JP2019069262A - Game machine - Google Patents

Abstract

To provide a game machine which is excellent in disposition mode of a stopper member.SOLUTION: A rotary arm member 550 moves in correspondence with an expansion and contraction performance device 540, so that the rotation arm member 550 in the case where the expansion and contraction performance device 540 is arranged at a first position can be used as the rotation arm member 550 in the case where the expansion and contraction performance device 540 is arranged at a second position. Thus, it is possible to save a rotation space to dispose the rotation arm member 550. The rotation arm member 550 changes a movement width of the expansion and contraction performance device 540, depending on whether the expansion and contraction performance device 540 is arranged at the first position or the expansion and contraction performance device 540 is arranged at the second position, so that it is possible to increase variations of movement widths of the expansion and contraction performance device 540.SELECTED DRAWING: Figure 42

Description

  The present invention relates to a gaming machine such as a pachinko machine.

  In a gaming machine such as a pachinko machine, there is a gaming machine provided with a movable member formed movably and a stopper member for restricting the movement width of the movable member (Patent Document 1).

JP, 2012-016623, A

  However, in the above-described conventional gaming machine, there is a problem that there is room for improvement in the aspect of the arrangement of the stopper member.

  The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a good gaming machine in which the stopper member is disposed.

  In order to achieve this object, the gaming machine according to claim 1 is movable along a predetermined movement trajectory, and movable members which can be arranged at different first and second positions, and the movable members thereof. The movement width of the predetermined movement trajectory of the movable member is restricted by moving in correspondence with the movable member, and the movable member is arranged at the first position or at the second position. And a stopper member that changes the moving width of the movable member depending on whether it is moved or not.

  The gaming machine according to claim 2 is the gaming machine according to claim 1, wherein the movable member is pivotally supported by the first shaft so as to be able to pivot and extend and contract in the radial direction of the first shaft. The telescopic length of the intermediate member differs between the first position and the second position, the predetermined movement trajectory is formed in an arc shape centered on the first axis, and the stopper member is The intermediate member is extended along the predetermined movement trajectory of the movable member when the intermediate member is in a predetermined expansion and contraction state.

  The gaming machine according to claim 3 is the gaming machine according to claim 2, wherein the movable member includes a projection which protrudes toward the stopper member, and the stopper is inserted through the projection. The movable member and the stopper member interlock in an expansion and contraction direction of the intermediate member in a state in which the insertion portion is provided, and the protrusion is inserted into the insertion portion, and the movable member is in contact with the insertion portion .

  According to the gaming machine of the first aspect, it is possible to improve the mode of arrangement of the stopper member.

  According to the gaming machine of the second aspect, in addition to the effects of the gaming machine of the first aspect, the aspect of the disposition of the stopper member can be made more favorable.

  According to the gaming machine of the third aspect, in addition to the effects of the gaming machine of the second aspect, the functions can be concentrated on the stopper member.

It is a front view of a pachinko machine in a 1st embodiment. It is a front view of a game board of a pachinko machine. It is a rear view of a pachinko machine. It is a block diagram which shows the electric constitution of a pachinko machine. It is a disassembled front perspective view of a game board and an operation unit. It is a disassembled front perspective view of an operation | movement unit. It is a disassembled front perspective view of an operation | movement unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front disassembled perspective view of a board and a board lower unit. It is a front disassembled perspective view of a board lower part unit. (A) is a front view of a base member, a 1st out port, a 2nd out port, a lower left board member, and a lower right board member, (b) is a base member in the XVb-XVb line of Drawing 15 (a) And FIG. 12 is a cross-sectional view of the lower left plate member. It is a front perspective view of an up-and-down operation unit. It is a rear perspective view of an up-and-down operation unit. It is a front disassembled perspective view of a vertical motion unit. It is a back surface disassembled perspective view of an up-and-down operation unit. It is a front view of a vertical motion unit. It is a front view of a vertical motion unit. It is a front perspective view of a compound operation unit. It is a rear perspective view of a compound operation unit. It is a front disassembled perspective view of a compound operation unit. FIG. 7 is a rear exploded perspective view of the combined operation unit. It is a front disassembled perspective view of an expansion-contraction production apparatus. It is a back surface disassembled perspective view of an expansion-contraction production apparatus. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. It is a front view of a rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. It is a graph showing the distance from a standard horizontal line of a projection part. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front perspective view of a tilting operation unit and a slide operation unit. It is a rear perspective view of a tilting operation unit and a slide operation unit. It is a front disassembled perspective view of a slide operation unit. It is a rear exploded perspective view of a slide operation unit. It is a front disassembled perspective view of a tilting operation unit. It is a rear exploded perspective view of a tilting operation unit. It is a front disassembled perspective view of a presentation member and a 2nd drive device. (A) And (b) is a front view of a transmission member and a torsion spring. (A) And (b) is a front view of a transmission member and a torsion spring. It is a schematic diagram which shows typically the rocking angle of the presentation member with respect to the rocking angle of a transmission member. It is a front view of a tilting operation unit and a slide operation unit. It is a front view of a tilting operation unit and a slide operation unit. (A) And (b) is a front view of the transmission member and torsion spring in 2nd Embodiment. It is a front view of a transmission member and a torsion spring. (A) And (b) is a front view of the transmission member and torsion spring in 3rd Embodiment. (A) is a back perspective view of the transmission member in 4th Embodiment, (b) is a back perspective view of a movement contact member. (A) And (b) is a rear perspective view of a transmission member, (c) and (d) is a top view of a transmission member. It is a front schematic diagram which illustrated the main body member of a production member typically. It is a front view of a transmission member and a torsion spring. It is a front view of the compound operation unit in a 5th embodiment. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. FIG. 69 (a) is a partial front view of the pivoting arm member in the sixth embodiment, and FIG. 70 (b) is a partial top view of the pivoting arm member in the direction of arrow LXIXb in FIG. ) Is a partial front view of a pivoting arm member. (A) And (b) is a front perspective view of a switching device. (A) And (b) is a front view of a compound operation unit. (A) And (b) is a front view of the tilting operation unit in 7th Embodiment.

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

  As shown in FIG. 1, the pachinko machine 10 has an outer frame 11 in which an outer shell is formed by a substantially rectangular combination of wooden frames, and an outer frame 11 having substantially the same outer shape as the outer frame 11. And an inner frame 12 supported so as to be openable and closable. In the outer frame 11, metal hinges 18 are attached to upper and lower two places on the left side in front view (see FIG. 1) to support the inner frame 12, and the side on which the hinge 18 is provided is used as an opening / closing axis A frame 12 is supported so as to be openable and closable to the front side.

  In the inner frame 12, the game board 13 (see FIG. 2) having a large number of nails and winning openings 63, 64 and the like is detachably mounted from the back side. A ball (game ball) flows down the front of the game board 13 to play a ball game. In the inner frame 12, a ball emitting unit 112a (see FIG. 4) for emitting balls to the front area of the game board 13 and a ball for guiding balls emitted from the ball emitting unit 112a to the front area of the game board 13 Rails (not shown) and the like are attached.

  On the front side of the inner frame 12, a front frame 14 covering the upper front side and a lower tray unit 15 covering the lower side are provided. In order to support the front frame 14 and the lower tray unit 15, metal hinges 19 are attached to upper and lower two places on the left side of the front view (see FIG. 1), and the side on which the hinge 19 is provided is the front frame The lower tray unit 14 and the lower tray unit 15 are supported so as to be able to open and close to the front side. The locking of the inner frame 12 and the locking of the front frame 14 are released by inserting a dedicated key into the key hole 21 of the cylinder lock 20 and performing a predetermined operation.

  The front frame 14 is formed by assembling a decorative resin part, an electric part, and the like, and a window portion 14 c having an opening formed in a substantially elliptical shape is provided at a substantially central portion thereof. A glass unit 16 having two glass sheets is disposed on the back side of the front frame 14, and the front of the game board 13 can be visually recognized on the front side of the pachinko machine 10 through the glass unit 16.

  In the front frame 14, an upper plate 17 for storing balls is formed in a substantially box shape with an open upper surface projecting to the front side, and prize balls, lending balls, etc. are discharged to the upper plate 17. The bottom surface of the upper plate 17 is formed to be inclined downward to the right as viewed from the front (see FIG. 1), and the inclination thereof guides the ball thrown into the upper plate 17 to the ball firing unit 112a (see FIG. 4). Further, a frame button 22 is provided on the upper surface of the upper plate 17. The frame button 22 is operated by the player, for example, when changing the stage of the effect displayed on the third symbol display device 81 (see FIG. 2) or changing the content of the effect of super reach. Ru.

  The front frame 14 is provided with light emitting means such as various lamps around its periphery (for example, a corner portion). These light emitting means are controlled to change the light emission mode by lighting up or flashing according to the change in the gaming state at the time of a big hit, a predetermined reach time, etc., and play a role of enhancing the rendering effect during the game. The electric decoration parts 29-33 which incorporated light emission means, such as LED, are provided in the periphery of the window part 14c. In the pachinko machine 10, these electric decoration parts 29 to 33 function as effect lamps such as a big hit lamp, and at the time of big hit or reach production etc., each electric decoration part 29 to 33 is lit by lighting and blinking of the built-in LED. Alternatively, it blinks to notify that it is in the middle of a jackpot, or that it is in reach before the jackpot. Further, at the upper left portion of the front frame 14 in a front view (see FIG. 1), a light emitting means such as an LED is incorporated and provided with a display lamp 34 capable of displaying a payout ball and an error occurrence time.

  A small window 35 is formed on the right side below the electric decoration 32 so that a transparent resin is attached from the back side so that the back side of the front frame 14 can be seen, and the bonding space K1 on the front of the game board 13 (see FIG. 2) is made visible from the front of the pachinko machine 10. In addition, in the pachinko machine 10, a plating member 36 made of ABS resin plated with chromium is attached to the area around the electric decoration parts 29 to 33 in order to create more refreshingness.

  Under the window portion 14c, a ball rental operation unit 40 is disposed. The rental ball operation unit 40 is provided with a frequency display unit 41, a ball rental button 42, and a return button 43. When the rental ball operation unit 40 is operated with a bill, a card, etc. being inserted into a card unit (ball lending unit) (not shown) arranged on the side of the pachinko machine 10, the ball is A loan will be made. Specifically, the frequency display unit 41 is an area in which the remaining amount information of a card or the like is displayed, and the built-in LED lights up and the remaining amount is displayed as a number as remaining amount information. The ball lending button 42 is operated to obtain a lending ball based on the information recorded in the card etc. (recording medium), and the lending ball supplies the upper plate 17 as long as the remaining amount is present in the card etc. Be done. The return button 43 is operated when it is requested to return a card or the like inserted in the card unit. In the case of a pachinko machine in which a ball is lent directly to the upper plate 17 from a ball lending device or the like without passing through a card unit, a so-called cash machine does not require the ball operating unit 40. In this case, the ball operating unit 40 is used. A decorative seal or the like may be added to the installation part of to make the part configuration common. A pachinko machine using a card unit and a cash machine can be shared.

  In the lower tray unit 15 located below the upper tray 17, a lower tray 50 for storing the balls that can not be stored in the upper tray 17 is formed in a substantially box shape whose upper surface is opened at the central portion thereof There is. On the right side of the lower plate 50, an operation handle 51 operated by the player to drive a ball into the front of the game board 13 is disposed.

  Inside the operation handle 51, there are a touch sensor 51a for permitting driving of the ball emission unit 112a, an emission stop switch 51b for stopping emission of the ball during the pressing operation, and rotation of the operation handle 51. A variable resistor (not shown) or the like for detecting the amount of movement operation (rotational position) by a change in electrical resistance is incorporated. When the operation handle 51 is turned clockwise by the player, the touch sensor 51a is turned on, and the resistance value of the variable resistor changes corresponding to the amount of the turning operation, and the resistance value of the variable resistor is changed. The ball is fired with a strength corresponding to the (shooting strength), whereby the ball is struck to the front of the game board 13 with a flying amount corresponding to the operation of the player. Further, in a state where the operation handle 51 is not operated by the player, the touch sensor 51a and the emission stop switch 51b are off.

  At the front lower portion of the lower plate 50, a ball removing lever 52 for operating when discharging the balls stored in the lower plate 50 downward is provided. The ball release lever 52 is always urged in the right direction, and by sliding it in the left direction against the urging, the bottom surface opening formed on the bottom surface of the lower plate 50 is opened. A ball falls naturally from the bottom opening and is discharged. The operation of the ball release lever 52 is usually performed with a box (generally referred to as a "seven box") for receiving the ball discharged from the lower plate 50 below the lower plate 50. The operating handle 51 is disposed on the right side of the lower plate 50 as described above, and the ashtray 53 is attached on the left side of the lower plate 50.

  As shown in FIG. 2, the gaming board 13 has a base plate 60 cut into a substantially square shape in a front view, a large number of nails (not shown) for guiding balls, a windmill, and rails 61 and 62. The first opening 63, the second opening 640, the first variable winning device 65, the second variable winning device 650, the through gate 67, the variable display unit 80, etc. It is attached to the back side of the frame 12 (see FIG. 1). The base plate 60 is made of a light transmissive resin material, and is formed so as to allow the player to visually recognize various structures disposed on the rear surface 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 device unit 80 are disposed in through holes formed in the base plate 60 by router processing, and the game board It is fixed by a tapping screw etc. from the front side of 13.

  The front center portion of the game board 13 can be viewed from the front side of the inner frame 12 through the window portion 14c (see FIG. 1) of the front frame 14. Hereinafter, the configuration of the game board 13 will be described mainly with reference to FIG. The first variable winning device 65 is disposed in a through hole formed in the base member 310 of the lower panel unit 300 by router processing, and is fixed from the front side of the game board 13 by a tapping screw or the like.

  On the front of the game board 13, an outer rail 62 formed by bending a strip-shaped metal plate into a substantially arc shape is planted, and at the inner position of the outer rail 62, a strip-shaped metal plate is formed similarly to the outer rail 62. The arc-shaped inner rail 61 formed in the above is planted. The front outer periphery of the game board 13 is surrounded by the inner rails 61 and the outer rails 62, and the front and back are surrounded by the game board 13 and the glass unit 16 (see FIG. 1). A game area in which a game is played is formed by the behavior of the game. The game area is a front area of the game board 13 and is divided by two rails 61 and 62 and a resin outer edge member 73 connecting the rails (a prize opening and the like are provided and launched). Area where the ball flows down).

  The two rails 61 and 62 are provided to guide the ball fired from the ball launch unit 112a (see FIG. 4) to the top of the game board 13. A return ball preventing member 68 is attached to the end portion (upper left part in FIG. 2) of the inner rail 61, and the situation in which the ball guided to the upper part of the game board 13 once comes back into the ball guide passage is prevented. Be done. At the end of the outer rail 62 (the upper right part in FIG. 2), the rubber return 69 is attached to a position corresponding to the largest flying portion of the ball, and the ball fired with a predetermined momentum strikes the rubber return 69 Is bounced toward the central part while being attenuated.

  First symbol display devices 37A and 37B provided with a plurality of LEDs as light emitting means and a 7-segment display are disposed on the lower left side of the game area (the lower left side in FIG. 2). The first symbol display devices 37A and 37B perform display according to each control performed by the main control unit 110 (see FIG. 4), and display of the gaming state of the pachinko machine 10 is mainly performed. In the present embodiment, the first symbol display devices 37A and 37B are configured to be used according to whether the ball has won the first winning opening 64 or the second winning opening 640. Specifically, when the ball wins the first winning opening 64, the first symbol display device 37A is activated, and when the ball wins the second winning opening 640, the first The symbol display device 37B is configured to operate.

  In addition, the first symbol display devices 37A and 37B indicate whether or not the pachinko machine 10 is in a steady change, a time-short or a normal, by means of LEDs, or indicate whether it is in fluctuation by means of an on-light condition. The stop symbol indicates whether the symbol corresponds to the probability variation big hit or the symbol corresponding to the normal big hit or not by the lighted state, or indicates the number of holding balls by the lighted state, and by the 7-segment display device, the round of the big hit Display numbers and errors. In addition, a plurality of LEDs may be configured to have different emission colors (for example, red, green, blue) of the respective LEDs, and the combination of the emission colors may suggest various gaming states of the pachinko machine 10 with a small number of LEDs. it can.

  In the pachinko machine 10, a lottery is performed in response to the first winning opening 64 and the second winning opening 640 having a winning. In the lottery, the pachinko machine 10 determines whether or not the jackpot is successful (jump lottery), and when it is determined that the jackpot is made, the jackpot type is also determined. As jackpot types determined here, 15R probability variation jackpots, 4R probability variation jackpots, and 15R regular jackpots are prepared. Not only is it shown whether or not the result of the lottery is a big hit as the stop symbol after the end of the fluctuation in the first symbol display devices 37A, 37B, and if it is a big hit, a symbol according to the big hit type is shown .

  Here, "15R probability variation jackpot" is a probability variation jackpot where the maximum number of rounds shifts to a high probability state after 15 round jackpots, and "4R probability variation jackpot" is a maximum number of round jackpots with 4 rounds It is a probability change jackpot to shift to a high probability state after. Also, “15R normal jackpot” is a jackpot in which the maximum number of rounds transitions to a low probability state after jackpots of 15 rounds and for a predetermined number of fluctuations (for example, 100 fluctuation numbers) becomes a short time state. is there.

  Also, "high probability state" refers to a state in which the subsequent jackpot probability is increased as added value after the end of the jackpot, so-called probability fluctuation (during a definite change), in other words, a game that is easy to shift to a special gaming state The state of The high probability state (during a definite change) in the present embodiment includes a game state in which the ball is likely to be won in the second winning opening 640 by increasing the hitting probability of the second symbol described later. The term "low probability state" refers to a time when the probability of change is not positive, and a state where the jackpot probability is normal, that is, a state in which the jackpot probability is lower than that of probability change. Moreover, with the time saving state (time saving) of the "low probability state", the jackpot probability is a normal state, and only the jackpot probability of the second symbol is increased with the jackpot probability unchanged, and the second winning opening 640 To say the state of the game where the ball is easy to win. On the other hand, when the pachinko machine 10 is normally medium is the state of the game which is neither a definite change nor a time reduction (a state in which neither the jackpot probability nor the hit probability of the second symbol is increased).

  The probability change of the second symbol not only increases during a definite change or time, but also the time when the motorized accessory 640a attached to the second winning opening 640 is changed, and a longer time than normal It is set. When the motorized part 640a is in the open state (open state), the ball reaches the second winning opening 640 compared to when the motorized part 640a is in the closed state (closed state). It becomes easy condition. Therefore, the ball is likely to be won in the second winning opening 640 during a definite change or during a time cut, and it is possible to increase the number of times a jackpot lottery is performed.

  In addition, in addition to changing the opening time of the motorized role thing 640a attached to the second winning a prize opening 640 during a definite change or during a short time, or in addition to changing the opening time, the electric operation per hit A change may be made to increase the number of times the accessory 640 a is released more than in the normal mode. In addition, the probability of hitting the second symbol does not change during definite changes or during a short time, and the electric symbol 640a is opened at a time and once when the electric symbol 640a associated with the second winning opening 640 is opened. At least one of the numbers may be changed. In addition, the time during which the electric winning combination 640a associated with the second winning opening 640 is open or the number of times the electric combination 640a is opened per hit does not occur during a certain change or during a short time, and the second symbol is hit Only the probability may be changed to be up relative to normal.

  In the game area, there are provided a plurality of general winning openings 63 in which five to fifteen balls are paid out as winning balls by winning balls. Further, a variable display device unit 80 is disposed in the central portion of the game area. The variable display device unit 80 is triggered by winnings (start winnings) to the first winning opening 64 and the second winning opening 640, while being synchronized with the variable display in the first symbol display devices 37A and 37B, the third symbol A third symbol display device 81 configured of a liquid crystal display (hereinafter simply referred to as “display device”) that performs variable display, and an LED that variably displays the second symbol triggered by the passage of a ball of through gate 67 A second symbol display device (not shown) is provided. Further, a center frame 86 is disposed in the variable display unit 80 so as to surround the outer periphery of the third symbol display device 81.

  The third symbol display device 81 is configured of a large 9-inch liquid crystal display, and the display content is controlled by the display control device 114 (see FIG. 4), for example, the upper, middle and lower 3 One symbol column is displayed. Each symbol row is constituted by a plurality of symbols (third symbol), and the third symbol is variably displayed on the display screen of the third symbol display device 81 by horizontally scrolling these third symbols for each symbol row It is supposed to be. The third symbol display device 81 of the present embodiment is the first symbol display device 37A, 37B in which the display of the gaming state accompanied by the control of the main control device 110 (see FIG. 4) is performed, but the first A decorative display is performed according to the display of the symbol display devices 37A and 37B. The third symbol display device 81 may be configured using, for example, a reel instead of the display device.

  The second symbol display device alternately turns on the symbol “o” and the symbol “x” as display symbols (the second symbol (not shown)) for a predetermined time each time the ball passes through gate 67 It is a variable display. In the pachinko machine 10, when it is detected that the ball has passed the through gate 67, a winning lottery is performed. If it is a result of the winning lottery, if it is a hit, the symbol of "o" is stopped and displayed after the variation display of the second symbol in the second symbol display device. Further, if the result of the winning lottery is out of alignment, the symbol "x" is stopped and displayed after the variation display of the third symbol in the second symbol display device.

  In the pachinko machine 10, when the variable display in the second symbol display device is stopped at a predetermined symbol (in the present embodiment, the symbol "o"), the motorized role 640a attached to the second winning opening 640 has a predetermined time It is configured to be activated (opened) only.

  The time taken for the variable display of the second symbol is set so as to be shorter during the probability change or during the time saving than when the gaming state is normal. As a result, since the variation display of the second symbol is performed in a short time during the definite change and during the short time, it is possible to perform the winning lottery more frequently than in the middle. Therefore, since the chance of winning in the winning lottery increases, it is possible to give the player a lot of opportunities for the electric winning combination 640 a of the second winning opening 640 to be in the open state. Therefore, it is possible to make it easy for the ball to win the second winning opening 640 during the probability change and during the time saving.

  In addition, the second winning opening 640 during the definite change or time reduction by other methods, such as increasing the open probability and increasing the opening time and opening number of the motorized combination 640a per hit, which increases the hit probability during definite change or time reduction. When the ball is in a state in which it is easy to win, the time taken for the variable display of the second symbol may be constant regardless of the gaming state. On the other hand, when the time taken for the variable display of the second symbol is set shorter during the definite change or during the short time than during the normal time, the winning probability may be made constant regardless of the gaming state, and a single hit The opening time and the number of times of opening of the motorized role product 640a with respect to may be constant regardless of the gaming state.

  The through gate 67 is assembled to the game board on the right side in the lower area of the variable display unit 80, and among the balls fired on the game board, a part of the ball flowing down the right of the game board can pass Is configured. When the ball passes through gate 67, a lottery for winning the second symbol is performed. After the winning lottery, the variable display is performed on the second symbol display device, and if the result of the winning lottery is a hit, the symbol of "○" is displayed as a stop symbol of the variable display, and the result of the winning lottery is out For example, the symbol of "x" is displayed as a stop symbol of the variable display.

  The number of times the ball passes through gate 67 is held up to a total of four times, and the number of balls held is indicated by the above-mentioned first symbol display devices 37A and 37B and the second symbol hold lamp (not shown) Is also displayed. Four second symbol holding lamps are provided for the maximum number of holdings, and are arranged symmetrically below the third symbol display device 81.

  In addition, as the variable display of the second symbol is performed by switching on and off of a plurality of lamps in the second symbol display device as in the present embodiment, the first symbol display devices 37A, 37B and the third A part of the symbol display device 81 may be used. Similarly, the lighting of the second symbol holding lamp may be performed by part of the third symbol display device 81. Further, the maximum number of holding balls for the passage of the ball of the through gate 67 is not limited to four times, and may be set to three times or less, or five times or more (for example, eight times). Further, the number of through gates 67 assembled is not limited to one, and may be plural (for example, two). Further, the assembly position of the through gate 67 is not limited to the right side of the variable display unit 80, and may be, for example, the left side of the variable display unit 80. Further, since the number of balls held is indicated by the first symbol display devices 37A and 37B, the second symbol holding lamp may not perform the lighting display.

  Below the variable display unit 80, there is disposed a first winning opening 64 in which a ball can be won. When the ball is won in the first winning opening 64, the first winning opening switch (not shown) provided on the back side of the game board 13 is turned on, and the main control unit 110 is turned on due to the turning on of the first winning opening switch. A lottery for a big hit is made at (see FIG. 4), and a display corresponding to the lottery result is shown by the first symbol display device 37A.

  On the other hand, on the right side in a front view of the first winning opening 64, a second winning opening 640 in which a ball can win is disposed. When a ball is won in the second winning opening 640, a second winning opening switch (not shown) provided on the back side of the game board 13 is turned on, and the main control unit 110 is turned on due to the second winning opening switch being turned on. A lottery for a big hit is made at (see FIG. 4), and a display corresponding to the lottery result is shown by the first symbol display device 37B.

  Further, each of the first winning opening 64 and the second winning opening 640 is also one of the winning openings in which five balls are paid out as winning balls when the balls win. In the present embodiment, the number of winning balls to be paid out when the ball is won in the first winning opening 64 and the number of winning balls to be paid out when the ball is winning in the second winning opening 640 are configured the same. The number of winning balls to be paid out when the ball has won the first winning opening 64 and the number of winning balls to be paid out when the second winning opening 640 has the ball, for example, to the first winning opening 64 The number of winning balls to be paid out when the player wins a prize may be three, and the number of winning balls to be paid out when the second prize winning hole 640 has won may be five.

  The second winning opening 640 is accompanied by a motorized role 640 a. The electric role object 640a is configured to be openable and closable, and normally, the electric role object 640a is in a closed state (shrinkage state), and it is difficult for the ball to win the second prize opening 640. On the other hand, when the symbol of "o" is displayed on the second symbol display device as a result of the fluctuation display of the second symbol performed triggered by the passage of the ball to the through gate 67, the motorized role piece 640a is in the open state (enlarged State), and the ball is likely to win the second winning opening 640.

  As mentioned above, the probability of hitting the second symbol is higher than that in the normal condition, and the time taken for the variable display of the second symbol is short as compared to the normal, and therefore, in the variable display of the second symbol The symbol of “” becomes easy to be displayed, and the number of times that the motorized role piece 640 a is in the open state (enlarged state) is increased. Furthermore, during definite period of time and short time, the time when the motorized accessory 640a is opened is also longer than usual. Therefore, it is possible to create a state in which the ball is more likely to win to the second winning opening 640 compared to the normal time during definite variation and during time saving.

  Here, the probability of being a big hit is the same in either the low probability state or the high probability state in the case where the ball has won in the first winning opening 64 and the case in which the ball has won in the second winning opening 640. However, the probability of becoming a 15R probability variation jackpot as the type of jackpot selected when jackpot is higher is higher in the case where the ball has won in the second winning opening 640 than in the case where the ball has won in the first winning opening 64 It is set. On the other hand, the first winning opening 64 does not have a motorized part like the second winning opening 640, and the ball is always in a state where it is possible to win.

  Therefore, during the normal operation, there are many cases in which the motorized prize associated with the second winning opening 640 is in the closed state, and it is difficult to win the second winning opening 640, and therefore, it is directed to the first prize opening 64 without the electric jack. Launch the ball so that the ball passes the left side of the variable display unit 80 (so-called "left-handed"), and the winning of the first winning opening 64 gives a lot of opportunities for a big hit lottery and becomes a big hit It is advantageous for the player to aim at things.

  On the other hand, the electric gate 640a attached to the second winning opening 640 is likely to be in the open state by passing the ball through the through gate 67 during definite variation or time, and it is easy to win the second winning opening 640. The ball is fired so that the ball passes the right side of the variable display 80 toward the second winning hole 640 (so-called "right-handed"), and the motor gate is opened by passing through the through gate 67. It is advantageous for the player to aim at becoming a 15R probability variation jackpot by winning in the second winning opening 640.

  As described above, the pachinko machine 10 according to the present embodiment emits a ball to the player according to the gaming state of the pachinko machine 10 (whether it is in the process of being changed, time is short, or is normal). You can change the way of “right-handed” and “right-handed”. Therefore, the player can enjoy the game because it can change the way of hitting the ball.

  A first variable winning device 65 is disposed on the lower right side of the first winning opening 64, and a first specified winning opening 65a is provided substantially at the center thereof. In addition, a second variable winning device 650 is disposed on the left side of the variable display device 80, and a second central portion of the second variable winning device 650 has a circular shape similar in size to the other winning openings 63, 64 and 640. A specific winning hole 650a is provided. In the pachinko machine 10, when the jackpot lottery performed due to the winning in the first winning opening 64 or the second winning opening 640 becomes a big hit, after a predetermined time (variation time) has elapsed, the stop symbol of the big hit and The first symbol display device 37A or the first symbol display device 37B is turned on, and the stop symbol corresponding to the jackpot is displayed on the third symbol display device 81, and the occurrence of the jackpot is indicated. Thereafter, the gaming state transitions to a special gaming state (big hit) in which the ball is easy to win. In this special game state, the special winning openings 65a and 650a which are normally closed are opened for a predetermined time (for example, until 30 seconds have elapsed or 10 balls have been won).

  The specific winning opening 65a, 650a is closed when a predetermined time passes, and after the closing, the specific winning opening 65a, 650a is opened again for a predetermined time. The opening / closing operation of the specific winning opening 65a, 650a can be repeated, for example, 15 times (15 rounds) at the maximum. The state in which the opening and closing operation is being performed is a form of special gaming state advantageous to the player, and the player is paid out a larger amount of prize balls than usual as the provision of the gaming value (game value). Is done.

  Specifically, the first variable winning device 65 is a horizontally long rectangular opening / closing plate covering the first specified winning opening 65a, and a large opening solenoid 65b for opening / closing drive to the right with the lower side of the opening / closing plate as an axis See FIG. 15, only the outline is shown). The first specified winning combination opening 65 a is normally in a closed state in which the ball can not win or is difficult to win. In the case of a big hit, the large opening solenoid 65b is driven to tilt the opening / closing plate to the front side, and the ball temporarily forms an open state in which the first specified winning opening 65a is easy to win, and the open state and normal time It operates so as to alternately repeat the state with the closed state of.

  Specifically, the second variable winning device 650 is opened and closed on the left and right of the second specified winning opening 650a on the left and right sides of the opening and closing plate of the front view triangular shape and the lower side of the opening and closing plate. And a large open port solenoid (not shown). The second specified winning opening 650a is normally in a closed state in which the ball can not win or is difficult to win. In the case of a big hit, the small opening solenoid is driven to tilt the opening / closing plate to the left, and the ball temporarily forms an open state in which the second specified winning opening 650a is easy to win, and the open state and normal time It operates so as to alternately repeat the state of the closed state.

  In the present embodiment, it is possible to make the second variable winning device 650 win a ball by performing left hitting, so eliminating the hassle of switching between left hitting and right hitting whenever the gaming state changes. can do.

  In addition, the special gaming state is not limited to the above-mentioned form. A large opening is provided in the game area which is opened and closed separately from the specific winning openings 65a and 650a, and the specific winning openings 65a and 650a are for a predetermined time when the LED corresponding to the large hit is lit in the first symbol display devices 37A and 37B. When the specific winning opening 65a, 650a is opened, the large opening opening provided separately from the specific winning opening 65a, 650a is triggered by the ball winning into the specific winning opening 65a, 650a during a predetermined time. A gaming state opened a predetermined number of times may be formed as a special gaming state. Further, the specific winning hole 65a, 650a is not limited to one, and one or more (for example, three) may be disposed, and the arrangement position is also the lower right side of the first winning hole 64, or Not limited to the left side of the variable display device 80, for example, it may be below the first winning opening 64.

  In the lower right corner of the game board 13, a sticking space K1 for sticking a certificate stamp, an identification label or the like is provided, and a test piece stamped on the sticking space K1 is a small window of the front frame 14. It can be viewed through 35 (see FIG. 1).

  The game board 13 is provided with a first out port 314 and a second out port 315. A ball that flows down the game area and does not win any of the winning openings 63, 64, 65a, 640, 650a is discharged through the first out port 314 or the second out port 315. You will be guided to the road. The first out port 314 is disposed below the left side of the first winning port 64, while the second out port 315 is disposed below the right side of the first prize port 64. That is, the second out port 315 is disposed on the opposite side of the first out port 314 with the first winning port 64 interposed therebetween.

  Therefore, a ball flowing down the game area, which reaches the lower end (inner rail 61 or outer edge member 73) of the game area on the right side (right side in FIG. 2) of the first winning opening 64 in the front view is the inner rail 61 Alternatively, it is flowed down along the slope of the outer edge member 73 and guided to the ball discharge path through the second out port 315, while the lower end (inner rail 61) of the game area on the left side in front view than the first winning port 64. The ball reached is flowed down along the slope (curve) of the inner rail 61 and is guided to the ball discharge path through the first out port 314.

  A large number of nails are implanted in the game board 13 in order to appropriately disperse and adjust the falling direction of the ball, and various members (features) such as a windmill are disposed.

  As shown in FIG. 3, control board units 90 and 91 and a back pack unit 94 are mainly provided on the rear surface side of the pachinko machine 10. The control board unit 90 is integrated with a main board (main controller 110), an audio lamp control board (audio lamp control apparatus 113), and a display control board (display control apparatus 114). In the control board unit 91, a delivery control board (delivery control device 111), a emission control board (firing control device 112), a power supply board (power supply device 115), and a card unit connection board 116 are mounted and unitized.

  In the back pack unit 94, a back pack 92 forming a protective cover and a dispensing unit 93 are unitized. In addition, each control board is used as an MPU as a one-chip microcomputer that controls each control, a port to communicate with various devices, a random number generator used in various lottery, time counting and synchronization etc. Clock pulse generation circuits etc. are mounted as needed.

  The main control unit 110, the audio lamp control unit 113 and the display control unit 114, the payout control unit 111 and the emission control unit 112, the power supply unit 115, and the card unit connection board 116 are accommodated in the substrate boxes 100 to 104, respectively. . The substrate boxes 100 to 104 each include a box base and a box cover that covers the opening of the box base. The box base and the box cover are connected to each other to accommodate the control devices and the respective substrates.

  In addition, the substrate box 100 (main controller 110) and the substrate box 102 (dispensing controller 111 and firing controller 112) connect the box base and the box cover unsealably (sealing structure) by a sealing unit (not shown) Consolidated). Further, a seal seal (not shown) is pasted over the box base and the box cover at the connection portion between the box base and the box cover. The sealing seal is made of a brittle material, and if it is attempted to peel off the sealing seal to open the substrate box 100 or 102, or if the substrate box 100 or 102 is to be opened forcibly, the box base side and the box cover It is cut to the side. Therefore, by confirming the sealing unit or the sealing seal, it can be known whether or not the substrate box 100, 102 has been opened.

  Dispensing unit 93 is located at the top of back pack unit 94 and opens upward, tank 130, tank rail 131 connected to the lower side of tank 130 and gently inclined toward the downstream side, and downstream of tank rail 131. A case rail 132 vertically connected to the side, and a dispensing device 133 provided at the most downstream portion of the case rail 132 for dispensing balls by a predetermined electrical configuration of the dispensing motor 216 (see FIG. 4) ing. The balls supplied from the island facility of the game hall are successively replenished to the tank 130, and the required number of balls are paid out by the payout device 133 as appropriate. The tank rail 131 is attached with a vibrator 134 for applying vibration to the tank rail 131.

  In addition, the payout control device 111 is provided with the state recovery switch 120, the emission control device 112 is provided with the operation knob 121 of the variable resistor, and the power supply device 115 is provided with the RAM erase switch 122. The state recovery switch 120 is operated to eliminate the ball clogging (return to the normal state) when a dispensing error occurs, such as a ball clogging of the dispensing motor 216 (see FIG. 4) portion, for example. 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 in order to return the pachinko machine 10 to the initial state.

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

  The main controller 110 is mounted with an MPU 201 as a one-chip microcomputer which is an arithmetic device. The MPU 201 is a ROM 202 storing various control programs to be executed by the MPU 201 and fixed value data, and a memory for temporarily storing various data etc. when the control program stored in the ROM 202 is executed. A certain RAM 203 and various circuits such as an interrupt circuit, a timer circuit, and a data transmission / reception circuit are incorporated. In the main control unit 110, main processing of the pachinko machine 10, such as a jackpot lottery, display setting in the first symbol display devices 37A and 37B and the third symbol display device 81, and lottery of display results in the second symbol display device by the MPU 201 Run.

  Although various commands are transmitted from the main control unit 110 to the sub control unit by the data transmission / reception circuit in order to instruct the sub control units such as the payout control unit 111 and the audio lamp control unit 113 to operate. Such command is transmitted from the main control unit 110 to the sub control unit in one direction only.

  The RAM 203 is a stack area in which various areas, counters, flags, contents of internal registers of the MPU 201, return addresses of control programs executed by the MPU 201, etc. are stored, various flags and counters, I / O, etc. And a work area (work area) in which values are stored. The RAM 203 is configured to be able to receive data (backup) supplied with a backup voltage from the power supply 115 even after the pachinko machine 10 is powered off, and all data stored in the RAM 203 is backed up. .

  When the power is shut off due to the occurrence of a power failure or the like, the stack pointer at the time of the power shutoff (including the time of the power failure, the same applies hereinafter) and the value of each register are stored in the RAM 203. On the other hand, when the power is turned on (including the power on after the power failure is eliminated, the same applies hereinafter), the state of the pachinko machine 10 is restored to the state before the power is shut off based on the information stored in the RAM 203. Writing to the RAM 203 is executed when the power is shut off by a main process (not shown), and restoration of each value written to the RAM 203 is executed in a start-up process (not shown) when the power is turned on. The power failure signal SG1 from the power failure monitoring circuit 252 is input to the NMI terminal (non-maskable interrupt terminal) of the MPU 201 at the time of power interruption due to the occurrence of a power failure or the like. When it is input, NMI interrupt processing (not shown) as processing upon power failure is immediately executed.

  An input / output port 205 is connected to the MPU 201 of the main control unit 110 via a bus line 204 configured by an address bus and a data bus. The input / output port 205 has a payout control device 111, an audio lamp control device 113, first symbol display devices 37A and 37B, a second symbol display device, a second symbol hold lamp, and the lower side of the opening / closing plate of the specified winning opening 65a. A solenoid 209 consisting of a large opening solenoid for opening and closing drive and a solenoid for driving an electric part is connected to the front side, and the MPU 201 receives various commands and control signals via the input / output port 205. Send

  The input / output port 205 includes various switches 208 including a switch group (not shown) and a sensor group including a slide position detection sensor S and a rotational position detection sensor R, and a RAM erase switch circuit 253 provided in the power supply 115 described later. Are connected, and the MPU 201 executes various processes based on the signals output from the various switches 208 and the RAM erase signal SG2 output from the RAM erase switch circuit 253.

  The payout control device 111 drives the payout motor 216 to control the payout of the winning balls and the lending balls. The MPU 211, which is an arithmetic device, has a ROM 212 storing a control program to be executed by the MPU 211, fixed value data and the like, and a RAM 213 used as a work memory or the like.

  The RAM 213 of the payout control device 111 is, like the RAM 203 of the main control device 110, a stack area where 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, various flags and counters , I / O, etc. are stored in the work area (work area). The RAM 213 is configured to be able to receive a backup voltage from the power supply device 115 even after the pachinko machine 10 is turned off and to hold (back up) data, and all data stored in the RAM 213 is backed up. Similar to the MPU 201 of the main control unit 110, the NMI terminal of the MPU 211 is configured to receive the power failure signal SG1 from the power failure monitoring circuit 252 at the time of power interruption due to the occurrence of a power failure or the like. When input to the MPU 211, NMI interrupt processing (not shown) as processing upon power failure is immediately executed.

  An input / output port 215 is connected to the MPU 211 of the payout control device 111 via a bus line 214 configured by an address bus and a data bus. The main controller 110, the payout motor 216, the emission control device 112, and the like are connected to the input / output port 215, respectively. Further, although not shown, the payout control device 111 is connected with a prize ball detection switch for detecting a prize ball paid out. The prize ball detection switch is connected to the payout control device 111 but not connected to the main control device 110.

  The emission control device 112 controls the ball emission unit 112 a so that the ball launch strength according to the amount of rotational operation of the operation handle 51 is obtained when the main controller 110 instructs the ball emission. . The ball launch unit 112a includes a launch solenoid and an electromagnet (not shown), and the launch solenoid and the electromagnet are permitted to be driven when predetermined conditions are met. Specifically, the touch sensor 51a detects that the player is touching the operation handle 51, and the operation is performed on condition that the firing stop switch 51b for stopping the firing of the ball is turned off (not operated). The firing solenoid is excited corresponding to the amount of rotational operation (rotational position) of the handle 51, and the ball is emitted with a strength corresponding to the amount of operation of the operation handle 51.

  The sound lamp control device 113 outputs sound in a sound output device (such as a speaker (not shown)) 226, outputs of lighting and extinguishing in a lamp display device (such as the illumination parts 29 to 33 and the display lamp 34) It controls the setting of the display mode of the third symbol display device 81 and the like performed by the display control device 114 such as display (display) and advance notice effect. The MPU 221, which is an arithmetic device, has a ROM 222 storing a control program executed by the MPU 221, fixed value data, and the like, and a RAM 223 used as a work memory or the like.

  An input / output port 225 is connected to the MPU 221 of the audio lamp control device 113 via a bus line 224 configured by an address bus and a data bus. To the input / output port 225, a main control unit 110, a display control unit 114, an audio output unit 226, a lamp display unit 227, other units 228, a frame button 22 and the like are connected. Other devices 228 include drive motors 431, 466, 531, 561, 631, 661, 751.

  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 commands the determined display mode. The display control device 114 is notified by (display variation pattern command, display stop type command, etc.). In addition, the audio lamp control device 113 monitors the input from the frame button 22, and when the frame button 22 is operated by the player, changes the stage displayed by the third symbol display device 81, or super reach It instructs the display control device 114 to change the effect contents of the hour. When the stage is changed, a rear surface image change command including information on the changed stage is transmitted to display control device 114 in order to display the rear surface image according to the changed stage on third symbol display device 81. . Here, the rear surface image is an image displayed on the rear surface side of the third symbol, which is a 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 in accordance with the command transmitted from the voice lamp control device 113.

  In addition, the audio lamp control device 113 receives a command (display command) representing display content of the third symbol display device 81 from the display control device 114. Based on the display command received from the display control device 114, the sound lamp control device 113 outputs a sound corresponding to the display content from the sound output device 226 in accordance with the display content of the third symbol display device 81. The lighting and extinguishing of the lamp display device 227 are controlled according to the display content.

  The display control device 114 is connected to the voice lamp control device 113 and the third symbol display device 81, and based on the command received from the voice lamp control device 113, the third symbol display effect variation effect of the third symbol display device 81, etc. It controls the display. Further, the display control device 114 appropriately transmits a display command for notifying the display content of the third symbol display device 81 to the voice lamp control device 113. The voice lamp control device 113 matches the display of the third symbol display device 81 with the voice output from the voice output device 226 by outputting the voice from the voice output device 226 according to the display content indicated by the display command. be able to.

  The power supply unit 115 includes a power supply unit 251 for supplying power to each part of the pachinko machine 10, a power failure monitoring circuit 252 for monitoring power interruption due to a power failure, and a RAM provided with a RAM erase switch 122 (see FIG. 3). And an erase switch circuit 253. The power supply unit 251 is a device that supplies necessary operating voltages to the control devices 110 to 114 and the like through a power supply path (not shown). As a summary, the power supply unit 251 takes in a voltage of 24 volts AC supplied from the outside, 12 volts voltage for driving various switches such as various switches 208, solenoids such as solenoid 209, motor, etc. A voltage of 5 volts for logic, a backup voltage for RAM backup, and the like are generated, and these 12 volts, 5 volts and a backup voltage are supplied to the respective control devices 110 to 114 and the like.

  The power failure monitoring circuit 252 is a circuit for outputting the power failure signal SG1 to each NMI terminal of the MPU 201 of the main control device 110 and the MPU 211 of the payout control device 111 when the power is shut off due to the occurrence of a power failure or the like. The power failure monitoring circuit 252 monitors the voltage of the stable DC voltage of 24 volts, which is the maximum voltage output from the power supply unit 251, and determines that a power failure (power loss, power loss) occurs when this voltage becomes less than 22 volts. Then, the blackout signal SG1 is outputted to the main control unit 110 and the payout control unit 111. By the output of the power failure signal SG1, the main controller 110 and the payout control device 111 recognize the occurrence of the power failure, and execute the NMI interrupt process. The power supply unit 251 outputs a 5-volt voltage, which is a driving voltage of the control system, for a time sufficient for execution of the NMI interrupt processing even after the voltage of the DC stable 24 volts becomes less than 22 volts. Is configured to maintain a normal value. Therefore, the main controller 110 and the payout controller 111 can execute and complete the NMI interrupt process (not shown) normally.

  The RAM erase switch circuit 253 is a circuit for outputting a RAM erase signal SG2 for clearing the backup data to the main control unit 110 when the RAM erase switch 122 (see FIG. 3) is pressed. The main control unit 110 controls the payout initialization command for clearing the backup data and causing the payout control unit 111 to clear the backup data when the RAM erase signal SG2 is input when the pachinko machine 10 is powered on. Transmit to the device 111.

  Next, with reference to FIG. 5 to FIG. 12, the gaming board 13 and the operation unit 200 will be described. First, the accommodation structure of each unit 300 to 700 in the back case 210 will be described with reference to FIGS. 5 to 7.

  FIG. 5 is an exploded front perspective view of the game board 13 and the operating unit 200, and FIGS. 6 and 7 are exploded front perspective views of the operating unit 200 in a front view of the operating unit 200 disassembled. Note that FIG. 7 illustrates the combined operation unit 500 mounted on the back case 210.

  As shown in FIGS. 5 to 7, one side (the front side of the sheet of FIG. 6) of the operation unit 200 is opened from the bottom wall portion 211 and the outer wall portion 212 erected from the outer edge of the bottom wall portion 211. A rear case 210 formed in a box shape is provided. The rear case 210 is formed in a rectangular frame shape in a front view by forming a rectangular opening 211 a at the center of the bottom wall portion 211. The opening 211a is formed in a size corresponding to the outer shape of the third symbol display device 81 (see FIG. 2) (that is, the third symbol display device 81 can be disposed).

  In the operation unit 200, the vertical operation unit 400, the combined operation unit 500, the tilting operation unit 600, and the slide operation unit 700 are accommodated in the inner space of the rear case 210, and are configured as one unit.

  Specifically, combined operation unit 500 is disposed in the upper right portion of the region formed by the inner side surface of outer wall portion 212 of rear case 210 (see FIG. 7). With respect to the state shown in FIG. 7, tilting operation unit 600 and slide operation unit 700 are disposed below the area formed by the inner side surface of outer wall portion 212 of rear case 210. Further, with respect to the state shown in FIG. 7, the vertical movement unit 400 is disposed on the front side of the combined movement unit 500 in a stacked state in which the vertical movement unit 400 is stacked and accommodated in the rear case 210 (see FIG. 5).

  As described above, in the present embodiment, another operation unit (for example, the vertical operation unit 400) is disposed in a stacked state in which the predetermined operation unit (for example, the combined operation unit 500) is superimposed on the front side. Therefore, in front view, a given operation unit can be shielded by another operation unit.

  In other words, when the game board 13 (see FIG. 2) is formed of a light transmitting material, and the operation unit disposed on the back side of the game board 13 can be viewed by the player, the predetermined operation unit It is possible to make the player visually recognize only the necessary part of and to shield other parts from the player by other operation units. As a result, it is not necessary to design a predetermined effect member shielded by another operation unit on the premise that the whole is viewed by the player, so that the degree of freedom in the design can be improved. .

  Next, with reference to FIGS. 8 to 10, outlines of operation modes of the vertical movement unit 400, the combined movement unit 500, the tilting movement unit 600, and the slide movement unit 700 will be described. In the description of FIGS. 8 to 10, FIGS. 5 to 7 will be referred to as appropriate.

  8 to 10 are front views of the operation unit 200. FIG. In FIG. 8, the state in which the arm member 440 (see FIG. 18) of the vertical movement unit 400 is disposed at the extended position is the expansion state of the expansion / contraction effect device 540 (see FIG. 26) of the combined movement unit 500 in FIG. 9. The formed state is illustrated in FIG. 10 in which the tilting operation unit 600 is disposed substantially at the center in the width direction.

  As shown in FIG. 8, the vertical movement unit 400 operates the arm member 440 (see FIG. 18) between the retracted position shown in FIG. 5 and the extended position shown in FIG. In the retracted position shown in FIG. 5, the arm member 440 is retracted above the opening 211 a of the back case 210 and is invisible 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 at the center of the opening 211a of the back case 210 (ie, the front of the third symbol display device 81; Placed in).

  As shown in FIG. 9, in the combined operation unit 500, the pivoting arm member 550 (see FIG. 22) is disposed at the downward projecting position, and the front plate member 546 is at the center of the opening 211a of the rear case 210 (ie, 2), and the front plate member 546 is disposed at the opening 211a of the rear case 210, to the retracted position where the pivoting arm member 550 is retracted upward. It is possible to form a contracted state (see FIG. 5) which is retracted upward. In the contracted state shown in FIG. 5, the front plate member 546 is retracted above the opening 211a of the back case 210, and is invisible to the player (see FIG. 2).

  As shown in FIG. 10, in the tilting operation unit 600, the support member 720 (see FIG. 47) of the slide operation unit 700 is slid to the left and right, so that the retracted position shown in FIG. It is movable between positions. In the retracted position shown in FIG. 5, the tilting operation unit 600 is retracted to the right of the opening 211a of the back case 210, and viewed from 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 at the center of the opening 211a of the back case 210 (that is, in front of the third symbol display 81, see FIG. 2).

  In FIG. 10, the state in which the first curtain member 624 and the second curtain member 625 (see FIG. 46) are opened and the liquid crystal device in the inside is viewed is illustrated. That is, when the tilting operation unit 600 is arranged in the state of FIG. 10, the effect displayed on the third symbol display device 81 (see FIG. 2) visually recognized through the opening 211a and the liquid crystal device inside the tilting operation unit 600. The player can visually recognize both of the effects displayed on the screen.

  Each of the operation units 400 to 700 is formed to be independently operable and, as described above, disposed in a stacked (stacked) state, and therefore, among the operation units 400 to 700, With regard to those disposed in different layers, even if the operation member is a mode in which the operation member projects inward of the opening 211a of the back case 210, it can be operated at the same time. That is, as illustrated in FIG. 8 to FIG. 10, not only the respective operation units 400 to 700 can be operated alone, but also these operations can be combined, so that the rendering effect can be enhanced.

  FIG. 11 is a front view of the operation unit 200. FIG. In FIG. 11, the expansion / contraction effect device 540 (see FIG. 22) of the combined operation unit 500 is in the expanded state, and the arm member 440 and the lens member 460 of the up and down operation unit 400 are disposed at the extended position. Form an open state.

  As shown in FIG. 11, the front plate member 546 of the combined operation unit 500 is visually recognized through the lens member 460 of the vertical movement unit 400. Since the lens processing is formed on the lens member 460 as described later, the front plate member 546 is viewed in an enlarged manner.

  That is, from the state shown in FIG. 11, the rotary plate 520 (see FIG. 24) of the combined operation unit 500 is pivoted about the first shaft 512 (see FIG. 24), and the front plate member 546 is moved up and down. The front plate member 546 is visually recognized in a normal size when it is moved from the lens member 470 to a position (see FIG. 39) separated in a front view. As a result, it is possible to switch between the state in which the front plate member 546 is viewed in a normal size and the state in which the front plate member 546 is viewed in an enlarged manner (see FIG. 11), thereby improving the rendering effect.

  FIG. 12 is a front view of the operation unit 200. In FIG. 12, the expansion / contraction effect device 540 (see FIG. 22) of the combined operation unit 500 is in the extended state, and the tilting operation unit 600 is disposed at the retracted position and is in the tilting state. The state immediately before the point of contact is illustrated. By further tilting the tilting unit 600, the tilting unit 600 and the front plate member 546 are brought into contact with each other. In this case, by swinging the compound operation unit 500 clockwise in a front view (see FIG. 39), it is possible to produce an effect that makes it appear that the force is applied from the tilting operation unit 600 to the compound operation unit 500. (It is possible to associate the operations of the units and perform more complicated effects). Thereby, the rendering effect can be improved.

  Next, the lower board unit 300 will be described with reference to FIGS. 13 to 15. FIG. 13 is a front exploded perspective view of the board 13 and the lower board unit 300. As shown in FIG. 13, at the lower part of the game board 13, there is formed a receiving opening 13a which is opened along the lower edge of the inner rail 61 and into which the board lower unit 300 is inserted.

  FIG. 14 is a front exploded perspective view of the lower board unit 300. As shown in FIG. 14, the lower board unit 300 has a base member 310 internally fitted and fixed to the receiving opening 13 a of the game board 13 and a ball disposed at the lower left of the base member 310 in a front view. A lower left plate member 320 guiding to 314, a lower right plate member 330 disposed on the lower right of the base member 310 in a front view and guiding a ball to the second out port 315, and a left lower plate fastened and fixed to the base member 310 from the front The front lid member 340 mainly supported by the member 320 and the lower right plate member 330 by the insertion shaft 343.

  The base member 310 has a plate-like main portion 311 which has a shape substantially the same as the shape of the receiving opening 13a of the game board 13 and formed in a slightly smaller cross-sectional shape than the receiving opening 13a. It is formed on the left of front view of the decoration front plate part 312 formed in thin plate shape in the covering aspect, the movable effect member 313 attached to the width direction approximate center part of the decoration front plate part 312, and the movable effect member 313 And a second out port 315 which is a rectangular shaped hole formed on the right side in a front view of the movable effect member 313.

  The movable effect member 313 is provided at the lower edge in the width direction center of the game board 13 and includes a rotation effect member 313 a which is rotated by a drive device (not shown). Here, when the out port is disposed at the center lower edge of the game board 13 in the width direction, the movable effect member 313 can not be disposed at the center lower edge of the game board 13 in the width direction. In the present embodiment, the first out port 314 and the second out port 315 are disposed at positions separated leftward and rightward from the center of the game board 13 without arranging the out port at the lower center of the game board 13 in the width direction. Thus, it is possible to secure a space for disposing the movable effect member 313 at the lower edge in the width direction center of the game board 13.

  The shapes of the first out port 314, the second out port 315, the lower left plate member 320, and the lower right plate member 330 will be described with reference to FIG. Fig.15 (a) is a front view of the base member 310, the 1st out port 314, the 2nd out port 315, the lower left board member 320, and the lower right board member 330, FIG.15 (b) is FIG. And a lower left plate member 320 taken along line XVb-XVb of FIG. In FIG. 15A, the outer shape of the front lid member 340 fastened and fixed to the base member 310 and the nail formed above the first out port 314 and the second out port 315 are illustrated.

  The first out port 314 and the second out port 315 are openings through which balls are discharged from the game area. The formed length in the width direction of the second out port 315 is shortened as compared to the first out port 314. The reason will be described later. In addition, a guide rib 315 a extending in the front-rear direction is formed on the upper inner surface of the second out port 315. The guide rib 315a allows the ball flowing into the second out port 315 to be highly splashed, thereby suppressing the resistance applied to the ball when the ball collides with the upper bottom surface of the second out port 315. Further, the flow of the balls discharged from the second out port 315 can be adjusted in the front-rear direction, and the variation in the direction of the discharged balls can be suppressed.

  Also, the buffer rib 322 of the lower left plate member 320 described later is formed higher toward the center in the width direction of the game board 13 (see FIG. 13) (see FIG. 15A). Thus, even in the present embodiment in which the vertical width of the game area increases toward the center of the game board 13 in the width direction, the effect of suppressing the bounce of the ball falling on the lower left plate member 320 is not impaired. That is, since the falling height of the ball becomes higher as it is closer to the center in the width direction of the game board 13, there is a possibility that the impact when the falling ball collides with the lower left plate member 320 may increase. On the other hand, since the buffer rib 322 is formed higher toward the center in the width direction of the game board 13, the buffer rib 322 is bent closer to the center in the width direction of the game board 13 to cushion the impact of falling. The degree can be increased.

  Here, the relationship between the aspect ratio of the buffer ribs 322 and 332 and the landing frequency of the falling ball will be described. For example, if the falling height of the ball landing on the buffer ribs 322 and 332 is high, but the frequency of arrival of the ball to the position is extremely low, failure to discharge the other balls without intentionally suppressing the bouncing of the ball. It may not be. In this case, if the aspect ratio of the buffer ribs 322 and 332 is increased, the space of the game area is unnecessarily reduced. Therefore, it is preferable that the aspect ratio of the buffer ribs 322 and 332 be set not only by the drop height of the ball but also by the drop height and the frequency with which the ball lands at that position.

  As shown in FIG. 15, the balls flowing down above the buffer ribs 322 and 332 are started to flow down in the paths c1 and c2, and then reach the landing areas z0 to z4 through the plurality of branches b1 to b10. In the following description, when the probability that the sphere flows down is equal (1/2) in the paths c1 and c2 and the left and right branches in the branches b1 to b10 are equally left and right (1/2), respectively. Explain. It is assumed that the ball does not flow down from the upper right.

  The probability of the ball reaching the landing area z0 will be described. In order to reach the landing area z0, it is necessary to flow down the left side at the branch b5 to reach the path c11. The branch b5 may be reached from the path c1 via the branch b1 or from the path c2. Therefore, the probability that the ball reaches the path c11 and the ball reaches the landing area z0 is 1/8 (= 1/2 × (1/2) ^ 2), the probability of the ball flowing down from the path c1; Since it is represented by the sum of the probability 1⁄4 (= 1⁄2 × 1⁄2) of the spheres flowing down from the path c 2, it is 3⁄8 (“^” means a power). That is, each probability is the product of the probability 1⁄2 that the sphere flows down paths c 1 and c 2, and the number of powers 1⁄2 of the number of branches b 1 to b 10 that the sphere passes before reaching the landing area z 0 Is represented by

  The probability that the ball reaches the landing area z1 will be described. In order to reach the landing area z1, the left side is branched down at branch b3 to reach path c15, the left side is branched down at branch b4 to path c16, or the right side is branched off at branch b6 path c14 Or the right side at branch b7 to reach path c13.

  Up to the branch b3 is considered only when the sphere flows down from the path c1, and there are three branches before the sphere reaches the path c15, so the probability that the sphere reaches the path c15 is 1/16 (= It is 1/2 × (1 × 2) ^ 3). In addition, it is conceivable that only the case in which the ball flows down from the path c1 up to the branch b4 and there are four branches before the ball reaches the path c16, so the probability that the ball reaches the path c16 is 1/32 It is (= 1/2 x (1 x 2) ^ 4). In addition, until the branch b6, only the case where the sphere flows down from the path c1 is considered, and there are three branches before the sphere reaches the path c14, so the probability that the sphere reaches the path c14 is 1/16 (= 1/2 × (1 × 2) ^ 3).

  Up to the branch b7, both the case where the sphere is dropped from the path c1 and the path c2 are considered, and there are four branches before the sphere dropped from the path c1 reaches the path c13, and three branches. May exist. There are two branches before the ball flowing down from the path c2 reaches the path c13. Therefore, the probability that the sphere reaches the path c13 is the probability 3/32 (= 1/2 x (1/2) ^ 4 + 1/2 x (1/2) ^ 3) of the sphere flowing down from the path c 1; It is 7/32 because it is represented by the sum of the probability 1/8 (= 1/2 × (1/2) ^ 2) of the sphere flowing down from the path c2.

  Here, the probability that the sphere reaches the landing area z1 is 12/32 because it is the sum of the probabilities that the sphere reaches the above-described paths c13 to c16.

  The probability of the ball reaching the landing area z2 will be described. The probability that the sphere reaches the landing area z2 can be expressed by the probability that the sphere reaches the path c12, which is equal to the probability that the sphere reaching the branch b7 reaches the path c13. Therefore, the probability that the ball reaches the landing area z2 is 7/32.

  The probability of the ball reaching the landing area z3 will be described. In order to reach the landing area z3, it is necessary to flow down the left side at the branch b9 to reach the path c17 or to flow the left side at the branch b10 to reach the path c18.

  Until the branch b9, there is only a case in which the sphere flows down from the path c1, and there are six branches before the sphere reaches the path c17, so the probability of the sphere reaching the path c17 is 1/128 (= It is 1/2 × (1 × 2) ^ 6). In addition, it is only considered that the ball flows down from the path c1 until the branch b10, and there are seven branches before the ball reaches the path c18, so the probability that the ball reaches the path c18 is 1/256 (= 1/2 × (1 × 2) ^ 7).

  The probability of the sphere reaching the landing area z3 is 3/256 since it is the sum of the probabilities of the sphere reaching the paths c17 and c18 described above.

  The probability of the ball reaching the landing area z4 will be described. In order to reach the landing area z4, it is necessary to flow down the right side at the branch b10 to reach the path c19. In addition, all the balls which flowed down the right side of the branch b10 shall flow down on the path c19. The probability that the sphere reaches the path c19 is equal to the probability that the sphere reaching the branch b10 reaches the path c18. Therefore, the probability that the sphere reaches the landing area z4 is 1/256 (= 1/2 × (1 × 2) ^ 7).

  From these facts, the rate at which the sphere reaches each landing area z0 to z4 is (z0: z1: z2: z3: z4) = (96: 96: 56: 3: 1). This ratio is correlated with the buffer ribs 322 and 332.

  For example, when the landing area z1 and the landing area z3 are compared, the heights of the balls falling to the landing areas z1 and z3 are equal but the aspect ratio of the buffer ribs 322 and 332 is the landing area for the landing area z3. Less than z1. This is because the rate at which the sphere reaches the landing area z3 is 1/32 of the rate at which the sphere reaches the landing area z1. That is, even if the bounding of the falling ball is not suppressed as much as the landing area z1, in the landing area z3, there is little possibility that the discharge of the ball will be delayed. Therefore, in the landing area z3, the arrangement position of the second out port 315 can be lowered downward by reducing the aspect ratio of the buffer rib 332 compared to the landing area z1.

  For example, when the landing area z2 and the landing area z4 are compared, the aspect ratio of the buffer ribs 322 and 332 is the same as the ball falling distance to the landing area z4 is longer than the ball falling distance to the landing area z2. The landing area z2 is larger than the landing area z4. This is because the rate at which the sphere reaches the landing area z4 is 1/56 of the rate at which the sphere reaches the landing area z2. That is, even if the bounding of the falling ball is not suppressed as much as the landing area z2, in the landing area z4, there is little possibility that the discharge of the ball will be delayed. Therefore, in the landing area z4, the arrangement position of the second out port 315 can be lowered downward by reducing the aspect ratio of the buffer rib 332 compared to the landing area z2.

  In addition, although the case where the branch probability of the ball of the branches b1 to b10 is equal left and right (1/2) was described in the above description, the ball is branched at the branches b1 to b10 by changing the width of the nail. It is possible to adjust the branching probability. For example, by making the distance between the nails of the flow path through which the arrow on the left side of the branch b1 passes is as small as the diameter of the sphere, the probability that the ball flows down along the arrow on the right at the branch b1 is greater than 1/2 can do. Also in the other branches b2 to b10, the probability of the branch of the sphere can be similarly adjusted.

  As a result, the frequency at which the sphere reaches the paths c11 to c19 can be adjusted, and the design freedom of the aspect ratio of the buffer rib 322 can be improved.

  In addition, the buffer rib 322 is formed to be inclined downward as the upper surface goes to the rear (see FIG. 15B). Thereby, the ball flow to the first out port 314 can be made faster.

  Referring back to FIG. The lower left plate member 320 has a long plate-like main body portion 321 and a buffer rib 322 in which thin plates continuously provided in the left-right direction on the upper surface of the main body portion 321 extend in the front-rear direction and the buffer rib A connection front plate 323 formed in such a manner as to connect the front of 322, a step 324 formed by being raised upward at the left end in a front view of the main body 321, and extending leftward from the step 324 The ball flow rail portion 325 is mainly provided, and the axial support hole 326 drilled in the front-rear direction at the front end right end portion of the main body portion 321.

  The buffer rib 322 is a portion through which the ball directed to the first out port 314 passes, and suppresses the rebounding of the ball falling in the vertical direction in the vertical direction. That is, since the buffer rib 322 is formed of a thin plate continuously provided in the left and right direction, when impacted by a falling ball, bending in the thickness direction can alleviate the impact of the collision. In addition, when the ball moves in the left-right direction on the upper surface of the buffer rib 322, the ball is engaged between the buffer ribs 322 to brake the ball. In addition, the formation height and the aspect ratio of the buffer rib 322 are made larger as it goes inward in the width direction of the game board 13 (see FIG. 2) in the front view right side.

  The connection front plate 323 improves the strength of the buffer rib 322 by connecting the buffer rib 322.

  The stepped portion 324 is a raised portion for causing the ball flowed down from the ball flow rail portion 325 to fall in the vertical direction. Thereby, it is possible to suppress the load in the lateral direction from being applied to the buffer rib 322 from the ball flowing down the ball flow rail portion 325. Thereby, the buffer rib 322 can be prevented from being bent in the left-right direction by receiving a load in the left-right direction.

  That is, since the buffer rib 322 is formed of a thin wall portion extending in the front-rear direction, there is a possibility that the buffer rib 322 may be broken by the load in the left-right direction. On the other hand, in the present embodiment, a ball rolling on the upper surface of the ball flow rail 325 which has a velocity in the left-right direction and may load the load in the left-right direction to the buffer rib 322 It is formed in the form of falling in the direction. Thus, the position at which the ball lands on the buffer rib 322 can be shifted to the right in the width direction as the speed in the left-right direction of the ball is higher.

  Therefore, when the ball lands on the buffer rib 322, the load applied to the buffer rib 322 in the left-right direction can be made smaller toward the left in the width direction (outside). Therefore, the possibility of the occurrence of bending due to the load in the left-right direction of the ball decreases as the buffer rib 322 moves to the left in the width direction, and the aspect ratio of the buffer rib 322 can be formed smaller than that to the right in the width direction. . In this case, since 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, the buffer rib 322 is disposed as compared to the case where the buffer rib 322 has the same length in the width direction. The position can be lowered downward.

  Here, the lower surface of the game board 13 while keeping the aspect ratio of the buffer rib 322 constant at the left and right positions in the width direction (with the upper surface of the buffer rib 322 formed by the same curve as the lower surface of the buffer rib 322). It is also conceivable to form the lower surface of the buffer rib 322 along the curved surface formed on However, in this case, the disposition position of the step portion 324 becomes high, and the disposition position of the ball flow rail portion 325 formed to be inclined downward toward the step portion 324 also becomes high. In this case, the dead space between the ball flow rail portion 325 and the inner rail 61 (see FIG. 13) is increased, and the game area is suppressed.

  On the other hand, the larger the aspect ratio of the buffer rib 322, the larger the action of decelerating the ball (deceleration action). Therefore, the buffer rib 322 is formed in such a manner as to increase the aspect ratio from the vicinity of the step 324 toward the center of the game area.

  The upper surface of the buffer rib 322 is formed in the same curve as the curve of the lower surface of the buffer rib 322 to the front of the step 324 so as not to affect the formation height of the step 324 (in the middle of the buffer rib 322 in the left-right direction) It is also conceivable that the height is formed maximally). However, in this case, the ball reaching the landing area z1 is prevented from rolling to the left. Therefore, the balls are easily retained in the landing area z1, and it becomes difficult to discharge the balls smoothly.

  On the other hand, in the present embodiment, since the variation in the height of the upper surface of the buffer rib 322 in the width direction of the buffer rib 322 is small, the ball reaching the landing region z1 is easily turned to the left (the landing region z2 side) Move. Therefore, since the balls can be flowed to the landing area z2 before the balls stay in the landing area z1, the balls can be discharged smoothly.

  In addition, the step portion 324 has a function of stopping the ball flowing up and down to the left above the buffer rib 322. This can prevent the ball from bouncing back beyond the width of the first out port 314 after colliding with the front lid member 340 (see FIG. 13).

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

  The lower right plate member 330 has a long plate-like main body portion 331 and a buffer rib 332 in which thin wall portions continuously provided in the left-right direction on the upper surface of the main body portion 331 extend in the front-rear direction, A connection front plate 333 formed in such a manner as to connect the front surfaces of the buffer ribs 332, a recessed portion 324 formed by being depressed downward at the right end in the front view of the main body 331, and a right side in a front view from the recessed portion 324 It mainly includes a ball flow rail portion 335 extended to the end, and an axial support hole 336 drilled in the front-rear direction at the left end of the main body portion 331 in a front view.

  The configuration of the lower right plate member 330 and the configuration of the lower left plate member 320 are common in many parts. That is, the main body portion 331 is a main body portion 321, the buffer rib 332 is a buffer rib 322, the connection front plate 333 is a connection front plate 323, the ball flow rail portion 335 is a ball flow rail portion 325, and the axial support hole 336 is a shaft The technical idea is common to the support hole 326, so the description of the common part is omitted.

  The buffer rib 332 is formed to have a shorter formation width on the left and right as compared with the buffer rib 322. As a result, the left and right formation width of the second out port 315 can be shortened, and the arrangement position of the second out port 315 can be lowered downward compared to the first out port 314, so that the first variable The arrangement space of the large opening solenoid 65b of the winning device 65 can be secured (the arranging position of the first variable winning device 65 can be lowered).

  Here, the formation width of the buffer rib 332 can be made shorter than that of the buffer rib 322 because the flow path of the ball to the second out port 315 is restricted. That is, as shown in FIG. 14, the first variable winning device 65 is disposed on the upper right of the second out port 315 in front view, so that the ball flows into the first specified winning opening 65a when the opening and closing plate is opened. When the opening and closing plate is closed, the ball is dropped vertically downward on the front side of the first variable winning device 65. Thereby, it is possible to prevent the ball from flowing down to the second out port 315 from the upper right of the front view. In other words, in the upper right portion of the second out port 315, a non-falling area in which the flow of the ball is restricted is formed.

  Therefore, the flow-down direction of the ball to the lower right plate member 330 is limited only to the falling in the vertical direction and the flow-down from the width direction (from the ball flow rail portion 335) (flow from the diagonal upper right is restricted) . Therefore, since there is no inflow of the ball from the upper right side, the direction in which the ball bounces can be limited, and the width of the buffer rib 332 can be narrowed and the width of the second out port 315 can be narrowed. As a result, the installation space of the first variable winning device 65 can be secured.

  The recess portion 334 is a recess for causing the ball flowing down the ball flow rail portion 335 to bounce. Therefore, the formation width of the recessed portion 334 is a width that allows the ball to be placed without being in contact with the adjacent buffer rib 332.

