JPS61502735A - Pressure control device for the hydraulically actuated coupling and/or brake of the press drive shaft - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Hydraulically actuated coupling of press drive shaft and/or pressure control device for brakes The invention also provides a hydraulic drive coupling-brake combination for a press drive shaft. or relating to pressure control devices for separately arranged couplings or brakes. .

This type of device for presses operating at partial pressure or maximum phase or shock relief and Many types of noise reduction measures are known.

According to E-P S 0051684, the work cylinder is equipped with a program-controlled printer. By connecting the robo-tioning valve in series in the feed pipe, the intermediate pressure is much higher than the partial pressure. The desired partial pressure is achieved by starting the compression stroke at a lower partial pressure and then switching to a lower partial pressure. After adjusting the rotational speed it is suggested to release the maximum working pressure for the specific working stroke again. has been done.

As a result, quick starting is not only coupled with high mechanical loads on the drive elements. The arrangement of the throttle valve in the feed pipe also slows down the flow of oil between the working cylinders. The stronger the buffer, the longer the switching time will be, so the partial discharge pipe will be smaller. It becomes. It is also essential to control the pressure release phase or braking phase at the end of the press stroke. It's on. Furthermore, safety considerations for the placement of the damping valve within the main pressure piping itself Seems to be legitimate.

Another solution is to use a constriction located at the intake or outlet of the working cylinder of the press. The possibility of realizing a damping effect is exploited.

Therefore, according to DB-O3 No. 1502319 and No. 1577264, after starting Only the partial pressure at the maximum pressure is released by the throttle part of the feed pipe, and then the pressure is released again. A compressed air control method is known in which the maximum pressure is released after the Discharge speed after passing through the press working range, although unfavorable speed transitions will be adjusted control is not considered at all. Therefore, the above method is appropriate for hydraulic systems. It cannot be called a thing.

According to DE-O5 No. 2321117, a pressure damping mechanism for hydraulic equipment is provided. The mechanism operates according to the pressure in the no-load pipe that branches from the pipe that leads the working oil. It consists of a flat slide valve that moves, and a restriction that changes according to the differential pressure within the flat slide valve. The passage cross-section is pre-prepared by a occluding material with a preselectable slope by means of a truncated cone. Different pressure relief effects must be triggered automatically depending on the position of the slam. stomach. This variant also makes it difficult to quickly fill the working cylinder. For example, in order to incorporate a truncated cone at other slopes, the buffer occluding material must be removed. It is not possible to have large adjustment variability. Another special feature in this case is viscosity control. will have important meaning. Furthermore, if the buffering effect is large, the flow will be gentler. Avoid prolonging the overall press stroke time as a result of longer adjustment intervals due to oil. Therefore, the partial impact effect of the press may be reduced in this case as well. Ru. A method to separate and control the ejection phase or braking phase after the bus passes through the working area. Steps are also not provided in this case or are not possible.

Starting from this hydraulic device of DE-O3 2321117, the object of the invention is to The damping valve in the oil supply pipe located after the safety safety valve and the pressure medium strongly dependent on viscosity By avoiding actuated switching parts, braking or pressure increases with increasing pressure. Pressure modulation for quick force reduction with shock mitigation and for example internal adjustment for adjustment work. something that rises or changes quickly without engaging with something and then easily repeats itself again The objective is to further develop pressure control devices for hydraulic work that can be achieved.

The above object is achieved by providing a tank with a fixed position and a plurality of pressure release rises as defined in claim 1. different in each case via a distribution valve which is electrically regulated by reversing the Squeezing pressure solution between the press safety valve kinematically coupled with it and the working cylinder The removal conditions are controlled and finely adjusted so that they are precisely parallel to the respective press ram position. If the flow is blocked in the main passage towards or from the working cylinder, There is no need to accept interference control. Electrical connection between the only common distribution valve and the press safety valve. Different pressure stages in the parallel pipes of the pressure relief pipes are activated via the pneumatic function circuit. By making adjustments, the working conditions selected in each case are maintained most accurately and the working conditions are An acceptable motion synchronization of the connecting elements is achieved such that they can be easily found again after stopping. the In order to change the respective adjustment position (e.g. a circle with a different slope) (for the awl unit) no valve structure is required and the pressure value or displacement value is independent of the operating time. Both can respond to changes or demands in a wide range, and in that case, it is natural that the press It is no longer necessary for individual work steps to be extended in time.

