Patent Abstract:
The present invention provides a compact transmission assembly for use in a coin storage and dispensing apparatus. The transmission assembly can connect the rotational output of a reversible electrical motor to a link unit that supports a switching gear unit. A helical gear unit can be mounted adjacent to the link unit and can be driven axially along a shaft to contact a mounting unit to receive a thrust force and to drive the link unit in a clockwise or counter-clockwise direction depending upon the rotation of the reversible motor. The switching gear unit is radially mounted at an offset position on the link unit and can appropriately contact output gears connected to output shafts for providing a selective dual power output.

Full Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention is directed to an improved compact transmission mechanism for driving a pair of output shafts by a reversible motor in a coin dispensing apparatus and more particularly to a simplified and economical switching gear mechanism that automatically responds to the output of a reversible electric motor. 
     2. Description of the Related Art 
     The present invention is directed to improvements in vending machine equipment wherein maintenance and costs are important factors. Vending machine equipment has been required to become more compact while still being required to handle the dispensing of coins and tokens for change or jackpots in gaming machines. 
     Generally, a coin hopper has components driven by a motor through a gear transmission system so that the motor can rotate in a clockwise direction and a counter-clockwise direction. Coin hopper equipment is usually driven to output coins from a bulk hopper. In a large capacity hopper equipment that is suitable, for example, in gambling and gaming machines, a large number of medallions or coins are stored and dispensed. As used in this application, the terminology “coin” includes not only coins of a monetary currency, but also can include medallions, disc-like medals, tokens, etc. 
     An example of a large capacity coin hopper can be found in the laid open Japanese Patent Application No. 11-251,652. Referring to FIG. 9, a perspective view of the hopper equipment is disclosed. A cross-sectional view of the motor drive transmission assembly is shown in FIG. 9. A rectangular support or baseboard  4  extends in a vertical installation position and is supported by a pair of support frames  3 . On one surface of the baseboard  4 , a primary tank  1  for coin storage having a cylindrical shape is disclosed. Attached to this primary tank  1  is a larger capacity slanted or angled barrel case  10  with a secondary tank of a large pot like configuration having an opening  5  for receiving bulk coins. As can be readily determined, the primary tank  1 , the intermediate case member  10  and the secondary tank  2  can store a large number of coins in bulk quantity. Within the primary tank  1 , a deep plate-like dispensing disc  50  as shown in FIG. 10 is capable of contacting and releasing coins in a controlled manner. The deep plate-like disc is mounted for free rotation. 
     Mounted within the intermediate case member  10  is a flexible belt  14  with teeth or projections  15  that can be utilized for elevating the coins from the secondary storage tank  2  and dropping the coins into the deep plate-like disc  50 . Thus, rotation of the belt  14  can distribute the coins to the primary tank I and as is conventionally known, the disc  50  or other structure can interact with the coins and selectively dispense the coins one by one. 
     To provide the rotational movement, a gear case  41  is fixed on the back surface of the baseboard  4  as can be seen in FIG.  10 . An electric motor  40  can be appended from the gear case  41  so that the electric motor  40  can drive a small pinion gear  44  which is fixed to a shaft of the electric motor  40 . The cross-section view of this gear arrangement is seen in FIG.  10 . The pinion gear  44  can in turn mesh with a larger gear  45 . The gear  45  is freely mounted within bearings to rotate. An output gear  46  further meshes with the large gear  45  and is also mounted for free rotation. Attached to this output gear  46  is a primary clutch member  47  and a secondary clutch member  48 . The primary clutch member  47  can rotate the primary output shaft  42  when the electric motor  40  is rotated in a first positive direction. In this rotation, the primary output shaft  42  is coupled to a disc  50  for sending out the coins in the primary tank  1 . The secondary clutch member  48  rotates a secondary output shaft  43  when the electric motor  40  is driven in a reverse direction. The secondary output shaft  43  is in turn coupled to a belt  31 , see FIG. 9, by an intervening driving of the pulley  38 , the belt  37 , the pulley  36  shown in FIG. 9, and the shaft  34 . This belt  31 , while not shown, is coupled to the belt  14  for driving the coins in the case  10 . 
