CA1327324C - Rotational control apparatus - Google Patents
Rotational control apparatusInfo
- Publication number
- CA1327324C CA1327324C CA000545801A CA545801A CA1327324C CA 1327324 C CA1327324 C CA 1327324C CA 000545801 A CA000545801 A CA 000545801A CA 545801 A CA545801 A CA 545801A CA 1327324 C CA1327324 C CA 1327324C
- Authority
- CA
- Canada
- Prior art keywords
- interface
- axially extending
- legs
- housing end
- housing
- 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.)
- Expired - Lifetime
Links
- 238000009434 installation Methods 0.000 claims description 9
- 238000007789 sealing Methods 0.000 claims description 9
- 239000012530 fluid Substances 0.000 claims description 5
- 238000013022 venting Methods 0.000 claims description 3
- 230000006872 improvement Effects 0.000 claims description 2
- 238000005266 casting Methods 0.000 abstract description 15
- 238000009423 ventilation Methods 0.000 abstract description 5
- 238000010276 construction Methods 0.000 description 13
- 238000004519 manufacturing process Methods 0.000 description 8
- 238000012423 maintenance Methods 0.000 description 7
- CYTYCFOTNPOANT-UHFFFAOYSA-N Perchloroethylene Chemical compound ClC(Cl)=C(Cl)Cl CYTYCFOTNPOANT-UHFFFAOYSA-N 0.000 description 6
- 238000001816 cooling Methods 0.000 description 6
- 230000000295 complement effect Effects 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 239000011800 void material Substances 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 1
- 241001272720 Medialuna californiensis Species 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000010974 bronze Substances 0.000 description 1
- 238000010073 coating (rubber) Methods 0.000 description 1
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Classifications
-
- 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
- F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
- F16D67/02—Clutch-brake combinations
- F16D67/04—Clutch-brake combinations fluid actuated
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
TITLE
Rotational Control Apparatus ABSTRACT OF THE DISCLOSURE
A rotational control apparatus is shown in its most preferred form as a clutch-brake including an improved housing having a cylindrical body portion and first and second housing ends removably secured thereto. The body portion includes an axially extending annular member intersecting with a radially extending annular member.
The radially extending annular member forms an interface surface and a surface for reciprocal receipt of a piston inside the axially extending annular member and forms a mounting flange outside the axially extending annular member for securing axially extending bolts threadably received in the second housing end. The first housing end includes an axially extending projection having surfaces for receipt in the axially extending annular member and for reciprocal receipt of the piston. The clutch-brake in a preferred form further includes an improved friction interface disc including a stamped flat ring portion secured to a second flat ring portion of a cast friction interface element in a spaced condition to form spaced cutouts for heat ventilation.
The improved friction interface disc allows easy and inexpensive cast components eliminating casting cores for heat ventilation access between the interface surfaces of the interface disc.
Rotational Control Apparatus ABSTRACT OF THE DISCLOSURE
A rotational control apparatus is shown in its most preferred form as a clutch-brake including an improved housing having a cylindrical body portion and first and second housing ends removably secured thereto. The body portion includes an axially extending annular member intersecting with a radially extending annular member.
The radially extending annular member forms an interface surface and a surface for reciprocal receipt of a piston inside the axially extending annular member and forms a mounting flange outside the axially extending annular member for securing axially extending bolts threadably received in the second housing end. The first housing end includes an axially extending projection having surfaces for receipt in the axially extending annular member and for reciprocal receipt of the piston. The clutch-brake in a preferred form further includes an improved friction interface disc including a stamped flat ring portion secured to a second flat ring portion of a cast friction interface element in a spaced condition to form spaced cutouts for heat ventilation.
The improved friction interface disc allows easy and inexpensive cast components eliminating casting cores for heat ventilation access between the interface surfaces of the interface disc.
Description
1~27329 :
1 : ROTATIONAL CONTROL APPARATUS
BACKGROUND
The present invention relates generally to rotational ~, control apparatus, particularly to apparatus for 5 controlling rotation of an output, and specifically in : the preferred form to combination clutch-brakes.
