CA2059348A1 - Coupling arrangement and roller mill equipped therewith - Google Patents
Coupling arrangement and roller mill equipped therewithInfo
- Publication number
- CA2059348A1 CA2059348A1 CA002059348A CA2059348A CA2059348A1 CA 2059348 A1 CA2059348 A1 CA 2059348A1 CA 002059348 A CA002059348 A CA 002059348A CA 2059348 A CA2059348 A CA 2059348A CA 2059348 A1 CA2059348 A1 CA 2059348A1
- Authority
- CA
- Canada
- Prior art keywords
- piston
- parts
- cylinder
- coupling arrangement
- roller
- Prior art date
- 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.)
- Abandoned
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C4/00—Crushing or disintegrating by roller mills
- B02C4/28—Details
- B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
Abstract
Abstract The invention relates to a coupling arrangement for connecting two components which are movable relative to one another, particularly for a roller mill. In this case the two components are constructed as cylinder parts each of which has a central guide lug and into each of which a piston part engages, the inner peripheral surfaces of the piston parts and the outer peripheral surfaces of the guide lugs of the cylinder parts being constructed in such a way that the two cylinder parts can carry out relative to one another not only a longitudinal movement but also a swivelling movement and a transverse movement. The movements, particularly the longitudinal movement, can be limited by stops.
Description
C35~
1 Couplin~ ~rrangement and roller_mlll equipped there~lth The invention relates to a coupllng arrangement (accordlng to the preamble to claim 1), a device (according to the generlc concept of clalm 9) for producing an ad~u~table pressure between two component6 which ara movable relatlve to one another, and a roller mill ~ccording to the ~eneric concept of claim 10).
. 10 Hydraulic cyllnders of flat con6truction are known CDE-A-38 20 373~ whi~h by mean~ of ~n internal spherical ~uide permit a limited lnclined po6ition of the pi6ton rod relative to the cyl-inder. Such-cyllnders can be u6ed when two 6urface6 whlch do not lie parallel to one another ar0 to be 6upported without additlonal llnks or compensatln~
interpositlon6.
However, 6wivelllng movement6 of the two parts which are 6upported ~gainst one anothAr are only po6~ible lf the polnt of rotation of the 6wivelllng movement i~ located in the centre of the 6pherical gu-lde.
If ln addition to such a swivelling movement di6placements also occur at right an~les to the cyllnder axl6 then addi-tional elements (such as pl~in or antifriction bearings sr ela6tomeric element6> are nece~sary to take up such tran~-verse movements, or the end face of the piston rod mu6t be of spherical con6tructlon ln order to be able to roll on the counter-6urface, but this entail6 high surface press-ures.
Depending upon the constructlon of these elements, durln~
the movement forces of reaction occur which ctrain both the guidin~ of the piston and the participating component~. If the ~ystem only permits }ow force~ of reactlon, thl~ ca~not ba achieved with the arrangement descrlbed above or can :
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. .
~ .
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1 only be achieved at very great expense ~for instance by means of a hydro6tatlc slidlng bearlng~.
The ob~ect of the invention is to create a couplln~
arran~ement for connecting two componants which are movable relative to one another which makes it po~6ible for both component6 to be able to carry out, in addltlon to a longi tudinal movement in the dlrection tow~rd6 one another, both a swlvelling movement and a transver6e movement ln at lea6t one direction at right angles to the lon~ltudlnal movement.
It ls a further ob~ect of the lnvention to build on ~uch a coupling arran~ement and create a device for producing an ad~u6table preeeure between two components whlch are movable relative to one another, a de~ice which can be u6ed in partlcular in a roller mlll of the type 6et out ln the preamble to claim lO and which thus facilitates all move~
ment6 of the floatin~ roller occurrlng ln the operation of 6uch a roller mill as well ais lmproved ad~u6tment of the zero gap in 6uch a roller mlll.
Thi6 ob~ect is achleved accordin~ to the lnventlon by the characteri6in~ features of claims 1, 9 and lO. Advantage ou6 embodiments of the lnvention are the ~ub~ect matter of the subordinate clalm6.
Detail6 of the invention are 6et out in the followin~ de6-cription of several embodlment~ which are lllustrated in the drawings. In the drawing6:
F~ure 1 shows a horizontal sectlon throu~h a roller mill equipped wlth the arrangement according to the ~nYentlon, Figure 2 6how6 an enlar~ed repre6entation of on~ of the two couplin~ arrangement6, :
. .. . : : . , : :. : . ~.. :. .
1 Couplin~ ~rrangement and roller_mlll equipped there~lth The invention relates to a coupllng arrangement (accordlng to the preamble to claim 1), a device (according to the generlc concept of clalm 9) for producing an ad~u~table pressure between two component6 which ara movable relatlve to one another, and a roller mill ~ccording to the ~eneric concept of claim 10).
. 10 Hydraulic cyllnders of flat con6truction are known CDE-A-38 20 373~ whi~h by mean~ of ~n internal spherical ~uide permit a limited lnclined po6ition of the pi6ton rod relative to the cyl-inder. Such-cyllnders can be u6ed when two 6urface6 whlch do not lie parallel to one another ar0 to be 6upported without additlonal llnks or compensatln~
interpositlon6.
However, 6wivelllng movement6 of the two parts which are 6upported ~gainst one anothAr are only po6~ible lf the polnt of rotation of the 6wivelllng movement i~ located in the centre of the 6pherical gu-lde.
If ln addition to such a swivelling movement di6placements also occur at right an~les to the cyllnder axl6 then addi-tional elements (such as pl~in or antifriction bearings sr ela6tomeric element6> are nece~sary to take up such tran~-verse movements, or the end face of the piston rod mu6t be of spherical con6tructlon ln order to be able to roll on the counter-6urface, but this entail6 high surface press-ures.
Depending upon the constructlon of these elements, durln~
the movement forces of reaction occur which ctrain both the guidin~ of the piston and the participating component~. If the ~ystem only permits }ow force~ of reactlon, thl~ ca~not ba achieved with the arrangement descrlbed above or can :
.
. .
~ .
~:" - ,. ,' ~ ' '" '- ' " :' ' '; ' ' '' ' - 2 - za~
1 only be achieved at very great expense ~for instance by means of a hydro6tatlc slidlng bearlng~.
The ob~ect of the invention is to create a couplln~
arran~ement for connecting two componants which are movable relative to one another which makes it po~6ible for both component6 to be able to carry out, in addltlon to a longi tudinal movement in the dlrection tow~rd6 one another, both a swlvelling movement and a transver6e movement ln at lea6t one direction at right angles to the lon~ltudlnal movement.