     In summary, the disc  50 , for picking up and sending the coins in a controlled manner, is rotated by the action of the primary clutch  47  when the electric motor  40  is rotated in a positive direction. At this time, the belt  14  for coin carrying is stopped by the action of the second clutch  48 . When, however, the electric motor  40  is reversed, the second output shaft  43  is rotated by the action of the second clutch  48 . As a result of this drive, the belt  31  is activated. During this activation, the disc  50  is not rotated by the action of the primary clutch  47 . Thus, in this disclosure, either the disc  50  is rotated or the belt  14  is rotated in a selective manner, depending upon the direction of rotation of the electric motor  40 . 
     As can be seen from FIG. 10, this arrangement requires a number of components and increases the size requirements of the coin dispenser. Additionally, since a pair of one-way clutches are utilized, there is always the possibility that inertia forces may jar and cause wear and vibration when the motor is reversed. 
     SUMMARY OF THE INVENTION 
     The present invention was developed in order to simplify transmission switching gear arrangement for dealing with a reversible motor. The present invention was also designed to decrease the number of parts and to simplify the transmission switching gear equipment. Additionally, the present invention was designed to absorb any reaction forces by a sudden stopping or reversing of the motor. The present invention was also designed to provide a relatively uncomplicated activation of one of two output shafts that can be automatically determined by a positive-reverse switching cycle relating to the direction of rotation of the motor. 
     The present invention provides a transmission assembly in a coin handling apparatus that can automatically activate one of two output shafts. A primarily stepped gear, which is freely mounted on a fixed shaft, includes a helical gear meshing with an output pinion of an electric motor. A spur gear is coaxially mounted on the shaft. A link unit comprising a pair of elongated movable boards or link members sandwich the primary step gear and are rotatable about the fixed shaft. Radially outward from the fixed shaft is a transfer shaft that extends between the respective link members and a second step gear is freely rotatably mounted on the transfer shaft and includes a switching gear that meshes with a coaxial spur gear. The spur gear can mesh with respective output shaft gears to respectively drive the desired output shafts. Positioned between the movable boards or link members and the primary step gear are elastic members such as spring like ring members to provide a frictional force between the primary step gear and the respective link members. Depending upon the rotation of the output shaft of the electric motor, the pinion gear will drive the helical gear to move upward or downward axially relative to the fixed shaft  23 . When driven upward, it will cause a frictional engagement through an elastic spring member to drive the upper link member to rotate in a specific direction, thereby bringing the switching gear into engagement with a gear train to drive one of the output shafts. Conversely, a reverse driving of the pinion gear will drive the helical gear shaft downward to engage the lower elastic spring member to frictionally move the lower link member and rotate the large switching gear in the other direction to engage a transmission gear assembly to drive the other output shaft. As can be appreciated, the spring mounting can absorb some of the thrust forces that can occur upon a reversing of the electric motor. 
     As can be further determined, the number of parts and components utilized are substantially less than the conventional transmission mechanisms that have heretofore been used. 
