EP0310454B1 - Régulateur de débit individuel à chute de pression constante - Google Patents
Régulateur de débit individuel à chute de pression constante Download PDFInfo
- Publication number
- EP0310454B1 EP0310454B1 EP19880309199 EP88309199A EP0310454B1 EP 0310454 B1 EP0310454 B1 EP 0310454B1 EP 19880309199 EP19880309199 EP 19880309199 EP 88309199 A EP88309199 A EP 88309199A EP 0310454 B1 EP0310454 B1 EP 0310454B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spool
- regulator
- land
- regulator spool
- vertical compartment
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F15B13/02—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
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
- 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
- F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
Definitions
- the present invention relates generally to the art of hydraulic valves used to regulate fluid flow. More specifically, the present invention relates to a valve which controls the flow across the spool opening of a proportional, directional valve as load or system pressures fluctuate.
- United States Patent No. 4,574,839 issued on March 11, 1986 to Yeh, et al discloses a pressure compensated directional control valve.
- the valve allows the flow rate to a given hydraulic load to be constant regardless of the load imposed and uses a piston mounted within a sleeve valve insert and a number of springs, wherein the piston moves to create a variable orifice to control the hydraulic fluid flow to the load.
- An adjustable sleeve works in connection with a hollow piston to provide for proper operation of the valve.
- FR-A-2180912 discloses a flow regulating valve designed to regulate flow of a fluid to a hydraulic device supporting a load, said valve having a valve body with means for supplying fluid to said body and comprising a first work port designed to be coupled to a hydraulic device supporting a load; means for controlling fluid flow in said valve to selectively seal off said first work port, permit fluid to flow to said first work port from said supply means or permit fluid to be exhausted from said first work port; means for sensing the load pressure induced by a load coupled to said first work port; means for generating feedback pressure representative of the flow of fluid from said supply means to said first work port; and means for comparing said load pressure and said feedback pressure, said comparing means comprising a generally cylindrical regulator spool axially movable within said valve and positioned so that feedback pressure is sensed on the lower face of said spool and the load pressure is sensed on the upper face of said spool, the position of said spool thereby being determined by the difference between the load pressure and the feedback pressure.
- a flow regulating valve including a valve body having a supply port, a work port designed to be coupled to a hydraulic device which creates a load pressure at said work port, an exhaust port capable of exhausting fluid from said work port, a horizontal bore intersecting said work port and said exhaust port, a vertical compartment intersecting said horizontal bore and said supply port, said vertical compartment having an upper bore land and lower bore land, said supply port being located between said upper and lower lands in said vertical compartment, a main spool in said horizontal bore being moveable to allow a first orifice to be opened to a preselectable area between said work port and said vertical compartment, and movable to a position in which said work port communicates with said exhaust port, a regulator spool biased towards the horizontal bore by a biasing force in said vertical compartment, said regulator spool having an upper land and a lower land, said upper land of said vertical compartment and said upper land of said regulator spool forming a fluid seal and bearing support that defines an upper chamber in said vertical compartment and lower chamber
- the regulator can also act as a maximum segment pressure limiter by inclusion of an orifice in the communicating line between the main spool load sensing flow passage and the load sensing spring chamber of the regulator valve. Once the pressure drop caused by a pilot relief valve exceeds the spring pre-load force on the regulator spool the regulator spool will close off flow to the main spool and will create a slight amount of leakage to maintain the pilot relief set pressure.
- FIGURE 1 The regulator of the present invention is shown in FIGURE 1 embodied in a housing 20. Two bores are drilled through housing 20, the first being the main spool bore 22 and the two landed regulator compartment 24. Cylinder ports 26, 27 are in communication with the main spool bore 22. Main spool bore 22 intersects regulator compartment 24 perpendicularly, with regulator compartment 24 terminating at it lower end at the main spool bore 22.
- a generally U-shaped chamber 28 connects sides of the main spool 30 on either side of the regulator compartment 24.
