JP7462501B2 - Reciprocating linear motion mechanism for can forming device and can forming device - Google Patents

Description

The present invention relates to a reciprocating linear motion mechanism for a can forming device and a can forming device.

Conventionally, bottomed cylindrical DI (Drawing & Ironing) cans are known. DI cans (hereinafter sometimes simply referred to as cans) are manufactured by subjecting a circular aluminum alloy blank to cupping, DI, and other processes. In cupping, the blank is drawn into a cup-shaped body. In DI, the cup-shaped body is pressed with a cup holder and drawn and ironed between a punch and a die. After DI, air is expelled from the punch into the inside of the can to release it from the punch.

Known can forming apparatuses for performing DI processing on a cup-shaped body include those described in Patent Documents 1 and 2. The can forming apparatus uses a reciprocating linear motion mechanism to linearly reciprocate a punch in a predetermined stroke direction via a ram shaft. The can forming apparatus also uses an air ejection mechanism to release (blow off) the formed can from the punch.
In Patent Documents 1 and 2, an air discharge mechanism supplies air to the punch through a ram shaft from outside the reciprocating linear motion mechanism.

JP 2005-169485 A Patent No. 3158312

Conventional can forming equipment has a structure that supplies air to the ram shaft from outside the reciprocating linear motion mechanism, which has many moving parts, and requires frequent maintenance and part replacement. As a result, a structure that supplies air to the ram shaft through the inside of the reciprocating linear motion mechanism has been considered, but even in this case, it is necessary to blow off the formed cans at the right time.

One of the objectives of the present invention is to provide a reciprocating linear motion mechanism for a can forming device that can supply air to the ram shaft through the inside of the reciprocating linear motion mechanism and can blow off the formed cans in a timely manner, and a can forming device.

One aspect of the reciprocating linear motion mechanism of the can forming apparatus of the present invention includes a housing having an internal gear centered on a first central axis, a first rotating body located inside the housing in a first radial direction perpendicular to the first central axis and connected to the housing so as to be rotatable relative to the housing about the first central axis, a second rotating body having an external gear centered on a second central axis parallel to the first central axis and meshing with the internal gear, and connected to the first rotating body so as to be rotatable relative to the first rotating body about the second central axis, a ram shaft connecting part connected to the second rotating body and centered on a third central axis parallel to the second central axis, and configured to perform reciprocating linear motion along a predetermined direction of the first radial direction while rotating about the third central axis, a valve part connected to the ram shaft connecting part, and an air supply path passing through each of the first rotating body, the second rotating body, the ram shaft connecting part, and the valve part, wherein the valve part is switched between a circulation mode in which air can pass through an interior thereof and a blockage mode in which air cannot pass through an interior thereof, depending on the rotational position of the ram shaft connecting part about the third central axis.
Furthermore, one aspect of the can forming apparatus of the present invention comprises a reciprocating linear motion mechanism of the can forming apparatus described above, a ram shaft extending in the predetermined direction and having one end connected to the ram shaft connecting portion, a punch arranged at the other end of the ram shaft, a die having a through hole through which the punch is inserted, a cup holder pressed against the end face of the die into which the through hole opens, and an air discharge mechanism that supplies air to the punch through an interior of the reciprocating linear motion mechanism of the can forming apparatus and the ram shaft, and the air discharge mechanism includes the air supply path.

In the present invention, the air supply passage passes through the inside of the reciprocating linear motion mechanism, so air can be supplied to the punch from inside the reciprocating linear motion mechanism through the ram shaft. Compared to the conventional structure in which air is supplied to the ram shaft from outside the reciprocating linear motion mechanism, the present invention reduces the number of moving parts and the frequency of maintenance and part replacement.

In the present invention, the valve unit is switched between a flow mode and a cutoff mode depending on the rotational position of the ram shaft connecting part about the third central axis. In other words, the supply and cutoff of air from the air supply path to the ram shaft is switched depending on whether the valve unit is in the flow mode or the cutoff mode. In more detail, when the ram shaft connecting part is caused to perform a reciprocating linear motion along a predetermined direction (stroke direction) while rotating about the third central axis, air is supplied to the ram shaft through the valve unit in a predetermined region in the stroke direction, and the supply of air to the ram shaft through the valve unit is cut off in other regions different from the predetermined region.

Unlike the present invention, which uses, for example, a solenoid valve, a sensor, and a control unit to electrically synchronize the discharge of air with the operation of the reciprocating linear motion mechanism, the present invention can mechanically synchronize the operation of the reciprocating linear motion mechanism and use a simple structure to timely discharge air from the punch into the inside of the can. For example, even if the can forming speed is changed, complex adjustment work is not required to synchronize the timing of the air discharge, and the formed can can be blown off in a timely manner.

In the reciprocating linear motion mechanism of the can forming device, the valve unit has a ram shaft fixing unit and a rotating unit connected to the ram shaft connecting unit and capable of rotating relative to the ram shaft fixing unit around the third central axis, the ram shaft fixing unit has an outer cylinder unit centered on the third central axis and an air long hole penetrating the outer cylinder unit in a third radial direction perpendicular to the third central axis and extending around the third central axis, the rotating unit has an inner cylinder unit located inside the outer cylinder unit in the third radial direction, an axial flow path extending axially inside the inner cylinder unit and connecting to the air flow path of the ram shaft connecting unit, and a radial flow path extending in the third radial direction inside the inner cylinder unit and opening to the axial flow path and the outer circumferential surface of the inner cylinder unit, and it is preferable that the radial flow path communicates with the air long hole within a predetermined range around the third central axis.

In this case, the rotating part rotates around the third central axis together with the ram shaft connecting part relative to the ram shaft fixed part, and while the radial flow path and the long air hole are in communication within a predetermined range around the third central axis, the valve part is in the flow mode and air is supplied from the air supply path to the ram shaft.
In addition, while the rotating part rotates around the third central axis together with the ram shaft connecting part relative to the ram shaft fixed part, and communication between the radial flow path and the long air hole is blocked in a range other than the specified range around the third central axis, the valve part is set in the blocking mode, and the supply of air from the air supply path to the ram shaft is blocked.
According to the above-described configuration of the present invention, the formed can can be blown off stably and timely with a simple structure.

It is preferable that the reciprocating linear motion mechanism of the can forming device is capable of adjusting the position of the air slot about the third central axis by rotating the outer tube about the third central axis.

In this case, the timing at which the long air hole communicates with the radial flow path can be adjusted by adjusting the position of the long air hole around the third central axis. In other words, the timing at which air is discharged into the inside of the can can be adjusted by the simple operation of rotating the outer cylinder part around the third central axis. This allows the can to be stably blown off from the punch after molding.

In the reciprocating linear motion mechanism of the can forming device, the ram shaft fixing portion has the outer tube portion, a fixed tube portion located outside the outer tube portion in the third radial direction, and a fixing screw that fixes the fixed tube portion and the outer tube portion, and the fixed tube portion has an adjustment long hole that penetrates the fixed tube portion in the third radial direction and extends around the third central axis, and it is preferable that the fixing screw is inserted into the adjustment long hole and screwed to the outer tube portion.

In this case, the long air hole can be positioned around the third central axis by rotating the outer cylinder part relative to the fixed cylinder part around the third central axis and fixing the fixed cylinder part and the outer cylinder part with a fixing screw while the position of the long air hole around the third central axis is adjusted. In other words, with a simple configuration, the position of the long air hole around the third central axis can be adjusted and fixed in position.

According to one embodiment of the reciprocating linear motion mechanism of a can forming device and a can forming device of the present invention, air can be supplied to the ram shaft through the inside of the reciprocating linear motion mechanism, and the formed can can be blown off in a timely manner.

FIG. 1 is a schematic diagram showing a can forming apparatus according to the present embodiment. FIG. 2 is a perspective view showing a reciprocating linear motion mechanism of the can forming apparatus of this embodiment. FIG. 3 is a front view showing the reciprocating linear motion mechanism of the can forming apparatus of this embodiment. FIG. 4 is a cross-sectional view showing a cross section taken along line IV-IV of FIG. FIG. 5 is a perspective view showing the first rotor, the convex portion, the first weight portion, and the shaft body. FIG. 6 is a perspective view showing the second rotating body, the recess, the second weight portion, and the ram shaft connecting portion. FIG. 7 is a front view showing the valve portion. FIG. 8 is a top view showing the valve portion. FIG. 9 is a cross-sectional view showing a cross section taken along line IX-IX of FIG. FIG. 10 is a cross-sectional view showing the X-X cross section of FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A can forming apparatus 1 according to one embodiment of the present invention and a reciprocating linear motion mechanism 10 (hereinafter, may be simply referred to as the reciprocating linear motion mechanism 10) of the can forming apparatus 1 will be described with reference to the drawings.
As shown in FIG. 1, the can forming apparatus 1 of this embodiment is a DI can manufacturing apparatus that performs DI processing on a cup-shaped body W, which is a workpiece, to produce a DI can 100.

First, the DI can 100 will be described.
The DI can 100 is a cylindrical shape with a bottom. The DI can 100 is used for can bodies such as two-piece cans and bottle cans in which contents such as beverages are filled and sealed. In the case of a two-piece can, the can body includes the DI can 100 and a disk-shaped can lid that is wrapped around the open end of the DI can 100. In the case of a bottle can, the can body includes a bottle can body formed by necking and threading the DI can 100, and a cap that is screwed onto the open end of the bottle can body.

The DI can 100 is formed into a bottomed cylindrical shape by performing a cupping process (drawing process) and a DI process (drawing and ironing process) on a disk-shaped blank punched out of a plate material such as an aluminum alloy. Specifically, in the case of a two-piece can, for example, the DI can 100 is manufactured through a plate material punching process, a cupping process, a DI process, a trimming process, a printing process, a painting process, a necking process, and a flanging process, in that order.

In the process of manufacturing the DI can 100, a blank is drawn (cupped) using a cupping press to form a cup-shaped body W. In other words, the cup-shaped body W is a formed intermediate body produced in the process of transitioning from the blank to the DI can 100 in the cupping process. The cup-shaped body W is a bottomed cylinder with a smaller peripheral wall height (length along the can axis) and a larger diameter than the DI can 100.

