EP1757817B1 - Valve arrangement for controlling a quick-acting valve of a gas or vapour turbine - Google Patents

Description

The invention relates to a valve arrangement for controlling a component with three input switching valves, through which a pressurized medium can be conducted, which are connected to the inflow side with supply lines to a pressure supply and which are arranged fluidically parallel to each other, and with a connecting element for the device, which Connecting element is connected by pressure lines with drain sides of all input switching valves.

Valve arrangements of this type are well known. For example, such valve arrangements are referred to as trip blocks with a 2 of 3 interconnection, and are known, for example, for the quick release of a quick-closing valve, in particular of gas or steam turbines. The designation 2 of 3 states that of three available signal channels, at least 2 must be actuated in order to trigger the fast-closing signal. In particular, arrangements have prevailed on a hydraulic basis, that is, the control medium for triggering the high-speed signal is usually a hydraulic oil.

In the known valve arrangements, it is structurally impossible, if necessary, to detect or monitor the conditions or the operating state at each point of the arrangement.

A valve assembly according to the preamble of claim 11 or claim 1 is made EP 0 540 963 A1 known.

Based on this prior art, it is an object of the invention to provide a valve assembly for driving a device, which provides a monitoring option for each component of the arrangement.

This object is achieved by a valve arrangement for driving a component with the features specified in claim 1 and with the features specified in claim 11.

Accordingly, the valve arrangement according to the invention for controlling a component of the type mentioned in that a connected to the medium control line is connected to the pressure supply that three control valve groups are controlled with the control line that each switching valve group are assigned two switching valves and one of the input switching valves, that between a switching valve group and the control line in each case a control valve is interposed, with which control valve the switching operations of the switching valves and the input valve of the corresponding switching valve group allows that between a drainage point for the medium and the connecting element three flow-parallel discharge lines are arranged for the medium, that in each of the drain lines two switching valves are arranged in series, and that the switching valves of each drain line of different Ansteu erventilen are actuated.

In this way it is ensured that the 2 of 3 principle is realized by a mechanical arrangement of different valves in the arrangement, so that according to the invention there is the possibility of both the states of the valves and their physical conditions; but also to detect or monitor all desired conditions of the pressure medium between the valves or the connected lines. Thus, it is also ensured that any conceivable or desired size can be monitored. In an advantageous embodiment, the control valve is designed as a solenoid valve.

In this way, a particularly simple control of the valve arrangement is made possible. In this case, each solenoid valve is a channel of a drive signal, which is separately controllable. In the present case, there are three channels, three Control options available. If only one of these channels fails, it is ensured according to the 2 of 3 principle that the valve arrangement according to the invention is still in the ready state. It is only of secondary importance, whether this channel has failed because of an electrical or a hydraulic error.

Advantageously, the generally known fail-safe principle can be carried out with the valve assembly according to the invention by, for example, the switching valves, the input valves and / or the control valves have a return element, in particular a return spring, which the valve in the idle state in a predetermined valve position , holds or brings, namely the fail-safe-proper position.

In the case of the input switching valves, which are preferably designed as hydraulic valves, the "closed position" is the position in the idle state. For the switching valves, which are also usually hydraulically driven valves, the "open position" is the position in the idle state and for the solenoid valves, the electric actuator operates against the return element, so that in the current-free state, the return element of the valve this also in the position of inoperative condition transferred.

An advantageous development of the subject invention is characterized in that the valves, namely the input valves, the switching valve and the control valves are arranged in a common housing.

In this way, a particularly space-saving arrangement is achieved according to the invention. The assembly is simplified and possible assembly errors are reduced to a minimum.

For a status evaluation of the valve arrangement and a continuous condition monitoring, pressure signals are provided in particular at different points of the valve arrangement according to the invention.

For adjusting certain currents and pressures within the valve assembly or in the corresponding connecting lines of the valve assembly also throttle bodies, such as orifices, Verstellblenden or valves and the like are provided, so that the valve arrangement according to the invention is adjustable in a particularly simple manner.

In addition, the object is achieved by a valve arrangement for driving a component having the features specified in patent claim 11.

The features specified in the aforementioned claim are the possibility to create a valve assembly according to the invention, as a safety principle a 2 out of 4, 2 out of 5, 3 out of 4, 3 out of 5, 3 out of 6, etc. principle, so any according to the wishes of a security default to be designed channel-Verschaltungsmöglichkeit. Even with such a valve arrangement advantages of the invention can be achieved.

