DE10024930A1 - Method and device for compressing moldings z. B. Foundry molding sand - Google Patents

Abstract

The invention relates to a method and a device for compacting molding materials (eg foundry molding sand) within a closed molding chamber 10. The compacting is carried out by the kinetic energy of an extremely high, up to 800 m / sec , which can optionally be supplemented by a synchronously running compressed air pulse and / or by a fluidization air flow (30.2 / 77/51) which is continuously connected upstream of the compression process. The pneumatically driven press rams 27.1 are arranged in a cylinder block 26.1 and each individual press ram 27.1 is accelerated by a compressed air jet of a Laval nozzle 25.1 located in the supersonic area, like a projectile or free-flight body. The Laval nozzles 25.1 are arranged in a base plate 20.2, which is located directly between the cylinder block 26.1 and a compressed air tank 19 / 20.1. The compressed air pulse is also triggered by Laval nozzles arranged in the base plate 20.2 and conducted into the molding chamber 10 via the channels 26.3 (FIG. 06) lying between the press ram cylinders 26.2 (FIG. 06). The multi-ram press pulse and the compressed air pulse are controlled by a valve tappet system 23.1 and 24.1 releasing the Laval nozzles so that there is a synchronous compression effect of the multi-ram press pulse and the compressed air pulse. The multi-stamp press pulse is due to its higher than the compressed air pulse ...

Description

The invention relates to a method and an apparatus for Compression of molding materials e.g. B. Foundry sand within egg ner closed molding chamber, the molding material through a Compressed air blast and compressed by mechanical pressing. The mold chamber is from the model plate surface, the Mold box and filler frame inner walls and the bottom of the Compression unit enclosed.

When it comes to compacting molding materials for foundry molds, there are a variety of influencing factors that affect the compression result and thus also affect the casting quality. It Therefore, flexible molding processes are particularly important take this diversity of influencing factors into account and correspond can be adapted accordingly. A special meaning have combined compression processes with stepless Transitions between the individual process steps.

It is particularly important for difficult models or shapes interpretation that the compression process and the flow state, in which the molding material be during the compression process takes place until the final compaction is reached without an undersize maintenance is maintained. Experience shows that with egg nem gradual compression process in which thus also the flow state of the molding material is interrupted Chen is the pre-compressed molding material from the previous one No compression level in a further compression level can be brought into an optimal flow state and that even depending on the model situation a flow in places was no longer possible. The consequence is that it is in the corresponding parts of the mold with low pre-compression remains, which also includes those that are frequently encountered in practice lower dimensional strength in certain parts of the mold u. a. to are to explain.

In the known single-stage air pulse compression process ren, which runs in the range of about 20 milliseconds, It is in the nature of things that the compression process runs without interruption until the final compaction. With the be knew mechanical presses by means of a press plate or many other things pelpresse, which runs in the range of about 3 seconds, can a short interruption of the press stroke movement or  the compressive force effect the flow state of the molding material under break and lead to corresponding disadvantages. With the be knew combined or multi-stage compression processes (such as DE 29 30 874, DE 37 40 185, EP 0 650 788 or EP 0 673 698), in which first a pre-compression and then post-compaction is inevitable fig that when moving from one process to another, e.g. B. from airflow to mechanical presses or from Luftim pulse for mechanical pressing, the flow state of the molding material fes is interrupted with the adverse effects. in the others have the known mechanical pressing devices such as press plate or multi-punch press the disadvantage that they only very limited to higher speed values can be inclined. On the one hand, this is due to the high weight ten or in the resulting high inertia of the moving parts of the pressing device. On the other hand would cause uneconomically high flow rates in hydraulics with appropriate dimensioning of the valves and piping gene required, with a high acceleration of the large hydraulic oil masses is problematic. It is therefore with these known systems not possible a quickly ablau air pulse with a much slower decay fenden mechanical press to synchronize so that a stepless compression transition is created in which the initiated flow state of the molding material without interruption until approximately the final compression is maintained.

The object of the invention is to avoid the previously be written disadvantages and under the collective term "multi- Airpress system "a flexible and multifunctional compression to create system, with which different compression comp drive individually or in combination with each other can be applied according to the model requirements and where with through targeted selection of compression methods or de combinations, especially in critical models improved molding compression can be achieved.

This object is achieved in that the molding material is compressed by the kinetic energy of an extremely high, up to 800 m / sec ² accelerated multi-die pressing pulse, in addition to the multi-die pressing pulse also a parallel compressed air pulse on the molding material Influence can be brought and the molding compression by a coordinated synchronization between the multi-plunger pressing pulse and the compressed air pulse he follows and the flow state of the molding material once initiated without interruption until the final compression is maintained. Furthermore, this compression method can also be preceded by an airflow method known from EP-0 995 522 and used in various variants, which fluidizes and homogenizes the molding material without recognizable pre-compression and which is followed by the combination of multi-stamp compression pulse and compressed air pulse in a continuous transition. Depending on the model-specific requirements, it is in principle also possible to carry out the compression of the molding material only with the multi-plunger pressing pulse or only with the compressed air pulse or with the multi-plunger pressing pulse and upstream air flow or with compressed air pulse and upstream air flow, whereby the once-introduced flow state of the Molding material is maintained without interruption until the final compression.

According to the invention, the multi-stamp press pulse occurs by that the individual, in cylinder and piston rod bores smoothly guided ram through the kinetic energy gie of a compressed air-powered and abruptly deployed Jet like a projectile or like a free-flying piston ex be accelerated extremely high, with each ram one own nozzle is assigned. Particularly advantageous for the generation A jet jet is a Laval nozzle because here with an optimal implementation of potential printing energy in kinetic energy is made possible. The acceleration of the Press ram can also by a sudden Druckbeauf impact of the plunger by means of an abrupt opening large-area drilling. The compression of molding material follows through the kinetic energy of the individual press stamps in a rectangular grid within a Cylinder block, lying close together and covering the whole area are arranged above the molding surface. With the final ver sealing of the molding material, the ram finally come to a standstill, which results in a smooth transition from the Pulse compression for static pressing with the pressure of the Compressed air tank or storage tank. The Press rams are preferably designed as hollow bodies and they have only a low weight or only a ge rings to accelerate mass, creating a much higher Acceleration is made possible and thus the maximum kine table energy compared to a full body in a very short time What is achieved in terms of synchronization of Multi-stamp press pulse and compressed air pulse is important.

The multi-stamp press pulse, especially in combination with egg nem compressed air pulse and also with a pre switched airflow allows a much improved homogeneous compression, especially with critical models. in the further causes the multi-stamp press pulse that in the end phase continuously and continuously in the state of stati presses, improved durability or load-bearing capacity of the mold within the mold box, which be especially with large molding box dimensions with regard to the Mold box transport within the molding system is important is. As is well known, only air pulse compressed shapes are used Back of the mold a strongly decreasing compression on where due to the carrying capacity of the form for large ones Mold box dimensions is no longer guaranteed. Form is therefore in such cases by mechanical re-pressing additionally solidified what the multi-stamp Press pulse in addition to its actual function of an improvement additional compression of critical models.

The effect of compression molding through a lot stamp press pulse in combination with a compressed air pulse is that both together a highly accelerated Ver  form sealing front on the molding surface, which un indirectly transferred to the molding material. The molding material is there at the same time and together with the compression front high accelerated and together with the press rams in state ho kinetic energy. The towards the model plate accelerated molding materials are from the rigid and un compliant model plate abruptly move on changed and braked, whereby the molding material is compressed. There the mass of the loose molding material from the mass of the individual Grains of sand exist, takes up the compacting effective mass of the Molding material and thus the compression-effective kinetic En ergie upwards and it is on the surface of the lo sen molding material almost zero. With the pure compressed air pulse As is well known, compression without repressing leads to the fact that the upper mold back layer remains undensified and up to useful compressed layers must be cut off. At the compression method according to the invention by the lot stamp press pulse in combination with a compressed air pulse, compensate for the rams that are used during compaction are constantly in contact with the surface of the molding material, with their solid mass and with their corresponding kineti energy, the previously described impact of the upward decreasing molding material mass. In theory, you could the feed stamp also as the last layer of grains of sand consider larger mass, with a common compressed air in pulse acts on the molding material and on the ram. How the multi-stamp press pulse has already been described finally infinitely and continuously in the state of static pressing over.

The press feet are circular, so that on one manoeuvrable anti-twist device, as used in the well-known Vierecki gene press feet is required, can be dispensed with. In order to the diagonal, lying between the circular press feet Molded areas also covered by compression ram the lower surfaces of the press feet are in accordance with the invention conical. This means that even with plane-parallel ones Compression cones arising in the molding material we considerably enlarged, so that even at a shallow depth an even compaction layer on the surface of the molding material arises. Furthermore, the diagonally between the circular press feet existing open areas the through course of the compressed air pulse, which is described below becomes.

The cylinder block for the press ram, in which the Through channels for the compressed air pulse are invented appropriately directly under the base plate of the compressed air arranged in which the compressed air for the multi-stamp Press pulse and for the compressed air pulse is stored. In The nozzles are located on the base plate of the compressed air tank for the individual press rams and for the compressed air pulse, see above that the potential compressed air energy in the immediate vicinity of the Press ram piston is present. The nozzles for the ram can via a valve system, which is within the pressure air tank, suddenly and simultaneously opened be, so that all ram simultaneously and abruptly  be charged with the same energy. This initially leads to a simultaneous start and for synchronous or synchronous running al Press stamp. The individual braking of the press rams is then carried out by the compression of the molding material among the individual NEN ram, depending on the respective mo dent-dependent height of the sand column, which is before compaction beginning between the presser foot and the model part. Through the large number of press rams (multiple ram system) by adapting the compression strokes to the model contour uniform compression even with strongly deviating Mo. dent contours reached.

Instead of opening the nozzles at the same time and thus simultaneous start of all press rams, but with special which advantage also possible, the press ram partially individually or start in groups at different times by the corresponding nozzles or openings suddenly but with a time lag. Since it is the multi-stamp press pulse by a very fast running Acting act, the time offset is of course in the range of fractions of a second. The delayed opening leads to egg synchronous advance of the press start started first pel, which means, for example, that through deeper model parts due to longer compression strokes almost simultaneously with the model-based shorter compression strokes the final compression reach. The starting sequence of the pressing system can be advantageous pel also be carried out so that the outer Press stamp and then increasingly the inner press stamped be what in relation to the material friction on the Formka stenrand advantageously to a bell-shaped lifting front the ram guides. Furthermore, the outer Pressstem pel also with egg due to the friction of the molding material on the edge of the molding box higher kinetic energy can be applied by the Nozzles or openings for the outer ram with one larger cross section. By the same En Energy supply to the corresponding ram of a group the synchronism or synchronous operation also remains within this Press group received.

According to the piston and piston rod seals the ram preferably as activatable seals performed, which significantly reduces the friction and ultimately resulting in a much higher acceleration and acceleration reaction of the ram is made possible. The seals are each pressurized of the room to be sealed and activated against the seal pressed. When not activated, they pull out Seals by their elasticity back from the sealing surface, so that there is no contact between the sealing surface and the seal stands. This state is before triggering the multi-stamp pre ßimpulses brought about by the in the piston rod side Space for lifting and holding up the ram Pressure to atmospheric pressure or to a certain Un ter pressure is reduced. Piston and piston rod of the press pel are therefore pressure-free on all sides, so that the seals are can withdraw from the sealing surfaces and only one smooth guidance over low-friction, non-metallic and  there is highly wear-resistant guide bands. The leadership banks which prevent a metallic touch of the sliding Parts. With the impact of the at supersonic speed nozzle jet emerging from a Laval nozzle onto the piston of the press ram can be extremely high be nigt, each press ram to its own Laval nozzle is ordered. Because the ram through the kinetic energy of the individual jet streams is an ab Seal the ram piston during exposure to the jet not mandatory. Only after the ram through their kinetic energy have compressed the molding material and Coming to a standstill arises via the ram piston Pressure built up from the air chamber. This Pressure activates the upper piston seal, with which a stepless This transition to static pressing takes place. To connect The piston on the piston side is raised by the press ram vented and the piston rod side cylinder chamber with Pressure applied. This pulls the upper piston out back and the lower piston seal and the piston rod gene seal are activated so that the piston rod side Space for lifting is sealed.

As previously described, the cylinder block is for the Press ram directly under the base plate of the compressed air arranged in which the compressed air for the most pel press pulse and for the compressed air pulse is stored. The plungers in the cylinder block are at right angles lattice grid and covering the entire surface of the molding material distributed. Furthermore, there are diagonal between the Press stamping also in a right-angled grid duct channels for the compressed air pulse covering the entire area Molded surface arranged distributed. In the base plate of the compressed air tank are the nozzles for the press stamp and for the compressed air pulse. The nozzles for the press stamps open directly into the cylinder rooms of the press system pel. The nozzles for the compressed air pulse open directly into the through channels of the cylinder block, the through bridges the distance of the cylinder block height and open directly into the molding chamber. The nozzles for the Compressed air pulses are preferably designed as Laval nozzles so that the air jet at supersonic speed from the Nozzle emerges and flows through the through-channel and closes Lich reaches the molding chamber as a compression pulse. By the variety of nozzles and passageways in one right-angled grid between the rams close together lying flat and covering the entire surface of the molding material are ordered and by the distribution effect of the tapered Press feet as well as that under the through channels for a front Diamond tubes arranged in the air flow form in the shape chamber an even and acting on the molding material the pressure wave compressing the molding material. Because the blast wave too acts on the top of the tapered press feet the press rams next to the radiance on their pistons an additional acceleration force.

