US3359608A - Friction and screw press for the manufacture of ceramic articles - Google Patents

Friction and screw press for the manufacture of ceramic articles Download PDF

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US3359608A
US3359608A US354223A US35422364A US3359608A US 3359608 A US3359608 A US 3359608A US 354223 A US354223 A US 354223A US 35422364 A US35422364 A US 35422364A US 3359608 A US3359608 A US 3359608A
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traverse
press
screw
pressure
hydraulic
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Walchhutter Ulrico
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/18—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by screw means
    • B30B1/22—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by screw means driven through friction disc means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/18—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by screw means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0497—Screw mechanisms

Definitions

  • This invention relates to improvement in friction and screw presses for the manufacture of ceramic articles, as
  • a first object of this invention is to obtain a means to regulate and preestablish one time for all the hoisting of the mobile traverse.
  • Another object of this invention is to obtain the elimination of the so called pastille play between the mobile traverse and the screw end, which requires a supplementary stroke .of the screw, and consequently an increase of the period of time for compressing of the ceramic material.
  • a further object of this invention is to maintain said mobile traverse independent from the press screw at a position the traverse has reached after its first downwards compression stroke, while said screw is recalled upwards in order to be newly thrown downwards for carrying out the second and strong compressing stroke together with said mobile traverse and their cooperating devices, in order to render the press screw lighter, by relieving it from the weight of the mobile traverse and its accessories, and from the work necessary to move these components, thus facilitating the screwing and unscrewing movements of the press screw.
  • Still another object of this invention is to eliminate the electromagnet for controlling the disc for the up and down movement of the press screw, and to replace it by a hydraulic jack, thus simplifying all the equipment of the friction press for its automatic operation.
  • Still a further object of this invention is to control the movement of the mobile traverse of the press by means of hydraulic jacks.
  • An object of the invention is also to obtain the synchronization of the movements of the several components of the machine by means of a sole hydraulic circuit and by using the combination through said hydraulic circuit of the hydraulic devices respectively controlling the movements of the mobile traverse, of the lower plungers of the molds, the mold matrix and the rotating disc.
  • a further object of this invention is to control the said pressure between the first and the second steps of compression in such a manner as to favor the elimination of the air in accordance with the kind and composition of the mass used for, this variation of pressure to be controlled or reduced until a zero value, f.i. in the case of material wherein the expelling of the air takes place spontaneously due to the swelling of the material which is due in turn to the pressure of the air within the mass of material to be compressed.
  • a further object of this invention is to provide for a lubricating system so that the screw and cooperating devices may be forcibly lubricated by making use of the movement of the press screw so that the oil is sucked from an oil container and pressed along the threaded portion of the screw, and exhausted back into the said container.
  • FIGURE 1 is a front view, partially in section of a press according to the invention.
  • FIGURE 2 shows the hydraulic circuit for controlling said press
  • FIGURE 3 represents a view of the mobile traverse sustaining elements, according to a variant of the inventron
  • FIGURE 4 shows the hydraulic circuit controlling the friction and screw press of FIGURE 3.
  • FIGURE 5 illustrates in a larger scale the lubricating system according to the invention.
  • a friction and screw press is composed as usual of a base plate 1, two uprights 2 and 3 projecting from the latter and sustaining at their upper ends a fixed traverse or press head 4 provided with two arms turned upwards in order to support a continuously rotating shaft 5 enabled to be alternately shifted in-axial direction, said shaft bearing two friction discs or wheels 6 and 7, the purpose of which is to frictionally move with a left or right hand rotating movement a flywheel 8 fixedly connected to the upper end of the press screw 9 which is moved downwards and upwards within a threaded bushing located in the center portion of the fixed upper press head 4, so that when one of said friction discs 6 or 7, frictionally engages the flywheel 8 the screw 9 runs upwards and when the otherfriction disc 7 or 6 frictionally engages said flywheel 8 said screw 9 runs downwards in order to effect the compression through the mobile traverse 11 and the respective accessories of the mass within the mold or molds, thus converting the kinetic force of the flywheel into a compressing force onto the mobile traverse.