Next, the can forming apparatus 1 will be described.
The can forming apparatus 1 is used in the DI process, and performs DI processing, i.e., drawing (redrawing) and ironing, on the cup-shaped body W to form a DI can 100 having a peripheral wall greater in height and a smaller in diameter than the cup-shaped body W. Furthermore, in the DI process, the can forming apparatus 1 forms the bottom of the DI can 100 into a dome shape.

The can forming apparatus 1 includes a reciprocating linear motion mechanism 10, a ram shaft 3 extending in a predetermined direction (hereinafter may be referred to as a stroke direction S) in which a ram shaft connecting part 35 of the reciprocating linear motion mechanism 10, which will be described later, is caused to linearly reciprocate, and having one end connected to the ram shaft connecting part 35, a punch 2 arranged at the other end of the ram shaft 3, a ram bearing 5 supporting the ram shaft 3 so as to be able to reciprocate along the axial direction of a central axis O of the ram shaft 3, a die 8 having a through hole 7 into which the punch 2 is inserted, a cup holder 6 pressed against an end face 9 into which the through hole 7 of the die 8 opens, a domer 11 that sandwiches the bottom of a DI can 100 between the punch 2 and the domer 11 to form it into a dome shape, and an air discharge mechanism 70 that supplies air to the punch 2 through the inside of the reciprocating linear motion mechanism 10 and the ram shaft 3.
The central axes O of the ram shaft 3, punch 2, ram bearing 5, through hole 7 of the die 8, cup holder 6, and domer 11 are arranged coaxially with one another. In this embodiment, the central axis O, which is the common axis of these members, extends in the horizontal direction.

The can forming device 1 also includes a cup feeder (not shown) that supplies a cup-shaped body W onto the end surface 9 of the die 8, a receiving seat (not shown) that holds the cup-shaped body W on the end surface 9, a can conveying mechanism (not shown) that conveys the formed DI can 100 to the outside of the device, a cup holder driving mechanism (not shown) that is driven in synchronization with the reciprocating linear motion mechanism 10 and moves the cup holder 6 back and forth in the axial direction of the central axis O with a stroke length different from that of the ram shaft connection part 35 of the reciprocating linear motion mechanism 10, and a driving source (not shown) such as a drive motor.

The reciprocating linear motion mechanism 10 converts a rotational driving force about a first central axis C1 input from a driving source into reciprocating linear motion in a stroke direction S along a central axis O, and outputs the reciprocating linear motion to a ram shaft connecting portion 35. A specific configuration of the reciprocating linear motion mechanism 10 will be described separately later.
The ram shaft 3 has a shaft shape extending along the central axis O. The ram shaft 3 is slidably supported by a pair of ram bearings 5 that are arranged spaced apart from each other in the axial direction of the central axis O.
The punch 2 has a cylindrical or columnar shape extending along a central axis O.

The pair of ram bearings 5 are arranged between the reciprocating linear motion mechanism 10 and the die 8 in the axial direction of the central axis O. Of the pair of ram bearings 5, one ram bearing 5 arranged closer to the die 8 is the front bearing 5F, and the other ram bearing 5 arranged closer to the reciprocating linear motion mechanism 10 is the rear bearing 5R. The front bearing 5F and the rear bearing 5R have a fluid bearing structure, such as a hydrostatic bearing or hydrostatic bearing.

A plurality of dies 8 are provided in line in the axial direction of the central axis O. Each of the plurality of dies 8 has a through hole 7 having a circular cross section penetrating the die 8 in the axial direction of the central axis O. The plurality of dies 8 includes one redrawing die 8A and a plurality of ironing dies (ironing dies) 8B located closer to the domer 11 than the redrawing die 8A. Although not shown in particular, a pilot ring is disposed on the domer 11 side of each ironing die 8B. The provision of the pilot ring prevents the punch 2 from contacting each ironing die 8B due to the impact when the DI can 100 leaves (passes through) each ironing die 8B during molding.
During forming, a coolant liquid is supplied to the redrawing die 8A and each ironing die 8B for lubrication and cooling.

The cup holder 6 has a cylindrical cup holder sleeve 6a extending in the axial direction of the central axis O. The cup holder sleeve 6a is fitted onto the outside of the punch 2 and is slidable in the axial direction of the central axis O relative to the punch 2. The cup holder sleeve 6a is inserted into the inside of a cup-shaped body W arranged on an end face 9 of the redrawing die 8A and holds the bottom wall of the cup-shaped body W by pressing it against the end face 9. In other words, the cup holder 6 supports the cup-shaped body W by pressing the bottom wall of the cup-shaped body W against the end face 9 facing the reciprocating linear motion mechanism 10 of the die 8.
Although not specifically shown, the cup holder drive mechanism converts the rotational drive force transmitted from the drive source via the reciprocating linear motion mechanism 10 into reciprocating motion in the axial direction of the central axis O, thereby moving the cup holder 6 back and forth in a linear manner in the axial direction of the central axis O.

The domer 11 is a mold that forms the bottom of the DI can 100. The domer 11 is substantially cylindrical and extends in the axial direction of the central axis O. When the punch 2 is positioned at the forward end position in the stroke direction S, the domer 11 faces the punch 2 in the axial direction of the central axis O.

The air discharge mechanism 70 discharges air from air discharge holes 71 opening on at least one of the tip surface and the outer peripheral surface of the punch 2, thereby releasing the DI can 100 from the punch 2. The air discharge mechanism 70 has air discharge holes 71 passing through the inside of the punch 2 and opening on the outer surface of the punch 2, an air supply path 28 (see FIGS. 4 and 9 ), which will be described later, passing through the inside of the reciprocating linear motion mechanism 10, an air communication path 72 passing through the inside of the ram shaft 3 and communicating between the air discharge hole 71 and the air supply path 28, and an air supply source (not shown). In other words, the air discharge mechanism 70 includes the air supply path 28.
The air communication passage 72 has a ram shaft passage 72a that is connected to the air discharge hole 71 and extends inside the ram shaft 3 along the axial direction of the central axis O, and a piping passage 72b that extends inside a piping member 73 such as a hose and connects the ram shaft passage 72a to the air supply passage 28. The air supply source is, for example, an air compressor, and supplies air (compressed air) to the air supply passage 28.

The DI processing into the cup-shaped body W by the can forming apparatus 1 is performed as follows.
First, the cup-shaped body W, which is the workpiece, is placed between the punch 2 and the redrawing die 8A with the cup axis (can axis) extended horizontally and its opening facing the punch 2. The bottom wall of the cup-shaped body W faces the end surface 9 of the redrawing die 8A.

The cup holder 6 and punch 2 are moved forward in the axial direction of the central axis O relative to this cup-shaped body W. That is, the cup holder 6 and punch 2 move in the stroke direction S from the reciprocating linear motion mechanism 10 toward the die 8, i.e., toward the front. Then, while the cup holder 6 presses the bottom wall of the cup-shaped body W against the end face 9 of the redrawing die 8A to perform a cup pressing operation, the punch 2 pushes the cup-shaped body W into the through hole 7 of the redrawing die 8A, thereby subjecting the cup-shaped body W to the redrawing process.

The redrawing process reduces the diameter of the cup-shaped body W and increases its length in the axial direction of the cup. The cup-shaped body W is then pressed into the punch 2 and ironed as it passes through each of the through holes 7 of the ironing dies 8B in sequence. That is, the peripheral wall of the cup-shaped body W is ironed and stretched, increasing the peripheral wall height and reducing the peripheral wall thickness, and is formed into the shape of a cylindrical DI can 100 with a bottom. The DI can 100 is cold-work hardened by ironing the peripheral wall, increasing its strength.

The ironed DI can 100 is pushed out by the punch 2 from the through hole 7 of the die 8 toward the domer 11. The bottom of the DI can 100 (the part that will become the bottom of the can) is then sandwiched and pressed between the punch 2 and the domer 11, so that the bottom of the DI can 100 is formed into a dome shape.

Next, the reciprocating linear motion mechanism 10 will be described.
2 to 4 and 9, the reciprocating linear motion mechanism 10 includes a housing 15 having an internal gear 16, a first rotating body 21 having a convex portion 25, a first bearing 31, a second rotating body 22 having an external gear 23 meshing with the internal gear 16 and a concave portion 27, a second bearing 32, an air coupling member 40, a ram shaft connecting portion 35, a first weight portion 51, a second weight portion 52, a shaft body 26, a valve portion 80, an air supply passage 28, a first oil supply passage 36, a second oil supply passage 37, and a gear (not shown). Note that the valve portion 80 is not shown in FIGS. 2 to 4.

The housing 15 and its internal gear 16, the first rotor 21 (other than the protruding portion 25), the first bearing 31, the shaft 26, and the gear are centered on the first central axis C1, i.e., are arranged coaxially with each other about the first central axis C1. The protruding portion 25, the second rotor 22 and its external gear 23, the recessed portion 27, the second bearing 32, and the air coupling member 40 are centered on the second central axis C2, i.e., are arranged coaxially with each other about the second central axis C2. The ram shaft connecting portion 35 and the valve portion 80 are centered on the third central axis C3, i.e., are arranged coaxially with each other about the third central axis C3.
The first central axis C1 and the second central axis C2 are parallel to each other and spaced apart from each other. The second central axis C2 and the third central axis C3 are parallel to each other and spaced apart from each other. In this embodiment, the first central axis C1, the second central axis C2, and the third central axis C3 extend in the horizontal direction.

In the following description, the direction in which the first central axis C1 extends, the direction in which the second central axis C2 extends, and the direction in which the third central axis C3 extends are simply referred to as the axial direction. The Z-axis direction shown in each drawing corresponds to this axial direction. In the axial direction, the first rotating body 21 and the ram shaft connecting part 35 are disposed at different positions from each other. In the axial direction, the direction from the first rotating body 21 to the ram shaft connecting part 35 (+Z side) is referred to as one axial side, and the direction from the ram shaft connecting part 35 to the first rotating body 21 (-Z side) is referred to as the other axial side. Note that the one axial side may be referred to as the front side, and the other axial side may be referred to as the rear side.

