Damper hinge and office machine

Abstract

To provide a damper hinge which facilitates torque adjustment of a hinge having a damper.SOLUTION: A damper hinge comprises: an attachment member to be attached to a machine body side; a support member being rotatably attached to the attachment member via a first hinge shaft; a lift member which is rotatably attached to a free end side of the support member via a second hinge shaft, in order to attach a lid body; a pressure receiving member attached to a side of the attachment member; a second slide member which is provided in a slidable manner to the support member, and has a pressure cam part abutting on the pressure receiving member; a first slide member which is provided in a slidable manner, opposite the second slide member, and abuts on an operation member; an elastic member which is stored in a support part, and elastically provided between the first slide member and the second slide member; and an attachment member which is positioned between a piston of a damper in an insertion hole provided in the second slide member, and which is provided in a slidable manner. During opening and closing operation of the lid body, the attachment member is in pressure-contact with the pressure receiving member.SELECTED DRAWING: Figure 7

Description

[Technical field]

[0001] The present invention relates to a hinge with a damper that connects an office machine body, such as a copying machine, a multifunction machine, a scanner, a facsimile machine, a printer, etc., to a cover body such as an original cover, etc. in an openable and closable manner, and to an office machine using this hinge with a damper. [Background technology]

[0002] 2. Description of the Related Art Office equipment such as copiers has a contact glass for reading an original on the top surface of the main body of the equipment, and an original pressing plate (lid) covering the contact glass is provided on the main body of the equipment via a hinge so as to be able to be opened and closed.

[0003] As described in Patent Document 1, the above-mentioned hinge with a damper is configured to include an attachment member attached to the side of the device body, a support member rotatably attached to the attachment member via a first hinge shaft, a lift member attached to the free end side of the support member via a second hinge shaft so as to be rotatable in the opposite direction to the support member and to which a lid is attached, a pressure-receiving member attached to the attachment member side, a second slide member slidably attached to the support member and having a pressing cam portion that abuts against the pressure-receiving member, a first slide member also slidably attached to the support member opposite the second slide member and abuts against an operating member attached to the lift member, an elastic member housed in the support part and elastically installed between the first slide member and the second slide member, and a damper housed in the elastic member and provided between the first slide member and the second slide member, and a piston of the damper abuts against the inner bottom portion of the second slide member. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 7045685 Summary of the Invention [Problem to be solved by the invention]

[0005] In the above-mentioned conventional damper hinge for office equipment, as disclosed in Patent Document 1, in order to close the lid and ground it on the contact glass, it is necessary to switch the cam shape of the slider to reduce the torque, which reduces the amount of movement of the slider and results in a smaller damper effect, which in turn negates the damper effect. SUMMARY OF THE PRESENT EMBODIMENT An object of the present invention is to provide a hinge with a damper that can ensure the amount of movement of a slider without relying on the cam shape of the slider, and an office machine using this hinge with a damper. [Means for solving the problem]

[0006] In order to solve the above problem, the damper-equipped hinge described in claim 1 is a damper-equipped hinge for connecting a cover to a main body of an office machine in an openable and closable manner, comprising: a mounting member attached to the main body of the machine; a support member rotatably attached to the mounting member via a first hinge shaft; a lift member attached to a free end side of the support member via a second hinge shaft so as to be rotatable in the opposite direction to the support member, and for mounting the cover; a pressure-receiving member attached to the mounting member side; and a pressure-receiving member slidably provided on the support member and in contact with the pressure-receiving member. The pressure-receiving member has a second slide member having a pressure cam portion, a first slide member which is similarly slidably mounted on the support member opposite the second slide member and which abuts against an operating member attached to the lift member, an elastic member which is housed in the support portion and elastically mounted between the first slide member and the second slide member, and an attachment member which is slidably mounted within an insertion hole provided in the second slide member and positioned between the piston of the damper and the pressure-receiving member, and which is configured so that the attachment member is pressed against the pressure-receiving member when the lid body is opened or closed.

[0007] Next, the damper-equipped hinge according to claim 2 is characterized in that both side plates of the support member are attached rotatably to both side plates of the attachment member via a first hinge shaft.

[0008] Next, the damper-equipped hinge according to claim 3 is characterized in that the lift member has both side plates rotatably attached to the free end sides of the both side plates of the support member via a second hinge shaft.

[0009] Next, the damper-equipped hinge described in claim 4 is characterized in that the attachment member is provided integrally with a piston of the damper.

[0010] Next, the invention described in claim 5 is characterized in that the attachment member is configured such that its tip does not protrude from the pressure cam portion while it is not in contact with the piston of the damper, by an elastic member provided between the attachment member and the second slide member.

