GB1580946A

GB1580946A - Flow control valve

Info

Publication number: GB1580946A
Application number: GB52833/77A
Authority: GB
Original assignee: Abex Corp
Current assignee: PepsiAmericas Inc
Priority date: 1977-05-27
Filing date: 1977-12-19
Publication date: 1980-12-10
Also published as: IT7847956A0; CA1092484A; IT1103589B; FR2392298A1; JPS541766A; FR2392298B1; DE2814103A1

Description

(54) FLOW CONTROL VALVE (71) We, ABEX CORPORATION, a corporation organized and existing under the laws of the State of Delaware, United States of America, of 530 Fifth Avenue, New York, State of New York 10036, United States of America, do hereby declare the invenion, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: A simple fonn of flow control is a fixed orifice. A more sophisticated type of flow control is a manually adjustable, variable orifice. One type of manually adjustable, variable orifice is a needle valve.

An orifice, either fixed or adjustable, is inserted in a line and sets the area available for fluid flow. It is frequently used with a pressure compensator to provide a constant flow of fluid to a device. A pressure compensator maintains a constant fluid pressure differential across the inlet and outlet of the orifice. If the pressure drop across the orifice is uniform, the flow through the orifice is constant regardless of variations in fluid pressure upstream or downstream of the orifice.

One device which requires a constant fluid flow rate is a hydraulic motor. This enables the motor to turn at a constant speed.

Another device is a hydraulic cylinder where it is necessary to provide a constant flow of fluid to enable the piston to move at a constant speed in the cylinder.

U.S. Patent No. 3,246,669 discloses a fixed orifice, pressure compensated flow control.

This control uses pilot fluid for a control fluid. The control fluid is fed from the inlet port through a fixed orifice and is pressure compensated. The pressure drop across the fixed orifice is maintained constant by a control piston in which the right end of the piston is exposed to pressure upstream of the orifice and the opposite end is subjected to fluid pressure downstream of the orifice which acts in conjunction with a light spring to resist movement of the piston caused by the high pressure fluid in a well known manner. Movement of the control piston causes a land on the control piston to restrict or increase flow through a port to thereby maintain a constant flow of fluid through the orifice.

A more sophisticated flow control is shown in U.S. Patent No. 3,200, 832. This control uses an electrical device for changing the size of a metering orifice. In this control the pressure differential of pilot fluid across a variable orifice acts on a metering spool to change the size of the metering orifice. The maximum force available to move the metering spool is limited to the amount of pressure drop across the variable orifice which is typically 100 psi. This control includes a pressure compensator assembly which assures a constant pressure differential across the main metering orifice.

An electrohydraulic flow control where the pilot fluid is pressure compensated to assure a constant flow rate is also shown in U.S. Patent No. 3,159,178. With a constant rate of fluid flow, the gap between the armature and the core remains the same for any selected flow rate setting and therefore the force in the poppet which controls the level of pilot pressure remains constant. If the pilot flow were not constant and the gap between the armature and core varied to accommodate different flow rates, the electro-magnetic force acting on the piston which controls the pilot pressure would not be uniform and the opening of the controlled orifice would not correspond to a given setting (either current or voltage) or the electric controller.

Another type of electrically controlled orifice can be found in ajet pipe or flapper type servo valve. In this type of valve the metering orifice spool is caused to move by the pressure differential across the ends of the spool caused by the difference of pressure between the jet pipe receiver ports. The difference in pressure in these receiver ports is a maximum of approximately 65% of the fluid inlet pressure at maximum input to the jet pipe coil.

It has been found that it is sometimes necessary to have a larger pressure differential acting across the spool which sets the size of an orifice than can be obtained from a conventional flow control using a pilot fluid or a jet pipe type of servo valve.