It takes more time to build up the multi-stamp press pulse than to build up the compressed air pulse. While after the sudden opening of the nozzles during the compressed air pulse, a compression-effective pressure wave forms over the surface of the molding material within approx. 10 milliseconds, the press rams must first overcome their static friction and their inertia before they reach a compression-effective kinetic energy. If the nozzles for the compressed air pulse and for the multi-stamp press pulse were opened simultaneously, this would result in an asynchronous effect of the compressed air pulse and multi-stamp press pulse, the flow state of the molding material being interrupted with the disadvantages described at the beginning. In order to avoid this and to achieve a synchronous compression effect of the compressed air pulse and the multi-stamp press pulse, the press stamp nozzles according to the invention are opened earlier than the nozzles for the compressed air pulse. Since the multi-stamp press pulse follows with acceleration values of up to 800 m / sec ² , this time offset is of course in the range of fractions of a second. An advantage of achieving such high acceleration values is in particular the low mass of the press rams designed as hollow bodies, the lack of friction in the seals (activatable seals), the smooth operation of the press rams with low-friction guide bands and the pressure-relieved cylinder spaces of the press rams in conjunction with a low vacuum in the piston rod side space of the press ram. By relieving the pressure in the cylinder spaces and by applying a small negative pressure in the cylinder chamber on the piston rod side, which occurs before the accelerating nozzle jet is triggered, the plungers are released from their upper starting position and from their static friction by their weight and by the negative pressure effect, so that the The ram is already in the state of sliding friction when the jet is triggered, which also contributes significantly to the achievement of a rapid acceleration response and high acceleration values. With their low weight and / or their low mass, a large number of existing press rams, which are distributed across the entire surface of the molding material in a right-angled grid, only make highly dynamic compression pulse compression possible. By dividing into many individual light press rams, the total mass to be accelerated is broken down into many small mass units, making the highly dynamic compression pulse compression easily manageable, which is not possible at the beginning as described in the prior art due to large mass units to be accelerated.

As already stated, the nozzles are for the lot stamp press pulse and for the compressed air pulse in the ground plate of the compressed air tank, under which also the Cylinder block for the press ram is arranged. The nozzles length corresponds to the base plate thickness, so that the po potential compressed air energy over the distance of the nozzle length un indirectly and without loss of flow in front of the press cylinder ben is ready. This allows the ram to open of the nozzles react without delay. The opening and closing The nozzles are made via valve lifters, which are within the pressure air container are arranged. The valve lifters are made by the pressure on your nozzles in the compressed air tank seat pressed and thereby kept closed. For you kung multi-stamp press pulse and compressed air pulse  the nozzles have to be opened suddenly. From Be The first interpretation is therefore that only a very short valve fault stroke of a quarter of a nozzle inlet diameter (d / 4) is required to have a throttle-free passage cross section to release at the nozzle inlet. The valve lifters are on one central lifting frame attached to the opening of the nozzles is suddenly raised, the throttle-free passage cross section of a nozzle (d / 4) in less than 7 milliseconds is released. The valve lifters have two designs tion forms, whereby for the multi-stamp press pulse ela Tically deformable valve lifters can be used relax when lifting the lifting frame and then with an already definite speed "in the flying Start "from the valve seat. The valve lifters for the pressure air impulses are attached to the lifting frame via drag pins, whereby they only after a certain lifting frame path and ent speaking delayed also with an already definite Lift the speed in "flying start" from the valve seat. Through an adjustment option according to the invention on the towing bolt The opening of the individual nozzles can be set individually be determined. In addition to the "flying start" effect can thus also the previously described time-delayed opening between the ram dies and the pressure pulse nozzles reali be used, which to avoid an asynchronous we Example of press ram pulse and compressed air pulse required is.

Instead of a central stroke operated by a lifting cylinder frame to which the valve lifters are attached, the Valve tappet for opening and closing the nozzles can also be carried out with individual drives, each individual valve lifters a lifting cylinder with integrated elec has solenoid valve. Here are made of an elastic sealing material (e.g. rubber) existing valve tappet di directly attached to the piston rod of the lifting cylinder. The ela The valve lifter is deformed by the locking force and it thus stores energy when lifting the valve lifter or is released by the springback when the nozzle is opened and which, in addition to the piston lifting force, the opening process supports. Furthermore, the valve tappet is released by the spring Only lifted off the valve seat when the piston has already been lifted reached a certain speed (flying start) has, which means the complete passage cross section of the nozzle is suddenly released in less than 7 milliseconds. The lifting cylinder has only a very short stroke feed, which results from the springback plus the opening stroke of a quarter of the nozzle inlet diameter (d / 4) results, which also leads to the sudden release of the complete Passage cross section of the nozzle contributes.

The individual drives of the valve lifters have in particular the Advantage that the opening of each nozzle depends on individual model-specific conditions can be voted. This is done by a corresponding time offset actuation of the directly in the cylinder head of the Ven Partial tappet cylinder integrated solenoid valves. Hereby can start with the already mentioned delayed start  realized between multi-stamp press pulse and compressed air pulse to ensure a synchronous compression effect of multi-stamp Press pulse and compressed air pulse to achieve. Furthermore, the start times depending on the respective model the press ram and / or the compressed air pulse nozzles free and be determined universally, for example different Compression strokes of the press rams due to different Compensate sand or model heights so that they are simultaneously reach the final compression, which is essential to a homogeneous and stress-free compression. The press Stamps with longer compression strokes will be used started earlier. Another exemplary application possibility is that by correspondingly different a bell-shaped lifting front of the press stamp and / or the compressed air pulse wave can be generated. The start time is due to the speed of the system differentiate in the range of fractions of a second, of course, what is easily mastered with modern control technology. It makes sense for the start times for each individual Valve tappets stored in model-related data sets, whereby the records are assigned to the model number. At a each model change will be the model number of the one being replaced Model by automatic reading or by manual on activated and the assigned data record is sent to the Transfer control, with which the individual start times the individual valve lifters for the model concerned automa table are activated.

It is also within the scope of the present invention that the single ram by the combustion pressure of an ignition capable gas / air or gasoline / air mixture the. Each press die is trained accordingly tied cylinder with piston and spark plug inside the cylinder assigned to the block. The function of the compressed air pulse with the nozzles and with the through-channels in the cylinder block remains unchanged. The ones already mentioned The starting times of the press cylinders are indicated by Realized timed control of the spark plugs.

In addition to the previously described pulse compression using Viel Stamp press pulse and / or compressed air pulse enables Device for performing these methods also a another compression process that does not take place in a pulsed manner, which only by switching the control program for example wise via a model-related data record or via a Selector switch can be activated. In this invention The first compression process is compressed air from below via the slot nozzles of the model plate against the Schwer blown into the molding chamber by force of the molding material until the Pressure in the molding chamber is equal to the pressure in the compressed air tank is. The blowing is done with a flat pressure gradient from approx. 2 to 4 bar around the loosely poured molding material not to raise. The mold chamber is closed during the blowing cordoned off in the free atmosphere so that a pressure build-up is possible is. The nozzles in the base plate are also during the Blowing closed by the valve lifters. A Verdich The molding material cannot take place because  between the loose molding surface and the mold chamber ceiling there is still a free space so that the molding material follows cannot support above. The mold chamber and the air pores in the Molding material is only in a state higher at brought atmospheric pressure, which pressure is equal to There is pressure in the compressed air tank. During blowing also the piston rod-side spaces of the press cylinder on the brought its pressure value. Now that these pressure values in the Molding chamber and in the piston rod-side rooms of the Preßzy The nozzles in the base plate of the Compressed air tank opened by lifting the valve tappet, which created a connection between the compressed air tank and the mold mer as well as between compressed air tank and ram piston will be produced. Because in this state pressure on all sides there is no movement. Only the press stamps can advantageously with their low egg Place the counterweight on the loose surface of the molding material. The Ver sealing process is now initiated by the space under the model plate and the piston rod side spaces of the Press cylinders to the free atmosphere or to a negative pressure relieved source. This creates an over the Mo dell plate nozzles flowing and from the compressed air tank fed compression air flow with simultaneous feeding the press ram towards the model plate. By starting heavily reduced relief of the space under the model plate, a fluidization stream can be initiated first the one by lifting the throttling of the compression air flow with the feeding press cylinder follows. The Air flow and the ram movement is within approx. 2 to 3 seconds due to increasing compression rare, with a smooth transition to static pressing created by the press ram. At the transition to static Pressing condition, the nozzles in the base plate are ver again closed and then the molding chamber is set to atmospheric Relieved of pressure. By relieving the mold chamber, the static pressing force increased further, because there is no mold chamber side low back pressure acts more on piston rod surfaces. A white tere increase in the pressing force is still possible in that the Press cylinder parallel to the mold chamber relief with the higher one Pressure of the compressed air network. After completion this compression process the ram in again moved back to their upper starting position.

The compression method described above has the Advantage that the Druckge triggering the compression air flow falls directly on the model surface and thus the compression airflow and the compression on the model surface begins and then builds upwards, the subsequent ram pressing the compression process support effectively. The formation of a compression front in the upper layer of molding material, as is the case with impulse compression device or occurs during mechanical compression largely avoided here. The side pressure on the form box wall and thus also the molding material friction on the Formka This significantly reduces the side wall. In the further has this compression process has the advantage that the un pressure build-up in the molding chamber at no preliminary stage seal leads and the flow state of the molding material during  the compression phase as in the other described Ver driving is not interrupted.

The multifunctional compression system according to the invention enables the use of various compression variants, which are summarized again as follows, according to the preceding description, depending on the model requirements:

• 1. 1.) Multi-stamp press pulse alone
• 2. 2.) Compressed air pulse alone
• 3. 3.) Multi-stamp press pulse together with compressed air pulse
• 4. 4.) Multi-stamp press pulse with upstream fluidisie air flow according to EP-0 995 522
• 5. 5.) Compressed air pulse with upstream fluidizing Airflow according to EP-0 995 522
• 6. 6.) Multi-stamp press pulse together with compressed air pulse and with an upstream fluidizing air flow according to EP-0 995 522
• 7. 7.) Compression air flow with subsequent ram without pre-fluidizing
• 8. 8.) Compression air flow with downstream press rams and with pre-fluidizing.

The compression variants 1, 2 and 3 can be with or without Mo dell plate nozzles are operated. In contrast, the Ver Seal variants 4 to 7 model plate nozzles are mandatory such. The arrangement and number of model plate nozzles rich depends on the model-specific circumstances. A before part of the combined or individually applicable compression level rianten is therefore u. a. in that not the entire model park, but only models with corresponding difficulty be provided with the required model plate nozzles have to. With the multifunctional compression system you can thus all model types by selecting the ver sealing variant are molded.

Exemplary embodiments are described below with reference to the drawings described the invention, from which still further features and Benefits can be seen. The drawings show:

Fig. 01 is a vertical cross section through a molding machine with a multi-stamp pulse and compressed air pulse compression unit

Fig. 02 is a partial vertical section through the Vielstempel- Preßimpuls- and compressed air pulse unit with Execute Licher representation of the Laval nozzles, the valve plunger and the Impulspreßstempel according to section line AA in FIG. 06

Fig. 03 is a vertical section through a Preßstempelzy cylinder with activatable seals.

FIG. 03a is a partial view with the cylinder block with the position Dar Preßstempelzylinderbefestigung according to view B in FIG. 03.

Fig. 04 is a horizontal section through the compressed air chamber and through the central lifting frame for the valve tappet on the section line CC in FIG. 01.

Fig. 05 is a horizontal section through the compressed air chamber and through the valve stem along section line DD in Fig. 01

Fig. 06 is a horizontal section through the cylinder block according to section line EE in Fig. 01 and Fig. 02

Fig. 07 is a horizontal representation of the area-wide arrangement of the press ram and the outlet openings for the compressed air pulse

Fig. 08 is a vertical longitudinal section through the cylinder block showing the through channels for the compressed air pulse and with the representation of the diamond tubes for the fluidizing air flow according to section line FF in Fig. 06

Fig. 08a diamond tube cross section with slot nozzles

Fig. 08b diamond tube cross section with round hole nozzles

Fig. 09 is a horizontal section through the bottom plate of the air pressure chamber showing the pneumatic Preßstempelkontrolle for the lifted state of the ram in accordance with section line GG in FIG. 01

Fig. 09a detailed representation of the pneumatic press ram control

Fig. 10 is a vertical cross section through the Druckluftkam mer and by the lifting device for the lifting frame zentalen, as an alternative to the lifting device in Fig. 01

Fig. 11 is a vertical cross section through the Druckluftkam mer and by the decentralized individual drives of the valve tappet, as an alternative to the lifting device in Fig. 01 and Fig. 10

FIG. 11a is a detailed view of the cylinder Ventilstößelhub

Fig. 11b an elastic valve tappet

Fig. 11c is a partial view of the cylinder heads of the valve tappet drives showing the cylinder head attachment according to view H and K in Fig. 11a

Fig. 12 is a vertical cross section through a molding machine with a Vielstempelpreßimpuls- and Druckluftim pulse compression unit, with the ram in the initial position located below, as Alterna tive to Fig. 01

Fig. 01 shows a vertical cross section through the compression unit according to the invention within a molding machine shown as an example. Of course, the compression unit according to the invention can also be used in other molding machine designs. The compression unit with the multi-stamp press pulse system ( Fig. 01), the compressed air pulse system ( Fig. 08) and the fluidization system ( Fig. 01/08) is integrated in the head frame 15 of the molding machine and it consists essentially of from the compressed air tank 19 with the built-in closure system 21.5 , 23.1 , 24.1 for the nozzles 25.1 , the base plate 20.2 with the nozzles 25.1 arranged therein, the cylinder block 26.1 fastened under the base plate 20.2 with the press rams 27.1 and the through-channels 26.3 ( Fig. 08) for the compressed air pulse and an intermediate frame 30.1 fastened under the cylinder block 26.1 , with which the free space 09 for the press ram feet 27.2 ( FIG. 02) and for the diamond tubes 30.2 of the fluidization system is formed. The molding machine consists in the area of the United compression station from the base frame 12 with the lifting table 13 , the support columns 14 and the head frame 15 with the compression unit. Furthermore, the molding machine also has a lower model plate roller conveyor 16 , a swing-out upper model plate roller conveyor 17 and a molding box roller conveyor 18 . The representation in Fig. 01 corresponds to the starting position for the compression process, wherein the existing from the model plate carrier 01 , the model plate 02 , the molding box 03 and the filling frame 04 and filled with loose molding material 08 molding unit 05 on the upper model plate roller conveyor 17 in the compression station is and there was pressed against the intermediate frame 30.1 by the lifting table 13 with egg ner the compression pressure corresponding closing force. The molding chamber 10 , consisting of the area of the loosely poured molding material 08 and the free space 09 above it, is thereby sealed pressure-tight to the free atmosphere via the seals 11.1 to 11.5 . The compression process, which will be described in more detail below, is carried out in this position. At the beginning of the compression process, the pourable model plate roller conveyor 17 is pivoted back so that the demolding can begin after the compression process and after the compression pressure has been released. The lifting table 13 is lowered abge, the molding box 03 touches down on the roller conveyor 18 after a short stroke and the model 01/02 then lowers out of the mold, after which it is deposited on the lower model plate roller conveyor 16 and after which the out swiveling model plate roller conveyor 17 swings again. Then the molded molding box 03 (e.g. as OK) with the filling frame 04 is moved out of the compression station and at the same time a molding unit 05 filled with loose molding material 08 (e.g. as UK) with filling frame 04 is inserted into the compression station. Simultaneously with the molding box transport the model is 01 / driven 02 on the lower model plate roller track 16 back to the sand-filling station, after which the lifting table 13 raises again and the mold unit 05 presses against the intermediate frame 30.1, thus a new compression will begin.

