FI63694B - TRYCKREGULATOR FOER STYRBROMSVENTILEN TILL EN INDIREKT VERKANDE TRYCKLUFTSBROMS - Google Patents

Description

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Switzerland-Switzerland (CH) 10915/77 (71) Werkzeugmaschinenfabrik Oerlikon-Biihrle AG, Birchstrasse 155, CH-805O Zurich, Switzerland-Switzerland (CH) (72) Walter Miiller, Bassersdorf, Heinz Deutsch, Zurich, Karl Oldani, Zurich, Switzerland-Switzerland (CH) (7 * 0 Berggren Oy Ab (5I +) Indirectly acting compressed air brake control brake pressure regulator - Tryckregulator för styrbromsventilen account en indirekt verkande tryckluftsbroms

The invention relates to a pressure regulator for an indirectly acting compressed air brake control brake valve, provided with a pressure control valve connected to the supply line, which is operated by a drill piston delimiting two chambers and loaded by an adjustable spring and a control pressure.

A pressure regulator of this type (CH-PS 344 749) is known, in which the piston is loaded on the one hand by the control pressure and on the other hand by the air-tail pressure and the adjustable spring. DE-1 146 520 discloses a pressure regulator with a step piston delimiting two chambers.

These models of pressure regulators have the disadvantage that relatively large and strong springs are required, e.g. a spring force of about 50 kg is required for a control pressure of 5 bar.

It is now an object of the present invention to provide a pressure regulator so that considerably smaller springs can be used.

2,63694

The pressure regulator according to the invention is characterized in that in the second chamber the step piston is loaded not only by the spring pressure but also by the air pressure, which is kept constant by means of a pressure limiter connected to the supply line.

Two model examples of a pressure regulator according to the invention are described in more detail below with the aid of the accompanying drawings. They see:

Figure 1: a schematic representation of a pressure regulator according to a first exemplary example; and Figure 2: a schematic representation of a pressure regulator according to another exemplary example.

According to Fig. 1, the pressure limiter 10 is connected to the supply line 11 and the main control member 12 to the main air line 13. The pressure regulator 14 is connected to the pressure limiter 10 via a side line 15 and to the main control member 12 via a second line 16 17, which cooperates with a fixed valve seat 18 on the one hand and a movable valve seat 19 on the other hand. The movable valve seat 19 is at the end of a piston rod 20 attached to a step piston consisting of a large piston 21 and a small piston 22. The spring 23 rests on a small piston 22 on the one hand and a lifter 24 on the other hand. pivotable to the bearing shaft 26. The control brake lever 35 is attached to the shaft 26 and operates the pressure regulator 14 described. The valve plate 17 has a vent 27 and is attached to the piston 28. The upper chamber 29 is restricted by this piston 28 and the chamber 30 connected via a side line 16 to the main control member 12. A second chamber 31 between the upper piston 28 and the valve plate 17 and a chamber 32 below the small piston 22 are connected via a side line 15 to a pressure limiter 10. Finally, the middle chamber 33, which is a large piston and a small piston between the piston 21 and 22, is connected to the opening 34 through the atmosphere.

The operation of the described pressure regulator is as follows. The pressure regulator 10 ensured that the compressed air taken from the supply line 11 always had as constant a value as possible, e.g. 5 bar. The second chamber 31 and the lower chamber 32 thus always have a constant pressure of 5 bar.

3 63694 With a fully released brake, there is also a maximum permissible pressure of 5 bar in the main air line 13. In order to achieve this pressure, the main control member 12 must be able to direct this pressure to the main air line 13. Therefore, the side line 16, the upper chamber 29 and the first chamber 30 must also have this pressure of 5 bar. Thus, the same pressure prevails in the first chamber 30 above the large piston 21 and in the lower chamber 32 below the small piston 22. In order to prevent compressed air from escaping from the first chamber 30 from the opening 27 of the valve plate 17 to the atmosphere in these pressure ratios, the spring 23 must be prestressed correspondingly strongly. This prestressing is achieved by turning the cam disc 25 to the release position by means of the control lever 35. Respectively, the difference between the two pistons 21 and 22 can be dimensioned relatively small.

For braking, the pressure in the main air line 12 must be reduced. According to the desired degree of braking, the control brake lever 35 is turned and the spring 23 is released. Thus, the force acting by the small piston 22 is reduced and both pistons 21, 22 decrease. Air can escape from the chamber 30 through the opening 27 into the atmosphere. The pressure in the chamber 30 therefore decreases until the forces acting on the step pistons 21, 22 from above and below are again in balance. Correspondingly, the pressure in the main air line 13 also decreases.

In order to release the brake, the pressure in the main air line 13 must be increased. According to the desired degree of release, the control brake lever 35 is turned and the spring 23 is thus released. The valve plate 17 is lifted from its seat 18 and compressed air flows from the second chamber 31 to the first chamber 30. The pressure in the chamber 30 thus increases until the forces acting on the step pistons 21, 22 from above and below are again in balance. Correspondingly, the pressure in the main air line 13 also increases.

In the model example according to Fig. 2, the compression spring 23 has been replaced by a tension spring 36, accordingly the arm 37 attached to the tension spring 36 rests on the underside of the cam disc 25. Thus, the tensile stress of the spring 36 can be varied exactly as the pressure of the compression spring 23 and thus the pressure in the main air line 13 can be controlled. However, in the indicated magnitude of the pistons 21 and 22, pressure uniformity in chambers 30 and 32 cannot always be achieved. in the chamber 30.

Claims (2)

4 6 36 9 4 A pressure regulator for a control brake valve for an indirectly acting compressed air brake, provided with a pressure control valve (17, 18, 19) connected to a supply line (11), operated by a step piston (21, 22) delimiting two chambers (30, 32) and loaded by an adjustable spring (23, 36) and on the other hand a control pressure, characterized in that in the second chamber (32) the step piston (21, 22) is loaded in addition to the spring pressure by an air pressure which is kept constant by a pressure limiter (10) connected to the supply line (11). Pressure regulator according to Claim 1, characterized in that the spring is formed as a tension spring (36). Il