JPH0377646B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The invention provides that a spring/mass/system can be held by an electromagnet in each end position of maximum deviation of vibration, so that at least two discontinuous switching positions occur; The present invention relates to an electromagnetic actuation regulating device in which the residence time in can be controlled by an arbitrary excitation time of the electromagnet.

This type of regulating device is designed because the actuated control member, such as a valve located in a position, and the actuating mechanism, such as an armature on an electromagnet, do not share the switching position in which they perform their functions. Extremely precise adjustments must be made to avoid manufacturing tolerances, thermal expansion, wear, etc., which may lead to functional defects.

Regarding the prior art Patent of the Federal Republic of Germany (DE-PS) in this connection
Specification No. 2335150 contains the following statement.
That is, a play is provided within the transmission member between the actuating mechanism and the valve, so that for the closing device the electromagnet contacts the electromagnet and at the same time the valve rests in that position. Armature strikes on the electromagnet are damped by a disc spring that is compressed towards the end of each stroke.
Federal Republic of Germany Application Publication (DE-OS) No.
The following proposal is described in the specification of No. 3024109. The elastic connection between the valve stem and the armature therefore provides the necessary length balancing and at the same time provides a certain damping of the armature's impacts on the electromagnet.

Large mechanical stresses, noise generation, and
In order to prevent collisions, components are applied which, in conjunction with electromagnets, provide pneumatic damping of all or a small part of the movement process by modifying the enclosed gas volume. In this case, special additional components are usually used. These components do not directly belong to the electromagnet.

In order to fulfill their role, these components are connected directly or indirectly to the corresponding components of the electromagnet, so that these components direct the relative movement of the components of the electromagnet to each other in the desired manner of the movement process. It can be attenuated within a range. Patent No. 1055091
In this issue, an additional attenuator is attached to the electromagnet.
In this case, the role of damping is taken care of by the bellows, which are tightly connected to the armature. This bellows is compressed at the end of the movement process by the contact of the stopper, so that the enclosed air is compressed and flows out through one opening.
The planned damping therefore takes place towards the end of the movement process.

This method of damping additional components involves the expense of the damper and the transmission elements necessary for movement and stopping of the associated parts.

Fundamental Problem of the Invention The basic problem of the invention is to provide a damped contact of the armature on the magnet and at the same time a damped positioning of the moved control member in one or several switching positions. The goal is to accurately position each position. In addition, the aim is to reduce construction costs, space occupancy and the number of moving parts by automatically making a precise adjustment of the regulator with respect to the final position of the moving parts.

This problem is solved by the following features of the present invention. That is, a gas volume is enclosed between the armature and the electromagnet, in which case the closed space is closed immediately before the switching position is reached by an elastic element or by a fixed wall with a negligible gap between the moving part and the fixed part. Formed into a grin. The enclosed gas volume can escape through a corresponding gap between the moving and stationary parts when using fixed walls to limit the gas volume in the jacket area. If an elastic member is used to limit the gas capacity in the jacket area, an outlet is required in the armature, magnet or elastic sealing element. The compressed gas volume flowing out from the outlet reaches the switching position damped by the armature on the electromagnet due to the energy conversion. This damping movement of the armature is transmitted to the valve by a frictionless, frictionless connection between the armature and the valve. By using adapted components, the approach of the valve to the valve seat proceeds in much the same way as the approach of the armature to the electromagnet. In that case, those components either provide the required positioning according to the invention of one or two electromagnets relative to the valve seat or, if the electromagnets are fixed, the positioning of the armature relative to the valve head is determined by a corresponding structure. This averages out manufacturing tolerances, thermal expansion, and wear and tear.

ADVANTAGES OF THE INVENTION Some of the advantages achieved by the invention are, in particular: This means that all moving parts of the adjusting device reach their switching position damped, so that noise generation is largely prevented and mechanical stresses are significantly reduced. Yet another advantage lies in the following points.
This means that the damping function can be implemented within the structural space in the electromagnet, and at the same time the structural outlay for the damping function can be reduced. Furthermore, no fine adjustment of the adjusting device is necessary either during assembly or during storage. The length balance of the adjusting member or device that moves during operation is automatically compensated for by thermal expansion.

