DE3428403A1 - Two stage, pressure-compensated hydraulic control device for at least two consuming units - Google Patents

Abstract

The invention relates to two-stage, pressure-compensated hydraulic control devices, which function independently of the load, and which feed a plurality of consuming units from one source - a pump. Each consuming unit has a proportional way valve, which is designed as a two-stage flow booster which comprises a control element and an booster stage. The control stage may be designed as a slide displaceable in a valve body, which slide is displaced in the valve body, with primary and secondary profiles which together form flow boosters and are arranged on the one sides of the consuming ducts, and brake profiles which are arranged on the other sides of the consuming ducts. The control device may be constructed as a control member and perform the function of the proportional way valves or be equipped with metering units and perform the function of servomechanisms. The control device according to the invention enables the hydraulic systems on many mobile machines to be simplified and the costs reduced. <IMAGE>

Description

PATENT AND LAWYERS

PATENTANWÄLTE DIPL.-ING. W. EITLE DR. RER. NAT. K. HOFFMANN - DIPU-ING. W. LEHN

D1PL.-ING. K. FDCHSLE. DR. RER. NAT. B, HANSEN DR. RER. NAT. H -A. BRAUNS ■ DIPL.-ING. K. GDRQ

DIPL-INQ. K. KOHLMANN · LAWYER A. NETTE

40 646

Zvody tözkaho etrojirenstvi

Vyzkumny uetav etavebnich a zöinnieh strojö, Brno (5SSR)

Two-stage, pressure compensated hydraulic control units

direction for at least two consumers

The invention relates to two-stage pressure compensated hydraulic load-independent control devices, directional control valves and servomechanisms, the several Consumers - hydraulic motors uus one source - a hydrogen generator Food.

Many directional control valves of this type are known. A device according to the US Patent 35 26 247 has for each consumer - hydraulic motor - one-way valve _t ei "ne control section that ausaer pressure actuated one a regulator of pressure difference for rhaltung the constant supply pressure and in the Zuflussektion a" spool valve has pressure valve "to Lastabnahroe , ie to decrease the pressure from each connected consumer rather - hydraulic motor - it has in the "grains, preferably in the control slide" or in both, various recesses, annular grooves and channels, which it represents large and complicated in comparison to other directional control valves "As a result With increasing pressures and flow rates of the directional control valves, the necessary adjusting forces and thus also the costs of the electrical, electronic and hydraulic adjusting devices increase significantly. The listed control devices as well as other known control devices allow you

not to control the Flussigkeitsablauf out of the drain branch of the hydraulic motor so that they control the movement of consumers - hydraulic motors, which are negatively charged, with a load tung acts in the direction of movement, do not allow. That is why they have to be supplemented with additional brake valves for this purpose, which further complicate the entire hydraulic system and make it more expensive.

Other gate valves other than the subject matter of the invention are also known, e.g. 35 61 488, with two-stage control, »o a control slide or a system nozzle-flap as the first stage serves, and the current amplifier forms the second stage.

These slide valves are designed to control a hydraulic motor from a constant pressure source, and do not allow the simultaneous supply of several hydraulic aerators, or the supply pressure after the load To compensate each individual consumer individually, also do not allow the pressure of the hydrogen generator the maximum pressure of the utterly burdened consumer adapt or relieve the pressure on the hydrogenerator,

when no consumer is working »The listed control valves do not allow the flow of liquid to be controlled from the hydraulic motors, which are negatively loaded.

With various facilities and machines, such as in machine tools, Steassenbau - u * earthmoving machines, Airplanes and ships come hydraulic Consumers who have different demands on the control «E.g. for excavators and sheepskin loaders

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ait wheels it is on the one hand the control of the boom ait the shovel and on the other hand the control of the direction of travel, or z. B, in aircraft, on the one hand, the control of the position of the undercarriage (pushed in - pushed out), and on the other hand, the control of the direction and altitude controls. In the first, less demanding group control valves are usually without recirculation, in the second / ispruchsvolleren group © be eistens Servonotore used with Ruckfuhrung "Though r in the group a & instruction dispatcher a series gegenwartiger hydraulic control devices is known, for example * to US PS 35 26 2:47 , DE OS 25 14 624, DE OS 23 04 334 and others, and in the öer group of hydraulic servo mechanisms, for example according to DE OS 27 23 490, DE OS 27 38 453, DE OS 28 32 847, the CSSR patent application 2969-83 none of the known devices, the demands on the control of both groups of consumers oer o- Rait a more uniform less control means to si. Ehern »As a result, different consumers or consumer groups have separate, independent control devices, often with independent source hydraulic generators.

The invention is based on the object of a hydraulic To create a control device for several consumers with all functions: current direction, stroo amplification and Lestbreasen with a simple, operational reliable facility secured with small outlets are.

/ 10

The stated disadvantages are eliminated by a device
according to the invention, which is common to every consumer
Has spool valve j, as a two-stage
pressure-compensated hydraulic control device
is designed, which is a two-stage pressure booster
which contains a control member and an amplifier stage. Both are connected to the inlet channel behind the regulator of the pressure difference, which is lined up between the Puapenkanal and the inflow consumption channel of the consumer. The amplifier stage may be used as a slide valve, in the de ta body of Schieberven · TILs is displaceable be formed Tait primary profiles associated with the control channels on the one hand it © aar control stage, on the other hand, by junctions with the

Control rooms are connected ^ with secondary profiles that are connected to the inlet channel and with braking profiles that are connected to the AfcJasskanal * the primary and secondary profiles are arranged in pairs that form power amplifiers on one side of the consumption channels, * on the other sides Bress profiles are arranged in the consumption channels. The current amplifiers can be combined with the command control elements, which are designed as 4/3 directional valves, and also with control stages designed as a rotary dosing unit, so that the control devices are either proportional valves or servo mechanisms can be used.

In the control device according to the invention, relatively small control levels can also be used for large flow rates, which only require small adjustment devices, which in particular in the case of _L remote, - hydraulic, electrical, electronic / controls brings further savings.

