NO171425B - HYDRAULIC CONTROL BLOCK - Google Patents

HYDRAULIC CONTROL BLOCK Download PDF

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Publication number
NO171425B
NO171425B NO885035A NO885035A NO171425B NO 171425 B NO171425 B NO 171425B NO 885035 A NO885035 A NO 885035A NO 885035 A NO885035 A NO 885035A NO 171425 B NO171425 B NO 171425B
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NO
Norway
Prior art keywords
valves
control block
pressure
load pressure
working
Prior art date
Application number
NO885035A
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Norwegian (no)
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NO885035L (en
NO885035D0 (en
NO171425C (en
Inventor
Hans Schwelm
Original Assignee
Hydrolux Sarl
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Application filed by Hydrolux Sarl filed Critical Hydrolux Sarl
Publication of NO885035D0 publication Critical patent/NO885035D0/en
Publication of NO885035L publication Critical patent/NO885035L/en
Publication of NO171425B publication Critical patent/NO171425B/en
Publication of NO171425C publication Critical patent/NO171425C/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Foreliggende oppfinnelse angår en hydraulisk styreblokk for hydraulikkenheter, særlig for styring av dobbeltvirkende hydraulikksylindre med fire integrerte enkeltventiler som ligger parvis over hverandre og innbyrdes motstående, anordnet i to plan parallelt med et overflateareal på styreblokken med standard tilkoplingsmønster, hvilke ventiler består av proporsjonale strupe-seteventiler som kan påvirkes parvis via en pilotventil. The present invention relates to a hydraulic control block for hydraulic units, in particular for control of double-acting hydraulic cylinders with four integrated single valves that lie in pairs above each other and mutually opposite, arranged in two planes parallel to a surface area on the control block with a standard connection pattern, which valves consist of proportional throttle seat valves which can be affected in pairs via a pilot valve.

En styreblokk av stort sett samme art som ovenfor angitt er kjent fra DE-Al-3 604 410. For at styreblokken skal kunne brukes universelt må operasjonssekvensen til den dobbeltvirkende hydrauliske sylinder finne sted med konstant hastighet. Dette er bare mulig dersom gjennomstrømningen av hydraulikk-væsken på forbrukersiden er konstant og svarer til en verdi som kan innstilles ved en proporsjonal-styreinnretning. Gjennomstrømningen gjennom de 2-veis monterte ventiler som er anordnet i den kjente styreblokk er imidlertid avhengig av ventilenes åpningstverrsnitt og av trykkforskjellen P mellom trykket i pumpeledningen og trykket i forbruksledningen. Men ettersom pumpetrykket ved den kjente styreblokk holdes konstant ved hjelp av en trykkbegrensningsventil, blir de belastningstrykk-avhengige variasjoner i P kompensert ved tilsva-rende tilpasninger av ventilenes åpningstverrsnitt. I dette øyemed er hver ventil utstyrt med en forskyvningsgiver og ventilstemplenes åpningsposisjon blir til enhver tid automatisk regulert inntil den målte maksimalverdi av hydraulikkvæske-gjennomstrømningen svarer til den ønskete, innstilte verdi. Denne elektroniske kompensering av ventilstemplenes posisjon krever imidlertid meget komplisert elektronikk. A control block of largely the same kind as stated above is known from DE-Al-3 604 410. In order for the control block to be used universally, the operation sequence of the double-acting hydraulic cylinder must take place at a constant speed. This is only possible if the flow of the hydraulic fluid on the consumer side is constant and corresponds to a value that can be set by a proportional control device. The flow through the 2-way mounted valves arranged in the known control block is, however, dependent on the opening cross-section of the valves and on the pressure difference P between the pressure in the pump line and the pressure in the consumption line. But as the pump pressure at the known control block is kept constant by means of a pressure limiting valve, the load pressure-dependent variations in P are compensated by corresponding adaptations of the valve's opening cross-section. To this end, each valve is equipped with a displacement sensor and the opening position of the valve pistons is automatically regulated at all times until the measured maximum value of the hydraulic fluid flow corresponds to the desired, set value. This electronic compensation of the position of the valve pistons, however, requires very complicated electronics.

Ved den kjente styreblokk unngår man riktignok oljelekkasje i tilfelle av strømbrudd, ettersom oljetrykket på pumpesiden holder alle ventiler lukket. Ved bortfall av trykk på pumpesiden vil imidlertid den kjente styreblokk ikke lenger kunne angis å være uten oljelekkasje. With the known control block, oil leakage is certainly avoided in the event of a power failure, as the oil pressure on the pump side keeps all valves closed. In the event of loss of pressure on the pump side, however, the known control block will no longer be able to be stated to be without oil leakage.

