EP0000445A1 - Servo valve - Google Patents
Servo valve Download PDFInfo
- Publication number
- EP0000445A1 EP0000445A1 EP78300136A EP78300136A EP0000445A1 EP 0000445 A1 EP0000445 A1 EP 0000445A1 EP 78300136 A EP78300136 A EP 78300136A EP 78300136 A EP78300136 A EP 78300136A EP 0000445 A1 EP0000445 A1 EP 0000445A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spool
- valve
- bore
- chamber
- orifice
- 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.)
- Granted
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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
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
- F15B13/0438—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being of the nozzle-flapper type
Definitions
- control pressure P is fed back to the armature via a nozzle bore and reacts with the torque motor and reaction spring to achieve a constant P c regardless of the pilot pressure P magnitude.
- control pressures vary with pilot supply pressure since P c is used as a feedback parameter.
- Jupa Another patent of interest-is that to E. C. Jupa, issued March 7, 1961, No. 2,973,746, which shows a bridge network.
- the adjustable nozzle is stationary and not attached to the main spool as in the instant invention.
- Jupa does not incorporate a moving nozzle with a one-to-one position feedback.
- Jupa also has two variable orifices.
- the flapper nozzle of course, is adjustable and his needle valve, on the end of the spool, is also adjustable.
- a flow control servo valve comprising a valve housing having an axial bore therethrough, a valve control spool axially movable within the bore so as to take up a balanced position with the housing and having an axial passageway therein extending from end to end of the spool to communicate with first and second end chambers one disposed at each end of the spool, a source of pilot pressure connected through first and second equal orifices respectively to the first and second end chambers, a third orifice equal to the first and second orifices and extending between the axial bore and the first end chamber, a fourth orifice of variable size between the axial bore and the second end chamber, and a force motor with an axially movable actuator member so arranged that axial movement of the actuator member varies the size of the variable orifice which in turn causes the control spool to move axial to assume a new position to reestablish the balance.
- This invention therefore provides a servo control valve wherein an electrical signal may be used to cause a mechanical movement which varies one orifice of a bridging network, which is carried by the main hydraulic spool, which causes a movement in the spool until balance is restored and accurate and continuous feedback is present for spool positioning.
- the invention also provides a pilot stage for a hydraulic control valve which comprises three fixed orifices and a single adjustable orifice, the latter of which may cooperate with an electromagnetic motor displacement to establish a variable orifice area that will control main spool location.
- the force motor proportionally varies pilot fluid pressure to thereby move the spool in proportion to the current or voltage used to adjust the space between a piston of the motor and a-nozzle formed on the main spool.
- the numeral 10 indicates a valve housing having a bore 12 therethrough. Reciprocally received within the bore 12 is a spool 14 equipped with four land areas 16, 18, 20, and 22. Between land areas 16 and 18 is a groove area 24, and between land areas 20 and 22 is a groove area 26. Land areas 18 and 20 are machined with close tolerances for reasons which will become apparent hereinafter.
- the valve housing 10 is machined with four internal grooves 28, 30, 32 and 34 located opposite the axial extremities of the land areas 18 and 20 when the spool 14 is in the position shown in Figure 2.
- Groove areas 24 and 26 communicate with a tank 36 (shown only in Figure 4) by way of a passageway 38 and a return can port 40.
- Internal grooves 28 and 30 /communicate with a load 42 by way of passageway 44, and ihternal grooves 32 and 34 can communicate with the load 42 by way of a passageway 46.
- Passageways 44 and 46 are closed and opened by the movements of land areas 18 and 20, respectively; in the location of the spool 14 shown in Figure 2, both.passageways are closed.
- a pressure groove 48 which communicates with a port 50 shown in Figure 1.
- the port 50 is connected to the output of a pump 52, so that pressure from the pump 52 is communicated to the pressure groove4 ⁇ and can then be communciated to either passageway 44 or passageway 46, depending on the position of spool 14.
- pressure from the pressure groove48 is communicated to neither passageway.
- pressurized fluid will flow to the load 42 through internal groove 30 and passageway 44 and return to tank 36 via passageway 46 and internal groove 34.
- pressurized fluid will flow to the load 42 through internal groove 32 and passageway 46 and return to tank 36 via passageway 44 and internal groove 2R.
- a chamber 54 closed by an end gland 56 retained in position on the valve housing 10 by clips 58 and bolts 60.
