Hydraulic control system for at least two consumers

Each consumer is provided with a load-compensated direction-reversing valve. Each valve performs a throttling function and a pressure-compensation function in order to establish a selected volumetric flow rate, and also a direction-control function. Each valve comprises a first control valve stage and a second control valve stage. One stage performs the throttling function, the other the pressure-compensation function. One of the two control valve stages also performs the direction-control function. The pressure drop across the stage which performs the throttling function at least in part controls the setting of the stage which performs the pressure-compensation function. Each valve is provided with an electromechanical transducer generating electrical signals indicative of the settings of the stage which performs the pressure-compensation function. These signals are evaluated by an electrical information-processing unit, and the results of the evaluations are used to automatically adjust the setting of a line pressure regulating valve.

BACKGROUND OF THE INVENTION 
The present invention relates to an hydraulic control system which controls 
the flow of fluid to at least two consumers. Associated with each consumer 
is a pressure-compensated direction-reversing valve. Each valve performs a 
throttling function and a pressure-compensation function to establish a 
selected volumetric flow rate, and also a direction-control function. 
German published patent application DT-OS 24 40 099 discloses a control 
system of this general type in which, in order to avoid energy losses, the 
output power of the pump of the control system is automatically adjusted 
to meet the prevailing demand of the system. In that system, the control 
spools of all direction-reversing valves are arranged one after the other 
between the pump (which is of adjustable per-cycle volumetric throughput) 
and the tank, and provided between the last control spool and the tank is 
an adjustable constrictor, the pressure drop across which is used to 
control an auxiliary control valve, which in turn effects adjustment of 
the per-cycle volumetric throughput of the pump. This purely hydraulic 
system has the disadvantage that the expense for the hydraulic lines is 
relatively high. Also, the system tends to be inexact and somewhat 
insensitive in operation. Above all, the system does not operate reliably 
during reversals of flow direction. 
SUMMARY OF THE INVENTION 
It is a general object of the invention to provide a control system of the 
general type in question which is, however, of inherently simpler design, 
particularly when the hydraulic lines of the system must be spread out 
over a considerable distance, which makes use of standard hydraulic 
control system components of simple and inexpensive types, and which 
operates very reliably. Above all, it is an object to provide a system 
which is operative, and reliably operative, during load direction 
reversals. 
These objects can be met by constructing each load-compensated 
direction-reversing valve from two control valve stages. One stage 
performs the aforementioned throttling function, the other the 
aforementioned pressure-compensation function, and one of the two stages 
also performs the direction-control function. Each load-compensated 
direction-reversing valve is provided with an electromechanical 
transducer. The transducer senses the settings of the control valve stage 
which performs the pressure-compensation function and generates 
corresponding electrical signals. The electrical signals are evaluated by 
an electrical information-processing unit, and the result of the 
evaluations are automatically employed to adjust the setting of a line 
pressure regulating device. 
Advantageously, the pressure drop across the valve stage performing the 
throttling function is used to control or modify the setting of the valve 
stage performing the pressure-compensation function. 
The electromechanical transducers employed can be, as explained in detail 
below, either simple double limit switches or, if greater exactness of 
operation is desired, analog-operating inductive transducers. 
The novel features which are considered as characteristic of the invention 
are set forth in particular in the appended claims. The invention itself, 
however, both as to its construction and its method of operation, together 
with additional objects and advantages thereof, will be best understood 
from the following description of specific embodiments when read in 
connection with the accompanying drawing.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
FIG. 1 depicts a control system 10 for a first and a second hydraulic 
consumer 11, 12. Associated with each of the two consumers is a respective 
one of two load-compensated direction-reversing valves 13 and 14. The two 
direction-reversing valves 13, 14 are identically constructed, so that 
only the structural details of the first valve 13 need be described. The 
inflow conduit 15 of each direction-reversing valve 13, 14 is connected 
via parallel pressure lines 16, 17 to a pump which sucks pressure fluid 
from a tank 19. The pump 18 is preferably a simple and inexpensive pump of 
non-adjustable per-cycle volumetric throughput. A return-flow conduit 21 
of each of the two valves 13, 14 is likewise connected to the tank 19, via 
respective return-flow lines 22, 23. 