  • a first light compression step in order to let the air. contained within the mass to be compressed, that is to say between the elements of said mass to go out, and to distribute the latter conveniently within the mold or molds, and
  • a second strong or more energetic compression step in order to impart to the article under treatment the necessary compactness and mechanical resistance so that the article may be used for the purpose for which it is manufactured.
  • the mobile traverse 11 is displaced along both press uprights 2 and 3 and sustains the upper plungers 12 of the molds; this mobile traverse is supported in known similar presses directly at the lower screw end or by means of parallel situated rods in respect of the press screw, said rods being attached to appropriate smaller horizontal controlling rods.
  • the mobile traverse 11 effects a first compressing step, broadly similar to that of the screw, with the exception of a play left between said mobile traverse and the lower end of the screw, said play being normally called pastille play (because it corresponds to the thickness of the article manufactured thereon), and which causes the mobile traverse not to ascend again after the first compression step has taken place, or, at most, to only go up again for a very small distance, but allowing the screw to run during the upwards stroke and the beginning of the final compression step to move in upwards direction a distance equal to said pastille play, thus producing on said screw a supplementary load which corresponds to the weight of the mobile traverse 11 plus the necessary force to move the latter.
  • the mold used pertains to the type molds in which the matrix 13 may be displaced downwards and sustained by means of at least two hydraulic jacks 14 and 15, by taking account that the plungers 12 have dimensions which are larger than those of the corresponding mold cavities.
  • the screw extends at its upper end through a cup-shaped member 19 fastened to the fixed traverse 4 and the upper part of press screw is engaged by bearings 20 of appropriate make carried by cap 19, while its lower part extends through a second cup-shaped member 21, and is engaged by bearings 22 carried'by the second cap 21, whereby the screw is properly guided.
  • a bushing 23 is screwed on the caps 21, and is set once for all to maintain its lower edge which serves as stopping member for the upward movement of the mobile traverse 11 at a selected elevation.
  • the mobile traverse 11 is made mechanically independent from the press screw 9,'and is bilaterally sustained by hydraulic jacks 24 and'25, respectively.
  • Said hydraulic jacks have the task to recall saidmobile traverse 11 upwards after each compression stroke, and to maintain it at its upper position until the press screw 9 will move downwards and move said mobile traverse in the same direction, by overcoming the fluid pressure as there will be explained further hereinafter) within the hydraulic jacks 24 and 25; the latter have also the purpose to stop the mobile traverse at its lower position as the second compression step takes place, this importing a raising and descending step of the screw.
  • the control of the shaft 5, which bears the friction discs or wheels 6 and 7, driving the screw rotation flywheel 8 takes place bymeans of the hydraulic jack 27, through the transmission rod 26, and of its leverage, the purpose of which being to replace the usual electromagnet used in combination with said rod 26, this with the view to simplify the electric or electronic equipment for the automatic operation of the press, whereby an advantage is obtained in the sense that all the protection and controlling devices for said electromagnet are rendered superfluous and consequently abolished.
  • a set of levers forthe rod 26 is intended to act in combination with an arm 28, which is bent in such manner as to extend over the friction disc 7 with the purpose to control the downwards stroke of the screw, this serving to contact the flywheel 8 and following its movements through a small roller 29, said arm being lifted together with the flywheel during the second upwards stroke of the latter in order to control the leverage which in turn controls the rod 26 in order to ensure the exact positioning of the friction disc 7 with respect to the flywheel 8 in order to brake and stop it at the required level.
  • a safety member with the purpose to mechanically brake said flywheel at the end of each one cycle of operations, and furthermore to control the means for the automatic operation of the press.
  • FIGURE 2 shows the hydraulic equipment, with which the press of FIGURE 1 is provided.
  • the hydraulic equipment is constructed to ensure a cooperation of all these hydraulic devices or hydraulic jacks which are necessary to control the friction-screw press in accordance with this invention.
