JPS5834208A - Single stage servo valve - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Operation (pilot) of two-stage servo valve *IJR (lf
It is believed that there are some inherent limitations.

For example, the frictionless pilot stage is essentially open in the middle and has continuous leakage flow.

This means a power loss that can be significant, especially in a complex control system that is provided with redundancy. Redundant controllers for the aircraft being operated are typically 15
It has 40 servo valves. Each servo valve maneuvering step consumes 174 horsepower. Therefore, the continuous loss of power due to leakage during such maneuvering phases is significant.

Contamination of the fluid used poses yet another problem.

The valve according to US Pat. No. 3,023,782 includes a small sized orifice during the maneuvering phase.

Therefore, the performance of the servovalve is impaired by contaminants that substantially restrict fluid flow. Other problems that exist in regular two-stage servo valves are:

The components are relatively delicate, sensitive to temperature changes1, stress issues due to pressure, shock and acceleration, environment? and other changes 11S due to changes in operating conditions.

These factors are the main cause of saza valve failure. Additionally, the dynamic response of a two-stage servo valve is affected by fluid viscosity, and the central open control stage is sensitive to instability at high speeds and pressures.

Considering the above-mentioned difficulties, it is preferable to eliminate the pilot stage from high-performance servo valves, and attempts to provide a high-performance single-stage servo valve that can be compared with two-stage servo valves due to controllability of power are desirable. was lacking in one or more of the following points:

namely, lack of sufficient spool drive (so-called "tip shear" force), excessive dimensions and quantities (e.g. levers,
Reliance on mechanisms that reduce and/or convert motion (balls, screws, etc.).

In one aspect, the present invention broadly relates to a body part.

a rotatable valve element mounted on the body and an electro-mechanical actuator having a rotor, the rotor being rigidly attached to the valve element for co-rotation with the valve element; An improvement is provided for a single stage servo valve that provides bearing support for a rotor.

Because the rotor and valve element are directly and rigidly connected, there is no backlash or idle motion between these elements. Furthermore, the servovalve according to the invention has a high degree of torque amplification, essentially with respect to the ratio of the diameter of the air gap of the rotary torque motor to the diameter of the single-turn valve element.

In another aspect, the invention provides an improved method of immobilizing a rotatable valve member relative to a body.

Is this method suitable for the interface between the valve element and the body? Valve element to provide a flow path for fluid terminating as a boat.

or providing a hole in one of the body parts, and a valve element;
Or, the shape corresponds to the boat that ends at the same boundary as above in the other part of the body.

Those boats rotate the valve element. N boats such that, when opened, the cross-sectional area of the fluid metering orifice defined by those boats is proportional to the angular position of the valve element relative to the body; selectively increasing the diameter of the hole so as to immobilize the valve when in the desired angular position.

Accordingly, an overall object of the present invention is to provide a single stage servo valve.

Another object of the invention is to provide many of the performance characteristics of a two-stage servo valve. An object of the present invention is to provide an improved single stage servo valve.

Another object of the invention is that an electromechanical actuator is directly connected to the rotatable valve element Vc. An object of the present invention is to provide an improved single stage servo valve.

Another object of the invention is its use in single stage servo valves.

The object of the present invention is to provide improved torque control.

Yet another object of the invention is to immobilize a rotatable valve element on the body. An object of the present invention is to provide an improved method.

These and other objects and advantages of the present invention will be apparent from the foregoing and following description, drawings, and claims.

First, like reference numerals are intended to consistently refer to the same elements, g and/or structures throughout the several drawings, and as such, this specification of which the following detailed description is an integral part. It should be clearly understood that elements, S and/or structures are explained in detail throughout the book.

Referring now to the drawings, and in particular to FIG. 1, the present invention provides an improved single stage servo valve, the presently preferred embodiment being designated generally at 10. In a broad sense, the square 10 includes a valve body 11 having a horizontally elongated through hole 12, and the hole 12.
a rotary torque motor 15 including a sleeve 13 disposed in the body, a valve spool 14, a rotor 16 and a stator 18;
A cover 19 which protects and encloses the. Those skilled in the art will appreciate that because of the number of passageways, sleeve 13 is typically formed separately and then assembled to the body for manufacturing convenience.

