JPS6039913B2 - Solenoid valve device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to an electromagnetic valve device for controlling the flow rate of pressure medium through a valve device, in which a stationary sleeve surrounded by an excitation coil is It relates to a type having an associated axially movable plunger, which plunger is centered by two ball bearings.

BACKGROUND OF THE INVENTION A valve arrangement of the type mentioned above is known from DE 240 377 A1.

In such known valve devices, the plunger is movably guided in a sleeve. The magnet can be excited in two stages. In this case, there are three stable positions of the valve closing member in the valve arrangement and thus three different directional control combinations. In other words, it is formed as a three-boat, three-position, directional control electromagnetic type. If the magnet is not excited,
, the force of the spring places the plunger in a stable end position, in which the working machine is connected to the pump and the return path is closed.

In the passageway, through which approximately half of the current flows, the closing member occupies a more stable position, in which all connections are interrupted. In a fully energized pump with full rated current, the plunger assumes another end position, the pump is switched off, and the work machine is connected to the return path. The switching dead time from a fully energized state to a half energized state is extremely important for the functionality of the valve. This time must be extremely short. Since the predetermined magnetic force remains when switching back from the fully energized state to the half-energized state, the spring force is reduced by the difference between it and the magnetic force, so that the force for returning the plunger becomes extremely small. Furthermore, since the rear pole is designed as a plunger, the friction between the plunger and the valve housing has a further negative effect on the movement of the plunger. OBJECT OF THE INVENTION The object of the invention is to eliminate the disadvantages of known valve arrangements.

Means for Solving the Problem The means taken to solve the above problem is that each ball bearing has a group of balls arranged on a circle, and these balls are placed in one cage. and that each retainer is tightly clamped in the valve arrangement leaving an axial gap for the ball at the size of the plunger stroke.

Effects of the Invention The advantage obtained by the invention is that, because the plunger is supported by a ball bearing according to the invention, there is little friction in the direction due to the rolling contact, so that the magnet can be halved from the fully energized state. This means that there is less wasted time for switching the rod back to the excited state.

Furthermore, the manufacture of such a valve arrangement is simple and inexpensive, since the valve seat, which is necessary in any case in the valve, and the pipe projection at the same time form the support for the bearing. The ball bearing according to the invention has a free-flow cross section which does not impede the flow of the pressure medium. Furthermore, the frictionless ball bearing according to the invention provides rapid switching of the plunger;
It can also be used advantageously for pressure regulation in electromagnetically operated anti-skid devices.

The invention will be explained below with reference to the exemplary embodiments shown.

An electromagnetic three-way control device 1 is arranged between a pressure receiver 2 and a pressure source 3 and a relief point 4 . A coil 5 is mounted on a coil support 6, which is placed on a guide tube 7, which has a non-metallic member 8. Two receptacles 9, 10 are fastened to the guide tube 7, each of which supports a tube piece 9' or 10'. Tube piece 1 towards pressure source 3
0' has an inlet valve seat 11, and the tube piece 9' leading to the relief point has an outlet valve seat 12. Both tube pieces 9
', 10' protrude over a relatively large area into a plunger 13 movable within the guide tube 7, which plunger is supported by an eccentrically arranged main spring 14 across the receiving part. . A smoothing ring 16 is located on the shoulder 15 of the receiving part 10, with which the plunger stroke is reduced in the end travel range and which prevents the plunger from sticking. The plunger 13 is provided with a recess 17, which leaves a shoulder 17' on the side facing the inlet, into which two ring-shaped elements 18, 19 are inserted.