It ls a further ob~ect of the lnvention to build on ~uch a coupling arran~ement and create a device for producing an ad~u6table preeeure between two components whlch are movable relative to one another, a de~ice which can be u6ed in partlcular in a roller mlll of the type 6et out ln the preamble to claim lO and which thus facilitates all move~
ment6 of the floatin~ roller occurrlng ln the operation of 6uch a roller mill as well ais lmproved ad~u6tment of the zero gap in 6uch a roller mlll.
Thi6 ob~ect is achleved accordin~ to the lnventlon by the characteri6in~ features of claims 1, 9 and lO. Advantage ou6 embodiments of the lnvention are the ~ub~ect matter of the subordinate clalm6.
Detail6 of the invention are 6et out in the followin~ de6-cription of several embodlment~ which are lllustrated in the drawings. In the drawing6:
F~ure 1 shows a horizontal sectlon throu~h a roller mill equipped wlth the arrangement according to the ~nYentlon, Figure 2 6how6 an enlar~ed repre6entation of on~ of the two couplin~ arrangement6, :
. .. . : : . , : :. : . ~.. :. .
- 3 - 2~
1 Figure~ 3 ~nd 4 show 6ections throu~h a further embodlment, Figures 5 to 8 show 6ections through a ~urther embodiment.
The roller mill 6hown in Figure 1 contains two rollers 1 and 2 which are pressed a~ainst one another at hlgh pres6-ure and of whlch the roller 1 i6 mounted as ~ fixed rollar ln stationary bearin~s 3, 4 and the roller 2 ls mounted a~
Q floating roller in bearln~s 5, 6 which are movable at right an~le~ to the roller axi6 (in the drawlng pl~ne of Figure 1).
The movable beàrings 5, 6 o~ the floatlng roller 2 are supported on a statlonary block 7 by means of cyllnder-piston 6ystems 8 and 9 respectively. Thls cylinder-piston systems ~, 9 are of the sama construction and constitute a couplin~ arran~ement (wlthln the term6 of clalm~ 1 to 8~ or a device <within the terms of claim 9> for producing an adJu6table pres6ure between two components which are mov-~0 able relatlve~to one another (namely the movable be~rin~s 5, 6 on the one hand the statlonary block 7 on the other hand).
The construction of~such a cylinder-pl6ton ~y6tem 8 or 9 16 explained in ~reater detall below wlth the aid of Fi~ure 2.
The cylinder-piston ~ystem shown in Fi~ura ~ contalns ~
hollow piston 40 with two cylinder part~ 11, 12, of which ln the case of the cylinder-pi6ton ~y~tem 8 the cyllnder ' 30 part 11 is connected to the movabla bearln~ ~ and the cyllnder part 12 is connected to the ~tatlonary block 7.
The two cylinder parts 11 and 12 each have a central guide lug lla, 12a.
A plston part 13, 14 engages in each of the two c,ylinder parts 11, 12, and the cylindrical ~uter peripheral surface '' : ~ . , ' , . - :
.' ~ . ',~ ' .
_ 4 ~ s~
13a, 14a of these piston parts i6 in fluid-tight contact by means of seal6 15 ~nd 16 re6pectlvely with the cylindrlcal inner peripheral surface 1lb, 12b of the cylincler parts 11, 12.
s In the embodlment of the lnventlon illu~trated ln ~lgure 2, the gulde lug6 lla, 12a havs a clrcular cro66-6ection in a cross-6ectional plane runnin~ at right angles to the common axis 17 of the guide lug~3 1la, 12a and the appertaining cylinder parts 11, 12 (i. e. at rl~3ht an~le~i to the drawing plane of Fi~ure 2~.
In the embodiment according to Figure 2 the pi~;ton part6 13, 14 have a cylindrical lnner peripheral 6urf~ce 13b, 14b respertlvely. By contrast, the outer peripheral 6urfaces 11c, 12c respectlvely of the gulde lu~s 1la, 12a - vlewed in a longltudinal sectional plane runnlng throuE~h the axl~
17 of the guide lug (approximately ln the drawing plane of Figure 2~ - is curved ln a convex manner. 1herefore the ao inner perlpAeral surfaces 13b, 14b of the pi6ton part~; 13, 14 co-operate with the outer peripheral 6urfaces 11c, 12c of the guide luK6 1la, 12~ for guldinE~ purpose~;.
Thus the inner peripheral 6urfaces 13b, 14b of the pi~;ton part~; 13, 1~ and the outer peripheral ~;urface6 11c, 12c of the guide lugs 11a, 12a are con~3tructed in E;uch a way that the two cylinder parts 11, 12 are able to carry out rela-tive to one another not only a lon~itudlnal movement (in ths direction of the axi~; 17) but al~;o a swivellinES move-ment with any c:entre of ~;wivelling ~or in~;tance in the centre Z of the floating roller 2 - cf. Figure 1), and additionally ~ transver~ movement ln at least one dlrec-tion at ri8ht angles to the cylinder axis 17. Thus the cylinder-piston ~ ;tems 8, 9 permit all movement~3 of the floating raller 2 which occur durln~ operation of th~
roller mill, and ln partic~llar al60 the incllnatlone o~ th~
:
.. . . ~. . . . . . . .
~ 5 - ~ ~5~
l floating roller 2 by an angle +J- ~ indicated in Figure 1.
The hollow spaces 18, 19, 20 between the cylinder partc 11 and 12 and the piston part6 13, 14 ara filled w.tth a fluld and are connected to one another for example by connecting channels 21, 22.
These hollow spaces 18, 19, 20 filled with a fluid are also connected by a channel 23 provided in the cyllnder part and a controllable valve 24 to an adJustable pressure mediu~
60urce which is not ~hown. Both cylinder-p~ston systems 8, 9 can advanta~eously be connected by separately adJu~table valves to a common ad~ustable pressure medium source.
Furthermore, the spaces in the two cyllnder-piston systems 8, 9 which are filled with fluid are each connected to a pre6sure medium store 25 constructed à6 a 6torage ba~ or storage fla6k and to a pressure limitlng valve 26, Thu6 by means of the cyllnder-piston sy6tems 8, 9 the two movable bearlngs 5, 6 of the floatlng roller 2 can be ~ub~ected to adJustable pressure6 or 6upportin~ forces.
A tran~verse displacement of the two cylinder part6 ll and 12 a~ain6t one another i5 taken up by an inclination of the pi~ton part6 13, 1,4 which are connected to one another or con~tructed inte~rally. The magnltude of the inclination depend6 upon the ratio of the extent of the tran~verse dis~
placement and the length of the piston parts 13l 14. Small lnclinatlon6 can be achieved by means of lon~ plston part6 13, 14.
