阅读说明：本技术 阀 (Valve with a valve body ) 是由 R·博南诺 于 2018-12-13 设计创作，主要内容包括：本发明涉及一种阀,包括：壳体；布置在壳体中的螺线管；可由螺线管移动的杆；与杆连接的罐形的活塞；布置在活塞的底部区域中的、与阀座共同起作用的密封结构；以及布置在活塞的开口端的区域中的密封部件,该密封部件使活塞相对于壳体密封。与阀座(11)共同起作用的密封结构(10)具有外径,该外径大致相当于在活塞(8)的开口端处的密封部件(13)的外径。(The invention relates to a valve comprising: a housing; a solenoid disposed in the housing; a rod movable by a solenoid; a pot-shaped piston connected to the rod; a sealing structure arranged in the bottom region of the piston and cooperating with the valve seat; and a sealing member arranged in the region of the open end of the piston, which sealing member seals the piston with respect to the housing. The sealing structure (10) which interacts with the valve seat (11) has an outer diameter which corresponds approximately to the outer diameter of the sealing part (13) at the open end of the piston (8).)

1. A valve, comprising: a housing; a solenoid disposed in the housing; a rod movable by a solenoid; a pot-shaped piston connected to the rod; a sealing structure arranged in the bottom region of the piston and cooperating with the valve seat; and a sealing member arranged in the region of the open end of the piston, which sealing member seals the piston with respect to the housing,

it is characterized in that the preparation method is characterized in that,

the sealing structure (10) co-acting with the valve seat (11) has an outer diameter which substantially corresponds to the outer diameter of the sealing member (13) at the open end of the piston (8).

2. A valve according to claim 1, characterized in that the two outer diameters of the sealing structure and the sealing member (10, 13) differ by a maximum of 5%.

3. A valve according to claim 1 or 2, wherein the sealing structure and the sealing member (10, 13) are made of rubber, preferably viton.

4. Valve according to at least one of the preceding claims, characterized in that the rubber for both the sealing structure and the sealing member (10, 13) is vulcanized.

5. Valve according to at least one of the preceding claims, characterized in that the sealing part (13) at the open end of the piston (8) has a base body (15) to which a circumferentially encircling sealing lip (14) is connected which faces the piston bottom.

6. A valve according to claim 5, characterized in that the piston (8) has a circumferentially encircling protrusion (16) in the region of the base body (15) of the sealing part (13).

7. Valve according to at least one of the preceding claims, characterized in that a metal disc (17) is connected to the piston (8) in the bottom region thereof, a sealing structure (10) co-acting with the valve seat (11) being arranged at least on the outer circumferential part of the disc (17).

8. Valve according to at least one of the preceding claims, characterized in that the radially outer edge (18) of the disk (17) is oriented in the direction of the valve seat (11).

9. Valve according to at least one of the preceding claims, characterized in that the metal disc (17) is welded or brazed to the piston (8).

10. Valve according to at least one of claims 1 to 8, characterized in that the metal disk (17) is connected to the piston (8) by means of a snap-on connection or a press connection.

11. Valve according to at least one of the preceding claims, wherein the sealing structure (10) extends radially inwards from a radially outer edge (18) of the disc (17) to seal the sealing structure (10) between the disc (17) and the piston (8).

Technical Field

The invention relates to a valve comprising: a housing; a solenoid disposed in the housing; a rod movable by a solenoid; a pot-shaped piston connected to the rod; a sealing structure/seal arranged in the bottom region of the piston, which sealing structure/seal interacts with the valve seat; and a sealing member/seal arranged in the region of the open end of the piston, which sealing member seals the piston with respect to the housing.

