Valve and aircraft

Abstract

The present disclosure relates to a valve, preferably a continuous valve or a proportional valve, wherein the valve comprises means configured to control and/or regulate a pressure and/or flow of a fluid, wherein the means are further configured to effect at least one further function or to participate in the function.

Claims

1. A valve, the valve comprising a spool within a spool sleeve, wherein the spool is configured to move axially relative to the spool sleeve between a neutral position and an extreme position, wherein, when the spool moves in a first direction from the neutral position to a first position between the neutral position and the extreme position, a first control opening in the spool sleeve is fluidically coupled to a first outlet in the spool sleeve while a second control opening in the spool sleeve is blocked, wherein, when the spool moves further in the first direction from the first position towards the extreme position, the second control opening is fluidically coupled to a second outlet in the spool sleeve, the second outlet in the spool sleeve fluidically coupled to a consumer, and wherein the first outlet communicates hydraulic pressure from the first control opening to a pressure sensor, directs the hydraulic pressure to open a brake in a high lift system, and/or directs the hydraulic pressure to a mode valve of a primary flight control system when the first outlet is fluidically coupled to the first control opening.

2. The valve according to claim 1, wherein the brake is engaged when there is no actuation of the valve, and wherein actuation of the valve opens the brake.

3. The valve according to claim 1, wherein fluidically coupling the first control opening to the first outlet causes a switching or proportional function.

4. The valve according to claim 1, wherein the valve is controlled via a mechanical input.

5. The valve according to claim 1, wherein the valve does not comprise switching valves and/or springs.

6. The valve according to claim 1, wherein the spool has a spool stroke of from 0.3 mm to 3 mm.

7. The valve according to claim 1, wherein the valve is an electrohydraulic servo valve (EHSV) and can be actuated with an actuating current of +/10 mA.

8. The valve according to claim 1, wherein the valve is arranged on and/or in a valve block for a hydraulic consumer, including a motor or a cylinder.

9. An aircraft comprising a valve according to claim 1.

10. The valve according to claim 1, wherein the first control opening is spaced apart from the second control opening by a distance of 0.1 mm to 1 mm, and wherein the spool stroke is 0.5 mm to 3 mm.

11. A method of operating a continuous or proportional valve, comprising: controlling and/or regulating a pressure and/or flow of a fluid, wherein controlling and/or regulating the pressure and/or the flow of the fluid comprises actuating a spool within a spool sleeve of the valve; and effecting at least one further operation or to participate in enabling the operation, wherein the operation comprises releasing a brake; wherein the spool sleeve comprises a plurality of control openings and a plurality of outlets; wherein a first outlet of the plurality of outlets is configured to direct operating fluid to the brake and a second outlet of the plurality of outlets is configured to direct the operating fluid to a consumer; wherein the valve is configured such that actuating the spool within the spool sleeve a first distance in a first direction from a neutral position comprises fluidly connecting a first control opening of the plurality of control openings and the first outlet while a second control opening of the plurality of control openings remains fluidly isolated from the second outlet, wherein fluidly connecting the first control opening and the first outlet releases the brake; wherein the valve is further configured such that actuating the spool within the spool sleeve a second distance in the first direction from the neutral position comprises fluidly connecting the second control opening and the second outlet; an wherein the first distance is less than the second distance.

12. The method according to claim 11, wherein a sensor is provided which can determine the pressure and/or flow rate for the component.

13. The method according to claim 11, wherein the brake is engaged when the valve is in the neutral position.

14. The method according to claim 13, wherein the operation is effected with the characteristic of a switching or proportional operation.

15. The method according to claim 14, wherein the valve is controlled via a mechanical input.

16. The method according to claim 15, wherein the valve does not comprise switching valves and/or springs.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further advantages, features and effects of the present disclosure will be apparent from the following description of preferred exemplary embodiments with reference to the Figures, in which the same or similar components are indicated by the same reference characters. Shown are in:

(2) FIG. 1: A view of an embodiment of a spool of a valve according to the disclosure.

(3) FIG. 2: A sectional view of an embodiment of a spool of a valve according to the disclosure.

(4) FIG. 3: A schematic circuit diagram of an embodiment of a valve block with a valve according to the disclosure.

(5) FIG. 4: A schematic circuit diagram of a further embodiment of a valve block with a valve according to the disclosure.