- End gland 56 receives a piston 62, a screw 64, a jam nut 66, and a centering spring 68.
- a chamber 70 which receives a second centering spring 72 and which is closed by apparatus described hereinafter.
- the piston 62, the screw 64, the jam nut 66 and the two centering springs 68 and 72 collectively serve as a mechanical "null" adjustment for the spool 14. That is, by adjusting screw 64 it is possible to initially locate land areas 18 and 20 on the spool 14 so that the internal grooves 28 and 30 align with land 18 and grooves 32 and 34 align witn land 2u of spool 14.
- Chambers 54 and 70 are subjected to intermediate control pressures by means of orifices 74 (A 1 ) and 76 (A 2 ), which communicate with the chambers 54 and 70 via the conduits 78 and 80, respectively.
- the orifices 74 and 76 are of fixed dimensions and are equal to each other.
- An isolated pilot port 82 communicates with the orifices 74 and 76 via an internal filter 84 which protects those orifices from fluid contamination.
- conduit 86 communicates at its right end with the groove area 26 via a hole 88 in the spool 14 and at its left end with the chamber 54 via a third fixed orifice 90 (A3) which is equal to orifice 74 (A,) and orifice 76 (A 2 ).
- a force motor 94 Attached to the right end of valve housing 10, as seen in Figure 2 by means of a mounting cap 92 is a force motor 94 having a force motor stem 96 terminating in a planar end 98 which extends toward the right end of the spool 14.
- the end of the spool 14 which faces the force motor 94 carries a pressed-in nozzle 100 having a planar annular surface 102 disposed opposite and parallel to the planar end 98 of the force motor stem 96.
- the area between the planar end 98 of the force motor stem 96 and the planar annular surface 102 on the nozzle 100 constitutes a fourth orifice 104 (A4), which, as explained hereinafter, is of variable area.
- the force motor 94 preferably includes a built-in bias spring to overcome any force built ap on the force motor stem 96 due to the pressure at the nozzle 100 opening.
- Mounting cap 92 is retained in position on the valve housing 10 by clips 106 and bolts 108. At the left end of mounting cap 94 is a flat washer 110 which abuts the centering spring 72 and which limits the travel of the spool 14 in the right-hand direction.
- the force motor 94 is mounted in the mounting cap 92 by threads 112 and retained for locking purposes by locking ring 114. This arrangement allows external adjustment of the force motor stem 96, which in turn permits external manual adjustment of the variable orifice 104 (A4).
- the force motor 94 is adjusted so that the variable orifice 104 (A4) equals the fixed orifices 74 (A,), 76(A 2 ), and 90 (A3) in effective area.
- the pressures in each of the chambers 54 and 70 is exactly half the pilot supply pressure applied to pilot port 82. Since the pressures in the chambers 54 and 70 are equal to each other, the spool 14 is held stationary, which is called the "null" of the valve.
- the spool 14 will move only that amount necessary to re-establish the face balance.
- the spool 14 is held in the newly attained position. If the input to the force motor 94 is later varied, the spool 14 will quickly move to a new position re-establishinq the force balance. In particular, if the input to the force motor 94 later ceases, the spool 14 will return to the "null" of the valve. Similarly, lack of controlling pressures in the chamber 54 and 70 caused, for instance, by failure of the pump 52 will cause the spool 14 to return to its "null" position.
- control pressure bridge is displayed schematically in Figure 4 .
- the subject invention provides a pilot pressure bridge arrangement in which there are four orifices, only one of which is variable. An automatic feedback is thus developed which provides accurate, continuous control.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Servomotors (AREA)
Abstract
Description
- There are many hydraulic applications in which a signal from a remote source such as an electric force motor is used to cause hydraulic response in a hydraulic control valve. Other workers in the prior art have utilized control pressure networks for establishing a movement in the main spool of the hydraulic valve in response to a movement in a remote control motor. For instance, the patent to W.C. Moog, Jr.,2,625,136, issued January 13, 1953, discloses a pilot stage circuitry in which a half- bridge pilot circuit with a stationary nozzle is disclosed. In the Moog patent, the torque motor is a force generating device whereas in the instant invention, a displacement-type force motor is used. In Moog, the control pressure P, is fed back to the armature via a nozzle bore and reacts with the torque motor and reaction spring to achieve a constant Pc regardless of the pilot pressure P magnitude. In the present invention., the control pressures vary with pilot supply pressure since Pc is used as a feedback parameter. United States Patent 3,410,308, issued to W.C. Moog, Jr. on November 12, 1968, United States Patent 3,430,656, issued March 4, 1969 to J. W. Hawk, and United States Patent 2,934,765, issued April 26, 1960 to T. H. Carson, are also of interest.
