CN109139587B

CN109139587B - Valve block assembly and method for valve block assembly

Info

Publication number: CN109139587B
Application number: CN201810678001.XA
Authority: CN
Inventors: W.维尔纳; B.塞莱斯; S.奥施曼
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2017-06-27
Filing date: 2018-06-27
Publication date: 2023-05-05
Anticipated expiration: 2038-06-27
Also published as: CN109139587A; DE102017213118A1

Abstract

A valve block assembly is disclosed having a valve block with at least two main slides for controlling a load, respectively. The respective main slide is connected to two electrically adjustable hydraulic presses.

Description

Valve block assembly and method for valve block assembly

Technical Field

The present invention relates to a valve block assembly and a method for controlling the same.

Background

Movable work machines, such as e.g. excavators, are known from the prior art, which work machines have a hydraulic system. In this case, a single hydraulic pump is usually provided, which is fixedly associated with a defined load. Some of the loads may also be supplied by two hydraulic pumps. In this case, one hydraulic pump is then usually provided as the main pump, and the other hydraulic pump is provided as the summation pump. In this case, it is disadvantageous that: the supply by the summation pump is energy inefficient when multiple loads are simultaneously operated.

DE 10 2012 218 428 A1 discloses a valve block which can be used in a construction machine. The valve block has a plurality of main skids for controlling the load. The respective main slide can be supplied with pressure fluid in parallel via the first and the second pump channel. The fluid flow which flows in by the pump channel is controlled by means of the associated first or second auxiliary slide.

Disclosure of Invention

In contrast, the invention is based on the task: a valve block assembly is provided, by means of which a load can be controlled efficiently with high flexibility and in a simple manner in terms of installation technology. Furthermore, the task of the invention is: a method for a valve block assembly is created with which a load can be handled in a simple manner and efficiently.

The task with respect to the valve block assembly is solved according to the features of claim 1 and the task with respect to the method is solved according to the features of claim 8.

Advantageous refinements of the invention are the subject of the dependent claims.

According to the invention, a valve block assembly is provided, which has a valve block, in particular a neutral shut-off valve (Closed Center). The valve block can have at least two, in particular electrically or electrohydraulically or hydraulically controllable main valve slides or main valve slides. The main slide or the main valve slide is used for controlling the hydraulic load respectively. At least one pressure connection and at least one working connection can be assigned to the respective main slide. Furthermore, two hydraulic machines with adjustable delivery capacity, in particular two electrically adjustable hydraulic machines, which are each connected to a respective pressure connection, can be provided. Alternatively, a hydraulic machine that can be hydraulically adjusted is also conceivable.

This solution has the following advantages: this makes possible a variable distribution and an individual adjustment of the volume flow to the load. This is achieved by suitable actuation of the electrically adjustable hydraulic machine and of the main slide. Furthermore, it is advantageous that: each load can be efficiently fed with more than one maximum pump quantity, since an accumulation of the feed volume flows of the hydraulic machine is made possible. If the torque required or the power required to be able to drive the drive means of the hydraulic machine is less than required, a separate limitation of the load supplying the volumetric flow can be achieved by the valve block assembly according to the invention. This makes possible a free and flexible change in the distribution of the supply volume flow for the respective load.

The neutral shut-off valve system (Closed Center System) involves a hydraulic circuit in which directional valves for controlling the load are closed at their central position. When using a constant pump (Konstantpumpen) as the pressure medium source, the volume flow is therefore usually guided through the bypass valve when the directional valve is closed. In the neutral opening valve system, hydraulic lines are provided, wherein the direction valves connected in succession for controlling the load are open to the oil flow in their central position, so that the pump flow of the constant pump can be guided through all the direction valves. If only one directional valve is provided, the pressure medium volume flow can be guided to the tank in its central position, wherein one is called the neutral cycle.

The valve block is preferably used as an RCS (MCV) motion control block.

In a further embodiment of the invention, it may be provided that: at least one of the main slides or at least one part of the main slides or the respective main slide is assigned a throttle valve, in particular electrically or hydraulically adjustable and/or controllable, in fluid communication between its pressure connection and a hydraulic machine connected thereto. This further increases the flexibility for adjusting the volume flow distribution. Alternatively or additionally, it is also conceivable to: a throttle valve, which can be actuated and/or actuated, in particular electrically or hydraulically, is assigned to one of the main slides or at least a part of the main slides or the respective main slide in fluid communication between its pressure connection and the respective further hydraulic machine. This results in a further improvement of the volumetric flow distribution between the loads, whereby the flexibility is further increased. The variable distribution and the regulation of the individual volume flows to the load can thus be further improved by a proportionally adjustable throttle valve. It is conceivable that: for cost reasons, instead of one or more throttle valves, a non-return valve (ruckschlagvenil) is provided, which blocks in the direction of the associated hydraulic machine. The throttle valves can be arranged in parallel in fluid communication and are connected, on the one hand, to the respectively associated main slide and, on the other hand, to the hydraulic machine.

