JPH0427679Y2 - - Google Patents

Description

[Detailed description of the invention] [Field of industrial application] The present invention relates to a device for lifting and lowering the head of a rail-type flexible parallel ruler, rail-type coordinate analyzer, etc. It is characterized in that it can be reliably held at any position floating relative to a surface.

[Conventional technology]

Conventionally, this type of device has been developed by the applicant of the present invention as shown in Japanese Patent Publication No. 57-50200. In this conventional device, the rotational moment due to the head's own weight is received by an inclined surface provided on one rotating part of the quadrilateral link and a protrusion in contact with the inclined surface, and the pressure between the inclined surface and the protrusion is applied to the rotating part of the link. It acts as a frictional force, and this frictional force holds the head in any raised position.

[Problem that the invention attempts to solve]

According to this configuration, the pressure between the inclined surface and the protrusion for holding the head in the raised position is only the rotational moment of the head supporting member relative to the link due to the weight of the head, so that the head can be held in any raised position. Even if it is possible to hold it in position,
The holding force was insufficient, and the state of holding the head portion upward was unstable. In order to eliminate this unstable state, the above-mentioned patent publication proposes an embodiment in which the link is biased in the upward direction by a spring, but if the spring force biasing the link in the upward direction is strong, , the head part stands out from the drawing surface. In this case, the scale tends to move inadvertently during plotting, resulting in a defect that it becomes difficult to plot.

The present invention aims to eliminate the above defects.

[Means for solving problems]

In the present invention, the vertical cursor 8, which is movable along the vertical rail 6, and the head side link 30, to which the head section 14 is connected, are rotated around the respective ends of the upper link 20 and the lower link 32, with the respective ends of the upper link 20 and the lower link 32 being the center of an axis parallel to the vertical rail 6. A parallel movement holding means is provided between the links 20 and 32, and at least one rotating portion of the links 20 and 32 relative to the vertical cursor 8 and the head side link 30 is brought into contact with the abutting body 40. The inclined surface 38 is a pivot point of the link 32 whose rotating portion is the contact point between the inclined surface 38 and the contact body 40, and the inclined surface 38.
The head side link 30 is tilted with respect to a plane perpendicular to a line along the swing plane of the inclined surface forming link connecting the contact point with the contact body 40, and the head side link 30 is rotated by the weight of the head portion 14. The force is received by the abutting body 40 and the inclined surface 38, and the pressure received from the abutting body 40 of the inclined surface 38 is applied to the joint between the parallel movement holding means and the link and the link 2.
In a device in which a braking force is applied to the rotating parts of 0.0 and 32 against the downward movement of the head part 14, the head side link 30 is applied with the weight of the head part 14 in the same direction as the rotation direction. The springs 54, 54', 54'' provide elasticity.

[Effect]

In the above configuration, the rotational force of the head side link 30 due to the weight of the head section 14 acts as pressure between the contact body 40 and the inclined surface 38, and this pressure is applied to the joint between the parallel movement holding means and the link. It acts as a braking force on the rotating part of the link, and
The rotational force of the head side link 30 is applied to the springs 54 and 5.
4' and 54'', the braking force is further increased, and this braking force can stably hold the head at any floating position.

〔Example〕

The configuration of the present invention will be described in detail below based on embodiments shown in the accompanying drawings.