EXAMPLES The figures showing some examples will be described in more detail.

For example, in Figure 1, electromagnets 1 and 2 and their coil 3
4 and coil covers 5 and 6. The electromagnet 2 is fixedly connected to the casing 7, while the electromagnet 2 is guided in the casing 7 in common with a pneumatic biasing device consisting of a cylinder 8 and a piston 9, and the stop 1
Axial movement between 0 and 11 is possible.
The valve 12 is guided in a valve guide 13 which is fixedly connected to the housing 7 . The spring 14 is conventionally connected to the valve 12 via a spring plate 15 and a valve cone 16. The armature 17 is guided by a guide 18 and is in frictional engagement with the rod end of the valve 12 via a central plate 20 by means of a spring 19 which is supported on the piston 9 of the biasing device. The positioning of the electromagnet 1 is determined by a length balancing member 21 acting on two sides together with a biasing device. Length balancing member 21
is fixedly connected to the casing by a screw 22, while the flange 23 of the vertically movable piston 24 is fixed to the electromagnet 1 via a threaded sleeve 25 and a cylinder 28, so that changes in the length of the adjusting member are prevented. is transmitted to the length balancing member. The non-frictionally engaging integration of the length-balancing member allows the transmission of both pressure and tensile forces.

FIG. 2 shows an electromagnetically actuated adjustment device with a unilaterally acting length balancing member 26 for positioning the electromagnet 1. FIG. The length balancing member 26 is inserted into a cylindrical recess in the cylinder 8 of the biasing device and is held by a cover 27. Frictional integration only allows the transmission of pressure.

FIG. 3 shows an electromagnetically actuated adjustment device having a bilateral acting length balancing member 28. FIG. The length balancing element 28 is fixedly screwed to the valve 12. The flange 24 of the length balancing member 28 is fixed by a cap nut 29 on the guide sleeve 30 with the armature 17 so as to be slidable relative to the valve.

FIG. 4 shows an electromagnetically actuated adjustment device having a single-sided acting length balancing member 28. FIG. The length balancing member is cover 3
1 to the guide sleeve 30 and the valve 12, so that only pressure is transmitted.

FIG. 5 shows a single-sided acting length balancing member. The hydraulic length balancing member composed of the cylinder component 32 and the piston component 33 is connected in an air-tight and liquid-tight manner by the bellows 34 between the cylinder component 32 and the piston component 33, so that fluid No substances can come out, and no harmful substances can enter. The relative sliding sleeves 35 of the piston component 33 and the cylinder component 32 are at the same time guide surfaces and sealing surfaces. Leak liquid chamber 37 and fluid storage chamber 38
The sealing of the pressure chamber 36 against the piston is achieved by a thin-walled extension 39 of the lower edge of the piston. Leakage fluid may flow back into the fluid reservoir 38 through the opening 40 in the piston wall. In the liquid storage chamber there is a pressure reservoir and a gas-filled bellows 41 as a volume balancing element, which gas-filled bellows is fixed to the top and bottom of the piston. The piston bottom 42 consists of a rotating part for accommodating an outflow hole 43 and a spring-loaded check valve 44. A spring 46, which closes the hole 47 with a ball 48, is supported by a spring 45, which is centered on the piston bottom and held in frictional engagement with the piston bottom by a spring 49. The upper end face 50 of the cylinder serves as an end stop for the maximum possible swaging of the length balancer. Piston component part 33
has an annular groove 51 above the thin-walled extension 39. The annular groove communicates with the leakage chamber 37 via the joint 52 .

FIG. 6 shows a length balancing member for two sides.