Fig. 02 shows a vertical partial section through the sealing unit Ver with detailed representation of the cylinder block 26.1 , the ram 27.1 , the compressed air pulse channels 26.3 and the nozzle and valve lifter system 25.1 / 23.1 / 24.1 according to the section line AA in Fig. 06 and also hinted the fluidization system 30.2 / 30.4 / 30.5 . In addition, Fig. 06 shows a horizontal section through the cylinder block 26.1 with the representation of the grid arrangement of the cylinder bores 26.2 for the ram (grid 25.7 ) and the through channels 26.3 for the compressed air pulse (grid 25.8 ). Fig. 08 shows a vertical longitudinal section through the compression unit showing the compressed air pulse system and the associated through-channels 26.3 as well as showing the diamond tubes 30.2 for the fluidization system. Furthermore, the, FIG. 07, the arrangement of the coverage Preßfußflächen 27.2 (Raster 25.7) and the pressure pulse of air channels 26.3 (Raster 25.8) in the region of the molding box 03 or to the mold back. Fig. 05 shows a horizontal section through the compressed air tank 19 and through the Ven tilstößelsystem 23.1 / 24.1 , the valve tappet 23.1 to the Ra stersystem 25.7 of the multi-stamp press pulse and the valve tappet 24.1 to the grid system 25.8 of the compressed air pulse.

The press rams 27.1 are designed as hollow bodies in order to achieve a low weight or a low mass to be accelerated. Accordingly, the press ram 27.1 shown in FIG. 02 consists of a hollow press foot 27.2 , a hollow piston rod 27.3 , a hollow piston support part 27 , 4 , a baffle plate 28.3 (each consisting of a steel material) and a light metal piston 28.1 / 28.2 . The piston rod 27.3 , the circular press foot 27.2 and the piston support part 27.4 are joined together to form a part by welded connections. At the throat 27.5 there is thus a continuous transition between the presser foot and the piston rod, thus avoiding the deposition of molding material at this transition. The top of the presser foot is designed as a steep-angled cone and the entire presser foot 27.2 and the piston rod 27.3 are hard-chrome-plated on the outer surfaces. These measures prevent the molding material from sticking. The chrome plating also prevents corrosion and it leads to a significant improvement in the sliding and friction properties of the piston rod, which is guided smoothly in the piston rod bearing 29.1 and in the low-friction and highly wear-resistant guide bands 29.7 . Likewise, the piston 28.1 / 28.2 is guided smoothly over the low-friction and highly wear-resistant guide bands 28.7 in the cylinder bore 26.2 of the cylinder block 26.1 . The piston seals 28.6 , the piston rod seals 29.4 / 29.5 and the wiper 29.6 are especially suitable for short-term and cyclically high speeds. The piston rod seal 29.4 seals the cylinder chamber 29.9 to the mold chamber 10 , while the piston rod seal 29.5 conversely seals the mold chamber pressure against the cylinder chamber 29.9 which is unpressurized during compression. The / 3 be detached from the piston 28.1 parts / 2 is mounted on the rod cover screen 28.4 and 28.8 the cap nut on the piston carrier portion 27.4 of the pistons. On the end plate 28.4 a damping rubber 28.5 is vulcanized, whereby the ram stop is damped at the end of the upward movement. In addition, a cushioning rubber is Siert aufvulkani 29.8 on the piston rod bearing 29.1, which is attenuated Preßstempelanschlag the supply at the end of Abwärtsbewe. The baffle plate 28.3 made of a steel material prevents overstressing of the piston part 28.1 made of light metal. The Preßstem pel have a sufficient stroke reserve, so that the Preßstem pelhub is not fully extended during the compression process and is limited by the compressed molding material. The lower damping rubber 29.8 is therefore only a safety measure for a possible faulty operation if, for. B. too little molding material 08 in the molding unit 05 . The presser foot 27.2 is circular ( Fig. 07), so that on an agile anti-rotation, as is required in the known Vierecki conditions press feet, can be dispensed with. Furthermore, the press foot 27.2 is tapered on its underside in order to enlarge the compression cone in the molding material, which, in conjunction with the adjacent compression cones, creates a uniform compression layer at a shallow depth below the surface of the molding material and thus eliminates the need for square press feet. The diameter of the presser foot 27.2 corresponds approximately to the diameter of the piston 28.1 , so that the pressure acting on the piston 28.1 is identical to the compression pressure of the presser foot 27.2 .

According to the representation in Fig. 02, the inner area of the cover plate 28.4 and the damping rubber 28.5 advantageously forms an impact cup 25.2 for the free jet, which emerges at a supersonic speed and bundled from the Laval nozzle 25.1 and which strikes the impact cup 25.2 immediately below the Laval nozzle 25.1 . An upward tapered widening and the spherical shape of the centrally arranged cap nut 28.8 form an advantageous inner shape of the impact cup 25.2 for the radiation effect. In the Laval nozzle 25.1 , the potential pressure energy in the compressed air tank 19 is converted into kinetic beam energy, with which the ram is accelerated extremely high like a free-flight piston or a projectile. Before the free jet is triggered, the cylinder chamber 29.9 on the piston rod side is relieved of pressure via the channels 26.4 , the distributor pipe 26.5 and the valves 72.1 / 2 to the atmosphere or via the valve 73.1 / 2 to a negative pressure source 84 , so that no counterpressure occurs during the free jet action acts on the piston rod side piston surfaces. The channels 26.4 , the manifolds 26.5 and the valves 72.1 / 2 and 73.1 / 2 are generously dimensioned so that the atmospheric or subatmospheric residual air displaced during the impulsive downward movement of the press rams can be displaced without special resistance, in particular the connection to the Un terdruckquelle the resistance particularly effectively reduced.

In the idle state or in the initial state, the press rams 27.1 are raised and they are in the process by the network pressure 40 , which via the switched-off valve 71 , via the distributor pipe 26.5 and via the channels 26.4 ( FIGS. 02 and 06) in the piston-side cylinder spaces 29.9 pending, held in the upper position. The upper piston chambers 25.3 are relieved to the atmosphere via the channels 26.6 , via the distributor pipe 26.7 and the switched-off valves 67.1 / 2 . In the end plate 28.4 are small relief bores 28.9 , through which possible leaks can flow from the valve seats 23.1 / 24.1 to the atmosphere, so that a disturbing pressure build-up in the impact cup 25.2 is avoided.

With the in Fig. 01 u. 02 shown intermediate frame 30.1 , the free space 09 is formed for the press feet 27.2 and for the fluidization system 30.2 . The free space 09 and the loose ge poured molding material 08 form the molding chamber 10 ( Fig. 01). The presser feet 27.2 are in the raised state in the protected area of the free space 09 and they are only a short distance 30.6 from the lower edge of the intermediate frame 30.1 . In order to avoid a collision of the press ram with the filling frame 04 ( FIG. 01) entering and exiting the lower frame of the intermediate frame 30.1 in a small distance, the raised state of the press ram is monitored by a pneumatic control device according to the invention. The Kontrolleinrich is processing in Fig. 01, Fig. 02, Fig. 09 and FIGS. 09a and consists of the disposed in the base plate 20.2 ver tical holes 33.1, the horizontal holes 33.2 / 33.3, and the distribution channels 33.4 / 33.5. Furthermore , the control device consists of the control valve 59 , the throttle valves 60.1 / 2 , the pressure sensors 61.1 / 2 and the check valves len 62.1 / 2 . The horizontal bores 33.2 and 33.3 are drilled into the bottom plate 20.2 because of the drilling depth limitation from two sides as blind bores ( FIG. 09). The vertical bores 33.1 are in the raised position of the press ram by the damper rubbers 28.5 as shown in FIG. 02 and FIG. 09a pressure-tightly closed. The control device works as follows: After the compression process and after the Laval nozzles 25.1 have been closed by the valve tappets, the rams are switched off by switching off valves 67.1 / 2 , 71 , and 72.1 / 2 (valves 64 , 73.1 / 2 and 75 are there when switched off) raised. The piston-side cylinder spaces 25.3 are depressurized and the pressure sensor 68 ( FIG. 01) drops. In the piston rod-side cylinder spaces 29.9 builds up a pressure required for lifting the ram, which increases to the network pressure 40 and leads to speaking of the pressure sensor 69 as soon as all rams have been raised or come to a standstill. The addressed pressure sensor 69, in coincidence with the dropped pressure sensor 68 , reports that the press rams have reached their safe upper end position in terms of the pressure conditions.

However, these pressure ratios can also arise if, for example, a press ram is stuck in the event of a fault and does not reach the upper end position. The coincidence signal of the addressed pressure sensor 69 and the dropped pressure sensor 68 therefore trigger a second pneumatic control process by briefly turning on the valve 59 . Compressed air flows with network pressure over the throttle orifices 60.1 / 2 , over the distribution channels 33.4 / 5 and over the horizontal bores 33.2 / 3 to the vertical bores 33.1 . When all the rams are raised and the vertical bores 33.1 are closed by the damping rubbers 28.5 , then a pressure builds up and the pressure sensors 61.1 / 2 respond and release the transport of the molding unit 05 with the filling frame 04 ( FIG. 01). If, for example, a press ram has not reached the upper end position, then the corresponding vertical bore 33.1 is not closed, so that the compressed air supplied by valve 59 can flow to the atmosphere via channels 26.6 and via valves 67.1 / 2 . As a result, the pressure sensors 61.1 or 61.2 cannot respond and the transport of the molding unit 05 with the filling frame 04 is not released in connection with a fault message. The throttle orifices 60.1 / 2 ensure that no back pressure can build up and the pressure sensors 61.1 / 2 do not respond if only one vertical bore 33.1 is not closed. Therefore, only as much compressed air flows through the throttle orifice as can flow through a vertical bore 33.1 without throttling. The lifting of the ram and the control of the ram is carried out during the demolding process, so that the cycle time is not affected.

The vertical bores 33.1 , the horizontal bores 33.2 / 3 and the distribution channels 33.4 / 5 can be used in addition to the control function for oil lubrication of the ram. For this purpose, an oil tank 56 via the throttle aperture 57.1 / 2 and through the check valves 58.1 / 2 with the distribution channels 33.4 / 5 (Fig. 02 and Fig. 09), respectively. By briefly and cyclically switching on the valve 55 , the oil container 56 is pressurized with compressed air, with which lubricating oil reaches the vertical bores 33.1 via the throttle orifices 57.1 / 2 . The amount of lubricating oil is determined by the duty cycle of the valve 55 and by the size of the throttle orifices 57.1 / 2 . The lubrication pulse expediently takes place during the phase of static pressing, that is, immediately after the multi-stamp pressing pulse, each with cyclical repetition after a certain number of sealing operations. For the rapid conveyance of the lubricating oil to the vertical bores 33.1 , after the lubrication pulse through the valve 55 , a brief pressure pulse can take place via the valve 59 . Check valves 58.1 / 2 and 62.1 / 2 prevent mutual interference between the control system and the lubrication system.

Fig. 03 shows a Preßstempelzylinder with activatable seals 31.7 and 32.6. Apart from the seals that can be activated, this ram cylinder has the same characteristics as the ram cylinder previously described in connection with FIG. 02. The piston seals 31.7 and the rod seals 32.6 are made of an elastic sealing material and they have a hat-shaped profile. The piston seals 31.7 are clamped with their in the collar area between the two uniform piston parts 31.1 , the intermediate ring 31.2 and the two uniform intermediate rings 31.3 , the sealing surface area and the web area between the sealing surface and the collar being freely movable. The interior of the seals are connected to the respective pressure side via channels 31.6 . If one side of the piston is depressurized, the corresponding interior of the seal is also depressurized and the elasticity of the seal retracts from the cylinder wall. If pressure is applied to one side of the piston, the pressure passes through the channel 31.6 into the interior of the seal and the seal 31.7 is expanded and pressed against the cylinder wall. In order to limit the pressing force against the cylinder wall, the conical webs of the seal are supported on the correspondingly conical surfaces of the piston part 31.1 and the intermediate ring 31.2 . The piston rod seals 32.6 work in the same way, which are also clamped in the collar area between the piston rod bearing 32.1 and the cylinder cover 32.4 and the intermediate rings 32.2 / 3 and are activated via the channels 325 with compressed air. The upper seal 32.6 seals the cylinder space 29.9 towards the mold chamber 10 , while the lower seal 32.6 conversely seals the mold chamber pressure against the cylinder space 29.9 which is unpressurized during compression. To avoid the ingress of dirt, channel 32.5 is provided with a filter 32.7 . The activatable seals have the particular advantage that no sealing friction is present during the acceleration phase of the pressing pulse. Furthermore, no seal is required even during the pressing pulse, because the press cylinders are depressurized on all sides when the compression process is triggered and the acceleration of the ram is not carried out by pressure but by the kinetic energy of the nozzle jets. Only at the end of the compression process does pressure build up, which activates the corresponding seals and creates a stepless transition to static pressing.

Fig. 03a shows the attachment of the cylinder cover 32.4 to the cylinder block 26.1 , this attachment applies to both the cylinder according to FIG. 03 and the cylinder according to FIG. 02. Due to the close-meshed press ram 25.7 and the diagonally between the cylinder covers 29.3 / 32.4 ( Fig. 02, 03 and 03a) arranged through channels 26.3 for the air pulse, the cylinder covers 29.3 / 32.4 over the tabs 27.6 with the screws 27.7 on the cylinder block 26.1 fixed.