The force of reactlon i6 produced from the friction force between the inner peripheral surface~ 13b, 14b of the piston parts 13, 14 and the ~onvex curved outer peripheral surfaces 11c, 12c of the gulde lu~s 1la~ 12a.
The path of outward travel of the two cylinder-pi6ton sy6tem6 8, 9 i6 advantageously limited by stop~ 27, 28 .
.: ' , .. , , ~ ',: . , ~
- 5 - ~ ~5~
l which co-operate wlth adJu6table ~top 6crews 29, 30.
In th~ embodiment illustrated in ~l~ures ~ and 4 the ~uide lu~6 ~e.~. 11'~) of the cyllnder part6 (e.~. 1l') have a rectangular, preferably ~quare cross-~ectlon in a ~ro6G~
6ectional plane running at right angles to the common axi6 of the ~uide lu~ and appertainin~ cyllndrical part <l.e.
in the drawlng plane of F~gure 4>. In a longltudinal sectlonal plane runnin~ throu~h the axis of the ~uida lug ~drawing plane of Figure 3> the outer perlpheral 6urface ll' of the ~ulde lug 1l'a co-operatin~ with the cylindric~l inner peripheral ~urface 13b of the piston part 13' i~
curved in a convex manner, Thu6 a swivellln~ movement of the pieton part 13' relative to the cylinder part 11' i~
pos61ble about an axl6 31 which constltutes the cylinder axic of the cylinder part surface formed by the outer peripheral curface6 11'c.
A further embodiment of the invention will be explained 2~ with the aid of Fi~ures 5 to 8, an~ in this case the 6ame reference numerals will be u~ed for the same component~ a~
ln Figure6 1 to 4. This embodiment of the coupling arran~e-ment facilitates in particular an advantageous adJu6tment of the 60-called zero ~ap of a roller mill.
Before the material for ~rindln~ is dellver~d to the two grinding roller6 of a roller mill, it mu6t be ensured that tha floating roller i6 clamped hydraulically or mechanic-ally with a certain initial tenslonal force in a fixed position ~the ~o-called zero ~ap po61tion> relative to the fixed roller. In thic zero ~ap position the two ~rindin~
rollers do not touch each other ~t the narrowqst polnt of the ~rindin~ ~p. The air ~pace at thl~ narrowest point i~
known ac the l'zero ~ap".
Until now the floatin~ roller ha~ been flxed ln th~ zero .
~ :
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- 7 - 2~5~
1 ~ap position by pressing the floatin~ roller unit hydraul-lcally with gre&t force by means of the workin~ cylinder~
a~alnst stop blocks whlch in turn are Qupported on the fixed roller unit. However, thi~ method of adJu6tlng the zero gap has two sub6tantial diQadvantages.
In view of the high stresses due to the great initial ten6ional f~rce, all bearing ~ewel~ must be of very stable construction, and above all the deformatlon of the bearing 10 Jewel~ of the floatin~ roller must not exceedrelativ91y low limitlng values.
In view of the a~dltion of~:unavoidable tolerance~, the position of the central axi~ of the floatin~ roller deter-mined by the initlal tenslonal force ls not exactly at right angles wlth reference to the machine frame, and ln the case of mountln~ wlth cylindrical bearin~s (these are plaln bearln~s and cyllndrlcal roller bearing~-) thi~ can lead to forcln~ of the floatln~ roller ehaft at the two bearing point~ and to re6ultlng breakdown~. -The disadvanta~es of the zero gap ad~u~tment indicated above can be avoided by the further embodlment of the couplin~ arrangement accordin~ to the lnvention which i6 shown in Flgures 5 to 8.
In thi6 embodiment a stop head 32, 33 respectively i~
connected to each of the guide lu~s lla, 12a of the two cyllnder part6 111 12 and deflne6 the maxlmum di6tance ` 30 between the two cyl~nder part~ 11, 12 by stop engagament with the appertaining plston part 13, 14 of the hollow pl~ton 40.
In this ca~e a free intermedlate member 34, 35 i~ provided ln each cese between a level ctop surface 32a, 33a of the stop head 32, 33 and the ~soc1ated pl~ton part 13, 14 of - . : , --:
- 8 - 2~
1 the hollow plston 40 and is constructed on its ~urface facing tha pi6ton part 13, 14 as a ball cup 34a, 35a which i8 in contact with a complementary ~pherlcal surface 13c, 14c of the piston part 13, 1~.
The stop heads 32, 33 are connected by a ~crew thread 36, 37 to the ~uide 1ug5 lla, 12a, 50 that the axlal distance between the stop fiurface 32a, 33a of the 6top head 32, 33 and the base 6urface lle, 12e of the cyllnder part6 ll, lZ
l~ i6 adJustable. Instead of thls lt is ~lso po6slble within the ~cope of the lnvention to provide a fixed connectlon between the 6top heads 32, 33 and the ~ylinder part6 ll, 12.
The outer peripheral 6urface llc, l2c re~pectlvely of the cylinder part~ 1l, 12 which i5 in contact with the cylln-drical inner peripheral 6urface 13b, 14b of the pi~ton parts 13, l4 i8 ~160 curved in a convex manner ln this embodiment.
~0 In thls embodiment the 6wivel artlculation of the cylinder part~ 11 and 12 relative to the hollow pi6ton 40 and tne 6wlvei articulation of the hollow piston 40 relative to each of the two cylinder part6 11l 12 18 al~a maintained ~5 when the lndividual parts are located ln the po~ition ~hown in Fi~ure 5, which corre6ponds to the zero ~ap posltion of the floating roller. Thus when hydraulic oll i8 delivered under pres6ure the two cyllnder part6 ll, 12 csn only travel outwards as far as the stop head6 32, 33 allow, Thu6 the entire cyllnder 6y6tem ls under an lnternal pre-stre6sin~, whilst the cylinder which is prestressed intern-ally i6 free of force toward6 the exterior. Thus tho bear-in~ Jewels of the floatin~ roller (bearings 5, 6 according to Flgure 1) al60 remain load-free in the zero gap posi tion; in contrast to the zero gap adJu6tment whlch wa6 u6ual in the pa6t no external force6 act on them.
:
2 ~ 5 ~ ?~ ~
l Since in thi6 2ero ~ap posltion of the coupling arrangement the articulation of the double ~oint cylinder formed by the two cylinder part6 ll and 12 and the hollow plston 40 i8 fully maintained, the bearin~ Jewel6 of the floatin~ rollar S ~bearing6 5, 6 with cylinder parts 11 connected thereto~
can swivel by a ~ertain amount relatlve to the machine frame. Thus the bearln~ Jewel of the relevant bearin~ i8 no lon~er pres6ed into any forced positlon, but can adapt to the partLcular po6ition of the 6haft, ~o -that in the CA6e of cylindrical bearings unde6irable end pres6ure6 are avoided. For the adapting movement of the bearing ~ewels it is merely neceseary to overcome the friction torque of the spherical support ~ball CUp6 34~, 35a> lyin3 under oil.