The length balancing member consists of a double-acting piston 4 and two cylinder components 53 and 54.
The cylinder components are firmly connected to each other via spacers 55. Since the piston 24 is air-tightly and liquid-tightly connected to the cylinder components 53 and 54 via the two bellows 56 and 57, no liquid leaks and no harmful substances enter.
The relatively sliding sleeve surfaces 58 and 59 are configured at the same time as guide surfaces and sealing surfaces. The piston bases 60 and 61 together with the cylinder components 53 and 54 enclose liquid volumes 62 and 63, which can flow into a liquid reservoir 66 through overflow holes 64 and 65. Sealing lips 67 and 68, which are constructed as thin-walled extensions of the piston sides, allow liquid to flow through sealing gaps 58 and 59 into leakage chambers 69 and 7.
This effect is assisted by annular grooves 71 and 72 which communicate with leakage chambers 69 and 70 via outflow grooves 73 and 74.

The unavoidable slight leakage flow flows back into the liquid storage chamber via backflow ports 75 and 76. The piston bottom 61 has a check valve 71 whose spring 78 is connected to the piston bottom by a spring 79 in a frictional engagement. A spring 80 in the liquid volume 62 is supported on the cylinder component 53 and on the piston base 60.

Figure 7 shows electromagnet 1, armature 17, and coil spring 1.
9 shows the part of the electromagnetically actuated adjustment device with the coil cover 5. The annular elements 82 and 83 are made of a non-magnetic, elastic material and are hermetically coupled to the electromagnet 1. Compressed gas may escape from the outlet 84, so that the armature 17 can be damped into contact.

FIG. 8 also shows a portion of a similar electromagnetic adjustment device. The space of the confined gas volume is not completely closed off, but a gap is formed, defined by the special configuration of the armature 17, the sleeve 85, the electromagnet 1 and the center plate 0, through which the compressed gas can escape. can.

9 and 10 show an alternative configuration of the piston bottom in enlarged size.

In the following, the function of the single- and double-acting length balance members will be described first, followed by a description of their use in electromagnetically actuated regulating devices.

When an external force is applied to the length balancing member shown in FIG. 5, the piston component 33 and the cylinder component 3
2, a strong pressure already develops in the fluid space 36 while the distance difference between the two is still small. This pressure forces the piston lower edge extension 39 against the cylinder wall, so that the fluid space 36 is almost sealed at the sealing surface 35.

Even if a sudden load change occurs through the annular groove 51 and the connecting groove 52, the pressure liquid between the guide surfaces can be quickly carried away, so the pressure difference required to press the extension part 39 is naturally reduced. Set. Check valve 44
2, and only a small amount of pressure liquid can flow out of the pressure chamber 36 into the liquid storage chamber 38 via the outflow hole 43, so that only a small displacement is possible when a force is applied.

A small leakage flow, which cannot be completely avoided, enters the reservoir chamber 38 through the hole 40. The size of the storage chamber is
The entire liquid expelled from the pressure chamber 36 is transferred to the bellows 4.
1 can be accommodated by corresponding compression. When the load is removed from the length balancing member, spring 49 averages out the difference in length by pulling piston 33 out of cylinder 32 until an applied external force causes force equilibrium. The check valve 44, which has just begun to open, and the slight overpressure in the liquid reservoir 38 serve for a rapid exchange of liquid and thus also for a rapid occupation of the new position determined by the force balance. . The maximum deviation of the length balanced member is bellows 34
The focus is on maximizing the possible extension of Torque introduced from the outside is absorbed by the bellows 34. In order to keep this stress to a small level,
At least one end face 53 is formed so that the various acting forces do not result in large torques.

