portion different from the first position; a movement range of the movable means when the predetermined moving means is abutted at the first position is different from a movement range of the movable means when the predetermined moving means is abutted at the second position, A gaming machine, characterized in that a driving mode of the first driving means is different when the first state is changed to the second state and when the second state is changed to the first state.

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