DE3200180A1 - Coke quenching car - Google Patents

Abstract

The invention relates to a coke quenching car with a compressed-air generator controlled by pressure prevailing in a compressed-air reservoir for supplying an airbrake and with a pressurised-fluid generator, from which the drain flap drives are supplied; in this arrangement it is provided that, with the drain flap drives (7.1-7.4) locked, the pressurised-fluid generator (1, 2) is used to act upon a working piston in a double-acting cylinder (35), the said working piston forming, together with a piston (32) of larger piston area in a compressed-air cylinder (31) serving as a compressed-air generator, a linear actuator (30) (circuit diagram). <IMAGE>

Description

The invention relates to a coke extinguishing car with the

Features of the preamble of claim 1.

Such a Kokalöschwagen stands with meaningful emptying flaps in front of the Furnace opening from which glowing coke is ejected. The fire truck is often used here in front of the furnace opening, to ensure an even distribution of the Reach coke on the wagon zil.

That sets daq. Release the brake shoes with the help of the brake cylinder advance, which are acted upon from the compressed air tank. After emptying In the furnace chamber, the loaded fire-fighting vehicle moves at increased speed to the extinguishing area, where it is slowed down. After the glowing coke has been extinguished the car then to the coke drop ramp. There the emptying flaps are opened. The hydraulic emptying flap actuation generally allows for a simplification the emptying flap drive and its remote control. According to recent developments hydraulic emptying flap drives can also be used in a simple and effective manner Way against unintentional opening of the emptying flaps as a result of in the opening direction acting K] appnbeiastungen and / or breakage of connecting lines or hoses to back up.

The invention is based on a previously known coke extinguishing car of the introduction The mode of operation of the compressed air generation system has proven to be disadvantageous here exposed. It uses a conventional type of compressor to generate compressed air. Such machines cause considerable noise during operation. In the operation of coking plants this turns out to be a serious disadvantage, because the communication on the stove batteries in many operating phases, it is still inevitable that it must be done by acclamation. In addition, the compressor jumps according to the respective Pressure drop in the compressed air tank also often occurs during the extinguishing process. Then in the compressor draws in air and vapors as well as air that is heavily laden with dust. That leads to significant damage because of the. Type of compressor the Can not protect suction chambers with the usual measures against this.

The invention is based on the object of a coke extinguisher of the type described to train its compressed air generator so that it is against Impairments of a harmful atmosphere, such as those in the extinguishing tower in particular. prevails, can be better protected and its operation with less noise the environment is connected, which also ensures with less effort shall be.

According to the invention, this object is achieved by the characterizing part of the claim 1 solved. Appropriate further developments of the invention are set out in the subclaims reproduced.

According to the invention, the compressor is by the thrust piston gear formed hydraulic converter replaced.

This gets its energy from the hydraulic fluid generation in the fire engine, whereby the technical effort is significantly reduced. In the hydraulic system but the converter is arranged downstream of the damper drives by on the one hand by a corresponding dependency circuit ensures that the converter is only in operation can be taken when the flaps are in their open or closed position stand and by on the other hand the compressed air supply in the compressed air tank so adjusts the compressed air requirement of the brakes so that it is sufficient to cope with the flap actuation enable the brakes to operate. Such a pressure transducer is substantial smaller than the usual compressors and can therefore be easily operated with a maintenance unit provide which of the air intake is connected upstream and the soiling prevents as well as indicating faults, if applicable. This type of converter is also based on this the possibility of the noise development during the generation of compressed air is decisive to belittle.

According to the invention, the dependency circuit described is preferably formed hydraulically. For this purpose, the feature of claims 2 is provided. That among other things used 4/3-way valve can also act on the hydraulic part of the Automatically control the thrust piston gear, which is the subject of claim 3.

Further details of the invention emerge from the following Description of an embodiment using the attached circuit diagram.

After that, the first and most central for all damper drives is on remote point from these arranged aggregate seen before, to which an oil tank c belongs, on which a radial piston pump is arranged, which is designated by the M Electric motor is driven. This has, for example, an output of 11 kW at 1,500 rpm. The electric motor is switched on and off with a non reproduced operating switch, which is operated, for example, with push buttons can be used for the operating position "emptying flaps and" emptying flaps to "are provided. If the push buttons are not pressed, the motor M stops.

The unit described also has a hydraulically pilot operated Drain valve 4-, which secures the unit a against pressure peaks and normally closed is. In the return line i.qt leading to the TP.nk; a filter installed, which can be bypassed with a by-pass, in which a non-return valve is built in. This device is generally designated by 3. Furthermore, the Unit a 5n the tank c built-in heating element 11, which ensures that the Working fluid is always kept at the starting temperature; the heating element will.

controlled automatically with a thermostat.

Furthermore, the working fluid level is determined with the help of two. Switch contacts 17 monitored. This system can be controlled with the help of a visual display on the oil tank check.

