JP2018180396A - Damper device and office equipment with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper device that can control a torque of a cover opened and closed to a main body of office equipment by an opening/closing angle from an opening angle 0° and further beyond a free-standing angle where the gravity center of the cover is positioned right above a hinge.SOLUTION: A damper device biases a cover in the direction to open the cover when an opening angle of the cover is less than a free-standing angle, prevents the cover from suddenly falling down to the rear at the opening action beyond the free-standing angle, further controls a torque of the cover so as to prevent a sudden closing action in the closing action from the free-standing angle. Alternatively, a constant braking torque operates to the cover by a friction mechanism in the all turning range (0°≤φ≤180°) . A free stop function is implemented in a predetermined opening angle range (40°≤φ≤120°) by this braking torque, and a sudden closing action is suppressed. Also, wobble in the free-standing angle of the cover is prevented by the braking torque.SELECTED DRAWING: Figure 8

Description

  The present invention is a cover used particularly for a sheet storage section of office equipment such as a large-size printing press for business use, and is suitably used for a cover opened and closed beyond 0 ° from a neutral angle, and this damper It relates to office equipment using the device.

  Among the above-mentioned paper covers, there is one in which a paper cover in the form of a cross-sectional key is configured to be opened from a closed state of 0 ° to a maximum of 180 ° over a neutral angle. Usually, such as a document press plate opening / closing device for office equipment called a multi-function machine, since a document press plate with an automatic document feeder is used, its weight at the time of opening operation from 0 ° in a closed state Control the opening and closing torque of the original cover by using a compression spring so that it can be opened without making it feel free to naturally fall from the open state in the middle, and free stop in the intermediate open angle range. There is. In addition, the elasticity of the compression spring is set to 0 at a predetermined opening angle (neutral angle) where the center of gravity of the cover is positioned immediately above the hinge so that the original cover does not jump up suddenly when the original cover is opened. It is configured to be The present situation is that there is no means for controlling the opening and closing torque of the cover after the neutral angle.

  As a damper device of this type, a slider and a cam are provided in a main body member fixed to an office equipment, and a cam torque of a cam member is pressed by a cam receiving portion of the slider to give a rotational torque to the cam member. By urging the cover in the opening direction to the office equipment through the damper arm fixed to the cam member, a so-called damper function is realized which prevents the cover from rotating rapidly in the closing direction to the office equipment. A so-called fleece capable of stopping the cover at an arbitrary rotation angle within a predetermined rotation range by generating a braking torque against the rotation of the cover using the frictional force between the slider and the main body member One having a top function is known (Patent Document 1).

JP, 2013-186277, A

  However, in the damper device described in Patent Document 1, the braking torque is generated in the cover by the frictional force between the slider and the main body member. Therefore, in order to realize the free stop function, predetermined rotation of the cover is performed. In the range, it is necessary to manufacture the body member and the slider with high precision so that the slider can contact with the inner circumferential surface of the body member with a constant pressure. This is one of the factors preventing the cost reduction of the damper device.

  Further, in the damper device described in Patent Document 1, it is possible to adjust the frictional force between the slider and the main body member, which are members manufactured to have a fixed shape and size, respectively, because the frictional force is generated between them. Have difficulty. For this reason, it has been difficult to adjust the braking torque at the time of manufacture or attachment of the damper device to improve the feeling of operation at the time of turning operation of the cover.

  An object of the present invention is a damper device capable of controlling the opening and closing torque of a cover opened and closed with respect to a main body of an office equipment from an opening angle of 0 ° to a neutral angle where the center of gravity of the cover is located directly above a hinge and beyond An object of the present invention is to provide office equipment using a damper device.

  In order to achieve the above object, a damper device according to the present invention is a damper device for controlling an opening operation of a cover openably and closably connected to a main body of an office machine via a hinge, and this damper device is A damper case fixed to a main body of office equipment, a shaft rotatably mounted between both side plates of the damper case, a cam rotatably mounted on the shaft in the damper case, and the cam A slider slidably provided in the damper case, an urging member provided in the damper case for pressing the slider toward the cam, and one end of the cam outside the damper case A damper arm fixed on the side and rotatable with the cam, and the damper arm and the shaft to control the rotation of the damper arm And a friction arm provided between the two, and a link arm rotatably coupled at one end to the other end of the damper arm and the other end connected to the cover. The apparatus is characterized in that the opening / closing operation of B. is biased in the opening direction from 0.degree. To the neutral angle, and in the closing direction above the neutral angle.

  According to the above configuration, the slider is urged toward the cam by the biasing member, and the cam receiving portion of the slider presses the cam surface of the cam, whereby the center of gravity of the cover is less than the neutral angle located immediately above the hinge. In the above, the cover is biased to open with respect to the main body of the office equipment, and at the opening angle beyond the neutral angle, the cover is biased to close to the main body of the office equipment. As a result, a damper function is realized that can control the rotational torque of the cover from an opening angle of 0 ° to a neutral angle or more, for example, up to 180 °.

  On the other hand, since the damper arm is in pressure contact with the friction member when the presser washer is pressed by the presser washer that constitutes the friction mechanism, constant rotational friction between the damper arm and the friction member when the cover rotates with respect to the main body of the office machine Resistance occurs. The rotational frictional resistance acts on the cover via the damper arm to generate a constant braking torque on the cover. The braking torque realizes a free stop function. The braking torque works even when the turning angle of the cover is the neutral angle, so that it is possible to prevent the cover from being wobbled at the neutral angle.

Thus, by adopting a friction mechanism that causes the cover to generate a braking torque by the rotational frictional resistance between the damper arm and the friction member, the related art that generates the braking torque in the cover by the frictional force between the slider and the main body member The free stop function can be realized with an inexpensive configuration as compared with the configuration of.
In addition, since the braking torque of the cover can be adjusted by adjusting the pressing force of the spring washer by the holding washer, the operation feeling of the cover can be adjusted by adjusting the braking torque at the time of manufacture or installation of the damper device. Can be made good.

