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US3215356A - Machine for grinding wooden clubs - Google Patents

Machine for grinding wooden clubs Download PDF

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Publication number
US3215356A
US3215356A US303445A US30344563A US3215356A US 3215356 A US3215356 A US 3215356A US 303445 A US303445 A US 303445A US 30344563 A US30344563 A US 30344563A US 3215356 A US3215356 A US 3215356A
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United States
Prior art keywords
press
piston
hydraulic
line
clubs
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Expired - Lifetime
Application number
US303445A
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English (en)
Inventor
Meinecke Curt
Herrmann Gerhard
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Miag Muehlenbau und Industrie GmbH
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Miag Muehlenbau und Industrie GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27L—REMOVING BARK OR VESTIGES OF BRANCHES; SPLITTING WOOD; MANUFACTURE OF VENEER, WOODEN STICKS, WOOD SHAVINGS, WOOD FIBRES OR WOOD POWDER
    • B27L11/00—Manufacture of wood shavings, chips, powder, or the like; Tools therefor
    • B27L11/06—Manufacture of wood shavings, chips, powder, or the like; Tools therefor of wood powder or sawdust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders

Definitions

  • the invention disclosed herein is concerned with a machine for grinding wooden clubs, comprising chains forming a shaft through which club blanks are moved downwardly and pressed against a grinding wheel.
  • the grinder according to the invention overcomes the above mentioned drawbacks and effects considerable reduction in costs, by the provision of two frames disposed upon the base which encloses the grinding wheel, said frames being laterally adjustable and having means for vertically adjustably supporting the mountings which are mutually separably connected and which carry the chains and individual drives therefor.
  • hydraulic presses or, briefly, as presses, which are adapted to provide for a very quick and well adjustable vertical motion of the chain mountings.
  • Spindles are additionally provided for setting or fixing the adjustment effected by the hydraulic presses.
  • This may be effected by a superstructure on the frame or by the raising press or by a guide in the form of angular profiles disposed at the top of the chain mounting, which may be arranged, for example, in the break-through of the ceiling of a floor.
  • a guide in the form of angular profiles disposed at the top of the chain mounting which may be arranged, for example, in the break-through of the ceiling of a floor.
  • FIG. 1 shows a grinder, representing the chain mountings only partially, the left half of the figure showing a vertical section as seen along line II of FIG. 3, and the right half showing an elevational side view as seen when looking in the direction of the arrow Z in FIG. 3;
  • FIG. 2 represents an elevational view as seen when looking in the direction Y of FIG. 1;
  • FIG. 3 illustrates a transverse section as seen along line IIIIII in FIG. 1;
  • FIG. 4 indicates part of the chain mounting
  • FIG. 5 shows in schematic manner and partially in sectional view a device for driving the chains
  • FIG. 6 is a graph showing the function scheme for the device according to FIG. 5.
  • the grinder comprises the following principal parts: Base 1 with the grinding wheel 2; frames 3 with two hydraulic presses 4, and two similar mountings 5 each with two chains 6 and associated drive means.
  • the machine stands upon a suitable foundation.
  • the base 1 is formed by a box-like structure provided with ribs and top and bottom flanges.
  • the grinding wheel is in known manner fastened on a shaft 21 which is journalled for rotation in bearings 22 disposed on separate mountings adjacent to the base 1.
  • the U-shaped frames 3 Upon the base 1, along the sides of the grinding wheel 2, are disposed the U-shaped frames 3, by means of screws 31, so that their spacing from the vertical plane 8 which bisects the axis 21, can be adjusted. Since the two frames 3 are independently adjustable, the spacing of the right hand frame 3 from the median plane 8 may be greater, at given shaft width, than the spacing of the left hand frame 3 from such median plane 8, with the consequence that the angle 9 between the horizontal and the tangent at the grinding wheel 2 is at the running-in place made as small as possible, which is desirable for technological reasons.
  • Each frame 3 carries a hydraulic press 4 which is disposed upon the transverse beam of the respective U- shaped frame 3, a positioning spindle 32 being fastened to each of the two end beams.
  • the chain mounting 5 (see also FIG. 4) comprises substantially the U-shaped base member 51 from the legs 51 of which extend the upwardly directed parts 52. At the top of the transverse member of the base part 51 is provided the part 53. The U-shaped base part 51 is terminated at the bottom by a trough-like part 51". The two uprights 52 of a mounting are provided with bores 52 (FIG. 4), through which are extended rods 54 which are disposed parallel to the shaft 21 of the grinding wheel. Profiled bars 54' are fastened to the rods 54 between the uprights 52 and parallel thereto. The rollers 6' of the chains 6 engage the flanges of the profiled bars 54.
