JP2014178013A - Torque limiter mechanism, overlapping detection mechanism using torque limiter mechanism and automatic transaction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrict a reduction of brake force for limiting a rotational torque of a shaft member.SOLUTION: There are provided a non-circular rotating member 11 rotated as a shaft 7 rotates, an abutting member 12 abutted against the outer peripheral surface of the rotating member and a biasing member 13 biasing the abutting member in a direction in which it is abutted against the outer peripheral surface of the rotating member. The abutting member intermittently limits the rotational torque of the shaft by abutting the abutting surface against the outer peripheral surface of the rotating member as the shaft rotates. It is preferable that the rotating member is formed such that a distance between the two sides where a plane passing through the rotating central axis and the outer peripheral surface cross to each other is applied as an outer diameter and its sectional shape becomes a non-circular shape around the central axis, and thereby it is divided into a maximum diameter part where the outer diameter value becomes maximum and a small diameter part where the outer diameter value becomes smaller than the maximum diameter part.

Description

  The present invention relates to a torque limiter mechanism that limits rotational torque of a shaft body, a heavy running detection mechanism that uses the torque limiter mechanism, and an automatic transaction apparatus.

  Conventionally, among various devices that transport a medium along a transport path, there is a device having a heavy running detection mechanism that detects heavy running of a medium (see, for example, Patent Document 1).

  One example is an automatic transaction apparatus installed in a financial institution, a distribution institution, or the like. An automatic transaction apparatus detects heavy running of a medium by a heavy running detection mechanism, when conveying various media, such as a bankbook, a form, a banknote, etc. along a conveyance path, for example. Note that “heavy running” means a state in which a plurality of media are traveling simultaneously on a conveyance path in a state where they overlap each other.

  For example, when a customer puts a plurality of media (especially a bankbook) into the insertion slot of a device in a state where they are mistakenly stacked, the automatic transaction device detects whether or not the medium has run heavy by a heavy run detection mechanism near the insertion slot. Detect. Then, when the heavy running of the medium is detected by the heavy running detection mechanism, the automatic transaction apparatus returns the medium to the insertion slot without taking the medium into the apparatus. As a result, the automatic transaction apparatus prevents a plurality of media erroneously input by the customer from being taken into the apparatus.

  In addition, for example, when an automatic transaction apparatus discharges a medium stored in a storage unit inside the apparatus to the outside of the apparatus, the automatic transaction apparatus detects the presence or absence of a medium overrun by a heavy-run detection mechanism near the outlet of the storage unit. . Then, when the heavy running of the medium is detected by the heavy running detection mechanism, the automatic transaction apparatus returns the medium to the original storage unit without discharging the medium to the outside of the apparatus. Or an automatic transaction apparatus isolate | separates each medium, conveys to the predetermined | prescribed storage part different from the original storage part in the state, and accommodates in the storage part. Thereby, an automatic transaction device prevents that a plurality of media are conveyed on a conveyance path in the state where it overlapped.

  The heavy running detection mechanism includes, for example, a position shifting mechanism that shifts at least one medium position when a plurality of media are running heavy, and a medium detection sensor that detects the presence or absence of the medium at positions before and after the position shifting mechanism. Based on the detection result of the medium detection sensor, it is calculated whether or not the length of the medium is changed at the position before and after the position shifting mechanism, and whether the medium is overrun based on the presence or absence of the change. And a determination unit for determining whether or not.

  The position shifting mechanism is configured such that, for example, one or a plurality of sets of driving-side transport rollers and driven-side transport are configured via a transport path so that one pair is configured by two transport rollers on the driving side and the driven side. The rollers are arranged opposite to each other, and a torque limiter mechanism is attached to the rotation shaft of the driven conveyance roller so that the rotation of the driven conveyance roller is braked by the torque limiter mechanism. Thus, the position shifting mechanism shifts the position of the medium by making the driving-side transport roller and the driven-side transport roller differential.

  The position shifting mechanism may be configured to brake the rotation of the separation roller by the torque limiter mechanism when the separation roller for separating the medium is provided separately from the driven conveyance roller. .

  The torque limiter mechanism includes a cylindrical drum and a pad disposed around the drum. In the torque limiter mechanism, the drum rotates with the rotation of the shaft body by attaching the drum to the shaft body (for example, the rotation shaft of the driven conveyance roller or the rotation shaft of the separation roller). The torque limiter mechanism limits the rotational torque (braking torque) of the shaft using the frictional force generated by pressing the pad against the cylindrical drum as a braking force.

  Such a heavy run detection mechanism performs a process of shifting the position of the medium by the position shifting mechanism when the medium is transported along the transport path. Specifically, when the medium is transported along the transport path by the driving-side transport roller, the heavy-running detection mechanism brakes the rotation of the driven-side transport roller by the torque limiter mechanism.

  As a result, the medium is conveyed while receiving different forces (a driving force by the driving-side conveying roller and a braking force by the driven-side conveying roller) from the driving-side conveying roller and the driven-side conveying roller. At this time, if a plurality of media are running heavily, the media are separated from each other and their positions are shifted. When the medium is shifted, the entire length of the medium remains the same as the original length of the medium when the medium is not overrun. On the other hand, the total length of the medium is longer than the original length of the medium when the medium is overrun. Become.

  Therefore, the heavy running detection mechanism detects the presence or absence of the medium at positions before and after the position shift mechanism by the medium detection sensor, and further determines the length of the medium based on the detection result of the medium detection sensor by the determination unit. It is calculated whether or not there is a change in the position before and after the shifting mechanism, and it is determined whether or not the medium is overrun based on the presence or absence of the change.

  The heavy running detection mechanism determines that the medium is not overrun when it is determined that the length of the medium does not change at the position before and after the position shifting mechanism, while the length of the medium shifts. When it is determined that the position has changed at the positions before and after the mechanism, it is determined that the medium is running heavily.

  The automatic transaction apparatus supports a driven-side conveyance roller so as to be movable in the vertical direction by a support member, and presses the driven-side conveyance roller against the driving-side conveyance roller by a spring. In the automatic transaction apparatus, when the medium travels between the driving-side conveying roller and the driven-side conveying roller, the driven-side conveying roller moves downward according to the thickness of the medium by the action of the spring. It is configured.

  In the automatic transaction apparatus, when the medium is not overrun, slip occurs between the medium and the transport roller on the driven side, and the surface of the medium becomes dirty (that is, slip marks are formed on the surface of the medium). In order to prevent this, the force relationship of the torque limiter mechanism is “friction force between the medium and the driven roller on the driven side”> “brake force of the torque limiter mechanism”> “friction force between the media” It is set to power relationship.

JP 2003-312895 A

  A conventional torque limiter mechanism is configured to limit the rotational torque of a shaft body by using a frictional force generated by pressing a pad against a cylindrical drum as a braking force.

  However, when the conventional torque limiter mechanism is used in various usage environments, the brake force that limits the rotational torque of the shaft body decreases due to wear of the surface of the pad and drum when the operating years become long. There was a problem that there was.

  The present invention has been made to solve the above-described problem, and includes a torque limiter mechanism that suppresses a decrease in braking force that limits the rotational torque of the shaft body, a heavy-running detection mechanism that uses the torque limiter mechanism, and The main purpose is to provide an automatic transaction apparatus.

  In order to achieve the above object, a first invention is a torque limiter mechanism for limiting a rotational torque of a shaft body, wherein the rotary member rotates in accordance with the rotation of the shaft body, and the rotation member An abutting member that abuts on the outer peripheral surface of the rotating member, and a biasing member that urges the abutting member in a direction in which the abutting member abuts on the outer peripheral surface of the rotating member. With the rotation, the abutment surface abuts on the outer peripheral surface of the rotating member, so that the rotational torque of the shaft body is intermittently limited.

  A conventional torque limiter mechanism is configured to press a pad against a cylindrical drum. Therefore, in the conventional torque limiter mechanism, the frictional force generated between the pad and the drum does not fluctuate. The conventional torque limiter mechanism continuously limits the rotational torque of the shaft body by using the non-fluctuating frictional force as a braking force.

  On the other hand, in the torque limiter mechanism according to the first invention, the rotating member is formed in a non-circular shape. Therefore, in this torque limiter mechanism, the contact member swings as the shaft body rotates.

  This torque limiter mechanism uses a balance between the pressing force of the urging member and the force that the outer peripheral surface of the rotating member pushes the abutting surface of the abutting member against the pressing of the urging member as a braking force.

  The balance of the force varies periodically with the rotation of the rotating member. Therefore, the torque limiter mechanism can intermittently limit the rotational torque of the shaft body by using the balance of periodically varying forces as a braking force.

  This torque limiter mechanism does not rely on a simple frictional force (a non-fluctuating frictional force as in the conventional torque limiter mechanism) generated between the contact member and the rotating member for generating the braking force. Therefore, this torque limiter mechanism can suppress a decrease in braking force that limits the rotational torque of the shaft body even if the surfaces of the contact member and the rotating member are worn.

  Further, the second invention is a torque limiter mechanism for limiting the rotational torque of the shaft body, and by engaging the non-circular connector member rotating with the rotation of the shaft body and the connector member, A rotating member that rotates as the connector member rotates, an abutting member that abuts on the outer peripheral surface of the rotating member, and a biasing force in a direction that abuts the abutting member on the outer peripheral surface of the rotating member And the contact member is configured such that when the connector member and the rotation member are engaged, the contact surface is rotated with the rotation of the shaft body. The rotational torque of the shaft body is intermittently limited by contacting the outer peripheral surface of the shaft.

  The abutting member of the torque limiter mechanism according to the second aspect of the invention has a non-circular shape of the rotating member, as with the torque limiter mechanism according to the first aspect of the invention. Therefore, in this torque limiter mechanism, the contact member swings as the shaft body rotates.

  This torque limiter mechanism, like the torque limiter mechanism according to the first aspect of the invention, is a force that pushes the abutting surface of the abutting member against the pressing force of the urging member and the outer peripheral surface of the rotating member against the pressing of the urging member. Is used as a braking force.

  The balance of the force varies periodically with the rotation of the rotating member. Therefore, the torque limiter mechanism can intermittently limit the rotational torque of the shaft body by using the balance of periodically varying forces as a braking force.

  This torque limiter mechanism does not rely on a simple frictional force (a non-fluctuating frictional force as in the conventional torque limiter mechanism) generated between the contact member and the rotating member for generating the braking force. Therefore, this torque limiter mechanism can suppress a decrease in braking force that limits the rotational torque of the shaft body even if the surfaces of the contact member and the rotating member are worn.

The third aspect of the present invention is a heavy-running detection mechanism, a rotating body that comes into contact with a transport surface of a medium traveling on a transport path, a shaft that rotates as the rotating body rotates, and the rotation of the shaft A torque limiter mechanism according to the first invention or the second invention for limiting the torque, and when a plurality of the media are running in heavy motion, a position shifting mechanism for shifting the position of each of the media, and the presence or absence of the media A medium detection sensor to be detected, and a determination unit that determines whether the medium is overrun based on whether the length of the medium is a predetermined length from the detection result of the medium detection sensor It is set as the structure which has.
Since this heavy-running detection mechanism uses the torque limiter mechanism according to the first invention or the second invention, it is possible to suppress a decrease in brake force that limits the rotational torque of the shaft body.

The fourth invention is an automatic transaction apparatus, in which a rotating body that abuts on a transport surface of a medium traveling on a transport path, a shaft body that rotates as the rotating body rotates, and a rotational torque of the shaft body A torque limiter mechanism according to the first or second aspect of the invention, and a position shifting mechanism that shifts the position of each medium when a plurality of the mediums are overrun, and detecting the presence or absence of the medium A medium detection sensor that determines whether or not the medium is overrun based on whether the length of the medium is a predetermined length from the detection result of the medium detection sensor; It is set as the structure which has.
Since this automatic transaction apparatus uses the torque limiter mechanism according to the first invention or the second invention, it is possible to suppress a decrease in brake force that limits the rotational torque of the shaft body.

