JP2002192439A - Machining device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem on a conventional translation constant pressure device whose machining attitude is limited by the influence of gravity. SOLUTION: A sliding mechanism having opposed sliding tables 10, 11 for sliding in parallel is arranged on a frame 2 to be mounted on a machine device. A machining tool is provided on at least one sliding table 10 of the sliding mechanism and the other sliding table 11 is balanced in gravity with the sliding table 10. Furthermore, a translation mechanism 12 is provided on the sliding mechanism for moving one sliding table 11 with the other sliding table 10 to be moved in linkage in the opposite direction, whereby the opposed sliding tables 10, 11 are balanced in gravity to give gravity compensation to the sliding mechanism and keep gravity balance in various machining attitudes.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a processing apparatus for performing finishing such as chamfering or surface finishing of a minute portion of a jet engine part or the like.

[0002]

2. Description of the Related Art Conventionally, in mechanical parts and the like, chamfering or rounding (hereinafter simply referred to as "chamfering") at corners or the like for the purpose of relaxing stress concentration and improving the appearance of products. Processing).

As a constant pressure device for performing such a chamfering operation, there is a rotary constant pressure device. This rotary constant-pressure apparatus is capable of performing constant-pressure processing in which an air grinder, which is a processing tool, is rotated by a torque control motor and a cutting tool is pressed against a processing surface with a constant force. However, with this rotary constant-pressure device, if the processing surface height changes during processing, the contact position between the processing part and the cutting tool will shift, or the contact area will change due to the change in the attitude of the cutting tool, and the processing pressure will increase. May change to cause processing unevenness. In particular, when performing an edge chamfering operation, the cutting tool may come off from the processed surface.

[0004] For example, as prior arts of this kind, there are the inventions of Japanese Patent No. 2977772 and Japanese Patent No. 30007342. However, since these are rotary type constant pressure devices, they have the above-mentioned problems.

To solve such a problem, a translation type constant pressure device is promising. However, since the translation type constant pressure device is affected by gravity, the working posture is limited. For example, there is a conventional technique in which the sliding direction of a processing tool is set to be only the horizontal direction and the sliding direction is perpendicular to the direction of gravity. However, the processing posture is limited, and processing in various postures cannot be performed.

There is another polishing apparatus described in JP-A-10-146748. However, in this device, a load cell for measuring the pressing force is provided and feedback control is performed so that the pressing force is always constant. Therefore, the configuration for attitude control is complicated, and a lot of cost is required for manufacturing the device. I need it.

[0007]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a slide mechanism having a slide member provided opposite to a frame mounted on a mechanical device so as to slide in parallel. A working tool is provided on at least one slide member of the slide mechanism, and the other slide member is gravity-balanced with the slide member,
Further, the slide mechanism is provided with a translation mechanism in which the other slide member moves in the opposite direction in conjunction with the movement of one slide member, so that gravity is balanced even when the opposed slide member moves. ing. As described above, by providing a translation mechanism in which a slide member provided with a slide member that slides in parallel with gravity balance is provided so that the other slide member is driven in the opposite direction in conjunction with the slide of one slide member, Since the two slide members always move in opposite directions so as to balance the gravity, the weight of the slide members can be always offset to maintain the gravity balance in various working postures.

The slide member may be provided with a drive member for applying a translational drive force in the slide direction so that the working tool is pressed against the workpiece with a constant force. As the driving member, a motor or a spring capable of applying a predetermined translation driving force to the slide member is employed. If the working tool is pressed against the workpiece with a constant force as described above, chamfering or finishing of a minute portion can be stably performed at a constant pressure.

Further, the translation mechanism has a support shaft between the slide members so that the other slide member moves in the opposite direction via the support shaft in conjunction with moving one of the slide members. If the support shaft is provided with a drive member for applying a translational driving force to the slide member in the slide direction and the processing tool is pressed against the workpiece with a constant force, the support provided between the slide members is provided. Since the pressing force can be generated by the shaft, it is easy to attach a separate processing tool to both slide members to perform a plurality of operations.