It is often desired to control an output at different conditlons such as by a clutch-brake. However, prior clutch-brakes suffered from deficiencles in ease of 10 manufacture, assembly, installation, and maintenance and : in: their ~bility:to be utilized with differing industrial sta~dard interconnectiQns. Thus, a need has arisen for a clutch-brake havlng an improved housing utilizing ,~
132732`~
1 : ROTATIONAL CONTROL APPARATUS
BACKGROUND
The present invention relates generally to rotational ~, control apparatus, particularly to apparatus for 5 controlling rotation of an output, and specifically in : the preferred form to combination clutch-brakes.
It is often desired to control an output at different conditlons such as by a clutch-brake. However, prior clutch-brakes suffered from deficiencles in ease of 10 manufacture, assembly, installation, and maintenance and : in: their ~bility:to be utilized with differing industrial sta~dard interconnectiQns. Thus, a need has arisen for a clutch-brake havlng an improved housing utilizing ,~
132732`~
i 1 modular, interchangeable, easily and inexpensively cast components which may be machined for varying industrial interconnections and which allow ease of apparatus !~ installation and maintenance.
The present invention solves these and other '~ deficiencies and problems in rotational control apparatus by providing easily and inexpensively cast or otherwise formed components which can be easily assembled into a 10 unit which in turn can be easily installed and l maintained. In particular, an improved housing is provided including first and second housing ends secured ; to a cylindrical body portion. The cylindrical body portion includes an integral interface member extending 15 radially inwardly and an integral mounting flange extending radially outwardly of an axially extending annular member. The first housing end is removably I secured to the cylindrical body portion and the second !~ housing end is removably secured to the integral mounting '! 20 flange allowing the apparatus to be readily disassembled into first and second major components which are particularly advantageous for installation and maintenance.
Further, in another aspect, the interface disc 25 having first ~nd second lnterface surfaces is formed of a first, flat ring portion and a cast interface element including a second, integral flat ring portlon. The first, flat ring portlon is held in a spaced condition for heat ventilation by upstanding , 30 webs cast on the second ring portion eliminating casting cores. Further, the removability of the first ring portion allows better access to the friction lining rin~ securement to allow removal thereof without requiring dismantling of the cast interface 35 element from the remaining components.
It is thus an aim of the present invention to provide a novel apparatus for controlling rotation of an ' :
; .
~', 132732`il . -3-output.
It is further an aim of the present invention to ;~ provide such a novel rotational control apparatus having r~` an improved housing.
It is further an aim of the present invention to provide such a novel rotational control apparatus having an improved interface disc having first and second interface surfaces.
It is further an aim of the present invention to 10 provide such a novel rotational control apparatus which can be separated into two major components for installation and maintenance.
It is further an aim of the present invention to provide such a novel rotational control apparatus having 15 more torque capacity.
It is further an aim of the present invention to provide such a novel rotational control apparatus having faster actuation.
It is further an aim of the present invention to 20 provide such a novel rotational control apparatus utilizing modular, interchangeable components.
t is further an aim of the present invention to provide such a novel rotational control apparatus ~; utilizing common castings for varying industrial 25 interconnections.
It is further an aim of the present invention to provide such a novel rotational control apparatus utilizing components which may be easily and ` inexpensively cast.
These and further aims and advantages of the present invention will become clearer in light of the following detailed description of illustrative embodlments of this invention described in connection with tAe drawing~.
35 DESCRIPTI~N OF THE DRAWINGS
The illustrative embodiments may best be described by :'~
.. . .
~`
`- 132732~
"
~ 1 reference to the accompanying drawings where:
,~ Figure 1 shows a cross sectional view of a clutch-brake ac~ording to the preferred teachings of the ~f present invention.
Figure 2 shows an exploded, perspective view of the , improved housing of the clutch-brake of Figure 1 illustrating the modular interchangeability thereof.
, Figure 3 shows a cross sectional view of an alternate embodiment of a clutch-brake according to the preferred ~; 10 teachings of the present invention.
Figure 4 shows an exploded, perspective view of the `~ clutch-brake of Figure 3.
