Hydraulic control for a dividing machine tool

A hydraulic control for a dividing machine tool, in particular a shear or cutting press, in which a damping device is provided in order to counteract a sudden downward movement of the working piston upon the cutting through of a workpiece during an operating stroke.

FIELD AND BACKGROUND OF THE INVENTION 
The present invention relates to a hydraulic control for a dividing machine 
tool. 
Such hydraulic controls are used, in particular, in shearing presses or 
cutting presses by which workpieces are brought to predetermined lengths. 
Thus, for instance, scrap shears are known by which railway rails can be 
divided into pieces of short length before melting or recycling. 
In such machine tools one distinguishes essentially between three 
individual strokes, during the first of which strokes (the closing stroke) 
the cutting tool is closed. This is then followed by the working stroke, 
in which the work piece is cut in two, while a last stroke performs the 
return movement, i.e. the opening of the tool in order to be able to 
remove or shift the workpiece. 
In order to prevent an uncontrolled lowering of the cutting tool, a back 
pressure acts on the working piston of the machine tool during the closing 
stroke, it approximately compensating for the weight of the parts to be 
lowered. 
In this way, assurance is had that the workpiece of the machine tool does 
not descend solely due to its own weight, so that the hydraulic pump must 
always operate against the back pressure and thus the hydraulic cylinder 
is always filled with hydraulic fluid. 
During the working stroke, i.e. during the cutting of the workpiece, the 
back pressure is decreased so that the maximum cylinder force can be used 
for the actual cutting process. 
Upon cutting the workpiece, the entire hydraulic pressure continues to act 
on the working piston, so that the latter is accelerated immediately after 
the cutting until the hydraulic pressure decreases due to the control of 
the machine tool and the return movement of the tool is commenced. This 
sudden acceleration of the working piston can lead to a tearing apart of 
the oil column on the pressure side in the work cylinder so that there is 
a sudden, uncontrolled movement of the working piston. This sudden change 
in speed of the work piston is also known as the "cutting shock" and it 
can lead to damage to the drive and hydraulic components of the machine 
tool. 
SUMMARY OF THE INVENTION 
In contradistinction to this, the object of the invention is to create a 
hydraulic control for a dividing machine tool with which, with a little 
apparatus expense, uncontrolled movement of the working piston can be 
prevented. 
According to the invention the measure of providing a damping device, a 
damping pressure which opposes the downward movement of the working piston 
can be applied at the moment that the workpiece is cut through, so that 
the oil column on the pressure side in the work cylinder does not tear 
apart and thus sudden load peaks are counteracted. 
The damping device is advantageously provided with means for limiting the 
maximum pressure so that hydraulic fluid can be expanded into a hydraulic 
tank when a maximum system pressure is exceeded. 
A particularly simple control of this pressure-limiting valve device is 
obtained if, on the control side thereof, a predetermined control pressure 
is applied during the closing stroke which produces a back pressure which 
becomes inactive when an adjustable work level is reached and which can 
have a damping pressure superimposed on it or be replaced by a damping 
pressure which is greater than the control pressure. Thus, during the 
closing stroke, a back pressure acts which becomes inactive upon the work 
stroke when the work level is reached and then, upon the parting, 
increases to a higher damping-pressure level so that the cutting shock is 
reduced. 
In accordance with an advantageous further development of the invention, 
the expansion control pressure can be taken from the feed line to the work 
cylinder, while the control pressure during the closing stroke is 
advantageously obtained from the return line. 
The pressure in the feed line can then advantageously be fed by a bypass 
line into the control circuit of the pressure-limiting valve device. In 
this connection, a non-return valve and a flow valve, for instance a 
nozzle, can be arranged in series with one another in the bypass line. 
In a further development of the invention, the control pressure is branched 
off to the work cylinder from the return line via another flow valve, for 
instance a nozzle, and the bypass line is allowed to debouch downstream of 
the flow valve into the control circuit. 