Once the sleeve has been inserted and assembled as described above, it becomes an actual part of the body. Therefore, the term "body" as used in this specification refers to various types of sleeves,
It shall mean either a body having passages and surfaces, or, unless otherwise specified, a body incorporating a separately formed sleeve. Moreover, the servo valve 10.

It is designed to handle a wide range of fluids, either liquid or gaseous.

Referring now to FIGS. 1 and 2, body 11 is shown as having a slightly L-shaped vertical cross section. The upper part of the body is provided with a single level horizontal through hole 20 for attaching an electrical connector 21 via a fitting 22. In this manner, connector 21 is supplied with appropriate electrical signals from an external power source (not shown) and is adapted to supply the signals to torque motor 15 via conductor 23. As mentioned above, the lower part of the body part 11 is provided with a horizontally elongated through hole 12.

A plurality of shallow annular recesses extend into the body from the cylindrical wall defining the bore 12 of the body at various sl-spaced locations, forming various passageways provided in the sleeve 13. It is shown as corresponding to. There are four separate passageways through the body VX.

It communicates with four boats located at the bottom of one body at intermittent points spaced apart in the M-line direction by 5 m along hole 12 (FIG. 2). For convenience, the boats at the bottom of these 41 gardens are designated as pressure (P), return (river, control 1 (C1) and control 2 (Cs). From left to right in the diagram, return (river,
Control 1 (C1), pressure (P), control 2 (Ca).

and counter-pulling R). As best shown in FIG. 1, hole 24 communicates the bottom opening C2 with the second hole location C1, and hole 25 connects the bottom opening C2 with the fourth hole location C1. It communicates with position (C2). The two wall return hole locations representing the first and fifth hole locations communicate with the bottom return hole (R) via suitable passageways (not shown). Similarly, the central position (P) of the hole communicates with the bottom pressure hole (Pl) via a suitable passage (not shown). The fluid is supplied to the central hole position via the bottom pressure hole PY, and the two end holes are connected via return ports (RY) to a suitable outlet or reservoir (not shown). # mouth C1 and C2
is conveniently used to control the flow of fluid to a suitable hydraulic or pneumatic device. for example.

The control ports C1 and 02 can communicate with opposing chambers of a hydraulically actuated device with a piston disposed in a cylinder.

A suitable end cap 26 having a slightly U-shaped cross-section seals the right end of the bore 12 in the body.

It is also fixed to the body via a fixture 28.

Referring now to FIG. 10, sleeve 13 is shown as a horizontally elongated tubular member disposed in operative relationship with body aperture 12. The sleeve 13 has a left end surface 29 disposed to abut the extension 44, an annular vertical right end surface 30 abutting a portion of the thick cap 26, and a cylindrical outer surface 3.
1 and a cylindrical inner surface 32. A pair of annular (
radially outwardly from said inner surface 32 a cutout 33,34;

A U-shaped elastic sealing member 35 extends perpendicularly from the left and right enlarged surfaces and acts between the sleeve and the spool.
Y are housed separately. S V-de is.

■Multiple holes are each drilled in the diametrical direction.

The holes are spaced apart from each other in the s-edge direction to align with the five hole locations. 8 in FIG. 1, from the left to the right, said sleeve has a first hole 37 communicating with the return position R of the body part and a second hole 3 communicating with the position C1 of the control boat.
8, and a third and a fourth, respectively communicating with the pressure position p of the body part.
40, a fifth hole 41 communicating with the control boat C2 of one body, and a sixth hole 42 communicating with the return port R of one body. The sleeve further includes the hole 37-
It is equipped with a plurality of annular depressions located in the middle of 42,
Each of the sleeves contains a suitable QIJ song that sealsly separates the fluid passageway from one side to the other.
It is shown mounted non-rotatably on the body by a pin 43 (FIG. 1) connecting the sleeve to the end cap. Depending on your wishes, the sleeve may include:
One or more pressure relief passages (not shown) may be provided at appropriate locations between the sleeve and the spool to relieve pressure build-up. The sleeve is held in place in this operative position by the left vertical end plate 44, which is suitably secured to the body by fittings 45 (FIG. 1).