In a further embodiment of the invention, it may be provided that: a bypass flow path branches off in fluid communication between the pressure port and the hydraulic machine. The bypass flow path can then be connected to the tank or to the low-pressure side via a shut-off valve (Cut-venturi), which can be controlled in particular electrically or hydraulically, and can be throttled via the shut-off valve. This has the following advantages: the desired load dependence or load sensitivity (lastfuhligkey) can be implemented with the shut-off valve, as is provided in the neutral opening valve system (Open Center System). Since the shut-off valve can in particular be electrically regulated and/or actuated, the opening section of the shut-off valve can be flexibly determined. The smaller the opening cross section of the shut-off valve, the stiffer the hydraulic system (steifer) and the less load-sensing. If, for example, the main slide is used to control the bucket of a single-bucket excavator and the bucket is in operation, for example, hitting a pipe, the bucket speed will be significantly reduced when there is a high load perception. The excavator driver will recognize through the lesser speed of the bucket: the bucket hits an obstacle so that he can "feel" the load in this way. When there is less load perception, which means that the opening cross section of the shut-off valve is relatively small, the speed of the bucket movement will not change or substantially not change or only change very little when, for example, it hits the pipe, whereby the excavator driver may not perceive this. Thus, there is little load perception for the excavator driver. The desired load dependence, as in a neutral-opening valve system, can thus be achieved in a manner that is simple in terms of equipment, in particular by means of an electrically adjustable or controllable shut-off valve.

In another embodiment of the invention, a bypass flow path may be branched off in fluid communication between the pressure connection and the further hydraulic machine. The bypass flow path can then be connected to the tank via a further, in particular electrically adjustable and/or controllable shut-off valve, and can be throttled via the shut-off valve. The neutral opening valve behavior can thereby be further improved.

A make-up interface and/or a further working interface may preferably be assigned to at least one of the main skids or to a part or all of the main skids outside the pressure interface and the working interface. Then, for example, pressure medium can flow out of the load via the replenishment connection. Through a further working interface, it is conceivable to: a double acting cylinder is provided as a load. Preferably in the main slide or in a part of the main slide or in all the main slides: they can be continuously adjusted. The actuating angle of the main slide or the individual main slide can then be provided as an adjusting element.

In a preferred embodiment, the main slide can be brought into a neutral position, in particular centered by a spring, in which the connections assigned to the main slide are separated from one another. Starting from the intermediate position, when the main slide is moved to the first switching position, the pressure connection is connected to the first working connection and the replenishment connection is connected to the second working connection. When the main slide is moved from the intermediate position in the direction of the second switching position, wherein the direction is opposite to the first switching position, the pressure connection can be connected to the second working connection and the first working connection can be connected to the supply connection. For adjusting the main slide, a valve slide actuating device or an actuator is provided. The first actuator can be used here for the first adjustment direction and the second actuator can be used for the second adjustment direction. The additional main skillets may be configured accordingly. The main slide associated with the two working ports, a pressure port and a supply port may be part of a 4/3-way valve. One or both throttle valves which can be associated with the main slide can then be provided as a valve subassembly.

In a further embodiment of the invention, the shut-off valve or the corresponding shut-off valve can be closed or opened continuously in order to flexibly adjust the load sensitivity. The shut-off valve or the corresponding shut-off valve is preferably open in the initial position, whereby the hydraulic machine is connected to the tank. The valve slide plate of the shut-off valve may be biased in the direction of the initial position by a spring force of the valve spring. The valve slide of the shut-off valve can then be moved in the direction of the closed position by the valve slide actuating device or by the actuator.

In a further embodiment of the invention, one of the hydraulic machines can be used as a main pump and accordingly the other hydraulic machine as an accumulator pump. The hydraulic machine is preferably volumetric flow controlled or pressure controlled. A pressure sensor is preferably arranged downstream of the respective hydraulic machine. If one or both hydraulic machines are pressure-controlled, a pivot angle sensor is preferably additionally provided for this type of hydraulic machine. Also contemplated are: one or more additional hydraulic presses are used in addition to the two hydraulic presses. The corresponding hydraulic machine can then preferably supply pressure medium from the tank to the associated main slide.

In a further embodiment of the invention, a control electronics unit is provided. The control electronics may have a matching module or a first module. In this matching module or first module, a predetermined value can then be entered or can be supplied for a load or for the respective main slide, in particular by means of an input device or a respective input device. The predetermined value or the corresponding predetermined value may then be changed to a matching or corresponding matching predetermined value by the matching module. In other words, in the matching module, a predetermined value can be matched, in particular smoothed, for each load. The joystick is provided for example as an input device, wherein the joystick signal can then be used as a predetermined value. The predetermined values are converted into matching predetermined values, for example by means of a monotonic or continuously increasing characteristic curve and/or by means of a time function, for example PT1 or PT 2. The matching by means of predetermined values advantageously enables signal conditioning (signalonconditioning). A joystick for the main slide is preferably provided. If a plurality of main skillets are provided, a respective joystick may be provided for a portion of the main skillets or for a respective main skillet.

A control electronics unit or the control electronics unit may advantageously have a predetermined module or a second module. With this or the second module, it is then possible to convert in particular the matched predetermined value or the corresponding in particular matched predetermined quantity into a predetermined volume flow quantity for the load or into a corresponding predetermined volume flow quantity for the corresponding load. Furthermore, the predetermined module can preferably be used to convert in particular the matched predetermined value or the corresponding in particular matched predetermined value into in particular desired load-sensing information or into in particular desired corresponding load-sensing information for the load or for the corresponding load. Alternatively or additionally, a predetermined module setting may be utilized: the in particular matched predetermined value or the corresponding in particular matched predetermined value is converted into in particular a desired or respectively a particularly desired maximum pressure. Along with the load-sensing information, there is a throttle valve preset amount for the shut-off valve, whereby a dynamic head (Staudruck) can then advantageously be adjusted, with which the load can be supplied according to the neutral opening valve principle. The predetermined volume flow can then predefine the speed of the load. The maximum pressure for the respective load can advantageously be used to switch the hydraulic machine to a higher level (Hochregeln) depending on a predetermined value or a control signal.