  In the damper device according to the present invention, a shaft hole through which one end of the shaft is inserted is formed at the base end of the damper arm, and the holding portion is a position near the damper arm of the shaft And the friction member is disposed between the damper arm and the holding portion in a state of being annularly mounted on the shaft, and the friction member is disposed on the shaft. The spring washer is a member that is non-rotatably locked to the holding portion, and the spring washer is a state in which one end of the shaft is inserted into the shaft hole from the one side of the damper arm, the one end And the presser washer is annularly mounted on the one end of the shaft while overlapping the axial direction outer side of the spring washer. And a member, to said one end of said shaft, it is desirable that the swaged portion is formed so as to press the pressing washer to the spring washer.

  According to the above configuration, the friction member is fitted to the shaft and locked to the holding portion, and the end portion of the shaft closer to the holding portion is inserted into the shaft hole of the damper arm. After fitting a spring washer and a pressure washer, form a caulking portion at the end, press the pressure washer against the spring washer by the caulking portion to generate a braking torque against the movement of the cover. To be realized. Further, according to this friction mechanism, the pressing force of the spring washer by the pressing washer can be adjusted by the axial size of the caulking portion of the shaft end, that is, the caulking amount of the shaft, so the manufacture of the damper device The braking torque can be adjusted at any time.

Preferably, the damper device according to the present invention further includes a friction member that rotates with the damper arm to generate rotational friction resistance with the spring washer.
According to this configuration, in addition to the rotational friction generated between the damper arm and the friction member, the rotational friction generated between the spring washer and the additional friction member acts to resist the movement of the cover. The braking torque can be generated more effectively.

Further, in the damper device according to the present invention, it is preferable that a sheet that covers the upper side of the cam is attached to the damper case.
According to this configuration, since the upper side of the cam is covered by the sheet, it is possible to prevent the problem that the finger is pinched between the slider and the cam and the finger is stained by the lubricant.

Further, in the damper device according to the present invention, the damper case includes an inner main body made of resin in which the slider is movably accommodated, and an outer side made of metal in which the inner main body is accommodated and fixed to the office equipment. It is desirable to consist of a body.
According to this configuration, the damper device can be firmly attached to the main body of the office machine while facilitating the movement of the slider relative to the damper case.

Further, in the damper device according to the present invention, it is preferable that one end of the sheet is attached to and supported by the end of the inner main body on the cam side, and the other end extends above the cam. desirable.
According to this configuration, the sheet covering the upper side of the cam can be attached to the damper case by a simple method of affixing to the inner main body of the damper case.

  According to the present invention, it is possible to control the opening and closing torque of the cover from the opening angle 0 ° to the neutral angle and beyond, and to provide a damper device having a free stop function with an inexpensive configuration. it can.

It is a perspective view which illustrates an embodiment of a damper device of the present invention. It is a perspective view of another angle of the damper apparatus shown in FIG. It is a right view of the damper apparatus shown in FIG. It is a left view of the damper apparatus shown in FIG. It is a top view of the damper apparatus shown in FIG. It is AA sectional drawing of FIG. It is a principal part enlarged view of FIG. It is a disassembled perspective view of the damper apparatus shown in FIG. It is a perspective view of an outer side body. (A) is a perspective view of the left member of an inner main body. (B) is a perspective view of the right member of the inner body. (A) is a perspective view of a slider. (B) is the perspective view. (A) is a perspective view of a cam. (B) is the perspective view. (A) is a perspective view of a damper shaft. (B) is the partial fracture front view. (C) is its left side view. (A) is a perspective view of office equipment when the cover is closed. (B) is a figure which shows the state of the damper apparatus in office equipment at that time. (A) is a perspective view of the office equipment when the rotation angle φ of the cover is 40 °. (B) is a figure which shows the state of the damper apparatus in office equipment at that time. (A) is a perspective view of the office equipment when the rotation angle φ of the cover is 120 °. (B) is a figure which shows the state of the damper apparatus in office equipment at that time. (A) is a perspective view of the office equipment when the rotation angle φ of the cover is 180 °. (B) is a figure which shows the state of the damper apparatus in office equipment at that time. It is sectional drawing which shows the state inside the damper apparatus of FIG.14 (b). It is sectional drawing which shows the state inside the damper apparatus of FIG.15 (b). It is sectional drawing which shows the state inside the damper apparatus of FIG.16 (b). It is sectional drawing which shows the state inside the damper apparatus of FIG.17 (b). It is a figure which shows the torque curve of the cover of office equipment, and a damper apparatus.

Hereinafter, an embodiment of a damper device according to the present invention will be described with reference to the attached drawings.
FIGS. 14 (a), (b) to 17 (a), (b) show perspective views and sectional views of various states of a large-scale printing press 50 for business use provided with the damper device 1 according to the present invention. ing.
The large-sized printing press 50 shown in FIGS. 14 (a) and (b) to FIGS. 17 (a) and 17 (b) includes a main body 51 of office equipment, a cover 52, a hinge 53, a link arm 54 and a damper device 1. The main body 51 of the office machine forms the main structure of the large printing machine 50, and various groups of devices constituting the large printing machine 50 (printing apparatus, printing paper conveying apparatus, control apparatus for controlling the operation of these apparatuses, etc. ) To accommodate. The cover 52 covers the opening 51 a of the sheet storage portion provided near the left end of the main body 51 of the office machine. The hinge 53 pivotally connects the cover 52 to the main body 51 of the office machine. The link arm 54 connects the damper device 1 and the cover 52. The damper device 1 is fixed to the main body 51 of the office equipment. That is, the damper device 1 is fixed to the main body 51 of the office machine and connected to the cover 52 through the link arm 54.

