SE455637B - DEVICE ON A HYDRAULIC CIRCUIT - Google Patents
DEVICE ON A HYDRAULIC CIRCUITInfo
- Publication number
- SE455637B SE455637B SE8503569A SE8503569A SE455637B SE 455637 B SE455637 B SE 455637B SE 8503569 A SE8503569 A SE 8503569A SE 8503569 A SE8503569 A SE 8503569A SE 455637 B SE455637 B SE 455637B
- Authority
- SE
- Sweden
- Prior art keywords
- pressure
- fluid
- pressure fluid
- source
- valve
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/433—Pump capacity control by fluid pressure control means
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- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
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- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
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- 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
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- 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
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- 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
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- 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
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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- 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
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- 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
- F15B2211/35—Directional control combined with flow control
- F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
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- 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
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- 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
- F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
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- 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
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- 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
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- 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
- F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
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- 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
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5156—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a return line and a directional control valve
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- 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
- F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve
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- 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
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- 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
- F15B2211/61—Secondary circuits
- F15B2211/613—Feeding circuits
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- 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
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- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
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- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Valve Device For Special Equipments (AREA)
Description
455 es? 2 det minimivätsketryck, som från fall till fall erfordras för att den eller de i kretsen ingående hydraulmotorerna skall fullgöra sina önskade arbetsuppgifter, och som också automatiskt anpassar det från tryckkällan levererade vätsketrycket därefter, så att en tillfredsställande funktion hos kretsen ständigt säkerställas. 455 es? 2 the minimum fluid pressure required from case to case for the hydraulic motors or motors included in the circuit to fulfill its desired functions, and which also automatically adjusts the fluid pressure supplied from the pressure source accordingly, so that a satisfactory function of the circuit is constantly ensured.
Därigenom kan vätsketrycket i kretsen alltid hållas på den nivå, som just för tillfället krävs, och vätsketrycket ökas blott när så erfordras.As a result, the liquid pressure in the circuit can always be kept at the level required at the moment, and the liquid pressure is increased only when required.
Enligt uppfinningen uppnås detta syfte genom att anord- ningen uppvisar det kännetecken. som anges i det efterföljande patentkravet l, medan underkraven anvisar vidareutvecklingar och utföringsformer av den grundläggande uppfinningstanken.According to the invention, this object is achieved by the device having that characteristic. as set out in the appended claim 1, while the subclaims indicate further developments and embodiments of the basic inventive concept.