[0011] The office equipment described in claim 6 is characterized in that each of the damper-equipped hinges is used between the equipment body and the cover. Effect of the Invention

[0012] As the present invention is configured as described above, it is possible to provide a damper-equipped hinge that can adjust the hinge torque without changing the shape of the pressure cam portion of the second slide member, as well as an office machine using this damper-equipped hinge. [Brief description of the drawings]

[0013] [Figure 1] FIG. 1 is a perspective view showing a copying machine as an example of an office machine using a damper-equipped hinge; [Diagram 2] FIG. [Diagram 3] FIG. [Figure 4]11 is a perspective view illustrating the relationship between a second slide member and a pressure-receiving member of the damper hinge. FIG. [Diagram 5] 5A to 5C are cross-sectional views illustrating the states of a damper hinge during opening and closing operations, in which (a) shows the open state of the damper hinge, (b) shows the intermediate state of the damper hinge, and (c) shows the closed state of the damper hinge. [Figure 6] 1A and 1B are diagrams for explaining the torque relationship between the pressure-receiving member of the damper hinge, the pressure cam portion of the second slide member, and the damper, where (a) is a diagram for explaining the torque relationship between the pressure cam portion and the pressure-receiving member in the open state. (b) is a diagram for explaining the torque relationship between the attachment member of the damper and the pressure-receiving member in the open state. (c) is a diagram for explaining the torque relationship between the pressure cam portion of the second slide member and the pressure-receiving member in the intermediate state. (d) is a diagram for explaining the torque relationship between the attachment member and the pressure-receiving member in the intermediate state. (e) is a diagram for explaining the torque relationship between the pressure cam portion of the second slide member and the pressure-receiving member in the closed state. (f) is a diagram for explaining the torque relationship between the attachment member and the pressure-receiving member in the closed state. (g) is another diagram for explaining the torque relationship between the attachment member and the pressure-receiving member in the closed state. [Figure 7] (a) A diagram explaining problems caused by using a pressure-receiving member when transitioning from an open state to a closed state. A diagram explaining the relationship between the pressure-receiving member and the attachment member when transitioning from an open state to a closed state. (c) A diagram explaining the relationship between the pressure-receiving member and the attachment member provided with an inclined portion when transitioning from an open state to a closed state. (d) A diagram explaining the relationship between the pressure-receiving member and the protrusion amount of the attachment member when transitioning from an open state to a closed state. [Figure 8] (a) A diagram for explaining problems caused by using a pressure-receiving member when transitioning from a closed state to an open state, (b) A diagram for explaining the relationship between the pressure-receiving member and the attachment member when transitioning from a closed state to an open state, and (c) Another diagram for explaining the relationship between the pressure-receiving member and the attachment member when transitioning from a closed state to an open state. [Figure 9] FIG. 13 is a perspective view of an attachment member provided on the pressing cam portion; [Figure 10](a) A cross-sectional view of a damped hinge provided with an attachment in an open state, (b) a cross-sectional view of a damped hinge provided with an attachment in an intermediate state, and (c) a cross-sectional view of a damped hinge provided with an attachment in a closed state. [Figure 11] (a) is an enlarged cross-sectional view illustrating the relationship between the pressure-receiving member and the attachment; (b) is a cross-sectional view illustrating the spring bias of the attachment; [Figure 12] FIG. 1A is a cross-sectional view of a conventional damper arrangement in an intermediate state; FIG. 1B is a cross-sectional view of a damper arrangement of the present invention in an intermediate state; and FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0014] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a damper-equipped hinge according to the present invention will be described with reference to the accompanying drawings. EXAMPLES

[0015] Fig. 1 shows a copier A as an example of an office machine using the damper-equipped hinge according to the present invention. In Fig. 1, the copier A is composed of a machine body A1 and a cover body A2 (original pressing plate) that covers a contact glass A3 provided on the machine body A1. The cover body A2 is attached to the machine body A1 via a pair of hinges B so as to be able to open and close. Note that the pair of hinges B do not need to have the same structure, and one may be a hinge with a damper according to the present invention and the other a hinge without a damper.

[0016] 2 to 12 are diagrams specifically showing an example of a damper-equipped hinge B according to an embodiment of the present invention. As shown in the perspective view of FIG. 2, the damper-equipped hinge B of the present invention is composed of a mounting member B1 and a support member B2. The support member B2 has a first slide member 50, a second slide member 51, which are sliding members, and first and second springs 60, 61 (see Figure 3 for the first spring 60), which are compression coil springs that urge the first and second slide members 50, 51 in directions separating them from each other, arranged in parallel and concentrically. The mounting member B1 and the support member B2 are connected to each other by a first hinge shaft 31 so as to be rotatable relative to each other. A lift member 40 is rotatably attached to the support base 30 constituting the support member B2 by a second hinge shaft .

[0017] 3, the mounting base 10 constituting the mounting member B1 is composed of a bottom plate 10a to be mounted on the device body A1, both side plates 10b, and a rear plate 10c, which are made by bending metal plates such as stainless steel. The both side plates 10b are formed with curved recesses 10d.