     In summary, the present invention can be utilized in a coin storage and dispensing apparatus for storing coins in bulk wherein a reversible electrical motor can provide a driving force for transporting coins and also dispensing coins from a dispensing member. The present invention includes a transmission assembly of a compact configuration connected to the rotational output of the reversible electrical motor. A first supporting member or fixed shaft can rotatably mount a link unit. The link unit can include a first link member and a second link member that are rotatably mounted about the first support member. A first gear unit is mounted adjacent to the link unit and is operatively connected to the rotational output of the reversible motor. The first gear unit can be a stepped helical gear that can mesh with a helical pinion gear connected to an output shaft of the reversible electrical motor. A mounting unit is positioned to operatively contact the first gear unit and to rotate the link unit about the first support member depending upon the direction and rotation of the reversible electrical motor. The mounting unit can comprise a pair of spring plates or flexible bearing members that are mounted on either side of the first gear unit adjacent the first and second link members, respectively. The first gear unit can be driven to axially move along the support member and apply a thrust force to the mounting unit. Depending upon the direction of rotation of the reversible electrical motor, the link unit can rotate about the first support member in a clockwise or counter-clockwise direction. Radially offset from the first support member is a switching gear unit that can be mounted on a transfer support member extending between the first and second link members. The switching gear unit can be a stepped gear unit and it can be operatively connected to the first gear unit so that it provides a driving force at two separate positions about the first support member depending upon the direction of rotation of the reversible motor. The switching gear unit can include a spur gear that can intermesh with one of two output gears that are connected respectively to output shafts. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The exact nature of this invention will be readily apparent from consideration of the following detailed description in conjunction with the accompanying drawings, wherein: 
     FIG. 1 is a perspective view of the electric motor and compact transmission mechanism for providing a pair of output shafts; 
     FIG. 2 is a side elevational view of FIG. 1 disclosing an output shaft on either side of the housing of the transmission mechanism; 
     FIGS. 3 a  and  3   b  are partial cross-sectional views of a switching gear mechanism contained within the transmission assembly; 
     FIGS. 4 a  and  4   b  are respectively a schematic bottom view and a partial cross-sectional view of the transmission assembly; 
     FIGS. 5 a  and  5   b  are respectively cross-sectionals views with certain elements missing on FIG. 4 for explanatory purposes; 
     FIGS. 6 a  and  6   b  are respectively bottom views of FIG. 2 with certain elements removed for explanatory purposes; 
     FIGS. 7 a  and  7   b  are respectively cross-sectional views of a portion of FIG. 6 with certain elements omitted for explanatory purposes; 
     FIGS. 8 a  and  8   b  are explanatory views for disclosing the switching operation of the transmission mechanism; 
     FIG. 9 is a perspective view of a conventional coin hopper equipment; and 
     FIG. 10 is a cross-sectional view of a portion of FIG.  9 . 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     The following description is provided to enable any person skilled in the art to make and use the invention and sets forth the best modes contemplated by the inventor of carrying out his invention. Various modifications, however, will remain readily apparent to those skilled in the art, since the general principles of the present invention have been defined herein to specifically provide a compact transmission of power that is automatically switchable to a coin dispenser. 
     The drawings disclosing the features of the present invention are illustrative only and not necessarily drawn to scale. Referring to FIG. 1, a perspective view of a compact gear box or transmission assembly including a housing that is split to have an upper casing member  1  and a lower casing member  2  is disclosed. The gear box, and more particularly the lower casing member  2  is mounted on a flange  9  attached to one end of the electric motor  10 . As can be seen in FIG. 1, the transmission assembly is relatively compact and provides an upper output shaft  20  and a lower output shaft  30 . The electric motor  10  that extends downward from the flange  9  can be of a direct current type and is reversible so that there is a positive rotation, for example, in a clockwise direction and a reverse rotation in a counter clockwise direction. As can be appreciated, as with a conventional hopper arrangement, the electric motor and transmission assembly can be appropriately mounted and suspended from the frame of a coin hopper for appropriately driving the coin hopper and components therein. Referring to FIG. 2, a side elevated view of the perspective view of FIG. 1 is disclosed. 
     Referring to FIGS. 3 a  and  3   b , the driving shaft of the electric motor  10  is connected to a small helical pinion gear  11  that is mounted between the upper case member  1  and the lower case member  2  within the gear box. See for example, FIGS. 5 a  and  5   b . Referring again to FIG. 1, the cylindrical output shaft  20 , which is shown at the right-hand portion of FIG. 1, is the primary output shaft of the gear transmission assembly. This primary output shaft  20  can rotate an internal disc (not shown) for selectively sending out coins in the hopper equipment. The disclosure of U.S. Pat. No. 5,984,771 is incorporated herein by reference to supplement the present disclosure. Fixed at the inner end of the primary output shaft  20  is a large output gear  21  as shown in FIG.  4 . Also shown in FIG. 1 at the left-hand side is a second output shaft  30 . This second output shaft  30  can drive a belt (not shown) for picking up and agitating coins within the hopper equipment so that coins could be translated from the open hopper through an intermediate casing member to the coin selecting disc. As shown in FIGS. 4 a  and  4   b , a large output gear  31  is fixed to an inner end of the second output shaft  30  within the transmission casings  1  and  2 . 