The direction-reversing valve 13 comprises a first control valve stage 24 
which controls both a first work line 25 and a second work line 26 
connected to opposite working chambers of the consumer 11. Connected in 
the second work line 26 is a second control valve stage 27. 
The load-compensated direction-reversing valve 13 performs three functions. 
First, it determines the direction of flow. Second, it determines the 
smallest flow-cross-section in the system. Third, it determines the line 
pressure from the pump. The establisment of the smallest flow 
cross-section in the system (one of the two factors determining the 
volumetric flow rate) is referred to herein as the throttling function. 
The establishment of the line pressure of fluid delivered by the pump to 
the direction-reversing valve (the other of the two factors determining 
the volumetric flow rate) is referred to herein as the 
pressure-compensation function. 
In the control system depicted in FIG. 1, the first control valve stage 24 
performs both the direction-control function and also the 
pressure-compensation function; the second control valve stage 27 performs 
the throttling function. 
The first control valve stage 24 is electrohydraulically piloted, and is 
provided with two electrical inputs 28, 29. To perform its 
pressure-compensation function, the first control valve stage 24 (e.g., 
the control valve member or control slide therein) is centered by 
centering springs 33 between its electrohydraulically actuated control 
pistons 31, 32. Additionally, the first control valve stage 24 is 
controlled, via control lines 34, 35, by the pressure drop across the 
second control valve stage 27. 
The first control stage 24 can assume, in addition to a middle blocking 
setting and non-blocking end settings, any flow-throttling intermediate 
setting, as symbolically indicated in the drawing. 
The first control valve stage 24 is provided with a groove 36. In terms of 
construction, this groove 36 may for example be an annular groove in the 
control spool within valve stage 24. Projecting into this groove is one 
end of a resilient contact blade 37, the other end of which is clamped 
stationary. Contact blade 37 forms part of a double limit switch 38. A 
first output 39 of double limit switch 38 is connected, via a first 
converter stage 40, to a first common line 41. The contact blade 37 
carries a first contact 42 which cooperates with the electrically 
conductive surface of groove 36; in addition, contact blade 37 carries a 
second contact which cooperates with two resilient contacts 44, 45. The 
outputs of the two contacts 44, 45 are both denoted by 46, and are 
connected together. 
The two outputs 46 are connected, via a second converter stage 46', to a 
second common line 47. The two common lines 41, 47 are connected, via 
electrical lines 48 and 49, to the inputs 51, 52 of a NOR-gate 53 and, via 
electrical lines 54 and 55, to the inputs of an AND-gate 58. The output 59 
of NOR-gate 53 controls the setting of a first electric switch 61 
connected in a first branch line 62. The output of AND-gate 58 controls 
the setting of a second electric switch 64 connected in a second branch 
line 65. The first branch line 62 leads from a D.C. current source 66 to a 
first, inverting input 67 of an integrating circuit 69 (e.g., an 
operational-amplifier Miller integrator having inverting and non-inverting 
inputs). The second branch line 65 leads, in parallel to the first branch 
line 62, from the D.C. current source 66 to the second, non-inverting 
input 68 of integrating circuit 69. 
The output 71 of integrator 69 is connected via a line 72 to the control 
magnet 73 of a proportionally adjustable pressure-regulating valve 74. 
Pressure-regulating valve 74 is connected in a relief line 75 which 
branches off from the pressure line 16. 
The second control valve stage 27 is controlled by a proportional magnet 76 
which has an electrical input 77; i.e., the setting of control valve stage 
27 is proportional to the energization of magnet 76. 
The outputs of the (non-illustrated) double limit switch associated with 
the second direction-reversing valve 14 are connected to the common lines 
41, 47 in the same manner as for the first direction-reversing valve 13. 
NOR-gate 53, AND-gate 58, the electric switches 61, 64 and the integrator 
69 are parts of an electrical information-processing unit 78. 
German published patent application DT-OS 24 61 021 discloses structural 
details of a valve corresponding to the first direction-reversing valve 
13; that valve is likewise comprised of a first control valve stage which 
performs the direction-control and pressure-compensation functions, and a 
second control valve stage which performs the throttling function. 