With further reference primarily to FIG. 10, the valve element is shown in detail in rotational movement relative to the sleeve 13.
3. The spool 14 is shown in the form of a valve spool 14 mounted in a valve spool 14 having an annular vertical left end face 46, an fR-shaped vertical right end face 48, and a right end from said left end face 46. a cylindrical surface 49 extending toward the end plate 44;
a left-facing annular vertical 7f1 rotatably coupled to
．． Part 50 and.

A cylindrical surface 51 extending to the right from the shoulder and disposed within the sleeve rotatably engaged the end cap 26 . a right-facing annular vertical shoulder 52;
2 and a generally cylindrical portion 53 disposed within the recess of the amphipod 26.

The spool is provided with six openings 37'-42', each diametrically extending therethrough.

These openings are spaced apart from each other in the @ line direction and are aligned in the S* direction with the corresponding sleeve holes 37-42, respectively. An S-line hole 54 extends rightward into the spool from its left end surface 46 and extends from the diametrical spool opening 37'.
It communicates with 38'X and 39'.

The left end of the hole 54 is closed by a suitable plug 55. Another axial bore 56 extends leftwardly into the spool from its right end face 48 and extends into the spool's diametrical opening 4G'.
, 41' and 42'.

The right end of the hole 56 is closed by a suitable plug 58.

In the case of FIGS. 11-16, there are six diametrical holes 37-42 (as shown).

The same is machined (i.e., formed) from the angular orientation device (i.e., from top to bottom as shown).

However, corresponding diametric openings 37'-42'
are machined through the spool from different angular positions. In this way, Suderka 1 Figures 11 to 16
In the angular position shown, the spool boat 37' is rotatably immobilized at the edge of the sleeve mouth 37 (Fig. ), and the spool pressure boat 39' is in full communication with the sleep pressure boat 39 (
(FIG. 13) The pressure boat 40' of the spool is rotatably immovable with respect to K and the control boat 41' of the spool is rotatably immobile with respect to the pressure boat 40 of the sleeve (FIG. 14). is the sleeve control boat 41 (first
(Fig. 5) is fully connected.

In addition, the spool return boat 42' is rotatably fixed relative to the sleeve return boat 42 (FIG. 16). Thus, in the positions shown in FIGS. 11 to 16, all pressure and return ports are in their fixed positions, so that no leakage (other than annular leakage) occurs from the pressure return ports). There is no flow. If the spool moves counterclockwise from this initial position relative to the sleep.

Control boat 38 is now open return boat 37
The control boat 41 communicates with the now open return boat 40. alternatively.

If the spool were to move counterclockwise relative to the sleep from the position shown in FIGS. 11-16, control boat 38 would now be in communication with open pressure boat 39 and control boat 41 would be It communicates with the now open return boat 42. In this way, the angular position of the spool with respect to sleep is used to control the control bows (C, N and CRY).
through which the flow of fluid is metered to a pneumatically or hydraulically operated device (not shown). Another desirable feature of this structure is the pressure of the fluid used in Figures 11 and 13.

As shown in FIGS. 14 and 16, the pressure forces are balanced in that they are applied to diametrically opposed locations on the spool.

Another feature is that the spool boat and sleep boat work together to form a trap.

This is how these boats are formed. Those skilled in the art will recognize that it is highly desirable to make the fluid outlet of the valve a linear function of the position of the spool relative to the sleeve and body.

At the same time, the spool is in a certain angular position.

The valve must be immovable as shown in FIGS. 11, 13, 14 and 16. To achieve this proportionality, the cross-sectional area of the defined fluid metering orifice varies linearly with the angular position of the spool.
The sleeve must be provided with various radial circular holes 37-42 (1° to 8° in the preferred embodiment) to apply a force of 1° to the actuation of the boat on the corresponding spool. The corresponding edges must be of corresponding shape.
1° Thus, to the extent that the working edge of the boat of the sleeve is concave along the axis of rotation of the spool, the corresponding edge of the cooperating spool is 37' in FIG.