     Referring to FIGS. 3 a  and  3   b , a switching gear mechanism is positioned within the transmission assembly between the primary output shaft  20  and the secondary output shaft  30 . 
     The switching gear mechanism has a fixed shaft or first support member  23  that extends between the top and bottom case members  1  and  2 . Freely rotated at either end of this fixed shaft member is a link unit comprising in one embodiment a pair of elongated movable board members or link members  25  and  27 . Also journaled for free rotation about the fixed shaft  23  between the movable boards  25  and  27  is a large helical gear  33  that can move along the axial direction of the shaft  23 . Additionally, a smaller spur gear  35  is coaxially mounted on the upper side of the gear  33  and with the gear  33  forms a primary stepped gear arrangement. A set of resilient bearing members such as plate springs  37 , having a relatively strong elastic or spring force are positioned between respectively the movable board or link member  25  and the spur gear and helical gear  33  and act as switch members to form a mounting unit. 
     As also can be seen, the plate springs  37  are arranged between the lower movable board or link member  27  and the helical gear  33 . Radially outward from the fixed shaft  23  is a transfer shaft  51  that is fixed adjacent to the end of each of the movable board members  25  and  27 . Mounted about the transfer shaft  51  between the movable boards or link members  25  and  27  is a large switching gear  53  that can be freely rotated and is movable in the axial line of direction of the transfer shaft  51 . This switching gear  53  further engages with a small spur gear  35  that is mounted on the fixed shaft  23 . Thus, when the pinion gear  11  drives the helical gear  33 , the spur gear  35  will drive the switching gear  53 . In addition, a small spur gear  55  is formed at one side of the switching gear  53  so that the large switching gear  53  and the small spur gear  55  provide a second step gear arrangement. The plate springs  57  which are mounted between the lower movable board of link member  27  and the spur gear  55  have a relatively weak elastic or resilient force. Likewise, the upper plate spring  57  that is mounted between a flange on the transfer shaft  51  and the switching gear  53  or spur gear  55  also has a relatively weak elastic or resilient force. 
     Referring to FIGS. 5 a  and  5   b , and FIGS. 7 a  and  7   b , the relative rotation of the transfer gear  53  in a clockwise and counter-clockwise direction is disclosed. 
     Referring to FIG. 8, a pivotable stop member or link arm  61  rotates about a hinge or support post  63  on the top case member  1 . This roughly U-shaped link  61  can act as a stopper or brake for the primary output shaft  20 . A spring  65  is arranged so that a portion of the stopper  61  may engage with a primary output gear  21  as shown in FIG.  6 . Additionally, the tip of the stopper  61  can freely contact the movable board or link member  25 . 
     In operation, the helical gear  33  can be rotated for example in a counter-clockwise direction when the electric motor  10  is rotated in the manner disclosed in FIG. 5 a . When the helical gear  33  is rotated by the pinion  11  in the counter-clockwise direction, the gear  33  will receive a force along its axial line direction, that is, the helical gear  33  which is rotated by the pinion  11  will receive the thrust so that the helical gear  33  will press the movable board  27  against the plate springs  37 . As a result, the movable board  27  will be moved in the counter-clockwise direction receiving a turning force of the helical gear  33  as can be seen in FIG. 4 b . Thus, when the helical gear  33  is rotated in this manner, the movable boards or link members  25  and  27  are moved in the counter-clockwise direction as a result of the compression of the appropriate set of plate springs  37 . The radially outboard transfer shaft  51  is then moved in the counter-clockwise direction so that the spur gear  55  will engage with the primary output gear  21  as can be seen in FIG. 5 a . In this condition, the counter-clockwise turning force of the helical gear  33  is transmitted to the switching gear  53  as shown in FIG. 5 b . Then, the turning force of the helical gear  33  is transmitted to the primary output gear  21  through the existing contact with the switching gear  53  and the spur gear  55  as shown in FIG. 5 a . At this time, the primary output gear  21  can be placed into a free or nondriven condition as the movable board  27  and movable board  25  are moved in the counter-clockwise direction as shown in FIG. 8 a . That is to say, the stopper  61  can separate from the primary output gear  21 . 
