FI103831B - Improved valve device - Google Patents

Description

, 103831

Improved valve device

The invention relates to an improved valve device for controlling a pressure medium actuator as defined in the preamble of claim 1.

The invention also relates to an improved valve arrangement for controlling a pressure medium actuator as defined in the preamble of claim 17.

10 A method and a device for controlling a pressure medium actuator are known from Finnish patent publication 91554. This method utilizes a control actuator and valve testing. When the control actuator is operating, the control means are moved and act on the valve means of the valve arrangement so that the pressure medium can travel to and from the actuator and exert pressure on the actuator by moving its output and the actuator output movement to the actuator. This method is characterized in that the movement of the control elements affecting the valve arrangement is effected in a linear motion, and from the output of the actuator the feedback moves to the control actuator in a linear motion such that the feedback movement wherein they continue to affect the valve arrangements in their displaced position so that the pressure medium can pass through the actuator during actuation of the actuator and exert pressure on the actuator, and that stopping the actuator results in the transmission of the actuator feedback to the ground, and their control effect terminates on the valve arrangements of the valve arrangement, the drive stops.

The device for controlling the pressure medium actuator includes a control actuator and a valve arrangement. Means for feedback of actuator movement to the actuator are connected from the actuator output to the actuator actuators for linear movement thereof. The linear actuation of the actuators by the actuator included in the actuator is eliminated by a backward-galvanized reverse linear motion when the actuator is actuated, which causes the actuation of the actuators to stop. In this case, the control elements are in such a position that they further influence the valve means of the valve arrangement so that the pressure medium can pass through the actuator actuator and exert pressure on it. Stopping the actuator results in the transmission of the feedback of the actuator feedback to the control elements to return them to their original position and the termination of the control effect on either valve actuator, whereby the actuator stops.

5

Each of the two valve means comprises a plurality of valves for controlling the passage of the pressure medium into and out of the actuator. There are four of these valves. The first valve is disposed between the actuator and the pressure medium container to control the pressure medium discharge flow. The second and third valves cooperate with each other. The second valve is disposed between the pressure medium container and the third valve to control the third valve. By moving the actuator controls, another valve is actuated. A third valve is disposed between the pressure medium pump or a corresponding source of pressure medium and the actuator to control the pressure medium supply flow. A fourth valve is provided in connection with the third vent-15 brick between the pressure medium pump or equivalent source and the first and second valves. By means of this valve, the first and third valves are closed after the control action of the control means on the second valve has ceased.

The disadvantage of the above arrangement is that each of the valve means 20 comprises a plurality of valves, whereby they form a complex mechanical structure. Further, the multi-stage valve arrangement has adverse effects such as delays in actuator operation. It also results in a loss of control accuracy for the drive. It should be noted, however, that the limits of both speed and control accuracy only become apparent, for example, at the large reciprocating reciprocal travel distances of the piston of the hydraulic cylinder and at high piston speeds.

The object of the invention is e.g. eliminates the valve device problems mentioned above. In particular, it is an object of the invention to provide a novel improved valve device and valve arrangement by which pressure medium actuators can be precisely controlled.

The improved valve device according to the invention is characterized in what is set forth in claim 1.

The improved valve device of the invention for controlling a pressure medium actuator actuated between a pressure medium source, such as a pump, and a return tank or similar pressure medium suction, includes two co-ordinated and co-operable valves and control means, from the pressure medium source through the supply channel and the first actuator channel to the actuator and through the second actuator channel and the outlet channel back to the pressure medium suction, and each second valve is arranged as a control valve for the first 5 valves.

According to the invention: - the valve chamber of the first valve and the spindle fitted therewith are divided in at least two parts in the direction of movement of the spindle: the front and spindle of the valve chamber and the rear of the valve chamber and rear of the spindle the maximum cross-sectional area of the back and the mandrel; - a tapering point is provided in the rear space of the valve chamber and in the front space respectively, with a first and a second seat respectively; 15 - the pressure medium supply channel and the first actuator channel are arranged in different directions of the spindle transmission along the first seat, and the pressure medium outlet channel which is connected to the outlet channel and the second actuator channel is arranged differently to the second seat; - a taper point is provided at the rear and the front of the mandrel, respectively, with a counter-part for the first and second seats respectively, the counterparts and the seats being adapted to engage tightly with each other in the closed position of the valve; a first and a second interconnecting channel are provided at the rear and front of the mandrel, respectively, by which the pressure medium supply channel and the first actuator channel and the pressure medium output channel and the second actuator channel are connected to each other in the valve open position; - the pressure medium source is connected by a control channel to the rear space of the first valve, the first valve stem being arranged to sink by the pressure of the pressure medium to a closed position whereby the first and second connecting channels are closed. - a second valve is connected to a bypass channel between the rear of the first valve and a container, and - the control means are arranged in connection with the second valve to control the first valve and the entire valve device; and wherein, when the second valve is opened, the bypass and the pressure in the rear space of the first valve stem is reduced, wherein the first valve opens into the valve chamber by the pressure acting on the pressure medium supply channel and the pressure medium 4 103831 is flowing from the through.

5

An advantage of the invention is the construction of the first valve of the valve device, which allows the valve to be closed and opened by utilizing the pressure of the pressure medium, i.e. the second valve.

A further advantage of the invention is that by controlling a small pressure medium flow (a second or control valve) in the valve device, a large pressure medium flow (first valve) of the actuator can be controlled.

It is also an advantage of the invention that the valve device and the valve arrangement based thereon provide a simpler, more accurate and reliable control of the pressure medium actuator.

A further advantage of the invention is that it is possible to carry out a pressure medium operation. preferably a hydraulic control arrangement having a short closed pressure medium system. This closed system is suitable for a small space and simple.

A further advantage of the invention is that the drive can be precisely controlled even at high operating speeds.

: 25

A further advantage of the invention is that the vibration tendencies of the valve device are substantially eliminated.

A further advantage of the invention is that both the valve device and the valve arrangement are controllable by means of a digitally suitable transfer device, e.g. a step motor.

A further advantage of the invention is that the valve 1 and the valve arrangement can be readily adapted to pressure media actuators of various sizes, such as hydraulic cylinders and hydraulic motors.

In the following, the invention will be described in detail with reference to the accompanying drawings, in which Fig. 1 is a partial longitudinal sectional view of a valve device according to the invention; Figure 2 shows a cross-sectional view B-B of the valve device of Figure 1; Figure 3 shows a cross-sectional view C-C of the valve device of Figure 1; Figure 4 shows a cross-sectional view D-D of the valve device of Figure 1; Figure 5 is a partial longitudinal cross-sectional view of another valve device according to the invention; Fig. 6 is a partial longitudinal cross-sectional view of a third valve device according to the invention; Figure 7 is a partial longitudinal cross-sectional view of a fourth valve device according to the invention; Fig. 8 is a partial longitudinal cross-sectional view of a valve arrangement according to the invention for controlling a pressure medium actuator; and Fig. 9 is a partial longitudinal cross-sectional view of a valve arrangement and a hydraulic cylinder actuated therewith.

An improved valve device 1 according to the invention for controlling a pressure medium driven actuator 4 is shown in Figure 1. The valve device 1 is fitted between a source of pressure medium 20, such as pump P, and a return tank T or a corresponding pressure medium suction.

The valve device 1 includes a pressure medium supply channel 2 connected to the pump P and a pressure medium outlet channel 3 connected to the reservoir T to discharge the pressure medium 25. The tank T is connected by a duct to the suction side of pump P. The valve device also includes two drive ducts 5; 6, which are connected to a pressure medium actuator 4.

The valve device 1 comprises two co-operating and cooperating valves 7, 8. The first valve 7 is disposed between the pump P and the tank T to control the pressure medium input and output flow through the drive means 5, 6. A second valve 8 is provided at the connection of the first valve 7 between the pump P and the tank T to control the first valve 7.