However, this friction torque i~ not very great becau~e of its relatively short lever arms.
If durin~ the ~rindin~ operatlon the floatin~ roller l~
pushed back by the matarial drawn into the ~rindin~ gap then the parts of the coupling arrangement take up a relative po6ition as 6hown 6chematically in Fl~ure 6. In this case the stop head6 32, 33 lift off from the level counter-6urfaces of the int3rmediate member~ 34, 35. Thu6 a dynamic ~Rp 38, 39 is produced in each ca~e between the top head6 32, 33 and the intermediate members 34, 35.
If the quantity of material for grlnding delivered to the roller mill is reduced and the delivery i& stopped, then the grindin~ operatlon chan~es a~ain to zero ~ap operation.
The ~top heads 32, 33 ara applled to the intarmediata ` ~0 member6 34, 35 ~o that the flux of force i~ again closed within the cylinder system formed by the cylinder part6 11, 12 and the hollow pi6ton 40, However, it i~ al60 po66ible that thls renewed contact between the stop head6 32, 33 and the intermedlate members 34, 35 re6ults ~rom a pravious incllnatlon of the ~loatlng .
-~o Z~5~
1 roller, The situation occurrln~ in this ca~e ls shown in Figures 7 and 8, In this case the contact is not 6imul-taneou6 and uniform on the two circular 6urfaces (l,e, the 6urfaces 32a, 34b or 33a, 35b> which face one another), but be~ins at one peripheral point which i6 initlally ~till free of force (cf. Fi~ure 7), With lncreasin~ contact the force on the contact point lncrease6 until with the flnal stoppa~e of the dellvery of material for grinding to the roller gap it has reached it6 predetermined ma~nitude for the zero ~ap operation ~cf.
Figure 8), In kinematic terms the following occurs between the stop head 32, 33 and the appertainln~ intermediate member 34, 35:
The central axis 40a of the hollow pi~ton 40 is inclined by a small angla (maximum of approximatel-y 3-) with respect to the axls 17 ~cylinder part with 6top head in horizontal plane), If the free intermediate member 34, 35 contact~
the appertainin~ stop head 32, 3~ at a point then a torque occurs on the intermediate member which rotate6 by mean6 of lts ball cup 34a, 35a into a force-absorbing position.
This force-~b60rblng po~itlon is raached when no unilater-ally actln~ force, i,e, no torque, scts any more on the lnter~ediate member 34, 35. Thus the two cylindrical sur-face6 32a, 34b or 33a, 35b have reached a posltlon parallel to one another which ls necessary for the transfer of pre~sure forces, After thi~ parallel position has been taken up the lnitlal tensional force belon~ln~ to the zero gap position can then be transferred, The point of rotation M1 formed by the ball cup 34a or 3~a re6pectlvely and the point of rotation M2 of the hollow piston ~0 do not need to be ident1cal. In~arly case durln~
~, . . .
- : . . :. ~
- - - : . . :
, . ~ , , ,. :
26~
l adJu6tin~ movement~ of the stop heads 32, 33 they change thelr relative po6itlon. The point of rotation M2 of the hollow piston 40 lie6 fixed in 6pace or ln the horizontal ? plane1 whilst the point of rotation Ml of the ball cups 3~a, 35a change~ in ~pace or in the horlzontal plane. The point of rotation of the ball cups 34a, 35a alw~ys lies on the central axis of the hollow pi~ton ~0. If the hollow piston 40 change6 its angular posit~on, then the point of rotation M1 of the ball CUp6 34a1 35a move6 on an arc of a circle with the point of rotation M2 of the hollow pl~ton ~ the central point.
The so-called 6iope of the spherical ~upport formed by the ball cups 34a1 35a i8 of course chosen 60 that the 6upport lS i6 not 6elf-locking but the intermediate member 341 35 can also rotate into its force-absorbing position with a rela-tively small rot~ry moment, The zero gap can be adJusted by chan~in~ the over~ll len~th of the double ~oint cylinder for~ed by the cyllnder parts 11, 12 and the hollow piston 40 to the de6ired value.
Shortenin~ the overall length of the cylinder sy6tem m~kes the zero gap greater1 whilst lengthenln6 lt makes the zero ~p smaller. The~changes in the overall len6th of the cylinder 6ystem are achieved by ad~ustin~ the 6top he~d 33 f~cing the bloclt 7 by means of a spindle which ls pa~sed throu~h the block 7 and en~a~es ln a rece6s 33c in the 6top head 33.
`30 The limits for the an~ular movabllity of the two cylinder part6 11, 12 relative to the hollow pi~ton 40 re~ult from the clearances between the cylinder part6 and hollow pi6ton.
', . .
1 Figure~ 3 ~nd 4 show 6ections throu~h a further embodlment, Figures 5 to 8 show 6ections through a ~urther embodiment.
The roller mill 6hown in Figure 1 contains two rollers 1 and 2 which are pressed a~ainst one another at hlgh pres6-ure and of whlch the roller 1 i6 mounted as ~ fixed rollar ln stationary bearin~s 3, 4 and the roller 2 ls mounted a~
Q floating roller in bearln~s 5, 6 which are movable at right an~le~ to the roller axi6 (in the drawlng pl~ne of Figure 1).
The movable beàrings 5, 6 o~ the floatlng roller 2 are supported on a statlonary block 7 by means of cyllnder-piston 6ystems 8 and 9 respectively. Thls cylinder-piston systems ~, 9 are of the sama construction and constitute a couplin~ arran~ement (wlthln the term6 of clalm~ 1 to 8~ or a device <within the terms of claim 9> for producing an adJu6table pres6ure between two components which are mov-~0 able relatlve~to one another (namely the movable be~rin~s 5, 6 on the one hand the statlonary block 7 on the other hand).
The construction of~such a cylinder-pl6ton ~y6tem 8 or 9 16 explained in ~reater detall below wlth the aid of Fi~ure 2.
The cylinder-piston ~ystem shown in Fi~ura ~ contalns ~
hollow piston 40 with two cylinder part~ 11, 12, of which ln the case of the cylinder-pi6ton ~y~tem 8 the cyllnder ' 30 part 11 is connected to the movabla bearln~ ~ and the cyllnder part 12 is connected to the ~tatlonary block 7.
