US3881852A - Means for maintaining spacing in a continuous press - Google Patents

Means for maintaining spacing in a continuous press Download PDF

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Publication number
US3881852A
US3881852A US391585A US39158573A US3881852A US 3881852 A US3881852 A US 3881852A US 391585 A US391585 A US 391585A US 39158573 A US39158573 A US 39158573A US 3881852 A US3881852 A US 3881852A
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United States
Prior art keywords
press
pressure
valve
platen
counter
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US391585A
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English (en)
Inventor
Karl-Heinz Ahrweiler
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Individual
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Individual
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Publication date
Priority claimed from DE19722242399 external-priority patent/DE2242399C3/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27N—MANUFACTURE BY DRY PROCESSES OF ARTICLES, WITH OR WITHOUT ORGANIC BINDING AGENTS, MADE FROM PARTICLES OR FIBRES CONSISTING OF WOOD OR OTHER LIGNOCELLULOSIC OR LIKE ORGANIC MATERIAL
    • B27N3/00—Manufacture of substantially flat articles, e.g. boards, from particles or fibres
    • B27N3/08—Moulding or pressing
    • B27N3/24—Moulding or pressing characterised by using continuously acting presses having endless belts or chains moved within the compression zone
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B5/00—Presses characterised by the use of pressing means other than those mentioned in the preceding groups
    • B30B5/04—Presses characterised by the use of pressing means other than those mentioned in the preceding groups wherein the pressing means is in the form of an endless band
    • B30B5/06—Presses characterised by the use of pressing means other than those mentioned in the preceding groups wherein the pressing means is in the form of an endless band co-operating with another endless band