Fig. 02 shows in the upper part of the Lavaldüsen- and Ventilstö ßelsystem. The Laval nozzles 25.1 are arranged in the base plate 20.2 of the compressed air container 19 and they open immediately in the piston chambers 25.3 of the ram cylinder or in the through channels 26.3 for the compressed air pulse. The valve tappets are opened and closed by the valve lifters 23.1 and 24.1 . The attached to a lifting frame 21.5 Ven tilstelel 23.1 and 24.1 have two different Ausfüh approximate shapes. With the different embodiments, the required and already mentioned earlier opening of the press ram nozzles is realized in order to achieve the synchronous interaction of the multi-ram press pulse and compressed air pulse. The valve lifter 23.1 for the press ram consists of an elastic sealing material which is vulcanized onto a steel core 23.2 and is fixed by means of a washer 23.3 and a screw 23.4 on the shaft 21.6 a of the lifting frame 21.5 . Due to the elastic sealing material (e.g. rubber), the valve tappet is deformable so that it is compressed by the downward force of the lifting frame 21.5 from the dimension 23.6 existing in the open state to the dimension 23.7 existing in the closed state. The spring force thereby stored finally supports the acceleration process of the lifting frame 21.5 when opening again. In further characterized the valve tappet 23.1 at a speed greater than zero ben abgeho from Ventilstiz in the "flying start", which is beneficial to the required sudden opening of the Laval nozzles. The conically formed gap 23.5 , which is set in the open state between the valve lifter 23.1 and the disk 23.3 , enables a largely frictionless deformation. In the closed state of the valve tappet is supported abge 23.1 forth from the disc 23.3 from the inside. The Laval nozzles for the ram located on the edge of the molding box can advantageously be designed with a larger diameter in order to compensate for the friction of the molding material on the molding box edge by a higher energy supply. The fully effective cross-section of the Laval nozzles is already after a short stroke of D / 4 ( Fig. 02 and Fig. 11 64084 00070 552 001000280000000200012000285916397300040 0002010024930 00004 63965b). However, the lifting frame 21.5 runs through a longer stroke 22.3 in order to also lift the valve tappet 24.1 described below for the compressed air pulse from the valve seat. The valve tappet 24.1 for the compressed air pulse consists of a valve plate 24.2 with a vulcanized-on seal 24.3 , where in the valve plate 24.2 it is fastened together with a damping disk 24.5 to a trailing pin 24.4 . The trailing pin 24.4 is guided in a shaft bushing 24.6 in the shaft 21.6 b of the lifting frame 21.5 . On the bearing bush 24.6 there is a damping disc 24.7 made of rubber and an impact disc 24.8 made of impact-resistant plastic. At the upper end of the tow pin 24.4 , a metallic drive plate 24.9 is attached. To open the nozzles 25.1 , the lifting frame 21.5 is raised abruptly, the press die nozzles being opened first (as described above). The nozzles for the compressed air pulse are only opened when the lifting frame 21.5 has covered the stroke 25.6 , with which the synchronous interaction of the multi-stamp press pulse and the compressed air pulse is achieved. Up to this point, the valve plates 24.2 are held on their valve seats by the pressure prevailing in the compressed air tank 19 . After the lifting frame 21.5 b with the shaft 21.6, the bearing bushing 24.6, the damping disc 24.7 and the impact disc has 24.8 fen pres the stroke 25.6, 24.8 proposes the impact disk on the carrier disc 24.9 and tears the towing pin 24.4 and the attached valve disc 24.2 with upwards, causing the Ven tilteller 24.2 to suddenly lift off the valve seat with the already highly accelerated lifting frame speed "on the fly". After the total stroke 22.3 , the valve lifters 24.1 have reached the maximum open position 22.5 (d / 4) and the valve lifters 23.1 have reached the open position 22.6 . The impact disk 24.8 made of impact-resistant plastic prevents a hard impact on the metallic driving disk 24.9 , and the rubber damping disk 24.7 further dampens the stop on the driving disk. With the closing process taking place much more slowly, the damping disc 24.5 made of impact-resistant plastic prevents a hard metallic impact on the bearing bush 24.6 . Furthermore, the damping disc 24.5 limits the closing stroke of the lifting frame 21.5 and thus also the deformation dimension 23.7 on the valve lifter 23.1 . The key holes 24.6 a in the bearing bush 24.6 and the hexagon 24.4 a on the trailing pin 24.4 allow for easy installation and removal of the valve tappet 24.1 in the event of maintenance or repair after removing the base plate 20.2 . The stroke dimension 25.6 can be determined for each individual valve lifter by determining the length of the trailing pin 24.4 or the striking disc 24.8 . For example, the laval nozzles on the outside can be opened first by means of correspondingly adjusted stroke dimensions 25.6 and then the inner laval nozzles increasingly, whereby an advantageous bell-shaped compressed air pulse wave is achieved. Furthermore, the valve lifters 24.1 could also be used for the internal press rams and the valve lifters 23.1 could continue to be used for the external press rams, whereby an advantageous glockenför shaped lifting front can also be realized for the press rams. The staggered, non-simultaneous opening of all Laval nozzles also has the advantage that the required lifting force of the lifting frame 21.5 is significantly reduced.

The lifting frame 21.5 previously described for FIG. 02 with the valve carrier shafts 21.6 a and 21.6 b further consists, as shown in FIG. 01, of the connecting tube 21.4 with the guide piston 21.3 and with the working piston 21.1 , which are guided in the cylinder tube 20.4 . The cylinder tube 20.4 is part of the head plate 20.3 , which forms the compressed air tank 19 together with the housing 20.1 integrated in the machine frame 15 and the base plate 20.2 . Through the openings 20.5 , 20.6 and 20.7 , the cylinder spaces 20.8 and 20.9 are part of the compressed air tank 19th Likewise, the inner regions of the valve carrier shafts 21.6 a and 21.6 b through the openings 21.8 and 21.9 are part of the compressed air tank 19 . Fig. 04 shows a horizontal section through the compressed air tank 19 showing the lifting frame 21.5 , which has a large number of openings 21.7 and 21.8 . The larger openings 21.7 are between the valve lifters ( Fig. 01 and 04) and they form an immediate passage for the air flow through the lifting frame 21.5 . The smaller openings 21.8 are in the center of the valve lifter and together with the openings 21.9 ( FIG. 02) they also form a passage through the lifting frame 21.5 . Due to this complex arrangement of the through openings, the compressed air goes directly to the Laval nozzles 25.1 . The lifting frame guided in the cylinder barrel 20.4 is secured against turning by the sliders 25.9 ( Fig. 02 and 04). The working piston 21.1 is provided with a damping disc 21.2 made of rubber material in order to dampen the stop of the working piston 21.1 at the end of the stroke. A hydraulic tandem cylinder 22.1 is placed on the top plate 20.3 , with the piston 22.2 of which the stroke of the working piston 21.1 can be limited. In the retracted state of the piston 22.2 , the working piston 21.1 or the lifting frame 21.5 passes through the long stroke 22.3 ( FIG. 01), whereby the Laval nozzles for the press ram cylinders and the Laval nozzles for the compressed air pulse are opened and the combined compression of the multi-punch press pulse / Compressed air pulse is triggered. In the extended state of the piston 22.2 , the working piston 21.1 or the lifting frame 21.5 passes through the short stroke 22.4 ( FIG. 01), whereby only the Laval nozzles for the ram are opened and thus only the multi-ram press pulse is triggered. If only the compressed air pulse is to be triggered, then the piston 22.2 is retracted and the working piston 21.1 or the lifting frame 21.5 runs through the long stroke 22.3 ( FIG. 01), whereby the Laval nozzles for the ram cylinders and the Laval nozzles for the compressed air pulse are opened. In order to prevent the multi-stamp press pulse, the piston rod-side cylinder spaces 29.9 remain pressurized with the high network pressure 40 , ie the valves 67.1 / 2 , 72.1 / 2 , 73.1 / 2 and 75 remain closed, and the valve 71 remains open for supplying pressure to the network , so that the pressure in the piston rod-side cylinder chambers 29.9 between the check valve 70 and the safety valve 74 is clamped and thus the multi-stamp press pulse is prevented. In the case of a still small movement of the ram, the clamped pressure would be further compressed, as a result of which the ram spring back into its upper starting position. The piston 22.2 is actuated hydraulically via the valve 103 . In the cross position of the Ven valve 103 , the piston 22.2 is pressed upward by the compressed air in the cylinder space 22.7 , the hydraulic oil flowing out via the check valve 102 to the tank. During the short-term pressure-free phase in the cylinder chamber 22.7 , which arises during the compression process, the Rückschlagven valve 102 prevents the piston 22.2 from lowering. In the parallel position of the valve 103 , the piston 22.2 is moved to the position shown in dashed lines ( FIG. 01) until it stops. The pressurized hydraulic oil is clamped between the piston 22.2 , the check valve 101 , the bladder accumulator 105 and the safety valve 104 , the stroke limitation of the working piston 21.1 or the lifting frame 21.5 being ensured by a corresponding pressure level. The Blasenspei cher 105 prevents 22.2 pressure peaks when the working piston 21.1 strikes against the piston. Instead of a hydraulic tandem cylinder 22.1 , of course, a pneumatic tandem cylinder (not shown) can also be used with a corresponding diameter.

The compressed air tank 19 is connected to the storage tank 45 via generously dimensioned lines, so that constant unrestricted refilling of the compressed air tank 19 can take place. The storage tank 45 is connected via the pressure control valve 43 and the switching valve 42 and via a pneumatic maintenance unit 41 to the compressed air network, which usually has a pressure of up to 8 bar. The pressure in the compressed air tank 19 required for the compression process is set on the pressure regulator 43 . This pressure can be a maximum of 8 bar, but a pressure of 3 to 6 bar is preferably used. The pressure setting can be carried out and monitored manually or automatically via a model-specific data record. Before the multi-plunger pressing pulse is triggered, the cylinder spaces 29.9 on the piston rod side are relieved of pressure via the valves 73.1 / 2 towards the vacuum source 84 . The plunger solve by the negative pressure and by their own weight and by the ge opened valves 67.1 / 2 from their upper starting position and from their static friction, so that when the Ver sealing or acceleration process triggers advantageously already in the state of the lesser Sliding friction. Al ternatively or in the absence of a vacuum source, the same effect can also be achieved if the piston rod side side cylinder spaces 29.9 are relieved to the open atmosphere via the valves 72.1 / 2 and at the same time the piston side cylinder spaces 25.3 via the pressure regulator 63 and the valve 64 with a slight overpressure who the. To trigger the compression process, the generously dimensioned quick- switching valves 48.1 / 2 are switched on, as a result of which the pressurized cylinder space 22.7 is suddenly relieved. The under the working piston 21.1 constantly standing pressure of the pressure vessel 19 thereby the working pistons 21.1 and lift the lifting frame 21.5 abruptly and open the Laval nozzles 25.1 abruptly for the compression process. The compression process, which at the end is continuously changed from a dynamic to a static state with a uniform compensation pressure in the area of the compressed air chamber 19 , the upper press cylinder spaces 25.3 and the molding chamber 10 , is acknowledged by the pressure sensors 68 and 87 . With the confirmation, the Laval nozzles 25.1 are closed again. To close the Laval nozzles or to lower the working piston 21.1 , the quick- switching valves 48.1 / 2 are switched off and the valve 46 is switched on briefly. With the brief switching on of the valve 46 , the cylinder space 22.7 is briefly acted upon with the higher network pressure 40 in order to accelerate the closing process. After closing the Laval nozzles 25.1 , the compensating pressure built up in the molding chamber 10 is reduced within a certain time via the switching valves 85.1 / 2 ( Fig. 08) and the throttle valves 86.1 / 2 ( Fig. 08). At the same time, the plungers are moved back to the upper starting position by switching off the valves 67.1 / 2 and 72.1 / 2 or 73.1 / 2 and by switching on the valve 71 . However, after the Laval nozzles have been closed and during the pressure reduction in the molding chamber 10, the press rams can be subjected to the higher network pressure 40 via the pressure regulator 63 and the valve 64 in order to increase the static pressure and only then be returned to their upper starting position . By using a pressure intensifier (not shown), the pressure can also be increased to up to 12 bar, which, due to the approximately identical diameter of the piston 28.1 and the presser foot 27.2, achieves a mold pressure of 120 N / cm ^{2 which} can be assigned to the high pressure. In the idle state with closed Laval nozzles, the cylinder chamber 22.7 with the valve 46 switched off is connected via the switched-off quick-switching valves 48.1 / 2 to the compressed air tank 19 , so that the same pressure prevails on both sides of the working piston 21.1 . The complete lifting device 21.1 to 21.6 is therefore with its own weight on the valve lifters 23.1 and 24.1 and the valve lifters are pressed by the pressure difference between the compressed air tank 19 and the atmospheric pressure under the Laval nozzles 25.1 on their valve seat, so that the La val nozzles are closed intrinsically safe . The compressed air lubricator 47 ensures the lubrication of the working piston 21.1 and the guide piston 21.3 .