A direction perpendicular to the first central axis C1 is referred to as a first radial direction. In the first radial direction, a direction approaching the first central axis C1 is referred to as an inner side of the first radial direction, and a direction away from the first central axis C1 is referred to as an outer side of the first radial direction.
The direction of rotation around the first central axis C1 is referred to as a first circumferential direction. Within the first circumferential direction, the direction in which the first rotor 21 is rotated relative to the housing 15 during operation of the can forming apparatus 1 is referred to as a first rotational direction T1.

A direction perpendicular to the second central axis C2 is referred to as a second radial direction. In the second radial direction, a direction approaching the second central axis C2 is referred to as an inner side of the second radial direction, and a direction away from the second central axis C2 is referred to as an outer side of the second radial direction.
The direction of rotation around the second central axis C2 is referred to as a second circumferential direction. Of the second circumferential directions, the direction in which the second rotor 22 is rotated relative to the first rotor 21 during operation of the can forming apparatus 1 is referred to as a second rotation direction T2.

A direction perpendicular to the third central axis C3 is referred to as a third radial direction. In the third radial direction, a direction approaching the third central axis C3 is referred to as an inner third radial direction, and a direction away from the third central axis C3 is referred to as an outer third radial direction.
The direction of rotation around the third central axis C3 is referred to as a third circumferential direction. Of the third circumferential directions, the direction in which the ram shaft connecting portion 35 is rotated relative to the ram shaft 3 during operation of the can forming apparatus 1 is referred to as a third rotational direction T3.

As shown in FIG. 4, the housing 15 is cylindrical and centered on the first central axis C1. The housing 15 has an internal gear 16 and a housing body 17.

The internal gear 16 is annular and centered on the first central axis C1. The internal gear 16 is cylindrical and extends in the axial direction. The internal gear 16 is disposed at one end of the housing 15 in the axial direction. The internal gear 16 is located in an opening on one axial side of the housing 15.

The internal gear 16 has a number of internal teeth 16a arranged in a first circumferential direction on the inner periphery of the internal gear 16. The internal teeth 16a are arranged on the inner periphery of the internal gear 16 over the entire axial length. In this embodiment, the internal teeth 16a are exposed to the outside of the reciprocating linear motion mechanism 10 through an opening on one axial side of the housing 15.

The housing body 17 is cylindrical and centered on the first central axis C1, and extends in the axial direction. A first rotating body 21 and a first bearing 31 are disposed inside the housing body 17. An internal gear 16 is fixed to one end of the housing body 17 in the axial direction.

The housing body 17 has a first outer ring support portion 17g. The first outer ring support portion 17g protrudes inward in a first radial direction from the inner peripheral surface of the housing body 17 and extends in a first circumferential direction. The first outer ring support portion 17g is annular plate-shaped and centered on the first central axis C1. A pair of plate surfaces of the first outer ring support portion 17g face in the axial direction.

The first rotor 21 is located inside the housing 15 in the first radial direction. The first rotor 21 is coupled to the housing 15 so as to be capable of relative rotation about a first central axis C1.
4 and 5 , the first rotating body 21 has a generally cylindrical shape centered on a first central axis C1. The first rotating body 21 is disposed within the housing main body 17. The first rotating body 21 is accommodated within the housing 15.

The first rotating body 21 has a hole portion 21 a , a flange portion 21 b , and a protrusion 25 .
The hole 21a is recessed toward one axial side from a surface 21e facing the other axial side of the first rotating body 21 and extends in the axial direction. The hole 21a is a circular hole centered on the first central axis C1. Specifically, the hole 21a is recessed toward one axial side from a portion of the surface 21e facing the other axial side of the first rotating body 21 other than the outer periphery. In other words, the hole 21a opens to the other axial side.

The flange 21b is disposed at one axial end of the outer periphery of the first rotor 21. The flange 21b is annular and has a first central axis C1 as its center. The flange 21b protrudes outward in a first radial direction from the outer periphery of the first rotor 21 and extends in a first circumferential direction. A pair of plate surfaces of the flange 21b face the axial direction. The plate surface of the pair of plate surfaces of the flange 21b facing the other axial side contacts the inner ring 31a of the first bearing 31 from one axial side.
The protrusion 25 will be described later.

The first bearing 31 is, for example, a tapered roller bearing. The first bearing 31 can support a load from a first radial direction (radial load) and a load from an axial direction (axial load). The first bearing 31 connects the housing 15 and the first rotor 21 so that they can rotate relative to each other around the first central axis C1.

The first bearing 31 has an inner ring 31a, a spacer 31d, an outer ring 31b, and rolling elements 31c.
The inner ring 31a is cylindrical and centered on the first central axis C1. The inner ring 31a fits onto the outer peripheral surface of the first rotating body 21. A plurality of inner rings 31a are provided lined up in the axial direction. In this embodiment, the first bearing 31 has a pair of inner rings 31a that are spaced apart from each other in the axial direction. A spacer 31d is disposed between the pair of inner rings 31a. The spacer 31d is cylindrical and centered on the first central axis C1. The spacer 31d fits onto the outer peripheral surface of the first rotating body 21.

Of the pair of inner rings 31a, one of the inner rings 31a located on one axial side is disposed between the flange 21b and the spacer 31d in the axial direction. The flange 21b contacts the end face of the one inner ring 31a facing the one axial side. The spacer 31d contacts the end face of the one inner ring 31a facing the other axial side.
Of the pair of inner rings 31a, the other inner ring 31a located on the other axial side has a spacer 31d in contact with an end face facing one axial side.

The outer ring 31b is cylindrical and centered on the first central axis C1. The outer ring 31b is located outside the inner ring 31a in the first radial direction. The outer ring 31b fits into the inner peripheral surface of the housing body 17. A plurality of outer rings 31b are provided side by side in the axial direction. In this embodiment, the first bearing 31 has a pair of outer rings 31b that are spaced apart from each other in the axial direction. A first outer ring support portion 17g is disposed between the pair of outer rings 31b.

Of the pair of outer rings 31b, one outer ring 31b located on one axial side is in contact with an end face facing the other axial side with a first outer ring support portion 17g.
Of the pair of outer rings 31b, the other outer ring 31b located on the other axial side has an end face facing one axial side that comes into contact with the first outer ring support portion 17g.

The rolling elements 31c are cylindrical rollers or the like. The rolling elements 31c are arranged between the inner ring 31a and the outer ring 31b in the first radial direction. A plurality of the rolling elements 31c are arranged side by side in the first circumferential direction. A plurality of rows of the rolling elements 31c arranged in the first circumferential direction (hereinafter simply referred to as the rows of the rolling elements 31c) are arranged side by side in the axial direction. In this embodiment, the first bearing 31 has a pair of rows of the rolling elements 31c arranged at a distance from each other in the axial direction.

Of the pair of rows of rolling elements 31c, one row of rolling elements 31c located on one axial side is rotatably held between one inner ring 31a and one outer ring 31b.
Of the pair of rows of rolling elements 31c, the other row of rolling elements 31c located on the other axial side is held rotatably between the other inner ring 31a and the other outer ring 31b.

The protrusion 25 protrudes in the axial direction from the surface 21d facing one axial side of the first rotor 21 and extends in the axial direction. The protrusion 25 is cylindrical with the second central axis C2 as its center. Specifically, the protrusion 25 protrudes in the axial direction from the outer portion in the first radial direction of the surface 21d facing one axial side of the first rotor 21.

The protrusion 25 has an outer circumferential step 25a.
The outer peripheral step 25a constitutes a part of the outer periphery of the protrusion 25. In the illustrated example, the outer peripheral step 25a is disposed at the other axial end of the outer periphery of the protrusion 25. The outer peripheral step 25a has an annular shape centered on the second central axis C2 and faces one axial side.

The second rotor 22 is disposed on one axial side of the first rotor 21. The second rotor 22 is coupled to the first rotor 21 so as to be capable of relative rotation about a second central axis C2.
4 and 6, the second rotating body 22 has a generally cylindrical shape with a top and a bottom, and is centered on the second central axis C2. The second rotating body 22 has an external gear 23, a top wall portion 22b, a bolt member 24, a joint insertion hole 22c, and a recess 27.

The external gear 23 is cylindrical and centered on the second central axis C2, and extends in the axial direction. A part of the surface 22e of the external gear 23 facing the other axial side faces a part of the surface 21d of the first rotor 21 facing one axial side with a gap in the axial direction. The other part of the surface 22e of the external gear 23 facing the other axial side faces a part of the first bearing 31 with a gap in the axial direction.

The external gear 23 has a plurality of external teeth 23a arranged in the second circumferential direction on the outer periphery of the external gear 23. The external teeth 23a are arranged on a portion of the outer periphery of the external gear 23 other than the end portion on one axial side. In this embodiment, the external teeth 23a are exposed to the outside of the reciprocating linear motion mechanism 10 through an opening on one axial side of the housing 15.
At least one of the plurality of external teeth 23a meshes with at least one of the plurality of internal teeth 16a. The pitch circle diameter of the external teeth 23a of the external gear 23 is half the pitch circle diameter of the internal teeth 16a of the internal gear 16.

The external gear 23 has a second outer ring support portion 23b. The second outer ring support portion 23b protrudes inward in the second radial direction from the inner peripheral surface of the external gear 23 and extends in the second circumferential direction. The second outer ring support portion 23b is cylindrical and centered on the second central axis C2. A pair of end faces of the second outer ring support portion 23b face in the axial direction.

2, when the can forming apparatus 1 is in operation, the external gear 23 rotates (revolves) in a first rotation direction T1 along the inner periphery of the internal gear 16 while rotating (rotating) in a second rotation direction T2. In this embodiment, when the reciprocating linear motion mechanism 10 is viewed from one axial side, that is, when viewed from the front of the reciprocating linear motion mechanism 10, the first rotation direction T1 is a counterclockwise direction centered on the first central axis C1, and the second rotation direction T2 is a clockwise direction centered on the second central axis C2. However, this is not limited to this, and when the reciprocating linear motion mechanism 10 is viewed from one axial side, the first rotation direction T1 may be a clockwise direction centered on the first central axis C1, and the second rotation direction T2 may be a counterclockwise direction centered on the second central axis C2.