De to tankventiler i den kjente styreblokk er enkle åpne/stengeventiler. Under normale arbeidsforhold er dette tilstrekkelig. Men dersom belastningen blir negativ vil styreblokken gå inn i en ukontrollert frittløpende tilstand. The two tank valves in the known control block are simple open/close valves. Under normal working conditions, this is sufficient. But if the load becomes negative, the control block will enter an uncontrolled free-running state.

Som ytterligere eksempler på kjent teknikk på området kan nevnes GB 1 182 641 og GB 1 045 764, som imidlertid ikke inne-holder noe som er egnet til å eliminere ovennevnte ulemper ved den kjente styreblokk ifølge DE-A1-3 604 410 . GB 1 182 641 and GB 1 045 764 can be mentioned as further examples of prior art in the area, which, however, do not contain anything suitable for eliminating the above-mentioned disadvantages of the known control block according to DE-A1-3 604 410.

Foreliggende oppfinnelse er basert på det formål å skape en ny og særegen styreblokk hvorved man unngår de ovennevte ulemper samtidig som den kompakte konstruksjon og det standar-diserte koplingsmønster opprettholdes. The present invention is based on the purpose of creating a new and distinctive control block whereby the above disadvantages are avoided while maintaining the compact construction and the standardized connection pattern.

Dette formål oppnås ifølge oppfinnelsen ved en styreblokk med de i hovedkravet angitte trekk. Ytterligere utføringsfor-mer er angitt i underkravene. This purpose is achieved according to the invention by a control block with the features stated in the main claim. Further embodiments are specified in the sub-claims.

Oppfinnelsen er nærmere beskrevet nedenfor ved hjelp av et utføringseksempel, med henvisning til den medfølgende tegning. The invention is described in more detail below by means of an embodiment, with reference to the accompanying drawing.

Denne tegning viser skjematisk koplingsdiagrammet for en styreblokk, hvis arrangement svarer til arrangementet ved den kjente styreblokk ifølge DE-A1-3 604 410. This drawing schematically shows the connection diagram for a control block, the arrangement of which corresponds to the arrangement of the known control block according to DE-A1-3 604 410.

Styreblokken består i hovedsaken av de fire ventiler som er betegnet med C1, C2, C3 og C4, idet C2 og C3 er arbeidsventilene og C2 og C4 er tankventilene. De fire ventiler styres som i den kjente styreblokk via en elektronisk styrt pilotventil 10. The control block mainly consists of the four valves designated C1, C2, C3 and C4, with C2 and C3 being the working valves and C2 and C4 being the tank valves. The four valves are controlled as in the known control block via an electronically controlled pilot valve 10.

Den dobbeltvirkende hydrauliske sylinder som skal styres er betegnet med 12. Under en første arbeidssyklus strømmer hydraulikkoljen ut av en pumpeledning P gjennom ventil C-j^ og arbeidsledningen A inn i sylinderens 12 stempelrom, slik at stemplet beveges til høyre i figuren. Oljen fra stempelstangrommet strømmer gjennom arbeidsledningen B og den åpnete ventil C4 inn i tankledning T. The double-acting hydraulic cylinder to be controlled is denoted by 12. During a first work cycle, the hydraulic oil flows out of a pump line P through valve C-j^ and the work line A into the piston chamber of the cylinder 12, so that the piston moves to the right in the figure. The oil from the piston rod chamber flows through the working line B and the opened valve C4 into the tank line T.

Ved omstilling ved hjelp av pilotventilen 10 stenges ventilene C-,^ og C4 og ventilene C2 og C3 åpnes. Hydraulikkoljen vil da strømme ut av pumpeledningen P gjennom ventilen C3 og arbeidsledningen B inn i stempelstangrommet, slik at sylinderen 12 beveges i den motsatte retning. Denne gang er stempelrommet via ventilen C2 forbundet med tankledningen T. When switching using the pilot valve 10, the valves C-,^ and C4 are closed and the valves C2 and C3 are opened. The hydraulic oil will then flow out of the pump line P through the valve C3 and the working line B into the piston rod space, so that the cylinder 12 is moved in the opposite direction. This time, the piston chamber is connected to the tank line T via the valve C2.

Ser man på den kjente styreblokk består de fire ventiler If you look at the familiar control block, it consists of four valves

Clf C2, C3 og C4 av enkle 2-veis monterte ventiler. Ved styreblokken ifølge foreliggende oppfinnelse består de fire ventiler Cx, C2, <C>3 og C4 av servobetjente, proporsjonale strupe-seteventiler med integrert belastningstrykk-tilbakekop-lingssignal. En slik ventil er beskrevet i US patentskrift 4 662 660. Clf C2, C3 and C4 of simple 2-way mounted valves. In the control block according to the present invention, the four valves Cx, C2, <C>3 and C4 consist of servo-operated, proportional throttle seat valves with an integrated load pressure feedback signal. Such a valve is described in US Patent 4,662,660.