För uppfinningens förtydligande skall i det följande och under hänvisning till bifogade ritningar beskrivas några ut- föringsexempel§ På ritningarna visar fig. l, 2 och 3 schematiskt tre delvis olika hydrauliska kretsar, vid vilka uppfinningen tillämpats. Det är därvid att märka, att var och en av dessa visade kretsar är i stånd att arbeta självständigt men vid behov låter sig kompletteras med ytterligare hydraulmotorer och till- hörande inloppsventilenheter, som tillförs tryckvätska från en och samma tryckvätskekälla. ' I fig. 1 betecknar 20 en hydraulmotor i form av en dubbel- verkande hydraulcylinder med en kolvstàng 21 och med två motor- inlopp A resp. B. Tryckvätska för drivning av denna hydraulmotor 20 levereras av en tryckvätskekälla, som generellt betecknats med 22 och som i det visade fallet innefattar en pump 100 med variabelt deplacement, som låter sig inställas med hjälp av en tryckstyrd regulator 102. Mellan tryckvätskekällan 22 och cylin- dern 20 är anordnat ett ventilhus, som generellt betecknats med 24 och till vilket ansluter en matarledning 25 från tryckvätske- källan. I detta ventilhus 24 ingår förutom ett flertal ventiler, som är=ovidkommande för uppfinningen och därför inte behöver be- skrivas, två till var sitt av de båda motorinloppen A resp. B anslutna kanaler 28 och 29. till vilka tryckvätskan från tryck- vätskekällan 22 via matarledningen 25 och ett ventilhusinlopp 26 kan styras med hjälp av en gemensam inloppsventil 27 av slidtyp.In order to clarify the invention, some embodiments will be described in the following and with reference to the accompanying drawings. In the drawings, Figs. 1, 2 and 3 schematically show three partly different hydraulic circuits, to which the invention has been applied. It should be noted that each of these circuits shown is able to operate independently but can be supplemented if necessary with additional hydraulic motors and associated inlet valve units, which are supplied with pressure fluid from one and the same pressure fluid source. In Fig. 1, 20 denotes a hydraulic motor in the form of a double-acting hydraulic cylinder with a piston rod 21 and with two motor inlets A resp. B. Pressure fluid for driving this hydraulic motor 20 is supplied by a source of pressure fluid, generally designated 22, which in the case shown includes a variable displacement pump 100 which can be adjusted by means of a pressure controlled regulator 102. Between the source of pressure fluid 22 and the cylinder The valve housing 20 is provided with a valve housing, which is generally designated 24 and to which a supply line 25 from the pressure fluid source connects. This valve housing 24 includes, in addition to a plurality of valves, which are irrelevant to the invention and therefore need not be described, two to each of the two motor inlets A resp. B connected channels 28 and 29. to which the pressure fluid from the pressure fluid source 22 via the supply line 25 and a valve housing inlet 26 can be controlled by means of a common inlet valve 27 of the wear type.
Sliden i denna inloppsventil 27 är fjäderbelastad mot ett på rit- ningen visat neutralläge, i vilket sliden hindrar inströmning av vätska till båda motorinloppen A och B. Inloppsventilens 27 455 637 3 slid, som på känt sätt är volymströmstyrande, kan fjärrstyras på hydraulisk väg från ett nanöverdon 23 via kanaler 30 och 31 för att öppna mer eller mindre till en av de båda kanalerna 28 eller 29 1 taget. I var och en av de båda kanalerna 28 och 29 är vidare anordnad en fjäderbelastad backventil 37 resp. 38, som tillsam- mans med motsvarande ändparti av sliden i inloppsventilen 27 av- gränsar en förkammare 32 resp. 33, genom vilken tryckvätskan måste passera på sin väg från inloppsventilen 27 till hydraul- cylindern 20.The slide in this inlet valve 27 is spring-loaded against a neutral position shown in the drawing, in which the slide prevents the inflow of liquid to both motor inlets A and B. The slide of the inlet valve 27, which in a known manner is volume flow-controlled, can be remotely controlled hydraulically from a nanover connector 23 via channels 30 and 31 to open more or less to one of the two channels 28 or 29 1 taken. A spring-loaded non-return valve 37 and 37, respectively, is further arranged in each of the two channels 28 and 29. 38, which together with the corresponding end portion of the slide in the inlet valve 27 delimits an antechamber 32 resp. 33, through which the pressure fluid must pass on its way from the inlet valve 27 to the hydraulic cylinder 20.
Förkammaren 33 är nu via en kanal 79 förbunden med ena än- den av en första växelventil 80, vars andra ände genom en kanal 81 och en därifrån utgående ledning är förbunden med en inlopps- anslutning LS2 i en kopplingsplint 104, som närmare skall be- skrivas längre fram. Växelventilens 80 mittparti är genom en kanal 83 förbundet med ena änden av en andra växelventil 82, vars andra ände genom en kanal 84 är förbunden med förkammaren 32 och vars mittparti är förbundet med en utloppsanslutning LSl, som 1 sin tur i det visade exemplet är förbundet direkt med den i tryckvätskekällan 22 ingående pumpens 100 tryckstyrda regula- tor 102.The antechamber 33 is now connected via a channel 79 to one end of a first changeover valve 80, the other end of which is connected by a channel 81 and a line extending therefrom to an inlet connection LS2 in a terminal block 104, which is to be more closely connected. written later. The middle portion of the gear valve 80 is connected through a channel 83 to one end of a second gear valve 82, the other end of which is connected to the antechamber 32 through a channel 84 and the middle portion of which is connected to an outlet connection LS1, which in turn in the example shown is connected directly with the pressure controlled regulator 102 of the pump 100 contained in the pressure fluid source 22.