Further, if the translation mechanism is constituted by a gear rotating about a support shaft provided between the slide members and a slide member having a rack meshing in parallel with the gear interposed therebetween, the support mechanism can be supported with a simple structure. The slide members provided with the shaft interposed therebetween can be synchronously moved in the opposite direction.

Further, if the gear rotating about the support shaft is constituted by combining gears of different diameters, and the gears of different diameters are meshed with the racks of the slide members, respectively, the moving amount changing mechanism is constituted. The amount of movement of the rack meshing with the small-diameter gear can be smaller than the amount of movement of the rack meshing with the large-diameter gear.

Further, if the driving member for applying the translation driving force is constituted by a motor, and the motor is provided on the slide member on the side of the non-machining tool and the motor is used as a weight balance member, the generation of the translation driving force (pressing force). Since the motor and the weight balance member that balances gravity can be used by the motor, the driving force generation source and the weight balance member can be configured with a small configuration.

Further, if a support member for receiving the driving force of the motor is provided on the frame side, and the translational driving force is obtained on the slide member by the reaction force of the driving force of the motor, the driving force of the motor can be reduced. Can act as

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. In the following description, a processing device attached to the tip of a robot arm will be described as an example. FIG. 1 is a front view of a processing apparatus showing a first embodiment of the present invention, FIG. 2 is a front view showing a force relationship in a vertical state of the processing apparatus, and FIG. 3 is a force relation in an inclined state of the processing apparatus. FIG.

As shown in FIG. 1, a support shaft 3 is provided at a substantially central position of a frame 2 attached to a distal end of a robot arm 1, and a support gear 4 is provided on the support shaft 3. Linear guides 5 and 6 are provided on the left and right sides of the support gear 4 so as to face each other. The linear guides 5, 6 are provided with slide tables 10, 11 as slide members in which racks 7, 8 meshing with the support gear 4 are fixed inward with bolts 9. Thus, the two slide tables 10 and 11 are arranged in parallel, and these slide tables 10 and 11 can slide in parallel in the vertical direction in the figure. These linear guides 5, 6 and slide tables 10, 11
A translation mechanism 12 is configured by these.

A substantially L-shaped rack support member 13 extending laterally is provided from the robot arm 1 side.
A rack 14 is attached to the rack support member 13 with bolts 14a toward the slide table 11 side.

The slide table 10 located on the left side of the figure is provided with a grinder mounting jig 16 for mounting a grinder 15 as a processing tool. In this embodiment, an air grinder 15 is mounted on a grinder mounting jig 16. In this example, the grinder 15 is provided with a chamfering blade 17. As the cutting tool 17, a grinding device such as a grinder, a polishing device, a brushing device, or the like is employed.

The slide table 11 located on the right side of the figure is provided with a servomotor 18 for applying a predetermined pressing force to the grinder 15. This servo motor 1
8 is a support member 19 provided on the slide table 11.
And the driving gear 20 of the servo motor 18 is
The rack 14 is provided so as to mesh with a rack 14 attached to the rack support member 13. The servo motor 18 is a weight balancing member for the grinder 15 and a driving member for moving the slide table 10 to the workpiece W in order to apply a predetermined translational driving force (pressing force) to the cutting tool 17. In this example, since the motor 18 is mounted as a weight balance member, the weight of the entire apparatus can be reduced.

As described above, the weights of the grinder mounting jig 16 and the servo motor 18 are adjusted so that the weights of the two slide members (including the portions supported by the slide tables 10 and 11) are the same. . In this state, the two slide tables 10 and 11 form a balance system using the support gear 4 sandwiched between the racks 7 and 8 as a support shaft, and are in a state of gravity balance and balance.

That is, in this state, the left and right slide tables 10 and 11 are in a state of gravity balance with the center of the support gear 4 as a fulcrum, and the two racks 7 and 8
Are linked to move in the opposite direction via the support gear 4,
Meshing portions (contact points) between the racks 7 and 8 and the support gear 4
Thus, the left and right slide tables 10 and 11 are in a state of gravity balance. In addition, you may comprise so that gravity balance may be carried out by another structure.