The operation of the control system depicted in FIG. 1 is as follows: 
Each of the two direction-reversing valves 13, 14 is controlled by a 
(non-illustrated) small and portable electrical control device having a 
(non-illustrated) control lever. The control lever has a middle or 
zero-volumetric-flow-rate position, and can be displaced therefrom in 
either direction to non-zero-volumetric-flow-rate positions. 
When the control system 10 is set into operation, the first control valve 
stage 24 will be in its illustrated middle or blocking setting, and the 
second control valve stage 27 in its illustrated blocking setting. The 
double limit switch 38 furnishes no signals to the common lines 41, 42 for 
transmission to the logic circuits 53, 58. Accordingly, NOR-gate 53 
maintains first switch 61 closed, whereas AND-gate 58 maintains second 
switch 64 open. Therefore, the first input 67 of integrator 69 receives a 
signal from current source 66 and so controls the magnet 73, that the 
pressure-regulating valve 74 is caused to assume its lowest-pressure 
setting, which may amount to a few bar. 
The line pressure which pressure-regulating valve 74 establishes when it is 
in its lowest-pressure setting is just sufficient to assure that the 
piloted first control valve stage 24 can be caused to leave its middle 
setting against any resisting forces which may be present (e.g., spring 
forces, frictional forces, and the like). Accordingly, pump 18 delivers 
pressure medium against only this lowest settable pressure -- i.e., so 
long as the first control valve stages 24 of the two direction-reversing 
valves 13, 14 are in their middle or blocking settings. 
If now the control lever is moved out of its middle or 
zero-volumetric-flow-rate position to one side, then, for example by means 
of the electrical input 28, the first control valve stage 24 is 
electrohydraulically piloted, and it is moved by its control piston 31 
through the intermediary of spring 33 in rightward direction, into an 
operative (non-blocking) setting. Simultaneously, an electrical signal is 
applied via electrical input 77 to the control magnet 76 of second control 
valve stage 27; as a result, second control valve stage 27 assumes a 
throttling setting proportional to the amount of shifting of the control 
lever relative to the zero-volumetric-flow-rate position of the control 
lever. 
Accordingly, as soon as the prevailing load pressure is overcome, pressure 
medium flows from the pump 18 through the first control valve stage 24, 
the second work line 26 and the second control valve stage 27, to the 
consumer 11 and, via the first work line 25, the first control valve stage 
24 and the return-flow line 22 to the tank 19. 
The pressure drop resulting across the second control valve stage 27 is 
transmitted via the control lines 34, 35 and acts upon the first control 
valve stage 24 in opposition to the precompression of spring 33 
established by control piston 31, thereby making it possible for the 
control valve stage 24 to perform its pressure-compensation function 
(defined above). 
Returning to the start, as soon as the control lever is moved out of its 
zero setting, the control piston 31 begins to move first control valve 
stage 24 out of its middle or blocking setting. When the setting of stage 
24 has changed to a very small predetermined extent, the first contact 42 
comes into electrically conductive engagement with the groove 36. Via the 
first output 39 and the converter stage 40, a signal is applied to the 
first common line 41, and transmitted to input 51 of NOR-gate 53 and to 
input 56 of AND-gate 58. 
As a result, NOR-gate 53 causes switch 61 to open; switch 64, which was 
already open, remains open. Accordingly, no input signal is applied to 
integrator 69, so that the output signal thereof remains constant at the 
value it had just before switch 61 opened. Thus, the pressure-regulating 
valve 74 is "locked-in" to the previously established lowest-pressure 
setting thereof, and continues to maintain the corresponding line pressure 
value. 
As the first control valve stage 24 begins to leave its middle or blocking 
setting, the line pressure is still at the lowest-pressure value. 
Accordingly, the pressure drop across second control valve stage 27 is 
correspondingly low, and insufficient to oppose the action of control 
piston 31. Therefore, control piston 31 moves the first control valve 
stage 24 all the way to its extreme (fully open) setting. 
