JPH106476A - Apparatus for multiplying torque for reversal coupling - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a necessary torque and enable prompt and well-balanced transmission of torque to all of coupling means by interposing a hypo-cycloid mechanism between an output gear being engaged with a plurality of coupling means and input means being rotated by standardizing the center of a circumference to transmit torque thereto. SOLUTION: A hypo-cycloid is interposed between an output gear 19 being engaged with coupling means 18 for a reversal coupling arranged on the end of the drum shaft 11 of a reversal drum in a manner being divided equally in its circumference and input means 41 to be rotated by standardizing the center of the circumference. A number of carrier pins 36 are projected on one side surface of the output gear 19, and the carrier pins 36 receive torque from the inside toothed member 37 even while being loosely engaged with pin holes 38 of the inside toothed member 37. On the outer periphery of the inside toothed member 37, a female simple arc tooth profile is formed having a reversed tooth profile to an outside toothed member 39, thus forming a hypo-cycloid mechanism through a small difference in the number of teeth between them.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reversing mechanism for switching between single-sided printing and double-sided printing in a sheet-fed printing press, and more particularly to a reversing mechanism for adjusting the phase of a gear group related to the reversing mechanism. The present invention relates to a torque multiplying device for a reversing coupling that engages / disengages a gear group at an end of a trunk shaft of a trunk.

[0002]

BACKGROUND OF THE INVENTION In sheet-fed printing presses for printing on sheets, single-sided printing for printing only on the front side of the sheet and double-sided printing for printing on the back side as well as the front side of the sheet are performed. . That is, in the case of single-sided printing, a plurality of printing units including a plate cylinder, a bracket cylinder, an impression cylinder, and an inking device are connected by a double-diameter cylinder, and printing is sequentially performed only on one side of a sheet. On the other hand, in the case of duplex printing, a paper feed cylinder, a double-diameter intermediate cylinder,
A printed sheet is reversed and printing is also performed on the back surface by interposing a reversing mechanism including a reversing cylinder. For example, printing such as four colors on the front surface and two colors on the back surface may be performed.

The center of the sheet reversing operation is the reversing cylinder and the reversing gripper, which is different from simplex printing in which the leading edge of the sheet is simply transferred. The reverse gripper receives the trailing edge of the sheet from the trailing edge gripper of the double-diameter intermediate cylinder located on the upstream side,
The sheet is turned over with the rotation of the reversing cylinder, and the sheet is delivered to the impression cylinder of the printing unit located downstream of the reversing cylinder.

[0004] Since the reversing gripper of the reversing cylinder receives the trailing edge of the sheet from the double-diameter intermediate cylinder on the upstream side, the trailing edge delivery phase of the sheet between the double-diameter intermediate cylinder and the reversing cylinder depends on the paper size. Must be set. In this case, the paper size of the sheet applied to the sheet-fed printing press varies, and in addition, the gears of the cylinder group of the printing unit and the cylinder group of the reversing mechanism are meshed in series and driven in a timely manner. It is necessary to adjust the phases of the drive gears of the cylinder group located upstream of the reversing cylinder and the drive gears of the cylinder group located downstream of the reversing cylinder in accordance with the paper size during duplex printing.

[0005] Therefore, at the end of the barrel shaft of the reversing cylinder, a gear meshing with the upstream drive gear group and a gear meshing with the downstream drive gear group can adjust the mutual phase in the rotational direction. The phase is adjusted according to the above-mentioned necessity, and is coupled to the barrel shaft.
And in order to perform such inversion coupling,
It is necessary to transmit a torque for coupling / disengaging the coupling.

[0006]

2. Description of the Related Art In Japanese Patent Publication No. 2-1020,
As shown in FIGS. 9 and 10, a fixed gear (3) and an adjusting gear (4) whose phase is adjusted with respect to the fixed gear (3) are provided at the end of the barrel shaft (2) of the reversing barrel (1). ) Is provided, wherein a set of a holding plate (5) for fastening the adjusting gear (4) to the fixed gear (3), a tightening bolt (6) and a tightening gear (7) is provided on the barrel shaft. The center gear (8) is arranged on the circumference with reference to the center of (2), and transmits torque for coupling / disengagement of the coupling by the center gear (8).