The top wall portion 22b is disposed on one axial side of the external gear 23. The top wall portion 22b is plate-shaped and extends in a direction perpendicular to the second central axis C2. As shown in FIG. 4, the top wall portion 22b is connected to the end portion on one axial side of the external gear 23 and the end portion on the other axial side of the ram shaft connecting portion 35. In other words, the top wall portion 22b connects the external gear 23 and the ram shaft connecting portion 35. The top wall portion 22b blocks the opening on one axial side of the external gear 23. The top wall portion 22b may also be referred to as the blocking wall portion 22b or the front wall portion 22b.

The top wall portion 22b has a fitting cylindrical portion 22d.
The fitting cylinder portion 22d protrudes in the other axial direction from a surface of the top wall portion 22b facing the other axial direction. The fitting cylinder portion 22d is cylindrical and centered on the second central axis C2. The fitting cylinder portion 22d is inserted into the external gear 23. The fitting cylinder portion 22d fits into the inner circumferential surface of the external gear 23.

As shown in Figures 2 and 3, the top wall portion 22b is fixed to the external gear 23 by a plurality of bolt members 24 arranged in the second circumferential direction. Each bolt member 24 extends in the axial direction. Each bolt member 24 is inserted into a bolt insertion hole that passes through the top wall portion 22b in the axial direction and screwed into a female threaded hole of the external gear 23.

As shown in FIG. 4, the joint insertion hole 22c penetrates the top wall portion 22b in the axial direction. The joint insertion hole 22c is a circular hole centered on the second central axis C2.

The recess 27 is recessed from the surface 22e facing the other axial side of the second rotating body 22 toward one axial side and extends in the axial direction. The recess 27 is a circular hole centered on the second central axis C2. Specifically, the recess 27 is recessed from the inner portion in the second radial direction of the surface 22e facing the other axial side of the external gear 23 toward one axial side. In other words, the recess 27 opens toward the other axial side. The end of the recess 27 on the one axial side is blocked by the top wall portion 22b. The protrusion 25 is inserted into the recess 27.

The second bearing 32 is, for example, a tapered roller bearing. The second bearing 32 can support a load from the second radial direction (radial load) and a load from the axial direction (axial load). The second bearing 32 connects the convex portion 25 and the concave portion 27 so that they can rotate relatively around the second central axis C2. In other words, the second bearing 32 connects the first rotating body 21 and the second rotating body 22 so that they can rotate relatively around the second central axis C2.

The second bearing 32 has an inner ring 32a, a spacer 32d, an outer ring 32b, and rolling elements 32c.
The inner ring 32a is cylindrical and centered on the second central axis C2. The inner ring 32a fits onto the outer peripheral surface of the protrusion 25. A plurality of inner rings 32a are provided lined up in the axial direction. In this embodiment, the second bearing 32 has a pair of inner rings 32a that are spaced apart from each other in the axial direction. A spacer 32d is disposed between the pair of inner rings 32a. The spacer 32d is cylindrical and centered on the second central axis C2. The spacer 32d fits onto the outer peripheral surface of the protrusion 25.

Of the pair of inner rings 32a, the one located on one axial side is disposed axially between an inner ring holding portion 41 (described later) of the air coupling member 40 and a spacer 32d. The inner ring holding portion 41 contacts the end face of the one inner ring 32a facing one axial side. The spacer 32d contacts the end face of the one inner ring 32a facing the other axial side. In other words, the one inner ring 32a is clamped from both sides in the axial direction by the inner ring holding portion 41 and the spacer 32d.

Of the pair of inner rings 32a, the other inner ring 32a located on the other axial side is disposed between the spacer 32d and the outer peripheral step 25a in the axial direction. The spacer 32d contacts the end face of the other inner ring 32a facing one axial side. The outer peripheral step 25a contacts the end face of the other inner ring 32a facing the other axial side. In other words, the other inner ring 32a is sandwiched from both sides in the axial direction by the spacer 32d and the outer peripheral step 25a.
Although not particularly shown, the surface 21d facing one axial side of the first rotating body 21 may come into contact with an end face of the other inner ring 32a facing the other axial side. In this case, the other inner ring 32a is sandwiched from both sides in the axial direction by the surface 21d facing one axial side of the first rotating body 21 and the spacer 32d.

The outer ring 32b is cylindrical and centered on the second central axis C2. The outer ring 32b is located outside the inner ring 32a in the second radial direction. The outer ring 32b fits into the inner peripheral surface of the external gear 23, i.e., the inner peripheral surface of the recess 27. A plurality of outer rings 32b are provided side by side in the axial direction. In this embodiment, the second bearing 32 has a pair of outer rings 32b spaced apart from each other in the axial direction. The second outer ring support portion 23b is disposed between the pair of outer rings 32b.

Of the pair of outer rings 32b, one outer ring 32b located on one axial side is in contact with the end face facing the other axial side with the second outer ring support portion 23b.
The second outer ring support portion 23b comes into contact with an end face facing one axial side of the other outer ring 32b located on the other axial side of the pair of outer rings 32b.

The rolling elements 32c are cylindrical rollers or the like. The rolling elements 32c are arranged between the inner ring 32a and the outer ring 32b in the second radial direction. A plurality of the rolling elements 32c are arranged side by side in the second circumferential direction. A plurality of rows of the rolling elements 32c arranged in the second circumferential direction (hereinafter simply referred to as the rows of the rolling elements 32c) are arranged side by side in the axial direction. In this embodiment, the second bearing 32 has a pair of rows of the rolling elements 32c arranged at a distance from each other in the axial direction.

Of the pair of rows of rolling elements 32c, one row of rolling elements 32c located on one axial side is held rotatably between one inner ring 32a and one outer ring 32b.
Of the pair of rows of rolling elements 32c, the other row of rolling elements 32c located on the other axial side is held rotatably between the other inner ring 32a and the other outer ring 32b.

When viewed from the second radial direction, the internal gear 16, the external gear 23, the recess 27, the second bearing 32, and the protrusion 25 overlap one another. That is, the internal gear 16, the external gear 23, the recess 27, the second bearing 32, and the protrusion 25 each include a portion that is arranged at the same position as one another in the axial direction. When viewed from the second radial direction, the second bearing 32 overlaps with the internal gear 16 and the external gear 23 over its entire axial length.
When viewed from the axial direction, a part of the second bearing 32 in the second circumferential direction and a part of the first bearing 31 in the first circumferential direction are disposed so as to overlap with each other. In other words, when viewed from the axial direction, a part of the second bearing 32 and a part of the first bearing 31 overlap with each other.

The air joint member 40 is attached to the protrusion 25 and the top wall portion 22b. The air joint member 40 allows air to flow therethrough, and constitutes a part of the flow path of the air supply passage 28.
The air joint member 40 has an inner ring pressing portion 41 , an outer cylinder 42 , and an inner cylinder 43 .

The inner ring holding portion 41 is a disk-shaped member centered on the second central axis C2 and extending in a direction perpendicular to the second central axis C2. The plate surface of the inner ring holding portion 41 facing the other axial side contacts the surface of the convex portion 25 facing one axial side. The inner ring holding portion 41 is fixed to the convex portion 25 by screwing or the like. The outer periphery of the inner ring holding portion 41 protrudes outward in the second radial direction beyond the outer periphery of the convex portion 25. The outer periphery of the inner ring holding portion 41 contacts one inner ring 32a of the second bearing 32 from one axial side. In other words, the inner ring holding portion 41 holds the inner ring 32a of the second bearing 32 from one axial side.

The inner ring pressing portion 41 has a pressing portion air hole 41a.
The holding portion air hole 41a axially passes through the inner ring holding portion 41. The holding portion air hole 41a is a circular hole centered on the second central axis C2.

The outer cylinder 42 is cylindrical and centered on the second central axis C2, and extends in the axial direction. The outer cylinder 42 is inserted into the joint insertion hole 22c. The outer cylinder 42 fits into the inner peripheral surface of the joint insertion hole 22c. The outer cylinder 42 is fixed to the top wall portion 22b by screwing or the like.

The outer cylinder 42 has an outer cylinder air hole 42a.
The outer cylinder air hole 42a penetrates in the second radial direction through the peripheral wall of the outer cylinder 42. When viewed in the axial direction, the outer cylinder air hole 42a is located on an imaginary line connecting the third center axis C3 and the second center axis C2 of the ram shaft connecting portion 35.

The inner tube 43 is a cylindrical shape with a top centered on the second central axis C2 and extends in the axial direction. The other axial end of the inner tube 43 contacts the plate surface of the inner race holding portion 41 facing one axial side. The inside of the inner tube 43 communicates with the holding portion air hole 41a of the inner race holding portion 41. The inner tube 43 is fixed to the inner race holding portion 41 by screwing or the like. In other words, the inner tube 43 is fixed to the convex portion 25 via the inner race holding portion 41. The inner tube 43 and the outer tube 42 are capable of relative rotation around the second central axis C2.

The inner cylinder 43 has an inner cylinder air groove 43a and an inner cylinder air hole 43b.
The inner cylinder air groove 43a is recessed inward in the second radial direction from the outer circumferential surface of the inner cylinder 43 and extends in the second circumferential direction. The inner cylinder air groove 43a is annular about the second central axis C2. The inner cylinder air groove 43a communicates with the outer cylinder air hole 42a.

The inner cylinder air hole 43b penetrates the peripheral wall of the inner cylinder 43 in the second radial direction. The inner cylinder air hole 43b extends in the second radial direction and opens to the inner peripheral surface of the inner cylinder 43 and the inner cylinder air groove 43a. The interior of the inner cylinder 43 and the inner cylinder air groove 43a communicate with each other through the inner cylinder air hole 43b. Multiple inner cylinder air holes 43b are provided side by side in the second circumferential direction. The multiple inner cylinder air holes 43b are arranged radially around the second central axis C2.

