JPS585139B2 - Protective devices on machine tool guideways - Google Patents

Description

[Detailed description of the invention] The invention relates in particular to a protection device on the guideway of a machine tool.

A guide path of a machine tool is formed on a bed of a machine tool such as a grinder or a lathe so as to guide important parts such as a carriage and a table so as to be movable in the longitudinal direction thereof.

Grinding chips and cut pieces often fall into the guide path during work, and if they get caught in the drive part of the machine tool or enter the hydraulic piping route, the entire machine tool must be stopped and removed. Must.

Therefore, in order to prevent these grinding chips and the like from falling onto the guideway, various types of protective devices for shielding the guideway have been proposed.

The protection device according to the invention comprises a support disposed at the end of the guideway, at least one rotary shaft supported by the support and provided with a drive gear at one end, and at least one drum concentric with the rotary shaft. and a shielding cover connected at one end to the carriage and arranged to be wound around the drum at the other end.

Protective devices of this type are already known in the prior art.

It serves to protect the vertical guideway or horizontal guideway of the machine tool from external influences and external effects.

In principle, there are three types of protection devices.

The first is the canopy, which has the disadvantage of not being able to completely close the gap and taking up a lot of space.

The second option is a retractable cover, which also takes up a lot of space and is expensive to manufacture, and can only be used when the machine tool's frequency is low.

Finally, there are so-called curtain covers. In this case, a curtain-shaped shielding cover is wrapped around the drum.

The drum is then under tension from a torsion spring.

The disadvantages in this case are that the life of the curtain-like shielding cover is relatively short, and that the tension of the torsion spring changes constantly during the reciprocating movement of the carriage connected to the shielding cover, as well as the distance In other words, the length of one stroke is limited.

In the case of curtain covers, it has already been proposed in the prior art to arrange a plurality of springs laterally in front of a stationary rotating shaft, so that the springs can be replaced immediately if necessary (German Patent Specification DE- PSNO, 1,803,
449).

However, in this case too, the disadvantage is that the tension of the torsion spring changes unbearably when the carriage moves, and the length of one stroke is limited.

Therefore, the aforementioned drawbacks still remain.

The object of the invention is to provide a machine tool with a relatively high frequency of vibration, so that the life of the protective device can be increased, the length of one stroke can be increased, and the spring tension can be increased. The purpose is to improve the protection device so that it can be operated even when the vehicle is in use.

This object is achieved according to the invention by designing the drum carrier as a rotary shaft supported on the machine tool and by connecting the drive of the carriage to the rotary shaft.

This has the advantage that the torsion spring is forced to move in accordance with the magnitude of the tension.

The rotating shaft, which acts as a drum support, therefore rotates accordingly.

This increases the service life of the protection device, increases the stroke length, and increases the spring tension so that the machine tool can operate even at relatively high vibration frequencies.

Another feature of the invention is that the drive shaft is mechanically, hydraulically or electrically connected to the drive of the carriage, so that a large number of embodiments are possible.

In a further embodiment of the invention, one drum can be arranged on each side of the carriage, the drum having a support designed as a rotation axis.

In this case, the carriage drives both rotating shafts.

This completely covers the guideway of the machine tool.

The two axes of rotation are then rotated accordingly by the respective momentum of the carriage.

In a further embodiment of the invention, two toothed belts connected to the carriage can be meshed with belt gears fixed to each of the two rotation axes.

By doing so, the rotating shaft and the carriage can be connected in a simple manner.

As a further feature of the invention, the carriage can also be connected to, for example, a worm drive.

The output shaft of the device is connected to two bevel gears that drive the rotating shaft that constitutes the drum support.

As yet another embodiment of the present invention, it is also possible to connect each crank mechanism, which drives each of the two rotating shafts constituting the drum support, to the reciprocating table.

A further mechanical connection is possible in that the carriage and both rotating shafts are connected to each other by means of a cross-slide mechanism and two belts.