According to the processing apparatus M configured as described above, when the servo motor 18 is rotated clockwise in the drawing in this state, the driving gear 20 is moved to the fixed rack support member 1.
The servo motor 18 itself rises by kicking the rack 14 attached to the rack 3. Accordingly, the slide table 11 also moves up along the linear guide 6, and the rack 8 rotates the support gear 4 counterclockwise. The rack 7 descends due to the counterclockwise rotation of the support gear 4 and the slide table 1
0 will be lowered. As a result, the grinder 15
Can be pressed against the workpiece W with a predetermined pressing force.

That is, the force for raising the servomotor 18 obtained by the rotation of the servomotor 18 is the translation driving force of the blade 17 provided at the tip of the grinder 15 fixed to the slide table 10 as it is.

In this way, the work W
When the contact angle with the workpiece W is maintained and the relative distance between the robot arm 1 and the workpiece W is changed, the slide table 10 supporting the grinder 15 is , The workpiece W can be pressed with a predetermined pressing force while maintaining the contact angle between the cutting tool 17 and the workpiece W at all times.

At this time, the slide tables 10 and 11 move symmetrically, and the gravity balance is maintained around the support gear 4. That is, since the left and right gravity balances are maintained with the support gear 4 as the center, the opposed slide tables 10 and 11 that translate with the support gear 4 as the center always maintain the gravity balance.

Further, in this embodiment, the grinder 1
Since the servomotor 18 which is a driving device for pressing the workpiece 5 against the workpiece W is used as a weight balance member,
The separate left and right slide tables 10 and 11 can be gravity-balanced with a small configuration without separately providing a weight balance member.

The force relationship in this state is shown in FIG.
As shown in the drawing, a weight balance member is shown in place of the servo motor 18 and the reference numeral 18 is attached). The weights m1 and m2 formed by the grinder 15 and the servomotors 18 provided on the respective slide tables 10 and 11 have a relationship of m1 = m2.

Further, as shown in FIG. 3 (this figure also shows a weight balance member instead of the motor 18 and is denoted by reference numeral 18), when the processing apparatus is inclined, m1 '= m1cos
θ, m2 ′ = m2cosθ, and if m1 = m2, m1 ′ = m2 ′. In other words, regardless of posture,
The weight balance of the two slide tables 10, 11 and the grinder 15 and the servomotor 18 provided on the respective slide tables 10, 11 is always kept in a balanced state. Therefore, even if the posture of the processing apparatus M is changed from the state shown in FIG. 2 to the state shown in FIG. 3, the two slide tables 10 and 11 maintain a balanced state with each other. (Translational driving force).

As described above, since the processing apparatus M does not lose its balance due to the influence of gravity, finishing processing can be performed in any posture. In addition, since the balance state is maintained in all postures, the servo motor 1 serving as a force generation source
8 only needs to be able to generate a thrust corresponding to the pressing force at the time of machining, and it is possible to reduce the size of the driving member serving as the force generating source. In addition, since the torque of the force source (motor) becomes the pressing force, the calculation is easy, and the pressing force (pressure) of the grinder 15 (working tool) does not need to be feedback-controlled by the detector. Simplification can be achieved. Further, since the attitude of the processing tool can be changed arbitrarily, a device for changing the attitude of the workpiece W is not required, and the apparatus can be simplified.

FIG. 4 is a front view showing another example of the slide table that is linked in the translation mechanism. In the following example, the same components as those in the above-described embodiment are denoted by the same reference numerals, and description thereof will be omitted. Further, a case will be described in which a processing tool is attached to the slide table 10 shown on the left side of the figure and pressed downward. The reverse direction is also possible. In this example, a drum 22 having a pin 21 and a slide table 10 having an elongated hole 23 in which the pin 21 slides are linked to the slide tables 10 and 11.
11 constitute a translation mechanism 24. As shown in the figure, the slide tables 10 and 11 arranged side by side so as to slide along the linear guides 5 and 6 are provided with long holes 23 in a direction orthogonal to the sliding direction.
A support shaft 25 is provided on a frame (not shown), and the drum 22 is rotatably provided on the support shaft 25. The pins 21 provided on the drum 22
Are inserted into the elongated holes 23 of the slide tables 10 and 11. Thereby, the one slide table 11 can be linked so that it rises and the other slide table 10 falls.