When first control valve stage 24 reaches its extreme (fully open) setting, 
second contact 43 electrically engages contact 45. From output 46, a 
signal is transmitted via converter stage 46', second common line 47, and 
the lines 49 and 55, to the inputs 52 and 57 of the logic gates. The first 
switch 61 remains open; the second switch 64 closes, because signals are 
now present at both inputs 56, 57 of AND-gate 58. Accordingly, a signal is 
transmitted via branch line 65 to the non-inverting input 68 of integrator 
69, causing the setting of pressure-regulating valve 74 to be changed to 
higher and higher pressure settings. The resultant line pressure rise can 
reach the maximum possible value in a time as short as about 1/10 of a 
second. However, in general, the maximum possible line-pressure value is 
not reached. 
Specifically, as the line pressure rises, the pressure drop across second 
control valve stage 27 rises correspondingly, due to the increase in 
volumetric flow rate. When the volumetric flow rate corresponding to the 
selected position of the control lever has been reached, the actual 
pressure drop across second control valve stage 27 will be strong enough 
to begin to move first control valve stage 24 out of its extreme (fully 
open) setting and back toward its middle setting. 
However, as soon as control valve stage 24 has moved a predetermined small 
amount out of its extreme (fully open) setting, the signal at output 46 of 
double limit switch 38 disappears, so that the line pressure rise under 
discussion terminates. Specifically, as soon as control valve stage 24 has 
left its extreme setting, switch 64 opens again, so that no input signal 
is applied to integrator 69; accordingly, pressure-regulating valve 74 is 
now locked in that pressure setting which it had as control valve stage 24 
began to leave its extreme setting. 
The switchover points of limit switch 38 are so matched to the stroke of 
the control spool (or the like) of the first control valve stage 24 that, 
at constant load, the control valve stage 24 is as near as possible to its 
fully open setting, in order to minimize energy losses. 
To summarize this sequence of events: 
Initially, the (non-illustrated) control lever is in the zero setting, for 
zero volumetric flow rate; accordingly, the pressure-regulating valve 74 
is locked into its lowest-pressure setting. When the control lever is 
moved to a non-zero setting, the stage 24 moves from its middle setting to 
an extreme setting. When the extreme setting is reached, there commences a 
fast rise in the line pressure. During this fast rise in line pressure, 
stage 24 begins to leave its extreme setting and return towards its middle 
setting. As soon as the rising line pressure has reached a value such that 
the pressure drop across stage 27 indicates that the selected volumetric 
flow rate has been reached, the line pressure rise is terminated. At this 
point, stage 24 will still be very near its fully open setting. The steady 
state of the control system has been achieved. 
From the foregoing, persons familiar with electrohydraulic control systems 
will understand the operation of the system in other conditions, E.g., if 
the load pressure of the consumer 11 now decreases, the signal at the 
first output 39 of limit switch 38 disappears, the switch 61 closes again, 
and there commences a line pressure drop towards the lowest-pressure 
value, but this line pressure drop terminates before the lowest-pressure 
value is reached, i.e., to form the new steady state of the system. 
Likewise, if the load pressure of the consumer increases, there occurs an 
automatic increase in the setting of the pressure-regulating valve 74, to 
effect an automatic compensatory increase in the line pressure and thereby 
maintain the volumetric flow rate at the selected value. 
Since the degree of flow restriction (throttling) effected by the second 
control valve stage 27 is determined by the setting of the 
(non-illustrated) control lever, one can select any desired volumetric 
flow rate between zero and the maximum value of which the system is 
capable. 
Furthermore, irrespective of the volumetric flow rate determined by the 
setting of second stage 27, the setting of the direction-control and 
pressure-compensation first stage 24 will, in the steady state, always be 
as near to fully open as possible, so that the pressure loss for the 
desired volumetric flow rate will be kept as low as possible. This is 
because valve stage 24 controls the line pressure indirectly, by 
terminating the adjustment of pressure-regulating valve 74 when the line 
pressure has reached the correct value for the selected volumetric flow 
rate. 
Accordingly, the control of fluid delivery to the consumer, besides being 
load-pressure compensated, is furthermore performed with the lowest 
possible energy losses. 