[0018] The bottom plate 10a is formed in a substantially rectangular shape and is provided with mounting holes 10e for mounting to the device body A1 with screws or the like. A first hinge shaft hole 10f and a stopper portion 10i are provided at the tip (upper portion) of each side plate 10b. A large diameter pressure-receiving member hole 10g and a small diameter pressure-receiving member hole 10h are provided near the first hinge shaft hole 10f. A large diameter shaft end 11b and a small diameter shaft end 11a provided at both ends of the pressure-receiving member 11 are inserted into the large diameter pressure-receiving member hole 10g and the small diameter pressure-receiving member hole 10h, respectively.

[0019] The bottom plate 10a of the mounting base 10 in the mounting member B1 is attached to the device main body A1 via button screws 20 passing through mounting holes 10e.

[0020] The support base 30 of the support member B2 is composed of an upper plate 30a, both side plates 30b, and a holding piece 30c, which are made by bending a metal plate such as stainless steel. Both side plates 30b of the support base 30 are provided with a first hinge shaft hole 30f through which the first hinge shaft 31 is inserted, a second hinge shaft hole 30e through which the second hinge shaft 42 is inserted, and a notch portion 30d into which the operating member 44 described later is inserted. The first hinge shaft hole 30f of both side plates 30b and the first hinge shaft hole 10f of the mounting base 10 are aligned with each other, and the first hinge shaft 31 is inserted therethrough. As a result, the support base 30 is connected to the mounting base 10 so as to be rotatable about the first hinge shaft 31. The first hinge shaft 31 is inserted through the bearing member 13, and is prevented from coming off by an E-ring 15 engaged in a groove 31a provided at one end, a washer 14, and an ear 31c provided at the other end, together with the washer 14. Also, the bias spring 12 provided coaxially with the first hinge shaft 31 absorbs axial play of the first hinge shaft 31 that occurs between the mounting base 10 and the support base 30, but this bias spring 12 is not an essential component.

[0021] The lift member 40 is composed of an upper plate 40a and both side plates 40c, which are made by bending a metal plate such as stainless steel, and covers the support base 30. When attaching the lid body A2 to the lift member 40, the positions of the lid body A2 and the lift member 40 are adjusted by linking the lid body attachment adjustment hole 40g of the upper plate 40a with an eccentric pin (not shown) on the lid body A2 side. After the adjustment is completed, the lid body A2 and the lift member 40 are screwed together using the lid body attachment screw hole 40f provided in the upper plate 40a. The lift member 40 is provided with a second hinge shaft hole 40d and an operating member hole 40e. An operating member 44 is inserted through the operating member hole 40e. The second hinge shaft hole 40d and the second hinge shaft hole 30e in the support base 30 are aligned with each other, and the second hinge shaft 42 is inserted through these holes. As a result, the lift member 40 and the support base 30 are connected so as to rotate with each other. The actuating member 44 is biased by the first slide member 50 to control the rotation of the lift member 40 relative to the support base 30. The second hinge shaft 42 and the actuating member 44 are prevented from coming off by E-rings 43 and 45 engaged with grooves 42a and 44a provided at both ends. The upper plate 40a of the lift member 40 is provided with a horizontal adjustment unit 41 for adjusting the parallelism with the upper plate 30a of the support base 30. The horizontal adjustment unit 41 has an adjustment screw 41a and an adjustment screw lock 41b, and the adjustment screw 41a is screwed into an adjustment screw hole 40b on the upper plate 40a, and its tip abuts against the upper plate 30a of the support base 30. Therefore, the angle between the lift member 40 and the support base 30, with the second hinge shaft 42 as the axis, is adjusted by rotating the adjustment screw 41a. After the adjustment is completed, the adjustment screw lock 41b is tightened in a direction in which it abuts against the adjustment screw hole 40b to restrict the rotation of the adjustment screw 41a.

[0022] A first slide member 50 having a closed surface 50a and a second slide member 51 having a similar closed surface (not visible in FIG. 3) and an oil leakage prevention piece 51b are slidably housed within the support base 30. The first and second slide members 50, 51 can slide individually in the direction of arrow 51j between them and the support base 30 by being held by a holding piece 30c of the support base 30. First and second springs 60, 61, which are compression coil springs, are elastically mounted in spring accommodating portions 50b, 51f (the spring accommodating portion 50b is on the back surface of the first slide member 50 and cannot be seen in FIG. 3) provided on the first and second slide members 50, 51, respectively. 5(a) and the like, the first spring 60 is pre-charged and sandwiched between the first spring bearing 50c of the first slide member 50 and the first spring bearing 51p of the second slide member 51, and the second spring 61 is pre-charged and sandwiched between the second spring bearing 50d of the first slide member 50 and the second spring bearing 51q of the second slide member 51. As a result, the first and second slide members 50, 51 are biased in directions away from each other.