All figures are drawn for ease of explanation of the basic teachings of the present invention only; the 15 extensions of the Figures with respect to number, ;~ position, relationship, and dimensions of the parts to form the preferred embodiment will be explained or will t be within the skill of the art after the following ' teachings of the present invention have been read and 20 understood. Further, the exact dimensions and dimensional proportions to conform to specific force, weight, strength, and similar requirements will likewise be within the ~kill of the art after the following teachings of the present invention have been read and `~ 25 understood.
Where used in the various figures of the drawings, the same numerals designate the same or similar parts.
Furthermore, when the terms "top", "bottom", "inward", "outward", "first", "second", "inside", "outside", 30 "radially", "axlally", "circumferentially", and similar terms are used herein, it should be understood that these terms have reference only to the structure shown ln the drawings ~s it would appear to a person viewing the drawings and are utilized only to facilitate describing 35 the invention.
:
:~
:~:
132732 ~
Apparatus for providing rotational control of an output with an input and a housing according to the ~i teachings of the present invention is shown in the i~Z drawings and is generally designated A. In the most 5 preferred embodiments of the present invention, apparatus , A is a clutch-brake and is an improvement of the type 'f shown and described in U.S. Patent No. 4,534,454. For purpose of explanation of the basic teachings of the 10 present invention, the same numerals designate the same , or similar parts in the present figures and the figures ' of U.S. Patent No. 4,534,454. The description of the t common numerals and the clutch-brake A may be found Z herein and in U.S. Patent No. 4,534,454.
Referring to the drawings in detail, the clutch-brake A includes the driven rotatable output shaft 10. Further provided is the interface dlsc shown in its preferred form as friction disc 28. In the preferred embodiment ' of Figures 1 and 2, mounted by means of bolts 29 on the ! 20 flrst face 30 of friction disc 28 is the first interface surface shown as friction lining ring 32. In the preferred embodiment of Figures 3 and 4, frictlon disc ~ 28 includes a flat ring portion 23b and a friction l~ interface element 25. Friction lnterface element 25 1~
~ 25 includes a flat ring portion 25a havlng Z circumferentlally spaced, radlally extending webs 27 ~ upstanding from the face opposite to the lnterface Z surface thereof. ~xlally extending openings 9S of the type shown and descrlbed in U.S. Patent No. 4,078,637 30 are formed in the flat ring portlon 25a lntermedlate ~; webs 27. Webs 27 include axially extendlng shoulders 27a for receipt of the radially inward axially extending opening of flat ring portlon 23b. Bolts 29 threadably received in webs 27 extend through and secure friction 35 llning rlng 32 and the flat rlng portion 23b to frlction interface element 25 with the face opposite ~ ,~
:
'~;` ' : .
~327~2~
1 to the interface surface of ring portion 23b abutting ~ with the free ends of webs 27 and spaced from the face of : ring portion 25a to form spaced cutouts 23a for heat - venting.
Disc 28 terminates radially inwardly in the hollow hub 34 formed with splines 36 slidably engaged with splines 38 of shaft 10. Formed on the hub 34 is the annular recess 40 forming the shoulder 42. Mounted in ; the recess 40 and against the shoulder 42 is the inner 10 race 44 of bearing 46.
The numeral 48 designates an annular piston which i includes the axially disposed annular flange portion 50.
The outer race 54 of bearing 46 is mounted on the inner : surface of piston flange portion 50 and against the 15 shoulder 56 thereby rotatably mounting shaft 10 and a portion of hub 34 within piston 48.
~: Clutch-brake A according to the teachings of the present invention includes a housing 150 of an ~; improved construction including modular, : 20 interchangeable components 82 or 156, 152, and 154.
Specifically, housing 150 includes a cylindrical body portion 152 having a first, generally axially :~ extending annular member 158 which intersects with a second, generally radially extending annular member 25 160. Member 158 includes a first, free annular end 164 and a second, free annular end 168. In the most preferred form, annular recess 186 is provided in the ~:~ radially inward diameter of annular member 158 and ad~acent end 168 for allowlng ease of assembly.