If both direction-reversing valves 13, 14 are in operation and furnish 
signals to the electrical information-processing unit 78, then the latter 
inherently singles out the input signal which commands a line pressure 
increase, or the greater line pressure increase if the signals from both 
valves 13, 14 are commanding a line pressure increase. Thus, the setting 
of pressure-regulating valve 74 will automatically be changed to a value 
establishing a line pressure meeting the requirement of whichever one of 
the two valves 13, 14 is placing the higher demand. In that event, the 
valve 13 or 14 associated with the lower load pressure, has its associated 
first control stage 24 in a setting corresponding to the selected 
volumetric flow rate. Any signals originating from this lower-demand valve 
have no effect upon the control system 10, so long as an input signal is 
present at input 52 of NOR-gate 53. In this way, in the control system 10, 
the pressure is always automatically caused to assume a value slightly 
above the respective maximum load pressure, so that unnecessary energy 
losses will not develop. Furthermore, the direction-reversing valves 13, 
14 operate not only under positive loading, but also under negative 
loading. If the direction of fluid delivery is reversed, the first control 
stage 24 of the affected valve(s) returns toward its middle setting, 
resulting in a line pressure decrease. 
FIG. 2 depicts a second control system 80 differing from that of FIG. 1 
mainly in a different construction of its two (identical) 
direction-reversing valves 81, 82 and in the construction of its 
electrical information-processing unit 83. Components in FIG. 2 
corresponding to those in FIG. 1 are denoted by the same reference 
numerals as in FIG. 1. 
The first direction-reversing valve 81 comprises a first control valve 
stage 84 which, in this embodiment, performs the direction-control 
function and the throttling function (both defined earlier) and also a 
second control valve stage 85 which performs the pressure-compensation 
function (likewise defined earlier). Second stage 85 is connected in the 
two work lines 25, 26. First stage 84 controls the four ways (port lines) 
for the work lines 25, 26, the inflow line 15 and the return-flow line 21, 
and also a fifth way for a control line 86. 
By means of the control line 86, one end of the second control valve stage 
85 (i.e., one end of the control spool thereof, or the like) is relieved 
into the return-flow line 21, when the first control stage 84 is in its 
middle setting. The opposite end of second stage 85 is connected, via a 
second control line 87, to the first work line 25 at a point thereof 
between the two control stages 84 and 85. 
The first control stage 84, besides its middle setting and its two extreme 
settings, can also assume any intermediate setting, in the course of 
performing the throttling function. 
The first, spring-centered control stage 84 is controlled by a 
bidirectional proportional-acting magnet 88. When first control stage 84 
leaves the middle setting, the first control line 86 is always connected 
to a point so located within the flow of pressure fluid passing through 
work lines 25, that the pressure drop across the first control stage 84 is 
applied via the control lines 86, 87 to the second control stage 85, to 
control the latter. 
The second control stage 85 (which performs the pressure-compensation 
function) has a middle setting in which it fully opens the work lines 25, 
26; additionally, it can assume settings to either side of its middle 
setting, so as to vary the smallest flow cross-section of the system in 
proportion to its displacement from the middle setting. 
The second control stage 85 is mechanically coupled to the moving component 
of an inductive transducer 89, whose input 91 is connected to an 
oscillator 92 and whose output 93 is connected to the input 94 of an 
electrical control device 95. The output 96 of the electrical control 
device 95 is connected, via a diode 97, to the input of a high-precision 
rectifier 99, whose input is also connected via a second diode 101 to the 
output of an electrical control device 102 associated with the second 
direction-reversing valve 82. The output 103 of rectifier 99 is connected, 
via a proportional amplifier 104, to the control magnet of the 
pressure-regulating valve 74. Amplifier 104, rectifier 99, diodes 97, 101, 
electrical control devices 95, 102, and oscillator 92 together form an 
electrical information-processing unit 83. 
The control system 80 of FIG. 2 operates as follows: 
Each of the two direction-reversing valves 81, 82 is controlled by a 
(non-illustrated) control lever on a small portable remote-control unit 
(likewise not illustrated). 
When the control system 80 is to be set into operation, the control lever 
first connects the electrical information-processing unit 83 to operating 
voltage. As a result, transducer 83 receives from oscillator 92 an A.C. 
signal, modulates it in dependence upon the setting (at this point, the 
middle setting) of second control valve stage 85, and furnishes the 
setting-modulated signal to the first electrical control device 95. In the 
latter, the signal is demodulated, filtered and amplified and furnished as 
a D.C. signal (after its transmission through diode 97 and precision 
rectifier 99) to the proportional amplifier 104. The latter sets 
pressure-regulating valve 74 for a pressure valve proportional to the 
signal. 