The subject of the invention is shown statically in the accompanying drawings »It shows:

Fig. 1 a Sch8Bö the ! Alternative of the principle of the invention - a two-stage, Druckkonpen. . eierte hydraulic control device, the

a proportional directional control valve for every consumer which is designed as a two-stage power amplifier /

TO Fig. 2 is a diagram of a 2nd alternative of the invention -

training principles, ait a load signaling off the control stage and nit a rule output tape, Fig. 2a a scheme of a partial alternative of the Invention principles with load signaling from the control channels by means of an alternating

valves,

Fig. 3 shows a construction of the first alternative aer invention of FIG. I ₁

Fig. 4 shows a construction of the second alternative of the invention of Fig. 2,

Fig. 5 is a diagram of the dependence of the current in

the consumers in relation to the tax deflection of the actuating organee,

Figure 6 shows a two-stage pressure-co-operated hydraulic Control device in which the actuator

gan are at least one control device Rorationsdosieinheit is used as a dosing unit tait a control slide is formed,

Fig. 7 shows an alternative embodiment of the actuator

ganes, which each form a dosing unit

is «which is connected to the inlet channel by means of two check valves _k

EPO CX) PY

jsr ·. ■. .. · :. Al ■ - '■ ":'

The two-stage, pressure-compensated hydraulic control device according to FIG. 1 of the invention is fed by a pump I ^ from the container Z via a common pump channel CJ ait branch 4, 1 04 to the proportional directional control valves ji, 105 of the consumers 65, 106 . Further branches 204 , 304 ,, ... to further propoftional directional control valves 205 , 305 .... aer further consumers 20 6, 306 ... The first consumer Jj is called a straight hydraulic motor

• 10 (hydraulic cylinder) shown, the second consumer as a rotary hydraulic motor. The consumer jB is with the proportional directional valve j> via two consumption & channels 7. » X * connected. Likewise aer consumers about the consumption kanale with his ProportionatWegeventil 105 "J5 * connected 106 107th 107th Oie proportional - way valves J | 105 1 10 * H) with regulators of pressure difference JL2, 112 are two Verstarkerstufen J ₁ O is formed. Since the proportional directional control valves j5, 105 or others to -. Sanmenfallend are formed, and the pilot valve Ji and the regulator oer pressure difference JL2 are designed to coincide in the system, only the proportional directional control valve J3 ßit the consumer J5 and the other members of the 1st circuit will be described. The pilot valve Q ₁ and the amplifier stage I ₁ O are connected to the inlet channel JLl in the ötrora direction behind deo regulator of the pressure difference JL2, which is connected to the pump channel j3 via branch 4. The pilot valve 9, which is shown in Fig. 1 as a Vlerweg -The three-position directional valve with .% Mechanical adjusting device is shown via its inlet L3 with the inlet s-

Channel 11 connected via branch 11 ′ a pair of control profiles e 14 , 14 of variable average - are now the control channels n 15 , 15 * with the profile profiles 24 . 24 * of the amplifier stage IQ connected and the flow 17 is • 35 with the flow branch 19 via the branch 18

Copy

connected · The pilot valve j9 can also be equipped with an ei-ηθφ other instead of the mechanical, for example an electromagnetic with propoetrionalEiagneten, an electrohydraulic, pnetmatic, etc. adjusting device. The amplifier stage 2Ό, which as a proportional -6/3. W.ßgventil J5 is shown comprises: the inlet channel 21 connected to a pair of Sökundarpro files, 23 ,, 23 * variable average άεί; (energy flow channels 23, 25 _'9 to the brake profiles 26, ^' variable-section are connected / a pair consumption channels 27, 27 _t which are connected via the consumption channels 7, 7? oit dero consumer 6 [a pair Betatigungsraurae ^ i, 3JL * o with centering springs 3_2 _# 32 *. Which are connected to the control channels 15, la ' via branches 2t3, 2J3 * and a pair of signal channels 34, 34 * _t that signal the load that is close to the consumption channels 27, 27 * hours The secondary profiles £ 3, 23 * and and the primary profiles 24 ₁ 2A * are arranged in pairs 23, 2A ^ and 23 *, 24 'which form the current amplifiers J22, 22 * . The current amplifiers 22, 22 * are connected to the one Sides of the consumption channels 27. · JZ * arranged, the gap profiles 26, 26 * on the other sides. In the branches 33 , 33 * of the control channels 15, jLS 'can be arranged a drop valve η j35 * and, if necessary, in parallel with them also check valves 36, .3 $ *. The orifice plates j35, 35 * o ± t the check valves ^, 3_6 * can be arranged directly in the control channels 15, Jj5 *. In this case it is necessary to dimension the check valves 3_5, ^ 6 * a little larger,
30th

The regulator of the pressure difference 2; 2 has the spring actuating space ^ 39 is connected to Ferier 40 via the control channel £ l bit de "shuttle valve 4J2 nit two signal channels 34, * connected to 34, and ate opposite Steuercaum 43 to the inlet channel jll via the branch 44th The regulator of the pressure difference maintains a certain pressure difference between the inlet channel 11 and the branch 11 _{and the 2H fuel} consumption channel

^ POCOPY

T ^ or "V upright, after sealing of the Veretellens the amplifier stage JLO. The pressure difference is determined van der Anfangsvorspannung and the steepness of the spring force aer spring 40. This can m§n the desired From hangigkeit Oer pressure difference in relation to the flow through the regulator aer pressure difference ^ 12, from the almost constant pressure difference to a pressure difference that (expressly) decreases with the flow rate » A throttle orifice AS can be installed in the control channel 41 and a throttle orifice 4_6 in the branch 44. The proportional directional valve 10 5 of the consumer chers 106, as well as that proportional Wegeverctil J5 of the load is carried out J3, has in the control channel 141 to the pressure prevailing in the feed consumption passage 107 or 107 ', and oer in the spring actuation chamber 139 of the regulator the pressure differential 112 acts · parallel to .Pump channel, 3, the pressure valve 47 is connected, which the spring actuation space » AB with spring 49

signal "" "" "

with the outlet channel JSO · connects and the opposite -

The remaining operating space JiI via branch J52 with

dera for urapenkanal j3 connects. The exit signal channel

J50 is connected to the control channels 41 , 141 of the adjacent proportional Vifege valves J5 via the shuttle valve 53. A small pilot pressure valve 54 must also be connected in parallel to the spring actuation space 8, which limits the value of the pressure ie the spring actuation space 8, and thus also in the pump channel 3 If a pilot pressure valve 4 is needed, it is useful to install a throttle orifice J55 in the outlet duct. When both consumers JS are working, the pressure signals from both consumers come via the control channels 4JL, 141 to the changeover valve 53, which is automatically blocked in such a way that it does.

SPOOQPY

High pressure signal through the outlet bar 50 to the pressure valve 47. This sets itself up so that the superfluous flow from the point bar J3 is transferred into the container 2 , at a slightly higher pressure than the pressure in the most heavily loaded consumer Q or 106 .