The two cylinder parts 11 and 12 each have a central guide lug lla, 12a.
A plston part 13, 14 engages in each of the two c,ylinder parts 11, 12, and the cylindrical ~uter peripheral surface '' : ~ . , ' , . - :
.' ~ . ',~ ' .
_ 4 ~ s~
13a, 14a of these piston parts i6 in fluid-tight contact by means of seal6 15 ~nd 16 re6pectlvely with the cylindrlcal inner peripheral surface 1lb, 12b of the cylincler parts 11, 12.
s In the embodlment of the lnventlon illu~trated ln ~lgure 2, the gulde lug6 lla, 12a havs a clrcular cro66-6ection in a cross-6ectional plane runnin~ at right angles to the common axis 17 of the guide lug~3 1la, 12a and the appertaining cylinder parts 11, 12 (i. e. at rl~3ht an~le~i to the drawing plane of Fi~ure 2~.
In the embodiment according to Figure 2 the pi~;ton part6 13, 14 have a cylindrical lnner peripheral 6urf~ce 13b, 14b respertlvely. By contrast, the outer peripheral 6urfaces 11c, 12c respectlvely of the gulde lu~s 1la, 12a - vlewed in a longltudinal sectional plane runnlng throuE~h the axl~
17 of the guide lug (approximately ln the drawing plane of Figure 2~ - is curved ln a convex manner. 1herefore the ao inner perlpAeral surfaces 13b, 14b of the pi6ton part~; 13, 14 co-operate with the outer peripheral 6urfaces 11c, 12c of the guide luK6 1la, 12~ for guldinE~ purpose~;.
Thus the inner peripheral 6urfaces 13b, 14b of the pi~;ton part~; 13, 1~ and the outer peripheral ~;urface6 11c, 12c of the guide lugs 11a, 12a are con~3tructed in E;uch a way that the two cylinder parts 11, 12 are able to carry out rela-tive to one another not only a lon~itudlnal movement (in ths direction of the axi~; 17) but al~;o a swivellinES move-ment with any c:entre of ~;wivelling ~or in~;tance in the centre Z of the floating roller 2 - cf. Figure 1), and additionally ~ transver~ movement ln at least one dlrec-tion at ri8ht angles to the cylinder axis 17. Thus the cylinder-piston ~ ;tems 8, 9 permit all movement~3 of the floating raller 2 which occur durln~ operation of th~
roller mill, and ln partic~llar al60 the incllnatlone o~ th~
:
.. . . ~. . . . . . . .
~ 5 - ~ ~5~
l floating roller 2 by an angle +J- ~ indicated in Figure 1.
The hollow spaces 18, 19, 20 between the cylinder partc 11 and 12 and the piston part6 13, 14 ara filled w.tth a fluld and are connected to one another for example by connecting channels 21, 22.
These hollow spaces 18, 19, 20 filled with a fluid are also connected by a channel 23 provided in the cyllnder part and a controllable valve 24 to an adJustable pressure mediu~
60urce which is not ~hown. Both cylinder-p~ston systems 8, 9 can advanta~eously be connected by separately adJu~table valves to a common ad~ustable pressure medium source.
Furthermore, the spaces in the two cyllnder-piston systems 8, 9 which are filled with fluid are each connected to a pre6sure medium store 25 constructed à6 a 6torage ba~ or storage fla6k and to a pressure limitlng valve 26, Thu6 by means of the cyllnder-piston sy6tems 8, 9 the two movable bearlngs 5, 6 of the floatlng roller 2 can be ~ub~ected to adJustable pressure6 or 6upportin~ forces.
A tran~verse displacement of the two cylinder part6 ll and 12 a~ain6t one another i5 taken up by an inclination of the pi~ton part6 13, 1,4 which are connected to one another or con~tructed inte~rally. The magnltude of the inclination depend6 upon the ratio of the extent of the tran~verse dis~
placement and the length of the piston parts 13l 14. Small lnclinatlon6 can be achieved by means of lon~ plston part6 13, 14.
The force of reactlon i6 produced from the friction force between the inner peripheral surface~ 13b, 14b of the piston parts 13, 14 and the ~onvex curved outer peripheral surfaces 11c, 12c of the gulde lu~s 1la~ 12a.
The path of outward travel of the two cylinder-pi6ton sy6tem6 8, 9 i6 advantageously limited by stop~ 27, 28 .
.: ' , .. , , ~ ',: . , ~
- 5 - ~ ~5~
l which co-operate wlth adJu6table ~top 6crews 29, 30.
In th~ embodiment illustrated in ~l~ures ~ and 4 the ~uide lu~6 ~e.~. 11'~) of the cyllnder part6 (e.~. 1l') have a rectangular, preferably ~quare cross-~ectlon in a ~ro6G~
6ectional plane running at right angles to the common axi6 of the ~uide lu~ and appertainin~ cyllndrical part <l.e.
in the drawlng plane of F~gure 4>. In a longltudinal sectlonal plane runnin~ throu~h the axis of the ~uida lug ~drawing plane of Figure 3> the outer perlpheral 6urface ll' of the ~ulde lug 1l'a co-operatin~ with the cylindric~l inner peripheral ~urface 13b of the piston part 13' i~
curved in a convex manner, Thu6 a swivellln~ movement of the pieton part 13' relative to the cylinder part 11' i~
pos61ble about an axl6 31 which constltutes the cylinder axic of the cylinder part surface formed by the outer peripheral curface6 11'c.
A further embodiment of the invention will be explained 2~ with the aid of Fi~ures 5 to 8, an~ in this case the 6ame reference numerals will be u~ed for the same component~ a~
ln Figure6 1 to 4. This embodiment of the coupling arran~e-ment facilitates in particular an advantageous adJu6tment of the 60-called zero ~ap of a roller mill.
Before the material for ~rindln~ is dellver~d to the two grinding roller6 of a roller mill, it mu6t be ensured that tha floating roller i6 clamped hydraulically or mechanic-ally with a certain initial tenslonal force in a fixed position ~the ~o-called zero ~ap po61tion> relative to the fixed roller. In thic zero ~ap position the two ~rindin~
rollers do not touch each other ~t the narrowqst polnt of the ~rindin~ ~p. The air ~pace at thl~ narrowest point i~
known ac the l'zero ~ap".
Until now the floatin~ roller ha~ been flxed ln th~ zero .
~ :
. .
. ~ . - ~ . . :
.
- 7 - 2~5~
1 ~ap position by pressing the floatin~ roller unit hydraul-lcally with gre&t force by means of the workin~ cylinder~
a~alnst stop blocks whlch in turn are Qupported on the fixed roller unit. However, thi~ method of adJu6tlng the zero gap has two sub6tantial diQadvantages.