Som allerede nevnt innledningsvis holdes pumpetrykket ved den kjente styreblokk konstant og strømningen gjennom arbeidsventilene C2 og C3 holdes konstant ved at ventilenes åpningsposisjon kontinuerlig tilpasses belastningstrykk-variasjonene. As already mentioned at the outset, the pump pressure at the known control block is kept constant and the flow through the working valves C2 and C3 is kept constant by the valves' opening position being continuously adapted to the load pressure variations.

Også ved styreblokken ifølge foreliggende oppfinnelse skal gjennomstrømningen holdes konstant, nærmere bestemt ved en verdi som kan innstilles ved at pilotventilen er konstruert som en proporsjonal-styreinnretning. Ved den nye styreblokk holdes imidlertid ventilenes åpningstverrsnitt konstant og styringen finner sted via en trykkstyreinnretning 14 i pumpeledningen, idet styreinnretningen styrer trykket i pumpeledningen i henhold til belastningstrykkvariasjonene, nærmere bestemt slik at trykkforskjellen P mellom pumpetrykk og belastningstrykk forblir permanent konstant. Størrelsen av denne trykkforskjell P bestemmes av en regulerbar fjær 15. Also with the control block according to the present invention, the flow rate must be kept constant, more specifically at a value that can be set by the fact that the pilot valve is designed as a proportional control device. With the new control block, however, the opening cross-section of the valves is kept constant and the control takes place via a pressure control device 14 in the pump line, the control device controls the pressure in the pump line according to the load pressure variations, more precisely so that the pressure difference P between pump pressure and load pressure remains permanently constant. The size of this pressure difference P is determined by an adjustable spring 15.

Fordelene med styringen ifølge oppfinnelsen er en betyde-lig forenklet elektronikk i forhold til den kjente styring. The advantages of the control according to the invention are significantly simplified electronics compared to the known control.

Belastningstrykk-målingen finner sted på den i US patentskrift 4 662 600 angitte måte og tilbakekoplingssignalet går via ledningene 16 og 18 som via en ledning 20 er tilkoplet trykkstyreinnretningen. The load pressure measurement takes place in the manner indicated in US patent document 4,662,600 and the feedback signal goes via the lines 16 and 18 which are connected via a line 20 to the pressure control device.

I belastningstrykk-tilbakekoplingssignalledningen 20 er der ved 22 et overtrykk-beskyttelseselement som beskytter mot unormalt høyt overtrykk i arbeidsledningen. Dersom belastningstrykket overskrider en forutbestemt maksimalverdi stenges gjennomstrømningen ved at den ventil som er i virksomhet, C1 eller C3, holdes lukket inntil belastningstrykket igjen har falt til under denne maksimalverdi, eller i praksis inntil feilkilden er blitt eliminert. In the load pressure feedback signal line 20, there is an overpressure protection element at 22 which protects against abnormally high overpressure in the working line. If the load pressure exceeds a predetermined maximum value, the flow is closed by keeping the valve that is in operation, C1 or C3, closed until the load pressure has again fallen below this maximum value, or in practice until the source of error has been eliminated.

Styreblokken ifølge oppfinnelsen er forsynt med en automatisk senke-bremsefunksjon. I dette øyemed påvirkes de to tankventiler C2 og C4 via ledningene 16 og 18 av belastningstrykket i arbeidsventilene C2 og C3. Under normale arbeidsforhold, dvs. med positiv belastning, er tankventilene C2 og C4 fullstendig åpne. Dersom belastningen er negativ blir tank-ventilenes C2 og C4 gjennomstrømningsåpning automatisk minsket, med sikte på å opprettholde den via pilotventilen innstilte gjennomstrømning, og disse ventiler arbeider som senke-bremse-ventiler. The control block according to the invention is equipped with an automatic lowering brake function. To this end, the two tank valves C2 and C4 are affected via lines 16 and 18 by the load pressure in the work valves C2 and C3. Under normal working conditions, i.e. with positive load, tank valves C2 and C4 are fully open. If the load is negative, the flow opening of the tank valves C2 and C4 is automatically reduced, with the aim of maintaining the flow set via the pilot valve, and these valves work as lowering-brake valves.