Reference numeral 2 designates a drawing board, and a horizontal rail 4 is fixed to the side thereof, and a vertical rail 6 is movably attached to the horizontal rail 4 in a right-angled relationship. Reference numeral 8 denotes a vertical cursor which is movably attached to the vertical rail 6 via rollers 10, to which an operating head 14 is moved toward and away from the drawing board 2 via a quadrilateral link mechanism 12. Installed to get you. Reference numerals 16 and 18 indicate scales, which are removably fixed to the scale mounting plate of the head section 14. Reference numeral 20 designates an upper link, to which four bearing members are fixed, and pivot shafts 22, 24, 26, and 28 are rotatably supported by each of the bearing members. The pivot shafts 22, 26 are fixed to the rising portion 8a of the vertical cursor 8, and the pivot shafts 24, 28 are fixed to the head side link 30 to which the head 14 is connected. A lower link 32 is rotatably supported by a shaft 34 on a protrusion 8b formed on the vertical cursor 8, and a guide curved surface 36 and an inclined surface 38 are formed on this lower link. A contact body 40 made of a shaft body is installed on a pair of hanging portions 30a provided on the link 30, and the contact body 40 is in contact with the inclined surface 38. The inclined surface 38
is the pivot point of the link 32 and the inclined surface 38
It is inclined at a predetermined angle with respect to a plane F perpendicular to a line L along the swinging plane of the link 32, which connects the point of contact with the contact body 40. The head side link 30 is
In order to prevent the link 32 from falling around the shaft 34 due to its own weight when the link 32 is rotated in the vertical direction as shown by the dotted line in the figure, the link 32 is
With the vertical cursor 8 as a fulcrum, the spring 42 biases the shaft 34 in the counterclockwise direction in FIG. 2, and this biasing force causes the guide curved surface 36 to
is the roller 4 supported by the upper link 20.
4 so as to lightly touch. 46 is a roller support member, on which the roller 44 is rotatably supported. One of the top walls of the roller support member 46 abuts a convex portion 48 protruding from the top wall of the link 20, and an adjustment screw 50 is screwed into the other top wall of the support member 46. The roller support member 46 is biased upward in FIG. 2 by a spring 52 supported by a member 20' integral with the link 20. The curvature of the guide curved surface 36 is the second
In the figure, when a circle tangent to the roller 44 is drawn centered on the midpoint of the line segment connecting the shaft 34 and the contact body 40, it is set to match the curvature of the circle,
Moreover, the guide surface 36 is located along the circle. In FIG. 2, the projected view of the line segment connecting the axes 22, 24 and the center of the contact body 40 on a plane perpendicular to the vertical rail 6 and the two planes of the drawing board forms a substantially parallelogram. There is. 54 is the member 20'
This is a tension spring suspended between the shaft body fixedly attached to the shaft body and the contact body 40, and due to its tensile elasticity, the head side link 30 uses the link 20 as a fulcrum, and as shown in FIG. The hour hand is biased in the direction of rotation about the shafts 24 and 28. The guide curved surface 36 formed on the link 32 and the rollers 44 in contact therewith constitute a parallel movement holding means for maintaining the parallelism of the links 20 and 32.

[Effect]

Next, the operation of this embodiment will be explained.