The first valve 7 includes a sheath 9, a valve chamber 10, and a spindle 11. Preferably, an elongated and cylindrical valve chamber 10 is provided inside the sheath 9, the spindle 11 being preferably displaceable in the longitudinal direction A-A of the valve chamber. The spindle 11 controls the flow of pressure medium Ä 103831 o from pressure medium source P through supply channel 2 and first drive through device channel 5 to drive device 4 and through second drive channel 6 and outlet channel 3 back to pressure medium suction T. Flow directions of pressure medium are indicated in the drawings.

5

The valve chamber 10 and the spindle 11 fitted thereto are divided into at least two parts in the displacement direction AA of the spindle 11: the first section, the front 12, and the second section, the rear 13. The maximum cross sectional area of the front chamber 12 is smaller than the max. buck. The valve chamber 10 is preferably cylindrical in symmetry, wherein the maximum diameter demax of the front space 12 (cf. Fig. 5) is smaller than the maximum diameter dtmax of the rear chamber 13 of the valve chamber. Each space 12, 13 of the valve chamber is provided with a reduction point where the cross-sectional area of the valve chamber space, and in particular the diameter demax → dtmax, is reduced: dsj -> dyj; ds2 -> dy2 (dsl <dtmax, ds2 <demax). The cross-sectional areas and diameters ds1, dy1, ds2, dy2 mentioned for Li-15 decrease towards the front end of the valve chamber. The tapering points form a first seat 310 at the rear of the valve chamber 13 and a second seat 311 at the front space 12 of the valve chamber. 311 to the first part of the valve chamber, i.e. the front face 12.

The valve chamber 10 is arranged on the housing 9 of the valve device 1, as shown in the embodiment of Figure 6. Alternatively, the valve chamber 10 is disposed within the subframe 30 and is housed in the subframe space 31 of the valve assembly 1, as will be described in greater detail below (cf., e.g., Figs. 1-4, 5). In either case, the valve chamber 10 and spindle 11 are preferably of similar construction; for like parts, the same reference numerals are used.

30th In addition to the valve chamber 10, the spindle 11 is divided into at least two maximal cross-sectional areas in the displacement direction A-A of the spindle 11: the first or the front 28 of the spindle and the second or rear 29. The said cross-sectional areas of the spindle 11 correspond to corresponding cross-sections. Preferably, both valve chamber 10 and spindle 11 are cylindrical symmetrically, wherein the maximum diameter of stem 28 of front spindle 28 corresponds to the maximum diameter demax of rear face 12 of valve stem 10, which corresponds to the maximum diameter dtmax of rear chamber 13.

7 103831

Each spindle member 29,28 includes a sealing region 110, 111 having a sealing ring 15, 16, a drive channel 5, 6 fitting channel 171, 181, a socket counterpart 312, 313, and a connecting channel 17, 18. The maximum spindle front 28 has a maximum cross-sectional area of 5 in the second sealing area, the maximum cross-sectional area of the lily backside spindle 29 is in the first sealing area 110. The sealing rings 15, 16 are fitted in the sealing grooves 150, 160 which are in the sealing regions 110, 111. As the spindle 11 is moved, the sealing rings 15, 16 slide against the inner surfaces of the front chamber 12 and the rear 13 of the valve chamber 10 in the movement of the spindle from the closed position to the open position and vice versa.

The actuation channel 171, 181 of the actuator channel 5, 6 is an annular channel adjacent to the sealing area 110, 111 to which the actuator channel 5, 6 is connected when the valve 7 is in the closed position. The seat counterpart 312, 313 is disposed between the drive channel fitting channel 171, 181 and the connecting channel 17, 18. The seats 310, 311 of the valve chamber 10 are arranged to fit exactly into the counterparts 312,313 when the valve 7 is in the closed position (Figures 1, 5, 6 and 7). Correspondingly, flow apertures 320, 321 are formed between the seats 310, 311 and the counterparts 312, 313 when the valve 7 is in the open position and the supply channels 5,6 are connected via these openings 320, 321 to the connection channels 17, 18 and further to the supply channel 2 and outlet 14. The diameter dsi, ds2 at the drive channel 5, 6 at the fitting channel 171, 181 is larger than the diameter dyj, dy2 at the connecting channel 17, 18. Said diameters dsi, ds2; dy1, dy2 are smaller than the maximum diameters dtmax, ^ Emax of the corresponding mandrel portion 28, 29 (Fig. 5).

The surfaces of the circumferential seats 310, 311 of the valve chamber 10 are preferably conical surfaces as well as the corresponding surfaces of their counterparts 312, 313, e.g. 1, 5, 6 and 7 are illustrated.

The first valve 7 includes a first and a second connecting duct 17, 18. The first-connecting duct 17 of the En-30 is disposed at the spindle 11 between the sealing rings 15, 16 at the rear of the spindle 29 near the second end of the spindle. By means of this connecting channel 17, the pressure medium supply channel 2 is connected to the valve 7 in the open position to the first actuator channel 5. The length of this connecting channel 17 in the spindle movement direction corresponds to the distance between the pressure medium supply channel 2 and the actuator channel 35. The first connecting duct 17 thus extends from the proximity of the first sealing ring 15 to the first seat counter part 312. The second connecting duct 18 of the first valve 7 is provided at the front 28 of the spindle 11 and extends from the second seat 313 of the spindle 11 to the first end.

Preferably, the structures of the first and second connecting channels 17, 18 are similar to the following 5.

The first connecting duct 17 includes a first annular connecting duct section 33 to which the end of the supply duct 2 is always connected regardless of the position of the spindle 11 in its path of movement in the valve chamber 10. Through the annular connecting duct 33 10 the pressure 11 acts on the spindle 11 when the second valve 8 (120 Fig. 6) is opened.

The first connecting duct 17 of the first valve 7 includes a plurality of spaced apart first spindle connecting portions 36 disposed about the circumference of the spindle 11 and the axis AA 15, connected at their first end to the annular first connecting duct 33 and in a plane perpendicular to the surface) with curved portions 37 on the outer surface of the mandrel. Through the opening 320, the curved portions 37 further connect the annular fitting duct 171 of the first drive duct 5 and 20 to the first duct duct portions 36, the first annular duct duct 33 and the feed duct 2 when the valve 7 is in the open position.

Preferably, the second connecting conduit 18 includes a plurality of spaced apart spaced-apart second grooved connecting conduit portions 38 relative to the circumference of the spindle 11 and parallel to the axis AA, which open at a first end from an end 28 of the mandrel 11 toward the outlet conduit 14 and the outlet conduit. one end being curved portions 39 in the radial direction (i.e., in a plane perpendicular to the surface of the spindle of circular cross-section) at the outer surface of the mandrel 11 in the vicinity of the circumferential counterpart 313 of the second socket. The curved portions 39 connect through the opening 321 with the second drive channel 6 and the annular fitting channel 181 to the outlet channel 14 and further to the outlet channel 3 when the valve 7 is in the open position.

Gateways 17, 18 such as those described above are flow-preferred; pressurized fluid flows remain as laminar as possible and no turbulence occurs. This also eliminates possible vibration tendencies of the spindle 11. Further, the grooved channel portions 36, 38 improve the control properties of the valve 7; the pressure medium flow through valve 7 can be precisely controlled.

9 103831

The pump P is connected via a control channel 19 to the rear space 13 of the valve chamber 5 of the first valve 7, so that the spindle 11 of the first valve 7 is arranged to move under pressure from the pressurized medium to a closed position and blocked through the discharge channels 2, 3.

The second valve 8, 55, 120 (cf. Figs. 1, 5 and 7) is arranged as a control valve of the first valve 7. Obviously, the second valve can be implemented in many different ways. It is a prerequisite that the flow rate of the second valve can be adjusted and thus affect the operating speed of the first valve. A preferred embodiment of the second valve is shown below.