Member 160 lncludes an integral, annular body portion 72 located radially inwardly of annular member 15~ and extending toward its s~cond end 168. Annular body portion 72 includes a backing portion 68 for mounting thereon the ~econd, fixed interface member ; 35 shown as friction lining ring 79 opposite frictlon disc ;~:
:~:
132732~
,, ~, 1 28. Friction lining ring 79 in the preferred form shown ~, in Figures 3 and 4 is formed of two, half-moon pieces to allow radial removal without removing friction interface 5'` element 25. Lining 79 is secured by bolts 81 to backing 5 portion 68.
Member 160 further includes an annular, radially .~ extending mounting flange 170 having circumferentially :~ spaced, axially extending apertures 172. Flange 170 is generally located such that body portion 72 is ,~ 10 slightly offset from flange 170.
. Body portion 152 further includes in its most preferred form, integral, axially extending, circumferentially spaced fins 176 extending from annular ; member 158 from flange 170 to a point slightly axially 15 spaced inwardly of end 168. Axially extending, circumferentlally spaced mounting shoulders 178 are further provided in the preferred embodiment extending from annular member 158 from flange 170 to end 168 and circumferentially spaced from fins 176. One of the 20 shoulders 178 in the preferred embodiment includes a port enlargement 180 including axially spaced, radially extending air ports 24 and 182.
Housing end 154 is generally planar and circular in configuration having a diameter larger than annular 25 member 158 of cylindrical body portion 152. End 154 includes axially extending, integral projection 23 having radially intermediate axially extending surface 188 and radially outward axially extending surface 190 in its most preferred form. Surface 190 has a 30 dlameter generally equal to recess 186 and for receipt therein. End 154 is removably secured to cylindrical body portion 152 in its most preferred form by bolts 200 extendlng through circumferentially spaced, axially extending apertures 202 formed in end 154 and 35 threadably received in mounting shoulders 178 of cyl1ndr~cal body portlon 152. IA the most preferred ~ 132732~
1 form, apertures 202 include counter sunk entries for . receipt of the heads of bolts 200. suitable fluid sealing provisions 192 such as an 0-rlng is provided in the preferred embodiment between surface 190 of 5 projection 23 of end 154 and cylindrical body portion 152.
In the preferred form of Figures 1 and 2, annular flange portion 50 of piston 48 has formed on the outer surface thereof adjacent to its first end the annular 10 groove 58 in which is positioned the O-ring 60 which ~; makes sliding and sealing contact with surface 188 of projection 23. An annular portion 52 extends radially outwardly from annular flange potion 50. The second, free end of annular portion 52 of piston 48 has formed , 15 therein the groove 62 in which is positioned the 0-ring 64 which makes sliding and sealing contact with the radially inward surface of annular member 158 of i housing 150.
In the preferred form of Figures 3 and 4, annular 20 piston 48 is generally Z-shaped and includes a second, axially disposed annular flange portion 51 and annular portion 52 extending radially between the ends of portions 50 and 51. The radlally outer surface of g~: portion 51 is complementary to and for sliding receipt ~:~ 25 within cylindrical body portion 152 and includes sultable sealing provlsions therebetween such as 0-ring 64 received within groove 62 formed in the radially outer . surface of portion 51. The radially inner surface of ` portion 51 is complementary to and for sliding receipt on 30 surface 188 of pro~ection 23 and includes suitable sealin~ p~ovisions therebetween such as 0-ring 60 .~ received within groove 58 formed in surface 188 of ~ pro~ectio~ 23.
The radially outer surface of portion 50 is ; 35 compleme~tary to and for sliding receipt within radially inward, axially extending surface 198 of body portion 72 and incl~des suitable sealing provisions tharebetween :
132732~
i g 1 such as 0-ring 196 received within groove 194 formed in surface 198 of body portion 72.
It will be seen that piston ~8, bearing 46, hub 34 and friction disc 28 thereof are all slidable on shaft 5 10. It will be further seen that the void defined by piston 48, cylindrical body portion 152, and end 154 forms a cylinder C to which there is communication by air port 24. It will be further seen that the void defined by piston 48, cylindrical body portion 152, and body 10 portion 72 forms a cylinder C' to which there is communication by air port 182. For rotatably relating piston 48 to housing 150, an antirotation pin 20~ shown in its preferred form as a spring pin is secured through the first end of annular flange portion 50 and is 15 slidably received in an aperture 206 formed in end 154 in the preferred form of Figures 1 and 2 and is secured in end 154 and is slidably received in an aperture 206 formed in the free end of annular flange portion 51 of : piston 48 in the preferred form of Figures 3 and 4. It :20 can then be appreciated that the particular arrangement of pin 204 and its interrelationship to piston 48 and housing end 154 are advantageous in regard to formation of the apertures for receiving pin 204 wlthout wall break through.