FIGS. 5A and 5B are views showing another example of a slide table that is linked in the translation mechanism, wherein FIG. 5A is a perspective view and FIG. 5B is a plan view. In this example, the support gear 4 provided on the support shaft 3 has a movement amount changing mechanism 31. The moving amount changing mechanism 31 is configured such that the supporting gear 4 provided between the racks 7 and 8 is provided with a large-diameter gear 26 meshing with one rack 7 and a small-diameter gear 2 meshing with the other rack 8.
7 is a two-stage gear in which gears of different diameters are combined. In this example, a block 28 is shown as the weight of the slide table 10 (see FIG. 1) and the like on the rack 7, and the slide table 11 (see FIG.
Block 29 is shown as the weight of the block 29).

With such a configuration, the weights are balanced at the meshing portions between the racks 7 and 8 and the gears 26 and 27, so that the weights M28 and M2 of the blocks 28 and 29 are provided.
9 and a distance L26 from the center axis 30 of the support shaft 3 to the meshing portion of the large-diameter gear 26 and a distance L27 from the center shaft 30 to the meshing portion of the small-diameter gear 27, M28 × L2
6 = M29 × L27, the strokes S7, S8 of both racks 7, 8 and the distance L26 from the central shaft 30 of the support shaft 3 to the meshing portion of the large-diameter gear 26, and the small-diameter gear 27 from the central shaft 30. S7: S8 = L26: L27.

According to such a configuration, for example, when one rack 7 is raised, the stroke S8 of the other rack 8 becomes smaller than its stroke S7. That is, the moving amount S7 of the rack 8 meshing with the small-diameter gear 27 is compared with the moving amount S7 of the rack 7 meshing with the large-diameter gear 26.
8 can be reduced. Conversely, the movement amount S7 of the rack 7 can be made larger than the movement amount S8 of the rack 8.

The distance L26 from the center axis 30 of the support shaft 3 to the meshing portion of the large-diameter gear 26 corresponds to the center axis 3
Since the distance L27 from 0 to the meshing portion of the small diameter gear 27 is small, the weight of the block M28 can be reduced with respect to the block M29. In this case, the weight of the weight balance member with respect to the weight of the processing tool such as a grinder can be changed. That is, the moving amount changing mechanism 31 can provide a difference in the moving amount of the racks 7 and 8 or a difference in the weight of the slide tables 10 and 11. These may be set as appropriate according to use conditions and the like.

FIG. 6 is a front view showing another example of the slide table that is linked in the translation mechanism. In this example, the slide tables 10 and 1 are provided by a central support guide 32 rotatably supported by the frame 2 and a guide member 33 provided to be extendable and contractable in the support guide 32.
The translation mechanism 34 in which 1 is interlocked is constituted. Both ends of the guide member 33 are respectively connected to the slide table 1.
0 and 11 are supported by a shaft 33a. Thereby, if one slide table 11 is raised, the guide member 3
3 is interlocked so as to extend and lower the other slide table 10.

FIG. 7 is a front view showing another example of the slide table which is linked in the translation mechanism, and showing an example using a belt. In this example, pulleys 35 are provided above and below the slide tables 10 and 11 provided on the frame 2 in the sliding direction, and a belt 36 is provided between these pulleys 35.
The translation mechanism 37 is configured by fixing the reference numerals 0 and 11 with a fixing member 36a. Thereby, when one slide table 11 moves up, the other slide table 10 can be linked so as to move down by the belt 36.