If a hydraulic coupling method is chosen, a further feature of the invention is that the rotary shaft can be coupled to a hydraulic motor that is connected to a hydraulic pump and a drive motor for driving the carriage.

In a further embodiment of a hydraulic drive, the carriage is driven by a hydraulic motor.

The hydraulic motor is connected to each of two variable hydraulic motors for the rotating shafts.

In addition, both hydraulic motors are connected to the drive motor by a switching valve and a variable pump.

If electric drive is chosen, in yet another embodiment of the invention, the carriage can be driven by an electric motor.

The electric motor is connected to the rotating shaft through a tachometer generator and comparator and one servo motor.

In yet another embodiment of the invention, the carriage drive can be comprised of a rack and pinion.

The pinion is connected by a belt to a pair of elliptical wheels that drive the rotating shaft.

A rotating shaft constituting the drum support can be coupled with a drive gear to effect rotation.

In this case, the diameter of the drive gear can be equal to, larger than, or smaller than the diameter of the covering drum.

If the diameters are equal, the tension in the torsion springs remains approximately equal throughout the entire travel of the carriage.

If the diameter of the drive gear is smaller than the diameter of the drum,
The tension decreases as the distance traveled by the carriage increases.

Conversely, if the diameter of the drive gear is larger than the diameter of the covering drum, the tension increases as the distance traveled by the carriage increases.

Next, the present invention will be described in more detail based on the embodiments shown in the drawings.

FIG. 1 shows a drum 1.

A curtain-like shielding cover 41 is wrapped around the drum 1.

This drum 1 is supported by a rotating shaft 40.

In other words, the rotating shaft 40 constitutes a drum support.

The rotating shaft 40 is supported by two supporting parts 42.

The support 42 is connected to a machine tool 43 (the details of which are not shown).

As an example, machine tool 43 can be a polishing machine.

Furthermore, bearings 46 and 47 are provided.

There is a torsion spring 23 between the drum 1 and the rotating shaft 40.

One end of the torsion spring 23 is fixed to the drum 1, and the other end is fixed to the rotating shaft 40.

As a result of this fixing, the drum 1 is under tension from a torsion spring 23.

This tension can be freely selected depending on the force at which the torsion spring 23 is attached, and is determined by the degree of rotation of the drive wheel 2 and the rotating shaft 40.

The rotating shaft 40 is coupled to the drive gear 2 in a torsionally resistant manner or through a fixed joint.

In the embodiment shown in FIG. 2, the carriage 4 is provided with two fixed plates 8. In the embodiment shown in FIG.

The two fixing plates 8 are each connected to a toothed belt 7 or 7'.

This toothed belt 7 or 7' each has a belt gear 6
Or meshed with 6'.

Through them the rotating shaft 40 or 40' and the drum are rotated by the movement of the carriage 4 with the torsion spring 23 under tension.

Determining the degree of tension or changing it can be done precisely by changing the diameter of the belt gear 6.

In the embodiment shown in FIG. 4, the carriage 4 is coupled to a worm drive.

The worm drive is rotated by an electric motor M.

The two output shafts 45 and 45' are connected to bevel gears 31 and 31', respectively.

The output shaft of this bevel gear 31 or 31' drives a rotating shaft 40 or 40'.

Both drums 1 or 1' receive the driving force through the carriage.

Depending on the configuration, the spring tension can then remain unchanged or it can be increased or decreased.

Yet another embodiment of the mechanical drive method is shown in FIG.

In this case, the carriage 4 is connected to two crank mechanisms 332 and 32'.

The output shaft of each crank mechanism is connected to one gear.

The gear is connected to drive gear 2 or 2 through one idle gear.
', thereby driving the rotating shaft 40 or 40'.

In the embodiment shown in FIG. 6, a cross-slide mechanism 33 is used.

It drives toothed belts 132 and 132' by one rotating shaft.

Both belts then drive a rotary shaft 40 or 40' by means of their respective output shafts.

FIG. 7 shows an embodiment of the invention with an electric drive.

In this case, an electric motor 12 is provided.