[0023] A viscous fluid circulating through an orifice is sealed in the cylinder 70a constituting the damper 70, and generates a resistance force corresponding to the speed. A piston 70b that transmits the damping action is provided at the tip of the cylinder 70a, and a flange 70c for mounting is provided at the rear end. The damper 70 is disposed in a space surrounded by the first and second springs 60 and 61, and as shown in FIG. 5, the end of the damper 70 is fixed to a damper receiver 50e provided in the spring accommodating portion 50b of the first slide member 50. The flange 70c is biased against the first slide member 50 by the first spring 60. The tip surface of the piston 70b and the piston surface 71b of the attachment member 71, which is a connecting member, are fixed by adhesive or other means. As shown in FIG. 5, the attachment member 71 has a role of extending the piston 70b, and is disposed so as to be insertable into the insertion hole 51a of the second slide member 51. If the piston 70b is sufficiently long, instead of the attachment member 71, the piston 70b may be extended and a connection member (attachment portion) may be provided integrally therewith.

[0024] FIG. 4 is a perspective view for explaining the relationship between the second slide member 51 and the pressure receiving member 11. The insertion hole 51a and the pressing cam portion 51c provided in the second slide member 51 will be explained using FIG. 4. A protrusion 51g is provided at the rear end of the second slide member 51, and a first inclined portion 51h and a second inclined portion 51i are formed, which are gradually inclined with the protrusion 51g as a boundary. The protrusion 51g and the first and second inclined portions 51h and 51i form the pressing cam portion 51c. An insertion hole 51a is provided at the center of the pressing cam portion 51c, and the pressing surface 71a of the attachment member 71 advances and retreats through the insertion hole 51a as the damper-equipped hinge B opens and closes. The pressure receiving member 11 abuts against the protrusion 51g, the first and second inclined portions 51h and 51i, and the pressing surface 71a according to the opening and closing angle of the mounting member B1 and the support member B2. The grease groove 51m is a grease reservoir provided for allowing the second slide member 51 and the support base 30, and the pressure cam portion 51c and the pressure-receiving member 11 to slide smoothly.

[0025] FIG. 5 is a cross-sectional view of the damper-equipped hinge B, and the damper 70 and the attachment member 71 are not shown in cross section. FIG. 5(a) shows the support member B2 at an angle of about 40 degrees (open state) with respect to the mounting member B1. In the open state, the first inclined portion 51h abuts against the pressure-receiving member 11, and the pressing surface 71a of the attachment member 71 does not abut against the pressure-receiving member 11. FIG. 5(b) shows the support member B2 at an angle of about 20 degrees (intermediate state) with respect to the mounting member B1. In the intermediate state, the protrusion 51g abuts against the pressure-receiving member 11, and the pressing surface 71a also begins to abut against the pressure-receiving member 11. FIG. 5(c) shows the support member B2 at an angle of about 0 degrees (closed state) with respect to the mounting member B1. In the closed state, the second inclined portion 51i abuts against the pressure-receiving member 11, and the pressing surface 71a also abuts against the pressure-receiving member 11.

[0026] Here, the action of the second slide member 51 on the opening and closing of the damper-equipped hinge B will be described. In the arrangement of the pressure cam portion 51c and the pressure-receiving member 11 in the open state in FIG. 6(a), the resistance torque T1 generated around the rotation center 31b of the first hinge shaft 31 is the product of the force F1 of the first and second springs 60, 61 (the arrows are in the opposite direction to the forces of the first and second springs 60, 61 to explain the resistance force) and the arm length L1. Here, the arm length L1 is related to the contact angle between the pressure-receiving member 11 and the first inclined portion 51h. In the arrangement of the pressure cam portion 51c and the pressure-receiving member 11 in the intermediate state in FIG. 6(c), the resistance torque T2 around the rotation center 31b is the product of the force F2 of the first and second springs 60, 61 and the arm length L2. Here, the arm length L2 is related to the contact angle between the pressure-receiving member 11 and the protrusion 51g. In the arrangement of the pressing cam portion 51c and the pressure-receiving member 11 in the closed state shown in Fig. 6(e), the resistance torque T3 around the rotation center 31b is the product of the force F3 of the first and second springs 60, 61 and the arm length L3. Here, the arm length L3 is related to the contact angle between the pressure-receiving member 11 and the second inclined portion 51i.

[0027] Now, if the main force generated by the first and second springs 60, 61 is the precharge force of the first and second springs 60, 61 between the first slide member 50 and the second slide member 51, it is considered that there is little change in F1, F2, and F3, and the magnitude of the resistance torque generated by the springs depends on the arm lengths L1, L2, and L3. That is, the resistance torque can be controlled by the first and second inclined portions 51h and 51i. In the present invention, the polarity of the inclination coefficient of the first inclined portion 51h and the second inclined portion 51i is made different, so that the arm length L3 in the closed state is sufficiently shorter than the arm length L1 in the open state. As a result, the resistance torque can be set large in the open state and intermediate state, and the lid body A2 does not enter the closed state due to its own weight. Also, when the intermediate state is changed to the closed state, the resistance torque becomes small, so that the lid body A2 enters the closed state due to its own weight. As a result, when the user performs an operation to close the lid body A2 from 40 degrees to 20 degrees, the lid body A2 then transitions to the closed state due to its own weight.