15

The second valve 8 in the embodiment of Figure 1 comprises a valve chamber 20 and a closure member 21 thereon arranged to close the valve flow passage, or valve chamber 20, by a spring member 22 or the like so that the pressure medium flow is prevented in the valve closing position. The throughflow channel 20 of the second valve 8 is arranged to be connected to the bypass channel 23 between the rear 13 of the first valve 7 and the outlet channel 3.

Preferably, the second valve 8 is connected to the spindle 11 of the first valve 7 such that the second valve 8 is movable simultaneously with the spindle 11 and in a directional direction. The spring-loaded closing member 21 of the second valve 8 is arranged to operate in the direction of travel of the spindle 11 of the first valve 7.

In the most preferred embodiment, the second valve 8 is disposed coaxially, i.e., on the shaft A-A, in the spindle 11 of the first valve 7, such as mm. Figures 1 and 7 illustrate ha-30.

•

The spindle 11 of the first valve 7 is provided with a hole in the direction of the trajectory and axis AA, which at the front end of the spindle 11 forms a bypass passage 23 and a second valve 8 throughflow channel or valve chamber 20 in the middle of the spindle. locked in place and locked in place by a screw sleeve 24 having a central hole 25 in the center of the bypass AA, which is part of the bypass conduit 23. The spindle 11 is provided with a seat 26 and an opening 27 which engages the bypass conduit 23. orifice 27 when the second valve 8 is in the closed position (as shown, inter alia, in Figure 1).

In another embodiment of the valve device, the second valve 120 is provided 5 outside the first valve 7, as shown in Figures 5 and 6. This valve 120 is substantially similar in construction to the second valve 8 fitted to the spindle 11 in Fig. 1 and its respective parts have been given the same reference numerals. The second valve 120 is then connected to a bypass passage 121 which connects the valve chamber 10 of the first valve 7 to the rear outlet 13 of the valve 13.

The first valve 7 preferably includes a sleeve-like subframe 30, as shown in the embodiments of Figures 1-4, 5 and 7. The subframe 30 is disposed in the subframe 31 of the valve housing 9 and is provided with seals 305, 306, 307, 308 in the displacement direction of the shaft 15 A-A and the mandrel 11 between the supply channel 2 and the actuator channels 5, 6. The auxiliary body 30 is provided with a suitable shape for the valve chamber 10. The subframe 30 and spindle 11 are closely matched. The matching of these is accomplished, for example, by grinding their opposite surfaces in a common grinding process. This is a cost-effective production solution for manufacturing the first valve 7. At the same time, the auxiliary body 30 can be fitted with matching channels associated with the feed channel 3 and the drive channels 5, 6, as will be described later. These fitting ducts are used to stabilize the valve function, e.g. such that the spindle 11 of the first valve 7 is uniformly subjected to pressure of the pressurizing fluid from all sides thereof. The subframe 30 and spindle 11 and associated parts are most preferably cylindrical in relation to the ac-25 selenium A-A.

The subframe 30 is staggered with respect to its inner and outer diameters in the direction A-A of the shaft, most preferably comprising three sleeve-like subframe portions 301, 302, 303 of different diameters (cf. Figs. 2-4). The outer diameter D3 of the front end of the subframe, i.e. the third subframe 303, is smaller than the outer diameter Dj of the rear end, i.e. the first subframe 301. The outer diameter D2 of the middle part of the subframe, i.e. the second subframe 302, is between said outer diameters Dj, D3, where Dj> D2> D3. The inner diameters d1, d2, d3 of the subframe portions 301, 302, 303 respectively relate to one another, i. dj> d2> d3. In addition, the auxiliary body portion 303 of the front end of the auxiliary 35 body 30 includes a reduction portion 304 having an opening which is aligned with the outlet valve 14 of the first valve and has a diameter d4 = dy2 <d3_11 103831

The maximum diameter demax of the front chamber 12 of the valve chamber 10 of the first valve 7 and the diameter 28 of the front 28 of the mandrel 11 at the sealing ring 15 corresponds to the inside diameter d3 of the third subframe 303 of the auxiliary body the diameter of the rear portion 29 of the spindle 11 at the sealing ring 16, which corresponds to the inside diameter d1 (taking into account the play) of the first body portion 301 of the subframe 30. With this arrangement, the movements of the spindle 11 are secured with the pressure of the pressure medium 10 acting on its rear 13 and the first interconnection channel 17 respectively in the closed position and the open position (dashed lines, e.g. in Figure 1).

The construction of the mandrel 11 is described above and is independent of whether or not a subframe 30 is used in the embodiment of the invention (cf. e.g. Fig. 5) or not (cf. Fig. 6). The spindle 11 comprises two cylindrical sealing regions 110, 111, in which areas the sealing rings 15, 16 are arranged in suitable sealing grooves. As the spindle 11 is moved, the sealing rings 15, 16 preferably slide against the cylindrical inner surfaces of the first and third subframe members 301, 303. The subframe 30 includes two circumferential seats 310, 311, the first 310 being disposed between the inner surfaces of the first and the second subframe portions 301, 302 having different diameters d 1, d 2 and the second 311 being disposed within the tapering portion 304 of the subframe 30 a third subframe 303 having a diameter d3, dy2 (= d4) and a reduction section 304. The spindle 11 includes recesses 312, 313 corresponding to the recesses 312, 313 corresponding to the recesses 311. The surfaces of the recessic recesses 310,311 are preferably inclined conical surfaces as well as the counter surfaces of their recesses 312, 313 and are precisely arranged to sit with

«

The first seat 310 and the corresponding opening 320 belong to the rear space 13 of the valve chamber 10 of the first valve 7. The supply channel 2 and the first connecting channel 17 are connected to the seat 310 and the opening 320 as well as the first drive port 30. : the valve 7 of the valve chamber 10 into the front space 12, in particular the end of the front space 12. The second drive duct 6, the second connecting duct 18 and the outlet duct 3 via the outlet duct 14 are connected to the opening 321. The circumferential counterparts 312, 313 rest against the plugs 310, 311 when the first valve 7 is in the closed position and close the pressure fluid flow openings 320, 321 .

. The first connecting duct 17 of the first valve 7 is arranged in connection with the spindle 11 and is preferably formed as described above. Connecting channel 12 103831 17 includes a first annular connecting channel section 33 to which the end of the supply channel 2 is connected. The end of the feed passage 2 is formed as an annular passage 34 disposed around the circumference of the sleeve-like subframe 30, in particular its central part 302, as shown in Figures 1-4 and 5. The annular passageway 34 is provided with radially apertures 5 and 35 passing through the subframe 30 and leading to the rear compartment 13 of the valve chamber 10 and further to the first interconnecting conduit 17, particularly the first annular conduit 33. when the second valve 8 is opened.

10

The first end of the drive channel 5 is formed as an annular channel 341 disposed on the circumference of the first subframe 301 of the sleeve-like subframe 30. The annular passageway 341 is provided with radial openings 342 which pass through the subframe 30 and lead to the rear space 13 of the valve chamber 10 and further through either aperture 15 320 to the first connecting passageway 17 or the first annular fitting duct 171, On the other side of the fitting duct 171 is a circumferential counterpart 312 of the first socket which is pressed against the socket 310 of the auxiliary body 30 when the valve 7 is in the closed position and respectively and the opening 320 is open when the valve 7 is in the open position.

The second connecting channel 18 of the first valve 7 is arranged in connection with the spindle 11. The second connecting channel 18 is located at the front end 28 of the spindle 11. The second connecting channel 18 is preferably formed as described above. The end 25 of the second drive channel 6 is formed as an annular channel 344 disposed on the outer circumference of the third subframe 303 of the sleeve-like subframe 30 as shown in Figures 1-4 and 5. The annular passageway 344 is provided with radial apertures 345 which pass through the valve body 30 and lead to the front space 12 of the valve chamber 10 and further through either opening 321 to the second connecting conduit 18 or to the second annular fitting conduit 30 181, depending on the position of the spindle 11. On the other side of this fitting duct 181 is a circumferential counter portion 313 of a second socket which is pressed against a second socket 311 of the subframe 30 when the valve 7 is in the closed position and respectively and the opening 321 is open when the valve 7 is in the open position.