In view of the high stresses due to the great initial ten6ional f~rce, all bearing ~ewel~ must be of very stable construction, and above all the deformatlon of the bearing 10 Jewel~ of the floatin~ roller must not exceedrelativ91y low limitlng values.
In view of the a~dltion of~:unavoidable tolerance~, the position of the central axi~ of the floatin~ roller deter-mined by the initlal tenslonal force ls not exactly at right angles wlth reference to the machine frame, and ln the case of mountln~ wlth cylindrical bearin~s (these are plaln bearln~s and cyllndrlcal roller bearing~-) thi~ can lead to forcln~ of the floatln~ roller ehaft at the two bearing point~ and to re6ultlng breakdown~. -The disadvanta~es of the zero gap ad~u~tment indicated above can be avoided by the further embodlment of the couplin~ arrangement accordin~ to the lnvention which i6 shown in Flgures 5 to 8.
In thi6 embodiment a stop head 32, 33 respectively i~
connected to each of the guide lu~s lla, 12a of the two cyllnder part6 111 12 and deflne6 the maxlmum di6tance ` 30 between the two cyl~nder part~ 11, 12 by stop engagament with the appertaining plston part 13, 14 of the hollow pl~ton 40.
In this ca~e a free intermedlate member 34, 35 i~ provided ln each cese between a level ctop surface 32a, 33a of the stop head 32, 33 and the ~soc1ated pl~ton part 13, 14 of - . : , --:
- 8 - 2~
1 the hollow plston 40 and is constructed on its ~urface facing tha pi6ton part 13, 14 as a ball cup 34a, 35a which i8 in contact with a complementary ~pherlcal surface 13c, 14c of the piston part 13, 1~.
The stop heads 32, 33 are connected by a ~crew thread 36, 37 to the ~uide 1ug5 lla, 12a, 50 that the axlal distance between the stop fiurface 32a, 33a of the 6top head 32, 33 and the base 6urface lle, 12e of the cyllnder part6 ll, lZ
l~ i6 adJustable. Instead of thls lt is ~lso po6slble within the ~cope of the lnvention to provide a fixed connectlon between the 6top heads 32, 33 and the ~ylinder part6 ll, 12.
The outer peripheral 6urface llc, l2c re~pectlvely of the cylinder part~ 1l, 12 which i5 in contact with the cylln-drical inner peripheral 6urface 13b, 14b of the pi~ton parts 13, l4 i8 ~160 curved in a convex manner ln this embodiment.
~0 In thls embodiment the 6wivel artlculation of the cylinder part~ 11 and 12 relative to the hollow pi6ton 40 and tne 6wlvei articulation of the hollow piston 40 relative to each of the two cylinder part6 11l 12 18 al~a maintained ~5 when the lndividual parts are located ln the po~ition ~hown in Fi~ure 5, which corre6ponds to the zero ~ap posltion of the floating roller. Thus when hydraulic oll i8 delivered under pres6ure the two cyllnder part6 ll, 12 csn only travel outwards as far as the stop head6 32, 33 allow, Thu6 the entire cyllnder 6y6tem ls under an lnternal pre-stre6sin~, whilst the cylinder which is prestressed intern-ally i6 free of force toward6 the exterior. Thus tho bear-in~ Jewels of the floatin~ roller (bearings 5, 6 according to Flgure 1) al60 remain load-free in the zero gap posi tion; in contrast to the zero gap adJu6tment whlch wa6 u6ual in the pa6t no external force6 act on them.
:
2 ~ 5 ~ ?~ ~
l Since in thi6 2ero ~ap posltion of the coupling arrangement the articulation of the double ~oint cylinder formed by the two cylinder part6 ll and 12 and the hollow plston 40 i8 fully maintained, the bearin~ Jewel6 of the floatin~ rollar S ~bearing6 5, 6 with cylinder parts 11 connected thereto~
can swivel by a ~ertain amount relatlve to the machine frame. Thus the bearln~ Jewel of the relevant bearin~ i8 no lon~er pres6ed into any forced positlon, but can adapt to the partLcular po6ition of the 6haft, ~o -that in the CA6e of cylindrical bearings unde6irable end pres6ure6 are avoided. For the adapting movement of the bearing ~ewels it is merely neceseary to overcome the friction torque of the spherical support ~ball CUp6 34~, 35a> lyin3 under oil.
However, this friction torque i~ not very great becau~e of its relatively short lever arms.
If durin~ the ~rindin~ operatlon the floatin~ roller l~
pushed back by the matarial drawn into the ~rindin~ gap then the parts of the coupling arrangement take up a relative po6ition as 6hown 6chematically in Fl~ure 6. In this case the stop head6 32, 33 lift off from the level counter-6urfaces of the int3rmediate member~ 34, 35. Thu6 a dynamic ~Rp 38, 39 is produced in each ca~e between the top head6 32, 33 and the intermediate members 34, 35.
If the quantity of material for grlnding delivered to the roller mill is reduced and the delivery i& stopped, then the grindin~ operatlon chan~es a~ain to zero ~ap operation.
The ~top heads 32, 33 ara applled to the intarmediata ` ~0 member6 34, 35 ~o that the flux of force i~ again closed within the cylinder system formed by the cylinder part6 11, 12 and the hollow pi6ton 40, However, it i~ al60 po66ible that thls renewed contact between the stop head6 32, 33 and the intermedlate members 34, 35 re6ults ~rom a pravious incllnatlon of the ~loatlng .
-~o Z~5~
1 roller, The situation occurrln~ in this ca~e ls shown in Figures 7 and 8, In this case the contact is not 6imul-taneou6 and uniform on the two circular 6urfaces (l,e, the 6urfaces 32a, 34b or 33a, 35b> which face one another), but be~ins at one peripheral point which i6 initlally ~till free of force (cf. Fi~ure 7), With lncreasin~ contact the force on the contact point lncrease6 until with the flnal stoppa~e of the dellvery of material for grinding to the roller gap it has reached it6 predetermined ma~nitude for the zero ~ap operation ~cf.
Figure 8), In kinematic terms the following occurs between the stop head 32, 33 and the appertainln~ intermediate member 34, 35:
The central axis 40a of the hollow pi~ton 40 is inclined by a small angla (maximum of approximatel-y 3-) with respect to the axls 17 ~cylinder part with 6top head in horizontal plane), If the free intermediate member 34, 35 contact~
the appertainin~ stop head 32, 3~ at a point then a torque occurs on the intermediate member which rotate6 by mean6 of lts ball cup 34a, 35a into a force-absorbing position.