  ADVANTAGE OF THE INVENTION According to this invention, the fall of the braking force which restrict | limits the rotational torque of a shaft body can be suppressed.

It is a figure (1) which shows the schematic structure around the heavy running detection mechanism of the automatic transaction apparatus concerning Embodiment 1. FIG. It is a figure (2) which shows schematic structure around the heavy running detection mechanism of the automatic transaction apparatus which concerns on Embodiment 1. FIG. It is a figure which shows the assembly structure of the torque limiter mechanism which concerns on Embodiment 1. FIG. FIG. 3 is a diagram (1) illustrating a configuration of components used in the torque limiter mechanism according to the first embodiment. FIG. 6 is a diagram (2) illustrating a configuration of components used in the torque limiter mechanism according to the first embodiment. It is a figure which shows schematic structure and operation | movement of the torque limiter mechanism which concern on Embodiment 1. FIG. It is explanatory drawing of the mechanism in which the brake force of the torque limiter mechanism which concerns on Embodiment 1 is generated. It is a figure which shows the relationship between rotation of a rotation member, and the braking force of the torque limiter mechanism which concerns on Embodiment 1. FIG. It is a figure which shows the relationship between the thickness of a medium, and the braking force of the torque limiter mechanism which concerns on Embodiment 1. FIG. It is a figure which shows the structure of the torque limiter mechanism which concerns on Embodiment 2. FIG. It is a figure which shows the relationship between the thickness of a medium, and the braking force of the torque limiter mechanism which concerns on Embodiment 2. FIG. FIG. 6A is a diagram (1) illustrating a configuration of a torque limiter mechanism according to a third embodiment. FIG. 6B is a diagram (2) illustrating the configuration of the torque limiter mechanism according to the third embodiment. FIG. 10 is a diagram (3) illustrating a configuration of a torque limiter mechanism according to a third embodiment.

  Hereinafter, an embodiment of the present invention (hereinafter referred to as “the present embodiment”) will be described in detail with reference to the drawings. Each figure is only schematically shown so that the present invention can be fully understood. Therefore, the present invention is not limited to the illustrated example. Moreover, in each figure, the same code | symbol is attached | subjected about the common component and the same component, and those overlapping description is abbreviate | omitted.

[Embodiment 1]
Hereinafter, the details of the torque limiter mechanism 10 (see FIG. 5) according to the first embodiment will be described. Here, as shown in FIG. 1, description will be made assuming that the torque limiter mechanism 10 is used for the heavy running detection mechanism 50 of the automatic transaction apparatus 100. The automatic transaction apparatus 100 is an apparatus that is installed mainly in a financial institution or a distribution institution and executes a transaction with a host computer. The heavy running detection mechanism 50 is a mechanism that detects heavy running of a medium traveling on the conveyance path.

  The automatic transaction apparatus 100 according to the first embodiment has the following problems (1) to (2) in the conventional automatic transaction apparatus. Therefore, the present embodiment is intended to solve these problems. 1 is used as the heavy-running detection mechanism 50.

  (1) As described below, the conventional automatic transaction apparatus has a problem that the heavy-running detection mechanism may not operate correctly when the operating years become long.

  For example, in a conventional automatic transaction apparatus, a heavy running detection mechanism uses a conventional torque limiter mechanism. The conventional torque limiter mechanism is configured to limit the rotational torque of the shaft body by using a frictional force generated by pressing the pad against a cylindrical drum as a braking force.

  However, the conventional torque limiter mechanism has a braking force that limits the rotational torque (braking torque) of the shaft body due to wear of the surface of the pad and drum when the operating years become long when used in various usage environments. Decreases. Therefore, the conventional automatic transaction apparatus has a possibility that the heavy-running detection mechanism may not operate correctly when the operation years are long.

  (2) In the conventional automatic transaction apparatus, as described below, when the medium is not overrun, a slip may occur between the medium and the transport roller, and the surface of the medium may become dirty. There was a problem.

  For example, an automatic transaction apparatus uses a force relationship of a torque limiter mechanism to prevent slippage between the medium and the transport roller when the medium is not overrun, and the surface of the medium becoming dirty. , “Friction force between medium and driven conveyance roller”> “Brake force of torque limiter mechanism”> “Friction force between media” needs to be set.

  However, when the medium travels between the driving-side conveyance roller and the driven-side conveyance roller, the automatic transaction apparatus causes the driven-side conveyance roller to move vertically in accordance with the thickness of the medium due to the action of the spring. Moving.

  At this time, in the conventional automatic transaction apparatus, the pressure that presses the driven-side conveyance roller against the driving-side conveyance roller changes, and accordingly, “the frictional force between the medium and the driven-side conveyance roller”. Also changes. As a result, in the conventional automatic transaction apparatus, the “friction force between the medium and the driven conveyance roller” may be smaller than the “braking force of the torque limiter mechanism”. Therefore, in the conventional automatic transaction apparatus, when the medium is not overrun, slip occurs between the medium and the transport roller, and the surface of the medium becomes dirty (that is, slip marks are attached to the surface of the medium). There was.

  As described later, the automatic transaction apparatus 100 according to the first embodiment solves these problems by using the torque limiter mechanism 10 (see FIG. 5) according to the first embodiment for the heavy-running detection mechanism 50. Yes.

<Configuration around the heavy-duty detection mechanism of automatic transaction equipment>
Hereinafter, with reference to FIG.1 and FIG.2, it demonstrates per structure of the heavy run detection mechanism 50 periphery of the automatic transaction apparatus 100 which concerns on this Embodiment 1. FIG. FIG.1 and FIG.2 is a figure which shows schematic structure around the heavy run detection mechanism 50 of the automatic transaction apparatus 100 which concerns on this Embodiment 1, respectively. FIG. 1 shows a schematic configuration of the heavy running detection mechanism 50 as viewed from the side. FIG. 2 shows a schematic configuration of the heavy running detection mechanism 50 as viewed from the front.

  Here, in the automatic transaction apparatus 100, the heavy running detection mechanism 50 is installed in the vicinity of the passbook insertion port 2 (see FIG. 1), and the heavy running detection mechanism 50 has the presence / absence of heavy running in the passbook as the medium M to be detected. A description will be given assuming that the system is configured to detect.

  In the example shown in FIG. 1, in the automatic transaction apparatus 100, the conveyance path 3 is provided from the passbook insertion port 2 toward the back thereof. The conveyance path 3 is formed by conveyance guides 3 a provided above and below the conveyance path 3.

  The automatic transaction apparatus 100 has a plurality of sets (two sets in the example shown in FIG. 1) of driving side transport rollers 6a and driven side transport rollers 6b on the back side of the insertion port 2 via the transport path 3. Are arranged opposite to each other. In the example illustrated in FIG. 1, the driving-side transport roller 6 a is disposed on the upper side of the transport path 3, and the driven-side transport roller 6 b is disposed on the lower side of the transport path 3.

  The drive-side transport roller 6a is a member that is rotationally driven by the drive unit 5 (see FIG. 2). On the other hand, the driven-side transport roller 6b is a member that rotates following the rotation of the drive-side transport roller 6a.

  The driving-side transport roller 6a and the driven-side transport roller 6b are two to form one set. Hereinafter, when the transport roller 6a on the driving side and the transport roller 6b on the driven side are collectively referred to as “conveyance roller 6”.

  Here, it is assumed that the drive unit 5 (see FIG. 2) is attached to the rotation shaft of the drive-side conveyance roller 6a and the drive unit 5 is configured to rotate the drive-side conveyance roller 6a. However, the drive unit 5 may be configured to rotate the drive-side transport roller 6a via a transmission mechanism (not shown) such as a gear or a belt.

  The driving-side transport roller 6a is rotatably supported by the frame 8 at a predetermined position. On the other hand, the driven-side transport roller 6b is rotatably supported by the frame 8 at a position facing the drive-side transport roller 6a while being movable in the vertical direction.

  The frame 8 corresponds to a “support member” recited in the claims. The driven-side transport roller 6b corresponds to a “rotating body” recited in the claims. Further, here, the rotation axis (the shaft 7 (see FIG. 2)) of the driven-side transport roller 6b is the rotation axis of the rotation member 11 (see FIG. 5) of the torque limiter mechanism 10 described later. Will be described. The rotating shaft of the rotating member 11 corresponds to a “shaft body” recited in the claims.

  The driven-side conveying roller 6b is normally pressed against the driven-side conveying roller 6a by a spring 9. When the medium M travels between the driving-side conveyance roller 6a and the driven-side conveyance roller 6b, the driven-side conveyance roller 6b moves downward according to the thickness of the medium M by the action of the spring 9. Moving. Hereinafter, the operation in which the transport roller 6b moves downward according to the thickness of the medium M is referred to as “retraction”.

  Here, a description will be given assuming that the second driving-side transport roller 6a and the driven-side transport roller 6b from the insertion port 2 constitute a position shifting mechanism 20. The position shifting mechanism 20 is a mechanism that shifts the position of at least one of the media M when a plurality of media M are running in heavy motion.

  The position shifting mechanism 20 includes a rotating body (here, the transport roller 6b on the driven side) that contacts the transport surface of the medium M traveling on the transport path 3, and a shaft body (here) that rotates as the rotating body rotates. Then, the shaft 7 (see FIG. 2) of the driven-side transport roller 6b, which is the rotational axis of the rotating member 11 (see FIG. 5), and the torque limiter mechanism 10 (see FIG. 2) for limiting the rotational torque of the shaft body. 2).

  That is, the position shifting mechanism 20 is configured such that the torque limiter mechanism 10 is attached to the driven shaft body, and the torque limiter mechanism 10 brakes the rotation of the driven shaft body. Accordingly, the position shifting mechanism 20 performs a process of shifting the position of the medium M by making the driving-side transport roller 6a and the driven-side transport roller 6b differential.

  In the first embodiment, the position shifting mechanism 20 will be described as having a configuration in which the torque limiter mechanism 10 is provided on the driven roller 6b closest to the insertion port 2. However, the torque limiter mechanism 10 can also be provided on the second and subsequent driven-side transport rollers 6b from the insertion port 2.

  In the position shifting mechanism 20, the medium detection sensor 30 and the determination unit 40 of the control unit 1 constitute a heavy running detection mechanism 50. The medium detection sensor 30 is a sensor that detects the presence or absence of the medium M.

  The medium detection sensor 30 outputs a detection signal (detection result) having a different value depending on the presence or absence of the medium M to the control unit 1. The control unit 1 is a functional unit that controls the overall operation of the automatic transaction apparatus 100. The control unit 1 functions as the determination unit 40. Whether the length of the medium M after performing the process of shifting the position of the medium M based on the value of the detection signal (detection result) output from the medium detection sensor 30 is a predetermined length. It is a functional means for determining whether or not the medium M is overrun based on whether or not it is running.

  In the first embodiment, the determination unit 40 determines whether or not the length of the medium M after the process of shifting the position of the medium M is a predetermined length. It is done by judging. However, the determination method of the heavy run of the medium M can also be performed by other methods.

  The heavy running detection mechanism 50 performs a process of shifting the position of the medium M by the position shifting mechanism 20 when the medium M is transported along the transport path 3. Specifically, when the medium M is transported along the transport path 3 by the driving-side transport roller 6a, the heavy-running detection mechanism 50 causes the torque limiter mechanism 10 to rotate the driven-side transport roller 6b. Apply the brakes.