Definitions

  • This invention relates to presses of the type wherein two pressure platens are each supported by a support construction so that the forces of each of the press platens are transmitted to their corresponding support construction and more particularly such a press in which the transmittal of force from the press platens to thc corresponding support construction is by means of a pressure fluid contained in a pressure element positioned between the platen and its respective support construction.
  • a press of this nature is described in U.S. Application Ser. No. 308,556.
  • the press disclosed therein is a continuous press for the manufacture of wood chip board and the like in which the material to be treated is moved continuously between two flexible endless conveyor belt spans.
  • the press platens in turn are positioned between support constructions comprising beams each positioned transversely to the movement of the belts with portions of such beams extending longitudinally above and below the press platens for the length of a press.
  • a hydraulic pressure cushion or a series of hydraulically connected pressure vessels are positioned between the beams and the pressure platens.
  • Such an arrangement causes transverse pressure on the work between the belts to be transmitted from the belt through the chain and the press platen to the beam, making pos sible equal pressure over the width of the work even when the beams deflect under forces acting thereon.
  • an actuator which comprises either a motorized or mechanical spindle or a hydraulic cylinder which can be positioned so as to determine the distance of the upper and lower belt and thus the ultimate thickness of the work.
  • the present invention provides an arrangement which solves these problems and permits constructing a press in which the regulation of the distance between the press platens is obtained with more accuracy, increase sensitivity and at a lower cost.
  • a rigid support is provided between the support connections, i.e., between the beams.
  • a guiding valve is installed which is sensitive to platen motion and regulates the pressure in the pressure elements installed between the platens and the beams so as to maintain a predetermined distance between the press platens.
  • the supports in the present invention are rigidly connected with one another resulting in a simplicity of design.
  • the pressure elements between the platens and the supports work directly against the press platens and can follow changes in pressure much more rapidly than when a shift in the relative position of the entire support structure must be made.
  • the guiding valve is arranged so that when the distance between the press platens is as predetermined, the valve is inactive.
  • a pressure pump coupled through the valve then causes an increase in the pressure in the pressure elements until the press platens begin to move together changing their position.
  • the guide valve opens to allow a bleed off of hydraulic fluid relieving the pressure so that the press platen moves back in a direction to cause it to again be at the predetermined distance, whereupon reaching this predetermined distance, the valve becomes inactive.
  • the guide valve of the present invention may comprise two parts movable with respect to one another, one of which is connected to the press platen and the other with corresponding beam.
  • the guide valve has an inlet which is connected to the pressure medium pump and a first outlet connected to the pressure element between the beam and the platen.
  • a second outlet to a reservoir is constructed so as to normally be blocked off when the platen is properly positioned. Movement of the platen from the predetermined position will, however, open this second outlet permitting a reduction in pressure and causing the platen to return to its predetermined position.
  • the guide valve comprises a glide valve operating parallel to the direction of movement of the press platens having a sliding element which has a sealing surface at its leading frontal edge, which sealing surface operates in a sealing manner with a counter surface into which is formed a channel opening to the inlet.
  • the second outlet is located in the housing of the longitudinal glide valve at a level corresponding the sealing surface and the counter surfaces.
  • the sliding member is coupled to the press platen and the valve housing to the beam.
  • the connections can be reversed. As long as a leading frontal surface of the sliding member abuts a counter surface, no pressure medium can pass out of the channel opening in the counter surface. Under these conditions the connection between the inlet and the first outlet to the pressure element permits the full inlet pressure to be passed through. This creates forces which increase tending to displace the press platen away from the board as it is acted on by the counter pressure of the work. The slide element connected to the press platen moves therewith thus separating its sealing surface from the counter surface.
  • the counter surface is placed on a counter sliding element which may be positioned axially within the valve body.
  • a threaded spindle protruding into the housing.
  • a plurality of pairs of guide valves on each side of the platen can be provided. In such a case, it is preferable to drive the threaded spindles used for positioning the counter slide element using a common drive means in order to obtain parallel positioning of the press platen.
  • FIG. 1 is an end view of the pressure of the present invention.
  • FIG. 2 is a cross-sectional view of the guide valve of the present invention.
  • the work I such as wood chips or the like which are to be pressed together to form press board or the like is passed between two endless conveyor belt loops 2, 3 made of thin strip metal in the manner described in the above identified copending U.S. application.
  • the conveyor belt 'vo s Z, 3 will have a thickness of about Ito 1.5mm.
  • the work 1 and the belts 2, 3 as shown in FIG. 1 move perpendicular to the plane of the drawing.
  • the belts 2 and 3 move endlessly and return above and below the construction of FIG. 1 to the beginning of the press zone.
  • Each of the belts 2 and 3 is supported by a press platen designated respectively 5 and 6 through roller chains 4.
  • the press platen 5 comprises a heatable platen 5' through which pressure and temperature is transmitted to the roller chains, a grooved return platen 5" and an insulating intermediate platen 5".
  • the roller chain loops move to the end of the press section and reverse their direction over the edge of the press platen 5 and 6 and return without any forces thereon through the channels Ill in the inner portions of the press platens 5 and 6 to return to the lower end of the press platen where they again reverse direction and pass between the press platen and the belts 2 and 3.
  • the press platen 6 is made up of the same segments as were described above in connection with press platen 5.
  • the roller chains 4 are shown as small rectangles on the drawing. More detail as to the actual construction thereof may be had from the above referenced U.S. application.
  • the platens 5, 6 are arranged between a support construction which comprises heavy I beams 7 and 8 oriented transversely to the direction of the work. Individual pairs of upper and lower beams 7 and 8 are connected at a point beyond the edge of the work and the belts 2 and 3 to a yoke 9. Connection is made by means of welding or through the use of nuts and bolts. The sequence of pairs of beams joined by yokes at their edges are positioned along the path of the belts 2 and 3. Between each lower I beam 8 and lower press platen 6 there are provided pressure vessels 10 which transmit pressure to the work l by lifting the platen 6 in the di rection of the platen 5.