Being convex as shown at 39', 40' and 42', respectively, when these pairs of boats are closed, the two corresponding edges overlap in generally line contact. therefore,
When the spool is subsequently rotated in the appropriate angular direction to release the polymerized boat, the cross-sectional area of the fluid metering orifice increases approximately proportionally to successive spool rotations. These convex openings in the spool are adjacent holes 3
6 (FIG. 7) by suitable electric discharge machining (BDM). When a fluid metering bow is thus formed on the spool with a convex edge, the corresponding concave edge of the sleeve's boat forms a hole 37 through the sleeve.
39. By increasing the diameters of 40 and 42 individually, they can be made "immovable" so that when the spool is in a particular angular position relative to the sleeve, the respective cooperating spools and sleeves The metering orifice between the two is considered to be exactly immovable. The sleep hole can be selectively enlarged using any of a variety of well-known techniques, such as honing, jig drilling, or electrical discharge machining.Thus, the present invention provides five aspects of the present invention. , machining holes in one of the valve element and the body to provide a fluid flow path terminating in one boat located in the other KWi of the valve element and the body; on the other hand, providing a fluid flow path terminating in another boat facing and matingly arranged with said one valve element and body, said other boat being connected to the Wfr of an orifice defined thereby; The ramming surface 1 has a shape that changes approximately in proportion to the angular position of the valve element with respect to the body within the operating range of movement, and the diameter of the one boat is changed when the valve element is at the desired angular position with respect to the body. An improved method of immobilizing a rotatable valve element in one body is provided which broadly includes the step of selectively enlarging the valve to immobilize it.

1 and 6, four longitudinally spaced projections 5,9,60,61g and 62 extend leftwardly from end plate 44 and have cooperating pairs. The six pairs of cooperating protrusions 59.6G, 61.62 arranged in the form of are each provided with a tapped hole aligned with its cooperating partner. Yoke assembly 63 including segmented clamp 64
is fixed to the extended cylindrical portion 49 of the valve spool 14 via a bolt 68.6& located between the four projections. Each clamp has an arm 68 extending to the right and an arm 69 extending to the left. Left arm 69.69
were located facing each other. Spring receiving recess 70
is provided. The stop bottle 11 is on the right protrusion 59.6
0, providing an adjustable stop member threaded into each tapped hole to limit the range of rotational movement of the spool relative to the body. Threaded bottle 72.72 is on the left protrusion 6
It is screwed into a 1.62 tapped hole. A helical compression spring T3 is arranged to act between the spring receiving recess 70 of the left arm and the pin 12. These springs therefore urge the spool toward a central angular position (FIGS. 11-16) against the body. Apply an opposing force to the left arm. The magnitude of each of these spring forces is 1 noa 2.0 for the left protrusion 61.62.
By selectively tightening and loosening 72, it is possible to change the position so that the net force is zero. By rotating the spool clockwise (FIG. 3) relative to the body, the force from the upper pressure spring is increased, and.

This reduces the force from the lower spring and generates a counterclockwise force that centripetes the spool due to the forceps, or vice versa.

As shown in FIG. 1, the torque motor is mounted in an integral part within a protective casing 19.An embodiment of the torque motor whose structure is simplified for ease of understanding is shown in FIGS. 4 to 6. Here, the torque motor 15
The rotor, shown as including rotor 16 and stator 18, is rigidly attached to the valve spool piezoelectrically via a keyed connection 771 for movement in rigid connection with the valve spool. Additionally, in one preferred embodiment, the valve spool provides the only bearing support for the rotor.

lIX as best shown in Figures 4 to 6.
Theta 18 includes a segmented core T5, which is suitably secured to the body by a fitting 65 and surrounds the valve spool. Also, the core is.

Each supports a 4 m rectangular coil designated 76. Each coil 76 provides, on either side of the core, a sheet of current conductor, respectively designated 78, 78', for purposes described below. These four coils may be connected in series or in parallel, but they should be wound in opposite directions so as to sieve the series buck magnetic flux indicated by magnetic pole rNJ and "8" in FIG. 5, and/or Selectively energize.