[0028] However, if the speed at which the lid A2 transitions to the closed state due to its own weight is fast, the impact of the lid A2 closing against the device body A1 generates an abnormal noise. In addition, this impact may cause a malfunction in the lid A2 or the device body A1. Therefore, the damper-equipped hinge B is provided with a damper 70 that generates a resistance torque proportional to the speed. However, if the damper 70 is applied even in the open state, the damper-equipped hinge becomes heavy to operate, so in the present invention, the damper 70 is set to apply between the intermediate state (20 degrees) and the closed state (0 degrees). In the arrangement of the pressing surface 71a and the pressure-receiving member 11 in the open state in FIG. 6(b), the pressing surface 71a and the pressure-receiving member 11 do not abut (see FIG. 5(a)). Therefore, the damper 70 does not act. In the arrangement of the pressing surface 71a and the pressure receiving member 11 in the intermediate state shown in FIG. 6(d), when the pressing surface 71a and the pressure receiving member 11 start to come into contact with each other (see FIG. 5(b)), the resistance torque T4 around the rotation center 31b is the product of the force F4 generated by the viscosity coefficient of the damper 70 and the opening / closing speed, and the arm length L4. Here, the arm length L4 is related to the contact angle between the pressure receiving member 11 and the pressing surface 71a. In the arrangement of the pressing surface 71a and the pressure receiving member 11 in the closed state shown in FIG. 6(f), the resistance torque T5 around the rotation center 31b due to the contact between the pressing surface 71a and the pressure receiving member 11 (see FIG. 5(c)) is the product of the force F5 generated by the viscosity coefficient of the damper 70 and the opening / closing speed, and the arm length L5. Here, the arm length L5 is related to the contact angle between the pressure receiving member 11 and the pressing surface 71a.

[0029] As described above, the change in arm length L3 in Fig. 6(e) is large (sufficiently short) compared to arm lengths L1 and L2 in Fig. 6(a) and (c). In contrast, since the pressing surface 71a does not have a cam inclination, the change in arm length L5 in Fig. 6(f) is small compared to arm length L4 in Fig. 6(d). Therefore, even when the state is close to being closed, the damper 70 can prevent the damper-equipped hinge B from attenuating the resistance torque, and the damper-equipped hinge B operates slowly until just before the state is closed. In addition, by providing an inclined portion 71d in the attachment member 71 as shown in Fig. 6(g), the arm can be lengthened (L6), and the damper 70 can further prevent the damper 70 from attenuating the resistance torque.

[0030] In the present invention, in order to achieve compactness, the pressure cam portion 51c and the pressure surface 71a are received by the same pressure receiving member 11, and the problems that arise as a result will be described with reference to Fig. 7(a). First, the transition of the damper hinge B from the open state to the closed state will be described. In Fig. 7(a), if the attachment member 71 protrudes beyond the pressure cam portion 51c, the pressure receiving member 11 sliding in the direction of the arrow 11c will collide with the attachment member 71, and the damper hinge B will not move any further. To avoid this, the present invention provides a control means for avoiding the collision.

[0031] The first control means is an adjustment so that the attachment member 71 does not protrude from the insertion hole 51a toward the pressure receiving member 11 side until the pressure receiving member 11 crosses the insertion hole 51a, and is the setting of the alignment of at least one of the pressing cam portion 51c, the pressure receiving member 11, the attachment member 71, and the piston 70b. FIG. 7(b) illustrates a state in which the pressure receiving member 11 starts to cross the insertion hole 51a, and in this state, by appropriately setting the length of the attachment member 71, the attachment member 71 does not protrude from the insertion hole 51a toward the pressure receiving member 11 side. Therefore, the pressure receiving member 11 does not collide with the attachment member 71. Instead of the length of the attachment member 71, the mounting position of the pressure receiving member 11 may be set so that the pressure receiving member 11 crosses the insertion hole 51a before the attachment member 71 protrudes from the insertion hole 51a. Alternatively, the cam inclination of the pressing cam portion 51c may be increased as it approaches the attachment member 71, so that the pressure-receiving cam 11 overcomes the attachment member 71. As shown in Fig. 7(c), even if the inclination of the pressing surface 71a' is steep and a part of the attachment member 71 protrudes from the insertion hole 51a (protrusion amount H1), it is sufficient as long as the attachment member 71 does not protrude from the insertion hole 51a at the insertion hole end face 51d on the side where the pressure-receiving member 11 begins to intersect with the insertion hole 51a. (In Fig. 7(c), the pressing surface end face 71c of the attachment member 71 is retracted from the insertion hole end face 51d by an amount H2.)