  The ball which has flowed down the ball flow rail portion 335 is dropped into the recess portion 334, and when the ball abuts on the upper surface of the recess portion 334, the ball bounces and falls into the buffer rib 332. This prevents the load from being applied to the buffer rib 332 in the width direction, and can prevent the buffer rib 332 from being broken.

  The recessed portion 334 is formed in front of the fastening hole B through which a fastening screw for fastening and fixing the base member 310 to the game board 13 is inserted. As a result, when the fastening screw is screwed into the fastening hole B in order to fasten and fix the lower panel unit 300 to the game board 13, it is possible to make easy to use a fastening tool such as a driver. That is, the recessed portion 334 has both the effect of preventing the buffer rib 332 from being broken and the effect of facilitating the fastening and fixing of the base member 310.

  The front lid member 340 has a plate-like main portion 341 having the first winning opening 64 formed at the top, and an opening 342 formed at the center of the main portion 341 to allow the rotation effect member 313a to be visible. It mainly includes a pair of insertion shafts 343 that are inserted into the shaft support holes 326 and 336.

  The main body portion 341 is formed in contact with the lower edge of the game area, and the flow-down direction of the ball is limited by the side wall portion. That is, the ball that has collided with the main body 341 from the right can not penetrate to the left, while the ball that collides with the main body 341 from the left can not penetrate to the right.

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

  Next, the vertical movement unit 400 will be described with reference to FIGS. FIG. 16 is a front perspective view of the vertical movement unit 400, and FIG. 17 is a rear perspective view of the vertical movement unit 400. 16 and 17, the state in which the arm member 440 of the vertical movement unit 400 is disposed at the retracted position is illustrated.

  FIG. 18 is a front exploded perspective view of the vertical movement unit 400, and FIG. 19 is a rear exploded perspective view of the vertical movement unit 400. As shown in FIGS. 18 and 19, the vertical movement unit 400 is provided with a base member 410 including a vertical groove portion 414 which is recessed from the rear side to the front side on the right in a rear view and the recess extends in the vertical direction. The rotary crank member 420 is rotated about the connection hole 413 of the base member 410, the driving device 430 for generating the driving force of the rotary crank member 420, and the driving force is transmitted from the rotary crank member 420 to the base member 410. The arm member 440 is pivoted about the shaft portion 412 of the head, and is disposed on the opposite side of the upper and lower groove portions 414 of the base member 410. The sliding member 450 and the sliding hole 443 formed at the tip of the arm member 440 are suspended and interlocked with the swinging of the arm member 440 in the vertical direction A lens member 460 is slidably formed mainly includes a pair of door member 470 which is respectively pivotally supported on the lens member 460, a.

  The base member 410 has a main body 411 which is formed in a plate shape elongated in the left and right direction, and a cylindrical support member 442 of an arm member 440 which protrudes from the right end of the main body 411 toward the front side. It is formed from the back side to the front side in the rear view right side of the main body 411 from the support shaft portion 412 supported, the connection hole 413 in which the rotary crank member 420 and the transmission gear 432 are connected in a circular shape in the longitudinal direction. An upper and lower groove portion 414 is vertically extended, and a concave portion 415 recessed from the front to the back side on both left and right outer sides of the upper and lower groove portions 414 is mainly provided.

  The upper and lower groove portions 414 are portions in which the expansion / contraction rendering device 540 of the combined operation unit 500 is accommodated on the back side in the assembled state (see FIG. 2). In the combined operation unit 500, the swing angle of the expansion / contraction effect device 540 is suppressed as the expansion / contraction effect device 540 moves to the reduction state, as described later, so that the expansion / contraction effect device 540 is oscillated. Collisions to the left and right inner side surfaces are prevented. The recessed portion 415 is a portion to which the slide guide portion 452 of the slide member 450 is guided.

  The rotating crank member 420 has a plate-like main body portion 421, and a sliding projection 422 projecting in a cylindrical shape on the front side from one end of the main body portion 421 and inserted through the insertion portion 444 of the arm member 440. Mainly includes an engaging portion 423 engaged with the fitting portion 432a of the transmission gear 432 and disabling relative rotation between the transmission gear 432 and the rotating crank member 420.

  The sliding projection 422 is inserted into the insertion portion 444 of the arm member 440 and rotated, whereby the driving force of the drive device 430 is transmitted to the arm member 440, and the arm member 440 is swung about the shaft 412. .

  Drive device 430 includes a drive motor 431 fastened and fixed to base member 410, a drive gear 431a rotationally driven by drive motor 431, a transmission gear 432 meshed with drive gear 431a, and transmission gear 432 And a fitting portion 432a which is formed with an outer diameter slightly smaller than the inner diameter of the connection hole 413 and whose inner side surface is fitted to the engaging portion 423 of the rotating crank member 420.

  The fitting portion 432a is a portion provided with a recess having a cross-sectional shape in which a circular shape is disposed at each vertex of a triangle, and is inserted into the connection hole 413 of the base member 410 and at the tip end thereof The engagement portion 423 of the is fitted non-rotatably. Thus, the main body 411 of the base member 410 is formed to be sandwiched between the transmission gear 432 and the rotating crank member 420, and as described above, relative rotation between the transmitting gear 432 and the rotating crank member 420 is disabled. The transmission gear 432 and the rotating crank member 420 rotate in synchronization with each other. That is, the driving force of the driving motor 431 is transmitted to the rotating crank member 420 via the transmission gear 432.

  The arm member 440 includes a body portion 441 formed in a long rod shape, a shaft support hole 442 which is bored on the base end side (right side in front view) and pivotably supported by the shaft portion 412, and the base end side. The slide hole 443 is formed as an elongated hole on the swinging end side which is the opposite end of the slide member and the slide projection 463 of the lens member 460 is inserted, and the slide projection 422 of the rotating crank member 420 is inserted And an insertion portion 444 in the form of a bottomed hole.

  The shape of the insertion portion 444 is set such that the rotating crank member 420 can rotate once while the sliding projection 422 is inserted through the insertion portion 444. Therefore, the arm member 440 can perform the swing operation regardless of the rotation direction of the rotation crank member 420.

  The slide member 450 has a rectangular plate-like main body 451, a slide guide 452 extending rearward from the left and right ends of the main body 451, and guided in the recessed portion 415 so as to be vertically slidable, and the main body A central guide recessed portion 453 which is a recess extending in the vertical direction formed on the front at the center in the width direction of 451 and into which the sliding projection 463 of the lens member 460 is inserted, and the left and right ends of the main body 451 It mainly includes a both-end guide recessed portion 454 which is a recess formed on the front in the portion and extended in the vertical direction and to which the stable slide portion 464 of the lens member 460 is guided.

  The lens member 460 includes a plate-like main body 461 having a circular opening at its center, a magnifying lens 462 having an enlargement lens processing formed therein and fitted in the opening of the main body 461, and a widthwise center of the main body 461 A sliding projection 463 which is projected to the back side at the upper end and is inserted in the slide hole 443 of the arm member 440 so as to be slidable up and down, and a slide projected to the back side at both widthwise ends of the main body 461 The lower end shaft portion 473 and the upper side of the door member 470 are disposed rotatably in the upper and lower sides of the main body portion 461 in a stable slide portion 464 inserted in the upper and lower slide guide portions of the member 450 so as to be vertically slidable. A pair of rotating cylinders 465 through which the shaft portion 474 is inserted, and a drive motor 466 for rotating the pair of rotating cylinders 465 in opposite directions by a transmission mechanism (not shown) are mainly provided. That.

  The moving operation of the vertical movement unit 400 will be described with reference to FIG. FIG. 20 is a front view of the vertical movement unit 400. FIG. Note that FIG. 20 illustrates the closed state of the door member 470 when the arm member 440 of the vertical movement unit 400 is disposed at the extended position.

  When the arm member 440 is swung from the retracted position (see FIG. 16) to the overhanging position (see FIG. 20), the sliding of the lens member 460 supported by the sliding hole 443 on the swinging end side of the arm member 440 The movable projection 463 (see FIG. 18) is slid on the central guide recess 453 of the slide member 450. The lens member 460 is vertically guided by the both-end guide concave portion 454 of the slide member 450, and the slide member 450 is vertically guided by the concave portion 415 of the base member 410. The member 460 is slid in the vertical direction.

  Referring back to FIG. 18 and FIG. The door member 470 is configured by dividing a circular plate into upper and lower parts, and is formed on the lower side with a lower main body portion 471, an upper main body portion 472 formed above the lower main body portion 471, and a lower side. A lower shaft portion 473 projecting in a cylindrical shape on the back side at the lower end portion of the main body portion 471 and inserted into the rotary cylinder 465 of the lens member 460 so as not to relatively rotate, and a circle on the back side at the lower end portion It mainly includes an upper shaft portion 474 which is provided in a columnar shape and which is inserted into the rotary cylinder 465 of the lens member 460 so as not to be relatively rotatable.

  The lower main body 471 is provided with a guide projection 471 a protruding on the side facing the upper main body 472, and the upper main body 472 is on the side facing the lower main body 471. The receiving recess 472a is provided in the The relative positioning between the lower main body 471 and the upper main body 472 in the closed state can be performed by fitting the guide projection 471 a and the receiving recess 472 a. In the present embodiment, since the guide projection 471a is protruded in a tapered shape, the guide projection 471a can be reliably fitted in the receiving recess 472a.

  The operation of the door member 470 will be described with reference to FIG. FIG. 21 is a front view of the vertical movement unit 400. FIG. Note that FIG. 21 illustrates the open state of the door member 470 when the arm member 440 of the vertical movement unit 400 is disposed at the extended position.

  The lower shaft portion 473 and the upper shaft portion 474 (see FIG. 19) are rotated by the rotation of the rotary cylinder 465 (see FIG. 18) of the lens member 460. The pair of rotary cylinders 465 are rotated in opposite directions by the driving force of the drive motor 466 (see FIG. 19), so the door member 470 is changed from the closed state (see FIG. 20) to the open state (see FIG. 21). In this case, the lower main body portion 471 and the upper main body portion 472 can be rocked outward (opposite direction) from each other. In addition, 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 inwardly.

  Thereby, the time for swinging the lower main body portion 471 and the upper main body portion 472 can be reduced to half as compared with the case where the front side of the lens member 460 is swung to cover a single cover member.

  Next, the combined operation unit 500 will be described with reference to FIGS. 22 to 45. The compound operation unit 500 arranges the telescopic effect device 540 on the front side of the third symbol display device 81 by swinging the pivoting arm member 550 from the retracted position (see FIG. 22) to the extended position (see FIG. 9). It is a unit. In addition, the expansion and contraction rendering device 540 is formed so as to be swingable about the first shaft portion 512 (see FIG. 24) of the base member 510.

  FIG. 22 is a front perspective view of combined operation unit 500, and FIG. 23 is a back perspective view of combined operation unit 500. As shown in FIG. FIGS. 22 and 23 illustrate that the pivoting arm member 550 is disposed at the retracted position which is the end position formed on the outside of the third symbol display device 81 (see FIG. 2).

  FIG. 24 is a front exploded perspective view of combined operation unit 500, and FIG. 25 is a back exploded perspective view of combined operation unit 500.

  As shown in FIG. 24 and FIG. 25, the combined operation unit 500 is a unit that effects by sliding and swinging the expansion and contraction rendering device 540, and includes a base member 510 that forms a skeleton and the base member 510. And a first drive device 530 that is fastened and fixed to the base member 510 to generate a driving force of the rotary plate 520, and is fastened to the front of the rotary plate 520. One end of the expansion / contraction effect device 540 which is fixed and formed so as to be expandable and contractible in the radial direction of the rotary plate 520 and one end thereof is connected to the expansion / contraction effect device 540 and the other end on the opposite side is axially supported by the base member 510 And a pivoting arm member 550 that forms an expansion and contraction operation of the expansion and contraction rendering device 540 by a pivoting operation, and a driving force of the pivoting arm member 550 that is fastened and fixed to the base member 510. The second driving device 560 to be generated, the rotating crank member 570 for transmitting the driving force of the second driving device 560 to the rotating arm member 550, and the rotating arm member 550 and the rotation are fastened and fixed from the front of the base member 510. And a front cover 580 for blinding a mechanical portion on the rotary shaft side such as the crank member 570.

  The base member 510 includes a main body portion 511 having a rectangular plate shape, a cylindrical first shaft portion 512 protruding forward from a substantially lower center of the main body portion 511 in the width direction, and the first shaft portion 512. Three rows of circular arc-shaped holes 513 drilled along a central circular arc, and a first through hole 514 drilled adjacent to a second circular arc-shaped hole 513b of the three rows of circular arc-shaped holes 513 , And a cylindrical second shaft 515 protruding forward from the main body 511 at a substantially intermediate position between the shaft 512 and the right end of the main body 511, and adjacent to the second shaft 515. A second through hole 516 to be bored, a cylindrical third shaft 517 projecting forward from the lower right end of the main body 511 in front view, and a bending from the edge of the main body 511 to the front And a bent wall portion 518.

  The first shaft portion 512 is a portion that is inserted into the shaft support hole 522 of the rotary plate 520 and becomes the rotation shaft of the rotary 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 rotary plate 520.

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

  The first circular arc hole 513 a and the third circular arc hole 513 c are long holes through which the insertion shaft 525 of the rotary plate 520 is inserted and which guides the rotation of the rotary plate 520. Thereby, when the rotating plate 520 is rotated, the load received by the first shaft portion 512 can be reduced, and the durability of the rotating plate 520 can be improved. Although FIGS. 24 and 25 show a state in which the 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 different from the collar and the main body portion 521. Placed between (inserted before fastening the collar).

  The second arc-shaped hole 513 b is a long hole in which the arc-shaped rack 526 of the rotary plate 520 is disposed and moved. The upper side of the substantially central portion is opened, and the drive gear 532 of the first drive device 530 is disposed in the opened portion. Thus, the toothed portion of the drive motor 531 of the first drive device 530 and the arc-shaped rack 526 of the rotary plate 520 can be disposed in the plate thickness portion of the main body portion 511. The dimension in the longitudinal direction (the dimension in the front-rear direction in FIG. 22) can be suppressed.

  The first through hole 514 and the second through hole 516 are through holes into 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.

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

  The third shaft portion 517 is a portion that is inserted into the pivot support hole 552 of the pivoting arm member 550 and serves as a central axis of pivoting of the pivoting arm member 550. Therefore, the diameter of the third shaft portion 517 is formed to be slightly smaller than the inner diameter of the pivot hole 552 of the pivot arm member 550. A torsion spring 517a is wound around the third shaft 517 to generate a biasing force for moving the pivoting arm member 550 toward the retracted position.

  The torsion spring 517 a is formed in such a manner that arms are extended from both ends of the coil portion wound around the third shaft 517. One arm portion is fixed to the lower right portion (in the vicinity of the first stopper portion 518 a) of the bent wall portion 518 in a front view, and the other arm portion on the opposite side of the one arm portion The locking portion 555 is locked.

  The bent wall portion 518 includes a first stopper portion 518 a adjacent to the third shaft portion 517, a second stopper portion 518 b formed on the right side of the first shaft portion 512, and a left side of the first shaft portion 512. And a third stopper portion 518c formed on the main body.

  The first stopper portion 518 a is a portion that regulates the rotation of the rotation arm member 550. That is, when the pivoting arm member 550 is lowered to the extended position (see FIG. 9), it is brought into contact with the first stopper portion 518a, and the lowering is stopped.

  As shown in FIG. 24, the second stopper portion 518b is disposed below the third stopper portion 518c. The lower surface of the rotary plate 520 is formed symmetrically with respect to the shaft support hole 522 (see FIG. 37), so that the rotary plate 520 rotates at a larger rotation angle in the direction of rotation toward the second stopper portion 512b. Can. That is, in the expansion / contraction effect device 540 described later, the maximum angle of the clockwise swing in the front view is formed larger than the swing in the counterclockwise direction in the front view.

  The rotary plate 520 has a fan-shaped plate-like main body portion 521, a pivot hole 522 circularly formed in the thickness direction at the base portion of the main body portion 521, and a body slightly wider than the inner diameter of the pivot hole 522 A rail receiving groove 523 which is rectilinearly recessed on the front surface of the portion 521, a pair of expansion and contraction stoppers 524 which are formed to project forward on both sides of the lower end portion of the rail receiving groove 523 An arc-shaped rack having a plurality of (three in this embodiment) insertion shafts 525 projecting from the back surface of the main body 521 in an arc shape centering on the pivot hole 522 and having gear teeth engraved on the outer peripheral portion And 526.

  The first shaft portion 512 of the base member 510 is inserted through the shaft support hole 522. Therefore, the rotary plate 520 is swung about the first shaft portion 512.

  The rail receiving groove 523 is a portion to which the slide rail 545 of the expansion and contraction rendering device 540 is fastened and fixed, and the expansion and contraction rendering device 540 extends and contracts along the extending direction of the rail receiving groove 523. Therefore, the moving direction of the expansion and contraction rendering device 540 is changed by the posture of the rotary plate 520.

  The expansion / contraction stopper 524 is a portion that is vertically abutted against the inner side surface of the slide plate 544 of the expansion / contraction effect device 540, and regulates the movement width of the slide plate 544. It is formed on both sides of the rail receiving groove 523 and is abutted with the inner side surface of the slide plate 544 on both sides, thereby suppressing load on the slide rail 545 in a direction orthogonal to the expansion and contraction direction, and improving the durability Can be

  The insertion shaft 525 is a portion which is inserted into the first arc-shaped hole 513a and the third arc-shaped hole 513c of the base member 510 and guides the rotation of the rotary plate 520, and has a diameter of the first arc-shaped hole 513a and the third circle. It is formed slightly smaller than the width dimension of the arc-shaped hole 513c. In addition, since the collar member having a diameter larger than the width dimension of the first circular arc hole 513a and the third circular arc hole 513c is fastened and fixed to the tip end, the rotary plate 520 is non-extractably connected to the base member 510.

  The arcuate rack 526 is inserted into the second arcuate hole 513 b of the base member 510 and engaged 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 the area including the thickness portion of the base member 510, the dimension in the thickness direction of the combined operation unit 500 can be suppressed.

  The first drive device 530 mainly includes a drive motor 531 fastened and fixed to the base member 510, and a drive gear 532 inserted into the first through hole 514 of the base member 510 and axially rotated by the drive motor 531.

  Next, the expansion and contraction rendering device 540 will be described with reference to FIGS. 26 and 27. FIG. 26 is a front exploded perspective view of the expansion / contraction effect device 540, and FIG. 27 is a rear exploded perspective view of the expansion / contraction effect device 540.

  As shown in FIG. 26 and FIG. 27, the expansion / contraction effect device 540 has a main body member 541 forming a skeleton, and a pair of the main body member 541 is fastened and fixed to the back surface thereof. The first guide member 542 and the second guide member 543 through which the portion 551 is inserted, and the axially movable direction of the first guide member 542 and the insertion holes 542 d of the second guide member 543 are provided. The slide plate 544, the slide plate 544 and the rotary plate 520, and one end of the slide rail 545 which is internally fitted in the rail receiving groove 523 and fastened and fixed; Of the front plate member 546 to be fastened and fixed, the connecting sliding member 547 slidably supported on the shaft support portion 546c of the front plate member 546, and the connecting sliding member 547 Mainly includes a decorative member 548 front drooping portion 548b is formed to be movable in the front of the body member 541 is fixed.

  The main body member 541 includes a plate-like main body portion 541a forming a skeleton, a columnar protrusion 541b protruding toward the back side at the center in the width direction of the main body portion 541a, and a back surface of the protrusion 541b The first bulking fastening portion 541c, which is provided on the left side in a pair, the second bulking fastening portion 541d, which is provided on the right side in the back view of the protrusion 541b, and the top left portion of the body portion 541a in a rear view. Mainly provided are a guide fastening portion 541e which is provided in a protruding manner, and a fastening hole 541f which is formed on the front side of the main body portion 541a in a plurality (in the present embodiment, three places) and the front plate member 546 is fastened and fixed.

  The protrusion 541 b is a portion that is inserted into the arc-shaped hole 554 of the pivoting arm member 550. Therefore, the diameter of the protrusion 541 b 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 projection 541 b is inserted into the arc-shaped hole 554, when the pivoting arm member 550 is swung, the main body member 541 can be interlocked.

  The first raised fastening portion 541 c is a portion for fastening and fixing the first guide member 542, and the second raised fastening portion 541 d is a portion for fastening and fixing the second guide member 543. The distance by which the second bulky fastening portion 541 d is separated in the vertical direction is longer than the first bulky fastening portion 541 c because a position not interfering with the pivoting arm member 550 is selected and disposed. Here, in the present embodiment, the pivoting arm member does not pass below the front left side of the main body member 541 in its pivoting trajectory (see FIGS. 37, 40 and 44). Therefore, the arrangement interval of the pair of second raised fastening portions 541 d can be increased compared to the first raised fastening portions 541 c, and the rigidity of the second raised fastening portions 541 d can be improved.

  The guide fastening portion 541 e is a portion to which the auxiliary fastening portion 542 e of the first guide member 542 is fastened and fixed, and is a portion to which the upper surface of the pivoting arm member 550 is guided when the expansion / contraction effect device 540 is in an expanded state. That is, even if the projection 541 b is not guided by the arc-shaped hole 554 of the pivot arm member 550, the guide fastening portion 541 e guides the upper surface of the pivot arm member 550 to pivot the pivot arm member 550 upward. Thus, the pivoting arm member 550 and the telescopic effect member 540 are operated in conjunction with each other.

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

  The first guide member 542 is a fastening plate portion 542a fastened and fixed to the first raised fastening portion 541c, and a back surface restricting portion extending upward from a position where one step up on the back surface side of the fastening plate portion 542a 542b, a guide rail portion 542c protruding in a wall shape from the left and right sides of the back surface restricting portion 542b to the back surface, and a portion protruding to the back surface at the upper end portion of the back surface restricting portion 542b And an auxiliary fastening portion 542 e extending from the back surface regulating portion 542 b and fastened and fixed to the guide fastening portion 541 e.

  The back surface restricting portion 542 b is a portion disposed on the back surface of the pivoting arm member 550 and is a portion that prevents the pivoting arm member 550 from moving back and the projection 541 b from coming off from the arc-shaped hole 554. is there.

  The guide rail portion 542 c guides the movement of the rail receiving portion 544 d of the slide plate 544 when the expansion / contraction effect device 540 performs expansion and contraction operations, and suppresses the displacement of the posture of the slide plate 544 with respect to the first guide member 542.

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

  The second guide member 543 is a fastening plate portion 543a to be fastened and fixed to the second raised fastening portion 541d, and a back surface regulating portion extending upward from a position where the vehicle rides on the top surface of the fastening plate portion 543a. 543b, guide rails 543c protruding in a wall shape from the left and right sides of the back surface restricting portion 543b to the back surface, and a portion of the upper surface of the back surface restricting portion 543b protruding upward in the vertical direction And an insertion hole 543d.

  The back surface regulating portion 543 b is a portion disposed on the back surface of the pivoting arm member 550, and is a portion that prevents the pivoting arm member 550 from moving back to the rear and the projection 541 b falling off from the arc-shaped hole 554. is there.

  The guide rail portion 543 c guides the movement of the rail receiving portion 544 d of the slide plate 544 when the expansion / contraction effect device 540 performs the expansion / contraction operation, and suppresses the displacement of the attitude of the slide plate 544 with respect to the first guide member 543.

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

  The slide plate 544 has a main body portion 544a formed in a rectangular plate shape, a concave portion 544b in which a wide concave portion extending in the vertical direction is formed on the back surface of the main body portion 544a, and the concave portion 544b. Recesses 544c at both ends where recesses extending in the vertical direction are formed in the front of the left and right sides, and rail receivers projecting in a semicircular shape toward the front side at upper and lower end portions of the recesses 544c at both ends A section 544d, a cylindrical slide rod 544e extending in the vertical direction inside the concave sections 544c at both ends, and a production assisting wall 544f projecting toward the front substantially in the vertical center of the main body section 544a; A stopper portion 544g is provided mainly at the upper and lower ends of the recessed portion 544b so as to protrude toward the back surface at both left and right ends.

  The recessed portion 544 b is a portion for guiding the slide plate 544 to the expansion / contraction stopper 524 of the rotary plate 520. Therefore, the width of the inner side surface of the recessed portion 544b is formed to be slightly larger than the width dimension of the expansion / contraction stopper 524.

  The both end recessed portion 544c is a portion that accommodates a protrusion in which the insertion holes 542d and 543d of the guide members 542 and 543 are formed. Thereby, the projection part by which penetration hole 542d, 543d of guide member 542, 543 is drilled can be guided from the outside.

  The rail receiving portion 544 d is a portion accommodated in the guide rail portions 542 c and 543 c of the guide members 542 and 543. Thereby, it is possible to suppress the wobbling of the guide members 542, 543 with respect to the slide plate 544.

  The slide rod 544 e is a cylindrical rod inserted through the insertion holes 542 d and 543 d of the guide members 542 and 543. Thereby, the guide members 542 and 543 are formed so as to be slidable in the extending direction (vertical direction in FIG. 26) of the slide bar 544e.

  The effect assisting portion 544f is a portion that is in contact with the rear hanging portion 548c of the decoration member 548 when the expansion / contraction effect device 540 is in an extended state, and moves the decoration member 548. Thereby, the external appearance of the expansion-contraction rendering device 540 can be changed.

  The stopper portion 544 g is a portion that is in contact with the expansion / contraction stopper 524 of the rotary plate 520 and that defines the vertically moving end of the slide plate 544.

  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 rotary 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.

  The front plate member 546 is an effect portion visually recognized by the player, and is a plate-like main body portion 546a formed in substantially the same shape as the main body member 541 in a front view, and is directed from the main body portion 546a to the back side. It mainly includes a fastening portion 546b protruding in accordance with the formation position of the fastening hole 541f, and a pair of pivoting portions 546c projecting from the upper end portion of the main body portion 546a toward the back side.

  The fastening portion 546b is a portion for fixing the front plate member 546 to the main body member 541, and the fastening portion 546b is fastened and fixed by screwing it through the fastening hole 541f.

  The shaft support portion 546c slidably supports the connection sliding member 547. Therefore, the diameter of the bearing portion 546c is formed slightly smaller than the width of the inner peripheral surface of the sliding long hole 547b of the connecting sliding member 547.

  The connection sliding member 547 is formed in a plate-like body portion 547a, a pair of sliding long holes 547b formed in an elongated hole shape extending vertically and drilled in the longitudinal direction, and a vertical direction A pair of insertion holes 547c are mainly provided.

  The sliding long hole 547 b is a portion through which the pivotal support portion 546 c of the front plate member 546 is inserted. Therefore, the width of the inner peripheral surface of the sliding long hole 547b is formed slightly larger than the shaft support portion 546c. The coupling sliding member 547 is pivotally supported by the front plate member 546 so as not to be pulled out by fastening and fixing a collar member having an outer shape larger than the width of the inner peripheral surface of the sliding long hole 547b to the front end of the shaft support portion 546c. Ru. The insertion hole 547 c is a circular hole through which a fastening screw for fastening and fixing the decorative member 548 is inserted.

  The decorative member 548 is formed in a plate shape, and a main body portion 548a to which the connection sliding member 547 is fastened and fixed from the lower side, a front hanging portion 548b formed to descend downward on the front side of the main body portion 548a, and a main body portion 548a And a rear hanging portion 548c which is formed to hang downward on the rear side of the main body.

  When the connection sliding member 547 moves relative to the front plate member 546, the front drooping portion 548b covers the front plate member 546 (see FIG. 43) and the front plate member 546 is separated and viewed (see FIG. 43). 37) can be formed. Thereby, the appearance of the expansion / contraction effect member 540 can be changed, and the effect of the effect can be improved.

  The back dripping portion 548c is a portion that is in contact with the rendering assistance wall 544f of the slide plate 544 by the expansion and contraction operation of the telescopic rendering device 540, and the decorative member 548 is made by the back flapping portion 548c being in contact with the rendering assist wall 544f. Is moved relative to the front plate member 546.

  Referring back to FIG. 24 and FIG. The pivoting arm member 550 has a body portion 551 formed in a long rod shape, a pivot hole 552 drilled in the front-rear direction at one end of the body portion 551, and a pivot hole 552 Formed on the back side of the main body 551 and on the front side of the other end which is the opposite end of the one end and the other end of the one end. An arc-shaped hole 554, which is an arc-shaped bottomed long hole, is protruded toward the back side in the vicinity of the shaft support hole 552 of the main body 551 and its tip is bent like a hook and the other arm of the torsion spring 517a is locked Mainly comprises a locking portion 555.

  The bearing hole 552 is a circular hole through which the third shaft 517 of the base member 510 is inserted. Therefore, the inner diameter of the shaft support hole 552 is formed to be slightly larger than the diameter of the third shaft portion 517, whereby the pivoting arm member 550 is formed so as to be pivotable about the third shaft portion 517.

  The deformed long hole 553 is a portion through which the sliding projection 574 of the rotating crank member 570 is inserted. The shape of the deformed long hole 553 will be described later.

  The arc-shaped hole 554 is a long hole through which the protrusion 541 b of the expansion and contraction rendering device 540 is inserted. Therefore, the width dimension of the arc-shaped hole 554 is formed to be slightly larger than the diameter of the protrusion 541 b. Further, the arc formed by the arc-shaped hole 554 coincides with the arc formed by the projection 541 b when the expansion / contraction effect device 540 is swung about the first shaft 512 in the expanded state (FIGS. 37 to 39). Up to see).

  In addition, the circular arc-shaped hole 554 is open at the tip of the other end of the rotary arm member 550, and includes a proboscis 554a whose width widens at the tip.

  The second drive device 560 is a device that generates a driving force for rotating the rotating crank member 570, and is inserted into the drive motor 561 fastened and fixed to the base member 510 and the second through hole 516 of the base member 510. And a drive gear 562 that is axially rotated by the drive motor 561.

  The drive gear 562 is engaged with the transmission gear teeth 572 of the rotating crank member 570. Accordingly, when the drive gear 562 is rotated, the rotating crank member 570 is rotated accordingly.

  The pivoting crank member 570 is a member for transmitting the driving force to the pivoting arm member 550, and is engraved on the ring-shaped main body portion 571 axially supported by the second shaft portion 515 and the outer peripheral surface of the main body portion 571. The transmission gear teeth 572 provided, the control umbrella portion 573 formed in such a manner as to cover the front side of the transmission gear teeth 572, and the slide protruding on the front side at a position eccentric to the center of the main body 571 A protrusion 574 and a lid 575 which is formed to have a diameter larger than the inner circumferential diameter of the main body 571 and which is fastened and fixed to the front side of the second shaft 515 are mainly included.

  The transmission gear teeth 572 mesh with the drive gear 562 of the second drive device 560. Thus, the driving force of the drive motor 561 is transmitted to the rotating crank member 570.

  The control umbrella portion 573 suppresses the positional shift of the drive gear 532 to the front side of the transmission gear teeth 572. Thereby, the meshing relationship between the drive gear 532 and the transmission gear teeth 572 can be made appropriate.

  The sliding projection 574 is a portion that is inserted into the deformed elongated hole 553 of the pivoting arm member 550. That is, based on the relationship between the sliding protrusion 574 and the shape of the pivoting arm member 550, it is determined whether or not the transmission of the driving force is formed.

  The lid 575 is a portion for disposing the main body 571 on the base member 510 in a non-extractable manner.

  The relationship between the swinging of the pivoting arm member 550 and the rotation of the pivoting crank member 570 will be described with reference to FIGS. 28 to 31. First, the shape of the modified long hole 553 of the pivoting arm member 550 will be described with reference to FIGS. 28 (a) and 29 (a).

  28 (a) and 29 (a) are front views of the pivoting arm member 550 and the pivoting crank member 570. FIG. In FIG. 28A, a state in which the pivoting arm member 550 is disposed at the retracted position is illustrated, and in FIG. 29A, a state in which the pivoting arm member 550 is disposed at the projecting position is illustrated. In FIGS. 28 (a) and 29 (a), the deformed long hole 553 and the sliding projection 574 are shown as hidden lines and the front plate member 546 and the projection 541b of the telescopic effect device 540 are shown as imaginary lines. Be done.

  As shown in FIG. 28A, in the state where the pivoting arm member 550 is disposed at the retracted position, a straight line connecting the rotary shaft of the pivoting crank member 570 and the sliding projection 574 and the pivoting crank member 570 An upward orthogonal state is formed in which the straight line connecting the rotation axis and the shaft support hole 552 is orthogonal.

  As shown in FIG. 29A, in a state where the pivoting arm member 550 is disposed at the extended position, a straight line connecting the rotation shaft of the pivoting crank member 570 and the sliding projection 574 and the pivoting crank member 570 It is possible to form a downward orthogonal state in which the axis of rotation of and the straight line connecting the shaft support hole 552 are orthogonal. In FIG. 29A, a state in which the rotating crank member 570 is rotated by a predetermined angle in a counterclockwise direction in a front view from the above-described downward orthogonal state is illustrated.

  The deformed long hole 553 is a transmission groove portion 553a in which the driving force is transmitted to the pivot arm member 550 by the movement of the sliding projection 574, and a first non-transmission wall portion connected from the upper end portion of the transmission groove portion 553a. 553b and a second non-transmission wall 553c connected from the lower end of the transmission groove 553a, and a selection wall 553d connecting the first non-transmission wall 553b and the second non-transmission wall 553c Prepare.

  As shown in FIG. 28A, the transmission groove portion 553a is a recessed groove linearly extended leftward from the sliding projection portion 574 of the rotating crank member 570 in the upward orthogonal state. Transmission groove portion 553a is formed with a length such that sliding projection 574 of rotating crank member 570 can move from the upward orthogonal state to the downward orthogonal state, and the formation width of the inner circumferential surface thereof is slightly smaller than the diameter of sliding projection 574 It is formed large. Therefore, while the sliding projection 574 moves in the transmission groove portion 553a, the driving force is transmitted from the rotating crank member 570 to the rotating arm member 550.

  As shown in FIG. 28A, the first non-transmission wall portion 553b slides from the upper wall surface of the right end portion of the transmission groove portion 553a around the rotation axis of the rotating crank member 570 in the upward orthogonal state. The wall portion is formed along the circumscribed circle of the portion 574. That is, when the rotating crank member 570 is rotated clockwise in a front view from the upward orthogonal state, the rotating crank member 570 idles relative to the rotating arm member 550, and the driving force from the rotating crank member 570 is the rotating arm It is not transmitted to the member 550.

  When the pivoting arm member 550 is rotated counterclockwise in a front view from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 28A), the movement of the first non-transmission wall portion 553b The direction is directed to the rotational axis of the pivoting crank member 570. Therefore, when the sliding projection 574 is disposed to face the first non-transmission wall 553b, the load applied to the sliding projection 574 by the rotation of the pivoting arm member 550 is the rotation of the pivoting crank member 570. It is directed to the axis. Therefore, when the sliding projection 574 is disposed to face the first non-transmission wall 553b, the rotation of the pivoting arm member 550 is prevented.

  The second non-transmission wall portion 553c is, as shown in FIG. 29A, a rotation crank from the lower side wall surface of the right end portion of the transmission groove portion 553a in a state where the rotation arm member 550 is disposed at the overhang position. The wall portion is formed along the circumscribed circle of the sliding projection 574 centered on the rotation axis of the member 570. That is, when the rotating crank member 570 is rotated counterclockwise from the front view from the orthogonal state (a state where the rotating crank member 570 is rotated clockwise by a predetermined amount from the state in FIG. 29A). The pivoting crank member 570 idles relative to the pivoting arm member 550, and the driving force is not transmitted from the pivoting crank member 570 to the pivoting arm member 550.

  When the pivoting arm member 550 is rotated clockwise in a front view from the state illustrated in FIG. 29A, the moving direction of the second non-transmission wall portion 553b is directed to the rotation shaft of the pivoting crank member 570. Be Therefore, when the sliding projection 574 is disposed to face the second non-transmission wall 553c (see FIG. 29B), the load applied to the sliding projection 574 by the rotation of the pivot arm member 550. Are directed to the rotational axis of the pivoting crank member 570. Therefore, when the sliding projection 574 is disposed to face the second non-transmission wall 553c, the rotation of the pivoting arm member 550 is prevented.

  The selection wall portion 553d is a wall portion formed of a smooth curved surface connecting the front end right end portion of the first non-transmission wall portion 553b and the front end portion of the second non-transmission wall portion 553c. The transfer wall portion 553b is formed on the upper side of the extended curve.

  The selection wall portion 553d is disposed to face the right side portion of the second non-transmission wall portion 553c, and is formed in such a manner that the distance to the second non-transmission wall portion 553c is increased toward the left end of the selection wall portion 553d. Therefore, for example, when rotating the rotating crank member 570 clockwise in a front view from the upward orthogonal state (see FIG. 28A), the sliding projection 574 passes the first non-transmission wall 553b and the second non-transmission In the margin D (see FIG. 32B) until the wall 553c is reached, no driving force is transmitted to the pivoting arm member 550, and no restriction of rotation occurs. That is, the driving force is not transmitted from the pivoting crank member 570 to the pivoting arm member 550, and the restriction of the rotation of the pivoting arm member 550 by the sliding projection 574 does not occur.

  The right end portion of the second non-transmission wall portion 553c is formed along an arc S1 centered on the pivotal support hole 552 (the formation angle with the arc S1 is small), while the right end portion of the selection wall portion 553d is The second non-transmission wall portion 553c is formed to intersect the arc S2 centered on the pivot support hole 552 at an angle larger than the formation angle between the right end portion of the second non-transmission wall portion 553c and the arc S1.

  In this case, when the distance between the sliding projection 574 and the shaft support hole 552 changes, the amount of swing of the pivoting arm member 550, which is necessary to cope with the amount of change, changes. That is, when the distance between the sliding projection 574 and the shaft support hole 552 changes by a predetermined amount in a state where the sliding projection 574 and the right end of the selection wall 553d abut on each other, the swing amount of the pivot arm member 550 is The amount is smaller than the amount of swinging of the pivoting arm member 550 when the sliding protrusion 574 and the right end of the second non-transmission wall 553c abut each other in a predetermined amount. Therefore, whether the sliding projection 574 rotates along the second non-transmission wall 553c or along the selection wall 553d, the pivoting arm member 550 swings with respect to the speed of the pivoting crank member 570. You can change the speed.

  Referring back to FIG. 28 to FIG. FIGS. 28 to 31 are front views of the pivoting arm member 550 and the pivoting crank member 570 in which the pivoting of the pivoting arm member 550 and the rotation of the pivoting crank member 570 are illustrated in time series. In FIG. 28A, the upward orthogonal state described above is formed (the pivoting arm member 550 is disposed at the retracted position), and in FIG. 28 to FIG. 31, the pivoting crank member 570 is counterclockwise in front view. The rotated state is sequentially illustrated, and the deformed elongated hole 553 and a part of the rotating crank member 570 are illustrated by a hidden line, and the front plate member 546 and the projection 541 b of the expansion and contraction rendering device 540 are illustrated by an imaginary line. .

  In FIGS. 28 to 31, the expansion / contraction effect device 540 is detected by the position detection sensor (not shown) in the posture to expand and contract in the vertical direction, and the swing is stopped in that posture. That is, in FIGS. 28 to 31, the protrusion 541 b moves only in the vertical direction. In this case, the rocking of the expansion and contraction rendering device 540 is prevented by the resistance between the first drive device 530 (see FIG. 25) and the drive gear 532.

  In the state of FIG. 28A, the rotating crank member 570 is in the upward orthogonal state. In this case, the reference horizontal line O is set at a position lowered vertically from the projection 541 b by the distance h1. That is, when the rotating crank member 570 is in the upward orthogonal state, the projection 541 b is disposed at a position vertically separated from the reference horizontal line O by the distance h1.

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 28 (a) (rotated counterclockwise by an angle T1 from the upward orthogonal state (see FIG. 28 (a))), A state in which the sliding projection 574 is moved in the transmission groove 553a of the deformed elongated hole 553 and the projection 541 is spaced vertically upward from the reference horizontal line O by a distance h2 (h2 <h1) (FIG. 28 (b )) To reach. During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ). That is, the pivoting arm member 550 is swung.

  From the state of FIG. 28 (b), the rotating crank member 570 is rotated counterclockwise as viewed from the front (refer to FIG. 28 (a)), and the angle T2 (T2 ≒ 180 degrees> T1) counterclockwise. And the sliding projection 574 is moved (transmission area) in the transmission groove 553a of the deformed elongated hole 553 and enters the area facing the second non-transmission wall 553c, and the projection 541 is the reference. It reaches the state of the state (see FIG. 29A) arranged at a position separated by a distance h3 (h3 <h2) vertically upward from the horizontal line O. That is, the pivoting arm member 550 is swung.

  From the state shown in FIG. 28C, the rotating crank member 570 is rotated counterclockwise by an angle T3 (T3> T2) counterclockwise from the counterclockwise rotation in the front view (see FIG. 28A). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state shown in FIG. 29 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  When the pivoting arm member 550 is to be rotated clockwise in a front view from the state of FIGS. 29A and 29B, the sliding projection 574 is directed to the rotation shaft of the pivoting crank member 570 in a second direction. It is pushed by the non-transmission wall portion 553c. In this case, the movement of the sliding projection 574 is restricted, whereby the swinging of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from clockwise rotation in a front view from the state of FIGS. 29 (a) and 29 (b).

  Here, as a method of stopping the rotation of the rotation arm member 550 in the state of FIG. 29A, it is conceivable to stop the rotation crank member 570. However, if the rotating crank member 570 is rapidly stopped until the rendering speed of the rotating arm member 550 is reached just before reaching the extended position, the second drive device 560 is loaded, and the speed of the rotating crank member 570 is reduced. If it makes it loose, it will be impossible to improve the rendering effect.

  On the other hand, in the present embodiment, as shown in FIGS. 28 and 29, the pivoting arm is not rotated in the state of FIG. 29 (a) but is rotated to the state of FIG. 29 (b). The rotation of the member 550 can be stopped in the state of FIG. 29A (the projection 541 can be stopped at a position separated vertically upward from the reference horizontal line O by the distance h3). Thereby, the speed of the rotating crank member 570 is maintained until the rotating arm member 550 reaches the extended position, and thereafter, the rotating crank member from the state of FIG. 29 (a) to the state of FIG. 29 (b) The 570 can be slowed down. Therefore, there is no need to stop the rotating crank member 570 rapidly. Therefore, coexistence with the improvement of the rendering effect of the rotation arm member 550 and the improvement of the durability of the 2nd drive device 560 can be aimed at.

  From the state of FIG. 29 (b), the rotating crank member 570 is rotated counterclockwise in a front view (refer to FIG. 28 (a)), and then an angle T4 (T44270 degrees> T3). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed long hole 553 to reach the state of FIG. 30 (a). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  That is, while the turning crank member 570 is rotated by 1⁄4 turn counterclockwise from the state shown in FIG. 29A, the turning arm member 550 is maintained in the same posture, and the projections 541b are in the same position. Maintained. In the present embodiment, the length at which the pivoting arm member 550 is maintained in the same position and the projection 541b is maintained in the same position is set while the pivoting crank member 570 is rotated by 1⁄4 turn in this embodiment, There is no need to be limited to that. The length by which the front plate member 546 is kept in the lower position can be changed by changing the length of the second non-transmission wall portion 553c (see FIG. 28A) of the deformed elongated hole 553. For example, by making the second non-transmission wall portion 553c longer than the present embodiment, the length by which the front plate member 546 is continuously disposed at the lower position can be made longer than the present embodiment.

  From the state of FIG. 30 (a), the rotating crank member 570 is rotated counterclockwise by an angle T5 (T5> T4) counterclockwise from the counterclockwise rotation in the front view (see FIG. 28 (a)). State, the sliding projection 574 pushes up the selected wall 553d of the deformed elongated hole 553 and the projection 541 is disposed at a position vertically separated from the reference horizontal line O by a distance h2 (h2> h3) (See FIG. 30 (b)). During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ).

  That is, when the pivoting arm member 550 and the pivoting crank member 570 are rotated counterclockwise in a front view, the selective wall portion 553d and the sliding projection 574 are in contact with each other, whereby the pivoting arm member The driving force is transmitted to 550 (transmission area).

  From the state of FIG. 30 (b), the rotating crank member 570 is rotated counterclockwise by an angle T6 (T6> T5) counterclockwise from a front view counterclockwise (see FIG. 28 (a)). And the sliding projection 574 enters the area facing the first non-transmission wall 553b of the deformed elongated hole 553 and the projection 541 vertically upward from the reference horizontal line O by the distance h1 (h1> h2). A state of being placed at a spaced position (see FIG. 31) is reached. During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ).

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 31, the sliding projection 574 is moved in the region facing the first non-transmission wall 553b of the deformed elongated hole 553, as shown in FIG. The state of 28 (a) is reached. During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm No driving force is transmitted to the member 550 (non-transmission area).

  When the pivoting arm member 550 is rotated counterclockwise in the front view from the state of FIG. 31, the sliding projection 574 is pushed by the second non-transmission wall portion 553c toward the rotation shaft of the pivoting crank member 570. . In this case, the movement of the sliding projection 574 is restricted, whereby the swinging of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from rotating counterclockwise in a front view from the state of FIG.

  Here, as a method of stopping the rotation of the rotation arm member 550 in the state of FIG. 31, it is conceivable to stop the rotation crank member 570. However, when the rotating crank member 570 is rapidly stopped until the rendering speed of the rotating arm member 550 reaches the retracted position immediately before reaching the retraction position, a load is applied to the second drive device 560 and the speed decrease of the rotating crank member 570 is moderated. If this is the case, it will not be possible to improve the rendering effect.

  On the other hand, in the present embodiment, the rotation of the rotation arm member 550 is stopped in the state of FIG. 31 by rotating the rotation crank member 570 to the state of FIG. 28 (a) without stopping in the state of FIG. Can. Thereby, the speed of the rotating crank member 570 is maintained until the rotating arm member 550 reaches the extended position, and thereafter, the rotating crank member 570 is decelerated from the state of FIG. 31 to the state of FIG. It can be done. Therefore, there is no need to stop the rotating crank member 570 rapidly. Therefore, coexistence with the improvement of the rendering effect of the expansion-contraction rendering device 540 interlocked with the rotation arm member 550 and the improvement of the durability of the second drive device 560 can be achieved.

  As shown in FIGS. 28 to 31, rotating the rotating crank member 570 once in the same direction enables the rotating arm member 550 to swing back and forth between the retracted position and the extended position.

  From these things, when rotating the rotation crank member 570 at a constant speed counterclockwise as shown in FIGS. 28 to 31, the projection 541b is a reference horizontal line in a half period of the rotation cycle of the rotation crank member 570. It is moved downward from a position separated by a distance h1 vertically upward from O to a position separated by a distance h3 (h3 <h1). The protrusion 541b is maintained at a position separated by a distance h3 vertically upward from the reference horizontal line O in a period of 1⁄4 of the subsequent rotation period, and in the period of 1⁄4 of the subsequent rotation period, the protrusion 541b is a reference horizontal line O From the position vertically separated by a distance h3 from above, the pressure is raised and moved to a position separated by a distance h1 (h1> h3). Thereby, even when the rotating crank member 570 is moved at a constant speed, the moving speed of the projection 541 b (moving speed of the expansion / contraction effect device 540 in the expansion / contraction direction) can be doubled.

  Here, at the retracted position of the pivoting arm member 550, the pivoting arm member 550 and the pivoting crank member 570 can form an upward orthogonal state (see FIG. 28A), and the overhang of the pivoting arm member 550 In the position, the pivoting arm member 550 and the pivoting crank member 570 can form a downward and orthogonal state (see FIG. 29A). It is possible to form a downward orthogonal state by rotating the rotating crank member 570 a predetermined amount clockwise in a front view from the state of FIG. 29 (a).

  Therefore, in the present embodiment, in order to swing the pivoting arm member 550 from the retracted position to the extended position, the pivoting crank member 570 is rotated by a half turn (180 degrees). Therefore, when the rotating crank member 570 is rotated at a constant speed, the time required for the rotating arm member 550 to swing from the retracted position to the extended position (from FIG. 28 (a) to FIG. 29 (a) 29) and the time required to swing from the extended position to the retracted position (see FIG. 29A through FIG. 31A to FIG. 28A) can be equal.

  The relationship between the swinging of the pivoting arm member 550 and the rotation of the pivoting crank member 570 will be described with reference to FIGS. 32 to 35 are front views of the pivoting arm member 550 and the pivoting crank member 570, which illustrate the pivoting of the pivoting arm member 550 and the rotation of the pivoting crank member 570 in time series. In FIGS. 32 to 35, a state in which the rotating crank member 570 is rotated clockwise in a front view is illustrated, and the deformed elongated hole 553 and a part of the rotating crank member 570 are illustrated as a hidden line. The front plate member 546 and the protrusion 541 b of the effect device 540 are illustrated by imaginary lines.

  In FIG. 32A, the above-described upward orthogonal state is formed (the pivoting arm member 550 is disposed at the retracted position), and from FIG. 32B to FIG. 35, the pivoting arm is from FIG. The state in which the member 550 and the rotation crank member 570 are rotated by a predetermined amount is sequentially illustrated in time series.

  In the state of FIG. 32A, the rotating crank member 570 is in the upward orthogonal state. In this case, the protrusion 541 b is disposed at a position vertically separated from the reference horizontal line O by a distance h1.

  From the state of FIG. 32 (a), the pivoting crank member 570 is rotated clockwise as viewed from the front (rotated clockwise by an angle T11 from the orthogonal upward state (see FIG. 32 (a))). The projection 574 is moved in the area facing the first non-transmission wall 553b of the deformed elongated hole 553 to reach the state of FIG. 32 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h1.

  When the pivoting arm member 550 is rotated counterclockwise in the front view from the state of FIG. 32 (b), the sliding projection 574 is restricted in movement, so that the pivoting of the pivoting arm member 550 is restricted. Ru. Therefore, the pivoting arm member 550 is prevented from rotating counterclockwise in a front view from the state of FIG. 32 (b).

  From the state of FIG. 32 (b), the pivoting crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)) and is rotated clockwise by an angle T12 (T12> T11). As shown in FIG. 33 (a), the sliding projection 574 is slightly separated from the inner circumferential surface of the deformed elongated hole 553 and the pivoting arm member 550 is swung downward by the action of gravity. In this case, in the margin D from the state shown in FIG. 32B until the sliding projection 574 passes the first non-transmission wall 553b and reaches the second non-transmission wall 553c, the pivot arm member 550 The driving force is not transmitted (non-transmission area), and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h4 (h4 <h1).

  From the state of FIG. 33 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)) and is rotated clockwise by an angle T13 (T13> T12). And as shown in FIG. 33 (b), the sliding projection 574 is brought into contact with the second non-transmission wall portion 553c of the deformed elongated hole 553 of the pivot arm member 550 pivoted downward by the action of gravity. Ru. That is, from the state of FIG. 33B to the state of FIG. 34A, the driving force is transmitted to the pivoting arm member 550 (transmission area). In the state of FIG. 33B, the protrusion 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h5 (h5 <h4).

  From the state of FIG. 33 (b), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), only by an angle T14 (T141490 degrees> T13). And the sliding projection 574 is accommodated at the right end of the second non-transmission wall 553c of the deformed elongated hole 553 and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by the distance h3 Is reached (see FIG. 34A). During this time, the inner circumferential surface of the deformed elongated hole 553 abuts in the moving direction of the sliding projection 574, and the driving force is transmitted to the pivoting arm member 550 (transmission area).

  Here, the rotation of the pivoting crank member 570 shown in FIG. 32 (b) to FIG. 34 (a) and the rotation of the pivoting crank member 570 shown in FIG. 30 (a) to FIG. Although the rotation direction of the movable crank member 570 is different, the rotation area (phase) of the rotating crank member 570 is the same.

  In this case, in the rotation of the pivoting crank member 570 shown in FIGS. 32 (b) to 34 (a), the inner periphery of the deformed elongated hole 553 in the moving direction of the sliding projection 574 of the pivoting crank member 570. While the surface is not in contact, the driving force is not transmitted to the rotating arm member 550 (non-transmission area), while the rotation of the rotating crank member 570 shown in FIG. 30A to FIG. The driving force is transmitted to the rotation arm member 550 (transmission area).

  Therefore, the mode of transmission of the driving force to the pivoting arm member 550 can be changed according to the rotation direction of the pivoting crank member 570. Thus, by reversing the rotation direction of the rotating crank member 570, two effects of the rotating arm member 550 can be formed.

  That is, in the present embodiment, when the sliding projection 574 of the pivoting crank member 570 rotates between FIG. 32A and FIG. 34A, the pivoting crank member 570 rotates clockwise as viewed from the front. When rotated, the pivoting arm member 550 is swung by free fall depending on the gravitational acceleration (non-transmission area) until the sliding projection 574 abuts on the inner circumferential surface of the deformed elongated hole 553. On the other hand, when the rotating crank member 570 is rotated counterclockwise in a front view, the rotating arm member 550 is swung at a speed depending on the rotational speed of the rotating crank member 570 (transmission area).

  Thereby, even when the rotation speed of the rotation crank member 570 is equalized, the rotation direction when the rotation crank member 570 is arranged in the same phase by reversing the rotation direction of the rotation crank member 570 Variations of the swing speed of the arm member 550 can be increased.

  Further, the variation of the swinging speed of the pivoting arm member 550 is achieved by the shape of the deformed elongated hole 553 (the formation of the margin D), so that the aspect of the transmission of the driving force to the pivoting arm member 550 is It is possible to eliminate the need for another member such as a changeover switch for changing, and to reduce the member cost.

  In the present embodiment, the margin D is formed on the side of the pivotal support hole 552 of the pivoting arm member 550. Therefore, while the sliding projection 574 passes through the margin D by a predetermined distance, as compared with the case where the margin D is formed on the opposite side of the support hole 552 with respect to the rotation shaft of the rotating crank member 570. The distance by which the protrusion 541 b moves downward can be increased. Therefore, it is possible to make the change of the operation of the pivoting arm member 550 in the case where the rotation direction of the pivoting crank member 570 is made different while suppressing the formation range of the surplus portion D of the pivoting crank member 570.

  From the state of FIG. 34 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), and is rotated clockwise by an angle T15 (T15> T14). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state shown in FIG. 34 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  When the pivoting arm member 550 is to be rotated clockwise in a front view from the state of FIG. 34 (b), the sliding projection 574 is directed to the rotation axis of the pivoting crank member 570 by the second non-transmission wall portion 553c. It is pushed. In this case, the movement of the sliding projection 574 is restricted, so that the pivoting of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from rotating clockwise in a front view from the state of FIG. 34 (b).

  From the state of FIG. 34 (b), the turning crank member 570 is rotated clockwise in a front view (refer to FIG. 32 (a)), and only by an angle T16 (T16 ≒ 180 degrees> T15). When it is rotated, the sliding projection 574 slides on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state of FIG. 35 (a). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  From the state of FIG. 35 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), and is rotated clockwise by an angle T17 (T17> T16). And the sliding projection 574 is moved in the transmission groove 553a (transmission area), and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h2 (h2> h3) (FIG. 35). (B) see). That is, the pivoting arm member 550 is swung.

  Here, when the rotation of the rotation crank member 570 and the swing of the rotation arm member 550 are always interlocked, it is difficult to shift the start timing of the rotation crank member 570 and the rotation arm member 550 . Therefore, when the pivoting crank member 570 and the pivoting arm member 550 are started, it is necessary to generate a large force corresponding to the rigidity of the force that overcomes the inertia of each member. Therefore, a drive having a large driving force is required, which may increase the size of the drive.

  On the other hand, in the present embodiment, the start timings of the pivoting crank member 570 and the pivoting arm member 550 can be shifted. That is, for example, from the state of FIG. 34 (b) to the state of FIG. 35 (a), only the pivoting crank member 570 is rotated, and from the state of FIG. 35 (a) to the state of FIG. 35 (b) The rotation arm member 550 can be started by interlocking with the rotation crank member 570.

  Thereby, since the force of the rotating crank member 570 can be utilized for starting the rotating arm member 550, the driving force necessary for the second drive device 560 can be suppressed. Therefore, the second drive device 560 can be miniaturized.

  When the rotating crank member 570 is rotated clockwise in a front view from the state of FIG. 35 (b), the sliding projection 574 is moved in the transmission groove portion 553a to reach the state of FIG. 32 (a). During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ). That is, the pivoting arm member 550 is swung.

  From these things, as shown in FIGS. 32 to 35, in the case where the rotating crank member 570 is rotated at the same speed clockwise, the protrusion 541b is a reference in a period of 1⁄4 of the rotation cycle of the rotating crank member 570. From a position separated by a distance h1 vertically upward from the horizontal line O, it is moved downward to a position separated by a distance h3 (h3 <h1). The protrusion 541b is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3 in a period of 1⁄4 of the subsequent rotation period, and the protrusion 541b is perpendicular to the reference horizontal line O in a period of half the subsequent rotation period. From a position spaced apart by a distance h3 upward, it is moved up to a position spaced by a distance h1 (h1> h3). Thereby, even when the rotating crank member 570 is moved at a constant speed, the moving speed of the projection 541 b (moving speed of the expansion / contraction effect device 540 in the expansion / contraction direction) can be doubled.

  In addition, the moving speed of the pivoting arm member 550 is partially accelerated by gravity acceleration when it is moved downward, while the moving speed of the rotating arm member 550 is always along the rotational speed of the rotating crank member 570 when it is moved upward. Be done. Thereby, the aspect of the speed change of the projection part 541b (the expansion-contraction effect device 540) can be changed by the movement direction of the projection part 541b (the expansion-contraction effect device 540).

  A change in the distance from the reference horizontal line O of the protrusion 541 b (the expansion / contraction effect device 540) when the turning crank member 570 is rotated clockwise or counterclockwise will be described with reference to FIG. 36.

  FIG. 36 is a graph showing the distance from the reference horizontal line O of the protrusion 541b (see FIG. 28A). In the graph shown in FIG. 36, the swing angle is shown on the horizontal axis with the upper right angle (see FIG. 28 (a)) of the rotating crank member 570 as the left end and increasing to the right The distance from the reference horizontal line O of the protrusion 541 b is shown in FIG.

  In FIG. 36, the distance from the reference horizontal line O of the protrusion 541b when the pivoting crank member 570 is rotated counterclockwise is indicated by a curve CC1, and the pivoting crank member 570 is rotated clockwise. The distance from the reference horizontal line O of the protrusion 541 b is indicated by a curve CW1. Curves CC1 and CW1 correspond to the states of the protrusions 541b shown in FIG. 28 to FIG. 35, respectively, and for the purpose of comparison when the rotating crank members 570 are arranged in the same phase, A curve obtained by inverting the curve CC1 from side to side is illustrated by an imaginary line as a curve CC2. As described above, the rising speed and the falling speed of the protrusion 541b moved up and down by the rotating arm member 550 are changed by reversing the rotating direction of the rotating crank member 570 as described above by comparing the curves CC1 and CW1. Can.

  As a comparison target of the curve CW1, when the rotating crank member 570 rotates clockwise, the sliding projection 574 rotates until it abuts on the second non-transmission wall 553c (see FIG. 28A). The case where the arm member 550 (see FIG. 28A) is disposed at the retracted position is illustrated by a broken line as a curve CW2. This corresponds to the case where the biasing force that causes the torsion spring 517a (see FIG. 23) to swing the pivoting arm member 550 upward is set large. In this case, the period in which the pivoting arm member 550 is disposed at the retracted position can be made longer.

  In the angle range N1 in which the distance from the horizontal reference line O of the protrusion 541b (see FIG. 28A) is maintained without being changed in the curves CC1 and CW1, the rotating crank member 570 and the rotating arm member 550 ( A non-transmission area to which the driving force is not transmitted is formed with respect to FIG. 28 (a). The width of the angular range N1 can be adjusted by the formation width of the second non-transmission wall portion 553c (see FIG. 28A).

  Further, in the curve CW1, an angle until the sliding projection 574 of the pivoting crank member 570 (see FIG. 28A) abuts on the deformed elongated hole 553 of the pivoting arm member 550 (see FIG. 28A). In the range N2, a non-transmission area in which the driving force is not transmitted is formed between the rotation crank member 570 and the rotation arm member 550. The width of the angle range N2 can be adjusted by the formation width of the first non-transmission wall portion 553b (see FIG. 28A).

  As shown in FIG. 36, a curve is formed between the angle T11 to the angle T14 and the angle T4 to the angle T6 in the case where the rotating crank members 570 (see FIG. 28A) are arranged in the same phase. The shapes of the CW1 and the curve CC1 are different (the curve CW1 and the curve CC2 obtained by inverting the left and right of the curve CC1 do not overlap).

  That is, the angle when the pivoting crank member 570 (see FIG. 28A) lifts the pivoting arm member 550 (see FIG. 28A) between the angle T4 and the angle T6 is the angle As compared with the case where the pivoting crank member 570 rotates in a mode in which the pivoting arm member 550 is pushed down from 11 to the angle T14, a gentle curve is obtained.

  This is because, in the curve CW1, the sliding projection 574 (see FIG. 28 (a)) abuts on the second non-transmission wall 553c (see FIG. 28 (a)) of the deformed elongated hole 553 and the pivoting arm member 550 (see FIG. FIG. 28 (a) is rotated, and in the curve CC1, the sliding projection 574 abuts on the selected wall 553d (see FIG. 28 (a)) of the deformed elongated hole 553 and the pivoting arm member 550 is rotated. Depends on

  Referring back to FIG. 28 (a), description will be made. As described above, in the deformed long hole 553, the right end of the second non-transmission wall portion 553c is formed along the arc S1 centering on the axial support hole 552 (the formation angle with the arc S1 is small) The right end portion of the selected wall portion 553d is formed to intersect the arc S2 centered on the pivot hole 552 at an angle larger than the formation angle of the right end portion of the second non-transfer wall portion 553c and the arc S1. Ru.

  In this case, when the distance between the sliding projection 574 and the shaft support hole 552 changes, the amount of swing of the pivoting arm member 550, which is necessary to cope with the amount of change, changes. That is, when the distance between the sliding projection 574 and the shaft support hole 552 changes by a predetermined amount in a state where the sliding projection 574 and the right end of the selection wall 553d abut on each other, the swing amount of the pivot arm member 550 is The amount is smaller than the amount of swinging of the pivoting arm member 550 when the sliding protrusion 574 and the right end of the second non-transmission wall 553c abut each other in a predetermined amount.

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

  Although the case where the rotation crank member 570 is rotated in one direction has been described with reference to FIGS. 28 to 35, it is also possible to reverse the rotation direction of the rotation crank member 570 halfway. As the timing to reverse the rotation direction of the rotating crank member 570, the sliding projection 574 is disposed opposite to the first non-transmission wall 553b (for example, FIG. 28A, FIG. 31 and FIG. 32A) 32 (b), the pivoting arm member 550 is disposed at the retracted position), and the sliding projection 574 is disposed opposite to the second non-transmission wall 553c (for example, FIG. 29 (a), 29 (b), 34 (b) and 35 (a), the pivoting arm member 550 is preferably disposed in the extended position).

  In this case, since the rotation arm member 550 is not in contact with the rotation direction of the rotation crank member 570, the resistance applied to the rotation crank member 570 from the rotation arm member 550 when the rotation direction of the rotation crank member 570 is reversed. It can be suppressed. Further, in the present embodiment, a position detection sensor (not shown) for detecting a state in which the pivoting arm member 550 is disposed at the retracted position and a state in which the pivoting arm member 550 is disposed at the overhang position is disposed. Control in which the rotation direction of the rotating crank member 570 is reversed can be facilitated with the movable arm member 550 disposed at the retracted position or the extended position.

  By reversing the rotation direction of the rotating crank member 570, variations of the reciprocating operation of the expansion and contraction rendering device 540 in the vertical direction can be increased.

  For example, from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 28A), the pivoting crank member 570 is rotated counterclockwise a half turn (see FIG. 29A), and then The direction of rotation of the movable crank member 570 is reversed, and the case where the pivoting arm member 550 is disposed at the retracted position is illustrated by being rotated by a half turn clockwise (see FIG. 28A). That is, the sliding projection 574 is moved on the opposite side of the support hole 552.

  In this case, the protrusion 541 b of the expansion / contraction effect device 540 is separated from the reference horizontal line O by a distance h1 from the reference horizontal line O in a half period of the rotation cycle of the rotary crank member 570 by a distance h3 (h3 <h1 Move down to a position separated by). In this case, the protrusion 541b moves downward along the curve CC1 (see FIG. 36) whose horizontal axis is from 0 degrees to 180 degrees. Then, the projection 541 b extends from a position separated by a distance h3 vertically upward from the reference horizontal line O in a half period of the rotation cycle of the rotary crank member 570 to a position separated by a distance h1 (h1> h3) from the reference horizontal line O Move up. In this case, the protrusion 541b moves upward along the curve CW1 (see FIG. 36) whose horizontal axis is from 180 degrees to 360 degrees.

  Thus, when the rotating crank member 570 rotates at a constant speed, the protrusion 541b of the expansion / contraction effect device 540 is moved upward by a predetermined distance (h1-h3) and a period in which the projection 541b descends by a predetermined distance (h1-h3). Period can be the same.

  Also, for example, from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 32A), the pivoting crank member 570 is rotated by 1⁄4 turn clockwise (see FIG. 34A) Then, the direction of rotation of the rotating crank member 570 is reversed, and the case where the rotating arm member 550 is disposed at the retracted position is illustrated by being rotated by 1⁄4 of the counterclockwise direction (FIG. 32). See (a)). That is, this is the case where the sliding projection 574 moves on the side in which the sliding projection 574 approaches the support hole 552.

  In this case, the protrusion 541 b of the expansion / contraction effect device 540 is a distance h3 (h3) from the reference horizontal line O from a position separated vertically upward from the reference horizontal line O by a distance h1 in a period of 1⁄4 of the rotation cycle of the rotary crank member 570. Move down to a position separated by <h1). In this case, the protrusion 541b moves downward along the curve CW1 (see FIG. 36) whose horizontal axis is from 0 degrees to 90 degrees. Then, the protrusion 541b is separated from the reference horizontal line O by a distance h1 (h1> h3) from a position separated by a distance h3 vertically upward from the reference horizontal line O in a period of 1⁄4 of the rotation cycle of the rotary crank member 570 Move up to the position. In this case, the protrusion 541b moves upward along a curve CC1 (see FIG. 36) whose horizontal axis is 270 degrees to 360 degrees.

  Thus, when the rotating crank member 570 is rotated at a constant speed, the protrusion 541b of the expansion / contraction effect device 540 is moved downward by a predetermined distance (h1-h3), and is raised by a predetermined distance (h1-h3). The period of movement can be made the same, and the predetermined period can be shortened as compared with the case where the sliding projection 574 is moved on the opposite side of the pivot hole 552.

  In addition, when the protrusion 541b of the expansion and contraction rendering device 540 moves downward, it can be partially dropped (from the angle T11 to the angle T13) as free fall, while the protrusion 541b of the expansion and contraction rendering device 540 moves upward In this case, it is always moved at a speed in accordance with the rotational speed of the rotating crank member 570. Therefore, even if the rotation speed of the rotation crank member 570 is the same, the movement mode of the expansion / contraction effect device 540 in the case where the rotation crank member 570 is disposed in the same phase depending on the movement direction of the protrusion 541b of the expansion / contraction effect device 540 The degree of speed change) can be changed. In other words, the curve CW1 and the curve CC2 in the range from the angle T11 to the angle T13 in FIG. 36 can be made different.

  Next, the difference in the swing angle due to the difference in the expansion / contraction state of the expansion / contraction effect device 540 will be described. First, the swing angle when the expansion / contraction effect device 540 forms an extended state will be described.

  FIGS. 37 to 39 are front views of the combined operation unit 500. FIG. Note that FIGS. 37 to 39 illustrate the case where the expansion / contraction effect device 540 forms an extended state (when the pivoting arm member 550 is disposed at the extended position). Further, FIG. 37 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 39, the state of being moved clockwise in a front view from the state of FIG. 37 is illustrated. The attitude of the pivoting arm member 550 shown in FIGS. 37 to 39 is the same as the attitude of the pivoting arm member 550 shown in FIG. Therefore, in FIGS. 37 to 39, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h3.

  As illustrated in FIGS. 37 to 39, the swinging locus of the protrusion 541b when the expansion / contraction effect device 540 forms an extended state is formed in an arc shape centering on the first shaft 512 and is rotated. Along the extending direction of the arc-shaped hole 554 of the arm member 550. In other words, the arc-shaped hole 554 is extended along the swinging trajectory of the protrusion 541 b. Therefore, the inner surface of the arc-shaped hole 554 is not disposed facing the swing direction of the protrusion 541 b, and the arc-shaped hole 554 does not function as a stopper for stopping the swing of the protrusion 541 b. Therefore, the swing angle of the protrusion 541 b depends on the method of regulating the swing of the rotary plate 520. That is, the rotary plate 520 can be rocked until it abuts on the third stopper portion 518c, and the protrusion 541b can be rocked to the rocking angle θ1 counterclockwise in a front view, and the rotary plate 520 is second The protrusion 541 b can be swung until it abuts against the stopper portion 518 b, and the protrusion 541 b can swing to a swing angle θ 2 clockwise in a front view.

  Here, as shown in FIG. 39, when the protrusion 541 b is swung leftward in a front view at a swing angle θ 2, the protrusion 541 b is separated from the arc-shaped hole 554 of the pivot arm member 550. In this case, the expansion / contraction effect device 540 is moved in the expansion / contraction direction independently from the pivoting arm member 550, and the projection 541b can not return to the arc-shaped hole 554, which may cause an operation failure.

  On the other hand, in the present embodiment, even when the protrusion 541b is separated from the arc-shaped hole 554 of the pivoting arm member 550, the first raised fastening portion 541c and the guide fastening portion 541e of the expansion and contraction rendering device 540 are pivoting arm members By being arranged so as to be engageable with 550, alignment between the protrusion 541b and the arc-shaped hole 554 can be performed. That is, the telescopic effect device 540 can be prevented from being moved in the telescopic direction independently of the pivoting arm member 550.

  Thus, the length of the pivoting arm member 550 can be shortened while eliminating the defect that the projection 541 b can not return to the arc-shaped hole 554. Thereby, the arrangement | positioning area | region of rotation arm member 550 can be suppressed, and the arrangement | positioning area | region of another movable member can be ensured by that much. In addition, the material cost of the pivoting arm member 550 can be reduced.

  When the pivoting arm member 550 swings in a state where the projection 541b is separated from the arc-shaped hole 554 (see FIG. 39), the positional relationship between the projection 541b and the arc-shaped hole 554 deviates, and the projection 541b is circular. It is difficult to return to the arc-shaped hole 554, which may cause malfunction. On the other hand, in the present embodiment, the sliding projection 574 abuts on the deformed elongated hole 553 to prevent the pivoting arm member 550 from swinging (see FIG. 39).