Kopplingsplinten lOü uppvisar förutom den förutnämnda in- loppsanslutningen LS2 även en anslutning P, som är förbunden med en avgrening 25a från tryokvätskekällans 22 matarledning 25, och en anslutning T, som är förbunden med en returledning 105, i vilken ett visst mottryck upprätthålles. Kopplingsplinten 104 är avsedd att utnyttjas för anslutning av ytterligare en inte visad enhet omfattande en hydraulmotor med tillhörande ventilhus till tryckvätskekällan 22, varvid denna ytterligare enhet i likhet med den redan beskrivna förutsättes innefatta minst en inlopps- ventil, en backventil och en mellanliggande förkammare, som är anslutbar till inloppsanslutningen LS2 1 kopplingsplinten 104. Är ingen sådan ytterligare enhet ansluten till kopplingsplinten 104 är givetvis den sistnämndas samtliga anslutningar LS2, P och T stängda.In addition to the aforementioned inlet connection LS2, the terminal block 10u also has a connection P, which is connected to a branch 25a from the supply line 25 of the pressure fluid source 22, and a connection T, which is connected to a return line 105, in which a certain back pressure is maintained. The terminal block 104 is intended to be used for connecting an additional unit (not shown) comprising a hydraulic motor with associated valve housing to the pressure fluid source 22, this additional unit, like the one already described, being assumed to comprise at least one inlet valve, a non-return valve and an intermediate chamber. is connectable to the inlet connection LS2 in the terminal block 104. If no such additional unit is connected to the terminal terminal 104, all the connections LS2, P and T of the latter are of course closed.
Påverkas nu i fig. 1 manöverdonet 23 för att exempelvis bringa inloppsslidventilen 27 att släppa fram tryckvätska från källan 22 till förkammaren 33, måste uppenbarligen trycket i denna förkammare först uppnå en tillräckligt hög nivå för att I 45.5 637 4 öppna backventilen 38. innan vätskan kan strömma vidare genom kanalen 29 fram till motorinloppet B. Pumpen 100 levererar även i tomgång vätska med ett visst minimitryck, som är tillräckligt för att ställa om växelventilen 80 och för att via kanalen 83, växelventilen 82 och utloppsanslutningen LSl påverka regulatorn 102, så att pumptrycket ökas till erforderlig nivå för att öppna backventilen 58. Först när så skett börjar sålunda hydraulcylin- derns 20 kolvstáng 21 att förflytta sig åt vänster i figuren.If the actuator 23 is now actuated in Fig. 1 to, for example, cause the inlet slide valve 27 to release pressure fluid from the source 22 to the antechamber 33, obviously the pressure in this antechamber must first reach a sufficiently high level to open the non-return valve 38 before the fluid can flow further through the channel 29 to the motor inlet B. The pump 100 also delivers liquid at idle with a certain minimum pressure, which is sufficient to switch the changeover valve 80 and to influence the regulator 102 via the channel 83, the changeover valve 82 and the outlet connection LS1, so that the pump pressure is thus increased to the required level to open the non-return valve 58. Only when this has happened does the piston rod 21 of the hydraulic cylinder 20 thus begin to move to the left in the figure.