[0032] The second control means is setting the relationship between the length of the attachment member 71 protruding from the insertion hole 51a and the diameter of the pressure-receiving member 11. In Fig. 7(d), the attachment member 71 protrudes from the insertion hole 51a. However, the length H3 (protruding length) from the pressing surface end face 71c to the insertion hole end face 51d is set to be short compared to the radius H4 of the pressure-receiving member 11, so the pressure-receiving member 11 can climb over the attachment member 71.

[0033] Next, the transition of the damper-equipped hinge B from the closed state to the open state will be described. In Fig. 8(a), the attachment member 71 protrudes from the pressure cam portion 51c, so the pressure-receiving member 11 sliding in the direction of the arrow 11d collides with the attachment member 71, and the damper-equipped hinge B cannot move any further. To avoid this, in the present invention, the control means is the setting of the diameter of the pressure-receiving member 11 or the size of the pressure surface 71a so that at least a part of the pressure-receiving member 11 abuts against the pressure surface 71a of the attachment member 71 even in the closed state, as shown in Figs. 8(b) and (c). As a result, the attachment member 71 does not protrude from the pressure cam portion 51c even in the closed state, so that the pressure-receiving member 11 can slide smoothly.

[0034] In the embodiment up to Fig. 8, an attachment member 71 is attached as a connecting member of the damper 70, but a connecting member that replaces the attachment member 71 may be attached to the second slide member 51. In Fig. 9, an attachment member 72 is attached as a connecting member to the pressing cam portion 51c of the second slide member 51. The attachment member 72 is composed of a pressing surface 72a that contacts the pressure-receiving member 11, a piston surface 72b that contacts the piston 70b, a sliding surface 72c that slides in the direction of an arrow 72e against the pressing cam portion 51c, and a stopper 72d (sliding limiting portion) that prevents the attachment member 72 from falling out of the pressing cam portion 51c. By providing the stopper 72, a connecting member that is easy to work with can be realized that will not fall out simply by inserting it into the insertion hole 51a.

[0035] The attachment 72 is pushed by the piston 70b, so that it protrudes from the insertion hole 51a and the pressing surface 72a comes into contact with the pressure-receiving member 11. FIG. 10 is a cross-sectional view of the damper-equipped hinge B provided with the attachment 72, and the damper 70 and the attachment 72 are not shown in cross section. In the open state of FIG. 10(a), the pressing surface 72a of the attachment 72 comes into contact with the pressure-receiving member 11, but the piston 70b does not come into contact with the piston surface 72b (first state). Therefore, no damping action occurs. In the intermediate state of FIG. 10(b), the pressing surface 72a comes into contact with the pressure-receiving member 11, and the piston 70b also comes into contact with the piston surface 72b, so that the damping action begins to occur. In the closed state of FIG. 10(c), the damping action continues due to the contact of the pressing surface 72a with the pressure-receiving member 11 and the contact of the piston 70b with the piston surface 72b (second state). In this way, by not generating the damping action from the open state to the intermediate state, the operation of the lid A2 is prevented from becoming heavy, and from the intermediate state to the closed state, a sufficient damping action is generated regardless of the cam inclination of the pressing cam portion 51c (FIGS. 6(a), (c), (e)). This allows the lid A2 to slowly descend relative to the device body A1, realizing a high-quality hinge B with a damper.

[0036] The advantage of the attachment member 72 is that it is not necessary to adhere to the piston 70b as in the attachment member 71. Therefore, not only can the time-consuming adhesion process be omitted, but also a highly reliable connection member that does not cause problems such as peeling off of the adhesive can be realized. On the other hand, the problem with the attachment member 72 is that it can slide freely against the pressing cam portion 51c. Therefore, when the damper-equipped hinge B moves from the open state to the intermediate state, the attachment member 72 may protrude from the pressing cam portion 51c and collide with the pressure-receiving member 11. Figure 11(a) illustrates the structure of the attachment member 72 that solves the above problem, and the above-mentioned control means is to set the shape of the attachment member 72 to abut against the pressure-receiving member 11 over the entire range of the rotation angle of the mounting member B1 and the support member B2. Alternatively, the control means is to set the shape of the attachment member 72 to abut against the pressure-receiving member 11 when the attachment member 72 is not in contact with the damper 70.