This is necessary, for example, when the device is equipped with individual travel paths and new working paths. Extreme working conditions such as those required can be controlled without hydraulic pressure fluctuations. special No mechanical obturators are used and the device can be fitted with standard valves. Since it can be done, it can be said that the expense is advantageous in terms of cost and can be implemented. Further production Cartridges allow convenient installation of control elements outside the area of the cylinder. Devices constructed according to the principle do not pose mounting position problems. Furthermore, electricity Various automatic safety controls and quick error detection for each individual work phase are achieved through air control. output ability becomes possible. Work systems free from flow obstructions, such as throttle valves, for example. Due to the cylinder oil mains, the cylinder is filled very quickly, allowing for flexible starting. Short stroke times with dynamic and coupling effects and therefore consistency and consistency of the entire press stroke A reduction in noise and wear is achieved without any loss of time during the release process.

In that case, in an extremely short period of time when transitioning to normal speed or stop conditions, Precise changes in the working pressure are necessary if it is outside the press working range and is not entirely necessary anyway. For a short period of time, the rotational moment of a surface that lies outside the working area is reduced unless Allows the kinetic energy to be reduced. In this way, the full rotation This makes it possible to prevent vibration resonance and impact from occurring even if the In this case itself The damping action can be automatically adapted to different desired rotational speeds by means of known proportional techniques. is desirable. Furthermore, there are especially It is also possible to take the dimensions of the grooves or surfaces, and to create valve units in special damping valves for different working conditions. Since the unit cannot be replaced or exchanged, the device is similarly can be used in almost the same way as the host configuration method. Once selected, the adjustment value Changes between e.g. for individual strokes can quickly be found to be the same again, and the pressure of a partial stroke A change in the situation also causes a change in the next substroke, although not unconditionally. mosquito In the case of a spring-brake combination, the spring and piston surface must be different. Since there is no such thing, a simple manufacturing ratio can be adjusted for this as well.

Other configurations of the present invention are as presented in the second and subsequent claims.

According to claim 2, a system with two partial pressure stages and a configuration advantageous for maximum pressure is provided. Pressure parallel to the oil supply line of the working cylinder from the main pump or tank A possibility of subsequent filling from the tube has been proposed, with a special automatic shut-off. Preselected conditions where the pressure increase as well as the pressure decrease with the valve is rapid and constant and equal This contributes to the flow of water into the water. If more pressure stages have to be operated be provided with only a number of corresponding pressure relief pipe branches and valve fittings. Would.

In the case of claim 3, the influence of the obstruction is automatically transmitted from the parallel pressure pipe into the oil supply pipe. Take the necessary IT to dynamically and reliably shut down.

In the case of claim 4, the shut-off valve is closed and at the same time the shut-off valve is automatically controlled from the differential pressure control. Possibility to automatically refill the tank even in situations where it is held gender is taken into account.

In the case of claim 5, both branch pipes of the pressure-limiting stage are provided with a unique pressure damping device. Protected from the oil supply line against the effects of disturbances.

In the case of claim 6, the starting phase begins with a reduced pressure, while the pressure The partial amount of working oil in the oil supply pipe set in advance in one branch of the release pipe is determined by the pressure release pipe. Alternatively, it can be introduced into the tank via a distribution valve.

In the case of claim 7, while high pressure is generated in the oil supply pipe, the pressure relief pipe is shut off, while still retaining the total damping net loss from the damping valve. .

In the case of claim 8, a further damping phase is started near the end of the press stroke. On the other hand, the braking moment for the press ram is exactly as required by the separate no-load position of the distribution valve. It can be reduced by the required amount.

In the case of claim 9, the preceding post-braking press stroke ends quickly and uniquely. Meanwhile, the press safety valve's discharge hole opens and the pressure release pipe is closed via the distribution valve. .