- Another patent of interest-is that to E. C. Jupa, issued March 7, 1961, No. 2,973,746, which shows a bridge network. In Jupa, the adjustable nozzle is stationary and not attached to the main spool as in the instant invention. Thus, Jupa does not incorporate a moving nozzle with a one-to-one position feedback. Jupa also has two variable orifices. The flapper nozzle, of course, is adjustable and his needle valve, on the end of the spool, is also adjustable.
- According to the present invention there is provided a flow control servo valve comprising a valve housing having an axial bore therethrough, a valve control spool axially movable within the bore so as to take up a balanced position with the housing and having an axial passageway therein extending from end to end of the spool to communicate with first and second end chambers one disposed at each end of the spool, a source of pilot pressure connected through first and second equal orifices respectively to the first and second end chambers, a third orifice equal to the first and second orifices and extending between the axial bore and the first end chamber, a fourth orifice of variable size between the axial bore and the second end chamber, and a force motor with an axially movable actuator member so arranged that axial movement of the actuator member varies the size of the variable orifice which in turn causes the control spool to move axial to assume a new position to reestablish the balance.
- This invention therefore provides a servo control valve wherein an electrical signal may be used to cause a mechanical movement which varies one orifice of a bridging network, which is carried by the main hydraulic spool, which causes a movement in the spool until balance is restored and accurate and continuous feedback is present for spool positioning.
- The invention also provides a pilot stage for a hydraulic control valve which comprises three fixed orifices and a single adjustable orifice, the latter of which may cooperate with an electromagnetic motor displacement to establish a variable orifice area that will control main spool location. The force motor proportionally varies pilot fluid pressure to thereby move the spool in proportion to the current or voltage used to adjust the space between a piston of the motor and a-nozzle formed on the main spool.
- These and other objects of the invention will become more apparent to those skilled in the art by reference to the following detailed description given by way of example when viewed in light of the accompanying drawings.
-
- FIGURE 1 is a side view of a servo valve according to this invention;
- FIGURE 2 is an elongated cross-sectional view, partially schematic, of the principal elements of the servo valve shown in Figure 1;
- FIGURE 3 is an enlarged section of the variable nozzle portion of Figure 2; and
- FIGURE 4 is a-schematic of the control pressure network of the apparatus of Figure 1.
- Referring now to the drawings wherein like numerals indicate like parts, the
numeral 10 indicates a valve housing having a bore 12 therethrough. Reciprocally received within the bore 12 is aspool 14 equipped with fourland areas 16, 18, 20, and 22. Betweenland areas 16 and 18 is a groove area 24, and between land areas 20 and 22 is agroove area 26.Land areas 18 and 20 are machined with close tolerances for reasons which will become apparent hereinafter. - The
valve housing 10 is machined with fourinternal grooves land areas 18 and 20 when thespool 14 is in the position shown in Figure 2.Groove areas 24 and 26 communicate with a tank 36 (shown only in Figure 4) by way of apassageway 38 and a return can port 40.Internal grooves 28 and 30/communicate with aload 42 by way of passageway 44, andihternal grooves 32 and 34 can communicate with theload 42 by way of apassageway 46.Passageways 44 and 46 are closed and opened by the movements ofland areas 18 and 20, respectively; in the location of thespool 14 shown in Figure 2, both.passageways are closed. - In the middle of
spool 14, betweenland areas 18 and 20, is apressure groove 48 which communicates with aport 50 shown in Figure 1. Theport 50 is connected to the output of apump 52, so that pressure from thepump 52 is communicated to the pressure groove4§ and can then be communciated to either passageway 44 orpassageway 46, depending on the position ofspool 14. Of course, in the position shown in Figure 2, pressure from the pressure groove48 is communicated to neither passageway. However, as thespool 14 moves to the left as viewed in Figure 2, pressurized fluid will flow to theload 42 through internal groove 30 and passageway 44 and return totank 36 viapassageway 46 and internal groove 34. Conversely, as thespool 14 moves to the right as viewed in Figure 2, pressurized fluid will flow to theload 42 throughinternal groove 32 andpassageway 46 and return totank 36 via passageway 44 and internal groove 2R. - At the left end of bore 12 as viewed in Figure 2 is a chamber 54 closed by an