  In addition to that, the movement locus of the point (the point furthest from the rotation axis) remote from the rotation axis of the slide projection 574 is formed along the side surface of the deformed elongated hole 553 which is in contact with the slide projection 574 Therefore, the rotating crank member 570 can be rotated counterclockwise from the state of FIG. 39 while maintaining the posture of the rotating arm member 550 (see FIG. 39).

  Here, for example, as shown in FIG. 28 to FIG. 31, when the rotating crank member 570 rotates counterclockwise, immediately after the rotating arm member 550 is placed at the extended position (FIG. 29 (a 30) the projection 541b is separated from the arc-shaped hole 554, and then the projection 541b returns to the arc-shaped hole 554 until the rotating crank member 570 is disposed in the state shown in FIG. think of. If the projection 541b is returned to the arc-shaped hole 554, the pivoting crank member 570 is further rotated, and even if the pivoting arm member 550 pivots to the state shown in FIG. 30 (b), the projection 541b However, there is no malfunction that the circular hole 554 can not return.

  In this case, when the pivoting arm member 550 and the expansion / contraction effect device 540 are respectively pivoted, stop control or start control of the pivoting crank member 570 is performed according to the positional relationship between the protrusion 541b and the arc-shaped hole 554. There is no need, and the rotation of the rotating crank member 570 can be continued. In other words, it is only necessary to control the swing timing of the expansion / contraction effect device 540, and the pivoting crank member 570 does not need to be controlled, and may be kept rotating. Therefore, it is possible to suppress the control load of the complicated operation of swinging the telescopic effect device 540 and the pivoting arm member 550 at different timings.

  In the present embodiment, the fore-end portion 554a is formed such that the width of the arc-shaped hole 554 can be increased toward the opening end (the left end of FIG. 39) of the arc-shaped hole 554. Thereby, the positional deviation (positional deviation of the expansion / contraction effect device 540 in the expansion / contraction direction) when the projection 541 b returns to the arc-shaped hole 554 can be largely tolerated, and the first bulky fastening portion 541 c and the guide fastening portion 541 e A large clearance from the pivoting arm member 550 can be secured.

  Next, a swing angle when the expansion / contraction effect device 540 forms an intermediate state which is a state between an extended state and a reduced state will be described. By swinging the pivoting arm member 550 clockwise from the state in which the expansion / contraction effect device 540 is in the expanded state (see FIG. 37), the protrusion 541 b moves corresponding to the arc-shaped hole 554, and the expansion / contraction effect Device 540 forms an intermediate state.

  40 to 42 are front views of the combined operation unit 500. FIG. FIGS. 40 to 42 illustrate the case where the expansion / contraction effect device 540 forms an intermediate state (when the pivoting arm member 550 is disposed between the overhanging position and the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541 b is shorter than the case where the expansion / contraction effect device 540 forms an extended state (see FIGS. 37 to 39). That is, the swinging trajectory of the protrusion 541 b is changed according to the state of the expansion / contraction effect device 540 in the expansion / contraction direction.

  Further, FIG. 40 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 42, the state of being moved clockwise in a front view from the state of FIG. 40 is illustrated.

  The attitude of the pivoting arm member 550 shown in FIGS. 40 to 42 is the same as the attitude of the pivoting arm member 550 shown in FIG. 28 (b). Therefore, in FIGS. 40 to 42, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h2.

  At this time, the front plate member 546 is driven to interlock with the upward movement of the arc-shaped hole 554 by the pivoting arm member 550 swinging. Therefore, the circular arc-shaped hole 554 has a function of changing the swing angle of the protrusion 541b as described later and a function of interlocking the pivot arm member 550 and the front plate member 546. This makes it possible to centralize the functions.

  As illustrated in FIG. 40 to FIG. 42, the swinging trajectory of the protrusion 541b when the expansion / contraction effect device 540 forms an intermediate state, and the shape of the arc-shaped hole 554 of the pivoting arm member 550 have a curvature radius Although the central axes of the two coincide with each other on the upper side, the radius of curvature and the posture differ from each other. Since the swinging locus of the protrusion 541b and the arc-shaped hole 554 intersect at the formation angle α1 (see FIG. 42), the arc-shaped hole 554 acts as a stopper for stopping the swing of the protrusion 541b (see FIG. 42) .

  As shown in FIG. 41, when the rotary plate 520 is rotated counterclockwise in a front view, the protrusion 541b is not in contact with the arc-shaped hole 554. That is, since the rotary plate 520 can be rocked until it abuts on the third stopper portion 518c, the projection 541b can be rocked to the rocking angle θ3 counterclockwise in a front view (angle θ3 = Angle θ1).

  As shown in FIG. 42, when the rotary plate 520 is rotated clockwise in a front view, the protrusion 541 b is abutted by the first stopper surface 554 b of the arc-shaped hole 554. In this state, the guide fastening portion 541e is in contact with the upper side surface of the pivoting arm member 550, and the change in state of the expansion / contraction effect device 540 in the expansion / contraction direction is prevented. Motion is stopped.

  That is, the rotary plate 520 is not rocked until it abuts on the third stopper 518c, and the projection 541b can be rocked clockwise to the rocking angle θ4 in a front view (angle θ4 <angle θ2). . Therefore, the swing angle of the protrusion 541 b can be changed depending on the state of the extension effect device 540 in the extension direction. As a result, by making the expansion and contraction state of the expansion and contraction rendering device 540 different, the variation of the swing angle of the expansion and contraction rendering device 540 can be increased. In the state shown in FIG. 42, the guide fastening portion 541e is in contact with the main portion 551 of the pivoting arm member 550.

  Next, the swing angle when the expansion / contraction effect device 540 forms a contracted state will be described. By swinging the pivoting arm member 550 clockwise from the state (see FIG. 40) in which the expansion / contraction effect device 540 is in the intermediate state, the protrusion 541 b moves corresponding to the arc-shaped hole 554, and expansion / contraction effect Device 540 forms a reduced state.

  43 to 45 are front views of the combined operation unit 500. FIG. FIGS. 43 to 45 illustrate the case where the expansion / contraction effect device 540 forms a contracted state (when the pivoting arm member 550 is disposed at the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541 b is shorter than that in the case where the expansion / contraction effect device 540 forms an intermediate state (see FIGS. 40 to 42). That is, the swinging trajectory of the protrusion 541 b is changed according to the state of the expansion / contraction effect device 540 in the expansion / contraction direction.

  Further, FIG. 43 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 45, the state of being moved clockwise in a front view from the state of FIG. 43 is illustrated. Note that the attitude of the pivoting arm member 550 shown in FIGS. 43 to 45 is the same as the attitude of the pivoting arm member 550 shown in FIG. Therefore, in FIGS. 43 to 45, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h1.

  At this time, the front plate member 546 is driven to interlock with the upward movement of the arc-shaped hole 554 by the pivoting arm member 550 swinging. Therefore, the arc-shaped hole 554 has a function of changing the swing angle of the protrusion 541b and a function of interlocking the pivot arm member 550 and the front plate member 546. This makes it possible to centralize the functions.

  As illustrated in FIGS. 43 to 45, the swinging trajectory of the protrusion 541b when the expansion / contraction effect device 540 forms a contracted state and the shape of the arc-shaped hole 554 of the pivoting arm member 550 are different from each other, The central axis of the radius of curvature is reversed. That is, the central axis of the radius of curvature of the rocking trajectory of the projection 541 b is below the projection 541 b, and the central axis of the radius of curvature of the arc-shaped hole 554 is disposed above the arc-shaped hole 554. In this case, the swinging trajectory of the protrusion 541b and the arc-shaped hole 554 intersect at the formation angle α2 (angle α2> angle α1), and the arc-shaped hole 554 acts as a stopper for stopping the swing of the protrusion 541b ( 44 and 45).

  As shown in FIG. 44, when the rotary plate 520 is rotated counterclockwise in a front view, the protrusion 541 b abuts on the second stopper surface 554 c of the arc-shaped hole 554. In this case, the rotary plate 520 is not rocked until it abuts on the third stopper portion 518c (see FIG. 41), and the projection 541b can be rocked counterclockwise to the rocking angle θ5 in a front view. (Angle θ5 <angle θ1 = angle θ3).

  As shown in FIG. 45, when the rotary plate 520 is rotated clockwise in a front view, the protrusion 541 b is abutted by the third stopper surface 554 d of the arc-shaped hole 554. In this case, the rotary plate 520 is not rocked until it abuts on the third stopper 518c, and the projection 541b can be rocked clockwise to the rocking angle θ6 in a front view (angle θ6 <angle θ4 <Angle θ 2). Therefore, the swing angle of the protrusion 541 b can be changed depending on the state of the extension effect device 540 in the extension direction. Thereby, the variation of the rocking width of the expansion / contraction effect device 540 can be increased.

  Here, the movement trajectory of projection 541 b in the contracted state and formation angle α2 of arc-shaped hole 554 are formed larger than the formation angle α1 of the movement trajectory of projection 541 b in the intermediate state and arc-shaped hole 554 Ru.

  In the relationship between the swinging locus of the protrusion 541b and the arc-shaped hole 554, if the formation angle is 90 degrees, the protrusion 541b is swung in a mode crossing the arc-shaped hole 554, and the protrusion 541b The rocking angle of is minimized. On the other hand, in the relationship between the swinging locus of the protrusion 541 b and the arc-shaped hole 554, if the formation angle is 0 degree (see FIGS. 37 to 39), the protrusion 541 b extends in the extending direction of the arc-shaped hole 554. As a result, the rocking angle of the projection 541 b is maximized. Therefore, the swing angle of the protrusion 541b in the reduced state (formation angle α2) can be smaller than the swing angle of the protrusion 541b in the intermediate state (formation angle α1) (formation angle α1 <formation angle α2 ).

  As described above, when the expansion / contraction state of the expansion / contraction effect device 540 is changed, the swing angle of the protrusion 541b is changed, and at that time, the inner peripheral surface of the arc-shaped hole 554 (first stopper surface 554b, second The stopper surface 554 c and the third stopper surface 554 d function as a stopper that regulates the swing angle of the expansion and contraction rendering device 540. Thus, the inner circumferential surface of the arc-shaped hole 554 can be used as a portion that regulates the swing angle of the protrusion 541b in each case where the expansion / contraction state of the expansion / contraction effect device 540 is different. Therefore, it is possible to reduce the space for arranging the stopper that regulates the swing angle of the protrusion 541b.

  In addition, the stopper that regulates the swing angle of the expansion / contraction effect device 540 is retracted from the front side of the third symbol display device 81 when the pivoting arm member 550 is disposed at the retracted position. Therefore, unlike the case where a fixed stopper is disposed on the front side of the third symbol display device 81, the stopper remains on the front surface of the third symbol display device 81 even when the pivoting arm member 550 is disposed at the retracted position. Can be prevented. Thereby, when the pivoting arm member 550 is disposed at the retracted position, another member can be disposed on the front surface of the third symbol display device 81, so that another movable member (for example, the slide operation unit 700). The overhanging space of the support member 720) can be secured.

  The arc-shaped hole 554 of the pivoting arm member 550 has a function as a stopper for restricting the swing angle of the stretching effect device 540 and a second drive of the stretching effect device 540 by swinging the pivoting arm member 550. And a function as a transmission device for transmitting the driving force of the device 560 and causing the expansion / contraction effect device 540 to perform the expansion / contraction operation. Thus, the functions can be consolidated and the number of parts can be reduced.

  The tilt operation unit 600 and the slide operation unit 700 will be described with reference to FIGS. 46 to 57. The tilt operation unit 600 is a unit that swings the effect member 620 (refer to FIG. 12) (see FIG. 12), and the slide operation unit 700 is a unit that slides the tilt operation unit 600 in the left-right direction. 46 is a front perspective view of the tilting operation unit 600 and the slide operation unit 700, and FIG. 47 is a rear perspective view of the tilting operation unit 600 and the slide operation unit 700. 46 and 47, a state in which the tilt operation unit 600 and the column member 720 (see FIG. 47) of the slide operation unit 700 are disposed at the retracted position is illustrated.

  FIG. 48 is a front exploded perspective view of the slide operation unit 700, and FIG. 49 is a rear exploded perspective view of the slide operation unit 700. In FIGS. 48 and 49, the tilting operation unit 600 is illustrated without being disassembled in order to facilitate understanding.

  The slide operation unit 700 has a base member 710 formed in a plate shape elongated in the left-right direction, and one end thereof fastened and fixed to the slide plate 711 of the base member 710, and is formed slidably in the left-right direction A post member 720, and a slide rail 730 at one end of which is fastened and fixed to the post member 720 and at which the other end to which the base member 610 of the tilting operation unit 600 is fastened and fixed is vertically expandable. A connection member 740 is formed slidably on the back rail 716 of the main body 710 and is pivotally supported by the pivoting protrusion 612 of the tilting operation unit 600, and generates a driving force for moving the support member 720 in the left-right direction. A driving device 750 and a back cover member 760 formed on the back side of the driving device 750 and fastened and fixed to the base member 710 are mainly included.

  The base member 710 is a member that forms the frame of the slide operation unit 700, and is formed slideably in the left-right direction and the slide plate 711 to which the support member 720 is fastened and fixed from the back side. A shaft support hole 712 recessed in the left lower part with a circular cross section and the fixed shaft portion 753a is pivotally supported, a long hole shape recessed in the right lower portion of the base member 710 in a rear view, a shaft support hole The slide shaft support hole 713 whose upper and lower positions coincide with each other 712 and in which the moving shaft portion 754a is slidably supported, and which is formed swingably in the vertical direction by a solenoid And the upper rolling member 742 of the connecting member 740 is rolled so as to project in a downward arc shape in cross section downward to the front side at the upper end portion of the base member 710. The front rail portion 715 mainly comprises a rear rail portion 716 through plate portion 741b is inserted in the recessed by the coupling member 740 from the rear arc-shaped cross section in a front rail portion 715, a.

  Since the lever member 714 restricts the slide movement of the support member 720 fixedly fixed to the slide plate 711 in the lateral direction, the driving force of the drive device 750 when maintaining the tilting operation unit 600 in the retracted position is not necessary. Can.

  Here, in the present embodiment, since the tilting operation unit 600 is moved along the formation direction (arc track) of the front rail portion 715 and the back rail portion 716, the left and right of the support members 720 connected to the tilting operation unit 600. A sliding movement in the direction can occur by the action of gravity loaded on the tilting movement unit 600. For example, when the tilting operation unit 600 is disposed at the retracted position (see FIG. 46), the moving direction of the tilting operation unit 600 is directed obliquely downward along the shape of the front rail portion 715. Therefore, even if the moving direction of the column member 720 connected to the tilting operation unit 600 is the left and right direction along the moving direction of the slide plate 711, the column member 720 may be moved by gravity. In the present embodiment, the lever member 714 is pivoted downward and engaged with the locking portion 725 of the support member 720, and the movement of the support member 720 in the left and right direction is restricted. It is possible to maintain the support member 720 in the retracted position even if the support member 720 is unnecessary. Therefore, the durability of the drive device 750 can be improved.

  The support member 720 includes a main body portion 721 formed in a plate shape elongated in the vertical direction, and a slide plate 711 of the base member 710 continuously provided in the left and right direction at the lower end portion of the main body portion 721. The first fastening portion 722 through which the screw fastened and fixed is inserted, and the second fastening in which the slide rail 730 is fastened and secured by being continuously provided vertically in the front end left end portion of the main body portion 721 The slide hole 724 which is an elongated hole extending in a direction parallel to the connecting direction of the portion 723 and the second fastening portion 723 and is formed on the right side of the main body 721 in a front view; A lower lid portion in which a belt 755 of the driving device 750 is sandwiched between a hook-like locking portion 725 protruding upward from the lower end and engaged with the lever member 714 and the lower surface of the main body 721 726 and the main unit 7 A rolling portion 727 protruding from the lower surface side of the lower end portion 1 and formed so as to be capable of rolling on the inner peripheral surface of the slide concave portion 764 of the back surface cover member 760 And a coil spring 728 connected to the hook portion 617 of the base member 610 at its lower end.

  The slide rail 730 is fastened and fixed to the support member 720 in a posture in which the slide rail 730 can expand and contract in the connection direction of the second fastening portion 723.

  The slide hole 724 is an elongated hole extending in a direction parallel to the connecting direction of the second fastening portions 723 and is an elongated hole through which the auxiliary member 615 of the tilting operation unit 600 is inserted. Therefore, the slide hole 724 can suppress the positional deviation (the relative rotation of the tilting unit 600 with respect to the column member 720) of the tilting unit 600 moving up and down in the left-right direction.

  The lower lid portion 726 is formed with a tooth shape extending in the front-rear direction on the upper surface side. This tooth profile is shaped to mesh with the tooth profile formed on the inner circumferential surface of the belt 755 of the drive device 750. Thereby, the support member 720 can be prevented from slipping on the belt 755 of the drive device 750.

  The rolling portion 727 is inserted into the slide concave portion 764 of the back cover 760 so as to be able to roll, thereby suppressing frictional resistance and suppressing tilting in the front-rear direction around the lower end portion of the support member 720. be able to.

  The coil spring 728 is a biasing force for moving the tilting operation unit 600 upward. Since the biasing force from the coil spring 728 is always loaded on the tilting operation unit 600, the tilting operation unit 600 is suppressed from being dropped downward by gravity.

  The connecting member 740 has a triangular plate-like main body member 741 rotatably supported by the pivotal support projection 612 of the tilting operation unit 600, and a base supported by a rolling shaft 741c projecting from the main body member 741. A pair of cylindrical upper rolling members 742 rolled on the upper surface of the front rail portion 715 of the member 710 and a rolling shaft 741 c of the main body member 741 are fastened and fixed from the front side to cover the front side of the front rail portion 715 And the lower half portion of the front cover member 743 disposed in a manner and the lower half portion thereof is externally fitted and held by the front cover member 743 and the upper half portion is the lower surface of the front rail portion 715 And a cylindrical lower rolling member 744 to be moved.

  The main body member 741 is a member formed in a triangular plate shape, and is a circular recess recessed from the rear surface at the upper end portion, and a shaft rotatably supported by the pivoting protrusion 612 of the tilting operation unit 600 A support portion 741a, a plate-like member protruding toward the front side at the lower end portion, and a through plate portion 741b slidably inserted in the back rail portion 716 of the base member 710, and a through plate portion from the shaft support portion 741a It mainly includes a pair of rolling shafts 741c protruding in a cylindrical shape toward the front side from a position symmetrical with respect to a perpendicular drawn to 741b and rotatably supported by the upper rolling member 742 rotatably.

  The insertion plate portion 741 b is inserted into the rear rail portion 716 of the base member 710, so that 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 portion 741 a is also formed to be movable along the back rail portion 716.

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

  The upper rolling member 742 is rotatably supported by the shaft support portion 741 a and abuts on 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. As a result, it is possible to reduce the frictional resistance generated when the connecting member 740 slides, and to suppress the driving force required for the sliding movement.

  The lower rolling member 744 has a lower half rotatably fitted to a lower portion of the front cover member 743, and an upper end abuts on a lower surface of the front rail portion 715. That is, when the connecting member 740 is slid along the front rail portion 715, the lower rolling portion 744 rolls on the lower surface of the front rail portion 715. Thus, it is possible to reduce the frictional resistance generated between the connection member 740 and the front rail portion 715 during the slide movement, and to suppress the driving force required for the slide movement.

  As described above, in the present 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. Thus, the upper and lower surfaces of the front rail portion 715 can be held by the upper rolling member 742 and the lower rolling member 744 of the connecting member 740 while suppressing the frictional resistance.

  Here, since the center of gravity of the tilting operation unit 600 is formed upward as described later, there is a risk of tilting in the front-rear direction. In this case, since the connecting member 740 sandwiches the upper and lower surfaces of the front rail portion 715 by the upper rolling member 742 and the lower rolling member 744, the tilt operation unit 600 is inclined in both forward and backward directions. , Can generate resistance. As a result, the attitude of the tilting operation unit 600 can be easily maintained.

  The front cover member 743 pivotally supports the upper rolling member 742 in a non-extractable manner by being pivotally supported from the front side of the rolling shaft 741 c of the connection member 740.

  The driving device 750 is fixed to the base member 710 and generates a driving force for sliding the column member 720, a driving gear 752 pivotally supported by the driving motor 751, and the driving gear 752 A shaft fixed gear 753 engaged with and meshed with the belt 755, and a shaft moving gear 754 disposed so as to be separated from the shaft fixed gear 753 and wound with the belt 755 and capable of sliding movement of the rotation shaft 754a. A belt 755 wound around the shaft fixed gear 753 and the shaft moving gear 754 and moved by rotation of the shaft fixed gear 753, and a coil generating an urging force moving the shaft moving gear 754 in a direction away from the shaft fixed gear 753. The spring 756 is mainly provided.

  The shaft fixed gear 753 is a cylindrical member as a rotation shaft, and includes a fixed shaft portion 753a inserted into the shaft support hole 712 of the base member 710. The shaft moving gear 754 is a cylindrical member as a rotating shaft, and includes a moving shaft portion 754 a which is inserted into the slide shaft support hole 713 of the base member 710.

  The shaft fixed gear 753 and the shaft moving gear 754 are formed as gears of the same shape. The inner circumferential surface of the belt 755 is formed with a tooth profile that meshes with the gear teeth of the shaft fixed gear 753 and the shaft moving gear 754. Thus, slippage between the belt 755 and the shaft fixed gear 753 and the shaft moving gear 754 can be suppressed, and the amount of rotation of the shaft fixed gear 753 can be reliably transmitted to the belt 755.

  One end of coil spring 756 is fixed to a hook-like portion formed on slide shaft support hole 713n of base member 710 on the right in a rear view, and the other end is fixed to a case covering axial movement gear 754 . As a result, an urging force can be generated to move the shaft moving gear 754 to the opposite side of the shaft support hole 712, and an appropriate tension can be applied to the belt 755. It is possible to prevent the gear 754 from falling off.

  The back cover member 760 is a member that covers the drive device 750 on the back surface of the base member 710, and has a main body 761 formed in a box shape whose front side is opened and a fixed shaft 753a on the bottom of the main body 761. A recessed portion 762 which is a recess for receiving, a movable recessed portion 763 which is extended in the same shape as the slide shaft support hole 713 and is a recess for receiving the moving shaft portion 754a, and is extended in the lateral direction to receive the rolling portion 727 And a slide recess 764 which is a recess.

  The slide recess 764 is a recess in which the rolling portion 727 rolls on the upper and lower inner side surfaces. The frictional resistance of the sliding movement of the column member 720 is suppressed, and the tilting of the column member 720 in the front-rear direction is suppressed. That is, when the support member 720 is inclined in the front-rear direction, the rolling portion 727 is in contact with either the upper inner side surface or the lower inner side surface of the slide recess 764. Thereby, the inclination to the front-back direction of the support member 720 can be suppressed.

  Next, with reference to FIGS. 50 and 51, the tilting operation unit 600 will be described. FIG. 50 is a front exploded perspective view of the tilting operation unit 600, and FIG. 51 is a rear exploded perspective view of the tilting operation unit 600.

  The tilting operation unit 600 includes a plate-like base member 610 fastened and fixed to the other end of the slide rail 730, and a box-like effect member 620 whose lower end is pivotally supported by the base member 610. A first drive device 630 for generating a driving force for swinging the effect member 620, a transmission member 640 for transmitting the drive force of the first drive device 630 to the effect member 620, and abut against the transmission member 640 for transmission A torsion spring 650 for generating an urging force for moving the member 640 and a second drive device 660 for generating a driving force for opening and closing the first curtain member 624 and the second curtain member 625 of the effect member 620 are mainly provided. .

  The base member 610 has a main body portion 611 which is fixed to the slide rail 730 and is formed in a vertically long plate shape, and a shaft support portion of a connecting member 740 which protrudes in a cylindrical shape from the front side of the main body portion 611. A pivotally supporting projection 612 on which the shaft 741a is pivotally supported, and a circular hole bored in the front-rear direction vertically above the pivotally supporting projection 612, the pivotal shaft 626 of the effect member 620 is pivotally pivotally supported. A first shaft support hole 613 and a circular hole drilled in the front-rear direction vertically above the first shaft support hole 613, and the cylindrical portion 642 of the transmission member 640 is pivotally supported. An insertion hole through which the drive shaft of the first drive device 630 is inserted, the biaxial support hole 614, the auxiliary member 615 formed on the rear surface of the main body 611 and slidably inserted into the slide hole 724 of the support member 720 616 and the lower end of the main body 611 A hook-shaped hook portion 617 that extends toward the side, mainly comprising.

  The second axial support hole 614 includes a lower receiving plate portion 614a projecting in a circular arc shape in cross section from the lower edge to the front side. The rotation of the cylindrical portion 642 of the transmission member 640 is guided by the lower receiving plate portion 614a. The lower support plate portion 614a is formed to have a left-right width substantially equal to the outer diameter of the cylindrical portion 642 (see FIG. 53A).

  By inserting the auxiliary member 615 into the slide hole 724, the inclination of the base member 610 in the left-right direction can be suppressed, so that the base member 610 can be slid smoothly in the vertical direction.

  The flange portion 617 is a portion to which one end of the coil spring 728 is hung and a biasing force is loaded.

  The effect member 620 and the second drive device 660 will be described with reference to FIG. FIG. 52 is a front exploded perspective view of the effect member 620 and the second drive device 660. As shown in FIG. The liquid crystal device disposed inside the effect member 620 is illustrated by an imaginary line, and FIGS. 50 and 51 are appropriately referred to for the description of the effect member 620 and the second drive device 660.

  The effect member 620 is a box-like member in which the liquid crystal device is disposed, and the main body member 621 having a rectangular plate shape and the main body member 621 are extended forward from above and below to cover the main body member 621 Upper and lower cover members 622 which can be bent, and left and right cover members 623 which are plate-like members attached from both sides of the upper and lower cover members 622 and which form a rectangular box shape opened forward with the upper and lower cover members 622; The first curtain member 624 which is a member for opening and closing the opening and connected and moved to the fitting hole 665a of the second drive device 660, and the member which opens and closes the front opening together with the first curtain member 624. A second curtain member 625 moved by being pulled by the curtain member 624, and a cylindrical swing shaft portion 626 protruding from the lower portion of the back surface of the main body member 621; Mainly it includes center of gravity G (see FIG. 53) is formed above (higher position) than the pivot shaft portion 626. The center of gravity G is formed on a straight line passing through the slide shaft 621a and the swing shaft 626 (see FIG. 53) in the inverted state (see FIG. 53).

  The main body member 621 includes a columnar sliding shaft 621 a (see FIG. 51) which protrudes on the back side vertically above the swinging shaft 626. The sliding shaft portion 621a is slidably inserted into the sliding hole 643 of the transmission member 640 (see FIG. 51).

  The upper and lower cover members 622 are members that accommodate 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 opened by the driving force of the drive device 660. .

  The left and right cover member 623 is provided with a slide groove 623a formed in a groove shape on the inner side surface and in which the slide projection 625c of the second curtain member 625 can slide.

  The slide groove 623a is connected to a curved groove formed in an arc at upper and lower ends of a linear groove extending vertically. As a result, the second curtain member 625 slides in a manner such that linear movement and curvilinear movement sequentially occur along the shape of the slide groove 623a.

  The first curtain member 624 is a member pivoted up and down around the opening and closing shaft 664 of the second drive device 660, and a main body 624a having a shape in which a plate material is bent into a C-shaped cross section, and its main body A fitting portion 624b which protrudes in the left-right direction from an end portion of the 624a and is fitted to the fitting hole 665a of the second drive device 660 so as to be relatively non-rotatable, and one end portion is a main portion near the fitting portion 624b And 624 a pivotally pivotally supported at the other end of the second curtain member 625.

  The second curtain member 625 is a member which is pulled by the first curtain member 624 and moved in the vertical direction, and has a main body 625a formed in a plate shape having a C-shaped cross section and a C shaped cross-section of the main body 624a. A connection protrusion 625b which protrudes in the left and right direction from the end and is connected to the other end of the connection member 624c, and a slide groove of the left and right cover member 623 which protrudes outward in the left and right direction And a slide protrusion 625c that is inserted into the 623a.

  In the second drive device 660, a drive motor 661 fastened and fixed to the back side of the effect member 620, a drive gear 662 pivotally supported by the drive motor 661, and one gear engaged with the drive gear 662 An open / close shaft rotatably supported on the front side of the main body member 621 of the effect member 620 by a pair of transmission gears 663 rotated in opposite directions and a non-illustrated shaft support mechanism. A transmission member 665, which is fixed to both ends of the pair of opening and closing shafts 664 so as to be relatively non-rotatable, is mainly provided.

  The transmission member 665 includes a fitting hole 665a in which the fitting portion 624b of the first curtain member 624 is non-rotatably fitted. Thus, the first curtain member 624 is swung up and down with the open / close shaft 664 as an axis.

  Referring back to FIGS. 50 and 51, description will be made. The first drive device 630 includes a drive motor 631 in which a drive shaft is inserted into the insertion hole 616 of the base member 610 and fastened and fixed to the base member, and a worm gear 632 in a screw gear shape fixed to the drive shaft of the drive motor 631. , A worm wheel 633 in the form of a helical gear meshing with the worm 632.

  The worm 632 is formed by a double thread screw. In the present embodiment, since the number of teeth of the worm wheel 633 meshing with the worm 632 is approximately 20, the worm wheel 633 rotates once while the worm 632 rotates 10 times. Thereby, the rotation angle of the worm wheel 633 and the transmission member 640 can be significantly reduced when the drive motor 631 is operated at the minimum unit of control resolution.

  The worm wheel 633 has a locking projection 633 a protruding from the center of the rotation shaft and inserted into the second shaft support hole 614 of the base member 610 and locked relative to the cylindrical portion 643 of the transmission member 640 in a non-rotatable manner. Prepare. Transmission of driving force between the worm 632 and the worm wheel 633 is structurally limited to one direction from the worm 632 to the worm wheel 633 (when the worm wheel 633 is actively rotated, the force is the worm). It takes about 632). Thereby, when stopping the worm wheel 633, the load which the drive motor 631 receives can be reduced. Further, the worm wheel 633 and the transmission member 640 can be stopped in a state where the power of the drive motor 631 is cut off, and the power consumption of the drive motor 631 can be suppressed.

  The transmission member 640 and the torsion spring 650 will be described with reference to FIG. 53 (a) and 53 (b) are front views of the transmission member 640 and the torsion spring 650. FIG. In FIGS. 53 (a) and 53 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines, and for the explanation of the transmission member 640 and the torsion spring 650, refer to FIGS. Do. Further, FIG. 53 (a) shows 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 corresponds to that of the transmission member 640. Balanced in the swing direction. 53B, the transmission member 640 is pivoted by a predetermined amount in a counterclockwise direction in a front view from the upright state of FIG. 53A, and the effect member 620 is pivoted by a predetermined amount.

  The transmission member 640 is a member that is swung by the rotation of the worm wheel 633 (see FIG. 50), and has a main body portion 641 formed in the shape of a long rectangular bar, and one end of the main body portion 641 Of the cylindrical portion 642 extending in the direction to which the locking projection 633a of the first drive device 630 is engaged and a length extending in the axial diameter direction of the cylindrical portion 642 at the other end of the main body 641 A sliding hole 643 drilled as a hole, an abutting portion 644 spaced apart on both sides in the swing direction of the main body 641, and a connection between the abutting portion 644 and the front side of the main body 641 An arc-shaped front arc plate portion 645 having a width which is wide and an arc-shaped back arc plate portion 646 which connects the contact portion 644 and the rear side surface of the main portion 641 are mainly provided.

  As shown in FIG. 53, the contact portion 644, the front arc plate portion 645 and the back arc plate portion 646 are disposed in a manner to surround the biasing arm portion 652 of the torsion spring 650. This can prevent the torsion spring 650 from falling off (disengaging) from the transmission member 640.

  The cylindrical portion 642 is pivotally supported by the second axial support hole 614 (see FIG. 50) of the base member 610, and is locked relative to the locking projection 633a (see FIG. 50) of the first drive device 630 so as not to rotate relative thereto. Ru.

  The slide shaft portion 621 a of the effect member 620 is inserted through the slide hole 643. Thus, when the transmission member 640 is swung around the second shaft support hole 614 (see FIG. 50) by the driving force of the first drive device 630 (see FIG. 50), the sliding shaft 621a of the effect member 620. Is slid on the slide hole 643 (slidingly moved in the axial radial direction), the effect member 620 is swung about the first shaft support hole 613.

  By swinging the effect member 620 in this manner, it is possible to suppress the swing angle of the effect member 620 in the case where the drive motor 631 is rotated by the minimum unit of resolution of control of the drive device. For example, as a method of swinging the effect member 620, a method of directly connecting a gear to the swing shaft portion 626 of the effect member 620 and transmitting the driving force of the drive motor to the gear can be considered. However, in this case, the drive motor is shown at an angle P0 of the smallest unit of control resolution (see FIG. 53 (a), and the angle is illustrated several times larger than the actual angle P0 to facilitate understanding. The moving amount X1 by which the center of gravity of the effect member 620 is shifted in the left-right direction from the inverted state increases as the center of gravity of the effect member 620 moves away from the swing shaft portion 626. Therefore, as the center of gravity of the effect member 620 separates from the swinging shaft portion 626, it becomes more difficult to adjust the position of the center of gravity of the effect member 620, and the center of gravity of the effect member 620 is inverted. It becomes difficult to stop the effect member 620 in the state.

  On the other hand, in the present embodiment, the transmission member 640 for transmitting the driving force of the drive motor 631 to the effect member 620 is connected to the sliding shaft 621 a of the effect member 620. The length from the slide shaft portion 621a to the cylindrical portion 642 which is the swing shaft of the transmission member 640 is the length from the slide shaft portion 621a to the swing shaft portion 626 which is the swing shaft of the effect member 620. It is formed short compared to.

  Therefore, even when the effect member 620 is long in the radial direction of the rocking shaft portion 626, the angle P0 of the minimum unit of resolution of control of the drive device (see FIG. 53 (a), to facilitate understanding) In order to do this, it is possible to suppress the movement amount X2 of the center of gravity of the effect member 620 when operating the drive device at an angle several times larger than the actual angle P0. Therefore, it is possible to make it easy to stop the movable member in an inverted state in which the center of gravity of the movable member is disposed directly above the first axis.

  Further, as a method of swinging the effect member 620, gear teeth are formed on the arc centered on the swing shaft portion 626 in the effect member 620, and the gear meshed with the gear teeth is rotated by the drive motor. A method of swinging the effect member 620 can be considered. However, in this case, as the swing range of the effect member 620 increases, the range in which the gear teeth on the arc are formed needs to be larger in the left-right direction of the effect member 620. Therefore, in the case where the effect member 620 is formed in a thin shape in the swing direction, the gear teeth on the arc protrude from the effect member 620, which hinders the effect. Therefore, the design freedom of the effect member 620 is reduced.

  On the other hand, in the present embodiment, the transmission member 640 for transmitting the driving force of the drive motor 631 to the effect member 620 has a swing shaft portion 626 where the cylindrical portion 642 which is a swing shaft is a swing shaft of the effect member 620. And the swing shaft portion 621 a at the center in the left-right direction of the effect member 620. Since the effect member 620 swings following the transfer member 640, the formation range of the transfer member 640 with respect to the swing range of the effect member 620 can be suppressed near the center in the left-right direction of the effect member 620. As a result, even if the effect member 620 is thin in the left-right direction, the transfer member 640 can be prevented from protruding from the effect member 620, and the design freedom of the effect member 620 can be improved.

  The lower surface of the slide shaft portion 621 a of the effect member 620 is in contact with the inner circumferential surface of the slide hole 643 of the transmission member 640. As a result, the weight of the effect member 620 is loaded not only to the swinging shaft portion 626 but also to the transfer member 640. That is, a force opposing the weight of the effect member 620 can be generated not only from the swinging shaft portion 626 but also from the cylindrical portion 642 of the transmission member 640. Therefore, the effect member 640 can be supported at two points of the rocking shaft portion 626 and the cylindrical portion 642, and the radial force applied to the rocking shaft portion 626 and the cylindrical portion 642 can be suppressed. .

  Here, since the effect member 620 is in the normal state in the inverted state shown in FIG. 53A, it can be quickly returned to the inverted state after the transmission member 640 is rocked and rocked from the inverted state by a predetermined amount. Is desirable.

  In the present embodiment, as shown in FIG. 53 (b), when the transmission member 640 is swung from the state shown in FIG. Is rocked at a rocking angle φ2 (φ2 <φ1).

  That is, the swing angle of the effect member 620 is smaller than the swing angle of the transmission member 640 which is swung by the driving force of the first drive device 630 (see FIG. 50). Therefore, the effect member 620 can be easily returned to the inverted state (see FIG. 53A).

  Further, in the present embodiment, the sliding hole 643 having a long hole shape is formed in the axial diameter direction of the transmission member 640, and the sliding shaft portion 621a of the effect member 620 is inserted into the sliding hole 643. The transmission axis of the transmission member 640 is different from that of the effect member 620, and the sliding radius of the transmission hole 640 of the transmission member 640 is shorter than that of the slide shaft portion 621a of the effect member 620. The sliding shaft portion 621 a moves further away from the rocking shaft of the transmission member 640 as Therefore, a state in which the arm length R1 from the sliding shaft 621a of the effect member 620 to the cylindrical portion 642 of the transmission member 640 in the inverted state (see FIG. 53A) is swung a predetermined amount from the inverted state ( As compared with the arm length R2 from the sliding shaft portion 621a of the effect member 620 to the cylindrical portion 642 of the transmission member 640 in FIG. 54 (b)).

  That is, the arm length of the transfer member 640 is shortened as it approaches the inverted state, and the swing length of the effect member 620 when the transfer member 640 is swung by a predetermined angle is constant in arm length of the transfer member 640. Compared to the case, it can be made smaller as it approaches an inverted state. Therefore, the operating speed of the effect member 620 is increased near the predetermined stop position without changing the rotational speed of the drive motor 631 while the operating speed of the effect member 620 is decreased near the inverted state, and the effect member 620 is inverted. It can be made easy to stand still in a state (It can be made easy to stop control the effect member 620 in a state where the center of gravity of the effect member 620 is disposed vertically above the first axial support hole 613).

  Referring to FIG. 55, swing of effect member 620 with respect to the swing angle of transfer member 640 by changing the arm length from sliding shaft portion 621a of effect member 620 to cylindrical portion 642 of transfer member 640. The change in angle will be described.

  FIG. 55 is a schematic view schematically showing the swing angle of the effect member 620 (see FIG. 53A) with respect to the swing angle of the transmission member 640 (see FIG. 53A). In FIG. 55, a cylindrical portion 642 whose rotation axis M1 corresponds to the swinging shaft portion 626 (see FIG. 53A) which is the rotation shaft of the effect member 620 and whose rotation axis M2 is the swinging shaft of the transmission member 640. This corresponds to (see FIG. 53 (a)). The straight lines a1 to a4 schematically represent the arrangement of the transmission member 640, and are straight lines drawn radially from the rotation axis M2, and the straight line a1 passes through the rotation axis M1 and the straight lines a2 to a4 are straight lines a1 and Are formed sequentially in increments of 15 degrees. That is, the angles formed by the straight lines a1 to a4 adjacent to each other are 15 degrees each.

  An arc drawn with a radius equal to the arm length R1 (see FIG. 53 (a)) around the rotation axis M2 is illustrated by an arc SR1, and an arm length R2 around the rotation axis M2 (see FIG. 54 (b)) An arc drawn with a radius equal to is illustrated by an arc SR2. The arc SR0 is an arc drawn around the rotation axis M1, and is an arc of a radius of a length obtained by adding the distance between the rotation axis M1 and the rotation axis M2 to the arm length R1.

  These arcs assume the locus of the connection position between the effect member 620 and the transfer member 640 (see FIG. 53A). In the present embodiment, a sliding shaft 621a (see FIG. 53A) as a connecting position is provided so as to protrude from the effect member 620, and the connecting position of the effect member 620 and the transfer member 640 moves along the arc SR0. . When the connecting position between the effect member 620 and the transfer member 640 moves along the arc SR1 or the arc SR2, a long elongated hole is formed in the axial diameter direction in the effect member 620, and from the transfer member 640 It is assumed that the shaft inserted into the long hole is provided in a protruding manner.

  Further, as shown in FIG. 55, an intersection point of the straight line a1 and the arc SR0 is illustrated by an intersection point P10, an intersection point of the straight line a1 and the arc SR1 is illustrated by an intersection point P11, and an intersection point of the straight line a1 and the arc SR2 is illustrated as an intersection point P12. It is illustrated by.

  Similarly, an intersection point of the straight line a2 and the arc SR0 is illustrated by an intersection point P20, an intersection point of the straight line a2 and the arc SR1 is illustrated by an intersection point P21, and an intersection point of the straight line a2 and the arc SR2 is illustrated by an intersection point P22. An intersection point of the straight line a3 and the arc SR0 is illustrated by an intersection point P30, an intersection point of the straight line a3 and the arc SR1 is illustrated by an intersection point P31, and an intersection point of the straight line a3 and the arc SR2 is illustrated by an intersection point P32. An intersection point of the straight line a4 and the arc SR0 is illustrated by an intersection point P40, an intersection point of the straight line a4 and the arc SR1 is illustrated by an intersection point P41, and an intersection point of the straight line a4 and the arc SR2 is illustrated by an intersection point P42. The intersection point P10 and the intersection point P11 are disposed at the same position, and the intersection point P40 and the intersection point P42 are disposed at the same position.

  Further, as shown in FIG. 55, an angle formed by a straight line passing through the rotation axis M1 and the intersection point P10 and a straight line passing through the rotation axis M1 and the intersection point P20 is illustrated by an angle A10, and a straight line passing through the rotation axis M1 and the intersection point P11 The angle formed by the rotation axis M1 and the straight line passing through the intersection point P21 is illustrated by an angle A11, and the angle formed by the straight line passing through the rotation axis M1 and the intersection point P12 and a straight line passing through the rotation axis M1 and the intersection point P22 is illustrated by an angle A12. Be done.

  Similarly, an angle formed by a straight line passing through the rotation axis M1 and the intersection point P20 and a straight line passing through the rotation axis M1 and the intersection point P30 is illustrated by an angle A20, and a straight line passing through the rotation axis M1 and the intersection point P21 and the rotation axis M1 and the intersection point P31. The angle formed by the straight line passing through is indicated by an angle A21, and the angle formed by the straight line passing through the rotation axis M1 and the intersection point P22 and the straight line passing through the rotation axis M1 and the intersection point P32 is illustrated by an angle A22. An angle formed by a straight line passing through the rotation axis M1 and the intersection point P30 and a straight line passing through the rotation axis M1 and the intersection point P40 is illustrated by an angle A30, and a straight line passing through the rotation axis M1 and the intersection point P31 and a straight line passing through the rotation axis M1 and the intersection point P41 The angle formed by A is illustrated by an angle A31, and the angle formed by a straight line passing through the rotation axis M1 and the intersection point P32 and a straight line passing through the rotation axis M1 and the intersection point P42 is illustrated by an angle A32. Note that these angles correspond to the swing angle of the effect member 620.

  Here, the ratio of (the distance between the rotation axis M1 and the rotation axis M2: arm length R1: arm length R2) is set to (1: 2.32: 2.54) in the present embodiment. When the angle is measured, the angle A32 is 11.07 degrees, the angle A31 is 10.77 degrees, and the angle A30 is 11.37 degrees. That is, in the case of swinging the transfer member 640 between the straight line a4 and the straight line a3, the swing angle of the effect member 640 is largest when the transfer member 640 and the effect member 620 are connected along the arc SR0. Thus, the transmission member 640 and the effect member 620 are formed along the arc SR2 to be connected (the angle A30 is closer to the angle A32 than the angle A31).

  The angle A22 is 10.87 degrees, the angle A21 is 10.59 degrees, and the angle A20 is 10.82 degrees. That is, in the case of swinging the transmission member 640 between the straight line a3 and the straight line a2, the swing angle in the case where the transmission member 640 and the effect member 620 are connected along the arc SR0 is along the arc SR2. It falls below the case where the transmission member 640 and the effect member 620 are connected. In this case, the difference between the angle A22 and the angle A20 is smaller than the difference between the angle A20 and the angle A21 (the angle A20 is closer to the angle A22 than the angle A21).

  The angle A12 is 10.78 degrees, the angle A11 is 10.50 degrees, and the angle A10 is 10.53 degrees. That is, in the case of swinging the transmission member 640 between the straight line a2 and the straight line a1, the swing angle when the transmission member 640 and the effect member 620 are connected along the arc SR0 is along the arc SR1. The case where the transmission member 640 and the effect member 620 are connected is exceeded. In this case, the difference between the angle A12 and the angle A10 is larger than the difference between the angle A10 and the angle A11 (the angle A10 is closer to the angle A11 than the angle A12).

  From these, by making the locus of the connection position of the transfer member 640 and the effect member 620 (see FIG. 53A) as the arc SR0, for example, when the transfer member 640 is swung at a constant speed, the effect member It can be seen that the freedom of adjustment of the angular velocity 620 can be improved. That is, when the transmission member 640 is disposed on the straight line a4, the locus of the connection position between the transmission member 640 and the rendering member 620 is closer to the angular velocity (high speed side) in the case of the arc SR2, and the transmission member 640 is The angular velocity at the time of arrangement can be made closer to the angular velocity (low speed side) in the case of the arc SR1 when the locus of the connection position between the transfer member 640 and the effect member 620 is circular.

  In addition, when the ratio of the respective angles is calculated, the angle A22 / the angle A32 is 0.98, and the angle A12 / the angle A22 is 0.99. The angle A21 / angle A31 is 0.98, and the angle A11 / angle A21 is 0.99. That is, when the locus of the connection position between the transfer member 640 and the effect member 620 (see FIG. 53A) is the arcs SR1 and SR2, the transfer member 640 is swung toward the inverted state at constant speed. The deceleration ratio of the angular velocity of the effect member 620 in the case is as small as 1 to 2%.

  On the other hand, the angle A20 / angle A30 is 0.95, and the angle A10 / angle A20 is 0.97. That is, when the locus of the connecting position of the transfer member 640 and the effect member 620 (see FIG. 53A) is the arc SR0 (the arc centered on the rotation axis M1), the transfer member 640 is inverted at a constant speed. The deceleration ratio of the angular velocity of the effect member 620 when it is swung toward the state can be set to 3 to 5%. That is, the deceleration ratio of the angular velocity of the effect member 620 can be increased as compared with the case where the locus of the connecting position is the arcs SR1 and SR2 (the arc centering on the rotation axis M2).

  As shown in FIG. 53A, the slide shaft portion 621a of the effect member 620 is in contact with the lower end portion of the slide hole 643 of the transmission member 640 in the inverted state. In the inverted state, the center of gravity G of the effect member 620 is formed vertically above the rocking shaft portion 626 of the effect member 620 and the cylindrical portion 642 of the transmission member 640. The portion 626 and the cylindrical portion 642 are vertically lowered. Therefore, the force of the component in the direction of swinging the effect member 620 is not generated due to the gravity of the effect member 620, so that the attitude of the effect member 620 is maintained in the inverted state even if the power of the first drive device 630 is shut off. Can. Thereby, durability improvement of the 1st drive device 630 can be aimed at.

  In addition, since the force due to the gravity G of the effect member 620 is applied vertically downward to the swing shaft portion 626 and the cylindrical portion 642, the rotational resistance of the swing shaft portion 626 and the cylindrical portion 642 can be increased. The attitude of the effect member 620 can be easily maintained in the inverted state.

  The torsion spring 650 is an elastic spring in which a biasing force is generated in a direction to rewind the coil portion 651 (direction to push back the transmission member 640) as the transmission member 640 swings. A coil portion 651 wound around the periphery, a biasing arm portion 652 extending along both swing direction side surfaces of the main body portion 641 of the transmission member 640, an end portion of the coil portion 651 and an end of the biasing arm portion 652 And a connecting arm 653 that connects the parts through between the cylindrical portion 642 and the swinging shaft portion 626.

  The coil portion 651 is formed to have an inner diameter that is about three times the diameter of the swinging shaft portion 626 of the effect member 620. Therefore, when the biasing arm portion 652 is swung to generate a load that causes the coil portion 651 to reduce its diameter, a deformation amount of the coil portion 651 can be secured, and the biasing arm portion 652 or the connecting arm portion 653 is deformed. Concentration can be suppressed.

  The biasing arm portion 652 is surrounded by the main body portion 641 of the transmission member 640, the contact portion 644, the front arc plate portion 645, and the back arc plate portion 646. Thus, the biasing arm 652 can be prevented from coming off (disengaging) from the transmission member 640.

  Further, the biasing arm portion 652 is formed to be able to abut on the lower receiving plate portion 614 a on the swinging plane of the transmission member 640. Therefore, a biasing force for pushing back the transmission member 640 is generated from the biasing arm portion 652 disposed in the pivoting direction of the transmission member 640, and the biasing arm portion disposed on the opposite side of the pivoting direction of the transmission member 640 The reference numeral 652 is prevented from moving to the lower support plate portion 614a. Thus, the torsion spring 650 is formed to be capable of generating a biasing force in the direction of pushing back the transmission member 640 regardless of the swing direction of the transmission member 640.

  A bending portion 653a is formed at the connecting portion of the biasing arm 652 and the connecting arm 653 to be bent to the opposite side of the transmission member 640. In this case, as the contact portion 644 of the transmission member 640 is pressed against the bending portion 653a of the torsion spring 650 as described later, the bending portion 653a is expanded (see FIG. 54 (b)). As a result, the contact position between the biasing arm 652 of the torsion spring 650 and the main body 641 of the transmission member 640 is far from the cylindrical portion 642 and the moment applied from the torsion spring 650 to the transmission member 640 is increased. Can.

  With reference to FIG. 54, a change in biasing force generated from the torsion spring 650 and pushing back the transmission member 640 will be described. 54 (a) and 54 (b) are front views of the transmission member 640 and the torsion spring 650. FIG. In FIGS. 54 (a) and 54 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines, and FIG. 53 is appropriately used to explain the change of the biasing force generated from the torsion spring 650. refer.

  Further, in FIG. 54 (a), from the state of FIG. 53 (b), the transmission member 640 is further rotated counterclockwise in front view, and the biasing arm 652 on the left in front view is the contact portion 644 of the transmission member 640. The state where it begins to be pressed against the inner surface is illustrated, and in FIG. 54 (b), the transmission member 640 is further rotated counterclockwise in a front view from the state of FIG. 54 (a), and the bending portion 653a of the torsion spring 650 is pulled. The extended state is illustrated.

  In the state shown in FIG. 54 (a), a biasing force that pushes the transmission member 640 back is generated on the biasing arm 652 on the left side of the torsion spring 650 in a front view. The biasing force is the sum of the biasing force generated starting from the coil portion 651 and the biasing force generated starting from the bending portion 653a.

  That is, in the state of FIG. 53 (b), since the transmission member 640 is not pressed against the bending portion 653a disposed on the left in front view among the pair of bending portions 653a, the biasing arm on the left side of the torsion spring 650 in front view In the portion 652, only a biasing force originating from the coil portion 651 is generated as a biasing force for pushing back the transmission member 640.

  On the other hand, in the state of FIG. 54 (a), in addition to the biasing force starting from the coil portion 651, the biasing force is generated by the deformation of the biasing arm portion 652 starting from the bending portion 653a. Therefore, the spring constant of the biasing arm 652 can be increased. The deformation of the biasing arm 652 starting from the bending portion 653 a is shorter in length than the deformation starting from the coil 651, so the unit deformation amount of the transmission member 640 It is possible to make the biasing force generated at the hit greater.

  In the state of FIG. 54B, the bending portion 653a of the torsion spring 650 is pushed by the contact portion 644 of the transmission member 640, whereby the angle formed by the biasing arm 652 and the connecting arm 653 is widened. Thus, in the state of FIG. 54 (a), the contact position length L1, which is the distance between the contact position of the main body 641 of the transmission member 640 and the biasing arm 652 of the torsion spring 650 and the cylindrical portion 642. 54B, the same contact position length L2 in the state of FIG. 54 (b) is separated from the cylindrical portion 642 of the transmission member 640. That is, the contact position length is extended. As a result, since the arm length of the torsion spring 650 for pushing back the transmission member 640 is increased, the moment applied from the torsion spring 650 to the transmission member 640 can be increased.

  Therefore, for example, when the biasing force generated by the torsion spring 650 is substantially equal between the state of FIG. 54 (a) and the state of FIG. 54 (b), more load is applied to the transmission member 640 in FIG. 54 (b). Can be increased. Therefore, the transmission member 640 and the effect member 620 can be more easily pushed back.

  As shown in FIG. 53 and FIG. 54, the biasing force of the torsion spring 650 for pushing back the transmission member 640 is small within a small swing angle from the retracted position of the transfer member 640 (effect member 620), and the swing angle is large. The degree is increased elastically, and is increased more than the amount of elastic increase bordering on the state of FIG. 54 (a). Therefore, when the biasing force of the torsion spring 650 necessary when the effect member 620 is set to the maximum swing angle (see FIG. 54B) is determined, the torsion spring performs only an elastic increase. In the case where the swing angle is small, the biasing force can be set smaller (the soft spring can be used).

  Thereby, it is possible to reduce the degree to which the operation speed at the start of swinging of the effect member 620 is decelerated by the biasing force of the torsion spring 650, and the operation speed at the start of operation of the effect member 620 can be increased. .

  Further, since the biasing force is increased by an elastic increase or more at the boundary of the state of FIG. 54 (a), the swing angle of the effect member 620 is set to the state of FIG. 54 (a) or more, The decelerating acceleration of the effect member 620 can be increased. Thereby, between the swinging operations of the effect member 620, the timing at which the effect member 620 starts to be decelerated can be delayed. Therefore, the swing angle at which the effect member 620 can be swung at high speed can be enlarged, and the effect of the tilting operation unit 600 can be improved.

  Next, with reference to FIG. 56, the sliding operation of the tilting operation unit 600 and the sliding operation unit 700 will be described. FIG. 56 is a front view of the tilting operation unit 600 and the sliding operation unit 700. In FIG. 56, a state in which the tilting operation unit 600 is disposed at the retracted position is illustrated by an imaginary line, and a state in which the tilting operation unit 600 is slid by a predetermined amount from the retracted position is illustrated by a solid line.

  As shown in FIG. 56, a connecting member 740 for connecting the tilt operation unit 600 slidably formed in the vertical direction and the slide operation unit 700 is formed so as to be movable in the extending direction of the front rail portion 715. . Here, since the weight of the tilting operation unit 600 is loaded on the connecting member 740, when the tilting operation unit 600 is disposed at the retracted position, the tilting operation unit 600 is gravity-followed along the front rail portion 715 by gravity. It is biased toward you. Therefore, in order to maintain the tilting operation unit 600 in the retracted position, it is conceivable to fix the drive device 750.

  On the other hand, in the present embodiment, the lever member 714 is formed so as to be vertically swingable, and when the lever member 714 is swung downward, the lever member 714 engages with the locking portion 725 of the support member 720. The sliding movement in the direction is restricted.

  As a result, since the tilting operation unit 600 can be mechanically maintained at the retracted position, the tilting operation unit 600 is stopped in a state where the drive device 750 is stopped when the tilting operation unit 600 is disposed at the retracted position. It can be maintained at the retracted position. Therefore, the durability of the drive device 750 can be improved.

  In the state where the tilting operation unit 600 is disposed at the retracted position, the support member 720 can be moved by swinging the lever member 714 upward and operating the driving device 750, and the tilting operation unit 600 can be moved in the left-right direction. You can slide it.

  As shown in FIG. 56, when the tilting operation unit 600 is disposed at the retracted position in the inverted state, the pivot portion 741a of the connecting member 740 is disposed vertically below the center of gravity G of the tilting operation unit 600.

  Here, since the direction of sliding movement of the tilting operation unit 600 is along the front rail portion 715, in FIG. 56, movement of the tilting operation unit 600 is performed while being slid by a predetermined amount from the retracted position (see phantom line in FIG. 56). Has a vertical component at all times.

  Therefore, if the center of gravity G of the tilting operation unit 600 and the shaft support portion 741a of the connecting member 740 deviate in the vertical direction, a load may be applied from the connecting member 740 in the direction to rotate the tilting operation unit 600. The same applies to the case where the tilting operation unit 600 is slid in the reverse direction.

  On the other hand, in the present embodiment, since the pivot portion 741a of the connection member 740 is disposed vertically below the center of gravity G, the vertical component of the force applied to the tilting operation unit 600 from the connection member 740 and the center of gravity G are It is formed on the same line. As a result, the application of a load from the connecting member 740 in the direction to rotate the tilting operation unit 600 can be suppressed, and the posture of the tilting operation unit 600 can be stabilized.

  Next, referring to FIG. 57, the influence of the tilting operation (swinging operation) of the tilting operation unit 600 on the slide operation of the slide operation unit 700 will be described. FIG. 57 is a front view of the tilting operation unit 600 and the slide operation unit 700. FIG. In FIG. 57, a state in which the effect member 620 of the tilting operation unit 600 is swung to the state of FIG. 54 (b) is illustrated.

  As shown in FIG. 57, when the effect member 620 is swung in a counterclockwise direction as viewed from the front, the center of gravity G of the effect member 620 is disposed to the left of the connecting member 740 in a front view. Therefore, the acceleration in the front view leftward applied to the connecting member 740 is increased.

  In this case, the driving force necessary to slide the tilting operation unit 600 from the retracted position can be suppressed, so the drive motor 751 of the driving device 750 can be miniaturized.

  Next, with reference to FIGS. 58 and 59, the tilting operation unit 2600 in the second embodiment will be described.

  In the first embodiment, the case where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 is flat has been described. However, the tilting operation unit 2600 in the second embodiment includes the main body of the transmission member 2640. Reference numeral 2641 includes an abutting portion 2641 a that is in contact with the tip of the biasing arm 652 of the torsion spring 650. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  58 (a), 58 (b) and 59 are front views of the transmission member 2640 and the torsion spring 650 in the second embodiment. In FIGS. 58 (a), 58 (b) and 59, the outlines of the base member 610 and the effect member 620 are shown by imaginary lines. Further, FIG. 58 (a) shows an inverted state in which the slide hole 643 of the transmission member 2640 is disposed vertically above the cylindrical portion 642, and FIG. 58 (b) shows the inverted state of FIG. 58 (a). The transmission member 2640 is swayed by a predetermined amount counterclockwise in a front view from the front, and the state in which the lower surface of the abutment portion 2641a is in contact with the tip of the biasing arm 652 of the torsion spring 650 is shown in FIG. A state in which the transmission member 2640 is further pivoted counterclockwise in a front view from the state of FIG. 58 (b) is illustrated.

  As shown in FIG. 58, when the transmission member 2640 is swung from the upside-down state (see FIG. 58A), the main body 2641 is pressed against the biasing arm 652 of the torsion spring 650, and the main body 2641 is The torsion spring 650 generates a biasing force that causes it to swing in the direction to return to the inverted state. When the transmission member 2640 is swung and the biasing arm 652 is deformed, the coil portion 651 is reduced in diameter by the connecting arm 653 connected to the biasing arm 652 on the deformed side. That is, as the diameter of the coil portion 651 is reduced, the urging force for swinging the transmission member 2640 in the direction of returning to the inverted state is increased.

  Further, as shown in FIG. 58, the contact position between the main body portion 2641 of the transmission member 2640 and the biasing arm portion 652 (the difference between the swing angles of the biasing arm portion 652 of the torsion spring 650 and the transmission member 2640) The tip end position of the biasing arm 652 is changed by the swing of the transmission member 2640. That is, as the transmission member 2640 is swung, the tip end portion of the biasing arm portion 652 is moved to the tip end side of the main body portion 2641 (the side approaching the sliding hole 643).

  Therefore, as shown in FIG. 58B, when the transmission member 2640 is further rotated counterclockwise in a front view in a state where the lower surface of the abutment portion 2641a is in contact with the tip end portion of the biasing arm portion 642. The biasing arm portion 642 is restricted by the abutment portion 2641 a from moving to the tip end side of the main body portion 2641.

  As shown in FIG. 59, when the transfer member 2640 is swung in a state in which the transfer arm portion 642 is restricted in movement by the abutment portion 2641a, the torsion spring 650 is deformed as a whole. That is, since the movement of the biasing arm 642 to the tip end side of the main body 2641 is restricted, the base side (the bending portion 653a side) of the biasing arm 642 is moved downward. Thus, the connecting arm 653 is moved in the direction of reducing the diameter of the coil portion 651 (the direction in which the biasing force of the torsion spring 650 is increased).

  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 as compared to the case where the abutting portion 2641a is not provided. Thereby, the degree of change in the urging force generated by the torsion spring 650 (the increase ratio of the urging force to the swing angle of the transmission member 2640) is increased in the state shown in FIG. 59 as compared to the state shown in FIG. Can. Therefore, when the swing angle of the transmission member 2640 is small, the biasing force of the torsion spring 650 is suppressed to increase the start speed of the transfer member 2640, and when the swing angle is large (see FIG. 59), It is possible to increase the biasing force of the torsion spring 650 nonlinearly (more than elastic change) and to obtain a biasing force sufficient to return the transmission member 2640 to the inverted state.

  Next, with reference to FIG. 60, a tilting operation unit 3600 in the third embodiment will be described.

  In the first embodiment, the case where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 has a constant width has been described, but the tilting operation unit 3600 in the third embodiment is the main body of the transmission member 3640 3641 includes an inclined side surface 3641a which is inclined in such a manner as to be wider toward the distal end side on the side surface that is in contact with the distal end portion of the torsion spring 650. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  60 (a) and 60 (b) are front views of the transmission member 3640 and the torsion spring 650 in the third embodiment. In FIGS. 60 (a) and 60 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines. 60 (a) shows an inverted state in which the slide hole 643 of the transmission member 3640 is disposed vertically above the cylindrical portion 642, and FIG. 60 (b) shows the inverted state shown in FIG. 60 (a). The state in which the transmission member 3640 is swung a predetermined amount counterclockwise in a front view is illustrated.

  As shown in FIG. 60, when the transmission member 3640 is swung from the inverted state (see FIG. 60A), the main body portion 3641 is pressed against the biasing arm portion 652 of the torsion spring 650, and the main body portion 3641 is The torsion spring 650 generates a biasing force that causes it to swing in the direction to return to the inverted state.

  When the transmission member 3640 is swung from the state shown in FIG. 60 (a) to the state shown in FIG. 60 (b), 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 distal end portion of the biasing arm portion 652 is closer to the distal end side of the main body portion 3641 (the side closer to the sliding hole 643) as the swing angle from the upside-down state (see FIG. 60A) of the transmission member 3640 increases. Moved to).

  Therefore, the tip end of the biasing arm 652 slides along the inclined side surface 3641 a of the main body 3641. That is, in the torsion spring 650, when the transmission member 3640 is swung, in addition to the deformation caused by the swing angle of the transmission member 3640, the deformation due to the width of the transmission member 3640 being expanded by the inclined side surface 3641a occurs. . In this case, the width of the transfer member 3640 is further expanded toward the tip end portion of the transfer member 3640. Therefore, the larger the swing angle from the inverted state of the transfer member 3640 (see FIG. 60A) As a result, the deformation of the torsion spring 650 due to the width of the transmission member 3640 is enlarged. Therefore, as the swing angle of the transmission member 3640 increases, it is possible to increase the rate of increase in the biasing force generated by the torsion spring 650 (change in the biasing force of the torsion spring 650 with respect to the swing angle of the transfer member 3640).

  Next, with reference to FIG. 61 to FIG. 64, the tilting operation unit 4600 in the fourth embodiment will be described.

  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 operation unit 4600 in the fourth embodiment, the transmission member 4640 is in addition to the contact portion 644 and the contact thereof A moving abutment member 4647 shorter in width than the portion 644 is provided. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  61 (a) is a rear perspective view of the transmission member 4640 in the fourth embodiment, and FIG. 61 (b) is a rear perspective view of the movable contact member 4647. In FIG. 61A, the movable contact member 4647 is not shown.

  As shown in FIG. 61 (a), the front arc plate portion 4645 of the transmission member 4640 is provided with a guide hole 4645a disposed symmetrically in the left-right direction at intervals shorter than the disposition interval of the contact portions 644. Prepare. The guide hole 4645a is a through hole which guides the pair of rear projection portions 4647b of the movable contact member 4647 so as to be movable in the front-rear direction.

  As shown in FIG. 61 (b), the movable contact member 4647 has a main body 4647a formed in a long plate shape, and a pair of rear projections protruding from both end portions of the main body 4647a to the rear side. It mainly includes a portion 4647 b and a front projection 4647 c which is provided so as to project from the approximate center of the main portion 4647 to the front side in a tip hemispherical shape.

  One end of the coil spring 4648 is fixed to the opposite side of the front projection 4647c of the main body 4647a, and the other end of the coil spring 4648 is fixed to the main body 641b (FIG. 62 (c) and See FIG. 62 (d)). Also, in order to facilitate understanding, the illustration of the coil spring 4648 is omitted in FIGS. 61 (a), 61 (b), 62 (a) and 62 (b).

  The rear projection 4647 b is a portion inserted from the front side into the guide hole 4645 a of the transmission member 4640 and has a sufficient length from the front arc plate 4645 (when in contact with the biasing arm 652 of the torsion spring 650). The possible lengths are formed in such a way that they are pushed out. The back projection 4647 b is formed so as to be inclined at an angle (see FIG. 64 (b)) in contact with the biasing arm 652 of the torsion spring 650 at the surface (line). As a result, the load applied to the biasing arm 652 is reduced (stress concentration is suppressed) as compared with the case where the biasing arm 652 and the rear projection 4647 b are abutted at points. Durability can be improved.

  The front projection 4647c is a portion that is in contact with the main body member 4621 (see FIG. 63) of the effect member 4620, and from the relationship with the relief opening 4621a formed in the main body member 4621 The moving abutment member 4647 may be separated from the front arc plate portion 4645 (see FIG. 62C) or may be moved closer to the front arc plate portion 4645 (see FIG. 62D). In addition, since the tip of the front projection 4647c is formed in a hemispherical shape, the front projection 4647c can be easily run on the surface of the main body member 4621 from the escape opening 4621a.

  62 (a) and 62 (b) are rear perspective views of the transmission member 4640, and FIGS. 62 (c) and 62 (d) are top views of the transmission member 4640. In FIGS. 62 (a) and 62 (c), the movable contact member 4647 is separated from the front arc plate portion 4645 in FIGS. 62 (b) and 62 (d). The state in which 4647 approached front arc board part 4645 is illustrated respectively.

  FIG. 63 is a schematic front view schematically showing the main body member 4621 of the effect member 4620. Note that the transmission member 4640 forming an inverted state with respect to the main body member 4621 is the central state 4640C, and the transmission member 4640 is swayed counterclockwise as viewed from the front view as the counterclockwise rocking state 4640L. A state in which it is swung clockwise as viewed from the front is illustrated by an imaginary line as a clock swing state 4640R. In addition, in central state 4640C, counterclockwise rocking state 4640L and clock rocking state 4640R, illustration of contact portion 644, front arc plate 4645 and back arc plate 646 is omitted to facilitate understanding. .

  The main body member 4621 is provided with a relief opening 4621 a drilled in the front-rear direction. As shown in FIG. 63, the relief opening 4621a is a region (center state 4640C and counterclockwise) in which the front projection 4647c (see FIG. 62) moves when the transmission member 4640 is swung counterclockwise in a front view. Between the motion state 4640L and the motion state 4640L).

  When the front projection 4647c of the transmission member 4640 overlaps 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 transmitted by the elastic force of the coil spring 4648. The main body 641 is separated from the main body 641 (see FIG. 62 (c)). On the other hand, when the front projection 4647c does not overlap with the relief opening 4621a (overlaps with the main body member 4621), the front projection 4647c abuts on the back side of the main body 4621 of the effect member 4620, and the moving abutment member 4647 is brought close to the main body 641 of the transmission member 4640 (see FIG. 62D).

  That is, the rear projection 4647 b of the movable contact member 4647 is projected to a position where it can be in contact with the biasing arm 652 of the torsion spring 650 when the transmission member 4640 is swung clockwise as viewed from the upside. Be Therefore, the biasing arm portion 652 of the torsion spring 650 is generated when the transmission member 4640 is swung clockwise as viewed from the upside, as compared to when it is swung counterclockwise as viewed from the front. It is possible to increase the rate of increase of the urging force (the degree of increase of the urging force with respect to the swing angle).

  FIGS. 64 (a) and 64 (b) are front views of the transmission member 4640 and the torsion spring 650. FIG. In FIGS. 64 (a) and 64 (b), the outlines of the base member 610 and the effect member 4620 are shown by imaginary lines, and the main body 4647a of the movable contact member 4647 for easy understanding. Illustration is omitted. Further, FIG. 64 (a) shows an inverted state in which the slide hole 643 of the transmission member 4640 is disposed vertically above the cylindrical portion 642, and FIG. 64 (b) shows the inverted state of FIG. 64 (a). From the above, it is illustrated that the transmission member 4640 is swung clockwise by a predetermined amount in a front view, and the biasing arm 652 on the left in a front view is abutted against the rear projection 4647 b.

  As shown in FIG. 64 (b), while the swing angle of the transmission member 4640 is small, the biasing arm 652 can be contacted from the opposite side (abutment portion 644 side) of the main body 641 of the transmission member 4640. By doing this, it is possible to increase the biasing force generated by the torsion spring 650 when the transmission member 4640 is rotated clockwise in a front view.

  Thus, it is possible to improve the biasing force when the transmission member 4640 is swung clockwise as viewed from the front while the start speed when the transmission member 4640 is swung counterclockwise in front view is increased. Can. Therefore, collision of the effect member 4620 with the inner side surface of the rear case 210 can be suppressed.

  That is, in the state where the tilting operation unit 4600 is disposed at the retracted position, when the effect member 4620 is in the inverted state, the inner side surface of the back case 210 approaches the effect member 620 (see FIG. 5). Here, if the effect member 4620 is vigorously swung toward the upside-down state from the state of swinging counterclockwise in a front view (see FIG. 57), the effect member 4620 can not be decelerated, and the rear case 210 There is a risk that the effect member 4620 may collide with the inner surface of the lens.

  On the other hand, in the present embodiment, the rear projection 4647b is protruded at the timing when the effect member 4620 is swung clockwise in a front view from the upside state (see FIG. 62D). It can be increased. Thus, the directing member 4620 is sufficiently inclined in the clockwise direction when viewed from the upside state while maintaining the operation speed when the directing member 4620 is tilted in the counterclockwise direction when viewed from the upside position. Can be slowed down.

  In addition, the direction in which the rear projection 4647b is pushed back at the contact point between the rear projection 4647b arranged on the opposite side of the swing direction of the transmission member 4640 and the biasing arm 652 (FIG. 64 (b) Bias is generated. Thus, the transmitting member 4640 is pushed with a larger urging force than in the case where the transmitting member 4640 is pushed back only by the urging arm portion 652 disposed on the side approaching the transmission member 4640 (right side in FIG. 64B). You can push it back. On the other hand, it is possible to improve the biasing force generated by the biasing arm portion 652 disposed on the side closer to the transmission member 4640.