The present invention further provides that the damping does not operate in accordance with the adjustment value and that such a case occurs. Press Safety Valve and Divider Valve Electrical Circuit for Fast Safety Switching Circuit (Not Shown) It offers the possibility of connecting. Press safety valve according to similar working principle It is necessary to install some kind of flow regulator in the specific oil supply line going from the to the working cylinder. Any number of pressure stages can be similarly combined with corresponding signal indicators and other distribution valves. It can be arranged logically.

Hereinafter, the present invention will be explained in detail with reference to embodiments shown in the drawings.

Figure 1 is a circuit diagram of a pressure control device that combines a press coupling and brake. Figure 1A shows the connection of the same system when the press coupling and brake are separated. indicates continuity.

Figure 2 is a progress diagram of the press stroke that defines the pressure control phase, and Figure 3 is the press safety valve. and related switching position table of the magnet body of the distribution valve, FIG. 4 shows a pressure control device of the present invention. It is a work diagram of a res process.

The first diagram shows the most important part of the hydraulic system in the press or its ram or drive shaft. A schematic electrical connection diagram of the element and the signal transmitter or remote position indicator is printed or Starts when the ram or drive shaft is at the top dead center (zero position) of the press ram. Accepting positions starting from position 0 are shown.

The pump 2 receives working oil from the tank 1 into the oil supply pipe 3, but the working oil is finally sent to the pump. brake 6 or cup of the coupling-brake combination via the safety valve 4. It flows into the working cylinder 5 of the ring 7. Inside the working cylinder 5 is the coupling side. The working piston 7 is supported in the direction of the return spring 9 . Piston rod 10 is in switching position Depending on the position, it can come into contact with the brake 6 or the coupling 7.

Since the press safety valve 4 releases pressure in the direction of the tank 1, the brake 6 is operated at the 0 position plane. As a result of the warping, the return spring 9 pressurizes the piston 8 and its rod 10 in the braking direction. The press ram (not shown) will be braked to allow this to occur.

A total of four sampling pipes branch off from the oil supply pipe 3.1. Press safety soon There are three (12, 13, 14) in front of valve 4, one of which (15) is connected to the same oil supply pipe 3. branch between cylinders. The pressure cutoff valve 16 is shut off via the sampling tube 12. However, the valve 16 applies supply pressure to that level in front of the press safety valve 4 via the check valve 51. Hold upright and adjust accordingly, regardless of location and possibly prior sampling. When knots occur, excessively supplied working oil is caused to flow back into the tank 1. sa The spring pipe 13 is equipped with one check valve 17 that prevents backflow, and one check valve 17 that prevents backflow. This is an unloader for two pressure resistance systems. The sampling tube depends on differential pressure It flows into the check pulp 17 in the sampling tubes 14 to 20, but the sample The sampling pipes 14 to 20 are connected to the check valve 18 and the tank via the throttle valve 21. 19, and the tank 19 is connected to the pipe 20 via another pipe 22. and communicates with the outlet of the 4/3 distribution valve 23 facing away from the press. This distribution valve 23 is a cutoff valve for the pressure release pipe 15, and the release pipe 15 allows flow in the four directions of the press safety valve. Branch the outlet into the connecting pipe 22 that the tank 1 touched first according to its position. turn to In the pressure release pipe 15 placed in front of the press side of the distribution valve 23, there is a pressure release pipe 15 in the downstream direction. When you look at it, the first thing you see is the brake valve 24, and its spring-loaded suspension. An inner throttle valve is placed downstream in the piston, and the brake valve 24 is not too steep. The drain hole can be opened to the tank 1 when a high load is applied. continue The pressure relief tube 15 branches into two branch tubes, each with its own adjustable and inlet port. A pressure-dependent pressure limiting valve 27,28 is provided. One branch pipe 2 5 then flows into the first press-side joint 29 of the 4/3 distribution valve 23, while the The second branch pipe 26 then flows into the second press side fitting 30. Side joints 29, 30 exists at the starting position or zero position of the press in the check valve depicted in Figure 1. Ru. In other words, in that case no pressure release occurs and the capacity is checked when connected. It is emitted via valve 53.