[0037] In FIG. 11(a), the attachment member 72 is slidably inserted into the insertion hole 51a of the second slide member 51, and the movement of the attachment member 72 toward the damper 70 is restricted by the relationship between the ear portion 72f and the insertion hole countersink 51e. In addition, the illustrated dimension H6 of the ear portion 72f is set longer than the illustrated dimension H5 of the sliding surface 72c, so the pressing surface 72a provided on the ear portion 72f abuts against the pressure receiving member 11 in the entire range from the open state to the closed state of the damper-equipped hinge B. Therefore, the movement of the attachment member 72 toward the pressure receiving member 11 is also restricted. As a result, the attachment member 72 does not protrude from the pressing cam portion 51c and collide with the pressure receiving member 11. In this way, the collision problem occurs because the attachment member 72 slides freely independent of the damper 70, but a control means is provided to restrict the free sliding. The control means is to set the shape of the attachment member 72 so that the pressing surface 72a provided on the ear portion 72f abuts against the pressure-receiving member 11 even in a free state where it is not in contact with the damper 70 (piston 70b), as shown in Figure 11 (a).

[0038] FIG. 11(b) shows another example of a control means for preventing the attachment member 72 from sliding freely. In FIG. 11(b), a retraction spring 72g such as a compression coil spring is provided as a control means between the stopper 72d of the attachment member 72 and the retraction spring receiver 51n of the pressure cam portion 51c. The retraction spring 72g biases the stopper 72d in the direction of the arrow 72h, which is the direction of the damper 70, so that the ear 72f of the attachment member 72 does not protrude beyond the pressure cam portion 51c. Therefore, the pressure receiving member 11 can slide smoothly on the pressure cam portion 51c. When the retraction spring 72g is provided as in FIG. 11(b), it is not necessary to greatly expand the ear 72f of the attachment member 72, and the attachment member 72 can be made smaller and lighter.

[0039] FIG. 12 is a diagram for explaining the effect of the damping action in the damper-equipped hinge B of the present invention, where FIG. 12(a) is a cross-sectional view of the intermediate state in a conventional damper arrangement, and FIG. 12(b) is a cross-sectional view of the intermediate state in the damper arrangement of the present invention. In each cross-sectional view, the damper 70 and the attachment member 71 are not shown in cross section. FIG. 12(c) is a diagram for explaining the damping effect of the present invention, where the spring, damper, and friction (the pressing cam portion 51c and the pressure-receiving member 11, the pressing surface 71a and the pressure-receiving member 11, and the first hinge shaft 31) are used as parameters, and the calculated values ​​are obtained when a force is applied in the closing direction from the open state to the intermediate state. In the conventional example in FIG. 12(a), the first and second springs 60 and 61 abut against the first and second spring receivers 51p and 51q, and the damper 70 abuts against the bottom 51k of the second slide member 51. In contrast, in the present invention in Fig. 12(b), the first and second springs 60, 61 abut against the first and second spring receivers 51p, 51q, and the attachment member 71 of the damper 70 penetrates the insertion hole 51a and abuts against the pressure-receiving member 11. The horizontal axis 70d in Fig. 12(c) is the time axis, the vertical axis 70e is the opening and closing angle of the lid A2, and the curves are the angle change 70f of the support member B2 relative to the mounting member B1 of the present invention, the angle change 70g of the support member B2 relative to the mounting member B1 of the conventional example, and the angle change 70h of the support member B2 relative to the mounting member B1 in the case without the damper 70. The angle changes 70f, 70g, and 70h all have the same angle change curve from the angle θ1 in the open state to the angle θ2 in the intermediate state, but they each show different angle changes from the intermediate state θ2 to the closed state θ3.

[0040] In the angle change 70h without the damper 70, after the intermediate state θ2, the second inclined portion 51i in Figs. 6(c) and (e) comes into contact with the pressure-receiving member 11, so the resistance torque becomes smaller. Therefore, the closed state is reached in a short time (the closing angular velocity becomes faster). In the angle change 70g of the conventional example, after the intermediate state θ2, the damper 70 comes into contact with the bottom portion 51k of the second slide member 51. As a result, the closing angular velocity of the lid body A2 becomes almost constant. However, since the damper 70 is also controlled by the second inclined portion 51i, the closing angular velocity of the damper 70 does not decrease. In contrast, in the angle change 70f of the present invention, after the intermediate state θ2, the angular relationship between the pressing surface 71a and the pressure-receiving member 11 becomes as shown in Figs. 6(d) and (f), so the effect of the damper 70 is large and the lid body A2 closes slowly. In this way, the effect of the damper 70 can be increased in the present invention, and a high-quality damper-equipped hinge B can be realized.