  That is, as shown in FIG. 64, the distance from the position at which the abutting portion 644 and the biasing arm portion 652 which are disposed on the opposite side to the side approaching the transmission member 4640 abuts on the lower receiving plate portion 614a. The distance from the lower support plate portion 614a to the bending portion 653a is shorter than the distance. In this case, it is easy to move the bending portion 653a by the force from the contact portion 644 with the lower receiving plate portion 614 as a fulcrum, but the opposite is difficult (the distance from the fulcrum to the action point is different Because there is).

  Therefore, the biasing force generated by the deformation of the biasing arm portion 652 in the front view left side generated by the abutment of the abutting portion 644 and the biasing arm portion 652 is generated by the deformation of the entire torsion spring 650. That is, when the biasing arm 652 on the left in the front view and the rear projection 4647b abut on each other, the bending portion 653a on the left in the front view with the lower receiving plate 641a as a fulcrum The deformation in the direction of narrowing causes deformation of the connection arm 653, the coil 651, and the biasing arm 652 in the right side in a front view. In this case, since the coil portion 651 is subjected to deformation to reduce the inner diameter, an urging force is generated on the coil portion 651 and the connecting arm portion 653 to increase the inner diameter of the coil portion 651. The biasing force of the biasing arm 652 on the side of the swing direction 4640 of the transmission member 640 can be improved.

  Next, a combined operation unit 5500 according to the fifth embodiment will be described with reference to FIGS. 65 to 68.

  In the first embodiment, when the pivoting arm member 550 is disposed at the overhanging position, the second non-transmission wall portion 553c has a shape along a circle centered on the rotation axis of the pivoting crank member 570. However, the pivoting arm member 5550 in the fifth embodiment includes the recessed portion 5556 in which the non-transmission wall portion 5553 c is recessed in the direction away from the pivoting crank member 570. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  65 to 68 are front views of a combined operation unit 5500 according to the fifth embodiment. Incidentally, in FIG. 65, the state in which the pivoting arm member 5550 is disposed at the extended position and the sliding projection 574 of the pivoting crank member 570 is disposed near the left end portion of the second non-transmission wall portion 5553c is shown in FIG. In the state shown in FIG. 65, the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 is accommodated in the first recessed portion 5556 from the left end of the second non-transmission wall 5553c. In FIG. 67, the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 66 to the position where the sliding projection 574 is disengaged from the recessed portion 5556. From the state, the state where the rotating crank member 570 is rotated counterclockwise in a front view and the sliding projection 574 is accommodated in the recessed portion 5556 of two surfaces from the left end of the second non-transmission wall portion 5553c is illustrated. Ru.

  As shown in FIGS. 65 to 68, the second non-transmission wall portion 5553c of the combined operation unit 5550 includes a recessed portion 5556 recessed in a direction away from the rotating crank member 570.

  The recessed portion 5556 has a first wall portion 5556a having an arc shape (approximately 1⁄4 of a circular shape) formed on the left side in front view, and an arc shape (approximately 1⁄4 of a circular shape) formed on the right side The second wall 5556 b is mainly formed to allow sliding of the sliding projection 574 of the rotating crank member 570. That is, the recess depth from the second non-transmission wall 5553c of the recess 5556 is equal to or less than the radius of the sliding projection 574, and the connection between the recess 5556 and the second non-transmission wall 5553c is smooth. It is formed of a curved surface.

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state shown in FIG. 65 to the state shown in FIG. 66, a gap is generated between the sliding projection 574 and the second non-transmission wall 5553 c, The pivoting arm member 5550 is swung until it abuts on the sliding projection 574 by the biasing force generated by the torsion spring 517a. In this case, as the rotating crank member 570 is rotated, the first wall 5556a of the first recessed portion 5556 from the left end of the second non-transmission wall 5553c is slid by the sliding projection 574 while being rotated. The movable arm member 5550 is swung.

  That is, from the state shown in FIG. 65 to the state shown in FIG. 66, the pivoting arm member 5550 is only swung by the biasing force of the torsion spring 517a, and is rotated by the driving force of the second drive device 560. The moving arm member 5550 is not rocked. Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 of the rotating crank member 570 is disposed to face the first wall 5556a, the rotating arm member 5550 and the rotation The crank member 570 forms a non-transmission state.

  When the rotating crank member 570 is rotated counterclockwise from the state shown in FIG. 66 to the state shown in FIG. 67, the sliding projection 574 is recessed first from the left end of the second non-transmission wall 5553 c. It is pressed against the second wall 5556 b of the setting portion 5556, and the pivoting arm member 5550 is swung again (pushed down) to the extended position. That is, from the state shown in FIG. 66 to the state shown in FIG. 67, since the second arm 5556b is pushed and moved by the sliding projection 574, the pivoting arm member 5550 is swung. The driving force of the second drive device 560 is transmitted to the pivoting arm member 5550 via the pivoting crank member 570.

  Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view and the sliding projection 574 of the rotating crank member 570 is disposed to face the second wall 5556b, the rotating arm member 5550 and the rotation The crank member 570 forms a transmission state.

  When the rotating crank member 570 is rotated counterclockwise from the state shown in FIG. 67 to the state shown in FIG. 68, a gap is generated between the sliding projection 574 and the second non-transmission wall portion 5553c, The pivoting arm member 5550 is swung until it abuts on the sliding projection 574 by the biasing force generated by the torsion spring 517a. In this case, as the rotating crank member 570 is rotated, the first wall 5556a of the second recessed portion 5556 from the left end of the second non-transmission wall 5553c is slid by the sliding projection 574 while being rotated. The movable arm member 5550 is swung.

  That is, from the state shown in FIG. 67 to the state shown in FIG. 68, the pivoting arm member 5550 is only swung by the biasing force of the torsion spring 517a, and is rotated by the driving force of the second drive device 560. The moving arm member 5550 is not rocked. Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 of the rotating crank member 570 is disposed to face the first wall 5556a, the rotating arm member 5550 and the rotation The crank member 570 forms a non-transmission state.

  As shown in FIGS. 65 to 68, when the sliding projection 574 is disposed to face the first wall 5556a in a state where the rotating crank member 570 is rotated counterclockwise in a front view. When a non-transmission state is formed between the moving crank member 570 and the rotating arm member 5550, and the sliding projection 574 is disposed opposite to the second wall 5556b, the rotating crank member 570 and the rotating arm member A communication state is formed with 5550.

  If the rotation direction of the rotating crank member 570 is reversed, the relationship between the first wall 5556a and the second wall 5556b is reversed. That is, when the rotating crank member 570 is rotated clockwise as viewed from the front, the rotating crank member 570 and the rotating arm member 5550 are arranged when the sliding projection 574 is disposed to face the first wall 5556 a. And when the sliding projection 574 is disposed to face the second wall 5556b, a non-transmission state is formed between the pivoting crank member 570 and the pivoting arm member 5550. Ru.

  As shown in FIGS. 65 to 68, in this embodiment, the pivoting arm member 5550 is in the retracted position (see FIG. 22) and the overhanging position without switching the pivoting direction of the pivoting crank member 570. In addition to the swinging motion swinging between them, the pivoting arm member 5550 has a small width near the overhanging position (a mode in which the lower end of the front plate member 546 is moved between the position U1 and the position U2) A rocking movement can be formed.

  As a result, it is possible to cause the pivoting arm member 5550 to produce a swinging motion that is difficult to form by switching the drive direction of the drive device 560. That is, to cause the swing arm member 5550 to perform a swing operation with a small width in the vicinity of the extended position can also be formed by repeatedly switching the drive direction of the drive device 560 at short intervals. However, in this case, the width of the rocking operation depends on the switching speed of the drive direction of the drive device 560. Further, even if the drive direction of the drive device 560 is switched in a state where the speed of the swinging motion of the pivot arm member 5550 is large, the inertia of the drive device 560 and the pivot arm member 5550 is large and the drive direction can not be switched instantaneously. The time required to switch the drive direction may be long.

  On the other hand, in the swinging operation near the extended position of the pivoting arm member 5550 in the present embodiment, there is no need to switch the rotation direction of the pivoting crank member 570, so the time required to switch the drive direction is unnecessary. can do.

  Further, the operation speed of the operation (the upward swinging operation) in which the pivoting arm member 5550 is pivoted clockwise in the front view depends on the biasing force generated by the torsion spring 517a, and the pivoting arm member 5550 is not The operating speed of the clockwise rocking movement (downward rocking movement) depends on the rotational speed of the rotating crank member 570. Therefore, by increasing the biasing force of the torsion spring 517a and increasing the rotational speed of the rotating crank member 570, it is possible to increase the swinging speed in the vicinity of the extended position of the rotating arm member 5550.

  As a result, it is possible to achieve both the speeding up of the rocking operation in the vicinity of the extended position of the rotary arm member 5550 and the shortening of the switching time of the rocking direction.

  Next, a combined operation unit 6500 according to the sixth embodiment will be described with reference to FIGS. 69 to 71.

  In the first embodiment, the case where the pivoting arm member 550 of the combined operation unit 500 is integrally molded has been described, but the pivoting arm member 6550 in the sixth embodiment is formed by connecting two members. . The relative swing of the two members changes the posture of the arc-shaped hole 554 formed at the other end. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  69 (a) and 69 (c) is a partial front view of the pivoting arm member 6550 in the sixth embodiment, and FIG. 69 (b) is a pivot in the direction of arrow LXIXb in FIG. 69 (a). FIG. 50 is a partial top view of an arm member 6550. 69 (a) shows a state in which the first attitude in which the tip of tip swing member 6556 is directed upward is formed, and in FIG. 69 (b), the tip of tip swing member 6556 is down. The state in which the second attitude to be directed is formed is illustrated.

  As shown in FIG. 69A, the pivoting arm member 6550 is connected to the main body portion 6551 pivotally supported by the third shaft portion 517 (see FIG. 71) and the other end of the main body portion 6551. A distal end swinging member 6556 and a switching device 6590 fixed to the upper surface of the other end of the main body portion 6551 to switch the attitude of the distal end swinging member 6556 are mainly provided. An arc-shaped hole 6554 is formed in the tip end swinging member 6556.

  The main body portion 6551 is provided with a shaft support hole 6551a which is bored in the other end portion in the front-rear direction and which becomes a swing center of the tip swing member 6556.

  The end swinging member 6556 is formed in such a manner that the end connected to the main body portion 6551 sandwiches the main body portion 6551 back and forth, and a shaft support hole 6556a drilled as a swing center of the tip swinging member 6556 A shaft support rod 6556b which is a rod inserted through the shaft support hole 6556a and the shaft support hole 6551a of the tip swing member 6556 and an extension provided extending from the shaft support hole 6556a to the opposite side of the arc-shaped hole 6554 The sliding shaft 6556c is mainly provided so as to protrude in the front-rear direction from the end of the portion and connected to the guide long hole 6591d of the switching device 6590.

  The arc-shaped hole 6554 is provided with a return portion 6554a protruding from the upper inner side surface. The return portion 6554a is a portion that slides on the protrusion 541b of the expansion / contraction effect member 6540, and when sliding from the tip end side of the arc-shaped hole 6554, resistance is suppressed, while sliding in the opposite direction It is a projection of the left-right asymmetrical shape where sliding resistance is increased when moved.

  70 (a) and 70 (b) are front perspective views of the switching device 6590. FIG. 70 (a) shows a push-up state where the C-shaped member 6591 is pushed up from the switch member 6592, and FIG. 70 (b) shows a pressed-down state where the C-shaped member 6591 is pushed down to the switch member 6592. Is illustrated. Further, the push-up state corresponds to the state of FIG. 69 (c), and the push-down state corresponds to the state of FIG. 69 (a).

  The C-shaped member 6591 has an inner diameter equal to the inner diameter of a long plate-like main body 6591a in which a hole having an inner diameter through which the movable cylindrical portion 6592a can be inserted is bored at the center and a hole bored in the main body 6591a. And a cylindrical guide portion 6591b protruding in a cylindrical shape and having a groove formed on the inner peripheral surface, extending downward from both end portions in the longitudinal direction of the main body portion 6591a and opposingly disposed in the front-rear direction of the main body portion 6551 A pair of arm portions 6591c and a guiding long hole 6591d which is a long hole formed on the tip end side of the arm portion 6591c and to which the sliding shaft 6556c of the tip swinging member 6556 is guided are mainly provided.

  The groove processing formed on the inner peripheral surface of the cylindrical guide portion 6591 b is a groove processing for forming a knock mechanism in relation to the movable cylindrical portion 6592 a of the switch member 6592. The C-shaped member 6591 is switched between the push-up state and the push-down state each time the C-shaped member 6591 is pushed in a direction to be pressed against the switch member 6592. In addition, illustration of other members, such as a spring member which forms an urging | biasing force required in order to form a knock mechanism, is abbreviate | omitted, In this embodiment, the cylindrical guide part 6591b is the pushing part 6541a of the expansion-contraction effect apparatus 6540 (figure 71)).

  In the switch member 6592, a movable cylindrical portion 6592a is inserted through the cylindrical guide portion 6591a, and a movable cylindrical portion 6592a is provided with a projection capable of moving the groove on the inner peripheral surface of the cylindrical guide portion 6591a from the outer peripheral surface. And a fixing plate portion 6592b rotatably connected and fixed to the upper surface of the main body portion 6551 of the rotating arm member 6550.

  Here, in the knock mechanism, the relative position in the axial direction is switched while the cylindrical member and the cylindrical member guided on the inner peripheral side of the cylindrical member are relatively rotated. That is, when the tubular member and the cylindrical member do not rotate relative to each other, it is difficult to switch the relative position in the axial direction.

  On the other hand, the movable cylindrical portion 6592a of the switch member 6592 is rotatably connected to the fixed plate portion 6592b. Therefore, when the C-shaped member 6591 is moved in the direction approaching the switch member 6592 (when pushed downward in FIG. 70A), the movable cylindrical portion 6592a can be relatively rotated with respect to the cylindrical guide portion 6591b. And the knock mechanism works.

  Therefore, it is possible to switch between the push-up state and the push-down state without relatively rotating the fixing plate portion 6592b fixed to the main body portion 6551 of the pivoting arm member 6550 and the C-shaped member 6591. Therefore, the state of the switching device 6590 can be switched between the push-up state and the push-down state while maintaining the state in which the slide shaft 6556c of the tip swing member 6556 is inserted into the guide long hole 6591d of the C-shaped member 6591. it can.

  71 (a) and 71 (b) are front views of the combined operation unit 6500. FIG. 71A shows a state in which the pivoting arm member 6550 is disposed at the overhanging position and the switching device 6590 is in the push-up state, and in FIG. K4, the pivoting arm member 6550 is disposed at the overhanging position and switched The device 6590 is shown in the depressed state. In FIGS. 71 (a) and 71 (b), the expansion / contraction effect device 6540 is disposed at a position where it is swung to the left end of the swingable range.

  As shown in FIGS. 71 (a) and 71 (b), the front view timepiece of the telescopic effect device 540 by switching the state of the switching device 6590 in the state where the pivoting arm member 6550 is disposed at the extended position. The maximum swing angle around can be switched.

  That is, when the switching device 6590 forms a push-up state (see FIG. 71A), the projection 541 b of the expansion / contraction effect member 6540 is in contact with the upper inner side surface of the arc-shaped hole 6554. The swing angle is limited.

  In this position, even if the inner surface of the circular arc shaped hole 6554 and the return portion 6554a function as a stopper and the swinging speed of the expansion / contraction effect device 6540 is high, the expansion / contraction effect device 6540 is arranged in the arrangement shown in FIG. A sudden stop can be made (the movement trajectory RI of the protrusion 541b is abutted on the return portion 6554a).

  On the other hand, when the switching device 6590 forms a depressed state (see FIG. 71B), the protrusion 541 b of the expansion / contraction effect device 6540 does not collide with the arc-shaped hole 6554 and the return portion 6554 a (the protrusion 541 b The movement trajectory RI is not in contact with the return portion 6554a). Therefore, the protrusion 541 b of the expansion and contraction rendering device 6540 is moved along the arc-shaped hole 6554, and the protrusion 541 b is discharged to the outside from the tip end 554 a of the arc-shaped hole 6554.

  Therefore, the expansion / contraction effect device 6540 is swung clockwise as viewed from the front until the rotary plate 520 is abutted against the second stopper portion 518b (see FIG. 71 (b)). In this position, the second stopper portion 518b functions as a stopper, and even when the swinging speed of the expansion and contraction rendering device 6540 is high, the expansion and contraction rendering device 540 can be rapidly stopped.

  Thereby, a plurality of swing angles (two types in the present embodiment) can be formed when swinging the expansion / contraction effect device 6540 clockwise in a front view and causing the expansion / contraction effect device 6540 to stop sharply. The variation of can be increased. The state of the switching device 6590 is switched by swinging the expansion / contraction effect member 6540 counterclockwise in a front view, so that the cylindrical guide portion 6591b of the switching device 6590 moves from the front right upper portion of the main body member 6541a to the right. It is generated by being pushed by a push-in portion 6541a extended in the direction. Therefore, since the second drive device 560 for causing the swing of the expansion / contraction effect member 6540 is also used as a drive device for swinging the tip swing member 6556, the number of drive devices can be reduced.

  Further, in FIGS. 71A and 71B, the swing range of the expansion / contraction effect device 6540 can be changed by slightly swinging the tip swing member 6556. In this case, since the rocking angle is slight, it is possible for the player to hardly notice the change.

  Here, if it is possible for the player to visually recognize the pivoting arm member 6550 (see FIG. 71), assuming that the swing angle of the expansion / contraction effect device 6540 can be grasped from the change in the state of the pivoting arm member 6550, The sense of expectation for the operation of the expansion and contraction producing device 6540 is weakened, and the attention of the expansion and contraction producing device 6540 is reduced.

  On the other hand, in the present embodiment, in order to change the swing angle of the expansion / contraction effect device 6540, the angle at which the tip swing member 6556 is swung is small, making it difficult for the player to notice the change. it can. Thus, the sense of expectation for the operation of the expansion / contraction effect device 6540 can be enhanced, and the degree of attention of the expansion / contraction effect device 6540 can be improved.

  Next, with reference to FIG. 72, a tilting operation unit 7600 in the seventh embodiment will be described.

  In the first embodiment, the slide hole 643 having a long hole shape is formed at the end of the transmission member 640, and the effect member 620 is supported by the slide hole 643 in a guideable manner. In the tilting operation unit 7600 in the embodiment, a pivot hole 7643 is formed at an end of the transmission member 7600, and the effect member 620 is pivotally supported by the pivot hole 7643. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  72 (a) and 72 (b) is a front view of the tilting operation unit 7600 in the seventh embodiment. FIG. 72 (a) shows an inverted state in which the shaft support hole 7643 of the transmission member 7640 is disposed vertically above the cylindrical portion 642, and in FIG. 72 (b), the inverted state from FIG. 72 (b). A state in which the transmission member 7640 is swung counterclockwise by a predetermined angle is illustrated. In FIGS. 72 (a) and 72 (b), in order to facilitate understanding, the outline of the effect member 620 is illustrated by an imaginary line, and the transmission member 7640 and the base member 7610 on the back side can be viewed. The illustration of the torsion spring 650 and the pivoting protrusion 612 is omitted.

  As illustrated in FIG. 72 (a), the base member 7610 is provided with a slide hole 7613 drilled in the front-rear direction vertically below the second shaft support hole 614 of the main body 611. The slide hole 7613 is a long hole through which the swinging shaft portion 626 of the effect member 620 is inserted, and the longitudinal direction of the long hole is formed along the vertical direction. The swing shaft portion 626 is slidably supported by the slide hole 7613.

  In the transmission member 7640, a shaft support hole 7643 is formed at an end opposite to the end where the cylindrical portion 642 of the main body 641 is formed. The shaft support hole 7643 pivotally supports the sliding shaft portion 621a of the effect member 620, and is bored with an inner diameter slightly larger than the diameter of the sliding shaft portion 621a.

  The swinging operation of the effect member 620 is generated by the transmission member 7640 swinging about the second support hole 614 by the rotation of the drive motor 631 of the first drive device 630 (see FIG. 51).

  In the present embodiment, since the sliding shaft portion 621a is pivotally supported by the shaft support hole 7643, when the transmission member 7640 swings, the sliding shaft portion 621a of the effect member 620 follows the swinging trajectory of the transmission member 7640. To move (the sliding shaft 621a does not move in the longitudinal direction of the main body 641). On the other hand, since the swinging shaft portion 626 is inserted into the slide hole 7613, when the transmission member 7640 swings, the swinging shaft portion 626 slides relative to the base member 7610.

  Here, the difference between the swing angle of the transmission member 7640 and the swing angle of the effect member 620 will be described. As shown in FIG. 72 (b), when the transfer member 7640 swings from the upside down by the transfer swing angle φ71, the effect member 620 swings by the effect swing angle φ72 (the effect swing angle φ72 <transfer shake Dynamic angle φ71). Therefore, when the transmission member 7640 is swung by the minimum unit of resolution of the drive motor 631, the swing angle of the effect member 620 can be smaller than the swing angle of the transmission member 7640. Thereby, the accuracy of the adjustment of the swing angle of the effect member 620 can be improved.

  Furthermore, in the present embodiment, the swing angle of the effect member 620 when the transfer member 7640 swings from the upright state by the transfer swing angle φ 71 can be made smaller than that in the first embodiment. explain.

  The connection line J1 illustrated in FIG. 72 (b) is a line drawn from the sliding shaft 621a to the swinging shaft 626. When the imaginary connecting line J2 has a length equal to that of the connecting line J1 and the rocking shaft 626 is disposed above the sliding hole 7613 from the line drawn in the longitudinal direction of the main body 641 through the cylindrical portion 642 It is a line drawn to the center of the swinging shaft portion 626 (see FIG. 72 (a)). In the case where the first shaft support hole 613 of the first embodiment is formed in the upper portion of the slide hole 7613, the virtual angle φ 73 which is the swing angle of the virtual connection line J2 in the first embodiment. This corresponds to the swing angle of the effect member 620 which is swung as the transmission member 640 is swung by the transmission swing angle φ71.

  As shown in FIG. 72 (b), the effect swing angle φ 72 is smaller than the virtual angle φ 73, and according to the tilting operation unit 7600 of the seventh embodiment, the effect in the case of swinging the transmission member 7640 by a predetermined angle The swing angle of the member 620 can be made smaller as compared with the case of the first embodiment. Therefore, when swinging the transmission member 7640 by the minimum unit of resolution of the drive motor 631 (see FIG. 51), the swing amount of the effect member 620 can be made smaller than that, and the swing angle of the effect member 620 is adjusted. Accuracy can be improved.

  As mentioned above, although the present invention was explained based on the above-mentioned embodiment, the present invention is not limited to the above-mentioned form at all, It is easy to be able to carry out various modification improvement in the range which does not deviate from the meaning of the present invention. It can be guessed.

  In each of the above-described embodiments, part or all of the configuration in one embodiment may be combined with or replaced with the configuration of part or all of the configuration in another embodiment to provide another embodiment.

  Although the case where the front rail part 715 was formed from a single circular arc shape was demonstrated in said each embodiment, it is not necessarily restricted to this. For example, the front rail portion 715 may be formed of a plurality of arcs, and the direction of the adjacent arcs may be reversed (wave shape). In this case, the slide movement speed of the effect member 620 is intermittently changed, and the posture of the effect member 620 is unstable. Therefore, it is possible to perform an effect of shaking the effect member 620.

  Although the case where the gravity center of the effect member 620 is vertically above the first shaft support 613 when the effect member 620 forms the inverted state has been described in the above embodiments, the present invention is not necessarily limited thereto. For example, the center of gravity may be disposed obliquely above the first shaft support 613.

  Although the case where the upper surface of the buffer rib 322 of the lower left plate member 320 is horizontal in the left-right direction has been described in the above embodiments, the present invention is not necessarily limited thereto. For example, the upper surface of the buffer rib 322 may be inclined downward as it approaches the width direction outer side. In this case, the velocity of the ball flowing into the upper surface of the lower left plate member 320 from the outer side in the board width direction can be decelerated by the acceleration in the gravity direction, and the deceleration time of the ball can be shortened.

  In each of the above embodiments, the case where the slide hole 643 of the transmission member 640 is formed as a long hole has been described, but the present invention is not necessarily limited to this. For example, the slide hole 643 may be formed in a circular shape, and the positional deviation between the slide hole 643 and the slide shaft portion 621a may be adjusted by the transmission member 640 extending and contracting. In this case, the arrangement range of the transmission member 640 can be suppressed.

  Although the case where the position of the contact part 644 can be switched by 2 positions was demonstrated in the said 4th Embodiment, it is not necessarily restricted to this. For example, the position of the contact portion 644 may be continuously changed (moved). In this case, the rate of change of the biasing force of the torsion spring 650 can be continuously increased.

  In the sixth embodiment, although the case where the attitude of the tip end swinging member 6556 changes at two positions has been described, the present invention is not necessarily limited thereto. For example, the posture change of the tip swinging member 6556 may be caused in a plurality of steps. In this case, the swing amount of the expansion / contraction effect device 6540 can be formed with a plurality of types, and variations of the effect can be increased.

  The present invention may be implemented on a type of pachinko machine or the like different from the above-described embodiments. For example, a pachinko machine (common name, two-time, three-time, and so on) in which the jackpot expected value can be increased until the jackpot state occurs a plurality of times (for example, two times, three times) including the jackpot once May be implemented as In addition, after the jackpot symbol is displayed, it may be implemented as a pachinko machine that generates a special game in which a predetermined game value is given to the player, as a prerequisite to winning a ball in a predetermined area. In addition, it is possible to have the winning device which possesses special territory such as V zone and to execute to the pachinko machine which becomes special game state as a necessary condition to make the special territory win the ball. Furthermore, in addition to pachinko machines, various types of gaming machines may be implemented, such as arelapachis, ball balls, slot machines, gaming machines in which so-called pachinko machines and slot machines are fused.

  In the slot machine, for example, a symbol is changed by operating the operation lever in a state where the coin is inserted and the symbol effective line is determined, and the symbol is stopped and determined by operating the stop button. It is a thing. Therefore, as a basic concept of the slot machine, “a display device is provided which displays the identification information after displaying the identification information sequence consisting of a plurality of identification information in a variable manner, and is derived from the operation of the starting operation means (for example, operation lever) The variable display of identification information is started, and the variable display of identification information is stopped and fixedly displayed due to the operation of the operation means for stop (for example, stop button) or when a predetermined time elapses. It is a slot machine that generates a special game that gives a predetermined game value to the player, as a prerequisite that the combination of identification information at the time is a specific one. In this case, the game medium is represented by coins, medals, etc. An example is given.

  In addition, as a specific example of a gaming machine in which a pachinko machine and a slot machine are fused, a display device is provided which variably displays a symbol row consisting of a plurality of symbols and then displays the symbols, and is provided with a handle for ball launch. Not included. In this case, after the injection of a predetermined amount of balls based on a predetermined operation (button operation), for example, the variation of the symbol is started due to the operation of the operation lever, for example, due to the operation of the stop button or By the passage of time, the fluctuation of the symbol is stopped, and a special game for giving a predetermined game value to the player is generated as a necessary condition that the determined symbol at the time of the stop is a so-called jackpot symbol. Is a lot of balls being dispensed to the lower tray. If such a gaming machine is used in place of a slot machine, only balls can be handled as gaming value in the gaming hall, so the gaming value is found in the current gaming hall where pachinko machines and slot machines are mixed. It is possible to solve the problems such as the burden on equipment due to the separate handling of medals and balls and the restriction on the installation location of gaming machines.

  Hereinafter, the concepts of various inventions included in the above-described embodiment in addition to the gaming machine of the present invention will be described.

<An example of the technical idea to change the driving force transmission by the deformed elongated hole 553 of the pivot arm member 550>
A crank member which is rotated about a first axis and has a projection projecting at a position eccentric to the first axis, and an insertion portion through which the projection is inserted, the first position and the first position are separated from each other An arm member movable between the second position and a drive device for generating a driving force for rotating the crank member about the first axis, the insertion portion being inserted The driving force is transmitted to the arm member by bringing the projection into contact with the inner peripheral surface of the insertion portion facing in the movement direction of the projection, and the arm member is moved to the first position and the second position. A gaming machine characterized by comprising: a transmission area movably formed between a position and a non-transmission area which is connected to the transmission area and in which transmission of the driving force is blocked. A1.

  Here, in a gaming machine such as a pachinko machine, the crank member includes a crank member provided with a protruding portion protruding from a rotational shaft and an arm member provided with an insertion portion into which the protruding portion of the crank member is inserted. There is a gaming machine in which an arm member operates in conjunction with rotation of a crank member (see, for example, JP-A-2009-000306). However, in the above-described conventional gaming machine, the crank member and the arm member always interlock. Therefore, the arm member is driven from the start of the crank member, and the timing of the start of the crank member and the timing of driving the arm member can not be shifted. In this case, at the time of starting the crank member, a large force is required to overcome the inertia of the crank member and the arm member, and there is a problem that the drive device becomes large.

  On the other hand, according to the gaming machine A1, since the insertion portion of the arm member includes the transmission region and the non-transmission region connected to the transmission region, the crank is inserted in the non-transmission region. By starting the member, it is possible to shift the timing for driving the arm member and the timing for starting the crank member. That is, even if the crank member is started, the driving force is not transmitted to the arm member until the projection intrudes from the non-transmission region into the transmission region. As a result, the driving force required for starting the crank member can be suppressed, and the drive device can be miniaturized.

  The arm member may be stopped or moved while the protrusion moves in the non-transmission area. For example, when an arm member is moved, the case where it moves by the elastic force etc. which gravity or the elastic spring for assistance generate | occur | produces is illustrated.

  In addition, as a penetration part, a hollow with a bottomed recessed part, a long hole penetrated etc. are illustrated.

  In the gaming machine A1, the crank member is formed so as to be able to rotate by one or more rotations, and the insertion portion becomes the transmission area by rotating the crank member in one rotation direction, while the crank member A game machine A2 comprising a selection area which becomes the non-transmission area by being rotated in another rotation direction opposite to the one rotation direction.

  According to the gaming machine A2, in addition to the effects achieved by the gaming machine A1, the mode of transmission of the driving force to the arm member can be changed according to the rotation direction of the crank member. In this way, by reversing the direction of the driving force of the driving device without changing the rotational speed of the crank member, it is possible to form two speed modes of the arm member when the crank members are arranged in the same phase. The variation of the speed of the arm members can be increased.

  In the gaming machine A2, the insertion portion is separated from the projection and an inner circumferential surface of the insertion portion facing in the movement direction of the projection when the crank member is rotated in the one rotation direction. A game machine A3 characterized in that the selection area is formed by providing an extra portion.

  In the gaming machine A3, in addition to the effects exhibited by the gaming machine A2, the selection area is formed by providing the insertion portion with the extra portion, so that the other for changing the mode of transmission of the driving force to the arm member Parts can be eliminated and material costs can be reduced.

  In any one of the gaming machines A1 to A3, at least one of the first position and the second position is formed as an end position of a movement range of the arm member, and the first position or the formed as an end position thereof. When the arm member is disposed at one of the second positions, the arm member directed to the other one of the first position or the second position formed opposite to the end position. A game machine A4 characterized in that a bound suppressing mechanism for suppressing movement is formed.

  According to the gaming machine A4, in addition to the effects of the gaming machine A3, when the arm member is disposed at either the first position or the second position formed as the end position of the movable range of the arm member, It is possible to suppress the driving force that the driving device needs to generate in order to suppress the movement of the arm member toward the other side on the opposite side. Therefore, the durability of the drive device can be improved.

  In addition, when using the adsorption | suction force of a magnet as a bound suppression mechanism, when suppressing a motion with a claw-shaped member, and the load which the projection part of a crank member receives from an arm member faces an axial direction of a crank member, an arm The case where the penetration part of a member is formed, etc. are illustrated.

  In the case of adsorbing with a magnet, although the magnet is required as a separate member, it is possible to generate various magnitudes of adsorption force by the internal composition of the magnet, and the design freedom can be improved.

  In the case where the movement is suppressed by the claw-shaped member, a driving device for operating the claw-shaped member is necessary, but the movement of the arm member can be mechanically arrested by the claw-shaped member.

  When the insertion portion of the arm member is formed in such a manner that the load received by the projection of the crank member from the arm member is directed to the axis of the crank member, provision of a separate member for restraining movement of the arm member is unnecessary. Bounce of the arm member can be suppressed mechanically.

  In the gaming machine A4, when the arm member is disposed at at least one of the first position or the second position, an outline of the non-transmission area of the insertion portion near the connection position with the transmission area is the external shape. A game machine A5 characterized in that the bound suppressing mechanism is formed by being substantially the same as the circumscribed circle of the protrusion centering on the rotation axis of the crank member.

  According to the gaming machine A5, in addition to the effects of the gaming machine A4, the bounce suppressing mechanism is formed by continuing the rotation of the crank member after the arm member is disposed at the first position or the second position. Thereby, the change from the movement state of an arm member to a stop state can be formed smoothly.

  Further, in the bounce suppressing mechanism, the load applied from the insertion portion to the projection is directed to the rotation shaft of the crank member, so that the load in the rotation direction of the crank member can be suppressed, and the load on the drive device is suppressed. can do.

  In any one of the gaming machines A1 to A5, when the arm member is disposed at the first position, an outline of the non-transmission area of the insertion portion near the connection position with the transmission area is the crank member. An urging force is applied to move the arm member from the first position to the second position, which is substantially the same as the circumscribed circle of the protrusion centering on the rotation axis, and the non-transmission area of the insertion portion The side surface on the first position side is formed with at least one of an inner recessed portion protruding inside of the insertion portion or an outer recessed portion protruding outside of the insertion portion with a size that can accommodate the protrusion. A game machine A6 characterized by being

  According to the gaming machine A6, in addition to the effects of any one of the gaming machines A1 to A5, when the arm member is disposed at the first position, the outer shape in the vicinity of the connection position with the transmission area of the non-transmission area of the insertion portion. Is substantially the same as the circumscribed circle of the protrusion centering on the rotation axis of the crank member, and an urging force for moving the arm member from the first position to the second position is loaded on the arm member. In this case, the projection of the crank member is disposed in the non-transmission area of the insertion portion, whereby the movement of the arm member is prevented by the projection and the arm member is stopped. When the crank member is rotated and the projection moves in the non-transmission area, the arm member is moved when the projection and the inner recess or the outer recess are opposed to each other. That is, when the protrusion is disposed to face the inner recess, the inner recess is pushed out by the protrusion, and the arm member is moved to the opposite side of the crank member. Further, when the protrusion is disposed to face the outer recess, the protrusion is accommodated in the outer recess, and the arm member is moved to the crank member side.

  As a result, the projection of the crank member moves in the non-transmission area, whereby the movement of the arm member, which is different from the movement of the arm member caused when the projection moves the transmission area by rotating the crank member Can occur. Therefore, coexistence with the improvement of durability of a drive device and the change of the movement width of an arm member can be aimed at.

  That is, in order to change the movement width of the arm member, it is necessary to reverse the direction of the driving force of the drive device according to the movement width of the arm member. In this case, the control load of the drive device is increased, and it is difficult to perform an operation with a small movement width such as vibration.

  On the other hand, according to the gaming machine A6, the projection of the crank member is moved in the non-transmission area, and the projection and the inner hollow portion or the outer hollow portion are disposed opposite to each other, thereby forming the movement of the arm members having different moving widths. Ru. Therefore, the movement width of the movement of the arm member can be changed without reversing the direction of the driving force of the driving device. In addition, by narrowing the formation interval of the adjacent inward depressions or outward depressions, it is possible to cause the arm member to perform an operation with a small movement width such as vibration.

  In addition, the aspect which can accommodate a projection part may be an aspect in which the whole projection part is included in a recess, and the aspect in which a part of projection part is contained in a recess may be sufficient.

<An example of the technical idea of limiting the swing width of the expansion / contraction effect device 540 by the arc-shaped hole 554>
The movable member which can move along a predetermined movement trajectory and can be disposed at the first position and the second position which are different from each other, moves corresponding to the movable member, and abuts on the movable member to move the movable member. A stopper member for restricting the movement width of the predetermined movement trajectory of the member and changing the movement width of the movable member depending on whether the movable member is disposed at the first position or the second position; , A game machine B1 characterized by comprising.

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine provided with a movable member formed movable and a stopper member for restricting the movement width of the movable member (for example, JP 2012-016623A). reference). However, in the above-described conventional gaming machine, the stopper member is fixed immovably, so the stopper member is separately prepared for the case where the movable member is disposed at the first position and the case where the movable member is disposed at the second position. And the space for disposing the stopper member is wide.

  On the other hand, according to the gaming machine B1, since the stopper member moves corresponding to the movable member, the movable member is arranged at the second position while the stopper member is arranged at the first position. It can also be used as a stopper in the case. Thereby, the space which arranges a stopper member can be controlled.

  In addition, since the stopper member changes the moving width of the movable member depending on whether the movable member is arranged at the first position or the movable member is arranged at the second position, the variation of the moving width of the movable member is increased be able to.

  The stopper member may be, for example, a protrusion projecting from the transmission member and coming into contact with the movable member, or an inner wall of a recess which is recessed in the transmission member and accommodates a part of the movable member.

  In addition, as a mode of movement, linear movement, curvilinear movement, meandering movement, vibration, rocking, rotational movement and the like are exemplified. Further, the movement width in each movement aspect means, for example, an actual movement distance or a linear distance between two points in the case of linear movement, curvilinear movement, meandering movement, vibration, etc. In the case of etc., it means the actual movement distance, movement angle, etc.

  In the gaming machine B1, the movable member includes an intermediate member pivotally supported by the first shaft so as to be swingable and extendable in the radial direction of the first shaft, and in the first position and the second position The expansion and contraction length of the intermediate member is different, the predetermined movement trajectory is formed in an arc shape centered on the first axis, and the stopper member is in a case where the intermediate member is in a predetermined expansion and contraction state A game machine B2 extending along the predetermined movement trajectory of the movable member.

  According to the gaming machine B2, in addition to the effects of the gaming machine B1, the movable member is pivotally supported so as to be pivotable about the first axis and is formed so as to be able to extend and contract in the radial direction of the first axis It has a member. Therefore, the curvature radius of the predetermined movement locus of the movable member centering on the first axis can be changed depending on the length of the intermediate member in the expansion and contraction direction.

  Here, the stopper member is extended along a predetermined movement trajectory of the movable member when the intermediate member is in a predetermined expansion / contraction state (a curvature of the extension direction of the stopper member and the predetermined expansion / contraction state of the intermediate member) And the curvature of the predetermined movement trajectory of the movable member in the same case). In this case, when the intermediate member is in a predetermined expansion and contraction state, the movable member is moved along the stopper member, and the movable member can be moved in the extending direction of the stopper member. Therefore, the movement width (swing angle) of the movable member can be maximized.

  On the other hand, when the intermediate member is in an expansion / contraction state different from the predetermined expansion / contraction state, the curvature of the predetermined movement trajectory of the movable member and the curvature in the extending direction of the stopper member can be made different, and the predetermined movement of the movable member The track and the extending direction of the stopper member can be crossed. Therefore, the movement width of the movable member can be shortened. Therefore, the movement width of the movable member can be changed by changing the expansion and contraction state of the intermediate member.

  In the gaming machine B2, the movable member includes a protrusion protruding toward the stopper member, the stopper member includes an insertion portion through which the protrusion is inserted, and the protrusion is on the insertion portion. In the inserted state, the movable member and the stopper member interlock in the expansion and contraction direction of the intermediate member, and the movable member abuts on the insertion portion.

  According to the gaming machine B3, in addition to the effects produced by the gaming machine B2, the movable member and the stopper member interlock in the expansion and contraction direction of the intermediate member by inserting the projection of the movable member into the insertion portion of the stopper member. The driving device for expanding and contracting the movable member and the driving device for moving the stopper member can be combined. Further, the insertion portion restricts the movement of the movable member by being in contact with the movable member. That is, the insertion portion of the stopper member has a function as a stopper for restricting the movement of the movable member, and a function for interlocking the movable member and the stopper member. This makes it possible to centralize the functions.

  In the game machine B3, the expansion and contraction operation of the intermediate member reverses the arrangement of the first shaft with respect to the insertion portion between the inner peripheral side and the outer peripheral side.

  According to the gaming machine B4, in addition to the advantageous effects of the gaming machine B3, the arrangement of the first shaft with respect to the insertion portion is reversed between the inner circumferential side and the outer circumferential side by the expansion and contraction operation of the intermediate member. Thereby, the movement width of the movable member can be changed between the case where the first shaft is disposed on the inner peripheral side of the insertion portion and the case where the first shaft is disposed on the outer peripheral side of the insertion portion.

  That is, in the case where the first axis is disposed on the inner peripheral side of the insertion portion (when the movement locus of the protrusion in the case where the movable member is moved with a predetermined movement locus follows the shape of the insertion portion), The movement locus and the shape of the insertion portion are approximated, and the movement width of the predetermined movement locus of the movable member can be increased. On the other hand, in the case where the first axis is disposed on the outer peripheral side of the insertion portion (when the movement trajectory of the projection when the movable member is moved with a predetermined movement trajectory substantially reverses the shape of the insertion portion), the projection The angle formed by the movement trajectory of the movable member and the inner wall surface of the insertion portion is increased, and the movement width of the predetermined movement trajectory of the movable member can be narrowed.

  In the gaming machine B3 or B4, the insertion portion is formed so as to be changeable in posture while maintaining the extended state of the intermediate member, and the posture of the insertion portion changes the contact position of the movable member and the insertion portion. Is changed, and the movement width of the predetermined movement trajectory of the movable member is changed.

  According to the gaming machine B5, in addition to the effects of the gaming machine B3 or B4, the contact position between the movable member and the insertion portion is changed by changing the posture of the insertion portion while maintaining the extended state of the intermediate member. In this case, the movement width of the predetermined movement trajectory of the movable member can be changed while maintaining the expansion and contraction state of the intermediate member.

  In any one of the game machines B3 to B5, the insertion portion includes a groove portion which allows the projection portion to move in and out along the movement path, and the projection portion is separated from the insertion portion through the groove portion. A game machine B6 that is capable of forming a state, and the movable member includes a positioning assisting portion that is engaged with the stopper member in the separated state.

  According to the gaming machine B6, in addition to the effects produced by any of the gaming machines B3 to B5, it is possible to form a separated state in which the projection is separated from the insertion portion through the groove and the movable member is in the separated state. A positioning aid is engaged with the stopper member. Therefore, the formation range of the stopper member can be made smaller than the movement range of the movable member, and the material cost of the stopper member can be reduced, and the positional deviation between the movable member and the stopper member in the separated state It can be prevented. That is, even if the projection is separated from the insertion portion of the stopper member, the relative movement of the movable member with respect to the stopper member is suppressed by the positioning assisting portion, so that the projection can be returned to the insertion portion again.

<An example of the technical idea of supporting the effect member 620 supported in an inverted position at two points>
A base member, a movable member displaceably supported by a support formed on the base member and moving upward from a predetermined position, a drive device generating a driving force for displacing the movable member, and the movable member A transmission member for transmitting a driving force generated from the drive device to the movable member, wherein the transmission member is pivotally supported by a pivot portion formed on the base member, A game machine C1 characterized in that the length from the pivot support portion to the connection position of the movable member and the transmission member is shorter than the length from the support portion to the connection position of the movable member and the transmission member. .

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine in which a movable member which is displaceably supported by a support formed on a base member and which moves upward from a predetermined position is driven by transmission of a driving force by a gear (for example, See JP 2011-120640 A). However, in the above-described conventional gaming machine, the movement amount of the center of gravity of the movable member when operating the drive device in the minimum unit of control resolution of the drive device (for example, one step for a stepping motor) is the support of the movable member Is proportional to the length from the center of gravity of the movable member to the center of gravity of the movable member. Therefore, the position adjustment of the center of gravity of the movable member becomes more difficult as the center of gravity of the movable member moves away from the support in the radial direction.

  In addition, when the center of gravity of the movable member is shifted to one side from an inverted state in which the center of gravity of the movable member is disposed directly above the support portion, a driving force is generated to displace the movable member in the opposite direction, and the movable member is inverted. If the center of gravity is shifted to the other side by the driving force even if the state is maintained, the direction of the driving force coincides with the direction of gravity, and the movable member is largely displaced.

  Therefore, as the movable member becomes longer in the radial direction of the support portion, there is a problem that it becomes more difficult to stop the movable member in an inverted state in which the center of gravity of the movable member is disposed directly above the support portion.

  On the other hand, according to the gaming machine C1, the transmission member for transmitting the driving force of the drive device to the movable member to move the movable member upward is pivotally supported by the pivotal portion of the base member and connected to the movable member. The length from the connection position of the movable member and the connection member to the support portion is formed shorter than the length from the connection position of the movable member and the connection member to the support portion. Therefore, even if the movable member is long in the radial direction of the support portion, the movement amount of the center of gravity of the movable member in the case of operating the drive device at the minimum unit of control resolution of the drive device is suppressed. it can. Therefore, it is easy to make the movable member stationary in an inverted state in which the center of gravity of the movable member is disposed directly above the support portion.

  Note that as a mode in which the movable member is supported by the base member, a mode in which the movable member is pivotally supported by the base member in a pivotable manner, a mode in which the movable member is slidably supported by the base member, The combined aspect etc. are illustrated.

  In the gaming machine C1, the transmission member is characterized in that the arm length from the pivot support portion to the connection position with the movable member is shortened as the movable member moves upward from the predetermined position. Machine C2.

  According to the gaming machine C2, in addition to the effects of the gaming machine C1, the more the movable member displaced around the support portion moves upward from the predetermined position, the more the transmitting member from the pivot portion to the connecting position with the movable member The arm length is shortened. Therefore, compared with the case where the arm length of the transmission member is constant, the design freedom of the speed of the movable member can be improved.

  For example, when the rotation number of the drive device for rotating the transmission member operates at a constant speed, the arm length of the transmission member is fixed at a predetermined first length, and the arm length of the transmission member is the first It is assumed that the second length is shorter than the second length. When the number of rotations of the drive device is constant, the transmission when the transmission member is fixed at the first length is higher than when the arm length of the transmission member is fixed at the second length. The moving speed of the center of gravity of the movable member is increased when the member is placed in a predetermined phase.

  Here, the speed generated when the movable member is operated quickly at a speed that occurs when the transmission member has the first arm length near a predetermined position, and the speed that occurs when the transmission member has the second arm length near the inverted state Now consider the case where you want to move the movable member slowly. As a method for that purpose, although it is conceivable to change the rotation speed of the drive device halfway, this method can not be adopted when it is difficult to change the rotation speed of the drive device. In addition, even if it is possible to change the number of rotations of the drive device, in order to change the number of rotations on the way, a detection sensor for detecting the timing of the change is required, which increases the cost. There was a point.

  On the other hand, according to the gaming machine C2, in addition to the effects of the gaming machine C1, the arm length from the pivotally supported portion of the transmission member to the connection position of the transmission member and the movable member is a predetermined position of the transmission member. Is formed in such a manner as to be shortened as it moves upward from the Therefore, the transmission member can be set to the first arm length near the predetermined position, and the transmission member can be set to the second arm length near the inverted state, so that the design freedom of the speed of the movable member can be improved. .

  In addition, as a structure by which the arm length from the pivotal support portion to the connection position of the transmission member and the movable member is fixed, the case where the projection protruding from the transmission member is inserted into and coupled to the movable member is exemplified. Ru. In addition, as a configuration in which the arm length can be changed, a long hole is formed in the transmission member, and a protrusion protruding from the movable member is slidably inserted into the long hole of the transmission member, or movable The case where a long hole is provided in the part by which a member is supported by a support part, and the insertion shaft rod penetrated by the long hole from a base member is formed is illustrated.

  In the gaming machine C1 or C2, the movable member includes a protrusion projecting in a direction parallel to the support portion, and the transmission member is an elongated hole extending in the radial direction of the pivot portion. A game machine C3 comprising an insertion portion through which the projection is inserted.

  In the gaming machine C3, in addition to the effects of the gaming machine C1 or C2, the insertion portion is extended in the radial direction of the shaft support portion, and the transmission member and the movable member are inserted by inserting the projection of the transmission member into the insertion portion. As a result, the moving direction of the connecting position is restricted in the radial direction of the shaft support. Therefore, with the swinging of the transfer arm, it is possible to mechanically change the length from the support portion to the connection position of the transfer member to the movable member.

  In addition, as an insertion part, the long hole by which penetration formation is carried out, the recessed part formed as a hollow with a bottom, etc. are illustrated.

  In the game machine C3, the axis support portion is disposed vertically above the support portion, and the center of gravity of the movable member is disposed on a straight line connecting the support portion and the projection portion.

  According to the gaming machine C4, in addition to the effects of the gaming machine C3, the center of gravity of the support portion, the shaft support portion, the projection portion and the movable member is the movable member when the projection portion is disposed vertically above the support portion. It is formed on the vertical line. In this case, the gravity applied to the center of gravity of the movable member is loaded vertically downward with respect to the support and the bearing. Therefore, since the force in the rotational direction is not loaded on the movable member, the posture of the movable member can be maintained even if the power of the drive device is cut off. Thereby, the burden on the drive device can be reduced.

  In the gaming machines C1 to C4, a worm gear is interposed between the transmission member and the drive device, and the rotation of the drive device is decelerated by the worm gear.

  According to the gaming machine C5, in addition to the effects exhibited by the gaming machines C1 to C4, a worm gear is interposed between the transmission member and the driving device, and the rotation of the driving device is decelerated by the worm gear. The moving width of the movable member can be significantly reduced when operating with the smallest unit of resolution of In addition, since the transmission direction of the force through the worm gear is limited to one direction from the drive device side to the transmission member side, it is possible to prevent the worm gear from rotating with a load from the transmission member side. It is possible to reduce the load placed on the drive device at the time of stopping the vehicle.

  In any one of the game machines C1 to C5, an urging device for generating an urging force for moving the center of gravity of the movable member in both directions of displacement of the movable member is provided above the support portion, the urging force being A game machine C6 characterized in that the center of gravity of the movable member is balanced in the displacement direction in the inverted state where the center of gravity of the movable member is disposed vertically above the support portion, and the movable member becomes larger as it is displaced from the inverted state.

  According to the gaming machine C6, in any one of the gaming machines C1 to C5, the biasing device generates a biasing force for moving the center of gravity of the movable member above the support portion, and the biasing force is that the center of gravity of the movable member is It becomes so large that a movable member displaces from the state (inverted state) arrange | positioned vertically above a support part. That is, the biasing force can be minimized in the inverted state.

  Therefore, by increasing the biasing force when the movable member moves upward from the predetermined position, the load on the driving device for moving the movable member upward from the state in which the movable member is disposed at the predetermined position can be reduced.

  Also, the biasing force is generated in both directions of the displacement direction of the movable member, and balanced in the displacement direction in the inverted state. Therefore, when the movable member is moved upward from the predetermined position and the drive device is controlled to stop, the posture of the movable member is inverted by the biasing force even when the movable member does not reach the inverted state or passes by the inverted state. It can be turned to This makes it easy to stop the movable member in the inverted state.

  In the gaming machine C6, the movable member can form a first state until the center of gravity is displaced by a predetermined amount from above the support portion by a predetermined amount, and a second state displaced by the predetermined amount or more. A game machine C7 characterized in that the rate of change in biasing force in the case of the same displacement is larger in the second state than in the one state.

  According to the gaming machine C7, in addition to the effects of the gaming machine C6, the movable member is larger than the predetermined amount from the inverted state than in the first state on the inverted state where the center of gravity of the movable member is disposed vertically above the support portion. In the second state to be displaced, the rate of change of the biasing force in the case of the same displacement is larger. In this case, when starting the movable member from the state where the movable member is disposed in the second state, it is possible to suppress the load at the time of starting the drive device. In addition, since the acceleration of the movable member can be reduced when the movable member is disposed near the inverted state, it is easy to stop the movable member in the inverted state.

<An example of a technical idea in which the spring constant of the torsion spring 650 changes in the middle of swinging>
A movable member movable between a first position and a second position, a drive device for generating a driving force for moving the movable member, and an urging force for returning the movable member to the first position In the gaming machine provided with an urging device for generating the movable member, the movable member is movable relative to a change ratio of the urging force generated when the movable member is disposed in the first urging region from the first position to the predetermined position. The rate of change of the biasing force generated when the member is disposed in the second biasing region which is a region connected to the first biasing region and is formed apart from the first position is formed large A game machine D1 characterized by

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine using an urging force by an urging device such as an elastic spring as an assisting force when moving a movable member by a driving force generated by a driving device (e.g. See -120640)). However, in the above-described conventional gaming machine, the biasing force of the biasing device is proportionally increased by the displacement amount of the movable member, and it is difficult to change the purpose of the biasing device by the arrangement of the movable member. There was a problem that it was. That is, it has been difficult to make the movement of the movable member flexible by suppressing the urging force in a certain area, and to make the movement of the movable member sharper by improving the urging force in another area.

  On the other hand, according to the gaming machine D1, the change ratio of the biasing force biased toward the first position indicates that the movable member has the second change ratio compared to the case where the movable member is disposed in the first bias region. The case where it is arranged in the pressure area is made larger. That is, for example, when the movable member stopped at the second position is started to the first position (the second urging region), a sufficient biasing force can be obtained by the biasing device, while the movable member is the first When the movable member is disposed in the urging region, the change in the urging force is suppressed, and the operation of the movable member can be made flexible (slowly).

  As a mode in which the rate of change of the biasing force of the biasing device is changed by the arrangement of the movable member, the number of biasing devices that cause the movable member to generate a biasing amount may increase during the process. The case where it is formed from an elastic spring and the spring constant of an elastic spring is changed by arrangement of a movable member etc. is illustrated.

  In the gaming machine D1, the biasing device is a pair of elongated members which are disposed on a pair of surfaces which intersect the moving direction of the movable member and sandwich the movable member in the moving direction, one end of which is one end And the other end, which is an end opposite to the one end, is formed of an elastic spring whose movement is suppressed, the movable member being A main body portion sandwiched between a pair of elongated members, and an opposite side of the main body portion with respect to the pair of elongated members, and at least one of the pair of elongated members in the moving direction of the main body portion And a contact portion formed to be contactable, wherein the contact portion is connected and fixed to the movable member, and when the movable member is disposed in the first biasing region, the movable member is a pair of the pair Of the movable member among the long members The movable member is brought into contact with one of the long members on the side where the distance to the movable member is short and is given an urging force, and the movable member is brought into contact with the other long member and the contact portion to be urged. A gaming machine D2 characterized by being given.

  According to the gaming machine D2, in addition to the effects of the gaming machine D1, the change timing of the changing ratio of the biasing force by the biasing device is shifted for each long member the contact timing of the movable member and the pair of long members. Can be formed by Therefore, it is unnecessary to change the biasing force of the biasing device by control or to prepare a separate member for improving the biasing force.

  That is, since the other end of the pair of long members is restricted in movement, one long member on the side where the distance to the movable member becomes short due to the movement of the movable member is pressed against the movable member and moves. The other long member on the opposite side receives no force from the movable member. Therefore, in the first biasing region, when the movable member moves, the other long member disposed on the opposite side of the moving direction of the movable member stays in place.

  On the other hand, in the second biasing region, the movable member is moved, whereby the other long member is in contact with the contact portion. As a result, the biasing force is also generated from the other long member. Therefore, the biasing force applied to the movable member in the second biasing region can be increased.

  In addition, a coil spring, a torsion spring, a leaf spring etc. are illustrated as an elastic spring.

  In the gaming machine D1 or D2, the biasing device is a pair of elongated members which are disposed on a pair of surfaces which intersect the moving direction of the movable member and sandwich the movable member in the moving direction, The other end of each of the two ends of the movable member is disposed opposite to the both side surfaces of the movable member, and the other end which is the opposite end of the one end is formed of an elastic spring whose movement is suppressed. A body portion sandwiched between the pair of elongated members, and at least one of the pair of elongated members formed on the opposite side of the body portion with respect to the pair of elongated members in the moving direction of the body portion And a contact portion formed to be contactable, the contact portion being connected and fixed to the movable member, and the movable member being disposed in the first biasing region, the movable member being Of the pair of elongated members, the movable member When the movable member is placed in the second urging region while being abutted against one long member on the side where the distance to the movable member is reduced by movement and the movable member is placed in the second biasing region, the one long member The game machine D3 characterized in that the middle part of the above is pressed against the contact part arranged on one long member side with respect to the main body part.

  According to the gaming machine D3, in addition to the effects of the gaming machine D1 or D2, the change ratio of the biasing force is formed by pressing the middle part of one long member against the contact part. That is, the change ratio of the biasing force is changed by further deforming one long member already deformed by the movement of the movable member starting from the middle portion pressed against the contact portion. Here, in the deformation starting from the intermediate portion, the length of the portion subjected to the deformation becomes shorter compared to the deformation starting from the other end portion, so the ratio of the change of the biasing force to the moving amount of the movable member is Increase. Thereby, in the second biasing region, it is possible to increase the change of the biasing force with respect to the moving amount of the movable member. Therefore, the change ratio of the biasing force can be increased.

  In the gaming machine D3, the one long member includes a first bending point bent toward the opposingly disposed contact portion, and the one long member is the first bending point at the first bending point. A game machine D4 characterized in that it is pressed against the contact portion.

  According to the gaming machine D4, in addition to the effects of the gaming machine D3, one long member is in contact with the abutting portion disposed oppositely at the first bending point, so one long member is in contact It is stretched by contact with the part. Therefore, the tip end portion of the biasing device that applies the biasing force to the movable member can be separated from the other end portion of the long member serving as the starting point of the biasing force and the first bending point. Therefore, the moment the movable member is loaded from the biasing device in the second biasing region can be made larger.

  In the gaming machine D4, the movable member includes a tip enlargement area which is enlarged in the moving direction as it moves away from the other end of the long member, and one of the movable member and the long member is enlarged in the tip enlargement region. A game machine D5 characterized in that the end of the game machine is abutted.

  According to the gaming machine D5, in addition to the effects of the gaming machine D4, the movable member has a tip enlargement area, and the movable member and one end of the elongated member abut in the tip enlargement area. Therefore, when one long member is stretched by pressing one long member against the contact portion, the contact position between the movable member and the long member separates from the other end of the long member. As it is moved in the direction, the amount of deformation of the elongated member is increased. Therefore, the biasing force applied to the movable member from the biasing device can be increased.

  In any one of the game machines D2 to D5, the arrangement interval between the contact portion and the main body portion is changeable.

  According to the gaming machine D6, in addition to the effects produced by any of the gaming machines D2 to D5, it is possible to increase the variation of the change in biasing force generated by the long members. That is, for example, when the arrangement interval between the contact portion and the main body portion is narrowed, the timing at which the rate of change of the biasing force of the long member increases can be set earlier.

<Example of a technical idea in which a plurality of out-ports are provided and the buffer rib 322 is formed on the lower plate 320>
Inside the game area where the ball is formed so as to allow flow-down, the board internal character placed in contact with the lower edge of the game area, and the ball formed on one side in the width direction of the board internal character A first out port, which is an opening for discharging from the area, and a second out port, which is an opening for discharging balls from the game area, formed on the other side in the width direction of the board internal component opposite to the one width direction side In the gaming machine, the first out port and the second out port are provided with a lower plate portion extending from the lower side surface of the opening to the front and having a guiding surface on the upper surface, and the guide of the lower plate portion The surface is provided with a buffer rib extending like a rib toward the opening direction on the corresponding side in the first out port or the second out port, and is formed to be raised from the guide surface in the width direction outer side And the buffer rib has an aspect ratio directed outward in the width direction. Gaming machine E1, characterized in that it is formed smaller.

  Here, in gaming machines such as pachinko machines, there are gaming machines in which a plurality of out-ports are arranged (see, for example, JP-A-9-192301). However, in the above-described conventional gaming machine, it is preferable to reduce the size of each out-port as the number of out-ports increases, because it is possible to secure the installation space for an attacker etc. There was a problem that discharge of the game ball might be overdue.

  For example, when the height at which the ball bounces up and down on the near side of the out-port becomes equal to or more than the vertical width of the out-port, the ball stays in front of the out-port. Also, for example, when the side surface is disposed on the side of the character at the side surface in the width direction of the out port and becomes a wall, the ball flowing from the width direction to the near side of the out port collides with the side surface of the character and rebounds in the width direction. At this time, when the amount of rebounding in the width direction becomes equal to or more than the width of the out port, the ball stays in front of the out port.

  On the other hand, according to the gaming machine E1, since the buffer rib is formed on the guide surface formed in the lower plate portion, it is possible to suppress the bounce of the ball or to decelerate the ball. That is, when the ball collides in the vertical direction, the buffer rib becomes a cushion by bending deformation of the buffer rib, and it is possible to suppress ball rebound. In addition, when the ball collides from the left and right direction, the ball is braked by being fitted into the buffer rib.

  Here, the buffer rib extended in the opening direction is weak to the load from the left and right direction, and may be damaged by the collision of the ball from the left and right direction.

  On the other hand, according to the gaming machine E1, since the guide surface is provided with the step portion on the outer side in the width direction, the ball flowing down from the left and right direction toward the buffer rib falls from above the step portion to the buffer rib . In this case, the vertical component of the direction of the collision of the ball with the buffer rib can be increased, and breakage of the buffer rib can be suppressed.

  In addition, since the step portion has a function of stopping the ball moving in the left and right direction on the guide surface, it is possible to prevent the ball moving on the guide surface from bouncing back beyond the width of the out port.

  Since the buffer rib is formed higher toward the center in the width direction of the game area, a large rebound suppressing effect can be obtained near the center in the width direction of the game area where flowing balls are easily concentrated. Thereby, the ball can be discharged smoothly from the out port. Further, by aligning the lower curve of the game area with the lower surface of the buffer rib, the arrangement position of the out port can be corrected downward.

  Here, the higher the height at which the buffer rib is formed, the greater the effect of suppressing ball bounce, because the amount of deflection of the buffer rib is increased. That is, as the amount of deflection of the buffer rib is larger, the cushioning effect works sufficiently, and it is easy to suppress the bounce. Therefore, it is preferable to make the aspect ratio of the buffer rib constant in the left-right direction (to make the length in the vertical direction constant) for the effect of suppressing the rebound.

  On the other hand, when the aspect ratio of the buffer rib is made constant (the length in the longitudinal direction is made constant), it is necessary to increase the height at which the step is formed, and the path of the ball up to the step is also upward As a result, the game area is narrowed, which is not preferable in terms of space efficiency.

  On the other hand, in the gaming machine E1, on the outer side in the width direction of the game area where flowing balls are hard to concentrate, the aspect ratio (longitudinal length) of the buffer rib is reduced, and the width direction center of the game area where flowing balls are easily concentrated In the above, the aspect ratio (longitudinal length) of the buffer rib is increased. Thereby, coexistence with improvement of discharge efficiency of a ball, and securing of a game area can be aimed at.

  In addition, extending in the opening direction is not particularly limited, and means extending in the opening direction in a linear shape, a waveform, a mountain shape, or the like.

  In the gaming machine E1, a gaming surface E2 characterized in that the guide surface includes an outer inclined portion that is inclined downward and outward in the width direction of the gaming area.

  According to the gaming machine E2, in addition to the effects of the gaming machine E1, the guide surface is provided with the outer inclined portion, so that the velocity of the ball flowing into the guide surface from the width direction outside can be decelerated by gravity acceleration. The deceleration time can be shortened.

  In the gaming machine E1 or E2, a non-falling area in which a ball can not flow down is formed obliquely above at least one of the first out port or the second out port.

  According to the gaming machine E3, in addition to the effects of the gaming machine E1 or E2, the flow of the ball flowing obliquely downward from the non-flowing area to the guide surface is restricted, so the flow of the ball to the guide surface The number of paths can be reduced. Therefore, it is possible to narrow the rebounding direction of the falling ball. Thereby, the outer shape of at least one of the first out port or the second out port can be narrowed.

  In the gaming machine E3, an opening / closing device which is disposed in the gaming area and which can be opened and closed to the front side is disposed above at least one of the first out port or the second out port. A game machine E4 formed on the front side of the opening / closing device;

  According to the gaming machine E4, in addition to the effects produced by the gaming machine E3, the non-flowing area is formed by the opening / closing device. Thereby, the space which arises by restrict | limiting the opening dimension of the direction to the non-flow area side of a 1st out port or a 2nd out port can be utilized as an arrangement | positioning space of a switchgear.

  In the closed state, the opening / closing device allows the ball flowing down the front of the opening / closing device to flow downward to the game area, and when the opening state is open, the ball flowing in front of the opening / closing device to the back of the game area Has the ability to drain. Therefore, the non-falling area can be formed more reliably than when the ball flows down irregularly due to collision with a nail or the like.

  In any one of the game machines E1 to E4, a game machine E5 including a direction adjustment rib extended in a rib shape in an opening direction on an upper bottom surface of the first out port or the second out port.

  According to the gaming machine E5, in addition to the effects of any of the gaming machines E1 to E4, the upper bottom surface of the first out port or the second out port is provided with a direction adjusting rib extended in a rib shape in the opening direction. The resistance to the ball flowing down while colliding with the upper bottom surface of the first out port or the second out port can be suppressed.

  A gaming machine F1 according to any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, and E1 to E5, wherein the gaming machine is a slot machine. Among them, as a basic configuration of the slot machine, “a variable display means for dynamically displaying an identification information sequence consisting of a plurality of identification information and subsequently displaying the identification information is provided, and the operation of the starting operation means (for example, operation lever) The dynamic display of the identification information is started as a result, and the dynamic display of the identification information is stopped due to the operation of the stop operation means (stop button) or when the predetermined time elapses. It is a gaming machine provided with a special gaming state generation means for generating a special gaming state advantageous to the player, as a necessary condition that the final identification information of is a specific identification information. In this case, the game medium may be a coin, a medal or the like as a representative example.

  A gaming machine F2 characterized in that the gaming machine is a pachinko gaming machine in any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, E1 to E5. Above all, the basic configuration of a pachinko gaming machine is provided with an operating handle, and in response to the operation of the operating handle, the ball is fired to a predetermined game area, and the ball is at an operating opening arranged at a predetermined position in the game area. As a necessary condition for winning (or passing through the operation opening), identification information dynamically displayed on the display means may be determined and stopped after a predetermined time. In addition, when the special game state occurs, the variable winning device (specific winning opening) disposed at a predetermined position in the gaming area is opened in a predetermined manner to enable the ball to be won, and the value according to the number of winnings There is a case where a value (including not only prize balls but also data etc. written to a magnetic card) is given.

  In any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, E1 to E5, the gaming machine is characterized in that a pachinko gaming machine and a slot machine are merged. Machine F3. Among them, as a basic configuration of the integrated gaming machine, "a variable display means for dynamically displaying an identification information sequence consisting of a plurality of identification information and subsequently displaying identification information, and for starting operation means (for example, operation lever) Fluctuation of the identification information is started due to the operation of, and the dynamic display of the identification information is stopped due to the operation of the operation means for stop (for example, the stop button) or when a predetermined time elapses. A special game state generation means for generating a special game state advantageous to the player, provided that the finalized identification information upon stopping is the specific identification information, and using a ball as a game medium and the identification information In order to start the dynamic display of the game, a predetermined number of balls are required, and when a special gaming state occurs, a large number of balls are paid out.

10 Pachinko machines (game machines)
13 game board 65 1st variable winning a prize device (opening and closing device)
313 Movable effect member (inside board)
314 1st out port 315 2nd out port 315a guide rib (direction adjustment rib)
320 Lower left plate member (lower plate part)
322 Buffer rib 324 step 330 lower right plate member (lower plate)
332 buffer rib 512 first shaft portion (first shaft)
540, 6540 Telescopic effect device (movable member)
541 Body member (part of the middle member)
544 Slide plate (part of the intermediate member)
545 Slide rail (part of the intermediate member)
541b projection 541e guide fastening portion (positioning assistance portion)
550, 5550, 6550 Rotating arm members (arm members, stopper members)
553 Modified long hole (insertion part)
553d Selected Wall (Selected Area)
554 Arc-shaped hole (insertion part)
554a mouth part (groove part)
554b First stopper surface (part of insertion part)
554c Second stopper surface (part of insertion part)
560 Second drive unit (drive unit)
570 Rotating Crank Member (Crank Member)
574 Sliding projection (projection)
610, 7610 Base member 613 first axial support hole (support portion)
614 Second shaft support hole (shaft support)
620, 4620 effect member (movable member)
621a Sliding shaft (protrusion)
630 1st drive (drive)
640, 2640, 3640, 4640, 7640 Transmission member (transmission member, movable member)
641, 2641, 3641 body part 643 sliding hole (insertion part)
644 Contact part 650 Torsion spring (biasing device, elastic spring)
652 Biasing arm (long member)
653a bending part (first bending point)
3641a Inclined side (tip enlargement area)
5556 Recess (outer recess)
7613 Sliding hole (support part)
7643 Shaft support hole (insertion part)
D margin

  The present invention relates to a gaming machine such as a pachinko machine.

  In a gaming machine such as a pachinko machine, there is a gaming machine provided with a movable member formed movably and a stopper member for restricting the movement width of the movable member (Patent Document 1).

JP, 2012-016623, A

  However, in the above-described conventional gaming machine, there is a problem that there is room for improvement in the aspect of the arrangement of the stopper member.

  The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a good gaming machine in which the stopper member is disposed.

  In order to achieve this object, the gaming machine according to claim 1 is movable along a predetermined movement trajectory, and movable members which can be arranged at different first and second positions, and the movable members thereof. The movement width of the predetermined movement trajectory of the movable member is restricted by moving in correspondence with the movable member, and the movable member is arranged at the first position or at the second position. And a stopper member that changes the moving width of the movable member depending on whether it is moved or not.

  According to the gaming machine of the first aspect, it is possible to improve the mode of arrangement of the stopper member.