The predetermined volume flow for the load or for the respective load can then be taken out by the characteristic field as a function of the matched predetermined value in relation to the respective load. Alternatively or additionally, a characteristic field can be set for the loaded or the corresponding loaded, corresponding load-awareness information, which is based on the loaded (corresponding) matched predetermined value. Alternatively or additionally, a characteristic field for the (respective) maximum pressure for the load or for the respective load can also be extracted, which characteristic field is likewise based on a predetermined value that has been adapted for the load or for the respective load. The predetermined value can thus be converted in a very simple manner by means of the characteristic field.

In a further embodiment of the invention, the control electronics or a control electronics can have a control module or a third module. The actuating module or the third module can then generate, in particular, an electrical or hydraulic actuating signal or, in particular, a plurality of electrical or hydraulic actuating signals, based on the converted predetermined quantity of the predetermined module. The manipulation signal may be set to: a total volume flow pre-determined amount for the hydraulic machine or a pump volume flow pre-determined amount for the main pump and a pump volume flow pre-determined amount for the summation pump and/or a total throttle pre-determined amount for the shut-off valve and/or a control amount for the main slide or a corresponding control amount and/or a control amount for the throttle valve or a part of the throttle valve or for the corresponding throttle valve or a corresponding control amount. In other words, the third module may integrate the load-based input values and generate the corresponding steering signals. In addition, the load pressure of the load or of some or all of the loads can be taken into account in the actuating module for generating the actuating signal or actuating signals in order to make improved load perception possible. The load pressure is preferably preset and is based on empirical values, for example. Alternatively or additionally, it may be provided that: the load pressure is detected by one or more sensors. The control variable for the valve slide actuation of the main slide and/or the control variable for the pump actuation of the at least one hydraulic machine and/or the control variable for the valve slide actuation of the shut-off valve can thus be calculated by means of the calculated value of the matched predetermined value and/or the calculated value of the maximum pressure for the respective load and/or the calculated value of the predetermined volume flow for the respective load and/or the load-sensing information for the respective load and/or the load pressure for the respective load.

In other words, a control device and software are provided in order to process the setpoint values or the driver's expectations and to calculate the necessary actuating signals.

In a further embodiment of the invention, it is conceivable that: the rotational speed of the hydraulic machine is taken into account in the actuating module, which is used to generate the actuating signal. A more accurate generation can thereby be achieved in a device-wise simple manner. The rotational speed of the hydraulic machine may be implemented as a predetermined parameter, for example based on empirical values, or as a measured value, for example detected by one or more sensors. Alternatively or additionally, the torque of one of the hydraulic machines or the torque of one of the drive units driving the hydraulic machine (e.g. motor or diesel engine) may be taken into account in the steering module to make it possible to generate the steering signal more accurately.

In other words, the data for actuating each load is supplied to an actuating module, which can actuate the valves, shut-off valves and pump actuating devices of the respective load in accordance with predefined arithmetic operations.

The manipulation by the manipulation signal is preferably implemented as a control of the feedback or in a "feed forward mode" (Feed Forward Modus). This results in an extremely simple handling of the device technology.

The module for the control electronics can be a software module which is implemented in particular on the control electronics in a simple and cost-effective manner.

Applicant reserves the independent claim itself for the electronic component according to one or more of the preceding aspects.

A method for controlling a valve block assembly according to one or more of the foregoing aspects may be provided according to the present invention. The supply volume flows for the loads that can be delivered by the hydraulic machine are individually or variably assigned to the connected loads by actuating the hydraulic machine, in particular the electrically adjustable hydraulic machine, with an adjustable delivery rate, and by actuating the main slide, in particular the electrically adjustable slide. What can be considered here are: the assignment is furthermore supported by controlling at least one shut-off valve.

This solution has the following advantages: this makes it possible to limit or shift the supply volume flow of the hydraulic machine in an efficient manner as a function of the driver demand and the available power. Furthermore, it is possible to reduce the supply volume flow, but also to the inflow cross section of the load, when the available power or the available torque (for driving the hydraulic machine) is exceeded.

In a further embodiment of the method, a separate assignment of the transportable supply volume flow for the load can additionally be achieved by actuating the, in particular electrically adjustable, throttle valve. The variable assignment and the adjustment of the individual volume flows to the load can thus be achieved flexibly and variably by means of a proportional adjustment throttle and an electrically adjustable hydraulic machine. A part of the volumetric flow distribution can then additionally be embodied by the, in particular electrically adjustable, main slide.

The use of the method according to the invention thus makes it possible to control the valve-and pump assembly according to one or more of the aforementioned aspects, wherein: the assignment of the hydraulic machine to the respective load can be controlled extremely efficiently and well.

In a preferred embodiment of the invention, the respective load can be assigned a priority, in particular by the control electronics. The assignment of the supply volume flow to the load can thus be effected depending on the priority. Thus, it is conceivable to: an adjustable or predefinable priority is set individually for the individual loads. Thus, for example, it is possible to provide: the higher the priority or priority, the later the supply amount of the load is reduced.

