DE186220C

DE186220C -

Info

Publication number: DE186220C
Application number: DENDAT186220D
Authority: DE

Description

KAISERLICHESIMPERIAL

PATENTAMT.PATENT OFFICE.

- JVIl86220 -- JVIl86220 -

KLASSE 14c. GRUPPEZ #-1 CLASS 14c. GROUPZ # - 1

in FRANKFURT a. M. ·in FRANKFURT a. M.

zugeführten Dampf.supplied steam.

Bekanntlich bietet es gewisse Vorteile, wenn man Dampfturbinen oder ähnlichen Maschinen den Dampf oder die Gase nicht unter gleichbleibendem Druck, sondern mit periodisch schwankendem Drucke zuführt. Um diesen Effekt zu erreichen, hat man bisher ein in den Dampf weg eingeschaltetes und in schwingende Bewegung gesetztes Ventil verwendet, mußte aber dabei beträchtliche DampfverlusteIt is well known that there are certain advantages to using steam turbines or similar machines the steam or the gases not under constant pressure, but with periodic supplies fluctuating pressure. In order to achieve this effect, an in uses a valve that is switched on and in motion with the steam off, but had to suffer considerable steam losses

ίο in Kauf nehmen, welche von der Drosselung und der abwechselnden Kondensation und Expansion des Dampfes usw. herrühren.ίο accept some of the throttling and the alternating condensation and expansion of the vapor, etc. result.

Gemäß der Erfindung werden die Dampfverluste dadurch erheblich verringert, daß an Stelle eines einzigen Absperr- oder Drosselungsorganes (Ventiles) deren mehrere nebeneinander in der Zuleitung angeordnet werden, ■ und zwar so, daß sie sich nicht mit gleicher Phase bewegen.According to the invention, the steam losses are significantly reduced that on Place a single shut-off or throttling device (valve) several of them next to each other be arranged in the supply line, ■ in such a way that they are not with the same Move phase.

Man kann beispielsweise zwei Ventile verwenden, deren Ventilkegel von einer Steuerwelle mittels je eines Exzenters bewegt werden, und zwar so, daß, wenn ein Ventil in der höchsten Lage ist, das andere sich in seiner tiefsten Lage befindet, gegebenenfalls ganz geschlossen ist. Zweckmäßig benutzt man diese Ventile zugleich als. Regelungsventile, indem durch einen Regler oder von Hand die mittlere Hubhöhe der Ventile je nach Belastung vergrößert oder verkleinert wird.For example, two valves can be used, the valve cone of which is controlled by a control shaft be moved by means of an eccentric, in such a way that when one valve is in the highest position, the other is in its lowest position is, if necessary, completely closed. Used appropriately one these valves at the same time as. Control valves by by a regulator or by Hand increases or decreases the mean lift height of the valves depending on the load will.

Ein Ausführungsbeispiel, bei welchem angenommen ist, daß die Drosselventile zugleich als Regelungsventile dienen und mittels einer Widnmann-Steuerung von einem Regler mittels Stange b und Winkelhebel c beeinflußt werden, ist in beiliegender Zeichnung Fig. ι und 2 dargestellt. Jedes der beiden Ventile e_t und e₂ wird von einem besonderen Exzenter α_λ bezw. a.₂ bewegt. Die Exzenter sind beispielsweise um i8o° gegeneinander verstellt. Werden die Ventile e_x und e₂, wie aus Fig. 2 ersichtlich, in einem gemeinsamen Gehäuse untergebracht, so ergibt sich als Druckkurve für die Dampfspannung des von beiden Ventilen in die Turbine g geschickten Dampfes die Kurve III aus Fig. 3, welche sich aus der vom Ventil e₁ allein erzeugten Druckkurve I und der vom Ventil e₂ erzeugten Druckkurve II zusammensetzt.An embodiment, in which it is assumed that the throttle valves also serve as control valves and are influenced by a controller by means of rod b and angle lever c by means of a Widnmann control, is shown in the accompanying drawing FIGS. Each of the two valves e _t and e ₂ is respectively a special eccentric α _λ. a. ₂ moves. The eccentrics are adjusted relative to one another by 180 °, for example. If the valves e _x and e ₂ , as can be seen from FIG. 2, are accommodated in a common housing, the pressure curve for the steam pressure of the steam sent by both valves into the turbine g is curve III from FIG composed of the pressure curve I generated by the valve e ₁ alone and the pressure curve II generated by the valve e _2.