It is a front view of a pachinko machine in a 1st embodiment. It is a front view of a game board of a pachinko machine. It is a rear view of a pachinko machine. It is a block diagram which shows the electric constitution of a pachinko machine. It is a disassembled front perspective view of a game board and an operation unit. It is a disassembled front perspective view of an operation | movement unit. It is a disassembled front perspective view of an operation | movement unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front view of an operation unit. It is a front disassembled perspective view of a board and a board lower unit. It is a front disassembled perspective view of a board lower part unit. (A) is a front view of a base member, a 1st out port, a 2nd out port, a lower left board member, and a lower right board member, (b) is a base member in the XVb-XVb line of Drawing 15 (a) And FIG. 12 is a cross-sectional view of the lower left plate member. It is a front perspective view of an up-and-down operation unit. It is a rear perspective view of an up-and-down operation unit. It is a front disassembled perspective view of a vertical motion unit. It is a back surface disassembled perspective view of an up-and-down operation unit. It is a front view of a vertical motion unit. It is a front view of a vertical motion unit. It is a front perspective view of a compound operation unit. It is a rear perspective view of a compound operation unit. It is a front disassembled perspective view of a compound operation unit. FIG. 7 is a rear exploded perspective view of the combined operation unit. It is a front disassembled perspective view of an expansion-contraction production apparatus. It is a back surface disassembled perspective view of an expansion-contraction production apparatus. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. It is a front view of a rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. (A) And (b) is a front view of rotation arm member and a rotation crank member. It is a graph showing the distance from a standard horizontal line of a projection part. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front perspective view of a tilting operation unit and a slide operation unit. It is a rear perspective view of a tilting operation unit and a slide operation unit. It is a front disassembled perspective view of a slide operation unit. It is a rear exploded perspective view of a slide operation unit. It is a front disassembled perspective view of a tilting operation unit. It is a rear exploded perspective view of a tilting operation unit. It is a front disassembled perspective view of a presentation member and a 2nd drive device. (A) And (b) is a front view of a transmission member and a torsion spring. (A) And (b) is a front view of a transmission member and a torsion spring. It is a schematic diagram which shows typically the rocking angle of the presentation member with respect to the rocking angle of a transmission member. It is a front view of a tilting operation unit and a slide operation unit. It is a front view of a tilting operation unit and a slide operation unit. (A) And (b) is a front view of the transmission member and torsion spring in 2nd Embodiment. It is a front view of a transmission member and a torsion spring. (A) And (b) is a front view of the transmission member and torsion spring in 3rd Embodiment. (A) is a back perspective view of the transmission member in 4th Embodiment, (b) is a back perspective view of a movement contact member. (A) And (b) is a rear perspective view of a transmission member, (c) and (d) is a top view of a transmission member. It is a front schematic diagram which illustrated the main body member of a production member typically. It is a front view of a transmission member and a torsion spring. It is a front view of the compound operation unit in a 5th embodiment. It is a front view of a compound operation unit. It is a front view of a compound operation unit. It is a front view of a compound operation unit. FIG. 69 (a) is a partial front view of the pivoting arm member in the sixth embodiment, and FIG. 70 (b) is a partial top view of the pivoting arm member in the direction of arrow LXIXb in FIG. ) Is a partial front view of a pivoting arm member. (A) And (b) is a front perspective view of a switching device. (A) And (b) is a front view of a compound operation unit. (A) And (b) is a front view of the tilting operation unit in 7th Embodiment.

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

  As shown in FIG. 1, the pachinko machine 10 has an outer frame 11 in which an outer shell is formed by a substantially rectangular combination of wooden frames, and an outer frame 11 having substantially the same outer shape as the outer frame 11. And an inner frame 12 supported so as to be openable and closable. In the outer frame 11, metal hinges 18 are attached to upper and lower two places on the left side in front view (see FIG. 1) to support the inner frame 12, and the side on which the hinge 18 is provided is used as an opening / closing axis A frame 12 is supported so as to be openable and closable to the front side.

  In the inner frame 12, the game board 13 (see FIG. 2) having a large number of nails and winning openings 63, 64 and the like is detachably mounted from the back side. A ball (game ball) flows down the front of the game board 13 to play a ball game. In the inner frame 12, a ball emitting unit 112a (see FIG. 4) for emitting balls to the front area of the game board 13 and a ball for guiding balls emitted from the ball emitting unit 112a to the front area of the game board 13 Rails (not shown) and the like are attached.

  On the front side of the inner frame 12, a front frame 14 covering the upper front side and a lower tray unit 15 covering the lower side are provided. In order to support the front frame 14 and the lower tray unit 15, metal hinges 19 are attached to upper and lower two places on the left side of the front view (see FIG. 1), and the side on which the hinge 19 is provided is the front frame The lower tray unit 14 and the lower tray unit 15 are supported so as to be able to open and close to the front side. The locking of the inner frame 12 and the locking of the front frame 14 are released by inserting a dedicated key into the key hole 21 of the cylinder lock 20 and performing a predetermined operation.

  The front frame 14 is formed by assembling a decorative resin part, an electric part, and the like, and a window portion 14 c having an opening formed in a substantially elliptical shape is provided at a substantially central portion thereof. A glass unit 16 having two glass sheets is disposed on the back side of the front frame 14, and the front of the game board 13 can be visually recognized on the front side of the pachinko machine 10 through the glass unit 16.

  In the front frame 14, an upper plate 17 for storing balls is formed in a substantially box shape with an open upper surface projecting to the front side, and prize balls, lending balls, etc. are discharged to the upper plate 17. The bottom surface of the upper plate 17 is formed to be inclined downward to the right as viewed from the front (see FIG. 1), and the inclination thereof guides the ball thrown into the upper plate 17 to the ball firing unit 112a (see FIG. 4). Further, a frame button 22 is provided on the upper surface of the upper plate 17. The frame button 22 is operated by the player, for example, when changing the stage of the effect displayed on the third symbol display device 81 (see FIG. 2) or changing the content of the effect of super reach. Ru.

  The front frame 14 is provided with light emitting means such as various lamps around its periphery (for example, a corner portion). These light emitting means are controlled to change the light emission mode by lighting up or flashing according to the change in the gaming state at the time of a big hit, a predetermined reach time, etc., and play a role of enhancing the rendering effect during the game. The electric decoration parts 29-33 which incorporated light emission means, such as LED, are provided in the periphery of the window part 14c. In the pachinko machine 10, these electric decoration parts 29 to 33 function as effect lamps such as a big hit lamp, and at the time of big hit or reach production etc., each electric decoration part 29 to 33 is lit by lighting and blinking of the built-in LED. Alternatively, it blinks to notify that it is in the middle of a jackpot, or that it is in reach before the jackpot. Further, at the upper left portion of the front frame 14 in a front view (see FIG. 1), a light emitting means such as an LED is incorporated and provided with a display lamp 34 capable of displaying a payout ball and an error occurrence time.

  A small window 35 is formed on the right side below the electric decoration 32 so that a transparent resin is attached from the back side so that the back side of the front frame 14 can be seen, and the bonding space K1 on the front of the game board 13 (see FIG. 2) is made visible from the front of the pachinko machine 10. In addition, in the pachinko machine 10, a plating member 36 made of ABS resin plated with chromium is attached to the area around the electric decoration parts 29 to 33 in order to create more refreshingness.

  Under the window portion 14c, a ball rental operation unit 40 is disposed. The rental ball operation unit 40 is provided with a frequency display unit 41, a ball rental button 42, and a return button 43. When the rental ball operation unit 40 is operated with a bill, a card, etc. being inserted into a card unit (ball lending unit) (not shown) arranged on the side of the pachinko machine 10, the ball is A loan will be made. Specifically, the frequency display unit 41 is an area in which the remaining amount information of a card or the like is displayed, and the built-in LED lights up and the remaining amount is displayed as a number as remaining amount information. The ball lending button 42 is operated to obtain a lending ball based on the information recorded in the card etc. (recording medium), and the lending ball supplies the upper plate 17 as long as the remaining amount is present in the card etc. Be done. The return button 43 is operated when it is requested to return a card or the like inserted in the card unit. In the case of a pachinko machine in which a ball is lent directly to the upper plate 17 from a ball lending device or the like without passing through a card unit, a so-called cash machine does not require the ball operating unit 40. In this case, the ball operating unit 40 is used. A decorative seal or the like may be added to the installation part of to make the part configuration common. A pachinko machine using a card unit and a cash machine can be shared.

  In the lower tray unit 15 located below the upper tray 17, a lower tray 50 for storing the balls that can not be stored in the upper tray 17 is formed in a substantially box shape whose upper surface is opened at the central portion thereof There is. On the right side of the lower plate 50, an operation handle 51 operated by the player to drive a ball into the front of the game board 13 is disposed.

  Inside the operation handle 51, there are a touch sensor 51a for permitting driving of the ball emission unit 112a, an emission stop switch 51b for stopping emission of the ball during the pressing operation, and rotation of the operation handle 51. A variable resistor (not shown) or the like for detecting the amount of movement operation (rotational position) by a change in electrical resistance is incorporated. When the operation handle 51 is turned clockwise by the player, the touch sensor 51a is turned on, and the resistance value of the variable resistor changes corresponding to the amount of the turning operation, and the resistance value of the variable resistor is changed. The ball is fired with a strength corresponding to the (shooting strength), whereby the ball is struck to the front of the game board 13 with a flying amount corresponding to the operation of the player. Further, in a state where the operation handle 51 is not operated by the player, the touch sensor 51a and the emission stop switch 51b are off.

  At the front lower portion of the lower plate 50, a ball removing lever 52 for operating when discharging the balls stored in the lower plate 50 downward is provided. The ball release lever 52 is always urged in the right direction, and by sliding it in the left direction against the urging, the bottom surface opening formed on the bottom surface of the lower plate 50 is opened. A ball falls naturally from the bottom opening and is discharged. The operation of the ball release lever 52 is usually performed with a box (generally referred to as a "seven box") for receiving the ball discharged from the lower plate 50 below the lower plate 50. The operating handle 51 is disposed on the right side of the lower plate 50 as described above, and the ashtray 53 is attached on the left side of the lower plate 50.

  As shown in FIG. 2, the gaming board 13 has a base plate 60 cut into a substantially square shape in a front view, a large number of nails (not shown) for guiding balls, a windmill, and rails 61 and 62. The first opening 63, the second opening 640, the first variable winning device 65, the second variable winning device 650, the through gate 67, the variable display unit 80, etc. It is attached to the back side of the frame 12 (see FIG. 1). The base plate 60 is made of a light transmissive resin material, and is formed so as to allow the player to visually recognize various structures disposed on the rear surface 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 device unit 80 are disposed in through holes formed in the base plate 60 by router processing, and the game board It is fixed by a tapping screw etc. from the front side of 13.

  The front center portion of the game board 13 can be viewed from the front side of the inner frame 12 through the window portion 14c (see FIG. 1) of the front frame 14. Hereinafter, the configuration of the game board 13 will be described mainly with reference to FIG. The first variable winning device 65 is disposed in a through hole formed in the base member 310 of the lower panel unit 300 by router processing, and is fixed from the front side of the game board 13 by a tapping screw or the like.

  On the front of the game board 13, an outer rail 62 formed by bending a strip-shaped metal plate into a substantially arc shape is planted, and at the inner position of the outer rail 62, a strip-shaped metal plate is formed similarly to the outer rail 62. The arc-shaped inner rail 61 formed in the above is planted. The front outer periphery of the game board 13 is surrounded by the inner rails 61 and the outer rails 62, and the front and back are surrounded by the game board 13 and the glass unit 16 (see FIG. 1). A game area in which a game is played is formed by the behavior of the game. The game area is a front area of the game board 13 and is divided by two rails 61 and 62 and a resin outer edge member 73 connecting the rails (a prize opening and the like are provided and launched). Area where the ball flows down).

  The two rails 61 and 62 are provided to guide the ball fired from the ball launch unit 112a (see FIG. 4) to the top of the game board 13. A return ball preventing member 68 is attached to the end portion (upper left part in FIG. 2) of the inner rail 61, and the situation in which the ball guided to the upper part of the game board 13 once comes back into the ball guide passage is prevented. Be done. At the end of the outer rail 62 (the upper right part in FIG. 2), the rubber return 69 is attached to a position corresponding to the largest flying portion of the ball, and the ball fired with a predetermined momentum strikes the rubber return 69 Is bounced toward the central part while being attenuated.

  First symbol display devices 37A and 37B provided with a plurality of LEDs as light emitting means and a 7-segment display are disposed on the lower left side of the game area (the lower left side in FIG. 2). The first symbol display devices 37A and 37B perform display according to each control performed by the main control unit 110 (see FIG. 4), and display of the gaming state of the pachinko machine 10 is mainly performed. In the present embodiment, the first symbol display devices 37A and 37B are configured to be used according to whether the ball has won the first winning opening 64 or the second winning opening 640. Specifically, when the ball wins the first winning opening 64, the first symbol display device 37A is activated, and when the ball wins the second winning opening 640, the first The symbol display device 37B is configured to operate.

  In addition, the first symbol display devices 37A and 37B indicate whether or not the pachinko machine 10 is in a steady change, a time-short or a normal, by means of LEDs, or indicate whether it is in fluctuation by means of an on-light condition. The stop symbol indicates whether the symbol corresponds to the probability variation big hit or the symbol corresponding to the normal big hit or not by the lighted state, or indicates the number of holding balls by the lighted state, and by the 7-segment display device, the round of the big hit Display numbers and errors. In addition, a plurality of LEDs may be configured to have different emission colors (for example, red, green, blue) of the respective LEDs, and the combination of the emission colors may suggest various gaming states of the pachinko machine 10 with a small number of LEDs. it can.

  In the pachinko machine 10, a lottery is performed in response to the first winning opening 64 and the second winning opening 640 having a winning. In the lottery, the pachinko machine 10 determines whether or not the jackpot is successful (jump lottery), and when it is determined that the jackpot is made, the jackpot type is also determined. As jackpot types determined here, 15R probability variation jackpots, 4R probability variation jackpots, and 15R regular jackpots are prepared. Not only is it shown whether or not the result of the lottery is a big hit as the stop symbol after the end of the fluctuation in the first symbol display devices 37A, 37B, and if it is a big hit, a symbol according to the big hit type is shown .

  Here, "15R probability variation jackpot" is a probability variation jackpot where the maximum number of rounds shifts to a high probability state after 15 round jackpots, and "4R probability variation jackpot" is a maximum number of round jackpots with 4 rounds It is a probability change jackpot to shift to a high probability state after. Also, “15R normal jackpot” is a jackpot in which the maximum number of rounds transitions to a low probability state after jackpots of 15 rounds and for a predetermined number of fluctuations (for example, 100 fluctuation numbers) becomes a short time state. is there.

  Also, "high probability state" refers to a state in which the subsequent jackpot probability is increased as added value after the end of the jackpot, so-called probability fluctuation (during a definite change), in other words, a game that is easy to shift to a special gaming state The state of The high probability state (during a definite change) in the present embodiment includes a game state in which the ball is likely to be won in the second winning opening 640 by increasing the hitting probability of the second symbol described later. The term "low probability state" refers to a time when the probability of change is not positive, and a state where the jackpot probability is normal, that is, a state in which the jackpot probability is lower than that of probability change. Moreover, with the time saving state (time saving) of the "low probability state", the jackpot probability is a normal state, and only the jackpot probability of the second symbol is increased with the jackpot probability unchanged, and the second winning opening 640 To say the state of the game where the ball is easy to win. On the other hand, when the pachinko machine 10 is normally medium is the state of the game which is neither a definite change nor a time reduction (a state in which neither the jackpot probability nor the hit probability of the second symbol is increased).

  The probability change of the second symbol not only increases during a definite change or time, but also the time when the motorized accessory 640a attached to the second winning opening 640 is changed, and a longer time than normal It is set. When the motorized part 640a is in the open state (open state), the ball reaches the second winning opening 640 compared to when the motorized part 640a is in the closed state (closed state). It becomes easy condition. Therefore, the ball is likely to be won in the second winning opening 640 during a definite change or during a time cut, and it is possible to increase the number of times a jackpot lottery is performed.

  In addition, in addition to changing the opening time of the motorized role thing 640a attached to the second winning a prize opening 640 during a definite change or during a short time, or in addition to changing the opening time, the electric operation per hit A change may be made to increase the number of times the accessory 640 a is released more than in the normal mode. In addition, the probability of hitting the second symbol does not change during definite changes or during a short time, and the electric symbol 640a is opened at a time and once when the electric symbol 640a associated with the second winning opening 640 is opened. At least one of the numbers may be changed. In addition, the time during which the electric winning combination 640a associated with the second winning opening 640 is open or the number of times the electric combination 640a is opened per hit does not occur during a certain change or during a short time, and the second symbol is hit Only the probability may be changed to be up relative to normal.

  In the game area, there are provided a plurality of general winning openings 63 in which five to fifteen balls are paid out as winning balls by winning balls. Further, a variable display device unit 80 is disposed in the central portion of the game area. The variable display device unit 80 is triggered by winnings (start winnings) to the first winning opening 64 and the second winning opening 640, while being synchronized with the variable display in the first symbol display devices 37A and 37B, the third symbol A third symbol display device 81 configured of a liquid crystal display (hereinafter simply referred to as “display device”) that performs variable display, and an LED that variably displays the second symbol triggered by the passage of a ball of through gate 67 A second symbol display device (not shown) is provided. Further, a center frame 86 is disposed in the variable display unit 80 so as to surround the outer periphery of the third symbol display device 81.

  The third symbol display device 81 is configured of a large 9-inch liquid crystal display, and the display content is controlled by the display control device 114 (see FIG. 4), for example, the upper, middle and lower 3 One symbol column is displayed. Each symbol row is constituted by a plurality of symbols (third symbol), and the third symbol is variably displayed on the display screen of the third symbol display device 81 by horizontally scrolling these third symbols for each symbol row It is supposed to be. The third symbol display device 81 of the present embodiment is the first symbol display device 37A, 37B in which the display of the gaming state accompanied by the control of the main control device 110 (see FIG. 4) is performed, but the first A decorative display is performed according to the display of the symbol display devices 37A and 37B. The third symbol display device 81 may be configured using, for example, a reel instead of the display device.

  The second symbol display device alternately turns on the symbol “o” and the symbol “x” as display symbols (the second symbol (not shown)) for a predetermined time each time the ball passes through gate 67 It is a variable display. In the pachinko machine 10, when it is detected that the ball has passed the through gate 67, a winning lottery is performed. If it is a result of the winning lottery, if it is a hit, the symbol of "o" is stopped and displayed after the variation display of the second symbol in the second symbol display device. Further, if the result of the winning lottery is out of alignment, the symbol "x" is stopped and displayed after the variation display of the third symbol in the second symbol display device.

  In the pachinko machine 10, when the variable display in the second symbol display device is stopped at a predetermined symbol (in the present embodiment, the symbol "o"), the motorized role 640a attached to the second winning opening 640 has a predetermined time It is configured to be activated (opened) only.

  The time taken for the variable display of the second symbol is set so as to be shorter during the probability change or during the time saving than when the gaming state is normal. As a result, since the variation display of the second symbol is performed in a short time during the definite change and during the short time, it is possible to perform the winning lottery more frequently than in the middle. Therefore, since the chance of winning in the winning lottery increases, it is possible to give the player a lot of opportunities for the electric winning combination 640 a of the second winning opening 640 to be in the open state. Therefore, it is possible to make it easy for the ball to win the second winning opening 640 during the probability change and during the time saving.

  In addition, the second winning opening 640 during the definite change or time reduction by other methods, such as increasing the open probability and increasing the opening time and opening number of the motorized combination 640a per hit, which increases the hit probability during definite change or time reduction. When the ball is in a state in which it is easy to win, the time taken for the variable display of the second symbol may be constant regardless of the gaming state. On the other hand, when the time taken for the variable display of the second symbol is set shorter during the definite change or during the short time than during the normal time, the winning probability may be made constant regardless of the gaming state, and a single hit The opening time and the number of times of opening of the motorized role product 640a with respect to may be constant regardless of the gaming state.

  The through gate 67 is assembled to the game board on the right side in the lower area of the variable display unit 80, and among the balls fired on the game board, a part of the ball flowing down the right of the game board can pass Is configured. When the ball passes through gate 67, a lottery for winning the second symbol is performed. After the winning lottery, the variable display is performed on the second symbol display device, and if the result of the winning lottery is a hit, the symbol of "○" is displayed as a stop symbol of the variable display, and the result of the winning lottery is out For example, the symbol of "x" is displayed as a stop symbol of the variable display.

  The number of times the ball passes through gate 67 is held up to a total of four times, and the number of balls held is indicated by the above-mentioned first symbol display devices 37A and 37B and the second symbol hold lamp (not shown) Is also displayed. Four second symbol holding lamps are provided for the maximum number of holdings, and are arranged symmetrically below the third symbol display device 81.

  In addition, as the variable display of the second symbol is performed by switching on and off of a plurality of lamps in the second symbol display device as in the present embodiment, the first symbol display devices 37A, 37B and the third A part of the symbol display device 81 may be used. Similarly, the lighting of the second symbol holding lamp may be performed by part of the third symbol display device 81. Further, the maximum number of holding balls for the passage of the ball of the through gate 67 is not limited to four times, and may be set to three times or less, or five times or more (for example, eight times). Further, the number of through gates 67 assembled is not limited to one, and may be plural (for example, two). Further, the assembly position of the through gate 67 is not limited to the right side of the variable display unit 80, and may be, for example, the left side of the variable display unit 80. Further, since the number of balls held is indicated by the first symbol display devices 37A and 37B, the second symbol holding lamp may not perform the lighting display.

  Below the variable display unit 80, there is disposed a first winning opening 64 in which a ball can be won. When the ball is won in the first winning opening 64, the first winning opening switch (not shown) provided on the back side of the game board 13 is turned on, and the main control unit 110 is turned on due to the turning on of the first winning opening switch. A lottery for a big hit is made at (see FIG. 4), and a display corresponding to the lottery result is shown by the first symbol display device 37A.

  On the other hand, on the right side in a front view of the first winning opening 64, a second winning opening 640 in which a ball can win is disposed. When a ball is won in the second winning opening 640, a second winning opening switch (not shown) provided on the back side of the game board 13 is turned on, and the main control unit 110 is turned on due to the second winning opening switch being turned on. A lottery for a big hit is made at (see FIG. 4), and a display corresponding to the lottery result is shown by the first symbol display device 37B.

  Further, each of the first winning opening 64 and the second winning opening 640 is also one of the winning openings in which five balls are paid out as winning balls when the balls win. In the present embodiment, the number of winning balls to be paid out when the ball is won in the first winning opening 64 and the number of winning balls to be paid out when the ball is winning in the second winning opening 640 are configured the same. The number of winning balls to be paid out when the ball has won the first winning opening 64 and the number of winning balls to be paid out when the second winning opening 640 has the ball, for example, to the first winning opening 64 The number of winning balls to be paid out when the player wins a prize may be three, and the number of winning balls to be paid out when the second prize winning hole 640 has won may be five.

  The second winning opening 640 is accompanied by a motorized role 640 a. The electric role object 640a is configured to be openable and closable, and normally, the electric role object 640a is in a closed state (shrinkage state), and it is difficult for the ball to win the second prize opening 640. On the other hand, when the symbol of "o" is displayed on the second symbol display device as a result of the fluctuation display of the second symbol performed triggered by the passage of the ball to the through gate 67, the motorized role piece 640a is in the open state (enlarged State), and the ball is likely to win the second winning opening 640.

  As mentioned above, the probability of hitting the second symbol is higher than that in the normal condition, and the time taken for the variable display of the second symbol is short as compared to the normal, and therefore, in the variable display of the second symbol The symbol of “” becomes easy to be displayed, and the number of times that the motorized role piece 640 a is in the open state (enlarged state) is increased. Furthermore, during definite period of time and short time, the time when the motorized accessory 640a is opened is also longer than usual. Therefore, it is possible to create a state in which the ball is more likely to win to the second winning opening 640 compared to the normal time during definite variation and during time saving.

  Here, the probability of being a big hit is the same in either the low probability state or the high probability state in the case where the ball has won in the first winning opening 64 and the case in which the ball has won in the second winning opening 640. However, the probability of becoming a 15R probability variation jackpot as the type of jackpot selected when jackpot is higher is higher in the case where the ball has won in the second winning opening 640 than in the case where the ball has won in the first winning opening 64 It is set. On the other hand, the first winning opening 64 does not have a motorized part like the second winning opening 640, and the ball is always in a state where it is possible to win.

  Therefore, during the normal operation, there are many cases in which the motorized prize associated with the second winning opening 640 is in the closed state, and it is difficult to win the second winning opening 640, and therefore, it is directed to the first prize opening 64 without the electric jack. Launch the ball so that the ball passes the left side of the variable display unit 80 (so-called "left-handed"), and the winning of the first winning opening 64 gives a lot of opportunities for a big hit lottery and becomes a big hit It is advantageous for the player to aim at things.

  On the other hand, the electric gate 640a attached to the second winning opening 640 is likely to be in the open state by passing the ball through the through gate 67 during definite variation or time, and it is easy to win the second winning opening 640. The ball is fired so that the ball passes the right side of the variable display 80 toward the second winning hole 640 (so-called "right-handed"), and the motor gate is opened by passing through the through gate 67. It is advantageous for the player to aim at becoming a 15R probability variation jackpot by winning in the second winning opening 640.

  As described above, the pachinko machine 10 according to the present embodiment emits a ball to the player according to the gaming state of the pachinko machine 10 (whether it is in the process of being changed, time is short, or is normal). You can change the way of “right-handed” and “right-handed”. Therefore, the player can enjoy the game because it can change the way of hitting the ball.

  A first variable winning device 65 is disposed on the lower right side of the first winning opening 64, and a first specified winning opening 65a is provided substantially at the center thereof. In addition, a second variable winning device 650 is disposed on the left side of the variable display device 80, and a second central portion of the second variable winning device 650 has a circular shape similar in size to the other winning openings 63, 64 and 640. A specific winning hole 650a is provided. In the pachinko machine 10, when the jackpot lottery performed due to the winning in the first winning opening 64 or the second winning opening 640 becomes a big hit, after a predetermined time (variation time) has elapsed, the stop symbol of the big hit and The first symbol display device 37A or the first symbol display device 37B is turned on, and the stop symbol corresponding to the jackpot is displayed on the third symbol display device 81, and the occurrence of the jackpot is indicated. Thereafter, the gaming state transitions to a special gaming state (big hit) in which the ball is easy to win. In this special game state, the special winning openings 65a and 650a which are normally closed are opened for a predetermined time (for example, until 30 seconds have elapsed or 10 balls have been won).

  The specific winning opening 65a, 650a is closed when a predetermined time passes, and after the closing, the specific winning opening 65a, 650a is opened again for a predetermined time. The opening / closing operation of the specific winning opening 65a, 650a can be repeated, for example, 15 times (15 rounds) at the maximum. The state in which the opening and closing operation is being performed is a form of special gaming state advantageous to the player, and the player is paid out a larger amount of prize balls than usual as the provision of the gaming value (game value). Is done.

  Specifically, the first variable winning device 65 is a horizontally long rectangular opening / closing plate covering the first specified winning opening 65a, and a large opening solenoid 65b for opening / closing drive to the right with the lower side of the opening / closing plate as an axis See FIG. 15, only the outline is shown). The first specified winning combination opening 65 a is normally in a closed state in which the ball can not win or is difficult to win. In the case of a big hit, the large opening solenoid 65b is driven to tilt the opening / closing plate to the front side, and the ball temporarily forms an open state in which the first specified winning opening 65a is easy to win, and the open state and normal time It operates so as to alternately repeat the state with the closed state of.

  Specifically, the second variable winning device 650 is opened and closed on the left and right of the second specified winning opening 650a on the left and right sides of the opening and closing plate of the front view triangular shape and the lower side of the opening and closing plate. And a large open port solenoid (not shown). The second specified winning opening 650a is normally in a closed state in which the ball can not win or is difficult to win. In the case of a big hit, the small opening solenoid is driven to tilt the opening / closing plate to the left, and the ball temporarily forms an open state in which the second specified winning opening 650a is easy to win, and the open state and normal time It operates so as to alternately repeat the state of the closed state.

  In the present embodiment, it is possible to make the second variable winning device 650 win a ball by performing left hitting, so eliminating the hassle of switching between left hitting and right hitting whenever the gaming state changes. can do.

  In addition, the special gaming state is not limited to the above-mentioned form. A large opening is provided in the game area which is opened and closed separately from the specific winning openings 65a and 650a, and the specific winning openings 65a and 650a are for a predetermined time when the LED corresponding to the large hit is lit in the first symbol display devices 37A and 37B. When the specific winning opening 65a, 650a is opened, the large opening opening provided separately from the specific winning opening 65a, 650a is triggered by the ball winning into the specific winning opening 65a, 650a during a predetermined time. A gaming state opened a predetermined number of times may be formed as a special gaming state. Further, the specific winning hole 65a, 650a is not limited to one, and one or more (for example, three) may be disposed, and the arrangement position is also the lower right side of the first winning hole 64, or Not limited to the left side of the variable display device 80, for example, it may be below the first winning opening 64.

  In the lower right corner of the game board 13, a sticking space K1 for sticking a certificate stamp, an identification label or the like is provided, and a test piece stamped on the sticking space K1 is a small window of the front frame 14. It can be viewed through 35 (see FIG. 1).

  The game board 13 is provided with a first out port 314 and a second out port 315. A ball that flows down the game area and does not win any of the winning openings 63, 64, 65a, 640, 650a is discharged through the first out port 314 or the second out port 315. You will be guided to the road. The first out port 314 is disposed below the left side of the first winning port 64, while the second out port 315 is disposed below the right side of the first prize port 64. That is, the second out port 315 is disposed on the opposite side of the first out port 314 with the first winning port 64 interposed therebetween.

  Therefore, a ball flowing down the game area, which reaches the lower end (inner rail 61 or outer edge member 73) of the game area on the right side (right side in FIG. 2) of the first winning opening 64 in the front view is the inner rail 61 Alternatively, it is flowed down along the slope of the outer edge member 73 and guided to the ball discharge path through the second out port 315, while the lower end (inner rail 61) of the game area on the left side in front view than the first winning port 64. The ball reached is flowed down along the slope (curve) of the inner rail 61 and is guided to the ball discharge path through the first out port 314.

  A large number of nails are implanted in the game board 13 in order to appropriately disperse and adjust the falling direction of the ball, and various members (features) such as a windmill are disposed.

  As shown in FIG. 3, control board units 90 and 91 and a back pack unit 94 are mainly provided on the rear surface side of the pachinko machine 10. The control board unit 90 is integrated with a main board (main controller 110), an audio lamp control board (audio lamp control apparatus 113), and a display control board (display control apparatus 114). In the control board unit 91, a delivery control board (delivery control device 111), a emission control board (firing control device 112), a power supply board (power supply device 115), and a card unit connection board 116 are mounted and unitized.

  In the back pack unit 94, a back pack 92 forming a protective cover and a dispensing unit 93 are unitized. In addition, each control board is used as an MPU as a one-chip microcomputer that controls each control, a port to communicate with various devices, a random number generator used in various lottery, time counting and synchronization etc. Clock pulse generation circuits etc. are mounted as needed.

  The main control unit 110, the audio lamp control unit 113 and the display control unit 114, the payout control unit 111 and the emission control unit 112, the power supply unit 115, and the card unit connection board 116 are accommodated in the substrate boxes 100 to 104, respectively. . The substrate boxes 100 to 104 each include a box base and a box cover that covers the opening of the box base. The box base and the box cover are connected to each other to accommodate the control devices and the respective substrates.

  In addition, the substrate box 100 (main controller 110) and the substrate box 102 (dispensing controller 111 and firing controller 112) connect the box base and the box cover unsealably (sealing structure) by a sealing unit (not shown) Consolidated). Further, a seal seal (not shown) is pasted over the box base and the box cover at the connection portion between the box base and the box cover. The sealing seal is made of a brittle material, and if it is attempted to peel off the sealing seal to open the substrate box 100 or 102, or if the substrate box 100 or 102 is to be opened forcibly, the box base side and the box cover It is cut to the side. Therefore, by confirming the sealing unit or the sealing seal, it can be known whether or not the substrate box 100, 102 has been opened.

  Dispensing unit 93 is located at the top of back pack unit 94 and opens upward, tank 130, tank rail 131 connected to the lower side of tank 130 and gently inclined toward the downstream side, and downstream of tank rail 131. A case rail 132 vertically connected to the side, and a dispensing device 133 provided at the most downstream portion of the case rail 132 for dispensing balls by a predetermined electrical configuration of the dispensing motor 216 (see FIG. 4) ing. The balls supplied from the island facility of the game hall are successively replenished to the tank 130, and the required number of balls are paid out by the payout device 133 as appropriate. The tank rail 131 is attached with a vibrator 134 for applying vibration to the tank rail 131.

  In addition, the payout control device 111 is provided with the state recovery switch 120, the emission control device 112 is provided with the operation knob 121 of the variable resistor, and the power supply device 115 is provided with the RAM erase switch 122. The state recovery switch 120 is operated to eliminate the ball clogging (return to the normal state) when a dispensing error occurs, such as a ball clogging of the dispensing motor 216 (see FIG. 4) portion, for example. 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 in order to return the pachinko machine 10 to the initial state.

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

  The main controller 110 is mounted with an MPU 201 as a one-chip microcomputer which is an arithmetic device. The MPU 201 is a ROM 202 storing various control programs to be executed by the MPU 201 and fixed value data, and a memory for temporarily storing various data etc. when the control program stored in the ROM 202 is executed. A certain RAM 203 and various circuits such as an interrupt circuit, a timer circuit, and a data transmission / reception circuit are incorporated. In the main control unit 110, main processing of the pachinko machine 10, such as a jackpot lottery, display setting in the first symbol display devices 37A and 37B and the third symbol display device 81, and lottery of display results in the second symbol display device by the MPU 201 Run.

  Although various commands are transmitted from the main control unit 110 to the sub control unit by the data transmission / reception circuit in order to instruct the sub control units such as the payout control unit 111 and the audio lamp control unit 113 to operate. Such command is transmitted from the main control unit 110 to the sub control unit in one direction only.

  The RAM 203 is a stack area in which various areas, counters, flags, contents of internal registers of the MPU 201, return addresses of control programs executed by the MPU 201, etc. are stored, various flags and counters, I / O, etc. And a work area (work area) in which values are stored. The RAM 203 is configured to be able to receive data (backup) supplied with a backup voltage from the power supply 115 even after the pachinko machine 10 is powered off, and all data stored in the RAM 203 is backed up. .

  When the power is shut off due to the occurrence of a power failure or the like, the stack pointer at the time of the power shutoff (including the time of the power failure, the same applies hereinafter) and the value of each register are stored in the RAM 203. On the other hand, when the power is turned on (including the power on after the power failure is eliminated, the same applies hereinafter), the state of the pachinko machine 10 is restored to the state before the power is shut off based on the information stored in the RAM 203. Writing to the RAM 203 is executed when the power is shut off by a main process (not shown), and restoration of each value written to the RAM 203 is executed in a start-up process (not shown) when the power is turned on. The power failure signal SG1 from the power failure monitoring circuit 252 is input to the NMI terminal (non-maskable interrupt terminal) of the MPU 201 at the time of power interruption due to the occurrence of a power failure or the like. When it is input, NMI interrupt processing (not shown) as processing upon power failure is immediately executed.

  An input / output port 205 is connected to the MPU 201 of the main control unit 110 via a bus line 204 configured by an address bus and a data bus. The input / output port 205 has a payout control device 111, an audio lamp control device 113, first symbol display devices 37A and 37B, a second symbol display device, a second symbol hold lamp, and the lower side of the opening / closing plate of the specified winning opening 65a. A solenoid 209 consisting of a large opening solenoid for opening and closing drive and a solenoid for driving an electric part is connected to the front side, and the MPU 201 receives various commands and control signals via the input / output port 205. Send

  The input / output port 205 includes various switches 208 including a switch group (not shown) and a sensor group including a slide position detection sensor S and a rotational position detection sensor R, and a RAM erase switch circuit 253 provided in the power supply 115 described later. Are connected, and the MPU 201 executes various processes based on the signals output from the various switches 208 and the RAM erase signal SG2 output from the RAM erase switch circuit 253.

  The payout control device 111 drives the payout motor 216 to control the payout of the winning balls and the lending balls. The MPU 211, which is an arithmetic device, has a ROM 212 storing a control program to be executed by the MPU 211, fixed value data and the like, and a RAM 213 used as a work memory or the like.

  The RAM 213 of the payout control device 111 is, like the RAM 203 of the main control device 110, a stack area where 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, various flags and counters , I / O, etc. are stored in the work area (work area). The RAM 213 is configured to be able to receive a backup voltage from the power supply device 115 even after the pachinko machine 10 is turned off and to hold (back up) data, and all data stored in the RAM 213 is backed up. Similar to the MPU 201 of the main control unit 110, the NMI terminal of the MPU 211 is configured to receive the power failure signal SG1 from the power failure monitoring circuit 252 at the time of power interruption due to the occurrence of a power failure or the like. When input to the MPU 211, NMI interrupt processing (not shown) as processing upon power failure is immediately executed.

  An input / output port 215 is connected to the MPU 211 of the payout control device 111 via a bus line 214 configured by an address bus and a data bus. The main controller 110, the payout motor 216, the emission control device 112, and the like are connected to the input / output port 215, respectively. Further, although not shown, the payout control device 111 is connected with a prize ball detection switch for detecting a prize ball paid out. The prize ball detection switch is connected to the payout control device 111 but not connected to the main control device 110.

  The emission control device 112 controls the ball emission unit 112 a so that the ball launch strength according to the amount of rotational operation of the operation handle 51 is obtained when the main controller 110 instructs the ball emission. . The ball launch unit 112a includes a launch solenoid and an electromagnet (not shown), and the launch solenoid and the electromagnet are permitted to be driven when predetermined conditions are met. Specifically, the touch sensor 51a detects that the player is touching the operation handle 51, and the operation is performed on condition that the firing stop switch 51b for stopping the firing of the ball is turned off (not operated). The firing solenoid is excited corresponding to the amount of rotational operation (rotational position) of the handle 51, and the ball is emitted with a strength corresponding to the amount of operation of the operation handle 51.

  The sound lamp control device 113 outputs sound in a sound output device (such as a speaker (not shown)) 226, outputs of lighting and extinguishing in a lamp display device (such as the illumination parts 29 to 33 and the display lamp 34) It controls the setting of the display mode of the third symbol display device 81 and the like performed by the display control device 114 such as display (display) and advance notice effect. The MPU 221, which is an arithmetic device, has a ROM 222 storing a control program executed by the MPU 221, fixed value data, and the like, and a RAM 223 used as a work memory or the like.

  An input / output port 225 is connected to the MPU 221 of the audio lamp control device 113 via a bus line 224 configured by an address bus and a data bus. To the input / output port 225, a main control unit 110, a display control unit 114, an audio output unit 226, a lamp display unit 227, other units 228, a frame button 22 and the like are connected. Other devices 228 include drive motors 431, 466, 531, 561, 631, 661, 751.

  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 commands the determined display mode. The display control device 114 is notified by (display variation pattern command, display stop type command, etc.). In addition, the audio lamp control device 113 monitors the input from the frame button 22, and when the frame button 22 is operated by the player, changes the stage displayed by the third symbol display device 81, or super reach It instructs the display control device 114 to change the effect contents of the hour. When the stage is changed, a rear surface image change command including information on the changed stage is transmitted to display control device 114 in order to display the rear surface image according to the changed stage on third symbol display device 81. . Here, the rear surface image is an image displayed on the rear surface side of the third symbol, which is a 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 in accordance with the command transmitted from the voice lamp control device 113.

  In addition, the audio lamp control device 113 receives a command (display command) representing display content of the third symbol display device 81 from the display control device 114. Based on the display command received from the display control device 114, the sound lamp control device 113 outputs a sound corresponding to the display content from the sound output device 226 in accordance with the display content of the third symbol display device 81. The lighting and extinguishing of the lamp display device 227 are controlled according to the display content.

  The display control device 114 is connected to the voice lamp control device 113 and the third symbol display device 81, and based on the command received from the voice lamp control device 113, the third symbol display effect variation effect of the third symbol display device 81, etc. It controls the display. Further, the display control device 114 appropriately transmits a display command for notifying the display content of the third symbol display device 81 to the voice lamp control device 113. The voice lamp control device 113 matches the display of the third symbol display device 81 with the voice output from the voice output device 226 by outputting the voice from the voice output device 226 according to the display content indicated by the display command. be able to.

  The power supply unit 115 includes a power supply unit 251 for supplying power to each part of the pachinko machine 10, a power failure monitoring circuit 252 for monitoring power interruption due to a power failure, and a RAM provided with a RAM erase switch 122 (see FIG. 3). And an erase switch circuit 253. The power supply unit 251 is a device that supplies necessary operating voltages to the control devices 110 to 114 and the like through a power supply path (not shown). As a summary, the power supply unit 251 takes in a voltage of 24 volts AC supplied from the outside, 12 volts voltage for driving various switches such as various switches 208, solenoids such as solenoid 209, motor, etc. A voltage of 5 volts for logic, a backup voltage for RAM backup, and the like are generated, and these 12 volts, 5 volts and a backup voltage are supplied to the respective control devices 110 to 114 and the like.

  The power failure monitoring circuit 252 is a circuit for outputting the power failure signal SG1 to each NMI terminal of the MPU 201 of the main control device 110 and the MPU 211 of the payout control device 111 when the power is shut off due to the occurrence of a power failure or the like. The power failure monitoring circuit 252 monitors the voltage of the stable DC voltage of 24 volts, which is the maximum voltage output from the power supply unit 251, and determines that a power failure (power loss, power loss) occurs when this voltage becomes less than 22 volts. Then, the blackout signal SG1 is outputted to the main control unit 110 and the payout control unit 111. By the output of the power failure signal SG1, the main controller 110 and the payout control device 111 recognize the occurrence of the power failure, and execute the NMI interrupt process. The power supply unit 251 outputs a 5-volt voltage, which is a driving voltage of the control system, for a time sufficient for execution of the NMI interrupt processing even after the voltage of the DC stable 24 volts becomes less than 22 volts. Is configured to maintain a normal value. Therefore, the main controller 110 and the payout controller 111 can execute and complete the NMI interrupt process (not shown) normally.

  The RAM erase switch circuit 253 is a circuit for outputting a RAM erase signal SG2 for clearing the backup data to the main control unit 110 when the RAM erase switch 122 (see FIG. 3) is pressed. The main control unit 110 controls the payout initialization command for clearing the backup data and causing the payout control unit 111 to clear the backup data when the RAM erase signal SG2 is input when the pachinko machine 10 is powered on. Transmit to the device 111.

  Next, with reference to FIG. 5 to FIG. 12, the gaming board 13 and the operation unit 200 will be described. First, the accommodation structure of each unit 300 to 700 in the back case 210 will be described with reference to FIGS. 5 to 7.

  FIG. 5 is an exploded front perspective view of the game board 13 and the operating unit 200, and FIGS. 6 and 7 are exploded front perspective views of the operating unit 200 in a front view of the operating unit 200 disassembled. Note that FIG. 7 illustrates the combined operation unit 500 mounted on the back case 210.

  As shown in FIGS. 5 to 7, one side (the front side of the sheet of FIG. 6) of the operation unit 200 is opened from the bottom wall portion 211 and the outer wall portion 212 erected from the outer edge of the bottom wall portion 211. A rear case 210 formed in a box shape is provided. The rear case 210 is formed in a rectangular frame shape in a front view by forming a rectangular opening 211 a at the center of the bottom wall portion 211. The opening 211a is formed in a size corresponding to the outer shape of the third symbol display device 81 (see FIG. 2) (that is, the third symbol display device 81 can be disposed).

  In the operation unit 200, the vertical operation unit 400, the combined operation unit 500, the tilting operation unit 600, and the slide operation unit 700 are accommodated in the inner space of the rear case 210, and are configured as one unit.

  Specifically, combined operation unit 500 is disposed in the upper right portion of the region formed by the inner side surface of outer wall portion 212 of rear case 210 (see FIG. 7). With respect to the state shown in FIG. 7, tilting operation unit 600 and slide operation unit 700 are disposed below the area formed by the inner side surface of outer wall portion 212 of rear case 210. Further, with respect to the state shown in FIG. 7, the vertical movement unit 400 is disposed on the front side of the combined movement unit 500 in a stacked state in which the vertical movement unit 400 is stacked and accommodated in the rear case 210 (see FIG. 5).

  As described above, in the present embodiment, another operation unit (for example, the vertical operation unit 400) is disposed in a stacked state in which the predetermined operation unit (for example, the combined operation unit 500) is superimposed on the front side. Therefore, in front view, a given operation unit can be shielded by another operation unit.

  In other words, when the game board 13 (see FIG. 2) is formed of a light transmitting material, and the operation unit disposed on the back side of the game board 13 can be viewed by the player, the predetermined operation unit It is possible to make the player visually recognize only the necessary part of and to shield other parts from the player by other operation units. As a result, it is not necessary to design a predetermined effect member shielded by another operation unit on the premise that the whole is viewed by the player, so that the degree of freedom in the design can be improved. .

  Next, with reference to FIGS. 8 to 10, outlines of operation modes of the vertical movement unit 400, the combined movement unit 500, the tilting movement unit 600, and the slide movement unit 700 will be described. In the description of FIGS. 8 to 10, FIGS. 5 to 7 will be referred to as appropriate.

  8 to 10 are front views of the operation unit 200. FIG. In FIG. 8, the state in which the arm member 440 (see FIG. 18) of the vertical movement unit 400 is disposed at the extended position is the expansion state of the expansion / contraction effect device 540 (see FIG. 26) of the combined movement unit 500 in FIG. 9. The formed state is illustrated in FIG. 10 in which the tilting operation unit 600 is disposed substantially at the center in the width direction.

  As shown in FIG. 8, the vertical movement unit 400 operates the arm member 440 (see FIG. 18) between the retracted position shown in FIG. 5 and the extended position shown in FIG. In the retracted position shown in FIG. 5, the arm member 440 is retracted above the opening 211 a of the back case 210 and is invisible 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 at the center of the opening 211a of the back case 210 (ie, the front of the third symbol display device 81; Placed in).

  As shown in FIG. 9, in the combined operation unit 500, the pivoting arm member 550 (see FIG. 22) is disposed at the downward projecting position, and the front plate member 546 is at the center of the opening 211a of the rear case 210 (ie, 2), and the front plate member 546 is disposed at the opening 211a of the rear case 210, to the retracted position where the pivoting arm member 550 is retracted upward. It is possible to form a contracted state (see FIG. 5) which is retracted upward. In the contracted state shown in FIG. 5, the front plate member 546 is retracted above the opening 211a of the back case 210, and is invisible to the player (see FIG. 2).

  As shown in FIG. 10, in the tilting operation unit 600, the support member 720 (see FIG. 47) of the slide operation unit 700 is slid to the left and right, so that the retracted position shown in FIG. It is movable between positions. In the retracted position shown in FIG. 5, the tilting operation unit 600 is retracted to the right of the opening 211a of the back case 210, and viewed from 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 at the center of the opening 211a of the back case 210 (that is, in front of the third symbol display 81, see FIG. 2).

  In FIG. 10, the state in which the first curtain member 624 and the second curtain member 625 (see FIG. 46) are opened and the liquid crystal device in the inside is viewed is illustrated. That is, when the tilting operation unit 600 is arranged in the state of FIG. 10, the effect displayed on the third symbol display device 81 (see FIG. 2) visually recognized through the opening 211a and the liquid crystal device inside the tilting operation unit 600. The player can visually recognize both of the effects displayed on the screen.

  Each of the operation units 400 to 700 is formed to be independently operable and, as described above, disposed in a stacked (stacked) state, and therefore, among the operation units 400 to 700, With regard to those disposed in different layers, even if the operation member is a mode in which the operation member projects inward of the opening 211a of the back case 210, it can be operated at the same time. That is, as illustrated in FIG. 8 to FIG. 10, not only the respective operation units 400 to 700 can be operated alone, but also these operations can be combined, so that the rendering effect can be enhanced.

  FIG. 11 is a front view of the operation unit 200. FIG. In FIG. 11, the expansion / contraction effect device 540 (see FIG. 22) of the combined operation unit 500 is in the expanded state, and the arm member 440 and the lens member 460 of the up and down operation unit 400 are disposed at the extended position. Form an open state.

  As shown in FIG. 11, the front plate member 546 of the combined operation unit 500 is visually recognized through the lens member 460 of the vertical movement unit 400. Since the lens processing is formed on the lens member 460 as described later, the front plate member 546 is viewed in an enlarged manner.

  That is, from the state shown in FIG. 11, the rotary plate 520 (see FIG. 24) of the combined operation unit 500 is pivoted about the first shaft 512 (see FIG. 24), and the front plate member 546 is moved up and down. The front plate member 546 is visually recognized in a normal size when it is moved from the lens member 470 to a position (see FIG. 39) separated in a front view. As a result, it is possible to switch between the state in which the front plate member 546 is viewed in a normal size and the state in which the front plate member 546 is viewed in an enlarged manner (see FIG. 11), thereby improving the rendering effect.

  FIG. 12 is a front view of the operation unit 200. In FIG. 12, the expansion / contraction effect device 540 (see FIG. 22) of the combined operation unit 500 is in the extended state, and the tilting operation unit 600 is disposed at the retracted position and is in the tilting state. The state immediately before the point of contact is illustrated. By further tilting the tilting unit 600, the tilting unit 600 and the front plate member 546 are brought into contact with each other. In this case, by swinging the compound operation unit 500 clockwise in a front view (see FIG. 39), it is possible to produce an effect that makes it appear that the force is applied from the tilting operation unit 600 to the compound operation unit 500. (It is possible to associate the operations of the units and perform more complicated effects). Thereby, the rendering effect can be improved.

  Next, the lower board unit 300 will be described with reference to FIGS. 13 to 15. FIG. 13 is a front exploded perspective view of the board 13 and the lower board unit 300. As shown in FIG. 13, at the lower part of the game board 13, there is formed a receiving opening 13a which is opened along the lower edge of the inner rail 61 and into which the board lower unit 300 is inserted.

  FIG. 14 is a front exploded perspective view of the lower board unit 300. As shown in FIG. 14, the lower board unit 300 has a base member 310 internally fitted and fixed to the receiving opening 13 a of the game board 13 and a ball disposed at the lower left of the base member 310 in a front view. A lower left plate member 320 guiding to 314, a lower right plate member 330 disposed on the lower right of the base member 310 in a front view and guiding a ball to the second out port 315, and a left lower plate fastened and fixed to the base member 310 from the front The front lid member 340 mainly supported by the member 320 and the lower right plate member 330 by the insertion shaft 343.

  The base member 310 has a plate-like main portion 311 which has a shape substantially the same as the shape of the receiving opening 13a of the game board 13 and formed in a slightly smaller cross-sectional shape than the receiving opening 13a. It is formed on the left of front view of the decoration front plate part 312 formed in thin plate shape in the covering aspect, the movable effect member 313 attached to the width direction approximate center part of the decoration front plate part 312, and the movable effect member 313 And a second out port 315 which is a rectangular shaped hole formed on the right side in a front view of the movable effect member 313.

  The movable effect member 313 is provided at the lower edge in the width direction center of the game board 13 and includes a rotation effect member 313 a which is rotated by a drive device (not shown). Here, when the out port is disposed at the center lower edge of the game board 13 in the width direction, the movable effect member 313 can not be disposed at the center lower edge of the game board 13 in the width direction. In the present embodiment, the first out port 314 and the second out port 315 are disposed at positions separated leftward and rightward from the center of the game board 13 without arranging the out port at the lower center of the game board 13 in the width direction. Thus, it is possible to secure a space for disposing the movable effect member 313 at the lower edge in the width direction center of the game board 13.

  The shapes of the first out port 314, the second out port 315, the lower left plate member 320, and the lower right plate member 330 will be described with reference to FIG. Fig.15 (a) is a front view of the base member 310, the 1st out port 314, the 2nd out port 315, the lower left board member 320, and the lower right board member 330, FIG.15 (b) is FIG. And a lower left plate member 320 taken along line XVb-XVb of FIG. In FIG. 15A, the outer shape of the front lid member 340 fastened and fixed to the base member 310 and the nail formed above the first out port 314 and the second out port 315 are illustrated.

  The first out port 314 and the second out port 315 are openings through which balls are discharged from the game area. The formed length in the width direction of the second out port 315 is shortened as compared to the first out port 314. The reason will be described later. In addition, a guide rib 315 a extending in the front-rear direction is formed on the upper inner surface of the second out port 315. The guide rib 315a allows the ball flowing into the second out port 315 to be highly splashed, thereby suppressing the resistance applied to the ball when the ball collides with the upper bottom surface of the second out port 315. Further, the flow of the balls discharged from the second out port 315 can be adjusted in the front-rear direction, and the variation in the direction of the discharged balls can be suppressed.

  Also, the buffer rib 322 of the lower left plate member 320 described later is formed higher toward the center in the width direction of the game board 13 (see FIG. 13) (see FIG. 15A). Thus, even in the present embodiment in which the vertical width of the game area increases toward the center of the game board 13 in the width direction, the effect of suppressing the bounce of the ball falling on the lower left plate member 320 is not impaired. That is, since the falling height of the ball becomes higher as it is closer to the center in the width direction of the game board 13, there is a possibility that the impact when the falling ball collides with the lower left plate member 320 may increase. On the other hand, since the buffer rib 322 is formed higher toward the center in the width direction of the game board 13, the buffer rib 322 is bent closer to the center in the width direction of the game board 13 to cushion the impact of falling. The degree can be increased.

  Here, the relationship between the aspect ratio of the buffer ribs 322 and 332 and the landing frequency of the falling ball will be described. For example, if the falling height of the ball landing on the buffer ribs 322 and 332 is high, but the frequency of arrival of the ball to the position is extremely low, failure to discharge the other balls without intentionally suppressing the bouncing of the ball. It may not be. In this case, if the aspect ratio of the buffer ribs 322 and 332 is increased, the space of the game area is unnecessarily reduced. Therefore, it is preferable that the aspect ratio of the buffer ribs 322 and 332 be set not only by the drop height of the ball but also by the drop height and the frequency with which the ball lands at that position.

  As shown in FIG. 15, the balls flowing down above the buffer ribs 322 and 332 are started to flow down in the paths c1 and c2, and then reach the landing areas z0 to z4 through the plurality of branches b1 to b10. In the following description, when the probability that the sphere flows down is equal (1/2) in the paths c1 and c2 and the left and right branches in the branches b1 to b10 are equally left and right (1/2), respectively. Explain. It is assumed that the ball does not flow down from the upper right.

  The probability of the ball reaching the landing area z0 will be described. In order to reach the landing area z0, it is necessary to flow down the left side at the branch b5 to reach the path c11. The branch b5 may be reached from the path c1 via the branch b1 or from the path c2. Therefore, the probability that the ball reaches the path c11 and the ball reaches the landing area z0 is 1/8 (= 1/2 × (1/2) ^ 2), the probability of the ball flowing down from the path c1; Since it is represented by the sum of the probability 1⁄4 (= 1⁄2 × 1⁄2) of the spheres flowing down from the path c 2, it is 3⁄8 (“^” means a power). That is, each probability is the product of the probability 1⁄2 that the sphere flows down paths c 1 and c 2, and the number of powers 1⁄2 of the number of branches b 1 to b 10 that the sphere passes before reaching the landing area z 0 Is represented by

  The probability that the ball reaches the landing area z1 will be described. In order to reach the landing area z1, the left side is branched down at branch b3 to reach path c15, the left side is branched down at branch b4 to path c16, or the right side is branched off at branch b6 path c14 Or the right side at branch b7 to reach path c13.

  Up to the branch b3 is considered only when the sphere flows down from the path c1, and there are three branches before the sphere reaches the path c15, so the probability that the sphere reaches the path c15 is 1/16 (= It is 1/2 × (1 × 2) ^ 3). In addition, it is conceivable that only the case in which the ball flows down from the path c1 up to the branch b4 and there are four branches before the ball reaches the path c16, so the probability that the ball reaches the path c16 is 1/32 It is (= 1/2 x (1 x 2) ^ 4). In addition, until the branch b6, only the case where the sphere flows down from the path c1 is considered, and there are three branches before the sphere reaches the path c14, so the probability that the sphere reaches the path c14 is 1/16 (= 1/2 × (1 × 2) ^ 3).

  Up to the branch b7, both the case where the sphere is dropped from the path c1 and the path c2 are considered, and there are four branches before the sphere dropped from the path c1 reaches the path c13, and three branches. May exist. There are two branches before the ball flowing down from the path c2 reaches the path c13. Therefore, the probability that the sphere reaches the path c13 is the probability 3/32 (= 1/2 x (1/2) ^ 4 + 1/2 x (1/2) ^ 3) of the sphere flowing down from the path c 1; It is 7/32 because it is represented by the sum of the probability 1/8 (= 1/2 × (1/2) ^ 2) of the sphere flowing down from the path c2.

  Here, the probability that the sphere reaches the landing area z1 is 12/32 because it is the sum of the probabilities that the sphere reaches the above-described paths c13 to c16.

  The probability of the ball reaching the landing area z2 will be described. The probability that the sphere reaches the landing area z2 can be expressed by the probability that the sphere reaches the path c12, which is equal to the probability that the sphere reaching the branch b7 reaches the path c13. Therefore, the probability that the ball reaches the landing area z2 is 7/32.

  The probability of the ball reaching the landing area z3 will be described. In order to reach the landing area z3, it is necessary to flow down the left side at the branch b9 to reach the path c17 or to flow the left side at the branch b10 to reach the path c18.

  Until the branch b9, there is only a case in which the sphere flows down from the path c1, and there are six branches before the sphere reaches the path c17, so the probability of the sphere reaching the path c17 is 1/128 (= It is 1/2 × (1 × 2) ^ 6). In addition, it is only considered that the ball flows down from the path c1 until the branch b10, and there are seven branches before the ball reaches the path c18, so the probability that the ball reaches the path c18 is 1/256 (= 1/2 × (1 × 2) ^ 7).

  The probability of the sphere reaching the landing area z3 is 3/256 since it is the sum of the probabilities of the sphere reaching the paths c17 and c18 described above.

  The probability of the ball reaching the landing area z4 will be described. In order to reach the landing area z4, it is necessary to flow down the right side at the branch b10 to reach the path c19. In addition, all the balls which flowed down the right side of the branch b10 shall flow down on the path c19. The probability that the sphere reaches the path c19 is equal to the probability that the sphere reaching the branch b10 reaches the path c18. Therefore, the probability that the sphere reaches the landing area z4 is 1/256 (= 1/2 × (1 × 2) ^ 7).

  From these facts, the rate at which the sphere reaches each landing area z0 to z4 is (z0: z1: z2: z3: z4) = (96: 96: 56: 3: 1). This ratio is correlated with the buffer ribs 322 and 332.

  For example, when the landing area z1 and the landing area z3 are compared, the heights of the balls falling to the landing areas z1 and z3 are equal but the aspect ratio of the buffer ribs 322 and 332 is the landing area for the landing area z3. Less than z1. This is because the rate at which the sphere reaches the landing area z3 is 1/32 of the rate at which the sphere reaches the landing area z1. That is, even if the bounding of the falling ball is not suppressed as much as the landing area z1, in the landing area z3, there is little possibility that the discharge of the ball will be delayed. Therefore, in the landing area z3, the arrangement position of the second out port 315 can be lowered downward by reducing the aspect ratio of the buffer rib 332 compared to the landing area z1.

  For example, when the landing area z2 and the landing area z4 are compared, the aspect ratio of the buffer ribs 322 and 332 is the same as the ball falling distance to the landing area z4 is longer than the ball falling distance to the landing area z2. The landing area z2 is larger than the landing area z4. This is because the rate at which the sphere reaches the landing area z4 is 1/56 of the rate at which the sphere reaches the landing area z2. That is, even if the bounding of the falling ball is not suppressed as much as the landing area z2, in the landing area z4, there is little possibility that the discharge of the ball will be delayed. Therefore, in the landing area z4, the arrangement position of the second out port 315 can be lowered downward by reducing the aspect ratio of the buffer rib 332 compared to the landing area z2.

  In addition, although the case where the branch probability of the ball of the branches b1 to b10 is equal left and right (1/2) was described in the above description, the ball is branched at the branches b1 to b10 by changing the width of the nail. It is possible to adjust the branching probability. For example, by making the distance between the nails of the flow path through which the arrow on the left side of the branch b1 passes is as small as the diameter of the sphere, the probability that the ball flows down along the arrow on the right at the branch b1 is greater than 1/2 can do. Also in the other branches b2 to b10, the probability of the branch of the sphere can be similarly adjusted.

  As a result, the frequency at which the sphere reaches the paths c11 to c19 can be adjusted, and the design freedom of the aspect ratio of the buffer rib 322 can be improved.

  In addition, the buffer rib 322 is formed to be inclined downward as the upper surface goes to the rear (see FIG. 15B). Thereby, the ball flow to the first out port 314 can be made faster.

  Referring back to FIG. The lower left plate member 320 has a long plate-like main body portion 321 and a buffer rib 322 in which thin plates continuously provided in the left-right direction on the upper surface of the main body portion 321 extend in the front-rear direction and the buffer rib A connection front plate 323 formed in such a manner as to connect the front of 322, a step 324 formed by being raised upward at the left end in a front view of the main body 321, and extending leftward from the step 324 The ball flow rail portion 325 is mainly provided, and the axial support hole 326 drilled in the front-rear direction at the front end right end portion of the main body portion 321.

  The buffer rib 322 is a portion through which the ball directed to the first out port 314 passes, and suppresses the rebounding of the ball falling in the vertical direction in the vertical direction. That is, since the buffer rib 322 is formed of a thin plate continuously provided in the left and right direction, when impacted by a falling ball, bending in the thickness direction can alleviate the impact of the collision. In addition, when the ball moves in the left-right direction on the upper surface of the buffer rib 322, the ball is engaged between the buffer ribs 322 to brake the ball. In addition, the formation height and the aspect ratio of the buffer rib 322 are made larger as it goes inward in the width direction of the game board 13 (see FIG. 2) in the front view right side.

  The connection front plate 323 improves the strength of the buffer rib 322 by connecting the buffer rib 322.

  The stepped portion 324 is a raised portion for causing the ball flowed down from the ball flow rail portion 325 to fall in the vertical direction. Thereby, it is possible to suppress the load in the lateral direction from being applied to the buffer rib 322 from the ball flowing down the ball flow rail portion 325. Thereby, the buffer rib 322 can be prevented from being bent in the left-right direction by receiving a load in the left-right direction.

  That is, since the buffer rib 322 is formed of a thin wall portion extending in the front-rear direction, there is a possibility that the buffer rib 322 may be broken by the load in the left-right direction. On the other hand, in the present embodiment, a ball rolling on the upper surface of the ball flow rail 325 which has a velocity in the left-right direction and may load the load in the left-right direction to the buffer rib 322 It is formed in the form of falling in the direction. Thus, the position at which the ball lands on the buffer rib 322 can be shifted to the right in the width direction as the speed in the left-right direction of the ball is higher.

  Therefore, when the ball lands on the buffer rib 322, the load applied to the buffer rib 322 in the left-right direction can be made smaller toward the left in the width direction (outside). Therefore, the possibility of the occurrence of bending due to the load in the left-right direction of the ball decreases as the buffer rib 322 moves to the left in the width direction, and the aspect ratio of the buffer rib 322 can be formed smaller than that to the right in the width direction. . In this case, since 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, the buffer rib 322 is disposed as compared to the case where the buffer rib 322 has the same length in the width direction. The position can be lowered downward.

  Here, the lower surface of the game board 13 while keeping the aspect ratio of the buffer rib 322 constant at the left and right positions in the width direction (with the upper surface of the buffer rib 322 formed by the same curve as the lower surface of the buffer rib 322). It is also conceivable to form the lower surface of the buffer rib 322 along the curved surface formed on However, in this case, the disposition position of the step portion 324 becomes high, and the disposition position of the ball flow rail portion 325 formed to be inclined downward toward the step portion 324 also becomes high. In this case, the dead space between the ball flow rail portion 325 and the inner rail 61 (see FIG. 13) is increased, and the game area is suppressed.

  On the other hand, the larger the aspect ratio of the buffer rib 322, the larger the action of decelerating the ball (deceleration action). Therefore, the buffer rib 322 is formed in such a manner as to increase the aspect ratio from the vicinity of the step 324 toward the center of the game area.

  The upper surface of the buffer rib 322 is formed in the same curve as the curve of the lower surface of the buffer rib 322 to the front of the step 324 so as not to affect the formation height of the step 324 (in the middle of the buffer rib 322 in the left-right direction) It is also conceivable that the height is formed maximally). However, in this case, the ball reaching the landing area z1 is prevented from rolling to the left. Therefore, the balls are easily retained in the landing area z1, and it becomes difficult to discharge the balls smoothly.

  On the other hand, in the present embodiment, since the variation in the height of the upper surface of the buffer rib 322 in the width direction of the buffer rib 322 is small, the ball reaching the landing region z1 is easily turned to the left (the landing region z2 side) Move. Therefore, since the balls can be flowed to the landing area z2 before the balls stay in the landing area z1, the balls can be discharged smoothly.

  In addition, the step portion 324 has a function of stopping the ball flowing up and down to the left above the buffer rib 322. This can prevent the ball from bouncing back beyond the width of the first out port 314 after colliding with the front lid member 340 (see FIG. 13).

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

  The lower right plate member 330 has a long plate-like main body portion 331 and a buffer rib 332 in which thin wall portions continuously provided in the left-right direction on the upper surface of the main body portion 331 extend in the front-rear direction, A connection front plate 333 formed in such a manner as to connect the front surfaces of the buffer ribs 332, a recessed portion 324 formed by being depressed downward at the right end in the front view of the main body 331, and a right side in a front view from the recessed portion 324 It mainly includes a ball flow rail portion 335 extended to the end, and an axial support hole 336 drilled in the front-rear direction at the left end of the main body portion 331 in a front view.

  The configuration of the lower right plate member 330 and the configuration of the lower left plate member 320 are common in many parts. That is, the main body portion 331 is a main body portion 321, the buffer rib 332 is a buffer rib 322, the connection front plate 333 is a connection front plate 323, the ball flow rail portion 335 is a ball flow rail portion 325, and the axial support hole 336 is a shaft The technical idea is common to the support hole 326, so the description of the common part is omitted.

  The buffer rib 332 is formed to have a shorter formation width on the left and right as compared with the buffer rib 322. As a result, the left and right formation width of the second out port 315 can be shortened, and the arrangement position of the second out port 315 can be lowered downward compared to the first out port 314, so that the first variable The arrangement space of the large opening solenoid 65b of the winning device 65 can be secured (the arranging position of the first variable winning device 65 can be lowered).

  Here, the formation width of the buffer rib 332 can be made shorter than that of the buffer rib 322 because the flow path of the ball to the second out port 315 is restricted. That is, as shown in FIG. 14, the first variable winning device 65 is disposed on the upper right of the second out port 315 in front view, so that the ball flows into the first specified winning opening 65a when the opening and closing plate is opened. When the opening and closing plate is closed, the ball is dropped vertically downward on the front side of the first variable winning device 65. Thereby, it is possible to prevent the ball from flowing down to the second out port 315 from the upper right of the front view. In other words, in the upper right portion of the second out port 315, a non-falling area in which the flow of the ball is restricted is formed.

  Therefore, the flow-down direction of the ball to the lower right plate member 330 is limited only to the falling in the vertical direction and the flow-down from the width direction (from the ball flow rail portion 335) (flow from the diagonal upper right is restricted) . Therefore, since there is no inflow of the ball from the upper right side, the direction in which the ball bounces can be limited, and the width of the buffer rib 332 can be narrowed and the width of the second out port 315 can be narrowed. As a result, the installation space of the first variable winning device 65 can be secured.

  The recess portion 334 is a recess for causing the ball flowing down the ball flow rail portion 335 to bounce. Therefore, the formation width of the recessed portion 334 is a width that allows the ball to be placed without being in contact with the adjacent buffer rib 332.

  The ball which has flowed down the ball flow rail portion 335 is dropped into the recess portion 334, and when the ball abuts on the upper surface of the recess portion 334, the ball bounces and falls into the buffer rib 332. This prevents the load from being applied to the buffer rib 332 in the width direction, and can prevent the buffer rib 332 from being broken.

  The recessed portion 334 is formed in front of the fastening hole B through which a fastening screw for fastening and fixing the base member 310 to the game board 13 is inserted. As a result, when the fastening screw is screwed into the fastening hole B in order to fasten and fix the lower panel unit 300 to the game board 13, it is possible to make easy to use a fastening tool such as a driver. That is, the recessed portion 334 has both the effect of preventing the buffer rib 332 from being broken and the effect of facilitating the fastening and fixing of the base member 310.

  The front lid member 340 has a plate-like main portion 341 having the first winning opening 64 formed at the top, and an opening 342 formed at the center of the main portion 341 to allow the rotation effect member 313a to be visible. It mainly includes a pair of insertion shafts 343 that are inserted into the shaft support holes 326 and 336.

  The main body portion 341 is formed in contact with the lower edge of the game area, and the flow-down direction of the ball is limited by the side wall portion. That is, the ball that has collided with the main body 341 from the right can not penetrate to the left, while the ball that collides with the main body 341 from the left can not penetrate to the right.

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

  Next, the vertical movement unit 400 will be described with reference to FIGS. FIG. 16 is a front perspective view of the vertical movement unit 400, and FIG. 17 is a rear perspective view of the vertical movement unit 400. 16 and 17, the state in which the arm member 440 of the vertical movement unit 400 is disposed at the retracted position is illustrated.

  FIG. 18 is a front exploded perspective view of the vertical movement unit 400, and FIG. 19 is a rear exploded perspective view of the vertical movement unit 400. As shown in FIGS. 18 and 19, the vertical movement unit 400 is provided with a base member 410 including a vertical groove portion 414 which is recessed from the rear side to the front side on the right in a rear view and the recess extends in the vertical direction. The rotary crank member 420 is rotated about the connection hole 413 of the base member 410, the driving device 430 for generating the driving force of the rotary crank member 420, and the driving force is transmitted from the rotary crank member 420 to the base member 410. The arm member 440 is pivoted about the shaft portion 412 of the head, and is disposed on the opposite side of the upper and lower groove portions 414 of the base member 410. The sliding member 450 and the sliding hole 443 formed at the tip of the arm member 440 are suspended and interlocked with the swinging of the arm member 440 in the vertical direction A lens member 460 is slidably formed mainly includes a pair of door member 470 which is respectively pivotally supported on the lens member 460, a.

  The base member 410 has a main body 411 which is formed in a plate shape elongated in the left and right direction, and a cylindrical support member 442 of an arm member 440 which protrudes from the right end of the main body 411 toward the front side. It is formed from the back side to the front side in the rear view right side of the main body 411 from the support shaft portion 412 supported, the connection hole 413 in which the rotary crank member 420 and the transmission gear 432 are connected in a circular shape in the longitudinal direction. An upper and lower groove portion 414 is vertically extended, and a concave portion 415 recessed from the front to the back side on both left and right outer sides of the upper and lower groove portions 414 is mainly provided.

  The upper and lower groove portions 414 are portions in which the expansion / contraction rendering device 540 of the combined operation unit 500 is accommodated on the back side in the assembled state (see FIG. 2). In the combined operation unit 500, the swing angle of the expansion / contraction effect device 540 is suppressed as the expansion / contraction effect device 540 moves to the reduction state, as described later, so that the expansion / contraction effect device 540 is oscillated. Collisions to the left and right inner side surfaces are prevented. The recessed portion 415 is a portion to which the slide guide portion 452 of the slide member 450 is guided.