The electrical information-processing unit 83 is so designed that, when the 
second control valve stage 85 is in its middle or blocking setting, the 
unit 83 causes a line pressure rise in the control system 80. Accordingly, 
to prevent the line pressure from rising to the maximum possible value 
when the system is not in operation, the information-processing unit 83 is 
not connected to operating voltage until the (non-illustrated) control 
lever leaves its zero-volumetric-flow-rate setting; however, as soon as 
the zero setting is left, the unit 83 is connected to power. 
In any event, when the control lever is moved from its zero setting an 
electrical signal, corresponding in polarity and magnitude to the 
direction and magnitude of the desired volumetric flow rate, is applied to 
the bidirectional control magnet 88. As a result, first control valve 
stage 84 undergoes a change of setting in the appropriate direction and to 
a proportional extent. 
To repeat, when the (non-illustrated) control lever is moved from its zero 
position, the information-processing unit 83 becomes activated (connected 
to operating voltage) and, so long as second stage 85 is in its middle 
setting, effects a line pressure rise. The line pressure rise occurs very 
fast; as soon as the load pressure of the consumer is overcome, pressure 
fluid commences to flow through check valve 105, the first and second 
control stages 84, 85 and into the first consumer 11. 
The resulting pressure drop across the first control valve stage 84 (i.e., 
between a point upstream of the flow-constricting structure therein and a 
point downstream thereof) acts, via the control lines 86, 87, upon the 
second control valve stage 85, so that stage 85 can perform its 
pressure-compensation function. Specifically, second control valve stage 
85 leaves its middle (unblocking) setting in one direction or the other, 
and assumes a throttling setting of such an extent as to tend to maintain 
the aforementioned pressure drop across stage 85 at a constant value. When 
stage 85 thusly leaves its middle setting, transducer 89 applies to 
information-processing processing unit 83 a signal causing the latter to 
lower the pressure setting of pressure-regulating valve 74. The electrical 
information-processing unit 83 is so designed that, if the load pressure 
is constant, the control system 80 adjusts the second control valve stage 
85 to a setting in which its flow cross-section is smaller than its 
maximum flow cross-section (corresponding to its middle setting) by only a 
small predetermined amount. This serves to prevent unnecessary energy 
losses, because the system maintains the line pressure just slightly 
higher than the prevailing load pressure. Nevertheless, the consumer 11 
receives pressure fluid at a volumetric rate whose magnitude is 
independent of load pressure and dependent only upon the flow 
cross-section to which the first control valve stage 84 is set. 
If the two direction-reversing valves 81 and 82 are both activated, and if 
consumer 12 demands a higher pressure, then the signal generated by the 
second electrical control device 102 predominates and the 
pressure-regulating valve 74 is set to a corresponding setting. In that 
event, the second control valve stage 85 of the first direction-reversing 
valve 81 assumes a more constricted setting than it would otherwise do, in 
order to maintain the pressure drop across the first control valve stage 
85 unchanged. The trnsducer 89 of the first valve 81 generates a signal 
commanding a line pressure decrease, but this signal has no effect upon 
the information-processing unit. The direction-reversing valve 81 operates 
not only under conditions of positive load, but also if a negative load 
appears during a direction reversal. 
The control system 80 of FIG. 2 is of somewhat more expensive construction 
than that of FIG. 1, but it has the advantage of analog operation and 
accordingly very exact pressure control. Additionally, the transducer 89 
can be arranged directly connected to and coaxial with the second control 
valve stage 85. The service life of the control system 80 is improved by 
the use of the contact-free inductive transducer 89. 
It will be understood that each of the elements described above, or two or 
more together, may also find a useful application in other types of 
circuits and constructions differing from the types described above. 
While the invention has been illustrated and described as embodied in two 
electrohydraulic control systems of particular type, it is not intended to 
be limited to the details shown, since various modifications and 
structural changes may be made without departing in any way from the 
spirit of the present invention. 
Without further analysis, the foregoing will so fully reveal the gist of 
the present invention the others can, by applying current knowledge, 
readily adapt it for various applications without omitting features that, 
from the standpoint of prior art, fairly constitute essential 
characteristics of the generic or specific aspects of this invention.