The operating mode of the length adjusting member shown in FIG. 6 depends on the direction of the external force acting on it. When an external force applied to the piston 24 is introduced in the direction of the cylinder component 54 via the flange 23, a high pressure is already generated in the pressure chamber 63 while the stroke difference between the piston 24 and the cylinder component 54 is small. This high pressure then presses the extension 68 against the cylinder wall, so that the pressure chamber 63 is almost sealed along the sealing surface 59. Since the check valve 77 also prevents the liquid from flowing into the liquid storage chamber 66 depending on the pressure in the pressure chamber 63 at that time, the liquid can escape from the pressure chamber 63 only through the overflow port 64. As a result, the descent of the piston 24 into the cylinder component 54 is caused by the overflow hole 6
4 corresponding configurations. The sealing action of the extension 68 is strengthened by the annular groove 72, and at the same time the liquid present in the sealing gap 59 is quickly carried away from the outflow groove 74, so that the sealing action of the extension has a sudden change in load. Sometimes it adjusts naturally. The unavoidable leakage flow flows back into the liquid storage chamber 66 through the backflow port 76. piston 24
The liquid leaving the storage chamber 66 during its movement in the direction of the cylinder component 54 can flow into the pressure chamber 62 through the overflow opening 65 . A gas-filled bellows 81 is provided in the reservoir to equalize changes in pressure and volume. When a force is applied to the balance member as described above, the stroke changes slightly depending on the external force applied and time.

When the force action is reversed, the piston enters the cylinder component 53 and the overflow hole 65 in the piston bottom 60 serves to quickly drain the liquid from the pressure chamber 62 into the reservoir chamber 66, so that the pressure chamber The pressure inside 62 increases very slightly. However, this pressure is strong enough to achieve sealing of the sealing gap, so that the lowering of the piston can be controlled by the outlet. A check valve 77 in the piston bottom 61 opens and serves for liquid exchange between the reservoir chamber 66 and the pressure chamber 63. When the balancing element is loaded in this way, the travel changes that occur as a result of the external forces and time are relatively large.

FIG. 1 shows an electromagnetically actuated adjustment device having a two-sided length balancing member 21. FIG. The member 21 positions the electromagnet 1 during operation as follows. That is, the position is such that the change in length that occurs between the magnetic pole surface of the armature 17 and the valve plate of the valve 12 corresponds to the distance between the magnetic pole surface of the electromagnet 1 and the valve seat. For this purpose, the member 21 is assembled so that the pressure chamber 63 is located at the top in FIG.

The force of spring 19, which is greater than that of spring 79 during the time the electromagnet is blocked, has the following effect.
That is, the electromagnet 1 is connected to the casing 7 together with the bias device.
The liquid slides upward against the pressure chamber 63.
It exits from the tank and is metered out through the overflow hole 64.
Upon reconnection of the electromagnet 1 and approach of the armature 17, the force of the electromagnet overcomes the force of the spring 19, and the electromagnetic force 1 is drawn together with the biasing device until it contacts the armature 17, at which point the valve 12 is moved by the force of the spring 14. It is held in its own position by elasticity. The downward movement of the electromagnet 1, carried out together with the biasing device, causes the check valve 7 to now open.
7 and an overflow hole 65 of a favorable shape for flow, and is supported by the force of spring 79, which is greater than spring 80. The desired time course of the positioning process can be set by the corresponding arrangement of check valve 77, overflow holes 64 and 65, and springs 79 and 80.

FIG. 2 shows a corresponding electromagnetically actuated adjustment device with a one-sided balancing member 26. FIG. The member 26 is a pressure chamber 36
It is installed so that it is located at the top of Fig. 2. When the electromagnet 1 is cut off, the piston component 33
Corresponding to the liquid flowing out from the pressure chamber 36 via the overflow hole 43, the liquid falls into the cylinder component due to the force of the spring 19, which is greater than the force of the spring 49. As a result, the electromagnet 1 slides upwards together with the biasing device. When the electromagnet is reconnected, no force is transmitted from the balance member to the electromagnet. Due to the spring 49, the length differences are quickly averaged out. This is because the check valve opens, and as a result, liquid from the storage chamber 38 rapidly flows into the pressure chamber 36.

FIG. 3 shows an electromagnetically actuated adjustment device with a length balancing member 28 acting on two sides. The member 28 is the first
In contrast to the adjusting device shown in FIGS. and 2, the spacing between the pole face of the armature and the valve plate is adapted to the spacing between the pole face of the electromagnet and the valve seat. The length balancing member is installed so that the pressure chamber 63 is located at the bottom in FIG.

