KR100938872B1 - The axail type tool turret - Google Patents

Abstract

The present invention relates to a turret tool, and more particularly, when the driving force of the main motor (drive motor) is transmitted to the drive shaft via the motor shaft and shaft, the noise is reduced by using a timing belt instead of the bevel gear which is a conventional transmission method. It is an axle type turret tool that reduces the occurrence and facilitates assembly.

Description

The axail type tool turret}

1 is a configuration example of the present invention

2 and 3 are partially enlarged views of FIG. 1.

<Description of Symbols in Drawings>

1. Body 2. Disc 3. Nameplate

4. Rotary tool 5. Tool holder 5a. key

6. Cover 10. Indexing motor 10a. Motor pulley

11. Timing belt

12. Gear Shaft 12a. Spur Gears 12b. Gearshaft pulley

13. Eccentric Housing b 14. Bearing 15. Swivel Cubic Coupling

16. Fixed Cubic Coupling 17. Piston Cubic Coupling 18. Tightening Bolt

20. Main motor 20a. Motor shaft 21. Motor gear

22. Shaft 22a. Shaft Gears 23. Bearings

24. Eccentric Housing: 25. Pulley: 26. Pulley b

27. Timing belt 28. Drive shaft

31, 32, 33. Proximity switch a, b, c 34. Sensing member

35. Dog 36. Fastening bolt 37. Fastening flange

38.Euro 1 39.Euro 2 40.Actuator

41. Actuator rod 42. Adapter 43. Cutting flow path 1

44. Cutting flow path 2 45. Front flange

C: center line

The present invention relates to a turret tool platform, and more particularly, when a driving force of a main motor (drive motor) is transmitted to a drive shaft through a motor shaft and a shaft, a timing belt is replaced with a configuration method such as a spur gear, which is a conventional transmission method. It is an axle type (axial type) turret tool stand that reduces the occurrence of noise and facilitates assembly.

In general, machine tools such as lathes and machining centers are easy to process complex shapes, and the use of turret tools is increasing due to the convenience of tool replacement.

These turret tool benches are classified according to the number of motors to be formed. The two-motor type motor is formed with both a main motor generating power for driving a tool and a servo motor (indexing motor) generating power for rotating a disk for tool change. The turret tool stand, the main motor and the servo motor can be divided into one motor type turret tool that performs both tool drive and tool change as one motor.

Another classification method can be divided into radial type and axle type according to the mounting surface of the tool holder. Radial type refers to the structure in which the tool holder is mounted on the divided surface of the disk. The tool holder is mounted on the cross section.

As a two-motor type turret tool stand, as disclosed in the patent application No. 0635256 filed by the applicant, the power of the main motor is transmitted to the shaft by a coupling, and the power transmitted to the shaft is engaged. The bevel gear is transmitted to the drive shaft, and the power transmitted to the drive shaft is transmitted to the rotary tool via the tool drive shaft.

In this conventional power transmission method, friction noise is generated and undercut occurs due to the degree of processing of the bevel gear, or assembly error, resulting in wear of gears or power consumption.

In order to solve this problem, the applicant has disclosed a belt type turret tool stand in Patent Registration No. 0655919, but the turret tool stand is equipped with a gear box deformed for driving a belt, and a tool holder is mounted on a divided surface of a disk. Earl type turret tool stand.

Therefore, the present invention provides a turret tool that transmits power as a belt instead of a conventional bevel gear, which is driven in a drive shaft, not a gearbox, unlike a conventional gearbox, and a tool holder is mounted on the end face of the disk. It is an object of the present invention to provide an axle type turret tool stand.

In addition, by forming an eccentric amount housing in the turret tool, by adjusting the distance between the pulley formed on the shaft and the pulley formed on the drive shaft by the control of the eccentric amount housing to properly adjust the tension of the timing belt to smoothly transmit power. The purpose is.

The present invention relates to a turret tool platform, and more particularly, when a driving force of a main motor (drive motor) is transmitted to a drive shaft through a motor shaft and a shaft, a timing belt is replaced with a configuration method such as a spur gear, which is a conventional transmission method. It is an axle type (axial type) turret tool stand that reduces the occurrence of noise and facilitates assembly.

Hereinafter, preferred embodiments of the present invention by referring to the accompanying drawings in detail as follows.

Figure 1 is an exemplary configuration of the present invention, Figures 2 and 3 is an enlarged view of a portion of Figure 1 axle-type turret tool according to the present invention generates a sphere power for transmitting power to the rotary tool (4) The main motor 20, the shaft 22 which receives power as a gear engaged with the motor shaft 20a of the main motor 20, and the shaft 22 is formed in parallel to the predetermined distance apart from the timing belt ( 27 to rotate the drive shaft 28, which is powered by the drive shaft 28, the rotary tool 4, which receives the rotational force by the drive shaft 28, and the disk 2 on which the tool holder 5 is mounted. Indexing motor 10 for generating power to the harm, gear shaft 12 is formed parallel to the motor shaft of the indexing motor 10 at a predetermined distance and the power is transmitted by the timing belt 11, the gear shaft Rotated by engaging with the spur gear (12a) formed in (12) It consists of a turning cubic coupling 15 is coupled to the base disk 2 and the fastening bolt 18.