FIGS. 8 (a) and 8 (b) show another example of an interlocking slide table in the translation mechanism. FIG. 8 (a) is a plan view showing an example using a ball screw, and FIG. 8 (b) is a front view thereof. It is. In this example, each slide table 10, 1
1 are provided with ball screws 38 and 39 in opposite directions,
A translation mechanism 41 is formed by providing a screw 40 that rotates along these ball screws 38 and 39 on the side, and providing a gear 42 at the end of the screw 40 and meshing with each other. Accordingly, if one of the screws 40 is rotated and the slide table 11 is raised by the ball screw 39, the other slide table 10 is linked to be lowered by the ball screw 38. At this time, the two screws 4
Synchronization of 0 is achieved.

The examples shown in FIGS. 4 to 8 are merely examples.
The translation mechanism may have another configuration.

FIG. 9 is a front view showing an example in which a linear motor is used for the translation driving force of the slide table. In this example, a linear motor is provided between the slide tables 10 and 11, a linear motor 43 is provided at the center, and a reaction plate 4 is provided inside the slide tables 10 and 11.
4 are provided. In addition, both slide tables 10, 11
Are synchronized by the gear 4 and the racks 7 and 8. Thus, if one slide table 11 is raised by the linear motor 43, the other slide table 1
It can be linked so that 0 falls. Therefore,
A processing tool attached to one slide table 10 (FIG. 1)
Can be pressed against the workpiece with a predetermined pressing force.

FIG. 10 is a front view showing an example in which a coil spring is used for the translation driving force of the slide table. In this example, a coil spring 45 is provided between the slide table 11 on the non-tool side and the frame 2 (fixed side), and the two slide tables 10 and 11 are synchronized by the gear 4 and the racks 7 and 8. . Thus, when the slide table 11 on the opposite side of the tool is raised by the coil spring 45, the slide table 10 on the tool side can be linked to be lowered. Accordingly, the processing tool (the grinder 15 in FIG. 1) attached to the slide table 10 on the tool side can be pressed against the workpiece with a predetermined pressing force.

FIG. 11 is a front view showing an example in which a spiral spring is used for the translation driving force of the slide table. In this example, the slide table 11 and the frame 2
A spiral spring 46 is provided between the slide table 10 (fixed side) and the slide tables 10 and 11 and the gear 4 and the racks 7 and 8 synchronize between the slide tables 10 and 11. Thus, when the slide table 11 on the opposite side of the tool is raised by the spiral spring 46, the slide table 10 on the side of the tool can be interlocked so as to be lowered. Therefore, the processing tool attached to the slide table 10 on the tool side (the grinder 15 in FIG. 1)
Can be pressed against the workpiece with a predetermined pressing force.

FIG. 12 is a front view showing an example in which an air cylinder is used for the translation driving force of the slide table. In this example, the air cylinder 4 is mounted on the frame 2 (fixed side) so that the slide table 11 on the opposite side of the tool is slid.
7 between the slide tables 10 and 11 and the gear 4
And the racks 7 and 8 synchronize with each other. Thus, when the slide table 11 on the opposite side of the tool is raised by the air cylinder 47, the slide table 10 on the side of the tool is raised.
Can be linked to descend. Therefore, the processing tool (FIG. 1) attached to the slide table 10 on the tool side
Can be pressed against the workpiece with a predetermined pressing force.

FIG. 13 is a front view showing an example in which an electromagnet is used for the translation driving force of the slide table. In this example,
An electromagnet 48 is provided on the frame 2 (fixed side) facing the upper surface of the slide table 11 on the opposite side of the tool, and the slide tables 10 and 11 are synchronized by the gear 4 and the racks 7 and 8. Thus, if the slide table 11 on the opposite side of the tool is raised by the electromagnet 48, the slide table 10 on the tool side can be linked to be lowered. Accordingly, the processing tool (the grinder 15 in FIG. 1) attached to the slide table 10 on the tool side can be pressed against the workpiece with a predetermined pressing force.

The examples shown in FIGS. 9 to 13 are merely examples, and other configurations may be used to obtain a translation driving force.