  The rotating crank member 420 has a plate-like main body portion 421, and a sliding projection 422 projecting in a cylindrical shape on the front side from one end of the main body portion 421 and inserted through the insertion portion 444 of the arm member 440. Mainly includes an engaging portion 423 engaged with the fitting portion 432a of the transmission gear 432 and disabling relative rotation between the transmission gear 432 and the rotating crank member 420.

  The sliding projection 422 is inserted into the insertion portion 444 of the arm member 440 and rotated, whereby the driving force of the drive device 430 is transmitted to the arm member 440, and the arm member 440 is swung about the shaft 412. .

  Drive device 430 includes a drive motor 431 fastened and fixed to base member 410, a drive gear 431a rotationally driven by drive motor 431, a transmission gear 432 meshed with drive gear 431a, and transmission gear 432 And a fitting portion 432a which is formed with an outer diameter slightly smaller than the inner diameter of the connection hole 413 and whose inner side surface is fitted to the engaging portion 423 of the rotating crank member 420.

  The fitting portion 432a is a portion provided with a recess having a cross-sectional shape in which a circular shape is disposed at each vertex of a triangle, and is inserted into the connection hole 413 of the base member 410 and at the tip end thereof The engagement portion 423 of the is fitted non-rotatably. Thus, the main body 411 of the base member 410 is formed to be sandwiched between the transmission gear 432 and the rotating crank member 420, and as described above, relative rotation between the transmitting gear 432 and the rotating crank member 420 is disabled. The transmission gear 432 and the rotating crank member 420 rotate in synchronization with each other. That is, the driving force of the driving motor 431 is transmitted to the rotating crank member 420 via the transmission gear 432.

  The arm member 440 includes a body portion 441 formed in a long rod shape, a shaft support hole 442 which is bored on the base end side (right side in front view) and pivotably supported by the shaft portion 412, and the base end side. The slide hole 443 is formed as an elongated hole on the swinging end side which is the opposite end of the slide member and the slide projection 463 of the lens member 460 is inserted, and the slide projection 422 of the rotating crank member 420 is inserted And an insertion portion 444 in the form of a bottomed hole.

  The shape of the insertion portion 444 is set such that the rotating crank member 420 can rotate once while the sliding projection 422 is inserted through the insertion portion 444. Therefore, the arm member 440 can perform the swing operation regardless of the rotation direction of the rotation crank member 420.

  The slide member 450 has a rectangular plate-like main body 451, a slide guide 452 extending rearward from the left and right ends of the main body 451, and guided in the recessed portion 415 so as to be vertically slidable, and the main body A central guide recessed portion 453 which is a recess extending in the vertical direction formed on the front at the center in the width direction of 451 and into which the sliding projection 463 of the lens member 460 is inserted, and the left and right ends of the main body 451 It mainly includes a both-end guide recessed portion 454 which is a recess formed on the front in the portion and extended in the vertical direction and to which the stable slide portion 464 of the lens member 460 is guided.

  The lens member 460 includes a plate-like main body 461 having a circular opening at its center, a magnifying lens 462 having an enlargement lens processing formed therein and fitted in the opening of the main body 461, and a widthwise center of the main body 461 A sliding projection 463 which is projected to the back side at the upper end and is inserted in the slide hole 443 of the arm member 440 so as to be slidable up and down, and a slide projected to the back side at both widthwise ends of the main body 461 The lower end shaft portion 473 and the upper side of the door member 470 are disposed rotatably in the upper and lower sides of the main body portion 461 in a stable slide portion 464 inserted in the upper and lower slide guide portions of the member 450 so as to be vertically slidable. A pair of rotating cylinders 465 through which the shaft portion 474 is inserted, and a drive motor 466 for rotating the pair of rotating cylinders 465 in opposite directions by a transmission mechanism (not shown) are mainly provided. That.

  The moving operation of the vertical movement unit 400 will be described with reference to FIG. FIG. 20 is a front view of the vertical movement unit 400. FIG. Note that FIG. 20 illustrates the closed state of the door member 470 when the arm member 440 of the vertical movement unit 400 is disposed at the extended position.

  When the arm member 440 is swung from the retracted position (see FIG. 16) to the overhanging position (see FIG. 20), the sliding of the lens member 460 supported by the sliding hole 443 on the swinging end side of the arm member 440 The movable projection 463 (see FIG. 18) is slid on the central guide recess 453 of the slide member 450. The lens member 460 is vertically guided by the both-end guide concave portion 454 of the slide member 450, and the slide member 450 is vertically guided by the concave portion 415 of the base member 410. The member 460 is slid in the vertical direction.

  Referring back to FIG. 18 and FIG. The door member 470 is configured by dividing a circular plate into upper and lower parts, and is formed on the lower side with a lower main body portion 471, an upper main body portion 472 formed above the lower main body portion 471, and a lower side. A lower shaft portion 473 projecting in a cylindrical shape on the back side at the lower end portion of the main body portion 471 and inserted into the rotary cylinder 465 of the lens member 460 so as not to relatively rotate, and a circle on the back side at the lower end portion It mainly includes an upper shaft portion 474 which is provided in a columnar shape and which is inserted into the rotary cylinder 465 of the lens member 460 so as not to be relatively rotatable.

  The lower main body 471 is provided with a guide projection 471 a protruding on the side facing the upper main body 472, and the upper main body 472 is on the side facing the lower main body 471. The receiving recess 472a is provided in the The relative positioning between the lower main body 471 and the upper main body 472 in the closed state can be performed by fitting the guide projection 471 a and the receiving recess 472 a. In the present embodiment, since the guide projection 471a is protruded in a tapered shape, the guide projection 471a can be reliably fitted in the receiving recess 472a.

  The operation of the door member 470 will be described with reference to FIG. FIG. 21 is a front view of the vertical movement unit 400. FIG. Note that FIG. 21 illustrates the open state of the door member 470 when the arm member 440 of the vertical movement unit 400 is disposed at the extended position.

  The lower shaft portion 473 and the upper shaft portion 474 (see FIG. 19) are rotated by the rotation of the rotary cylinder 465 (see FIG. 18) of the lens member 460. The pair of rotary cylinders 465 are rotated in opposite directions by the driving force of the drive motor 466 (see FIG. 19), so the door member 470 is changed from the closed state (see FIG. 20) to the open state (see FIG. 21). In this case, the lower main body portion 471 and the upper main body portion 472 can be rocked outward (opposite direction) from each other. In addition, 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 inwardly.

  Thereby, the time for swinging the lower main body portion 471 and the upper main body portion 472 can be reduced to half as compared with the case where the front side of the lens member 460 is swung to cover a single cover member.

  Next, the combined operation unit 500 will be described with reference to FIGS. 22 to 45. The compound operation unit 500 arranges the telescopic effect device 540 on the front side of the third symbol display device 81 by swinging the pivoting arm member 550 from the retracted position (see FIG. 22) to the extended position (see FIG. 9). It is a unit. In addition, the expansion and contraction rendering device 540 is formed so as to be swingable about the first shaft portion 512 (see FIG. 24) of the base member 510.

  FIG. 22 is a front perspective view of combined operation unit 500, and FIG. 23 is a back perspective view of combined operation unit 500. As shown in FIG. FIGS. 22 and 23 illustrate that the pivoting arm member 550 is disposed at the retracted position which is the end position formed on the outside of the third symbol display device 81 (see FIG. 2).

  FIG. 24 is a front exploded perspective view of combined operation unit 500, and FIG. 25 is a back exploded perspective view of combined operation unit 500.

  As shown in FIG. 24 and FIG. 25, the combined operation unit 500 is a unit that effects by sliding and swinging the expansion and contraction rendering device 540, and includes a base member 510 that forms a skeleton and the base member 510. And a first drive device 530 that is fastened and fixed to the base member 510 to generate a driving force of the rotary plate 520, and is fastened to the front of the rotary plate 520. One end of the expansion / contraction effect device 540 which is fixed and formed so as to be expandable and contractible in the radial direction of the rotary plate 520 and one end thereof is connected to the expansion / contraction effect device 540 and the other end on the opposite side is axially supported by the base member 510 And a pivoting arm member 550 that forms an expansion and contraction operation of the expansion and contraction rendering device 540 by a pivoting operation, and a driving force of the pivoting arm member 550 that is fastened and fixed to the base member 510. The second driving device 560 to be generated, the rotating crank member 570 for transmitting the driving force of the second driving device 560 to the rotating arm member 550, and the rotating arm member 550 and the rotation are fastened and fixed from the front of the base member 510. And a front cover 580 for blinding a mechanical portion on the rotary shaft side such as the crank member 570.

  The base member 510 includes a main body portion 511 having a rectangular plate shape, a cylindrical first shaft portion 512 protruding forward from a substantially lower center of the main body portion 511 in the width direction, and the first shaft portion 512. Three rows of circular arc-shaped holes 513 drilled along a central circular arc, and a first through hole 514 drilled adjacent to a second circular arc-shaped hole 513b of the three rows of circular arc-shaped holes 513 , And a cylindrical second shaft 515 protruding forward from the main body 511 at a substantially intermediate position between the shaft 512 and the right end of the main body 511, and adjacent to the second shaft 515. A second through hole 516 to be bored, a cylindrical third shaft 517 projecting forward from the lower right end of the main body 511 in front view, and a bending from the edge of the main body 511 to the front And a bent wall portion 518.

  The first shaft portion 512 is a portion that is inserted into the shaft support hole 522 of the rotary plate 520 and becomes the rotation shaft of the rotary 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 rotary plate 520.

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

  The first circular arc hole 513 a and the third circular arc hole 513 c are long holes through which the insertion shaft 525 of the rotary plate 520 is inserted and which guides the rotation of the rotary plate 520. Thereby, when the rotating plate 520 is rotated, the load received by the first shaft portion 512 can be reduced, and the durability of the rotating plate 520 can be improved. Although FIGS. 24 and 25 show a state in which the 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 different from the collar and the main body portion 521. Placed between (inserted before fastening the collar).

  The second arc-shaped hole 513 b is a long hole in which the arc-shaped rack 526 of the rotary plate 520 is disposed and moved. The upper side of the substantially central portion is opened, and the drive gear 532 of the first drive device 530 is disposed in the opened portion. Thus, the toothed portion of the drive motor 531 of the first drive device 530 and the arc-shaped rack 526 of the rotary plate 520 can be disposed in the plate thickness portion of the main body portion 511. The dimension in the longitudinal direction (the dimension in the front-rear direction in FIG. 22) can be suppressed.

  The first through hole 514 and the second through hole 516 are through holes into 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.

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

  The third shaft portion 517 is a portion that is inserted into the pivot support hole 552 of the pivoting arm member 550 and serves as a central axis of pivoting of the pivoting arm member 550. Therefore, the diameter of the third shaft portion 517 is formed to be slightly smaller than the inner diameter of the pivot hole 552 of the pivot arm member 550. A torsion spring 517a is wound around the third shaft 517 to generate a biasing force for moving the pivoting arm member 550 toward the retracted position.

  The torsion spring 517 a is formed in such a manner that arms are extended from both ends of the coil portion wound around the third shaft 517. One arm portion is fixed to the lower right portion (in the vicinity of the first stopper portion 518 a) of the bent wall portion 518 in a front view, and the other arm portion on the opposite side of the one arm portion The locking portion 555 is locked.

  The bent wall portion 518 includes a first stopper portion 518 a adjacent to the third shaft portion 517, a second stopper portion 518 b formed on the right side of the first shaft portion 512, and a left side of the first shaft portion 512. And a third stopper portion 518c formed on the main body.

  The first stopper portion 518 a is a portion that regulates the rotation of the rotation arm member 550. That is, when the pivoting arm member 550 is lowered to the extended position (see FIG. 9), it is brought into contact with the first stopper portion 518a, and the lowering is stopped.

  As shown in FIG. 24, the second stopper portion 518b is disposed below the third stopper portion 518c. The lower surface of the rotary plate 520 is formed symmetrically with respect to the shaft support hole 522 (see FIG. 37), so that the rotary plate 520 rotates at a larger rotation angle in the direction of rotation toward the second stopper portion 512b. Can. That is, in the expansion / contraction effect device 540 described later, the maximum angle of the clockwise swing in the front view is formed larger than the swing in the counterclockwise direction in the front view.

  The rotary plate 520 has a fan-shaped plate-like main body portion 521, a pivot hole 522 circularly formed in the thickness direction at the base portion of the main body portion 521, and a body slightly wider than the inner diameter of the pivot hole 522 A rail receiving groove 523 which is rectilinearly recessed on the front surface of the portion 521, a pair of expansion and contraction stoppers 524 which are formed to project forward on both sides of the lower end portion of the rail receiving groove 523 An arc-shaped rack having a plurality of (three in this embodiment) insertion shafts 525 projecting from the back surface of the main body 521 in an arc shape centering on the pivot hole 522 and having gear teeth engraved on the outer peripheral portion And 526.

  The first shaft portion 512 of the base member 510 is inserted through the shaft support hole 522. Therefore, the rotary plate 520 is swung about the first shaft portion 512.

  The rail receiving groove 523 is a portion to which the slide rail 545 of the expansion and contraction rendering device 540 is fastened and fixed, and the expansion and contraction rendering device 540 extends and contracts along the extending direction of the rail receiving groove 523. Therefore, the moving direction of the expansion and contraction rendering device 540 is changed by the posture of the rotary plate 520.

  The expansion / contraction stopper 524 is a portion that is vertically abutted against the inner side surface of the slide plate 544 of the expansion / contraction effect device 540, and regulates the movement width of the slide plate 544. It is formed on both sides of the rail receiving groove 523 and is abutted with the inner side surface of the slide plate 544 on both sides, thereby suppressing load on the slide rail 545 in a direction orthogonal to the expansion and contraction direction, and improving the durability Can be

  The insertion shaft 525 is a portion which is inserted into the first arc-shaped hole 513a and the third arc-shaped hole 513c of the base member 510 and guides the rotation of the rotary plate 520, and has a diameter of the first arc-shaped hole 513a and the third circle. It is formed slightly smaller than the width dimension of the arc-shaped hole 513c. In addition, since the collar member having a diameter larger than the width dimension of the first circular arc hole 513a and the third circular arc hole 513c is fastened and fixed to the tip end, the rotary plate 520 is non-extractably connected to the base member 510.

  The arcuate rack 526 is inserted into the second arcuate hole 513 b of the base member 510 and engaged 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 the area including the thickness portion of the base member 510, the dimension in the thickness direction of the combined operation unit 500 can be suppressed.

  The first drive device 530 mainly includes a drive motor 531 fastened and fixed to the base member 510, and a drive gear 532 inserted into the first through hole 514 of the base member 510 and axially rotated by the drive motor 531.

  Next, the expansion and contraction rendering device 540 will be described with reference to FIGS. 26 and 27. FIG. 26 is a front exploded perspective view of the expansion / contraction effect device 540, and FIG. 27 is a rear exploded perspective view of the expansion / contraction effect device 540.

  As shown in FIG. 26 and FIG. 27, the expansion / contraction effect device 540 has a main body member 541 forming a skeleton, and a pair of the main body member 541 is fastened and fixed to the back surface thereof. The first guide member 542 and the second guide member 543 through which the portion 551 is inserted, and the axially movable direction of the first guide member 542 and the insertion holes 542 d of the second guide member 543 are provided. The slide plate 544, the slide plate 544 and the rotary plate 520, and one end of the slide rail 545 which is internally fitted in the rail receiving groove 523 and fastened and fixed; Of the front plate member 546 to be fastened and fixed, the connecting sliding member 547 slidably supported on the shaft support portion 546c of the front plate member 546, and the connecting sliding member 547 Mainly includes a decorative member 548 front drooping portion 548b is formed to be movable in the front of the body member 541 is fixed.

  The main body member 541 includes a plate-like main body portion 541a forming a skeleton, a columnar protrusion 541b protruding toward the back side at the center in the width direction of the main body portion 541a, and a back surface of the protrusion 541b The first bulking fastening portion 541c, which is provided on the left side in a pair, the second bulking fastening portion 541d, which is provided on the right side in the back view of the protrusion 541b, and the top left portion of the body portion 541a in a rear view. Mainly provided are a guide fastening portion 541e which is provided in a protruding manner, and a fastening hole 541f which is formed on the front side of the main body portion 541a in a plurality (in the present embodiment, three places) and the front plate member 546 is fastened and fixed.

  The protrusion 541 b is a portion that is inserted into the arc-shaped hole 554 of the pivoting arm member 550. Therefore, the diameter of the protrusion 541 b 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 projection 541 b is inserted into the arc-shaped hole 554, when the pivoting arm member 550 is swung, the main body member 541 can be interlocked.

  The first raised fastening portion 541 c is a portion for fastening and fixing the first guide member 542, and the second raised fastening portion 541 d is a portion for fastening and fixing the second guide member 543. The distance by which the second bulky fastening portion 541 d is separated in the vertical direction is longer than the first bulky fastening portion 541 c because a position not interfering with the pivoting arm member 550 is selected and disposed. Here, in the present embodiment, the pivoting arm member does not pass below the front left side of the main body member 541 in its pivoting trajectory (see FIGS. 37, 40 and 44). Therefore, the arrangement interval of the pair of second raised fastening portions 541 d can be increased compared to the first raised fastening portions 541 c, and the rigidity of the second raised fastening portions 541 d can be improved.

  The guide fastening portion 541 e is a portion to which the auxiliary fastening portion 542 e of the first guide member 542 is fastened and fixed, and is a portion to which the upper surface of the pivoting arm member 550 is guided when the expansion / contraction effect device 540 is in an expanded state. That is, even if the projection 541 b is not guided by the arc-shaped hole 554 of the pivot arm member 550, the guide fastening portion 541 e guides the upper surface of the pivot arm member 550 to pivot the pivot arm member 550 upward. Thus, the pivoting arm member 550 and the telescopic effect member 540 are operated in conjunction with each other.

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

  The first guide member 542 is a fastening plate portion 542a fastened and fixed to the first raised fastening portion 541c, and a back surface restricting portion extending upward from a position where one step up on the back surface side of the fastening plate portion 542a 542b, a guide rail portion 542c protruding in a wall shape from the left and right sides of the back surface restricting portion 542b to the back surface, and a portion protruding to the back surface at the upper end portion of the back surface restricting portion 542b And an auxiliary fastening portion 542 e extending from the back surface regulating portion 542 b and fastened and fixed to the guide fastening portion 541 e.

  The back surface restricting portion 542 b is a portion disposed on the back surface of the pivoting arm member 550 and is a portion that prevents the pivoting arm member 550 from moving back and the projection 541 b from coming off from the arc-shaped hole 554. is there.

  The guide rail portion 542 c guides the movement of the rail receiving portion 544 d of the slide plate 544 when the expansion / contraction effect device 540 performs expansion and contraction operations, and suppresses the displacement of the posture of the slide plate 544 with respect to the first guide member 542.

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

  The second guide member 543 is a fastening plate portion 543a to be fastened and fixed to the second raised fastening portion 541d, and a back surface regulating portion extending upward from a position where the vehicle rides on the top surface of the fastening plate portion 543a. 543b, guide rails 543c protruding in a wall shape from the left and right sides of the back surface restricting portion 543b to the back surface, and a portion of the upper surface of the back surface restricting portion 543b protruding upward in the vertical direction And an insertion hole 543d.

  The back surface regulating portion 543 b is a portion disposed on the back surface of the pivoting arm member 550, and is a portion that prevents the pivoting arm member 550 from moving back to the rear and the projection 541 b falling off from the arc-shaped hole 554. is there.

  The guide rail portion 543 c guides the movement of the rail receiving portion 544 d of the slide plate 544 when the expansion / contraction effect device 540 performs the expansion / contraction operation, and suppresses the displacement of the attitude of the slide plate 544 with respect to the first guide member 543.

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

  The slide plate 544 has a main body portion 544a formed in a rectangular plate shape, a concave portion 544b in which a wide concave portion extending in the vertical direction is formed on the back surface of the main body portion 544a, and the concave portion 544b. Recesses 544c at both ends where recesses extending in the vertical direction are formed in the front of the left and right sides, and rail receivers projecting in a semicircular shape toward the front side at upper and lower end portions of the recesses 544c at both ends A section 544d, a cylindrical slide rod 544e extending in the vertical direction inside the concave sections 544c at both ends, and a production assisting wall 544f projecting toward the front substantially in the vertical center of the main body section 544a; A stopper portion 544g is provided mainly at the upper and lower ends of the recessed portion 544b so as to protrude toward the back surface at both left and right ends.

  The recessed portion 544 b is a portion for guiding the slide plate 544 to the expansion / contraction stopper 524 of the rotary plate 520. Therefore, the width of the inner side surface of the recessed portion 544b is formed to be slightly larger than the width dimension of the expansion / contraction stopper 524.

  The both end recessed portion 544c is a portion that accommodates a protrusion in which the insertion holes 542d and 543d of the guide members 542 and 543 are formed. Thereby, the projection part by which penetration hole 542d, 543d of guide member 542, 543 is drilled can be guided from the outside.

  The rail receiving portion 544 d is a portion accommodated in the guide rail portions 542 c and 543 c of the guide members 542 and 543. Thereby, it is possible to suppress the wobbling of the guide members 542, 543 with respect to the slide plate 544.

  The slide rod 544 e is a cylindrical rod inserted through the insertion holes 542 d and 543 d of the guide members 542 and 543. Thereby, the guide members 542 and 543 are formed so as to be slidable in the extending direction (vertical direction in FIG. 26) of the slide bar 544e.

  The effect assisting portion 544f is a portion that is in contact with the rear hanging portion 548c of the decoration member 548 when the expansion / contraction effect device 540 is in an extended state, and moves the decoration member 548. Thereby, the external appearance of the expansion-contraction rendering device 540 can be changed.

  The stopper portion 544 g is a portion that is in contact with the expansion / contraction stopper 524 of the rotary plate 520 and that defines the vertically moving end of the slide plate 544.

  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 rotary 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.

  The front plate member 546 is an effect portion visually recognized by the player, and is a plate-like main body portion 546a formed in substantially the same shape as the main body member 541 in a front view, and is directed from the main body portion 546a to the back side. It mainly includes a fastening portion 546b protruding in accordance with the formation position of the fastening hole 541f, and a pair of pivoting portions 546c projecting from the upper end portion of the main body portion 546a toward the back side.

  The fastening portion 546b is a portion for fixing the front plate member 546 to the main body member 541, and the fastening portion 546b is fastened and fixed by screwing it through the fastening hole 541f.

  The shaft support portion 546c slidably supports the connection sliding member 547. Therefore, the diameter of the bearing portion 546c is formed slightly smaller than the width of the inner peripheral surface of the sliding long hole 547b of the connecting sliding member 547.

  The connection sliding member 547 is formed in a plate-like body portion 547a, a pair of sliding long holes 547b formed in an elongated hole shape extending vertically and drilled in the longitudinal direction, and a vertical direction A pair of insertion holes 547c are mainly provided.

  The sliding long hole 547 b is a portion through which the pivotal support portion 546 c of the front plate member 546 is inserted. Therefore, the width of the inner peripheral surface of the sliding long hole 547b is formed slightly larger than the shaft support portion 546c. The coupling sliding member 547 is pivotally supported by the front plate member 546 so as not to be pulled out by fastening and fixing a collar member having an outer shape larger than the width of the inner peripheral surface of the sliding long hole 547b to the front end of the shaft support portion 546c. Ru. The insertion hole 547 c is a circular hole through which a fastening screw for fastening and fixing the decorative member 548 is inserted.

  The decorative member 548 is formed in a plate shape, and a main body portion 548a to which the connection sliding member 547 is fastened and fixed from the lower side, a front hanging portion 548b formed to descend downward on the front side of the main body portion 548a, and a main body portion 548a And a rear hanging portion 548c which is formed to hang downward on the rear side of the main body.

  When the connection sliding member 547 moves relative to the front plate member 546, the front drooping portion 548b covers the front plate member 546 (see FIG. 43) and the front plate member 546 is separated and viewed (see FIG. 43). 37) can be formed. Thereby, the appearance of the expansion / contraction effect member 540 can be changed, and the effect of the effect can be improved.

  The back dripping portion 548c is a portion that is in contact with the rendering assistance wall 544f of the slide plate 544 by the expansion and contraction operation of the telescopic rendering device 540, and the decorative member 548 is made by the back flapping portion 548c being in contact with the rendering assist wall 544f. Is moved relative to the front plate member 546.

  Referring back to FIG. 24 and FIG. The pivoting arm member 550 has a body portion 551 formed in a long rod shape, a pivot hole 552 drilled in the front-rear direction at one end of the body portion 551, and a pivot hole 552 Formed on the back side of the main body 551 and on the front side of the other end which is the opposite end of the one end and the other end of the one end. An arc-shaped hole 554, which is an arc-shaped bottomed long hole, is protruded toward the back side in the vicinity of the shaft support hole 552 of the main body 551 and its tip is bent like a hook and the other arm of the torsion spring 517a is locked Mainly comprises a locking portion 555.

  The bearing hole 552 is a circular hole through which the third shaft 517 of the base member 510 is inserted. Therefore, the inner diameter of the shaft support hole 552 is formed to be slightly larger than the diameter of the third shaft portion 517, whereby the pivoting arm member 550 is formed so as to be pivotable about the third shaft portion 517.

  The deformed long hole 553 is a portion through which the sliding projection 574 of the rotating crank member 570 is inserted. The shape of the deformed long hole 553 will be described later.

  The arc-shaped hole 554 is a long hole through which the protrusion 541 b of the expansion and contraction rendering device 540 is inserted. Therefore, the width dimension of the arc-shaped hole 554 is formed to be slightly larger than the diameter of the protrusion 541 b. Further, the arc formed by the arc-shaped hole 554 coincides with the arc formed by the projection 541 b when the expansion / contraction effect device 540 is swung about the first shaft 512 in the expanded state (FIGS. 37 to 39). Up to see).

  In addition, the circular arc-shaped hole 554 is open at the tip of the other end of the rotary arm member 550, and includes a proboscis 554a whose width widens at the tip.

  The second drive device 560 is a device that generates a driving force for rotating the rotating crank member 570, and is inserted into the drive motor 561 fastened and fixed to the base member 510 and the second through hole 516 of the base member 510. And a drive gear 562 that is axially rotated by the drive motor 561.

  The drive gear 562 is engaged with the transmission gear teeth 572 of the rotating crank member 570. Accordingly, when the drive gear 562 is rotated, the rotating crank member 570 is rotated accordingly.

  The pivoting crank member 570 is a member for transmitting the driving force to the pivoting arm member 550, and is engraved on the ring-shaped main body portion 571 axially supported by the second shaft portion 515 and the outer peripheral surface of the main body portion 571. The transmission gear teeth 572 provided, the control umbrella portion 573 formed in such a manner as to cover the front side of the transmission gear teeth 572, and the slide protruding on the front side at a position eccentric to the center of the main body 571 A protrusion 574 and a lid 575 which is formed to have a diameter larger than the inner circumferential diameter of the main body 571 and which is fastened and fixed to the front side of the second shaft 515 are mainly included.

  The transmission gear teeth 572 mesh with the drive gear 562 of the second drive device 560. Thus, the driving force of the drive motor 561 is transmitted to the rotating crank member 570.

  The control umbrella portion 573 suppresses the positional shift of the drive gear 532 to the front side of the transmission gear teeth 572. Thereby, the meshing relationship between the drive gear 532 and the transmission gear teeth 572 can be made appropriate.

  The sliding projection 574 is a portion that is inserted into the deformed elongated hole 553 of the pivoting arm member 550. That is, based on the relationship between the sliding protrusion 574 and the shape of the pivoting arm member 550, it is determined whether or not the transmission of the driving force is formed.

  The lid 575 is a portion for disposing the main body 571 on the base member 510 in a non-extractable manner.

  The relationship between the swinging of the pivoting arm member 550 and the rotation of the pivoting crank member 570 will be described with reference to FIGS. 28 to 31. First, the shape of the modified long hole 553 of the pivoting arm member 550 will be described with reference to FIGS. 28 (a) and 29 (a).

  28 (a) and 29 (a) are front views of the pivoting arm member 550 and the pivoting crank member 570. FIG. In FIG. 28A, a state in which the pivoting arm member 550 is disposed at the retracted position is illustrated, and in FIG. 29A, a state in which the pivoting arm member 550 is disposed at the projecting position is illustrated. In FIGS. 28 (a) and 29 (a), the deformed long hole 553 and the sliding projection 574 are shown as hidden lines and the front plate member 546 and the projection 541b of the telescopic effect device 540 are shown as imaginary lines. Be done.

  As shown in FIG. 28A, in the state where the pivoting arm member 550 is disposed at the retracted position, a straight line connecting the rotary shaft of the pivoting crank member 570 and the sliding projection 574 and the pivoting crank member 570 An upward orthogonal state is formed in which the straight line connecting the rotation axis and the shaft support hole 552 is orthogonal.

  As shown in FIG. 29A, in a state where the pivoting arm member 550 is disposed at the extended position, a straight line connecting the rotation shaft of the pivoting crank member 570 and the sliding projection 574 and the pivoting crank member 570 It is possible to form a downward orthogonal state in which the axis of rotation of and the straight line connecting the shaft support hole 552 are orthogonal. In FIG. 29A, a state in which the rotating crank member 570 is rotated by a predetermined angle in a counterclockwise direction in a front view from the above-described downward orthogonal state is illustrated.

  The deformed long hole 553 is a transmission groove portion 553a in which the driving force is transmitted to the pivot arm member 550 by the movement of the sliding projection 574, and a first non-transmission wall portion connected from the upper end portion of the transmission groove portion 553a. 553b and a second non-transmission wall 553c connected from the lower end of the transmission groove 553a, and a selection wall 553d connecting the first non-transmission wall 553b and the second non-transmission wall 553c Prepare.

  As shown in FIG. 28A, the transmission groove portion 553a is a recessed groove linearly extended leftward from the sliding projection portion 574 of the rotating crank member 570 in the upward orthogonal state. Transmission groove portion 553a is formed with a length such that sliding projection 574 of rotating crank member 570 can move from the upward orthogonal state to the downward orthogonal state, and the formation width of the inner circumferential surface thereof is slightly smaller than the diameter of sliding projection 574 It is formed large. Therefore, while the sliding projection 574 moves in the transmission groove portion 553a, the driving force is transmitted from the rotating crank member 570 to the rotating arm member 550.

  As shown in FIG. 28A, the first non-transmission wall portion 553b slides from the upper wall surface of the right end portion of the transmission groove portion 553a around the rotation axis of the rotating crank member 570 in the upward orthogonal state. The wall portion is formed along the circumscribed circle of the portion 574. That is, when the rotating crank member 570 is rotated clockwise in a front view from the upward orthogonal state, the rotating crank member 570 idles relative to the rotating arm member 550, and the driving force from the rotating crank member 570 is the rotating arm It is not transmitted to the member 550.

  When the pivoting arm member 550 is rotated counterclockwise in a front view from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 28A), the movement of the first non-transmission wall portion 553b The direction is directed to the rotational axis of the pivoting crank member 570. Therefore, when the sliding projection 574 is disposed to face the first non-transmission wall 553b, the load applied to the sliding projection 574 by the rotation of the pivoting arm member 550 is the rotation of the pivoting crank member 570. It is directed to the axis. Therefore, when the sliding projection 574 is disposed to face the first non-transmission wall 553b, the rotation of the pivoting arm member 550 is prevented.

  The second non-transmission wall portion 553c is, as shown in FIG. 29A, a rotation crank from the lower side wall surface of the right end portion of the transmission groove portion 553a in a state where the rotation arm member 550 is disposed at the overhang position. The wall portion is formed along the circumscribed circle of the sliding projection 574 centered on the rotation axis of the member 570. That is, when the rotating crank member 570 is rotated counterclockwise from the front view from the orthogonal state (a state where the rotating crank member 570 is rotated clockwise by a predetermined amount from the state in FIG. 29A). The pivoting crank member 570 idles relative to the pivoting arm member 550, and the driving force is not transmitted from the pivoting crank member 570 to the pivoting arm member 550.

  When the pivoting arm member 550 is rotated clockwise in a front view from the state illustrated in FIG. 29A, the moving direction of the second non-transmission wall portion 553b is directed to the rotation shaft of the pivoting crank member 570. Be Therefore, when the sliding projection 574 is disposed to face the second non-transmission wall 553c (see FIG. 29B), the load applied to the sliding projection 574 by the rotation of the pivot arm member 550. Are directed to the rotational axis of the pivoting crank member 570. Therefore, when the sliding projection 574 is disposed to face the second non-transmission wall 553c, the rotation of the pivoting arm member 550 is prevented.

  The selection wall portion 553d is a wall portion formed of a smooth curved surface connecting the front end right end portion of the first non-transmission wall portion 553b and the front end portion of the second non-transmission wall portion 553c. The transfer wall portion 553b is formed on the upper side of the extended curve.

  The selection wall portion 553d is disposed to face the right side portion of the second non-transmission wall portion 553c, and is formed in such a manner that the distance to the second non-transmission wall portion 553c is increased toward the left end of the selection wall portion 553d. Therefore, for example, when rotating the rotating crank member 570 clockwise in a front view from the upward orthogonal state (see FIG. 28A), the sliding projection 574 passes the first non-transmission wall 553b and the second non-transmission In the margin D (see FIG. 32B) until the wall 553c is reached, no driving force is transmitted to the pivoting arm member 550, and no restriction of rotation occurs. That is, the driving force is not transmitted from the pivoting crank member 570 to the pivoting arm member 550, and the restriction of the rotation of the pivoting arm member 550 by the sliding projection 574 does not occur.

  The right end portion of the second non-transmission wall portion 553c is formed along an arc S1 centered on the pivotal support hole 552 (the formation angle with the arc S1 is small), while the right end portion of the selection wall portion 553d is The second non-transmission wall portion 553c is formed to intersect the arc S2 centered on the pivot support hole 552 at an angle larger than the formation angle between the right end portion of the second non-transmission wall portion 553c and the arc S1.

  In this case, when the distance between the sliding projection 574 and the shaft support hole 552 changes, the amount of swing of the pivoting arm member 550, which is necessary to cope with the amount of change, changes. That is, when the distance between the sliding projection 574 and the shaft support hole 552 changes by a predetermined amount in a state where the sliding projection 574 and the right end of the selection wall 553d abut on each other, the swing amount of the pivot arm member 550 is The amount is smaller than the amount of swinging of the pivoting arm member 550 when the sliding protrusion 574 and the right end of the second non-transmission wall 553c abut each other in a predetermined amount. Therefore, whether the sliding projection 574 rotates along the second non-transmission wall 553c or along the selection wall 553d, the pivoting arm member 550 swings with respect to the speed of the pivoting crank member 570. You can change the speed.

  Referring back to FIG. 28 to FIG. FIGS. 28 to 31 are front views of the pivoting arm member 550 and the pivoting crank member 570 in which the pivoting of the pivoting arm member 550 and the rotation of the pivoting crank member 570 are illustrated in time series. In FIG. 28A, the upward orthogonal state described above is formed (the pivoting arm member 550 is disposed at the retracted position), and in FIG. 28 to FIG. 31, the pivoting crank member 570 is counterclockwise in front view. The rotated state is sequentially illustrated, and the deformed elongated hole 553 and a part of the rotating crank member 570 are illustrated by a hidden line, and the front plate member 546 and the projection 541 b of the expansion and contraction rendering device 540 are illustrated by an imaginary line. .

  In FIGS. 28 to 31, the expansion / contraction effect device 540 is detected by the position detection sensor (not shown) in the posture to expand and contract in the vertical direction, and the swing is stopped in that posture. That is, in FIGS. 28 to 31, the protrusion 541 b moves only in the vertical direction. In this case, the rocking of the expansion and contraction rendering device 540 is prevented by the resistance between the first drive device 530 (see FIG. 25) and the drive gear 532.

  In the state of FIG. 28A, the rotating crank member 570 is in the upward orthogonal state. In this case, the reference horizontal line O is set at a position lowered vertically from the projection 541 b by the distance h1. That is, when the rotating crank member 570 is in the upward orthogonal state, the projection 541 b is disposed at a position vertically separated from the reference horizontal line O by the distance h1.

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 28 (a) (rotated counterclockwise by an angle T1 from the upward orthogonal state (see FIG. 28 (a))), A state in which the sliding projection 574 is moved in the transmission groove 553a of the deformed elongated hole 553 and the projection 541 is spaced vertically upward from the reference horizontal line O by a distance h2 (h2 <h1) (FIG. 28 (b )) To reach. During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ). That is, the pivoting arm member 550 is swung.

  From the state of FIG. 28 (b), the rotating crank member 570 is rotated counterclockwise as viewed from the front (refer to FIG. 28 (a)), and the angle T2 (T2 ≒ 180 degrees> T1) counterclockwise. And the sliding projection 574 is moved (transmission area) in the transmission groove 553a of the deformed elongated hole 553 and enters the area facing the second non-transmission wall 553c, and the projection 541 is the reference. It reaches the state of the state (see FIG. 29A) arranged at a position separated by a distance h3 (h3 <h2) vertically upward from the horizontal line O. That is, the pivoting arm member 550 is swung.

  From the state shown in FIG. 28C, the rotating crank member 570 is rotated counterclockwise by an angle T3 (T3> T2) counterclockwise from the counterclockwise rotation in the front view (see FIG. 28A). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state shown in FIG. 29 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  When the pivoting arm member 550 is to be rotated clockwise in a front view from the state of FIGS. 29A and 29B, the sliding projection 574 is directed to the rotation shaft of the pivoting crank member 570 in a second direction. It is pushed by the non-transmission wall portion 553c. In this case, the movement of the sliding projection 574 is restricted, whereby the swinging of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from clockwise rotation in a front view from the state of FIGS. 29 (a) and 29 (b).

  Here, as a method of stopping the rotation of the rotation arm member 550 in the state of FIG. 29A, it is conceivable to stop the rotation crank member 570. However, if the rotating crank member 570 is rapidly stopped until the rendering speed of the rotating arm member 550 is reached just before reaching the extended position, the second drive device 560 is loaded, and the speed of the rotating crank member 570 is reduced. If it makes it loose, it will be impossible to improve the rendering effect.

  On the other hand, in the present embodiment, as shown in FIGS. 28 and 29, the pivoting arm is not rotated in the state of FIG. 29 (a) but is rotated to the state of FIG. 29 (b). The rotation of the member 550 can be stopped in the state of FIG. 29A (the projection 541 can be stopped at a position separated vertically upward from the reference horizontal line O by the distance h3). Thereby, the speed of the rotating crank member 570 is maintained until the rotating arm member 550 reaches the extended position, and thereafter, the rotating crank member from the state of FIG. 29 (a) to the state of FIG. 29 (b) The 570 can be slowed down. Therefore, there is no need to stop the rotating crank member 570 rapidly. Therefore, coexistence with the improvement of the rendering effect of the rotation arm member 550 and the improvement of the durability of the 2nd drive device 560 can be aimed at.

  From the state of FIG. 29 (b), the rotating crank member 570 is rotated counterclockwise in a front view (refer to FIG. 28 (a)), and then an angle T4 (T44270 degrees> T3). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed long hole 553 to reach the state of FIG. 30 (a). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  That is, while the turning crank member 570 is rotated by 1⁄4 turn counterclockwise from the state shown in FIG. 29A, the turning arm member 550 is maintained in the same posture, and the projections 541b are in the same position. Maintained. In the present embodiment, the length at which the pivoting arm member 550 is maintained in the same position and the projection 541b is maintained in the same position is set while the pivoting crank member 570 is rotated by 1⁄4 turn in this embodiment, There is no need to be limited to that. The length by which the front plate member 546 is kept in the lower position can be changed by changing the length of the second non-transmission wall portion 553c (see FIG. 28A) of the deformed elongated hole 553. For example, by making the second non-transmission wall portion 553c longer than the present embodiment, the length by which the front plate member 546 is continuously disposed at the lower position can be made longer than the present embodiment.

  From the state of FIG. 30 (a), the rotating crank member 570 is rotated counterclockwise by an angle T5 (T5> T4) counterclockwise from the counterclockwise rotation in the front view (see FIG. 28 (a)). State, the sliding projection 574 pushes up the selected wall 553d of the deformed elongated hole 553 and the projection 541 is disposed at a position vertically separated from the reference horizontal line O by a distance h2 (h2> h3) (See FIG. 30 (b)). During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ).

  That is, when the pivoting arm member 550 and the pivoting crank member 570 are rotated counterclockwise in a front view, the selective wall portion 553d and the sliding projection 574 are in contact with each other, whereby the pivoting arm member The driving force is transmitted to 550 (transmission area).

  From the state of FIG. 30 (b), the rotating crank member 570 is rotated counterclockwise by an angle T6 (T6> T5) counterclockwise from a front view counterclockwise (see FIG. 28 (a)). And the sliding projection 574 enters the area facing the first non-transmission wall 553b of the deformed elongated hole 553 and the projection 541 vertically upward from the reference horizontal line O by the distance h1 (h1> h2). A state of being placed at a spaced position (see FIG. 31) is reached. During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ).

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 31, the sliding projection 574 is moved in the region facing the first non-transmission wall 553b of the deformed elongated hole 553, as shown in FIG. The state of 28 (a) is reached. During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm No driving force is transmitted to the member 550 (non-transmission area).

  When the pivoting arm member 550 is rotated counterclockwise in the front view from the state of FIG. 31, the sliding projection 574 is pushed by the second non-transmission wall portion 553c toward the rotation shaft of the pivoting crank member 570. . In this case, the movement of the sliding projection 574 is restricted, whereby the swinging of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from rotating counterclockwise in a front view from the state of FIG.

  Here, as a method of stopping the rotation of the rotation arm member 550 in the state of FIG. 31, it is conceivable to stop the rotation crank member 570. However, when the rotating crank member 570 is rapidly stopped until the rendering speed of the rotating arm member 550 reaches the retracted position immediately before reaching the retraction position, a load is applied to the second drive device 560 and the speed decrease of the rotating crank member 570 is moderated. If this is the case, it will not be possible to improve the rendering effect.

  On the other hand, in the present embodiment, the rotation of the rotation arm member 550 is stopped in the state of FIG. 31 by rotating the rotation crank member 570 to the state of FIG. 28 (a) without stopping in the state of FIG. Can. Thereby, the speed of the rotating crank member 570 is maintained until the rotating arm member 550 reaches the extended position, and thereafter, the rotating crank member 570 is decelerated from the state of FIG. 31 to the state of FIG. It can be done. Therefore, there is no need to stop the rotating crank member 570 rapidly. Therefore, coexistence with the improvement of the rendering effect of the expansion-contraction rendering device 540 interlocked with the rotation arm member 550 and the improvement of the durability of the second drive device 560 can be achieved.

  As shown in FIGS. 28 to 31, rotating the rotating crank member 570 once in the same direction enables the rotating arm member 550 to swing back and forth between the retracted position and the extended position.

  From these things, when rotating the rotation crank member 570 at a constant speed counterclockwise as shown in FIGS. 28 to 31, the projection 541b is a reference horizontal line in a half period of the rotation cycle of the rotation crank member 570. It is moved downward from a position separated by a distance h1 vertically upward from O to a position separated by a distance h3 (h3 <h1). The protrusion 541b is maintained at a position separated by a distance h3 vertically upward from the reference horizontal line O in a period of 1⁄4 of the subsequent rotation period, and in the period of 1⁄4 of the subsequent rotation period, the protrusion 541b is a reference horizontal line O From the position vertically separated by a distance h3 from above, the pressure is raised and moved to a position separated by a distance h1 (h1> h3). Thereby, even when the rotating crank member 570 is moved at a constant speed, the moving speed of the projection 541 b (moving speed of the expansion / contraction effect device 540 in the expansion / contraction direction) can be doubled.

  Here, at the retracted position of the pivoting arm member 550, the pivoting arm member 550 and the pivoting crank member 570 can form an upward orthogonal state (see FIG. 28A), and the overhang of the pivoting arm member 550 In the position, the pivoting arm member 550 and the pivoting crank member 570 can form a downward and orthogonal state (see FIG. 29A). It is possible to form a downward orthogonal state by rotating the rotating crank member 570 a predetermined amount clockwise in a front view from the state of FIG. 29 (a).

  Therefore, in the present embodiment, in order to swing the pivoting arm member 550 from the retracted position to the extended position, the pivoting crank member 570 is rotated by a half turn (180 degrees). Therefore, when the rotating crank member 570 is rotated at a constant speed, the time required for the rotating arm member 550 to swing from the retracted position to the extended position (from FIG. 28 (a) to FIG. 29 (a) 29) and the time required to swing from the extended position to the retracted position (see FIG. 29A through FIG. 31A to FIG. 28A) can be equal.

  The relationship between the swinging of the pivoting arm member 550 and the rotation of the pivoting crank member 570 will be described with reference to FIGS. 32 to 35 are front views of the pivoting arm member 550 and the pivoting crank member 570, which illustrate the pivoting of the pivoting arm member 550 and the rotation of the pivoting crank member 570 in time series. In FIGS. 32 to 35, a state in which the rotating crank member 570 is rotated clockwise in a front view is illustrated, and the deformed elongated hole 553 and a part of the rotating crank member 570 are illustrated as a hidden line. The front plate member 546 and the protrusion 541 b of the effect device 540 are illustrated by imaginary lines.

  In FIG. 32A, the above-described upward orthogonal state is formed (the pivoting arm member 550 is disposed at the retracted position), and from FIG. 32B to FIG. 35, the pivoting arm is from FIG. The state in which the member 550 and the rotation crank member 570 are rotated by a predetermined amount is sequentially illustrated in time series.

  In the state of FIG. 32A, the rotating crank member 570 is in the upward orthogonal state. In this case, the protrusion 541 b is disposed at a position vertically separated from the reference horizontal line O by a distance h1.

  From the state of FIG. 32 (a), the pivoting crank member 570 is rotated clockwise as viewed from the front (rotated clockwise by an angle T11 from the orthogonal upward state (see FIG. 32 (a))). The projection 574 is moved in the area facing the first non-transmission wall 553b of the deformed elongated hole 553 to reach the state of FIG. 32 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h1.

  When the pivoting arm member 550 is rotated counterclockwise in the front view from the state of FIG. 32 (b), the sliding projection 574 is restricted in movement, so that the pivoting of the pivoting arm member 550 is restricted. Ru. Therefore, the pivoting arm member 550 is prevented from rotating counterclockwise in a front view from the state of FIG. 32 (b).

  From the state of FIG. 32 (b), the pivoting crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)) and is rotated clockwise by an angle T12 (T12> T11). As shown in FIG. 33 (a), the sliding projection 574 is slightly separated from the inner circumferential surface of the deformed elongated hole 553 and the pivoting arm member 550 is swung downward by the action of gravity. In this case, in the margin D from the state shown in FIG. 32B until the sliding projection 574 passes the first non-transmission wall 553b and reaches the second non-transmission wall 553c, the pivot arm member 550 The driving force is not transmitted (non-transmission area), and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h4 (h4 <h1).

  From the state of FIG. 33 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)) and is rotated clockwise by an angle T13 (T13> T12). And as shown in FIG. 33 (b), the sliding projection 574 is brought into contact with the second non-transmission wall portion 553c of the deformed elongated hole 553 of the pivot arm member 550 pivoted downward by the action of gravity. Ru. That is, from the state of FIG. 33B to the state of FIG. 34A, the driving force is transmitted to the pivoting arm member 550 (transmission area). In the state of FIG. 33B, the protrusion 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h5 (h5 <h4).

  From the state of FIG. 33 (b), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), only by an angle T14 (T141490 degrees> T13). And the sliding projection 574 is accommodated at the right end of the second non-transmission wall 553c of the deformed elongated hole 553 and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by the distance h3 Is reached (see FIG. 34A). During this time, the inner circumferential surface of the deformed elongated hole 553 abuts in the moving direction of the sliding projection 574, and the driving force is transmitted to the pivoting arm member 550 (transmission area).

  Here, the rotation of the pivoting crank member 570 shown in FIG. 32 (b) to FIG. 34 (a) and the rotation of the pivoting crank member 570 shown in FIG. 30 (a) to FIG. Although the rotation direction of the movable crank member 570 is different, the rotation area (phase) of the rotating crank member 570 is the same.

  In this case, in the rotation of the pivoting crank member 570 shown in FIGS. 32 (b) to 34 (a), the inner periphery of the deformed elongated hole 553 in the moving direction of the sliding projection 574 of the pivoting crank member 570. While the surface is not in contact, the driving force is not transmitted to the rotating arm member 550 (non-transmission area), while the rotation of the rotating crank member 570 shown in FIG. 30A to FIG. The driving force is transmitted to the rotation arm member 550 (transmission area).

  Therefore, the mode of transmission of the driving force to the pivoting arm member 550 can be changed according to the rotation direction of the pivoting crank member 570. Thus, by reversing the rotation direction of the rotating crank member 570, two effects of the rotating arm member 550 can be formed.

  That is, in the present embodiment, when the sliding projection 574 of the pivoting crank member 570 rotates between FIG. 32A and FIG. 34A, the pivoting crank member 570 rotates clockwise as viewed from the front. When rotated, the pivoting arm member 550 is swung by free fall depending on the gravitational acceleration (non-transmission area) until the sliding projection 574 abuts on the inner circumferential surface of the deformed elongated hole 553. On the other hand, when the rotating crank member 570 is rotated counterclockwise in a front view, the rotating arm member 550 is swung at a speed depending on the rotational speed of the rotating crank member 570 (transmission area).

  Thereby, even when the rotation speed of the rotation crank member 570 is equalized, the rotation direction when the rotation crank member 570 is arranged in the same phase by reversing the rotation direction of the rotation crank member 570 Variations of the swing speed of the arm member 550 can be increased.

  Further, the variation of the swinging speed of the pivoting arm member 550 is achieved by the shape of the deformed elongated hole 553 (the formation of the margin D), so that the aspect of the transmission of the driving force to the pivoting arm member 550 is It is possible to eliminate the need for another member such as a changeover switch for changing, and to reduce the member cost.

  In the present embodiment, the margin D is formed on the side of the pivotal support hole 552 of the pivoting arm member 550. Therefore, while the sliding projection 574 passes through the margin D by a predetermined distance, as compared with the case where the margin D is formed on the opposite side of the support hole 552 with respect to the rotation shaft of the rotating crank member 570. The distance by which the protrusion 541 b moves downward can be increased. Therefore, it is possible to make the change of the operation of the pivoting arm member 550 in the case where the rotation direction of the pivoting crank member 570 is made different while suppressing the formation range of the surplus portion D of the pivoting crank member 570.

  From the state of FIG. 34 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), and is rotated clockwise by an angle T15 (T15> T14). And the sliding projection 574 is slid on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state shown in FIG. 34 (b). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  When the pivoting arm member 550 is to be rotated clockwise in a front view from the state of FIG. 34 (b), the sliding projection 574 is directed to the rotation axis of the pivoting crank member 570 by the second non-transmission wall portion 553c. It is pushed. In this case, the movement of the sliding projection 574 is restricted, so that the pivoting of the pivoting arm member 550 is restricted. Therefore, the pivoting arm member 550 is prevented from rotating clockwise in a front view from the state of FIG. 34 (b).

  From the state of FIG. 34 (b), the turning crank member 570 is rotated clockwise in a front view (refer to FIG. 32 (a)), and only by an angle T16 (T16 ≒ 180 degrees> T15). When it is rotated, the sliding projection 574 slides on the second non-transmission wall 553c of the deformed elongated hole 553 to reach the state of FIG. 35 (a). During this time, since the inner peripheral surface of the deformed elongated hole 553 is not disposed in the moving direction of the sliding projection 574, the sliding projection 574 is idled relative to the pivoting arm member 550, and the pivoting arm The driving force is not transmitted to the member 550 (non-transmission area), and the projection 541 is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3.

  From the state of FIG. 35 (a), the rotating crank member 570 is rotated clockwise as viewed from the front (refer to FIG. 32 (a)), and is rotated clockwise by an angle T17 (T17> T16). And the sliding projection 574 is moved in the transmission groove 553a (transmission area), and the projection 541 is disposed at a position separated vertically upward from the reference horizontal line O by a distance h2 (h2> h3) (FIG. 35). (B) see). That is, the pivoting arm member 550 is swung.

  Here, when the rotation of the rotation crank member 570 and the swing of the rotation arm member 550 are always interlocked, it is difficult to shift the start timing of the rotation crank member 570 and the rotation arm member 550 . Therefore, when the pivoting crank member 570 and the pivoting arm member 550 are started, it is necessary to generate a large force corresponding to the rigidity of the force that overcomes the inertia of each member. Therefore, a drive having a large driving force is required, which may increase the size of the drive.

  On the other hand, in the present embodiment, the start timings of the pivoting crank member 570 and the pivoting arm member 550 can be shifted. That is, for example, from the state of FIG. 34 (b) to the state of FIG. 35 (a), only the pivoting crank member 570 is rotated, and from the state of FIG. 35 (a) to the state of FIG. 35 (b) The rotation arm member 550 can be started by interlocking with the rotation crank member 570.

  Thereby, since the force of the rotating crank member 570 can be utilized for starting the rotating arm member 550, the driving force necessary for the second drive device 560 can be suppressed. Therefore, the second drive device 560 can be miniaturized.

  When the rotating crank member 570 is rotated clockwise in a front view from the state of FIG. 35 (b), the sliding projection 574 is moved in the transmission groove portion 553a to reach the state of FIG. 32 (a). During this time, the inner peripheral surfaces of the deformed elongated holes 553 are disposed in the moving direction of the sliding projection 574 and are in contact with each other, so that the driving force is transmitted from the sliding projection 574 to the pivoting arm member 550 (transmission area ). That is, the pivoting arm member 550 is swung.

  From these things, as shown in FIGS. 32 to 35, in the case where the rotating crank member 570 is rotated at the same speed clockwise, the protrusion 541b is a reference in a period of 1⁄4 of the rotation cycle of the rotating crank member 570. From a position separated by a distance h1 vertically upward from the horizontal line O, it is moved downward to a position separated by a distance h3 (h3 <h1). The protrusion 541b is maintained at a position separated vertically upward from the reference horizontal line O by the distance h3 in a period of 1⁄4 of the subsequent rotation period, and the protrusion 541b is perpendicular to the reference horizontal line O in a period of half the subsequent rotation period. From a position spaced apart by a distance h3 upward, it is moved up to a position spaced by a distance h1 (h1> h3). Thereby, even when the rotating crank member 570 is moved at a constant speed, the moving speed of the projection 541 b (moving speed of the expansion / contraction effect device 540 in the expansion / contraction direction) can be doubled.

  In addition, the moving speed of the pivoting arm member 550 is partially accelerated by gravity acceleration when it is moved downward, while the moving speed of the rotating arm member 550 is always along the rotational speed of the rotating crank member 570 when it is moved upward. Be done. Thereby, the aspect of the speed change of the projection part 541b (the expansion-contraction effect device 540) can be changed by the movement direction of the projection part 541b (the expansion-contraction effect device 540).

  A change in the distance from the reference horizontal line O of the protrusion 541 b (the expansion / contraction effect device 540) when the turning crank member 570 is rotated clockwise or counterclockwise will be described with reference to FIG. 36.

  FIG. 36 is a graph showing the distance from the reference horizontal line O of the protrusion 541b (see FIG. 28A). In the graph shown in FIG. 36, the swing angle is shown on the horizontal axis with the upper right angle (see FIG. 28 (a)) of the rotating crank member 570 as the left end and increasing to the right The distance from the reference horizontal line O of the protrusion 541 b is shown in FIG.

  In FIG. 36, the distance from the reference horizontal line O of the protrusion 541b when the pivoting crank member 570 is rotated counterclockwise is indicated by a curve CC1, and the pivoting crank member 570 is rotated clockwise. The distance from the reference horizontal line O of the protrusion 541 b is indicated by a curve CW1. Curves CC1 and CW1 correspond to the states of the protrusions 541b shown in FIG. 28 to FIG. 35, respectively, and for the purpose of comparison when the rotating crank members 570 are arranged in the same phase, A curve obtained by inverting the curve CC1 from side to side is illustrated by an imaginary line as a curve CC2. As described above, the rising speed and the falling speed of the protrusion 541b moved up and down by the rotating arm member 550 are changed by reversing the rotating direction of the rotating crank member 570 as described above by comparing the curves CC1 and CW1. Can.

  As a comparison target of the curve CW1, when the rotating crank member 570 rotates clockwise, the sliding projection 574 rotates until it abuts on the second non-transmission wall 553c (see FIG. 28A). The case where the arm member 550 (see FIG. 28A) is disposed at the retracted position is illustrated by a broken line as a curve CW2. This corresponds to the case where the biasing force that causes the torsion spring 517a (see FIG. 23) to swing the pivoting arm member 550 upward is set large. In this case, the period in which the pivoting arm member 550 is disposed at the retracted position can be made longer.

  In the angle range N1 in which the distance from the horizontal reference line O of the protrusion 541b (see FIG. 28A) is maintained without being changed in the curves CC1 and CW1, the rotating crank member 570 and the rotating arm member 550 ( A non-transmission area to which the driving force is not transmitted is formed with respect to FIG. 28 (a). The width of the angular range N1 can be adjusted by the formation width of the second non-transmission wall portion 553c (see FIG. 28A).

  Further, in the curve CW1, an angle until the sliding projection 574 of the pivoting crank member 570 (see FIG. 28A) abuts on the deformed elongated hole 553 of the pivoting arm member 550 (see FIG. 28A). In the range N2, a non-transmission area in which the driving force is not transmitted is formed between the rotation crank member 570 and the rotation arm member 550. The width of the angle range N2 can be adjusted by the formation width of the first non-transmission wall portion 553b (see FIG. 28A).

  As shown in FIG. 36, a curve is formed between the angle T11 to the angle T14 and the angle T4 to the angle T6 in the case where the rotating crank members 570 (see FIG. 28A) are arranged in the same phase. The shapes of the CW1 and the curve CC1 are different (the curve CW1 and the curve CC2 obtained by inverting the left and right of the curve CC1 do not overlap).

  That is, the angle when the pivoting crank member 570 (see FIG. 28A) lifts the pivoting arm member 550 (see FIG. 28A) between the angle T4 and the angle T6 is the angle As compared with the case where the pivoting crank member 570 rotates in a mode in which the pivoting arm member 550 is pushed down from 11 to the angle T14, a gentle curve is obtained.

  This is because, in the curve CW1, the sliding projection 574 (see FIG. 28 (a)) abuts on the second non-transmission wall 553c (see FIG. 28 (a)) of the deformed elongated hole 553 and the pivoting arm member 550 (see FIG. FIG. 28 (a) is rotated, and in the curve CC1, the sliding projection 574 abuts on the selected wall 553d (see FIG. 28 (a)) of the deformed elongated hole 553 and the pivoting arm member 550 is rotated. Depends on

  Referring back to FIG. 28 (a), description will be made. As described above, in the deformed long hole 553, the right end of the second non-transmission wall portion 553c is formed along the arc S1 centering on the axial support hole 552 (the formation angle with the arc S1 is small) The right end portion of the selected wall portion 553d is formed to intersect the arc S2 centered on the pivot hole 552 at an angle larger than the formation angle of the right end portion of the second non-transfer wall portion 553c and the arc S1. Ru.

  In this case, when the distance between the sliding projection 574 and the shaft support hole 552 changes, the amount of swing of the pivoting arm member 550, which is necessary to cope with the amount of change, changes. That is, when the distance between the sliding projection 574 and the shaft support hole 552 changes by a predetermined amount in a state where the sliding projection 574 and the right end of the selection wall 553d abut on each other, the swing amount of the pivot arm member 550 is The amount is smaller than the amount of swinging of the pivoting arm member 550 when the sliding protrusion 574 and the right end of the second non-transmission wall 553c abut each other in a predetermined amount.

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

  Although the case where the rotation crank member 570 is rotated in one direction has been described with reference to FIGS. 28 to 35, it is also possible to reverse the rotation direction of the rotation crank member 570 halfway. As the timing to reverse the rotation direction of the rotating crank member 570, the sliding projection 574 is disposed opposite to the first non-transmission wall 553b (for example, FIG. 28A, FIG. 31 and FIG. 32A) 32 (b), the pivoting arm member 550 is disposed at the retracted position), and the sliding projection 574 is disposed opposite to the second non-transmission wall 553c (for example, FIG. 29 (a), 29 (b), 34 (b) and 35 (a), the pivoting arm member 550 is preferably disposed in the extended position).

  In this case, since the rotation arm member 550 is not in contact with the rotation direction of the rotation crank member 570, the resistance applied to the rotation crank member 570 from the rotation arm member 550 when the rotation direction of the rotation crank member 570 is reversed. It can be suppressed. Further, in the present embodiment, a position detection sensor (not shown) for detecting a state in which the pivoting arm member 550 is disposed at the retracted position and a state in which the pivoting arm member 550 is disposed at the overhang position is disposed. Control in which the rotation direction of the rotating crank member 570 is reversed can be facilitated with the movable arm member 550 disposed at the retracted position or the extended position.

  By reversing the rotation direction of the rotating crank member 570, variations of the reciprocating operation of the expansion and contraction rendering device 540 in the vertical direction can be increased.

  For example, from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 28A), the pivoting crank member 570 is rotated counterclockwise a half turn (see FIG. 29A), and then The direction of rotation of the movable crank member 570 is reversed, and the case where the pivoting arm member 550 is disposed at the retracted position is illustrated by being rotated by a half turn clockwise (see FIG. 28A). That is, the sliding projection 574 is moved on the opposite side of the support hole 552.

  In this case, the protrusion 541 b of the expansion / contraction effect device 540 is separated from the reference horizontal line O by a distance h1 from the reference horizontal line O in a half period of the rotation cycle of the rotary crank member 570 by a distance h3 (h3 <h1 Move down to a position separated by). In this case, the protrusion 541b moves downward along the curve CC1 (see FIG. 36) whose horizontal axis is from 0 degrees to 180 degrees. Then, the projection 541 b extends from a position separated by a distance h3 vertically upward from the reference horizontal line O in a half period of the rotation cycle of the rotary crank member 570 to a position separated by a distance h1 (h1> h3) from the reference horizontal line O Move up. In this case, the protrusion 541b moves upward along the curve CW1 (see FIG. 36) whose horizontal axis is from 180 degrees to 360 degrees.

  Thus, when the rotating crank member 570 rotates at a constant speed, the protrusion 541b of the expansion / contraction effect device 540 is moved upward by a predetermined distance (h1-h3) and a period in which the projection 541b descends by a predetermined distance (h1-h3). Period can be the same.

  Also, for example, from the state where the pivoting arm member 550 is disposed at the retracted position (see FIG. 32A), the pivoting crank member 570 is rotated by 1⁄4 turn clockwise (see FIG. 34A) Then, the direction of rotation of the rotating crank member 570 is reversed, and the case where the rotating arm member 550 is disposed at the retracted position is illustrated by being rotated by 1⁄4 of the counterclockwise direction (FIG. 32). See (a)). That is, this is the case where the sliding projection 574 moves on the side in which the sliding projection 574 approaches the support hole 552.

  In this case, the protrusion 541 b of the expansion / contraction effect device 540 is a distance h3 (h3) from the reference horizontal line O from a position separated vertically upward from the reference horizontal line O by a distance h1 in a period of 1⁄4 of the rotation cycle of the rotary crank member 570. Move down to a position separated by <h1). In this case, the protrusion 541b moves downward along the curve CW1 (see FIG. 36) whose horizontal axis is from 0 degrees to 90 degrees. Then, the protrusion 541b is separated from the reference horizontal line O by a distance h1 (h1> h3) from a position separated by a distance h3 vertically upward from the reference horizontal line O in a period of 1⁄4 of the rotation cycle of the rotary crank member 570 Move up to the position. In this case, the protrusion 541b moves upward along a curve CC1 (see FIG. 36) whose horizontal axis is 270 degrees to 360 degrees.

  Thus, when the rotating crank member 570 is rotated at a constant speed, the protrusion 541b of the expansion / contraction effect device 540 is moved downward by a predetermined distance (h1-h3), and is raised by a predetermined distance (h1-h3). The period of movement can be made the same, and the predetermined period can be shortened as compared with the case where the sliding projection 574 is moved on the opposite side of the pivot hole 552.

  In addition, when the protrusion 541b of the expansion and contraction rendering device 540 moves downward, it can be partially dropped (from the angle T11 to the angle T13) as free fall, while the protrusion 541b of the expansion and contraction rendering device 540 moves upward In this case, it is always moved at a speed in accordance with the rotational speed of the rotating crank member 570. Therefore, even if the rotation speed of the rotation crank member 570 is the same, the movement mode of the expansion / contraction effect device 540 in the case where the rotation crank member 570 is disposed in the same phase depending on the movement direction of the protrusion 541b of the expansion / contraction effect device 540 The degree of speed change) can be changed. In other words, the curve CW1 and the curve CC2 in the range from the angle T11 to the angle T13 in FIG. 36 can be made different.

  Next, the difference in the swing angle due to the difference in the expansion / contraction state of the expansion / contraction effect device 540 will be described. First, the swing angle when the expansion / contraction effect device 540 forms an extended state will be described.

  FIGS. 37 to 39 are front views of the combined operation unit 500. FIG. Note that FIGS. 37 to 39 illustrate the case where the expansion / contraction effect device 540 forms an extended state (when the pivoting arm member 550 is disposed at the extended position). Further, FIG. 37 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 39, the state of being moved clockwise in a front view from the state of FIG. 37 is illustrated. The attitude of the pivoting arm member 550 shown in FIGS. 37 to 39 is the same as the attitude of the pivoting arm member 550 shown in FIG. Therefore, in FIGS. 37 to 39, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h3.

  As illustrated in FIGS. 37 to 39, the swinging locus of the protrusion 541b when the expansion / contraction effect device 540 forms an extended state is formed in an arc shape centering on the first shaft 512 and is rotated. Along the extending direction of the arc-shaped hole 554 of the arm member 550. In other words, the arc-shaped hole 554 is extended along the swinging trajectory of the protrusion 541 b. Therefore, the inner surface of the arc-shaped hole 554 is not disposed facing the swing direction of the protrusion 541 b, and the arc-shaped hole 554 does not function as a stopper for stopping the swing of the protrusion 541 b. Therefore, the swing angle of the protrusion 541 b depends on the method of regulating the swing of the rotary plate 520. That is, the rotary plate 520 can be rocked until it abuts on the third stopper portion 518c, and the protrusion 541b can be rocked to the rocking angle θ1 counterclockwise in a front view, and the rotary plate 520 is second The protrusion 541 b can be swung until it abuts against the stopper portion 518 b, and the protrusion 541 b can swing to a swing angle θ 2 clockwise in a front view.

  Here, as shown in FIG. 39, when the protrusion 541 b is swung leftward in a front view at a swing angle θ 2, the protrusion 541 b is separated from the arc-shaped hole 554 of the pivot arm member 550. In this case, the expansion / contraction effect device 540 is moved in the expansion / contraction direction independently from the pivoting arm member 550, and the projection 541b can not return to the arc-shaped hole 554, which may cause an operation failure.

  On the other hand, in the present embodiment, even when the protrusion 541b is separated from the arc-shaped hole 554 of the pivoting arm member 550, the first raised fastening portion 541c and the guide fastening portion 541e of the expansion and contraction rendering device 540 are pivoting arm members By being arranged so as to be engageable with 550, alignment between the protrusion 541b and the arc-shaped hole 554 can be performed. That is, the telescopic effect device 540 can be prevented from being moved in the telescopic direction independently of the pivoting arm member 550.

  Thus, the length of the pivoting arm member 550 can be shortened while eliminating the defect that the projection 541 b can not return to the arc-shaped hole 554. Thereby, the arrangement | positioning area | region of rotation arm member 550 can be suppressed, and the arrangement | positioning area | region of another movable member can be ensured by that much. In addition, the material cost of the pivoting arm member 550 can be reduced.

  When the pivoting arm member 550 swings in a state where the projection 541b is separated from the arc-shaped hole 554 (see FIG. 39), the positional relationship between the projection 541b and the arc-shaped hole 554 deviates, and the projection 541b is circular. It is difficult to return to the arc-shaped hole 554, which may cause malfunction. On the other hand, in the present embodiment, the sliding projection 574 abuts on the deformed elongated hole 553 to prevent the pivoting arm member 550 from swinging (see FIG. 39).

  In addition to that, the movement locus of the point (the point furthest from the rotation axis) remote from the rotation axis of the slide projection 574 is formed along the side surface of the deformed elongated hole 553 which is in contact with the slide projection 574 Therefore, the rotating crank member 570 can be rotated counterclockwise from the state of FIG. 39 while maintaining the posture of the rotating arm member 550 (see FIG. 39).

  Here, for example, as shown in FIG. 28 to FIG. 31, when the rotating crank member 570 rotates counterclockwise, immediately after the rotating arm member 550 is placed at the extended position (FIG. 29 (a 30) the projection 541b is separated from the arc-shaped hole 554, and then the projection 541b returns to the arc-shaped hole 554 until the rotating crank member 570 is disposed in the state shown in FIG. think of. If the projection 541b is returned to the arc-shaped hole 554, the pivoting crank member 570 is further rotated, and even if the pivoting arm member 550 pivots to the state shown in FIG. 30 (b), the projection 541b However, there is no malfunction that the circular hole 554 can not return.

  In this case, when the pivoting arm member 550 and the expansion / contraction effect device 540 are respectively pivoted, stop control or start control of the pivoting crank member 570 is performed according to the positional relationship between the protrusion 541b and the arc-shaped hole 554. There is no need, and the rotation of the rotating crank member 570 can be continued. In other words, it is only necessary to control the swing timing of the expansion / contraction effect device 540, and the pivoting crank member 570 does not need to be controlled, and may be kept rotating. Therefore, it is possible to suppress the control load of the complicated operation of swinging the telescopic effect device 540 and the pivoting arm member 550 at different timings.

  In the present embodiment, the fore-end portion 554a is formed such that the width of the arc-shaped hole 554 can be increased toward the opening end (the left end of FIG. 39) of the arc-shaped hole 554. Thereby, the positional deviation (positional deviation of the expansion / contraction effect device 540 in the expansion / contraction direction) when the projection 541 b returns to the arc-shaped hole 554 can be largely tolerated, and the first bulky fastening portion 541 c and the guide fastening portion 541 e A large clearance from the pivoting arm member 550 can be secured.

  Next, a swing angle when the expansion / contraction effect device 540 forms an intermediate state which is a state between an extended state and a reduced state will be described. By swinging the pivoting arm member 550 clockwise from the state in which the expansion / contraction effect device 540 is in the expanded state (see FIG. 37), the protrusion 541 b moves corresponding to the arc-shaped hole 554, and the expansion / contraction effect Device 540 forms an intermediate state.