  As a result, the medium M receives different forces (driving force from the driving-side conveying roller 6a and braking force from the driven-side conveying roller 6b) from the driving-side conveying roller 6a and the driven-side conveying roller 6b. Be transported. At this time, if a plurality of mediums M are overlapped, the medium M is separated and shifted in position. When the process of shifting the position of the medium M is performed, the entire length remains the original length of the medium M when it is not overrun, while the entire length is the original length of the medium M when overrun. Longer than that.

  Therefore, the heavy running detection mechanism 50 detects the medium M by the medium detection sensor 30, and further performs a process of shifting the position of the medium M from the value of the detection signal (detection result) of the medium detection sensor 30 by the determination unit 40. Whether or not the medium M is overrun is determined based on whether or not the length of the medium M after the execution is a predetermined length.

  The heavy running detection mechanism 50 determines that the medium M is not heavy running when it is determined that the length of the medium M is a predetermined length. On the other hand, when it is determined that the length of the medium M is not the predetermined length, it is determined that the medium M is running heavily.

  When it is determined that the medium M is heavy running (that is, when it is determined that the length of the medium M is not the predetermined length), the automatic transaction apparatus 100 loads the medium M. Return to the insertion slot 2 without taking it into the apparatus. As a result, the automatic transaction apparatus 100 prevents a plurality of media M input by the customer by mistake from being taken into the apparatus.

<Configuration of torque limiter mechanism>
The position shifting mechanism 20 according to the first embodiment is configured so that the torque limiter mechanism 10 intermittently restricts the rotational torque (braking torque) of the shaft body, so that each of the plurality of media M is overrun. The position of the medium M is shifted. As a configuration for that purpose, the torque limiter mechanism 10 has a configuration described below.

  The configuration of the torque limiter mechanism 10 will be described below with reference to FIGS. 3, 4A and 4B, and FIG. FIG. 3 is a view showing an assembly structure of the torque limiter mechanism 10 according to the first embodiment. FIG. 4A and FIG. 4B are diagrams each showing a configuration of components used in the torque limiter mechanism 10 according to the first embodiment. FIG. 4A shows the configuration of the rotating member 11. FIG. 4B shows a configuration of the pad 12 described later. FIG. 5 is a diagram illustrating a schematic configuration and operation of the torque limiter mechanism 10 according to the first embodiment.

  As shown in FIG. 3, the torque limiter mechanism 10 includes a rotating member 11, a pad 12, a torsion spring 13, a cam 14, and a drive unit 23. In FIG. 3, an arrow indicated by a dotted line indicates a mounting position of each component with respect to the frame 8. Each component is configured as shown in FIG. 5 by being attached to the frame 8, for example. 5 shows a schematic configuration of the torque limiter mechanism 10 viewed from the side, excluding the frame 8, the drive unit 23, and the like.

(Rotating member)
The rotating member 11 is a member that rotates as the shaft body rotates. Here, the “shaft body” means the rotating shaft of the rotating member 11. In the first embodiment, the rotation shaft of the rotating member 11 that is the shaft body is integrated with the rotation shaft (shaft 7) of the driven-side transport roller 6b. Therefore, in the first embodiment, the rotating member 11 is attached to the rotation shaft (shaft 7) of the transport roller 6b.

  The torque limiter mechanism 10 is configured so that the opposing surfaces 141a and 142a (see FIG. 4B) of the first projecting portion 141 and the second projecting portion 142 described later of the pad 12 abut on the outer peripheral surface of the rotating member 11, thereby Generates braking force that limits rotational torque.

  The rotating member 11 is formed so that the cross-sectional shape thereof becomes a non-circular shape around the central axis of rotation (rotation center O shown in FIG. 4A). For example, in the first embodiment, as shown in FIG. 4A, the rotary member 11 has a hexagonal cross section. That is, in the first embodiment, the rotating member 11 is formed in a hexagonal column shape.

  The rotating member 11 is formed so as to have a non-circular cross-sectional shape (in the example shown in FIG. 4A, a hexagonal shape), whereby the maximum diameter portions R1, R2, R3 (maximum outer diameter values) 4A) and a small-diameter portion whose outer diameter value is smaller than the maximum-diameter portions R1, R2, and R3 (that is, portions other than the maximum-diameter portions R1, R2, and R3). In the rotating member 11, the value of the outer diameter of the maximum diameter portions R1, R2, R3 is the maximum diameter T1 of the rotating member 11, and the value of the outer diameter of the small diameter portion is less than the maximum diameter T1. In addition, the diameter of the circumscribed circle of the rotating member 11 is the maximum diameter, and the diameter of the inscribed circle is the minimum diameter.

  Here, the “outer diameter” means a virtual plane passing through the center axis of rotation of the rotating member 11 (rotation center O shown in FIG. 4A) (that is, extending in the axial direction of the center axis and including the center axis). This means a distance between two sides where a virtual plane) and the outer peripheral surface of the rotating member 11 intersect.

  However, if the rotary member 11 is formed so that the cross-sectional shape is non-circular, the cross-sectional shape is formed in a polygonal shape other than a hexagon, such as a triangle, a quadrangle, or an octagon. Also good. That is, the rotating member 11 may be formed in a polygonal shape having a cross-sectional shape of a triangle or more. Further, the rotating member 11 may have an elliptical or oval cross-sectional shape. These shapes can obtain the same effect as the case where the cross-sectional shape is a hexagon. The rotating member 11 may be formed in a polygonal shape, but is preferably formed in an even-numbered rectangle such as a quadrangle, a hexagon, or an octagon. Furthermore, the rotation member 11 is a regular hexagon or a regular octagon. It is preferable that it is formed in an even number of squares.

  When the medium M travels between the driving-side conveying roller 6a and the driven-side conveying roller 6b, the rotating member 11 is moved together with the driven-side conveying roller 6b according to the thickness of the medium M. Move (retract) downward.

  The rotating member 11 is attached to the frame 8 after the cam 14 is attached to the frame 8 and the torsion spring 13 and the pad 12 are attached to the frame 8.

(Composition of pad and torsion spring)
The pad 12 is an abutting member that abuts on the outer peripheral surface of the rotating member 11. The pad 12 has a structure like a clothespin. Specifically, the pad 12 is configured by a first shaft support member 121 and a second shaft support member 122 that are pivotally supported by pins 151. Here, the pin 151 is described as having a tip portion formed in a bolt shape and fixed by a nut 152. The central axis of the pin 151 corresponds to an “open / close fulcrum” described in the claims. Hereinafter, the central axis of the pin 151 may be referred to as “opening / closing fulcrum 151a (see FIGS. 3 and 5)”.

In the first embodiment, the first shaft support member 121 has a shape including a first body portion 131, a first protrusion 141, and a third protrusion 143.
The first body part 131 is a part that is pivotally supported by a pin 151. In the first embodiment, the first body portion 131 is formed in a columnar shape, and a circular hole 161 through which the pin 151 is passed is provided in the center portion thereof.
The first protruding portion 141 is a portion protruding from the first body portion 131 in a plane perpendicular to the axial support direction of the pin 151.
The third protruding portion 143 is a portion protruding from the first body portion 131 in a plane perpendicular to the axial support direction of the pin 151 and in a direction different from the protruding direction of the first protruding portion 141.

On the other hand, the second shaft support member 122 has a shape including a second body part 132, a second projecting part 142, and a fourth projecting part 144.
The second body part 132 is a part that is pivotally supported by the pin 151 together with the first body part 131 of the first shaft support member 121. In the first embodiment, the second body part 132 is formed in a columnar shape having the same diameter as the first body part 131 of the first shaft support member 121, and a circular hole 162 through which the pin 151 is passed is a central part thereof. Is provided.
The second projecting portion 142 is a portion projecting from the second body portion 132 in a plane perpendicular to the axial direction of the pin 151 so as to face the first projecting portion 141 via the rotating member 11.
The fourth projecting portion 144 is a portion projecting from the second body portion 132 in a direction different from the projecting direction of the second projecting portion 142 so as to face the third projecting portion 143, and the axial support direction of the pin 151 Rotate in a vertical plane.

  As shown in FIG. 4B, the first pivot member 121 and the second pivot member 122 have an inclination angle θ121 between the projecting direction of the first projecting portion 141 and the projecting direction of the third projecting portion 143, as shown in FIG. It is formed to be substantially equal to the inclination angle θ122 between the protruding direction of the protruding portion 142 and the protruding direction of the fourth protruding portion 144. That is, the fourth protrusion 144 of the second shaft support member 122 is inclined between the protrusion direction of the first protrusion 141 and the protrusion direction of the third protrusion 143 with respect to the protrusion direction of the second protrusion 142. It is configured to protrude from the second body portion 132 in the direction of the inclination angle θ122 substantially equal to the angle θ121.

The first projecting portion 141 of the first shaft support member 121 and the second projecting portion 142 of the second shaft support member 122 function as contact surfaces whose opposing surfaces contact the outer peripheral surface of the rotating member 11.
On the other hand, the third projecting portion 143 of the first shaft support member 121 and the fourth projecting portion 144 of the second shaft support member 122 function as contact surfaces whose opposing surfaces contact the outer peripheral surface of the cam 14.

  Further, since the rotating member 11 is retracted downward according to the thickness of the medium M, the opposing surfaces 141a and 142a (see FIG. 4B) of the first protruding portion 141 and the second protruding portion 142 of the pad 12 are mutually connected. Is preferably substantially equal to the distance between the two opposing surfaces of the hexagonal rotation member 11. The distance between the two opposing surfaces of the hexagonal rotation member 11 is equal to the diameter of the inscribed circle of the rotation member 11.

  In the pad 12, the first shaft support member 121 and the second shaft support member 122 are opposed to each other so that the circular hole 161 of the first shaft support member 121 coincides with the circular hole 162 of the second shaft support member 122. Formed by. A torsion spring 13 is attached to the outside of the pad 12.

  The torsion spring 13 urges the contact surface of the contact member (here, the opposing surface of the first protrusion 141 and the second protrusion 142 of the pad 12) to contact the outer peripheral surface of the rotating member 11. It is an urging member.

  The torsion spring 13 sandwiches the first projecting portion 141 and the second projecting portion 142 of the pad 12 by both of the tip portions thereof, and the winding shaft is aligned with the circular holes 161 and 162 of the pad 12. It is arranged at a position outside the 12 first body parts 131 (position on the side close to the first support part 81 of the frame 8). The torsion spring 13 presses the first projecting portion 141 and the second projecting portion 142 of the pad 12 in a proximity direction that brings them closer to each other.

  The torsion spring 13 and the pad 12 are attached to the frame 8 after the cam 14 is attached to the frame 8.

(Composition of cam)
The cam 14 is in a contact state where the opposed surfaces of the first projecting portion 141 and the second projecting portion 142 are in contact with the outer peripheral surface of the rotating member 11, and the opposed surfaces of the first projecting portion 141 and the second projecting portion 142. When the state in which the first member is separated from the outer peripheral surface of the rotating member 11 is the separated state, the state of the first projecting portion 141 and the second projecting portion 142 of the pad 12 is either the contact state or the separated state. This is a switching member that is selectively switched.

  The cam 14 is disposed between the opposed surfaces of the third projecting portion 143 and the fourth projecting portion 144 so that the outer peripheral surface thereof is in contact with the opposed surfaces of the third projecting portion 143 and the fourth projecting portion 144 of the pad 12. The

  The cam 14 is provided with a circular hole 14a at the center thereof. The circular hole 14a is a hole through which the shaft 231 of the drive unit 23 is passed. The cam 14 is attached to the drive unit 23 (see FIG. 3) by passing the shaft 231 of the drive unit 23 through the circular hole 14a.