According to the illustrated embodiment, in addition to the main pressure generator 1, an auxiliary pressure generator 2 is provided, which is set up for manual operation. Included it is a hand pump, but it can only be operated when the 4/3-way valve 5 is switched to manual emergency operation.

The following first describes the details of the valve drive explained in more detail based on the various operating positions: Open the emptying flaps First, the directional control valve 5 must electrically open with the aid of the aforementioned push buttons control side B can be switched. Then comes from the hydraulic pressure generator 1 for each of the hydraulic working cylinders labeled 8.1, 8.2, 8.3 and 8.t Hydraulic fluid in the Pilot control of the drain valves 7.1, 7.2, 7.3 and 7.4.

This ensures safe and simultaneous opening of the drain valves thereby guaranteed. that the oil tank in the A working line is at the specified pressure, e.g. 35 bar is applied to another drain valve. If the pressure continues to rise, the drain valve 7.1 are consequently open. The increasing pressure the working fluid leads to overcoming the hydraulically piloted drain valve 9 and a check valve 21, so that the respective piston area in the working cylinder 8.1 - 8.4 the damper drives are loaded. Because di: e limited by the piston ring surfaces Working rooms with the open drain valves 7.1 - 7.4 switched to return the piston rods move while maintaining a constant counter pressure from the working cylinders.

This will result in the liquid column in the A line being torn off prevented when opening the emptying flaps.

For this purpose, according to the exemplary embodiment, the return valves 7.1 - 7.4 can be set to a pilot pressure of approx. 35 bar. The speed the piston in the working cylinder therefore only depends on the delivery volume of the pump away. As a result, a. Adjustment of the i.m pressure generator 1 existing Pump or through a speed control on the drive motor M, the speed of the Pistons and thus the opening movement of the flaps are controlled The pressure regulation is done by the pressure regulator of the pump.

Not shown] .gte mechanical stops on the working cylinders 8.1 - 8.4 limit the piston stroke.

With 9 and 10 the main parts of a hydraulic arrangement are referred to, which the pistons in extended Hydraulic position of the piston rod locked. For the sake of simplicity, this hydraulic piston lock is only drawn once, although it is present in every line leading to the piston area of the working cylinder in question 8.1 - 8.4 leads. Will the piston by load of the emptying flaps concerned with the piston rod on the one in the piston area of the working cylinder in question pressed working fluid, so prevented the normally closed and hydraulically piloted valve from the B line 9 any outflow of working fluid from the designated space of the working cylinder.

Closing the emptying flaps Closing the emptying flaps takes place with the help of an electrical control signal for the pilot operated directional control valve 5 and for starting the motor M of the hydraulic main pressure generator.

The directional control valve 5 is thus switched to control side A. Through this pressure medium can reach the piston ring spaces. First the pressure medium flows via by-pass lines 15.1 - 15.4 to the drain valves 7.1 - 7.4 under opening a self-closing valve 16.1-16.4.

The second control line 18.1 - 18.4 remains unaffected at this pressure, so that the drain valves 7.1 - 7.4 remain closed. At the same time, the Pilot line 19 the pump pressure for opening the pilot operated working valve 9 used. Since that in the drain. direction closing check valve 21 in the by-pass 20 from the one from the piston area of the working cylinder in question 8.1 - 8.4 cannot be opened, the pressure medium flows out of this working space Via a throttle 10, this maintains the desired counter pressure. This counter pressure P 2 is then present in the by-pass 22 of the pressure switch and is with the check valve 23 which closes against the direction of flow is maintained.

The speed of the piston is therefore regulated via the Throttle 10. The pressure regulation is done by the pressure regulator on the pump.

The stroke limit of the piston when retracting the piston rod is formed by a mechanical stop on the cylinders 8.1 - 8.4. Once the Piston has reached the end position, the directional control valve 5 is in the neutral position brought back, a control signal stops the motor M and a corresponding one Signal can operate a visual indicator showing the closed position of the flaps indicates. The control signals can be set automatically with the aid of a limit switch give. After the pressure drop 1 which now occurs, remain in the connecting lines the flow valves 7.1 - 7.4 closed. Those in the direction of discharge in the by-pass lines 15.1 - 15.4 closing check valves 16.1 - 16.4 are closed so that no pressure medium can escape from the annular spaces of the working cylinders 8.1 - 8.4. As a result, the pistons are locked hydraulically.

The switching of the directional valve 5 is equivalent to a break in a connecting line between the aggregate described and those from the organs 9, 10 and 20 and 21st existing hydraulic locks or those from organs 7.1 - 7.4 or 15.1 - 15.4 and 16.1 - 16.4 existing hydraulic locks that are attached to each Working cylinder 8.1 - 8.4 are arranged.

In these skins, the pistons are therefore automatically in the working cylinders locked.

The drain valves 7.1 - 7.4, which in the non-activated state over the line 17 are closed, are on the leading to the piston ring spaces Control lines 18.1 - 18.4 open at a predetermined maximum pressure. This can be approx. 35 bar in the exemplary embodiment. That would counter the working cylinder Secure overloads with loads of more than 9 t.