When the handle 14a of the head section 14 is used to manually pull up the abutting body 40 in the upward direction while keeping it in contact with the inclined surface 38, the links 20 and 32 are moved upwardly from the shaft 22, as shown in FIG. ,2
6 and 34 as centers, the roller 44 moves along the guide curved surface 36 relative to this, and the head side link 30 maintains parallel to the two planes of the drawing board. It rises in a state of When the handle 14a is released from the handle 14a at an arbitrary raised position, the rotational moment of the head side link 30 about the shafts 24, 28 due to the weight of the head portion 14 and the tensile elasticity of the spring 54 is applied to the abutting body 40. The lower link 32 and the upper link 20 are moved by the component force in the arrow direction x that is applied to the inclined surface 38 via
Pressure is applied in the direction in which the swinging ends approach each other, and the rollers 44, the guide curved surface 36, the inclined surface 38 and the contact body 4
0 is crimped to prevent the links 20 and 32 from swinging between the spindle of the roller 44 and the bearing that receives it, between the roller 44 and the guide curved surface 36, and between the inclined surface 38 and the contact body 40. A large frictional force is generated. Furthermore, the rotational moment of the head side link 30 is
0 to the right in FIG.
A straining friction force is generated between the bearing 6 and the bearing that receives it. Due to the combined frictional force of this frictional force and the above-mentioned frictional force, the head portion 14 is reliably and stably held in a position floating above the drawing board 2.
In addition, when cleaning the second side of the drawing board, etc., the head portion 14 is raised greatly and the head side link 30 is moved to the fourth position.
As shown by the dotted line in the figure, when the spring 54 swings to a substantially vertical stopper position, the direction of action of the spring 54 on the link 30 changes, and the link 30
In FIG. 4, the hour hand is biased in the counterclockwise direction of rotation about the center point. This makes it possible to maintain the head portion 14 in a stable upright state. If the handle 14a of the head section 14 is grasped by hand and a slight rotational force is applied to the head section 14 by hand about the shafts 24 and 26 in the counter-clockwise direction in FIG. 4, it will come into contact with the inclined surface 38. Since the crimped state with the contact body 40 is released, the head portion 14 can be lowered or raised with a light force, and the head portion 14 can be placed closely on the drawing board 2. The guide curved surface 36
As another embodiment of the parallel movement holding means consisting of a roller 44 and a roller 44, as shown in FIG.
2', the link 60 may be pivotally connected 56, 58. Further, as shown in FIG. 6, the tension spring 54 is connected to the rotational support shaft 34 of the link 32 and
It may be hung between 0 and 0. Furthermore, as shown in FIG. 7, if an arcuate elongated hole 62 is provided in the link 32 and the roller 44 on the link 20 side is inserted into the hole,
A spring 42 for preventing the link 32 from falling, shown in FIG.
becomes unnecessary. Since the spring 54 is used to generate a rotational moment in the head side link 30 with the link 20 as a fulcrum, as shown in FIG.
It can be attached between the pivot shaft 58 and the contact body 40 or other appropriate location. The inclined surface 38 and the contact body 4
0 is the rotational moment of the head side link 30,
Since the links 20, 32, 32' are for converting force into component forces in the approaching direction or the separating direction, they can have various shapes and structures. In FIG. 9, the link 32 is shown with an inclined surface in a direction opposite to the inclined surface 38 shown in FIG.
10 and 11 show an embodiment in which an inclined surface 38 is provided on the left end side of the link 32.
Although two tension springs 54 are shown in each of FIGS. 10 and 11, only one of them may be used. FIG. 12 shows another embodiment in which one of the repulsion springs 54' is rotatably supported on the upper link 20.
The other end of the repulsion spring 54' is pivotally supported on the head side link 30 by a pin-shaped abutting body 40, and the grounding body 40 is provided at the open end of the upper link 20 and is connected to the inclined surface 38. It is in ballistic contact with the As shown in FIG. 18, the repulsion spring 54' has a coil spring 66 compressed and disposed within a pair of slidable cylinders 62 and 64. In the above configuration, the head side link 30 generates a rotational moment clockwise in the figure around the pivot 72 with the link 32 due to the weight of the head, and this rotational moment causes the head side link 30 to rotate clockwise in the figure. The abutting body 40 connected to the head 30 presses into the inclined surface 38 and pressure is generated between the abutting body 40 and the inclined surface 38, and this pressure acts as a braking force to prevent the head from falling. On the other hand, the repulsive force of the repulsive spring 54' is
Using the pivot point 70 as a fulcrum, a rotation moment acts on the head side link 30 to rotate the head side link 30 clockwise around the pivot point 72, and the spring force of the repulsion spring 54' causes the head side link 30 to come into contact. The pressure between body 40 and ramp 38 increases further. In the embodiment shown in FIG. 13, an inclined surface 38 is provided above the open end of the upper link 20, and a repulsion spring 54' and the head side link 30 are rotatably supported on this inclined surface 38. The contact body 40 is in elastic contact. Other configurations and operating principles are substantially the same as the embodiment shown in FIG. 12. In the embodiment shown in FIG. 14, the open end side of the upper link 20 is set to the rising part side of the vertical cursor 8, and an upwardly inclined surface 38 is formed on this open end side. One side of the upper link 20 is connected to the repulsion spring 5 by the pivot 74.
4' is pivotally supported on the head side link 30. The other end of the repulsion spring 54' is pivoted to the rising portion of the vertical cursor 8 by a pin-shaped abutment body 40, and the abutment body 40 is rotated against the inclined surface by the repulsion force of the repulsion spring 54'. It is in bullet contact with 38.