The distributor valve 23 is then switched back to the starting phase 41, 42 so that the tank 19 can only be filled via the throttle valve 54. Check valve 18 is closed After being closed, the tank 19 is connected to the fuel supply pipe 14 only via the throttle valve 52.

The press safety valve 4 is in this case magnetized on one side of it in order to open the flow-through position. The final control element 31 is depicted in simplified form as having a final control element 31 on the other side. The return spring 32 acts in the direction.

The distribution valve 23 is equipped with a magnet final control element and return springs 33.34 and 35.36. They are arranged opposite to each other and are connected to the magnetic field of the press safety valve 4 via the control box 38. It operates via an electrical control system 37 coupled to a final control element 31, Is it a remote position indicator, timer, angle indicator, etc. inside the Resram or drive shaft? The switching command consisting of the following information is obtained not only from the hand but also from one or several signal indicators 39. be able to.

In Fig. 1, when the brake 6 and the compulsory ring 7 are arranged separately, the oil supply pipe 3 requires a permanent switching part to be divided into its separate working cylinders 5 I don't.

In Fig. 2, the starting position (0 position) when the press flywheel 40 is 360'' 0 is drawn. In the case of starting phase 41.42, the first switching position is approximately 10-2 In the case of 06, it is normally arranged according to the starting position 0. Therefore, in the case of the present invention First, in the case of approximately 120@ to 150@, the ram's working range is 43A. A significant pressure rise value will occur across the coupling. Here, the contact pressure area 43B connects. After that, the second switching position is set to the low position when the angle is approximately 270 to 320°. A pressure drop range 44 below pressure follows.

The working cylinder 8 then assumes its starting position in the range 44 at approximately 340-3506 degrees. In the third switching position of Braking is performed in the moving range 44.

In region 46, valve 4.23 is again in the starting position.

FIG. 3 shows the magnet adjustment device 31, 33, 35 or the valve 4.2 corresponding to the above-mentioned strokes. The position of number 3 is drawn in the form of a table. In that case, the dots painted black are magnetic in each case. The open circle indicates the stop position, and the intersection indicates the valve passage is blocked. means cut off.

In the case of 0 @ to 360', all the magnet adjustment devices are at the starting position, so the adjustment device 31.33.35 is not energized and the press safety valve 4 is in the no-load position and the distribution Valve 23 is in the shutoff position.

Since the magnet adjustment gi31 is excited at the time of departure, the press safety valve 4 is closed to the working cylinder. Cancel entry in 5 directions. However, at the same time, the first negative voltage of the distribution valve 23 is Since the load position is actuated by the excitation of the first magnet regulator, the pump pressure The expansion pressure that deviates from this will be conveyed.

The press safety valve 4 or the magnet device 31 is activated during the press stroke from 106" to 20". However, the distributor valve 23 or its magnet device 33 moves back to the uppermost indexed position, reducing the total pump pressure. The force acts as an expansion pressure in the working region 43 of the working cylinder 8 .

If the height is 270 to 320", the press safety valve 4 or the magnet device 31 will operate again. However, the magnet device 35 or its distribution valve 23 is now activated via the other starting no-load condition. , at the same time the reduced rotational moment in the braking phase 45 is reduced by a pressure corresponding to the cutoff position. cause a decline.

Since the first pressure release position is activated by the excitation of the first magnet 33, the pump pressure The filling pressure that deviates from is manipulated.

The press safety valve 4 or the magnet body 31 remains in the operating state during the press stroke of about 10 to 20'. However, the distribution valve 23 or its magnet body 23 moves back to the cutoff position and the filling pressure is The entire pump pressure is available for the working area 43 of the working cylinder 8.

When the pressure is about 270 to 3200, the press safety valve 4 or the magnet body 31 is activated again. But now the magnet body 35 or its distribution valve 23 is opened via another pressure relief start. and at the same time induce a decrease in pressure in accordance with the reduced rotational moment within the braking phase 45. wake up

In the case of approximately 340 to 350', the press stroke is such that the magnet body 31 returns to the pressure release position and is demagnetized. When the stone body 35 returns to the blocking position, the press safety valve 4 stops its activity. ends at

FIG. 4 shows the passage of various pressures in the working cylinder 8 over the press stroke time t. By line 47, the course of rotational moment) Mx in the camp ring is determined by dotted line 48; Furthermore, the course n of the rotational speed is plotted by a dash-dotted line 49. Actually soba It goes without saying that streamlined and rounded transitions can be obtained between various values. .