The rotor is shown as including a pair of left and right magnetic supports 79, 79' spaced apart in 411 linear turns, the supports being rigidly secured to the spool. The two magnet supports are arranged symmetrically with respect to each other. As best shown in FIG. 6, 4 m permanent magnets, each indicated at 81 and preferably formed of samarium cobalt, are mounted in cooperating pairs on each magnet support. Fixed magnetic flux plate 80°8
T)' (FIG. 1) is secured to the body proximate the outer surface of the set of magnets by means of fixtures 65.65.

As best shown in FIG. 4, the sets of magnets on the left and right sides of the torque motor are arranged with the coil 76 in the middle and the magnetic poles rNJ and "8" oriented as shown in FIG. The spacing between each conductor coil sheet 78, 78' and each opposing magnet is an effective air gap, each designated 82° 82'.

The six pairs of cooperating adjacent magnets in the 61st
I faced 2. It has opposing poles rNJ and "8".

Similarly, the poles of the opposing magnets 81 face the air gap 82'. Has opposite &'Y. In this way, the torque motor includes a pair of cooperating magnets 81, a fixed magnetic flux plate 80,
A first magnetic flux path comprising an air gap 82 and a facing conductor sheet 78 and a core 75 has the other cooperating set of magnets 81, a fixed magnetic flux plate 80, an air gap 82, and an opposing sheet. It has a second magnetic flux path including a shaped conductor 78 and a core 75. Similarly, a pair of magnets '81' in which the third and fourth magnetic flux paths cooperate, a fixed magnetic flux plate 80', and an air gap 82
' and the core 75.

The force generated by the sum of currents in a conductor located in the transverse direction of the magnetic field of magnetic flux is expressed by the following equation.

F Rin 11B? - Transverse force 1 = = Current in the conductor 1 - Length of the conductor B - Flux in the air gap The direction of this force is perpendicular to the direction of the current and the magnetic flux, respectively. Since the conductors extend radially with respect to the rotor's rotation 45 wire, the torque generated by a single conductor in one current sheet is .

TOwz Torque generated by a current in one conductor r - radius of the conductor rl, rl - inner radius 8 and outer radius of the sheet of current conductor dr - d1 = incremental length of the conductor.

Since the magnetic flux B in the air gap is constant for each steady state of current, the torque per conductor is L M-T@-rl == length of the conductor Air gap 8
Since the direction of magnetic flux in sheet 2' is opposite to the direction of flux in air gap 82 and the direction of current in sheet 78' is opposite to the direction of current in sheet 78, the force on each side of each coil causes The generated torque is added - Adjacent coils of the cooperating pair are also energized and/or wound to provide additional torque -18
Similarly, VC, the magnets, coil turns, and current poles associated with the second set of air gaps are also arranged to provide additional torque. Therefore, the total generated torque is TI(8NBRL), and TI=-total torque.

To N-4 coil? is the number of conductors that can be connected. Since all parameters in parentheses are constant, the magnitude of the motor torque is proportional to the magnitude of the current, and the direction of the torque (ie, clockwise or counterclockwise) is determined by the pole of the current.

The steady-state torque generated by the sum of the two currents in the four coils 76 is balanced by the appropriate deflection of the suppression spring 73. In this way, the supplied current causes the susol to rotate relative to the sleeve as desired.

A modification of the single stage servo valve is shown in Figure 8, which shows [
Also in , the same prime sign designates the corresponding structure described above. However, in this embodiment, the end cap 26 is replaced by a plate 84 attached to the body via fittings 28 and is provided with an axial hole 85 through which the spool can be attached. 14' extended portion 8
6 is extended. This extended portion 86 is splined and suitably connected to a position sensing transducer, generally indicated at 88, which is mounted on a suitable frame 89 and enclosed within a protective cover 90. ing. An electrical connector 91 protrudes into the cover 90. Position sensing transducer 88 is operatively arranged to generate an electrical signal indicative of the actual relative angular position of the spool with respect to the body.