An alternative version of the two-stage, pressure-compensated hydraulic dam device according to Fig. 2 differs from the embodiment according to Fig. 1 as follows:

A regulating pump 201 with an adjusting device 5 7 , which is connected to the outlet channel J50, is used

- The control channel 4JL is not old connected to the signal channels 34 , J4 * of the amplifier stage JLO, but to the signal channel 116 of the pilot valve S ». The signal channel JL6 is connected in the middle position 0 with data flow, 17, and in the working positions R, L with the inflow control channel V5 or 2 ^ 5 'behind the control profile JL4 oö & r l £ i

On the partial Ecbenatlian figure Fig.2a 1st des; Shuttle valve j> 9 shown, which enaoglicht the gain of the load signal from the control channels 15, 3 ^ * of the pre- control valve 9 "Although in both cases the load signal of the consumer £ is obtained indirectly, its value is clearly determined so that it can be used to control the Regulator of the ^ pressure difference JL2 as well as of the whole proportional - '^ egeventlies yes,

3 shows the construction of the proportional directional control valve j5 or 105 in the embodiment 30 5 according to FIG.

EPOCOPY

: 3A28403

shown schematically in section “The reference numbers of the same functional parts have been retained or increased by 300 due to the differentiation. Tnögli- from many, chen the functions equivalent arrangements dee proportional here - 5_-way valve with the arrangement of the channels sycetrischen 2JL, 27, * 25 and * 27 illustrated 25th The amplifier stage lp_ is designed as a slide 551 , which is slidable in the body 362 and has round recesses 311 that adjoin the inlet ducts JLL and 21 and are functionally identical to them, furthermore round recesses 325 , 325 * that adjoin the Connect drainage channels 2JS, 25 * and they are functionally identical and have round recesses 327 * 327 *. which are connected to the consumption ducts 27, 27_ * and are functionally identical to them. The slide is centered on both sides by centering springs 3 £, £ 2 * . The ends of the slide 361 are covered with covers 363 «363 * which close the actuation spaces 3jL, 3_l /. The primary profile © 24, 24 *, the auegef as an oblique local recesses dor surface of the slider 361 and are leads are permanently connected to the pilot valve 9, the upper control channels 15 "1 5 * The connected. Sekundä'rprofille 23, 23 *, which are designed as oblique local recesses on the surface daa slider 561 are permanently dera inlet duct 1I ₁ and is identical to this circular recess 311 is connected sit. The braking profiles 26_, 26 * »which are designed as conical beveled collars of the slide 361, which are arranged on the outside of the consumption channels 27, 27 *, are permanently connected to the drainage channels 25, 25 * * on the surface of the slide 361 in Close to the consumption ducts 27, 27_ *, local recesses 334 , 534 ^ are provided (in section A - A), which are connected on the one hand above slgnalkanSle 34, 34 * in slide 361 «with the actuation areas 3I _{1 1} 31 *, on the other hand by means of the control codes & le

COPy

> r

341 341 * and salt cover valve 42 and the control channel 41 are connected to the spring actuation mechanism 39_ of the regulator of the pressure difference. In the control channel 41 to an orifice 45 can be located "The slider 361 suird gsgan d i radially guided body 362 so that it can not come to its rotation. This can easily be done with the help of a pen (not shown) or some other element. The main component of the regulator of the pressure difference 12 is a hollow slide 365 "with a longitudinal bore 366, the radial openings 367 and 311 . that of the spring 40 in the right-open position. is pressed · The longitudinal bore 366 of the slide 365 is permanently connected to the branch 4 of the Puopenkanals 3_ via the radial openings 567 * The round recesses 311 «» earth when the slide is moved to the left - against the spring 40 - half closed to fully closed; so that they control the flow of de "Punpenksnal 3 ^ in ά & η inlet channel in July and datnit the pressure in Eintrittekenal JLjL * The size of the pressure difference is ß> it the regulation screw 364 adjustable. The pilot valve 9 is al © one VierwegerBreipoeitionswegeventil ausgeföhrt * dae of a body 368 old moved © ^ slider 369 with two collars and 371 is "centered with Z <? Mtrierfedern 370th 370 *" Io body 368 are rum recess! "? 313 . 315. 315 * and 317, 317 "are provided. The circular recess 3 1 3 is functionally identical to the inlet u & r control members 13 en and let rait inta, the circular recesses 315 connect to the control channels & l @ 15, 15 * and are functionally identical to them and the circular recesses 317 . 317 * sen sch lies at the outlet 17 and are with him functionally identical · The inner sides aer collars 371 dee slider 369 are cut obliquely, thus forming control profile 32.4. 314 ". Which is continuously

42 :: Ί ^: ': -

ren Sintrittsrundaussparung 313 of the inlet 23 of the control links are connected "The outer sides of the collars 371, 571 * of the slider 369 in the Kittel position, which is not shown, connect the SteuerkanSie, 15th, 15th, * means of Ruixtaussparungen 317th 317 "with dec. Drain V7. Between the control channels 3L5., 15, * a shuttle valve 5Ώ can be arranged, see Fig. 2a and its description«

On Fig. 4 iet schematically in section. the proportional directional valve, 5 of the amplifier stage 10 shown, "with asymmetrical arrangement of the channels 11, 27, 27 * and 25 (the drainage channels 25 and 25 / of FIG. 3 merge into one another in FIG. 4 into a channel 25, which enables a very compact construction with a minimal number of simple channels and thus also with extremely small structural dimensions). The VerstSrkerstufe 10 is thus formed of a slider 461 in the body 462, which is provided with Rundausaparungen 4JUL, 427, 427 and 4 * 25th The circular recess 411 adjoins the inlet channel 11 / with which it is functionally identical, the circular recesses 427 and 427 adjoin the consumption channel 27, 27, * with which they are functionally identical, and the round recess -425 connects to the outlet channel j | 5, bit that is functionally identical. The bias of the centering springs 32_, 32. ' is by means of regulating screws 475 . 475 * adjustable in the Geckein 453 , 463 *. The inlet channel is designed as a channel 11 in the body 462 , which connects to the circular recess 411 and is continued by "other" circular recesses 411 * and further "it the opening 411 ** in the slide 461. The prinar profiles 24, 24 *. all of the inclined local recesses on the surface of the slide 461 . on the outside of the consumption canals 27, 27 * _f are permanently suit