2, the ram shaft connecting part 35 is connected to the second rotor 22 and is caused to perform reciprocating linear motion along a predetermined direction (stroke direction S) of the first radial direction while rotating around the third central axis C3. That is, when the can forming device 1 is in operation, the ram shaft connecting part 35 performs reciprocating linear motion along the stroke direction S while rotating (rotating) in the third rotation direction T3 of the third circumferential direction. In this embodiment, when the reciprocating linear motion mechanism 10 is viewed from one axial side, the second rotation direction T2 of the second rotor 22 is a clockwise direction centered on the second central axis C2, and the third rotation direction T3 of the ram shaft connecting part 35 is a clockwise direction centered on the third central axis C3. However, this is not limited to this, and when the reciprocating linear motion mechanism 10 is viewed from one axial side, the second rotation direction T2 may be a counterclockwise direction centered on the second central axis C2, and the third rotation direction T3 may be a counterclockwise direction centered on the third central axis C3.

As shown in Fig. 4, the ram shaft connecting portion 35 is cylindrical and has a bottom, and extends in the axial direction. The ram shaft connecting portion 35 opens on one axial side. The opening on one axial side of the ram shaft connecting portion 35 is closed by a valve portion 80 (see Fig. 9).
The ram shaft connecting portion 35 protrudes from the top wall portion 22b to one side in the axial direction. The ram shaft connecting portion 35 is located on one side in the axial direction relative to the housing 15. The ram shaft connecting portion 35 protrudes from the top wall portion 22b to the outside in the second radial direction.

The third central axis C3 of the ram shaft connecting part 35 is parallel to the first central axis C1. The third central axis C3 of the ram shaft connecting part 35 is arranged parallel to and spaced apart from the second central axis C2. The second radial distance between the third central axis C3 and the second central axis C2 is equal to the second radial distance between the first central axis C1 and the second central axis C2. When the reciprocating linear motion mechanism 10 is viewed from the axial direction, the third central axis C3 of the ram shaft connecting part 35 is located on the pitch circle diameter of the external teeth 23a of the external gear 23.

The ram shaft connecting portion 35 has an air cylinder 35a.
The air cylinder 35a is disposed inside the ram shaft connecting portion 35. The air cylinder 35a is cylindrical and centered on the third central axis C3, and extends in the axial direction. The air cylinder 35a allows air to flow therethrough, and constitutes a part of the flow path of the air supply passage 28.

In FIG. 1, the ram shaft connecting portion 35 is connected to one end of the ram shaft 3 via a connecting bearing 54 (see FIG. 9) provided on the outer periphery of the ram shaft connecting portion 35. This connecting bearing 54 connects the ram shaft connecting portion 35 and the ram shaft 3 so that they can rotate relatively around the third central axis C3.

As shown in Figures 4 and 5, the first weight 51 is connected to the first rotor 21 and is located on the opposite side of the second center axis C2 in the first radial direction, sandwiching the first center axis C1 therebetween. The first weight 51 functions as a so-called counterweight to maintain good rotational balance in the first circumferential direction when the first rotor 21 and its protruding portion 25, the second bearing 32, the second rotor 22 and its recessed portion 27, the ram shaft connecting portion 35, the valve portion 80, and the second weight 52 rotate around the first center axis C1.

The first weight portion 51 is disposed on one axial side of the first rotating body 21. The first weight portion 51 is semicircular. The surface of the first weight portion 51 facing the other axial side contacts the surface 21d of the first rotating body 21 facing the one axial side. The outer end of the first radial direction of the first weight portion 51, i.e., the outer periphery, protrudes outward in the first radial direction beyond the outer periphery of the first rotating body 21. The outer periphery of the first weight portion 51 overlaps with the first bearing 31 when viewed from the axial direction.

The first weight portion 51 is fixed to the first rotating body 21 by a plurality of bolt members 53 arranged in the first circumferential direction. Each bolt member 53 extends in the axial direction. Each bolt member 53 is inserted into a bolt insertion hole that passes through the first weight portion 51 in the axial direction, and is screwed into a female threaded hole of the first rotating body 21.

As shown in Figures 2 to 4 and 6, the second weight portion 52 is connected to the second rotor 22 and is located on the opposite side of the ram shaft connecting portion 35 and the valve portion 80 in the second radial direction, with the second central axis C2 in between. The second weight portion 52 functions as a so-called counterweight to maintain good rotational balance in the second circumferential direction when the second rotor 22, the ram shaft connecting portion 35, and the valve portion 80 rotate around the second central axis C2.

The second weight portion 52 protrudes outward in the second radial direction from the top wall portion 22b. The second weight portion 52 and the top wall portion 22b have an overall shape that is generally disk-shaped. The second weight portion 52 is formed integrally with a part of the ram shaft connecting portion 35 and the top wall portion 22b.

As shown in FIG. 4, the shaft body 26 is a multi-stage cylindrical shape centered on the first central axis C1 and extends in the axial direction. The shaft body 26 is disposed on the other axial side of the first rotating body 21. The shaft body 26 is connected to the first rotating body 21. The outer diameter of the shaft body 26 is smaller than the outer diameter of the first rotating body 21. The outer diameter of the end of the shaft body 26 on one axial side is larger than the outer diameter of the portion other than the end of the shaft body 26 on one axial side. The end of the shaft body 26 on one axial side fits into the opening of the hole 21a of the first rotating body 21. The end of the shaft body 26 on one axial side is fixed to the end of the first rotating body 21 on the other axial side by a screw member or the like. In other words, the shaft body 26 is fixed to the first rotating body 21.

The shaft body 26 is supported by a third bearing (not shown) so as to be rotatable about the first central axis C1. A rotational driving force in a first rotational direction T1 is input to the shaft body 26 from a driving source (not shown). The shaft body 26 and the first rotating body 21 are rotated in the first rotational direction T1 relative to the housing 15 by the rotational driving force of the driving source.

The shaft body 26 has a shaft body hole portion 26c.
The shaft hole portion 26c is recessed from a surface facing one axial side of the shaft 26 toward the other axial side and extends in the axial direction. The shaft hole portion 26c is a multi-stage circular hole centered on the first central axis C1. The shaft hole portion 26c opens to one axial side.

The shaft hole portion 26c has a large diameter hole portion 26d and a small diameter hole portion 26e.
The large diameter hole portion 26d constitutes one axial side portion of the shaft body hole portion 26c. The large diameter hole portion 26d is connected to the hole portion 21a of the first rotor 21. The large diameter hole portion 26d is disposed on the other axial side of the hole portion 21a. The inner diameter dimension of the large diameter hole portion 26d is smaller than the inner diameter dimension of the hole portion 21a. The axial dimension of the large diameter hole portion 26d is larger than the axial dimension of the hole portion 21a.

The small diameter hole portion 26e constitutes the other axial side portion of the shaft hole portion 26c. The small diameter hole portion 26e is disposed on the other axial side of the large diameter hole portion 26d. The inner diameter dimension of the small diameter hole portion 26e is smaller than the inner diameter dimension of the large diameter hole portion 26d. The axial dimension of the small diameter hole portion 26e is larger than the axial dimension of the large diameter hole portion 26d.

1 and 9 , the valve unit 80 is connected to the ram shaft connecting portion 35. The valve unit 80 is disposed on one axial side of the ram shaft connecting portion 35. The valve unit 80 is attached to the ram shaft connecting portion 35 and the ram shaft 3. The valve unit 80 allows air to flow therethrough, and constitutes part of the flow path of the air supply passage 28.
The valve unit 80 can be switched between a flow mode (the state shown in FIGS. 9 and 10 ) in which air can pass through the interior, and a blocking mode (not shown) in which air cannot pass through the interior, depending on the rotational position of the ram shaft connecting part 35 about the third central axis C3.

As shown in FIGS. 7 to 10 , the valve portion 80 has a ram shaft fixing portion 81 , a rotating portion 82 , and a valve bearing 83 .
The ram shaft fixing portion 81 is fixed to the ram shaft 3. Specifically, the ram shaft fixing portion 81 is fixed to a connecting rod located at one end of the ram shaft 3 by a bolt member 84 (see FIG. 1 ).

The ram shaft fixing portion 81 has a fixing plate portion 85 , a fixing cylinder portion 86 , an outer cylinder portion 87 , an air slot 87 a , and a fixing screw 88 .
The fixing plate portion 85 is shaped like a plate extending in a direction perpendicular to the third central axis C3. In this embodiment, the fixing plate portion 85 is shaped like a substantially rectangular plate. The fixing plate portion 85 is attached to one end of the ram shaft 3 by a plurality of bolt members 84.

The fixed cylinder portion 86 is cylindrical and centered on the third central axis C3, and extends in the axial direction. The fixed cylinder portion 86 protrudes to one axial side from a plate surface facing one axial side of the fixed plate portion 85. The fixed cylinder portion 86 is fixed to the ram shaft 3 via the fixed plate portion 85.

As shown in FIGS. 9 and 10, the fixed cylinder portion 86 has an adjustment slot 86a and an air connection port 86b.
The adjustment elongated hole 86a penetrates the fixed cylinder portion 86 in the third radial direction and extends around the third central axis C3. In the illustrated example, the adjustment elongated hole 86a is disposed in an upper portion of the fixed cylinder portion 86 in the vertical direction.
The air connection port 86b is a hole that penetrates the fixed cylinder portion 86 in the third radial direction. In the illustrated example, the air connection port 86b is disposed in a lower portion of the fixed cylinder portion 86 in the vertical direction. One end of a piping member 73 such as a hose is connected to the air connection port 86b (see FIG. 1). The other end of the piping member 73 is connected to a piping connection port of the ram shaft 3.

The outer tube portion 87 is tubular about the third central axis C3 and extends in the axial direction. The outer tube portion 87 is cylindrical. The outer tube portion 87 is slidably fitted into the fixed tube portion 86. The outer peripheral surface of the outer tube portion 87 is in sliding contact with the inner peripheral surface of the fixed tube portion 86 in the third circumferential direction so as to be freely rotatable. In other words, the fixed tube portion 86 is located outside the outer tube portion 87 in the third radial direction.

The long air hole 87a penetrates the outer tube portion 87 in the third radial direction and extends around the third central axis C3. The long air hole 87a is a slit-like hole that extends through the peripheral wall of the outer tube portion 87 over a predetermined range in the third circumferential direction. In the illustrated example, the long air hole 87a is disposed in the lower part of the outer tube portion 87 in the vertical direction. At least a part of the long air hole 87a faces the air connection port 86b in the third radial direction. In other words, the long air hole 87a and the air connection port 86b communicate with each other. The position of the long air hole 87a around the third central axis C3 can be adjusted by rotating the outer tube portion 87 around the third central axis C3 relative to the fixed tube portion 86.