Fig. 10 shows an alternative embodiment of in Fig. Actuator of the lifting frame 01 illustrated 21.5. This alternative has the advantage that the lifting frame 21.5 reacts and accelerates considerably faster when opening its lifting movement to open the Laval nozzles 25.1 , because the lifting force is divided between two working pistons arranged in tandem and only one of them can be controlled with a significantly reduced displacement got to. The two pistons arranged in tandem consist of the tube designed as a working piston Füh approximately 34.1 and the additional piston 35.2 coupled thereto, the guide tube designed as a working piston 34.1 is constantly under the pressure of the compressed air tank 19 and the reduced additional piston 35.2 for the opening and closing process of the Laval nozzles 25.1 is operated with the higher pressure of the compressed air network 40 . The guide tube 34.1 is part of the lifting frame 21.5 with its Ventilträgerschäf th 21.6 a and 21.6 b. Overall, the lifting frame 21.5 has the same features as described for FIGS. 01, 02 and 04, as does the compressed air container 19 . The interior 34.7 of the guide tube 34.1 is part of the compressed air tank 19 through the openings 20.5 and 20.6 . The guide tube 34.1 is guided in the low-friction and highly wear-resistant guide bands 34.2 of the cylinder 34.6 , which is part of the head plate 34.5 . The cylinder is further provided with a seal 34.3 and a dirt wiper 34.4 . The cylinder 35.1 for the additional piston 35.2 is attached to the head plate 34.5 via the four rods 35.3 . The hydraulic cal tandem cylinder 35.4 ( Fig. 10) with its piston 22.2 ( Fig. 10) has the same function as previously described for Fig. 01, and the stroke dimensions 22.3 and 22.4 in Fig. 10 are the same as 22.3 and 22.4 in Fig. 01. The additional piston 35.2 is provided with a damping disc 35.5 made of rubber material in order to dampen the stop of the additional piston 35.2 at the stroke end. The control valves 89.1 / 2 and 90.1 / 2 are attached directly to the head plates of the additional cylinder 35.1 in order to achieve short and low-loss compressed air paths. The compressed air lubricator 88 serves to lubricate the additional piston 35.2 . The piston rod of the additional piston 35.2 is coupled via the connecting disks 34.8 and 34.9 to the guide tube 34.1 . In the rest position, the guide tube 34.1 with the lifting frame 21.5 and the valve lifters 23.1 and 24.1 is on the base plate 20.2 . The additional piston 35.2 to the bottom flange of the additional cylinder has only a slight play 35.6 of, for example, 5 mm, as a result of which the pressure action begins without delay when the valves 90.1 / 2 are opened. In the idle state, the valves 89.1 / 2 and 90.1 / 2 are switched off, so that the additional piston 35.2 is depressurized on both sides. Designed as a working piston guide tube 34.1 exerts an upward force on the lifting frame 21.5 , while the elastic Ven tilstößel 23.1 exert a downward force on the lifting frame 21.5 by their closing force on the valve seat. The area ratios between the guide tube 34.1 and the elastic valve tappets 23.1 are designed so that the resulting force is directed downwards, in a size that ensures intrinsically safe closing of the Laval nozzles 25.1 . To trigger the compression pulse who the valves 90.1 / 2 turned on, the higher network pressure 40 applied to the additional piston 35.2 from below and where with a correspondingly large force for suddenly lifting the lifting frame 21.5 or for suddenly opening the Lavaldü sen 25.1 . The sudden lifting is particularly favored because the piston chamber above the additional piston 35.2 is depressurized and connected via the generously dimensioned valves 89.1 / 2 to the free atmosphere and because the small, only about 5 mm high space (dimension 35.6 ) under the additional piston 35.2 after switching on the generously dimensioned valves 90.1 / 2 enables a pressure effect without delay. To close the Laval nozzles 25.1 after the compression process, the valves 89.1 / 2 are switched on and the valves 90.1 / 2 are switched off. As a result, the guide tube 34.1 is pressed down with the lifting frame 21.5 and the Laval nozzles are closed. After the pressure reduction in the molding chamber 10 and in the press cylinder spaces 25.3 , the valves 89.1 / 2 are switched off again, so that the additional piston 35.2 is depressurized on both sides. The force described above, resulting from the area ratio between the guide tube 34.1 and the elastic valve lifters 23.1 , then takes over the intrinsically safe locking of the Laval nozzles.

Fig. 11 shows a further alternative to opening and closing the Laval nozzles 25.1 by individually driven Ven tilstößel, the valve tappet shown in Fig. 05 also applies to this alternative. The individual drive be consists of a reciprocating piston 37.1 , an associated hollow piston rod 37.2 , at the lower end of which an elastic valve tappet 23.1 is attached, and furthermore from a cylinder 36.3 , a cylinder cover 36.7 with integrated quick-switching valve 92 and a piston rod guide 38.3 / 38.4 . The resilient valve stem 23.1 is identical to the already be previously for Fig. 02 described elastic valve tappet 23.1. It consists of an elastic sealing material that is vulcanized onto a steel core 23.2 and is attached to the piston rod shaft 37.3 by means of a washer 23.3 and a screw 23.4 . Due to the elastic sealing material (e.g. rubber), the valve tappet is deformable so that it is compressed by the downward closing force of the lifting piston 37.1 from the existing dimension 23.6 in the open state to the existing dimension 23.7 in the closed state. The spring force thereby stored supports the acceleration of the reciprocating piston 37.1 and the piston rod 37.2 during the stroke 38.6 during the opening process. Furthermore, the valve tappet is lifted after the stroke 38.6 at a speed greater than zero "in the flying start" from the valve seat, which has an advantageous effect on the sudden opening of the Laval nozzles. The conically formed gap 23.5 , which is set in the open state between the valve lifter 23.1 and the disk 23.3 , enables a largely frictionless deformation. In the closed state of the valve tappet is supported abge 23.1 forth from the disc 23.3 from the inside. The fully effective cross-section of the Laval nozzles is reached after a small opening stroke of D / 4 ( Fig. 11a and 11b), so that the total stroke of the piston 37.1 is very small and results from the expansion stroke 38.6 (dimension 23.6 minus dimension 23.7 ) plus the dimension D / 4 composed. When closed, the reciprocating piston 37.1 has a sufficient stroke reserve downwards to ensure that the Laval nozzles are securely closed. The piston 37.1 , the piston rod 37.2 and the piston rod shaft 37.3 are joined to one part by welded connections. The cavities of the piston rods 37.2 are part of the compressed air tank 19 through the openings 37.4 . The piston 37.1 and the piston rod 37.2 are guided in the low-friction and highly wear-resistant guide bands 38.1 and 38.4 and sealed by the seals 38.2 and 38.5 . The piston 37.1 is provided with a damping rubber 37.5 , whereby the stop on the cylinder cover 36.7 is damped during the opening process. During the closing process, damping takes place through the elastic valve tappet 23.1 . The quadra table cylinder covers 36.7 and 36.8 are each attached to the converging corners with the screw connection 36.9 because of the engmaschi gene grid according to FIG. 05 and FIG. 11e. The reciprocating pistons 37.1 for the valve tappets are operated with the higher pressure of the compressed air network 40 in order to achieve the required opening or acceleration force. To lubricate the piston 37.1 and the piston rod bearing 37.2 , the compressed air is passed through the compressed air lubricator 91 . On the side of the piston rods, the pistons 37.1 are under permanent pressure via the sealed air chamber 36.4 and via the ring channels 36.5 . The sealed compressed air chamber 36.4 and the cylinder plate 36.2 are part of the head plate 36.1 , which closes the compressed air container 19 at the top. The compressed air is supplied to the sealed chamber 36.4 via the channels 36.6 . In the idle state, the quick-switching valves 92 are switched off, so that the upper piston spaces 37.6 are also under pressure. The valve lifters 23.1 are pressed by the pressure difference between the pressure in the compressed air tank 19 and the atmospheric pressure under the Laval nozzles 25.1 onto the valve seat, so that the Laval nozzles are closed intrinsically safe. Furthermore, an additional closing force acts on the valve tappet 23.1 , which results from the differential areas of the piston and the hollow piston rod and from the pressure difference between the pressure in the compressed air tank 19 and the network pressure 40 . The quick-switching valves 92 are switched on to open the Lavald nozzles or to lift the valve tappets 23.1 , as a result of which the small-volume cylinder spaces 37.6 are suddenly relieved. This creates an upward opening force, which is supported by the previously described spring action of the elastic valve lifter 23.1 , whereby the Laval nozzles are suddenly released according to the stroke D / 4.

The advantage of the individually driven valve lifters is in particular that the control of each Laval nozzle 25.1 can be freely determined. Thus, the already described time-shifted start between the multi-stamp press pulse and the compressed air pulse can be realized simply by switching the quick-switching valves 92 accordingly in time-shifted manner. Furthermore, the selection of the compression programs "combined multi-stamp press pulse / compressed air pulse", "only multi-stamp press pulse" or "only compressed air pulse" can be realized simply by switching only the quick-switching valves 92 required for the compression program. Model-dependent compression profiles can also be realized with the individually driven valve lifters, by coordinating the opening times of the press ram nozzles and / or the compressed air pulse nozzles or the switching times of the corresponding quick-switching valves 92 with the model contour. For example, different compression strokes of the press rams can be compensated for because of different sand or model heights so that they simultaneously achieve the final compression in the corresponding mold areas. Also by correspondingly staggered actuation of the quick-switching valves 92, a bell-shaped lifting front of the press ram and / or the compressed air pulse wave, which is advantageous in terms of the material friction at the edge of the molding box, can be generated. The switching times for each individual quick-switching valve 92 are stored in model-related data records associated with the model number. The corresponding data set is called up via the model number, which can be read out automatically when a model is replaced or can be entered manually, so that the switching times for the individual quick-switching valves 92 are automatically activated. Another advantage of the individual drives is that the compressed air can flow freely through the compressed air tank 19 with better efficiency between the piston rods 37.2 .

Th to expand the multifunctional Verdichtungsmöglichkei, it is also possible in the other, which is known from EP-0995522 air flow method as shown in FIGS. 01 to 02 and 08 integieren system in the inventive compression. In this process, the loosely poured molding material is first homogenized and fluidized by an air flow lasting approx. 1 to 3 seconds, without causing a recognizable pre-compression. In this case, only as much compressed air is blown into the molding chamber 10 as can flow back out through the model plate nozzles 07 without a further increase in pressure given a corresponding pressure drop. Alternatively, the air flow can also be generated by a vacuum source 84 below the model plate 02 or from a combination of vacuum under the model plate 02 and a slight excess pressure in the molding chamber 10 . In the ongoing homogenization and fluidization process, the compression pulse according to the invention is then introduced in a stepless transition. The integration of this method takes place via the diamond-shaped tubes 30.2 , which are arranged uniformly distributed in the intermediate frame 30.1 as shown in FIGS . 01 and 08. The diamond-shaped design of the tubes 30.2 was chosen in order to effect a flow division of the nozzle jets emerging from the channels 26.3 . The lozenge 30.2 tubes are shown in FIG. 08a provided with narrow slots or according to Fig. 08b with small holes which are distributed in RESIZE ßerer number over the tube length and through which the air stream flows evenly distributed in the molding chamber. The slots Fig. 08a and the bores Fig. 08b form a total cross-section in number and size, so that the mass flow depending on the flow capacity of the model plate nozzles 07 depending on the laws of subcritical leakage by the pressure in the diamond tubes 30.2 be is true. This pressure is set at the pressure regulator 51 and supplied to the diamond tubes 30.2 via the regulator tank 52 , the valve 77 and the distribution channel 30.5 , the valve 78 being closed. The airflow flowing out through the model plate nozzles reaches the free atmosphere via the switched-off valves 80 , 81 and 83 or alternatively via the switched-off valves 80 and 81 and via the switched-on valve 83 to the vacuum source 84 . If the air flow is to be generated only from the vacuum source, then the valves 77 , 80 and 81 are switched off and the valves 78 , 83 and 85.1 / 2 are switched on and the air flow is sucked in from the free atmosphere via diamond pipes 30.2 and via the valve 78 , so that no vacuum effect can arise in the molding chamber 10 . Referring to FIG. 01, the diamond tubes 30.2 left side inserted into the intermediate frame 30.1 and fastened via the flange 30.3. On the right side, the diamond tubes 30.2 open into the distribution channel 30.5 ( FIGS. 01 and 02) with their openings 30.4 , which is integrated in the intermediate frame 30.1 . Check valve 76 prevents compression pressure from mold chamber 10 from entering the airflow pressure system. The pressure to be set on the pressure regulator 51 is model-dependent due to the different nozzle configuration of the model plates 02 . The pressure values are therefore also stored in the data records already described, so that the pressure setting can be carried out automatically when a model is replaced.

As already stated at the outset, the device for carrying out the pulse compression according to the invention also enables a further compression process which does not run in a pulse-like manner and which can be activated simply by switching to an appropriate control program. In this compression method according to the invention, compressed air is first blown from below via the model plate nozzles 07 against the gravity of the molding material into the molding chamber 10 until the pressure in the molding chamber 10 is equal to the pressure in the compressed air container 19 or in the storage tank 45 . This pressure, which is set at the pressure regulator 43 , can be between 2 bar and the maximum network pressure of 8 bar, but preferably between 3 bar and 6 bar. The blowing is carried out with a flat pressure gradient of 1 to 6 bar / sec (preferably 2 to 4 bar / sec) adjustable at the throttle valve 79 in order not to raise the loosely poured molding material. This Einla sen causes no compression molding, because above the loosely poured molding material 08 is still the free space 09 , so that the molding material cannot be supported upwards. The molding chamber 10 and the air pores in the molding material are only brought into a state of higher atmospheric pressure. Starting from the initial position shown in Fig. 01, in which only the two valves 42 and 50 are switched on and all other valves and the valves in Fig. 08 are switched off or de-energized, the relevant compression process proceeds as follows: Be preparatory first the valves 49 , 71 , 75 , 67.1 / 2 and 85.1 / 2 switched on and the valve 50 switched off. By switching off the valve 50 and switching on the valve 49 , the pressure system 52 for the air flow method according to EP-0 995 522 switches to the pressure system of the compressed air tank 19 or storage tank 45 , which is necessary for the blowing in this compression process. By switching the valves 71 and 75, the piston rod-side cylinder spaces are 29.9 / switched to the printing system of the pressure vessel 19 45 by the network printing system 40 and by turning the valves 67.1 / 2, and 85.1 / 2 (Fig. 08) are on the one hand the cylinder chambers 25.3 and on the other the mold chamber 10 shut off from the free atmosphere. Thereafter, the valve 80 is turned on, whereby the compressed air of the compressed air container is / into the cavity 06 of the pattern plate carrier 01 and from there via the sen Modellplattendü injected 19 45 07 into the molding chamber 10 degrees. Because of the shape of chamber 10 compressed air can escape, turns a finally, the same pressure as the compressed air tank 19/45 here. When this pressure is reached, the molding chamber pressure sensor 87 ( FIG. 08) switches on the lifting of the valve tappets 23.1 / 24.1, as a result of which a connection is established between the compressed air tank 19 and the molding chamber 10 and between the compressed air tank 19 and the upper press cylinder spaces 23.5 via the nozzles 25.1 . Since there is constant pressure on all sides in this state, there is no movement. Only the press rams lay on the loose molded material surface with their low weight. Then a fluidization process is switched on by switching off the valve 80 and by switching on the valve 81, a small amount of the fluidization corresponding to the fluidization flowing out to the free atmosphere via the model plate nozzles 07 , the valve 80 , the throttle 82 and the valve 83 . The time for this fluidization is freely selectable and during this time the Druckluftbehäl is ter / 19 45 fed via the valve 42 and via the pressure regulator 43 according to. After the fluidization, the compression process follows continuously, with the valves 72.1 / 2 switched on and the valves 75 and 81 switched off. By turning off the valve 81 , the fluidization is released and the compression air flow is released. By simultaneously switching on the valves 72.1 / 2 , the piston rod-side cylinder spaces 29.9 are relieved to the free atmosphere, so that the ram in contact with the molding material are moved down and compress the molding material together with the compression air flow. The compression air flow and Preßstem pelbewegung be thereby fed ge 45 of the compressed air tank 19 /, where this is in turn fed in via the valve 42 and via the pressure regulator 43 from the air supply 40th This combined compression begins with the expansion of the mold chamber pressure directly on the model plate nozzles 07 and thus advantageously directly on the model plate surface, the resulting compression air flow being effectively supported by the immediately pressing ram. After about 70% of the compression time, the nozzles / 25.1 closed by lowering the valve tappet 23.1 24.1 again, where / is terminated 45 by the water make-up from the compressed air container 19th The compression air flow is then fed by the compressed air in the molding chamber 10 and in the through channels 26.3 which still exist. With the closing of the nozzles 25.1 , the valve 64 is switched on, as a result of which the upper press cylinders 25.3 are acted upon by the pressure regulator 63 with a higher pressure, up to a maximum of the network pressure, and as a result of which a continuous and continuous transition to static pressing takes place. When the maximum pressure reported by the pressure sensor 68 is reached , the valves 85.1 / 2 ( FIG. 08) are switched off, as a result of which the molding chamber pressure is reduced in a controlled manner via the throttle valves 86.1 / 2 ( FIG. 08). This ent ent pressure chamber side pressure effect on the piston rod gene surfaces of the ram, which further increases the pressing force of the ram. After the pressure reduction in the molding chamber 10 reported by the pressure sensor 87 ( FIG. 08), the valves 64 , 67.1 / 2 and 72.1 / 2 are switched off and the valve 71 is switched on, so that the ram is lifted back into its upper starting position. Simultaneously with the lifting of the ram, the demolding process is started with the lowering of the lifting table 13 . Provided that the vacuum source is stalled in 84, the piston rod-side cylinder chambers 29.9 may be used to more intensive compacting effect rather than to the free atmosphere also for the negative pressure source 84 through are switched by the valves are switched 73.1 / 2 instead of the valves 72.1 / 2. Furthermore, after the fluidization process, the compression air stream flowing out of the model plate nozzles 07 can also be led to the negative pressure source 84 by switching the valve 83 on by switching off the valve 81 . If a compression unit is to be operated only with the compression method described here, then instead of the Laval nozzles, only simple cylindrical bores can be used and, in addition, the valve tappet system can also be considerably simplified.