ψ copy

the control channels 33, 15, * connected. The secondary profiles 423 , 423 * are designed as radial or inclined recesses, which are guided from the longitudinal opening 411 ** to the surface of the slide 4SI also on the outside of the consumption ducts 27_, 27 * »The Braras profiles 26_, 26, *, which are designed as inclined incisions on the surface of the slide on the inside of the consumption channels . 27, 27, are permanently connected to the drainage channel - 25. Aassenseiten d®r VerbrauchskanSl © 27, 27 * are local recesses 434, 434 *, which is a part of the Signalkanlle 34, 34 * are shown in the SteuerkanSle 4 3 1 4 31 * ssÜnden "The slider 461 is against the body 462 'guided radially by means of a unit not shown, for example a »pin. The main component of the regulator of the pressure difference is JL2. Here, the full slide 480 with aer circular recess 473rd which is connected to the Purapenkenal, 5 via branch 4. The slots 474 of the slide 480 are narrowed or closed by moving the slide 480 to the left in relation to the spring 40. ntil «s 59, with the control channels IS.» . λΆ connected * "D r gsgenßberliegende BetStigungsraun 43. Upper the (control) Abzwfsdg 44, in which a throttle - may nozzle are, permanently ait the inlet channel 11, connected to the pilot valve 9, to Figure 4 is also susgefßhrt. like the Vorst © u «rv © ntil 9, on Fig _# 3 *

_s ■

The two-stage, druckkospensierte hydraalischa control device according to Figure · 6 consists of a pump 1, Rait deo container 32 is connected, from a common Puapenkanal 3_ «it Abzvjeigen 4, 104 to the proportional Because valves 5_ _f 105. consumer yes, 106th

■ - <■ '

So copy

Branches 204 , 304 etc. to further proportional directional control valves 203, 505 of further consumers 205 , 306 etc., which are not shown here, can also be included in the hydraulic circuit. The first consumer 6_ is shown as a straight hydraulic motor, the second consumer 105 as a rotary hydraulic motor. The consumer 6 is connected to the »proportional directional control valve J5 via two consumer _{channels J -} , 7 /. The consumer 106 is also the proportional directional control valve 105 with the consumer channels 107 . 107 'connected. The control devices J5, 105 and designed as two-stage current amplifiers, which contain the pilot valves 0, 1.09 and the Varstarkerstufen XO, 110 , 'Here' has the first control device 5, the pilot valve £, which is designed as a dosing unit that comes from the dosing unit J3 and the pilot valve J3Q, while the second dam device 105 has the pilot valve 109 designed as a proportional 4/3 way valve. The control devices JS, 105 are connected to the inlet channels 11 , 111 behind the äegulatore ^ the pressure difference 12, 112 ,

The VorstGusrventil 9 is old to its inlet 13 via the branch I ₁ I * sa.it connected to the inlet channel IjL, old its outlet .17 via the branch IQ to the waste channel IS. connected and connected via the control channels 15 , J5 'old to the profile profiles 24, 24 * of the amplifier stage 10. The pilot valve 109 is connected to the amplifier stage 110 in a similar manner. The pilot valve is provided as a rapid control element, for example a steering wheel. The pilot valve 109 is provided with an actuating element 128 , for example a control lever. The advance valves S ₁ , 109 can also be equipped with adjusting devices, for example bit electromagnetic, electrohydraulic, pneumatic, etc. The ones shown

EPO COPY

34284C3

Vsrstarkerstuf-sn 10, 110, as well as further amplifier stages 210 , 310 etc. as well as other SSusrslnriöhtungen 205 , 305 etc. are identical. 3 © de Vsrhökerstuf ^Q 12, 3.3.0 «which is shown as an OrsipositionsmshrwsDaventil, it has the inlet channel 21, connected since the pair of secondary profiles 23_, 23," variable average, dig waste channel © 25, 25_ * rait the braking profile 2 £ ± _t 26, * connected to a variable average, a pair of consumption channels 27 ,, 27 * but consumption channels Z »Z * (I9Z. ^ 07 *} old dsa consumer §, (^ Οδ) connected, then a pair of operating ratios! 31 _# Sl ^ ' Sait centering springs 32, 32 ^ * vsrbundsn, ssit branches 33, 33 * ait dan Stouerkanälen Ij5, 15, * and a pair of load-signaling signaling channels 34, 34 * _t dia close to the consumption canals 27., Z7f taDndan, Oia SECONDAVprofila 23_, 23_ * and the primary profiles 24, 24 ^ are arranged in pairs ^, 24 and 23 *, 24 * , which form the current amplifiers 22, 22 *. The current amplifiers 22_, 22 * are on the d © n © inen sides and the pulp profiles 2S, , "arranged 25 * don on other sides of the Verbraucharkanäls 27_, 27_ * In the branches 33rd 35 * of StsuerkanSl © 15 ,, JS * know throttle orifices 35 . 35 * and also in parallel with them also check valves, 35 ,, 38, "^ as © ord © t. The Orossel orifice 3S, 35 * ait RDckschlagv ^ itilsR 3j5 ^, 3§_ * know directly in the StsuerksnSlen J5, IS _- * be arranged »In this case it is necessary to diasnsion the non-return valves Jtö, ZS ^ a little as much as possible»

The regulator of the pressure diffarsnz 12 has the Fedsr- * batStigungsraua 3S ₁ with F $ the 40 ait dea Steusrksnal _ £! _ 'I'verbundsn and the g @ gon5b @ rliegond @ n stau er raun £ 3_ bit _r the entry channel JJL Ober the branch 44 is connected. · · 'The regulator d r Oruckdifferenz JL2 halt a beetiotnte pressure difference between dea immersion rides channel J ₁ I. nit d © B branch ^ * and de "Zuflussvorbrauchskanal 7 or 7'

B »0 CJOPY

22 -. "" Γ "

in the direction of adjusting © of the pilot valve £ the control device J> upright. The pressure difference r. is vcn the initial bias and the steepness of the Force of the spring 40 determines. flow above the regulator of the pressure difference, itn range from an almost constant pressure difference to a pressure difference that is significant with the flow sinks «In the control channel 41 the throttle orifice can 0 de 45 and in the branch 44, the orifice plate 46. tricked into Gleichföroig halt the regulator oer pressure difference J.12 a certain pressure difference between the entry "channel 111 with the branch 11Γ * and the inflow consumption channel 107 or 107 * on the direction of Ümstellens of

Control member 109 of the control device 105 upright.