The main motor 20 and the shaft 22 may transmit power as a gear coupling as in the above-described embodiment, or may be formed to transmit power by using a timing belt instead of a gear.

In addition, the shaft 22 and the motor shaft 20a may be arranged on the same line to be coupled to each other by coupling to allow power transmission.

The eccentric amount housing a (24) is formed on the outside of the shaft 22 to surround the shaft 22, the eccentric amount housing (24) is eccentric with respect to the absolute center line (C) by a certain dimension, the eccentric amount The rotation of the housing a 24 allows the distance between the pulley a 25 formed on the shaft 22 and the pulley b 26 formed on the drive shaft 28 to be adjusted, resulting in the shaft 22 and the drive shaft 28. Since the tension of the timing belt 27 hanging in between can be adjusted, power transmission can be made in an optimal state.

At this time, the main motor 20 is in a loosely released state, that is, in a pre-tightened state, and then performs tension adjustment of the timing belt 27 by the eccentric amount housing a 24 and then adjusts the position of the motor 20 to the shaft gear 22a. ), And adjusts the bite ratio between the motor gear 21 to the optimum state.

That is, the tension of the timing belt 27 is adjusted by the distance between the shaft and the drive shaft by the rotation of the eccentric housing a (24), and the distance between the shaft gear (22a) and the motor gear (21) is controlled by the main motor ( 20) is adjusted as the fastening flange 37 is fastened.

In other words, the main motor 20 is coupled to the fastening flange 37 by a fastening bolt, and the fastening flange 37 is formed with a long hole (not shown), so that the main motor 20 is shown in FIG. 1. Since the distance between the shaft 22 and the main motor 20 can be adjusted by being moved to the left and right of the drawing as a reference, the shaft gear 22a and the motor gear 21 can be assembled in an optimal bite state. Do.

A pulley a 25 is formed at one side of the shaft 22, and a drive shaft 28 is formed in a direction parallel to the shaft 22 at a predetermined distance. A pulley b is formed at one side of the drive shaft 28. 26) is formed. The timing belt 27 is preferably formed between the pulley a 25 and the pulley b 26 so that accurate power transmission is achieved.

If the power transmission is performed as a general belt, not only the power transmission may not be performed due to the slip, but also the spindle of the tool holder 5 should maintain a constant direction through the origin check operation of the rotation for tool change. However, there is a fear that it is difficult to maintain this orientation.

The power transmitted to the drive shaft 28 is transmitted to the tool drive shaft (not shown) in the tool holder coupled with the key and eventually to the rotary tool 4.

Subsequently, when the tool change operation is briefly described, when the indexing motor 10 is driven, the gear shaft pulley 12b connected to the motor pulley 10a and the timing belt 11 rotates and the gear shaft 12 also rotates. . One side of the gear shaft 12 is formed with a spur gear (12a) to rotate the turning cubic coupling (15) engaged with the spur gear (12a) and the turning cubic coupling (15) and the fastening bolt (18) The disk 2, which is fixedly coupled by), is also rotated so that a tool change is performed.

At this time, the key (5a) of the tool holder (5) should be confirmed the rotation origin by the sensing unit (not shown) formed in the proximity switch a (31) and the shaft gear (22a) in the state of engagement with the drive shaft (28). . If a tool change occurs in a state where the operation of checking the rotation origin is not performed, a collision occurs between the key groove of the drive shaft 28 and the key 5a of the tool holder.

In addition, in order for the key 5a of the tool holder 5 to be accurately coupled to the key groove formed in the drive shaft 28, the key 5a formed in the tool holder 5 should not lose its orientation during rotation. The groove 45 (not shown) is formed so that the key 5a of the tool holder 5 is guided by the groove of the front flange 45 while the disk 2 rotates, and the tool is activated. It can be combined with the key groove of the drive shaft 28 exactly.
The front flange 45 is fixed to the body, the guide groove is formed on one side, the guide groove is a circular shape of the front flange 45, that is, the rotational trajectory of the key (5a) (when the disk is rotated) And the rotational trajectory of the keys rotated together. Therefore, the outer surface of the key 5a formed in the tool holder 5 by the guide groove is rotated in contact with the guide groove.
If the key 5a is arbitrarily rotated according to the position of the disc 2, the rotary tool can also be rotated arbitrarily, so that the initial machining position of the rotary tool 4 is not constant, and the amount of processing can be changed for each workpiece. This is to prevent the key (5a) is broken because it is not accurately coupled to the key groove of the shaft (28).
As a result, the key 5a formed on the tool holder 5 is rotated while the outer surface is contacted by the guide groove formed on the front flange 45 when the disk 2 rotates. It can be accurately coupled to the key groove of (28) and can always maintain the initial machining position of the rotary tool (4).