Background

Such valves are primarily used as air-switching valves in turbochargers in motor vehicles in order to open a bypass to the intake side during freewheeling and are therefore known. In order to prevent too violent braking of the turbocharger, but also to ensure rapid starting, rapid opening and closing of the valves is an important prerequisite. Particularly when closing, it is important that immediate closing is achieved by the piston being placed on the valve seat. The valve seat is formed by the housing of the turbocharger to which the valve is flanged. Furthermore, the axially movable piston must be sealed with respect to the housing. For this purpose, it is known to provide the piston with a seal, wherein the seal covers the entire outer side, so that the seal assumes two sealing tasks. At the open end of the piston, the seal has a relatively large sealing lip. Such a dimensioning of the sealing lip is necessary, since the piston moves relative to the valve when the valve is opened and closed, and sealing must be ensured not only in the stationary state but also during the movement of the piston. The diameter of the seal at the open end is therefore greater than in the bottom region of the piston, whereby the projected areas are not equal. This results in the additional presence of a resultant force acting in the closing direction, which force holds the piston in the closed position. A disadvantage is that the solenoid must generate a correspondingly large magnetic force when opening the valve in order to additionally counteract the resultant force. Such valves therefore require large solenoids, which must be supplied with a corresponding current.

Disclosure of Invention

It is therefore an object of the present invention to provide a valve which requires a low current consumption when opening and closing.

This object is achieved in that the outer diameter of the sealing structure co-operating with the valve seat corresponds substantially to the outer diameter of the sealing part at the open end of the piston. With this embodiment according to the invention, it is achieved that the projected areas of the two sealing structures/components are almost identical. Thus, when the piston is pressurized, a resultant force of almost zero or a small difference from zero is generated. The non-zero force is so small that it is negligible for the design of the solenoid, in particular the coil and the power. The advantage is that the coil can thereby be dimensioned smaller. The valve according to the invention therefore requires less installation space and has a significantly reduced weight. The resulting lower power results in a reduced load on the vehicle electrical system and in less fuel consumption.

If the two outer diameters of the seal are exactly the same, the total force is equal to zero. However, a prerequisite for this is a high level of demands in manufacturing, in order to keep the tolerances determined by the manufacturing conditions correspondingly small. Such high and therefore cost-intensive manufacturing expenditure can be avoided if, according to an advantageous embodiment, the two outer diameters differ slightly in size, preferably by a maximum of 5% and in particular by a maximum of 3%. The resultant force generated thereby is negligible in terms of the magnetic force of the solenoid.

In this case, it has also proved to be advantageous if the outer diameter of the sealing structure in the base region is smaller than the outer diameter of the sealing part at the open end. Since the sealing lip of the sealing part at the opening of the piston in the installed state rests against the housing of the valve, the outer diameter of the sealing lip is already reduced in the installed position and thus approaches the outer diameter of the sealing structure in the bottom region of the piston as a result of the installation.

Good medium resistance of the seal is obtained by using rubber, preferably fluororubber, as sealing material. Another advantage is that such rubber seals have a heat resistance of up to 180 ℃.

When the rubber for both seals is vulcanized, a reliable connection of the seals to the base material is advantageously achieved.

In a further embodiment, the sealing element with high long-term stability at the open end of the piston is realized in that the sealing element has a base body, on which a circumferentially encircling sealing lip is connected in the direction of the piston base. The base body forms a good base for the connection of the sealing lip, which ensures a functional function over the service life of the valve.

In order to achieve an improved and long-term stable connection of the sealing part to the piston, in a further advantageous embodiment the piston has a circumferentially encircling projection at the open end in the region of the base body of the sealing part.

The sealing structure interacting with the valve seat advantageously has a sealing lip. Since the sealing lip is in contact with the other component only in the closed state, the sealing lip may be deformed by the pressure ratio during the movement of the piston, which results in a new resultant force. This ratio can be avoided according to a particularly advantageous embodiment in that the metal disk is connected to the piston in the region of the bottom of the piston, and the sealing means which interacts with the valve seat is arranged at least on the outer circumference of the disk. The advantage of the metal disc is that the shape stability of the sealing structure is significantly improved.

If the sealing structure has almost the same layer thickness at every position of the disk, deformation of the sealing structure due to pressure changes can be reliably avoided here.