Other advantageous embodiments of the invention are provided herein.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
The FIGURE shows a circuit diagram of a hydraulic control for a scrap shear 
in accordance with the invention. In this connection, a working piston 2 
guided in a work cylinder 4 is supplied with hydraulic fluid by means of a 
hydraulic pump 6, each of the two cylinder chambers 10, 12 being adapted 
to be connected with a line conducting the pump pressure P or with a line 
leading to the tank T via a directional valve or similar control means, in 
particular a proportional valve 8. 
For this purpose, in the embodiment shown the proportional valve 8 is 
developed as a pilot controlled 4/3-directional valve which can be 
controlled via electromagnets a,b and/or pilot control valves. In its 
basic position shown in the FIGURE, the valve slide is urged into its 
neutral position N by means of two springs. 
From the hydraulic pump 6 a line section 14 leads to a connection P of the 
proportional valve 8. This connection P is connected in the neutral 
position N to a connection T of the proportional valve 8, which, in its 
turn, is connected via a tank-relief line 16 to the tank T. 
From a branch 17 of the line section 14, a branch line 14a branches off in 
which there is connected a pilot controlled pressure-limiting valve the 
opening pressure of which is adjustable. The pressure prevailing in the 
branch line 14a is conducted via a control pressure line 20 to the control 
side of the pressure-limiting valve 18 so that, when a maximum pressure is 
exceeded, a connection to the tank T can be made via the pressure-limiting 
valve 18, and the pump conveys the hydraulic fluid into the tank T until 
the increase in pressure has been done away with. 
From the outlet side of the proportional valve 8, a work line 22 
(hereinafter referred to as return line 22) extends from a connection A to 
the lower cylinder chamber 12 in the FIGURE. Another work line 24 (in the 
following referred to as the feed line 24) leads from a connection B of 
the proportional valve 8 to the upper cylinder chamber 10 in the FIGURE of 
the working cylinder 4. 
The working piston 2 is developed as a differential piston, the weight of 
the working piston 2 and of the tool indicated by G in the FIGURE. 
In the neutral position N shown, the connections A and B are blocked 
while--as already mentioned--the connections T and P are connected to each 
other so that the hydraulic fluid is circulated into the tank T in the 
neutral position N (constant pump). 
In the lift position, designated H in the FIGURE, of the valve slide of the 
proportional valve 8, the connections A, P and B, T respectively are 
connected to each other, so that the hydraulic fluid is conveyed via the 
line section 14, the connections P, A, and the return line 22 to the 
piston-rod-side cylinder chamber 12, while the hydraulic fluid can flow 
out of the piston-side cylinder chamber 10 via the feed line 24, the 
connections B, T, and the tank-relief line 16 into the tank T. In this 
way, the working piston 2 moves upward in the FIGURE, so that the tool of 
the machine tool moves away from the workpiece W and the scrap shear is 
opened. 
In the "lower" position S of the valve slide, the two connections A and T 
are closed off, while the connections P and B are connected to each other 
so that hydraulic fluid is conveyed via the line section 19, the 
connections P, B, and the feed line 24 into the piston-side cylinder 
chamber 10 in order to lower the working piston 2 (closing stroke). In 
order to avoid controlled lowering, a back pressure is built up in the 
piston-rod-side cylinder chamber 12 which acts against the pump pressure 
in the feed line 24 and in the piston-side cylinder chamber 10. 
The back pressure is limited via a valve device 26, which will be described 
in further detail below, to a value which is about 10 to 20% higher than 
the load pressure produced by the weight G. 
When the preset back pressure is exceeded, a back pressure line 30 which 
branches off from the return line 22 downstream of the proportional valve 
8, is connected via a control chamber 31 of a precontrolled power part, or 
value element, 28 to a connecting line 32 which leads to the tank T so 
that the pressure in the piston-rod-side cylinder chamber 12 can be broken 
down to the tank T and the preset back pressure maintained. The 
controlling of the power part 28 is effected via the valve device 26, the 
construction of which is explained below. 