This force-~b60rblng po~itlon is raached when no unilater-ally actln~ force, i,e, no torque, scts any more on the lnter~ediate member 34, 35. Thus the two cylindrical sur-face6 32a, 34b or 33a, 35b have reached a posltlon parallel to one another which ls necessary for the transfer of pre~sure forces, After thi~ parallel position has been taken up the lnitlal tensional force belon~ln~ to the zero gap position can then be transferred, The point of rotation M1 formed by the ball cup 34a or 3~a re6pectlvely and the point of rotation M2 of the hollow piston ~0 do not need to be ident1cal. In~arly case durln~
~, . . .
- : . . :. ~
- - - : . . :
, . ~ , , ,. :
26~
l adJu6tin~ movement~ of the stop heads 32, 33 they change thelr relative po6itlon. The point of rotation M2 of the hollow piston 40 lie6 fixed in 6pace or ln the horizontal ? plane1 whilst the point of rotation Ml of the ball cups 3~a, 35a change~ in ~pace or in the horlzontal plane. The point of rotation of the ball cups 34a, 35a alw~ys lies on the central axis of the hollow pi~ton ~0. If the hollow piston 40 change6 its angular posit~on, then the point of rotation M1 of the ball CUp6 34a1 35a move6 on an arc of a circle with the point of rotation M2 of the hollow pl~ton ~ the central point.
The so-called 6iope of the spherical ~upport formed by the ball cups 34a1 35a i8 of course chosen 60 that the 6upport lS i6 not 6elf-locking but the intermediate member 341 35 can also rotate into its force-absorbing position with a rela-tively small rot~ry moment, The zero gap can be adJusted by chan~in~ the over~ll len~th of the double ~oint cylinder for~ed by the cyllnder parts 11, 12 and the hollow piston 40 to the de6ired value.
Shortenin~ the overall length of the cylinder sy6tem m~kes the zero gap greater1 whilst lengthenln6 lt makes the zero ~p smaller. The~changes in the overall len6th of the cylinder 6ystem are achieved by ad~ustin~ the 6top he~d 33 f~cing the bloclt 7 by means of a spindle which ls pa~sed throu~h the block 7 and en~a~es ln a rece6s 33c in the 6top head 33.
`30 The limits for the an~ular movabllity of the two cylinder part6 11, 12 relative to the hollow pi~ton 40 re~ult from the clearances between the cylinder part6 and hollow pi6ton.
', . .
Claims (10)
1. Coupling arrangement for connecting two components which are movable relative to one another, characterised by the following features:
a) the two components are constructed as cylinder parts (11, 12 each having a central guide lug (11, 12a);
b) a piston part (13, 14) engage in each of the cylinder parts (11, 12), and the cylindrical outer peripheral surface (13a, 14a) of these piston parts is in fluid-tight contact with the cylindrical inner peripheral surface (11b, 12b) of the cylinder parts (11, 12) whilst the inner peripheral surface (13b, 14b) of the said piston parts co-operates at least partially with the outer peripheral surface (11c, 12c) of the guide lug for guiding purposes;
c) the inner peripheral surfaces (13b) 14b) of the piston parts (13, 14) and the outer peripheral surfaces (11c, 12c) of the guide lugs (11a, 12a) of the cylinder parts (11, 12) are constructed in such a way that the two cylinder parts are able to carry out relative to one another not only a longitudinal move-ment in the direction of one cylinder axis (17) but also a swivelling movement and a transverse movement in at least one direction at right angles to the cylinder axis;
d) the hollow spaces (18, 19, 20) between the cylinder parts (11, 12) and the piston parts (13, 14) are filled with a fluid.
a) the two components are constructed as cylinder parts (11, 12 each having a central guide lug (11, 12a);
b) a piston part (13, 14) engage in each of the cylinder parts (11, 12), and the cylindrical outer peripheral surface (13a, 14a) of these piston parts is in fluid-tight contact with the cylindrical inner peripheral surface (11b, 12b) of the cylinder parts (11, 12) whilst the inner peripheral surface (13b, 14b) of the said piston parts co-operates at least partially with the outer peripheral surface (11c, 12c) of the guide lug for guiding purposes;
c) the inner peripheral surfaces (13b) 14b) of the piston parts (13, 14) and the outer peripheral surfaces (11c, 12c) of the guide lugs (11a, 12a) of the cylinder parts (11, 12) are constructed in such a way that the two cylinder parts are able to carry out relative to one another not only a longitudinal move-ment in the direction of one cylinder axis (17) but also a swivelling movement and a transverse movement in at least one direction at right angles to the cylinder axis;
d) the hollow spaces (18, 19, 20) between the cylinder parts (11, 12) and the piston parts (13, 14) are filled with a fluid.
2. Coupling arrangement as claimed in claim 1, charac-terised in that the guide lugs (11a, 12a) have a circular cross-section in a cross-sectional plane running at right angles to the common axis (17) of the guide lug and appertaining cylindrical part (11, 12).
3. Coupling arrangement as claimed in claim 1, charac-terised in that the guide lugs (e.g. 11'a) have a rectangu-lar, preferably square cross-section in a cross-sectional plane running at right angles to the common axis of the guide lug and appertaining cylindrical part (e.g. 11'a).
4. Coupling arrangement as claimed in claim 1, charac-terised in that the inner peripheral surface (13b, 14b) of the piston parts (13, 14) is of cylindrical construction, and the outer peripheral surface (11c, 12c) of the guide lugs (11a 12a) which co-operates with the said inner peripheral surface of the piston parts is curved in a convex manner - viewed in a longitudinal sectional plane running through the axis (17) of the guide lug.
5. Coupling arrangement as claimed in claim 1, charac-terised in that the outer peripheral surface of the guide lugs is of cylindrical construction and the inner peripher-al surface of the piston parts which co-operates with the said outer peripheral surface of the guide lugs is curved in a convex manner - viewed in a longitudinal sectional plane running through the axis of the piston part.
6. Coupling arrangement as claimed in claim 1, charac-terised in that a stop head (32, 33) is connected to each of the guide lugs (11a, 12a) of the two cylinder parts (11, 12) and defines the maximum distance between the two cylinder parts (11a, 12a) by stop engagement with the apper-taining piston part (13, 14) of a hollow piston (40).
7. Coupling arrangement as claimed in claim 6, charac-terised in that the axial distance between a stop surface (32a, 33a) of the stop head (32, 33) which co-operates with the appertaining piston part (13, 14) and the base of the cylinder part (11, 12) bearing this stop head is adjust-able.