  40 to 42 are front views of the combined operation unit 500. FIG. FIGS. 40 to 42 illustrate the case where the expansion / contraction effect device 540 forms an intermediate state (when the pivoting arm member 550 is disposed between the overhanging position and the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541 b is shorter than the case where the expansion / contraction effect device 540 forms an extended state (see FIGS. 37 to 39). That is, the swinging trajectory of the protrusion 541 b is changed according to the state of the expansion / contraction effect device 540 in the expansion / contraction direction.

  Further, FIG. 40 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 42, the state of being moved clockwise in a front view from the state of FIG. 40 is illustrated.

  The attitude of the pivoting arm member 550 shown in FIGS. 40 to 42 is the same as the attitude of the pivoting arm member 550 shown in FIG. 28 (b). Therefore, in FIGS. 40 to 42, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h2.

  At this time, the front plate member 546 is driven to interlock with the upward movement of the arc-shaped hole 554 by the pivoting arm member 550 swinging. Therefore, the circular arc-shaped hole 554 has a function of changing the swing angle of the protrusion 541b as described later and a function of interlocking the pivot arm member 550 and the front plate member 546. This makes it possible to centralize the functions.

  As illustrated in FIG. 40 to FIG. 42, the swinging trajectory of the protrusion 541b when the expansion / contraction effect device 540 forms an intermediate state, and the shape of the arc-shaped hole 554 of the pivoting arm member 550 have a curvature radius Although the central axes of the two coincide with each other on the upper side, the radius of curvature and the posture differ from each other. Since the swinging locus of the protrusion 541b and the arc-shaped hole 554 intersect at the formation angle α1 (see FIG. 42), the arc-shaped hole 554 acts as a stopper for stopping the swing of the protrusion 541b (see FIG. 42) .

  As shown in FIG. 41, when the rotary plate 520 is rotated counterclockwise in a front view, the protrusion 541b is not in contact with the arc-shaped hole 554. That is, since the rotary plate 520 can be rocked until it abuts on the third stopper portion 518c, the projection 541b can be rocked to the rocking angle θ3 counterclockwise in a front view (angle θ3 = Angle θ1).

  As shown in FIG. 42, when the rotary plate 520 is rotated clockwise in a front view, the protrusion 541 b is abutted by the first stopper surface 554 b of the arc-shaped hole 554. In this state, the guide fastening portion 541e is in contact with the upper side surface of the pivoting arm member 550, and the change in state of the expansion / contraction effect device 540 in the expansion / contraction direction is prevented. Motion is stopped.

  That is, the rotary plate 520 is not rocked until it abuts on the third stopper 518c, and the projection 541b can be rocked clockwise to the rocking angle θ4 in a front view (angle θ4 <angle θ2). . Therefore, the swing angle of the protrusion 541 b can be changed depending on the state of the extension effect device 540 in the extension direction. As a result, by making the expansion and contraction state of the expansion and contraction rendering device 540 different, the variation of the swing angle of the expansion and contraction rendering device 540 can be increased. In the state shown in FIG. 42, the guide fastening portion 541e is in contact with the main portion 551 of the pivoting arm member 550.

  Next, the swing angle when the expansion / contraction effect device 540 forms a contracted state will be described. By swinging the pivoting arm member 550 clockwise from the state (see FIG. 40) in which the expansion / contraction effect device 540 is in the intermediate state, the protrusion 541 b moves corresponding to the arc-shaped hole 554, and expansion / contraction effect Device 540 forms a reduced state.

  43 to 45 are front views of the combined operation unit 500. FIG. FIGS. 43 to 45 illustrate the case where the expansion / contraction effect device 540 forms a contracted state (when the pivoting arm member 550 is disposed at the retracted position). In this case, the radius formed by the swinging trajectory of the protrusion 541 b is shorter than that in the case where the expansion / contraction effect device 540 forms an intermediate state (see FIGS. 40 to 42). That is, the swinging trajectory of the protrusion 541 b is changed according to the state of the expansion / contraction effect device 540 in the expansion / contraction direction.

  Further, FIG. 43 illustrates a state in which the protrusion 541 b of the expansion and contraction rendering device 540 is disposed on the vertical line of the first shaft 512 of the base member 510, and in FIG. The state of being moved in a counterclockwise direction is illustrated, and in FIG. 45, the state of being moved clockwise in a front view from the state of FIG. 43 is illustrated. Note that the attitude of the pivoting arm member 550 shown in FIGS. 43 to 45 is the same as the attitude of the pivoting arm member 550 shown in FIG. Therefore, in FIGS. 43 to 45, the front plate member 546 is disposed at a position spaced apart from the reference horizontal line O by the distance h1.

  At this time, the front plate member 546 is driven to interlock with the upward movement of the arc-shaped hole 554 by the pivoting arm member 550 swinging. Therefore, the arc-shaped hole 554 has a function of changing the swing angle of the protrusion 541b and a function of interlocking the pivot arm member 550 and the front plate member 546. This makes it possible to centralize the functions.

  As illustrated in FIGS. 43 to 45, the swinging trajectory of the protrusion 541b when the expansion / contraction effect device 540 forms a contracted state and the shape of the arc-shaped hole 554 of the pivoting arm member 550 are different from each other, The central axis of the radius of curvature is reversed. That is, the central axis of the radius of curvature of the rocking trajectory of the projection 541 b is below the projection 541 b, and the central axis of the radius of curvature of the arc-shaped hole 554 is disposed above the arc-shaped hole 554. In this case, the swinging trajectory of the protrusion 541b and the arc-shaped hole 554 intersect at the formation angle α2 (angle α2> angle α1), and the arc-shaped hole 554 acts as a stopper for stopping the swing of the protrusion 541b ( 44 and 45).

  As shown in FIG. 44, when the rotary plate 520 is rotated counterclockwise in a front view, the protrusion 541 b abuts on the second stopper surface 554 c of the arc-shaped hole 554. In this case, the rotary plate 520 is not rocked until it abuts on the third stopper portion 518c (see FIG. 41), and the projection 541b can be rocked counterclockwise to the rocking angle θ5 in a front view. (Angle θ5 <angle θ1 = angle θ3).

  As shown in FIG. 45, when the rotary plate 520 is rotated clockwise in a front view, the protrusion 541 b is abutted by the third stopper surface 554 d of the arc-shaped hole 554. In this case, the rotary plate 520 is not rocked until it abuts on the third stopper 518c, and the projection 541b can be rocked clockwise to the rocking angle θ6 in a front view (angle θ6 <angle θ4 <Angle θ 2). Therefore, the swing angle of the protrusion 541 b can be changed depending on the state of the extension effect device 540 in the extension direction. Thereby, the variation of the rocking width of the expansion / contraction effect device 540 can be increased.

  Here, the movement trajectory of projection 541 b in the contracted state and formation angle α2 of arc-shaped hole 554 are formed larger than the formation angle α1 of the movement trajectory of projection 541 b in the intermediate state and arc-shaped hole 554 Ru.

  In the relationship between the swinging locus of the protrusion 541b and the arc-shaped hole 554, if the formation angle is 90 degrees, the protrusion 541b is swung in a mode crossing the arc-shaped hole 554, and the protrusion 541b The rocking angle of is minimized. On the other hand, in the relationship between the swinging locus of the protrusion 541 b and the arc-shaped hole 554, if the formation angle is 0 degree (see FIGS. 37 to 39), the protrusion 541 b extends in the extending direction of the arc-shaped hole 554. As a result, the rocking angle of the projection 541 b is maximized. Therefore, the swing angle of the protrusion 541b in the reduced state (formation angle α2) can be smaller than the swing angle of the protrusion 541b in the intermediate state (formation angle α1) (formation angle α1 <formation angle α2 ).

  As described above, when the expansion / contraction state of the expansion / contraction effect device 540 is changed, the swing angle of the protrusion 541b is changed, and at that time, the inner peripheral surface of the arc-shaped hole 554 (first stopper surface 554b, second The stopper surface 554 c and the third stopper surface 554 d function as a stopper that regulates the swing angle of the expansion and contraction rendering device 540. Thus, the inner circumferential surface of the arc-shaped hole 554 can be used as a portion that regulates the swing angle of the protrusion 541b in each case where the expansion / contraction state of the expansion / contraction effect device 540 is different. Therefore, it is possible to reduce the space for arranging the stopper that regulates the swing angle of the protrusion 541b.

  In addition, the stopper that regulates the swing angle of the expansion / contraction effect device 540 is retracted from the front side of the third symbol display device 81 when the pivoting arm member 550 is disposed at the retracted position. Therefore, unlike the case where a fixed stopper is disposed on the front side of the third symbol display device 81, the stopper remains on the front surface of the third symbol display device 81 even when the pivoting arm member 550 is disposed at the retracted position. Can be prevented. Thereby, when the pivoting arm member 550 is disposed at the retracted position, another member can be disposed on the front surface of the third symbol display device 81, so that another movable member (for example, the slide operation unit 700). The overhanging space of the support member 720) can be secured.

  The arc-shaped hole 554 of the pivoting arm member 550 has a function as a stopper for restricting the swing angle of the stretching effect device 540 and a second drive of the stretching effect device 540 by swinging the pivoting arm member 550. And a function as a transmission device for transmitting the driving force of the device 560 and causing the expansion / contraction effect device 540 to perform the expansion / contraction operation. Thus, the functions can be consolidated and the number of parts can be reduced.

  The tilt operation unit 600 and the slide operation unit 700 will be described with reference to FIGS. 46 to 57. The tilt operation unit 600 is a unit that swings the effect member 620 (refer to FIG. 12) (see FIG. 12), and the slide operation unit 700 is a unit that slides the tilt operation unit 600 in the left-right direction. 46 is a front perspective view of the tilting operation unit 600 and the slide operation unit 700, and FIG. 47 is a rear perspective view of the tilting operation unit 600 and the slide operation unit 700. 46 and 47, a state in which the tilt operation unit 600 and the column member 720 (see FIG. 47) of the slide operation unit 700 are disposed at the retracted position is illustrated.

  FIG. 48 is a front exploded perspective view of the slide operation unit 700, and FIG. 49 is a rear exploded perspective view of the slide operation unit 700. In FIGS. 48 and 49, the tilting operation unit 600 is illustrated without being disassembled in order to facilitate understanding.

  The slide operation unit 700 has a base member 710 formed in a plate shape elongated in the left-right direction, and one end thereof fastened and fixed to the slide plate 711 of the base member 710, and is formed slidably in the left-right direction A post member 720, and a slide rail 730 at one end of which is fastened and fixed to the post member 720 and at which the other end to which the base member 610 of the tilting operation unit 600 is fastened and fixed is vertically expandable. A connection member 740 is formed slidably on the back rail 716 of the main body 710 and is pivotally supported by the pivoting protrusion 612 of the tilting operation unit 600, and generates a driving force for moving the support member 720 in the left-right direction. A driving device 750 and a back cover member 760 formed on the back side of the driving device 750 and fastened and fixed to the base member 710 are mainly included.

  The base member 710 is a member that forms the frame of the slide operation unit 700, and is formed slideably in the left-right direction and the slide plate 711 to which the support member 720 is fastened and fixed from the back side. A shaft support hole 712 recessed in the left lower part with a circular cross section and the fixed shaft portion 753a is pivotally supported, a long hole shape recessed in the right lower portion of the base member 710 in a rear view, a shaft support hole The slide shaft support hole 713 whose upper and lower positions coincide with each other 712 and in which the moving shaft portion 754a is slidably supported, and which is formed swingably in the vertical direction by a solenoid And the upper rolling member 742 of the connecting member 740 is rolled so as to project in a downward arc shape in cross section downward to the front side at the upper end portion of the base member 710. The front rail portion 715 mainly comprises a rear rail portion 716 through plate portion 741b is inserted in the recessed by the coupling member 740 from the rear arc-shaped cross section in a front rail portion 715, a.

  Since the lever member 714 restricts the slide movement of the support member 720 fixedly fixed to the slide plate 711 in the lateral direction, the driving force of the drive device 750 when maintaining the tilting operation unit 600 in the retracted position is not necessary. Can.

  Here, in the present embodiment, since the tilting operation unit 600 is moved along the formation direction (arc track) of the front rail portion 715 and the back rail portion 716, the left and right of the support members 720 connected to the tilting operation unit 600. A sliding movement in the direction can occur by the action of gravity loaded on the tilting movement unit 600. For example, when the tilting operation unit 600 is disposed at the retracted position (see FIG. 46), the moving direction of the tilting operation unit 600 is directed obliquely downward along the shape of the front rail portion 715. Therefore, even if the moving direction of the column member 720 connected to the tilting operation unit 600 is the left and right direction along the moving direction of the slide plate 711, the column member 720 may be moved by gravity. In the present embodiment, the lever member 714 is pivoted downward and engaged with the locking portion 725 of the support member 720, and the movement of the support member 720 in the left and right direction is restricted. It is possible to maintain the support member 720 in the retracted position even if the support member 720 is unnecessary. Therefore, the durability of the drive device 750 can be improved.

  The support member 720 includes a main body portion 721 formed in a plate shape elongated in the vertical direction, and a slide plate 711 of the base member 710 continuously provided in the left and right direction at the lower end portion of the main body portion 721. The first fastening portion 722 through which the screw fastened and fixed is inserted, and the second fastening in which the slide rail 730 is fastened and secured by being continuously provided vertically in the front end left end portion of the main body portion 721 The slide hole 724 which is an elongated hole extending in a direction parallel to the connecting direction of the portion 723 and the second fastening portion 723 and is formed on the right side of the main body 721 in a front view; A lower lid portion in which a belt 755 of the driving device 750 is sandwiched between a hook-like locking portion 725 protruding upward from the lower end and engaged with the lever member 714 and the lower surface of the main body 721 726 and the main unit 7 A rolling portion 727 protruding from the lower surface side of the lower end portion 1 and formed so as to be capable of rolling on the inner peripheral surface of the slide concave portion 764 of the back surface cover member 760 And a coil spring 728 connected to the hook portion 617 of the base member 610 at its lower end.

  The slide rail 730 is fastened and fixed to the support member 720 in a posture in which the slide rail 730 can expand and contract in the connection direction of the second fastening portion 723.

  The slide hole 724 is an elongated hole extending in a direction parallel to the connecting direction of the second fastening portions 723 and is an elongated hole through which the auxiliary member 615 of the tilting operation unit 600 is inserted. Therefore, the slide hole 724 can suppress the positional deviation (the relative rotation of the tilting unit 600 with respect to the column member 720) of the tilting unit 600 moving up and down in the left-right direction.

  The lower lid portion 726 is formed with a tooth shape extending in the front-rear direction on the upper surface side. This tooth profile is shaped to mesh with the tooth profile formed on the inner circumferential surface of the belt 755 of the drive device 750. Thereby, the support member 720 can be prevented from slipping on the belt 755 of the drive device 750.

  The rolling portion 727 is inserted into the slide concave portion 764 of the back cover 760 so as to be able to roll, thereby suppressing frictional resistance and suppressing tilting in the front-rear direction around the lower end portion of the support member 720. be able to.

  The coil spring 728 is a biasing force for moving the tilting operation unit 600 upward. Since the biasing force from the coil spring 728 is always loaded on the tilting operation unit 600, the tilting operation unit 600 is suppressed from being dropped downward by gravity.

  The connecting member 740 has a triangular plate-like main body member 741 rotatably supported by the pivotal support projection 612 of the tilting operation unit 600, and a base supported by a rolling shaft 741c projecting from the main body member 741. A pair of cylindrical upper rolling members 742 rolled on the upper surface of the front rail portion 715 of the member 710 and a rolling shaft 741 c of the main body member 741 are fastened and fixed from the front side to cover the front side of the front rail portion 715 And the lower half portion of the front cover member 743 disposed in a manner and the lower half portion thereof is externally fitted and held by the front cover member 743 and the upper half portion is the lower surface of the front rail portion 715 And a cylindrical lower rolling member 744 to be moved.

  The main body member 741 is a member formed in a triangular plate shape, and is a circular recess recessed from the rear surface at the upper end portion, and a shaft rotatably supported by the pivoting protrusion 612 of the tilting operation unit 600 A support portion 741a, a plate-like member protruding toward the front side at the lower end portion, and a through plate portion 741b slidably inserted in the back rail portion 716 of the base member 710, and a through plate portion from the shaft support portion 741a It mainly includes a pair of rolling shafts 741c protruding in a cylindrical shape toward the front side from a position symmetrical with respect to a perpendicular drawn to 741b and rotatably supported by the upper rolling member 742 rotatably.

  The insertion plate portion 741 b is inserted into the rear rail portion 716 of the base member 710, so that 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 portion 741 a is also formed to be movable along the back rail portion 716.

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

  The upper rolling member 742 is rotatably supported by the shaft support portion 741 a and abuts on 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. As a result, it is possible to reduce the frictional resistance generated when the connecting member 740 slides, and to suppress the driving force required for the sliding movement.

  The lower rolling member 744 has a lower half rotatably fitted to a lower portion of the front cover member 743, and an upper end abuts on a lower surface of the front rail portion 715. That is, when the connecting member 740 is slid along the front rail portion 715, the lower rolling portion 744 rolls on the lower surface of the front rail portion 715. Thus, it is possible to reduce the frictional resistance generated between the connection member 740 and the front rail portion 715 during the slide movement, and to suppress the driving force required for the slide movement.

  As described above, in the present 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. Thus, the upper and lower surfaces of the front rail portion 715 can be held by the upper rolling member 742 and the lower rolling member 744 of the connecting member 740 while suppressing the frictional resistance.

  Here, since the center of gravity of the tilting operation unit 600 is formed upward as described later, there is a risk of tilting in the front-rear direction. In this case, since the connecting member 740 sandwiches the upper and lower surfaces of the front rail portion 715 by the upper rolling member 742 and the lower rolling member 744, the tilt operation unit 600 is inclined in both forward and backward directions. , Can generate resistance. As a result, the attitude of the tilting operation unit 600 can be easily maintained.

  The front cover member 743 pivotally supports the upper rolling member 742 in a non-extractable manner by being pivotally supported from the front side of the rolling shaft 741 c of the connection member 740.

  The driving device 750 is fixed to the base member 710 and generates a driving force for sliding the column member 720, a driving gear 752 pivotally supported by the driving motor 751, and the driving gear 752 A shaft fixed gear 753 engaged with and meshed with the belt 755, and a shaft moving gear 754 disposed so as to be separated from the shaft fixed gear 753 and wound with the belt 755 and capable of sliding movement of the rotation shaft 754a. A belt 755 wound around the shaft fixed gear 753 and the shaft moving gear 754 and moved by rotation of the shaft fixed gear 753, and a coil generating an urging force moving the shaft moving gear 754 in a direction away from the shaft fixed gear 753. The spring 756 is mainly provided.

  The shaft fixed gear 753 is a cylindrical member as a rotation shaft, and includes a fixed shaft portion 753a inserted into the shaft support hole 712 of the base member 710. The shaft moving gear 754 is a cylindrical member as a rotating shaft, and includes a moving shaft portion 754 a which is inserted into the slide shaft support hole 713 of the base member 710.

  The shaft fixed gear 753 and the shaft moving gear 754 are formed as gears of the same shape. The inner circumferential surface of the belt 755 is formed with a tooth profile that meshes with the gear teeth of the shaft fixed gear 753 and the shaft moving gear 754. Thus, slippage between the belt 755 and the shaft fixed gear 753 and the shaft moving gear 754 can be suppressed, and the amount of rotation of the shaft fixed gear 753 can be reliably transmitted to the belt 755.

  One end of coil spring 756 is fixed to a hook-like portion formed on slide shaft support hole 713n of base member 710 on the right in a rear view, and the other end is fixed to a case covering axial movement gear 754 . As a result, an urging force can be generated to move the shaft moving gear 754 to the opposite side of the shaft support hole 712, and an appropriate tension can be applied to the belt 755. It is possible to prevent the gear 754 from falling off.

  The back cover member 760 is a member that covers the drive device 750 on the back surface of the base member 710, and has a main body 761 formed in a box shape whose front side is opened and a fixed shaft 753a on the bottom of the main body 761. A recessed portion 762 which is a recess for receiving, a movable recessed portion 763 which is extended in the same shape as the slide shaft support hole 713 and is a recess for receiving the moving shaft portion 754a, and is extended in the lateral direction to receive the rolling portion 727 And a slide recess 764 which is a recess.

  The slide recess 764 is a recess in which the rolling portion 727 rolls on the upper and lower inner side surfaces. The frictional resistance of the sliding movement of the column member 720 is suppressed, and the tilting of the column member 720 in the front-rear direction is suppressed. That is, when the support member 720 is inclined in the front-rear direction, the rolling portion 727 is in contact with either the upper inner side surface or the lower inner side surface of the slide recess 764. Thereby, the inclination to the front-back direction of the support member 720 can be suppressed.

  Next, with reference to FIGS. 50 and 51, the tilting operation unit 600 will be described. FIG. 50 is a front exploded perspective view of the tilting operation unit 600, and FIG. 51 is a rear exploded perspective view of the tilting operation unit 600.

  The tilting operation unit 600 includes a plate-like base member 610 fastened and fixed to the other end of the slide rail 730, and a box-like effect member 620 whose lower end is pivotally supported by the base member 610. A first drive device 630 for generating a driving force for swinging the effect member 620, a transmission member 640 for transmitting the drive force of the first drive device 630 to the effect member 620, and abut against the transmission member 640 for transmission A torsion spring 650 for generating an urging force for moving the member 640 and a second drive device 660 for generating a driving force for opening and closing the first curtain member 624 and the second curtain member 625 of the effect member 620 are mainly provided. .

  The base member 610 has a main body portion 611 which is fixed to the slide rail 730 and is formed in a vertically long plate shape, and a shaft support portion of a connecting member 740 which protrudes in a cylindrical shape from the front side of the main body portion 611. A pivotally supporting projection 612 on which the shaft 741a is pivotally supported, and a circular hole bored in the front-rear direction vertically above the pivotally supporting projection 612, the pivotal shaft 626 of the effect member 620 is pivotally pivotally supported. A first shaft support hole 613 and a circular hole drilled in the front-rear direction vertically above the first shaft support hole 613, and the cylindrical portion 642 of the transmission member 640 is pivotally supported. An insertion hole through which the drive shaft of the first drive device 630 is inserted, the biaxial support hole 614, the auxiliary member 615 formed on the rear surface of the main body 611 and slidably inserted into the slide hole 724 of the support member 720 616 and the lower end of the main body 611 A hook-shaped hook portion 617 that extends toward the side, mainly comprising.

  The second axial support hole 614 includes a lower receiving plate portion 614a projecting in a circular arc shape in cross section from the lower edge to the front side. The rotation of the cylindrical portion 642 of the transmission member 640 is guided by the lower receiving plate portion 614a. The lower support plate portion 614a is formed to have a left-right width substantially equal to the outer diameter of the cylindrical portion 642 (see FIG. 53A).

  By inserting the auxiliary member 615 into the slide hole 724, the inclination of the base member 610 in the left-right direction can be suppressed, so that the base member 610 can be slid smoothly in the vertical direction.

  The flange portion 617 is a portion to which one end of the coil spring 728 is hung and a biasing force is loaded.

  The effect member 620 and the second drive device 660 will be described with reference to FIG. FIG. 52 is a front exploded perspective view of the effect member 620 and the second drive device 660. As shown in FIG. The liquid crystal device disposed inside the effect member 620 is illustrated by an imaginary line, and FIGS. 50 and 51 are appropriately referred to for the description of the effect member 620 and the second drive device 660.

  The effect member 620 is a box-like member in which the liquid crystal device is disposed, and the main body member 621 having a rectangular plate shape and the main body member 621 are extended forward from above and below to cover the main body member 621 Upper and lower cover members 622 which can be bent, and left and right cover members 623 which are plate-like members attached from both sides of the upper and lower cover members 622 and which form a rectangular box shape opened forward with the upper and lower cover members 622; The first curtain member 624 which is a member for opening and closing the opening and connected and moved to the fitting hole 665a of the second drive device 660, and the member which opens and closes the front opening together with the first curtain member 624. A second curtain member 625 moved by being pulled by the curtain member 624, and a cylindrical swing shaft portion 626 protruding from the lower portion of the back surface of the main body member 621; Mainly it includes center of gravity G (see FIG. 53) is formed above (higher position) than the pivot shaft portion 626. The center of gravity G is formed on a straight line passing through the slide shaft 621a and the swing shaft 626 (see FIG. 53) in the inverted state (see FIG. 53).

  The main body member 621 includes a columnar sliding shaft 621 a (see FIG. 51) which protrudes on the back side vertically above the swinging shaft 626. The sliding shaft portion 621a is slidably inserted into the sliding hole 643 of the transmission member 640 (see FIG. 51).

  The upper and lower cover members 622 are members that accommodate 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 opened by the driving force of the drive device 660. .

  The left and right cover member 623 is provided with a slide groove 623a formed in a groove shape on the inner side surface and in which the slide projection 625c of the second curtain member 625 can slide.

  The slide groove 623a is connected to a curved groove formed in an arc at upper and lower ends of a linear groove extending vertically. As a result, the second curtain member 625 slides in a manner such that linear movement and curvilinear movement sequentially occur along the shape of the slide groove 623a.

  The first curtain member 624 is a member pivoted up and down around the opening and closing shaft 664 of the second drive device 660, and a main body 624a having a shape in which a plate material is bent into a C-shaped cross section, and its main body A fitting portion 624b which protrudes in the left-right direction from an end portion of the 624a and is fitted to the fitting hole 665a of the second drive device 660 so as to be relatively non-rotatable, and one end portion is a main portion near the fitting portion 624b And 624 a pivotally pivotally supported at the other end of the second curtain member 625.

  The second curtain member 625 is a member which is pulled by the first curtain member 624 and moved in the vertical direction, and has a main body 625a formed in a plate shape having a C-shaped cross section and a C shaped cross-section of the main body 624a. A connection protrusion 625b which protrudes in the left and right direction from the end and is connected to the other end of the connection member 624c, and a slide groove of the left and right cover member 623 which protrudes outward in the left and right direction And a slide protrusion 625c that is inserted into the 623a.

  In the second drive device 660, a drive motor 661 fastened and fixed to the back side of the effect member 620, a drive gear 662 pivotally supported by the drive motor 661, and one gear engaged with the drive gear 662 An open / close shaft rotatably supported on the front side of the main body member 621 of the effect member 620 by a pair of transmission gears 663 rotated in opposite directions and a non-illustrated shaft support mechanism. A transmission member 665, which is fixed to both ends of the pair of opening and closing shafts 664 so as to be relatively non-rotatable, is mainly provided.

  The transmission member 665 includes a fitting hole 665a in which the fitting portion 624b of the first curtain member 624 is non-rotatably fitted. Thus, the first curtain member 624 is swung up and down with the open / close shaft 664 as an axis.

  Referring back to FIGS. 50 and 51, description will be made. The first drive device 630 includes a drive motor 631 in which a drive shaft is inserted into the insertion hole 616 of the base member 610 and fastened and fixed to the base member, and a worm gear 632 in a screw gear shape fixed to the drive shaft of the drive motor 631. , A worm wheel 633 in the form of a helical gear meshing with the worm 632.

  The worm 632 is formed by a double thread screw. In the present embodiment, since the number of teeth of the worm wheel 633 meshing with the worm 632 is approximately 20, the worm wheel 633 rotates once while the worm 632 rotates 10 times. Thereby, the rotation angle of the worm wheel 633 and the transmission member 640 can be significantly reduced when the drive motor 631 is operated at the minimum unit of control resolution.

  The worm wheel 633 has a locking projection 633 a protruding from the center of the rotation shaft and inserted into the second shaft support hole 614 of the base member 610 and locked relative to the cylindrical portion 643 of the transmission member 640 in a non-rotatable manner. Prepare. Transmission of driving force between the worm 632 and the worm wheel 633 is structurally limited to one direction from the worm 632 to the worm wheel 633 (when the worm wheel 633 is actively rotated, the force is the worm). It takes about 632). Thereby, when stopping the worm wheel 633, the load which the drive motor 631 receives can be reduced. Further, the worm wheel 633 and the transmission member 640 can be stopped in a state where the power of the drive motor 631 is cut off, and the power consumption of the drive motor 631 can be suppressed.

  The transmission member 640 and the torsion spring 650 will be described with reference to FIG. 53 (a) and 53 (b) are front views of the transmission member 640 and the torsion spring 650. FIG. In FIGS. 53 (a) and 53 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines, and for the explanation of the transmission member 640 and the torsion spring 650, refer to FIGS. Do. Further, FIG. 53 (a) shows 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 corresponds to that of the transmission member 640. Balanced in the swing direction. 53B, the transmission member 640 is pivoted by a predetermined amount in a counterclockwise direction in a front view from the upright state of FIG. 53A, and the effect member 620 is pivoted by a predetermined amount.

  The transmission member 640 is a member that is swung by the rotation of the worm wheel 633 (see FIG. 50), and has a main body portion 641 formed in the shape of a long rectangular bar, and one end of the main body portion 641 Of the cylindrical portion 642 extending in the direction to which the locking projection 633a of the first drive device 630 is engaged and a length extending in the axial diameter direction of the cylindrical portion 642 at the other end of the main body 641 A sliding hole 643 drilled as a hole, an abutting portion 644 spaced apart on both sides in the swing direction of the main body 641, and a connection between the abutting portion 644 and the front side of the main body 641 An arc-shaped front arc plate portion 645 having a width which is wide and an arc-shaped back arc plate portion 646 which connects the contact portion 644 and the rear side surface of the main portion 641 are mainly provided.

  As shown in FIG. 53, the contact portion 644, the front arc plate portion 645 and the back arc plate portion 646 are disposed in a manner to surround the biasing arm portion 652 of the torsion spring 650. This can prevent the torsion spring 650 from falling off (disengaging) from the transmission member 640.

  The cylindrical portion 642 is pivotally supported by the second axial support hole 614 (see FIG. 50) of the base member 610, and is locked relative to the locking projection 633a (see FIG. 50) of the first drive device 630 so as not to rotate relative thereto. Ru.

  The slide shaft portion 621 a of the effect member 620 is inserted through the slide hole 643. Thus, when the transmission member 640 is swung around the second shaft support hole 614 (see FIG. 50) by the driving force of the first drive device 630 (see FIG. 50), the sliding shaft 621a of the effect member 620. Is slid on the slide hole 643 (slidingly moved in the axial radial direction), the effect member 620 is swung about the first shaft support hole 613.

  By swinging the effect member 620 in this manner, it is possible to suppress the swing angle of the effect member 620 in the case where the drive motor 631 is rotated by the minimum unit of resolution of control of the drive device. For example, as a method of swinging the effect member 620, a method of directly connecting a gear to the swing shaft portion 626 of the effect member 620 and transmitting the driving force of the drive motor to the gear can be considered. However, in this case, the drive motor is shown at an angle P0 of the smallest unit of control resolution (see FIG. 53 (a), and the angle is illustrated several times larger than the actual angle P0 to facilitate understanding. The moving amount X1 by which the center of gravity of the effect member 620 is shifted in the left-right direction from the inverted state increases as the center of gravity of the effect member 620 moves away from the swing shaft portion 626. Therefore, as the center of gravity of the effect member 620 separates from the swinging shaft portion 626, it becomes more difficult to adjust the position of the center of gravity of the effect member 620, and the center of gravity of the effect member 620 is inverted. It becomes difficult to stop the effect member 620 in the state.

  On the other hand, in the present embodiment, the transmission member 640 for transmitting the driving force of the drive motor 631 to the effect member 620 is connected to the sliding shaft 621 a of the effect member 620. The length from the slide shaft portion 621a to the cylindrical portion 642 which is the swing shaft of the transmission member 640 is the length from the slide shaft portion 621a to the swing shaft portion 626 which is the swing shaft of the effect member 620. It is formed short compared to.

  Therefore, even when the effect member 620 is long in the radial direction of the rocking shaft portion 626, the angle P0 of the minimum unit of resolution of control of the drive device (see FIG. 53 (a), to facilitate understanding) In order to do this, it is possible to suppress the movement amount X2 of the center of gravity of the effect member 620 when operating the drive device at an angle several times larger than the actual angle P0. Therefore, it is possible to make it easy to stop the movable member in an inverted state in which the center of gravity of the movable member is disposed directly above the first axis.

  Further, as a method of swinging the effect member 620, gear teeth are formed on the arc centered on the swing shaft portion 626 in the effect member 620, and the gear meshed with the gear teeth is rotated by the drive motor. A method of swinging the effect member 620 can be considered. However, in this case, as the swing range of the effect member 620 increases, the range in which the gear teeth on the arc are formed needs to be larger in the left-right direction of the effect member 620. Therefore, in the case where the effect member 620 is formed in a thin shape in the swing direction, the gear teeth on the arc protrude from the effect member 620, which hinders the effect. Therefore, the design freedom of the effect member 620 is reduced.

  On the other hand, in the present embodiment, the transmission member 640 for transmitting the driving force of the drive motor 631 to the effect member 620 has a swing shaft portion 626 where the cylindrical portion 642 which is a swing shaft is a swing shaft of the effect member 620. And the swing shaft portion 621 a at the center in the left-right direction of the effect member 620. Since the effect member 620 swings following the transfer member 640, the formation range of the transfer member 640 with respect to the swing range of the effect member 620 can be suppressed near the center in the left-right direction of the effect member 620. As a result, even if the effect member 620 is thin in the left-right direction, the transfer member 640 can be prevented from protruding from the effect member 620, and the design freedom of the effect member 620 can be improved.

  The lower surface of the slide shaft portion 621 a of the effect member 620 is in contact with the inner circumferential surface of the slide hole 643 of the transmission member 640. As a result, the weight of the effect member 620 is loaded not only to the swinging shaft portion 626 but also to the transfer member 640. That is, a force opposing the weight of the effect member 620 can be generated not only from the swinging shaft portion 626 but also from the cylindrical portion 642 of the transmission member 640. Therefore, the effect member 640 can be supported at two points of the rocking shaft portion 626 and the cylindrical portion 642, and the radial force applied to the rocking shaft portion 626 and the cylindrical portion 642 can be suppressed. .

  Here, since the effect member 620 is in the normal state in the inverted state shown in FIG. 53A, it can be quickly returned to the inverted state after the transmission member 640 is rocked and rocked from the inverted state by a predetermined amount. Is desirable.

  In the present embodiment, as shown in FIG. 53 (b), when the transmission member 640 is swung from the state shown in FIG. Is rocked at a rocking angle φ2 (φ2 <φ1).

  That is, the swing angle of the effect member 620 is smaller than the swing angle of the transmission member 640 which is swung by the driving force of the first drive device 630 (see FIG. 50). Therefore, the effect member 620 can be easily returned to the inverted state (see FIG. 53A).

  Further, in the present embodiment, the sliding hole 643 having a long hole shape is formed in the axial diameter direction of the transmission member 640, and the sliding shaft portion 621a of the effect member 620 is inserted into the sliding hole 643. The transmission axis of the transmission member 640 is different from that of the effect member 620, and the sliding radius of the transmission hole 640 of the transmission member 640 is shorter than that of the slide shaft portion 621a of the effect member 620. The sliding shaft portion 621 a moves further away from the rocking shaft of the transmission member 640 as Therefore, a state in which the arm length R1 from the sliding shaft 621a of the effect member 620 to the cylindrical portion 642 of the transmission member 640 in the inverted state (see FIG. 53A) is swung a predetermined amount from the inverted state ( As compared with the arm length R2 from the sliding shaft portion 621a of the effect member 620 to the cylindrical portion 642 of the transmission member 640 in FIG. 54 (b)).

  That is, the arm length of the transfer member 640 is shortened as it approaches the inverted state, and the swing length of the effect member 620 when the transfer member 640 is swung by a predetermined angle is constant in arm length of the transfer member 640. Compared to the case, it can be made smaller as it approaches an inverted state. Therefore, the operating speed of the effect member 620 is increased near the predetermined stop position without changing the rotational speed of the drive motor 631 while the operating speed of the effect member 620 is decreased near the inverted state, and the effect member 620 is inverted. It can be made easy to stand still in a state (It can be made easy to stop control the effect member 620 in a state where the center of gravity of the effect member 620 is disposed vertically above the first axial support hole 613).

  Referring to FIG. 55, swing of effect member 620 with respect to the swing angle of transfer member 640 by changing the arm length from sliding shaft portion 621a of effect member 620 to cylindrical portion 642 of transfer member 640. The change in angle will be described.

  FIG. 55 is a schematic view schematically showing the swing angle of the effect member 620 (see FIG. 53A) with respect to the swing angle of the transmission member 640 (see FIG. 53A). In FIG. 55, a cylindrical portion 642 whose rotation axis M1 corresponds to the swinging shaft portion 626 (see FIG. 53A) which is the rotation shaft of the effect member 620 and whose rotation axis M2 is the swinging shaft of the transmission member 640. This corresponds to (see FIG. 53 (a)). The straight lines a1 to a4 schematically represent the arrangement of the transmission member 640, and are straight lines drawn radially from the rotation axis M2, and the straight line a1 passes through the rotation axis M1 and the straight lines a2 to a4 are straight lines a1 and Are formed sequentially in increments of 15 degrees. That is, the angles formed by the straight lines a1 to a4 adjacent to each other are 15 degrees each.

  An arc drawn with a radius equal to the arm length R1 (see FIG. 53 (a)) around the rotation axis M2 is illustrated by an arc SR1, and an arm length R2 around the rotation axis M2 (see FIG. 54 (b)) An arc drawn with a radius equal to is illustrated by an arc SR2. The arc SR0 is an arc drawn around the rotation axis M1, and is an arc of a radius of a length obtained by adding the distance between the rotation axis M1 and the rotation axis M2 to the arm length R1.

  These arcs assume the locus of the connection position between the effect member 620 and the transfer member 640 (see FIG. 53A). In the present embodiment, a sliding shaft 621a (see FIG. 53A) as a connecting position is provided so as to protrude from the effect member 620, and the connecting position of the effect member 620 and the transfer member 640 moves along the arc SR0. . When the connecting position between the effect member 620 and the transfer member 640 moves along the arc SR1 or the arc SR2, a long elongated hole is formed in the axial diameter direction in the effect member 620, and from the transfer member 640 It is assumed that the shaft inserted into the long hole is provided in a protruding manner.

  Further, as shown in FIG. 55, an intersection point of the straight line a1 and the arc SR0 is illustrated by an intersection point P10, an intersection point of the straight line a1 and the arc SR1 is illustrated by an intersection point P11, and an intersection point of the straight line a1 and the arc SR2 is illustrated as an intersection point P12. It is illustrated by.

  Similarly, an intersection point of the straight line a2 and the arc SR0 is illustrated by an intersection point P20, an intersection point of the straight line a2 and the arc SR1 is illustrated by an intersection point P21, and an intersection point of the straight line a2 and the arc SR2 is illustrated by an intersection point P22. An intersection point of the straight line a3 and the arc SR0 is illustrated by an intersection point P30, an intersection point of the straight line a3 and the arc SR1 is illustrated by an intersection point P31, and an intersection point of the straight line a3 and the arc SR2 is illustrated by an intersection point P32. An intersection point of the straight line a4 and the arc SR0 is illustrated by an intersection point P40, an intersection point of the straight line a4 and the arc SR1 is illustrated by an intersection point P41, and an intersection point of the straight line a4 and the arc SR2 is illustrated by an intersection point P42. The intersection point P10 and the intersection point P11 are disposed at the same position, and the intersection point P40 and the intersection point P42 are disposed at the same position.

  Further, as shown in FIG. 55, an angle formed by a straight line passing through the rotation axis M1 and the intersection point P10 and a straight line passing through the rotation axis M1 and the intersection point P20 is illustrated by an angle A10, and a straight line passing through the rotation axis M1 and the intersection point P11 The angle formed by the rotation axis M1 and the straight line passing through the intersection point P21 is illustrated by an angle A11, and the angle formed by the straight line passing through the rotation axis M1 and the intersection point P12 and a straight line passing through the rotation axis M1 and the intersection point P22 is illustrated by an angle A12. Be done.

  Similarly, an angle formed by a straight line passing through the rotation axis M1 and the intersection point P20 and a straight line passing through the rotation axis M1 and the intersection point P30 is illustrated by an angle A20, and a straight line passing through the rotation axis M1 and the intersection point P21 and the rotation axis M1 and the intersection point P31. The angle formed by the straight line passing through is indicated by an angle A21, and the angle formed by the straight line passing through the rotation axis M1 and the intersection point P22 and the straight line passing through the rotation axis M1 and the intersection point P32 is illustrated by an angle A22. An angle formed by a straight line passing through the rotation axis M1 and the intersection point P30 and a straight line passing through the rotation axis M1 and the intersection point P40 is illustrated by an angle A30, and a straight line passing through the rotation axis M1 and the intersection point P31 and a straight line passing through the rotation axis M1 and the intersection point P41 The angle formed by A is illustrated by an angle A31, and the angle formed by a straight line passing through the rotation axis M1 and the intersection point P32 and a straight line passing through the rotation axis M1 and the intersection point P42 is illustrated by an angle A32. Note that these angles correspond to the swing angle of the effect member 620.

  Here, the ratio of (the distance between the rotation axis M1 and the rotation axis M2: arm length R1: arm length R2) is set to (1: 2.32: 2.54) in the present embodiment. When the angle is measured, the angle A32 is 11.07 degrees, the angle A31 is 10.77 degrees, and the angle A30 is 11.37 degrees. That is, in the case of swinging the transfer member 640 between the straight line a4 and the straight line a3, the swing angle of the effect member 640 is largest when the transfer member 640 and the effect member 620 are connected along the arc SR0. Thus, the transmission member 640 and the effect member 620 are formed along the arc SR2 to be connected (the angle A30 is closer to the angle A32 than the angle A31).

  The angle A22 is 10.87 degrees, the angle A21 is 10.59 degrees, and the angle A20 is 10.82 degrees. That is, in the case of swinging the transmission member 640 between the straight line a3 and the straight line a2, the swing angle in the case where the transmission member 640 and the effect member 620 are connected along the arc SR0 is along the arc SR2. It falls below the case where the transmission member 640 and the effect member 620 are connected. In this case, the difference between the angle A22 and the angle A20 is smaller than the difference between the angle A20 and the angle A21 (the angle A20 is closer to the angle A22 than the angle A21).

  The angle A12 is 10.78 degrees, the angle A11 is 10.50 degrees, and the angle A10 is 10.53 degrees. That is, in the case of swinging the transmission member 640 between the straight line a2 and the straight line a1, the swing angle when the transmission member 640 and the effect member 620 are connected along the arc SR0 is along the arc SR1. The case where the transmission member 640 and the effect member 620 are connected is exceeded. In this case, the difference between the angle A12 and the angle A10 is larger than the difference between the angle A10 and the angle A11 (the angle A10 is closer to the angle A11 than the angle A12).

  From these, by making the locus of the connection position of the transfer member 640 and the effect member 620 (see FIG. 53A) as the arc SR0, for example, when the transfer member 640 is swung at a constant speed, the effect member It can be seen that the freedom of adjustment of the angular velocity 620 can be improved. That is, when the transmission member 640 is disposed on the straight line a4, the locus of the connection position between the transmission member 640 and the rendering member 620 is closer to the angular velocity (high speed side) in the case of the arc SR2, and the transmission member 640 is The angular velocity at the time of arrangement can be made closer to the angular velocity (low speed side) in the case of the arc SR1 when the locus of the connection position between the transfer member 640 and the effect member 620 is circular.

  In addition, when the ratio of the respective angles is calculated, the angle A22 / the angle A32 is 0.98, and the angle A12 / the angle A22 is 0.99. The angle A21 / angle A31 is 0.98, and the angle A11 / angle A21 is 0.99. That is, when the locus of the connection position between the transfer member 640 and the effect member 620 (see FIG. 53A) is the arcs SR1 and SR2, the transfer member 640 is swung toward the inverted state at constant speed. The deceleration ratio of the angular velocity of the effect member 620 in the case is as small as 1 to 2%.

  On the other hand, the angle A20 / angle A30 is 0.95, and the angle A10 / angle A20 is 0.97. That is, when the locus of the connecting position of the transfer member 640 and the effect member 620 (see FIG. 53A) is the arc SR0 (the arc centered on the rotation axis M1), the transfer member 640 is inverted at a constant speed. The deceleration ratio of the angular velocity of the effect member 620 when it is swung toward the state can be set to 3 to 5%. That is, the deceleration ratio of the angular velocity of the effect member 620 can be increased as compared with the case where the locus of the connecting position is the arcs SR1 and SR2 (the arc centering on the rotation axis M2).

  As shown in FIG. 53A, the slide shaft portion 621a of the effect member 620 is in contact with the lower end portion of the slide hole 643 of the transmission member 640 in the inverted state. In the inverted state, the center of gravity G of the effect member 620 is formed vertically above the rocking shaft portion 626 of the effect member 620 and the cylindrical portion 642 of the transmission member 640. The portion 626 and the cylindrical portion 642 are vertically lowered. Therefore, the force of the component in the direction of swinging the effect member 620 is not generated due to the gravity of the effect member 620, so that the attitude of the effect member 620 is maintained in the inverted state even if the power of the first drive device 630 is shut off. Can. Thereby, durability improvement of the 1st drive device 630 can be aimed at.

  In addition, since the force due to the gravity G of the effect member 620 is applied vertically downward to the swing shaft portion 626 and the cylindrical portion 642, the rotational resistance of the swing shaft portion 626 and the cylindrical portion 642 can be increased. The attitude of the effect member 620 can be easily maintained in the inverted state.

  The torsion spring 650 is an elastic spring in which a biasing force is generated in a direction to rewind the coil portion 651 (direction to push back the transmission member 640) as the transmission member 640 swings. A coil portion 651 wound around the periphery, a biasing arm portion 652 extending along both swing direction side surfaces of the main body portion 641 of the transmission member 640, an end portion of the coil portion 651 and an end of the biasing arm portion 652 And a connecting arm 653 that connects the parts through between the cylindrical portion 642 and the swinging shaft portion 626.

  The coil portion 651 is formed to have an inner diameter that is about three times the diameter of the swinging shaft portion 626 of the effect member 620. Therefore, when the biasing arm portion 652 is swung to generate a load that causes the coil portion 651 to reduce its diameter, a deformation amount of the coil portion 651 can be secured, and the biasing arm portion 652 or the connecting arm portion 653 is deformed. Concentration can be suppressed.

  The biasing arm portion 652 is surrounded by the main body portion 641 of the transmission member 640, the contact portion 644, the front arc plate portion 645, and the back arc plate portion 646. Thus, the biasing arm 652 can be prevented from coming off (disengaging) from the transmission member 640.

  Further, the biasing arm portion 652 is formed to be able to abut on the lower receiving plate portion 614 a on the swinging plane of the transmission member 640. Therefore, a biasing force for pushing back the transmission member 640 is generated from the biasing arm portion 652 disposed in the pivoting direction of the transmission member 640, and the biasing arm portion disposed on the opposite side of the pivoting direction of the transmission member 640 The reference numeral 652 is prevented from moving to the lower support plate portion 614a. Thus, the torsion spring 650 is formed to be capable of generating a biasing force in the direction of pushing back the transmission member 640 regardless of the swing direction of the transmission member 640.

  A bending portion 653a is formed at the connecting portion of the biasing arm 652 and the connecting arm 653 to be bent to the opposite side of the transmission member 640. In this case, as the contact portion 644 of the transmission member 640 is pressed against the bending portion 653a of the torsion spring 650 as described later, the bending portion 653a is expanded (see FIG. 54 (b)). As a result, the contact position between the biasing arm 652 of the torsion spring 650 and the main body 641 of the transmission member 640 is far from the cylindrical portion 642 and the moment applied from the torsion spring 650 to the transmission member 640 is increased. Can.

  With reference to FIG. 54, a change in biasing force generated from the torsion spring 650 and pushing back the transmission member 640 will be described. 54 (a) and 54 (b) are front views of the transmission member 640 and the torsion spring 650. FIG. In FIGS. 54 (a) and 54 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines, and FIG. 53 is appropriately used to explain the change of the biasing force generated from the torsion spring 650. refer.

  Further, in FIG. 54 (a), from the state of FIG. 53 (b), the transmission member 640 is further rotated counterclockwise in front view, and the biasing arm 652 on the left in front view is the contact portion 644 of the transmission member 640. The state where it begins to be pressed against the inner surface is illustrated, and in FIG. 54 (b), the transmission member 640 is further rotated counterclockwise in a front view from the state of FIG. 54 (a), and the bending portion 653a of the torsion spring 650 is pulled. The extended state is illustrated.

  In the state shown in FIG. 54 (a), a biasing force that pushes the transmission member 640 back is generated on the biasing arm 652 on the left side of the torsion spring 650 in a front view. The biasing force is the sum of the biasing force generated starting from the coil portion 651 and the biasing force generated starting from the bending portion 653a.

  That is, in the state of FIG. 53 (b), since the transmission member 640 is not pressed against the bending portion 653a disposed on the left in front view among the pair of bending portions 653a, the biasing arm on the left side of the torsion spring 650 in front view In the portion 652, only a biasing force originating from the coil portion 651 is generated as a biasing force for pushing back the transmission member 640.

  On the other hand, in the state of FIG. 54 (a), in addition to the biasing force starting from the coil portion 651, the biasing force is generated by the deformation of the biasing arm portion 652 starting from the bending portion 653a. Therefore, the spring constant of the biasing arm 652 can be increased. The deformation of the biasing arm 652 starting from the bending portion 653 a is shorter in length than the deformation starting from the coil 651, so the unit deformation amount of the transmission member 640 It is possible to make the biasing force generated at the hit greater.

  In the state of FIG. 54B, the bending portion 653a of the torsion spring 650 is pushed by the contact portion 644 of the transmission member 640, whereby the angle formed by the biasing arm 652 and the connecting arm 653 is widened. Thus, in the state of FIG. 54 (a), the contact position length L1, which is the distance between the contact position of the main body 641 of the transmission member 640 and the biasing arm 652 of the torsion spring 650 and the cylindrical portion 642. 54B, the same contact position length L2 in the state of FIG. 54 (b) is separated from the cylindrical portion 642 of the transmission member 640. That is, the contact position length is extended. As a result, since the arm length of the torsion spring 650 for pushing back the transmission member 640 is increased, the moment applied from the torsion spring 650 to the transmission member 640 can be increased.

  Therefore, for example, when the biasing force generated by the torsion spring 650 is substantially equal between the state of FIG. 54 (a) and the state of FIG. 54 (b), more load is applied to the transmission member 640 in FIG. 54 (b). Can be increased. Therefore, the transmission member 640 and the effect member 620 can be more easily pushed back.

  As shown in FIG. 53 and FIG. 54, the biasing force of the torsion spring 650 for pushing back the transmission member 640 is small within a small swing angle from the retracted position of the transfer member 640 (effect member 620), and the swing angle is large. The degree is increased elastically, and is increased more than the amount of elastic increase bordering on the state of FIG. 54 (a). Therefore, when the biasing force of the torsion spring 650 necessary when the effect member 620 is set to the maximum swing angle (see FIG. 54B) is determined, the torsion spring performs only an elastic increase. In the case where the swing angle is small, the biasing force can be set smaller (the soft spring can be used).

  Thereby, it is possible to reduce the degree to which the operation speed at the start of swinging of the effect member 620 is decelerated by the biasing force of the torsion spring 650, and the operation speed at the start of operation of the effect member 620 can be increased. .

  Further, since the biasing force is increased by an elastic increase or more at the boundary of the state of FIG. 54 (a), the swing angle of the effect member 620 is set to the state of FIG. 54 (a) or more, The decelerating acceleration of the effect member 620 can be increased. Thereby, between the swinging operations of the effect member 620, the timing at which the effect member 620 starts to be decelerated can be delayed. Therefore, the swing angle at which the effect member 620 can be swung at high speed can be enlarged, and the effect of the tilting operation unit 600 can be improved.

  Next, with reference to FIG. 56, the sliding operation of the tilting operation unit 600 and the sliding operation unit 700 will be described. FIG. 56 is a front view of the tilting operation unit 600 and the sliding operation unit 700. In FIG. 56, a state in which the tilting operation unit 600 is disposed at the retracted position is illustrated by an imaginary line, and a state in which the tilting operation unit 600 is slid by a predetermined amount from the retracted position is illustrated by a solid line.

  As shown in FIG. 56, a connecting member 740 for connecting the tilt operation unit 600 slidably formed in the vertical direction and the slide operation unit 700 is formed so as to be movable in the extending direction of the front rail portion 715. . Here, since the weight of the tilting operation unit 600 is loaded on the connecting member 740, when the tilting operation unit 600 is disposed at the retracted position, the tilting operation unit 600 is gravity-followed along the front rail portion 715 by gravity. It is biased toward you. Therefore, in order to maintain the tilting operation unit 600 in the retracted position, it is conceivable to fix the drive device 750.

  On the other hand, in the present embodiment, the lever member 714 is formed so as to be vertically swingable, and when the lever member 714 is swung downward, the lever member 714 engages with the locking portion 725 of the support member 720. The sliding movement in the direction is restricted.

  As a result, since the tilting operation unit 600 can be mechanically maintained at the retracted position, the tilting operation unit 600 is stopped in a state where the drive device 750 is stopped when the tilting operation unit 600 is disposed at the retracted position. It can be maintained at the retracted position. Therefore, the durability of the drive device 750 can be improved.

  In the state where the tilting operation unit 600 is disposed at the retracted position, the support member 720 can be moved by swinging the lever member 714 upward and operating the driving device 750, and the tilting operation unit 600 can be moved in the left-right direction. You can slide it.

  As shown in FIG. 56, when the tilting operation unit 600 is disposed at the retracted position in the inverted state, the pivot portion 741a of the connecting member 740 is disposed vertically below the center of gravity G of the tilting operation unit 600.

  Here, since the direction of sliding movement of the tilting operation unit 600 is along the front rail portion 715, in FIG. 56, movement of the tilting operation unit 600 is performed while being slid by a predetermined amount from the retracted position (see phantom line in FIG. 56). Has a vertical component at all times.

  Therefore, if the center of gravity G of the tilting operation unit 600 and the shaft support portion 741a of the connecting member 740 deviate in the vertical direction, a load may be applied from the connecting member 740 in the direction to rotate the tilting operation unit 600. The same applies to the case where the tilting operation unit 600 is slid in the reverse direction.

  On the other hand, in the present embodiment, since the pivot portion 741a of the connection member 740 is disposed vertically below the center of gravity G, the vertical component of the force applied to the tilting operation unit 600 from the connection member 740 and the center of gravity G are It is formed on the same line. As a result, the application of a load from the connecting member 740 in the direction to rotate the tilting operation unit 600 can be suppressed, and the posture of the tilting operation unit 600 can be stabilized.

  Next, referring to FIG. 57, the influence of the tilting operation (swinging operation) of the tilting operation unit 600 on the slide operation of the slide operation unit 700 will be described. FIG. 57 is a front view of the tilting operation unit 600 and the slide operation unit 700. FIG. In FIG. 57, a state in which the effect member 620 of the tilting operation unit 600 is swung to the state of FIG. 54 (b) is illustrated.

  As shown in FIG. 57, when the effect member 620 is swung in a counterclockwise direction as viewed from the front, the center of gravity G of the effect member 620 is disposed to the left of the connecting member 740 in a front view. Therefore, the acceleration in the front view leftward applied to the connecting member 740 is increased.

  In this case, the driving force necessary to slide the tilting operation unit 600 from the retracted position can be suppressed, so the drive motor 751 of the driving device 750 can be miniaturized.

  Next, with reference to FIGS. 58 and 59, the tilting operation unit 2600 in the second embodiment will be described.

  In the first embodiment, the case where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 is flat has been described. However, the tilting operation unit 2600 in the second embodiment includes the main body of the transmission member 2640. Reference numeral 2641 includes an abutting portion 2641 a that is in contact with the tip of the biasing arm 652 of the torsion spring 650. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  58 (a), 58 (b) and 59 are front views of the transmission member 2640 and the torsion spring 650 in the second embodiment. In FIGS. 58 (a), 58 (b) and 59, the outlines of the base member 610 and the effect member 620 are shown by imaginary lines. Further, FIG. 58 (a) shows an inverted state in which the slide hole 643 of the transmission member 2640 is disposed vertically above the cylindrical portion 642, and FIG. 58 (b) shows the inverted state of FIG. 58 (a). The transmission member 2640 is swayed by a predetermined amount counterclockwise in a front view from the front, and the state in which the lower surface of the abutment portion 2641a is in contact with the tip of the biasing arm 652 of the torsion spring 650 is shown in FIG. A state in which the transmission member 2640 is further pivoted counterclockwise in a front view from the state of FIG. 58 (b) is illustrated.

  As shown in FIG. 58, when the transmission member 2640 is swung from the upside-down state (see FIG. 58A), the main body 2641 is pressed against the biasing arm 652 of the torsion spring 650, and the main body 2641 is The torsion spring 650 generates a biasing force that causes it to swing in the direction to return to the inverted state. When the transmission member 2640 is swung and the biasing arm 652 is deformed, the coil portion 651 is reduced in diameter by the connecting arm 653 connected to the biasing arm 652 on the deformed side. That is, as the diameter of the coil portion 651 is reduced, the urging force for swinging the transmission member 2640 in the direction of returning to the inverted state is increased.

  Further, as shown in FIG. 58, the contact position between the main body portion 2641 of the transmission member 2640 and the biasing arm portion 652 (the difference between the swing angles of the biasing arm portion 652 of the torsion spring 650 and the transmission member 2640) The tip end position of the biasing arm 652 is changed by the swing of the transmission member 2640. That is, as the transmission member 2640 is swung, the tip end portion of the biasing arm portion 652 is moved to the tip end side of the main body portion 2641 (the side approaching the sliding hole 643).

  Therefore, as shown in FIG. 58B, when the transmission member 2640 is further rotated counterclockwise in a front view in a state where the lower surface of the abutment portion 2641a is in contact with the tip end portion of the biasing arm portion 642. The biasing arm portion 642 is restricted by the abutment portion 2641 a from moving to the tip end side of the main body portion 2641.

  As shown in FIG. 59, when the transfer member 2640 is swung in a state in which the transfer arm portion 642 is restricted in movement by the abutment portion 2641a, the torsion spring 650 is deformed as a whole. That is, since the movement of the biasing arm 642 to the tip end side of the main body 2641 is restricted, the base side (the bending portion 653a side) of the biasing arm 642 is moved downward. Thus, the connecting arm 653 is moved in the direction of reducing the diameter of the coil portion 651 (the direction in which the biasing force of the torsion spring 650 is increased).

  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 as compared to the case where the abutting portion 2641a is not provided. Thereby, the degree of change in the urging force generated by the torsion spring 650 (the increase ratio of the urging force to the swing angle of the transmission member 2640) is increased in the state shown in FIG. 59 as compared to the state shown in FIG. Can. Therefore, when the swing angle of the transmission member 2640 is small, the biasing force of the torsion spring 650 is suppressed to increase the start speed of the transfer member 2640, and when the swing angle is large (see FIG. 59), It is possible to increase the biasing force of the torsion spring 650 nonlinearly (more than elastic change) and to obtain a biasing force sufficient to return the transmission member 2640 to the inverted state.

  Next, with reference to FIG. 60, a tilting operation unit 3600 in the third embodiment will be described.

  In the first embodiment, the case where the contact surface of the main body 641 of the transmission member 640 with the torsion spring 650 has a constant width has been described, but the tilting operation unit 3600 in the third embodiment is the main body of the transmission member 3640 3641 includes an inclined side surface 3641a which is inclined in such a manner as to be wider toward the distal end side on the side surface that is in contact with the distal end portion of the torsion spring 650. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  60 (a) and 60 (b) are front views of the transmission member 3640 and the torsion spring 650 in the third embodiment. In FIGS. 60 (a) and 60 (b), the outlines of the base member 610 and the effect member 620 are shown by imaginary lines. 60 (a) shows an inverted state in which the slide hole 643 of the transmission member 3640 is disposed vertically above the cylindrical portion 642, and FIG. 60 (b) shows the inverted state shown in FIG. 60 (a). The state in which the transmission member 3640 is swung a predetermined amount counterclockwise in a front view is illustrated.

  As shown in FIG. 60, when the transmission member 3640 is swung from the inverted state (see FIG. 60A), the main body portion 3641 is pressed against the biasing arm portion 652 of the torsion spring 650, and the main body portion 3641 is The torsion spring 650 generates a biasing force that causes it to swing in the direction to return to the inverted state.

  When the transmission member 3640 is swung from the state shown in FIG. 60 (a) to the state shown in FIG. 60 (b), 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 distal end portion of the biasing arm portion 652 is closer to the distal end side of the main body portion 3641 (the side closer to the sliding hole 643) as the swing angle from the upside-down state (see FIG. 60A) of the transmission member 3640 increases. Moved to).

  Therefore, the tip end of the biasing arm 652 slides along the inclined side surface 3641 a of the main body 3641. That is, in the torsion spring 650, when the transmission member 3640 is swung, in addition to the deformation caused by the swing angle of the transmission member 3640, the deformation due to the width of the transmission member 3640 being expanded by the inclined side surface 3641a occurs. . In this case, the width of the transfer member 3640 is further expanded toward the tip end portion of the transfer member 3640. Therefore, the larger the swing angle from the inverted state of the transfer member 3640 (see FIG. 60A) As a result, the deformation of the torsion spring 650 due to the width of the transmission member 3640 is enlarged. Therefore, as the swing angle of the transmission member 3640 increases, it is possible to increase the rate of increase in the biasing force generated by the torsion spring 650 (change in the biasing force of the torsion spring 650 with respect to the swing angle of the transfer member 3640).

  Next, with reference to FIG. 61 to FIG. 64, the tilting operation unit 4600 in the fourth embodiment will be described.

  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 operation unit 4600 in the fourth embodiment, the transmission member 4640 is in addition to the contact portion 644 and the contact thereof A moving abutment member 4647 shorter in width than the portion 644 is provided. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  61 (a) is a rear perspective view of the transmission member 4640 in the fourth embodiment, and FIG. 61 (b) is a rear perspective view of the movable contact member 4647. In FIG. 61A, the movable contact member 4647 is not shown.

  As shown in FIG. 61 (a), the front arc plate portion 4645 of the transmission member 4640 is provided with a guide hole 4645a disposed symmetrically in the left-right direction at intervals shorter than the disposition interval of the contact portions 644. Prepare. The guide hole 4645a is a through hole which guides the pair of rear projection portions 4647b of the movable contact member 4647 so as to be movable in the front-rear direction.

  As shown in FIG. 61 (b), the movable contact member 4647 has a main body 4647a formed in a long plate shape, and a pair of rear projections protruding from both end portions of the main body 4647a to the rear side. It mainly includes a portion 4647 b and a front projection 4647 c which is provided so as to project from the approximate center of the main portion 4647 to the front side in a tip hemispherical shape.

  One end of the coil spring 4648 is fixed to the opposite side of the front projection 4647c of the main body 4647a, and the other end of the coil spring 4648 is fixed to the main body 641b (FIG. 62 (c) and See FIG. 62 (d)). Also, in order to facilitate understanding, the illustration of the coil spring 4648 is omitted in FIGS. 61 (a), 61 (b), 62 (a) and 62 (b).

  The rear projection 4647 b is a portion inserted from the front side into the guide hole 4645 a of the transmission member 4640 and has a sufficient length from the front arc plate 4645 (when in contact with the biasing arm 652 of the torsion spring 650). The possible lengths are formed in such a way that they are pushed out. The back projection 4647 b is formed so as to be inclined at an angle (see FIG. 64 (b)) in contact with the biasing arm 652 of the torsion spring 650 at the surface (line). As a result, the load applied to the biasing arm 652 is reduced (stress concentration is suppressed) as compared with the case where the biasing arm 652 and the rear projection 4647 b are abutted at points. Durability can be improved.

  The front projection 4647c is a portion that is in contact with the main body member 4621 (see FIG. 63) of the effect member 4620, and from the relationship with the relief opening 4621a formed in the main body member 4621 The moving abutment member 4647 may be separated from the front arc plate portion 4645 (see FIG. 62C) or may be moved closer to the front arc plate portion 4645 (see FIG. 62D). In addition, since the tip of the front projection 4647c is formed in a hemispherical shape, the front projection 4647c can be easily run on the surface of the main body member 4621 from the escape opening 4621a.

  62 (a) and 62 (b) are rear perspective views of the transmission member 4640, and FIGS. 62 (c) and 62 (d) are top views of the transmission member 4640. In FIGS. 62 (a) and 62 (c), the movable contact member 4647 is separated from the front arc plate portion 4645 in FIGS. 62 (b) and 62 (d). The state in which 4647 approached front arc board part 4645 is illustrated respectively.

  FIG. 63 is a schematic front view schematically showing the main body member 4621 of the effect member 4620. Note that the transmission member 4640 forming an inverted state with respect to the main body member 4621 is the central state 4640C, and the transmission member 4640 is swayed counterclockwise as viewed from the front view as the counterclockwise rocking state 4640L. A state in which it is swung clockwise as viewed from the front is illustrated by an imaginary line as a clock swing state 4640R. In addition, in central state 4640C, counterclockwise rocking state 4640L and clock rocking state 4640R, illustration of contact portion 644, front arc plate 4645 and back arc plate 646 is omitted to facilitate understanding. .

  The main body member 4621 is provided with a relief opening 4621 a drilled in the front-rear direction. As shown in FIG. 63, the relief opening 4621a is a region (center state 4640C and counterclockwise) in which the front projection 4647c (see FIG. 62) moves when the transmission member 4640 is swung counterclockwise in a front view. Between the motion state 4640L and the motion state 4640L).

  When the front projection 4647c of the transmission member 4640 overlaps 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 transmitted by the elastic force of the coil spring 4648. The main body 641 is separated from the main body 641 (see FIG. 62 (c)). On the other hand, when the front projection 4647c does not overlap with the relief opening 4621a (overlaps with the main body member 4621), the front projection 4647c abuts on the back side of the main body 4621 of the effect member 4620, and the moving abutment member 4647 is brought close to the main body 641 of the transmission member 4640 (see FIG. 62D).

  That is, the rear projection 4647 b of the movable contact member 4647 is projected to a position where it can be in contact with the biasing arm 652 of the torsion spring 650 when the transmission member 4640 is swung clockwise as viewed from the upside. Be Therefore, the biasing arm portion 652 of the torsion spring 650 is generated when the transmission member 4640 is swung clockwise as viewed from the upside, as compared to when it is swung counterclockwise as viewed from the front. It is possible to increase the rate of increase of the urging force (the degree of increase of the urging force with respect to the swing angle).

  FIGS. 64 (a) and 64 (b) are front views of the transmission member 4640 and the torsion spring 650. FIG. In FIGS. 64 (a) and 64 (b), the outlines of the base member 610 and the effect member 4620 are shown by imaginary lines, and the main body 4647a of the movable contact member 4647 for easy understanding. Illustration is omitted. Further, FIG. 64 (a) shows an inverted state in which the slide hole 643 of the transmission member 4640 is disposed vertically above the cylindrical portion 642, and FIG. 64 (b) shows the inverted state of FIG. 64 (a). From the above, it is illustrated that the transmission member 4640 is swung clockwise by a predetermined amount in a front view, and the biasing arm 652 on the left in a front view is abutted against the rear projection 4647 b.

  As shown in FIG. 64 (b), while the swing angle of the transmission member 4640 is small, the biasing arm 652 can be contacted from the opposite side (abutment portion 644 side) of the main body 641 of the transmission member 4640. By doing this, it is possible to increase the biasing force generated by the torsion spring 650 when the transmission member 4640 is rotated clockwise in a front view.

  Thus, it is possible to improve the biasing force when the transmission member 4640 is swung clockwise as viewed from the front while the start speed when the transmission member 4640 is swung counterclockwise in front view is increased. Can. Therefore, collision of the effect member 4620 with the inner side surface of the rear case 210 can be suppressed.

  That is, in the state where the tilting operation unit 4600 is disposed at the retracted position, when the effect member 4620 is in the inverted state, the inner side surface of the back case 210 approaches the effect member 620 (see FIG. 5). Here, if the effect member 4620 is vigorously swung toward the upside-down state from the state of swinging counterclockwise in a front view (see FIG. 57), the effect member 4620 can not be decelerated, and the rear case 210 There is a risk that the effect member 4620 may collide with the inner surface of the lens.

  On the other hand, in the present embodiment, the rear projection 4647b is protruded at the timing when the effect member 4620 is swung clockwise in a front view from the upside state (see FIG. 62D). It can be increased. Thus, the directing member 4620 is sufficiently inclined in the clockwise direction when viewed from the upside state while maintaining the operation speed when the directing member 4620 is tilted in the counterclockwise direction when viewed from the upside position. Can be slowed down.

  In addition, the direction in which the rear projection 4647b is pushed back at the contact point between the rear projection 4647b arranged on the opposite side of the swing direction of the transmission member 4640 and the biasing arm 652 (FIG. 64 (b) Bias is generated. Thus, the transmitting member 4640 is pushed with a larger urging force than in the case where the transmitting member 4640 is pushed back only by the urging arm portion 652 disposed on the side approaching the transmission member 4640 (right side in FIG. 64B). You can push it back. On the other hand, it is possible to improve the biasing force generated by the biasing arm portion 652 disposed on the side closer to the transmission member 4640.

  That is, as shown in FIG. 64, the distance from the position at which the abutting portion 644 and the biasing arm portion 652 which are disposed on the opposite side to the side approaching the transmission member 4640 abuts on the lower receiving plate portion 614a. The distance from the lower support plate portion 614a to the bending portion 653a is shorter than the distance. In this case, it is easy to move the bending portion 653a by the force from the contact portion 644 with the lower receiving plate portion 614 as a fulcrum, but the opposite is difficult (the distance from the fulcrum to the action point is different Because there is).

  Therefore, the biasing force generated by the deformation of the biasing arm portion 652 in the front view left side generated by the abutment of the abutting portion 644 and the biasing arm portion 652 is generated by the deformation of the entire torsion spring 650. That is, when the biasing arm 652 on the left in the front view and the rear projection 4647b abut on each other, the bending portion 653a on the left in the front view with the lower receiving plate 641a as a fulcrum The deformation in the direction of narrowing causes deformation of the connection arm 653, the coil 651, and the biasing arm 652 in the right side in a front view. In this case, since the coil portion 651 is subjected to deformation to reduce the inner diameter, an urging force is generated on the coil portion 651 and the connecting arm portion 653 to increase the inner diameter of the coil portion 651. The biasing force of the biasing arm 652 on the side of the swing direction 4640 of the transmission member 640 can be improved.

  Next, a combined operation unit 5500 according to the fifth embodiment will be described with reference to FIGS. 65 to 68.