  • Said hydraulic equipment comprises a high pressure pumping set, composed of the pump 30 and the electric motor 31; said pumping set supplies the fluid under pressure to a conduit 32, cooperating with a hydraulic compensator 33'.
  • Conduit 32 is divided into a first conduit 33 to feed the hydraulic jack 27 for controlling the two friction disc 6 and 7 bearing shaft 5, said feeding taking place through an electromagnetic valve 34, which, when turned to one direction, allows the fluid under pressure to reach and invest the hydraulic jack 27, while, when turned to the opposite direction, allows exhausting of the fluid therefrom.
  • a throttle valve Downstream of the electromagnetic valve 34, still in said conduit 33 a throttle valve is inserted, which has a regulatable passage, and a check valve 36 in parallel to the throttle valve, the first one used to control the inlet stream speed of the fluid under pressure into the cylinder of the hydraulic jack 27, and the second to permit a quick exhausing of the fluid.
  • the high pressure conduit 32 is further divided into a conduit 37 which is in turn divided into two conduits, the one 37 being intercepted by an electromagnetic valve 38, and the other 37" being intercepted by an electromagnetic valve 39.
  • the electromagnetic valve 38 controls feeding of pressure fluid into the hydraulic jack 17 in order to control the lifting device of the lower mold plungers or covering plates, or the exhausting of said jack.
  • the electromagnetic valve 39 permits feeding of pressure fluid into the hydraulic jack 18, and in turn its exhausting valve 39 permits at the same time feeding of pressure fluid, through conduits 40, 41, 42 and 43, into hydraulic jack 24 or 25, the one or the other sustaining the mobile traverse 11 of the press, and into hydraulic jack 14 or 15, the one or the other sustaining the mold matrix.
  • Conduit 40 is intercepted by a non-return valve 44 which impedes the return of the fluid under pressure to the conduit 37".
  • Conduit 41 is intercepted by an electromagnetic valve 45 serving to control the opening and closing of a valve 46 used for establishing the maximum pressure checked in order to ensure the communication with the exhaust exclusively when said valve is put under a larger pressure than necessary for operation of the press in question.
  • the usual operation pressure of the press being about atm. (about 13,750 lbs. p.s.i.), said valve will be set for 600 atm. (about 82,500 lbs. p.s.i.).
  • Conduits 41 and 43 communicate with the high pressure conduit 32 through a conduit 47 which is intercepted by a non-return valve 48 permitting the arrival of the high pressure fluid into the high pressure conduit 32 without any possibility of return.
  • Said suspension of the mobile traverse besides giving a supplementary security for the correct operation of the press, also provides for the protection of the filling carriage of the press molds.
  • the hydraulic jacks 24 and 25 are of the double action type. Their cylinders rest on brackets 24' and 25 fastened to the press base plate, while their pistons are connected with the mobile traverse through hinges 24" and 25".
  • two further hydraulic jacks 49 and 500f the single action kindare fed in such a manner as to show the constant tendency to expand.
  • the piston ends of jacks 49 and 50 are provided with regulatable members 51 and 52, the purpose of which 6 is to ensure their exact positioning at the required level.
  • the piston shaft ends 51 and 52 are set at such a level as to ensure the cooperation with the mobile traverse, or eventually with rigid connecting members of said mobile traverse, as the latter is displaced from the position at which it is resting to that position wherein it contacts the molds to the position which it assumes immediately after the complying of the first step of compression, the whole so that within the travel followed by the mobile traverse the cited jacks 49 and 50 are put into the condition to exert a throw upwards against said mobile traverse.
  • the pressure of the fluid to feed the jacks 49 and 50 may be checked once for all in the sense of submitting the throw of said jacks exerted onto the mobile traverse 11 exclusively during this travel.
  • the throw exerted by the hydraulic jacks 49 and 50 i smaller than that exerted downwards by the jacks 24, 25, so that as a general proceeding a downwards throw will take place, the speed of which Will de pend mainly from the importance of the contrasting throw exerted by the jacks 49 and 50.
