DE102009033645A1 - Hydraulic control arrangement - Google Patents

Abstract

A hydraulic control arrangement for mobile working machines with several double-acting consumers is disclosed. A first working port of each consumer can be connected to a first hydraulic machine via a directional valve and a common first main line, and a second working port of each consumer can be connected to a second hydraulic machine via a directional valve and a common second main line.

Description

The The invention relates to a hydraulic control arrangement for mobile machines.

at hydraulic control arrangements for multiple consumers There are different approaches.

In the publication EP 0 809 737 B1 is a hydraulic control arrangement for controlling the pressure medium supply of multiple consumers via a variable displacement pump and a main circuit disclosed. The consumers are designed as differential cylinders, wherein each of its pressure chambers is associated with a directional control valve. These directional valves are each designed as 3/3-way valves with closed spring-centered zero position.

adversely At such control arrangements is the device technical effort of the two 3/3-way valves with two actuators each for are provided for each consumer.

The publication DE 10 2007 029 358 A1 shows a control arrangement for a plurality of differential cylinders, wherein also each pressure chamber or working port of each cylinder is associated with a directional control valve. The directional valves are designed as (compared to the above-described prior art) simplified 3/2-way valves and require only one actuator.

there is by appropriate adjustment of the directional control valve in a return line feeding the fluid flowing back possible in a pump line. This can be a volume compensation of the rod volume or a reduction of the other cylinder to be pumped pump volume.

adversely to the hydraulic control arrangements described above is that the energy of the backflowing pressure medium (in particular potential energy from lifted parts of the mobile work machine) can not be regenerated.

the In contrast, the invention is based on the object, a inexpensive hydraulic control arrangement for to create multiple double-acting consumers who have a low Energy consumption.

These Task is solved by a hydraulic control arrangement for mobile machines according to the Features of claim 1.

The inventive hydraulic control arrangement for mobile work machines has several double-acting Consumer. A first work connection of each consumer can over depending on a directional control valve and a common first main line with a first hydraulic machine, and a second working port Each consumer can use one directional valve and over a common second main line with a second hydraulic machine get connected. This allows the energy of a first work connection a consumer back flowing pressure medium (eg, potential energy from being lifted by a lift cylinder Parts of the mobile implement) are regenerated, in which the pressure medium to one over the first main line connected first working connection of another to be supplied Consumer is encouraged. This can reduce the performance of the connected to the first main line and operated as a pump first hydraulic machine can be reduced and energy saved.

Further advantageous embodiments of the invention are in the dependent Claims described.

A Particularly preferred embodiment of the invention hydraulic control assembly has a summing valve connected to the connected to both main lines, and about the two Main lines can be interconnected. In order to can the energy of back flowing pressure medium one consumer for both directions of movement of the other Consumer be used. If the work connection with the back flowing pressure medium not directly via a main line with the working connection of the other consumer to be supplied is connected, the regeneration of energy is carried out according to this development the opened summing valve and over the other Main line.

alternative or in addition to the connecting line with summation valve it is of particular advantage if both hydraulic machines have a Wave are connected to each other, and each as a pump or as Motor can be operated. If from one to the first Main line connected working port pressure medium back flows can be operated as a pump second hydraulic machine via powered as a motor first hydraulic machine powered by renewable energy become.

there it is preferred if the shaft with an internal combustion engine, z. B. a diesel engine connected. So that can Consumers even without the regenerative invention Operation be supplied with pressure medium.

In a preferred embodiment, the summation valve is a 2/2-way valve, are separated by the spring in a basic position, the two main lines, and over in a Switching position, the two main lines are interconnected. Both connections of each consumer can be connected via the associated directional valve with a tank. As a result, a full-load operation of each consumer is possible, is waived in the regeneration, and in which the back flowing pressure medium can flow almost without resistance to the tank.

Preferably The two hydraulic machines are each electrically over a proportional solenoid adjustable adjustment. In order to The machines can be demand-oriented in engine operation (in particular depending on the highest consumer) Taxes.

at an embodiment of the invention Control arrangement, each directional valve is a continuously adjustable 3/3-way valve, of the associated in a spring-centered basic position Work connection is shut off, and about that in switch positions the assigned working connection either with one of the two main lines or connected to the tank.

at another embodiment of the invention Control arrangement, each directional control valve is a continuously adjustable 3/2-way valve, over the in a spring-biased basic position of the assigned work connection connected to the tank, and about that in switch positions the assigned working connection with one of the two main lines connected is.