  In the first embodiment, when the pivoting arm member 550 is disposed at the overhanging position, the second non-transmission wall portion 553c has a shape along a circle centered on the rotation axis of the pivoting crank member 570. However, the pivoting arm member 5550 in the fifth embodiment includes the recessed portion 5556 in which the non-transmission wall portion 5553 c is recessed in the direction away from the pivoting crank member 570. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  65 to 68 are front views of a combined operation unit 5500 according to the fifth embodiment. Incidentally, in FIG. 65, the state in which the pivoting arm member 5550 is disposed at the extended position and the sliding projection 574 of the pivoting crank member 570 is disposed near the left end portion of the second non-transmission wall portion 5553c is shown in FIG. In the state shown in FIG. 65, the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 is accommodated in the first recessed portion 5556 from the left end of the second non-transmission wall 5553c. In FIG. 67, the rotating crank member 570 is rotated counterclockwise in a front view from the state of FIG. 66 to the position where the sliding projection 574 is disengaged from the recessed portion 5556. From the state, the state where the rotating crank member 570 is rotated counterclockwise in a front view and the sliding projection 574 is accommodated in the recessed portion 5556 of two surfaces from the left end of the second non-transmission wall portion 5553c is illustrated. Ru.

  As shown in FIGS. 65 to 68, the second non-transmission wall portion 5553c of the combined operation unit 5550 includes a recessed portion 5556 recessed in a direction away from the rotating crank member 570.

  The recessed portion 5556 has a first wall portion 5556a having an arc shape (approximately 1⁄4 of a circular shape) formed on the left side in front view, and an arc shape (approximately 1⁄4 of a circular shape) formed on the right side The second wall 5556 b is mainly formed to allow sliding of the sliding projection 574 of the rotating crank member 570. That is, the recess depth from the second non-transmission wall 5553c of the recess 5556 is equal to or less than the radius of the sliding projection 574, and the connection between the recess 5556 and the second non-transmission wall 5553c is smooth. It is formed of a curved surface.

  When the rotating crank member 570 is rotated counterclockwise in a front view from the state shown in FIG. 65 to the state shown in FIG. 66, a gap is generated between the sliding projection 574 and the second non-transmission wall 5553 c, The pivoting arm member 5550 is swung until it abuts on the sliding projection 574 by the biasing force generated by the torsion spring 517a. In this case, as the rotating crank member 570 is rotated, the first wall 5556a of the first recessed portion 5556 from the left end of the second non-transmission wall 5553c is slid by the sliding projection 574 while being rotated. The movable arm member 5550 is swung.

  That is, from the state shown in FIG. 65 to the state shown in FIG. 66, the pivoting arm member 5550 is only swung by the biasing force of the torsion spring 517a, and is rotated by the driving force of the second drive device 560. The moving arm member 5550 is not rocked. Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 of the rotating crank member 570 is disposed to face the first wall 5556a, the rotating arm member 5550 and the rotation The crank member 570 forms a non-transmission state.

  When the rotating crank member 570 is rotated counterclockwise from the state shown in FIG. 66 to the state shown in FIG. 67, the sliding projection 574 is recessed first from the left end of the second non-transmission wall 5553 c. It is pressed against the second wall 5556 b of the setting portion 5556, and the pivoting arm member 5550 is swung again (pushed down) to the extended position. That is, from the state shown in FIG. 66 to the state shown in FIG. 67, since the second arm 5556b is pushed and moved by the sliding projection 574, the pivoting arm member 5550 is swung. The driving force of the second drive device 560 is transmitted to the pivoting arm member 5550 via the pivoting crank member 570.

  Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view and the sliding projection 574 of the rotating crank member 570 is disposed to face the second wall 5556b, the rotating arm member 5550 and the rotation The crank member 570 forms a transmission state.

  When the rotating crank member 570 is rotated counterclockwise from the state shown in FIG. 67 to the state shown in FIG. 68, a gap is generated between the sliding projection 574 and the second non-transmission wall portion 5553c, The pivoting arm member 5550 is swung until it abuts on the sliding projection 574 by the biasing force generated by the torsion spring 517a. In this case, as the rotating crank member 570 is rotated, the first wall 5556a of the second recessed portion 5556 from the left end of the second non-transmission wall 5553c is slid by the sliding projection 574 while being rotated. The movable arm member 5550 is swung.

  That is, from the state shown in FIG. 67 to the state shown in FIG. 68, the pivoting arm member 5550 is only swung by the biasing force of the torsion spring 517a, and is rotated by the driving force of the second drive device 560. The moving arm member 5550 is not rocked. Therefore, when the rotating crank member 570 is rotated counterclockwise in a front view, and the sliding projection 574 of the rotating crank member 570 is disposed to face the first wall 5556a, the rotating arm member 5550 and the rotation The crank member 570 forms a non-transmission state.

  As shown in FIGS. 65 to 68, when the sliding projection 574 is disposed to face the first wall 5556a in a state where the rotating crank member 570 is rotated counterclockwise in a front view. When a non-transmission state is formed between the moving crank member 570 and the rotating arm member 5550, and the sliding projection 574 is disposed opposite to the second wall 5556b, the rotating crank member 570 and the rotating arm member A communication state is formed with 5550.

  If the rotation direction of the rotating crank member 570 is reversed, the relationship between the first wall 5556a and the second wall 5556b is reversed. That is, when the rotating crank member 570 is rotated clockwise as viewed from the front, the rotating crank member 570 and the rotating arm member 5550 are arranged when the sliding projection 574 is disposed to face the first wall 5556 a. And when the sliding projection 574 is disposed to face the second wall 5556b, a non-transmission state is formed between the pivoting crank member 570 and the pivoting arm member 5550. Ru.

  As shown in FIGS. 65 to 68, in this embodiment, the pivoting arm member 5550 is in the retracted position (see FIG. 22) and the overhanging position without switching the pivoting direction of the pivoting crank member 570. In addition to the swinging motion swinging between them, the pivoting arm member 5550 has a small width near the overhanging position (a mode in which the lower end of the front plate member 546 is moved between the position U1 and the position U2) A rocking movement can be formed.

  As a result, it is possible to cause the pivoting arm member 5550 to produce a swinging motion that is difficult to form by switching the drive direction of the drive device 560. That is, to cause the swing arm member 5550 to perform a swing operation with a small width in the vicinity of the extended position can also be formed by repeatedly switching the drive direction of the drive device 560 at short intervals. However, in this case, the width of the rocking operation depends on the switching speed of the drive direction of the drive device 560. Further, even if the drive direction of the drive device 560 is switched in a state where the speed of the swinging motion of the pivot arm member 5550 is large, the inertia of the drive device 560 and the pivot arm member 5550 is large and the drive direction can not be switched instantaneously. The time required to switch the drive direction may be long.

  On the other hand, in the swinging operation near the extended position of the pivoting arm member 5550 in the present embodiment, there is no need to switch the rotation direction of the pivoting crank member 570, so the time required to switch the drive direction is unnecessary. can do.

  Further, the operation speed of the operation (the upward swinging operation) in which the pivoting arm member 5550 is pivoted clockwise in the front view depends on the biasing force generated by the torsion spring 517a, and the pivoting arm member 5550 is not The operating speed of the clockwise rocking movement (downward rocking movement) depends on the rotational speed of the rotating crank member 570. Therefore, by increasing the biasing force of the torsion spring 517a and increasing the rotational speed of the rotating crank member 570, it is possible to increase the swinging speed in the vicinity of the extended position of the rotating arm member 5550.

  As a result, it is possible to achieve both the speeding up of the rocking operation in the vicinity of the extended position of the rotary arm member 5550 and the shortening of the switching time of the rocking direction.

  Next, a combined operation unit 6500 according to the sixth embodiment will be described with reference to FIGS. 69 to 71.

  In the first embodiment, the case where the pivoting arm member 550 of the combined operation unit 500 is integrally molded has been described, but the pivoting arm member 6550 in the sixth embodiment is formed by connecting two members. . The relative swing of the two members changes the posture of the arc-shaped hole 554 formed at the other end. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  69 (a) and 69 (c) is a partial front view of the pivoting arm member 6550 in the sixth embodiment, and FIG. 69 (b) is a pivot in the direction of arrow LXIXb in FIG. 69 (a). FIG. 50 is a partial top view of an arm member 6550. 69 (a) shows a state in which the first attitude in which the tip of tip swing member 6556 is directed upward is formed, and in FIG. 69 (b), the tip of tip swing member 6556 is down. The state in which the second attitude to be directed is formed is illustrated.

  As shown in FIG. 69A, the pivoting arm member 6550 is connected to the main body portion 6551 pivotally supported by the third shaft portion 517 (see FIG. 71) and the other end of the main body portion 6551. A distal end swinging member 6556 and a switching device 6590 fixed to the upper surface of the other end of the main body portion 6551 to switch the attitude of the distal end swinging member 6556 are mainly provided. An arc-shaped hole 6554 is formed in the tip end swinging member 6556.

  The main body portion 6551 is provided with a shaft support hole 6551a which is bored in the other end portion in the front-rear direction and which becomes a swing center of the tip swing member 6556.

  The end swinging member 6556 is formed in such a manner that the end connected to the main body portion 6551 sandwiches the main body portion 6551 back and forth, and a shaft support hole 6556a drilled as a swing center of the tip swinging member 6556 A shaft support rod 6556b which is a rod inserted through the shaft support hole 6556a and the shaft support hole 6551a of the tip swing member 6556 and an extension provided extending from the shaft support hole 6556a to the opposite side of the arc-shaped hole 6554 The sliding shaft 6556c is mainly provided so as to protrude in the front-rear direction from the end of the portion and connected to the guide long hole 6591d of the switching device 6590.

  The arc-shaped hole 6554 is provided with a return portion 6554a protruding from the upper inner side surface. The return portion 6554a is a portion that slides on the protrusion 541b of the expansion / contraction effect member 6540, and when sliding from the tip end side of the arc-shaped hole 6554, resistance is suppressed, while sliding in the opposite direction It is a projection of the left-right asymmetrical shape where sliding resistance is increased when moved.

  70 (a) and 70 (b) are front perspective views of the switching device 6590. FIG. 70 (a) shows a push-up state where the C-shaped member 6591 is pushed up from the switch member 6592, and FIG. 70 (b) shows a pressed-down state where the C-shaped member 6591 is pushed down to the switch member 6592. Is illustrated. Further, the push-up state corresponds to the state of FIG. 69 (c), and the push-down state corresponds to the state of FIG. 69 (a).

  The C-shaped member 6591 has an inner diameter equal to the inner diameter of a long plate-like main body 6591a in which a hole having an inner diameter through which the movable cylindrical portion 6592a can be inserted is bored at the center and a hole bored in the main body 6591a. And a cylindrical guide portion 6591b protruding in a cylindrical shape and having a groove formed on the inner peripheral surface, extending downward from both end portions in the longitudinal direction of the main body portion 6591a and opposingly disposed in the front-rear direction of the main body portion 6551 A pair of arm portions 6591c and a guiding long hole 6591d which is a long hole formed on the tip end side of the arm portion 6591c and to which the sliding shaft 6556c of the tip swinging member 6556 is guided are mainly provided.

  The groove processing formed on the inner peripheral surface of the cylindrical guide portion 6591 b is a groove processing for forming a knock mechanism in relation to the movable cylindrical portion 6592 a of the switch member 6592. The C-shaped member 6591 is switched between the push-up state and the push-down state each time the C-shaped member 6591 is pushed in a direction to be pressed against the switch member 6592. In addition, illustration of other members, such as a spring member which forms an urging | biasing force required in order to form a knock mechanism, is abbreviate | omitted, In this embodiment, the cylindrical guide part 6591b is the pushing part 6541a of the expansion-contraction effect apparatus 6540 (figure 71)).

  In the switch member 6592, a movable cylindrical portion 6592a is inserted through the cylindrical guide portion 6591a, and a movable cylindrical portion 6592a is provided with a projection capable of moving the groove on the inner peripheral surface of the cylindrical guide portion 6591a from the outer peripheral surface. And a fixing plate portion 6592b rotatably connected and fixed to the upper surface of the main body portion 6551 of the rotating arm member 6550.

  Here, in the knock mechanism, the relative position in the axial direction is switched while the cylindrical member and the cylindrical member guided on the inner peripheral side of the cylindrical member are relatively rotated. That is, when the tubular member and the cylindrical member do not rotate relative to each other, it is difficult to switch the relative position in the axial direction.

  On the other hand, the movable cylindrical portion 6592a of the switch member 6592 is rotatably connected to the fixed plate portion 6592b. Therefore, when the C-shaped member 6591 is moved in the direction approaching the switch member 6592 (when pushed downward in FIG. 70A), the movable cylindrical portion 6592a can be relatively rotated with respect to the cylindrical guide portion 6591b. And the knock mechanism works.

  Therefore, it is possible to switch between the push-up state and the push-down state without relatively rotating the fixing plate portion 6592b fixed to the main body portion 6551 of the pivoting arm member 6550 and the C-shaped member 6591. Therefore, the state of the switching device 6590 can be switched between the push-up state and the push-down state while maintaining the state in which the slide shaft 6556c of the tip swing member 6556 is inserted into the guide long hole 6591d of the C-shaped member 6591. it can.

  71 (a) and 71 (b) are front views of the combined operation unit 6500. FIG. 71A shows a state in which the pivoting arm member 6550 is disposed at the overhanging position and the switching device 6590 is in the push-up state, and in FIG. K4, the pivoting arm member 6550 is disposed at the overhanging position and switched The device 6590 is shown in the depressed state. In FIGS. 71 (a) and 71 (b), the expansion / contraction effect device 6540 is disposed at a position where it is swung to the left end of the swingable range.

  As shown in FIGS. 71 (a) and 71 (b), the front view timepiece of the telescopic effect device 540 by switching the state of the switching device 6590 in the state where the pivoting arm member 6550 is disposed at the extended position. The maximum swing angle around can be switched.

  That is, when the switching device 6590 forms a push-up state (see FIG. 71A), the projection 541 b of the expansion / contraction effect member 6540 is in contact with the upper inner side surface of the arc-shaped hole 6554. The swing angle is limited.

  In this position, even if the inner surface of the circular arc shaped hole 6554 and the return portion 6554a function as a stopper and the swinging speed of the expansion / contraction effect device 6540 is high, the expansion / contraction effect device 6540 is arranged in the arrangement shown in FIG. A sudden stop can be made (the movement trajectory RI of the protrusion 541b is abutted on the return portion 6554a).

  On the other hand, when the switching device 6590 forms a depressed state (see FIG. 71B), the protrusion 541 b of the expansion / contraction effect device 6540 does not collide with the arc-shaped hole 6554 and the return portion 6554 a (the protrusion 541 b The movement trajectory RI is not in contact with the return portion 6554a). Therefore, the protrusion 541 b of the expansion and contraction rendering device 6540 is moved along the arc-shaped hole 6554, and the protrusion 541 b is discharged to the outside from the tip end 554 a of the arc-shaped hole 6554.

  Therefore, the expansion / contraction effect device 6540 is swung clockwise as viewed from the front until the rotary plate 520 is abutted against the second stopper portion 518b (see FIG. 71 (b)). In this position, the second stopper portion 518b functions as a stopper, and even when the swinging speed of the expansion and contraction rendering device 6540 is high, the expansion and contraction rendering device 540 can be rapidly stopped.

  Thereby, a plurality of swing angles (two types in the present embodiment) can be formed when swinging the expansion / contraction effect device 6540 clockwise in a front view and causing the expansion / contraction effect device 6540 to stop sharply. The variation of can be increased. The state of the switching device 6590 is switched by swinging the expansion / contraction effect member 6540 counterclockwise in a front view, so that the cylindrical guide portion 6591b of the switching device 6590 moves from the front right upper portion of the main body member 6541a to the right. It is generated by being pushed by a push-in portion 6541a extended in the direction. Therefore, since the second drive device 560 for causing the swing of the expansion / contraction effect member 6540 is also used as a drive device for swinging the tip swing member 6556, the number of drive devices can be reduced.

  Further, in FIGS. 71A and 71B, the swing range of the expansion / contraction effect device 6540 can be changed by slightly swinging the tip swing member 6556. In this case, since the rocking angle is slight, it is possible for the player to hardly notice the change.

  Here, if it is possible for the player to visually recognize the pivoting arm member 6550 (see FIG. 71), assuming that the swing angle of the expansion / contraction effect device 6540 can be grasped from the change in the state of the pivoting arm member 6550, The sense of expectation for the operation of the expansion and contraction producing device 6540 is weakened, and the attention of the expansion and contraction producing device 6540 is reduced.

  On the other hand, in the present embodiment, in order to change the swing angle of the expansion / contraction effect device 6540, the angle at which the tip swing member 6556 is swung is small, making it difficult for the player to notice the change. it can. Thus, the sense of expectation for the operation of the expansion / contraction effect device 6540 can be enhanced, and the degree of attention of the expansion / contraction effect device 6540 can be improved.

  Next, with reference to FIG. 72, a tilting operation unit 7600 in the seventh embodiment will be described.

  In the first embodiment, the slide hole 643 having a long hole shape is formed at the end of the transmission member 640, and the effect member 620 is supported by the slide hole 643 in a guideable manner. In the tilting operation unit 7600 in the embodiment, a pivot hole 7643 is formed at an end of the transmission member 7600, and the effect member 620 is pivotally supported by the pivot hole 7643. In addition, the same code | symbol is attached | subjected to the part same as each embodiment mentioned above, and the description is abbreviate | omitted.

  72 (a) and 72 (b) is a front view of the tilting operation unit 7600 in the seventh embodiment. FIG. 72 (a) shows an inverted state in which the shaft support hole 7643 of the transmission member 7640 is disposed vertically above the cylindrical portion 642, and in FIG. 72 (b), the inverted state from FIG. 72 (b). A state in which the transmission member 7640 is swung counterclockwise by a predetermined angle is illustrated. In FIGS. 72 (a) and 72 (b), in order to facilitate understanding, the outline of the effect member 620 is illustrated by an imaginary line, and the transmission member 7640 and the base member 7610 on the back side can be viewed. The illustration of the torsion spring 650 and the pivoting protrusion 612 is omitted.

  As illustrated in FIG. 72 (a), the base member 7610 is provided with a slide hole 7613 drilled in the front-rear direction vertically below the second shaft support hole 614 of the main body 611. The slide hole 7613 is a long hole through which the swinging shaft portion 626 of the effect member 620 is inserted, and the longitudinal direction of the long hole is formed along the vertical direction. The swing shaft portion 626 is slidably supported by the slide hole 7613.

  In the transmission member 7640, a shaft support hole 7643 is formed at an end opposite to the end where the cylindrical portion 642 of the main body 641 is formed. The shaft support hole 7643 pivotally supports the sliding shaft portion 621a of the effect member 620, and is bored with an inner diameter slightly larger than the diameter of the sliding shaft portion 621a.

  The swinging operation of the effect member 620 is generated by the transmission member 7640 swinging about the second support hole 614 by the rotation of the drive motor 631 of the first drive device 630 (see FIG. 51).

  In the present embodiment, since the sliding shaft portion 621a is pivotally supported by the shaft support hole 7643, when the transmission member 7640 swings, the sliding shaft portion 621a of the effect member 620 follows the swinging trajectory of the transmission member 7640. To move (the sliding shaft 621a does not move in the longitudinal direction of the main body 641). On the other hand, since the swinging shaft portion 626 is inserted into the slide hole 7613, when the transmission member 7640 swings, the swinging shaft portion 626 slides relative to the base member 7610.

  Here, the difference between the swing angle of the transmission member 7640 and the swing angle of the effect member 620 will be described. As shown in FIG. 72 (b), when the transfer member 7640 swings from the upside down by the transfer swing angle φ71, the effect member 620 swings by the effect swing angle φ72 (the effect swing angle φ72 <transfer shake Dynamic angle φ71). Therefore, when the transmission member 7640 is swung by the minimum unit of resolution of the drive motor 631, the swing angle of the effect member 620 can be smaller than the swing angle of the transmission member 7640. Thereby, the accuracy of the adjustment of the swing angle of the effect member 620 can be improved.

  Furthermore, in the present embodiment, the swing angle of the effect member 620 when the transfer member 7640 swings from the upright state by the transfer swing angle φ 71 can be made smaller than that in the first embodiment. explain.

  The connection line J1 illustrated in FIG. 72 (b) is a line drawn from the sliding shaft 621a to the swinging shaft 626. When the imaginary connecting line J2 has a length equal to that of the connecting line J1 and the rocking shaft 626 is disposed above the sliding hole 7613 from the line drawn in the longitudinal direction of the main body 641 through the cylindrical portion 642 It is a line drawn to the center of the swinging shaft portion 626 (see FIG. 72 (a)). In the case where the first shaft support hole 613 of the first embodiment is formed in the upper portion of the slide hole 7613, the virtual angle φ 73 which is the swing angle of the virtual connection line J2 in the first embodiment. This corresponds to the swing angle of the effect member 620 which is swung as the transmission member 640 is swung by the transmission swing angle φ71.

  As shown in FIG. 72 (b), the effect swing angle φ 72 is smaller than the virtual angle φ 73, and according to the tilting operation unit 7600 of the seventh embodiment, the effect in the case of swinging the transmission member 7640 by a predetermined angle The swing angle of the member 620 can be made smaller as compared with the case of the first embodiment. Therefore, when swinging the transmission member 7640 by the minimum unit of resolution of the drive motor 631 (see FIG. 51), the swing amount of the effect member 620 can be made smaller than that, and the swing angle of the effect member 620 is adjusted. Accuracy can be improved.

  As mentioned above, although the present invention was explained based on the above-mentioned embodiment, the present invention is not limited to the above-mentioned form at all, It is easy to be able to carry out various modification improvement in the range which does not deviate from the meaning of the present invention. It can be guessed.

  In each of the above-described embodiments, part or all of the configuration in one embodiment may be combined with or replaced with the configuration of part or all of the configuration in another embodiment to provide another embodiment.

  Although the case where the front rail part 715 was formed from a single circular arc shape was demonstrated in said each embodiment, it is not necessarily restricted to this. For example, the front rail portion 715 may be formed of a plurality of arcs, and the direction of the adjacent arcs may be reversed (wave shape). In this case, the slide movement speed of the effect member 620 is intermittently changed, and the posture of the effect member 620 is unstable. Therefore, it is possible to perform an effect of shaking the effect member 620.

  Although the case where the gravity center of the effect member 620 is vertically above the first shaft support 613 when the effect member 620 forms the inverted state has been described in the above embodiments, the present invention is not necessarily limited thereto. For example, the center of gravity may be disposed obliquely above the first shaft support 613.

  Although the case where the upper surface of the buffer rib 322 of the lower left plate member 320 is horizontal in the left-right direction has been described in the above embodiments, the present invention is not necessarily limited thereto. For example, the upper surface of the buffer rib 322 may be inclined downward as it approaches the width direction outer side. In this case, the velocity of the ball flowing into the upper surface of the lower left plate member 320 from the outer side in the board width direction can be decelerated by the acceleration in the gravity direction, and the deceleration time of the ball can be shortened.

  In each of the above embodiments, the case where the slide hole 643 of the transmission member 640 is formed as a long hole has been described, but the present invention is not necessarily limited to this. For example, the slide hole 643 may be formed in a circular shape, and the positional deviation between the slide hole 643 and the slide shaft portion 621a may be adjusted by the transmission member 640 extending and contracting. In this case, the arrangement range of the transmission member 640 can be suppressed.

  Although the case where the position of the contact part 644 can be switched by 2 positions was demonstrated in the said 4th Embodiment, it is not necessarily restricted to this. For example, the position of the contact portion 644 may be continuously changed (moved). In this case, the rate of change of the biasing force of the torsion spring 650 can be continuously increased.

  In the sixth embodiment, although the case where the attitude of the tip end swinging member 6556 changes at two positions has been described, the present invention is not necessarily limited thereto. For example, the posture change of the tip swinging member 6556 may be caused in a plurality of steps. In this case, the swing amount of the expansion / contraction effect device 6540 can be formed with a plurality of types, and variations of the effect can be increased.

  The present invention may be implemented on a type of pachinko machine or the like different from the above-described embodiments. For example, a pachinko machine (common name, two-time, three-time, and so on) in which the jackpot expected value can be increased until the jackpot state occurs a plurality of times (for example, two times, three times) including the jackpot once May be implemented as In addition, after the jackpot symbol is displayed, it may be implemented as a pachinko machine that generates a special game in which a predetermined game value is given to the player, as a prerequisite to winning a ball in a predetermined area. In addition, it is possible to have the winning device which possesses special territory such as V zone and to execute to the pachinko machine which becomes special game state as a necessary condition to make the special territory win the ball. Furthermore, in addition to pachinko machines, various types of gaming machines may be implemented, such as arelapachis, ball balls, slot machines, gaming machines in which so-called pachinko machines and slot machines are fused.

  In the slot machine, for example, a symbol is changed by operating the operation lever in a state where the coin is inserted and the symbol effective line is determined, and the symbol is stopped and determined by operating the stop button. It is a thing. Therefore, as a basic concept of the slot machine, “a display device is provided which displays the identification information after displaying the identification information sequence consisting of a plurality of identification information in a variable manner, and is derived from the operation of the starting operation means (for example, operation lever) The variable display of identification information is started, and the variable display of identification information is stopped and fixedly displayed due to the operation of the operation means for stop (for example, stop button) or when a predetermined time elapses. It is a slot machine that generates a special game that gives a predetermined game value to the player, as a prerequisite that the combination of identification information at the time is a specific one. In this case, the game medium is represented by coins, medals, etc. An example is given.

  In addition, as a specific example of a gaming machine in which a pachinko machine and a slot machine are fused, a display device is provided which variably displays a symbol row consisting of a plurality of symbols and then displays the symbols, and is provided with a handle for ball launch. Not included. In this case, after the injection of a predetermined amount of balls based on a predetermined operation (button operation), for example, the variation of the symbol is started due to the operation of the operation lever, for example, due to the operation of the stop button or By the passage of time, the fluctuation of the symbol is stopped, and a special game for giving a predetermined game value to the player is generated as a necessary condition that the determined symbol at the time of the stop is a so-called jackpot symbol. Is a lot of balls being dispensed to the lower tray. If such a gaming machine is used in place of a slot machine, only balls can be handled as gaming value in the gaming hall, so the gaming value is found in the current gaming hall where pachinko machines and slot machines are mixed. It is possible to solve the problems such as the burden on equipment due to the separate handling of medals and balls and the restriction on the installation location of gaming machines.

  Hereinafter, the concepts of various inventions included in the above-described embodiment in addition to the gaming machine of the present invention will be described.

<An example of the technical idea to change the driving force transmission by the deformed elongated hole 553 of the pivot arm member 550>
A crank member which is rotated about a first axis and has a projection projecting at a position eccentric to the first axis, and an insertion portion through which the projection is inserted, the first position and the first position are separated from each other An arm member movable between the second position and a drive device for generating a driving force for rotating the crank member about the first axis, the insertion portion being inserted The driving force is transmitted to the arm member by bringing the projection into contact with the inner peripheral surface of the insertion portion facing in the movement direction of the projection, and the arm member is moved to the first position and the second position. A gaming machine characterized by comprising: a transmission area movably formed between a position and a non-transmission area which is connected to the transmission area and in which transmission of the driving force is blocked. A1.

  Here, in a gaming machine such as a pachinko machine, the crank member includes a crank member provided with a protruding portion protruding from a rotational shaft and an arm member provided with an insertion portion into which the protruding portion of the crank member is inserted. There is a gaming machine in which an arm member operates in conjunction with rotation of a crank member (see, for example, JP-A-2009-000306). However, in the above-described conventional gaming machine, the crank member and the arm member always interlock. Therefore, the arm member is driven from the start of the crank member, and the timing of the start of the crank member and the timing of driving the arm member can not be shifted. In this case, at the time of starting the crank member, a large force is required to overcome the inertia of the crank member and the arm member, and there is a problem that the drive device becomes large.

  On the other hand, according to the gaming machine A1, since the insertion portion of the arm member includes the transmission region and the non-transmission region connected to the transmission region, the crank is inserted in the non-transmission region. By starting the member, it is possible to shift the timing for driving the arm member and the timing for starting the crank member. That is, even if the crank member is started, the driving force is not transmitted to the arm member until the projection intrudes from the non-transmission region into the transmission region. As a result, the driving force required for starting the crank member can be suppressed, and the drive device can be miniaturized.

  The arm member may be stopped or moved while the protrusion moves in the non-transmission area. For example, when an arm member is moved, the case where it moves by the elastic force etc. which gravity or the elastic spring for assistance generate | occur | produces is illustrated.

  In addition, as a penetration part, a hollow with a bottomed recessed part, a long hole penetrated etc. are illustrated.

  In the gaming machine A1, the crank member is formed so as to be able to rotate by one or more rotations, and the insertion portion becomes the transmission area by rotating the crank member in one rotation direction, while the crank member A game machine A2 comprising a selection area which becomes the non-transmission area by being rotated in another rotation direction opposite to the one rotation direction.

  According to the gaming machine A2, in addition to the effects achieved by the gaming machine A1, the mode of transmission of the driving force to the arm member can be changed according to the rotation direction of the crank member. In this way, by reversing the direction of the driving force of the driving device without changing the rotational speed of the crank member, it is possible to form two speed modes of the arm member when the crank members are arranged in the same phase. The variation of the speed of the arm members can be increased.

  In the gaming machine A2, the insertion portion is separated from the projection and an inner circumferential surface of the insertion portion facing in the movement direction of the projection when the crank member is rotated in the one rotation direction. A game machine A3 characterized in that the selection area is formed by providing an extra portion.

  In the gaming machine A3, in addition to the effects exhibited by the gaming machine A2, the selection area is formed by providing the insertion portion with the extra portion, so that the other for changing the mode of transmission of the driving force to the arm member Parts can be eliminated and material costs can be reduced.

  In any one of the gaming machines A1 to A3, at least one of the first position and the second position is formed as an end position of a movement range of the arm member, and the first position or the formed as an end position thereof. When the arm member is disposed at one of the second positions, the arm member directed to the other one of the first position or the second position formed opposite to the end position. A game machine A4 characterized in that a bound suppressing mechanism for suppressing movement is formed.

  According to the gaming machine A4, in addition to the effects of the gaming machine A3, when the arm member is disposed at either the first position or the second position formed as the end position of the movable range of the arm member, It is possible to suppress the driving force that the driving device needs to generate in order to suppress the movement of the arm member toward the other side on the opposite side. Therefore, the durability of the drive device can be improved.

  In addition, when using the adsorption | suction force of a magnet as a bound suppression mechanism, when suppressing a motion with a claw-shaped member, and the load which the projection part of a crank member receives from an arm member faces an axial direction of a crank member, an arm The case where the penetration part of a member is formed, etc. are illustrated.

  In the case of adsorbing with a magnet, although the magnet is required as a separate member, it is possible to generate various magnitudes of adsorption force by the internal composition of the magnet, and the design freedom can be improved.

  In the case where the movement is suppressed by the claw-shaped member, a driving device for operating the claw-shaped member is necessary, but the movement of the arm member can be mechanically arrested by the claw-shaped member.

  When the insertion portion of the arm member is formed in such a manner that the load received by the projection of the crank member from the arm member is directed to the axis of the crank member, provision of a separate member for restraining movement of the arm member is unnecessary. Bounce of the arm member can be suppressed mechanically.

  In the gaming machine A4, when the arm member is disposed at at least one of the first position or the second position, an outline of the non-transmission area of the insertion portion near the connection position with the transmission area is the external shape. A game machine A5 characterized in that the bound suppressing mechanism is formed by being substantially the same as the circumscribed circle of the protrusion centering on the rotation axis of the crank member.

  According to the gaming machine A5, in addition to the effects of the gaming machine A4, the bounce suppressing mechanism is formed by continuing the rotation of the crank member after the arm member is disposed at the first position or the second position. Thereby, the change from the movement state of an arm member to a stop state can be formed smoothly.

  Further, in the bounce suppressing mechanism, the load applied from the insertion portion to the projection is directed to the rotation shaft of the crank member, so that the load in the rotation direction of the crank member can be suppressed, and the load on the drive device is suppressed. can do.

  In any one of the gaming machines A1 to A5, when the arm member is disposed at the first position, an outline of the non-transmission area of the insertion portion near the connection position with the transmission area is the crank member. An urging force is applied to move the arm member from the first position to the second position, which is substantially the same as the circumscribed circle of the protrusion centering on the rotation axis, and the non-transmission area of the insertion portion The side surface on the first position side is formed with at least one of an inner recessed portion protruding inside of the insertion portion or an outer recessed portion protruding outside of the insertion portion with a size that can accommodate the protrusion. A game machine A6 characterized by being

  According to the gaming machine A6, in addition to the effects of any one of the gaming machines A1 to A5, when the arm member is disposed at the first position, the outer shape in the vicinity of the connection position with the transmission area of the non-transmission area of the insertion portion. Is substantially the same as the circumscribed circle of the protrusion centering on the rotation axis of the crank member, and an urging force for moving the arm member from the first position to the second position is loaded on the arm member. In this case, the projection of the crank member is disposed in the non-transmission area of the insertion portion, whereby the movement of the arm member is prevented by the projection and the arm member is stopped. When the crank member is rotated and the projection moves in the non-transmission area, the arm member is moved when the projection and the inner recess or the outer recess are opposed to each other. That is, when the protrusion is disposed to face the inner recess, the inner recess is pushed out by the protrusion, and the arm member is moved to the opposite side of the crank member. Further, when the protrusion is disposed to face the outer recess, the protrusion is accommodated in the outer recess, and the arm member is moved to the crank member side.

  As a result, the projection of the crank member moves in the non-transmission area, whereby the movement of the arm member, which is different from the movement of the arm member caused when the projection moves the transmission area by rotating the crank member Can occur. Therefore, coexistence with the improvement of durability of a drive device and the change of the movement width of an arm member can be aimed at.

  That is, in order to change the movement width of the arm member, it is necessary to reverse the direction of the driving force of the drive device according to the movement width of the arm member. In this case, the control load of the drive device is increased, and it is difficult to perform an operation with a small movement width such as vibration.

  On the other hand, according to the gaming machine A6, the projection of the crank member is moved in the non-transmission area, and the projection and the inner hollow portion or the outer hollow portion are disposed opposite to each other, thereby forming the movement of the arm members having different moving widths. Ru. Therefore, the movement width of the movement of the arm member can be changed without reversing the direction of the driving force of the driving device. In addition, by narrowing the formation interval of the adjacent inward depressions or outward depressions, it is possible to cause the arm member to perform an operation with a small movement width such as vibration.

  In addition, the aspect which can accommodate a projection part may be an aspect in which the whole projection part is included in a recess, and the aspect in which a part of projection part is contained in a recess may be sufficient.

<An example of the technical idea of limiting the swing width of the expansion / contraction effect device 540 by the arc-shaped hole 554>
The movable member which can move along a predetermined movement trajectory and can be disposed at the first position and the second position which are different from each other, moves corresponding to the movable member, and abuts on the movable member to move the movable member. A stopper member for restricting the movement width of the predetermined movement trajectory of the member and changing the movement width of the movable member depending on whether the movable member is disposed at the first position or the second position; , A game machine B1 characterized by comprising.

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine provided with a movable member formed movable and a stopper member for restricting the movement width of the movable member (for example, JP 2012-016623A). reference). However, in the above-described conventional gaming machine, the stopper member is fixed immovably, so the stopper member is separately prepared for the case where the movable member is disposed at the first position and the case where the movable member is disposed at the second position. And the space for disposing the stopper member is wide.

  On the other hand, according to the gaming machine B1, since the stopper member moves corresponding to the movable member, the movable member is arranged at the second position while the stopper member is arranged at the first position. It can also be used as a stopper in the case. Thereby, the space which arranges a stopper member can be controlled.

  In addition, since the stopper member changes the moving width of the movable member depending on whether the movable member is arranged at the first position or the movable member is arranged at the second position, the variation of the moving width of the movable member is increased be able to.

  The stopper member may be, for example, a protrusion projecting from the transmission member and coming into contact with the movable member, or an inner wall of a recess which is recessed in the transmission member and accommodates a part of the movable member.

  In addition, as a mode of movement, linear movement, curvilinear movement, meandering movement, vibration, rocking, rotational movement and the like are exemplified. Further, the movement width in each movement aspect means, for example, an actual movement distance or a linear distance between two points in the case of linear movement, curvilinear movement, meandering movement, vibration, etc. In the case of etc., it means the actual movement distance, movement angle, etc.

  In the gaming machine B1, the movable member includes an intermediate member pivotally supported by the first shaft so as to be swingable and extendable in the radial direction of the first shaft, and in the first position and the second position The expansion and contraction length of the intermediate member is different, the predetermined movement trajectory is formed in an arc shape centered on the first axis, and the stopper member is in a case where the intermediate member is in a predetermined expansion and contraction state A game machine B2 extending along the predetermined movement trajectory of the movable member.

  According to the gaming machine B2, in addition to the effects of the gaming machine B1, the movable member is pivotally supported so as to be pivotable about the first axis and is formed so as to be able to extend and contract in the radial direction of the first axis It has a member. Therefore, the curvature radius of the predetermined movement locus of the movable member centering on the first axis can be changed depending on the length of the intermediate member in the expansion and contraction direction.

  Here, the stopper member is extended along a predetermined movement trajectory of the movable member when the intermediate member is in a predetermined expansion / contraction state (a curvature of the extension direction of the stopper member and the predetermined expansion / contraction state of the intermediate member) And the curvature of the predetermined movement trajectory of the movable member in the same case). In this case, when the intermediate member is in a predetermined expansion and contraction state, the movable member is moved along the stopper member, and the movable member can be moved in the extending direction of the stopper member. Therefore, the movement width (swing angle) of the movable member can be maximized.

  On the other hand, when the intermediate member is in an expansion / contraction state different from the predetermined expansion / contraction state, the curvature of the predetermined movement trajectory of the movable member and the curvature in the extending direction of the stopper member can be made different, and the predetermined movement of the movable member The track and the extending direction of the stopper member can be crossed. Therefore, the movement width of the movable member can be shortened. Therefore, the movement width of the movable member can be changed by changing the expansion and contraction state of the intermediate member.

  In the gaming machine B2, the movable member includes a protrusion protruding toward the stopper member, the stopper member includes an insertion portion through which the protrusion is inserted, and the protrusion is on the insertion portion. In the inserted state, the movable member and the stopper member interlock in the expansion and contraction direction of the intermediate member, and the movable member abuts on the insertion portion.

  According to the gaming machine B3, in addition to the effects produced by the gaming machine B2, the movable member and the stopper member interlock in the expansion and contraction direction of the intermediate member by inserting the projection of the movable member into the insertion portion of the stopper member. The driving device for expanding and contracting the movable member and the driving device for moving the stopper member can be combined. Further, the insertion portion restricts the movement of the movable member by being in contact with the movable member. That is, the insertion portion of the stopper member has a function as a stopper for restricting the movement of the movable member, and a function for interlocking the movable member and the stopper member. This makes it possible to centralize the functions.

  In the game machine B3, the expansion and contraction operation of the intermediate member reverses the arrangement of the first shaft with respect to the insertion portion between the inner peripheral side and the outer peripheral side.

  According to the gaming machine B4, in addition to the advantageous effects of the gaming machine B3, the arrangement of the first shaft with respect to the insertion portion is reversed between the inner circumferential side and the outer circumferential side by the expansion and contraction operation of the intermediate member. Thereby, the movement width of the movable member can be changed between the case where the first shaft is disposed on the inner peripheral side of the insertion portion and the case where the first shaft is disposed on the outer peripheral side of the insertion portion.

  That is, in the case where the first axis is disposed on the inner peripheral side of the insertion portion (when the movement locus of the protrusion in the case where the movable member is moved with a predetermined movement locus follows the shape of the insertion portion), The movement locus and the shape of the insertion portion are approximated, and the movement width of the predetermined movement locus of the movable member can be increased. On the other hand, in the case where the first axis is disposed on the outer peripheral side of the insertion portion (when the movement trajectory of the projection when the movable member is moved with a predetermined movement trajectory substantially reverses the shape of the insertion portion), the projection The angle formed by the movement trajectory of the movable member and the inner wall surface of the insertion portion is increased, and the movement width of the predetermined movement trajectory of the movable member can be narrowed.

  In the gaming machine B3 or B4, the insertion portion is formed so as to be changeable in posture while maintaining the extended state of the intermediate member, and the posture of the insertion portion changes the contact position of the movable member and the insertion portion. Is changed, and the movement width of the predetermined movement trajectory of the movable member is changed.

  According to the gaming machine B5, in addition to the effects of the gaming machine B3 or B4, the contact position between the movable member and the insertion portion is changed by changing the posture of the insertion portion while maintaining the extended state of the intermediate member. In this case, the movement width of the predetermined movement trajectory of the movable member can be changed while maintaining the expansion and contraction state of the intermediate member.

  In any one of the game machines B3 to B5, the insertion portion includes a groove portion which allows the projection portion to move in and out along the movement path, and the projection portion is separated from the insertion portion through the groove portion. A game machine B6 that is capable of forming a state, and the movable member includes a positioning assisting portion that is engaged with the stopper member in the separated state.

  According to the gaming machine B6, in addition to the effects produced by any of the gaming machines B3 to B5, it is possible to form a separated state in which the projection is separated from the insertion portion through the groove and the movable member is in the separated state. A positioning aid is engaged with the stopper member. Therefore, the formation range of the stopper member can be made smaller than the movement range of the movable member, and the material cost of the stopper member can be reduced, and the positional deviation between the movable member and the stopper member in the separated state It can be prevented. That is, even if the projection is separated from the insertion portion of the stopper member, the relative movement of the movable member with respect to the stopper member is suppressed by the positioning assisting portion, so that the projection can be returned to the insertion portion again.

<An example of the technical idea of supporting the effect member 620 supported in an inverted position at two points>
A base member, a movable member displaceably supported by a support formed on the base member and moving upward from a predetermined position, a drive device generating a driving force for displacing the movable member, and the movable member A transmission member for transmitting a driving force generated from the drive device to the movable member, wherein the transmission member is pivotally supported by a pivot portion formed on the base member, A game machine C1 characterized in that the length from the pivot support portion to the connection position of the movable member and the transmission member is shorter than the length from the support portion to the connection position of the movable member and the transmission member. .

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine in which a movable member which is displaceably supported by a support formed on a base member and which moves upward from a predetermined position is driven by transmission of a driving force by a gear (for example, See JP 2011-120640 A). However, in the above-described conventional gaming machine, the movement amount of the center of gravity of the movable member when operating the drive device in the minimum unit of control resolution of the drive device (for example, one step for a stepping motor) is the support of the movable member Is proportional to the length from the center of gravity of the movable member to the center of gravity of the movable member. Therefore, the position adjustment of the center of gravity of the movable member becomes more difficult as the center of gravity of the movable member moves away from the support in the radial direction.

  In addition, when the center of gravity of the movable member is shifted to one side from an inverted state in which the center of gravity of the movable member is disposed directly above the support portion, a driving force is generated to displace the movable member in the opposite direction, and the movable member is inverted. If the center of gravity is shifted to the other side by the driving force even if the state is maintained, the direction of the driving force coincides with the direction of gravity, and the movable member is largely displaced.

  Therefore, as the movable member becomes longer in the radial direction of the support portion, there is a problem that it becomes more difficult to stop the movable member in an inverted state in which the center of gravity of the movable member is disposed directly above the support portion.

  On the other hand, according to the gaming machine C1, the transmission member for transmitting the driving force of the drive device to the movable member to move the movable member upward is pivotally supported by the pivotal portion of the base member and connected to the movable member. The length from the connection position of the movable member and the connection member to the support portion is formed shorter than the length from the connection position of the movable member and the connection member to the support portion. Therefore, even if the movable member is long in the radial direction of the support portion, the movement amount of the center of gravity of the movable member in the case of operating the drive device at the minimum unit of control resolution of the drive device is suppressed. it can. Therefore, it is easy to make the movable member stationary in an inverted state in which the center of gravity of the movable member is disposed directly above the support portion.

  Note that as a mode in which the movable member is supported by the base member, a mode in which the movable member is pivotally supported by the base member in a pivotable manner, a mode in which the movable member is slidably supported by the base member, The combined aspect etc. are illustrated.

  In the gaming machine C1, the transmission member is characterized in that the arm length from the pivot support portion to the connection position with the movable member is shortened as the movable member moves upward from the predetermined position. Machine C2.

  According to the gaming machine C2, in addition to the effects of the gaming machine C1, the more the movable member displaced around the support portion moves upward from the predetermined position, the more the transmitting member from the pivot portion to the connecting position with the movable member The arm length is shortened. Therefore, compared with the case where the arm length of the transmission member is constant, the design freedom of the speed of the movable member can be improved.

  For example, when the rotation number of the drive device for rotating the transmission member operates at a constant speed, the arm length of the transmission member is fixed at a predetermined first length, and the arm length of the transmission member is the first It is assumed that the second length is shorter than the second length. When the number of rotations of the drive device is constant, the transmission when the transmission member is fixed at the first length is higher than when the arm length of the transmission member is fixed at the second length. The moving speed of the center of gravity of the movable member is increased when the member is placed in a predetermined phase.

  Here, the speed generated when the movable member is operated quickly at a speed that occurs when the transmission member has the first arm length near a predetermined position, and the speed that occurs when the transmission member has the second arm length near the inverted state Now consider the case where you want to move the movable member slowly. As a method for that purpose, although it is conceivable to change the rotation speed of the drive device halfway, this method can not be adopted when it is difficult to change the rotation speed of the drive device. In addition, even if it is possible to change the number of rotations of the drive device, in order to change the number of rotations on the way, a detection sensor for detecting the timing of the change is required, which increases the cost. There was a point.

  On the other hand, according to the gaming machine C2, in addition to the effects of the gaming machine C1, the arm length from the pivotally supported portion of the transmission member to the connection position of the transmission member and the movable member is a predetermined position of the transmission member. Is formed in such a manner as to be shortened as it moves upward from the Therefore, the transmission member can be set to the first arm length near the predetermined position, and the transmission member can be set to the second arm length near the inverted state, so that the design freedom of the speed of the movable member can be improved. .

  In addition, as a structure by which the arm length from the pivotal support portion to the connection position of the transmission member and the movable member is fixed, the case where the projection protruding from the transmission member is inserted into and coupled to the movable member is exemplified. Ru. In addition, as a configuration in which the arm length can be changed, a long hole is formed in the transmission member, and a protrusion protruding from the movable member is slidably inserted into the long hole of the transmission member, or movable The case where a long hole is provided in the part by which a member is supported by a support part, and the insertion shaft rod penetrated by the long hole from a base member is formed is illustrated.

  In the gaming machine C1 or C2, the movable member includes a protrusion projecting in a direction parallel to the support portion, and the transmission member is an elongated hole extending in the radial direction of the pivot portion. A game machine C3 comprising an insertion portion through which the projection is inserted.

  In the gaming machine C3, in addition to the effects of the gaming machine C1 or C2, the insertion portion is extended in the radial direction of the shaft support portion, and the transmission member and the movable member are inserted by inserting the projection of the transmission member into the insertion portion. As a result, the moving direction of the connecting position is restricted in the radial direction of the shaft support. Therefore, with the swinging of the transfer arm, it is possible to mechanically change the length from the support portion to the connection position of the transfer member to the movable member.

  In addition, as an insertion part, the long hole by which penetration formation is carried out, the recessed part formed as a hollow with a bottom, etc. are illustrated.

  In the game machine C3, the axis support portion is disposed vertically above the support portion, and the center of gravity of the movable member is disposed on a straight line connecting the support portion and the projection portion.

  According to the gaming machine C4, in addition to the effects of the gaming machine C3, the center of gravity of the support portion, the shaft support portion, the projection portion and the movable member is the movable member when the projection portion is disposed vertically above the support portion. It is formed on the vertical line. In this case, the gravity applied to the center of gravity of the movable member is loaded vertically downward with respect to the support and the bearing. Therefore, since the force in the rotational direction is not loaded on the movable member, the posture of the movable member can be maintained even if the power of the drive device is cut off. Thereby, the burden on the drive device can be reduced.

  In the gaming machines C1 to C4, a worm gear is interposed between the transmission member and the drive device, and the rotation of the drive device is decelerated by the worm gear.

  According to the gaming machine C5, in addition to the effects exhibited by the gaming machines C1 to C4, a worm gear is interposed between the transmission member and the driving device, and the rotation of the driving device is decelerated by the worm gear. The moving width of the movable member can be significantly reduced when operating with the smallest unit of resolution of In addition, since the transmission direction of the force through the worm gear is limited to one direction from the drive device side to the transmission member side, it is possible to prevent the worm gear from rotating with a load from the transmission member side. It is possible to reduce the load placed on the drive device at the time of stopping the vehicle.

  In any one of the game machines C1 to C5, an urging device for generating an urging force for moving the center of gravity of the movable member in both directions of displacement of the movable member is provided above the support portion, the urging force being A game machine C6 characterized in that the center of gravity of the movable member is balanced in the displacement direction in the inverted state where the center of gravity of the movable member is disposed vertically above the support portion, and the movable member becomes larger as it is displaced from the inverted state.

  According to the gaming machine C6, in any one of the gaming machines C1 to C5, the biasing device generates a biasing force for moving the center of gravity of the movable member above the support portion, and the biasing force is that the center of gravity of the movable member is It becomes so large that a movable member displaces from the state (inverted state) arrange | positioned vertically above a support part. That is, the biasing force can be minimized in the inverted state.

  Therefore, by increasing the biasing force when the movable member moves upward from the predetermined position, the load on the driving device for moving the movable member upward from the state in which the movable member is disposed at the predetermined position can be reduced.

  Also, the biasing force is generated in both directions of the displacement direction of the movable member, and balanced in the displacement direction in the inverted state. Therefore, when the movable member is moved upward from the predetermined position and the drive device is controlled to stop, the posture of the movable member is inverted by the biasing force even when the movable member does not reach the inverted state or passes by the inverted state. It can be turned to This makes it easy to stop the movable member in the inverted state.

  In the gaming machine C6, the movable member can form a first state until the center of gravity is displaced by a predetermined amount from above the support portion by a predetermined amount, and a second state displaced by the predetermined amount or more. A game machine C7 characterized in that the rate of change in biasing force in the case of the same displacement is larger in the second state than in the one state.

  According to the gaming machine C7, in addition to the effects of the gaming machine C6, the movable member is larger than the predetermined amount from the inverted state than in the first state on the inverted state where the center of gravity of the movable member is disposed vertically above the support portion. In the second state to be displaced, the rate of change of the biasing force in the case of the same displacement is larger. In this case, when starting the movable member from the state where the movable member is disposed in the second state, it is possible to suppress the load at the time of starting the drive device. In addition, since the acceleration of the movable member can be reduced when the movable member is disposed near the inverted state, it is easy to stop the movable member in the inverted state.

<An example of a technical idea in which the spring constant of the torsion spring 650 changes in the middle of swinging>
A movable member movable between a first position and a second position, a drive device for generating a driving force for moving the movable member, and an urging force for returning the movable member to the first position In the gaming machine provided with an urging device for generating the movable member, the movable member is movable relative to a change ratio of the urging force generated when the movable member is disposed in the first urging region from the first position to the predetermined position. The rate of change of the biasing force generated when the member is disposed in the second biasing region which is a region connected to the first biasing region and is formed apart from the first position is formed large A game machine D1 characterized by

  Here, in a gaming machine such as a pachinko machine, there is a gaming machine using an urging force by an urging device such as an elastic spring as an assisting force when moving a movable member by a driving force generated by a driving device (e.g. See -120640)). However, in the above-described conventional gaming machine, the biasing force of the biasing device is proportionally increased by the displacement amount of the movable member, and it is difficult to change the purpose of the biasing device by the arrangement of the movable member. There was a problem that it was. That is, it has been difficult to make the movement of the movable member flexible by suppressing the urging force in a certain area, and to make the movement of the movable member sharper by improving the urging force in another area.

  On the other hand, according to the gaming machine D1, the change ratio of the biasing force biased toward the first position indicates that the movable member has the second change ratio compared to the case where the movable member is disposed in the first bias region. The case where it is arranged in the pressure area is made larger. That is, for example, when the movable member stopped at the second position is started to the first position (the second urging region), a sufficient biasing force can be obtained by the biasing device, while the movable member is the first When the movable member is disposed in the urging region, the change in the urging force is suppressed, and the operation of the movable member can be made flexible (slowly).

  As a mode in which the rate of change of the biasing force of the biasing device is changed by the arrangement of the movable member, the number of biasing devices that cause the movable member to generate a biasing amount may increase during the process. The case where it is formed from an elastic spring and the spring constant of an elastic spring is changed by arrangement of a movable member etc. is illustrated.

  In the gaming machine D1, the biasing device is a pair of elongated members which are disposed on a pair of surfaces which intersect the moving direction of the movable member and sandwich the movable member in the moving direction, one end of which is one end And the other end, which is an end opposite to the one end, is formed of an elastic spring whose movement is suppressed, the movable member being A main body portion sandwiched between a pair of elongated members, and an opposite side of the main body portion with respect to the pair of elongated members, and at least one of the pair of elongated members in the moving direction of the main body portion And a contact portion formed to be contactable, wherein the contact portion is connected and fixed to the movable member, and when the movable member is disposed in the first biasing region, the movable member is a pair of the pair Of the movable member among the long members The movable member is brought into contact with one of the long members on the side where the distance to the movable member is short and is given an urging force, and the movable member is brought into contact with the other long member and the contact portion to be urged. A gaming machine D2 characterized by being given.

  According to the gaming machine D2, in addition to the effects of the gaming machine D1, the change timing of the changing ratio of the biasing force by the biasing device is shifted for each long member the contact timing of the movable member and the pair of long members. Can be formed by Therefore, it is unnecessary to change the biasing force of the biasing device by control or to prepare a separate member for improving the biasing force.

  That is, since the other end of the pair of long members is restricted in movement, one long member on the side where the distance to the movable member becomes short due to the movement of the movable member is pressed against the movable member and moves. The other long member on the opposite side receives no force from the movable member. Therefore, in the first biasing region, when the movable member moves, the other long member disposed on the opposite side of the moving direction of the movable member stays in place.

  On the other hand, in the second biasing region, the movable member is moved, whereby the other long member is in contact with the contact portion. As a result, the biasing force is also generated from the other long member. Therefore, the biasing force applied to the movable member in the second biasing region can be increased.

  In addition, a coil spring, a torsion spring, a leaf spring etc. are illustrated as an elastic spring.

  In the gaming machine D1 or D2, the biasing device is a pair of elongated members which are disposed on a pair of surfaces which intersect the moving direction of the movable member and sandwich the movable member in the moving direction, The other end of each of the two ends of the movable member is disposed opposite to the both side surfaces of the movable member, and the other end which is the opposite end of the one end is formed of an elastic spring whose movement is suppressed. A body portion sandwiched between the pair of elongated members, and at least one of the pair of elongated members formed on the opposite side of the body portion with respect to the pair of elongated members in the moving direction of the body portion And a contact portion formed to be contactable, the contact portion being connected and fixed to the movable member, and the movable member being disposed in the first biasing region, the movable member being Of the pair of elongated members, the movable member When the movable member is placed in the second urging region while being abutted against one long member on the side where the distance to the movable member is reduced by movement and the movable member is placed in the second biasing region, the one long member The game machine D3 characterized in that the middle part of the above is pressed against the contact part arranged on one long member side with respect to the main body part.

  According to the gaming machine D3, in addition to the effects of the gaming machine D1 or D2, the change ratio of the biasing force is formed by pressing the middle part of one long member against the contact part. That is, the change ratio of the biasing force is changed by further deforming one long member already deformed by the movement of the movable member starting from the middle portion pressed against the contact portion. Here, in the deformation starting from the intermediate portion, the length of the portion subjected to the deformation becomes shorter compared to the deformation starting from the other end portion, so the ratio of the change of the biasing force to the moving amount of the movable member is Increase. Thereby, in the second biasing region, it is possible to increase the change of the biasing force with respect to the moving amount of the movable member. Therefore, the change ratio of the biasing force can be increased.

  In the gaming machine D3, the one long member includes a first bending point bent toward the opposingly disposed contact portion, and the one long member is the first bending point at the first bending point. A game machine D4 characterized in that it is pressed against the contact portion.

  According to the gaming machine D4, in addition to the effects of the gaming machine D3, one long member is in contact with the abutting portion disposed oppositely at the first bending point, so one long member is in contact It is stretched by contact with the part. Therefore, the tip end portion of the biasing device that applies the biasing force to the movable member can be separated from the other end portion of the long member serving as the starting point of the biasing force and the first bending point. Therefore, the moment the movable member is loaded from the biasing device in the second biasing region can be made larger.

  In the gaming machine D4, the movable member includes a tip enlargement area which is enlarged in the moving direction as it moves away from the other end of the long member, and one of the movable member and the long member is enlarged in the tip enlargement region. A game machine D5 characterized in that the end of the game machine is abutted.

  According to the gaming machine D5, in addition to the effects of the gaming machine D4, the movable member has a tip enlargement area, and the movable member and one end of the elongated member abut in the tip enlargement area. Therefore, when one long member is stretched by pressing one long member against the contact portion, the contact position between the movable member and the long member separates from the other end of the long member. As it is moved in the direction, the amount of deformation of the elongated member is increased. Therefore, the biasing force applied to the movable member from the biasing device can be increased.

  In any one of the game machines D2 to D5, the arrangement interval between the contact portion and the main body portion is changeable.

  According to the gaming machine D6, in addition to the effects produced by any of the gaming machines D2 to D5, it is possible to increase the variation of the change in biasing force generated by the long members. That is, for example, when the arrangement interval between the contact portion and the main body portion is narrowed, the timing at which the rate of change of the biasing force of the long member increases can be set earlier.

<Example of a technical idea in which a plurality of out-ports are provided and the buffer rib 322 is formed on the lower plate 320>
Inside the game area where the ball is formed so as to allow flow-down, the board internal character placed in contact with the lower edge of the game area, and the ball formed on one side in the width direction of the board internal character A first out port, which is an opening for discharging from the area, and a second out port, which is an opening for discharging balls from the game area, formed on the other side in the width direction of the board internal component opposite to the one width direction side In the gaming machine, the first out port and the second out port are provided with a lower plate portion extending from the lower side surface of the opening to the front and having a guiding surface on the upper surface, and the guide of the lower plate portion The surface is provided with a buffer rib extending like a rib toward the opening direction on the corresponding side in the first out port or the second out port, and is formed to be raised from the guide surface in the width direction outer side And the buffer rib has an aspect ratio directed outward in the width direction. Gaming machine E1, characterized in that it is formed smaller.

  Here, in gaming machines such as pachinko machines, there are gaming machines in which a plurality of out-ports are arranged (see, for example, JP-A-9-192301). However, in the above-described conventional gaming machine, it is preferable to reduce the size of each out-port as the number of out-ports increases, because it is possible to secure the installation space for an attacker etc. There was a problem that discharge of the game ball might be overdue.

  For example, when the height at which the ball bounces up and down on the near side of the out-port becomes equal to or more than the vertical width of the out-port, the ball stays in front of the out-port. Also, for example, when the side surface is disposed on the side of the character at the side surface in the width direction of the out port and becomes a wall, the ball flowing from the width direction to the near side of the out port collides with the side surface of the character and rebounds in the width direction. At this time, when the amount of rebounding in the width direction becomes equal to or more than the width of the out port, the ball stays in front of the out port.

  On the other hand, according to the gaming machine E1, since the buffer rib is formed on the guide surface formed in the lower plate portion, it is possible to suppress the bounce of the ball or to decelerate the ball. That is, when the ball collides in the vertical direction, the buffer rib becomes a cushion by bending deformation of the buffer rib, and it is possible to suppress ball rebound. In addition, when the ball collides from the left and right direction, the ball is braked by being fitted into the buffer rib.

  Here, the buffer rib extended in the opening direction is weak to the load from the left and right direction, and may be damaged by the collision of the ball from the left and right direction.

  On the other hand, according to the gaming machine E1, since the guide surface is provided with the step portion on the outer side in the width direction, the ball flowing down from the left and right direction toward the buffer rib falls from above the step portion to the buffer rib . In this case, the vertical component of the direction of the collision of the ball with the buffer rib can be increased, and breakage of the buffer rib can be suppressed.

  In addition, since the step portion has a function of stopping the ball moving in the left and right direction on the guide surface, it is possible to prevent the ball moving on the guide surface from bouncing back beyond the width of the out port.

  Since the buffer rib is formed higher toward the center in the width direction of the game area, a large rebound suppressing effect can be obtained near the center in the width direction of the game area where flowing balls are easily concentrated. Thereby, the ball can be discharged smoothly from the out port. Further, by aligning the lower curve of the game area with the lower surface of the buffer rib, the arrangement position of the out port can be corrected downward.

  Here, the higher the height at which the buffer rib is formed, the greater the effect of suppressing ball bounce, because the amount of deflection of the buffer rib is increased. That is, as the amount of deflection of the buffer rib is larger, the cushioning effect works sufficiently, and it is easy to suppress the bounce. Therefore, it is preferable to make the aspect ratio of the buffer rib constant in the left-right direction (to make the length in the vertical direction constant) for the effect of suppressing the rebound.

  On the other hand, when the aspect ratio of the buffer rib is made constant (the length in the longitudinal direction is made constant), it is necessary to increase the height at which the step is formed, and the path of the ball up to the step is also upward As a result, the game area is narrowed, which is not preferable in terms of space efficiency.

  On the other hand, in the gaming machine E1, on the outer side in the width direction of the game area where flowing balls are hard to concentrate, the aspect ratio (longitudinal length) of the buffer rib is reduced, and the width direction center of the game area where flowing balls are easily concentrated In the above, the aspect ratio (longitudinal length) of the buffer rib is increased. Thereby, coexistence with improvement of discharge efficiency of a ball, and securing of a game area can be aimed at.

  In addition, extending in the opening direction is not particularly limited, and means extending in the opening direction in a linear shape, a waveform, a mountain shape, or the like.

  In the gaming machine E1, a gaming surface E2 characterized in that the guide surface includes an outer inclined portion that is inclined downward and outward in the width direction of the gaming area.

  According to the gaming machine E2, in addition to the effects of the gaming machine E1, the guide surface is provided with the outer inclined portion, so that the velocity of the ball flowing into the guide surface from the width direction outside can be decelerated by gravity acceleration. The deceleration time can be shortened.

  In the gaming machine E1 or E2, a non-falling area in which a ball can not flow down is formed obliquely above at least one of the first out port or the second out port.

  According to the gaming machine E3, in addition to the effects of the gaming machine E1 or E2, the flow of the ball flowing obliquely downward from the non-flowing area to the guide surface is restricted, so the flow of the ball to the guide surface The number of paths can be reduced. Therefore, it is possible to narrow the rebounding direction of the falling ball. Thereby, the outer shape of at least one of the first out port or the second out port can be narrowed.

  In the gaming machine E3, an opening / closing device which is disposed in the gaming area and which can be opened and closed to the front side is disposed above at least one of the first out port or the second out port. A game machine E4 formed on the front side of the opening / closing device;

  According to the gaming machine E4, in addition to the effects produced by the gaming machine E3, the non-flowing area is formed by the opening / closing device. Thereby, the space which arises by restrict | limiting the opening dimension of the direction to the non-flow area side of a 1st out port or a 2nd out port can be utilized as an arrangement | positioning space of a switchgear.

  In the closed state, the opening / closing device allows the ball flowing down the front of the opening / closing device to flow downward to the game area, and when the opening state is open, the ball flowing in front of the opening / closing device to the back of the game area Has the ability to drain. Therefore, the non-falling area can be formed more reliably than when the ball flows down irregularly due to collision with a nail or the like.

  In any one of the game machines E1 to E4, a game machine E5 including a direction adjustment rib extended in a rib shape in an opening direction on an upper bottom surface of the first out port or the second out port.

  According to the gaming machine E5, in addition to the effects of any of the gaming machines E1 to E4, the upper bottom surface of the first out port or the second out port is provided with a direction adjusting rib extended in a rib shape in the opening direction. The resistance to the ball flowing down while colliding with the upper bottom surface of the first out port or the second out port can be suppressed.

  A gaming machine F1 according to any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, and E1 to E5, wherein the gaming machine is a slot machine. Among them, as a basic configuration of the slot machine, “a variable display means for dynamically displaying an identification information sequence consisting of a plurality of identification information and subsequently displaying the identification information is provided, and the operation of the starting operation means (for example, operation lever) The dynamic display of the identification information is started as a result, and the dynamic display of the identification information is stopped due to the operation of the stop operation means (stop button) or when the predetermined time elapses. It is a gaming machine provided with a special gaming state generation means for generating a special gaming state advantageous to the player, as a necessary condition that the final identification information of is a specific identification information. In this case, the game medium may be a coin, a medal or the like as a representative example.

  A gaming machine F2 characterized in that the gaming machine is a pachinko gaming machine in any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, E1 to E5. Above all, the basic configuration of a pachinko gaming machine is provided with an operating handle, and in response to the operation of the operating handle, the ball is fired to a predetermined game area, and the ball is at an operating opening arranged at a predetermined position in the game area. As a necessary condition for winning (or passing through the operation opening), identification information dynamically displayed on the display means may be determined and stopped after a predetermined time. In addition, when the special game state occurs, the variable winning device (specific winning opening) disposed at a predetermined position in the gaming area is opened in a predetermined manner to enable the ball to be won, and the value according to the number of winnings There is a case where a value (including not only prize balls but also data etc. written to a magnetic card) is given.

In any one of gaming machines A1 to A6, B1 to B6, C1 to C7, D1 to D6, E1 to E5, the gaming machine is characterized in that a pachinko gaming machine and a slot machine are merged. Machine F3. Among them, as a basic configuration of the integrated gaming machine, "a variable display means for dynamically displaying an identification information sequence consisting of a plurality of identification information and subsequently displaying identification information, and for starting operation means (for example, operation lever) Fluctuation of the identification information is started due to the operation of, and the dynamic display of the identification information is stopped due to the operation of the operation means for stop (for example, the stop button) or when a predetermined time elapses. A special game state generation means for generating a special game state advantageous to the player, provided that the finalized identification information upon stopping is the specific identification information, and using a ball as a game medium and the identification information In order to start the dynamic display of the game, a predetermined number of balls are required, and when a special gaming state occurs, a large number of balls are paid out.
<Others>
In a gaming machine such as a pachinko machine, there is a gaming machine provided with a movable member formed movable and a stopper member for limiting the moving width of the movable member (for example, Patent Document 1: JP 2012-016623A) Gazette).
However, in the above-described conventional gaming machine, there is a problem that there is room for improvement in the aspect of the arrangement of the stopper member.
The present technical concept is made to solve the problems exemplified above, and it is an object of the present invention to provide a good gaming machine in the aspect of the arrangement of the stopper member.
<Means>
In order to achieve this object, the gaming machine of the technical idea 1 is movable along a predetermined movement trajectory, and movable members which can be arranged at different first and second positions, and the movable members thereof The movement width of the predetermined movement trajectory of the movable member is restricted by moving in correspondence with the movable member, and the movable member is arranged at the first position or at the second position. And a stopper member that changes the moving width of the movable member depending on whether it is moved or not.
The gaming machine according to the technical idea 2 is the gaming machine according to the technical idea 1, wherein the movable member is pivotally supported by a first shaft so as to be able to swing and extend and contract in the radial direction of the first shaft. The telescopic length of the intermediate member differs between the first position and the second position, the predetermined movement trajectory is formed in an arc shape centered on the first axis, and the stopper member is The intermediate member is extended along the predetermined movement trajectory of the movable member when the intermediate member is in a predetermined expansion / contraction state.
In the gaming machine according to the technical idea 3, in the gaming machine according to the technical idea 2, the movable member includes a protrusion protruding toward the stopper member, and the protrusion is inserted through the stopper member. The movable member and the stopper member interlocked in the expansion and contraction direction of the intermediate member in a state in which the protrusion is inserted into the insertion portion, and the movable member is abutted against the insertion portion Ru.
<Effect>
According to the gaming machine described in the technical idea 1, the mode of arrangement of the stopper member can be improved.
According to the gaming machine described in the technical idea 2, in addition to the effects of the gaming machine described in the technical idea 1, the aspect of the arrangement of the stopper member can be further improved.
According to the gaming machine described in the technical idea 3, in addition to the effects of the gaming machine described in the technical idea 2, the functions can be integrated into the stopper member.

10 Pachinko machines (game machines)
13 game board 65 1st variable winning a prize device (opening and closing device)
313 Movable effect member (inside board)
314 1st out port 315 2nd out port 315a guide rib (direction adjustment rib)
320 Lower left plate member (lower plate part)
322 Buffer rib 324 step 330 lower right plate member (lower plate)
332 buffer rib 512 first shaft portion (first shaft)
540, 6540 Telescopic effect device (movable member)
541 Body member (part of the middle member)
544 Slide plate (part of the intermediate member)
545 Slide rail (part of the intermediate member)
541b projection 541e guide fastening portion (positioning assistance portion)
550, 5550, 6550 Rotating arm members (arm members, stopper members)
553 Modified long hole (insertion part)
553d Selected Wall (Selected Area)
554 Arc-shaped hole (insertion part)
554a mouth part (groove part)
554b First stopper surface (part of insertion part)
554c Second stopper surface (part of insertion part)
560 Second drive unit (drive unit)
570 Rotating Crank Member (Crank Member)
574 Sliding projection (projection)
610, 7610 Base member 613 first axial support hole (support portion)
614 Second shaft support hole (shaft support)
620, 4620 effect member (movable member)
621a Sliding shaft (protrusion)
630 1st drive (drive)
640, 2640, 3640, 4640, 7640 Transmission member (transmission member, movable member)
641, 2641, 3641 body part 643 sliding hole (insertion part)
644 Contact part 650 Torsion spring (biasing device, elastic spring)
652 Biasing arm (long member)
653a bending part (first bending point)
3641a Inclined side (tip enlargement area)
5556 Recess (outer recess)
7613 Sliding hole (support part)
7643 Shaft support hole (insertion part)
D margin

Claims (3)

Movable members that are movable along a predetermined movement trajectory and can be disposed at different first and second positions;
The movement width of the predetermined movement trajectory of the movable member is restricted by moving corresponding to the movable member and contacting the movable member, and the movable member is disposed at the first position or the second And a stopper member configured to change the moving width of the movable member depending on whether the movable member is disposed at a position.   The movable member includes an intermediate member pivotally supported by a first shaft so as to be swingable and capable of expanding and contracting in the radial direction of the first shaft, and the intermediate member is provided at the first position and the second position. The expansion and contraction lengths are different, the predetermined movement trajectory is formed in an arc shape centered on the first axis, and the stopper member is the movable member in the case where the intermediate member is in a predetermined expansion and contraction state The gaming machine according to claim 1, wherein the gaming machine is extended along a predetermined movement trajectory.   The movable member includes a protrusion protruding toward the stopper member, the stopper member includes an insertion portion through which the protrusion is inserted, and the protrusion is inserted into the insertion portion. 3. The gaming machine according to claim 2, wherein the movable member and the stopper member are interlocked in an expansion and contraction direction of the intermediate member, and the movable member is in contact with the insertion portion.

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