  The control part 1 (refer FIG. 1) of the automatic transaction apparatus 100 operates the drive part 23 at arbitrary timings, and rotates the cam 14 of the torque limiter mechanism 10. FIG. As the cam 14 rotates, the outer peripheral surface of the cam 14 is alternately switched between a state in which it is in contact with the opposing surfaces of the third protrusion 143 and the fourth protrusion 144 of the pad 12 and a state in which it is separated.

  When the outer peripheral surface of the cam 14 abuts against the opposing surfaces of the third projecting portion 143 and the fourth projecting portion 144 of the pad 12, the third projecting portion 143 and the fourth projecting portion 144 are pushed apart in the separating direction. Then, the first protrusion 141 and the second protrusion 142 of the pad 12 are pushed apart in the separating direction against the pressing of the torsion spring 13.

(Frame structure)
In the example illustrated in FIG. 3, the frame 8 includes a first support portion 81 and a second support portion 82 that protrude vertically upward from a bottom surface portion that extends in the horizontal direction. The cam 14, the pad 12, the torsion spring 13, and the rotating member 11 are disposed between the first support portion 81 and the second support portion 82.

  The first support portion 81 of the frame 8 is provided with circular holes 81a and 81b and a vertically long opening portion 81c. On the other hand, in the second support portion 81 of the frame 8, the circular holes 82a and 82b and the vertically long opening portion 82c are respectively positioned at positions facing the circular holes 81a and 81b and the vertically long opening portion 81c of the first support portion 81. Is provided.

  The circular holes 81a and 82a are holes through which the shaft 231 of the drive unit 23 is passed. The circular holes 81b and 82b are holes through which pins 151 that support the first shaft support member 121 and the second shaft support member 122 are passed. The vertically long openings 81c and 82c are portions through which the shaft 7 to which the rotating member 11 is attached is passed.

  The vertically long openings 81 c and 82 c are provided so as to extend in a direction perpendicular to the transport path 3. Therefore, the frame 8 is retractable in a vertical retracting direction with respect to the transport path 3 (and consequently with respect to the transport surface of the medium M traveling on the transport path 3), and the shaft 7 (and thus the rotating member). 11 and the driven-side transport roller 6b).

  The circular holes 81a and 82a are arranged at positions deviating from the extending direction of the vertically long openings 81c and 82c. On the other hand, the circular holes 81b and 82b are arranged at positions in the extending direction of the vertically long openings 81c and 82c.

First, the cam 14 is attached to the frame 8.
The cam 14 includes a first support portion 81 and a second support portion 82 of the frame 8 such that the circular hole 14 a coincides with the circular hole 81 a of the first support portion 81 of the frame 8 and the circular hole 82 a of the second support portion 82. Between.

  In the cam 14, the shaft 231 of the drive unit 23 is passed through the circular hole 81 a of the first support part 81 of the frame 8, the circular hole 14 a of the cam 14, and the circular hole 82 a of the second support part 82. Therefore, it is rotatably supported at a predetermined position.

When the cam 14 is attached to the frame 8, the pad 12 and the torsion spring 13 are then attached.
In the pad 12, the first shaft support member 121 and the second shaft support member 122 are opposed to each other so that the circular hole 161 of the first shaft support member 121 coincides with the circular hole 162 of the second shaft support member 122. . A torsion spring 13 is attached to the outside of the pad 12.

  The torsion spring 13 has a pad so that both ends of the torsion spring 13 sandwich the first protrusion 141 and the second protrusion 142 of the pad 12 and the winding axis thereof coincides with the circular holes 161 and 162 of the pad 12. It is arranged at a position outside the 12 first body parts 131 (a position on the side close to the first support part 81 of the frame 8).

  In this state, the pad 12 and the torsion spring 13 include the winding shaft of the torsion spring 13, the circular hole 161 of the first shaft support member 121, and the circular hole 162 of the second shaft support member 122. The circular hole 81 b is arranged between the first support part 81 and the second support part 82 of the frame 8 so as to coincide with the circular hole 82 b of the second support part 82.

  With the pad 12 and the torsion spring 13 in this state, the pin 151 has the circular hole 81b of the first support portion 81 of the frame 8, the winding shaft of the torsion spring 13, the circular hole 161 of the first pivotal support member 121, and the second shaft. By passing through the circular hole 162 of the support member 122 and the circular hole 82 b of the second support portion 82 of the frame 8, the support member 122 is supported at a predetermined position. The pin 151 is fixed by attaching a nut 152 to a tip portion formed in a bolt shape.

When the cam 14, the pad 12, and the torsion spring 13 are attached to the frame 8, the rotating member 11 is then attached.
The rotating member 11 is disposed between the first protrusion 141 and the second protrusion 142 of the pad 12. The rotating member 11 is formed by extending the vertically long openings 81c and 82c by passing the shaft 7 to which the rotating member 11 is attached through the vertically long openings 81c and 82c of the first support portion 81 of the frame 8. It is rotatably supported in a state that can move in the direction (that is, a state that can be retracted in the retracting direction).

  In this way, the torque limiter mechanism 10 (see FIG. 5) is assembled by attaching the components to the frame 8.

<Operation of torque limiter mechanism>
Hereinafter, the operation of the torque limiter mechanism 10 will be described with reference to FIGS. 5 and 6. FIG. 5 is a diagram showing a schematic configuration and operation of the torque limiter mechanism 10 according to the first embodiment as described above. FIG. 5A shows the state of the torque limiter mechanism 10 when the brake is turned on. FIG. 5B shows a state of the torque limiter mechanism 10 when the brake is turned off. FIG. 6 is an explanatory diagram of a mechanism for generating a braking force of the torque limiter mechanism 10 according to the first embodiment.

  As shown in FIG. 5, the pad 12 of the torque limiter mechanism 10 has a first shaft support member 121 and a second shaft support member 122 supported by pins 151. The pin 151 is disposed at a position in the retracting direction of the rotating member 11 with respect to the rotating shaft (shaft 7) of the rotating member 11.

  The control unit 1 of the automatic transaction apparatus 100 operates the drive unit 23 at an arbitrary timing to rotate the cam 14 of the torque limiter mechanism 10. As described above, the cam 14 is alternately switched between a contact state in which the outer peripheral surface is in contact with the opposing surfaces of the third protrusion 143 and the fourth protrusion 144 of the pad 12 and a separated state in which the cam 14 is separated. .

  As shown in FIG. 5A, the torque limiter mechanism 10 is configured so that the torsion spring 13 is moved when the outer peripheral surface of the cam 14 does not contact the opposing surfaces of the third protrusion 143 and the fourth protrusion 144 of the pad 12. The first protrusion 141 and the second protrusion 142 of the pad 12 are pressed in the proximity direction. Thereby, the 1st protrusion part 141 and the 2nd protrusion part 142 of the pad 12 will be in the closed state.

  As a result, the opposing surfaces of the first protrusion 141 and the second protrusion 142 of the pad 12 come into contact with the outer peripheral surface of the rotating member 11. As a result, the torque limiter mechanism 10 enters a state in which the generation of the braking force is turned on.

  On the other hand, as shown in FIG. 5B, when the outer peripheral surface of the cam 14 abuts against the opposing surfaces of the third protrusion 143 and the fourth protrusion 144 of the pad 12, the torque limiter mechanism 10 The third projecting portion 143 and the fourth projecting portion 144 are pushed apart in the separating direction (directions of arrows B1a and B1b). As a result, the cam 14 pushes the first projecting portion 141 and the second projecting portion 142 of the pad 12 against the pressing of the torsion spring 13 in the separating direction (directions of arrows C1a and C1b). Thereby, the 1st protrusion part 141 and the 2nd protrusion part 142 of the pad 12 will be in the open state.

  As a result, the opposing surfaces of the first protrusion 141 and the second protrusion 142 of the pad 12 are separated from the outer peripheral surface of the rotating member 11. As a result, the torque limiter mechanism 10 enters a state in which the generation of the braking force is turned off.

  The torque limiter mechanism 10 is normally in a state shown in FIG. 5B (when the medium M is not transported).

  For example, when the customer inserts the medium M into the insertion slot 2 (see FIG. 1), the control unit 1 of the automatic transaction apparatus 100 detects this by a sensor (not shown). Then, the control unit 1 operates the drive unit 5 (see FIG. 2), and the medium M is directed from the insertion port 2 toward the inside of the apparatus by the transport roller 6 (that is, in the direction of the arrow A1 (see FIG. 1)). Transport. At this time, when the conveyance roller 6 sandwiches the medium M, the conveyance roller 6b on the driven side is retracted in the direction of the arrow A2 (see FIGS. 1 and 2) according to the thickness of the medium M.

  When the medium M reaches the position for performing the process of shifting the position of the medium M (specifically, the position of the medium detection sensor 30 on the insertion port 2 side of the position shifting mechanism 20 (see FIG. 1)). Further, this is detected based on the value of the detection signal output from the medium detection sensor 30.

  When the control unit 1 detects that the medium M has reached the position where the process for shifting the position of the medium M is performed, the state of the torque limiter mechanism 10 is changed from the state shown in FIG. 5B to the state shown in FIG. Switch to state. That is, the control unit 1 operates the drive unit 23 to rotate the cam 14 so that the first protrusion 141 and the second protrusion 142 of the pad 12 are closed.

  At this time, in the pad 12, the torsion spring 13 presses the first projecting portion 141 and the second projecting portion 142 in the proximity direction, so that the first projecting portion 141 and the second projecting portion 142 sandwich the rotating member 11. As a result, the opposing surfaces of the first protrusion 141 and the second protrusion 142 are in contact with the outer peripheral surface of the rotating member 11.

  As shown in FIG. 6, when the driven roller 6b (see FIGS. 1 and 2) rotates in the direction of arrow D1, the torque limiter mechanism 10 is driven via the shaft 7 to the driven roller 6b. Is transmitted to the rotating member 11. As a result, the rotating member 11 rotates in the direction of the arrow D1 together with the driven-side transport roller 6b. At this time, since the rotary member 11 has a hexagonal cross section, the outer peripheral surface of the maximum diameter portions R1, R2, R3 (see FIG. 4A) is padded against the pressing E1 of the torsion spring 13. The twelve first protrusions 141 and the second protrusions 142 are rotated while being pushed in the directions of arrows F1a and F1b.

  On the other hand, since the opposing surfaces of the first projecting portion 141 and the second projecting portion 142 are pressed against the outer peripheral surface of the rotating member 11 by the torsion spring 13, the pad 12 has a shaft body (the rotational axis of the rotating member 11 ( A braking force is generated that limits the rotation of the shaft 7)). As a result, the torque limiter mechanism 10 brakes the rotation of the driven-side transport roller 6b.

  As a result, the medium M receives different forces (driving force from the driving-side conveying roller 6a and braking force from the driven-side conveying roller 6b) from the driving-side conveying roller 6a and the driven-side conveying roller 6b. Be transported. At this time, if a plurality of mediums M are overlapped, the medium M is separated and shifted in position. When the process of shifting the position of the medium M is performed, the entire length remains the original length of the medium M when the medium M is not overrun. On the other hand, in the case of heavy running, each position of the medium M overlapped in the vertical direction is shifted in the transport direction, so that the total length becomes longer than the original length of the medium M.

  Therefore, the heavy running detection mechanism 50 of the automatic transaction apparatus 100 detects the medium M by the medium detection sensor 30, and further, from the value of the detection signal (detection result) output from the medium detection sensor 30 by the determination unit 40, Based on whether the length of the medium M after the process of shifting the position of the medium M is a predetermined length, it is determined whether the medium M is overrun.