Styreblokken ifølge oppfinnelsen er fullstendig uten oljelekkasje både ved eventuelt strømbrudd og ved eventuelt bortfall av trykk. Tilbakeslagsventilene RI og R2 som er montert i arbeidsledningene hindrer tilbakestrømning av hydraulikkvæske, slik at arbeidssylinderen 12 kan holdes i nøytrale posisjoner uten oljelekkasje. The control block according to the invention is completely without oil leakage both in the event of a power failure and in the event of a loss of pressure. The non-return valves RI and R2 which are mounted in the work lines prevent the backflow of hydraulic fluid, so that the work cylinder 12 can be held in neutral positions without oil leakage.

Claims (4)

1. Hydraulisk styreblokk for hydraulikkenheter, særlig for styring av dobbeltvirkende hydraulikksylindre (12) med fire integrerte enkeltventiler ( Clf C2, C3, C4) som ligger parvis over hverandre og innbyrdes motstående, anordnet i to plan parallelt med et overflateareal på styreblokken med standard tilkoplingsmønster, hvilke ventiler består av proporsjonale strupe-seteventiler som kan påvirkes parvis via en pilotventil (10), karakterisert ved at de enkelte ventiler (C1# C2, C3, og C4) har integrert belastningstrykk-tilbakekoplingssignal, og at gjennomstrømningen gjennom arbeidsventilene (C-^, C3) holdes konstant ved hjelp av en belastningstrykkavhengig trykkstyreinnretning (14).1. Hydraulic control block for hydraulic units, in particular for control of double-acting hydraulic cylinders (12) with four integrated single valves (Clf C2, C3, C4) which lie in pairs above each other and mutually opposite, arranged in two planes parallel to a surface area of the control block with a standard connection pattern , which valves consist of proportional throttle seat valves that can be actuated in pairs via a pilot valve (10), characterized in that the individual valves (C1# C2, C3, and C4) have an integrated load pressure feedback signal, and that the flow through the working valves (C- ^, C3) is kept constant by means of a load pressure-dependent pressure control device (14). 2. Styreblokk ifølge krav 1, karakterisert ved at trykkstyreinnretningen (14) er koplet til en overtrykk-beskyttelse (22). 9142. Control block according to claim 1, characterized in that the pressure control device (14) is connected to an overpressure protection (22). 914 3. Styreblokk ifølge krav 1, karakterisert ved at tankventilene (C2, C4) styres ved hjelp av belastningstrykket på arbeidsventilene (C1; C3) .3. Control block according to claim 1, characterized in that the tank valves (C2, C4) are controlled by means of the load pressure on the working valves (C1; C3). 4. Styreblokk ifølge krav 1, karakterisert ved tilbakeslagsventiler som er montert i arbeidsledningene.4. Control block according to claim 1, characterized by non-return valves which are mounted in the working lines.
NO885035A 1987-11-12 1988-11-11 HYDRAULIC CONTROL BLOCK NO171425C (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
LU87045A LU87045A1 (en) 1987-11-12 1987-11-12 HYDRAULIC CONTROL BLOCK

Publications (4)

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NO885035D0 NO885035D0 (en) 1988-11-11
NO885035L NO885035L (en) 1989-05-16
NO171425B true NO171425B (en) 1992-11-30
NO171425C NO171425C (en) 1993-03-10

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NO885035A NO171425C (en) 1987-11-12 1988-11-11 HYDRAULIC CONTROL BLOCK

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GB (1) GB2212220B (en)
LU (1) LU87045A1 (en)
NO (1) NO171425C (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU87794A1 (en) * 1990-08-31 1991-02-18 Hydrolux Sarl PROPORTIONAL-WEGEVENTIL IN SITZBAUWEISE
DE19500749C2 (en) * 1995-01-12 2000-12-07 Danfoss As Three-way or multi-way valve
DE19500748C2 (en) * 1995-01-12 2000-12-14 Danfoss As Three-way or multi-way valve
DE19537482A1 (en) * 1995-10-09 1997-04-10 Schwelm Hans Hydraulic control block
DE10006141A1 (en) * 2000-02-11 2001-09-06 Zf Lenksysteme Gmbh Electro-hydraulic control device
CN104832485B (en) * 2015-05-19 2017-03-22 江苏柳工机械有限公司 Hydraulic control system for backhoe loader
CN111089088B (en) * 2019-12-27 2022-03-29 中国航空工业集团公司沈阳飞机设计研究所 Multi-mechanism series connection motion coordination control loop

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE26028E (en) * 1963-05-16 1966-05-17 Pilot operated control valve mechanism
US3411536A (en) * 1966-07-06 1968-11-19 Koehring Co Pilot operated control valve mechanism

Also Published As

Publication number Publication date
NO885035L (en) 1989-05-16
NO885035D0 (en) 1988-11-11
GB8826322D0 (en) 1988-12-14
GB2212220B (en) 1992-01-08
GB2212220A (en) 1989-07-19
LU87045A1 (en) 1988-05-03
NO171425C (en) 1993-03-10

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