To the pump channel 3 is connected paralall a pressure valve 47 'DAS upper spring actuation space 48 is connected to the outlet channel 50, una old deta Opposite BettStigungsraua 5_ϊ, connected via branch 52_ to the Puapenkanal 3, « The exit signal channel, 5Jp _- let old the shuttle valve 53. old de? previously described StauerkanSlen 41, 141 of the adjacent control devices yes, 105 connected «The spring 48 be starts the pressure difference p _ß by which the pressure in the Puropean canal 3, is higher than the pressure in the most heavily loaded consumption canal 7, 7 *, or 107 . 107 ^ of the most loaded consumer 6 ,, resp. 106 . The pilot pressure valve can be used in parallel to the spring actuation space ^ 48 5 £ be connected «that is the maximum value of the pressure In the FederbetStigungsraun 48 limited and thus the Maximum pressure value in the generator channel 3, controls ♦ Will • Used in pilot pressure valve 5_4, it is suitable for the Exit signal channel, 50 to arrange a throttle screen 55 hen «To ensure that the control

facilities £. 105 it is necessary that the pressure difference. p _{s of} the pressure valve 47 is somewhat (2-3 bar) higher than the pressure difference p _{v of} the regulators of the pressure difference 12, 112 . A smaller pilot pressure valve 54 can be connected in parallel to the spring actuation chamber 48, the complements the pressure level in the spring actuating chamber 48, lim &, and thus also the amount of pressure in the pump channel 3. Io case that a pilot pressure valve 54 is used, it is expedient © channel-classified into the outlet a Droseelblende JiS ₁ * Instead of Purape JL together with the »pressure valve 47 a © control output tape bit control element can be used« which is connected to the outlet channel JiO «

On FIG. 7 an alternative embodiment of the pilot control valve 9 is shown schematically according to the invention, which is designed like a rotary pump jB *, which by means of

a pair of shuttle valves. 29_, 29, with the entry »

channel, 11 is connected.

When the actuator is at Fig. I (lever 372

or 472) is in standstill, the pilot valve 9 is in the middle position D, in which it _{connects both control channels IS -} , 15 ^ old to the process 17 * As a result, the pressure in the control channels JLS _- , 15. * and the channels 3JL5, 315 * on Fig. 5 and in the channels 415 , 415 * on FIG. 4 and in control rates 3jL, 32, * and 431 . 431 *. the bits connected to them are off, and the amplifier stage 10 niraot through the. Effect of the centering springs 32 . 52 * in both cases her smock position O a * Xn This middle position 0 is the entry s, channel 11, resp _#

. the round expulsions 311 . 411 the drainage channel 25, 25 * on Fig. 3 and the waste channel 25 on Fig. 4, the consumption channels 27, 27 * on Fig. 3.4. the signal channels 34, 34 * closed against each other «The consumer’s position <3 - the hydraulic motor »is thus locked. The low one

• uff -J,

Waste pressure comes from the signal channels S £, 34_ * via the shuttle valve 42 (Fig. 1, 3) and the control channel £ L » 1- ^ 1 in the spring actuation room 39 ^, 439 of the pressure difference regulator 12 ,
5

In the embodiment according to FIG. 2, the control channel 41 is connected to the outlet 17 by means of the regulator of the pressure difference 12 and, according to FIG. In the opposite actuation chamber 43 there is the pressure that controls the pressure difference regulator IZ against the force of the spring 4 (3 in throttled to closed Lag® hSlt. The same applies to the embodiment in Fig. 3, 4.

4 shows the distributor of the two-stage, pressure-compensated hydraulic control device according to the invention in the right working position R. Is a ^ r lever moved 472 of the pilot valve £ to the right, slide aer adjusted 469 to the left. Thus " d _Qr entry becomes 13th,

which is connected to branch 2Λ * .istr io the entry channel, 11 with your control channel ^ 15 switched through and the outlet 17 with the second control channel 15 *,

The Flßssigkeitestrora q from the inlet channel JLL is vondea passed control profile 414 in the control channel J3, by initially zugsführte FlOssigkeitsvolutnen through the branch 433. In the left ßetStigungsrauo 431 VerstSrkerstufs 10 and above that shuttle valve 59 and s control channel 43 of the FederbetStigungsraum 353 Regulator represents the pressure difference 3L2. The slide 461 of the current amplifier 3Ό and the slide 430 of the regulator © of the pressure difference IZ ₁ thus move to the right into the positions shown. Hit the slider 461 will be connected at about the same time

Consumption channel 27 with the secondary profiles 423 a with an edamate flow area © A, with the primary profiles 24 with a flow area a and with the signal channel 54 * (and its recess 434 *), which leads into the set-up room 451 ". The waste consumption channel 27 * becomes

over the fire profile 25, connected to the drainage channel. From the Puspenkanal £ via the slots 474 of the regulator of the pressure difference 12, flieset the Strota Q ^, which divides the Arbeitsstrora Q, the 11th from dec inlet channel Ov & r Radiälsussparungeri 411 *, the long hole 411 * * and the Sekundarprofilö 423 of the Schiebera 461 runs into the consumption channel 27, and on the control flow q, which runs from the branch, 11 * above the control profile 414 of the slide 4SI, the preconditioning valve 9, and continues via the control channel 15 and the primary profiles 2 £ of the slide 4Gl of the amplifier stage 1 £ in the same consumption channel 27, where calibrate both lines. The control unit pink q and d & r work roa Q, again in the overall route Q ^ varöinigsn, which loosens via the consumption channel into the left area of the straight hydraulic engine £ from the consumption channel 27, branches off via the recess 434 * and the signal channel 34 * negligibly small signal current Q _x from, "3 it transmits the pressure - the load signal - to the opposite actuation space 431 *. The signal trota is the seat of the throttle orifice 455 * and the current load pressure." This ensures that in the entry control channel 33 & i & also in the intrittssteuerraua 431 the pressure ust eissm bestiaoten value, which defines the force of the opposite centering spring £ 2 * and the centered hydrodynamic forces of all str & sa that act on the slide 469 1st, gr & seer 1st, than the Drude In de "Inflow consumption channel 27" From the right drain space of the consumer - the hydraulic motor £ - the liquid is old the Kolbon through the consumption channel

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7. * above the braking profile 26 * in the drainage channel. 25 urged. The regulator of pressure difference .12 wirät right is pressure from the immersion rides channel 11 ,, from left, the pressure from the entry control channel ^ 5 and the power of Fväar 40. Di © force of the spring 40, that is * her to catch svor voltage and di © Kraftcharakteristik, determine the grosso of the pressure difference p _v , between data inlet channel 11 and döa inlet consumption channel 27, resp. 27 *. This pressure difference py in relation to the load la consumer 6 ,, jLOjB is almost independent. The pressure difference p _v is used to control the control current ^ in the control profiles 414 , 414 * of the pilot valve S * and in the primary profiles 24, 24 * of the amplifier stage I O, and at the same time to control the working current Q in the secondary profiles 23. It it is assumed that the flow area A »f (y) of the secondary profiles 23, 23. * is larger than the flow area." a * » f (y) of the primary profiles 24, 24 * and the flow area © R« f (x) of the control profiles 14, 14 * «The specified flow areas and pretension and force characteristics of the springs 52 _A 32 * 6 amplifier stage 10 and the spring 40 of the regulator of the pressure difference 12 can be changed within wide limits as required and the desired properties and flow characteristics of the proportional directional valve! 3, 105 ue ». achieve. One can, for example, with klainea control current q sinsn large consumption roa Q ^ achieve * The ratio of the consumption * current Q ^ to the StQuaretrotn q, which is called amplification, can be realized within wide limits, eg "B" 2 - 100 "By d © a From the user's point of view, an important panorama is the dependence of the consumption flow Qm on the control deflection - sB, the adjustment X of the control member 9 from the cover position.