As shown in FIGS. 14A and 14B, when the cover 52 is completely closed to the main body 51 of the office machine, the cover 52 closes the opening 51a of the main body 51 of the office machine. From this state, when the cover 52 is opened, the intermediate state illustrated in FIGS. 15 (a) and (b) and FIGS. 16 (a) and 16 (b) is obtained. Thus, the cover 52 is completely open to the main body 51 of the office machine.
In the state shown in FIGS. 17 (a) and 17 (b), the cover 52 is disposed at a position completely separated rearward from the opening 51a of the main body 51 of the office machine. As described above, when the cover 52 is completely open to the main body 51 of the office machine, the user (worker) inserts his hand into the main body 51 of the office machine from the opening 51a of the main body 51 of the office machine It is possible to perform replenishment work and the like.

  The damper device 1 has a damper function to buffer the sudden rotation of the cover 52 with respect to the main body 51 of the office equipment, and generates a constant braking torque in the cover 52 so that the cover 52 can be rotated any time in a predetermined rotation range. And a free stop function capable of stopping at a dynamic angle.

[Configuration of damper device]
In the following description, the configuration of the damper device 1 will be described on the basis of vertical and horizontal directions indicated by three-axis or two-axis orthogonal arrow lines appropriately described in the drawings.

  As shown in FIGS. 1 to 8, the damper device 1 includes a damper case 2, a damper arm 3, a cam 4, a shaft 5, a slider 6, an urging member 7, a friction mechanism 8, and a mounting substrate 9.

[Damper case]
As shown in FIGS. 1 and 2, the damper case 2 includes an outer main body 10 and an inner main body 20.
As shown in FIG. 9, the outer main body 10 is a box-like member manufactured by appropriately bending a metal plate, and has a left side plate portion 11, a right side plate portion 12 and a front plate portion 13.

The left side plate portion 11 of the outer main body 10 forms the left side portion of the damper case 2, and the right side plate portion 12 forms the right side portion of the damper case 2. The side view shapes of the left side plate portion 11 and the right side plate portion 12 are generally rectangular long in the front-rear direction. The rear end portions of the left side plate portion 11 and the right side plate portion 12 are provided with protruding portions 11a, 12a protruding backward, respectively, and bearing holes respectively at positions corresponding to the left and right direction of both protruding portions 11a, 12a. 11b and 12b are provided. The left end portion 5 a of the shaft 5 is inserted into the bearing hole 11 b of the left side plate portion 11 as described later. The shaft 5b of the shaft 5 is inserted into the bearing hole 12b of the right side plate 12 as described later. The bearing holes 11b of the left side plate portion 11 are formed in a polygonal shape (a pentagon in this example). The bearing hole 12b of the right side plate 12 is formed in a substantially elliptical shape that is long in the front-rear direction according to the cross-sectional shape (see FIGS. 13A and 13C) and dimensions of the shaft 5b of the shaft 30.
Further, the left side plate portion 11 and the right side plate portion 12 are bent in a direction in which the upper edges and the lower edges of each other approach. Thus, upper plate portions 11c and 12c and lower plate portions 11d and 12d extending in the front-rear direction are formed on the left side plate portion 11 and the right side plate portion 12, respectively.
Further, in the left side plate portion 11, a screw insertion hole 11e through which a screw 43 (see FIGS. 4 and 8) for fixing the mounting substrate 9 to the outer surface (left side surface of the damper case 2) of the left side plate portion 11 is inserted. Are provided at a plurality of places (four places in this example).

The front plate portion 13 of the outer main body 10 forms a front end portion of the damper case 2. The front view shape of the front plate portion 13 is
It is roughly square. The left side plate 11 and the right side plate 12 are connected via the front plate 13. The upper edge and the lower edge of the front plate 13 are bent at substantially right angles toward the front. Thereby, engaging edge parts 13a and 13b engaged with the front end part of the inner side main body 20 are formed in the upper edge part and lower edge part of the front plate part 13 (refer FIG. 8, FIG. 18-FIG. 21). ).

  As shown in FIGS. 8 and 10A and 10B, the inner main body 20 is composed of a left member 21 and a right member 22. The inner main body 20 is accommodated in the outer main body 10 in a state where the left member 21 and the right member 22 are joined.

  As shown in FIG. 10A, the left member 21 projects from the upper edge of the left side plate portion 23 to the left side plate portion 23 forming the left side portion of the inner main body 20 and extends to the right (inner side) from the upper edge 24, a left lower plate 25 extending from the lower edge of the left side plate 23 to the right (inward) extending in the front-rear direction, an upper left beam 26 provided on the lower end of the front end of the upper plate 24, and the lower left plate 25 And a left lower beam 27 provided on the front end upper side.

  As shown in FIG. 10 (b), the right member 22 projects from the upper edge of the right side plate 28 to the left side (inner side) from the upper edge of the right side plate 28 which forms the right side of the inner main body 20 29, a lower right plate 30 extending to the left (inward) from the lower edge of the right side plate 28 and extending in the front-rear direction, an upper right beam 31 provided on the lower end of the front end of the upper plate 29, and a lower right plate And 30 a lower right beam 32 provided on the upper side of the front end.

  As shown in FIGS. 10 (a) and 10 (b), rear end portions of the left side plate portion 23 and the right side plate portion 28 of the inner main body 20 are provided with protruding portions 23a and 28a that project rearward. . The protrusions 23a and 28a are formed so as to overlap with the protrusions 11a and 12a of the outer main body 10 right and left, respectively, when the inner main body 20 is accommodated in the outer main body 10. And, in the projections 23a, 28a of the inner main body 20, circular bearing holes 23b, 28b communicating with the bearing holes 11b, 12b of the outer main body 10 are respectively formed.

As shown in FIG. 10A, the right edge of the upper left plate 24 and the lower left plate 25 of the left member 21 is fitted with the left edge of the upper right plate 29 and the lower right plate 30 of the right member 22. The fitting steps 24a, 25a are formed. Further, fitting protrusions 26 a and 27 a are formed at the right ends of the upper left beam 26 and the lower left beam 27 so as to fit with the left ends of the upper right beam 31 and the lower right beam 32 of the right member 22.
Further, on the right side portion of the upper surface portion of the upper left plate portion 24, an upward convex surface portion 24d extending in the front-rear direction is formed. A downward convex portion 25 d extending in the front-rear direction is formed on the right side portion of the lower surface portion of the lower left plate portion 25.