Om i stället manöverdonet 23 påverkas för att bringa sliden i inloppsventilen 27 att röra sig åt vänster i figuren och att därmed släppa fram tryckvätska till förkammaren 32, kommer det tryck, som bygges upp i denna förkammare 52 för att slutligen öppna backventilen 37, att omställa växelventilen 82 och att där- med i sin tur påverka regulatorn 102, så att pumptrycket anpassas efter vad som krävs för att hydraulcylinderns 20 kolvstàng 21 skall förflyttas åt höger i figuren.If, instead, the actuator 23 is actuated to cause the slide of the inlet valve 27 to move to the left in the figure and thereby release pressure fluid to the antechamber 32, the pressure which builds up in this antechamber 52 to finally open the non-return valve 37 will change. the changeover valve 82 and thereby in turn actuate the regulator 102, so that the pump pressure is adapted to what is required for the piston rod 21 of the hydraulic cylinder 20 to be moved to the right in the figure.
Det bör stå klart, att det förkammaretryck, i 52 resp. 33. som från fall till fall erfordras för att öppna backventilen 37 resp. 38, bestäms av å ena sidan backventilens fjäderbelastning och á andra sidan det mottryck, som i vissa fall kan råda i kana- len 28_resp. 29 och som utgör ett mätt på den belastning, för vilken hydraulmotorn eventuellt är utsatt. Backventilens fjäder- belastning säkerställer, att den passerande vätskans tryck all- tid är tillräckligt för att åstadkomma ett inflöde av vätska till tillhörande motorinlopp A resp. B. Genom kanal- och växel- ventilsystemet 79-84 avkännes den belastning, för vilken hydraul- motorn 20 i varje ögonblick står, och trycket hos den av tryck- vätskekällan 22 levererade tryckvätskan styrs i beroende av denna belastning på ett sätt. som kan betecknas såsom förutseende.It should be clear that the atrial pressure, in 52 resp. 33. which from case to case is required to open the non-return valve 37 resp. 38, is determined on the one hand by the spring load of the non-return valve and on the other hand by the back pressure, which in some cases may prevail in the channel 28_resp. 29 and which is a measure of the load to which the hydraulic motor may be exposed. The spring load of the non-return valve ensures that the pressure of the passing liquid is always sufficient to cause an inflow of liquid to the associated motor inlet A resp. B. The channel and gear valve system 79-84 senses the load that the hydraulic motor 20 is at any moment, and the pressure of the pressure fluid supplied by the pressure fluid source 22 is controlled in a manner dependent on this load. which can be described as foresight.
Om nu ytterligare en motor-ventil-enhet är ansluten till tryckvätskekällan 22 via den förutnämnda kopplingsplinten 10%, kommergminst en ytterligare förkammare liknande förkamrarna 32 och 33 att via inloppsanslutningen LS2 vara ansluten till kanal- och växelventilsystemet 79-84. Därigenom kommer även belastningen på den tillfogade hydraulmotorn att avkännas och, om denna andra motor kräver ett högre matartryck från tryckvätskekällan 22 än motorn 20, att överta uppgiften att styra trycket hos den från tryckvätskekällan 22 levererade tryckvätskan. Det förhållandet, att matartrycket då ökas även till den första motorns 20 ventil- 455 63? 5 hus 24. har givetvis ingen skadlig verkan. och att märka är. att matartryoket snabbt reduceras så snart som ingen av de båda hydraulmotorerna är i arbete eller belastningen på den eller de arbetande hydraulmotorerna sjunker. ' Givetvis kan pà liknande sätt flera motor-ventil-enheter kopplas till en och samma tryckvätskekälla genom att de egent- liga arbetskretsarna kopplas parallellt medan avkännarekretsarna, dvs kanal- och växelventilsystemen, kopplas s.a.s. i serie, såsom beskrivits i det föregående.If an additional motor-valve unit is now connected to the pressure fluid source 22 via the aforementioned coupling terminal 10%, at least one further antechamber similar to the antechambers 32 and 33 will be connected to the duct and changeover valve system 79-84 via the inlet connection LS2. Thereby, the load on the added hydraulic motor will also be sensed and, if this second motor requires a higher supply pressure from the pressure fluid source 22 than the engine 20, it will take over the task of controlling the pressure of the pressure fluid supplied from the pressure fluid source 22. The fact that the supply pressure is then also increased to the valve motor 455 63? 5 house 24. has of course no harmful effect. and to notice is. that the feed pressure is rapidly reduced as soon as neither of the two hydraulic motors is in operation or the load on the operating hydraulic motor or motors decreases. Of course, in a similar manner several motor-valve units can be connected to one and the same source of pressure fluid by the actual working circuits being connected in parallel while the sensor circuits, ie the duct and changeover valve systems, are connected, e.g. in series, as described above.