The valve chamber 10 of the first valve 7 includes a shoulder 52 or the like barrier. The spindle 11 of the valve 7 is adapted to move within the valve chamber 10 so that its movement is stopped by this shoulder 52 when the valve 7 is in the fully open position.

Valve chamber 10 and rear space 13 are bordered by shoulder 52. Extension of rear chamber 13 of valve chamber 10 and 13 103831 is an end space 53 in the movement direction of spindle 11 and axial A-A. In this embodiment, end space 53 is smaller than rear space 13 and shoulder 52 is formed between them. Through the end space 53, the rear space 13 is pressurized, i.e. pressurized medium is supplied thereto via a control channel 5 19.

A choke 40, such as mm, is preferably provided between the rear space 13 of the first valve 7 and the pump P. Figure 1 shows. This is arranged in the control channel 19.

In a preferred embodiment, the throttle 40 includes a threaded throttle pin 41 disposed in a correspondingly threaded throttle body 42. A small diameter hole 43 is drilled in the longitudinal center of the throttle pin 41, and is preferably sealed by a closure such as a throttle cap 44 and closable. The purpose of the choke 40 15 is to reduce the flow of pressure medium through the control channel 19, particularly when the second valve 8 is in the open position. After this, the pressure medium flows through the control duct 19 to the rear space 13 of the first valve 7 and further through the second valve 8 to the outlet duct 3 and back to the tank T. The choke pin 41 can be rotated out of the choke housing 42 The diameter of the hole 43 of the new throttle pin 41 may be selected so that it differs from the diameter of the hole of the previous pin. The amount of pressure medium flowing through can thus be selected as appropriate. This affects eg. the operating speed of the valve device and the flow of fluid through the valve device.

Alternatively, instead of the throttle 40, the control channel 190 may be dimensioned in such a way that the pressure medium flow in the bypass channel is of the desired size when the valves 7, 8 are in the open position (cf. Figure 5).

The control means 45 of the valve device 1 preferably includes an electric transfer device 46, 30 a control shaft 47 and a guide pin 48 disposed at its free end (cf. Figs. 1, 5 and 7). The drive means 46 moves the steering shaft 47 and the guide pin 48 in a straight line. The steering shaft 47 is disposed in the shaft space 49 of the housing 9. The steering shaft 47 is supported in the shaft space 49 by one or more bearings 50 on the valve body shell 9. The steering shaft 47 is further provided with a seal 54. The bearing 50 allows linear movement of the steering shaft 35 47. The control elements 45 further include a control unit 51 for electrically controlling the electrical conveyor 46. · 46 includes, for example, an electric motor, such as a stepper motor, and a screw nut motion transducer 14 103831 for converting a rotary movement into a linear movement of the steering shaft 47 and pin 48.

The spindle 11 of the first valve 7 has two extreme positions: a closing position in which the first counter part 312 of the spindle 5 11 rests against the first socket 310 and the second counter part 313 rests against the second socket 311 (as shown in Fig. 1). 11 rear end 29 resting against shoulder 52, and flow openings 320, 321 (shown by dashed lines) open between counter portions 312, 313 and seats 310, 311. These correspond to the closed and open positions of the valve device 1.

10

Consider, for example, the valve device 1 of Figure 1. Let us first assume that the first valve 7 is in the closed position. The actuator 46 is guided by the control unit 51 to move the control shaft 47 and pin 48 in the direction E and to act on the closing member 21 of the second valve 7 against spring loading. Thus, the passage 23 from the rear 13 of the first valve 7 through the outlet duct 3 to the tank T opens and the pressure in the rear boiler 13 decreases rapidly. As a result of the pressure of the pressure medium acting on the mandrel 10 through the annular connecting channel 33, the mandrel 11 moves towards the shoulder 52, whereby the first valve 7 opens. The pressure medium can then flow from the pump P to the actuator 4 via the supply conduit 2, the first interconnection channel 17 and 20 through the first actuation channel 5, and back from the actuator 4 to the reservoir T via the second actuation channel 6, second interconnection channel 18 and outlet conduit 3. At the same time, the spindle 11 moves in conjunction with the second valve 7 and this closing member 21 in the direction of travel of the guide pin 48, i.e. the axis A-A, thereby keeping the guide pin 48 in controlled contact with the closing member 21.

25

The length of the control stroke 48 of the guide pin 48 of the control members 45 depends on how much the spindle 11 of the first valve 7 opens and opens the openings 320, 321. Similarly, the amount of control stroke is adjusted by the first interconnection channel 17 (second interconnection 18) and first actuation channel 5 ) throttling, i.e. the flow of pressure medium to actuator 4 (out of actuator 4). Thus, the medium is fed and discharged in a controlled manner from the actuator 4.

«>

After the transfer device 46 has been moved a sufficient distance from the guide pin 48, the spindle 11 of the first vent-35 brick 7 has been moved to its extreme position against the shoulder 52. The first valve 7 and at the same time the valve device 1 is in the fully open position.

, 5 103831

When the control pin 48 is moved by the transfer device 46 in the opposite direction F to the foregoing, the second valve 7 begins to close and the spindle 11 of the first valve 7 begins to move towards the closed position in the same manner but in reverse order. The spindle 11 reaches the closing position when the guide pin 48 is moved sufficiently far out of the spindle 11.

When the second valve 120 is disposed outside the first valve 7, as in the embodiments of Figures 5 and 6, the valves 120, 7 operate in principle as described above. A significant difference, however, is the fact that there is no direct feedback mechanism between the first valve 10 and the second valve 7, 120, such as e.g. 1, where the adjustment of the second valve 8 affects the first valve 7 and, as the spindle 11 of the first valve 7 is moved, the opening / closing of the second valve 8 is also affected.

15

The transfer device 46 can also be implemented as a mechanical lever device known per se, by means of which the steering shaft 47 and the guide pin 48 are moved. In this case, a separate control unit 51 is not required. It is also possible with the mechanical lever device arranged as part of the control unit 51 to control the electric transfer device 46 20 and thereby the valve device 1.

Figure 7 shows another valve device 55 according to the invention, in which the corresponding parts of the valve device 1 of Figure I are used with the same reference numerals. The second valve 8 is coaxially mounted on the spindle 11 of the first valve 7, as in the valve device 1 of Figure 1. In this embodiment, the second valve 8 includes an auxiliary body 56 housing the actual portions of the second valve device 8 of Figure 1, such as bypass , a valve chamber 20, a closure member 21, a spring member 22, and a screw sleeve 25. The subframe 56 is disposed within the subframe space 57 provided in the spindle 11 of the first valve 7a. The position of the subframe 56 is adjustable in the direction of

The subframe 56 and the subframe space 57 preferably have matching threads 58. The subframe 56 may be rotated and adjusted with a suitable tool, such as a screwdriver, to rotate its position in the direction of travel of the spindle II. Specifically, it is intended to eliminate any play 35 between the control elements 46, in particular the control pin 48 and the closing member 21, when the valve device 55 is brought into operation.

The actuator 4 is controlled by a valve device 1 in Figure 1, which in this embodiment is a double acting hydraulic cylinder 60. This cylinder 60 includes a piston 61, a piston rod 62 and a cylinder space 63. The piston 61 divides the cylinder space 63 into two parts: a first part 64 and a second part 65. in addition, a valve 66, such as a 5/4 valve or the like, by means of which the direction G, R of the cylinder 60 is changed. Your control unit controls the actuator46 and valve66 of valve valve 1. The arrangement also includes a position detector 67 for indicating the position of the piston 61 and the piston rod 62. The position detector 67 is connected to the control unit 51.

10, the valve 66 has two operating modes, the first of which a first side of the valve device 1, the actuator channels 5, 6 and a second side of the actuator so. the connecting channels 66a, 66b of the hydraulic roller cylinder 60 are directly connected to one another: 5 to 66a and 6 to 66b and to one another to 5 to 66b and 6 to 66a.