As shown in FIG. 10B, the right edge of the upper right plate 29 and the lower right plate 30 of the right member 22 is fitted with the right edge of the upper left plate 24 and the lower left plate 25 of the left member 21. The fitting steps 29a, 30a are formed. Further, at the left ends of the upper right beam 31 and the lower right beam 32 of the right member 22, fitting recesses 31a and 32a are formed, which fit with the right ends of the upper left beam 26 and the lower left beam 27.
Further, on the left side portion of the upper surface portion of the upper right plate portion 29, an upward convex portion 29d extending in the front-rear direction is formed. A downward convex surface portion 30 d extending in the front-rear direction is formed on the left side portion of the lower surface portion of the lower right plate portion 30.

The left member 21 and the right member 22 configured as described above fit the fitting stepped portions 24 a and 25 a of the left member 21 and the fitting stepped portions 29 a and 30 a of the right member 22 to each other. Are integrated by fitting the fitting projections 26a, 27a and the fitting recesses 31a, 32a of the right member 22 to each other to form a box-like inner main body 20. And when the inner main body 20 is accommodated in the outer main body 10, both are integrated and the box-shaped damper case 2 is comprised.
At that time, the engaging portions 13a and 13b formed at the front end portions of the engaging edge portions 13a and 13b of the outer main body 10 engage with the upper beam portions 26 and 31 and the lower beam portions 27 and 32 of the inner body 20, respectively. . Alternatively, the upward convex portions 24 d and 29 d of the inner main body 20 fit between the upper left plate portion 11 c and the upper right plate portion 12 c of the outer main body 10, and the downward convex portions 25 d and 30 d of the inner main body 20 are the outer main body 10. Between the lower left plate portion 11d and the lower right plate portion 12d. As a result, the resin inner body 20 is stably held by the metal outer body 10. The slider 6 and the biasing member 7 are accommodated in the inner body 20.

  The inner surface of the inner main body 20 functions as a guide surface for guiding the slider 6 in the front-rear direction. In detail, portions close to the left side plate portion 23 of the lower surface of the upper left plate portion 24 and the upper surface of the lower left plate portion 25 form sliding contact surfaces 24b, 25b with which the upper surface left end portion and the lower surface left end portion of the slider 6 make sliding contact. Similarly, portions close to the right side plate portion 28 of the lower surface of the upper right plate portion 29 and the upper surface of the lower right plate portion 30 form sliding contact surfaces 29b, 30b with which the upper surface right end portion and the lower surface right end portion of the slider 6 come in sliding contact.

  Further, the lower surface of the upper left plate portion 24 and the portions near the fitting step portions 24a and 25a of the upper surface of the lower left plate portion 25 are respectively separated above and below the sliding contact surfaces 24b and 25b, and the sliding contact surfaces 24b and 25b Steps 24c and 25c are formed at the boundary between the two. Similarly, the lower surface of the upper right plate portion 29 and the portions near the fitting step portions 29a and 30a of the upper surface of the lower right plate portion 30 are respectively separated above and below the sliding contact surfaces 29b and 30b, and the sliding contact surface 29b Step portions 29c and 30c are formed at the boundary between the step portions 30b and 30b.

  The rear end of the inner main body 20 is opened so that the cam receiving portion 6h of the slider 6 can protrude and retract (see FIGS. 18 to 21). In addition, the upper left beam 26 and the upper right beam 31 and the lower left beam 27 and the lower right beam 32 are vertically separated to receive the front end 7Bb of the biasing member 7.

  Also, a resin sheet 35 covering the upper side of the cam 4 is attached to the rear end portion of the convex portion 24 d of the upper left plate portion 24 of the inner main body 20 and the rear end portion of the convex portion 29 d of the upper right plate portion 24. The pasting surfaces 24e and 29e of each are formed. The pasting surfaces 24e, 29e are formed by lowering the rear end portions of the convex portions 24d, 29d by the thickness of the sheet 35, and form a continuous flat surface when the left member 21 and the right member 22 are joined. One end (front end) 35 a of the sheet 35 is attached to the pasting surfaces 24 e and 29 e of the inner main body 20 and supported in a cantilever state, and the other end (rear end) 35 b extends above the cam 4. It exists (see Figure 1).

[Damper arm]
The damper arm 3 is a rod-like member manufactured by appropriately bending a metal plate (iron plate), and is connected to a base 3 a fixed to the cam 4 and a link arm 54 as shown in FIGS. 1 to 8. And a tip 3b.
The base 3 a of the damper arm 3 is formed to be larger than the side view sectional area of the cam 4. The base 3a is formed with a pin insertion hole 3d, a shaft hole 3e, a fitting hole 3f and a locking portion 3g (see FIG. 8). The right end portions 33a of the three pins 33 inserted into the cam 4 are respectively inserted into the pin insertion holes 3d. The damper arm 3 is fixed to the cam 4 by attaching the fixing bracket 34 to the right ends 33 a of the three pins 33 and caulking the right ends 33 a of the pins 33. The right end portion 5 c of the shaft 5 inserted into the cam 4 is inserted into the shaft hole 3 e. The damper arm 3 is coupled to the right end 5 c of the shaft 5 via the friction mechanism 8. Further, the fitting projection 4d (see FIG. 12A) of the cam 4 is fitted in the fitting hole 3f. A part of a second friction washer 37 described later is locked to the locking portion 3g.

  A link arm connection hole 3 c is provided at the tip 3 b of the damper arm 3. The damper arm 3 is mounted on the link arm 54 by mounting the pivot pin 55 in both connection holes in a state where the link arm connection hole 3c and the connection hole formed at one end of the link arm 54 are communicated. It is connected rotatably. The other end of the link arm 54 is pivotably connected via a pivot pin 57 to a bracket 56 fixed to the back of the cover 52 of the main body 51 of the office machine. That is, the damper arm 3 is connected to the cover 4 via the link arm 54, the bracket 56, and the pivot pins 55, 57 (see FIGS. 14 (b) to 17 (b)).