Around a lead of the consumer (eg when lowering a lifting cylinder) without preventing regeneration is in a respective work line arranged between the working port and directional valve a lowering brake valve.

there It is preferred if each lowering brake valve is a continuously adjustable 2/2-way valve is over that in a spring-biased Basic position, the directional control valve with the working port on a from the directional valve to the pressure chamber opening check valve is connected, and about that in switching positions of the working connection connected to the directional control valve. Each lowering brake valve is over one Control line with the other working line of the same Connected consumer, and a pressure in the control line acted upon a valve body of the lowering brake valve in the direction of its switching positions. Thus, a lead of the consumer is effectively prevented, wherein each lowering brake valve with increasing pressure in the other working line of the same consumer opens, so that in the lowering brake valve converted power loss is minimized.

At Each consumer-side work line section can with a pressure limiting line be connected to a pressure relief valve, the consumer side Working line section relieved to the tank.

A preferred development of the invention Control arrangement has a microcontroller, which is connected to the two Main lines arranged pressure sensors and with the proportional magnets the adjustment units is connected. This allows the swivel angle the adjustment units depending on the in the respective Main measured pressure.

The Consumers may use differential or synchronous cylinders be, whose first pressure chamber with the first working port and whose second pressure chamber is connected to the second working port are.

The Mobile work machine can be an excavator, wheel loader or backhoe loader be.

in the Below are various embodiments with reference to the figures the invention described in detail. Show it:

1 a first embodiment of a hydraulic control arrangement according to the invention; and

2 A second embodiment of a hydraulic control arrangement according to the invention.

1 shows a first embodiment of a hydraulic control arrangement of an excavator according to the invention. The control arrangement serves to supply a plurality of consumers, of which in the 1 exemplified two differential cylinders 1 . 2 are shown. The differential cylinder 1 serves to raise or lower an excavator arm (not shown) during the differential cylinder 2 for extending and retracting a (not shown) bucket serves. The differential cylinder 1 has a first floor-side work connection 4 and a second annular space working port 6 wherein pressurization of the floor space causes lifting of the excavator arm. The differential cylinder 2 has a first working connection on the annular space side 8th and on the floor side a second working connection 10 , wherein pressurization of the floor space causes an extension of the bucket.

Every work connection 4 . 6 . 8th . 10 is about a work line 14 . 16 . 18 . 20 to a 3/3-way valve 24 . 26 . 28 . 30 connected. These are each via a tank connection T and a tank line 34 . 36 . 38 . 40 to a tank 41 joined.

Furthermore, the two way valves 24 . 28 each via a port P to a first main line 42 connected while the two way valves 26 . 30 each to a second main line 44 are connected.

The first main line 42 is to a hydraulic machine 46 connected, which can be operated as a pump and as a motor, while the second main line 44 to a pump 48 connected. The two machines 46 . 48 are designed as tandem machines and a common shaft 50 with a diesel engine 52 connected to the excavator.

At every main line 42 . 44 is a pressure sensor 54 . 56 arranged, and the two main lines 42 . 44 are via a summing valve 58 connected with each other.

Every 3/3-way valve 24 . 26 . 28 . 30 is always adjustable. It locks in one (in 1 shown) spring-centered basic position the respective working line 14 . 16 . 18 . 20 , the respective tank line 34 . 36 . 38 . 40 and the respective connection to one of the main lines 42 . 44 from. Each directional valve 24 . 26 . 28 . 30 has two actuators that attach a valve body to each directional valve 24 . 26 . 28 . 30 in one of the switching positions a, b can move. In this case, those switching positions are marked with a, in which the respective working line 14 . 16 . 18 . 20 over the respective tank line 34 . 36 . 38 . 40 with the tank 41 is connected, while b those switching positions are marked, in which the first working lines 14 . 18 with the first main line 42 or the second working lines 16 . 20 with the second main line 44 are connected.

The summing valve 58 is designed as a 2/2-way valve, which in its spring-biased basic position, the two main lines 42 . 44 separates it, while it energizes its actuator in the switching position marked with a the two main lines 42 . 44 connects with each other.