When the electromagnet 1 is switched off and the electromagnet 2 is connected, the valve 12 and the length balance member 28 are accelerated by the spring 19, and the "open valve" is brought into the connected position and held there, while at the same time the electrical The child 17 is kept in the open position by the electromagnet 2, so that the position of the piston 24 with respect to the electromagnet 2 is fixed. Part 2
The inertial force of the valve and the elasticity of the spring 14 resist the acceleration force of the spring 19 acting on the valve via the valve. Since the check valve 77 is stopped, a very small amount of oil flows from the pressure chamber 63 into the liquid storage chamber 66 through the outflow hole 64, so that the relative movement between the armature 17 and the valve 12 is very small. so that the valve opens in the desired manner. The armature 17 is damped in the manner shown in FIGS. 7 or 8 until it reaches the stop of the electromagnet 2, in which case the very slight resistance of the flowing oil to the inertia of the valve is Since it is only counteracted via the non-stop check valve 77, the movement of the valve 12 exceeds the maximum stroke that would occur with a rigid connection of the armature 17 and the valve 12. During the time that the armature is held by the electromagnet 2, the tensioned spring 14 acts on the balance member 28 via the spring plate 15, the valve cone 16 and the valve 12, so that the now stopped non-return check In the case of the valve 77, a very small amount of oil leaves the pressure chamber 63 and flows into the storage chamber 66 through the backflow hole 64.
This causes the spring 14 to bring the valve back close to the position of strong armature-valve coupling. When the electromagnet 2 is now switched off and the electromagnet 1 is connected, the valve is brought by the spring 14 together with the member 28 into the position shown in FIG. 3 and held by the electromagnet 1.

Due to the corresponding design of the overflow hole 64, both the valve 12 and the armature 17 are damped almost simultaneously in that position and come into contact with the electromagnet 1. In the illustrated connection position, the force flow between the electromagnet 1 and the spring 19 is confined via the armature 17, the central sleeve 20 and the piston 9. In that case, the overflow hole 6
The armature is drawn in by the flow-enhancing arrangement 5 and the check valve 77. The frictional connection between the armature 17 and the guide sleeve 30 is achieved by the elastic force of a spring 79 which is stronger than the spring 80, the spring 79 being supported on the valve 12 and the valve 12 being supported by the spring 7.
9 is held in position by the force of a strong spring 14. In this way changes in the axial length of the valve that occur during operation are compensated for.

FIG. 4 shows an electromagnetically actuated adjustment device with a single-sided acting length balancing member 29. FIG. Member 29 has the same role as length balancing member 28 shown in FIG. The member 28 is assembled so that the pressure chamber 36 is at the bottom in FIG.

The opening process proceeds as described above for member 28. Changes in length during operation of the adjustment device resulting in an extension of the member 29 cannot be prevented or influenced. This is because no tensile force can be transmitted from the member 29. This length difference is averaged out inside member 29 by spring 49.

7 and 8 show an embodiment of a shock damper for an electromagnetic adjustment device.

The armature 17 is undisturbed and first faces the electromagnet 1, the elastic rings 82 and 83 contacting the armature,
As a result, the magnetic pole face of the armature 17, the magnetic pole face of the electromagnet 1, and the coil cover 5 move until they form one space that seals the gas. At the point of contact, this movement process is influenced by the compression of the gas enclosed, so that the armature 17 rests damped on the electromagnet 1. The sealing ring then performs an essentially sealing but dampening function.

In the example shown in FIG. 8, the armature 17 approaches the electromagnet 1 due to the special formation of the armature 17, the sleeve 85 and the center plate 20, without the buffering gas volume being completely enclosed. This is done in such a way that an extremely narrow gap is created. As the approach progresses, these gaps become more and more impeded to the escape of the compressed gas.