[0041] As described above, the damper-equipped hinge B which connects the lid A2 to the device body A1 in an openable and closable manner includes an attachment member B1 attached to the device body A1 or the lid A2, a support member B2 attached to the lid A2 or the device body A1 and rotatable relative to the attachment member B1, a pressure-receiving member 11 provided on the attachment member B1, a slider (second slide member 51) slidably provided on the support member B2, a pressing cam portion 51c provided on the slider (second slide member 51) and in contact with the pressure-receiving member 11, springs (first and second springs 60, 61) which bias the pressing cam portion 51c in a direction opposite to the pressure-receiving member 11, and a spring (second slide member 52) which biases the pressing cam portion 51c in a direction opposite to the pressure-receiving member 11. The hinge B with a damper is composed of a damper 70 housed in the inner space of the support member B2 (51), a connecting member (attachment members 71, 72 or attachment member 71, piston 70b) that connects the damper 70 and the pressure-receiving member 11, and an insertion hole 51a provided in the pressure cam portion 51c through which the connecting member (attachment members 71, 72, piston 70b) protrudes. When the contact point between the pressure-receiving member 11 and the pressure cam portion 51c moves relatively due to the rotation of the support member B2 with respect to the mounting member B1, a control means is provided for controlling the connecting member (attachment members 71, 72, piston 70b) so as to enable the pressure-receiving member 11 to cross the insertion hole 51a, thereby making it possible to realize a compact and highly reliable damped hinge B.

[0042] The damper-equipped hinge B connects the cover A2 to the device body A1 in an openable and closable manner, and includes an attachment member B1 attached to the device body A1 or the cover A2, a support member B2 attached to the cover A2 or the device body A1 and rotatable relative to the attachment member B1, a pressure-receiving member 11 provided on the attachment member B1, a slider (second slide member 51) slidably provided on the support member B2, and a pressure-receiving member 12 provided on the slider (second slide member a pressure cam portion 51c provided on the slider (second slide member 51) and in contact with the pressure-receiving member 11, springs (first and second springs 60, 61) for biasing the pressure cam portion 51c in a direction facing the pressure-receiving member 11, a damper 70 housed in an inner space of the slider (second slide member 51), a connection member (attachment member 72) for connecting the damper 70 and the pressure-receiving member 11, and an insertion hole 51a provided in the pressure cam portion 51c and through which the connection member (attachment member 72) slides. It is composed of By providing a first state in which the damper 70 and the connecting member (attachment member 72) are separated by rotating the support member B2 relative to the mounting member B1, and a second state in which the damper 70 and the connecting member (attachment member 72) abut, a compact, highly reliable hinge B with a damper has been realized.

[0043] Although the damper-equipped hinge B shown in the above embodiment has the first slide member 50, the damper-equipped hinge B according to the present invention is not limited to this, and the first slide member 50 may be omitted. [Industrial Applicability]

[0044] Because the present invention is configured as described above, it is possible to realize a hinge with a damper that is small yet easy to adjust the torque, and it can be widely used in office equipment such as copiers, multi-function machines, and printers, home appliances, and Western-style toilet covers and fittings. [Explanation of symbols]

[0045] 10 Mounting base 11 Pressure-receiving member 30 Support Base 31 First hinge shaft 40 Lifting members 41 Horizontal adjustment section 42 Second hinge shaft 43 E-Ring 44 Actuating member 45 E-Ring 50 First slide member 51 Second slide member 51c Pressing cam part 60 First Spring 61 Second Spring 70 Damper 70b piston 71 Attachment material 72 Attachment material A Copying machine (office equipment) A1 Device body A2 Lid body A3 Contact Glass B. Hinge with damper B1 Mounting material B2 Support member

Claims

1. A damper-equipped hinge that connects a cover body to a main body of an office machine in an openable and closable manner, An attachment member attached to the device body; a support member rotatably attached to the mounting member via a first hinge shaft; a lift member that is attached to a free end side of the support member via a second hinge shaft so as to be rotatable in a direction opposite to the support member, and that attaches the lid; A pressure-receiving member attached to the side of the mounting member; a second slide member slidably provided on the support member and having a pressure cam portion that comes into contact with the pressure-receiving member; a first slide member that is slidably provided on the support member opposite the second slide member and that abuts against an operating member attached to the lift member; an elastic member accommodated in the support portion and elastically disposed between the first slide member and the second slide member; an attachment member that is slidably provided within an insertion hole provided in the second slide member and positioned between the piston of the damper and the pressure-receiving member, A hinge with a damper, characterized in that the attachment member is in pressure contact with the pressure-receiving member when the lid is opened or closed.

2. 2. The damper-equipped hinge according to claim 1, wherein both side plates of the support member are rotatably attached to both side plates of the mounting member via a first hinge shaft.

3. 2. The damper-equipped hinge according to claim 1, wherein both side plates of the lift member are rotatably attached to the free end sides of the both side plates of the support member via second hinge shafts.

4. 2. The damper-equipped hinge according to claim 1, wherein the attachment member is provided integrally with a piston of the damper.

5. 2. The damper-equipped hinge according to claim 1, wherein the attachment member is configured such that a tip end of the attachment member does not protrude from the pressure cam portion while the attachment member is not in contact with the piston of the damper by an elastic member provided between the attachment member and the second slide member.

6. An office machine, comprising: a hinge with a damper according to any one of claims 1 to 5, the hinge being disposed between the machine body and the lid.

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