FIG. 12 shows a possible variant that can be carried out as an alternative to FIG. 01. Here, the distance measure allows a 30.7 Extension and retraction of the filling frame 04 and the mold unit 05 in fully lowered press dies 27.1 / 27.2, with between 27.2 and Preßfüßen the Füllrah men 04 a safety margin of for example 15 to 20 mm is provided. A security monitoring of the press ram for filling frame transport (according to Fig. 09 / 09a) is not necessary with this variant. In the right half of FIG. 12, the starting or rest position is Darge. In the left half of Fig. 12, the Ar beits- or compression position is shown. The compression process with the various possible combinations can continue to run exactly as described so far, with the ram being moved back to the upper end position after the compression process. But there is also the possibility that the ram after sealing Ver are left in their lower position and the cylinder spaces 25.3 and 29.9 are throttle-free to the free atmosphere. When the molding unit 05 is lifted into the compression position, the press rams are then raised by the loosely poured molding material 08 . The low weight of the press ram, which is designed as a hollow body, and the low friction due to the deactivated seals according to FIG. 03, only have a slight pressure on the loose surface of the molding material, so that the press feet 27.2 already have contact with the loose surface of the molding material when the compression process is triggered. Such a mode of operation would not be possible, for example, with a hydraulically driven ram. A white direct compression possibility with the embodiment of FIG. 12 is that in the lowered state of the Preßstem pel the cylinder chambers 25.3, with a correspondingly turned alternate th pressure of the compressed air tank 19 by opening the Preßstem peldüsen be subjected 25.1, wherein the kolbenstangensei term cylinder chambers 29.9 to free Atmosphere are relieved. The molding unit 05 with the loose molding material 08 is then moved against the prestressed press rams, the individual press rams acting as an elastic press plate and the individual press ram being pressed up against the pretensioning in accordance with the molding contour dependent on the model contour. This compression variant, for which only a corresponding control program is to be activated, can also be supported by a fluidization stream drawn in by the vacuum source 84 . In order to avoid a long idle stroke until demolding after compression, a lifting device 30.8 can be provided, which after pressing the filling frame 04 onto the intermediate frame 30.1 ( Fig. 12, left half of the cut) with the holding plates 30.9 against the mold box 03 is driven. The lowering process by the lifting table 13 can thus begin immediately after the compression and after the pressure reduction in the molding chamber 10 and in the press cylinder spaces 25.3 , specifically from the position which the molding box had assumed during compression. After a certain Aussenkhub the pattern plate 01/02 and the lifting device 30.8 to the molding box 03 and the filling frame is lowered 04 times in parallel with the remaining stroke of the pattern plate, whereby the molding box 03 with the overlying filling frame 04 lenbahn the Formkastenrol is deposited 18th

The data records mentioned repeatedly in the description can of course all model-related data for the Ver seal and for other functions. A record is always a model number or the associated model assigned. When changing a model into the molding machine the model number is entered manually or by auto automatic reading activated. The data of the assigned Mon dells are then automatically transferred to the controller and the corresponding actuators are automatically matched to the appropriate values.  

Reference list

01

Model plate carrier

02

Model plate

03

Molded box

04

Filling frame

05

Molding unit consisting of

01

to

04

06

Cavity under model plate

02

07

Model plate nozzles

08

loose molding material

09

Free space above the loose molding material

10th

Molding chamber

11.1

Seal in the intermediate frame

30.1

to the filling frame

04

11.2

Seal in the filling frame

04

to the molding box

03

11.3

Seal in model plate

02

to the molding box

03

11.4

Seal in the model carrier

01

to the model plate

02

11.5

Seal in the model carrier

01

to the lifting table

13

12th

Molding machine base frame

13

Molding machine lifting table

14

Molding machine support columns

15

Molding machine head frame

16

lower model plate roller conveyor

17th

Upper swiveling model plate roller conveyor

18th

Mold box roller conveyor

19th

Compressed air tank

20.1

Housing for the compressed air tank

19th

20.2

Base plate for the compressed air tank

19th

20.3

Head plate for the compressed air tank

19th

20.4

Cylinder tube to the compressed air tank

19th

20.5

Openings to the compressed air tank

19th

20.6

Openings to the compressed air tank

19th

20.7

Openings to the compressed air tank

19th

8/20

Cylinder rooms for the compressed air tank

19th

20.9

Cylinder rooms for the compressed air tank

19th

21.1

Working piston for valve lifter lifting device

Fig.

01

21.2

Damping rubber for valve lifter lifting device

Fig.

01

21.3

Guide piston to the valve lifter lifting device

Fig.

01

April 21

Connection pipe to the valve lifter lifting device

Fig.

01

21.5

Lift frame for valve lifter lifting device

Fig.

01

21.6

a Valve carrier shafts for the valve lifter lifting device

Fig.

01

21.6

b Valve support shafts for the valve lifter lifting device

Fig.

01

21.7

Openings in

21.5

to the valve lifter lifting device

Fig.

01

21.8

Openings in

21.5

to the valve lifter lifting device

Fig.

01

21.9

Openings in

21.6

to the valve lifter lifting device

Fig.

01

22.1

Tandem cylinder to limit the stroke of the lifting frame

21.5

22.2

Piston to the tandem cylinder

22.1

/

35.4

22.3

Lifting dimension for full lifting of the lifting frame

21.5

22.4

Lifting dimension for shortened lifting of the lifting frame

21.5

22.5

maximum opening dimension d / 4 for the valve lifter

24.1

22.6

maximum opening dimension for the valve tappet

23.1

22.7

Cylinder space between the pistons

21.1

and

22.2

23.1

elastic valve lifters

23.2

Steel core to the valve lifter

23.1

23.3

Tensioning and support disc for the valve tappet

23.1

April 23

Fixing screw to the valve lifter

23.1

23.5

Deformation gap to the valve lifter

23.1

23.6

relaxed length to the valve lifter

23.1

23.7

stretched length to the valve lifter

23.1

24.1

Valve tappet with drag pin

24th

,

2

Valve plate to the valve lifter

24.1

24.3

Seal to the valve lifter

24.1

24.4

Trailing pin to the valve lifter

24.1

24.4

a Hexagon on the drag pin to the valve lifter

24.1

24.5

Damping disc to the valve lifter

24.1

24.6

Bearing bush to the valve lifter

24.1

24.6

a Key holes on the bearing bush to the valve lifter

24.1

24.7

Damping disc to the valve lifter

24.1

24.8

Impact disc to the valve lifter

24.1

24.9

Driving plate to the valve lifter

24.1

25.1

Laval nozzles

25.2

Impact cup for free jet

25.3

Press cylinder rooms under the Laval nozzles

25.4

Nozzle inlet diameter on the Laval nozzle

25.5

Throttle-free inlet opening for the Laval nozzle D / 4

25.6

Lifting dimension for drag pins

24.4

25.7

Laval nozzle grid for press ram cylinders

25.8

Laval nozzle grid for compressed air impulse channels

25.9

Anti-rotation device for lifting frames

21.5

26.1

Cylinder block for press rams

26.2

Cylinder bores for press rams

26.3

Through channels for compressed air pulse

April 26

Compressed air channels on the piston rod side for press rams

26.5

Distribution pipes for compressed air ducts

April 26

26.6

piston-side compressed air channels for press rams

26.7

Distribution pipes for compressed air ducts

26.6

27.1

Ram

27.2

Press foot to the press ram

27.1

27.3

Piston rod to the press ram

27.1

April 27

Piston support part to the press ram

27.1

May 27

stepless transition from piston rod to press foot

27.6

Tab for fastening the cylinder cover

29.3

/

32.4

27.7

Screw for fastening the tab

27.6

28.1

Piston to the ram

27.1

28.2

Seal carrier to the press ram

27.1

28.3

Baffle plate to the press ram

27.1

April 28

End plate to the press ram

27.1

28.5

upper damping rubber to the press ram

27.1

28.6

Piston seal to the ram

27.1

28.7

Piston sliding rings for the press ram

27.1

28.8

Cap nut for the stamp

27.1

28.9

Leakage channel in the lens

April 28

respectively.

May 31

29.1

Piston rod bearing for press ram

27.1

29.2

Seal carrier to the press ram

27.1

29.3

Cylinder cover for the ram

27.1

29.4

Piston rod seal 1 to the press ram

27.1

29.5

Piston rod seal 2 to the press ram

27.1

29.6

Piston rod scraper for press ram

27.1

29.7

Piston rod sliding rings for the press ram

27.1

29.8

lower damping rubber to the press ram

27.1

29.9

cylinder chamber on the piston rod side to the press ram

27.1

30.1

Intermediate frame to the cylinder block

26.1

30.2

Diamond tubes for fluidizing airflow

30.3

Mounting flange for diamond tube

30.2

April 30

Inflow opening for diamond tube

30.2

30.5

Distribution channel for the diamond tubes

30.2

30.6

Residue press foot

27.2

/ Intermediate frame

30.1

,

Fig.

02

30.7

Filling frame distance 0

4

/ Intermediate frame

30.1

,

Fig.

12th

30.7

a distance of presser foot

27.2

/ Fill frame 0

4

,

Fig.

12th

30.8

Mold box lifting device

Fig.

12th

30.9

Holding plate for the mold box lifting device

30.8

,

Fig.

12th

31.1

Piston to the ram with activatable seals

31.2

Intermediate ring for press ram with activatable seals

31.3

Intermediate ring for press ram with activatable seals

April 31

Baffle plate for press ram with activatable seals

May 31

End plate for press ram with activatable seals

31.6

Activation channels in

31.1

,

31.3

,

April 31

,

May 31

July 31

activatable piston seals

32.1

Piston rod bearing for pressing. with activatable seal.

32.2

Intermediate ring to the press. with activatable seal.

32.3

Intermediate ring to the press. with activatable seal.

32.4

Cylinder cover for pressing. with activatable seal.

32.5

Activation channels in

32.1

,

32.2

,

32.4

32.6

activatable piston rod seals

32.7

Slot nozzle in

32.4

33.1

vertical holes for press ram control

33.2

horizontal holes for press ram control, left

33.3

horizontal holes for press ram control, right

33.4

Distribution channel to the horizontal holes

33.2

33.5

Distribution channel to the horizontal holes

33.3

34.1

Guide tube to the valve lifter lifting device

Fig.

10

34.2

Guide belts for valve lifter lifting device

Fig.

10

34.3

Valve lifter seals

Fig.

10

34.4

Dirt scraper for valve lifter lifting device

Fig.

10

34.5

Headstock too

20.1

to the valve lifter lifting device

Fig.

10

34.6

Cylinder tube for valve lifter lifting device

Fig.

10

34.7

Interior guide tube for valve lifter lifting device

Fig.

10

34.8

Connecting washer

1

to the valve lifter lifting device

Fig.

10

34.9

Connecting washer

2

to the valve lifter lifting device

Fig.

10

35.1

Additional cylinder for valve lifter lifting device

Fig.

10

35.2

Additional piston for valve lifter lifting device

Fig.

10

35.3

Connecting rods to the valve lifter lifting device

Fig.

10

35.4

Tandem cylinder for valve lifter lifting device

Fig.

10

35.5

Damping disc for valve lifter lifting device

Fig.

10

35.6

small space under the additional piston

35.2

to the valve lifter lifting device

Fig.

10

35.7

Upper piston chamber to the valve lifter lifting device

Fig.

10

36.1

Head plate for valve lifter lifting device

Fig.

11

36.2

Cylinder plate for valve lifter lifting device

Fig.

11

36.3

Cylinder bore for valve lifter lifting device

Fig.

11

36.4

partitioned pressure chamber for valve lifter lifting device

Fig.

11

36.5

Ring channels in the head plate for the valve lifter lifting device

Fig.