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Fig. 5 shows a total of four. _of ^ _n possible dependencies of the consumption rate Q ^ «f (j <), the linear dependency is fully drawn, the progressive dependency dashed, the degressive dependency dash-dotted and the cosbinated dependency dotted Dependency QH * f (x) from Fig. 5 shows you that different consumption flows Qm can be achieved for one and the second working position of the distributor, an arbitrary property with any hydraulically operated devices and mobile machines. This can easily be achieved, for example by different numbers or different sizes of the profiles 24, 24 * on one and the other side of the current amplifier 10 ·

If the Ou rch disturbance flee C _# D of the Breos diameter to the Ourchströssungsfliehe A, B, a, b of the secondary profiles 23, 23 * "and the primary profiles 24, 24 / is suitably dimensioned, it is achieved that in the case of a positive load, i.e. «H« against the direction of movement, the effect of the brake diameter is relatively small, but is large in the case of negative load, ie in the direction of movement, e.g. when the load is lowered Profiles achieved, or with them, & a && the slide 361 , 461 of the amplifier stage 10, 110 analogous to the pressure-controlled

ftfickschlag-valve, which ensures constant harmony between the inflow and outflow side of the consumer i>, 106 of the hydraulic motor, works in such a way that the flow from the consumer 6> a is exactly or approximately in harmony with the flow in the consumer JS . Oa the slide 361, 461 of the amplifier stage 10, 110 as well as the 'supply of the liquid' depending on the load, so too

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controls the flow of the liquid from the consumer hydraulic motor 6_, 106 , all control processes (start-up, process processes) run without disruptive time delays and the distributor device according to the invention ensures exceptionally good control - namely dynamic properties. This also reduces the tendency to unstable, oscillating activity "

If the Steuororgane 2J3, located on Figure "6128 is stopped and the pilot valves 9 ,, in which they take the SteuerkanBle 15, the center position O one. 15 *. rösp. 115 . 115 * »it connect the drains T7 and thus with the skin branch, 19, · As a result, the pressures in the operating areas 31, 31, * are balanced and the stroke amplifiers 10, 110 are located by the action of the centering springs 32, 32, * in the middle position 0, in which the consumption channels 7_, j /, respectively. 107 . 107 * are closed and the position of the consumer 6 ,, 106 is aretted · From the signal codes 34, ££ * of the amplifier stage 110 into the control line 141 and further via the shuttle valve SZ ₁ through the outlet signal channel 50. into the spring actuation chamber 48 dos pressure valve 47 Konuat low discharge pressure. As a result, the pressure valve 47 is set in such a way that the entire flow from the hydrator 1 flows through it into the container 2 at low pressure.

When the actuator 28 is moved, for example when the steering wheel is adjusted to the right, the pilot valve 30 of the control member 9 is adjusted first! In the position R · Proportional to its rotation, the dosing unit 8, the liquid over the branch I] / from the inlet _{channel J 1} I, pours it and conveys it via the control profile JL4 and further the control channel 15 into the left BetStigungsrauia 3J ^ the fore

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etarkeretufe JLO. This means that the amplifier level JLO in the position R adjusted.

6, in position R the inflow consumption channel 27 is connected to the inlet channel IjL via the secondary profiles 23 and to the (inflow) control channel 15 via the primary profiles 24. via the signal channel 34 * with the passive actuation chamber 31 * and the control channel 41 mi, t the spring actuation area 39, the regulator of the pressure difference jL2 and further via the changeover valve 53 and the outlet channel 50 with the spring actuation valve 48 of the pressure valve 47. This turns itself on automatically like the regulator of the pressure difference JL2, so does the pressure valve 47. For example, if the inlet pressure - the load - is 50 bar in the inlet channel 7, the pressure difference LZ in the inlet channel I ^ aer pressure is set, for example, 55 bar via the pressure valve 47 and the pressure in the pump channel 3 ,, e.g. 58bar, the liquid gus of the pump 1, flows through the pump channel ^ over the regulator of the pressure difference JL2 in the inlet channel II and from it in both stages of ^{the control ^ lorichtuns} S _{- of} the control member 9, and the amplifier stage 3 £ and the overflow of the current fills via the pressure valve 47 into the container «2. The control current q, which is measured by the Dosierwin unit, 8 flows out of the« control channel JL5 via primary profiles 24 of the amplifier 10. Simultaneously with the the synchronously calibration covering Sekunda'rprofilen ^ 3 flows in dan consumption channel 27 aar working rom Q. Both Stro- 'me', the control flow q and the Arbsltestroa Q, are combined in the consumption of channel 27 in ύ & η Gesantstrora Q _M a Q + q and penetrate Via the consumption bar 7_ in the consumer 6 ^ - the straight hydronictor. At the same time, it branches out of the consumption channel 27 via the signal channel 34 / into the control room 31. * a negligible

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small signal rom Qy, which enters the outlet 17 via the throttle orifice 35 *, the branch 33 /, the control channel jLEi'. and via the pilot valve 30. This ensures that there is a constant pressure difference between the entry control channel 15 , which is connected to the active actuation space 3jL and the opposite passive actuation space 31 ', whatever the loads on the consumer € i, which is smaller than the current pressure losses in the control element 9 the pressure difference p _v , which is obtained via the regulator of the pressure difference 12 . From the right drain pipe of the consumer 6, the liquid is from a piston via ήβη consumption channel 7; the consumption channel 27 'via the braking profiles 26 * into the waste channel 25 * of the amplifier stage 22 and further via the waste channel 20 into the container Z.