If at least two loads are provided, the first load may have the highest, in particular first, priority and the second load may have a smaller, in particular second, priority. It is conceivable that: the priorities for the further loads are accordingly ranked further. If, for example, at least three loads are provided, a first load may have the highest, in particular first, priority, a second load may have a smaller, in particular second, priority and a third load may have a smaller, in particular third, priority.

Preferably, the respective predetermined volume flow for the respective load can be predefined, in particular by means of a control lever. The respective predetermined volume flow can then be assigned a respective limiting factor, in particular by the control electronics, by which the respective predetermined volume flow value is then reduced, if necessary, in a predetermined manner. The respective load may thus be assigned a respective limiting factor. In a preferred embodiment of the invention, the respective, in particular desired, predetermined volume flow for the respective load can then be multiplied by its associated limiting factor in order then to obtain an actual predetermined volume flow for the respective load. The respective limiting factor is preferably located between 0 and 1 or 0 or 1. In other words, the respective limiting factor may lie in a region between 0 and 1, with

boundaries

0 and 1 belonging to this range. If the limiting factor for the load is greater than 0 and less than 1, the limiting factor may be calculated as a function of the power of the drive unit available to the hydraulic machine and/or as a function of the power required by the further load and/or as a function of the minimum power associated with it.

In a further embodiment of the invention, a minimum predetermined volume flow can be provided for the respective load or at least for a part of the load, wherein the predetermined volume flow is identical or different. In other words, for each load or part of a load, a minimum amount can be determined, which is maintained as long as it is feasible, whereby a minimum operation of the work machine, for example, using the method can be maintained.

The controller may preferably be provided with a mode or a plurality of different modes in which a predetermined limiting factor for the load, in particular depending on its priority, is set. A model of a type of limiting factor for the load can thus be set in a mode or in a corresponding mode. The associated change in the supply volume flow for the respective load can thus be achieved, for example, in a simple and flexible manner by switching modes. In other words, it is possible that: the different accumulation policies are applied by suitable software functions.

One or more of the modes mentioned below may be set to a mode (Modus or Modi):

In one mode, in particular the first mode, the limiting factor may be the same or 1. If the limiting factor is 1, a predetermined volume flow amount may be set for the respective load, which may correspond to the actual predetermined volume flow amount.

In a further, in particular second, mode, the limiting factor for the load with the highest, in particular first, priority is greater than for the load with the smaller priority. Thus ensuring that: for the load with the highest priority, a virtually predetermined volume flow is set, which is at least the highest or corresponds to the desired volume flow, if the limiting factor is 1. The volume flow of the load with the smaller priority can then be reduced by: the limiting factor is smaller than the limiting factor of the load with the highest priority. In the case of loads with a smaller, in particular third, priority, the limiting factor can be derived from the following difference: the difference is the difference between the power that can be provided for the hydraulic machine and the power that is required by the further load, wherein said difference is placed in a ratio, in particular in a first ratio, which is the ratio to the power required by the load with a smaller, in particular third priority. Preferably, in the case of loads with intermediate, in particular second, priorities, the limiting factor is likewise 1 and/or the limiting factor corresponding to the load with the highest, in particular first, priority.

For the load with the smallest, in particular third, priority, then the ratio, in particular the first ratio, may be set as limiting factor.

In a further, in particular third mode, it is possible to provide: in the case of loads with intermediate, in particular second, priorities, the limiting factor is 0. For example, a limiting factor of 1 is thus set for the load with the highest, in particular first priority, and the ratio, in particular the first ratio, is set as limiting factor for the load with the smallest, in particular third priority.

In a further preferred, in particular fourth mode, the limiting factor for the load with the highest, in particular first, priority may be 1, or at least greater than the limiting factor for the load with the smaller priority. In the case of loads with a smaller, in particular third, priority, the limiting factor can then be derived from, in particular, a second ratio of the predefined minimum power for the load with a smaller, in particular third, priority and the power required for the load with a smaller, in particular third, priority. In the case of further loads with likewise smaller, in particular second priority, the limiting factor can then be derived from the difference between the power available via the hydraulic machine and the power required by the load with the highest, in particular first, priority and the minimum power predefined by the load with the smaller, in particular third, priority. The difference can then be placed in a ratio, in particular in a third ratio, which is the ratio to the power required by the load with the smaller, in particular second, priority.

In a further, in particular fifth mode, the limiting factor for the load with the highest, in particular first, priority may then be 1, or at least greater than the limiting factor for the load with the further lesser priority. For the load with the smaller, in particular second and third priority, it is possible to provide that: the loads have the same limiting factor, which can then consist of the ratio of the difference to the sum, in particular of the fourth ratio. The difference may be the difference between the power available by the hydraulic machine and the power required by the load with the highest, in particular first priority. The sum can then consist of the power of the load with the smaller, in particular the second and third, priority.

In a further, in particular sixth mode, it can be provided that: the limiting factor for the load with the highest, in particular first priority, is formed by the ratio, in particular the fifth ratio, of the power that can be used by the hydraulic machine to the power required by the load with the highest, in particular first priority. For loads with a smaller, in particular second or third, priority, the limiting factor may then be 0. Thus, in the sixth mode, it may be advantageously provided that: the supply amount of the load having the highest priority is reduced only in the following cases: all further loads have been completely reduced. This is advantageous in particular in special additional devices, for example in magnetic holders (magnethane), which require greater safety.