  • Members 54" are provided for slightly tensioning the chain mountings 5 with respect to one another, such members 54" being readily adjustably disposed at the end of the members 54, as is apparent from the figure.
  • the bearings 55' for the bottom shafts 67 of the respective chains, chain wheels 68 being fastened to such shafts.
  • the flanges 66 forming ratchcts for the chain pawl drive which is actuated by the hydraulic presses 7, 7'. The latter will be presently described more in detail.
  • the two portions of the chains which are disposed in opposition to one another form a shaft extending up to the upper chain wheels, not shown, with the opposed portions of such chains moving downwardly.
  • the shaft so formed is filled with wooden clubs 10 which are supplied thereto more or less continuously in small quantities.
  • the clubs are gripped by the chain links 6, fed downwardly thereby and pressed against the rotating grinding stone 2 which, with the aid of water, defibrates the clubs in known manner.
  • Plates or sheets 57 are provided for covering the shaft on the sides thereof, such plates being tensioned with respect to one another, thereby reinforcing the structure.
  • the action of the diagonal tensioning is already obtained by engagement of the edges of the plate 57 with the tubular member 54 which project from the uprights 52, as is indicated in FIG. 1.
  • a spray nozzle 58 is arranged in the space between the bottom chain part and the lower chain wheel 68 for spraying the running rollers 6' of the chain 6 and also the gaps between the teeth of the chain wheels so as to remove moist grinding material adhering thereto.
  • the function of the nozzle is important for the proper operation of the machine.
  • the upper guiding of the chain mounting 5 with respect to the frames 3 is in the illustrated embodiment effected by guide collars 53 disposed below the boxes 53 of the base 51, the pistons of the hydraulic presses 4 projecting into the respective collars.
  • Both hydraulic presses are advantageously connected to the same hydraulic system so as to obtain identical force-and load conditions.
  • the mountings are moreover Supported by spindles 32 of the frames 3, by means of flanges 59 which are welded to the leg portions 51' of the base 51, such flanges 59 being clamped between nuts disposed upon the respective spindle.
  • These additional supporting means are as such known; they serve to fix the height adjusted by the hydraulic presses 4, thus relieving the presses of a continuous load.
  • the drive shafts 67 of the chains 6 must be driven with practically constant and relatively very low speed of revolution while exerting a constant relatively great torque.
  • Suitable for this purpose are at least two pawlratchet drives which are alternately actuated by hydraulic presses.
  • the control must be such, especially for the start of the operation, that the uniform functioning of the controlled interplay is reliably obtained at any position of the two hydraulic presses.
  • the invention proposes a drive which comprises a changeover control and a switch, both forming part of the respective hydraulic presses, such change-over control actu ating shortly before the conclusion of the power stroke of the piston, the change-over control of the other bydraulic press in such a manner that the piston of the other hydraulic press is caused to execute the power stroke, the teeth of the pawl-ratchet wheels being angularly displaced with respect to one another.
  • the first mentioned hydraulic press is the master press and the other is the follower press.
  • the hydraulic master press is shown at the top of FIG. 5.
  • Each driven chain shaft 67 is provided with two ratchet wheels 66, 66', each with eight teeth, resulting in an angle of division w:45.
  • Upon the shaft 67 are also provided the pawl carriers 13, 13', to which are linked the spring biased pawls 14, 14'.
  • the drive of the pawls is effected by means of the hydraulic presses 7, 7' the piston rods 60, 60 of which cooperate in known manner with parts 15 of the pawl carriers.
  • Each hydraulic press 7, 7 is provided with a changeover press 80, 80', which is in the case of the master press 7 connected with electrical switches 81, 82 and in the case of the follower press 7' with the electromagnet 84.
  • the piston rod 60 carries a control rod 61 which is by means of two link members 62 connected with the shift rod 83 of the change-over device 80.
  • the control rod 61 of the hydraulic master press 7 carries an extension 60" which engages the left end of the shift rod 83 when the piston rod 60 is near its right end position, thereby taking the shift rod 83 along and effecting in known manner the switching-over of the hydraulic master press 7.
  • Each change-over device 80, 80 is made in the form of a known hydraulic shift switch with a pressure line 91, two distributor lines 93, 94 and two return lines 92.
  • Each hydraulic press 7, 7 is provided with an annular cover 71 through which extends the respective piston rod 60, 60', and cover 72 at the other end which contains the pressure controlled check valve 73.
  • the cover 72 is also provided with a fixed auxiliary piston 74 which projects into a bore 63 formed in the respective piston rod 60, 60', and contains an oil feed line 75 which is by way of the bore 76 connected with the distributor line 94 and otherwise closed by the pressure controlled check valve 73.