The pressure difference p _y is used to control the control current q in the control profiles,! £ · 14 'of the control element j9 and in the primary profiles 24, 24 * of the amplifier stage JLO and, at the same time, to control the operating current Q in the secondary profiles 23, is common the through area A "f (y) of the secondary profiles 23, 23 * larger" than the flow area a "f (y) of the prairie profiles 24, 24 'and than the through-flow area R * f (x) aar control profiles 14, 14J where χ the conversion of the control member 9, respectively. IQB means, and y the conversion of the amplifier stage 10, reap " 110 .ist" The specified flow areas A, a, R also the pretension and the force characteristics of the Zemtrierfedern 3_2, 32 'of the amplifier stage JLO and the springs 40 of the regulators of the pressure difference IZ , 112, nech demand especially the current characteristics uer Verstarkeretufe JLO, 110 uew "Z. example, small" Steuerstrota can be changed within wide limits to achieve so desired properties, q a big Verbrauchestrors Q ^ ₅ be achieved. The ratio of the consumption flow Q ^ to the

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Control current q _f, which is called amplification, can be implemented within a wide range, e.g. »B» 2 to 100.

If both control elements JJ, 109 are in operation, both amplifier stages 10, 110 are adjusted to the working positions R or L and both consumers £, 106 are tStig. The pressure signal from the consumer j5 B penetrates through the control channel 41 and the pressure signal from the consumer 106 penetrates via the control channel 141 to the shuttle valve 53, which automatically adjusts so that it lets the higher pressure signal through the outlet signal channel 50 to the pressure valve 47 . At the same time, the pressure signals from the consumers 6, 106, the regulators of the pressure difference JL2. " l ^ ^{2 in} such a way that the pressure in the inlet channel 11 is greater by the value p _v than the pressure in the consumption channel 7, respectively. 7 ^ , and in the inlet channel 111 the pressure above the value p ^, ar ^ G & mr ^ ⁸ ** ^a ^ ^s ^ ^{er pressure} ^ ⁱⁿ the consumption channel 107 . resp. 107Γ Ζ · Β · if the current pressure in the consumption channel 7 is 50 bar - as stated earlier - and in the consumption channel 107 the pressure is 100 bar «, the pressure 108 bar is set in the purapen channel £ by means of the regulator of the pressure difference 1 £, In the inlet channel 11 the pressure difference 12 is set by means of the regulator, the pressure is approx. 55 bar and in the inlet channel 111 via the regulator the pressure difference 112 is the pressure approx. 105 bar · The desired flow into the consumers J5, 106 Quantities and the overflow «is transferred from the pressure valve 4J7 into the container Z. The consumer (S is controlled as described joyful "The consumer IQS ₁ by means of the control Glieders 109 nit the control member 128 - a shift lever - controlled" Viird the pilot valve adjusted 109 for example to the position R, the VerstSrkerstufe 110 is moved to the position of R " A

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Part of the liquid from the hydrogenerator 3 flows out of the Puapon channel 3 via the regulator of the pressure difference 112 into the inlet channel 111 and from there into both stages into the pilot valve 109 and the amplifier stage 110 of the proportional directional control valve 105 proportional directional valve 109 - the opening of the control profiles 14, of the proportional Wegeventlles 109 - also the VerstSrkerstufe 11Q so adjusted that _t is synchronn the secondary profile 23 and 24 and also the Priraarprofile Bremeprofile 26 'open. The amplifier stage 110 works very similarly to the amplifier stage

The control element 9 / in the embodiment according to FIG. 2 as a rotary metering unit 13 * acts on the amplifier stage 10, with a uniform effect like the control element 9 ^ on FIG. 1 * when the control element 2J5 - the steering wheel - are at a standstill . the OrDcke in the control channels 13, 15. * balanced and the amplifier "stage 1 £ is in a middle position O. But if the operation acts on the control element 28_ - the steering wheel - the torque from the control element 28, in the rotary dosage unit 8 * In the pressure difference between the suction and displacement control channel 15> 15 * DberfDhrti If the control element 28, z * 8 * is rotated to the right, is in the (displacement) control channel, 15. the pressure © twae is higher than in the (suction) control channel 15, ** As a result, the check valve 29_ is closed and the check valve 2J3 * is open * Kit turning the rotary dose unit J3 * to the right is made from branch 11, * of the entry kenale 11 Above the raised 'check valve 23_' the liquid from the control channel ij, sucked in and transported by the (VerdrSngt * ⁿ gs-) control channel Jl5 into the left actuating room 3JL, the amplifier stage JLO. The Veretar-

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similar koretufe 2Ό and dis whole control device, as already described at embodiment according to FIG dor,. 6

The control device according to the invention, the generation of 'very different parameters ^ f ^Q "* individual consumers - Hydronotore desired warden adapted. The user can also do this with a simple action - for example by adjusting the adjusting screws 475 _{1 |} 475 * increase or decrease the current Q ^, Q ^ * in the consumers. All elements of the control device 5 ^, 105 can either be implemented in a block or some of them can be implemented separately. Particularly advantageous the separate execution of the control elements £ * can be Λ ^09, the AOR in the area of use, for example, can be installed in the cab. The control members 109 can be of small size with small, short sliders 369 . 469 with weak centering springs 570 . 370 *. 470th 470 *. Executed in this way, they offer small adjustment forces and enable kcxtpattei to use electromagnetic, electronic or other adjustment devices, thus saving both expenditure and installation space. Be the control members E »3- ° Q" Α * can run zvsei separate slides "the hit, such as a C arm, a pair of electromagnets, etc. The control device according to aer invention may be one or two control members are controlled to be manufactured in many equivalent Konstruktionsausföhrungen «Two of which are indicated in FIGS. 3 and 4. Even with a combination of the illustrated scheraatisehen embodiments, a number of other solutions can be achieved, which in principle are included in the solution according to the invention.

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Furthermore, the hydraulic control device according to the invention can use command control elements that control the current as well as metering elements so that it can perform the function of the proportional directional control valves and also of the servomotors. This is mainly advantageous in mobile devices and machines, in which the same auftitt the needs of both types of control devices, z * B "controlling the blade and controlling the direction of travel aer loader or excavator. There .

the subject of the invention is the safeguarding of the control system different consumers with different tax needs with a single control device «that from a single source - a hydrogen generator is fed 'enables' the hydraullschen Systems of facilities and machines, namely mobile machines, are simplified.