Further, in Japanese Patent Publication No. 2-1022, as shown in FIG. 11, a tightening gear (9) corresponding to the above-mentioned tightening gear (7) is arranged axially symmetrically, and There is disclosed a technique in which a torque of a coupling is transmitted by a worm shaft (10).

[0008]

However, according to the above-mentioned prior art, the required torque becomes excessively large due to the very limited space at the location, and the work is performed. In addition, there is a problem that the balance of the torque transmission to the plurality of fastening means is easily lost, and furthermore, the members related to the torque transmission are likely to be overloaded.

[0009] The present invention has been made in view of the above problems,
The purpose of the present invention is to provide a torque multiplication device for advanced reversing couplings, which aims to reduce the required torque and to transmit torque to all fastening means in a balanced manner quickly and simultaneously. And to avoid causing any trouble to the related members.

[0010]

For this purpose, the present invention provides a fastening means for a reversing coupling, which is disposed at the end of the barrel shaft (11) of the reversing cylinder with its circumference equally divided. (1
8) A torque multiplying device for transmitting a torque for fastening / releasing to an output gear (1) rotatably provided around a center of a circumference and engaged with a plurality of fastening means (18).
9) and in order to transmit torque to this output gear (19),
Input means (41) also rotated around the center of the circumference
And a hypocycloid mechanism is interposed between them.

[0011]

The torque from the input means (41) such as a steering wheel is transmitted to the output gear (19) via a hypocycloid mechanism providing a high reduction ratio, and the coupling is engaged / disengaged. As a result, all of the above-described objects are achieved, and the apparatus is extremely practical.

[0012]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a sectional view showing an embodiment of a torque multiplier according to the present invention, FIG. 2 is a side view thereof, and FIG.
Is an exploded perspective view.

The reversing cylinder in which the devices for the reversing coupling are provided, only the trunk shaft (1) is typically shown. At the end of the torso shaft (11), in effect, this torso shaft (1
The mounting base (12) which can be said to be an extension of (1) is a bolt (1).
The fixed gear (14) and the adjustment gear (15) are attached to the attachment base (12).

The fixed gear (14) is fixed to the mounting base (12) by bolts (16), and meshes with the drive gear of the impression cylinder of the next printing unit downstream of the reversing cylinder, for example. . Further, the adjusting gear (15) is arranged in parallel with the fixed gear (14) in a state where the adjusting gear (15) is rotatable with respect to the mounting base (12) and thus the trunk shaft (11). It meshes with the drive gear of the double diameter intermediate cylinder.

After adjusting the phase of the adjusting gear (15) rotatable about the barrel shaft (11) for double-sided printing (or for adjusting the phase), the mounting base is fixed by the holding plate (17). (12) It is a reversal coupling that is fastened (or released) to the fixed gear (14). For this purpose, a plurality of fastening means (18) are provided corresponding to the holding plate (17). ing.

That is, as shown in FIG. 2, the plurality of fastening means (18) and the pressing plate (17) are arranged in a satellite shape with the circumference around the trunk shaft (11) being equally divided. .
However, the fact that the center of the circumference coincides with the center of the trunk shaft (11) is only for the convenience of design, and the center of the circumference is aligned with the trunk shaft (1).
It may be deviated from the center of 1).

The details of the fastening means (18) very schematically shown in FIG. 1 are shown in FIG. 8, but such fastening means (18) are not essential to the present invention and A simple tightening bolt shown in the description of the technology may be used. In other words, a bolt having a gear portion that meshes with the output gear (19) may be used. The details of the fastening means (18) shown in FIG. 8 are already known from Japanese Patent Application Laid-Open No. 7-1713.

The bolt body (20) of the fastening means (18)
Is a neck (21) threaded on the outer periphery, this neck (2
Medium diameter part (22) which was also threaded following 1),
It comprises a large diameter portion (25) having a rolling surface (24) for a number of rollers (23). Large diameter part (25)
A number of rollers (23) are arranged on a rolling surface (24) of the outer periphery with a fixed torsion angle by a retainer (26), and these rollers (23) are further surrounded by an outer periphery. An outer ring gear (27) having a tooth portion is fitted. (By the way, the outer ring gear (27) meshes with the output gear (19) of the device of the present invention.)