  The heavy running detection mechanism 50 determines that the medium M is not heavy running when it is determined that the length of the medium M is a predetermined length. On the other hand, when it is determined that the length of the medium M is not the predetermined length, it is determined that the medium M is running heavily.

  In the automatic transaction apparatus 100, when the medium M is not overrun, the rotating member 11 of the torque limiter mechanism 10 is the outermost surface of the maximum diameter portions R1, R2, R3 (see FIG. 4A) and the pad 12 The first protrusion 141 and the second protrusion 142 are rotated while being pushed away.

  Therefore, in the automatic transaction apparatus 100, no slip occurs between the medium M and the driven-side transport roller 6b. Therefore, the automatic transaction apparatus 100 can convey the medium M without making the surface of the medium dirty.

  Here, in the automatic transaction apparatus 100, the torque relationship of the torque limiter mechanism 10 is such that “the friction force between the medium M and the driven-side transport roller 6b”> “braking force of the torque limiter mechanism 10”> “medium Although the force relationship of “the frictional force between M” is set, the force relationship is maintained even during operation.

<Operation of torque limiter mechanism>
A conventional torque limiter mechanism is configured to press a pad against a cylindrical drum. Therefore, in the conventional torque limiter mechanism, the frictional force generated between the pad and the drum does not fluctuate. The conventional torque limiter mechanism continuously limits the rotational torque of the shaft body by using the non-fluctuating frictional force as a braking force. Therefore, in the conventional torque limiter mechanism, the brake force that limits the rotational torque of the shaft body may be reduced due to wear of the surface of the pad or the drum.

  On the other hand, in the torque limiter mechanism 10 according to the first embodiment, as shown in FIG. 6, the cross-sectional shape of the rotating member 11 is a non-circular shape (in the illustrated example, a hexagonal shape) around the central axis. Is formed. Therefore, in the torque limiter mechanism 10, as the shaft body rotates, the contact surface of the pad 12 is the outer peripheral surface of the maximum diameter portions R 1, R 2, R 3 (see FIG. 4A) of the rotating member 11 and the outer peripheral surface of the small diameter portion. And abut against each other. As a result, in the torque limiter mechanism 10, the pad 12 swings with the rotation of the shaft body.

  In the torque limiter mechanism 10, the pressing force of the biasing member (here, the torsion spring 13) and the outer peripheral surface of the maximum diameter portions R1, R2, R3 (see FIG. 4A) of the rotating member 11 resist the pressing of the biasing member. The balance with the force that pushes off the first projecting portion 141 and the second projecting portion 142 of the pad 12 is used as a braking force.

  The balance of the force varies periodically with the rotation of the rotating member 11. Accordingly, the torque limiter mechanism 10 can intermittently limit the rotational torque of the shaft body by using the balance of periodically varying forces as a braking force.

  The torque limiter mechanism 10 does not rely on a simple frictional force (a non-fluctuating frictional force as in the conventional torque limiter mechanism) generated between the contact member and the rotating member for generating the braking force. Therefore, the torque limiter mechanism 10 is a brake that limits the rotational torque of the shaft body even if the surfaces of the abutting members (the first protrusion 141 and the second protrusion 142 of the pad 12) and the rotating member 11 are worn. The decrease in power can be suppressed.

  In addition, the torque limiter mechanism 10 wears the corners of the rotating member 11 even if it is assumed that the hexagonal corners of the rotating member 11 are greatly worn by long-term use. The relationship between the amount and the braking force can be easily calculated in advance. Therefore, the torque limiter mechanism 10 can predict the time when the setting of the force relationship of the torque limiter mechanism is out of order, and can be replaced before the setting of the force relationship of the torque limiter mechanism is out of order.

  In the torque limiter mechanism 10, the braking force changes according to the cross-sectional shape of the rotating member 11. That is, the brake force of the torque limiter mechanism 10 has an amplitude. In the first embodiment, as shown in FIG. 7, in the torque limiter mechanism 10, the peak appears six times while the hexagonal rotation member 11 makes one rotation. FIG. 7 is a diagram illustrating the relationship between the rotation of the rotating member 11 and the braking force of the torque limiter mechanism 10 according to the first embodiment. Since the brake force of the torque limiter mechanism 10 oscillates in small increments, the medium M is more easily separated than when a constant pressing brake force that does not vary is applied to the medium M unlike the conventional torque limiter mechanism.

  Further, the torque limiter mechanism 10 increases the retracted amount (pressed amount) of the driven-side transport roller 6b as the thickness of the medium M increases. As a result, the upper and lower transport rollers 6 have a larger force for sandwiching the medium M by the spring 9.

  If the medium M is running heavily, the frictional force acting between the overlapping media M is determined by “static friction coefficient μ” × “pressing F”. Therefore, if the medium M is running heavily, the thickness of the medium M increases, and the frictional force increases accordingly. At this time, “the frictional force between the medium M and the driven-side transport roller 6b” also increases.

  In the conventional torque limiter mechanism, when the thickness of the medium M is constant, “friction force between the medium M and the driven-side transport roller”> “brake force of the torque limiter mechanism”> “medium M The force relationship of “frictional force” can be maintained. However, the conventional torque limiter mechanism is used when the thickness of the medium M is not constant (for example, when the medium M is a booklet-shaped medium such as a passbook and it is not known which page is inserted). If the braking force is constant, either the thin medium M or the thick medium M cannot satisfy the force relationship of the torque limiter mechanism described above.

  On the other hand, the torque limiter mechanism 10 according to the first embodiment is configured such that when the transport roller 6b on the driven side is retracted (lowered), the rotating member 11 is also retracted (lowered) together.

  For this reason, when the medium M travels between the drive-side transport roller 6a and the driven-side transport roller 6b, the torque limiter mechanism 10 allows the rotating member 11 to move to the center axis (opening / closing fulcrum of the pin 151 of the pad 12). 151a (see FIG. 5)).

  In the torque limiter mechanism 10, the closer the rotating member 11 is to the center axis of the pin 151 of the pad 12, the first protruding portion 141 and the second protruding portion 142 of the pad 12 are moved to the rotating member 11 according to the lever principle. The force (pushing E1, E2 of the torsion spring 13 (see FIG. 8)) is increased. In proportion to this, the braking force that limits the rotation of the shaft also increases. Therefore, the torque limiter mechanism 10 can increase or decrease the braking force according to the thickness of the medium M.

  FIG. 8 is a diagram illustrating the relationship between the thickness of the medium M and the braking force of the torque limiter mechanism 10 according to the first embodiment. FIG. 8A shows the state of the torque limiter mechanism 10 when the medium M is thin. FIG. 8B shows a state of the torque limiter mechanism 10 when the medium M is thick.

  In the torque limiter mechanism 10, when the medium M is thin, as shown in FIG. 8A, the rotating member 11 slightly approaches the central axis of the pin 151. On the other hand, in the torque limiter mechanism 10, when the medium M is thick, as shown in FIG. 8B, the rotating member 11 largely approaches the central axis of the pin 151.

  The torque limiter mechanism 10 is configured so that the first projecting portion 141 and the second projecting portion 142 of the pad 12 pinch the rotating member 11 (the pressure E1 of the torsion spring 13) as the rotating member 11 approaches the central axis of the pin 151. E2) becomes stronger. In FIG. 8, the press when the medium M is thin is “E1”, the press when the medium M is thick is “E2”, and the force relationship between “E1” and “E2” is “E2”. > E1 ”.

  The torque limiter mechanism 10 </ b> B can increase the braking force according to the thickness of the medium M because the pressure that the compression spring 18 presses the pad 12 </ b> B against the rotating member 11 increases according to the thickness of the medium M.

  Further, for example, when a customer who wants to use the automatic transaction apparatus 100 mistakenly inserts two passbooks as the medium M, the medium M being inhaled is pulled out by the customer who notices the heavy running of the medium M. Even so, in the torque limiter mechanism 10, the rotating member 11 only rotates in the direction opposite to the arrow D1 while pushing the first projecting portion 141 and the second projecting portion 142 of the pad 12, and thus the torque limiter mechanism. 10 is not broken, and the overlapped medium M is not damaged.

  As described above, according to the torque limiter mechanism 10 according to the first embodiment, it is possible to suppress a decrease in the braking force that limits the rotational torque of the shaft body.

[Embodiment 2]
The position shifting mechanism 20 of the heavy-running detection mechanism 50 according to the first embodiment uses a pad 12 in which the torque limiter mechanism 10 includes a first pivot support member 121 and a second pivot support member that are pivotally supported by pins 151. The rotating member 11 is sandwiched between the first protrusion 141 and the second protrusion 142 of the pad 12 (see FIG. 5).

  On the other hand, the position shifting mechanism 20B of the heavy-running detection mechanism 50B according to the second embodiment is configured such that the torque limiter mechanism 10B uses the pad 12B configured in a plate shape and presses the pad 12B against the rotating member 11. (See FIG. 9).

  Hereinafter, the configuration of the torque limiter mechanism 10B according to the second embodiment will be described with reference to FIG. FIG. 9 is a diagram illustrating a configuration of a torque limiter mechanism 10B according to the second embodiment.

  As shown in FIG. 9, the torque limiter mechanism 10 </ b> B has a configuration in which a pad 12 </ b> B is disposed below the rotating member 11. The pad 12 </ b> B is a contact member that is formed in a flat plate shape and contacts the outer peripheral surface of the rotating member 11. Here, the upper surface of the pad 12 </ b> B is opposed to the outer peripheral surface of the rotating member 11, and the upper surface functions as a contact surface that contacts the outer peripheral surface of the rotating member 11.

  The pad 12B is supported by a guide member (not shown) so as to be movable in the contact / separation direction (here, the vertical direction) with respect to the rotating member 11.

  A compression spring 18 is disposed below the pad 12B. The compression spring 18 is a biasing member that presses the pad 12 </ b> B against the outer peripheral surface of the rotating member 11. In the example shown in FIG. 9, only one compression spring 18 is shown, but actually, a plurality of compression springs 18 are provided. Each compression spring 18 is configured to press the upper surface of the pad 12 </ b> B against the outer peripheral surface of the rotating member 11 with equal pressure.

  In the torque limiter mechanism 10B, a cam 14B is disposed at a position near the upper surface of the pad 12B and at a position that does not overlap the rotating member 11. The cam 14B is in a contact state when the upper surface of the pad 12B is in contact with the outer peripheral surface of the rotating member 11, and is in a separated state when the upper surface of the pad 12B is separated from the outer peripheral surface of the rotating member 11. It is a switching member that selectively switches the state to one of a contact state and a separation state.

  The cam 14B is pivotally supported by a shaft 232 of a drive unit (not shown) at an eccentric position. The cam 14B is driven away from the position where the free end abuts the upper surface of the pad 12B and the upper surface of the pad 12B with the rotation of the shaft 232 when the driving unit (not shown) rotates in the forward direction or the reverse direction. It pivots between the position to be.

  As shown in FIG. 9A, when the free end of the cam 14B comes into contact with the upper surface of the pad 12B, the cam 14B presses the pad 12B downward to push down the pad 12B. As a result, the pad 12B is in a separated state in which the upper surface is separated from the outer peripheral surface of the rotating member 11. As a result, the torque limiter mechanism 10B enters a state in which the generation of the braking force is turned off.

  On the other hand, when the free end of the cam 14B is separated from the upper surface of the pad 12B as shown in FIG. 9B, the pad 14B is released from the pressing. At this time, the compression spring 18 presses the pad 12B upward, and pushes up the pad 12B in the direction of the arrow G1. As a result, the pad 12 </ b> B is in a contact state in which the upper surface thereof is in contact with the outer peripheral surface of the rotating member 11. As a result, the torque limiter mechanism 10B enters a state in which the generation of the braking force is turned on.

