EP1826407A1 - Valve for piston compressors - Google Patents

Abstract

The automatic valve (1) for reciprocating compressors comprises a valve seat (2) with passage openings (2a), a catcher (3) and a plurality of closure members (4) arranged between valve seat (2) and catcher (3) for closing the passage openings (2a), wherein the closing members (4) from the catcher (3) by means of springs (5) against the passage openings (2a) of the valve seat (2) are loaded, and wherein the valve has at least two differently acting part valve areas (6a, 6b), a first part valve area (6a), the closing members (4a) are loaded with springs (5a) lower spring force, and a second part valve portion (6b), the closing members (4b) are loaded with springs (5b) of higher spring force.

Description

The invention relates to an automatic valve for reciprocating compressors according to the preamble of claim 1.

Such a valve is for example from the document EP 0 572 748 known. This valve has the disadvantage that during compressor operation with extremely light gases such as, for example, hydrogen has an improvement in runtime, since relatively soon wear of the valve seat and / or the closing member can occur.

The compression of light gases, in particular of hydrogen, is becoming increasingly important. For example, hydrogen is increasingly used as an energy source for motor vehicles, which is why there is a great demand for compressed hydrogen in the future, which should be available in large quantities and also at low cost.

It is an object of the present invention to propose a technically and economically advantageous valve for reciprocating compressors. The valve should in particular have a higher transit time.

This object is achieved with an automatic valve for reciprocating compressors having the features of claim 1. The dependent claims 2 to 9 relate to further advantageous embodiments.

The object is achieved in particular with an automatic valve for reciprocating compressors, comprising a valve seat with passage openings, a catcher and a plurality of valve seat and catcher closing members for closing the passage openings, wherein the closing organs are charged by the catcher by means of springs against the passage openings of the valve seat, wherein the valve has at least two differently acting partial valve areas, a first partial valve area, the closing members of which are loaded with springs of lower spring force, and a second partial valve area, the closing members of which are loaded with springs of higher spring force.

The inventive valve has two partial valve areas, which are designed for different heavy gases. The first part of the valve range is designed so that it already opens during operation with a light gas, whereas the second part of the valve range opens only when operating with a heavy gas.

By a light gas herein is meant a gas having a molecular mass of less than 10, whereas by a heavy gas herein is meant a gas having a molecular mass greater than 10. Molecular weight or molecular mass is the sum of the atomic masses of all atoms in a molecule. At the same time, the molecular mass indicates how heavy 1 mol of a substance is. 1 mole is 6 0221367 × 10 ²³ particles. Thus, for example, hydrogen (H ₂ ) has a molecular mass of 2 and nitrogen (N ₂ ) has a molecular mass of 28.

Before compressing hydrogen, it is necessary for process and safety reasons that any air or any oxygen is removed from the compressor. This is achieved, for example, by supplying the compressor with a heavy gas such as nitrogen for compression for a period of time to thereby flush out any oxygen. After this purging process, the compressor is supplied with a light gas such as hydrogen for compression.

The valve according to the invention now has two partial valve areas, wherein during the compression of the heavy gas both partial valve areas open and close, whereas during the compression of the light gas only the first partial valve area opens and closes. The first part of the valve range is adapted to the requirements of light gas and has a closing member with a lower spring force and preferably also a closing member with a lower stroke and / or a smaller passage opening, in comparison to the second part valve area.

The valve according to the invention thus has the advantage that the second part of the valve region remains closed during the compression of the light gas, and thus hardly any or no wear during this phase of operation. In addition, the first part of the valve range is designed for compressing light gas, and has during this phase of operation on a light gas optimized, ie in particular low-wear performance on. This shut-off performance is achieved in particular by the fact that the first part of the valve region with respect to the second part of the valve range has a lower spring force and optionally also a small stroke.

Fig. 1

eine Explosionszeichnung eines Ventils;

Fig. 2

einen Längsschnitt durch das Ventil gemäss Figur 1;

Fig. 3-5

Ringventile mit einer Hubbegrenzungsvorrichtung;

Fig. 6

ein Poppetventil mit einer Hubbegrenzungsvorrichtung;

Fig. 7

ein Plattenventil mit einer Hubbegrenzungsvorrichtung;

Fig. 8

eine Aufsicht auf die im Ventil gemäss Figur 7 angeordneten Platten.

The invention will be explained in more detail with reference to the partially schematic figures. Show it:

Fig. 1

an exploded view of a valve;

Fig. 2

a longitudinal section through the valve according to Figure 1;

Fig. 3-5

Ring valves with a stroke limiting device;

Fig. 6

a Poppetventil with a stroke limiting device;

Fig. 7

a plate valve with a stroke limiter;

Fig. 8

a plan view of the arranged in the valve according to Figure 7 plates.

Figure 1 shows an automatic valve 1 for a reciprocating compressor comprising a valve seat 2 with passage opening 2a and a catcher 3 with a plurality of closing members 4 arranged between valve seat 2 and catcher 3, which are intended to close the passage openings 2a. The closing organs 4 are configured as rings 4a, 4b. The closing members 4 are loaded by means of springs 5a, 5b against the passage openings 2a of the valve seat 2. The valve 1 comprises two differently acting partial regions 6a, 6b, the first partial region 6a comprising the closing element 4a with springs 5a, and the second partial valve region 6b the closing element 4b with springs 5b. The springs 5a have a lower spring force than the springs 5b. This has the consequence that the first part of the valve portion 6a is already active at lower applied forces, whereas the second part of the valve portion 6b is active only at larger applied forces. The first part valve area 6a is for example for the Operation optimized with the light gas hydrogen. The second part valve area 6b is optimized for operation with a heavy gas such as nitrogen. The closing member 4b has a substantially larger area than the closing member 4a, with the result that the closing member 4b covers a substantially larger flow opening 2a than the closing member 4a. The valve 1 shown in Figure 1 also includes power transmission means 7 via which the springs 5 are supported on the closing member 4. The valve 1 also includes a bolt 9 with nut 10 and washer 11 to connect the valve seat 2 fixed and releasably connected to the catcher 3.