Reference numeral (28) denotes a preload bearing, and the preload bearing (28) also has a large diameter portion (25).
And is pressed against the end face of the outer ring gear (27) by two preload springs (29) fitted to the middle diameter portion (22). Furthermore, a disc spring-shaped preload spring (29)
The spring pressure adjusting nut (30) generates a predetermined spring pressure. The rollers (33), the outer ring gear (27), and the like constitute what is called one-way clutch means.

The one-way clutch means will be described. First, when the fastening means (18) is loosened, FIG.
The outer ring gear (27) is rotated counterclockwise as viewed from the right side of the drawing. Then, at this time, a large number of rollers (23) arranged on the rolling surface (24) with a constant torsion angle
Is in a locked state of being tightened with respect to the large diameter portion (25), and is in a so-called biting clutch state. According to this, the release torque is increased from the outer ring gear (27) to the large diameter portion (25).
And the fastening means (18) is loosened, and the holding plate (17) also releases the adjusting gear (15).

Conversely, when the fastening means (18) is tightened, the outer ring gear (2) is rotated clockwise as viewed from the right side in FIG.
7) Rotate. At this time, since many rollers (23) are separated from each other and roll and rotate in a free state, no torque is transmitted to the large diameter portion (25). At this time, the transmission of the fastening torque is performed by the preload bearing (28) pressed against the end of the outer ring gear (27) by the preload spring (29). A predetermined spring pressure is generated in the preload spring (29) by the spring pressure adjusting nut (30), but up to a constant torque proportional to the spring pressure through the preload bearing (28). The fastening torque is transmitted to (25). However, if the fastening torque exceeds this fixed value, the preload bearing (2
8) Slip occurs, and no more torque transmission is performed anymore, so that only a constant torque is always transmitted. In other words, the one-way clutch means in the fastening means (18) of the present embodiment absorbs a torque equal to or more than a certain value in the fastening direction, and transmits the torque as it is in the releasing direction.

Returning to FIGS. 1 to 3 again, the shaft body (31) is attached so as to coincide with the center of the circumference serving as a reference for the arrangement of the holding plate (17) and the corresponding fastening means (18). The projection is fixed to the base (12). This shaft body (31)
Is a so-called core material of the apparatus of the present invention which is integrally modularized, and includes a flange portion fixed to the mounting base (12), a large-diameter portion fitted to the casing (32), and an output gear. It has a medium diameter portion which is the center of rotation of (19) and a small diameter portion which is the center of rotation of the eccentric bush (33).

The mounting base (1) together with the shaft (31) is provided.
The casing (32), which is fastened to the 2) by bolts (34), also integrates the device according to the invention, as can be seen from FIGS. 2 and 3, the fastening means (18) and the output gear. This portion is a dish-shaped member that is cut out so as not to prevent meshing with (19).

An output gear (19) which is freely attached to a middle diameter portion of the shaft body (31) has a fastening means (1) on its outer periphery.
8) has a gear portion (35) that meshes with the outer ring gear (27), and has a plurality of carrier pins (3
6) is projected at a constant pitch on a constant circumference. The carrier pin (36) is engaged with a pin hole (38) of an inner tooth member (37) described later,
7) plays the role of receiving torque from

The ring-shaped outer tooth member (39) is fixed to the side end of the casing (32) by bolts (40). Therefore, this outer tooth member (39) always remains in the fixed position. A simple arc tooth shape having the number of teeth Z2 is formed on the inner periphery of the outer tooth member (39). In addition, as the tooth profile,
It may have a normal involute shape.