In the starting phase 41 in which a low pressure is created in the brake cylinder 8, the phase 41 is first The working pressure PA must be reached, e.g. sufficient pressure to connect the coupling. Spring resistance and static friction must be overcome before PK is realized. after that, Furthermore, using the accelerating pressure ΔPle, the pressure is reduced to the nominal pressure P, after the coupling engagement ends. The connection remains in the rotary motor until the specific press working pressure 43A begins with increased pressure. The cut-in pressure increases to a value of so-called cut-in pressure Pε which maintains the element MK. constant After pressure region 43B, the pressure shifts toward pressure reduction region 44, but within this region 44, The working oil is transferred to the brake cylinder 8 along with the braking range 45 reduced by the hydraulic back pressure P. The pressure due to the pressure reduction area 44 pushed out from the constant pressure area 43B flows out.

The rotational speed is gradually changed by the braking action of the braking pressure ΔpHr. the In this case, the braking moment M must be switched until the rotation speed completely returns to 0. I can car. Therefore, the filling pressure in the brake cylinder 8 avoids the collision of the curved bundle part. As a result, the pressure decreases to low and within range 45 valve 4.23 is again in the starting position.

In that case, the press rotation speed n starts from the engagement point of the coupling at the end of the starting phase 41. The maximum value reaches the end of the pressure increase area 42, and the working area 43A and the constant pressure area 4 It stays at this value for 3B. At the beginning of the pressure reduction range 44 it drops to a low pressure and the Toward the end of the release stroke, the braking range 45 decreases and quickly reaches zero at the starting position 46. to return. Gradual acceleration that rises or falls without interruption within a short period of time The starting phase is the same as when braking is applied after the press operation is completed. The impact of tearing and tearing is also avoided or significantly reduced. mentioned earlier Differences between conventional types of pressure control based on the technological level are shown by dotted lines in Figure 4. This is implied by the pressure course curve 50 drawn at .

The working process begins with the press ram stopping at the dead center above at the zero position, and then starting. Pressure compensation preselected in pressure limiting valve 27 with press safety valve in aspect 41.42 under the first magnet body of the distribution valve 23 that invites the pressure release pipe 15 through the first branch pipe 25 It begins with the descent stroke and excitation. In that case, the tank 19 has a shutoff valve 18 connected to the pipe 1. The load is released to the tank 1 via the distribution valve 23 to the spring side via the 4A and piping 22. Oil is supplied into the main feed pipe 3 through the check valve 53 or the pipe 14 as far as possible.

The throttle valve 21 causes oil to flow back into the pipe 14A, thereby blocking the shutoff valve. 18 is too early and prevents it from being closed again. At the same time, in this case the oil is in a high pressure phase. The pressure of the pump 2 and tank 19 flows together with the pressure of the pump 2 and the tank 19, and at that time, another throttle part There is no need to pass outside the entire valve 4. Coupling-brake coupling 6/7 pis The tongue rod 10 remains as it was before due to the pressure of the spring 9 at the braking position of the brake 6. It stopped. When the hydraulic pressure in the brake cylinder 5 becomes equal to the spring pressure Pv, the piston The pin 8 comes into contact with the coupling 7.

In this case, if the feed quantity is maximum (without the throttling action of reference number 3), the working cylinder The pressure inside 5 first rises to the spring pressure Pr according to the spring characteristics, and then further decreases. Due to the spring properties of the spring 7, the closing pressure of the coupling increases to PK. compression capacity Since the product is no longer needed, the pressure depends on the total supply capacity from pump 2 and tank 19. In addition, the closing pressure P of the coupling quickly acts as a cut-in pressure P, The pressure above K is increased to a preselected value by the pressure limiting valve 27. therefore attenuates with it #, 24 releases pressure on the spring side and excess pressure is released to tank 1, resulting in this station The pressure in the in-plane working cylinder 5 is again kept at a constant low pressure value. Play with it The acceleration of the drive shaft of the It is controlled by the differential pressure obtained from K. Therefore, this relatively small acceleration pressure Δ The same is true for the total pump pressure in a short period of time depending on pHm (from zero to Changes in the number of times up to the working speed with much less pressure shock occur on the shaft It turns out.