FIG. 2 shows a longitudinal section through the valve 1 shown in FIG. 1. Again, the two differently acting partial valve areas 6a, 6b can be seen, as well as the closing members 4a, 4b, their associated springs 5a, 5b and the passage openings 2a covered by the closing members 4a, 4b , The spring force of the springs 5a, 5b arranged in the first and second part valve regions 6a, 6b preferably differs at least by a factor of 1.5, that is to say the spring constant differs by a factor of 1.5. The closing members 4a of the first part valve portion 6a preferably have a lower stroke than the closing members 4b of the second part valve portion 6b. The stroke of the closing member of the first part valve portion 6a is preferably at least a factor 1.5 smaller than the stroke of the closing member of the second part valve portion 6b. In addition, the sum of the total flow areas of the first and second partial valve area 6a, 6b differs by at least a factor of 1.5. The flow areas can be determined either by the sum of the areas of the illustrated flow openings 2a. The Flow area can also be defined by the laterally resulting passage area, which results between the open closing member 4a, 4b and the valve seat 2.

In a preferred embodiment, the valve 1, as shown in Figure 1, designed rotationally symmetrical, wherein the first part of the valve portion 6a is arranged against the center of the circle, whereas the second part of the valve portion 6b is arranged against the periphery. 1, the closing element 4a can cover substantially more individual passage openings 2a than the second closing element 4b, so that the sum of the covered passage openings 2a for the closing element 4b is substantially greater greater than for the closing organ 4a.

The closing members 4 can also, as shown in FIG. 6, be designed as a round poppet valve 4c or, as shown in FIG. 7, as a plate valve 4a, 4b. FIG. 8 shows a plan view of the plates 4a, 4b shown in FIG. The closing member 4 comprises an inner, plate-shaped closing member 4a and a concentrically arranged, outer closing member 4b.

As shown in FIGS. 3 to 5, the first or the second partial valve region 6a, 6b may also comprise a plurality of closing members 4a, 4b, which are mounted biased towards the valve seat 2 via springs 5a, 5b. The valve 1, as shown in Figures 3 to 5, also be provided with a stroke limiting device 8, which has a plurality of engagement means or bars 8a, which in the direction of movement of the closing members 4a, 4b are slidably mounted. In addition, a spring 8b may be provided to cause a restoring force upwards. The stroke limiting device 8 can be designed such that the stroke limiting means 8, as shown in FIG. 3, act only on the first part valve region 6a or the closing member 4a or, as shown in FIG. 4, only on the second part valve region 6b or the Closing member 4b, or, as shown in Figure 5, both on the first and on the second part valve portion 6a, 6b act.

Figure 6 shows a longitudinal section through a Poppventil with a stroke limiting device 8, which acts on the closing members 4a of the first part of the valve portion 6a.

Figure 7 shows a longitudinal section through a plate valve with a stroke limiting device 8, which acts on both the first and on the second part valve portion 6a, 6b, and affects the stroke of the first and second closing member 4a, 4b.

Claims (10)

Automatic valve (1) for reciprocating compressors, comprising a valve seat (2) with passage openings (2a), a catcher (3) and a plurality of closing members (4) arranged between valve seat (2) and catcher (3) for closing the passage openings (2a), wherein the closing members (4) are loaded by springs (5) against the passage openings (2a) of the valve seat (2) from the catcher (3), characterized in that the valve has at least two differently acting part valve areas (6a, 6b) first part valve region (6a), the closing members (4a) are loaded with springs (5a) lower spring force, and a second part valve portion (6b), the closing members (4b) are loaded with springs (5b) of higher spring force. Valve according to claim 1, characterized in that the spring force of the first and second part valve area (6a, 6b) arranged springs (5a, 5b) differ by at least a factor of 1.5. Valve according to one of the preceding claims, characterized in that the closing member (4a) of the first part valve portion (6a) has a lower stroke than the closing member (4b) of the second part valve portion (6b). Valve according to claim 3, characterized in that the stroke of the closing member (4a) of the first part valve portion (6a) by at least a factor 1.5 is smaller than the stroke of the closing member (4b) of the second part valve portion (6b). Valve according to one of the preceding claims, characterized in that the flow cross-section of the first and the second part valve area (6a, 6b) differ by at least a factor of 1.5. Valve according to one of the preceding claims, characterized in that the valve is designed rotationally symmetrical, that the first part of the valve region (6a) is arranged against the center of the circle, and that the second part of the valve region (6b) is arranged against the periphery. Valve according to one of the preceding claims, characterized in that the closing members (4) are designed as concentrically arranged annular plates. Valve according to one of the preceding claims, characterized in that a Hubbegenzungsvorrichtung (8) affects the stroke of the closing organs (4) in the first and / or second part of the valve region (6a, 6b). Valve according to one of the preceding claims, characterized in that the first part valve portion (6a) already opens during operation with a light gas, wherein the light gas has a molecular weight of less than 10, and wherein the second part valve portion (6b) only during operation with opens a heavy gas, wherein the heavy gas has a molecular weight of more than 10. Plant for compressing hydrogen, comprising a valve according to one of the preceding claims.

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