Further advantageous embodiment of the stop device according to the invention can be found in the further dependent claims.

Reference to an embodiment shown in the drawings, the invention, advantageous embodiment, improvement of the invention and particular advantages to be explained and described in detail.

Fig.1

Eine Prinzipsskizze einer Auslösevorrichtung in Betriebszustand und

Fig.2

die Prinzipsskizze der Auslösevorrichtung in ausgelösten Zustand.

Show it:

Fig.1

A schematic diagram of a tripping device in the operating state and

Fig.2

the schematic diagram of the triggering device in tripped state.

Fig.1 shows a triggering device 10 in a schematic representation, in the present example, three signal channels are available, with two of these channels must trigger to actuate the triggering device 10. In addition, in this example, the valves, sensors and piping shown are essentially realized in a single device, so that the triggering device 10 is designed to be particularly compact and thus space-saving.

The triggering device 10 is prepared with a first flange 12 to be connected to a pressure supply, not shown in this figure. The embodiment of the invention shown in the figure is realized by a hydraulic system, so that the pressure supply is ensured for example by a pump for hydraulic oil. The hydraulic oil will supply the triggering device 10 with hydraulic oil through the connection point on the first flange 12 into a first pipeline 14. In this case, a first 16, a second 18, and a third input switching valve 20 are fluidly connected in parallel to the first pipe 14. The input switching valves 16, 18, 20 essentially have two switching positions, wherein a first switching position is shown in this figure and should be referred to as "open", so that the hydraulic oil flows through the input switching valves 16, 18, 20. A second switching position, referred to as "closed", may be adjusted by the input switching valves 16, 18, 20 by actuating a hydraulic cylinder 22 provided on each input switching valve 16, 18, 20 and correspondingly changing the valve position. In this case, the hydraulic cylinder 22 operates against a spring, not shown in this figure, the failure of the hydraulic system, in particular in a pressure drop at the hydraulic cylinder 22, the input switching valves 16, 18, 20 in the predetermined first position "open" spends.

The hydraulic oil now flows from the first flange 12 through the first pipe 14 to and through the first input switching valve 16, which is connected on the output side to a first side of a second pipe 24, while a second side of the second pipe 24, the hydraulic oil into a manifold 26 leads. At a first manifold 28, a first check valve 30 with tubing fittings is disposed between the first manifold and the manifold 26. Branches or junctions of lines are highlighted in the figure with black dots.

In this case, the first spring-loaded check valve 30 ensures that only from a set minimum pressure hydraulic oil into the manifold 26 passes at corresponding pressure conditions in the pipes a return flow of oil against the planned pressure gradient back into the second pipe 24 is prevented. In this way, a pressure relief of the system is realized.

Between the first pipe branch 28 and the first input switching valve 16, a first adjustable orifice 32 is arranged as a throttle member. With the first orifice 32, a predeterminable pressure in the second pipe 24 is adjusted, and thus also the flow rate. Downstream of the first orifice 32, a first pressure sensor 34 is arranged, which measures the pressure downstream of the first orifice 32.

In a similar manner, further pipelines, orifices and pressure sensors are connected downstream of the second 18 and the third input switching valve 20, all of which conduct hydraulic oil into the manifold 26. For the sake of clarity in the figure, however, the corresponding reference numerals have been omitted here. The manifold 26 also has a second pressure sensor 36 which measures the resulting pressure of all three supply systems from the pressure supply via the input switching valve 16, 18, 20. In addition, the manifold 26 still has a connection point 38 with a connecting element, not shown, on which quite generally a component can be shot. In a preferred embodiment, the component is a quick-acting valve, for example for a gas turbine or a steam turbine, which ultimately receives a control signal via which the connecting element. As long as a certain pressure prevails in the manifold 26 and thus at the junction, the quick-closing valve remains open. In the other case, if there is a pressure drop in the manifold 26 below the certain, predetermined, value, the quick-closing valve will close, in particular by a certain biasing force, moved to its "closed" position. The quick-closing valve can accordingly be used as a safety valve.

The first pipe 14 also branches at a second pipe branch 40 on the one hand to a pressure relief valve 42 and on the other hand in a control line 44. The control line 44 passes the hydraulic oil, which is now used as control oil, to a first 46, a second 48 and a third control valve 50. These control valves 46, 48, 50 are designed so that they are electromagnetically are controlled, which is symbolized by a corresponding symbol 52 in the figure. The drive operates in each case against a spring 54, which ensures in the case of failure of the drive that the control valves 46, 48, 50 are spent in a design-related situation and held there.