As shown in FIG. 4, an inner tooth member (37) is provided corresponding to the outer tooth member (40). On the outer periphery of the inner tooth member (37), a so-called female simple arc tooth profile is formed which is opposite to the tooth shape of the outer tooth member (40), and the number of teeth Z1 is the same as that of the outer tooth member (39). The number of teeth is slightly different from Z2. Incidentally, FIG. 5 to FIG.
As indicated by the numbers up to, there is a difference in the number of single teeth of Z2 = 18 and Z1 = 17. Such a small tooth number difference forms the essence of the hypocycloid mechanism.

The inner tooth member (37) is provided with an eccentric bush (3).
Via 3), it is freely attached to the small diameter portion of the shaft body (31). As the name implies, the eccentric bush (33) has its graphic center at a position different from the center of the shaft (31). 31) brings eccentric rotation to the inner tooth member (37). Also, the inner teeth member (3
7) are provided with a number of pin holes (38) for receiving the carrier pins (36). The gap between the pin hole (38) and the carrier pin (36) is formed by the eccentric bush (3).
The amount of eccentricity of the inner tooth member (37) according to 3) is set to twice.

The eccentric bush (33) has, at one end thereof, a pin receiver (43) which engages with a pin (42) of a handle (41) (which is an input means). The torque is received from the handle (41) which is turned around the center. Of course, an appropriate motor may be connected instead of the handle (41) inserted into the center hole (44) of the shaft body (31). The ring (45) and the snap ring (46) are used to prevent the eccentric bush (33) from coming off, so that the device of the present invention is finally integrally formed with the shaft (31), the casing (32) and the like.

Next, the operation will be described. The hypo-cycloid mechanism, which is the core of the torque intensifier according to the present invention, has an inner tooth member (37) (number of teeth Z1) with a small number of small teeth. High reduction ratio (Z2-Z) due to the inscribed planetary motion of the outer tooth member (39) (number of teeth Z2)
1) The speed reduction mechanism is defined as / Z1, and the speed reduction ratio of the mechanism shown in FIGS. 5 to 7 is (18-17) / 17, that is, 1/17.

As shown in the figure, the inner tooth member (37) receives the torque from the handle (41) as input means via the eccentric bush (33), and in the same direction as the input torque direction, the outer tooth member (37). Revolves while inscribed with 39).

At the same time, the inner tooth member (37) is decelerated in the direction opposite to the input torque direction since the outer tooth member (39) is fixed and slidable with the eccentric bush (33). Rotate.

Then, the rotation reduced at this high ratio is transmitted from the output gear (19) to the fastening means (18) via the carrier pin (36), and is used for fastening / releasing the coupling.

[0033]

According to the torque multiplier according to the present invention,
Despite the very limited space at the installation location, the work is easy to carry out, and of course, the required torque can be greatly reduced and the transmission balance can be improved. It can greatly contribute.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a torque multiplier according to the present invention.

FIG. 2 is also a side view.

FIG. 3 is an exploded perspective view of various members constituting the device.

FIG. 4 is a front view of a hypocycloid mechanism forming the core of the device.

FIG. 5 is a diagram illustrating the operation of the hypocycloid mechanism.

FIG. 6 is an operation explanatory view showing a state following the state of FIG. 5;

FIG. 7 is an operation explanatory diagram showing a state following the state of FIG. 6;

FIG. 8 is a sectional view showing an example of a fastening means.

FIG. 9 is a cross-sectional view of the prior art.

FIG. 10 is also a front view of the related art.

FIG. 11 is a front view of another related art.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 Body shaft 12 Mounting base 14 Fixed gear 15 Adjustment gear 17 Pressing plate 18 Fastening means 19 Output gear 31 Shaft 32 Casing 33 Eccentric bush 36 Carrier pin 37 Inner tooth member 38 Pin hole 39 Outer tooth member 41 Handle (input means)

Claims (1)

[Claims] 1. A torque for fastening / unlocking is transmitted to a fastening means (18) for a reversing coupling, which is disposed at an end of a barrel shaft (11) of the reversing cylinder and is equally divided in circumference. And an output gear (19) rotatably provided around the center of the circumference and meshing with the plurality of fastening means (18), and transmitting torque to the output gear (19). A torque multiplier for a reversing coupling, wherein a hypocycloid mechanism is interposed between the input means (41) and the input means (41) which is also rotated around the center of the circumference.