The double-acting hydraulic cylinder 60 is controlled by the valve device 1 as follows. It is assumed that the valve device 1 is in the closed position as shown in Figure 1, i.e. no pressure medium passes through it. The piston 61 of the cylinder 60 is then locked in an intermediate position between its extreme position of travel, as illustrated in Figure 1. According to a message from the position detector 67, the intermediate station is known to the control unit 51.

20

It is desired to displace the piston 61 of the cylinder 60, and in particular the piston rod 62, in a direction G in a predetermined distance a. According to the operating command of the control unit 51, the valve 66 is set to the first operating state (cf. above) and the operating elements 45 are given an operating command. The transfer-25 device 46 then begins to move the control shaft 47 and pin 48 towards the closing member 21 (direction E) of the second valve 8 of the valve device 1 to open it, with the consequences described above. When the first valve 7 is in the open position, the pressure fluid enters the pump P pass conduit valve means 2 and 1 via the first drive unit channel 5 and further valve 66 and the channel 66a of the first 60 to 30 side of the hydraulic cylinder space 64. The piston 61 under the influence of the pressure medium in the direction of G. At the same time 61 of the second piston When the piston 61 reaches a predetermined position, i.e. displaced by a distance, this is detected by a position detector 67 and information is provided to the control unit 51. The control unit 51 is provided to the control unit 51. immediately commanding the control means 45 and its actuator 46, which begins to move the control shaft 47 and pin 48 away from the closing member 21 (direction F) of the second valve 8 of the valve device 1 to close it as previously described. When the first valve 7 is in the closed position, the pressurized fluid does not transfer from the pump P via the valve device 1 to the hydraulic cylinder 60 and from there to the tank T.

When the piston 61 in the hydraulic cylinder 60 is to be moved in the other direction R, the valve 5 66 is placed in a second mode of operation in which the channels 66a and 6 and the channels 66b and 5 respectively communicate with one another. Thereafter, the valve device 1 is operated just as described above. However, the pressure medium is now supplied from the pump P via the supply channel 2 and valve device 1 to the drive channel 5 and through the valve 66 10 to the channel 66b and thence to the second cylinder space 65 of the cylinder 60 and the pressure medium 3 and to tank T. The piston moves in the R direction.

It should be noted that the valve device of the invention, such as the valve device of Figs. 1 and 5, can be directly used to control a single acting hydraulic cylinder or the like, wherein the return of the piston of the cylinder is arranged to occur by a spring. However, in the piston return step, however, the pressure medium must be returned to the container T via e.g. a return passage 6 and a valve, such as valve 66, in substantially the same manner as above but without supplying the pressure medium 20 to the drive.

Figure 8 shows a valve arrangement for controlling a pressure medium actuator actuator according to the invention.

. The valve arrangement comprises two valve devices la and Ib. The first valve device 1a is the valve device of Figure 1 and the second valve device Ib is the valve device of Figure 7. They are housed within a common body 70. Each valve device 1a, Ib has a pressure medium supply channel 2a; 2b connected to pump P or a corresponding pressure medium source. Correspondingly, the valve means 1a, Ib have a common pressure medium outlet conduit 3 connected to the reservoir T or the corresponding pressure medium bone 30 for removing pressure medium from the valve arrangement. The tank T is connected by a duct to the suction side of pump P. Each of the valve means 1a, Ib has two drive means channels 5a, 5b; 6a; 6b for a pressure medium actuator 71.

Drive channels 5a, 6b are coupled and connected to first actuator side 35 of actuator 71 to move actuator outlet 72 in one direction G: 'and actuator channels 5b, 6a are coupled and connected to other actuator outlet 18 18 to actuate actuator outlet 72 in the other direction R.

Each valve device la, Ib includes two valves. First valve 5 7a; 7b is disposed between the pump P and the reservoir T to control the pressure medium inlet and outlet flow of the actuator 71. Second valve 8a; 8b is arranged in connection with the first valve 7a, 7b between the pump P and the tank T for controlling the first valve 7a, 7b. The structure of the valve device 1a corresponds to the structure of the valve device 1 according to Fig. 1. The valve device 1a and the corresponding parts 10 of the valve device 1 of Fig. 1 are used interchangeably with reference numeral a. The structure of the valve device Ib corresponds to that of the valve device of Fig. 7, and the parts thereof corresponding to the same reference numeral, but with the addition of the letter "b".

The control means 73 of the valve arrangement include a transfer device 74 and a control unit 88 thereof. The control means 73 may also be counted to include a position detector 97 of the actuator output 72 15.

The transfer device 74 includes an actuator, preferably a stepper motor 75, and a guide shaft 76 associated therewith, a motion transducer such as a screw nut motion converter 91 and a lever member 77. The shaft of the stepper motor 75 is coupled to the steering shaft 76. A motion transducer such as a screw nut motion transducer 91 converts the rotational movement of the steering shaft 76 into a linear motion thereof. The stepper motor 75 is supported in connection with the switch space 83. Within the switching space 83 is a switch 89 for engaging the shaft of the stepping motor 75 to the first end 76a of the steering shaft 76. By means of the switch 89 * ', the rotary movement of the stepper motor 75 is transmitted to the steering shaft 76 so that a small reciprocating linear movement of the steering shaft 75 is also allowed. The steering shaft 76 is disposed in the shaft space 78. The steering shaft 76 is supported in the shaft space by two bearings 79, 80 on the body 70. The bearings 79, 80 also permit axial movement of the steering shaft 76. The passage of the first end 76a of the steering shaft 76 through the opening 81 to the outside of the body 70 is provided with a seal 82. The second of the steering shaft 76; The end 76b is supported by a bearing 80 on the body 70 at one end of the shaft 78.

The lever assembly 77 of the transfer device 74 is secured to the steering shaft 76 by a lever frame 84a. The lever frame 84a is preferably a cylindrical portion movably disposed in the shaft space 78. The lever frame 84a is secured to the shaft 35 76 by means of the retainers 85a, 85b. The lever frame 84a is movable along the axis 76 when moved linearly in the shaft space 78. The steering shaft 76 is rotatable in an opening 85 in the center of the lever body 84a 19 103831. The lever body 84a includes a projection 84b arranged to protrude from the lever body 84a and the shaft 76 preferably in a plane perpendicular thereto. A first and a second pin 86, 87 are provided at the free end of the projection 84b. Each pin 86, 87 is formed by a rod.

The pins 86, 87 are preferably formed of a continuous straight bar passing through the projection 84b, wherein the pins 86, 87 are located at opposite ends of the bar. This rod and, at the same time, the pins 86, 86 are in this case substantially parallel to the longitudinal axis of the control shaft 76 and the main axis A-A of the valve means 1a, Ib.

The valve arrangements 1a, Ib of the valve arrangement are arranged in cooperation with one another. Two valves 7a, 7b of each valve device; 8a, 8b are arranged in connection with intermediate space 90. This intermediate space 90 is part of the outlet duct 3 and communicates with the tank T. The shaft space 78 is connected to the intermediate space 90. The lever frame 84a is disposed in the shaft space 78 so that the projection 84b extends into the intermediate space 90. The lever frame 84a 15 slides linearly 84b can move in intermediate space 90.

The valve means 1a, Ib, in particular the first valves 7a, 7b having spindles 1a, 1b associated with the second valves 8a, 8b, are arranged across the space 90 so that the movement paths of the spindles 11a, 11b are on the same straight or axis AA . The spindles 11a, 11b of the first valves 7a, 7b are then moved coaxially in the valve chambers 10a, 10b. The lever 77 of the transfer device 74 is disposed in the intermediate space 90 such that the pins 86, 87 are disposed between the spindles 11a, 1b of the first valves 7a, 7b and the closing members 21a, 21b of the second valves 8a, 8b and are moved by the spindles of the first valves 7a, 7b. 11a, 11b in the direction of the trajectory. The pins 86, 87 then extend into the bypass passages 23a, 23b and are in the closing position of the first valves 7a, 7b in the immediate vicinity of the closing members 21a, 21b of the second valves 8a, 8b. If there is a clearance between the pins 86, 87 and the closing members 21a, 21b, it is removed by adjusting the position of the subframe 56b of the valve device Ib by adjusting the movement 30 of the closing member 21b of the second valve 8b as described in connection with FIG.