The action of the control valves 46, 48, 50, will now be explained in more detail on the first control valve 46: This is designed so that it simultaneously switches two hydraulic lines with a switching movement. In the illustrated example of this figure for the first switching position while the hydraulic oil is passed from the control line 44 to a first supply line 56, which ensures that the pressure, by means of hydraulic oil, to a first control cylinder 58 of a first switching valve 60 and a second control cylinder 62 of a second switching valve 64 is supplied.

The pending before the first 60 and second switching valve 64 pressure causes the corresponding control cylinder 60, 62, the switching valves 68, 64 in the first switching position, spends. In this case, each of the switching valves 60,64 operates against a spring, so that the switching position of the switching valves 60, 64 is only achieved as long as a pressure in front of the control cylinders 58, 62 is present. Should a pressure drop in this system be caused for any reason, the relevant switching valve 60,64 is automatically transferred by the error in its second switching position, which releases the hydraulic path through the valve. In addition, a second pressure relief valve between the first switching valve 60 and the first control valve 46 is interposed in the first supply line 56. In particular, it fulfills a safety function.

In addition, the hydraulic cylinder 22 of the first input switching valve 16 is connected via the second supply line 57 and the first control valve 46 with a drainage pipe 68, which ultimately leads to a substantially unpressurized outflow point 70, which returns the incoming there hydraulic oil in an oil system. This is usually in turn connected to the pressure supply, so that overall results in a non-illustrated closed circuit for the hydraulic oil. By the second supply line 57 is also ensured that in the illustrated first switching position of the first control valve 46 whose hydraulic cylinder 22 is not driven and accordingly, the return spring, not shown, the first input switching valve 16 has spent in the switching position shown.

The manifold 26 is connected by a first 72, a second 74 and a third drainage line 76 to the drainage pipe 68. In this case, in the first drainage line 72, the second switching valve 64 and a further switching valve, which is switched by the second control valve 48, installed in the pipeline in series. This is achieved according to the invention that in the first drainage line 72 through the aforementioned switching valves at two points, the flow of hydraulic oil from the manifold 26 can flow at a relatively high pressure level in the drainage pipe 68 with a comparatively low pressure level. Only when both switching valves are depressurized on their control cylinder and thus open, the drainage of the hydraulic oil through the first drainage pipe 72 is ensured.

Accordingly, two switching valves are also arranged in the second drainage line 74, of which a first via the second control valve 48 and a second via the third control valve 50 is driven. In addition, the corresponding two switching valves in the third drainage line 76 are actuated by the third control valve 50 or by the first control valve 46.

By means of this interconnection, it is ensured and apparent that the respective two connection valves in each rotary line 72, 74, 76 are actuated by different combinations of two of the three control valves 46, 48, 50. For the interconnection, this means, even if one of the switching valves should fail, and is moved by the return spring in its fail-safe position and thus releases the path for the hydraulic oil through the respective switching valve, is still a second switching valve in each drainage line 72, 74,76, which still blocks the flow of hydraulic oil. In addition, it is ensured that a failure of one of the control valves 46, 48, 50 does not cause the pressure drop in the manifold 26. Because each of the control valves 46, 48, 50 controls a total of two of the switching valves. However, these are installed in each different drainage line 72, 74, 76, so that a pressure drop, for example in the first supply line 56 only causes the first switching valve 60 in the third drainage line 76 is switched to passage, and the second switching valve 64 in the first drainage line 72 is switched to passage. In both drainage line 72, 76 there are but still another switching valve that ensures that the drainage line 72, 76 remain closed and no pressure drop in the manifold 26 is effected. In this way, a mechanical interconnection of the two of three principle is ensured according to the invention.

The first pipe 14 is also still connected by means of a first 78, a second 80 and a third bypass line 82 to the drainage pipe 68. These serve in particular for the comfortable adjustment of the pressure conditions in the system. For this purpose, throttle bodies 84, for example throttle orifices, are installed in the bypass lines 78, 80, 82 at points marked "D". The pressure conditions upstream of these throttle bodies can thereby be adjusted in a particularly simple manner. In this case, the first bypass line 78 is connected to the first drainage line 72 and in the pipe section between the two switching valves, wherein the two throttle bodies "D", which are installed in the first bypass line 78, upstream and downstream of the connection point are arranged. Between the two built-throttle elements also a third pressure sensor 86 is also arranged, which measures according to the pressure between the two throttle points and also on the principle of the connected tubes and the pressure between the two switching valves of the first drainage line 72. It can be determined via the pressure level which is established there, whether one of the two switching valves is open and from this the inference to appropriate errors or damages in the system or the switching valves or also the control valves to draw. However, the necessary evaluation devices for the measurements and possibly further measuring and control technology are not shown in the figure.