     When the electric motor  10  is reversed, the helical gear  33  is rotated in the clockwise direction, for example, as shown in FIG. 7 a . When the helical gear  33  is rotated in a clockwise direction by the pinion gear  11 , the gear  33  will receive a thrust force along the axial line direction. As a result of this thrust force, the helical gear  33  will press the movable board  25 , for example, against the force of the plate spring  37 . Upon receiving the thrust or turning force of the helical gear  33 , the movable board or link  25  will be moved in the clockwise direction as shown in FIG. 8 b . Thus, when helical gear  33  is rotated in a clockwise direction, the respective movable boards or link members  25  and  27  are also moved in the clockwise direction against the force of the plate spring  37 . As a result, the transfer shaft  51  is also moved in a clockwise direction and the spur gear  55  will engage the second output gear  31  as shown in FIG. 7 a.    
     In this condition, the clockwise rotation of the helical gear  33  is transmitted to the switching gear  53  and the existing gear  35  as shown in FIG. 7 b  when the rotation of the helical gear  33  is transmitted to the second output gear  31  through the switching gear  53  and the spur gear  55  as shown in FIG. 7 a . Additionally, at this time, the stopper  61  becomes in a free condition since the movable board or link member  25  is moved in the clockwise direction as can be seen in FIG. 8 b . Therefore, as a result of the action of the spring  65 , a part of the stopper  61  will mesh with the primary output gear  21  and thereby will act as a braking member to prevent gear  21  from being rotated. See, for example, FIG.  6 . 
     While not shown, a second similar stopper can also mesh freely with the second output gear  31 . In this case, the second output gear  31  becomes in a free condition when the movable board or link member  25  is moved in the clockwise direction. Thus, the second stopper can be placed in a free condition when the movable board or link member  25  is moved in the counter-clockwise direction. As a result of a spring (not shown), a part of the second stopper can mesh with the second output gear  31  and thus brake or hold the gear  31  from rotating. 
     It should be understood that each of the plate springs  37  can also be alternatively provided with a friction material to transmit the thrust of the helical gear  33  to each of the movable board or link members  25  and  27 . In the preferred embodiment, each of the plate springs  37  may be of a ring shaped spring and washer member and each of the plate springs  57  between the second step gear and the movable board or link members  25  and  27  can be expressed as a load member which is arranged properly. When the load member such as plate springs  57  are arranged, the thrust of the primary step gear is smoothly transmitted to each of the respective movable boards or link members  25  and  27 . 
     Thus, wherein a load is applied to the second step gear, the thrust of the primary step gear can be smoothly transmitted to the movable boards  25  and  27 . As can be appreciated, it is an advantage to permit the plate springs  27  to be made in a ring-type configuration such as a spring and washer or file plate. 
     In the preferred embodiment, the pinion gear  11  and the gear  33  were designed to be helical. However, it is possible that the pinion gear  11  and the gear  33  may be gears which generate thrust when they are rotated. 
     In the present invention, the large gear  33  with a helical tooth engaging the small pinion gear  11  with a helical tooth arrangement can be utilized as a driving force. Therefore, the repeated operations of positive rotation, stop and reverse operations and subsequent stopping of the electric motor can be surely transmitted to the output gears  21  and  31  while absorbing any inertia forces that would be imposed on the output gears  21  and  31  as a result of the axial movement and the elastic spring members. 
     As can be readily appreciated, this relatively simple construction permits an improved performance with a minimum of parts to thereby permit a relatively compact transmission gear assembly for use with a reversible electrical motor. The relative selection or choice of the output shafts can be easily performed by the automatic swing mechanism that is simply activated by the appropriate rotation of the electric motor. The present invention therefore can simply switch the rotating shafts from a hopper disc to a handler belt by a simple switching of the rotational direction of the electric motor. 
     In each of the above embodiments, the different positions and structures of the present invention are described separately in each of the embodiments. However, it is the full intention of the inventor of the present invention that the separate aspects of each embodiment described herein may be combined with the other embodiments described herein. Those skilled in the art will appreciate that adaptations and modifications of the just-described preferred embodiment can be configured without departing from the scope and spirit of the invention. Therefore, it is to be understood that, within the scope of the appended claims, the invention may be practiced other than as specifically described herein.

Technology Classification (CPC): 8