The above-mentioned shock damping for electromagnetically actuated regulators is possible in principle if all the electromagnets or one or several components moving perpendicularly towards the pole faces are activated by electromagnetic or other forces. In similar devices which can be carried or held in one or several positions, it is suitable for realizing a damped mounting of the moving component on the pole face.

When the length balancing member of FIGS. 5 and 6 is incorporated into the electromagnetically actuated adjustment device of FIGS. 3 and 4, the length balancing member is subjected to significant acceleration forces. To guarantee functional reliability for these applications, it may be necessary to have a special construction of the check valve.

FIGS. 9 and 10 show an enlarged view of the structure of the piston bottom used in that case.

The check valve of FIG. 9 consists of a ball 86 acted upon by a spring 87 pretensioned by a plug 88, the direction of movement of which is perpendicular to the line of action of the acceleration of the valve gap balancer. Therefore, an unexpected opening of the check valve can be prevented by a slight action of acceleration force on the ball.

FIG. 10 shows the acceleration neutral mode of the check valve. A check valve consisting of a ball 89 and a cylindrical stem 92, which is connected to a guide 90 via a cylindrical component 91, is loaded by a spring 93, which is supported on a plug 94, into a liquid reservoir 95. is closed to the pressure chamber 96. The components of the check valve are sized as follows: This means that during the acceleration of the valve gap balancer that occurs primarily, the mass moment of inertia of the stem 92 and that of the ball 89 and the component 91 in the direction perpendicular to the direction of movement of the check valve are of the same magnitude with respect to the guide 90; The valve seat is designed so that no reaction force is generated on the valve seat due to acceleration of the check valve. The same pressure level prevails in the valve chamber 97 via the connecting portion 98 as in the pressure chamber 96 at all times.

Note that embodiments of the present invention are listed below.

(1) According to claim 1 or 3, the hydraulic length balancing member having a pressure chamber is hermetically and liquid-tightly sealed and has a liquid storage chamber for filling the length balancing pressure chamber. The device described.

(2) The liquid storage chamber is provided in a hollow piston component of a piston-cylinder structure having a piston component and a cylinder component.
The device described in (1).

(3) The overlapping and sliding surfaces of the cylinder component and the piston component mutually guide the two parts, forming a single sealed space.
The device according to (2) above.

(4) The bottom of the piston component has a cylindrical thin extension, the outer diameter of the extension matches that of the piston component, and the extension is expanded under the working pressure of the pressure fluid in the pressure chamber. The device according to (2) or (3) above, which comes into fixed contact with the cylinder surface, thereby sealing the pressure chamber against a sealing gap.

(5) The device according to any one of (1) to (4) above, wherein a gas-filled pressure storage section is provided in the liquid storage chamber, and this storage section keeps the pressure in the liquid storage chamber almost constant. .

(6) The bellows used for airtight and liquid-tight closure of the piston, cylinder, and structure should be kept between the cylinder component and the piston component while keeping the length of the hydraulic balancing member within the permissible limit. The device according to any one of (2) to (5) above, having sufficient mechanical rigidity to avoid damage by torque.

(7) The device according to any one of (1) to (6) above, wherein the pressure chamber communicates with the liquid storage chamber via an outflow hole.

(8) The device according to any one of (1) to (7) above, which is configured such that the pressure liquid exiting the liquid storage chamber can rapidly flow into the pressure chamber via the check valve.

(9) The device according to any one of (1) to (8) above, which is configured such that the flow leaking from the sealing gap can flow back into the liquid storage chamber from the opening of the piston component.

(10) An annular groove connected to a liquid storage chamber is provided above the extension, so that even if the pressure difference necessary for pressing the cylindrical thin extension encounters a sudden load change, the liquid remains The device according to any one of (4) to (9) above, wherein the device is configured such that the pressure behind the extension portion is rapidly reduced by being rapidly discharged from the sealing gap.

(11) The end face of the cylinder component and/or the piston component is configured such that the bearing force is absorbed by the central bearing surface with a short outer diameter, as described in (2) above.
The device according to any one of (10) to (10).