Den i fig. 2 visade hydraulkretsen skiljer sig från den i fig. l i huvudsak endast därigenom. att hydraulcylinderns 20 båda motorinlopp A resp. B har var sin volymströmstyrande inlopps- ventil 27a resp. 27b, som kan bringas att öppna från var sitt ventilhusinlopp 26a resp. 26b in till tillhörande förkammare 32 resp. 33 genom påverkan av manöverdonet 23. När den ena inlopps- ventilen 27a eller 27b i ventilhuset 24a öppnas genom tillförsel av manövertryck genom tillhörande manöverkanal 3la resp. 30a, hålls den andra inloppsventilen stängd av samma manövertryok. Även i detta fall kommer givetvis kanal- och växelventilsystemet 79-84, som är oförändrat i förhållande till det som visas i fig. 1, att sörja för. att tryckvätskekällans tryckregulator lO2 påverkas av det högsta arbetstryck, som uppträder i någon av de förkamrar 32, 33. som är anslutna till tryckvätskekällan 22; så att en ständig anpassning-av matartrycket àstadkommes.The hydraulic circuit shown in Fig. 2 differs from that in Fig. 1 substantially only thereby. that the two engine inlets A resp. B each has a volume flow control inlet valve 27a resp. 27b, which can be made to open from their respective valve housing inlets 26a resp. 26b into the associated antechamber 32 resp. 33 by actuation of the actuator 23. When one of the inlet valves 27a or 27b in the valve housing 24a is opened by supplying actuating pressure through the associated actuating channel 3la resp. 30a, the second inlet valve is kept closed by the same operating pressure. Also in this case, of course, the duct and changeover valve system 79-84, which is unchanged in relation to that shown in Fig. 1, will provide. that the pressure regulator source pressure regulator 102 is affected by the highest operating pressure which occurs in one of the atria 32, 33. which are connected to the pressure fluid source 22; so that a constant adjustment of the feed pressure is achieved.
Vid den hydraulkrets, som visas i fig. 3, är en enkelver- kande hydraulcylinder 20a med en kolvstång 2la och ett enda motorinlopp B ansluten till en tryckvätskekälla 22 via ett ven- tilhus 24b, som innefattar en enda volymströmstyrande inlopps- ventil 27b. Tryokvätskekällan 22 är genom en matarledning 25 an- sluten till ventilhusets 24b enda inlopp 26b samt till en kopp- lingsplint 10ü för eventuell anslutning av en ytterligare motor- ventil-enhet. I ventilhuset 24b ingår också en fjäderbelastad backventil 38, som tillsammans med inloppsventilen 27b avgrän- sar en förkammare 33, genom vilken tryokvätskan från källan 22 måste passera på sin väg från ventilhusinloppet 26b till motor- inloppet B. Förkammaren 33 är genom en kanal 79 ansluten till ena änden av en växelventil 80a, vars andra ände genom en kanal 81 och en därifrån utgående ledning är ansluten till inloppsan- slutningen LS2 i kopplingsplinten 10Ä, medan växelventilens 80a 455 637 6 mittparti är anslutet till tryokvätskekällans 22 tryckregulator 102 via utloppsanslutningen LSl. Manöverdonet 23 är i detta fall anordnat att antingen öppna inloppsventilen 27b mer eller mindre eller att öppna en utloppsventil 40, så att hydraulcylinderns 20a kolv kan återföras till ett utgångsläge av en kraft utövad av en returfjäder eller en belastning. I detta exempel är det tydligt, att trycket hos den från tryckvätskekällan 22 levererade tryckvätskan ständigt kommer att primärt anpassas till vad som krävs för att hydraulcylinderns 20a kolvstång 2la skall sättas i rörelse mot en eventuell belastning. Om emellertid en ytterli- gare motor-ventil-enhet