  • the invention comprises also the case wherein the pressure within the jacks 49 and 50 will reach such a value that the upwards directed throw will be equal to the whole effort produced by the throw of the jacks 24 and 25, as well as deriving from the weight of the mobile traverse itself.
  • FIGURE 4 The hydraulic controlling circuit of the press according to this invention is represented in FIGURE 4, wherein but a variant has been introduced to the arrangement of FIGURE 2.
  • the upper rooms of the jacks 24 and 25 are fed through a conduit 53; in free communication with the high pres-.
  • the lower rooms of said jacks 24 and 25 are fed with high pressure fluid through the conduit 37, the electromagnetic valve 59 and the conduit 40, thus reaching a circuit composed of'two parallel branches.
  • the first one, 54, of these branches ensures a-direct feeding of the jacks as the electromagnetic valve 39 opens.
  • the other of said branches,-55 comprises the electro-magnetic valve 45 which, when closed, impedes the return of, pressure fluid to the conduit 40, while, when opened, it permits said return, comprising further the valve 46 set for the maximum pressure of operationof the press, besides of a throttle valve 56 to be checked at will, and connected in parallel with a further valve 57.
  • valve 57 is controlled by mechanical means, more precisely by means of a cam 58 provided on the mobile traverse 11 (FIGURE 3).
  • Theposition of valve 57 is such that it is closed shortly before the upper plungers of the molds, 12, contact the matrix, thus forcing the fluid to exhaust through the throttle valve 56, so that the last portion of the downwards stroke is submitted to braking with the purpose to avoid a too hard engagement of the plungers with said matrix.
  • Both hydraulic jacks 14 and 15, which sustain the matrix, are fed through two hydraulic circuits, the first of which is formed by the electromagnetic valve 39 and the conduit 40, further comprising a throttle valve 59, a nonreturn valve 60 and a cock 61.
  • the second of these hydraulic circuits derives fromthe compression conduit 32 and comprises a non-return valve 62 and a throttling plungers should lower onto the molds, the latter in turn lowering so as to cause the exhausting of a small quantity of fluid past valve 64 and cock 65 back to the conduit 32.
  • valve 39 Although the communication with the valve 39 remains open, the hydraulic jacks 14 and 15 do not receive any pressure fluid, because the valve 39due to the lowering of the mobile traverse 11- in the exhausting position, such that the matrix remains lowered and consequently doesnt follow the movements of the upper plungers, which thus are enabled to detach from them, also only for a short portion of the upwards stroke.
  • the hydraulic jacks 49 and 50 are fed from a hydraulic circuit derived from the high pressure conduit 32.
  • a cock 66, a safety valve 67 with an according gauge 68 for controlling the pressure value, and a pressure accumulating device 69 are foreseen in connection with this feeding conduit.
  • the safety valve 67 is regul'atable, so that once it has been set for a certain value there will be no possibility for the hydraulic circuit to surpass the preestablished limit of the pressure.
  • conduit 70 which will be equal to that which was set by means of the safety valve 67 and controlled by the gauge 68, after which the cock 66 will be closed again in order to provide in this way a blocked circuit in condition to feed a constant pressure to the hydraulic jacks 49 and 50.
  • the variations of volume within the interior of the jack rooms, and which will be due to the effort of the mobile traverse during its'downwards stroke, will be compensated by the pressure accumulator 69.
  • a complete cycle of compression operations obtained by means of the hereabove mentioned equipment comprises the following steps:
  • valves 38 and 39 are open at the beginning; their task is to maintain jacks 17 and 18 under pressure, such that the lower plungers of the molds are located at the level of the matrix.
  • the lower rooms of jacks 24 and 25 are under pressure.
  • the matrix is lifted, since the jacks 14 and 15 are under pressure, due to feeding of pressure fluid through the cock 65, and through the cock 61.
  • the filling carriage which is not represented for being universally known, will now move forward, consequently discharging from the press the tiles manufactured in the preceding cycle of operations.
  • the electromag netic valve 38 is moved to its exhaust position, such that jack 17 lowers, and the plungers are moved to the position of filling, thus permitting the filling operation by said carriage.