The actuator 71 is a double-acting pressure medium cylinder, preferably a hydraulic cylinder. The piston 92 of the cylinder blade is disposed in the cylinder space 93. On one side of the piston 92, a first part of the cylinder space 93, i.e. a first cylinder space 94, and on the other side a second part of the cylinder space 93, i.e. a second cylinder space 95. a first actuator channel 5a for a valve device la and a second actuator for the second valve device Ib! terminal 6b is connected to drive cylinder 71 of first actuator 71 or hydraulic cylinder 104. Further, second drive channel 6a of first valve device 1a and first drive channel 5b of second valve device Ib are connected to second cylinder space 95 of actuator 71 or hydraulic cylinder.

The operation of the valve arrangement according to the invention will now be described, and with reference to Figure 8. The valve devices 1a, Ib function as described above, e.g.

Assume that pump P is running and fluid is pumped into the supply channels 2a, valve 1a, Ib of the valve arrangement 10; 2b. The pressurized medium passes through the control duct 19a, 19b and the throttle 40a, 40b to the rear valves 13a, 13b of the first valves 7a, 7b and closes these valves, i.e. pushes the spindles 1a, 1b to the closing position. The pressurized medium cannot flow to or from the actuator 71. The other valves 8a, 8b are also closed; the lever device 77 of the transfer device 74 is in the central position 15 (as shown in Fig. 8) and the pins 86, 87 are close to the closing members 21a, 21b, preferably closed in the closing members, but the other valves 8a, 8b are still closed.

The output 72 of the actuator 71, such as the piston 92 of the hydraulic cylinder and the piston rod 20 96, is to be displaced in the s direction in G. The control unit 88 commands the actuator 74, in particular the stepper motor 75. The stepper 75 and associated steering shaft 76 in the direction of rotation H. The screw nut movement converter 91 converts the rotation movement of the steering shaft 76 into a linear displacement movement, whereby the first rotation direction 25 H causes the steering shaft 76 and also part of the stepper motor switch 89a to move in the same direction. The first control pin 86 begins to press the closing member 21a of the second valve 8a of the first valve device 1a and the second valve 8a opens. Bypass passage 23a between the rear valve 13a of the first valve 7a and the intermediate space 90 opens.

30

8, the drive medium 5a of the first valve actuator 1a is connected to the first cylinder space 94 of the hydraulic cylinder acting as actuator 71, thus the pressure medium flows into this cylinder space 94 and acts on the piston 92 and piston rod 96 96 of the piston rod. At the same time, the pressure medium is discharged from the actuator 71 through the second actuator channel 6a of the first valve device 1a. 8, the second actuator channel 6a is connected to the second cylinder 95 of the hydraulic cylinder 21 103831 which acts as actuator 71. Thus, the pressure medium flows out of this cylinder blade 95 as displacement of the piston 92 reduces the cylinder space 95 and outputs the second actuator. The pressure medium is directed from the actuator duct 6a to the second connecting duct 18a of the first valve 7a of the first valve device 1a and out of the valve chamber 10a through the outlet 14a and intermediate space 90 to the outlet duct 3 and further to the container T.

When the spool 1a of the first valve la and the spool 1a of the first valve 7a are moved towards the rear space 13a, i.e. the open position, in the chamber 1a, the second valve device 8a moves with the spool 1a. The lever member 77 of the control member, and in particular the guide pin 86, holds the second valve 8a open for a displacement of a given spindle 1a. If this displacement distance is exceeded, the action of the pin 86 on the closing member 21a of the second valve 8a ceases and the second valve 8a closes; the pressure medium is again transferred to the rear space 13a of the first valve 7a through the guide duct 19a and the throttle 40a and acting on the spindle 1a, pushing it toward the lunar position (direction L), i.e., reducing the second connecting duct 18a. At the same time, the second valve 8a returns to the control pin 86 and the situation is balanced, i.e. the second valve 8a opens. A similar situation is repeated when the first valve device 1a is closed.

When the piston 92 of the hydraulic cylinder has been moved the desired distance s, this is detected by the position detector 97 in the control unit 51 and the actuator 74, in particular the stepper motor 75, commanded to start rotating in the opposite direction. a screw nut motion converter 91 to a linear linear displacement stroke; because of the second direction of rotation K, the steering shaft 76 moves in the direction L. The lever arm 77 and the first steering pin 86 connected to the steering shaft 76 move with it. The first guide pin 86 begins to move away from the closing member 21a of the second valve 8a and the second valve 8a closes. The bypass duct 23a between the rear valve 13a of the first valve 7a and the intermediate space 90 is closed. The pressure of the pressure medium 30 in the rear space 13a of the first valve increases, so that the spindle 1a is moved towards the front space 12 to the closed position; the first valve 7a closes. The pressure medium flow path from the pump P to the supply channel 2a and through the first connecting channel 17a to the first drive channel 5a and the drive 71 and the respective drive 71 through the second drive channel 6a and the second connecting channel 18a is closed off to the discharge channel 3a and the tank T.

The stepper motor 75 is stopped when the control shaft 76 and the first control pin 86 of the lever assembly 77 associated therewith are moved to an initial position 22 103831 (cf. Fig. 8), i.e., the first and second valves 7a, 8a in the closed position 8a in the immediate vicinity of the closing member 21a, even touching it. In this initial position, the second control pin 87 of the lever device 77 is likewise in the immediate vicinity of the second valve 8b closing member 21b of the second valve device Ib.

During the above operation, the first and second valves 7b, 8b of the second valve device Ib are in a closed state and no pressure medium is passed through the valve device Ib in any direction.

10

When changing the operating direction of the actuator 71 output 72 in relation to the above, i.e. displacing the hydraulic cylinder piston 92 in the R direction, the control pin 87 acts on the second valve 8b of the second valve device Ib in a manner similar to that described above for the first valve device 1a. The operation of the second valve device Ib is completely analogous to that of the valve device 1a described above. Only the actuator channels 5b, 6b are cross-coupled to opposite sides of the actuator 71, such as the hydraulic cylinder piston 92 on different sides of the cylinder spaces 94, 95, to change the operating direction of the actuator 71.

During the above operation, the first and second valves 7a, 8a of the first valve device 1a are in a closed state and no pressure medium 25 passes through the valve device 1a in any direction.

Figure 9 illustrates an actuator and actuator actuated therewith, such as a hydraulic cylinder 103. The actuator includes actuators 100, 101 and a valve arrangement 102. The actuators include a control unit 100 and an adjustable actuator 30 101 for controlling operation of the actuator 103 and thereby.

The valve arrangement 102 includes two valve devices 1a, Ib and are preferably similar to those shown in Figure 8. In addition, means 104 are provided at the connection between the hydraulic cylinder 103 and the transfer device 101 for the output of the actuator, i. a hydraulic cylinder 103 for pivoting the piston 107 on the transfer device 101.

35

The transfer device 101 is similar in structure to the transfer device 73 of the valve arrangement of Figure 8.

The transmission device 101 includes an actuator as the actual transmission device, such as an electric motor, preferably a stepper motor 75, and a control shaft 23 103831 76 and a lever device 77 arranged in connection therewith. The stepper motor 75 is connected to the first end 76a of the steering shaft 76. The coupling 89 is disposed in the coupling space 83. The oh-axis shaft 76 is disposed in the shaft space 78 such that in addition to its rotational movement, axial movement is also permitted.