According to the present invention we provide a flow control valve having metering orifice opening in proportion to an electric current comprising: a body, a fluid inlet in the body, a fluid outlet in the body, a bore in the body which connects the fluid inlet and outlet, a metering spool mounted in the bore, a land in the bore between the fluid inlet and outlet, a control surface on the spool co-operative with the land to form an orifice between the fluid inlet and outlet wherein the size of the orifice is dependent upon the relative linear position of the metering spool and land, means for connecting said inlet, to a source of fluid under pressure, a control chamber at one end of the metering spool, passage means for providing pilot fluid from the fluid inlet to the control chamber, means for maintaining a constant rate of pilot fluid flow, said pilot fliud in the control chamber biasing the metering spool to open the orifice, means for connecting the other end of the metering spool to low (tank) pressure, spring means at said other end of the metering spool opposing the force of the pilot fluid and biasing the spool to close the orifice, a second valve for controlling the pressure of the pilot fluid in the control chamber to set the position of the metering spool and the orifice size, means connecting the control chamber with the valve, wherein the second valve includes a movable control spool and a seat, said second valve forming a second variable orifice the opening of which is determined by the relative positions of the control spool and a seat, a solenoid having a movable plunger tending to close the second valve, means for adjusting the force of the plunger acting on the second valve in response to an electrical input to the solenoid, a feedback spring positioned between the metering spool and the control spool tending to open the second valve, wherein the force of the plunger sets the size of the second orifice which sets the pressure of the pilot fluid, and the pilot fliud in the control chamber moves the metering spool to open the first orifice and the resulting movement of the metering spool biases the feedback spring against the valve control spool to overcome the solenoid plunger force and open the second valve to thereby limit the pressure of the pilot fluid and stop the movement of the metering spool when the force of the feedback spring on the control spool equals the force of the solenoid plunger.

An embodiment of the invention will now be further described, by way of example only, with reference to the accompanying drawings: Figure 1 is a partial cross-sectional view of an electrically controlled flow control valve.

Figure 2 is a view along lines 2-2 of Figure 1 showing the inlet and outlet ports of the metering orifice.

Referring to Figures 1 and 2 of the drawings, a flow control valve 10 comprises a main housing 11 which contains a metering spool 12 axially movable in a longitudinal bore 13. Metering spool 12 has a pair of lands 14, 15 at opposite ends which taper along surfaces 16, 17 respectively to a reduced diameter portion 18.

Inlet port P, is connected to the outlet or exhaust port P0 through land 19 in bore 13.

Metering spool 12 is axially movable in bore 13 between a first extreme position in which land 14 co-operates with land 19 to seal the passage between the ports P, P0, through an intermediate position in which the tapered surface 16 co-operates with land 19 to limit the flow of fluid from port P1 to port PO, to the second extreme position in which reduced diameter portion 18 of spool 12 co-operates with land 19 to permit maximum fluid flow from port P1 to port P0. The position of metering spool 12 is determined by the amount of electrical input to a solenoid as described below.

Metering spool 12 is moved by pilot fluid which enters a port 20 in metering spool 12 and flows through a small pressure compensate ed, fixed rate, flow control assembly which meters in approximately one quart per minute of the pilot fluid to a control chamber 21 at one end of spool 12 as will now be described. The flow control assembly provides a constant flow of pilot fluid for controlling spool 12 regardless of variation in pressure of the fluid in the inlet port P, The internal flow control assembly is mounted in an internal, axial bore 22 in metering spool 12. The assembly includes a hub 23 which has an internal bore 24 and is bottomed in bore 22 against a lateral support 25 on spool 12. Hub 23 is secured in position by a sleeve 26 with an internal bore 27 which is sealed by an end cap 28.Hub 23, sleeve 26 and cap 28 are retained in bore 22 by a spacer 29 and a spring clip 30.

A flow control piston 31 with an internal bore 32 and a metering orifice 33 is slidably received in sleeve bore 27. A spring 34 mounted in piston bore 32 acts against end cap 28 to bias piston 31 towards the bottom surface of hub bore 24.

Fluid port 20 is aligned with another port 35 in the side wall of hub 23 to permit pilot fluid to flow into bore 24. Pilot fluid in bore 24 acts against end 36 of flow control piston 31 to move the piston 31 against spring 34 sufficiently to permit pilot fluid to flow through control orifice 33. The balanced piston 31 and spring 34 set the pressure drop across orifice 33. Pilot fluid flows from the interior of piston 3 1 through fluid passage 37 to the outside of sleeve 26. The fluid then flows through bores 38, 39 in end cap 28 and spacer 29, respectively, to the control chamber 21 formed by enlarged internal bore 40 in metering spool 12.