end gland 56 retained in position on thevalve housing 10 byclips 58 andbolts 60.End gland 56 receives apiston 62, ascrew 64, ajam nut 66, and a centeringspring 68. At the right end of bore 12 is achamber 70 which receives a second centering spring 72 and which is closed by apparatus described hereinafter. Thepiston 62, thescrew 64, thejam nut 66 and the two centeringsprings 68 and 72 collectively serve as a mechanical "null" adjustment for thespool 14. That is, by adjustingscrew 64 it is possible to initially locateland areas 18 and 20 on thespool 14 so that theinternal grooves 28 and 30 align withland 18 andgrooves 32 and 34 align witn land 2u ofspool 14. - Chambers 54 and 70 are subjected to intermediate control pressures by means of orifices 74 (A1) and 76 (A2), which communicate with the
chambers 54 and 70 via theconduits orifices isolated pilot port 82 communicates with theorifices internal filter 84 which protects those orifices from fluid contamination. - Throughout the length of
spool 14 is aconduit 86. Theconduit 86 communicates at its right end with thegroove area 26 via a hole 88 in thespool 14 and at its left end with the chamber 54 via a third fixed orifice 90 (A3) which is equal to orifice 74 (A,) and orifice 76 (A2). - Attached to the right end of
valve housing 10, as seen in Figure 2 by means of amounting cap 92 is aforce motor 94 having aforce motor stem 96 terminating in aplanar end 98 which extends toward the right end of thespool 14. As best seen in Figure 3, the end of thespool 14 which faces theforce motor 94 carries a pressed-innozzle 100 having a planarannular surface 102 disposed opposite and parallel to theplanar end 98 of theforce motor stem 96. The area between theplanar end 98 of theforce motor stem 96 and the planarannular surface 102 on thenozzle 100 constitutes a fourth orifice 104 (A4), which, as explained hereinafter, is of variable area. As is well known in the art, theforce motor 94 preferably includes a built-in bias spring to overcome any force built ap on theforce motor stem 96 due to the pressure at thenozzle 100 opening. -
Mounting cap 92 is retained in position on thevalve housing 10 byclips 106 andbolts 108. At the left end of mountingcap 94 is aflat washer 110 which abuts the centering spring 72 and which limits the travel of thespool 14 in the right-hand direction. Theforce motor 94 is mounted in themounting cap 92 by threads 112 and retained for locking purposes by lockingring 114. This arrangement allows external adjustment of theforce motor stem 96, which in turn permits external manual adjustment of the variable orifice 104 (A4). - Initially, after the
screw 64 has been adjusted to align thespool 14 in thevalve housing 10 as shown in Figure 2, theforce motor 94 is adjusted so that the variable orifice 104 (A4) equals the fixed orifices 74 (A,), 76(A2), and 90 (A3) in effective area. At that point, the pressures in each of thechambers 54 and 70 is exactly half the pilot supply pressure applied topilot port 82. Since the pressures in thechambers 54 and 70 are equal to each other, thespool 14 is held stationary, which is called the "null" of the valve. - When current or voltage applied to the
force motor 94 causes theforce motor stem 96 to move to the.left towardspool 14, orifice 104 (A4) is reduced in area. As a result, the pressure inchamber 70 increases, and thespool 14 moves to the left, causing pressurized fluid to actuate theload 42 through internal groove 30 and passageway 44. Correspondingly, when current or voltage applied to theface motor 94 causes the force motor stem 96 to move to the right away fromspool 14, orifice 104 (A4) is increased in area. As a result, the pressure in thechamber 70 decreases, and thespool 14 moves to the right, causing pressurized fluid to actuate theload 42 through internal groove 3? andpassageway 46. In each case, of course, thespool 14 will move only that amount necessary to re-establish the face balance. When the faces are again in balance, thespool 14 is held in the newly attained position. If the input to theforce motor 94 is later varied, thespool 14 will quickly move to a new position re-establishinq the force balance. In particular, if the input to theforce motor 94 later ceases, thespool 14 will return to the "null" of the valve. Similarly, lack of controlling pressures in thechamber 54 and 70 caused, for instance, by failure of thepump 52 will cause thespool 14 to return to its "null" position. - The foregoing control pressure bridge is displayed schematically in Figure 4. As shown therein, the subject invention provides a pilot pressure bridge arrangement in which there are four orifices, only one of which is variable. An automatic feedback is thus developed which provides accurate, continuous control.