The electric motor 12 drives the carriage 4 through the drive device 13.

This electric motor 12 is electrically connected to a tachometer generator 20 and a comparator 25.

Furthermore, there are electrical connections to the servo motors 21 and 21'.

As a function of the movement of the carriage 4, the servomotor 21 or 21' drives the rotary shaft 40 or 40' accordingly.

As a result, the rotating shafts 40 and 40' are rotated according to the movement of the carriage 4.

Figure 8 shows the hydraulic drive method.

In this case, one drum 1 and one shielding cover 41 are used.
Only.

It is connected to the carriage 4.

In this embodiment, an electric motor 12 drives the carriage 4 via a drive 13.

This electric motor 12 is connected to the hydraulic pump 10.

Hydraulic pump 10 is connected to hydraulic motor 9.

This hydraulic motor 9 drives a rotating shaft 40 in accordance with the movement of the carriage 4.

In the embodiment shown in FIG. 9, the carriage 4 is driven by a hydraulic motor 19. In the embodiment shown in FIG.

Hydraulic motor 19 is variable hydraulic motor 14 and 14'
is connected to.

The variable hydraulic motors 14 and 14' serve to drive the rotating shafts 40 and 40', and are connected to the drive motor M through a switching valve 16 and a variable pump 18.

The mode of operation of this switching valve 16 is the same as in the embodiment shown in FIG.

According to FIG. 10, the carriage 4 can also be connected to a rank 26 meshing with a gearwheel 27.

Gear 27 operates in conjunction with a pair of oval wheels 38.

At that time, the power is extracted from this oval ring by the belt 132.
and 132'.

Belts 132 and 132' rotate shafts 40 and 40' through their associated shafts as appropriate for their functions.

FIG. 11 shows the relationship between the spring tension Vs and the moving distance Sw of the carriage.

The prior art mentioned at the beginning has the disadvantage that the spring tension changes very greatly, ie increases, as the travel distance Sw of the carriage increases, as is clear from the curve a.

In the present invention, if the drive gear 2 according to FIG. 1 is used to drive the rotary shaft 40, and the diameter of the drive gear 2 is equal to the diameter of the drum 1, then the curve b of FIG. An almost constant value results throughout the entire travel of the platform.

There is also the possibility that the diameter of the drive gear 2 is smaller than the diameter of the drum 1.

In that case, the moving distance S of the carriage as shown by curve c
As w increases, spring tension Vs decreases.

On the other hand, if the diameter of the drive gear 2 is larger than the diameter of the drum 1, an increase in the spring tension occurs as the travel distance Sw of the carriage increases, as shown by curve d.

If an elliptical ring 38 is used according to FIG. 10, curve e in FIG. 11 results, by way of example.

That is, the spring tension is not constant throughout the entire travel of the carriage.

All of the embodiments described above have in common that the torsion spring is caused to rotate in response to the movement of the carriage.

In this case, the rotation of the rotating shaft 40 can be effected mechanically, hydraulically or by compressed air.

The invention offers the advantage of a very long service life for the torsion spring, the possibility of increasing the stroke length and the possibility of operating even at relatively high vibration frequencies of the machine tool.

[BRIEF DESCRIPTION OF THE DRAWINGS] Fig. 1 is a front sectional view of a drum equipped with a curtain-like cover, Figs. 2 and 3 are a plan view and a side view showing a first embodiment of the protection device, and Fig. 6 to 6 are side views showing still another embodiment of the protection device of the present invention equipped with a mechanical drive device, FIG. 7 is an embodiment of the protection device of the present invention equipped with an electric drive device, 8 and 9 are further embodiments of the invention with a hydraulic drive; FIG. 10 is a side view of an embodiment of the invention with a mechanical drive;
FIG. 1 is a graph showing the magnitude of spring tension with respect to the moving distance of the carriage. 1.1'...Drum, 2,2'...Drive gear, 4...Mountain carriage, 6,6'...
Belt gear, 7, 7'...Toothed belt, 9.
... Hydraulic motor, 10 ... Hydraulic pump, 12 ... Electric motor, 13 ... Drive device, 14.14' ... Variable hydraulic motor , 16・
...Switching valve, 18...Variable pump, 19
・・・・・・Hydraulic motor. 20... Tachometer generator, 21, 21'.
... Servo motor, 23 ... Torsion spring, 25 ... Comparator -226 ...
・Rack, 27...Pinion, 32.32'・
... Crank mechanism, 33 ... Cross slide mechanism, 38 ... Oval ring, 40.40'.
... Rotating axis, 41, 41'... Shielding cover, 43... Machine tool, 132, 132'...
····belt.