8. Coupling arrangement as claimed in claim 6, charac-terised in that a free intermediate member (34, 35) is provided in each case between the two stop heads(32, 33) and the appertaining piston parts (13, 14) of the hollow piston (40) and is constructed on its surface facing the piston part as a ball cup (34a, 35a) and is in contact with a complementary spherical surface (13c, 14c) of the piston part (13, 14), whilst the surface (32a, 34b, and 33a, 35b respectively) which face one another of the stop head (32, 33) and of the intermediate member (34, 35) are constructed as level stop surfaces.
9. Device for producing an adjustable pressure between two components which are movable relative to one another, characterised by a coupling arrangement as claimed in claim 1, in which the hollow spaces (18, 19, 20) between the cylinder parts (11, 12) and the piston parts (13, 14) are connected to an adjustable pressure medium source.
10. Roller mill for crushing brittle material for grind-ing, containing two rollers which are pressed towards one another at high pressure and of which one roller is mounted as a fixed roller (1) in stationary bearings (3, 4) and the other roller is mounted as a floating roller (2) in bear-ings (5, 6) which are movable at right angles to the roller axis, the movable bearings (5, 6) of the floatings roller (2) being supported on a stationary block (7) by means of a cylinder-piston system (8, 9) connected to an adjustable pressure medium source, characterised. by two devices as claimed in claim 9 associated with the two movable bearings (5, 6) of the floating roller (2), wherein in each of the two devices one of the two components connected to one another by the coupling arrangement is connected to the stationary block and the other component is connected to the appertaining movable bearing of the floating roller.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4103887A DE4103887A1 (en) | 1991-02-08 | 1991-02-08 | CLUTCH DEVICE AND ROLL MILL EQUIPPED WITH IT |
| DEP4103887.8 | 1991-02-08 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2059348A1 true CA2059348A1 (en) | 1992-08-09 |
Family
ID=6424678
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002059348A Abandoned CA2059348A1 (en) | 1991-02-08 | 1992-01-14 | Coupling arrangement and roller mill equipped therewith |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0498074A3 (en) |
| KR (1) | KR920016737A (en) |
| AU (1) | AU1025892A (en) |
| CA (1) | CA2059348A1 (en) |
| DE (1) | DE4103887A1 (en) |
| FI (1) | FI920515A (en) |
| MX (1) | MX9200543A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102218356A (en) * | 2010-04-16 | 2011-10-19 | 坡利西斯股份公司 | Roller grinding mill |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4234481A1 (en) * | 1992-10-13 | 1994-04-14 | Krupp Polysius Ag | Roller mill for crashing brittle material with - has two high pressure rollers and machine frame has two swivelable clamping frames at both roller sides with tensile anchors |
| CN111992104A (en) * | 2020-08-13 | 2020-11-27 | 湖州爆米花信息科技有限公司 | Production SMC material's for auto parts dispersion devices |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE165372C (en) * | ||||
| DD48112A (en) * | ||||
| DE597775C (en) * | 1932-08-20 | 1934-06-02 | Schneider Jaquet & Cie Sa | Device for regulating the contact pressure of grinding rollers |
| DE938579C (en) * | 1953-09-15 | 1956-02-02 | Braunschweigische Maschb Ansta | Storage for a roller of roller mills with several rollers, especially sugar cane mills |
| DE1151428B (en) * | 1959-04-17 | 1963-07-11 | Kenneth Gauldie | Jaw crusher with hydraulic power transmission device |
| DE2726955C2 (en) * | 1977-06-15 | 1983-01-20 | Bremshey Ag, 5650 Solingen | Lockable hydro-pneumatic lifting unit |
| DE3007112A1 (en) * | 1980-02-26 | 1981-09-03 | J.M. Voith Gmbh, 7920 Heidenheim | SUPPORT DEVICE FOR A ROLLER |
| IT1147385B (en) * | 1981-07-16 | 1986-11-19 | Giacomo Ferrero | CYLINDRIA OR CYLINDER MILL WITH HYDRAULIC ADJUSTMENT AND SAFETY |
| DE8129516U1 (en) * | 1981-10-09 | 1983-05-05 | J.M. Voith Gmbh, 7920 Heidenheim | Hydrostatic bearing support for highly loaded press rolls, especially for paper machines |
| GB2123709A (en) * | 1982-07-05 | 1984-02-08 | Bowman And Sons Limited Jas | Roller mounting arrangement for a roller mill |
| IT1173599B (en) * | 1984-05-10 | 1987-06-24 | Carle & Montanri Spa | PRESSURE CONTROL CIRCUIT ON THE SUPPORTS OF THE CHOCOLATE REFINER CYLINDERS |
| DE3910827A1 (en) * | 1988-04-30 | 1989-11-09 | Voith Gmbh J M | Cylinder/piston unit for displacing a roller transversely to its longitudinal axis |
| FI891868A (en) * | 1988-04-30 | 1989-10-31 | Voith Gmbh J M | CYLINDER-PISTON-ENHET FOER ATT FOERSKJUTA EN VALS TVAERS OEVER DESS LAENGDAXELL. |
-
1991
- 1991-02-08 DE DE4103887A patent/DE4103887A1/en not_active Withdrawn
- 1991-12-20 EP EP19910121883 patent/EP0498074A3/en not_active Withdrawn
-
1992
- 1992-01-14 CA CA002059348A patent/CA2059348A1/en not_active Abandoned
- 1992-01-16 AU AU10258/92A patent/AU1025892A/en not_active Abandoned
- 1992-01-31 KR KR1019920001425A patent/KR920016737A/en not_active Application Discontinuation
- 1992-02-07 FI FI920515A patent/FI920515A/en not_active Application Discontinuation
- 1992-02-07 MX MX9200543A patent/MX9200543A/en unknown
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102218356A (en) * | 2010-04-16 | 2011-10-19 | 坡利西斯股份公司 | Roller grinding mill |
| US20110253825A1 (en) * | 2010-04-16 | 2011-10-20 | Daniel Frerich | Roller grinding mill |
| US8517296B2 (en) * | 2010-04-16 | 2013-08-27 | Polysius Ag | Grinding mill with dual articulation actuation cylinder |
| CN102218356B (en) * | 2010-04-16 | 2015-02-25 | 坡利西斯股份公司 | Roller grinding mill |
Also Published As
| Publication number | Publication date |
|---|---|
| KR920016737A (en) | 1992-09-25 |
| MX9200543A (en) | 1992-08-01 |
| FI920515A (en) | 1992-08-09 |
| FI920515A0 (en) | 1992-02-07 |
| EP0498074A3 (en) | 1993-01-13 |
| DE4103887A1 (en) | 1992-08-13 |
| AU1025892A (en) | 1992-08-13 |
| EP0498074A2 (en) | 1992-08-12 |
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