The valve device 26 which produces the control pressure for the control of 
the power part 28 has three connections X, Y and Z2, of which the 
connection X can be connected to the back pressure line 30 of the return 
line 22 and the piston-rod-side cylinder chamber 12, the connection Y can 
be connected to the tank T, and the connection Z2 can be connected to the 
feed line 24 and thus to the piston-side cylinder chamber 10. The control 
pressure for the power part 28 is present on another connection Z1. 
A control line 34 which extends away from the inlet connection X leads, via 
a damping choke 36, to the input P of a pressure-controlled switch valve 
38. The latter is prestressed via an adjustable spring into a position 
connecting the connection P with an output connection A (see FIGURE). On 
the other control side of the pressure-controlled switch valve 38, there 
is conducted a signal pressure line 40, so that, at a predetermined signal 
pressure, the valve slide of the pressure-controlled switch valve 38 can 
be displaced against the spring bias pressure and the connection A of the 
pressure-controlled switch valve 38 can be connected with a connection T 
from which a relief line 22 leads to the connection Y of the valve device 
26 and thus to the tank T. From the relief line 42, a signal pressure line 
40 leads back to the spring prestressed control side. 
From the output connection A of the pressure-controlled switch valve 38, a 
control-pressure line section 46 extends via a choke 46 to the connection 
Z1 of the valve device 26 and thus to the control side of the power part 
28. In the region between the choke 46 and the connection A, a branch line 
48 branches off, into which line there is switched a maximum-pressure 
limiting valve 50 by which the pressure in the branch line 48, and thus in 
the control-pressure line section 44 can be relieved via the connection Y 
into the tank T as soon as the preadjustable maximum value for the control 
pressure in the control circuit has been reached. 
Between the connection A and the branch line 48, another branch line 52 
branches off in which there is provided a back pressure limiting valve 54. 
This back pressure limiting valve 54 is also preadjustable, so that when a 
predetermined back pressure is exceeded, it is conducted via a control 
pressure line 56 branching off from the other branch line 52 to the 
control side of the back pressure limiting valve 54 and in this way the 
piston slide is brought into a position connecting the connections P and T 
of the back pressure limiting valve 54 to each other, so that the pressure 
in the control circuit can be relieved via a switch valve 58, described in 
further detail below, and the connection Y into the tank T of the 
hydraulic valve. 
As already mentioned above, the back pressure is so adjusted that it is 
about 10 to 20% above the load pressure produced by the weight G. 
Ordinarily, the back pressure thus lies in the range of 100 to 150 bar. 
The maximum pressure to be switched via the maximum-pressure limiting 
valve 50 is substantially higher than this back pressure, which is 
essentially presettable via the back pressure limiting valve 54. 
The above-mentioned switch valve 58 is developed as an electromagnetically 
actuatable 4/2-way directional valve, the control line section 60 leading 
from the connection T of the back pressure limiting valve being conducted 
to a connection A of the switch valve. The control side of the 
pressure-controlled switch valve 38 is connected via the signal pressure 
line 40 to a connection B of the switch valve 58. 
The pressure in the piston-side cylinder chamber 10 is conducted via a 
signal pressure line 62 to the connection Z2 of the valve device 26 and 
further to a connection P of the switch valve 58. From a tank connection T 
of the switch valve 58, a relief line 64 leads to the connection Y of the 
valve device 26. 
In its neutral position N, the valve slide of the switch valve is urged by 
spring bias pressure into a position in which the connections A and P are 
blocked while the connections B and T are connected to each other, so that 
the control pressure in the upper control side in the FIGURE of the 
pressure-controlled switch valve 38 is reduced via the single pressure 
line 40, the connections B and T of the switch valve 58, the relief line 
64 and via the connection Y of the valve device 26 into the tank T so that 
the valve slide of the pressure-controlled switch valve 38 is urged by 
spring action into the position thereof which connects the connections A 
and P of the pressure-controlled switch valve 38 together. 