  In such a configuration, the torque limiter mechanism 10B is normally in a state shown in FIG. 9A (when the medium M is not transported).

  For example, when the customer inserts the medium M into the insertion slot 2 (see FIG. 1), the control unit 1 of the automatic transaction apparatus 100 detects this by a sensor (not shown). And the control part 1 operates the drive part 5 (refer FIG. 2), and conveys the medium M from the insertion port 2 toward the inside of an apparatus with the conveyance roller 6. FIG. At this time, when the conveyance roller 6 sandwiches the medium M, the conveyance roller 6b on the driven side is retracted according to the thickness of the medium M.

  When the medium M reaches the position for performing the process of shifting the position of the medium M (specifically, the position of the medium detection sensor 30 on the front side of the position shifting mechanism 20 (see FIG. 1)), the control unit 1 This is detected based on the value of the detection signal output from the detection sensor 30.

  When the control unit 1 detects that the medium M has reached the position where the process for shifting the position of the medium M is performed, the state of the torque limiter mechanism 10B is changed from the state shown in FIG. 9A to the state shown in FIG. 9B. Switch to state.

  In this manner, the automatic transaction apparatus 100 rotates the cam 14B at a timing when the medium M is desired to be separated, and presses the upper surface of the pad 12B against the outer peripheral surface of the rotating member 11.

  The rotating member 11 rotates together with the driven-side transport roller 6b. At this time, since the cross-sectional shape of the rotating member 11 is hexagonal, the rotating member 11 rotates while pushing down the pad 12B on the outer peripheral surface of the maximum diameter portions R1, R2, R3 (see FIG. 4A). Thereby, the rotation member 11 presses the compression spring 18 via the pad 12B, and compresses the compression spring 18.

  Since the upper surface of the pad 12B is pressed against the outer peripheral surface of the rotating member 11 by the compression spring 18, a braking force that restricts the rotation of the shaft body (the rotating shaft (shaft 7) of the rotating member 11) is generated. As a result, the torque limiter mechanism 10B brakes the rotation of the driven-side transport roller 6b.

  In the torque limiter mechanism 10B, the amount of compression of the compression spring 18 increases as the driven roller 6b on the driven side is pushed down according to the thickness of the medium M, as shown in FIG.

  FIG. 10 is a diagram illustrating the relationship between the thickness of the medium M and the braking force of the torque limiter mechanism 10B according to the second embodiment. FIG. 10A shows the state of the torque limiter mechanism 10B when the medium M is thin. FIG. 10B shows the state of the torque limiter mechanism 10B when the medium M is thick.

  In the torque limiter mechanism 10B, as shown in FIG. 10A, when the medium M is thin, the driven-side transport roller 6b is pushed down by the medium M and the compression spring 18 is compressed. Is relatively small.

  On the other hand, in the torque limiter mechanism 10B, as shown in FIG. 10B, when the medium M is thick, the driven-side transport roller 6b is pushed down by the medium M, and the compression spring 18 is compressed. However, the compression amount is larger than the compression amount in the state shown in FIG.

  In the torque limiter mechanism 10B, as the compression amount of the compression spring 18 increases, the pressure with which the compression spring 18 presses the pad 12B against the rotating member 11 increases. In FIG. 10, the pressure when the medium M is thin is “H1”, the pressure when the medium M is thick is “H2”, and the force relationship between “H1” and “H2” is “H2”. > H1 ”.

  The torque limiter mechanism 10 </ b> B can increase the braking force according to the thickness of the medium M because the pressure that the compression spring 18 presses the pad 12 </ b> B against the rotating member 11 increases according to the thickness of the medium M.

  Moreover, in the torque limiter mechanism 10B, compared to the torque limiter mechanism 10B according to the first embodiment, the direction in which the compression spring 18 presses the pad 12B matches the direction in which the driven-side transport roller 6b is pressed against the medium M. Thus, it is possible to increase the pressure of pressing the driven-side transport roller 6b against the medium M.

  The torque limiter mechanism 10B aligns the retracted direction (here, the downward direction) of the driven-side transport roller 6b with the direction in which the pressure that presses the pad 12B against the rotating member 11 by the action of the compression spring 18 increases. There is a need.

  In the second embodiment, the torque limiter mechanism 10B uses the compression spring 18. However, if the direction of pressing the pad 12B against the rotating member 11 is correct, the tension spring is used instead of the compression spring 18. May be used.

  As described above, according to the torque limiter mechanism 10 </ b> B according to the second embodiment, similarly to the torque limiter mechanism 10 according to the first embodiment, it is possible to suppress a decrease in brake force that limits the rotational torque of the shaft body.

  Moreover, according to the torque limiter mechanism 10B, it is possible to increase the pressure for pressing the driven-side transport roller 6b against the medium M. Therefore, according to the torque limiter mechanism 10B, even if the thickness of the medium M is thin and the “frictional force between the medium M and the driven-side transport roller 6b” tends to be insufficient, the medium and the transport roller It is possible to efficiently prevent the occurrence of slippage between the two and the surface of the medium from becoming dirty.

[Embodiment 3]
In the position shifting mechanism 20 of the heavy-running detection mechanism 50 according to the first embodiment, the rotating member 11 of the torque limiter mechanism 10 is fixed to the rotating shaft (shaft 7) of the driven-side transport roller 6b. Is configured to rotate with the rotation of the driven-side transport roller 6b (see FIG. 2).

  On the other hand, in the position shifting mechanism 20C of the heavy-running detection mechanism 50C according to the third embodiment, the rotating member 11C of the torque limiter mechanism 10C is fixed to the rotating shaft (shaft 7) of the driven-side transport roller 6b. First, the rotation member 11C is configured to rotate with the rotation of the connector member 21 by engaging with the connector member 21 that rotates with the rotation of the driven-side transport roller 6b (see FIG. 11). .

  Hereinafter, the configuration of the torque limiter mechanism 10C according to the third embodiment will be described with reference to FIGS. FIGS. 11-13 is a figure which respectively shows the structure of 10 C of torque limiter mechanisms which concern on this Embodiment 3. FIG. The torque limiter mechanism 10C has a configuration in which, for example, the cams 14 and 14B are excluded from the torque limiter mechanism 10 according to the first embodiment or the torque limiter mechanism 10B according to the second embodiment. Here, as shown in FIG. 13, the torque limiter mechanism 10 </ b> C will be described as a configuration in which the cam 14 is excluded from the torque limiter mechanism 10 according to the first embodiment.

  As shown in FIG. 11, the torque limiter mechanism 10 </ b> C includes a connector member 21, a switching lever 22, and a drive unit 24. FIG. 11A shows an overall schematic configuration of the torque limiter mechanism 10C, and FIG. 11B excludes members around the rotating member 11C such as the pad 12C shown in FIG. 11A. The configuration is shown. FIG. 11A shows that the pad 12C is disposed around the rotating member 11C (see FIG. 11B). The configuration of the pad 12C will be described later with reference to FIG. FIG. 11B shows that the rotating member 11 </ b> C is formed in a hexagonal shape and the engaging portion 11 </ b> Ca is provided on the surface facing the connector member 21.

  The connector member 21 is a member that transmits the rotation torque of the rotation shaft (shaft 7) of the driven-side conveyance roller 6b to the rotation member 11C. The connector member 21 is fixed to the shaft 7 and rotates with the rotation of the driven-side transport roller 6b. The connector member 21 corresponds to a “position fixing member” recited in the claims.

  The connector member 21 is provided with an engaging portion 21a on the surface facing the rotating member 11C. The engaging portion 21a is a portion that engages with an engaging portion 11Ca provided on the rotating member 11C. Here, the description will be made assuming that the engaging portion 21a is constituted by a gear.

  On the other hand, the rotating member 11C is not fixed to the rotating shaft (shaft 7) of the driven-side transport roller 6b, and is configured to be movable in the axial direction of the shaft 7. The rotating member 11 </ b> C corresponds to a “moving member” recited in the claims.

  The rotating member 11 </ b> C is provided with an engaging portion 11 </ b> Ca on the surface facing the connector member 21. The engaging portion 11 </ b> Ca is a portion that engages with an engaging portion 21 a provided on the connector member 21. Here, the description will be made assuming that the engaging portion 11Ca is constituted by a gear. The rotating member 11 </ b> C moves in the axial direction of the shaft 7, whereby the engaging portion 11 </ b> Ca engages with the engaging portion 21 a of the connector member 21. The rotating member 11 </ b> C rotates with the rotation of the connector member 21 when the engaging portion 11 </ b> Ca engages with the engaging portion 21 a of the connector member 21.

  The switching lever 22 corresponds to a “lever member” recited in the claims. That is, the switching lever 22 uses the position where the moving member (here, the rotating member 11C) engages with the position fixing member (here, the connector member 21) as the engaging position, and the moving member engages with the position fixing member. This is a member that selectively moves the moving member to either the engaged position or the non-engaged position, with the position not being used as the non-engaged position.

  In the example illustrated in FIG. 11, the switching lever 22 is configured as a long member, and is disposed below the rotating member 11 </ b> C in parallel with the shaft 7. The switching lever 22 is provided with projecting portions 221 and 222 (see FIG. 11B) and a rack portion 223 (see FIG. 11A) on the upper surface thereof.

  The protrusions 221 and 222 (see FIG. 11B) are provided near the end of the upper surface of the switching lever 22 on the side close to the connector member 21. In the example shown in FIG. 11B, the protruding portion 221 is provided on the side closer to the connector member 21 than the protruding portion 222. The protruding portion 221 functions as a pressing portion that comes into contact with the inner surface of the rotating member 11C (the surface on which the engaging portion 11Ca is provided) and separates the rotating member 11C from the connector member 21. On the other hand, the projecting portion 222 abuts on the outer surface of the rotating member 11C (the surface on which the engaging portion 11Ca is not provided) and functions as a pressing portion that presses the rotating member 11C against the connector member 21.

  The rack portion 223 (see FIG. 11A) is provided on the upper surface of the switching lever 22 at a position farther from the connector member 21 than the protruding portions 221 and 222. The rack portion 223 is a gear that meshes with the pinion 241 attached to the rotation shaft of the drive portion 24.

  The drive unit 24 is a component that moves the switching lever 22 and selectively moves the moving member (the rotating member 11 </ b> C) to one of the engagement position and the non-engagement position. The driving unit 24 and the switching lever 22 are preferably configured to retract together with the transport roller 6b when the transport roller 6b on the driven side retracts according to the thickness of the medium M.

  As for the drive part 24, the pinion 241 is attached to the rotating shaft. The drive unit 24 moves the switching lever 22 through the pinion 241 in the direction I1 shown in FIG. 12A or the direction I2 shown in FIG. FIG. 12A shows the state of the torque limiter mechanism 10C when the brake is turned off. FIG. 12B shows a state of the torque limiter mechanism 10C when the brake is turned on.

  In the torque limiter mechanism 10C, when the brake is turned off, the drive unit 24 moves the switching lever 22 in the direction I1 as shown in FIG. Thereby, in the switching lever 22 of the torque limiter mechanism 10C, the protruding portion 221 contacts the inner surface of the rotating member 11C (the surface on the side where the engaging portion 11Ca is provided) so that the rotating member 11C moves in the direction I1. Press on. As a result, the rotating member 11C is separated from the connector member 21.