A functional block diagram of this modification is shown in FIG.
An electrical command signal representing the desired angular position of the spool is provided to summing point 92. A feedback signal generated by the spool position sensing transducer 88 is also provided to the summing point 92. The error signal from the summing point is supplied to an amplifier 93 which supplies current to the coil of the single stage servo valve 10 to rotate the spool. The error signal is an algebraic combination of the command signal and the negative feedback signal. When the spool is actually at the commanded position, the error signal becomes zero. If the intended position differs from the commanded position, an appropriate error signal τ is applied to one coil of the torque motor to perform a corrective movement.

Many modifications and variations are possible in the invention. Various construction materials and shapes can also be easily modified.

It is clear that the use of position sensing transducers is optional. Especially if one position sensing transducer force is used.

The use of centripetal spring 73 is optional. The dynamic seal 35 at the end of the spool is approximately four in size.

Laminar leakage passing through these seals is then directed to the return pipe. Also, U.S. Patent No. 2.835,265
A torsion-flexible tube as shown in No. 1 is used between the body and the spool to connect the torque motor cavity below the cover 19 and the fluid sight contained in the body 11. Leakage can be reduced to zero. The centripetal force of the spring 73 can be substituted for the torsion spring that suppresses the torsion tube described above. The detailed placement of Suzor, sleeve, and body can be changed.

If desired, the sleeper may be rotatable relative to the spool and body. Similarly, the method of forming cooperating shaped boats can be varied. Collaborate? Although this is preferable, the shape of the groove is not necessarily convex or concave.

The particular torque motor illustrated is only one example of a large electro-mechanical actuator. Such an actuator may be provided with a separate rotating support for the rotor if the motion is rotational, in which case the rotor is fitted with one position sensing transducer 88, indicated at 94 in FIG. Suitable anti-backlash coupling, such as
Alternatively, it can be attached to the rotary valve member by a flexible coupling. The illustrated embodiment is a torque motor with 8
Permanent magnets are used, but the number can be increased or decreased as desired. If desired, the coils may be mounted on the rotor and the magnets may be mounted on the stator (or both coils and magnets may be mounted on the same member. need not be connected to a series or parallel circuit energized by a source of instruction. Instead.

These four coils can be individually energized from four separate sources, such as a quadrant redundant flight control system. The particular material forming the permanent magnet is currently preferred, but samarium cobalt is not critical.

Accordingly, while the presently preferred embodiment of an improved single stage servo valve has been shown and described, and various modifications thereof have been described, without departing from the spirit of the invention as defined in the following claims. (1) Various changes and modifications are possible.

[Brief explanation of drawings]

FIG. 1 is a partial vertical cross-sectional view of an improved single-stage servo valve. Figure 2 is its bottom view. 3 is a lateral vertical cross-sectional view taken generally along line 43-3 of FIG. 1; FIG. FIG. 4 is a simplified vertical sectional view of the torque motor. FIG. 5 is a lateral vertical cross-sectional view taken generally along line 5-5 of FIG. 4 and showing the stator in side view. 6 is a lateral vertical cross-sectional view taken generally along line 6--6 of FIG. 4 and showing the rotor flux plates in side view; FIG. FIG. 7 is a perspective view of the spool shown in FIG. 1. FIG. 8 is a partial vertical cross-sectional view of a modified single stage servo valve incorporating a position sensing transducer. FIG. 9 is a design diagram of a modified version of the servo valve shown in FIG. 8; FIG. 10 is an enlarged partial view of the valve spool and sleeve shown in FIG. 1; FIG. 11 is a lateral vertical partial cross-sectional view taken generally along line 11--11 of FIG. Figure 12 shows the overall VC along lines 12-12 in Figure 10.
FIG. 13 is a transverse vertical partial cross-sectional view taken generally along Ill 5-15 of FIG. 10; FIG. 14 is a lateral vertical partial cross-sectional view taken generally along line 14--14 of FIG. Figure 15 shows I! of Figure 1o! 15-15, and FIG.
FIG. 3 is a lateral vertical partial cross-sectional view taken generally along @ 16-16 of the figure; In fig. 10... Servo valve 11... Valve body 12... Hole 1
3...”)--f 14...Spool 15...
・Torque motor 16...Rotor 18...Stator 24.25・JL 37.38.39.40°41
, 42 , 37', 3B', 39', 40',
41'. 42'...Boat 63...Rice assembly 15.
...Core T6...Coil 78...! Seed 79...
- Magnet support 81... Magnet 82, 82'...
Gap 84... Plate 88... Converter 92.
...Additional points 93...Amplifier representative Asamura Kogai 4 people