In the above configuration, due to the weight of the head part, the head side link 30 generates a rotational moment in the clockwise direction in the figure around the pivot point 70 with the link 32, and this rotational moment causes the head side link 30 to rotate clockwise in the figure. The link 20 is pulled to the right and the inclined surface 38
is in pressure contact with the contact body 40, and the inclined surface 38 and the contact body 4
0, and this pressure acts as a braking force to prevent the head from falling.On the other hand, the repulsive force of the repulsive spring 54' uses the abutment body 40 as a fulcrum.
A rotational moment acts on the head-side link 30 to rotate the head-side link 30 clockwise around the pivot 72, and this rotational moment pulls the upper link 20 to the right, causing the inclined surface 38 to Pressing against the contact body 40, the repulsion spring 54'
The spring force further increases the pressure between the abutting body 40 and the inclined surface 38, and this pressure acts as a force to prevent the head from descending. Figure 15 shows
A sloped surface 38 is provided downwardly at the open end of the upper link 20, and the other configuration and operation are the same as the embodiment shown in FIG. 14. FIG. 16 shows another embodiment, in which both ends of the repulsion spring 54' are connected to a pivot shaft 24 that pivots the upper link 20 and the head side link 30, and a shaft 34 that pivots the lower link 32 to the vertical cursor 8. It is rotatably connected to. A sloped surface 38 is formed at the left open end of the upper link 20, and the sloped surface 38 abuts a contact body 40 protruding from the rising portion of the vertical cursor 8. Reference numeral 60 denotes a link constituting a parallel holding means, and both ends are pivotally supported by the upper link 20 and the lower link 32.

In the above configuration, the weight of the head portion generates a clockwise rotational moment about the pivot shaft 72 in the head side link 30, and this rotational moment pushes the upper link 20 to the right, causing the upper link 20 to move toward the inclined surface. 38 comes into pressure contact with the abutting body 40, and the pressure between the abutting body 40 and the inclined surface 38 is further increased by the spring force of the repulsion spring 54', and this pressure prevents the head from descending. Acts as a force. 1st
In FIG. 7, the inclined surface 38 is provided upward on the open end side of the upper link 20, and other configurations are shown in FIG.
This is the same as shown in Figure 6. In FIG. 17, the upper link 20 is pulled to the right by the weight of the head, the inclined surface 38 comes into pressure contact with the contact body 40, and due to the repulsive force of the repulsive spring 54',
The upper link 20 is pushed to the right and the inclined surface 3
8 presses against the contact body 40. FIG. 19 shows another embodiment, in which one ring portion of the linear spring 54'' is rotatably fitted to the pivot shaft 24, and one end is locked to the upper link 20. The other end is in elastic contact with the contact body 40. The other configurations are the same as the embodiments shown in FIGS. 4 and 6, and parts corresponding to the embodiments are given the same numbers.

In the above configuration, a rotational moment about the pivot 24 is generated in the head side link 30 due to the pressing force of the linear spring 54'', whose fulcrum is the engagement portion with the upper link 20, against the contact body 40.
This rotation moment causes the contact body 40 to come into pressure contact with the inclined surface 38, and this contact force acts as a braking force to prevent the head from falling due to the weight. on the other hand,
The abutting body 40 is pressed against the inclined surface 38 due to the rotational moment in the clockwise direction in the drawing about the pivot axis 24 of the head side link due to the weight of the head portion. Due to the interaction of this pressure contact force and the pressure contact force due to the elasticity of the linear spring 54'', a force acts to prevent the head portion from falling, and the head portion is stably held at any floating position. Fig. 20 The link portion of the linear spring 54'' is rotatably fitted to the pivot shaft 24, and one end portion of the spring 54'' is locked to the pivot shaft 56 of the link 60 with respect to the upper link 20.
The other side of the linear spring 54'' is a pivot shaft 72 that rotatably connects the head side link 30 and the lower link 32.
It is in ballistic contact with the The other configurations are the same as the embodiment shown in FIG.

In the configuration described above, the pivot 72 of the spring 54''
, a clockwise rotational moment about the pivot shaft 24 is generated in the head side link 30 due to the pressing force using the link 60 as a fulcrum, and this rotational moment causes the lower link 32 to rotate in the left direction in the figure. Due to this pressing force, the inclined surface 38
comes into pressure contact with the contact body 40. Due to the weight of the head part, a clockwise rotational moment is generated in the head side link 30 about the pivot shaft 24, and this rotational moment also causes the inclined surface 38 to rotate against the contact body 40.
press against. In FIG. 21, a downwardly inclined surface 38 is provided on the open end side of the lower link 32,
The other configurations and operations are the same as the embodiment shown in FIG. 20. In FIG. 22, 54'' is a linear spring, the ring part of which is rotatably fitted to the pivot shaft 72, and one end part of which is connected to the link 60 and the lower link 3.
2, and the other end is locked to the pivot shaft 24.