  • the latter is then moved back and as soon as it is outside the matrix zone, the valve 39 is moved to its exhausting position, thus causing the lowering of the hydraulic jack 18, and the plungers to rest onto the base plate of the press.
  • valve 39 is in exhaust position, the electromagnetic valve 45 will open, so that the pressure fluid discharges from the lower rooms of the jacks 24 and 25 thus traversing quickly the throttle member 56 and the corresponding valve 57.
  • member 58 controls the valve 57 in order to have it in blocking position, so that the pressure fluid will be constrained to travel only through the throttle member 56, thus considerably reducing the speed of the mobile traverse to avoid a too rapid engagement of the plungers 12 with the matrix.
  • the mobile traverse may smoothly contact said matrix, which is in turn also lowered, thus forcing some pressure fluid to discharge from the hydraulic jacks 14 and 15.
  • the matrix can also be further subjected to a movement by means of the jacks 14 and 15, or be brought to a stop, respectively.
  • the mobile traverse will eflect the compression of the material in the mold by also exerting a force resulting from the action of the hydraulic jacks 24 and 25 plus its own weight against the counterforce provided by the jacks 14 and 15.
  • a first compression step pressure fluid fed into jack 27 causes axial displacement of shaft 5 of the two friction disc 6, 7 in order to start rotation of the flywheel 8, which in turn causes downward movement of the mobile traverse 11.
  • the speed of this downward movement has to be regulated according to the kind and composition of the mass of ceramic material to be compressed, imparting to said flywheel a more or less forced braking action before any further compression occurs, by moving the jack 27 to its exhausting position.
  • This step of compression causes the reduction of the thickness of the mass within the press molds, such that both the mobile traverse 11 and the upper mold plungers 12 move from the position of precompression to a lower level.
  • the flywheel 8 is inverted in its rotation, so as to be recalled upwards, thus drawing again in the same direction its screw 9.
  • the mobile traverse meets the shaft ends 51 and 52 of the hydraulic jacks 49 and 50, which impart to the mobile traverse an opposed throw.
  • the jacks 14 and 15 are fed from the hydraulic circuit which connects them to the condu t 32, such that the matrix is maintained to rest with force against the upper plungers 12, while the counterpressure produced by the jacks 49 and 50 will be maintained smaller than the total force exerted by the mobile traverse.
  • the jacks 14 and 15 are fed with fluid under pressure by means of the electromagnetic valve 39; this fluid pressure provided to feed the jacks 49 and 50 is checked in such a manner that the latter provide a throw equal to the total effort produced by the mobile traverse.
  • the mass of material besides of swelling during the first step of compression, also exerts a throw onto the plungers 12 thus lifting the same for a very short stroke, suflicient to allow the air contained therein to exhaust. Due to the fact that the pressure onto the mass of material remains unaltered during the whole interval between the first and the second step of compression, there is the certainty that all the air is exhausted from the molds of the press.
  • the upper plungers are made in the form of covering plates, the sizes of which are larger than those of the mold cavities, so that said covering plates are brought in direct contact with the upper surface of the respective mold or molds, thus requiring a matrix of the kind as already considered hereabove.
  • the improved press according to this invention is also usable with molds having upper plungers entering the mold cavities.
  • the matrix will be fixed in a stable position, and the hydraulic jacks 14 and 15 together with their corresponding equipment and circuits for feeding them with pressure fluid are eliminated. The remaining elements and devices are unchanged, and so is also the operation.
  • a further advantage which can be realized with the press of this invention is represented by the factas already stated hereabove-that the discharge of the air from the mass in the mold takes place slower, laterally of the upper plungers of the mold, so that the latter will not be soiled with residues transported by the air on exhausting, also in case the molds have to be heated, as it was necessary to do till now.
  • FIGURE 5 of the drawings 4 is the fixed upper traverse of the press, said traverse having at its center portion a threaded bushing 10 for causing the up and down movement of the screw 9 of the press.