FIG. 14 is a front view showing an example of applying a translation driving force of the slide table to the support shaft. In this example, between the slide tables 10 and 11, the gear 4 and the rack 7,
8, a motor 49 is provided which applies a driving force to the support shaft 3 of the gear 4 in synchronization with the gear 4. Separate working tools are provided on both slide tables 10 and 11 to balance gravity. In this example, a grinder 50 is provided on the slide table 10 on the left side of the figure, and a drill 51 is provided on the slide table 11 on the right side of the figure. As described above, since a processing tool can be attached to each of the tables 10 and 11, different tools such as a chamfering blade on one side and a polishing tool such as a buff on the other side can be set at the same time. The combination of these tools is not limited, and it is sufficient that the two slide tables 10, 11 can be gravity-balanced.

According to this example, when the grinder 50 is pressed with a predetermined translational driving force (pressing force) by directly driving the support shaft 3 which is a balance point, the slide table 11 is moved by the gear 4. When the workpiece W is moved to the arrow 52 side, the workpiece W is stably pressed by the grinder 50 in a state where the drill side is raised and gravity is balanced, and the drill 5 is moved.
When pressing 1 with a predetermined translational driving force (pressing force), the gear 4
When the slide table 10 is moved to the arrow 53 side with
The workpiece W can be stably pressed by the drill 51 in a state where the grinder side is raised and gravity balance is achieved.

That is, in this example, when one working tool (the grinder 50 or the drill 51) is used while being lowered, the other working tool (the drill 51 or the grinder 5) is used.
0) is linked so as to ascend, so that the working tools (grinder 50 or drill 51) attached to both slide tables 10 and 11 are slid in parallel and always at the same contact angle with a predetermined pressing force. It can be pressed against the workpiece W. Further, it is possible to easily adopt a configuration in which a plurality of operations are continuously performed.

In all of the above-described embodiments, the pressing process is described as an example. However, in the present invention, it is easy to replace the cutting tool and replace the grinder with a rotary coating and cleaning apparatus even if the processing object is another object. Possible, for example,
In a finishing process such as chamfering and surface polishing, the present invention can be applied to a finishing apparatus in which a grinding / polishing tool such as a blade tool or a grindstone is pressed against a processing target object with a constant pressing force to make a processing amount constant. Also in this case, the angle of the cutting tool 17 with respect to the workpiece W can be maintained while maintaining the pressing force of the replaced processing tool. These combinations may be appropriately selected according to the operation.

Further, in the above-described embodiment, an example is described in which the processing apparatus is provided in an industrial robot which is a machining tool. However, as a processing tool such as an NC (numerical control) processing machine,
It can be used for various processing machines, and is not limited to the above embodiment.

The above-described embodiment is one embodiment, and various changes can be made without departing from the spirit of the present invention, and the present invention is not limited to the above-described embodiment.

[0050]

The present invention is embodied in the form described above, and has the following effects.

Since the balance of gravity is not lost under the influence of gravity, the workpiece can be pressed with a constant pressing force in any posture, and the range of application such as finishing by a processing device is expanded to greatly increase production. Costs can be reduced.

[Brief description of the drawings]

FIG. 1 is a front view of a processing apparatus showing a first embodiment of the present invention.

FIG. 2 is a front view showing a force relationship in a vertical state of the processing apparatus shown in FIG. 1;

FIG. 3 is a front view showing a force relationship in an inclined state of the processing apparatus shown in FIG. 1;

FIG. 4 is a front view showing another example of an interlocking slide table in the translation mechanism.

FIGS. 5A and 5B are diagrams showing another example of a slide table that is linked in the translation mechanism, wherein FIG. 5A is a perspective view and FIG. 5B is a plan view.

FIG. 6 is a front view showing another example of a slide table that is linked in the translation mechanism.

FIG. 7 is a front view showing another example of the interlocking slide table in the translation mechanism, and showing an example using a belt.

8 (a) and 8 (b) show another example of an interlocking slide table in the translation mechanism, FIG. 8 (a) is a plan view showing an example using a ball screw, and FIG. 8 (b) is a front view thereof. .

FIG. 9 is a front view showing an example in which a linear motor is used for the translation driving force of the slide table.