The pressure of the pilot fluid in chamber 21 sets the position of metering spool 12.

Bore 13 is sealed at one end by a plug 41 which sets the first extreme position of spool 12.

A fluid port 42 opens into the right end of bore 13 and receives pilot fluid from control chamber 21 when spool 12 is moved away from plug 41. Port 42 is connected through fluid passage 43 to a port 44 which opens into the left end of bore 13. Port 44 is aligned with a lateral bore 45 in a sleeve 46 which is press fitted into bore 13. Sleeve 46 has an internal bore 47.

A balanced seat control poppet 48 with ball bearings 49 mounted on its outside diameter 50 is mounted in sleeve bore 47. The function of poppet 48 is to set the pressure of the pilot fluid and thereby set the position of metering spool 12 as described below. Control poppet 48 has an enlarged end 51 with a tapered edge 52 which co-operates with a seat 53 formed by an edge on one end of sleeve 46 to provide a second variable orifice. The diameter of seat edge 53 is equal to the diameter of the sleeve bore 47 so that the effective areas are equal. Therefore, there is no net longitudinal force acting on poppet 48 from the pilot fluid.

Pilot fluid from bore 45 flows through the variable orifice to a cavity 54 at the left end of poppet 48 and into a passage 55 in the poppet 48. A hub 56 having an internal bore 57 is seated against one end of the sleeve 46. From passage 55 the pilot fluid flows through bore 57 into a cavity 58 in bore 13 between hub 56 and spool 12. Clearance is provided between hub 56 and a port T connected to tank in order to pass fluid from cavity 58.

A heavy spring 59 has one end seated around a protrusion 60 on a hub 56 and the other end bottomed in an internal bore 61 in the left end of metering spool 12. The spring 59 biases spool 12 to the right against plug 41.

A light fcedback spring 62 passes through internal bore 57 in hub 56 and has one end scated in a bore 63 in the right end of poppet 48 and has its other end seated around a cylindrical projection 64 on hub 23. Feedback spring 62 exerts a force on the right side of control poppet 48. The magnitude of the force is dependent upon the axial position of metering spool 12.

The poppet 48 is also acted upon by a solenoid pin 65 which engages the left side of the poppet. The amount of force exerted by pin 65 is dependent upon the current or voltage supplied to a solenoid 66 which imparts force to pin 65 in a well known manner.

Therefore, a particular current or voltage input to solenoid 66 produces a force on the left side of poppet 58 which is counterbalanced by the force on the right side exerted by feedback spring 62.

In operation, assuming the control valve 10 is closed, an electrical input is supplied to the solenoid 66 dependent upon the desired position of the metering spool 12. Pilot fluid from control chamber 21 flows into the port 42, passage 43, port 44 and bore 45 to the poppet 48. Since the poppet 48 is balanced, the pilot fluid will not move the poppet. The pressure of the pilot fluid in the control chamber 21 increases until the metering spool 12 moves to the left sufficiently for feedback spring 62 to exert a force on the right side of the poppet 48 which equals the force exerted on the left side by solenoid pin 65. There will be a small pressure drop across orifice 33; however, the pressure of the pilot fluid in chamber 21 can build to a level which, for all practical purposes, is as high as the pressure in the inlet port P, if it is necessary.It is some times necessary to reach a pressure substantially equal to inlet pressure in chamber 21 as when metering spool 12 is wedged in bore 13 by dirt.

When pilot fluid in control chamber 21 has moved metering spool 12 to the left to set an area of the metering orifice 16, 19, and feedback spring 62 exerts a force on poppet 48 which slightly exceeds the force on the left side of poppet 48 exerted by solenoid pin 65, the tapered edge 52 of the poppet 48 will move farther from seat 53. Increased pilot fluid will thus flow through the second variable orifice 52, 53 to tank and the pressure of the pilot fluid will stop increasing. At this time, the leftward movement of the control spool 12 will stop.

If the electrical input to the solenoid 66 is re-adjusted the force from the pin 65 on the control poppet 48 will change, which will unbalance the poppet 48 and change the size of the second variable orifice 52, 53. The pilot fluid pressure will change or shift metering spool 12 until poppet 48 is acted upon by equal forces at its opposite ends.