  • the pressure vessels 10 between the I beam 8 and the platen 6 are hydraulically coupled so that hydraulic pressure is uniform along the width of the work I irrespective of any deflection of the beams 7, 8.
  • a single hydraulic pressure cushion or pressure chamber may be positioned across the entire width of the work.
  • a guide valve 20 is provided [only half of the press apparatus is shown so that only one yoke 9 and guide valve 20 is illustrated. It will be recognized that the same construction is present on the other side of the press]
  • the housing of the valve 20 is connected to the I beam 8. It has a thrust transmitting member 21 which is coupled to an intermediate platen 12 which is installed between the press platen 6 and the pressure vessel 10 extending parallel to the work 1 over its entire width.
  • the thrust transmitting members 21 are connected directly with the press platen 6 and transmit their motion directly to the guide valves 20, the axes of which guide valves are parallel to the direction of the action of the pressure vessels and to the direction of the motion of the pressure vessels and the press platen 6.
  • FIG. 2 illustrates the construction of the guide valve in detail.
  • the guide valve 20 comprises a cylindrical housing 22 into which are inserted cylindrical gliding bushings 23 and 24. As illustrated, the gliding bushings 23, 24 are inserted from each end and bolted into place. Within the gliding bushing 23, mounted for sliding motion therein is a slide 25. In order to avoid lateral transmission of forces, the transmitting member 21 is coupled to the slide 25 through a spherical cap or ball joint 26. Within the gliding bushing 24 is positioned a counter slide 27 which is axially displaceable therein.
  • the counter slide 27 contains on its end a threaded spindle 29 which is threaded into an element 30 inserted in the end of the gliding bushing 24 and bolted to the housing 22.
  • the counter slide 27 is coupled to the threaded spindle 29 through an axial ball bearing 28. Turning of the spindle 29 will result in positioning of the counter slide 27 up and down along the axis of the guide valve.
  • a coupling 31 is provided for imparting rotary motion to the spindle 29.
  • the slide 25 contains at its leading edge a sealing surface 40.
  • This comprises a ring formed ridge in a plane perpendicular to the plane of motion of the slide.
  • the sealing surface 40 acts against a counter surface 41 on the counter slide 27. When the counter slide 27 and the slide 25 are in contact an effective seal is maintained to prevent any hydraulic fluid escaping from inside the sealing surface 40 to the outside.
  • An axial channel is formed in the center of the counter slide 27 running to the counter surface 41. This channel is connected with a circumferential groove 43 which is formed in the counter slide 27.
  • a first inlet opening 43 is formed in the housing 22 and through the gliding bushing 24 to communicate with the groove 43.
  • a passage through the groove 43 permits communication with the channel 42.
  • a first outlet opening is formed on the other side of the housing being formed through the housing and the gliding bushing 24.
  • the groove 43 is made with an enlarged width so that it will remain in communication with the inlet 44 and outlet 43 even as the counter slide is axially displaced. The width of this groove should be sufficient to allow communication over the range of work thicknesses expected to be processed in the press.
  • a second outlet 47 is provided which communicates with a groove 46 which is formed in a space between the bushings 23 and 24. This groove is formed in the area of the sealing surface 40 and the counter surface 41 and permits communication between the channel 42 and the outlet 47 when the sealing surface 40 and counter surface 41 are separated.
  • the outlet 47 is coupled to a fluid reservoir via conventional hydraulic piping (not shown).
  • the inlet 44 is coupled to a hydraulic pump and the first outlet 45 to the pressure vessels 10.
  • the coupling 31 which displaces the counter slide 27 to adjust its position and thereby adjust the work thickness is driven by a gear 50 which itself is driven by a pilot motor 51.
  • a similar gear 50 will be provided to drive the coupling 31 associated with the guide valve on the other side of the press.
  • a shaft 52 which couples the two gears 50 to insure that both valves are adjusted together to maintain the press platen 6 parallel.
  • Additional valves 20 may be installed along the length of the press and similarly mechanically coupled to the pilot motor 51 to assure equal pressure over the press plate platen 6.
  • a pressure pump which is not shown supplies hydraulic fluid at a constant pressure to the inlet 44 of the guide valves 20. From the inlet, the hydraulic fluid passes through the groove 43 into the out let 45 and then to the pressure vessels 10. This results in an increase in pressure in the pressure vessels causing them to tend to raise up the platen plate 6 away from the beam 8.
  • the slide 25 which is coupled to the platen plate 6 moves therewith because of the pressure acting on the end surface of the slide through the channel 42 which is in communication with the inlet 44. This tends to push the slide away from the end surface 41 of the counter slide. When the pressure platen 6 is raised, the slide 25 will tend to follow it. As the slide 25 moves up, communication between the channel 42 and the second outlet 46 will be established.
  • the thickness of the work is regulated by the positioning of the counter slide 27 through the use of the pilot motor 51. For each position of the counter surface 41, a different equilibrium position is established for the press platen 6. Through the inter-connection of all the guide valves, this is accomplished simultaneously and results in a parallel displacement of the press platen.
  • b. means for sensing deviations of one press platen from a predetermined position and for regulating the pressure elements so as to maintain said one press platen at said predetermined position during a pressing operation so as to maintain said predetermined position throughout the pressing operation.
  • Apparatus according to claim 1 in which said means for sensing and maintaining comprises a guide valve comprising:
  • a first outlet port in said valve coupled to said pressure element and in communication with said inlet port;
  • Apparatus according to claim 4 wherein a plurality of guide valves are provided and further including means to jointly drive the spindles of each of said plurality of guide valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Wood Science & Technology (AREA)
  • Forests & Forestry (AREA)
  • Press Drives And Press Lines (AREA)
  • Veneer Processing And Manufacture Of Plywood (AREA)
  • Dry Formation Of Fiberboard And The Like (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Presses And Accessory Devices Thereof (AREA)
US391585A 1972-08-29 1973-08-27 Means for maintaining spacing in a continuous press Expired - Lifetime US3881852A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19722242399 DE2242399C3 (de) 1972-08-29 Presse zur Ausübung einer Flächenpressung