FIG. 10 is a front view showing an example in which a coil spring is used for a translation driving force of a slide table.

FIG. 11 is a front view showing an example in which a spiral spring is used for the translation driving force of the slide table.

FIG. 12 is a front view showing an example in which an air cylinder is used for a translation driving force of a slide table.

FIG. 13 is a front view showing an example in which an electromagnet is used for the translation driving force of the slide table.

FIG. 14 is a front view showing an example in which a translation driving force of a slide table is applied to a spindle.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Robot arm 2 ... Frame 3 ... Support shaft 4 ... Support gear 5, 6 ... Linear guide 7, 8 ... Rack 9 ... Bolt 10, 11 ... Slide table 12 ... Translation mechanism 13 ... Rack support member 14 ... Rack 15 ... Grinder DESCRIPTION OF SYMBOLS 16 ... Grinder mounting jig 17 ... Blade 18 ... Servo motor 19 ... Support member 20 ... Drive gear 21 ... Pin 22 ... Drum 23 ... Long hole 24 ... Translation mechanism 25 ... Support shaft 26 ... Large diameter gear 27 ... Small diameter gear 28, 29 Block 30 Central axis 31 Moving amount changing mechanism 32 Support guide 33 Guide member 34 Translation mechanism 35 Pulley 36 Belt 37 Translation mechanism 38, 39 Ball screw 40 Screw 41 Translation mechanism 42 Gear 43 ... linear motor 44 ... reaction plate 45 ... coil spring 46 ... spiral spring 47 ... air series Da 48 ... electromagnet 49 ... motor 50 ... grinder 51 ... drill 52 ... arrow W ... workpiece M ... processing device

Continuing from the front page (72) Inventor Akihiko Kameya 1-1, Kawasaki-cho, Akashi-shi, Hyogo Kawasaki Heavy Industries, Ltd. Inside the Akashi Factory Co., Ltd. (72) Inventor Takao Manabe 1-1, Kawasaki-cho, Akashi-shi, Hyogo Kawasaki Heavy Industries, Ltd. In-plant F-term (reference) 3C011 AA04 3C034 AA08 AA13 BB15 3C048 AA01 BB01 BC03 DD05 EE06 EE11 3F060 AA06 AA09 GB06 GB22 HA21 HA35

Claims (7)

[Claims] A slide mechanism having a slide member provided so as to slide in parallel to a machine device is disposed on a frame mounted on a mechanical device, and a processing tool is provided on at least one slide member of the slide mechanism, and the other is provided. The sliding member is provided with a translation mechanism in which the other sliding member is moved in the opposite direction in accordance with the movement of one of the sliding members. A processing device configured to balance gravity even if it moves. 2. The machining according to claim 1, wherein a driving member for applying a translational driving force in a sliding direction is provided on the slide member, and the machining tool is pressed against the workpiece with a constant force. apparatus. 3. A translation mechanism having a support shaft between slide members so that one slide member moves in the opposite direction via the support shaft in conjunction with moving one slide member. 2. The apparatus according to claim 1, wherein the supporting shaft is provided with a driving member for applying a translational driving force to the sliding member in the sliding direction, and the processing tool is pressed against the workpiece with a constant force. Processing equipment. 4. The translation mechanism is characterized in that the translation mechanism comprises a gear provided between the slide members and rotating about a support shaft, and a slide member having a rack meshing in parallel with the gear therebetween. The processing device according to claim 1. 5. A moving amount changing mechanism wherein gears rotating around a support shaft are formed by combining gears of different diameters, and gears of different diameters are meshed with racks of slide members, respectively. The processing apparatus according to claim 4, wherein 6. A motor according to claim 2, wherein the driving member for applying the translational driving force is constituted by a motor, and the motor is provided on a slide member on the side of the non-machining tool, and the motor is used as a weight balance member. The processing device according to claim 1. 7. The apparatus according to claim 6, wherein a supporting member for receiving the driving force of the motor is provided on the frame side, and a translation driving force is obtained on the slide member by a reaction force of the driving force of the motor. Processing equipment.