In the position G of the valve slide, the connections P, B, on the one 
hand, and the connections A, T of the switch valve 58 on the other hand 
are connected with each other. In this case, the pressure in the 
piston-side cylinder chamber 10 is conducted over the signal pressure line 
62, the connections P, B of the switch valve 58, and the signal pressure 
line 40 to the control side of the pressure controlled switch valve 38, so 
that its control slide is brought against the spring bias pressure into 
the position thereof which connects the connections A and T with each 
other and in which the pressure in the control pressure line section 14, 
and thus the pressure on the control side of the power part 28, can be 
relieved to the tank T via the connections A, T of the pressure-controlled 
switch valve 38, the relief lines 42, 64 and the connection Y. In other 
words, in this switch position, the control pressure on the control side 
of the power part 28 is determined solely by a mechanical prestressing 
device, such as, for instance, a spring 66. 
From the signal pressure line 62, a bypass line 68 branches off, it 
debauching into the control pressure line 34 between the choke 36 and the 
pressure-controlled switch valve 38. 
A choke 70 and non-return valve 72 are connected in series in the bypass 
line 68. By means of the non-return valve 72, a fluid flow from the 
control pressure line 34 via the bypass line 68 to the signal pressure 
line 62 is prevented, while a flow in opposite direction upon the 
exceeding of a pressure predetermined by the spring bias tension of the 
non-return valve 72 is possible. In this way, the pressure in the 
piston-side cylinder chamber 10 can be fed via the bypass line 68 into the 
control circuit for controlling the power part 28. 
For a better understanding of the function, the switch processes during the 
closing stroke, the working stroke, and the return movement of the working 
piston 2 will be explained below. 
Lowering of the Working Piston 2 (Closing Stroke) 
For the lowering of the working piston 2, the magnet a of the proportional 
valve 8 is provided with current so that the valve slide of the 
proportional valve 8 is displaced from its neutral position N into the 
position S. In this position S, as already mentioned, the connections P 
and B of the proportional valve 8 are connected to each other, while the 
connections A and T are blocked. In this way, hydraulic fluid is pumped by 
the pump 6 into the piston-side cylinder chamber 10 so that the piston is 
lowered. The lowering is effected against a back pressure in the 
piston-rod-side cylinder chamber 12 which is established via the power 
part 28 and the valve device 26. 
In this connection, the control pressure corresponding to the pressure in 
the cylinder chamber 12 is conducted via the connection X of the valve 
device 26 to the connection P of the pressure-controlled switch valve 38. 
Upon the downward movement of the working piston 2, the magnet a of the 
switch valve 58 is also provided with current, so that the valve slide of 
this valve is in the position in which the connections P, B and A, T 
respectively are connected to each other and the pressure in the 
piston-side cylinder chamber 10 is present on the control side of the 
pressure-controlled switch valve 38, which pressure, however, is still not 
sufficient to bring the valve slide of the pressure-controlled switch 
valve 38 into its position connecting the connections A, T. As a result, 
the connections A, P of the pressure-controlled switch valve 38 are 
connected with each other so that the control pressure is conducted in the 
control pressure line 34, the connections A, P of the pressure-controlled 
switch valve 38, the control pressure line section 44 and the choke 46 on 
the control side of the power part 28. The back pressure upon the lowering 
of the working piston 2 is then determined by the back pressure limiting 
valve 54 the input connection P of which can be connected via the tank 
connection T and the control-line section 60, the connections A, T of the 
switch valve 58, and the connection Y to the tank T if the back pressure 
exceeds a preset value. 
Working Stroke (Cutting of the Workpiece) 
As soon as the tool of the scrap shear comes against the workpiece W, the 
pressure in the piston-side cylinder chamber 10 increases greatly, whereby 
the control pressure in the signal pressure lines 40, 62 also increases, 
so that the valve slide of the pressure-controlled switch valve 38 is 
brought out of its position shown in the FIGURE, against the bias tension 
of the spring, into its position connecting the connections A and T, and 
the control pressure in the control-pressure line section 36 can be 
relieved into the tank T via the relief lines 42, 64 and the connection Y. 