Claims (1)

Claims: (1) A body having a passageway having a hole and terminating in a boat positioned opposite the hole. a passageway terminating in a boat disposed in the bore for rotation relative to the body and facing a wall of the bore, the body and the boat having a variable cross-sectional area therebetween; an electromechanical actuator having a rotor coupled directly to the valve element for rotational interlocking therewith. A single stage servo valve that controls fluid output in response to an IE command signal. (2. The servo-valve according to claim 1, characterized in that the valve element provides the only pronged support for the rotor. (3) ) The servo valve according to claim 1, wherein the electric mechanical actuator is a dorsal motor. (4) A single-stage servo valve according to claim 1. In the servo valve according to claim 4, one of the boats has a circular cross section. (5) In the servo valve according to claim 4, the boat of the body portion has a circular cross section. (6) The servo valve according to claim 1, wherein the body portion includes a sleeve, and the boat of the body portion has a circular cross section. (7) A single stage valve according to claim 6, characterized in that the boat of the sleeve has a circular cross section. Stage servo valve. (8) A single stage servo valve according to claim 4, characterized in that the other of the boats is bounded by an arcuate edge. (9) Claim A single stage servo valve according to claim 8, characterized in that the edge is convex. A single stage servo-valve according to claim 1, further comprising a spring device actuated to urge the valve element to a particular angular position relative to the body. A single-stage servo valve, further comprising a position sensing transducer operatively arranged to detect the angular position of the servo valve and to provide the sensed position as a negative feedback symbol. The single-stage servo valve according to claim 1, wherein the algebraic phase of the command signal and the negative feedback signal is supplied as an error signal to the electro-mechanical actuator. A single stage servo valve according to claim 1, further comprising a fluid seal separating said body from said electric 1 wA mechanical actuator. an electrically mechanical actuator having a rotor, said valve element being securely mounted such that said rotor rotates with said valve element, and said valve element having a bearing for said rotor. A single stage servo valve characterized in that it provides a support. a5 In the servo valve according to claim 14, the valve 1! a single stage servo valve, the valve being operatively arranged to meter the flow rate of fluid flowing through the body; αe The servo valve according to claim 15, further comprising a spool and a sleeve, the relative positions thereof metering the flow rate of the fluid flowing through the body, and the valve element comprises the spool and the sleeve. Being on the other hand is 1f! : Features a single-stage sirza valve. (I7) A single-stage servo valve according to claim 16, wherein the sleeper is fixed to the body. 15. The single-stage servo valve according to claim 14, wherein the valve element is a spool. (1!J) In the valve according to claim 18, each of the body part and the sleeve is provided with a fluid passage ending in -1, and the body part and the spool are connected to each other. The degree to which the body and the boat of the spool meet defines a variable orifice through which fluid flows, and the flow control area of the orifice and the chair defines a variable orifice through which fluid flows, and the flow control area of the orifice and the chair is between the spool and the body A single-stage servo valve characterized by having a shape that cooperates so as to be approximately proportional to the relative angular position of the servo valve.
201 Body part. a valve element rotatably attached to the body; a torque rotor having a rotor connected to the cough valve element for rotation therewith; with the stator. a plurality of permanent magnets eccentrically mounted on one of the rotor and the stator; a first magnetic flux path provided through the rotor and the stator and including a first air gap; and a stator; and at least one coil disposed in the first air gap so that a current supplied to it causes a current to be generated in the rotor. A single-stage serza valve characterized in that a blade generates torque on the rotor. A second permanent magnet is attached to one of the rotor and the stator, and is disposed in the second air gap to generate a magnetic flux, and one part of the conductor of the coil is attached to the first permanent magnet. The one coil is mounted such that the one coil is located in the air gap and another part is located in the second air gap, and the Wrl magnet and the air gap are arranged so that the sword generated in both air gaps by the current of the coil is A single-stage servo valve, characterized in that the servo valves are arranged in cooperation to individually generate additional torque on the rotor. and the stator, on the other hand 2