Then the working speed n in the press (not shown) is reached and the regulated signal By adjusting the transmitter 39, the magnet body 33 maladjustment occurs, causing the distribution valve 23 to return to the shutoff position, resulting in pressure No drop in pressure occurs, and the upper Maximum pressure from the directionally limited pump 2 will build up quickly. and This is because at that time, depending on the aspect ratio, the damping valve 24 also prevents the outflow toward the tank 1. This is because it closes. In this case, this changeover from low to high pressure is interrupted after the acceleration stroke. As a result, when the press stroke in the oil supply pipe 3 is 180°, it reaches the bottom dead center. Nominal pressure P in the working range of the previous press. is obtained, along with the required nominal force. This is because a rotational moment M, .

When the magnet body 33 is demagnetized, the cutoff valve 18 is also closed again depending on its aspect ratio. Ta As soon as the tank is filled, a connection to the line 3 via the throttle tube 52 takes place at the same time.

This is because the pressure compensation pipe 13 also communicates with the oil supply pipe 3 of the tank 19 via the valve 17. This is because it blocks the At the same time, oil flows from pump 2 via line I3.14.20. The latter flows toward the tank 19 through the throttle valve 54, so the latter flows to the nearest starting stroke. The tank is automatically refilled and the nominal pressure in the filler line 3 is immediately obtained. On the other hand, no pressure relief occurs via the distribution valve 23. The impact of the signal transmitter 39 is If you can get more on Reslam's next ascent (habo 270-320') ) The m-cuboid 35 is excited and the branch pipe 30 is depressurized. The tank can be switched in one direction. At the same time, the nominal pressures arranged before and after the damping valve 24 are Then open the pressure limiting valve 28, which is regulated to a value below the pressure P. In that case The impact point of the signal transmitter 39 and the excitation of the magnet 35 are set when the press ram is at the top dead center and at the starting position. It is set to be located at position O and is electrically adjusted. The pressure inside the pipe 26 decreases. As soon as the damping valve 24 opens on the spring side, it relieves the working cylinder 5 from pressure and its connection. As a result, the piston loft 10 receives the spring force of the camp ring 7 and is pushed backwards toward the brake 6. You will be disciplined.

This then works under spring pressure. However, through the pressure limiting valve 28, The brakes are not fixed because the carefully selected hydraulic backpressure is released. It stops due to shock attenuation.

In that case, the distribution valve 23 with the pressure gradient in the pulp 24.28 will cause the press safety valve 4 to As a result of being held upright via the throttle valve 52 from the supply of tanks 1 and 9 through The effective braking pressure ΔPlr corresponds to the pressure limiting valve 26 by subtracting the back pressure from the spring pressure Pr. Ru. The magnet body 26 of the press safety valve 4 and the magnet body 35 of the distribution valve 23 are turned off by pressing When the stroke is approximately 340 to 350°, it is carried out immediately before the excitation of the starting position O at top dead center. In order to However, no pressure is applied. Therefore, a reliable full-off action is guaranteed and the connection Due to the parallel connection of the pressure compensation system in the supply pipe, despite the damping during braking and The entire course will occur as rapidly as without damping.