5

The steering shaft 76 is provided with a device for converting the rotary motion into a linear motion, which in this case is a screw nut assembly 91 (or a corresponding ball nut assembly). It is disposed at one end 76b of the steering shaft 76. By means of the screw nut assembly 91, the rotational movement 10 H, K transmitted to the steering shaft 76 of the step motor 75 is converted to a linear longitudinal movement of the steering shaft 76 in either direction I or L.

The lever shaft 77 is connected to the steering shaft 76, comprising a lever frame 84a and a projection 84b. The guide pins 86, 87 are provided with the projection 84b. By means of the guide pins 86, 87, one of the second valves 8a, 8b belonging to the first and second valve means 1a, Ib, and thereby also the corresponding first valve 7a, 7b, is opened, as described in connection with Fig. 8.

In the embodiment of Figure 9, the pressure medium, in particular the hydraulic cylinder 103, is provided as a drive device. Cylinder 103, as is known per se, includes a piston 107, a piston rod 108, and a cylinder space 109. The piston 107 is imaged to move into the cylinder space 109. The piston 107 divides the cylinder rod 109 into two parts; first and second cylinder spaces 109a, 109b. Drive channels 5a, 5b; 6a, 6b of the valve means 1a, Ib from each of the first valves 7a, 7b are cross-connected to the first and second cylinders. 25 for grating 109a, 109b on different sides of piston 107.

The feedback means 104 for feedback of movement of the actuator outlet, such as the piston 107 of the hydraulic cylinder 103, the transfer device 101 includes a screw-nut movement converter 106, a transmission portion 115 and a connection portion 105. The feedback means 104 provide a linear displacement movement of the piston 107. This rotation is coupled to the screw nut motion converter 91 of the transfer device 101. This arrangement allows the rotational motion of the stepper motor 75 to be compensated for and the linear movement of the steering shaft 76 and the associated lever assembly 77 and the guide pins 86, 87 are stopped. The lever assembly 77 and the control pin 86, 87 remain in the position where they hold the first (or second) valve means la, (Ib) open and the piston 107 of the hydraulic cylinder 103 continue to move in the desired direction G, R.

24 103831

In this embodiment, a motion converter adapted to the piston 107 of the hydraulic cylinder for converting the linear motion of the piston into a rotational motion is implemented by means of a screw-nut motion transducer 106. The screw nut movement converter 106 includes a sliding screw 113 and a motion nut 114. The piston 107 is coupled to the movement screw 113 and this 5 threaded to the movement nut 114. The motion nut 114 is connected to the transmission 115 and this is further coupled to the drive nozzle so that they cannot rotate when the piston 107 is displaced by the piston 107 in the axial direction G, R. The linear displacement of the piston 107 and the propeller 113 is then transmitted by the threads between the propeller 113 and the motion nut 114 to the rotary movement N, Q. and further through the coupling portion 105 to the conveyor 101 for the screw nut motion converter 91, which is similar in structure to the screw nut motion converter 106 of the aforementioned cylinder 107 (we also refer to earlier Finnish patent application 91554 of the same applicant). converts rotation N, Q into a linear motion on the steering shaft 76 of the transfer device 101. This feedback rotation N, Q moves the steering shaft 76 in the direction L, I, or opposite to the linear motion I, L. provided by the stepper motor 75. the directions L, I and I, L are aligned with each other 20 so that they offset each other so that the lever 77 of the transfer device 101 is substantially stationary and tends to keep the second valve 8a, 8b of the valve device la, Ib of one of the valve arrangements 102 open each time the stepper motor 75 is in operation.

The actuator for actuating the hydraulic cylinder 103 or similar actuator according to Fig. 9 operates in principle as follows. When the piston 107 of the hydraulic cylinder 103 and its arm 108 are to be moved in the G (R) direction, the stepper motor 75 is actuated through the control unit 100 and rotated in the H (K) direction, causing the steering shaft 76 and lever 77 with guide pins 86 (87) I (L). The second valve 8a of the first valve device 1a is actuated by moving the control shaft 76 and the guide pin 86 in the first direction I and the second valve device 8b is actuated by moving the control elements 76 and the control pin 87 in the second or opposite direction L. The second valve 8a (8b) acting on the second valve 8a (8b) of the first (second) valve device 1a (Ib) is opened 35 together with the first valve 7a (7b) and the pressure medium is supplied from pump P to the supply channel 2a (2b) and first valve 7a (7b). ) to the first drive channel 5a (5b) and further to the hydraulic cylinder 103 to the first (second) cylinder space 109a (109b) to move it in the direction G (R). The pressure medium is discharged from the second (first) cylinder space 109b (109a) of the hydraulic cylinder 103 through the second drive channel 6a (6b) and the first valve 7a (7b) to the outlet channel 3 and the tank T.

When it is desired to stop the movement of the piston 107 of the hydraulic cylinder 103, for example, after a certain distance of travel, the control unit 100 orders the stepper motor 75 to stop. As a result of stopping the stepper motor 75, the piston 107 of the hydraulic cylinder 103 does not immediately stop, but moves for a brief moment and causes feedback in reverse direction to the steering shaft 76; the stepper motor 10 75 now does not rotate the steering shaft 76 and does not compensate for the feedback rotational motion. As a result, the steering action of the control shaft 76 and the control pin 86, 87 of the lever assembly 77 on either valve assembly 1a, Ib of the valve assembly 102 is terminated, resulting in the movement of the piston 107 of the hydraulic cylinder.

The pulse encoder 117 detects the rotational motion of the coupling member 105 or, generally, the motion converter 106 of the hydraulic cylinder 15. It is arranged to act as a position detector for the piston 107 of the hydraulic cylinder 103, the information of which is provided to the control unit 100. Based on the information provided by the pulse sensor 117, the position of the piston 107 is confirmed (or can be used to calibrate piston position data). The actual piston 107 position information is obtained directly from the control unit 100; based on the direction of rotation information and the control pulses (step pulses) provided to the stepper motor 75 20, the output position of the piston 107 or the corresponding actuator can be directly calculated without even a position indicator.

When the first valve device 1a, Ib is in the closed position, no pressure medium 25 passes through it and the piston 107 of the hydraulic cylinder 103, or the outlet of the corresponding actuator, cannot move; medium is present in both cylindrical spaces 109a, 109b of the hydraulic cylinder 103.

In the embodiments of Figures 8 and 9 described above, instead of a hydraulic cylinder, the actuator may be a hydraulic motor or similar rotary or linear actuator driven by a pressure medium. The rotational motion of the rotary drive is controlled in principle in much the same way as the linear motion of the piston of a hydraulic cylinder. In this regard, we refer to the earlier Finnish patent application 91554 of the same applicant.

35 26 103831

It should be noted that the movement distances of the control elements, such as the steering shaft 76 in the direction of the axis A-A, are relatively small, such as about 5 mm or even less. Thus, the control means, and in particular the guide pins 86, 87, can actuate very quickly the corresponding second valves 8a of the first or second valve device 1a, Ib of the valve arrangement; 8b and further to the first valves 7a, 7b.

The actuator, such as an actuator, preferably a stepper motor, is controlled from the control unit. The control unit comprises a data processing unit, the core of which is generally a microprocessor. The amount of movement of the actuator, such as the length of the movement or the degree of rotation or the number of revolutions, may be pre-set in the transfer device and its implementation monitored, for example, by position data and / or motion data from the position detector. Many other programmable control modes known per se are possible.

The invention is not limited to the above embodiments only, but many modifications are possible within the scope of the inventive idea defined by the claims.