In a further embodiment of the invention, in particular as a further mode, it may be provided that: the accumulator pump is used when: the supply volume flow that can be delivered by the main pump is no longer sufficient to cover the volume flow of the load by a predetermined amount. This has the following advantages: the main pump may be fully utilized and fully swung out (ausgeschwenkt) as much as possible before the summation pump is used, since it is shown that: the fully swung out hydraulic machine has the best efficiency. In other words, as soon as the main pump has not been fully utilized, the additional quantity of the summation pump is discarded as much as possible, wherein a so-called implicit summation (implizierte Summierung) is involved.

In a preferred embodiment, in particular in a further mode, if the available power, in particular the power of the drive unit, is insufficient for switching the pump volume flow for the main pump and the summation pump by a predetermined amount, it can be provided that: the main pump then delivers the greatest supply volume flow or at least substantially the greatest possible supply volume flow, and in particular here swings out completely or at least substantially completely. This is advantageous because the main pump is most efficient in a fully swinging out condition. The summation pump can then deliver little or no supply volume flow. At least the main pump is therefore operationally extremely efficient.

In a further embodiment of the invention, in particular as a further mode, it can be provided that: at least two loads are used as the travel axle and thus drive the tracks of a tracked vehicle or a tracked excavator, respectively, for example. In addition, a further load may be provided or a plurality of further loads may be provided. In this case, one of the hydraulic machines can then be used for supplying the drive axle and the other hydraulic machine can be used for supplying the load or the other load. Shown are: this is extremely efficient, especially when additional loads are used for the following functions in the working machine: this function is not used to drive the work machine. In another mode, it is then conceivable that: the respective travel shaft is fed by a respective hydraulic machine, wherein at least one of the hydraulic machines is then used to feed a further load or at least a part of a further load. The additional hydraulic machine can then likewise be used to supply additional parts of additional loads if required. It is thus possible to use one hydraulic machine for both driving axles or a corresponding hydraulic machine for the corresponding driving axle, if desired, with great flexibility. When the working machine is traveling straight, it is extremely advantageous to use one hydraulic machine for both traveling shafts.

The load or the further load outside the travel axis can be: in particular the boom (auseger), bucket (L ffel), swing mechanism (Drehwerk) and stick (Stiel) of an excavator.

In another mode, it can be provided that: one of the hydraulic presses can be used for a single load, which then involves in particular additional equipment. The further hydraulic machine may then be provided for a further load. This is advantageous because in some special additional devices it may be required that: the hydraulic machine is reserved for this purpose when the additional device is activated. This may be advantageous, in particular, for energy reasons, when the additional device requires a certain stable pressure level.

The mode may be selected automatically and/or activated by an operator.

Drawings

Preferred embodiments of the invention are further elucidated below with the aid of schematic illustrations. Shown are:

figure 1 shows a valve block assembly according to an embodiment in a hydraulic circuit diagram,

figure 2 shows in schematic view the control electronics of the valve block assembly of figure 1,

figure 3 shows in schematic diagram a different mode for controlling the load of figure 1,

Fig. 4 shows a simplified characteristic curve for representing an additional mode for the valve block assembly of fig. 1,

fig. 5 and 6 each show a table for simplified presentation of the corresponding modules for the valve block assembly of fig. 1.

Detailed Description

According to fig. 1 a valve block assembly 1 according to an embodiment is shown. The valve block assembly has a first hydraulic machine in the form of a hydraulic pump, which is used as the main pump 2. Furthermore, a second hydraulic machine in the form of a hydraulic pump is provided, which is used as a summation pump 4. Pressure sensors 6 are connected to the outlet sides of the respective pumps 2 and 4. Furthermore, three

main skids

8, 10, 12 are provided. The three main skids are arranged in parallel in fluid communication and are connected to two pumps 2 and 4, respectively. The respective main slides 8 to 12 each have a pressure connection P. Between the respective pressure connection P and the main pump 2, in particular electrically

adjustable throttle valves

14, 16 and 18 are each provided. Furthermore, in each case, an in particular electrically

adjustable throttle valve

20, 22, 24 is likewise provided between the respective pressure connection P and the summation pump 4. The

throttles

14, 16 and 18 are thus connected in parallel in fluid communication to the main pump 2, and the

throttles

20, 22 and 24 are connected in parallel in fluid communication to the summation pump 4.

Furthermore, a replenishment connection T is provided for the respective main slide 8 to 12. The replenishment interfaces are connected to tank 28 via replenishment pipes 26, respectively. Furthermore, a first work interface a and a second work interface B are provided for the respective main skids 8 to 12. The

loads

30, 32 and 34 are each connected to a respective working connection A, B, which are each designed as differential cylinders (differential cylinders) with a single-sided piston rod. The respective main skids 8 to 12 are therefore used to control the respective loads 30 to 34 associated with them.

The respective main slides 8 to 12 are spring-centered in their initial position a. Starting from its initial position a, the respective main slide 8 to 12 can be actuated by the

actuators

36, 38 in the direction of the first switch position b. In this case, the pressure port P is connected to the working port a and the working port B is connected to the replenishment port T. Furthermore, the respective main slide 8 to 12 can be moved from their initial position a in the direction of the switch position c opposite to the switch position b. In this case, the respective pressure port P is connected to the second working port B and the first working port a is connected to the replenishment port T. The main slides 8 to 12 are each continuously adjustable.