- the main spool 30 has a pair of lands 32 which permit or restrict fluid communication between chamber 28 and compartment 24. Additionally, main spool 30 has lands 34 which permit or restrict fluid communication between the chamber 28 and the cylinder ports 26, 27. Movement of the main spool 30 either to the left or the right will permit selective communication between one of the cylinder ports 26, 27 and the regulator compartment 24. When main spool 30 is shifted, the cylinder port which does not receive fluid from the supply communicates with the appropriate exhaust port 36 or 37.
- Regulator compartment 24 is sealed at its upper end with a plug 38 utilizing an O-ring 40 to assure a tight seal.
- Compartment 24 has a first metering land 42 and an upper slidable spool land 44 which acts as a bearing support for the spool 46. Fluid from a supply port 48 enters the regulator compartment 24 between lands 42 and 44.
- regulator spool 46 also has two lands - a metering land 50 and an upper land 52 which slides within the upper bore land 44.
- regulator spool lands 50 and 52 and bore lands 42 and 44 all have the same nominal diameters.
- a bias spring 54 biases the regulator spool 46 downward toward the main spool bore 22.
- a spring chamber 56 is defined by the upper portion of regulator spool 46, the plug 38 and the walls of regulator compartment 24.
- the U-shaped chamber 28 is in fluid communication with the spring chamber 56 by way of a sensing passage 58 therebetween.
- the lower surface 60 of regulator spool 46 serves as a feedback surface. That is, fluid under pressure within the regulator compartment 24 beneath land 42 induces a feedback signal on the lower surface 60 of regulator spool 46 which counteracts the force caused by bias spring 54.
- FIGURE 1 shows the valve of the present invention in its neutral state, that is, with regulated fluid flow to neither cylinder port 26 nor 27.
- handle 31 which controls the position of main spool 30, may be arcuately moved either up or down. Movement of handle 31 induces movement of the main spool 30.
- FIGURE 2 shows the main spool shifted to the right as a result of handle 31 being raised.
- This right hand movement of the main spool 30 causes fluid communication to open between cylinder port 26 and vent 36, thereby permitting passage of fluid from cylinder port 26 to the exhaust port 36.
- fluid communication is permitted between cylinder port 27 and the supply bore 48.
- Supply flow from port 48 is throttled across the unsupported land 50 of the regulator spool 46 as it opens away from the valve bore land 42. The only time the metering land 50 of the regulator spool 46 is supported is when it is shut off.
- a load pressure from port 27 is transmitted to the spring chamber 56 above regulator spool 46 when the main directional control spool 30 is shifted to the right, as shown in FIGURE 2.
- the load pressure will be sensed in the spring chamber 56.
- the load pressure acting on the top of the regulator spool 46 will cause the regulator spool metering land 50 to open away from bore land 42.
- the regulator spool land 50 opens, the increasing flow to the main spool 30 will result in an increasing pressure drop across the main spool area opening at land 32.
- This opposing force is a feedback force that is used to close down the regulator spool metering land 50 as flow and the pressure drop across the main spool 30 increase beyond the pre-load force of the bias spring 54.
- the regulated/feedback pressure is upstream of the main spool area opening at land 32, making it a higher pressure than the load pressure due to the pressure drop across the main spool 30. Therefore, the pressure drop across the main spool 30 will equal the spring pre-load force acting on the regulator spool 46 since the load pressure plus the spring pre-load force will collectively equal the regulated pressure.
- the regulator spool metering land 50 will position itself to allow for the forces to become balanced, and the metering land 50 will automatically adjust its position within chamber 24 as the main spool metering area along land 32 changes and/or as the load pressure or supply fluid pressure to the regulator spool 46 itself changes.
- the feedback surface 60 at the end of the spool 46 is part of the metering land 50 that throttles the supply pressure from port 48 to the regulated pressure.
- the supply fluid pressure is throttled down to a lower "regulated" pressure
- the fluid flows around the metering land 50 of the spool 46 to act directly on the area 60 at the end of the spool 46.
- the regulated pressure creates a feedback force directly upon end 60 of the spool 46 as the fluid flows to the main spool area opening at land 32.
- An angle 51 is added to the regulator spool metering land 50 to compensate for the flow forces acting on the spool 46.
- the spool displacement greatly increases as the flow forces tend to close down the spool opening between metering land 50 and valve bore land 42.