The spacing between the ring-shaped members 18 and 19 is determined by the sleeve 20 and the plurality of rings. In the gap 21 between the rings and on the shoulder 22 formed by the rings,
2 each supporting one closure member 27 or 28
Two holding members 25 and 26 are located. Tension spring 2
9 via the holding members 25, 26 and also the closing member 27.
, 28 are pressed outward. The closure village 27 together with the valve seat 11 forms the inlet valve 11/27, and the closure village 28 together with the valve seat 12 represents the outlet valve 12/28. Tube pieces 9', 10 supporting each valve seat 11 or 12
' has a pivot member pressed against the inner race of the ball bearings 30,31. Each ball bearing inner race is made of hardened material and is non-magnetic. The balls of each ball bearing 30, 31 are arranged between a bearing inner race and a ring-like element 18, 19, which also has a hardened surface which serves as a running surface for the ball. The spheres are formed as simple continuous spheres and are chosen to be as large as possible so that the plane compression is maintained. Ball bearing 30 or 31 is 1
(See Figures 3 to 6). The ball holder 32 essentially consists of a cylindrical plastic injection-molded part having a wall thickness slightly smaller than the ball diameter as the base body 32'. The plastic injection molded part is reinforced with glass fibers. Cylindrical wall 3 of base body 32'
3, a cylindrical blind hole 34 in which the bearing only has a ball has a diameter slightly larger than the ball diameter. Therefore, each blind hole 34 is provided with one slit 35 on the inside and one on the outside. Switch IJt 35 is ball 4
The width of the slit is such that the 0 can be transferred by friction, but the slit is smaller than the diameter of the sphere. After the ball 40 is erected, the hole 34 is closed by a disk 36 (see FIG. 5) on the open end side.

The disc 36 is centered by a pin 37 that is integrally injection molded into the base 32' of the ball holder. The base body 32' and the disc 36 are joined together by adhesion or ultrasonic welding. In short, the ball holder 32 with the balls 40 is present as a pre-prepared component during the final assembly (FIG. 3). The ball holder 32 is fixedly assembled in the ring-shaped members 18, 19 as already mentioned. Since the flow of such a valve arrangement 1 takes place through ball bearings 30, 31, the inner diameter of the ball retainer 32 is made as large as possible, so that a sufficiently large annular gap is created for the flow. left free. The mode of operation of the valve arrangement according to the invention is as follows: FIG. 1 shows the valve arrangement in its de-energized starting position.

Outlet valve 12/28 is closed. Therefore, the inlet return valve 11/
27 is relatively wide open due to the main spring 14 forcing the plunger 13 completely upwardly. A pressure receiver 2 is connected to a pressure source 3. To obtain the first excitation phase, a partial current is supplied to the coil 5.

Plunger 13 advances through a first portion of the plunger stroke. In this neutral position, the inlet valve 11/27 as well as the outlet valve 12
/28 will be closed.

In order to move from the neutral position to the energized end position, a force bounce is created which is overcome. This force bounce provides absolute stability in the neutral position.
If the valve arrangement 1 is to be completely switched, the current for the coil 5 will be increased and the plunger 3 will go completely downwards. The main spring 14 is strongly compressed. The retaining member 26 supporting the closing member 28 in this position is pulled downwards to such an extent that the closing member 28 no longer covers the valve seat 12 . The outlet valve 12/28 is opened and the pressure medium flows out of the pressure receiver 2 to the relief point. Plunger 13 cannot advance through the last part of the plunger stroke.

This is because the plunger is prevented from doing so by the smoothing ring 16. As a result, steep ranges of the magnetic force characteristic curve are eliminated, so that for the operation of the plunger 13 a flat range of the magnetic force characteristic curve of the magnet can be used. Between switching the magnet from fully energized back to half energized, some magnetic force remains retained and the spring force is therefore reduced by the difference between the magnet and the return force. The force is extremely small.

However, the fact that it is mounted on a friction-free ball bearing nevertheless results in very short switching times of the plunger. FIG. 2 shows the use of a valve device 41 according to the invention as a pressure regulating valve.