A first bypass flow path 40, which is connected to tank 28, branches off in fluid communication between

throttle valves

14, 16, and 18 and main pump 2. A continuously, in particular electrically adjustable shut-off valve 42 is provided in the bypass flow path. The valve slide of the shut-off valve 42 is acted upon by the spring force of the valve spring in this case toward its open position. In the closed position, the valve slide of the shut-off valve 42 can be acted upon by an actuator, which can be actuated in particular electrically. The shut-off valve 42 can thus be used to control the pressure medium connection between the outlet side of the main pump 2 and the tank 28.

Furthermore, a further second bypass flow path 44 branches off between the

throttle valves

20, 22 and 24 and the summation pump 4. In this second bypass path, a shut-off valve 46 is likewise arranged in order to control the pressure medium connection between the outlet side of the summation pump 4 and the tank 28. The shut-off valve 46 is in this case embodied in correspondence with the shut-off valve 42.

Further, a controller or control electronics 48 is schematically illustrated in fig. 1. The control electronics are used to control the main slides 8 to 12, the throttle valves 14 to 24, the shut-off valves 42 and 46 and the pumps 2, 4. The control electronics 48 are further illustrated in fig. 2 which follows.

The control electronics 48 of the valve block assembly 1 of fig. 1 are shown according to fig. 2. In order to control the respective loads 30 to 34, as shown in fig. 1, in each case one actuating

lever

50, 52 and 54 is provided, which is connected to the control electronics 48. The respective levers 50 to 54 are each connected to a block 56, which is part of a matching module or a first module 58. In which the respective predetermined values a1 to a3 predefined by the levers 50 to 54 are adapted. The corresponding, matched predetermined values b1 to b3 are then output by the corresponding blocks 56. The adaptation is achieved by means of a characteristic curve and by means of a time function, for example PT1 or PT 2.

The respective matched predetermined values b1 to b3 are fed in the respective blocks 60 of the control electronics 48. The block 60 forms a predetermined module or second module 62. The predetermined values b1 to b3 are then converted in their respective blocks 60 to maximum pressures p_max_1 to p_max_3 using a characteristic curve. The respective maximum pressure p_max_i can be raised linearly with the respective increased matched predetermined value bi to a defined value, from which the maximum pressure p_max_i remains unchanged, even if the respective matched predetermined values b1 to b3 continue to rise. Thus, at the beginning of the respective deflection of the levers 50 to 54, the respective predetermined amount for the maximum pressure p_max_i is continuously increased together with the deflection. From the determined actuation path of the respective actuation lever 50 to 54, the respective maximum pressure p_max_i then remains constant. Furthermore, in the second module 62, the respective matched predetermined values b1 to b3 are converted into respective predetermined volumes Q1 to Q3 of the volume flows for the respective loads 30 to 34 (see fig. 1). They are likewise matched by means of a characteristic curve. In this case, the respective predetermined volume flow amounts Q1 to Q3 can then be raised by the respective matched predetermined values b1 to b3. Furthermore, a desired load awareness information A1 to A3 is generated in the respective blocks 60 of the second module 62. The respective load-sensing information A1 to A3 likewise depends on a characteristic curve on the respective predetermined values b1 to b3 that are adapted. The larger the predetermined values b1 to b3 are, the smaller the corresponding load perception information A1 to A3 are.

According to fig. 2, the matched predetermined values b1 to b3, the predetermined volumes Q1 to Q3 of the volume flows, the load-sensing information A1 to A3 and the maximum pressures p_max_1 to p_max_3 are input in a block 64 of the control electronics 48. The blocks form a steering or third module 66. In addition, the pump pressures p_pmp_1 and p_pmp2 detected by the sensor 6 of fig. 1 are input in a block 64. In addition, in a block 64, the rotational speed n_engine (not shown) of the motor driving the pumps 2, 4 in fig. 1 and the torque m_engine of the motor are input. From the input calculated values and pressures, as well as rotational speeds and torques, control values or actuating signals a1, a2 and a3 for the respective actuator 36 in fig. 1 and b1, b2 and b3 for the respective actuator 38 are generated. Furthermore, control values or control signals c1, c2 and c3 for the

throttle valves

14, 16 and 18 of fig. 1 and d1, d2 and d3 for the

throttle valves

20, 22 and 24 of fig. 1 are produced. In addition, x_cut_1 and x_cut_2 are generated for the respective shut-off valves 42 and 46 of fig. 1 as control signals for the respective throttle valve by a predetermined amount. Furthermore, a predetermined volume flow rate Vg1 and Vg2 for the respective pump 2, 4 of fig. 1 is produced.