The hydraulic arrangements, generally denoted by d and e bp are located directly on the working cylinders 8.1 - 8.4, so that line breaks between the work areas concerned and the hydraulic locks can occur.

Operation of compressed air generation The one for the compressed air brake of the fire engine The required compressed air is generated with a thrust piston gear 30.

It has a single-acting compressed air cylinder 31 with a piston 32 on a piston rod 33 with a smaller cross-section Piston 34 is arranged. The piston 34 works in a double with pressure fluid loadable cylinder 35. The transmission ratio amounts to 1:10. The air cylinder 31 is flanged in front of the cylinder 35 40/28 x 300 stroke. The thrust piston gear 30 is housed in the fire engine.

If a pressure of e.g. 6 har fallen below, the pressure switch 15, which each has a contact for minimum and maximum has in cylinder 35 in the pressure fluid flow in which the 4/3-way valve 5.1 is brought into switching position A. Then the change of direction takes place of the 4/3-way valve 9.1 with the help of a time relay that sets a switching time of e.g. 1.5 sec. The piston 34 in the cylinder 35 therefore performs pure reciprocating motion and drives the piston 32 until the maximum pressure in the container 14 of e.g. 8 cash is due again. Then the pressure switch 15 switches the 4/3-way valve 5.1 i.n. its neutral position.

The pressure switch is of course also usually on the compressed air tank provided safety valves, so that a. excessive pressure on everyone Case is excluded.

On the hydraulic side, the safety is ensured by the valves 10.1 and 10.2 increased. these are switched in such a way that an overpressure in the compressed air tank is excluded will.

This results in a threefold security.

If in the hydraulic system the working cylinders 7.1 - 7.4 for the Flap actuation to "open" or "closed" via the directional control valve 5 falls the pressure in the baffle line P 1 decreases accordingly, so that when the 4/3-way valve 5.1 on the throttles arranged behind the directional valve a sufficient pressure to actuate the piston 34 in the cylinder 35 can. The throttles q are in turn provided with by-pass lines in which pressure relief valves are arranged, which allow the discharge of the pressure medium from the Zyl.indr 35. The safety valves 10.1 and 1n.2 are in turn arranged in by-pass lines, which the working lines A and B directly with; the tank line T 1.

The invention has the significant advantage that in the event of a failure. of the electrical network, possibly even after a repair in the case of an exposed Fire-fighting train - alo without connection to the electrical network, for example a contact wire - two of the hydraulic accumulators are pumped up by means of a hand pump or only by actuating them the ground pump and simultaneous pressing of the emergency manual override on the directional control valve 5.1 the brakes of the locomotive including the fire engine can be released.

When the piston 32 rotates back, compressed air is overwinding the Pressure relief valve 12.4 by the maintenance unit indicated at 13, which mainly contains a filter system, sucked in. The air behind the piston 32 is pressed into the pressure vessel 14 while overcoming the pressure relief valve 12.1. That The non-return valve 12.3 prevents the suction of air from the pressure vessel 14, while the check valve 12.2 excludes the backflow of air through the filter 13.

In the opposite direction, however, overcomes that in cylinder 31 compressed air the check valve 12.3 and gets in this way in the Compressed air tank 14, while fresh air over the maintenance unit 13 under overcoming of the pressure relief valve 12.2 in the space behind the piston 32 sucked will.

A blockage of the filter in the maintenance unit 13 can e.g. an acoustic signal can be displayed electrically.

Claims (3)

P a t e n t a n s p r ü c h e 1.) Coke fire truck with one of in a compressed air tank for the application of a compressed air brake prevailing pressure-controlled compressed air generator and a hydraulic fluid generator, including the the emptying flap drives are acted upon, so d u r c h e k e n n z E i c h e t that with the hydraulic fluid generator (1, 2) when the drain cap drives are blocked (7.1 - 7.4) a working piston (34) can be acted upon in a double-acting cylinder (35) is, the one with a piston (32) larger piston area in a compressed air generator serving compressed air cylinder (31) forms a thrust piston gear (30). 2.) coke extinguishing car according to claim 1, d a d u r c h g e k e n n z e i c h n e t that in a parallel branch (P1 T1) that of the emptying flap drives (7.1 - 7.4) leading working fluid lines (P T) a 4/3-way valve (5.1) and in the continuing to the hydraulic cylinder (35) of the piston mechanism (30) Working fluid lines (A 1 B 1) throttles (9) are installed. 3.) coke extinguishing car according to one of claims 1 or ', d a d u r e h g e k e n n z e i. c h n e t that for pressure limitation in the hydraulic fluid generator a pressure switch (15), a safety valve in the compressed air tank (14) and on the hydraulic side a safety valve (10.1, 10.2) in each working fluid line (A 1. B 1) is mounted in by-pass lines leading to the tank line (C).