In order to reliably seal the sealing structure against the valve seat, it has proven to be advantageous if the radially outer edge of the disk is oriented in the direction of the valve seat.

In a further embodiment, the metal disk can be connected to the piston particularly simply and reliably if it is welded or soldered to the piston.

In a further advantageous embodiment, the secure connection of the metal disk to the piston is achieved in that the metal disk is connected to the piston by means of a snap-fit connection and a plug connection or a press connection. In a further embodiment, the press connection can also be realized in that the disk and the piston are pressed against one another by means of a metal rod.

Both the bottom area of the piston and the disk have notches which enable pressure equalization between the interior of the valve and the pipe. It has proven advantageous here to seal the disk against the piston. This is achieved in a simple manner in that the sealing structure extends radially inwards from the radially outer edge of the disc to such an extent that the sealing structure seals between the disc and the piston. In addition, the disadvantage of relative movement between the piston and the disk is reliably avoided by this design.

If the piston is made of stainless steel, preferably chrome-nickel steel, greater resistance to aggressive media and thus a longer service life is obtained, and furthermore, the metal piston has the advantage of a higher temperature resistance, so that the valve according to the invention can cover a wider field of application, in particular with higher temperatures.

Due to the higher stability of metal in relation to plastic, the wall thickness of the piston can be made significantly smaller. Depending on the field of application, it has proven advantageous for the metal of the piston to have a thickness of 0.3mm to 1mm, preferably 0.4mm to 0.8mm and in particular 0.5 mm.

According to a further advantageous embodiment, the piston can be produced in a particularly cost-effective manner in one working step if the piston and/or the disk are deep-drawn parts.

Drawings

The present invention is described in detail in one embodiment. Shown in the drawings

Fig. 1 shows a cross-sectional view of a valve according to the prior art, an

Fig. 2 shows an enlarged cross-sectional view of the piston of the valve according to the invention.

Detailed Description

Fig. 1 shows a valve comprising a housing 1. Furthermore, the housing 1 has an integrally formed flange 3, by means of which the housing 1 is flanged to a turbocharger, not shown, in the region of a bypass line 4. In the housing 1 a solenoid 5 with a coil 6 and a metal rod 7 is arranged. The metal rod 7 is connected to a pot-shaped piston 8 which has a sealing structure 10 on the periphery of its bottom 9. In the closed position shown, the sealing structure 10 bears against the valve seat 11 in order to close the bypass duct 4, so that no medium can flow from the duct 4 into the duct 12. Here, the spring 7a urges the piston 8 toward the valve seat 11. At the open end of the piston 8, a further sealing part 13 with a sealing lip 14 is arranged. If the solenoid 5 is energized, a magnetic force acts on the armature 2, thereby moving the piston 8 in the direction of the housing 1. The sealing lip 14 seals the piston 8 in this case against the housing 1.

The piston 8 according to the invention in fig. 2 likewise has a sealing part 13 at the open end of the piston 8 and a sealing structure 10 in the bottom region of the piston 8. The sealing part 13 comprises a base body 15 from which a sealing lip 14 extends in the direction of the piston bottom. In order to improve the connection between the sealing part 13 and the piston 8, the latter has a circumferential projection 16 in the region of the base body 15.

In the region of the base of the piston 8, the latter is welded to a stamped part in the form of a metal disk 17, wherein the welded connection is arranged centrally in the base. The radially outer edge 18 of the disk 17 is oriented in the direction of the valve seat. The seal 10 is vulcanized to the radially outer edge 18. The sealing structure extends radially inwardly from the radially outer edge 18 to such an extent that it seals the disc 17 against the piston 8. Viewed radially, this seal is realized in the region of the cylindrical wall of the pot-shaped piston 8. The sealing structure 10 has in this case almost the same layer thickness at each location of the disk 17. The outer diameter of the sealing structure 10 is here only slightly smaller than the outer diameter of the sealing part 13.