The fixing screw 88 fixes the fixed cylinder portion 86 and the outer cylinder portion 87. The fixing screw 88 is inserted into the adjustment slot 86a and screwed into the outer cylinder portion 87.
The fixing screw 88 has a bolt 88a and a nut 88b. The bolt 88a is inserted into the adjustment elongated hole 86a from the outside in the third radial direction and is screwed into a female threaded hole that opens into the outer circumferential surface of the outer tubular portion 87. The nut 88b is screwed into the male threaded portion of the bolt 88a and comes into contact with the outer circumferential surface of the fixing tubular portion 86 from the outside in the third radial direction.

When the bolt 88a is screwed into the outer cylinder portion 87, the nut 88b is tightened inward in the third radial direction to fix the fixed cylinder portion 86 and the outer cylinder portion 87, restricting the relative movement between the fixed cylinder portion 86 and the outer cylinder portion 87 in the third circumferential direction. This positions the air long hole 87a in the third circumferential direction.

The rotating part 82 is connected to the ram shaft connecting part 35 and can rotate relatively to the ram shaft fixing part 81 around the third central axis C3. In this embodiment, the rotating part 82 is connected to the ram shaft fixing part 81 so as to be rotatable relatively to the ram shaft fixing part 81 in the third circumferential direction by a pair of valve bearings 83 that are arranged apart from each other in the axial direction. The pair of valve bearings 83 are arranged on one axial side and the other axial side of the outer cylinder part 87. In other words, the outer cylinder part 87 is located between the pair of valve bearings 83 in the axial direction.

The rotating portion 82 has an attachment plate 89 , an inner cylinder portion 90 , an axial flow passage 90 a , a radial flow passage 90 b , and an inner ring pressing plate 91 .
The mounting plate 89 is in the shape of an annular plate centered on the third central axis C3 and extending in a direction perpendicular to the third central axis C3. The outer periphery of the mounting plate 89 is fixed to one axial end of the ram shaft connecting portion 35 by screwing or the like. In other words, the rotating portion 82 is fixed to the ram shaft connecting portion 35. The outer periphery of the mounting plate 89 presses an inner ring (not shown) of the connecting bearing 54 from one axial side. The air cylinder 35a fits into the inner periphery of the mounting plate 89.

The inner cylinder portion 90 is cylindrical and extends in the axial direction, centered on the third central axis C3. The inner cylinder portion 90 protrudes from the mounting plate 89 to one side in the axial direction. The inner cylinder portion 90 is cylindrical with a top. The inner cylinder portion 90 has a peripheral wall and a top wall connected to the end of the peripheral wall on one side in the axial direction. The inner cylinder portion 90 slidably fits into the outer cylinder portion 87. The outer peripheral surface of the inner cylinder portion 90 is in sliding contact with the inner peripheral surface of the outer cylinder portion 87 in the third circumferential direction so as to be freely rotatable. In other words, the inner cylinder portion 90 is located inside the outer cylinder portion 87 in the third radial direction. The other axial end of the inner cylinder portion 90 fits into the inner peripheral portion of the mounting plate 89. The inner cylinder portion 90 and the mounting plate 89 are fixed to each other by screws or the like. In other words, the inner cylinder portion 90 is fixed to the ram shaft connecting portion 35 via the mounting plate 89. Therefore, when the can forming device 1 is in operation, the inner cylinder portion 90 rotates together with the ram shaft connecting portion 35 in the third rotation direction T3 around the third central axis C3.

The axial flow passage 90a extends axially inside the inner cylinder 90. The axial flow passage 90a is disposed on the third central axis C3. One axial end of the axial flow passage 90a is blocked by the top wall of the inner cylinder 90. The other axial end of the axial flow passage 90a opens to a surface of the inner cylinder 90 facing the other axial side. The axial flow passage 90a communicates with the inside of the air cylinder 35a. The axial flow passage 90a is connected to a fourth air flow passage (air flow passage) 28e (described later) of the ram shaft connecting portion 35.

The radial flow passages 90b extend inside the inner cylinder portion 90 in the third radial direction and open to the axial flow passages 90a and the outer peripheral surface of the inner cylinder portion 90. When the inner cylinder portion 90 rotates in the third circumferential direction relative to the outer cylinder portion 87, the radial flow passages 90b communicate with the air long holes 87a within a predetermined range around the third central axis C3.

As shown in FIG. 10, the state in which the radial flow passages 90b and the long air holes 87a face each other in the third radial direction and are connected to each other corresponds to the flow mode of the valve unit 80. In the flow mode, the inside of the air cylinder 35a (fourth air flow passage 28e) and the inside of the piping member 73 (piping flow passage 72b) are connected to each other through the inside of the valve unit 80, that is, the axial flow passages 90a, the radial flow passages 90b, the long air holes 87a, and the air connection port 86b. Therefore, in the flow mode, air is supplied from the ram shaft connection part 35 to the ram shaft 3 through the inside of the valve unit 80.

Although not specifically shown, the state in which the radial flow passages 90b and the long air holes 87a do not face each other in the third radial direction and communication between the radial flow passages 90b and the long air holes 87a is blocked corresponds to the blocking mode of the valve unit 80. In the blocking mode, communication between the inside of the air cylinder 35a (fourth air flow passage 28e) and the inside of the piping member 73 (piping flow passage 72b) through the inside of the valve unit 80 is blocked. Therefore, in the blocking mode, the supply of air from the ram shaft connection part 35 to the ram shaft 3 through the inside of the valve unit 80 is blocked (stopped).

As shown in Figures 7 to 9, the inner race pressing plate 91 is a disk-shaped plate centered on the third central axis C3 and extending in a direction perpendicular to the third central axis C3. The inner race pressing plate 91 is fixed to one axial end of the inner cylinder portion 90, i.e., the top wall, by means of screws or the like. The outer periphery of the inner race pressing plate 91 presses down on the inner race of one of the pair of valve bearings 83, which is disposed on one axial side of the outer cylinder portion 87, from one axial side.

As shown in Figures 4 and 9, the air supply passage 28 is an air flow path formed inside the reciprocating linear motion mechanism 10. The air supply passage 28 extends through the inside of the shaft body 26, the inside of the first rotor 21, the inside of the convex portion 25, the inside of the air coupling member 40, the inside of the top wall portion 22b of the second rotor 22, the inside of the ram shaft connecting portion 35, and the inside of the valve portion 80. In other words, the air supply passage 28 passes through the insides of the first rotor 21, the air coupling member 40, the second rotor 22, the ram shaft connecting portion 35, and the valve portion 80.

The air supply passage 28 has a first air flow path 28a, an air chamber 29, a second air flow path 28b, an air joint flow path 28c, a third air flow path 28d, a fourth air flow path 28e, and a valve section flow path 28g. The first air flow path 28a, the air chamber 29, the second air flow path 28b, the air joint flow path 28c, the third air flow path 28d, the fourth air flow path 28e, and the valve section flow path 28g are connected to each other. Air supplied to the air supply passage 28 from an air supply source (not shown) flows from the upstream to the downstream side inside the air supply passage 28 in the order of the first air flow path 28a, the air chamber 29, the second air flow path 28b, the air joint flow path 28c, the third air flow path 28d, the fourth air flow path 28e, and the valve section flow path 28g.

As shown in FIG. 4, the first air flow passage 28a is disposed inside the shaft body 26. In this embodiment, the first air flow passage 28a is located at the other axial end of the shaft body 26 and extends axially on the first central axis C1.

The air chamber 29 is disposed at least inside the first rotor 21. The air chamber 29 extends axially on the first central axis C1. Among the flow paths constituting the air supply passage 28, the air chamber 29 has the largest flow path cross-sectional area and the largest volume. The air chamber 29 can temporarily store air (compressed air) inside the air chamber 29. In other words, air is stored in the air chamber 29. In this embodiment, the air chamber 29 is disposed throughout the first rotor 21 and the shaft 26. The air chamber 29 is formed throughout the hole 21a of the first rotor 21 and the shaft hole 26c of the shaft 26.

The volume of the air chamber 29 is equal to or greater than the total volume of the air flow paths located downstream of the air chamber 29, specifically, equal to or greater than the sum of the volumes of the second air flow path 28b, the air joint flow path 28c, the third air flow path 28d, the fourth air flow path 28e, the valve portion flow path 28g, the air communication passage 72, and the air discharge hole 71.

The air chamber 29 has a first chamber 61 disposed inside the first rotor 21 and a second chamber 62 disposed inside the shaft body 26 and formed integrally with the first chamber 61 .
The first chamber 61 is a chamber defined by the hole 21a and an end face facing one axial direction of the shaft body 26. The first chamber 61 has a larger inner diameter dimension and a smaller axial dimension than the second chamber 62.

The second chamber 62 is a chamber defined by the shaft hole 26c. The second chamber 62 has a smaller inner diameter dimension and a larger axial dimension than the first chamber 61.
The second chamber 62 has a large diameter chamber 62a and a small diameter chamber 62b.

The large diameter chamber 62a is defined by the large diameter hole portion 26d. The large diameter chamber 62a is located at one axial side of the second chamber 62 and is connected to the first chamber 61.
The small diameter chamber 62b is defined by the small diameter hole portion 26e. The small diameter chamber 62b is located on the other axial side of the second chamber 62. The small diameter chamber 62b has a smaller inner diameter dimension and a larger axial dimension than the large diameter chamber 62a.

The second air flow path 28b is disposed inside the first rotating body 21 and inside the convex portion 25. The second air flow path 28b extends in the axial direction on the second central axis C2. The other axial end of the second air flow path 28b opens into the hole portion 21a. The one axial end of the second air flow path 28b opens into the surface of the convex portion 25 facing one axial side.

The air joint flow path 28c has a holding part air hole 41a, the inside (internal space) of the inner cylinder 43, an inner cylinder air hole 43b, an inner cylinder air groove 43a, and an outer cylinder air hole 42a. Air that flows into the air joint flow path 28c from the second air flow path 28b flows through the holding part air hole 41a, the inside of the inner cylinder 43, the inner cylinder air hole 43b, the inner cylinder air groove 43a, and the outer cylinder air hole 42a in this order, and flows out into the third air flow path 28d.