Operation of the turning cubic coupling 15, the fixed cubic coupling 16, and the piston cubic coupling 17 for the rotation of the disk 2 for tool change and the positioning of the disk 2 during machining by the tool. Is disclosed in Patent Registration No. 0535256, which is filed by the applicant, but the clamp operation and the unclamp operation are as follows.
The state in which the disc 2 is fixed to the body 1 is a clamp state, and the disc 2 must be fixed to the body 1 so as to sufficiently overcome the cutting load when the machining is performed by the rotary tool 4. Is carried out by the turning cubic coupling 15, the fixed cubic coupling 16 and the piston cubic coupling 17.
Firstly, the fixed cubic coupling 16 is fixed to the body as a bolt and the turning cubic coupling 15 is fixed to the disc 2 as a fastening bolt. At this time, the geared (threaded) is formed in the cross-section of the fixed cubic coupling 16 and the turning cubic coupling 15, and the fixed cubic coupling 16 and the turning cubic coupling 15 Gears which mesh with gears are formed in the piston curb coupling 17.
And the gear which meshes with the spur gear 12a of the gear shaft 12 is formed in the outer peripheral surface of the turning cubic coupling 15. As shown in FIG.
Accordingly, when the gears of the piston curb coupling 17 and the fixed curvature coupling 16 and the turning cubic coupling 15 are engaged with each other, the fixed curvature coupling 16 is fixed to the body 1 and thus fixed. Since the turning cubic coupling 15 cannot be rotated by the cubic coupling 16, the disk 2 is also clamped so as not to rotate.
This state is the state of FIG. 3 in which hydraulic pressure is applied to the flow path 1 (38), and the piston cubic coupling 17 moves toward the fixed cubic coupling 16 and the turning cubic coupling 15 so that the piston cubic coupling 17 ), The gears formed on the end faces of the fixed curb coupling 16 and the turning cubic coupling 15 is meshed with each other to prevent the turning cubic coupling 15 from rotating.
On the contrary, in the unclamped state, hydraulic pressure is applied to the passage 2 (39) so that the actuator (40) and the actuator rod (41) push the piston cubic coupling (17) upward in the drawing. 2 is a state in which gear engagement with the ring 16 and the turning cubic coupling 15 is released.
When the pivotal coupling 15 is moved upward by the actuator 40 and the gear engagement between the fixed Kirby coupling 16 and the pivotal coupling 15 is released, the pivotal coupling 15 Since the piston curb coupling 17 and the fixed curb coupling 16 are not interrupted by rotation, the turning curvature coupling 15 can be rotated by the gear shaft 12, that is, the disk 2. ) Will be rotated to the tool change state.
As a result, the turning cubic coupling 15 is in a state capable of rotating like the disk 2 when the gear is not engaged by the fixed cubic coupling 16 and the piston cubic coupling 17, and the gears engage with each other. Can not be rotated by the fixed cubic coupling (16).

However, the difference is that the conventional method of operating the piston cubic coupling is formed in each of the upper and lower portions of the piston cubic coupling, so that the hydraulic fluid flows in and out of the passage to operate the piston cubic coupling to clamp or unclamp the disk. Although the present invention, the present invention forms the flow path 1 (38) for the clamp only on the upper portion of the piston cubic coupling 17 and the unclamp operation is formed on one side of the piston cubic coupling 17 and the actuator rod This is done as (41).

That is, when the hydraulic pressure is applied to the flow path 1 (38), as in the prior art, the piston cubic coupling (17) descends to the lower portion of the drawing, and the piston cubic coupling (17) and the fixed cubic coupling (16) and the turning cubic couple When the disk 2 is clamped due to the fastening of the ring 15, and when hydraulic pressure is applied to the flow path 2 39, the actuator 40 and the actuator rod 41 coupled with the actuator are lifted up and the swing couple is coupled. By pushing the ring 15 upwards, the piston and coupling couplings 17, 16 and the pivotal coupling 15 are released so that the disk 2 can rotate for tool change. Can be unclamped.

This method can make the configuration more concise than the conventional method.

Reference numerals are proximity switches b, c (32, 33) and the sensing member 34 and the dog 35, proximity switches b (32) and c (33) to detect the position of the sensing member 34, The sensing member 34 is integrally coupled with the dog 35 and the dog 35 is moved by the piston cubic coupling 17 so that the position of the dog 35 is coupled to the disc 2. I can grasp the condition.