(6) FIG. 5: A schematic circuit diagram of an embodiment of a prior art switching block with a valve and a motor.

DETAILED DESCRIPTION

(7) An exemplary continuous valve includes a spool assembly comprising a spool and a spool sleeve. The continuous valve is, for example, an electrohydraulic servo valve (EHSV). The spool is designed to be capable to deliver hydraulic flow to a consumer, such as a motor, in proportion to the spool stroke.

(8) In addition, the spool valve is designed in such a way that when the spool valve is moved from its neutral position, additional hydraulic pressure is supplied to a single solenoid valve. When this is actuated, pressure is available, for example, to open a brake of a high-lift system.

(9) By means of a pressure sensor, e.g. at the switching output, it can be checked whether a deflection of the spool has taken place during actuation. In addition, direct information about the supply pressure is available when the valve is actuated.

(10) Thus, all hydraulic functions and safety levels are implemented, which are included in the solution according to the prior art.

(11) FIG. 1 shows the spool sleeve 6 of the continuous valve. Hydraulic fluid is supplied through the control slots 1 and 4. The openings 8 and 9 allow the hydraulic fluid to flow to and from the consumer, e.g. a hydraulic motor. The expanded working fluid flows back through slots 2 and 3 into the return line of the system.

(12) FIG. 2 shows the spool group in partial section. Depending on the direction of movement of the spool 7 relative to the spool sleeve 6, the individual control openings are connected to each other. If the spool 7 in FIG. 2 moves to the right, the supply pressure applied to opening 4 is connected to outlet 9, which directs the fluid to the consumer. The fluid thus flows to the consumer and from this via opening 8 back into the sleeve. The fluid flows into the return flow of the system via the opening 2, which is now also open. With the shape of the control openings 1, 2, 3 and 4, it is possible to achieve, for example, a linear relationship between the spool stroke and the flow to the consumer. In this example, this would be the characteristic of a proportional valve.

(13) If the spool 7 is moved by a sufficiently large amount out of the neutral position, then, depending on the direction of movement, further control edges 5a and 5b are opened in addition to the above-mentioned control edges for the consumer. If the spool moves to the right, for example, opening 5b is unblocked. Through this, a pressure or flow signal is routed to the opening 10, where it is available for a further function. In this example, two functions are implemented at outlet 10. On the one hand, the pressure is monitored by means of a pressure sensor. This indirectly signals whether the spool is in neutral position or not. On the other hand, if pressure is applied, a brake in the high-lift system, which is held closed by means of springs, can be opened hydraulically.

(14) By selecting different overlaps of the control edges for the primary consumer 11 at the control openings for these 1, 2, 3 and 4 in relation to the control edges for the additional function 12 at the control openings for these 5a, 5b, a certain switching behavior can be set. For example, the main consumer can only be supplied with operating liquid when the additional function has been triggered or vice versa.

(15) In the present case, the overlaps are selected in such a way that a pressure can be measured at outlet 10 or the brake can be opened before the consumer, e.g. a hydraulic motor, is supplied with the operating medium.

(16) FIG. 3 and FIG. 4 show details of schematic views of valves with the ports S, C1, R, C2, and P, where P denotes the supply inlet, R denotes the outlet, C1 and C2 denote the pressure and/or flow control ports, and S denotes the port for another function.

(17) The disclosure has the following advantages:

(18) The integrated switching function eliminates the need for multiple solenoid valves.

(19) The use of EHSV technology eliminates the need for a complex spring assembly or the clocked switching of solenoid valves.

(20) The current demand is significantly reduced. For example, only+/10 mA instead of several amperes per solenoid valve are required to switch the valve.

(21) The pressure signal at the switching function, for example, instead of an LVT, the LVDT can be used as a monitoring means for the spool position.

(22) Due to the high dynamics of the EHSV, arbitrary control dynamics can be implemented by means of appropriate actuation.

(23) When a pressure sensor is integrated, the pressure can be measured much more accurately.

(24) Because of the EHSV function, speed control is possible even with a fixed displacement motor.

(25) The elimination of switching valves and throttles makes the valve block much more compact and saves the cost of these purchased parts.

(26) FIGS. 1-2 are drawn to scale, although other relative dimensions may be used.