The third air flow passage 28d is disposed inside the top wall portion 22b and extends in the second radial direction. When viewed in the axial direction, the third air flow passage 28d extends along an imaginary straight line connecting the third central axis C3 and the second central axis C2 of the ram shaft connecting portion 35. The inner end of the third air flow passage 28d in the second radial direction is connected to the outer cylinder air hole 42a. The outer end of the third air flow passage 28d in the second radial direction is blocked by the plug portion 28f.

The fourth air flow passage 28e is disposed inside the ram shaft connecting portion 35. The fourth air flow passage 28e extends axially on the third central axis C3 of the ram shaft connecting portion 35. The other axial end of the fourth air flow passage 28e is connected to the third air flow passage 28d. As shown in FIG. 9, one axial end of the fourth air flow passage 28e is connected to the axial flow passage 90a that constitutes part of the internal space of the valve portion 80. The portion of the fourth air flow passage 28e other than the other axial end is constituted by the air cylinder 35a (the internal space).

The valve section flow path 28g has an axial flow path 90a, a radial flow path 90b, an air long hole 87a, and an air connection port 86b. Air that flows into the inside (internal space) of the valve section 80 from the fourth air flow path 28e flows through the axial flow path 90a, the radial flow path 90b, the air long hole 87a, and the air connection port 86b in this order only when the valve section 80 is in the flow mode, and flows out into the piping flow path 72b.

As shown in FIG. 4, the first oil supply passage 36 penetrates the housing 15 and supplies oil to the first bearing 31. In this embodiment, the first oil supply passage 36 penetrates the peripheral wall of the housing body 17. The outer end of the first oil supply passage 36 in the first radial direction opens to the outer peripheral surface of the housing body 17. The inner end of the first oil supply passage 36 in the first radial direction opens to the inner peripheral surface of the housing body 17. That is, the first oil supply passage 36 extends inside the housing 15 and opens toward the first bearing 31. Oil is supplied to the first oil supply passage 36 from the outside of the housing 15 via a first oil supply port 36a (see FIG. 2) provided on the outer peripheral portion of the housing body 17.

A plurality of first oil supply passages 36 are provided. The plurality of first oil supply passages 36 are arranged at intervals from one another in the first circumferential direction. The plurality of first oil supply passages 36 includes one first oil supply passage 36 that extends linearly within the housing body 17, and another first oil supply passage 36 that bends and extends in a crank shape within the housing body 17.

In this embodiment, at least one first oil supply passage 36 is disposed in a portion of the housing body 17 that is located above the first central axis C1 in the vertical direction. This makes it easier for the oil supplied to the first bearing 31 from above to be distributed stably throughout the entire first bearing 31.

As shown in FIG. 4, the second oil supply passage 37 passes through the internal gear 16 and the external gear 23 and supplies oil to the second bearing 32. The second oil supply passage 37 has an internal gear flow path 37a and an external gear flow path 37b.

The internal gear flow passage 37a penetrates the peripheral wall of the internal gear 16. In this embodiment, the internal gear flow passage 37a penetrates the internal gear 16 in the first radial direction. The outer end of the internal gear flow passage 37a in the first radial direction opens to the outer peripheral surface of the internal gear 16. The inner end of the internal gear flow passage 37a in the first radial direction opens to the inner peripheral surface of the internal gear 16, i.e., the internal teeth 16a. In other words, the internal gear flow passage 37a extends inside the internal gear 16 and opens to at least the internal teeth 16a. Oil is supplied to the internal gear flow passage 37a from outside the housing 15 via a second oil supply port 37c provided on the outer periphery of the internal gear 16.

The external gear flow passage 37b penetrates the peripheral wall of the external gear 23. In this embodiment, the external gear flow passage 37b penetrates the external gear 23 in the second radial direction. The outer end of the external gear flow passage 37b in the second radial direction opens to the outer peripheral surface of the external gear 23, i.e., the external teeth 23a. The inner end of the external gear flow passage 37b in the second radial direction opens to the inner peripheral surface of the second outer ring support portion 23b. In other words, the external gear flow passage 37b extends inside the external gear 23 and has a portion that opens to the external teeth 23a and a portion that opens toward the second bearing 32.

Multiple second oil supply passages 37 are provided. That is, multiple pairs of internal gear flow passages 37a and external gear flow passages 37b are provided. In this embodiment, for example, three or more second oil supply passages 37 are provided. That is, three or more pairs of internal gear flow passages 37a and external gear flow passages 37b are provided. The multiple internal gear flow passages 37a are arranged at intervals from each other in the first circumferential direction. The multiple external gear flow passages 37b are arranged at intervals from each other in the second circumferential direction.

Although not shown in particular, when the external gear 23 is placed at a predetermined position around the first center axis C1 with respect to the internal gear 16, the internal gear flow path 37a and the external gear flow path 37b face each other in the first radial direction and communicate with each other. In more detail, when the external gear 23 rotates in the second circumferential direction and revolves in the first circumferential direction along the inner periphery of the internal gear 16, and is placed at a predetermined position in the first circumferential direction, the internal gear flow path 37a and the external gear flow path 37b communicate with each other through the meshing portion between the internal teeth 16a and the external teeth 23a. As a result, the oil in the internal gear flow path 37a flows into the external gear flow path 37b, and the oil that flows into the external gear flow path 37b flows inward in the second radial direction through the external gear flow path 37b and is discharged toward the second bearing 32.

The number of internal teeth 16a of the internal gear 16 is twice the number of external teeth 23a of the external gear 23. Therefore, the internal gear flow path 37a and the external gear flow path 37b face each other at the predetermined position for each revolution around the first center axis C1 of the external gear 23, i.e., each revolution. In other words, oil flows from the internal gear flow path 37a to the external gear flow path 37b, and oil is discharged from the external gear flow path 37b to the second bearing 32, for each revolution of the external gear 23.

In this embodiment, at least one internal gear flow passage 37a is disposed in a portion of the internal gear 16 that is located above the first central axis C1 in the vertical direction. At least one external gear flow passage 37b faces and communicates with the internal gear flow passage 37a in a portion of the external gear 23 that is located above the second central axis C2 in the vertical direction. In other words, when the internal gear flow passage 37a and the external gear flow passage 37b are connected, the oil flowing through the internal gear flow passage 37a is supplied to the second bearing 32 from above through the external gear flow passage 37b, making it easier for the oil to be distributed stably throughout the entire second bearing 32.

Although not shown in particular, the gear is annular plate-shaped with the first central axis C1 as the center. The inner peripheral surface of the gear fits with the outer peripheral surface of the end of the shaft body 26 on one axial side. The surface of the gear facing one axial side contacts the surface 21e of the first rotating body 21 facing the other axial side. The gear is fixed to the surface 21e of the first rotating body 21 facing the other axial side by screwing or the like. In other words, the gear is provided on the first rotating body 21. The gear may be fixed to the shaft body 26. At least a part of the gear is exposed to the outside of the housing 15. The gear is connected to a cup holder drive mechanism or the like (not shown) via a connecting gear or the like (not shown). The gear outputs the rotational drive force of the first rotating body 21 and the shaft body 26 around the first central axis C1 to the outside of the reciprocating linear motion mechanism 10.

In the reciprocating linear motion mechanism 10 of this embodiment described above, when a rotational driving force about the first central axis C1 is transmitted from a driving source (not shown) to the shaft body 26 and the first rotating body 21, the first rotating body 21 is rotated about the first central axis C1 relative to the housing 15. When the first rotating body 21 is rotated about the first central axis C1, the second rotating body 22 supported by the first rotating body 21 is also rotated about the first central axis C1.

At this time, because the external gear 23 of the second rotating body 22 and the internal gear 16 of the housing 15 are meshed with each other, the second rotating body 22 is rotated (revolved) around the first central axis C1 while also rotating (rotating) around the second central axis C2. When the reciprocating linear motion mechanism 10 is viewed from the axial direction, the first rotation direction T1 in which the second rotating body 22 is revolved around the first central axis C1 and the second rotation direction T2 in which the second rotating body 22 is rotated around the second central axis C2 are opposite to each other.

The ram shaft connecting portion 35 connected to the second rotating body 22 and the rotating portion 82 of the valve portion 80 rotate in a third rotational direction T3 around the third central axis C3 while performing a reciprocating linear motion along a predetermined direction in the first radial direction, i.e., the stroke direction S.
In this way, the reciprocating linear motion mechanism 10 of the present embodiment converts the rotational driving force input to the first rotor 21 into reciprocating linear motion in the stroke direction S and outputs it to the ram shaft connecting part 35. As a result, the punch 2 connected to the ram shaft connecting part 35 via the ram shaft 3 is caused to perform reciprocating linear motion in the stroke direction S. The punch 2, die 8, cup holder 6, etc. make it possible to perform DI processing on the cup-shaped body W, and the cup-shaped body W can be formed into a DI can 100.

In this embodiment, the air supply passage 28 passes through the inside of the reciprocating linear motion mechanism 10, so air can be supplied to the punch 2 from inside the reciprocating linear motion mechanism 10 through the ram shaft 3. Compared to a conventional structure in which air is supplied to the ram shaft from outside the reciprocating linear motion mechanism, this embodiment reduces the number of moving parts and the frequency of maintenance and part replacement.

According to this embodiment, the air supply passage 28 has an air chamber 29, so that by temporarily storing air in the air chamber 29, the pressure drop when the DI can (can) 100 is released from the punch 2 and the air discharge hole 71, the air communication passage 72, and the air supply passage 28 (hereinafter referred to as the air supply passage 28, etc.) are opened to the atmosphere can be suppressed to a small value. In other words, the air chamber 29 can mitigate the sudden pressure drop in the air supply passage 28, etc. caused by blowing off (releasing) the can 100 after molding, and the pressure of the air supply passage 28, etc. can be restored to a predetermined value or higher in a short time. Therefore, the air supply pressure from the air supply passage 28, etc. to the punch 2 is stabilized, and the next molded can 100 can be stably released from the punch 2. It becomes possible to mold and blow off the can 100 at high speed, and cans 100 with stable quality can be efficiently manufactured, thereby improving productivity.