From the above, it can be seen that the area of the metering orifice 19, 16 is determined by the force exerted on the control poppet 48 by the solenoid pin 65, which force determines the size of the second variable orifice and the pressure of the pilot fluid. An increased force on poppet 48 by solenoid pin 65 will reduce the size of the second vraiable orifice 62, 53 and increase the pressure of the pilot fluid. The increased pilot fluid pressure will move the metering spool 12 to the left and enlarge the main metering orifice.

WHAT WE CLAIM IS: 1. A flow control valve having a metering orifice opening in proportion to an electric current comprising: a body, a fluid inlet in the body, a fluid outlet in the body, a bore in the body which connects the fluid inlet and outlet, a metering spool mounted in the bore, a land in the bore between the fluid inlet and outlet, a control surface on the spool co-operative with the land to form an orifice between the fluid in let and outlet wherein the size of the orifice is dependent upon the relative linear position of the metering spool and land, a means for connecting said inlet to a source of fluid under pressure, a control chamber at one end of the metering spool, passage means for providing pilot fluid from the fluid inlet to the control chamber, means for maintaining a constant

**WARNING** end of DESC field may overlap start of CLMS **.

Claims

**WARNING** start of CLMS field may overlap end of DESC **. from plug 41. Port 42 is connected through fluid passage 43 to a port 44 which opens into the left end of bore 13. Port 44 is aligned with a lateral bore 45 in a sleeve 46 which is press fitted into bore 13. Sleeve 46 has an internal bore 47. A balanced seat control poppet 48 with ball bearings 49 mounted on its outside diameter 50 is mounted in sleeve bore 47. The function of poppet 48 is to set the pressure of the pilot fluid and thereby set the position of metering spool 12 as described below. Control poppet 48 has an enlarged end 51 with a tapered edge 52 which co-operates with a seat 53 formed by an edge on one end of sleeve 46 to provide a second variable orifice. The diameter of seat edge 53 is equal to the diameter of the sleeve bore 47 so that the effective areas are equal. Therefore, there is no net longitudinal force acting on poppet 48 from the pilot fluid. Pilot fluid from bore 45 flows through the variable orifice to a cavity 54 at the left end of poppet 48 and into a passage 55 in the poppet 48. A hub 56 having an internal bore 57 is seated against one end of the sleeve 46. From passage 55 the pilot fluid flows through bore 57 into a cavity 58 in bore 13 between hub 56 and spool 12. Clearance is provided between hub 56 and a port T connected to tank in order to pass fluid from cavity 58. A heavy spring 59 has one end seated around a protrusion 60 on a hub 56 and the other end bottomed in an internal bore 61 in the left end of metering spool 12. The spring 59 biases spool 12 to the right against plug 41. A light fcedback spring 62 passes through internal bore 57 in hub 56 and has one end scated in a bore 63 in the right end of poppet 48 and has its other end seated around a cylindrical projection 64 on hub 23. Feedback spring 62 exerts a force on the right side of control poppet 48. The magnitude of the force is dependent upon the axial position of metering spool 12. The poppet 48 is also acted upon by a solenoid pin 65 which engages the left side of the poppet. The amount of force exerted by pin 65 is dependent upon the current or voltage supplied to a solenoid 66 which imparts force to pin 65 in a well known manner. Therefore, a particular current or voltage input to solenoid 66 produces a force on the left side of poppet 58 which is counterbalanced by the force on the right side exerted by feedback spring 62. In operation, assuming the control valve 10 is closed, an electrical input is supplied to the solenoid 66 dependent upon the desired position of the metering spool 12. Pilot fluid from control chamber 21 flows into the port 42, passage 43, port 44 and bore 45 to the poppet 48. Since the poppet 48 is balanced, the pilot fluid will not move the poppet. The pressure of the pilot fluid in the control chamber 21 increases until the metering spool 12 moves to the left sufficiently for feedback spring 62 to exert a force on the right side of the poppet 48 which equals the force exerted on the left side by solenoid pin 65. There will be a small pressure drop across orifice 33; however, the pressure of the pilot fluid in chamber 21 can build to a level which, for all practical purposes, is as high as the pressure in the inlet port P, if it is necessary.It is some times necessary to reach a pressure substantially equal to inlet pressure in chamber 21 as when metering spool 12 is wedged in bore 13 by dirt. When pilot fluid in control chamber 21 has moved metering spool 12 to the left to set an area of the metering orifice 16, 19, and feedback spring 62 exerts a force on poppet 48 which slightly exceeds the force on the left side of poppet 48 exerted by solenoid pin 65, the tapered edge 52 of the poppet 48 will move farther from seat 53. Increased pilot fluid will thus flow through the second variable orifice 52, 53 to tank and the pressure of the pilot fluid will stop increasing. At this time, the leftward movement of the control spool 12 will stop. If the electrical input to the solenoid 66 is re-adjusted the force from the pin 65 on the control poppet 48 will change, which will unbalance the poppet 48 and change the size of the second variable orifice 52, 53. The pilot fluid pressure will change or shift metering spool 12 until poppet 48 is acted upon by equal forces at its opposite ends. From the above, it can be seen that the area of the metering orifice 19, 16 is determined by the force exerted on the control poppet 48 by the solenoid pin 65, which force determines the size of the second variable orifice and the pressure of the pilot fluid. An increased force on poppet 48 by solenoid pin 65 will reduce the size of the second vraiable orifice 62, 53 and increase the pressure of the pilot fluid. The increased pilot fluid pressure will move the metering spool 12 to the left and enlarge the main metering orifice. WHAT WE CLAIM IS:

1. A flow control valve having a metering orifice opening in proportion to an electric current comprising: a body, a fluid inlet in the body, a fluid outlet in the body, a bore in the body which connects the fluid inlet and outlet, a metering spool mounted in the bore, a land in the bore between the fluid inlet and outlet, a control surface on the spool co-operative with the land to form an orifice between the fluid in let and outlet wherein the size of the orifice is dependent upon the relative linear position of the metering spool and land, a means for connecting said inlet to a source of fluid under pressure, a control chamber at one end of the metering spool, passage means for providing pilot fluid from the fluid inlet to the control chamber, means for maintaining a constant

rate of pilot fluid flow, said pilot fluid in the control chamber biasing the metering spool to open the orifice, means for connecting the other end of the metering spool to low (tank) pressure, spring means at said other end of the metering spool opposing the force of the pilot fluid and biasing the spool to close the orifice, a second valve for controlling the pressure of the pilot fluid in the control chamber to set the position of the metering spool and the orifice size, means connecting the control chamber with the valve, wherein the second valve in dudes a movable control spool and a seat, said second valve forming a second variable orifice the opening of which is determined by the relative positions of the control spool and seat, a solenoid having a movable plunger tending to close the second valve, means for adjusting the force of the plunger acting on the second valve in response to an electrical input to the solenoid, a feedback spring positioned between the metering spool and the control spool tending to open the second valve, wherein the force of the plunger sets the size of the second orifice which sets the pressure of the pilot fluid, and the pilot fluid in the control chamber moves the metering spool to open the first orifice and the resulting movement of the metering spool biases the feedback spring againt the valve control spool to overcome the solenoid plunger force and open the second valve to thereby limit the pressure of the pilot fluid and stop the movement of the metering spool when the force of the feedback spring on the control spool equals the force of the solenoid plunger.

2. A flow control valve according to Claim 1, wherein the means for maintaining a constant rate of pilot fluid flow includes a pressure compensated flow control valve mounted within the metering spool and the pressure compensated flow control valve includes a balanced piston and spring which sets the pressure drop across a third orifice.

3. A flow control valve according to Claim 1 or 2, including a stop member mounted in the bore between the metering spool and the second valve, the stop member having a second axial bore, the spring means engages said stop member and the feedback spring passes through the second axial bore without engaging the stop member.

4. A flow control valve according to Claims 1,2 or 3, wherein the second valve includes a balanced piston whereby the pilot fluid does not influence the opening of the second valve.

5. A flow control valve according to any one of the preceding Clams, including means blocking the flow of pilot fluid to maintain the second valve closed until the metering spool moves to open the first said orifice wherein the pressure of the pilot fluid can reach the pressure of the fluid in the inlet if said metering spool does not move.

6. A flow control valve substantially as hereinbefore described with reference to and as shown in the accompanying drawings.