According to fig. 3, different modes (cases) are illustrated, which can be implemented by the control electronics 48. The respective loads 30 to 34 of fig. 1 are assigned priorities Prio0, prio1, prio2, respectively. The load 34 here has the highest first priority Prio2. The load 32 has a smaller, second priority Prio1 and the load 30 has a smaller, third priority Prio0. In the different modes, a minimum predetermined volume flow (PDemMin) is set for the respective load. Furthermore, a limiting factor is assigned to the respective load 30 to 34. Here, a limiting factor fac_p2 is set for the load 34, a limiting factor fac_p1 is set for the load 32, and a limiting factor fac_p0 is set for the load 30. Furthermore, a predetermined volume flow Q1 to Q3 is predefined for the respective load 30 to 34 (see also fig. 2). In this case, the desired predetermined volumes Q1 to Q3 (q_demprio (i)) are then involved. In different modes, it is then possible to adjust different limiting factors according to fig. 3, which limiting factors are then multiplied by the respective desired volume flow predetermined amounts, wherein the actual volume flow predetermined amounts (q_prio (i)) for the

respective loads

30, 32, 34 then occur, which can be expressed by the following formula:

，

Where i represents the corresponding load and either 0.1 or 2 may be employed for the

load

30, 32 or 34. Thus, a resulting nominal amount is derived from the nominal amount originally requested by the driver multiplied by the corresponding limiting factor.

According to fig. 3, in a mode (case 1) setting is made: the limiting factors are each 1, with which the desired predetermined amounts of volume flow are respectively allocated to the loads 30 to 34, if this is possible.

In another mode (case 2), the limiting factor for

loads

32 and 34 is 1, whereby they are allocated the desired volume flow predetermined amount. A limiting factor of less than 1 is set for load 30, which limiting factor can also be derived from the following equation:

，

where P_avail represents the power available to pumps 2, 4, P_Prio1 represents the power required by load 32, P_Prio2 represents the power required by load 34 and P_Prio0 represents the power required by load 30. In the second module, only a small part of the desired volume flow of the load 30 is thus provided for the load, whereby the limiting factor is smaller than 1. The predetermined volume flow for the load 30 is preferably greater than the minimum predetermined volume flow (PDenMin).

In the other mode, different from the mode (case 2), there is provided: the limiting factor for the second load 32 is 0, whereby only the first load 30 and the third load 34 are used.

In another mode (case 3), a limiting factor of 1 is set for the load 34. The limiting factor for load 30 is less than 1 and can be derived from the following equation:

，

where p_prio0Min is the minimum volume flow preset amount set for the load 30 and p_prio0 is the desired volume flow preset amount for the load 30. The limiting factor for load 32 is less than 1 and then is derived from the following equation:

。

in another mode (case 4) a limiting factor of 1 for the load 34 may be set.

Loads

30 and 32 may have the same limiting factor and/or a limiting factor less than 1, which may be derived from the following equation:

. The predetermined volume flow for the load 30 may then correspond to a minimum predetermined volume flow (PDemMin), while the predetermined volume flow for the load 32 may be above the minimum predetermined volume flow (PDemMin).

In another mode (case 5), the limiting factor for

loads

30 and 32 is 0 and the limiting factor for the third load is less than 1 and can be derived from the following equation:

。

When all the further loads have been completely reduced, the supply of the load 34 with the highest priority is thus reduced. The predetermined volume flow amount for the

respective load

30, 32 may be below a minimum predetermined volume flow amount (PDemMin).

Four graphs are shown in fig. 4. The left two show here the old solution and the right two show the solution according to the invention. The upper graph shows the power available (p_wr) for the pumps 2, 4 of fig. 1 on their ordinate and the time (time) on their abscissa, respectively. In the lower diagram, the volume flow Q is shown on the ordinate and the time (time) is shown on the abscissa. According to the upper left graph, the available power (p_wr_avail) for the pumps 2, 4 of fig. 1 should first rise linearly and then take a constant value. The required power (p_wr_demand) is first below the available power and should then correspond to the available power in a continued time curve. Thus, the required power is limited by the available power. This results from the diagram in the lower left-hand part of fig. 4: the required volume flow (q_demhauptpmp) of the main pump 2 and the required volume flow (q_demsumpmp) of the summation pump 4 cannot be used because the available power (p_wr_avail) is insufficient. The method comprises the following steps: the two pumps 2, 4 are swung back in this type of case (zur uckschwenken). The main pump 2 and the summation pump 4 each deliver a smaller volume flow (q_limhauptpmp, q_limsumpmp) and in particular do not swing out completely. Then there should be a corresponding initial situation with respect to power according to the diagram in the upper right in fig. 4 according to the invention. In contrast, the available power is used according to the lower right diagram in fig. 4 in order to fully use the main pump 2, whereby the required volume flow (q_demhauptpmp) can be delivered via the main pump 2. In contrast, the summation pump 4 swings back significantly farther than in the previous solutions and delivers a correspondingly smaller volume flow. This is very advantageous because the pump is significantly more efficient in the outward swinging condition or in the fully outward swinging condition. Thus, according to the new solution at least one pump is used efficiently, whereas in the old solution both pumps are used inefficiently.

Two additional modes are shown according to fig. 5. In one mode "running inactive", the main pump 2 (Pmp 1) is used for the left-side track drive (left-side track) of the tracked vehicle, and the summation pump 4 (Pmp 2) is used for the right-side track drive (right-side track). The main pump 2 is used for a swing mechanism and a handle of a construction machine using the valve block assembly 1. The accumulator pump is furthermore used for the boom and for the bucket. In contrast, in the other mode (travel activation), there is provided: the summation pump 4 is provided for crawler drives on both sides, while the main pump 2 is used for cantilevers, buckets, slewing gears and levers.