Publications (1)

Publication Number Publication Date
US3881852A true US3881852A (en) 1975-05-06

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US391585A Expired - Lifetime US3881852A (en) 1972-08-29 1973-08-27 Means for maintaining spacing in a continuous press

Country Status (8)

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US (1) US3881852A (sv)
JP (1) JPS5311702B2 (sv)
BR (1) BR7306555D0 (sv)
FI (1) FI59553C (sv)
GB (1) GB1406385A (sv)
IT (1) IT993752B (sv)
SE (1) SE392240B (sv)
SU (1) SU506281A3 (sv)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3969051A (en) * 1975-06-13 1976-07-13 D.G. Rung Industries, Inc. Vulcanizing apparatus
US3992134A (en) * 1974-05-31 1976-11-16 Konstruktiewerkhuize Demets N.V. Continuously operating prepress or finishing press
US4017235A (en) * 1974-10-30 1977-04-12 Edward Kusters Apparatus for avoiding an excess of pressure in a continuous press
US4050872A (en) * 1975-10-11 1977-09-27 Eduard Kusters Roller chain guide arrangement
US4053276A (en) * 1975-03-18 1977-10-11 Eduard Kusters Press for exerting a pressure over an area
US4164387A (en) * 1977-06-30 1979-08-14 Sandvik Conveyor Gmbh Apparatus for producing sheet material
US4164386A (en) * 1977-07-02 1979-08-14 Sandvik Conveyor Gmbh Apparatus for producing sheet material
US4213748A (en) * 1978-05-06 1980-07-22 Eduard Kusters Press for compacting material to form a traveling web
US4240778A (en) * 1979-08-27 1980-12-23 Efco, Inc. System for providing for parallelism in fluid powered press or the like
US4269580A (en) * 1980-06-11 1981-05-26 General Motors Corporation Compression molding press with hydraulic controls
US4307050A (en) * 1979-12-14 1981-12-22 Bison-Werke Bahre & Greten Gmbh & Co. Kg Heated platten press
US4370116A (en) * 1981-10-13 1983-01-25 Package Machinery Company Tonnage indicator for injection molding machine
US4615857A (en) * 1984-11-30 1986-10-07 Motorola, Inc. Encapsulation means and method for reducing flash
US4621998A (en) * 1984-08-06 1986-11-11 Continental Gummi-Werke Aktiengesellschaft Press for continuously producing band-like articles
US5112431A (en) * 1989-04-28 1992-05-12 C. Siempelkamp Gmbh & Co. Press for making pressed board
US5493961A (en) * 1993-12-11 1996-02-27 G. Siempelkamp Gmbh & Co. Continuous board-making press including press plate deformation safety device
US5537919A (en) * 1993-12-24 1996-07-23 Maschinenfabrik J. Dieffenbacher Gmbh & Co. Measuring and control system for a continuously operating press