  On the other hand, in the torque limiter mechanism 10C, when the brake is turned on, as shown in FIG. 12B, the drive unit 24 moves the switching lever 22 in the direction I2. Thereby, in the switching lever 22 of the torque limiter mechanism 10C, the protruding portion 222 abuts on the outer surface of the rotating member 11C (the surface on the side where the engaging portion 11Ca is not provided) and the rotating member 11C is moved to the I2 position. Press in the direction. As a result, the rotating member 11 </ b> C is pressed against the connector member 21. Thereby, the engaging portion 11Ca of the rotating member 11C is engaged with the engaging portion 21a of the connector member 21.

  Note that the torque limiter mechanism 10C is normally in a state shown in FIG. 12A (when the medium M is not transported).

  In the torque limiter mechanism 10C, when the engaging portion 11Ca of the rotating member 11C is engaged with the engaging portion 21a of the connector member 21, the connector member 21 rotates with the rotation of the driven-side transport roller 6b. As the connector member 21 rotates, the rotating member 11C rotates. The torque limiter mechanism 10C brakes the rotation of the rotating member 11C with the pad 12C (see FIGS. 11A and 13).

  FIG. 13 shows a specific configuration of the pad 12C. The pad 12C includes a first shaft support member 121C and a second shaft support member 122C. The first pivot support member 121C and the second pivot support member 122C of the pad 12C are pivotally supported by the pin 151, similarly to the first pivot support member 121 and the second pivot support member 122 of the pad 12 according to the first embodiment. The

  The first shaft support member 121C of the pad 12C corresponds to the first body portion 131C corresponding to the first body portion 131 of the pad 12 according to the first embodiment and the first projecting portion 141 of the pad 12 according to the first embodiment. The first protrusion 141C is provided. That is, the first shaft support member 121C of the pad 12C has a configuration in which the third protrusion 143 is excluded from the first shaft support member 121 of the pad 12 according to the first embodiment.

  On the other hand, the second shaft support member 122C of the pad 12C is provided on the second body part 132C corresponding to the second body part 132 of the pad 12 according to the first embodiment and the second protrusion part 142 of the pad 12 according to the first embodiment. It has a configuration provided with a corresponding second protrusion 142C. That is, the second pivot support member 122C of the pad 12C has a configuration in which the fourth protrusion 144 is excluded from the second pivot support member 122 of the pad 12 according to the first embodiment.

  As shown in FIG. 13, the torque limiter mechanism 10 </ b> C is configured to sandwich the outer peripheral surface of the rotating member 11 </ b> C between the first protrusion 141 </ b> C and the second protrusion 142 </ b> C of the pad 12 </ b> C.

  Unlike the torque limiter mechanism 10 according to the first embodiment, the torque limiter mechanism 10C does not have the cam 14. Therefore, the pad 12 </ b> C is in a state where the first protrusion 141 </ b> C and the second protrusion 142 </ b> C are always closed by the action of the torsion spring 13.

  Therefore, the torque limiter mechanism 10C has the opposite side of the rotating member 11C in which the first projecting portion 141C and the second projecting portion 142C of the pad 12C are formed in a hexagonal shape even when the pad 12C is completely closed. A stopper 25a for defining the position of the first projecting portion 141C and a stopper 25b for defining the position of the second projecting portion 142C are provided so as not to be sandwiched. Hereinafter, the stoppers 25a and 25b are collectively referred to as “stopper 25”.

  The distance between the outermost ends of the stopper 25a and the stopper 25b is slightly longer than the distance t1 (see FIG. 13A) of the opposite side of the rotating member 11C, and the diagonal distance of the rotating member 11C. A value shorter than t2 (see FIG. 13B) is set.

  In the torque limiter mechanism 10C, as shown in FIG. 13A, even if the pad 12C is completely closed, the distance between the outermost ends of the stoppers 25a and 25b is the distance t1 between the opposite sides of the rotating member 11C. Therefore, a slight gap can be formed between the first projecting portion 141C and the second projecting portion 142C and the opposite side of the rotating member 11C.

  Further, as shown in FIG. 13B, the torque limiter mechanism 10C has a rotating member 11C that rotates, and the outer peripheral surfaces of the maximum diameter portions R1, R2, and R3 (see FIG. 4A) of the rotating member 11C. When pushing away the first protrusion 141C and the second protrusion 142C of the pad 12C, the distance between the outermost ends of the stoppers 25a and 25b is shorter than the diagonal distance t2 of the rotating member 11C. It is possible not to disturb the operation.

  In such a configuration, when the medium M is transported on the transport path 3 by the transport roller 6, the torque limiter mechanism 10C rotates only the driven-side transport roller 6b and the connector member 21, and the rotating member 11C rotates. do not do.

  The torque limiter mechanism 10C moves the switching lever 22 at the timing at which the medium M is to be separated, and engages the engaging portion 11Ca of the rotating member 11C and the engaging portion 21a of the connector member 21. As a result, in the torque limiter mechanism 10C, the driven-side transport roller 6b and the rotating member 11C rotate together.

  At this time, in the torque limiter mechanism 10C, as in the torque limiter mechanism 10 according to the first embodiment, the outer peripheral surface of the maximum diameter portion R1, R2, R3 (see FIG. 4A) of the rotating member 11C is the first protrusion of the pad 12C. The brake force is generated by pushing away the portion 141C and the second projecting portion 142C.

  The torque limiter mechanisms 10 and 10B according to the first and second embodiments need to use strong springs 13 and 18 when a large braking force is required. The torque limiter mechanisms 10 and 10B according to the first and second embodiments open and close (or retract) the pads 12 and 12B using the cams 14 and 14B. In order to open and close (or retract) 12B, a large driving force for rotating cams 14 and 14B is required. Therefore, in this case, the torque limiter mechanisms 10 and 10B according to the first and second embodiments require the driving unit 23 having a large driving force or a driving unit (not shown).

  On the other hand, the torque limiter mechanism 10C according to the third embodiment is configured such that the lever member 22 moves the rotating member 11C while the pad 12C is closed. Therefore, in the torque limiter mechanism 10C, regardless of whether or not a large braking force is required (that is, whether or not the strong springs 13 and 18 need to be used), the lever member 22 rotates. Only a sufficient driving force is required to move the moving member 11C. Therefore, the torque limiter mechanism 10C can use the drive unit 24 with a small drive force.

  As described above, according to the torque limiter mechanism 10 </ b> C according to the third embodiment, similarly to the torque limiter mechanism 10 according to the first embodiment, it is possible to suppress a decrease in brake force that limits the rotational torque of the shaft body.

  Moreover, according to the torque limiter mechanism 10C, it is possible to use the driving unit 24 with a small driving force regardless of whether or not a large braking force is required.

  The present invention is not limited to the above-described embodiment, and various changes and modifications can be made without departing from the gist of the present invention.

<First Modification>
In the first to third embodiments, the rotating members 11 and 11C are formed in a hexagonal cross section. However, the rotating members 11 and 11C may be formed in a polygonal shape other than a hexagon, such as a triangle, a quadrangle, or an octagon, for example. That is, the turning members 11 and 11C may be formed in a polygonal shape having a cross-sectional shape of a triangle or more. The rotating members 11 and 11C may be formed in an elliptical or oval cross-sectional shape. These shapes can obtain the same effect as the case where the cross-sectional shape is a hexagon.

<Second Modification>
The torque limiter mechanisms 10, 10 </ b> B according to the first and second embodiments remove a cam 14 and transmit a clutch mechanism (not shown) that transmits the driving force of the driving unit 5 to the transport roller 6 b on the driven side. And the driven-side transport roller 6b may be added.

  In the torque limiter mechanism of this configuration, when the clutch mechanism is connected, a braking force is always generated in the rotating member 11, but a driving torque larger than the braking force is transmitted to the driven-side transport roller 6b. The In the torque limiter mechanism configured as described above, the driving torque is not transmitted to the driven-side transport roller 6b when the clutch mechanism disconnects the clutch. At this time, the torque limiter mechanism having this configuration can separate the medium M because only the braking force works.

<Third Modification>
The torque limiter mechanism 10C according to the third embodiment is configured with the connector member 21 as a position fixing member and the rotating member 11C as a moving member. However, the torque limiter mechanism 10C can also be configured with the connector member 21 as a moving member and the rotating member 11C as a position fixing member.

  For example, the torque limiter mechanism 10C fixes the rotating member 11C only in the axial direction of the driven-side transport roller 6b and allows it to rotate in the rotating direction, and fixes the connector member 21 only in the rotating direction to axially You may make it the structure which can move to. The torque limiter mechanism having this configuration is configured to move the connector member 21 to engage with the rotating member 11C by switching the switching lever 22.

  In the torque limiter mechanism having this configuration, when the medium M is transported by the transport roller 6, only the transport roller 6b and the connector member 21 on the driven side rotate, and the rotating member 11C does not rotate.

  The torque limiter mechanism having this configuration moves the switching lever 22 at a timing when the medium M is desired to be separated, and engages the rotation member 11C with the connector member 21, thereby driving the transport roller 6b on the driven side and the rotation member. 11C will rotate together.

<Fourth Modification>
The torque limiter mechanisms 10, 10 </ b> B, and 10 </ b> C according to the first to third embodiments use a driven-side transport roller 6 b that is disposed to face the drive-side transport roller 6 a as a member that applies a braking force to the medium M.

  However, the member that applies the braking force to the medium M is not necessarily the driven roller 6b. That is, the torque limiter mechanisms 10, 10 </ b> B, and 10 </ b> C according to the first to third embodiments may be configured to apply a braking force to the medium M using a separation roller for medium separation that is different from the conveyance roller 6 b.

  For example, in the torque limiter mechanisms 10, 10 </ b> B, and 10 </ b> C according to the first to third embodiments, one to a plurality of sets of separation rollers are arranged to face each other via the conveyance path 3 so as to form one set with two rollers. You may do it. The torque limiter mechanism having this configuration is usually configured such that the separation roller idles.

  The separation roller is not necessarily configured as a single set of two rollers if a desired frictional force can be obtained between the roller and the medium M by a method such as pressing the medium M against the carrying guide 3a. It does not have to be. In this case, the torque limiter mechanism may switch the brake depending on whether or not the separation roller is pressed against the medium M.

<Fifth Modification>
In the torque limiter mechanisms 10 and 10B according to the first and second embodiments, the rotating member 11 is attached to the shaft 7 of the driven conveyance roller 6b, and the rotational torque of the driven conveyance roller 6b is transmitted to the shaft 7. Thus, the rotation member 11 is rotated.

  However, for example, in the torque limiter mechanisms 10 and 10B according to the first and second embodiments, the rotation member 11 is attached to a shaft different from the shaft 7 of the driven conveyance roller 6b, and a transmission mechanism such as a gear or a belt is provided. Alternatively, the rotation member 11 may be rotated by transmitting the rotational torque of the driven-side transport roller 6b to the shaft.

<Sixth Modification>
In the torque limiter mechanisms 10 and 10B according to the first and second embodiments, the rotating member 11 is attached to the shaft 7 of the driven conveyance roller 6b, and the rotational torque of the driven conveyance roller 6b is transmitted to the shaft 7. Thus, the rotation member 11 is rotated.

However, for example, when the torque limiter mechanisms 10 and 10B according to the first and second embodiments have a transport belt for transporting the medium M, the rotating member 11 is attached to the pulley shaft of the transport belt so that the transport belt travels. The rotating member 11 may be configured to rotate in conjunction with each other.
The same applies to other conveying methods in the case of a rotating body.