[cam]
The cam 4 is made of POM (polyoxymethylene) which is a kind of resin material.
As shown to FIG. 12 (a), (b), the cam 4 is provided with the trunk | drum 4a and the overhang | projection part 4b. The body portion 4a forms a main structure of the cam 4, and the outer peripheral surface thereof forms a cam surface 4c that abuts on the cam receiving portion 6h (see FIG. 11) of the slider 6. The overhanging portion 4b is a portion that overhangs to the right of the body portion 4a.

  The cam 4 is formed with a shaft hole 4d, a pin through hole 4e and a fitting protrusion 4d. The shaft hole 4d passes through the body 4a from side to side. The shaft hole 4d is a cylindrical hole through which the shaft 5b (see FIGS. 8 and 13) of the shaft 5 is rotatably inserted. The pin through holes 4e pass through the body portion 4a and the overhang portion 4b from side to side. A plurality of (three in this example) pin insertion holes 4 e are formed corresponding to the pin insertion holes 3 d of the damper arm 3. The fitting protrusion 4 d is provided on the right side surface of the overhang portion 4 b in correspondence with the fitting hole 3 f of the damper arm 3.

  A metal bracket 36 (see FIG. 8) is mounted on the left side surface of the body 4a of the cam 4. A plurality of (three in this example) pin through holes are formed in the bracket 36 in correspondence with the pin through holes 4 e of the cam 4. When the cam 4 is fixed to the damper arm 3, the bracket 36 is attached to the left side surface of the body 4 a of the cam 4, and the pin 33 is inserted into the pin penetration hole 4 e of the cam 4 through the pin penetration hole of the bracket 36.

  As shown in FIG. 12B, the cam surface 4c has a guide surface 4f, a first holding surface 4g, a second holding surface 4h, and a third holding surface 4i in the counterclockwise direction. The guide surface 4f is a smooth curved surface having a substantially arc shape. The first holding surface 4g and the second holding surface 4h are flat surfaces. The third holding surface 4i is a concave surface having a slight curvature. A blank groove 4j is provided between the first holding surface 4g and the second holding surface 4h.

[shaft]
The shaft 5 is a rod-like metal member.
As shown in FIGS. 13 (a), (b) and (c), the shaft 5 has a shaft 5b and a holder 5d. The shaft portion 5 b is a portion that rotatably holds the cam 4 with respect to the damper case 2. The holding portion 5 d is a part that is a component of the friction mechanism 8.

  The shaft portion 5 b has a substantially elliptical shape whose cross-sectional shape is long in the front-rear direction. Specifically, as shown in FIGS. 13 (a) and 13 (c), the front and rear side surfaces 5h of the shaft portion 5b are outwardly convex partial cylindrical surfaces, and the upper and lower side surfaces 5i are planes parallel to each other. The shaft portion 5 b is non-rotatably fitted with the bearing hole 12 b of the outer main body 10. On the other hand, the front and rear side surfaces 5 h of the shaft portion 5 b slidably contact the inner surface of the shaft hole 4 d of the cam 4 in a rotatable manner.

  When the cam 4 is mounted on the damper case 2, the left end 5 a side of the shaft 5 is inserted into the damper case 2 from the bearing holes 12 b and 28 b on the right side and penetrates the shaft hole 4 d of the cam 4 disposed in the damper case 2 Then, the left bearing holes 11 b and 23 b of the damper case 2 are inserted. Thus, the shaft 5 is bridged between the left and right side plates of the damper case 2. The cam 4 is rotatably supported by the damper case 2. On the other hand, the shaft 5 is held non-rotatably with respect to the damper case 2.

  The holding portion 5d is a substantially annular flange portion formed in the vicinity of the right end portion 5c of the shaft portion 5b (position close to the damper arm 3). The diameter of the holding portion 5d is larger than the diameter of the shaft hole 12b. The holding portion 5d is formed with a locking recess 5e for locking a friction washer 36 (see FIGS. 7 and 8) described later. The right end portion 5c of the shaft portion 5b has a cylindrical portion 5f opened to the right. The cylindrical portion 5f is a caulking portion 40 (see FIG. 7) described later.

[Slider, biasing member]
As shown in FIGS. 8 and 11 (a) and 11 (b), the slider 6 is a substantially rectangular member, and is made of POM (polyoxymethylene) which is a kind of resin material.
As shown in FIG. 8, the biasing member 7 comprises an outer spring 7A and an inner spring 7B. Each of the outer spring 7A and the inner spring 7B is a cylindrical wound spring, and as shown in FIGS. 18 to 21, the inner spring 7B is disposed in the outer spring 7A. The outer spring 7A and the inner spring 7B are compressed in the front-rear direction, and the slider 6 is always urged toward the cam 4 by the repulsive force thereof.

  As shown in FIGS. 11A and 11B, the slider 6 is formed with an outer spring receiving hole 6a, an inner spring receiving hole 6b, a first cam receiving protrusion 6c, a second cam receiving protrusion 6d, and a guide protrusion 6e. It is done.

Both the outer spring receiving hole 6 a and the inner spring receiving hole 6 b are open at the front of the slider 6.
The outer spring receiving hole 6a is an annular hole, into which the rear end side portion of the outer spring 7A is inserted. The rear end 7Aa (see FIG. 8) of the outer spring 7A abuts on the bottom surface 6f of the outer spring receiving hole 6a. Further, the front end 7Ab (see FIG. 8) of the outer spring 7A abuts on the rear surfaces of the beam portions 26, 27, 31, 32 of the inner main body 20.