In this way, the spring bias pressure of the power part 28 is determined 
solely by the action of the spring 66 so that, as a result of the 
comparatively low spring initial tension over the power part 28, the 
pressure in the back pressure line 30 is relieved into the tank T, and the 
back pressure decreases to zero and the full cylinder pressure can be used 
for the cutting of the workpiece W. 
Cutting Shock 
Upon the cutting of the workpiece W, the full cylinder force acts on the 
working piston 2 so that a back pressure must be built up in order to 
prevent the above-described cutting shock. 
By the sudden elimination of the resistance applied by the workpiece, the 
pressure in the piston-side cylinder chamber 10 drops, as a result of 
which the control pressure on the control side of the pressure-controlled 
switch valve 38 also decreases and the latter is again moved into its 
basic position, shown in the FIGURE, in which the connections A and P are 
connected to each other via valve slide so that--as described above--the 
pressure prevailing in the piston-rod-side cylinder chamber 12 can be 
built up as control pressure or as back pressure on the control side of 
the power part 28. The building-up of this back pressure takes place, 
however, too slowly to assure effective damping of the cutting shock. In 
order to accelerate the build-up of pressure, the greater pressure in the 
piston-side cylinder chamber 10 is fed via the bypass line 68, the choke 
70 and the non-return valve 72, into the control-pressure line 34, which 
pressure is conducted via the connections P, A of the pressure-controlled 
switch valve 38 and the control pressure line section 44, the choke 46 to 
the connection Z1 and thus to the control side of the power part 28, so 
that a sufficient pressure builds up very rapidly on the control side of 
the power part 28 in order to block the connection between the back 
pressure line 30 and the connecting line 32 to the tank T. By the action 
of the comparatively high pressure in the piston-side cylinder chamber 10, 
the power part 28 can thus be brought very rapidly into its closed 
position so that a back pressure can build up very rapidly in the 
piston-rod-side cylinder chamber 12. 
By this measure, the cutting shock is effectively damped so that damage to 
and overloading of the parts of the scrap shear upon the cutting of 
workpieces is prevented. 
Return Movement of the Working Piston 2 
For the return movement of the working piston 2, the electromagnet b of the 
proportional valve 8 is provided with current so that its valve slide is 
brought into the H position in which the connections A, P and B, T 
respectively are connected to each other. Furthermore, the electromagnet a 
of the switch valve 58 becomes without current so that its valve slide is 
brought by the initial spring tension into the neutral position N shown in 
the FIGURE, in which the connections A and P are blocked, while the 
connections B and T are connected to each other. In this way, the control 
side of the pressure-controlled switch valve 38 is connected with the tank 
T so that its control slide remains in the position connecting the 
connections A, P, solely as a result of the spring initial tension. 
The section of the control line of the back pressure limiting valve 54 
which leads away from the tank connection T is blocked by the switch valve 
58 so that a higher pressure than the preset holding pressure can be 
adjusted in the control pressure line section 44 and thus on the control 
side of the power part 28. Since in this switch position, the pressure at 
the inlet of the power part 28 (line section 30) and at the control side 
of the power part 28 are the same, the power part 28 is held by the action 
of the spring 66 in its closed position in which the connection between 
the back pressure line 30 and the connecting line 32 is blocked off. 
Thus, hydraulic fluid can be pumped by the pump via the connections P, A 
and the return line 22 into the piston-rod-side cylinder chamber 12 so 
that the working piston 2 is moved back into its initial position shown in 
the FIGURE. The hydraulic fluid displaced from the piston-side cylinder 
chamber 10 is discharged via the feed line 24, the connections B, T of the 
proportional valve 8, and the tank relief line 16 into the tank T. 
Of course, the circuit shown can be expanded so that, in order to handle 
more complicated operating tasks, a control for the differential downward 
movement of the working piston can also be provided. 
The method of the invention, thus, for the first time, provides an 
effective cutting shock damping which can be produced in simple manner and 
without fundamental changes in the control block.