  • the roller bearing 20 engages a cylindrical sleeve 71 fixed to an upper portion of. the screw spindle 9 and the outer surface of the sleeve '71 is engaged by a packing 72 held by an appropriate ring 73 supported by a bushing 74 which is screwed around the rim 75 of the cupshaped member 19.
  • a packing 72 held by an appropriate ring 73 supported by a bushing 74 which is screwed around the rim 75 of the cupshaped member 19.
  • annular space 77 which is fluid tightly sealed. This sealed space serves to prevent any leakage of lubricating oil, and it will also prevent introduction of dust and other impurities into said space and between bushing and screw.
  • the space is hermetically closed by means of a packing 33 held by a ring 84 set at the end of the member 21, said packing in turn embracing the cylindrical portion 79 of the screw 9.
  • Said member 21 also bears a bearing of lining 85 in order to engage the screw at its main lower portion, and to protect it against cross loads, further pro viding a convenient guiding means in the vertical direction.
  • the space 80 can communicate through the intervals consented by a blocking ring 86 within the member 21 and the lining 85, with a conduit 88.
  • Space 77 communicates with an oil container 89 through a conduit 90, which is conveniently connected to the wall of the member 19.
  • Said last mentioned conduit enters the interior of said container89 above the liquid level therein.
  • Said room is in communication through a conduit 88 with another conduit 91 entering said container 89, and the end of which is submerged into the liquid, further bearing an oil filtering member 92 in order to filter the lubrieating oil.
  • Two one way valves 93 and 94 opening in opposite directions are provided in conduit 91.
  • Valve 93 allows the passage of the oil from the container 89 to the space 80 also when the sucking factor is a minimum, this being due to the fact that this valve is deprived of any acting spring thereon.
  • Valve 94 allows the passage of the oil for lubricating only from the space 80 to the oil container 89. This valve is held in place by a spring 95 so that the oil, which is directed to the oil container can reach the latter only when the oil pressure will reach such a value as to be enabled to open valve 32.
  • valve 94 opens so that a part of the lubricating oil at least will return to the oil container 89.
  • the invention provides a system for the forced lubrication of suflicient simplicity and immediate function, because of the valve 94, and without provoking any brakage upon said screw 9.
  • a tile press comprising, in combination, a base having an upper surface; a fixed traverse; support means sup porting said fixed traverse in fixed position upwardly spaced from said upper surface of said base; a movable traverse located in the space between-said upper surface and said fixed traverse and being guided on said support means for movement toward and away from said upper surface; a threaded bushing carried by said fixed traverse and having an axis substantially normal to said upper surface; a screw spindle extending through said bushing threadingly engaged therewith and having a lower end abutting against said movable traverse; friction drive means cooperating with said screw spindle to turn the latter in one and in the opposite direction about its axis to thereby move said spindle in axial direction so that said lower end of said spindle will exert during downward movement thereof a downward pressure on said movable traverse; hydraulic jack means carried by said base and cooperating with said movable traverse; means for controlling flow of pressure fluid into and out from said hydraulic jack means so
  • said friction drive means comprise a shaft turnably carried by said fixed traverse above the latter substantially normal to the axis of said spindle and movable in direction of its own axis, a pair of friction discs carried spaced from each other by said shaft for rotation therewith, a flywheel located between said friction discs and fixed to the upper end of said spindle, hydraulic means for shifting the shaft in axial direction to alternately bring said friction discs in contact with said flywheel, and control means controlling said hydraulic means in dependence on the position of said flywheel.
  • a tile press as defined in claim 1 and including upper and lower guide means on said fixed traverse for guiding said screw spindle in said axial direction, said lower guide means including stop means cooperating with said movable traverse for stopping upward movement of the latter under the influence of said hydraulic jack means.
  • said lower mold means include a matrix and plate means movable relative to said matrix between a lower filling position and an upper ejecting position, and including further hydraulic jack means mounted on said base and yieldably supporting said matrix above said upper surface of said base, additional hydraulic jack means connected to and cooperating with said plate means for moving the latter between said positions thereof, and means for controlling flow of pressure fluid into and out from said further and additional hydraulic jack means.