  The inner spring receiving hole 6b is a cylindrical hole formed inside the outer spring receiving hole 6a via the cylindrical partition wall 6h, and the rear end side portion of the inner spring 7B is inserted therein. On the inner peripheral surface of the partition wall 7h, there is formed an inclined surface 7i whose diameter increases from the front-rear direction middle portion toward the opening (the front end). The outer diameter of the inner spring 7B is substantially equal to the opening diameter of the inner spring receiving hole 6b. For this reason, the rear end side portion of the inner spring 7B is inserted into the inner spring receiving hole 6b while being compressed following the inclined surface 7i. The rear end 7Ba (see FIG. 8) of the inner spring 7B abuts on the bottom surface 6g of the inner spring receiving hole 6b. Further, the front end 7Bb (see FIG. 8) of the inner spring 7B abuts on the rear surface of the front plate portion 13 of the outer main body 10. The angle of the inclined surface 7i with respect to the axial direction of the inner spring receiving hole 6b in this example is 3 °.

  The first cam receiving projection 6 c and the second cam receiving projection 6 d are portions that abut on the cam surface 4 c of the cam 4. That is, the first cam receiving projection 6 c and the second cam receiving projection 6 d constitute the cam receiving portion 6 h of the slider 40. The first cam receiving projection 6c and the second cam receiving projection 6d are formed so as to be symmetrical with each other in vertical symmetry, and both extend over the left and right ends of the rear end portion of the slider 6.

  As shown in FIG. 11A, the guide protrusion 6e is formed in the vicinity of the left end of the upper surface of the slider 6 and extends in the front-rear direction. The guide projection 6e is a portion in contact with the step 24c (see FIG. 10A) formed on the lower surface of the upper left plate portion 24 of the inner main body 20 when the slider 6 is accommodated in the inner main body 20.

As shown in FIGS. 18 to 21, the slider 6 is accommodated in the inner main body 20 so as to be movable in the front-rear direction. Then, as the slider 6 moves in the front-rear direction with respect to the inner main body 20, the first cam receiving projection 6c and the second cam receiving projection 6d protrude and retract rearward from the inner main body 20. At this time, the guide projection 6e of the slider 6 is in sliding contact with the step portion 24c of the inner main body 20, and both end portions of the upper and lower surfaces of the slider 6 are in sliding contact with the sliding contact surfaces 24b, 25b, 29b, 30b of the inner main body 20. The guide projection 6e of the slider 6 is in sliding contact with the step 24c of the inner main body 20 and is guided in the front-rear direction, so that the slider 6 can move in the front-rear direction with a stable posture.
A lubricant is appropriately supplied between the slider 6 and the inner main body 20 and between the slider 6 and the cam 4 so as to facilitate the movement of the slider 6 with respect to the inner main body 20 and between the slider 6 and the cam 4. Improvement of the sliding property of the

[Friction mechanism]
The cross-sectional structure of the friction mechanism 8 is shown by FIG. The friction mechanism 8 of this embodiment comprises a first friction washer 36, a holding part 5d, a second friction washer 37, a spring washer 38, a flat washer 39 and a caulking part 40.

  The first friction washer 36 is an annular friction plate (friction member) that contacts the left side surface (one side surface) 3 h of the damper arm 3 and generates rotational friction resistance with the damper arm 3. The first friction washer 36 is disposed between the damper arm 3 and the holding portion 5d in a state of being ring-mounted on the right front end portion 5c of the shaft 5, and a portion thereof is locked in the locking recess 5e of the holding portion 5d. Thus, the shaft 5 is held non-rotatably.

  The holding portion 5d is a substantially annular flange portion formed in the vicinity of the right end portion 5c of the shaft portion 5b of the shaft 5 as described above. The holding portion 5 d holds the first friction washer 36 non-rotatably with respect to the shaft 5 in a state where the first friction washer 36 is in contact with the left side surface 3 h of the damper arm 3.

  The second friction washer 37 is an annular friction plate (friction member) provided on the right side surface (the other side surface) 3 i side of the damper arm 3, and the right end portion (one end portion) 5 c of the shaft 5 The shaft 5 is inserted into the shaft hole 3 e from the left side surface 3 h and then annularly mounted on the right front end 5 c of the shaft 5. A part of the second friction washer 37 is locked to the locking portion 3 g of the damper arm 3 and rotates together with the damper arm 3.

  The spring washer 38 is an annular spring plate (spring washer) provided on the right surface of the second friction washer 37 so as to press the damper arm 3 against the first friction washer 36. The spring washer 37 is annularly mounted on the right end 5 c of the shaft 5 together with the second friction washer 37 after the right end 5 c of the shaft 5 is inserted into the shaft hole 3 e of the damper arm 3. The spring washer 38 is pivotable relative to the second friction washer 37. A rotational frictional resistance may also occur between the second friction washer 37 and the spring washer 38.

  The flat washer 39 is an annular flat plate (presser washer) that presses the second friction washer 37 and the spring washer 38 toward the right side surface 3i of the damper arm 3. The flat washer 39 is annularly mounted on the right end portion 5 c of the shaft 5 so as to overlap the right surface of the spring washer 38. A caulking portion 40 is formed on the right end portion 5c of the shaft 5 so as to press the flat washer 39 toward the holding portion 5d.

  The caulking portion 40 is formed to plastically deform the cylindrical portion 5 f of the right end portion 5 c of the shaft 5 using a caulking tool. The flat washer 39 is pressed by the caulking portion 40 toward the holding portion 5d, whereby the first friction washer 36 disposed between the holding portion 5d and the flat washer 39 in a stacked manner, the damper arm 3, and the holding portion 5d. The second friction washer 37 and the spring washer 38 are pressurized from both left and right sides. Therefore, when the damper arm 3 rotates with respect to the damper case 2, a constant rotational frictional resistance is generated between the first friction washer 36 and the damper arm 3 and between the second friction washer 37 and the spring washer 38. The rotational friction resistance is transmitted to the cover 52 through the damper arm 3 and the link arm 54, whereby a constant braking torque is generated in the cover 52.