  • the latter is controlled by means of the small spring biased piston 77 and is by way of line 78 connected with the larger side of the piston 69 from which extends the piston rod 60.
  • the smaller piston 77 is effected by pressure via the line 95 which is branched off from the distributor line 94.
  • the shift rod 83 of the change-over or switch-over device 80 is by means of a flexible member 96' connected with the positive terminal of the line 96 and can conduct the current in its right end position, by way of contact 88 to the counter 89 which is by way of line 90 connected to the negative terminal.
  • the electrical switch 81 having a contact 85 disposed upon the shift rod 83, which contact is electrically connected with the housing contact 86 responsive to pulling out of the shift rod 83. This is the case when the piston rod 60 with its control rod 61 stretches the link members 62. Closure of the switch 85, 86 connects over the line 97 current to the electromagnet 84 which causes positioning of the switch-over device 80', cooperatively associated with the piston rod 60 of the hydraulic follower press 7, into power stroke position, shortly before the master piston 69 has concluded its power stroke.
  • the hydraulic system comprises the pumps 11 for the hydraulic master press and the pump 12 for the hydraulic follower press. Both pumps are disposed in the reservoir 16 and are driven by the motor 17 with the aid of a gear 17 operating with continuously adjustable gear ratio.
  • the oil flows from the pump 11 by way of the line 91 to the change-over device 89 and thence by way of the lines 94, 76, 75 into the cylinder 63 of the piston rod 60. Since the amount of oil supplied is constant, the piston 69 will be rapidly driven forwardly until the pawl 14 is in engagement with the tooth of the ratchet wheel 66 which is nearest to it. It may be mentioned at this place that the illustrated position of the hydraulic master press 7 does not practically occur, since the shaft 67 rotates continuously and since the piston, upon reaching its initial position, reaches in rapid advance the next tooth of the ratchet which moves ahead thereof. However, the position shown in FIG. 5 is assumed to constitute the initial position which may be adjusted.
  • the links 62 are stretched responsive to the motion of the piston 60 to the right, taking along the shift rod 83, whereby the switch 85, 86 is closed and the switch-over device 80' 0f the follower is actuated by the electromagnet 84; consequently, as described before, the piston rod 60' of the hydraulic follower is set in motion and the master piston 60, 69 is switched over and returns, since the oil from the line 91 now flows by way of the line 93 and the bore 79 in the annular cover 71, to the smaller side of the piston 69. Since the left end of the piston is smaller than the right end, while the amount of oil delivered in a time unit is constant, the piston will move faster in the return stroke than in the power stroke.
  • the extension 60" on the control rod 61 will move the shift rod 83 back and will effect the switching over of the hydraulic master press.
  • the counter 89 is coincidently actuated responsive to connection of the shift rod 83. with contact 88.
  • the operation is similar in the case of the hydraulic follower press, except that the control rod 61 remains in the position indicated by dot-dash lines, so that the shift rod 83' is not affected by the action of the piston rod 60.
  • the switch-over device 80' is controlled by the electromagnet 84 in the manner already described. This results in a control of the hydraulic follower press 7 which depends upon the motion of the master piston 69, whereby the drive from any position of the two hydraulic presses falls into the proper working play at the latest after one working beat of the hydraulic master press 7.
  • the piston rod 60' of the follower press 7' after executing its rapid motion d, has caused its pawl 14 to engage at the diagram point 2.3/0.4 the tooth lying next ahead thereof and has from thereon operated in driving sense.
  • the diagram point 25/05 for the tooth is identical with the diagram point 0.5/ 0.5 for the succeeding tooth.
  • the lines n for the ratchet tooth and p for the pawl rise at the last noted point jointly in power transmitting sense, up to the point 1.5/ 1, the pawl returning at such point with accelerated motion according to line q to the diagram point 2.0.
  • the line q for the return of the pawl 14' of the piston 60' can extend from the point 1.5/1 more or less inclined, without detrimentally affecting the function; a stronger inclined curve, that is, a quicker return motion of the follower piston, practically does not occur, since the speed is with properly tightly seated piston, given by the amount of oil supplied; however, a slower return may be caused by lacking tightness and in such case, the line q will be flatter.