(12) A check valve according to any one of (8) to (11) above, wherein a check valve is provided at the bottom of the piston component so that its movement direction does not coincide with the main acceleration direction of the length balancing member. Device.

(13) Since the check valve at the bottom of the piston component is acceleration-neutral, no force is generated on the sealing surface between the valve and the valve seat as a result of acceleration of the valve play/balance member. ) to (12).

(14) One or more electromagnetic components are
Claims (1) and (3), wherein at least the element of the pole face in the direction perpendicular to the direction of motion is formed in such a way that it is part of a space having an effective volume of the pneumatic damper. The device according to any one of 1) to (13).

(15) The plane of the damping capacity is formed by the parallel or nearly parallel surfaces of the components parallel to the direction of motion, so that the damping capacity is constant or non-uniform in parallel or nearly parallel in this range. The device according to any one of claims (1) to (4) and (1) to (14) above, wherein the space is formed by a surface having a string.

(16) Claims (1) to (4) and any one of (1) to (15) above, wherein the surface of the damping capacity parallel to the direction of motion is made of a rigid or elastic material. equipment.

(17) The sealing gap formed parallel to the direction of movement by the paired surfaces is configured to determine various shapes and dimensions of the cross section for the outflow of the sealed gas according to the stroke. , Claims (1)
-(4), the device according to any one of (1) to (16) above.

(18) Any of claims (1) to (4) and (1) to (17) above, in which the plane parallel to the direction of movement is configured so that a tight seal is achieved between the gas capacities. The device described in item 1 above.

(19) Claims (1) to (4), in which all components enclosing a gas volume are provided with a constant outlet;
The device according to any one of (1) to (18) above.

(20) As a constant outlet provided in a component passes close to another component during the course of the movement distance, some outlets may take on different shapes and dimensions depending on the travel. The device according to any one of claims (1) to (4) and (1) to (19) above, configured as follows.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment of the device according to the invention, FIGS. 2 to 4 are views showing separate embodiments shown in the same manner as FIG. 1, and FIGS. 5 and 6. 7 and 8 are partial views of a preferred embodiment of the electromagnetic adjustment device according to the present invention, respectively,
9 and 10 are detailed views of another preferred construction of a length balancing member according to the invention. Symbols in the figure: 1, 2...electromagnet, 7...casing, 17...armature, 21, 26, 28...length balancing member.

Claims (1)

Claims: 1. For a piston machine with an oscillatory spring-mass system, which is held in each final position with maximum vibrational deviation by an electromagnet, resulting in at least two discontinuous switching positions. In the device for an electromagnetically actuated regulator, the armature and the electromagnet are constructed as part of a damping device, one or both electromagnets being connected to the casing by a hydraulically actuating length equalizer, and in which the valve seat and The spacing between the pole faces of the electromagnet is adapted to the spacing between the valve head and the pole faces of the armature, such that the approach of the armature to the electromagnet and the approach of the valve to the valve seat are damped in the same manner. A device configured to perform 2. The device for an electromagnetically actuated regulator as claimed in claim 1, wherein the opposing relatively moving parts of the electromagnet are configured such that a gas volume is enclosed throughout the whole or part of the travel distance. 3. Device for an electromagnetically actuated regulator for a piston machine with an oscillatory spring-mass system, which is held in each final position with maximum vibration deviation by an electromagnet, resulting in at least two discontinuous switching positions. in which the armature and electromagnet are configured as part of a shock absorber, the armature being connected to the valve by a hydraulically actuated length equalizing member, and the spacing between the valve head and the pole face of the armature being is adapted to the spacing between the valve seat and the magnetic pole face of the electromagnet so that the approach of the armature to the electromagnet and the approach of the valve to the valve seat are carried out in the same buffered manner. Device. 4. The device for an electromagnetically actuated regulator as claimed in claim 3, wherein the opposing relatively moving parts of the electromagnet are configured such that a gas volume is enclosed throughout the entire or part of the travel distance.