är ansluten till kopplingsplinten 104 kan på samma sätt som tidigare beskrivits den tryckstyrande funk- tionen växla mellan de olika enheterna.In the hydraulic circuit shown in Fig. 3, a single-acting hydraulic cylinder 20a with a piston rod 2la and a single engine inlet B is connected to a source of pressure fluid 22 via a valve housing 24b, which includes a single volume flow control inlet valve 27b. The pressure fluid source 22 is connected via a supply line 25 to the only inlet 26b of the valve housing 24b and to a connection terminal 10ü for possible connection of an additional motor valve unit. The valve housing 24b also includes a spring-loaded non-return valve 38, which together with the inlet valve 27b defines an antechamber 33, through which the pressure fluid from the source 22 must pass on its way from the valve housing inlet 26b to the engine inlet B. The antechamber 33 is connected through a channel 79 to one end of a gear valve 80a, the other end of which is connected through a channel 81 and a conduit extending therefrom to the inlet connection LS2 in the terminal block 10Ä, while the middle portion of the gear valve 80a 455 637 6 is connected to the pressure regulator 102 pressure regulator 102 via the outlet connection LS1. The actuator 23 in this case is arranged to either open the inlet valve 27b more or less or to open an outlet valve 40, so that the piston of the hydraulic cylinder 20a can be returned to a starting position by a force exerted by a return spring or a load. In this example, it is clear that the pressure of the pressure fluid supplied from the pressure fluid source 22 will constantly be primarily adapted to what is required for the piston rod 2la of the hydraulic cylinder 20a to be set in motion against a possible load. However, if an additional motor-valve unit is connected to the terminal block 104, the pressure-controlling function can switch between the different units in the same way as previously described.
Av de visade och beskrivna exemplen torde framgå, att upp- finningen erbjuder en värdefull möjlighet att fortlöpande anpassa det tryck, som en tryckvätskekälla levererar till en hydraulisk krets, efter vad kretsen vid varje tillfälle behöver. Samtidigt säkerställer naturligtvis förekomsten av en backventil mellan in- loppsventilen och motorinloppet inte blott på i och för sig känt sätt att vätska i händelse av brott pà matarledningen från tryck- vätskekällan hindras från att baklänges strömma ut genom inlopps- ventilen, om denna skulle stå helt eller delvis öppen eller av något skäl medge läckage, utan också att ett i motorinloppet even- tuellt rådande tryck föronsakat av en belastning på hydraulmotorn hindras från att nå tryckvätskekällans tryckregulator.From the examples shown and described, it should be apparent that the invention offers a valuable opportunity to continuously adapt the pressure which a source of pressure fluid delivers to a hydraulic circuit, according to what the circuit needs at any given time. At the same time, of course, the presence of a non-return valve between the inlet valve and the engine inlet not only ensures in a manner known per se that liquid in the event of a break in the supply line from the pressure fluid source is prevented from flowing backwards through the inlet valve. or partially open or for some reason allow leakage, but also that any pressure prevailing in the engine inlet caused by a load on the hydraulic motor is prevented from reaching the pressure regulator of the pressure fluid source.