- the spool displacement causes the effect of the spring pre-load to increase, which offsets the opposing flow forces.
- Another feature which may be added to the system is the ability of the regulator to act as a maximum segment pressure limiter. If an orifice 62, as seen in shadow in FIGURE 2, is installed in the communicating line 58 between the main spool load sensing flow passage 28 and the load sensing spring chamber 56 of the regulator valve, then a pressure drop will be taken across the orifice 62 when a pilot relief valve is connected into the spring chamber 56 and as the relief valve is cracked open to its preset valve. Once the pressure drop exceeds the spring pre-load force of spring 54 on the regulator spool 46, the regulator spool 46 will close off flow to the main spool 30 and will create just enough leakage between land 50 and land 42 to maintain a pressure at which the pilot relief was set. This is done to limit the maximum pressure to a function or to maintain a fixed clamping force on a cylinder or a fixed torque on a rotary motor.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Control Of Fluid Pressure (AREA)
- Fluid-Pressure Circuits (AREA)
Claims (6)
- Soupape de régulateur de débit comportant un corps de soupape (20) pourvu d'un orifice d'alimentation (48), d'un orifice de travail (26, 27) destinés à être couplés à un dispositif hydraulique créant une pression de charge sur l'orifice de travail, d'un orifice de sortie (36, 37) apte à faire sortir le fluide dudit orifice de travail, d'un alésage horizontal (22) raccordant l'orifice de travail et l'orifice de sortie, d'un compartiment vertical (24) raccordant l'alésage horizontal et l'orifice d'alimentation, ledit compartiment vertical comportant un épaulement supérieur d'alésage (44) et un épaulement inférieur d'alésage (42), ledit orifice d'alimentation étant situé entre lesdits épaulements inférieur et supérieur dans le compartiment vertical, d'un tiroir étagé (30) dans l'alésage horizontal qui est déplaçable de façon à ouvrir un premier orifice vers une zone présélectionnée entre ledit orifice de travail et ledit compartiment vertical, et déplaçable vers une position dans laquelle l'orifice de travail communique avec l'orifice de sortie, d'un tiroir de régulation (46) poussé dans le compartiment vertical vers l'alésage horizontal par une force de poussée (54), ledit tiroir de régulation comportant un épaulement supérieur (52) et un épaulement inférieur (50), ledit épaulement supérieur (44) dudit compartiment vertical et ledit épaulement supérieur (52) dudit tiroir de régulation formant une étanchéité au fluide et un appui, ce qui définit une chambre supérieure dans le compartiment vertical et une chambre inférieure dans le compartiment vertical, d'un passage de détection (58) reliant ladite chambre supérieure au dit orifice de travail afin de permettre que la pression de charge soit établie dans la chambre supérieure, caractérisée en ce que le tiroir de régulation (46) solide comporte une face inférieure (60) faisant face à l alésage horizontal, l'épaulement inférieur (50) du tiroir de régulation et l'épaulement inférieur (42) du compartiment vertical formant un second orifice de taille variable, la taille du second orifice étant déterminée par la position dudit tiroir de régulation dans le compartiment vertical, ledit tiroir principal étant positionné pour ouvrir le premier orifice vers une première position présélectionnée, la pression de charge établie dans la chambre supérieure poussant le tiroir de régulation vers le bas en appuyant sur sa face supérieure, une pression de rétroaction établie dans la chambre inférieure poussant le tiroir régulateur vers le haut en appuyant sur sa face inférieure, la position du tiroir de régulation étant ainsi déterminée par la différence entre la pression de rétroaction exercée sur le fond du tiroir de régulation et la combinaison des pressions de poussée et de charge exercées sur le sommet du tiroir de régulation.
- Soupape selon la revendication 1, caractérisée en ce que le compartiment vertical est étanché à son extrémité supérieure avec un bouchon (38), et en ce que les forces de poussées sont produites par un ressort (54) logé entre le bouchon et la face supérieure du tiroir de régulation.
- Soupape selon la revendication 1 ou 2, caractérisée en ce que l'épaulement inférieur du tiroir de régulation présente une conicité (51) pour compenser les forces du fluide agissant sur ledit tiroir de régulation.