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Claims (16)

PATENT- AND LAWYERS PATENTANWÄLTE DIPL.-ING. W. EITLE. DR. RER. NAT. K. HOFFMANN DIPL.-ING. W. LEHN DIPL.-ING. K. FÜCHSLE - DR. RER. NAT. B. HANSEN - DR. RER. NAT. H -A. BRAUNS DIPL.-ING. K. GORG DIPL.-ING. K. KOHLMANN · RECHTSANWALT A. NETTE p 34 28 403.640 646 27.12.1984 Zavody tezkeho strojirenstvx Vyzkumny ustav stavebnich a zemnich stroju Brno (CSSR) Two-stage, pressure-compensated hydraulic control device for at least two consumer claims 1. Two-stage, pressure-compensated hydraulic control device for at least two consumer hydraulic motors, - which are fed from a common source - a pump, with a controlled pressure valve as well a regulating pump that constantly supplies the current Total consumption of all simultaneously active consumers "" - and adjust the pump pressure to the pressure of the most heavily loaded consumer, furthermore for each consumer a proportional directional valve or a directional valve - ~ 7 10 section, a regulator of the pressure difference between the inlet channel and the inflow consumption channel of the consumer is lined up and on the one hand with a spring and the pressure from the inflow consumption channel and on the other hand with the pressure from T5 is applied to the inlet channel, characterized in that at least one proportional directional control valve (5, 105) of the consumers (6, 106), preferably further proportional directional valves of the further consumers, is or are designed as a current amplifier with two stages, which is a pilot valve (9, 109) and an amplifier stage (10, 110), both of which are connected to a common inlet channel (11, 111) behind the regulator of the pressure difference. ~ pQ _C q _py λ ^ ARABELLA STREET 4. D-BOOO MUNICH B1 · TELEFON CO89} 911087 · TELEX 5-29619 CPATHE ^ · TELbKOF ⁵ IERKR OIÜ3 £ .- '3 _ 2 - 2. Two-stage, pressure-compensated hydraulic control device according to claim 1, characterized in that the amplifier stage (10, 110) is designed as a slide (361, 461) which is mounted in the body (362, 4.62), with primary profiles (24, 24 ¹ ), which are connected by means of control channels (15, 15 ') on the one hand to the pilot valves (9, 109) and on the other hand to the actuation spaces (31, 31') of the amplifier stage (10, 110), with consumption channels (27, 27 ') which are connected to the consumer (6, 106) by means of the consumption ^{channels (7, 7 1} ), the primary profiles (24, 24 ') and the secondary profiles (23, 23') being made up of pairs (24, 23, 24 ') , 23 ') formed current amplifiers (22, 22') are arranged on the one hand the consumption ducts (27, 27 '), while on the other hand the consumption ducts (27, 27') brake prviles (26, 26 ') are arranged. 3. Two-stage, pressure-compensated hydraulic control device according to claims .1 and 2, thereby characterized in that the secondary profiles (23, 23 ') and the primary profiles (24, 24') of the amplifier stage (10, 110) may be geometrically different.
25th 4. Two-stage, pressure-compensated hydraulic control device according to claims 1 and 3 or 2, characterized in that the number and / or the size of the secondary profiles (23) on one Side of the slide (361) on the number and / or size of the secondary profiles (23 ') on the other Side of the slide (361) of the amplifier stage (10, 110) is or are different. 5. Two-stage, pressure-compensated hydraulic control device according to claims 1, 2, 3 or 4, characterized in that the number and / or the size of the primary profiles (24) on one Side of the slide (361) on the number and / or size of the primary profiles (24) on the other Side of the slide (361) of the amplifier stage (10, 110) is or are different. 6. Two-stage, pressure-compensated hydraulic control device according to claims 1 and 2 or 3, 4 and 5, characterized in that the amplifier stage (10) is in the rest position of the pilot valve (9) in the center position 0 and in the working position R of the pilot valve ( 9) the one inflow consumption channel (27) is connected at the same time with the primary profiles (24), with the secondary profiles (23) and with the signal channel (34 '), and the outflow consumption channel (27') is connected with the braking profiles (26 '), while in the working position L of the pilot valve (9) the further inflow consumption channel (27 ') is connected simultaneously with the primary profiles (24 ¹ ) * with the secondary profiles (23 *) and' with the signal channel (34), the outflow consumption channel (27) is connected to the brake profiles (26). 7. Two-stage, pressure-compensated hydraulic control device according to one of the preceding claims, characterized in that in the working positions L and R of the slide (361) the Amplifier stage (10) the spring actuation chamber (39) the regulator of the pressure difference (12) with the inflow consumption channel (27 or 27 ') is connected. 8. Two-stage / pressure-compensated hydraulic control device according to one of the preceding claims, characterized in that in the working positions L and R of the slide (361) the Booster stage (10) of the spring actuation chamber (39) of the regulator of the pressure difference (12) with the inflow control channel (15, 15 ') is connected. 9. Two-stage, pressure-compensated hydraulic control device according to one of the preceding claims, characterized in that the pilot valve (9) is designed as a directional control valve 4/3 which is connected with its inlet (13) to the inlet channel (11) and to the pair of outlet control channels (15, 15 ') is connected to the amplifier stage (10). 10. Two-stage, pressure-compensated hydraulic control device according to one of the preceding claims, characterized in that between the inlet (13) and the outlets of the control channels (15, 15 ') of the pilot valve (9) control profiles (14, 14 ') variable average are arranged. 11. Two-stage, pressure-compensated hydraulic control device for at least two consumer hydraulic motors according to claim 1 or according to claims 1 to 8, wherein each control device of each consumer is designed as a two-stage control device, which has a control element and an amplifier stage contains, both of which are connected to a common inlet channel behind the pressure differential regulator EPO COPY are connected, characterized that at least one control member (9, 109) at least one control device (5, 10 5) as a dosing unit is designed, the exits of which via the control channels (15, 15 ') with the amplifier stage (10) are connected. 12. Two-stage, pressure-compensated hydraulic control device according to claim 11, characterized characterized because the dosing unit consists of a dosing unit (8) and a pilot valve (30), which are mechanically or hydraulically coupled to one another. 13. Two-stage, pressure-compensated hydraulic control device according to claims 1 to 8 and 11, characterized in that the metering unit is a rotary metering unit (8 ¹ ) - a hydrogen generator - which by means of control channels (15, 15 ') and the check valves ( 29, 29 ') is connected to the inlet channel (11). 14. Two-stage, pressure-compensated hydraulic control device according to claims 11, 12 and 13, thereby characterized in that the inlet shaft of the metering unit (8) with an actuator (28) - a steering wheel - is provided. 15. Two-stage, pressure-compensated hydraulic control device according to claim 1 or 1 to 8, characterized characterized in that the pilot valve (9, 109) is designed as a straight metering unit is. COPV 16. Two-stage, pressure-compensated hydraulic control device according to claim 15, characterized characterized in that the pilot valve (9, 109) as a straight hydraulic motor (Hydraulic cylinder) is executed. '& o copy