Furthermore, the control arrangement according to the invention has a (not shown) microcontroller, via electrical lines with the pressure sensors 54 . 56 , with each two actuators of the directional control valves 24 . 26 . 28 . 30 . 58 and with the adjusting devices of the hydraulic machines 46 . 48 connected is.

In the following, the function of the hydraulic control arrangement according to the invention according to 1 explained.

Target via the differential cylinder 1 the arm of the excavator will be raised, so will the directional control valve 24 in one of the switching positions marked b and the directional control valve 26 adjusted to one of the switching positions marked with a. Thus, over that of the diesel engine 52 driven and operated as a pump hydraulic machine 46 , about the first main line 42 and about the work management 14 the bottom-side pressure chamber of the differential cylinder 1 filled with pressure medium. This flows out of the annulus of the cylinder 1 displaced pressure medium via the working line 16 and the tank line 36 to the tank 41 from.

If additionally and simultaneously the bucket (not shown) of the excavator over the cylinder 2 extended and corresponding to the bottom pressure chamber of the differential cylinder 2 is to be supplied with pressure medium, via the (not shown) microcontroller, the pivot angle of the pump 48 increased, causing the corresponding pressure chamber of the cylinder 2 via the directional valve 30 and the work management 20 is supplied.

To lower the excavator arm is the conventional way in which the bottom-side pressure chamber of the cylinder 1 via the directional valve 24 , which is switched to one of the switch positions marked a, to the tank 41 is relieved.

Or the directional valve 24 remains in one of the switch positions marked b. In this case, the pressure medium of the bottom-side pressure chamber of the cylinder 1 by the weight of the excavator arm in the first main line 42 displaced, resulting in the following inventive possibilities of regenerative use of the energy of the pressure medium:
If at the same time the blade over a supply of the annulus of the differential cylinder 2 can be retracted or folded, the directional control valve 28 be placed in one of the positions indicated by b, whereby the regenerative pressure medium to be used via the first main line 42 and the work management 18 to the annulus of the cylinder 2 flow and so at least can support the desired movement.

If, however, the blade via a supply of the bottom-side pressure chamber of the differential cylinder 2 is to be retracted or closed, the directional control valve 30 in one of the positions marked b and the summation valve 58 placed in the switching position marked a. As a result, the regenerative pressure to be used flows through the main line 42 and the summation valve 58 in the second main line 44 , From there, the pressure medium flows either alone or in addition to that of the pump 48 conveyed pressure medium via the working line 20 to the floor space of the differential cylinder 2 ,

In a third variant of the regenerative use of the bottom space of the differential cylinder 1 displaced pressure medium, the summation valve 58 remain in the shut-off position, and the pressure medium flows through the first main line 42 to the hydraulic machine used as the engine 46 , Thus, the drive of the pump 48 over the wave 50 supported and the diesel engine 52 relieved. The diesel engine 52 can also be completely dispensable, with only the hydraulic machine 46 the pump 48 drives.

2 shows a second embodiment of the hydraulic control arrangements according to the invention, wherein the essential differences of the second embodiment compared to the first embodiment will be explained below.

Instead of the 3/3-way valves in the second embodiment 3/2-way valves 124 . 126 . 128 . 130 intended. It is in a spring-loaded basic position each work line section 14b . 16b . 18b . 20b with the respective tank line 34 . 36 . 38 . 40 connected, while in switching positions a, the two first working line sections 14b . 18b with the first main line 42 and the two second working line sections 16b . 20b with the second main line 44 are connected. It thus accounts for simplified valves, the respective shut-off positions, one spring and one actuator.

Furthermore, in every working line 14a . 14b . 16a . 16b . 18a . 18b . 20a . 20b a lowering brake valve 134 . 136 . 138 . 140 arranged. These are designed as 2/2-way valves with a continuously adjustable valve body. In an initial position biased by an adjustable spring, a non-return function is provided, which is a flow direction from the respective working port 4 . 6 . 8th . 10 to the directional valve 124 . 126 . 128 . 130 shut off and thus supports a load leak-free. The valve body of each lowering brake valve 134 . 136 . 138 . 140 is acted upon in the opening direction (positions a) by a control pressure, which at the other working line 14b . 16b . 18b . 20b of the same differential cylinder 1 . 2 is tapped. There is a corresponding control line 134a . 136a . 138a . 140a to the respective work line section 14b . 16b . 18b . 20b connected to the respective directional control valve 124 . 126 . 128 . 130 with the respective lowering brake valve 134 . 136 . 138 . 140 combines.