- Soupape selon la revendication 1, 2 ou 3, caractérisée en ce qu'une chambre intermédiaire en forme de U (28) est positionnée de telle sorte que ses extrémités supérieures se raccordent à l'alésage horizontal de chaque côté de l'intersection entre l'alésage horizontal et le compartiment vertical ladite chambre intermédiaire reliant l'orifice de travail, le passage de détection, et le premier orifice.
- Soupape selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'un troisième orifice (62) fixé est placé dans le passage de détection et en ce qu'une servo-valve de sureté (63) est couplée à la chambre supérieure, limitant ainsi la pression maximale à l'intérieur de l'alésage horizontal.
- Soupape selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le tiroir de régulation comporte en outre une bague de limitation (53) pour limiter le mouvement vers le bas du tiroir de régulation à l'intérieur du compartiment vertical.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10361087A | 1987-10-02 | 1987-10-02 | |
US103610 | 2008-04-15 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0310454A2 EP0310454A2 (fr) | 1989-04-05 |
EP0310454A3 EP0310454A3 (en) | 1990-11-28 |
EP0310454B1 true EP0310454B1 (fr) | 1994-08-24 |
Family
ID=22296071
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19880309199 Expired - Lifetime EP0310454B1 (fr) | 1987-10-02 | 1988-10-03 | Régulateur de débit individuel à chute de pression constante |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0310454B1 (fr) |
JP (1) | JPH01145401A (fr) |
CA (1) | CA1302203C (fr) |
DE (1) | DE3851193T2 (fr) |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1033109A (en) * | 1963-07-19 | 1966-06-15 | Dowty Hydraulic Units Ltd | Control valves for fluid-pressure-operated mechanisms |
US3534774A (en) * | 1968-11-14 | 1970-10-20 | Koehring Co | Pressure compensated control valve |
US3901264A (en) * | 1972-03-06 | 1975-08-26 | Gresen Manufacturing Co | Adjustable flow control for hydraulic valves having high pressure main supply and controls fluid flow to cylinder and exhaust ports |
US3774635A (en) * | 1972-04-18 | 1973-11-27 | Sperry Rand Corp | Power transmission |
US4037410A (en) * | 1976-05-26 | 1977-07-26 | The Cessna Aircraft Company | Hydraulic control valve |
US4154262A (en) * | 1977-10-17 | 1979-05-15 | Gresen Manufacturing Company | Hydraulic control system |
US4253482A (en) * | 1979-03-05 | 1981-03-03 | Gresen Manufacturing Company | Hydraulic valve having pressure compensated demand flow |
US4519420A (en) * | 1982-09-29 | 1985-05-28 | Commercial Shearing, Inc. | Hydraulic valves |
CA1246425A (fr) * | 1984-02-13 | 1988-12-13 | Raud A. Wilke | Distributeur hydraulique monobloc a compensateur de pressions inverses |
DE3540061A1 (de) * | 1985-02-28 | 1987-05-14 | Rexroth Mannesmann Gmbh | Mehrwegeventil mit druckwaage |
DE3507121A1 (de) * | 1985-02-28 | 1986-08-28 | Mannesmann Rexroth GmbH, 8770 Lohr | Mehrwegeventil mit druckwaage |
-
1988
- 1988-10-03 EP EP19880309199 patent/EP0310454B1/fr not_active Expired - Lifetime
- 1988-10-03 DE DE19883851193 patent/DE3851193T2/de not_active Expired - Lifetime
- 1988-10-03 CA CA000579109A patent/CA1302203C/fr not_active Expired - Lifetime
- 1988-10-03 JP JP24972588A patent/JPH01145401A/ja active Pending
Also Published As
Publication number | Publication date |
---|---|
EP0310454A2 (fr) | 1989-04-05 |
DE3851193T2 (de) | 1995-04-06 |
CA1302203C (fr) | 1992-06-02 |
DE3851193D1 (de) | 1994-09-29 |
JPH01145401A (ja) | 1989-06-07 |
EP0310454A3 (en) | 1990-11-28 |
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