Two additional modes are shown according to fig. 6. In the other mode (with the additional equipment inactive), the main pump is again used for left track drive and the summation pump is used for right track drive. Furthermore, the main pump 2 is provided for a swing mechanism and a handle, and the summation pump is provided for a boom and a bucket. The use of the additional device is not set in this mode. If the add-on device is now in use, it is switched on in another mode (add-on device active). In this case, the main pump 2 is used only for additional equipment, while the summation pump 4 is provided for additional loads.

A valve block assembly is disclosed having a valve block with at least two main slides for controlling a load, respectively. The respective main slide is connected here to two, in particular electrically adjustable hydraulic presses.

Claims

1. Valve block assembly having a valve block with at least two main slides (8, 10, 12) each provided with a load (30, 32, 34) for controlling the hydraulic pressure, wherein a pressure connection (P) and at least one working connection (A, B) are assigned to the respective main slide (8, 10, 12), and wherein two hydraulic presses with an adjustable delivery are provided, which are each connected to the respective pressure connection (P),

wherein a throttle valve (14, 16, 18) is allocated to at least a part of the main slide plate in fluid communication between its pressure connection (P) and one hydraulic machine (2, 4) connected thereto, and a further throttle valve (20, 22, 24) is arranged in fluid communication between its pressure connection (P) and the respective further hydraulic machine (2, 4), wherein the two throttle valves associated with the same pressure connection (P) are located on different flow paths for independently controlling the volume flow of the respective hydraulic machine (2, 4) to the pressure connection (P).

2. Valve block assembly according to claim 1, wherein a bypass flow path (40) is branched in fluid communication between the pressure connection (P) and the hydraulic machine (2), which bypass flow path can be connected to the tank (28) via an adjustable shut-off valve (42) and can be throttled by means of the shut-off valve, and/or wherein a bypass flow path (44) is branched in fluid communication between the pressure connection (P) and the further hydraulic machine (4), which bypass flow path can be connected to the tank (28) via an adjustable shut-off valve (46) and can be throttled by means of the shut-off valve.

3. Valve block assembly according to claim 2, wherein the one hydraulic machine acts as a main pump (2) and the other hydraulic machine acts as an accumulating pump (4) depending on the load.

4. A valve block assembly according to claim 3, wherein a control electronics unit (48) is provided, which has a matching module (58) in which predetermined values (A1, A2, A3) can be input via the input device (50, 52, 54) for the respective load (30, 32, 34), wherein the respective predetermined values (A1, A2, A3) are changed by the matching module (58) to the respective matched predetermined values (b 1, b2, b 3), and/or wherein a control electronics unit or the control electronics unit (48) has a predetermined module (62) in order to convert the respective predetermined values (A1, A2, A3) to predetermined amounts of volume flow (Q1, Q2, Q3) for the respective load (30, 32, 34) and/or to load-sensing information (A1, A2, A3) for the respective load (30, 32, 34) and/or to a maximum pressure (p_max_1, p_2, p_max_3).

5. The valve block assembly of claim 4, wherein the control electronics (48) has a steering module (66) that generates a steering signal based on the converted predetermined amount, wherein the steering signal is configured to: the pump volume flow rate preset quantity (Vg 1, vg 2) for the main pump (2) and the pump volume flow rate preset quantity for the summation pump (4) and/or the total throttle preset quantity (x_cut_2 ) for the stop valves (42, 46) or for the corresponding stop valves (42, 46) and/or the corresponding control quantity (ai, bi) for the corresponding main slide and/or the corresponding control quantity (ci, di) for the corresponding throttle valves (14 to 24).

6. Method for controlling a valve block assembly (1) according to any of the preceding claims 2-5, wherein the feed volume flows for loads (30, 32, 34) that can be delivered by a hydraulic machine (2, 4) can each be distributed to connected loads (30, 32, 34) by actuating the hydraulic machine with an adjustable delivery volume (2, 4) and by actuating an adjustable main slide (8, 10, 12) and by actuating at least one shut-off valve (42, 46).

7. The method according to claim 6, wherein the respective allocation of the transportable supply volume flows for the loads (30, 32, 34) is additionally achieved by actuating adjustable throttles (14 to 24).

8. Method according to claim 6 or 7, wherein the respective load (30 to 34) is assigned a priority, wherein the allocation of the supply volume flow to the load (30, 32, 34) is effected in dependence on the priority.

9. The method of claim 8, wherein a first load (34) has a highest priority, a second load (32) has a lesser priority and a third load (30) has a lesser priority among the at least three loads.

10. Method according to claim 6, wherein a respective predetermined volume flow quantity (Q1 to Q3) for the respective load (30, 32, 34) can be predefined, wherein a respective limiting factor (fac_pi) is assigned to the respective predetermined volume flow quantity (Q1 to Q3), by means of which the respective predetermined volume flow quantity (Q1 to Q3) is reduced in a predetermined manner if required.

11. Method according to claim 10, wherein the control electronics (48) set one mode or a plurality of different modes in which a predetermined limiting factor (fac_pi) for the load (30, 32, 34) is set.

12. The method of claim 11, wherein the mode is selected automatically and/or activatable by an operator.

13. The method according to claim 6, wherein: a hydraulic machine (4) is used when the supply volume flow which can be delivered by the further hydraulic machine (2) is no longer sufficient to cover the volume flow of the load (30, 32, 34) by a predetermined amount.