Ehuru de givna exemplen på hydrauliska kretsar, vid vilka uppfinningen tillämpats, visar en tryckvätskekälla, som omfattar en pump, vars angivna tryck är variabelt med hjälp av en deplace- mentregulator, bör det stå klart, att uppfinningen även kan till- lämpas vid kretsar. som matas från en pump med fast deplacement via en variabel tryckbegränsningsventil, i vilket fall sistnämnda ventil på motsvarande sätt styrs av trycket i någon av de före- fintliga förkamrarna. Resultatet blir i båda fallen, att den effekt, som krävs för att driva pumpen vid vilket som helst önskat flöde, reduceras vid alla de tillfällen, då maximalt tryck inte behöver användas i kretsen.Although the given examples of hydraulic circuits to which the invention has been applied show a source of pressurized fluid comprising a pump, the stated pressure of which is variable by means of a displacement regulator, it should be clear that the invention can also be applied to circuits. which is fed from a pump with fixed displacement via a variable pressure relief valve, in which case the latter valve is correspondingly controlled by the pressure in one of the existing antechambers. The result is in both cases that the power required to drive the pump at any desired flow is reduced at all times when maximum pressure does not need to be used in the circuit.
Claims (3)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/024,058 US4201052A (en) | 1979-03-26 | 1979-03-26 | Power transmission |
US11793680A | 1980-02-04 | 1980-02-04 |
Publications (3)
Publication Number | Publication Date |
---|---|
SE8503569L SE8503569L (en) | 1985-07-23 |
SE8503569D0 SE8503569D0 (en) | 1985-07-23 |
SE455637B true SE455637B (en) | 1988-07-25 |
Family
ID=26697984
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE8002302A SE443409B (en) | 1979-03-26 | 1980-03-25 | VALVE DEVICE FOR CONTROL OF THE FUNCTION OF A HYDRAULIC ENGINE |
SE8503569A SE455637B (en) | 1979-03-26 | 1985-07-23 | DEVICE ON A HYDRAULIC CIRCUIT |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE8002302A SE443409B (en) | 1979-03-26 | 1980-03-25 | VALVE DEVICE FOR CONTROL OF THE FUNCTION OF A HYDRAULIC ENGINE |
Country Status (10)
Country | Link |
---|---|
JP (1) | JPS6479405A (en) |
AU (1) | AU536970B2 (en) |
CA (1) | CA1142057A (en) |
DE (1) | DE3011088A1 (en) |
FR (1) | FR2452618A1 (en) |
GB (1) | GB2044366B (en) |
IN (1) | IN154913B (en) |
IT (2) | IT1221037B (en) |
NO (1) | NO155211C (en) |
SE (2) | SE443409B (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4345435A (en) * | 1980-05-05 | 1982-08-24 | Sperry Corporation | Power transmission |
US4353289A (en) * | 1980-05-29 | 1982-10-12 | Sperry Corporation | Power transmission |
FI72579C (en) * | 1981-11-12 | 1987-06-08 | Vickers Inc | Transmission. |
DE3347000A1 (en) * | 1983-12-24 | 1985-07-04 | Robert Bosch Gmbh, 7000 Stuttgart | Electrohydraulic arrangement for controlling a double-acting hydraulic motor |
CA1234529A (en) * | 1984-04-30 | 1988-03-29 | Vinod K. Nanda | Power transmission |
LU85774A1 (en) * | 1985-02-13 | 1985-07-24 | Hydrolux Sarl | STEUERBLOCK HYDRAULISCHER |
DE3629479A1 (en) * | 1985-09-03 | 1987-07-16 | Barmag Barmer Maschf | Directional control valve |
DE3841507C1 (en) * | 1988-01-22 | 1989-06-29 | Danfoss A/S, Nordborg, Dk | |