Each work line section 14a . 16a . 18a . 20a is via a pressure limiting line 144 . 146 . 148 . 150 and via a pressure relief valve 154 . 156 . 158 . 160 relieved, wherein the response pressure is adjustable via a spring. When the respective pressure relief valve responds 154 . 156 . 158 . 160 the pressure medium flows to the respective tank line 34 . 36 . 38 . 40 ,

As continues in 2 are shown, the spring chambers of the adjustable springs of the lowering brake valves 134 . 136 . 138 . 140 and the springs of the directional control valves 124 . 126 . 128 . 130 with the respective tank line 34 . 36 . 38 . 40 connected or vented to the atmosphere.

The pressure limiting lines 144 . 146 . 148 . 150 with the pressure relief valves 154 . 156 . 158 . 160 can also according to the first embodiment 1 on the work lines 14 . 16 . 18 . 20 be provided.

The lowering brake valves 134 . 136 . 138 . 140 can also according to the first embodiment 1 in the working pipes 14 . 16 . 18 . 20 be provided.

deviant Of the embodiments shown, the inventive Control arrangement also have more than 2 consumers. The consumers can also use synchronized cylinders or hydrostatic motors be. Thus, the regeneratively used consumer z. B. a slewing motor be, the pressure medium at the completion of a rotary motion of the upper carriage in the hydraulic control arrangement according to the invention promotes.

Notwithstanding the embodiments shown, the pump 48 also be designed as a hydraulic machine, which can also be operated as a motor.

The Regeneration of the energy of the invention back flowing pressure medium can only be done if the pressure in the corresponding consumer z. B. by the load the excavator arm or by braking the rotating superstructure is higher than in the consumer, which supplied the pressure medium shall be.

Disclosed is a hydraulic control arrangement for mobile work machines with several double-acting consumers. A first work connection Each consumer can use one directional valve and over a common first main line with a first hydraulic machine can be connected, and a second working connection of each consumer can over one directional control valve and a common second main line be connected to a second hydraulic machine.

LIST OF REFERENCE NUMBERS

1, 2

differential cylinders

4, 6, 8, 10

working port

14 16, 18, 20

working line

24 26, 28, 30

3/3-way valve

34 36, 38, 40

tank line

41

tank

42

first main

44

second main

46

first hydromachine

48

pump

50

wave

52

diesel engine

54 56

pressure sensor

58

summing

124 126, 128, 130

3/2-way valve

14a, 14b, 18a, 18b

Working line section

16a, 16b, 20a, 20b

Working line section

134 136, 138, 140

lowering valve

134a, 136a, 138a, 140a

control line

144 146, 148, 150

Pressure relief line

154 156, 158, 160

Pressure relief valve

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• EP 0809737 B1 [0003]
• - DE 102007029358 A1 [0005]

Claims (16)