<·

Claims (17)

1 Ib) halutaan siirtää sulkuasennosta aukiasentoon ja paineenalaista veliainetta johtaa käyttölaitteen (71) yhdelle puolelle ja poistaa toiselta puolelta käyttölaitteen ulosoton 30 (72) liikuttamiseksi haluttuun suuntaan. si 103831 An improved valve assembly (1) for controlling a print media driven drive assembly (71) positioned between a print media source (P) such as a pump and a return container (T) or such print media neck, the valve assembly (1) comprising two interconnected and cooperating valves (7, 8) and control means (45), the first valve (7) including a spindle (11) fitted into the valve chamber (10), with which the pressure medium flow is controlled from the pressure medium source (P) via the supply channel (2) and the the first drive channel (5) to the drive device (71) and via the second drive channel (6) and the output channel (3) back to the pressure medium neck (T) and the second valve (8) being arranged as a control valve for the first valve (7) , characterized in that - the valve chamber (10) of the first valve (7) and at the same time the spin part (11) arranged therein is divided into at least two parts in the direction of movement of the spindle (AA): the front chamber (12) of the valve chamber and the spindle the ffamp portion (28) and the rear chamber (13) of the valve chamber 15 and the rear portion (29) of the spindle, the maximum transverse area of the valve chamber front chamber (12) and the spindle ffamp portion (28) being smaller than the maximum transverse area of the valve chamber rear chamber (13) and rear portion (29), - in the rear chamber (13) and front chamber (12) of the valve chamber, there is provided a taper into which a first and second chuck (310, 311) are adapted; 20. a pressure medium supply channel (2) and the first drive channel (5) are arranged in the direction of movement of the spindle (AA) on different sides of the first chuck (310), and the pressure medium output channel (14) connected to the output channel (3). ), and the second drive channel (6) is arranged on different sides of the chuck (311); 25. A taper with a counterpart (312, 313) for the first and second chucks (310, 311), respectively, is provided in the rear portion (29) of the spindle (29), whereby the counterparts and chucks are arranged to close tightly together in the closed valve. bearing; - a first and second second connecting channel (17, 18), respectively, with the supply channel (2) for the printing medium and the first drive channel (5) and the output channel (14) for the printing medium have been arranged in the rear and ffamp portions (29, 28), respectively. and the second drive channel (6) is connected in the open position of the valve (7); - the pressure medium source (P) is connected to a control channel (19) with the rear space (13) of the first valve 35 (7), whereby the spindle (11) of the first valve (7) is arranged to be pressed in the closed position under pressure from the pressure medium, in which the first and second connecting ducts (17, 18) are closed and at the same time the flow of the first pressure medium is blocked through the first valve (7) and via the supply and discharge channels (2, 3); The second valve (8) has been connected to the bypass channel (23) between the rear space (13) of the first valve (7) and the container (T) and - the control means (45) have been arranged in connection with the second valve (8). controlling the second valve (8) and with it the first valve (7) and the entire valve device (1), whereby in the valve device (1), when the second valve (8) is opened, the bypass channel (23) denη the first the back chamber (13) of the valve (7) to the pressure medium neck (T) is opened and the pressure in the back chamber (13) of the spindle (11) of the first valve (7) decreases, the first valve (7) being opened against the valve chamber (10) under pressure via the print medium supply channel (2) and the print medium can flow from the print media source (P) to the drive device (71) via the supply channel (2), the first connection channel (17) and the first drive channel (5) and from the drive device (71) back to the print media neck ( T) via the second drive channel the second connecting channel (18) and the output channel (3). Valve device according to claim 1, characterized in that the second valve (8) comprises a valve chamber (20) and a locking member (21) which is adapted to close the valve with a spring eye (22) or the like; and the control means (45) comprise a control pin (48) by which the locking member (21) of the second valve (8) is controlled as the flow of the valve (8) is controlled and the valve device (1) is simultaneously controlled. Valve device according to claim 2, characterized in that the second valve (8) is connected to the spindle (11) of the first valve (7) so that the second valve (8) is movable parallel to the spindle (11) and that the spring-loaded locking means ( 21) arranged to operate in the direction of movement of the first valve spindle (11). « Valve device according to claim 3, characterized in that the second valve (8) is arranged coaxially on the spindle (11) of the first valve (7). 5. An improved valve assembly according to claim 3 or 4, characterized in that the second valve (55) comprises an auxiliary body (56) into which a flow passage (23), a locking means (21) and a spring means (22) are fitted, wherein the auxiliary body (56) is adapted in the spindle (11) of the first valve (7), preferably in the auxiliary body (57) arranged in its path, and the position of the auxiliary body (56) is adjustable in the direction of movement of the spindle (11) (Figure 7 ). Improved valve assembly according to claim 5, characterized in that threads (58) between the auxiliary body (56) and the auxiliary body (57) are provided so that by rotating the auxiliary body (56), its position can be changed in the path of the spindle (11) to eliminate gap between the control means (45), in particular the control pin (48) and the locking means (21). Valve device according to claim 3, 4, 5 or 6, characterized in that the exit channel (14) of the first valve (7) is arranged at the end of the front chamber (12) of the valve chamber (10), and the control pin (48) is arranged to run via the output channel (14) of the second valve device (8) adjacent to the spindle (11) of the first valve (10), the control pin (48) actuating the locking member (21) of the second valve (8) in controlling the valve (1). 10 Valve device according to any one of the preceding claims, characterized in that the first connecting channel (17) comprises a first annular connecting channel section (33) to which the supply channel (2) is connected, and by which the pressure of the pressure medium affects the spindle (7) of the first valve (7). 11) and pushes it toward the rear compartment 15 (13) as the second valve (7) opens. Valve assembly according to claim 8, characterized in that the first connecting channel (17) comprises a plurality of first locking connecting channel portions (36) spaced apart on the circumference of the spindle (11) parallel to the spindle path (AA) connected at its first end. with the annular first connecting channel section (33). An improved valve assembly according to claim 8, characterized in that the first lock-shaped connecting channel portions (36) are connected at one end to the outer surface of the spindle (11) in parallel with the radius of the spindle (11) near the: peripheral counterpart (312). of the first chuck. Valve assembly according to any one of the preceding claims, characterized in that the second connecting channel (18) comprises a plurality of second locking connecting section sections (38) spaced apart on the circumference of the spindle (11) parallel to the axis (A-A). An improved valve assembly according to claim 11, characterized in that the second lock-shaped connecting channel portions (38) are connected at one end to the outer surface of the spindle (312) with the radius of parallel to the spindle (11) near the peripheral counterpart (312). the other chuck. t Valve device according to any of the preceding claims, characterized in that the first valve (7) comprises a hollow-mapped auxiliary body (30) arranged in the jacket (9) of the valve device, the valve chamber (10) being suitably formed with the auxiliary body (30) and the auxiliary body (30) and the spindle (11) are adapted to each other. Valve device according to claim 13, characterized in that adaptation channels (341, 342; 34, 35; 344, 345) connected to the supply channel (2) and the drive device channels (5, 6) are adapted in the hollow-mapped auxiliary body (30). Valve device according to any of the preceding claims, characterized in that the surfaces of the chucks (310, 311) in the valve chamber (10) of the first valve (7) are cone-shaped surfaces, as well as the abutment surfaces of the counterparts (312, 313) in their spindle ( 11). Valve device according to any of the preceding claims, characterized in that a throttle (40) is arranged in the control channel (19) between the rear space (13) of the first valve (7) and the pressure medium source (P). An improved valve arrangement (70) for controlling a print media driven drive device (71), wherein the valve arrangement between a print media source such as a pump (P) and a container (T) or such print media neck, characterized in that the valve arrangement (70) ) further comprises two mating valve assemblies (1a, 1b) according to any of the preceding claims, each comprising a first valve (7a, 7b) and a second valve (8a, 8b) arranged adjacent to its spindle (11a, 11b), which arranged coaxially (AA) on opposite sides of the gap (90) so that the exit channel (14a, 14b) from the valve chamber (10a, 10b) of the first valve (7a, 7b) in each valve device opens into the gap (90) and from here, further in the container (T), and the control means (73) comprise two control pins (86, 87) arranged movably in the space (90) so as to transmit via the output channel (14a, 14b) a blocking device (21a, 21b) transmitted valve device (1a, 1b) second valve (8a, 8b) to the spring load where the first valve spindle (11a, 11b) is to be removed from the closed position in the open position and the pressurized medium is guided to one side of the drive (71) and removed from the other the side to move the output device (72) of the drive in the desired direction.