[Mounting board]
The mounting substrate 9 is a flat member made of metal. As shown in FIG. 4, the mounting substrate 9 is provided with a plurality of screw insertion holes 9 a corresponding to the screw insertion holes 11 e of the left side plate portion 11 of the outer main body 10. A plurality of screw insertion holes 9 b for fixing are provided. The screw insertion holes 9 b are provided in the vicinity of the peripheral edge of the mounting substrate 9. The mounting substrate 9 is fixed to the left surface of the left side plate portion 11 of the outer main body 10, that is, the left surface of the damper case 2 with a screw 43, as shown in FIG. 4 to FIG. Then, the mounting substrate 9 fixed to the damper case 2 is fixed to the large printing press 50 with the screws 45, so that the damper device 1 is a large printing press as shown in FIG. 14 (b) to FIG. 17 (b). Attached to 50.

[Damper device operation]
Next, the operation of the damper device 1 will be described with reference to FIGS. 14 (a) and (b) to 17 (a) and (b) and FIGS. 18 to 22.

In the following description, the opening angle of the cover 52 with respect to the horizontal plane is φ, and the angle of the damper device 1 (angle of the damper arm 3) is θ. When the cover 52 is completely closed, φ = 0 ° and θ = −23.8 ° (see FIG. 14 (b)). When the cover 52 is completely open, φ = 180 ° and θ = 110.4 ° (see FIG. 17B).
Further, FIG. 22 illustrates a torque curve I of the cover 52 and a torque curve II of the damper device 1. In addition, the torque curve I of the cover 52 is a torque curve which synthesize | combined the torque torque of the cover 52, and the rotational torque of the damper arm 3 resulting from the biasing member 7. FIG.

  When the cover 52 is completely closed as shown in FIGS. 14 (a) and 14 (b) (when φ = 0 ° and θ = −23.8 °), as shown in FIG. One cam receiving projection 6 c is in contact with the guide surface 4 f of the cam 4. When the cover 52 is opened from this state, φ increases and in conjunction therewith, θ also increases.

  In the range of 0 ° ≦ φ ≦ 40 ° (−23.8 ° ≦ θ ≦ 10 °), the first cam receiving projection 6c of the slider 6 is rotated with the clockwise rotation of the cam 4 in a right side view as viewed from the right. It moves forward while in sliding contact with the guide surface 4 f of the cam 4. As a result, the slider 6 moves toward the front end side of the damper case 2 and the biasing member 7 is compressed. At this time, the torque of the cover 52 is increased (see FIG. 22).

  FIGS. 15A and 15B show the states of the cover 52 and the damper device 1 when φ = 40 ° (θ = 10 °). At this time, as shown in FIG. 19, the slider 6 is moved to the front end side of the damper case 2 most and the biasing member 7 is most compressed, so the slider 6 is moved by the strongest repulsive force by the biasing member 7. Is in contact with the guide surface 4 f of the cam 4.

  In the range of 40 ° ≦ φ ≦ 120 ° (10 ° ≦ θ ≦ 82.3 °), the first cam receiving projection 6c of the slider 6 is a cam along with the rotation of the cam 4 in the clockwise direction as viewed from the right side. It moves rearward while sliding on the guide surface 4f. As a result, the slider 6 moves toward the rear end side of the damper case 2 and the compression of the biasing member 7 is released. At this time, the torque of the cover 52 decreases (see FIG. 22).

  FIGS. 16A and 16B show the states of the cover 52 and the damper device 1 at the neutral angle, that is, φ = 120 ° (θ = 82.3 °). At this time, as shown in FIG. 20, the first cam receiving projection 6 c of the slider 6 abuts on the first holding surface 4 g of the cam 4 and the second cam receiving projection 6 d of the slider 6 is the second holding surface 4 h of the cam 4. And the force caused by the biasing member 7 does not act in the rotational direction of the cam 4. Then, the torque of the cover 52 is substantially minimized (see FIG. 22). Therefore, while the state of FIGS. 15 (a) and 15 (b) is changed to the state of FIGS. 16 (a) and 16 (b), the cover 52 can be rotated with a relatively small force. Then, in the state of FIGS. 16A and 16B, since the center of gravity of the cover 52 is positioned immediately above the hinge 53, the cover 52 is stably maintained in this state.

  In the range of 120 ° ≦ φ ≦ 180 ° (82.3 ° ≦ θ ≦ 110.4 °), the first cam receiving projection 6 c of the slider 6 is accompanied by the clockwise rotation of the cam 4 in the right side view of the cam 4. The second holding surface 4h is separated from the Then, after the second cam receiving projection 6c of the slider 6 is moved slightly forward while in sliding contact with the second holding surface 4h, the cover 52 is completely opened, and at the same time, the second cam receiving projection 6c is third holding It will be in the state contact | abutted to the surface 4i. In the process of the opening angle φ from 120 ° (neutral angle) to 180 ° (maximum opening angle), the torque of the cover 52 sharply increases (see FIG. 22).

  When the cover 52 is completely open as shown in FIGS. 17 (a) and 17 (b) (when φ = 180 °, θ = 110.4 °), as shown in FIG. The cam receiving projection 6 c is in contact with the guide surface 4 f of the cam 4. At this time, the cover 52 is kept stable by its own weight.

  As described above, when the cover 52 is rotated within the range of 0 ° ≦ φ ≦ 120 °, the torque of the cover 52 reaches a peak when φ = 40 °. That is, when the rotation angle θ of the damper device 1 is −23.8 ° ≦ θ <10 °, the rotation torque of the damper arm 3 caused by the biasing member 7 acts in the direction to close the cover 52, 10 ° ≦ When θ <82.3 °, the torque of the damper arm 3 caused by the spring washer 7 acts to open the cover 52. Thus, when the cover 52 is closed from the state shown in FIGS. 16 (a) and 16 (b) (the opening angle is the neutral angle), the cover 52 is prevented from rapidly rotating in the closing direction. From the state shown in 15 (a) and 15 (b), the cover 52 can be forcibly closed to prevent the cover 52 from jumping up.