- In a general manner, while there has been disclosed an effective and efficient embodiment of the invention, it should be well understood that the invention is not limited to such an embodiment as there might be changes made in the arrangement, disposition, and form of the parts without departing from the principle of the present invention as comprehended within the scope of the accompanying claims.
Claims (10)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US81546777A | 1977-07-13 | 1977-07-13 | |
US815467 | 1977-07-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0000445A1 true EP0000445A1 (en) | 1979-01-24 |
EP0000445B1 EP0000445B1 (en) | 1982-11-24 |
Family
ID=25217875
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19780300136 Expired EP0000445B1 (en) | 1977-07-13 | 1978-07-10 | Servo valve |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0000445B1 (en) |
JP (2) | JPS5420275A (en) |
CA (1) | CA1093426A (en) |
DE (1) | DE2862092D1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3216692A1 (en) * | 1982-05-05 | 1983-11-10 | Kienzle Apparate Gmbh, 7730 Villingen-Schwenningen | Electropneumatic servo valve |
WO2020002472A1 (en) | 2018-06-28 | 2020-01-02 | Basf Se | Use of alkynylthiophenes as nitrification inhibitors |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60118075U (en) * | 1984-01-18 | 1985-08-09 | 株式会社トキメック | Proportional solenoid type spool valve |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2972999A (en) * | 1955-11-01 | 1961-02-28 | Sanders Associates Inc | Two-stage, differential, hydraulic servo valve |
US2973746A (en) * | 1957-06-03 | 1961-03-07 | Edward C Jupa | Hydraulic servo valve |
US2977985A (en) * | 1958-12-29 | 1961-04-04 | Pegasus Lab Inc | Electro-hydraulic servo control valve |
US3012579A (en) * | 1959-06-08 | 1961-12-12 | Pneumo Dynamics Corp | Electrohydraulic servo valve |
GB1268767A (en) * | 1968-06-26 | 1972-03-29 | Dowty Technical Dev Ltd | Electro-hydraulic and electro-pneumatic servo valves |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5421912B2 (en) * | 1971-12-02 | 1979-08-02 | ||
US3799202A (en) * | 1972-11-29 | 1974-03-26 | Sperry Rand Corp | Power transmission |
-
1978
- 1978-07-10 DE DE7878300136T patent/DE2862092D1/en not_active Expired
- 1978-07-10 EP EP19780300136 patent/EP0000445B1/en not_active Expired
- 1978-07-12 CA CA307,244A patent/CA1093426A/en not_active Expired
- 1978-07-13 JP JP8464178A patent/JPS5420275A/en active Pending
-
1985
- 1985-12-09 JP JP18852185U patent/JPS61116205U/ja active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2972999A (en) * | 1955-11-01 | 1961-02-28 | Sanders Associates Inc | Two-stage, differential, hydraulic servo valve |
US2973746A (en) * | 1957-06-03 | 1961-03-07 | Edward C Jupa | Hydraulic servo valve |
US2977985A (en) * | 1958-12-29 | 1961-04-04 | Pegasus Lab Inc | Electro-hydraulic servo control valve |
US3012579A (en) * | 1959-06-08 | 1961-12-12 | Pneumo Dynamics Corp | Electrohydraulic servo valve |
GB1268767A (en) * | 1968-06-26 | 1972-03-29 | Dowty Technical Dev Ltd | Electro-hydraulic and electro-pneumatic servo valves |
Non-Patent Citations (1)
Title |
---|
OLEODINAMICA-PNEUMATICA, vol. 17, no. 9, 1976, edited by Tecnicke Nuove, Milano, Italy, JAMES T. JOHNSON: "Servosistemi elettroidraulici", Pages 146,147. * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3216692A1 (en) * | 1982-05-05 | 1983-11-10 | Kienzle Apparate Gmbh, 7730 Villingen-Schwenningen | Electropneumatic servo valve |
WO2020002472A1 (en) | 2018-06-28 | 2020-01-02 | Basf Se | Use of alkynylthiophenes as nitrification inhibitors |
Also Published As
Publication number | Publication date |
---|---|
EP0000445B1 (en) | 1982-11-24 |
DE2862092D1 (en) | 1982-12-30 |
JPS5420275A (en) | 1979-02-15 |
JPS61116205U (en) | 1986-07-22 |
CA1093426A (en) | 1981-01-13 |
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