The spring 54'' is biased in a direction in which both ends are opened.The other configurations are the same as the embodiment shown in FIG. 17, and parts corresponding to those in the embodiment are given the same reference numerals.

In the above configuration, due to the elastic force of the linear spring 54'', a rotation moment is generated in the head side link 30 in the clockwise direction about the pivot shaft 72, and this rotation moment causes the upper link 20 to be pulled to the right. , the inclined surface 38 comes into pressure contact with the abutting body 40. Also due to the weight of the head part, a rotational moment is generated in the head side link 30 about the pivot shaft 72, and this rotational moment causes the upper link 20 to rotate.
is pulled to the right, and the inclined surface 38 comes into pressure contact with the contact body 40. In FIG. 22, the inclined surface 38 is formed upward on the open end side of the upper link 20, but as shown in FIG. 23, it may be formed downward on the open end side of the upper link 20.

〔effect〕

As mentioned above, the present invention utilizes both the spring force and the weight of the head to generate a large pressure between the inclined surface provided on the link mechanism and the abutting body, and by this pressure, the parallel holding means Frictional force that holds the head at any floating position is generated in the joint between the head and the link and at the rotating part of the link, making it possible to stably hold the head at any floating position. This has the advantage that the head portion can be brought into close contact with the drawing surface.

[Brief explanation of drawings]

The figures show a preferred embodiment of the invention, FIG.
2 is a sectional side view, 3 is a sectional plan view, 4 is an explanatory diagram, 5 is an explanatory side view showing another embodiment, and 6 is another embodiment. FIG. 7 is a side explanatory diagram showing another embodiment. FIG. 8 is a side explanatory diagram showing another embodiment. FIG. 9 is a side explanatory diagram showing another embodiment. 10 is a side explanatory view showing another embodiment, and FIG. 11 is an explanatory side view showing another embodiment.
FIG. 12 is a side view showing another embodiment. FIG. 13 is a side view showing another embodiment. FIG. 14 is a side view showing another embodiment. 15 is a side explanatory view showing another embodiment; FIG. 16 is a side explanatory view showing another embodiment; FIG. 17 is a side explanatory diagram showing another embodiment; FIG. 18 is an explanatory diagram of a repulsion spring, FIG. 19 is a side explanatory diagram showing another embodiment, and FIG. 20 is an explanatory diagram of a repulsion spring.
FIG. 21 is a side explanatory view showing another embodiment. FIG. 22 is a side explanatory view showing another embodiment. FIG. 23 is a side explanatory diagram showing another embodiment. FIG. 2...Drawing board, 4...Horizontal rail, 6...Vertical rail, 8...Vertical cursor, 10...Colo, 12...
Link mechanism, 14... Head portion, 16, 18...
Scale, 20... Upper link, 22, 24, 2
6, 28... Pivot axis, 30... Head side link, 32... Lower link, 38... Inclined surface, 40
...Abutting body, 54...Spring.

Claims (1)

[Scope of utility model registration request] Both ends of the upper link 20 and the lower link 32 are attached to the head side link 30 to which the vertical cursor 8, which is movable along the vertical rail 6, and the head part 14 are connected, so as to be rotatable about an axis parallel to the vertical rail 6. , a parallel movement holding means is provided between the links 20 and 32, and at least one rotating portion of the links 20 and 32 relative to the vertical cursor 8 and the head side link 30 is connected to the abutting body 40 and the inclined surface 38 in contact therewith. The inclined surface 38
along the swinging plane of the slope-forming link that connects the pivot point of the link 32 whose rotating portion is the contact point between the slope 38 and the contact body 40, and the contact point between the slope 38 and the contact body 40. The rotating force due to the weight of the head portion 14 of the head side link 30 is received by the contact body 40 and the inclined surface 38, and the contact body 40 and the inclined surface 38 In the device, the pressure received from the contact body 40 is applied to the connecting portion between the parallel movement holding means and the link and the rotating portion of the links 20 and 32 as a braking force against the downward movement of the head portion 14, The head portion 14 is attached to the head side link 30.
springs 54, 5 in the same direction as the rotation direction due to the weight of
A device for lifting and lowering a head portion of a rail type flexible parallel ruler, etc., characterized in that it is provided with elasticity of 4', 54''.