Accordingly, the second bypass line 80 is connected to the second drainage line 74 and the third bypass line 82 to the third drainage line 76. In the figure, however, the corresponding reference numerals are not included for reasons of simplicity.

FIG. 2 shows the triggering device 10 in which by appropriate control of the control valves 46, 48, 50, the system has been depressurized at the junction to reach, so that a quick-acting valve connected thereto exerts its quick-closing function. Since this figure is the same triggering device 10 as in FIG. 1 The previously used reference numerals, the same components, are also used in this figure. However, only those components are provided with reference numerals to explain this figure or the deviations from FIG. 1 necessary.

In the present case, the control valves 46, 48, 50 are deliberately de-energized, so that the corresponding return springs on these valves spend them in a predefined end position, the second position, and hold there. The internal interconnection of the control valves 46, 48, 50 is designed such that the pressure prevailing in the control line 44 passes via the first control valve 46 to the second supply line 57 and thus supplies the hydraulic cylinder 22 with pressure, and thus the first input switching valve 16 in a Position is spent, in which the flow of hydraulic oil through the first pipe 14 to the second pipe 24 is interrupted. Since all input switching valves 16, 18, 20 close the first pipe 14, the pressure supply of the manifold 26 is prevented altogether.

In addition, the first supply line 56 is now connected to the drainage pipe 68 by the described valve position of the first control valve 46. This ensures that the first switching valve 60 and the second switching valve 64 and the control cylinder 58, 62 are depressurized, so that the restoring springs there also spend these switching valves 60, 64 in the second position and hold there. In this position, the valves allow passage of hydraulic oil from the manifold 26 to the drainage pipe 68. Since there are two switching valves in each drainage line 72, 74, 76, both switching valves are switched to passage to allow the hydraulic oil from the manifold 26 to enter the drainage pipe 68 can. This is inventively achieved in that all three control valves 46, 48, 50 are connected without power, so that all existing switching valves are spent in their second position and are also held there.

LIST OF REFERENCE NUMBERS

10

triggering device

12

first flange

14

first pipeline

16

first input switching valve

18

second input switching valve

20

third input switching valve

22

hydraulic cylinders

24

second pipeline

26

manifold

28

first pipeline branching

30

first check valve

32

first aperture

34

first pressure sensor

36

second pressure sensor

38

junction

40

second pipeline branch

42

Pressure relief valve

44

control line

46

first control valve

48

second control valve

50

third control valve

52

symbol

54

feather

56

first supply line

57

second supply line

58

first control cylinder

60

first switching valve

62

second control cylinder

64

second switching valve

66

second pressure relief valve

68

drainage pipe

70

drainage point

72

first drainage line

74

second drainage line

76

third drainage line

78

first bypass cable

80

second bypass line

82

third bypass line

84

throttle member

86

third pressure sensor

Claims (11)

1. Valve arrangement for the activation of a structural element comprising three inlet switching valves (16, 18, 20), inflow lines (14), pressure lines (24, 26) and a connection element (38) for connection of the structural element to the valve arrangement, wherein

   • a pressure-loaded medium can be conducted through the inlet switching valves (16, 18, 20),

   • the inlet switching valves (16, 18, 20) can be connected on their inflow side to a pressure supply by means of the inflow lines (14),

   • the inlet switching valves (16, 18, 20) are arranged parallel to one another in flow terms, and

   • the connection element (38) is connected to outflow sides of all the inlet switching valves (16, 18, 20) by means of the pressure lines (24, 26),

   characterized in that
   the valve arrangement furthermore comprises a control line (44), three switching-valve groups, activation valves (46, 48, 50) and three outflow lines (72, 74, 76) for the medium, wherein

   • the control line (44) is acted upon by the medium and can be connected to the pressure supply,

   • the three switching-valve groups can be activated by means of the control line (44),

   • each switching-valve group comprises two switching valves (60, 64) and one of the inlet switching valves (16, 18, 20),