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3834269C1 (sv) * 1988-10-08 1990-01-04 Thyssen Industrie Ag, 4300 Essen, De

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2148704A (en) * 1934-09-15 1939-02-28 Merritt Engineering & Sales Co Veneer press
US2220798A (en) * 1935-10-01 1940-11-05 Baldwin Locomotive Works Power control system for hydraulic presses
US3545053A (en) * 1967-03-08 1970-12-08 Besser Co Apparatus for controlling the height of concrete block during their manufacture
US3719445A (en) * 1971-05-10 1973-03-06 Danly Machine Corp Use of metal working press for plastic compression molding
US3792953A (en) * 1971-08-10 1974-02-19 Kuesters E Maschf Machine for compressing a traveling web

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2148704A (en) * 1934-09-15 1939-02-28 Merritt Engineering & Sales Co Veneer press
US2220798A (en) * 1935-10-01 1940-11-05 Baldwin Locomotive Works Power control system for hydraulic presses
US3545053A (en) * 1967-03-08 1970-12-08 Besser Co Apparatus for controlling the height of concrete block during their manufacture
US3719445A (en) * 1971-05-10 1973-03-06 Danly Machine Corp Use of metal working press for plastic compression molding
US3792953A (en) * 1971-08-10 1974-02-19 Kuesters E Maschf Machine for compressing a traveling web

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992134A (en) * 1974-05-31 1976-11-16 Konstruktiewerkhuize Demets N.V. Continuously operating prepress or finishing press
US4017235A (en) * 1974-10-30 1977-04-12 Edward Kusters Apparatus for avoiding an excess of pressure in a continuous press
US4053276A (en) * 1975-03-18 1977-10-11 Eduard Kusters Press for exerting a pressure over an area
US3969051A (en) * 1975-06-13 1976-07-13 D.G. Rung Industries, Inc. Vulcanizing apparatus
US4050872A (en) * 1975-10-11 1977-09-27 Eduard Kusters Roller chain guide arrangement
US4164387A (en) * 1977-06-30 1979-08-14 Sandvik Conveyor Gmbh Apparatus for producing sheet material
US4164386A (en) * 1977-07-02 1979-08-14 Sandvik Conveyor Gmbh Apparatus for producing sheet material
US4213748A (en) * 1978-05-06 1980-07-22 Eduard Kusters Press for compacting material to form a traveling web
US4240778A (en) * 1979-08-27 1980-12-23 Efco, Inc. System for providing for parallelism in fluid powered press or the like
US4307050A (en) * 1979-12-14 1981-12-22 Bison-Werke Bahre & Greten Gmbh & Co. Kg Heated platten press
US4269580A (en) * 1980-06-11 1981-05-26 General Motors Corporation Compression molding press with hydraulic controls
US4370116A (en) * 1981-10-13 1983-01-25 Package Machinery Company Tonnage indicator for injection molding machine
US4621998A (en) * 1984-08-06 1986-11-11 Continental Gummi-Werke Aktiengesellschaft Press for continuously producing band-like articles
US4615857A (en) * 1984-11-30 1986-10-07 Motorola, Inc. Encapsulation means and method for reducing flash
US5112431A (en) * 1989-04-28 1992-05-12 C. Siempelkamp Gmbh & Co. Press for making pressed board
US5493961A (en) * 1993-12-11 1996-02-27 G. Siempelkamp Gmbh & Co. Continuous board-making press including press plate deformation safety device
US5537919A (en) * 1993-12-24 1996-07-23 Maschinenfabrik J. Dieffenbacher Gmbh & Co. Measuring and control system for a continuously operating press

Also Published As

Publication number Publication date
IT993752B (it) 1975-09-30
FI59553B (fi) 1981-05-29
SU506281A3 (ru) 1976-03-05
DE2242399B2 (de) 1975-07-17
JPS5311702B2 (sv) 1978-04-24
DE2242399A1 (de) 1974-03-21
SE392240B (sv) 1977-03-21
FI59553C (fi) 1981-09-10
BR7306555D0 (pt) 1974-07-25
GB1406385A (en) 1975-09-17
JPS4986966A (sv) 1974-08-20

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