11

36.6

Channels in the top plate to the valve lifter lifting device

Fig.

11

36.7

Upper cylinder cover for valve lifter lifting device

Fig.

11

36.8

lower cylinder cover for valve lifter lifting device

Fig.

11

36.9

Fastening the cylinder cover to the valve lifter lifting device

Fig.

11

37.1

Piston for valve lifter lifting device

Fig.

11

37.2

Piston rod for valve lifter lifting device

Fig.

11

37.3

Piston rod shaft for valve lifter lifting device

Fig.

11

37.4

Openings in the piston rod to the valve lifter lifting device

Fig.

11

37.5

Damping rubber for valve lifter lifting device

Fig.

11

37.6

Upper piston chamber to the valve lifter lifting device

Fig.

11

38.1

Piston slide rings for the valve lifter lifting device

Fig.

11

38.2

Piston seals 2 to the valve lifter lifting device

Fig.

11

38.3

Piston rod bearing for valve lifter lifting device

Fig.

11

38.4

Piston rod sliding rings for valve lifter lifting device

Fig.

11

38.5

Piston rod seals for the valve lifter lifting device

Fig.

11

38.6

Relaxation stroke to the valve lifter lifting device

Fig.

11

Pneumatic units

40

Compressed air network with a network pressure of approx. 7 bar

41

Maintenance unit

42

Main valve to the pulse system

43

Pressure regulator to the pulse system

44

Pressure sensor to the pulse system

45

Storage boiler to the pulse system

46

Close valve lifter switching valve

47

Pneumatic oiler for

21.1

/

3rd

48.1

/

2

Fast switching valve for working pistons

21.1

49

Switch valve for system changeover

45

50

Switch valve for system changeover

52

51

Pressure regulator for fluidization

52

Storage boiler for fluidization

53

Pressure sensor for fluidization

54

Compressed air lubricator

55

Switch valve for press ram lubrication

56

Oil reservoir

57.1

/

2

Throttling orifices for lubricating oil

58.1

/

2

Check valve for lubricating oil system

59

Switch valve for press ram control

60.1

/

2

Throttling orifices for press ram control

61.1

/

2

Pressure sensor for press ram control

62.1

/

2

Check valves for press ram control

63

Pressure regulator for baling pressure

64

Switching valve for baling pressure

65

Check valve for baling pressure

66

Throttle valve for baling pressure

67

,

1

/

2

Switch valve for cylinder rooms

25.3

68

Pressure sensor for baling pressure

69

Pressure sensor for press ram raised

70

check valve

71

Raise the control valve of the press ram with network pressure

72.1

/

2

Switch valve cylinder rooms

29.9

relieve the atmosphere

73.1

/

2

Switch valve cylinder rooms

29.9

relieve to the vacuum source

74

Safety valve for cylinder rooms

29.9

75

Switch valve for switching pressure system

40

to

45

76

Check valve for fluidization

77

Switching valve for fluidization

78

Aspirate switching valve fluidization from atmosphere

79

Throttle valve for pressure gradient when fluidizing

80

Switching valve for blowing in from below

81

Switching valve for fluidization after blowing in from below

82

Throttle valve for fluidization after blowing in from below

83

Switching valve fluidizing to the atmosphere or vacuum source

84

Vacuum source

85.1

/

2

Relieve mold valve switching valve

86.1

/

2

Relieve the throttle valve of the molding chamber

87

Mold chamber pressure sensor

88

Compressed air lubricator for additional pistons

89.1

/

2

Switch valve for additional cylinder on the piston side

Fig.

10

90.1

/

2

Switching for additional cylinder on the piston rod side

Fig.

10

91

Pneumatic oiler for

37.1

/

2

92

Fast switching valves for individual drives of the valve lifters

Hydraulic units

101

Check valve, network

102

Check valve, tank

103

Switching valve for pistons

22.2

(

Fig.

01) or

35.5

(

Fig.

10)

104

Safety valve

105

Bladder accumulator for pressure peak damping

Cross reference to the figures

Claims (36)