  • the illustrated mechanical arrangement can be modified. It is, for example, possible to fixedly link the piston rods to the pawl holders 13, 13' while pivotally suspending the presses 7, 7'. Uniform construction of both presses and the pawl-ratchet mechanism is advantageous for reasons of simplicity and far-reaching coordination of the working strokes, as may be seen from the diagram, for example, line b between the points /025 and 15/05. It is also readily possible to provide an arrangement with dissimilar presses and pawl-ratchet mechanisms, wherein one group needs to effect only a bridging stroke with smaller angular extent, so as to control the drive of the shaft during the return motion of the master piston.
  • the control may be effected with various modifications, for example, fully hydraulic or fully electric.
  • the switchover device may be utilized to operate as a relay for the control of a switch-over piston, as may be indicated in an installation of relatively great size.
  • the drive may always be uniformly constructed irrespective of the spacing of the conveyor chains, further, that the chains can be individually operated so as to avoid vacant spaces at the feed-in of the wooden clubs, and that the operating speed of revolution can be very finely adjusted, by the use of hydraulic adjustment pumps, or, as illustrated, by gears which are continuously adjustable, that is, adjustable without stages. Adjustment pumps may be relatively very small as compared with a mechanical finely continuously regulatable drive.
  • the motion acceleration provides the advantage of quickly utilizing the full pressing force of the chains.
  • the pawl carrier may be constructed as a long lever, makes it possible to construct the drive according to the invention aside from its use in connection with the particular grinder, so as to reliably control great forces with lowest speed of revolution.
  • a machine for grinding wooden clubs comprising a base containing a grinding wheel rotatably disposed therein, conveyor chains, forming partial walls delimiting a shaft extending vertically upwardly from said base, for downwardly transporting clubs to press such clubs against said grinding wheel, a pair of frames disposed upon said base and being laterally adjustable with respect thereto, an upright mounting extending from such frame, each mounting carrying a chain and drive means therefor, means for separably connecting said mountings, and means for vertically adjustably disposing said mountings to adjust the spacing of said chains with respect to said grinding wheel.
  • a machine according to claim 1 comprising means for guiding said mountings at points above the respective frames.
  • a machine according to claim 1 comprising hydraulic means for guiding said mountings at points above the respective frames.
  • a machine according to claim 1 comprising threaded spindles and hydraulic devices fastened on the respective frames, for guiding said mountings at points above such frames.
  • a machine according to claim 1 comprising threaded spindles and hydraulic devices fastened on the respective frames, for guiding said mountings at points above such frames, and means for connecting said hydraulic devices to the same hydraulic system.
  • a machine according to claim 1 comprising a spray device disposed in the space above the bottom drives for said chains.
  • a chain drive device comprising a plurality of chains, a shaft carrying toothed ratchets for respectively driving said chains, a pawl for each ratchet, a hydraulic press for operatively actuating each pawl, one of said presses constituting a master press and the other constituting a follower press, and means for controlling the actuation of said follower press depending upon the piston motion of the master press.
  • a chain drive device wherein the tooth divisions of said ratchets are mutually displaced, a switch-over device for said master press and for said follower press, respectively, a switch operable by the switch-over device of said master press for causing the switch-over device of said follower press to operate shortly before conclusion of .the power stroke of the piston of the master press, whereby the piston of said follower press is actuated to execute a power stroke.
  • a chain drive device comprising a fixed piston extending into a bore formed in the piston of the respective presses, a channel formed in the respective fixed piston, and means for connecting said channel with a pressure line and by way of a check valve with another line terminating ahead of the end of the piston of said master press.
  • a machine for grinding wooden clubs comprising a base containing a grinding wheel rotatably disposed therein, conveyor chains, forming partial walls delimiting a shaft extending vertically upwardly from said base, for downwardly transporting clubs to press such clubs against said grinding wheel, a pair of frames disposed upon said base and being laterally adjustable with respect thereto, an upright mounting extending from such frame, each mounting carrying a chain and drive means therefor, each of said driving means comprising a shaft carrying toothed ratchets for driving the respective chains, a pawl for each ratchet, a hydraulic press for operatively actuating each pawl, one of said presses constituting a master press, and the other a follower press, and means for controlling the actuation of said follower press depending upon the piston motion of the master press, means for separably connecting said mountings, and means for vertically adjustably disposing said mountings to adjust the spacing of said chains with respect to said grinding wheel.