  Further, in the process in which the rotation angle φ of the cover 52 becomes from 120 ° to 180 °, the torque of the cover 52 sharply increases. That is, when the rotation angle θ of the damper device 1 is 82.3 ° ≦ θ <110.4 °, the rotation torque of the damper arm 3 caused by the biasing member 7 acts in the direction of closing the cover 52. Accordingly, when the cover 52 is further opened from the state shown in FIGS. 16A and 16B (the opening angle is the neutral angle), the cover 52 is rapidly rotated to open the state shown in FIGS. The fully open state shown in b) can be prevented.

  As described above, in the damper device 1 of the present embodiment, the slider 6 is biased toward the cam 4 by the biasing member 7, and the cam receiving portion 6 h of the slider 6 presses the cam surface 4 c of the cam 4 Thus, when the center of gravity of the cover 52 is less than the neutral angle (.phi. = 120.degree.) Located immediately above the hinge 53, the cover 52 is urged against the main body 51 of the office equipment to open the neutral angle. At the open angle (120 ° <φ ≦ 180 °), the cover 52 is biased in the closing direction with respect to the main body 51 of the office machine. As a result, a damper function is realized that can control the rotational torque of the cover 52 from an opening angle of 0 ° to a neutral angle or more, for example, up to 180 °.

  On the other hand, since the rotational frictional resistance generated in the damper arm 3 by the friction mechanism 8 is constant at all rotation angles θ (−23.8 ° ≦ 110.4 °) of the damper device 1, the cover 52 has all rotations A constant braking torque is generated by the friction mechanism 8 in the movement range (0 ° ≦ φ ≦ 180 °). This braking torque prevents rapid rotation of the cover 52 and realizes a free stop function within a predetermined range of opening angles (40 ° ≦ φ ≦ 120 °). The braking torque works even when the opening angle φ of the cover 52 is at the neutral angle (120 °), so that the wobble of the cover 52 at the neutral angle can be prevented.

  And, according to the damper device 1 of the present embodiment, depending on the size (the amount of caulking) of the caulking portion 40 formed at the end of the shaft 5, between the first friction washer 36 and the damper arm 3 and the second friction washer Since the rotational friction resistance generated between 37 and the spring washer 38 can be adjusted, the braking torque generated in the cover 52 can be adjusted at the time of manufacturing or attachment of the damper device 1 or the like. Thereby, the operation feeling of the cover 52 can be made favorable.

  Further, according to the present embodiment, the damper case 2 is made of metal that accommodates the inner body 20 made of resin, which accommodates the slider 6 so as to be able to move smoothly, and the inner body 20, and is fixed to the body 51 of office equipment. The damper device 1 can be firmly attached to the main body 51 of the office machine while facilitating the movement of the slider 6 with respect to the damper case 2.

  Further, according to the present embodiment, since the sheet covering the upper side of the cam 4 is attached to the damper case 2, the finger may be pinched between the slider 6 and the cam 4 or the finger may be contaminated by the lubricant. Can be prevented. The sheet 35 is made of resin, and can be attached to the damper case 2 by a simple method of attaching one end 35 a thereof to the inner main body 20 made of resin.

[Others]

  Although said embodiment demonstrated the damper apparatus 1 with which the large sized commercial printer 50 for businesses is equipped, the damper apparatus of this invention is applicable also to the damper apparatus of another apparatus.

  In the above embodiment, although the damper device of the present invention is applied to a damper device of an apparatus having a cover neutral angle of 120 °, the neutral angle is an angle other than 120 °, for example, 90 °. Of course, it is applicable also to a certain apparatus.

  In the above embodiment, although the friction mechanism 8 is provided with the first friction washer 36 and the second friction washer 37, the cover 52 is fully opened only by the rotational frictional resistance generated between the first friction washer 36 and the damper arm 3. If sufficient braking torque can be generated over the same range, the second friction washer 37 can be omitted. In this case, the spring washer 38 is in pressure contact with the left side surface of the damper arm 3.

Further, in the above embodiment, although the cam 4, the slider 6 and the inner main body 20 are all made of POM, resin materials other than POM, for example, ABS resin, polyamide or the like may be used.
Further, the numerical values, the shapes of members, the arrangement, the materials, and the like described in the above embodiments are all examples, and can be appropriately changed.

  Since the present invention is configured as described above, from the open state to the cover attached to the main body of the office machine via the hinge so as to be openable and closable, and further opened from the closed state of 0 ° to the freestanding angle. A damper device capable of preventing a rapid fall into a closed state and a rapid fall back beyond a self-supporting angle, and is suitably used as an office equipment provided with this damper device.

Reference Signs List 1 damper device 2 damper case 3 damper arm 4 cam 5 shaft 6 slider 7 biasing member 8 friction mechanism 10 outer main body 20 inner main body 35 sheet 51 main body of office equipment 52 cover 53 hinge 54 link arm

Claims (5)

A damper device for controlling an opening operation of a cover openably and closably connected to a main body of an office machine via a hinge, wherein the damper device comprises:
A damper case fixed to the main body of the office equipment;
A shaft rotatably mounted between both side plates of the damper case;
A cam rotatably mounted on the shaft in the damper case;
A slider slidably provided in the damper case in contact with the cam;
An urging member provided in the damper case to press the slider toward the cam;
A damper arm fixed to the cam at one end thereof outside the damper case and made rotatable with the cam;
A friction mechanism provided between the damper arm and the shaft to control the rotation of the damper arm;
And a link arm rotatably coupled to the other end of the damper arm such that the other end is coupled to the cover.
A damper device characterized in that the opening and closing operation of the cover is biased in the opening direction from 0 ° to the neutral angle, and biased in the closing direction above the neutral angle.   The damper device according to claim 1, wherein a sheet that covers the upper side of the cam is attached to the damper case. The damper case is
A resin inner body accommodating the slider so as to be able to move smoothly;
The damper device according to any one of claims 1 to 2, characterized in that it comprises a metal outer body which accommodates the inner body and is fixed to the office equipment. A sheet that covers the upper side of the cam is attached to the damper case,
4. The sheet according to claim 3, wherein one end of the sheet is attached to and supported by the end of the inner body on the cam side, and the other end extends above the cam. Damper device.   An office machine comprising the damper device according to any one of claims 1 to 4.

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