   • one of the activation valves (46, 48, 50) is interposed in each case between a switching-valve group and the control line (44), by means of which activation valve (46, 48, 50) the switching actions of the switching valves (60, 64) and of the inlet switching valve (16, 18, 20) of the corresponding switching-valve group are made possible,

   • the outflow lines (72, 74, 76) are connected in parallel in flow terms and are arranged between an outflow location (70) for the medium and the connection element (38),

   • two switching valves (60, 64) are arranged in a series connection in each of the outflow lines (72, 74, 76), and

   • the switching valves of each outflow line (72, 74, 76) are actuated by different activation valves (46, 48, 50).
2. Valve arrangement according to Claim 1, characterized in that the medium is a gas or a liquid, in particular an oil.
3. Valve arrangement according to Claim 1 or 2, characterized in that the structural element is a quick-acting shut-off valve or a safety device.
4. Valve arrangement according to one of the abovementioned claims, characterized in that the activation valve (46, 48, 50) is a solenoid valve.
5. Valve arrangement according to one of the abovementioned claims, characterized in that the switching valves (60, 64), the inlet switching valves (16, 18, 20) and/or the activation valves (46, 48, 50) have a return element, in particular a return spring, which, when the valve is in the inoperative state, keeps the latter in or brings the latter into a predetermined valve position.
6. Valve arrangement according to one of the abovementioned claims, characterized in that the switching valves (60, 64), the inlet switching valves (16, 18, 20) and the activation valves (46, 48, 50) or the valves of a switching-valve group are arranged in a common housing belonging to the valve arrangement.
7. Valve arrangement according to one of the abovementioned claims, characterized in that a pressure sensor (34, 36, 86) is arranged in each pressure line connected to an inlet switching valve (16, 18, 20).
8. Valve arrangement according to one of the abovementioned claims, characterized in that a pressure sensor (34, 36, 86) is arranged in each outflow line in the line portion between the two switching valves (60, 64) arranged in the respective outflow line.
9. Valve arrangement according to one of the abovementioned claims, characterized in that three bypass lines (78, 80, 82) belonging to the valve arrangement, with at least one throttle member (54) in each bypass line (78, 80, 82), are arranged between the inflow lines and the outflow lines of the valve arrangement, and in that the bypass lines (78, 80, 82) are connected to the outflow lines in the region between the switching valves (60, 64) and the outflow location of the bypass lines (78, 80, 82).
10. Valve arrangement according to one of the abovementioned claims, characterized in that in each case one bypass line (78, 80, 82) belonging to the valve arrangement is connected to an outflow line, and in that the connection point is arranged between the two switching valves (60, 64) of the respective outflow line.
11. Valve arrangement for the activation of a structural element comprising three inlet switching valves (16, 18, 20), inflow lines (14), pressure lines (24, 26) and a connection element (38) for connection of the structural element to the valve arrangement, wherein

    • a pressure-loaded medium can be conducted through the inlet switching valves (16, 18, 20),

    • the inlet switching valves (16, 18, 20) can be connected on their inflow side to a pressure supply by means of the inflow lines,

    • the inlet switching valves (16, 18, 20) are arranged parallel to one another in flow terms, and

    • the connection element is connected to outflow sides of all the inlet switching valves (16, 18, 20) by means of the pressure lines,

    characterized in that
    the valve arrangement furthermore comprises a control line (44), a first number of switching-valve groups, activation valves (46, 48, 50) and the first number of outflow lines (72, 74, 76) for the medium, wherein

    • the control line (44) is acted upon by the medium and can be connected to the pressure supply,

    • the first number of switching-valve groups can be activated by means of the control line,

    • the first number of switching-valve groups corresponds to the number of inlet switching valves present,

    • a second number of switching valves (60, 64) and one of the inlet switching valves (16, 18, 20) are assigned to each switching-valve group,

    • the second number of switching valves (60, 64) is obtained from the first number of switching valve groups minus a whole number, insofar as the result is the number two or a greater number,

    • one of the activation valves (46, 48, 50) is interposed in each case between a switching-valve group and the control line, by means of which activation valve (46, 48, 50) the switching actions of the switching valves (60, 64) and of the inlet switching valve (16, 18, 20) of the corresponding switching-valve group are made possible,

    • the outflow lines (72, 74, 76) are connected in parallel in flow terms and are arranged between an outflow location for the medium and the connection element,

    • a second number of switching valves (60, 64) is arranged in a series connection in each of the outflow lines, and

    • the switching valves (60, 64) of each outflow line are actuated by different activation valves (46, 48, 50).

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