  • said hydraulic jack means comprise a pair of single acting hydraulic jacks engaging said movable traverse at laterally spaced portions thereof for imparting to the latter only an upwardly directed force.
  • said hydraulic jack means comprise a pair of double acting hydraulic jacks each having a piston connected to said movable traverse respectively at laterally spaced portions of the latter, and wherein said means for controlling flow of fluid into and out of said hydraulic jack means are arranged to .alternatingly fee-d pressure fluid to one side of each piston and discharge pressure fluid from the other side thereof and vice versa so that said double acting hydraulic jacks may also be used for imparting a downward pressure to said movable traverse independent from said spindle to thus impart a precompression onto mate-rial in said mold means.
  • a tile press as defined in claim 8 and including single acting hydraulic jack means mounted on said base upwardly projecting therefrom, said single acting hydraulic jack means having upper acting ends engaging said movable traverse when the latter is pressed downwardly.
  • a tile press as defined in claim 1 and including means forming a pair of sealed annular lubricating spaces at opposite ends of said screw bushing about said screw spindle, and means on said screw spindle for respectively increasing and decreasing the volume of at least one of said lubricating spaces during axial movement of said spindle so as to force lubricating oil in said spaces in axial direction along said spindle.
  • said means forming said lubricating spaces comprise a pair of cup-shaped members fixed to and respectively projecting upwardly and downwardly from said fixed traverse coaxial with said screw spindle, and sealing means on said cup-shaped members and engaging said spindle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US354223A 1963-03-27 1964-03-24 Friction and screw press for the manufacture of ceramic articles Expired - Lifetime US3359608A (en)

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IT625263 1963-03-27
IT625163 1963-03-27
IT596164 1964-03-17

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3535754A (en) * 1966-12-10 1970-10-27 Ulrico Walchhutter Cross-head or mobile mold platen
US3604076A (en) * 1969-12-05 1971-09-14 Crossley Machine Co Inc Automatic screw-operated press
US4363612A (en) * 1979-03-29 1982-12-14 Ulrich Walchhutter Flywheel and screw press for producing ceramic articles
US5158723A (en) * 1988-06-10 1992-10-27 Ulrico Walchhutter Method and apparatus for hydraulic pressing
US5325668A (en) * 1988-06-10 1994-07-05 S.I.T.I. Societa Impianti Termoelettrici Industriali S.P.A. Method and apparatus for hydraulic pressing
CN113968037A (zh) * 2021-10-21 2022-01-25 湖北致合通机械有限公司 一种高效率摩擦片专用液压机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES406212A1 (es) * 1971-09-02 1976-01-16 Walchhutter Mejoras introducidas en las prensas destinadas especialmen-te para la produccion de materiales ceramicos y refracta- rios.

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US3097411A (en) * 1963-07-16 Apparatus for shaping pressure-shapable materials
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* Cited by examiner, † Cited by third party
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US3535754A (en) * 1966-12-10 1970-10-27 Ulrico Walchhutter Cross-head or mobile mold platen
US3604076A (en) * 1969-12-05 1971-09-14 Crossley Machine Co Inc Automatic screw-operated press
US4363612A (en) * 1979-03-29 1982-12-14 Ulrich Walchhutter Flywheel and screw press for producing ceramic articles
US5158723A (en) * 1988-06-10 1992-10-27 Ulrico Walchhutter Method and apparatus for hydraulic pressing
US5325668A (en) * 1988-06-10 1994-07-05 S.I.T.I. Societa Impianti Termoelettrici Industriali S.P.A. Method and apparatus for hydraulic pressing
CN113968037A (zh) * 2021-10-21 2022-01-25 湖北致合通机械有限公司 一种高效率摩擦片专用液压机
CN113968037B (zh) * 2021-10-21 2023-07-25 湖北致合通机械有限公司 一种高效率摩擦片专用液压机

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IT690203B (enExample) 1965-04-14
GB1065072A (en) 1967-04-12
FR1398001A (fr) 1965-05-07
IT690204B (enExample) 1965-04-14

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