coils are mounted, each of which is suitably wound to provide an additional torque to the respective torque force applied to the rotor when current is applied to the coil. A single-stage sirza valve with a 'V% sign. (c) In the servo valve according to claim 20, four magnets are attached to one of the rotor and the stator, and the magnets are arranged such that their magnetic force acts as an additional force. Arranged in two pairs working together I11. A single-stage servo valve characterized by: (24) In the sirza valve according to claim 23, four coils are attached to the other of the rotor and the stator, and each of the coils is disposed in the gap. 1. A single-stage servo or valve, characterized in that the coil is suitably wound so that when current is supplied to the coil, the torque force applied to the rotor becomes an additional torque. c! 5. The servo valve according to claim 20, including a second magnetic flux path provided through the rotor and stator, and a second magnetic flux path provided in the second magnetic flux path and between the rotor and stator. at least one other permanent magnet eccentrically mounted on one of said second
The magnetic flux path of includes a second air gap, with said coil in front! e@
By providing a first sheet of conductor that conducts current in one air gap and a second sheet of conductor that conducts current in said second air gap, when current is supplied to said coil, said rotor Single-stage servo valve, characterized in that the added torque τ results in an additional torque. @ The servo valve according to claim 25, wherein the first and second magnetic flux paths share a common path in one of the rotor and the stator. valve. (21) The servo valve according to claim 20 is characterized in that each of the magnets is attached to the rotor, and each of the coils is attached to the stator. Servo valve. @ A single-stage servo, characterized in that the servo according to claim 20 is arranged on the valve, and each magnet is mounted at the same distance in the radial direction from the @ line of the rotor. Valve. @ The servo valve according to claim 25, wherein each coil is disposed between the magnets of the first and second magnetic flux paths.Hiroshi Patent 21. The single-stage servo valve according to claim 20, further comprising an elastic member acting on the rotor in a direction opposite to the electrically generated torque. 64. A servo valve according to claim 30, characterized in that the rotor is resiliently pressed to a particular angular position with respect to the body. The single-stage servo valve according to claim 20, wherein the magnitude of the angular interlocking of the rotor is proportional to the magnitude of the current supplied to the coil. The described servo valve further includes a position sensing transducer disposed to detect the angular position of the rotor and provide a negative feedback signal, and the current supplied to the coil is a command signal. and said negative feelback signal. (2) The servo valve according to claim 20, wherein the A single-stage servo valve, characterized in that the valve is positioned at the same distance in the radial direction from the axis of the rotor. A servo valve comprising a valve element operatively arranged to meter the flow rate of a fluid, and a torque motor mounted on said body portion and having an electrically movable member, the only one of said torque motors having a movable member. The improvement is that the serve valve essentially consists of an N valve element arranged to provide a bearing support for the body. A servo-valve comprising a rotatable valve element defining an orifice of variable cross-sectional area whose angular position is adapted to meter the flow rate of fluid, and a torque motor mounted on the body, wherein the rotor A servo valve, characterized in that it is mounted on a valve element for rotational movement about the axis of rotation of said valve element. 07) Improved servo-valve IC according to claim 36, characterized in that the valve element provides the only bearing support for the rotor. (c) forming a hole in one of the valve element and the body;
*Providing a fluid flow path terminating in one boat facing the other in the cord and body. The other of the valve element and body is provided with a fluid flow path terminating in another boat positioned facing the one of the valve element and body. When the boats are mated together, the other boat is shaped such that the dimensions of the orifice defined by the boats are generally proportional to the angular position of the valve element relative to the body. A method of immobilizing a rotatable valve element with respect to a body, characterized in that said valve element is immobilized in a desired angular position relative to said body. 1ciI4'PFFm (D range F! Mtjg38 term KW
iiff'7) Method c) A method for immobilizing a rotatable valve element relative to the body, characterized in that said other boat is formed by electrical discharge machining techniques. (In the method described in claim 68 of the 41st patent,
A method for immobilizing a rotatable valve element relative to a body, characterized in that said one boat is honed to increase its diameter.