Macht man gemäß Fig. 4 den Dämpfweg vom Kessel k zu den Ventilen e_x und e₂ gleich groß, die von den Ventilen zur Turbine g führenden Dampfwege aber derart ungleich, daß die vom Ventil ε_λ herrührende Druck-Schwankung I sich zu der vom Ventil e.₂ herrührenden Druckschwankung II addiert, so erhält man für die Dampfspannung zwischen Ventilgehäuse und Turbine das Druckdiagramm IV aus Fig. 5. Während hier die Druckschwankungen erheblich sind, werden die Druckschwankungen auf der Dampfkesselseite gemäß Kurve III (Fig. 6) sehr gering.4, the damping path from the boiler k to the valves e _x and e _{2 is the} same, but the steam paths leading from the valves to the turbine g are so unequal that the pressure fluctuation I originating from the valve ε _{λ becomes that of the} Valve e. _{If the pressure fluctuation II resulting from 2 is} added, the pressure diagram IV from FIG. 5 is obtained for the steam tension between the valve housing and the turbine.

Der durch k eintretende Dampf findet nämlich gemäß dem Diagramm (Fig. 6) in dem ersten in Betracht gezogenen Zeitpunkt dasAccording to the diagram (FIG. 6), the steam entering through k finds that at the first point in time considered

Claims

Valve e ₂ closed, valve e _x open, with valve e. ₂ the greatest resistance to movement occurs that the valve e ₂ can offer at all, at the same time the valve e _x offers the least resistance to movement. Accordingly, a pressure will be established in the supply line k which corresponds to the full opening of a valve. Valve e _{x is then} gradually closed, valve e. ₂

ίο gradually opened, and you can set up the movement device of both valves in such a way that at every moment approximately the same opening is released by both valves that one valve alone releases at its maximum stroke, so that on one stream side k during the valve clearance, the steam pressure is approximately constant remain. In FIG. 6, the pressure fluctuations resulting from the movement of the valve e _{x are shown} by curve I, and the _{pressure fluctuations resulting from valve e 2} are shown by the pressure curve II. The pressure fluctuations caused by the two valves together give, by simple summation, curve III, which illustrates the state prevailing in feed line k.

In Fig. 6 it is assumed that both valves together when they are in one Are in the middle position, open slightly more passage openings than one valve alone at its greatest stroke. As already said above, the sum of the Keep the approved cross-sections constant at all times.

The effect of the special valve arrangement is most evident when the distance between the valves is related to their number of stroke periods and the steam speed. Make z. B. the valves 150 strokes per minute, and two valves are used and the steam speed on the path between the two valves is about 10 m per second, the second valve opens ^] / ₅ seconds later than the first valve, and the distance between the two valves must now be so great that the steam let in from the first valve arrives at the second valve as precisely as possible after this fifth of a second. In the example chosen, this corresponds to a distance of two meters between the valves.

In order not to have to provide a special drive mechanism for each valve, you can also couple the valves with each other, for example by means of balancing, and only one valve control use in whole.

60 Godfather nt-A ν Proverbs:

I. Device for generating periodic pressure fluctuations in the a steam turbine supplied steam, characterized in that 'that several shut-off (resp. Throttling) organs are arranged side by side in the supply line and periodically moved in different phases will.

2. Embodiment according to claim i, characterized in that two throttle valves are moved as shut-off devices be that each one reaches its maximum stroke when the other reaches its minimum stroke.

3. Äusführungsform according to claim 1 or 2, characterized in that the Steam paths in front of the individual shut-off organs on the one hand and those behind the shut-off devices on the other hand are dimensioned so that the inflow of the Propellant to the shut-off devices, if possible without pressure fluctuations, the outflow from the shut-off devices to the turbine with the greatest possible pressure fluctuations he follows.

1 sheet of drawings.