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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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Press Drives And Press Lines (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
US303445A 1962-08-22 1963-08-20 Machine for grinding wooden clubs Expired - Lifetime US3215356A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1962M0053977 DE1503340A1 (de) 1962-08-22 1962-08-22 Antrieb einer langsamen Welle
DEM54890A DE1207204B (de) 1962-08-22 1962-11-21 Stetigschleifer

Publications (1)

Publication Number Publication Date
US3215356A true US3215356A (en) 1965-11-02

Family

ID=25987287

Family Applications (1)

Application Number Title Priority Date Filing Date
US303445A Expired - Lifetime US3215356A (en) 1962-08-22 1963-08-20 Machine for grinding wooden clubs

Country Status (6)

Country Link
US (1) US3215356A (fi)
AT (1) AT259351B (fi)
CH (1) CH406826A (fi)
DE (2) DE1503340A1 (fi)
FI (1) FI44510B (fi)
FR (1) FR1358808A (fi)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3524980A (en) * 1968-09-03 1970-08-18 Lear Siegler Inc Gas light-gas grill combination
US3883081A (en) * 1973-02-14 1975-05-13 Borregaard As Apparatus for shredding baleformed compressed fiber material

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1465069A (en) * 1920-08-07 1923-08-14 John J Warren Apparatus for grinding wood pulp
US1948189A (en) * 1930-02-27 1934-02-20 Andrew N Russell Wood grinding machine
US2445081A (en) * 1940-10-11 1948-07-13 Pouille Robert Francois Hydraulic device for controlling several members with a predetermined automatic interdependency
US2626487A (en) * 1950-07-20 1953-01-27 Anthony J Janusauskas Chain and gear driven semiautomatic buffing machine
US2965077A (en) * 1958-09-29 1960-12-20 Shell Oil Co Prime mover comprising two hydraulic single-cylinder piston engines
US3024576A (en) * 1959-04-03 1962-03-13 Quality Metal Finishing Co Buffing machine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1499547A (en) * 1923-08-16 1924-07-01 American Voith Contact Co Machine for grinding wood into pulp
GB234190A (en) * 1924-02-26 1925-05-26 John James Warren New and improved apparatus for grinding wood pulp
DE1747685U (de) * 1956-12-15 1957-06-27 Miag Muehlenbau & Ind Gmbh Holzschleifer.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1465069A (en) * 1920-08-07 1923-08-14 John J Warren Apparatus for grinding wood pulp
US1948189A (en) * 1930-02-27 1934-02-20 Andrew N Russell Wood grinding machine
US2445081A (en) * 1940-10-11 1948-07-13 Pouille Robert Francois Hydraulic device for controlling several members with a predetermined automatic interdependency
US2626487A (en) * 1950-07-20 1953-01-27 Anthony J Janusauskas Chain and gear driven semiautomatic buffing machine
US2965077A (en) * 1958-09-29 1960-12-20 Shell Oil Co Prime mover comprising two hydraulic single-cylinder piston engines
US3024576A (en) * 1959-04-03 1962-03-13 Quality Metal Finishing Co Buffing machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3524980A (en) * 1968-09-03 1970-08-18 Lear Siegler Inc Gas light-gas grill combination
US3883081A (en) * 1973-02-14 1975-05-13 Borregaard As Apparatus for shredding baleformed compressed fiber material

Also Published As

Publication number Publication date
CH406826A (de) 1966-01-31
AT259351B (de) 1968-01-10
DE1207204B (de) 1965-12-16
FR1358808A (fr) 1964-04-17
DE1503340A1 (de) 1969-12-18
FI44510B (fi) 1971-08-02

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