In the cutting process by the rotary tool 4, the cutting oil is constantly supplied. In order to supply the cutting oil, a cutting oil supply device including a cutting flow path must be formed in the body of the turret tool bench.
The cutting flow paths 43 and 44 and the flow paths 38 and 39 formed in the present invention should be formed separately. The cutting flow paths 38 and 39 are supplied with cutting oils that are commonly used, and the flow paths 38 and 39 are generally used. Working oil is supplied.
The cutting oil supplied from the cutting oil supply device and passed through the cutting flow path 43 in the adapter is supplied to the cutting flow path 44 formed in the name plate 3, and a nozzle (not shown) at the end of the cutting flow path 44. It is formed so that the cutting oil is ejected toward the rotary tool (4) through the nozzle.

In other words, the cutting oil supply device of the turret tool according to the present invention is formed of the cutting flow path 1 (43) formed in the adapter 42 and the cutting flow path 2 (44) formed in the name plate (3). That is, the cutting oil is supplied to the cutting flow path 1 (43) and the cutting oil is supplied to the cutting flow path 2 (44) which is in contact with the cutting flow path 1 (43), and the cutting flow path 2 (44) is toward the activated rotary tool. Since the coolant must be supplied, it must be bent and formed at least once in the nameplate 3 as shown.

In addition, the cutting flow path 1 (43) may be formed only because the position of the adapter 42 is fixed, but the cutting flow path 2 (44) is a tool that is fastened to the disk 2 because the cutting oil must be supplied to each tool It should be formed by the number of holders 5, the cutting flow path 2 (44) is preferably formed in the name plate (3) radially as the number of tool holders (5).

As described above, the present invention is an axle-type turret tool tool that is equipped with a tool holder in the cross section of the disk is formed so that the power transmission system from the shaft to the drive shaft to transmit power as a belt instead of a conventional bevel gear. It is a turret tool bench that can be assembled so that there is little noise and no undercut.

In addition, by forming an eccentric amount housing in the turret tool, by adjusting the eccentric amount housing to adjust the distance between the drive shaft and the shaft, that is, the distance between the pulley a and the pulley b turret that can achieve power transmission in an optimal state It is a tool stand.

Claims (6)

In turret tools used in machine tools, The turret tool stand is a main motor 20 generating a driving force for transmitting power to the rotary tool 4, and a shaft 22 receiving power as a gear engaged with the motor shaft 20a of the main motor 20. ), A drive shaft 28 formed in parallel with a predetermined distance away from the shaft 22 and receiving power by the timing belt 27, and a rotating tool 4 receiving rotational force by the drive shaft 28. ), An indexing motor 10 generating power to rotate the disk 2 on which the tool holder 5 is mounted, and a timing belt formed parallel to the motor shaft of the indexing motor 10 at a predetermined distance. Rotation that is engaged with the gear shaft 12 receives power by the 11 and the spur gear 12a formed on the gear shaft 12 and is coupled to the disk 2 and the fastening bolt 18. It is configured to include a cubic coupling (15), An eccentric amount housing a 24 having one or more bearings 23 embedded therein and eccentric with respect to an absolute center line C is formed outside the shaft 22, so that the eccentric amount housing a 24 is formed. The axle is characterized by being able to adjust the distance between the shaft gear 22a of the shaft 22 and the shaft gear 22a by rotation to transmit power and to adjust the distance between the motor gear 21 formed on the motor shaft 20a. Type turret tool bench delete The method of claim 1, Pulleys a and b (25 and 26) are formed at one side of the shaft 22 and the drive shaft 28, respectively. The pulleys a and b (25 and 26) are powered by a timing belt 27. Axle type turret tool stand The method of claim 1, The clamping and unclamping operation of the disk 2 is performed as a piston cubic coupling 17, The piston cubic coupling 17 forms a flow path 1 (38) for clamping in the upper portion and when the hydraulic pressure is applied to the flow path 1 (38), the disk 2 is clamped, the unclamping operation is the piston When hydraulic pressure is applied to the flow path 2 (39) as the actuator 40 and the actuator rod 41 formed on one side of the (17), the actuator 40 and the actuator rod 41 operates the piston cubic coupling 17 Axle-type turret tool stand characterized by the disc 2 being unclamped The method of claim 1, The cutting oil supply device of the turret tool bench is formed of the cutting flow path 1 (43) formed in the adapter 42 and the cutting flow path 2 (44) formed in the name plate (3), and the cutting flow path 2 (44) is the name plate (3). Axle-type turret tool bench, characterized by being bent at least once in The method of claim 1, The key 5a formed in the tool holder 5 is guided by a guide groove formed in the front flange 45 while the disk is rotated.

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