1. A method for compressing molding materials (e.g. foundry mold sand) within a closed, to the atmosphere sealed molding chamber, which consists of a model plate provided with ventilation nozzles, a molding box and a filling frame and the top of which by applying to a compression device can be closed and the loose, filled molding material is compressed by the action of a compressed air surge fed by a compressed air reservoir and by mechanical repressing, characterized in that
that the individual rams 27.1 of a multi-ram system are each accelerated up to 800 m / sec ² by a compressed air-operated free jet from a Laval nozzle 25.1 or by a blast of compressed air from a large-area cylindrical opening, and the molding material compression by the kinetic energy of the individual rams 27.1 in the form of a Most pel press pulse occurs,
that in addition to the multi-stamp press pulse, a synchronously running compressed air pulse can be brought into effect on the molding material via a Vieldüsensy system consisting of Laval nozzles 25.1 or large cylindrical openings, whereby a synchronized and thus single-stage compression effect can be brought about by a timed switch-on sequence between the multi-stamp press pulse and compressed air pulse of the two impulses it follows and
that the flow state of the molding material is maintained during the compression process without interruption until almost the final compression due to the synchronous and single-stage compression effect. 2. The method according to claim 1, characterized in that the multi-die system for the multi-die press pulse in a grid 25.7 and the multi-nozzle system for the Druckluftim pulse in a staggered intermediate grid 25.8 is arranged area-wide above the surface of the molding material. 3. The method according to claims 1 and 2, characterized in that the Laval nozzles 25.1 or cylindrical openings for the multi-stamp press pulse and for the compressed air pulse are arranged within the base plate 20.2 , whereby an immediate and for triggering the compression process in the shortest possible way largely lossless connection between the compressed air container 19 on the one hand and the press cylinder chambers 25.3 and the compressed air pulse channels 26.3 is released on the other. 4. The method according to claims 1 to 3, characterized in that
that the multi-stamp press pulse and the compressed air pulse are fed from a common compressed air tank 19 and
that the adjustable on the pressure regulator 43 , before the Verdichtervor pending output pressure in the compressed air tank 19 is a maximum of 8 bar, preferably 3 to 6 bar. 5. The method according to claims 1 to 4, characterized draws, that the compression process optionally with the combination of Multi-stamp press pulse and compressed air pulse or only with that Multi-stamp press pulse or only with the compressed air pulse is feasible. 6. The method according to claims 1 to 5, characterized in that after the multi-stamp press pulse and with the start of the pressure reduction in the molding chamber 10, a continuous and continuous transition to static pressing by means of the press ram 27.1 , the pressure in the Piston chambers 25.3 up to the network pressure of 8 bar or via an additional pressure intensifier up to a pressure of 12 bar can be increased by the approximately the same diameter of the cylinder 26.2 and the presser foot 27.2, a high pressure pressure of 120 N / cm ² can be reached. 7. The method according to claims 1 to 6, characterized in that the compression process, a fluidization air flow can be pre-switched, the area over the diamond tubes 30.2 with a large number of small openings and evenly ver shares in the loose molding material 08 and is injected without recognizable Effect of a pre-compression fluidized and homogenized the loose molding material 08 and flows back to the free atmosphere via the model plate nozzles 07 , and which follows the compression process in a continuous and continuous transition. 8. The method according to claims 1 to 7, characterized in that the ram 27.1 can all be started at the same time, resulting in a plane-parallel lifting front of the ram, or that the ram 27.1 can be started at different times, with a professional Liert Hubfront results and what can be compensated for by the model contour and / or by the molded box edge position differing compression strokes so that they largely achieve their final compression at the same time, which significantly contributes to a stress-free and homogeneous compression. 9. The method according to claims 1 to 8, characterized in that the accelerating force on the individual ram 27.1 with the same Laval nozzles 25.1 or the same cylindrical openings is the same size and that since syn presses are simultaneously accelerated by the respectively started ram . 10. The method according to claims 1 to 9, characterized draws, that the outside nozzles for the press ram and enlarge for the compressed air pulse compared to the interior ßert can be through a higher energy supply and there due to higher acceleration force, the molding material friction on To compensate the edge of the molding box. 11. The method according to claims 1 to 10, characterized in that the air jets emerging from the channels 26.3 for the compressed air pulse are divided by the diamond tubes 30.2 ( Fig. 08) and thereby mix in the region of the free space 09 to form a uniform pressure wave. 12. Apparatus for carrying out the method according to claims 1 to 11 , consisting of a molding unit 05 , a lifting table 13 for vertical movement of the molding unit 05 and for pressing the molding unit 05 against a compression device, a housing 20.1 forming the compressed air container 19 , a lower one Base plate 20.2 with nozzles 25.1 arranged in the grid therein for triggering a compressed air pulse, an upper head plate 20.3 with a cylinder 20.4 arranged therein and a lifting device 21.1 to 21.5 guided in the cylinder 20.4 with valve tappets 23.1 attached thereto for opening and closing the nozzles 25.1 , characterized in that
that under the base plate 20.2 is a cylinder block 26.1 is angeord, which has a plurality of cylinder bores 26.2 in a grid 25.7 for receiving the ram 27.1 of the most pelsystem and in a further intermediate grid 25.8 has a plurality of through channels 26.3 for the compressed air pulse,
that in the base plate 20.2 are arranged in a congruent grid to 25.7 and 25.8 Laval nozzles 25.1 , the Laval nozzles 25.1 assigned to the grid 25.7 opening directly into the piston-side spaces 25.3 of the cylinder 26.2 and the Laval nozzles 25.1 assigned to the grid 25.8 directly into the through- channels 26.3 for muzzle the compressed air pulse,
that the bottom plate 20.2 forms the lower end of the compressed-air container 19 and thereby results in an immediate and almost loss-free connection between the compressed-air container 19 and the piston-side cylinder spaces 25.3 and the through-channels 26.3 via the Laval nozzles 25.1 ,
that the Laval nozzles 25.1 can be closed by the valve lifters 23.1 / 24.1 and opened for the compression process by suddenly lifting the valve lifters 23.1 / 24.1 , the Laval nozzles 25.1 being opened for the compressed air pulse after a short delay or after the preliminary stroke 25.6 to achieve a synchronous compression effect of a lot of stamp press pulse and compressed air pulse and
that the cylinder block 26.1 has an intermediate frame 30.1 in the lower area, with which the free space 09 for the press ram feet 27.2 , for the diamond tubes 30.2 and for the spreading of the compressed air pulse wave is formed and on which the filling frame 04 is pressed and removed via the seals 11.1 is sealed. 13. The apparatus according to claim 12, characterized in that instead of the Laval nozzles 25.1 also large-area cylindrical bores or a combination of Laval nozzles 25.1 and large-area cylindrical bores can be provided, the cross section of a large-area cylindrical Boh tion up to 40% of the cross section of a cylinder bore Is 26.2 . 14. Device according to claims 12 and 13, characterized in
that the press die 27.1 has a circular press foot 27.2 with a conical press surface,
that the presser foot 27.2 tapers conically in a cylindrical part to the piston rod diameter and merges smoothly into the piston rod 27.3 ,
that the conical transition from the presser foot to the piston rod 27.3 to avoid mold deposits has a Kegelwin angle of a maximum of 60 degrees and
that the entire surface of the presser foot and the surface of the piston rod are hard chrome-plated in order to avoid or substantially reduce the sticking of the molding material 15. Device according to claims 12 to 14, characterized in that the press ram 27.1 preferably have a lightweight design to reduce the mass to be accelerated, the presser foot 27.2 , the piston rod 27.3 and the piston carrier part 27.4 are formed as a hollow body and of a steel material are made and the piston parts 28.1 / 2/4 and 31.1 / 2/3/5 are made of a light metal material. 16. The device according to claims 12 to 15, characterized in
that the piston rod bearing 29.1 has a vulcanized damping rubber 29.8 , whereby the downward movement of the press ram 27.1 is damped if the molding material filling is too low,
that the piston end plate 28.4 / 31.5 has a vulcanized damping rubber 28.5 , with which the end stop is damped during the upward movement of the ram 27.1 , and
that the damping rubber 28.5 together with the piston end plate 28.4 and the spherical cap nut 28.8 forms an impact cup 25.2 for the free jet emerging from the Laval nozzle 25.1 at supersonic speed. 17. The device according to claims 12 to 16, characterized in
that the press rams 27.1 preferably have activatable seals 31.7 and 32.6 in order to reduce the friction losses during the acceleration phase triggered by the action of the jet,
that the activatable seals 31.7 and 32.6 are expanded by the action of a certain pressure and pressed against the surfaces to be sealed,
that the activatable seals 31.7 and 32.6 withdraw from the surfaces to be sealed due to their elasticity in the non-pressurized state,
that the expansion of the seals 31.7 and 32.6 by the compressed air from the respective pressurized rooms 10 / 32.7 , 25.3 or 29.9 takes place and
that the compressed air for widening the seals via the channels 31.6 or 32.5 is brought into effect in the respective interior spaces between the seal 31.7 and the intermediate ring 31.3 or between the seal 32.6 and the intermediate ring 32.2 . 18. Device according to claims 12 to 17, characterized in
that before triggering the multi-stamp press pulse, the piston-side cylinder spaces 29.9 completely relieved of pressure and who
that the ram 27.1 before triggering the multi-ram press pulse by applying a slight negative pressure in the cylinder spaces 29.9 or a slight excess pressure in the cylinder spaces 25.3 are brought from the state of static friction into the state of sliding friction. 19. Device according to claims 12 to 18, characterized in
that for opening and closing the Laval nozzles 25.1 or the alternatively usable cylindrical bores, directly opening valve lifters 23.1 for the multi-plunger pressure pulse and delayed opening valve lifters 24.1 for the compressed air pulse are used in order to achieve a synchronous compression effect of the multi-piston press pulse and compressed air pulse.
that the valve lifters 23.1 and 24.1 are arranged via the shafts 21.6 a / b on a lifting frame 21.5 provided with through-flow openings 21.7 / 21.8 / 21.9 ,
that the directly opening valve lifters 23.1 consist of an elastic material (e.g. rubber), which is compressed when closed and relaxes again when opened, and as a result the valve lifter 23.1 after the expansion stroke (dimension 23.6 minus dimension 23.7 ) with an already definite one Speed suddenly lifts off the valve seat,
that the valve lifter deformation runs largely smoothly to the support disk 23.3 through the gap 23.5 in the open state,
that the valve tappets 24.1, which open with a delay, each consist of a valve plate 24.2 with a vulcanized-on seal 24.3 , a damping disk 24.5 and a drag pin 24.4 with a driving disk 24.9 attached thereto,
that the trailing pin 24.4 is guided in a bush 24.6 inserted in the lifting frame 21.5 / 21.6 b,
that on the bushing 24.6 a rubber damping disc 24.7 and an impact-resistant plastic impact disc 24.8 rests, which detects the driving disc 24.9 after the stroke 25.6 and thereby the valve plate 24.2 / 24.3 suddenly lifts off from the valve seat at an already definite speed and
that after the full stroke 22.3 of the lifting frame 21.5 there are the opening gaps 22.5 and 22.6 , an opening gap bearing at least a quarter of the nozzle inlet diameter 25.4 (D / 4). 20. Device for performing the method according to claims 1 to 11, with a lifting frame from a lifting frame 21.5 and attached valve lifter, a lifting and guiding piston 21.1 to 21.4 and a lifting frame anti-rotation device 25.9 best existing lifting device for opening and closing a raster nozzle system used for molding compression, characterized in that
that the lifting frame 21.5 is connected to a guide tube 34.1 designed as a working piston which is guided in a cylinder 34.6 projecting into the compressed air tank 19 and integrated in the head plate 34.5 and the interior 34.7 of which is part of the compressed air tank 19 through the openings 20.5 , 20.6 and 21.7 ,
that the guide tube 34.1 is under the pressure of the compressed air container 19 and thereby exerts an upward force on the lifting frame 21.5 and on the valve lifters 23.1 attached to it,
that the valve tappet 23.1 by the pressure of the compressed air tank 19 exert a downward force on the stroke frame 21.5 , the surface ratios between the guide tube 34.1 and the Ven tilstößeln 23.1 is greater than the upward force of the guide tube 34.1 , so that the valve lifters 23.1 are held intrinsically safe in the closed position without additional force,
that an additional cylinder 35.1 is arranged on the head plate 34.5 , the piston 35.2 of which is forcibly connected to the guide tube 34.1 via the connecting disks 34.8 and 34.9 , the piston 35.2 being depressurized on both sides in the idle state and exerting no force on the guide tube 34.1 ,
that the piston 35.2 for lifting and accelerating the Hubrah mens 21.5 and the valve lifters 23.1 and 24.1 is relieved of the piston chamber 35.7 via the valves 90.1 / 2 with the network pressure 40 , whereby an additional upward-directed force acts on the guide tube 34.1 , which acts together with the force exerted by the guide tube 34.1 forms a total, upward lifting force which is greater than the locking force of the valve lifter and which causes an abrupt lifting and accelerating of the lifting frame 21.5 with the valve lifters 23.1 and 24.1 attached to it,
that the piston 35.2 for lowering the lifting frame 21.5 or for closing the nozzles when the lower piston chamber is relieved is acted upon by the network pressure 40 via the valves 89.1 / 2 , where a downward force acts on the guide tube 34.1 which is greater than the force exerted upwards by the guide tube 34.1 , as a result of which the valve lifters 23.1 and 24.1 are pressed onto their valve seat and, after the intrinsically safe closing of the valve lifters 23.1 has been set, the upper piston chamber 35.7 is relieved again via the valves 89.1 / 2 ,
and that the diameter of the additional cylinder 35.1 can be kept correspondingly small by the partial lifting force of the guide tube 34.1 , which means that the volume of compressed air to be controlled and thus the pressure build-up time is substantially reduced and the opening speed of the valve lifter is increased significantly. 21. The apparatus according to claim 20, characterized in
that one or more valves 89.1 / 2 are attached directly to the upper cylinder flange for quick control of the upper cylinder space 35.7 ,
that one or more valves 90.1 / 2 are attached to the lower cylinder flange for quick control of the lower cylinder chamber in order to achieve a rapid stroke reaction for the sudden opening of the valve lifters and
that the piston 35.2 in its lower starting position has a very small distance 35.6 from the cylinder flange in order to achieve a rapid pressure build-up and a rapid stroke reaction for the sudden opening of the valve lifters. 22. Device according to claims 20 and 21, characterized in
that the lifting frame 21.5 runs through the total stroke 22.3 in order to trigger the multi-stamp press pulse and the compressed air pulse or
that the lifting frame 21.5 only passes through the partial stroke 22.4 in order to trigger only the multi-ram press pulse
that the additional cylinder 35.1 has a tandem cylinder 35.4 , the piston 22.2 in the extended state as an end stroke limits the partial stroke 22.4 and
that the piston 35.2 has a damping rubber 35.5 , whereby the end stop on the tandem piston 22.2 or on the upper cylinder flange is damped. 23. Device for carrying out the method according to claims 1 to 11, with individually driven valve tappets for opening and closing a grid system arranged and used for compression molding, characterized in that
that each individual drive has a piston 37.1 with a damping rubber 37.5 , a piston rod 37.2 , an elastically deformable valve tappet 23.1 , and an integrated, electrically operated quick-switching valve 92 in the cylinder cover 36.7 ,
that the differential areas formed by the pistons 37.1 and the piston rods 37.2 on the piston undersides are continuously acted upon by the pressure 40 present in the sealed-off pressure chamber 36.4 ,
that the quick-acting valve 92 37.6 acted upon in the off state the piston chamber pressure with the network 40 and thereby exerted downward closing force on the valve stem 23.1,
that the quick-acting valve 92 suddenly releases the piston chamber 37.6 towards the free atmosphere, causing an upward opening force to act on the valve tappet 23.1 , which is further supported by the resilience of the elastic valve tappet and as a result of which the valve tappet 23.1 abruptly from the valve seat is lifted off
that the quick-switching valves 92 for the compressed air pulse are switched on with a time delay compared to the quick-switching valves for the multi-stamp press pulse in order to bring about a synchronous compression effect of the two pulses,
that the individual quick-switching valves 92 for the multi-punch press pulse can be switched on individually at different times in order to bring about a profiled lifting front adapted to the model contour or an otherwise profiled lifting front of the press rams 27.1 / 27.2 ,
that only the quick-switching valves 92 for the multi-stamp Fre ßimpulse are turned on to be able to perform the compression process only with the multi-stamp press pulse and without the compressed air pulse and
that only the quick-switching valves 92 are switched on for the compressed air pulse in order to be able to carry out the compression process only with the compressed air pulse and without the multi-stamp press pulse. 24. The device according to claim 23, characterized in
that the piston rod 37.2 consists of a tube and the Kol benstangeninnenraum through the openings 37.4 is part of the compressed air tank 19 ,
that on the lower piston rod shaft 37.3 an elastically deformable z. B. rubber valve tappet 23.1 is attached, which is compressed when closing and which relaxes again when opened, whereby the valve tappet 23.1 after the expansion stroke 38.6 (measure 23.6 minus measure 23.7 ) suddenly lifts off from the valve seat with an already definite speed and
that the valve lifter deformation runs largely smoothly to the support disk 23.3 through the gap 23.5 in the open state. 25. Device according to claims 23 and 24, characterized in
that the individual valve tappet 23.1 resulting from the pressure difference between the pressure of the compressed air tank 19 and the atmospheric pressure below the base plate 20.2 resulting closing force and by a further closing force of the piston 37.1 is pressed intrinsically safely onto its valve seat and
that the individually driven valve lifters 23.1 in the press pelraster 25.7 and in the compressed air pulse grid 25.8 are arranged and have an opening stroke 25.5 of D / 4 (D 25.4 ). 26. Device according to claims 23 to 25, characterized in
that the top plate 36.1 / 36.2 of the compressed air tank 19 Zylin derbohrungen 36.3 for the piston 37.1 and a compressed air tank 19 to the pressure chamber 36.4 has,
that the sealed-off pressure chamber 36.4 is connected to the compressed air network 40 via the channels 36.6 and to the cylinder spaces below the pistons 37.1 via the annular gaps 36.5 and
that the piston rod bearings 38.3 / 38.4 and the piston rod seals 38.5 in the bottom plate of the sealed pressure chamber 36.4 are arranged. 27. Device for carrying out the method according to claims 1 to 11, with a control device for monitoring the raised position of the press ram 27.1 and for releasing the mold box and filler frame transport, characterized in that
that the base plate 20.2 has the vertical bores 33.1 , which are closed by the damping rubbers 28.5 of the individual press rams 27.1 in the upper ram position by the pressure in the piston rod-side cylinder spaces 29.9 ,
that an outgoing from the valve 59 compressed air pulse, the ge over the throttle orifices 60.1 / 2 and the horizontal bores 33.2 / 3 up to the closed vertical channels 33.1 , causes a dynamic pressure, whereby the pressure sensors 61.1 / 2 respond and the raised position of all the pressing system pel 27.1 is confirmed
that with at least one not fully raised press ram 27.1 with the vertical bore 33.1 not closed, the compressed air flow proceeding from the valve 59 and passing through the throttle diaphragms 60.1 / 2 without a backlog effect via the corresponding piston chamber 25.3 , via the channels 26.6 / 7 and via the valves 67.1 / 2 flows to the free atmosphere, where the corresponding pressure sensor 61.1 / 2 does not respond and thus no confirmation of the raised ram 27.1 is issued and
that in the further this ram control over one or more circuits with a corresponding number of Dros selblende 60 and pressure sensors 61 can be done. 28. The apparatus according to claim 27, characterized in
that the vertical bores 33.1 and the horizontal bores 33.2 / 3 in conjunction with the valve 55 and the oil container 56 can also be used for lubricating the ram cylinders,
that the lubrication takes place in the form cycle intervals by compressed air loading of the oil container 56 and
that the amount of lubricating oil is determined by the duty cycle of the valve 55 and the aperture size 57.1 / 2 . 29. A method for compacting molding materials (eg foundry mold sand) using the device according to claims 12 to 28, characterized in that
that compressed air from the compressed air tank 19 via the valves 49 and 80 and via the model plate nozzles 07 against the gravity of the molding material 08 is blown into the molding chamber 10 , whereby the molding chamber 10 and the air pores in the molding material 08 put in the state of a higher atmospheric pressure are, this pressure corresponds to the pressure in the compressed air tank 19 ,
that then the piston rod-side press cylinder spaces 29.9 by closing the valve 71 and opening the valve 75 and the piston-side press cylinder spaces 25.3 and the Druckluftim pulse channels 26.3 by opening the Laval nozzles 25.1 with the compressed air tank 19 , whereby all-round pressure equality in the molding chamber 10 , in the compressed air tank 19 and arises in the press cylinder rooms 23.5 and 29.9 and where the press rams 27.1 can lay down with their own weight on the loose farm material,
that at the earliest after the all-round pressure equalization by switching off the valve 80, a compression air flow is initiated, from the compressed air tank 19 , through the molding chamber 10 , via the model plate nozzles 07 , via the valves 80 , 81 and via the switched-off valve 83 to the free atmosphere or alternatively flows via the switched-on valve 83 to a vacuum source 84 ,
that when the compression air flow is switched on, the quay benstang-side press cylinder spaces 29.9 by switching off the valve 75 and by switching on the valves 72.1 / 2 to the free atmosphere or, optionally, by switching on the valves 73.1 / 2 to a vacuum source 84 , who is relieved, whereby the press rams 27.1 are moved downward together with the compression air flow and the molding material 08 is compressed by the synchronous effect of the compression air flow and the pressing force of the downstream press rams 27.1 ,
that after about 70% of the compression time, the Laval nozzles 25.1 are closed and to increase the molding pressure, the piston-side press cylinder spaces 25.3 are acted upon via valve 64 with a higher pressure which can be set on the pressure regulator 63 or on a pressure intensifier, and then with Errei chen this Pressure of the remaining mold chamber pressure, with which the compression air was operated further after closing the Laval nozzles 25.1 , via the valves 85.1 / 2 u. 86.1 / 2 is removed in a controlled manner and then the press rams are moved back to their upper starting position. 30. The method according to claim 29, characterized in that after the pressure equalization and before triggering the compression process, either an adjustable in intensity at the throttle 82 and starting from the pressure vessel 19, the fluidizing stream is passed through the molding material 08 and which is passed through the model plate nozzles 07 , flows off via the switched off valves 80 and 83 and via the throttle 82 to the free atmosphere, the fluidization stream fluidizing and homogenizing the molding material 08 without any recognizable precompression and in a continuous and continuous transition by switching off the valves 75 and 81 and through Switching on valves 72.1 / 2 or 73.1 / 2 the compression process follows. 31. The method according to claims 29 and 30, characterized in that the blowing of the compressed air into the molding chamber 10 with a flat, adjustable on the throttle 79 pressure gradient of 1 to 6 bar / sec, preferably from 2 to 4 bar / sec . 32. The method according to claims 29 to 31, characterized in that the compression process with an adjustable on the pressure regulator 43 and stored in the compressed air tank 19 pressure of a maximum of 8 bar, preferably from 3 to 6 bar is operated. 33. The method according to claims 29 to 32, characterized in that a pressure translator can be used to increase the molding pressure or the pressure in the press cylinder spaces 25.3 beyond the network pressure. 34. The method according to claims 29 to 33, characterized draws, that as a mechanical press device a multi-punch system as well as a single press plate can be used. 35. Device according to claims 1 to 34, characterized ge features that all model-related operating parameters in one of the respective current model number assigned to the data set in the case of a model change through automatic reading of the mo Activate cell number or by manually entering the model number fourth, the operating parameters automatically to the corresponding controls are output and where these controls automatically set to the output value to adjust. 36. Device according to claims 12 to 26, characterized in
that between the filling frame 04 and the intermediate frame 30.1, a spacing 30.7 can be provided in order to enable a movement of the filling frame when the ram 27.1 / 27.2 is completely lowered,
that the press rams 27.1 / 27.2, which are lowered at the start of compression and are in the unpressurized state, lightly press on the loosely filled molding material 08 when the molding unit 05 is lifted and thereby lifted, and then after the filling frame 04 is pressed onto the intermediate frame 30.1, the compression process is triggered and
that to bridge the distance 30.7 a lifting device 30.8 is provided, which is lifted after pressing the filling frame 04 to the intermediate frame 30.1 with the holding plates 30.9 under the molding box 03 , so that the demolding process begins immediately after the compression and the reduction of the compression pressure can, the mold box being placed on the roller conveyor 18 after removal from the mold.