DESCRIPTION OF SYMBOLS 1 Control part 2 Insertion port 3 Conveyance path 3a Conveyance guide which comprises a conveyance path 5 Drive part 6 (6a) Driving-side conveyance roller 6 (6b) Driven-side conveyance roller (rotating body)
7 Shaft
8 Frame (support member)
9 Spring 10, 10B, 10C Torque limiter mechanism 11, 11C Rotating member 11Ca Engaging portion 12, 12C Pad (contact member)
12B pad (plate-like contact member)
13, 13C Torsion spring (biasing member)
18 Compression spring (biasing member)
14, 14B Cam (switching member)
20, 20B, 20C Position shifting mechanism 21 Connector member 21a Engaging portion 22 Switching lever (lever member)
23, 24 Drive unit 25 Stopper 30 Medium detection sensor 40 Determination unit 50, 50B, 50C Heavy travel detection mechanism 81, 82 First support unit, second support unit 81a, 81b, 82a, 82b Circular hole 100 Automatic transaction device 121, 122, 121C, 122C First and second shaft support members 131, 132, 131C, 132C First and second body parts 141, 142, 143, 144 First to fourth projecting parts 151 Pin 151a Opening / closing fulcrum 152 Nut 161 162 Circular hole 221, 222 Protruding part 223 Rack part 231 Shaft 241 Pinion M Medium R1, R2, R3 Maximum diameter part

Claims (18)

In the torque limiter mechanism that limits the rotational torque of the shaft body,
A non-circular rotating member that rotates with the rotation of the shaft;
A contact member that contacts the outer peripheral surface of the rotating member;
An urging member that urges the abutting member in a direction in which the abutting member abuts on an outer peripheral surface of the rotating member;
The contact member intermittently restricts the rotational torque of the shaft body by the contact surface contacting the outer peripheral surface of the rotating member as the shaft body rotates. Torque limiter mechanism. In the torque limiter mechanism that limits the rotational torque of the shaft body,
A non-circular connector member that rotates as the shaft rotates.
A rotating member that rotates as the connector member rotates by engaging with the connector member;
A contact member that contacts the outer peripheral surface of the rotating member;
An urging member that urges the abutting member in a direction in which the abutting member abuts on an outer peripheral surface of the rotating member;
When the connector member and the rotation member are engaged, the contact member is brought into contact with the outer peripheral surface of the rotation member as the shaft body rotates. The torque limiter mechanism characterized by intermittently limiting the rotational torque of the shaft body. The torque limiter mechanism according to claim 2,
The connector member and the rotating member are both provided on the same shaft body, and either one is configured as a position fixing member fixed at a predetermined position in the axial direction of the shaft body. And the other is configured as a moving member that is movable in the axial direction of the shaft body,
Further, a position where the moving member engages with the position fixing member is set as an engaging position, a position where the moving member does not engage with the position fixing member is set as a non-engaging position, and the moving member is set to the engaging position and A torque limiter mechanism comprising a lever member that selectively moves to any one of the non-engagement positions. The torque limiter mechanism according to any one of claims 1 to 3,
The rotating member is formed such that a distance between two sides intersecting a plane passing through the central axis of rotation and the outer peripheral surface is an outer diameter, and a cross-sectional shape thereof is noncircular around the central axis. By being done, it is divided into a maximum diameter portion where the value of the outer diameter is maximum and a small diameter portion where the value of the outer diameter is smaller than the maximum diameter portion,
As the shaft member rotates, the contact surface alternately contacts the outer peripheral surface of the maximum diameter portion and the outer peripheral surface of the small diameter portion of the rotating member, thereby A torque limiter mechanism characterized by intermittently limiting the rotational torque of the shaft body. In the torque limiter mechanism according to any one of claims 1 to 4,
The contact member is constituted by a first pivot support member and a second pivot support member that are pivotally supported by an opening / closing fulcrum,
The first shaft support member includes a first body portion that is pivotally supported by the opening and closing fulcrum, and a first projecting portion that projects from the first body portion in a plane perpendicular to the shaft support direction of the opening and closing fulcrum. Prepared,
The second shaft support member is perpendicular to the shaft support direction of the opening and closing fulcrum so as to face the second body portion pivotally supported by the opening and closing fulcrum and the first projecting portion via the rotating member. A second projecting portion projecting from the second body portion in a plane,
The urging member presses the first projecting portion and the second projecting portion in a proximity direction to bring them close to each other,
The torque limiter mechanism, wherein both opposing surfaces of the first projecting portion and the second projecting portion function as the contact surfaces that contact the outer peripheral surface of the rotating member. The torque limiter mechanism according to claim 5,
The rotating member is supported by a support member in a state in which the rotating member can be retracted in a retracting direction perpendicular to the transport surface of the medium in the vicinity of a transport path through which the medium is transported. And
The opening / closing fulcrum is disposed in the retracting direction of the rotating member,
The first projecting portion and the second projecting portion are set such that the distance between both opposing surfaces is narrower than the outer diameter of the smallest diameter portion at which the value of the outer diameter of the rotating member is minimized,
The urging member moves the opposing surfaces of the first projecting portion and the second projecting portion of the rotating member when the rotating member approaches the opening / closing fulcrum as the rotating member is retracted. A torque limiter mechanism characterized in that the pressure to be brought into contact with the outer peripheral surface increases. In the torque limiter mechanism according to claim 5 or 6,
Furthermore, a state where the opposing surfaces of the first projecting portion and the second projecting portion are in contact with the outer peripheral surface of the rotating member is defined as an abutting state, and the opposing surfaces of the first projecting portion and the second projecting portion are A state where the rotating member is separated from the outer peripheral surface is set as a separated state, and the state of the first projecting portion and the second projecting portion is selectively switched to one of the contact state and the separated state. A torque limiter mechanism comprising a switching member. The torque limiter mechanism according to claim 7,
The first shaft support member projects from the first body portion in a plane perpendicular to the shaft support direction of the opening and closing fulcrum and in a direction different from the projecting direction of the first projecting portion. Part
The second shaft support member is disposed in a plane perpendicular to the shaft support direction of the opening / closing fulcrum so as to face the third protrusion, and with respect to the protrusion direction of the second protrusion. A fourth projecting portion projecting from the second body portion in a direction equivalent to an inclination angle between the projecting direction of the one projecting portion and the projecting direction of the third projecting portion;
The switching member is disposed between the opposing surfaces of the third projecting portion and the fourth projecting portion such that an outer peripheral surface thereof contacts both opposing surfaces of the third projecting portion and the fourth projecting portion. A torque limiter mechanism characterized in that the torque limiter mechanism is configured as a cam member. The torque limiter mechanism according to claim 8, wherein
The switching member configured as the cam member is
When the outer peripheral surface abuts against the opposing surfaces of the third projecting portion and the fourth projecting portion, the first projecting portion and the second projecting portion are moved away from each other against the pressing of the biasing member. Spread and make the state of the first protrusion and the second protrusion into the separated state,
On the other hand, when the outer peripheral surface is separated from the opposing surfaces of the third protrusion and the fourth protrusion, the first protrusion and the second protrusion are pushed back in the proximity direction by the pressing of the biasing member. Thus, the torque limiter mechanism is characterized in that the first protrusion and the second protrusion are brought into the contact state. The torque limiter mechanism according to claim 5,
The rotating member is supported by a support member in a state in which the rotating member can be retracted in a retracting direction perpendicular to the transport surface of the medium in the vicinity of a transport path through which the medium is transported. And
The opening / closing fulcrum is disposed in the retracting direction of the rotating member,
The first projecting portion and the second projecting portion are set such that the distance between the opposing surfaces is wider than the outer diameter of the smallest diameter portion at which the value of the outer diameter of the rotating member is minimized,
Furthermore, the interval between the opposing surfaces of the first protrusion and the second protrusion is smaller than the outer diameter of the maximum diameter portion of the rotating member, and more than the outer diameter of the small diameter portion of the rotating member. And a stopper for stopping the first projecting portion and the second projecting portion pressed in the proximity direction by the biasing member at a wider position. In the torque limiter mechanism according to any one of claims 1 to 4,
The contact member is configured as a plate-like member urged in the direction of the rotating member by the urging member,
The torque limiter mechanism according to claim 1, wherein a surface of the plate-like member that faces the rotating member functions as the contact surface that contacts the outer peripheral surface of the rotating member. The torque limiter mechanism according to claim 11,
The rotating member is supported by a support member in a state in which the rotating member can be retracted in a retracting direction perpendicular to the transport surface of the medium in the vicinity of a transport path through which the medium is transported. And
The plate-like member and the biasing member are disposed on the retraction direction of the rotating member,
As the urging member is retracted, the urging member presses the urging member through the plate-like member to increase the amount of compression of the urging member, A torque limiter mechanism characterized in that the pressure that causes the opposing surface of the plate-like member to abut against the outer peripheral surface of the rotating member increases. The torque limiter mechanism according to claim 11 or 12,
Further, the state in which the opposing surface of the plate-like member is in contact with the outer peripheral surface of the rotating member is defined as a contact state, and the state in which the opposing surface of the plate-shaped member is separated from the outer peripheral surface of the rotating member is separated. And a switching member that selectively switches the state of the plate-like member to one of the contact state and the separated state. The torque limiter mechanism according to claim 13,
The torque limiter mechanism, wherein the switching member is configured as a cam member provided in the vicinity of the plate-like member so that an outer peripheral surface thereof is in contact with an opposing surface of the plate-like member. The torque limiter mechanism according to claim 14,
The switching member configured as the cam member is
When the outer peripheral surface is in contact with the opposing surface of the plate-like member, the plate-like member is moved away from the outer peripheral surface of the rotating member against the pressing of the biasing member, The state of the plate-like member is changed to the separated state,
On the other hand, when the outer peripheral surface is separated from the opposing surface of the plate-shaped member, the plate-shaped member is moved in the proximity direction to be close to the outer peripheral surface of the rotating member by the pressing of the biasing member, A torque limiter mechanism characterized in that a plate-like member is brought into the contact state. The torque limiter mechanism according to any one of claims 1 to 15,
The torque limiter mechanism, wherein the turning member is formed so that a cross-sectional shape thereof is any one of a polygon having a triangle shape or more, an elliptical shape, and an oval shape. A plurality of the medium, comprising: a rotating body that comes into contact with a conveying surface of a medium traveling on the conveying path; a shaft body that rotates as the rotating body rotates; and a torque limiter mechanism that limits a rotational torque of the shaft body. A position shifting mechanism for shifting the position of each medium when
A medium detection sensor for detecting the presence or absence of the medium;
From the detection result of the medium detection sensor, a determination unit that determines whether the medium is overrun based on whether the length of the medium is a predetermined length,
The torque limiter mechanism includes a non-circular rotating member that rotates with the rotation of the shaft body, an abutting member that abuts on an outer peripheral surface of the rotating member, and the abutting member that is disposed on the rotating member. An urging member for urging in a direction to contact the outer peripheral surface;
The contact member intermittently restricts the rotational torque of the shaft body by the contact surface contacting the outer peripheral surface of the rotating member as the shaft body rotates. Heavy running detection mechanism. A plurality of the medium, comprising: a rotating body that comes into contact with a conveying surface of a medium traveling on the conveying path; a shaft body that rotates as the rotating body rotates; and a torque limiter mechanism that limits a rotational torque of the shaft body. A position shifting mechanism for shifting the position of each medium when
A medium detection sensor for detecting the presence or absence of the medium;
From the detection result of the medium detection sensor, a determination unit that determines whether the medium is overrun based on whether the length of the medium is a predetermined length,
The torque limiter mechanism includes a non-circular rotating member that rotates with the rotation of the shaft body, an abutting member that abuts on an outer peripheral surface of the rotating member, and the abutting member that is disposed on the rotating member. An urging member for urging in a direction to contact the outer peripheral surface;
The contact member intermittently restricts the rotational torque of the shaft body by the contact surface contacting the outer peripheral surface of the rotating member as the shaft body rotates. Automatic transaction device.

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