Claims (1)

[Scope of Claims] 1. A support part disposed at the end of the guide path, at least one rotating shaft supported by the supporting part and having a drive gear at one end, and at least one rotating shaft concentric with the rotating shaft. one drum and
In a protection device on a guideway of a machine tool, which consists of a shielding cover connected to a carriage at one end and arranged so as to be wound around the drum at the other end, a torsion spring 23 is connected to the drum 1 and the rotating shaft. 40, one end of which is fixed to the drum 1 and the other end to the rotating shaft; b. connected to the rotating shaft 40 via a drive member so as to continuously drive the carriage 4; c. A protection device on a guideway of a machine tool, characterized in that the diameter of the belt gear 6 is larger than the drum diameter of the shielding cover 41. 2. In a protection device on the guideway of a machine tool in which the carriage is provided with shields on both sides thereof, the carriage 4 engages with belt gears 6, 6' fixed to each of the rotating shafts 40, 40'. A protection device on a guideway of a machine tool according to claim 1, characterized in that the device is connected to a toothed belt 7. 3. A protection device on a guideway of a machine tool according to claim 1 or 2, wherein the drive device for the rotating shaft is mechanical. 4. A protection device on a guideway of a machine tool according to claim 1 or 2, wherein the drive device for the rotating shaft is hydraulic. 5. A protection device on a guideway of a machine tool according to claim 1 or 2, wherein the drive device for the rotating shaft is of an electric type. 6 Two toothed belts 7゜7' connected to the carriage 4 drive belt gears 6, 6 fixed to each of the two rotating shafts.
A protective device on a guideway of a machine tool according to claim 2 or 3, characterized in that the device engages with the guideway of a machine tool. 7. Claim 2, characterized in that each crank mechanism 32, 32' that drives the two rotating shafts constituting the drum support body, one by one, is connected to the carriage 4. or a protective device on the guideway of a machine tool as described in paragraph 3. 8 The carriage 4 and both rotating shafts 40, 40' are connected to the cross slide mechanism 33 and the two belts 132°132
A protection device on a guideway of a machine tool according to claim 2 or 3, characterized in that the devices are connected to each other by . 9 Hydraulic pump 10 and drive device 1 that drives the carriage 4
Hydraulic motor 9 connected to electric motor 12 for 3 and
A protection device on a guideway of a machine tool according to claim 1 or 4, characterized in that a rotating shaft 40 is connected to the machine tool. 10 The drive device 13 for the carriage 4 is driven by a hydraulic motor 19, and the hydraulic motor 19 is connected to the rotating shaft 40.
, 40', respectively, and both variable hydraulic motors 14,
5. A protection device on a guideway of a machine tool according to claim 2, wherein 14' is connected to a drive motor M by a switching valve 16 and a variable pump 18. 11 Tachometer generator 20 and comparator 2
Claim 2 or 5, characterized in that the carriage 4 is driven by an electric motor 12 connected to the rotating shafts 40, 40' through servo motors 21 and 21'. Protective installation on guideways of machine tools as described in Section 2. 12 The drive device of the carriage 4 is the rank 26 and pinion 27
The pinion 27 is connected to the belt 132.13.
3. A protection device on a guideway of a machine tool according to claim 2 or 3, characterized in that the device is coupled to a pair of elliptical wheels 38 which drive rotating shafts 40, 40' by means of 2'.