A plunger 42 is fixed to a rod 43, which is made of a non-magnetic hardened material. The plunger 42 is
Together with the coil 55, a magnet is formed which has a linear characteristic curve over approximately 15 degrees. Stick 43 has a f. In addition to the plunger, a closing member 44 or a throttle member is fixed, which closure member 44 or throttle member is connected to the conical valve seat 4.
5, the flow cross-section of the valve seat can be adjusted within a wide range. The magnet is continuously energized until it is fully magnetized, so that the closure element 44 always releases an increasingly larger flow cross section.
When the magnet is not energized, the tuft 46 positions the plunger 42 in a stable end position. The regulated pressure of this 'fair pressure regulating valve' is at most 4. When fully energized, the plunger 42 reaches its other end position and the controlled flow pressure is at its maximum. Between these two end positions, the pressure is regulated steplessly, and the pressure once regulated is maintained precisely, independent of the magnetic supply of the pump. The demands on magnetic force linearity and hysteresis are therefore very high. However, by frictionally supporting the plunger as in the present invention, the above requirements can be fully met. Two ball bearings 47 and 48 are fixed to the rod 43,
In this case, one ball bearing 47 is attached to the stationary core 49 and the other ball bearing 48 is attached to the cylindrical casing protrusion 50.
It is located in Both ball bearings 47 and 48 are arranged in a different manner 43 between the shank pieces 51 and 52 and the retaining rings 53 and 54, respectively.
is permanently incorporated into. Both ball bearings 47, 48
The bearing is formed as a bearing as shown in FIGS. 3 to 5.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view showing a plunger bearing in a 3-boat 3-position directional control solenoid valve device, Fig. 2 is a longitudinal sectional view showing a plunger bearing in a pressure regulating valve, and Fig. 3 is a longitudinal sectional view showing a plunger bearing in a 3-boat 3-position directional control solenoid valve device. FIG. 4 is a front view and a plan view of the ball bearing retainer base, and FIG. 5 is a plan view of the cage thin plate. 1... Three-way control valve device, 2... Pressure receiver, 3... Pressure source, 4... Load reduction point, 5... Coil, 6... Coil support,
7... Guide tube, 8... Nonmetallic member, 9, 1
0...accommodating part, 9', 10'...tube piece, 11...
...Inlet valve seat, 12...Outlet valve seat, 13...Plunger, 14...Main spring, 15...Shoulder, 1
6... Suba ring, 17... Notch, 17'...
...Shoulder, 18, 19...Ring-shaped member, 20...Sleeve, 21...Gap, 22...Shoulder, 25
, 26... Holding member, 27, 28... Closing member, 29... Tension spring, 30, 31... Ball bearing, 32... Ball retainer, 32 '...Base, 33
......Same cylindrical wall, 34...Blind hole, 35.
...slit, 36...disk, 37...pin, 4
0... Ball, 41... Valve device, 42...
... Plunger, 43... Haru, 44...
・Closing member, 45... Valve seat, 46...
Come back, 47, 48... Ball bearing, 49...
・Ri○ part, 50... protruding part, 51, 52... shank piece,
53, 54...stop theory, 55...coil. FIG. 3FIG. IFIG. 5 FIG. 2 Fl6. L

Claims (1)

[Scope of Claims] 1. An electromagnetic valve device for controlling the flow of pressure medium through a valve device, the valve device comprising an axially movable sleeve associated with an immovable sleeve surrounded by an excitation coil. of the type having a plunger, the plunger being centered by two ball bearings, each ball bearing having a group of balls arranged on a circle, the balls being one are held at intervals along two retainers 32, each retainer being tightly clamped within the valve arrangement 1, 41 leaving an axial gap for the balls at the magnitude of the plunger stroke. An electromagnetic valve device characterized by: 2 It is designed as a 3-port 3-position directional control solenoid valve and has two valve seats respectively provided at the ends of the tube pieces, and the tube pieces 9' and 10' are arranged on the rolling surface of the ball. The electromagnetic valve device according to claim 1, which is formed as a support portion for. 3. The rolling surface is an inner race of hardened material, which inner race is pressed against the outer wall of the tube pieces 9', 10', and each retainer 32 is attached to a ring-shaped member 18, 1 in the plunger 13.
9. The electromagnetic valve device according to claim 2, which is retained in Patent No. 9. 4. It is designed as a pressure regulating valve, furthermore the plunger supports the closing member, and the plunger 42 is fixed to a rod 43 coaxially passing through the valve arrangement 41;
2. The electromagnetic valve device according to claim 1, wherein the rod is centered in the casing via the balls of both groups and the support and the rolling surface.