US5088384A (en) * | 1989-08-30 | 1992-02-18 | Vickers, Incorporated | Hydraulic actuator controlled by meter-in valves and variable pressure relief valves |
DE4342487B4 (en) * | 1993-12-13 | 2005-03-31 | Linde Ag | Hydrostatic drive system with after-suction valve |
DE10216958B8 (en) * | 2002-04-17 | 2004-07-08 | Sauer-Danfoss (Nordborg) A/S | Hydraulic control |
US20060168955A1 (en) * | 2005-02-03 | 2006-08-03 | Schlumberger Technology Corporation | Apparatus for hydraulically energizing down hole mechanical systems |
EP3064654A4 (en) * | 2013-10-31 | 2017-06-28 | Volvo Construction Equipment AB | Flow control valve for construction equipment, having floating function |
Family Cites Families (10)
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 |
GB1302741A (en) * | 1969-04-07 | 1973-01-10 | ||
DE1936370A1 (en) * | 1969-07-17 | 1971-02-04 | Volkswagenwerk Ag | Valve unit for controlling double-acting working cylinders |
DE2232857C2 (en) * | 1972-07-05 | 1983-11-24 | Robert Bosch Gmbh, 7000 Stuttgart | Control device for a hydraulically driven implement |
CH563532A5 (en) * | 1973-03-14 | 1975-06-30 | Buehler Ag Geb | |
SE387415B (en) * | 1974-03-22 | 1976-09-06 | Tedeco Ag | FLUID VALVE DEVICE |
DE2500096C3 (en) * | 1975-01-03 | 1984-08-02 | Sauer Getriebe KG, 2350 Neumünster | Hydraulic circuit device for pressure medium path control with constant control of the pressure medium flow for a double-acting hydraulic motor |
US3991571A (en) * | 1976-03-15 | 1976-11-16 | Caterpillar Tractor Co. | Fluid system of a work vehicle having fluid combining means and signal combining means |
JPS5482574A (en) * | 1977-12-13 | 1979-06-30 | Kobe Steel Ltd | Control circuit of actuator |
-
1980
- 1980-03-22 DE DE19803011088 patent/DE3011088A1/en not_active Withdrawn
- 1980-03-24 IT IT48246/80A patent/IT1221037B/en active
- 1980-03-25 AU AU56824/80A patent/AU536970B2/en not_active Ceased
- 1980-03-25 GB GB8009963A patent/GB2044366B/en not_active Expired
- 1980-03-25 NO NO800846A patent/NO155211C/en unknown
- 1980-03-25 CA CA000348366A patent/CA1142057A/en not_active Expired
- 1980-03-25 FR FR8006633A patent/FR2452618A1/en active Granted
- 1980-03-25 SE SE8002302A patent/SE443409B/en not_active IP Right Cessation
- 1980-09-02 IN IN1004/CAL/80A patent/IN154913B/en unknown
-
1985
- 1985-07-23 SE SE8503569A patent/SE455637B/en not_active IP Right Cessation
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1988
- 1988-09-06 JP JP63223358A patent/JPS6479405A/en active Pending
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1989
- 1989-07-18 IT IT8948200A patent/IT1232358B/en active
Also Published As
Publication number | Publication date |
---|---|
AU536970B2 (en) | 1984-05-31 |
NO155211B (en) | 1986-11-17 |
IN154913B (en) | 1984-12-22 |
JPS6479405A (en) | 1989-03-24 |
FR2452618A1 (en) | 1980-10-24 |
NO155211C (en) | 1987-02-25 |
IT1221037B (en) | 1990-06-21 |
SE8503569L (en) | 1985-07-23 |
IT8048246A0 (en) | 1980-03-24 |
GB2044366A (en) | 1980-10-15 |
DE3011088A1 (en) | 1980-10-09 |
SE443409B (en) | 1986-02-24 |
FR2452618B1 (en) | 1984-02-24 |
SE8002302L (en) | 1980-09-27 |
IT8948200A0 (en) | 1989-07-18 |
NO800846L (en) | 1980-09-29 |
IT1232358B (en) | 1992-01-28 |
SE8503569D0 (en) | 1985-07-23 |
GB2044366B (en) | 1983-08-03 |
AU5682480A (en) | 1980-10-02 |
CA1142057A (en) | 1983-03-01 |
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