More specifically, since the air chamber 29 is disposed at least inside the first rotating body 21, a large volume of the air chamber 29 can be ensured. This stabilizes the function of the air chamber 29 described above, and the effects of this embodiment are stably achieved.

In addition, in this embodiment, the air chamber 29 integrally comprises the first chamber 61 disposed inside the first rotor 21 and the second chamber 62 disposed inside the shaft 26, so that the overall volume of the air chamber 29 is secured to be larger. The air chamber 29 can further reduce the pressure drop in the air supply passage 28 etc. when the can 100 is blown off from the punch 2. The can 100 can be stably released from the punch 2.

In this embodiment, the first chamber 61 has an inner diameter dimension larger than that of the second chamber 62 , and the second chamber 62 has an axial dimension larger than that of the first chamber 61 .
Since the first rotor 21 has a large outer diameter, it is easy to ensure that the first chamber 61 located inside the first rotor 21 has a large inner diameter. Since the shaft 26 has a large axial dimension, it is easy to ensure that the second chamber 62 located inside the shaft 26 has a large axial dimension.
That is, according to the above-described configuration of this embodiment, the volume of the air chamber 29 can be stably secured to be large.

In this embodiment, the second chamber 62 has a large diameter chamber 62a and a small diameter chamber 62b.
In this case, the large diameter chamber 62a ensures a large volume capable of storing air inside the shaft body 26. The small diameter chamber 62b ensures a volume capable of storing air inside the shaft body 26 while ensuring the rigidity of the shaft body 26.

In this embodiment, the valve unit 80 is switched between a flow mode and a cut-off mode depending on the rotational position of the ram shaft connecting part 35 about the third central axis C3. That is, the supply and cut-off of air from the air supply path 28 to the ram shaft 3 is switched depending on whether the valve unit 80 is in the flow mode or the cut-off mode. In more detail, when the ram shaft connecting part 35 is caused to perform a reciprocating linear motion along a predetermined direction (stroke direction S) while rotating about the third central axis C3, air is supplied to the ram shaft 3 through the valve unit 80 in a predetermined region of the stroke direction S, and the supply of air to the ram shaft 3 through the valve unit 80 is cut off in other regions different from the predetermined region.

Unlike the present embodiment, which uses, for example, a solenoid valve, a sensor, and a control unit to electrically synchronize the discharge of air with the operation of the reciprocating linear motion mechanism, this embodiment can mechanically synchronize with the operation of the reciprocating linear motion mechanism 10 and use a simple structure to timely discharge air from the punch 2 into the inside of the can 100. For example, even if the molding speed of the can 100 is changed, the molded can 100 can be blown off in a timely manner without requiring complex adjustment work to synchronize the timing of the air discharge.

In this embodiment, the rotating portion 82 rotates around the third central axis C3 together with the ram shaft connecting portion 35 relative to the ram shaft fixing portion 81, and while the radial flow passage 90b and the long air hole 87a are in communication with each other within a predetermined range around the third central axis C3, the valve portion 80 is in the flow mode, and air is supplied from the air supply path 28 to the ram shaft 3.
In addition, while the rotating part 82 rotates around the third central axis C3 together with the ram shaft connecting part 35 relative to the ram shaft fixing part 81 and communication between the radial flow passage 90b and the long air hole 87a is blocked in a range other than the specified range around the third central axis C3, the valve part 80 is set in the blocking mode, and the supply of air from the air supply path 28 to the ram shaft 3 is blocked.
According to the above-described configuration of this embodiment, the formed can 100 can be blown off stably and timely with a simple structure.

In this embodiment, the position of the long air hole 87a about the third central axis C3 can be adjusted by rotating the outer cylinder portion 87 relative to the fixed cylinder portion 86 about the third central axis C3.
In this case, it is possible to adjust the timing at which the long air holes 87a communicate with the radial flow paths 90b. That is, the timing at which air is discharged into the inside of the can 100 can be adjusted by the simple operation of rotating the outer cylinder portion 87 about the third central axis C3. This allows the formed can 100 to be stably blown off from the punch 2.

In this embodiment, the fixing screw 88 is inserted into the adjustment slot 86 a and screwed into the outer cylinder portion 87 .
In this case, the long air hole 87a can be positioned about the third central axis C3 by rotating the outer cylinder portion 87 relative to the fixed cylinder portion 86 about the third central axis C3 and fixing the fixed cylinder portion 86 and the outer cylinder portion 87 with the fixing screw 88 in a state where the position of the long air hole 87a about the third central axis C3 is adjusted. In other words, with a simple configuration, the position of the long air hole 87a about the third central axis C3 can be adjusted and that position can be fixed.

In addition, in this embodiment, the internal gear 16, the external gear 23, the recess 27, the second bearing 32, and the protrusion 25 are arranged to overlap each other when viewed from the second radial direction. In other words, the axial positions of the internal gear 16, the external gear 23, the recess 27, the second bearing 32, and the protrusion 25 are the same, so that the bulkiness of the axial dimension of the reciprocating linear motion mechanism 10 can be reduced. The axial external dimensions of the reciprocating linear motion mechanism 10 can be kept small, and the structure can be simplified.

In addition, in this embodiment, the rotational driving force of the first rotor 21 around the first central axis C1 can be output to the outside of the reciprocating linear motion mechanism 10 via a gear. A cup holder driving mechanism or the like other than the reciprocating linear motion mechanism 10 provided in the can forming device 1 can be stably operated in synchronization with the operation of the reciprocating linear motion mechanism 10.

The present invention is not limited to the above-described embodiment, and the configuration may be modified without departing from the spirit of the present invention, for example as described below.

The shapes of the first weight portion 51 and the second weight portion 52 are not limited to those described in the above embodiment.

The present invention may be implemented by combining the various configurations described in the above-mentioned embodiments and modifications, etc., without departing from the spirit of the present invention, and addition, omission, substitution, and other modifications of configurations are possible. Furthermore, the present invention is not limited to the above-mentioned embodiments, etc., but is limited only by the scope of the claims.

The reciprocating linear motion mechanism of the can forming device and the can forming device of the present invention allow air to be supplied to the ram shaft through the inside of the reciprocating linear motion mechanism, and the formed cans can be blown off in a timely manner. Therefore, it has industrial applicability.

1...can forming device, 2...punch, 3...ram shaft, 6...cup holder, 7...through hole, 8...die, 9...end surface, 10...reciprocating linear motion mechanism, 15...housing, 16...internal gear, 21...first rotating body, 22...second rotating body, 23...external gear, 28...air supply path, 28e...fourth air flow path (air flow path of ram shaft connection part), 35...ram shaft connection part, 70...air discharge mechanism, 80...valve part, 81...ram shaft fixing part, 82...rotating part, 86...fixed cylinder part, 86a...adjustment long hole, 87...outer cylinder part, 87a...air long hole, 88...fixing screw, 90...inner cylinder part, 90a...axial flow path, 90b...radial flow path, 100...DI can (can), C1...first central axis, C2...second central axis, C3...third central axis

Claims (5)

a housing having an internal gear centered on a first central axis;
a first rotor located inside the housing in a first radial direction perpendicular to the first central axis and coupled to the housing so as to be rotatable relative to the housing about the first central axis;
a second rotating body having an external gear meshing with the internal gear about a second central axis parallel to the first central axis, the second rotating body being connected to the first rotating body so as to be rotatable relative to the second central axis;
a ram shaft connecting portion connected to the second rotor and adapted to rotate about a third central axis parallel to the second central axis and to be caused to perform a reciprocating linear motion along a predetermined direction in the first radial direction while rotating about the third central axis;
a valve portion connected to the ram shaft connecting portion;
an air supply passage passing through the first rotating body, the second rotating body, the ram shaft connecting portion, and the valve portion;
The valve unit is switched between a circulation mode in which air can pass therethrough and a blocking mode in which air cannot pass therethrough, depending on a rotational position of the ram shaft connecting portion about the third central axis.
Reciprocating linear motion mechanism for can forming equipment. The valve portion is
A ram shaft fixing portion;
a rotating portion connected to the ram shaft connecting portion and capable of rotating relatively to the ram shaft fixing portion around the third central axis,
The ram shaft fixing portion is
an outer cylinder portion centered on the third central axis;
an air hole penetrating the outer cylinder portion in a third radial direction perpendicular to the third central axis and extending around the third central axis;
The rotating part is
an inner cylinder portion located inside the outer cylinder portion in the third radial direction;
an axial flow passage extending in the axial direction inside the inner cylindrical portion and connected to an air flow passage of the ram shaft connecting portion;
a radial flow passage extending in the third radial direction inside the inner cylindrical portion and opening to the axial flow passage and an outer circumferential surface of the inner cylindrical portion;
The radial flow passage communicates with the air hole within a predetermined range around the third central axis.
2. The reciprocating linear motion mechanism of a can forming apparatus according to claim 1. the outer cylinder portion rotates about the third central axis, thereby making it possible to adjust the position of the air hole about the third central axis.
3. The reciprocating linear motion mechanism for a can forming apparatus according to claim 2. The ram shaft fixing portion is
The outer cylinder portion,
a fixed cylinder portion located outside the outer cylinder portion in the third radial direction;
A fixing screw for fixing the fixed cylinder portion and the outer cylinder portion,
the fixed cylinder portion has an adjustment slot penetrating the fixed cylinder portion in the third radial direction and extending around the third central axis,
The fixing screw is inserted into the adjustment slot and screwed into the outer cylinder portion.
4. The reciprocating linear motion mechanism for a can forming apparatus according to claim 3. A reciprocating linear motion mechanism for a can forming apparatus according to any one of claims 1 to 4;
a ram shaft extending in the predetermined direction and having one end connected to the ram shaft connecting portion;
a punch disposed at the other end of the ram shaft;
a die having a through hole into which the punch is inserted;
a cup holder that is pressed against an end surface of the die where the through hole is open;
an air discharge mechanism for supplying air to the punch through an interior of the reciprocating linear motion mechanism of the can forming device and through the ram shaft,
The air discharge mechanism includes the air supply passage.
Can forming equipment.

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