Hydraulic control arrangement for a mobile work machine with several double-acting consumers ( 1 . 2 ), with a first working connection ( 4 . 8th ) of each consumer ( 1 . 2 ) via a directional control valve ( 24 . 28 ; 124 ; 128 ) and a common first main line ( 42 ) with a first hydraulic machine ( 46 ), and wherein a second working connection ( 6 . 10 ) of each consumer ( 1 . 2 ) via a directional control valve ( 26 . 30 ; 126 ; 130 ) and a common second main line ( 44 ) with a second hydraulic machine ( 48 ) is connectable. Hydraulic control arrangement according to claim 1, with a summing valve ( 58 ) connected to the two main lines ( 42 . 44 ) and via which the two main lines ( 42 . 44 ) are connectable to each other. Hydraulic control arrangement according to claim 1 or 2, wherein the two hydraulic machines ( 46 . 48 ) over a wave ( 50 ) are connected to each other, and each operable as a motor and as a pump. Hydraulic control arrangement according to claim 3, wherein the shaft ( 50 ) with an internal combustion engine ( 52 ) connected is. Hydraulic control arrangement according to one of the claims 2 to 4, wherein the summing valve ( 58 ) a 2/2-way valve ( 58 ) is, by the spring-loaded in a basic position, the two main lines ( 42 . 44 ) are separated, and on the in a switching position (a) the two main lines ( 42 . 44 ) are interconnected. Hydraulic control arrangement according to one of the preceding claims, wherein both connections ( 4 . 6 . 8th . 10 ) of each consumer ( 1 . 2 ) via the associated directional control valve ( 24 . 26 . 28 . 30 ; 124 . 126 . 128 . 130 ) with a tank ( 41 ) are connectable. Hydraulic control arrangement according to one of claims 3 to 6, wherein both hydraulic machines ( 46 . 48 ) each electrically via a proportional solenoid adjustable adjusting units ( 46 . 48 ) are. Hydraulic control arrangement according to claim 6 or 7, wherein each directional control valve ( 24 . 26 . 28 . 30 ) a continuously adjustable 3/3-way valve ( 24 . 26 . 28 . 30 ) of which, in a spring-centered basic position, the associated working connection ( 4 . 6 . 8th . 10 ) is shut off, and via the in switching positions (a, b) of the associated working connection ( 4 . 6 . 8th . 10 ) either with one of the two main lines ( 42 . 44 ) or with the tank ( 41 ) connected is. Hydraulic control arrangement according to claim 6 or 7, wherein each directional control valve ( 124 . 126 . 128 . 130 ) a continuously adjustable 3/2-way valve ( 124 . 126 . 128 . 130 ) is, in the spring-loaded basic position of the associated work connection ( 4 . 6 . 8th . 10 ) with the tank ( 41 ) and, via the switching port (a), the associated working port ( 4 . 6 . 8th . 10 ) with one of the two main lines ( 42 . 44 ) connected is. Hydraulic control arrangement according to claim 9, wherein in a respective working line ( 14a . 14b . 16a . 16b . 18a . 18b . 20a . 20b ) between work connection ( 4 . 6 . 8th . 10 ) and directional control valve ( 124 . 126 . 128 . 130 ) a lowering brake valve ( 134 . 136 . 138 . 140 ) is arranged. Hydraulic control arrangement according to claim 10, wherein each lowering brake valve ( 134 . 136 . 138 . 140 ) a continuously adjustable 3/2-way valve ( 134 . 136 . 138 . 140 ) is, via the in a spring-biased home position the directional control valve ( 124 . 126 . 128 . 130 ) with the working connection ( 4 . 6 . 8th . 10 ) via a from the directional control valve ( 124 . 126 . 128 . 130 ) to the work connection ( 4 . 6 . 8th . 10 ) opening check valve is connected, and via the in switching positions (a) of the working port ( 4 . 6 . 8th . 10 ) with the directional control valve ( 124 . 126 . 128 . 130 ) connected is. Hydraulic control arrangement according to claim 11, wherein each lowering brake valve ( 134 . 136 . 138 . 140 ) via a control line ( 134a . 136a . 138a . 140a ) with the other working line ( 14b . 16b . 18b . 20b ) of the same consumer ( 1 . 2 ), wherein a pressure in the control line a valve body of the lowering brake valve ( 134 . 136 . 138 . 140 ) in the direction of its switching positions (a) acted upon. Hydraulic control arrangement according to one of the claims 10 to 12, wherein at each consumer-side working line section ( 14a . 16a . 18a . 20a ) a pressure limiting line ( 144 . 146 . 148 . 150 ) with a pressure relief valve ( 154 . 156 . 158 . 160 ) connected by the consumer-side work line section ( 14a . 16a . 18a . 20a ) to the tank ( 41 ) relieved. Hydraulic control arrangement according to one of the claims 7 to 13 with a microcontroller connected to the two main lines ( 42 . 44 ) arranged pressure sensors ( 54 . 56 ) and with the proportional solenoids of the adjusting units ( 46 . 48 ) connected is. Hydraulic control arrangement according to one of the preceding claims, wherein the consumers ( 1 . 2 ) Differential cylinder ( 1 . 2 ) or Gleichgangzylinder are whose first pressure chamber with the first working port ( 4 . 8th ) and the second one Pressure chamber with the second working connection ( 6 . 10 ) are connected. Hydraulic control arrangement according to one of the preceding Claims, wherein the mobile working machine is an excavator, Wheel loader or backhoe loader is.

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