hair tour code 3...Oil supply pipe 4...Press safety valve 5...Work cylinder 8...Working piston 9...Return spring 12...Sampling tube 13...Sampling tube 14...Sampling tube 15...Pressure release pipe 16...Pressure cutoff valve 20...Sampling tube 21... Throttle valve 22...Connecting pipe 23...4/3 distribution valve 24...Brake valve 25... branch pipe 26...branch pipe 27...Proportional pressure stage 28...Proportional pressure stage 31... Magnet adjustment device 32...Return spring 33・　・・　61 stones 8 cycles device 34...Return spring 35... Magnet adjustment device 36...Return spring 37...Electrical control system 38...control box 39...Signal transmitter 40...Press flywheel 41...Start phase 42...Starting phase 43...Work scope 44...Work scope 45...braking phase 46...Starting position 47...Pressure inside the working cylinder 8 48... Coupling moment 49... Press rotation speed 50...-Pressure progression curve 51...Check valve 52... Throttle valve PAbzw, Py... Working pressure to spring pressure PII... Extraction back pressure P,...Coupling closing pressure PE　・・・Cut-in pressure PN...Nominal pressure ΔP□・・・Acceleration pressure Δpar...braking pressure MK...Coupling rotational moment M2...Nominal moment n... Number of revolutions L...Time International search report 1), TltllQ<INIt+1ANNEX To T',: E:NTER)IAτl0NAL Se:ARCHREPORT 0NPahi ent document Publication Patant ElmL Ly Publication sitecl in 5earch date rnernber(s) date

Claims (1)

[Claims] 1. (a) Press safety valve (4) in the oil supply pipe (3) pouring into the operating sill (5) ) and a distributing valve (23) that adjusts the breather or cutoff position are connected to the partial pressure and the main pressure. Hydraulic actuation of the press drive shaft that cooperates in the shock damping direction by a combination of force phases (b) in the coupling and/or brake pressure control device; The distribution valve (23) is externally adjusted in the pressure relief pipe (15) facing away from the oil supply pipe (3). located downstream behind the pressure control or proportional pressure stage (27, 28), (c) The distribution valve (23) together with the press safety valve (4) is connected to the magnet final control element (31, 33, 35) are fitted together, and these can be used as the press rotation angle indicator, remote position indicator or through the electronic program controller (37, 38) connected to the timer (39). connected, (d) Electronic control device (37, 38) or magnet final control element (31, 33, 35) ) to increase (coupling) and decreasing (braking) the working pressure in the working shilling (5) There is an assigned frequency of pressure control proportional to the rotation speed to The device characterized in: 2. a) The distribution valve (23) is a four-way three-position distribution valve, and b) The press sides on both sides thereof. fittings (29, 30) are arranged in parallel branch pipes (25, 26) of the pressure relief pipe (15). c) the pressure limit or proportional pressure valve (27, 28) placed The diagonal coupling (22, 1) is adapted to the pressure via its own pressure compensating tube (22). Connect to the check valve (18) or tank (1) of the tank (19) to be automatically switched. 2. The device according to claim 1, wherein the device is 3. a) The check valve (18) is connected to the oil supply pipe (3) in front of the press safety valve (4) on the one hand. ) and on the other hand to the tank (19), b) whose connection is connected to the check valve ( 18) is closed under the differential pressure that exists when the distribution valve (23) is in the starting position. maintained in a 3. A device according to claim 2, characterized in that: 4. Check valve (17) inside which the tank (19) is connected to the oil supply pipe (3) Claim characterized in that the pressure is compensated by a pressure compensating pipe (13) in which The device according to item 2 or 3 of the scope. 5. Brake valve aligned with upstream pressure limiting stage (27, 28) in pressure relief pipe (15) (24) is equipped with a unique discharge switching device according to pressure. The device according to any one of items 1 to 4 of the claimed scope. 6. At the start of the press stroke from zero position 0, the press safety valve (4) is in the through-flow position. The distribution valve (23) is connected to the tank (1) via its first press side joint (29). ) is located at a discharge position in the direction of The device described in 1. 7. In addition, in the case of a press safety valve (4) with a flow-through position, from the zero position 0 to approximately 10-2 The discharge position of the distribution valve (23) via the first joint (29) in the range of 0° is again shut off. 7. A device according to claim 6, characterized in that: 8. In addition, in the case of a press safety valve (4) with a flow-through position, from the zero position 0 to about 270~ The distribution valve (23) is connected to the tap via its second press side joint (30) in a range of 320°. Claim 6 or 7, characterized in that the discharge position is located in the direction of the tank. The device described in 1. 9. Press safety device (4) releases pressure in the range of approximately 340° to 350° from zero position 0. Claim 1, characterized in that the distribution valve (23) is in the cutoff position and the distribution valve (23) is in the cutoff position. The device according to any one of items 6 to 8.