~: 2s In the preferred form of Flgures 1 and 2, clutch-brake A includes first and second, L-shaped bushlngs 208 which are oppositely directed with the free ends of the flrst legs being contiguous and with the first legs of the first and second L-shaped bushings 30 belng received on output shaft 10. Bushings 208 ~re prevented from axially movin~ on shaft 10 by a shoulder 21~ formed on shaft 10 and by a retaining ring 212 secured o~ shaft 10. In the most preferred form, bushings 20a are formed of Ollite Bronze. The second 35 legs o~ bushings 2Q8 capture an annular shoulder 19 formed in circular opening 18 of end 154 for axially ' ~` 132732~
1 securing bushings 208 in end 154.
In the preferred form of Figures 3 and 4, mounted on shaft 10 are the inner races 12 of bearings 14 and 14a with the outer races 16 mounted in the circular opening 5 18 of housing end 154. In the preferred form of Figures 3 and 4, opening 18 is formed by projection 23 which is of a two step form. Races 12 and 16 of bearings 14 and 14a are retained by a shoulder 210 formed on shaft lo, by retaining rings 211 secured in opening 18 of housing end 10 154, and by retaining ring 212 secured on shaft 10.
In the preferred form of Figures 1 and 2, member 158 includes a first cylindrical portion 162 having the first, free annular end 164 and having a second end integrally attached to a first end of a second 15 cylindrical portion 166 having the second, free annular end 168. The radlally inward diameter of cyllndrical j portion 162 is generally equal to the radially outward f, ' diameter of cylindrical portion 166. Annular recess 184 is provided in the radially lnward diameter of 20 cylindrical portion 162 ad~acent end 164 for allowing ease of assembly. Body portion 152 further includes in ;~ the preferred form of Figures 1 and 2, integral, axially -~ extending, circumferentially spaced, heat dissipating fins 174 extendlng from cylindrical portion 162 from 25 flange 170 to a point slightly axially spaced inwardly of end 16~.
The inner race 96 of bearing 94 is mounted in recess 98 formed on hub 100 of frlction disc 102 having frlction face 104. Hub 100 is keyed to the live input shaft of a .30 motor or other source of power by means of keyway 110.
Thus, as the power source shaft rotates so does disc 102.
In the preferred embodiment of Figures 1 and 2, housing end 156 is generally planar and circular in configuration having a diamet2r larger than cyllndrical 35 body portlon 152. End 156 lncludes integral, axially extending shoulder 214 having a diameter generally equal , 13273~1 1 to recess 184 and for receipt therein. End 156 is removably secured to housing body 150 in its most preferred form by studs 216 extending through apertures 172 and threadably received in end 156. A jam nut 218 . 5 may be provided threadably received on stud 216 and abutting with end 156. Further, a lock washer and nut 220 may be provided threadably received on stud 216 and abutting with flange 170.
: In the preferred embodiment of Figures 3 and 4, 10 axially extending fingers 80 of housing end 82 shown in its preferred form as stationary input housing define openings 84 for air cooling and the fingers 80 terminate at their outer e~ge in the ring like and radially disposed outer end wall 86. The lnner diameter of 15 fingers 80 is greater than the outer diameter of axially extending annular member 158. The inner edge of fingers 80 includes an annular recess 184 provided in the inner diameter of fingers 80 of a size and shape complementary to and for slidable receipt on an axially extending 20 shoulder 185 integrally formed on mounting flange 170 of ~:~: free end 164 of cylindrical body portion 152. Stationary input housing 82 is removably secured to body portion 152 in its most preferred form by bolts 216 extending through apertures 172 and threadably received in the inner edge 25 of fingers 80. Disc 102 of Figures 3 and 4 is equipped with the spaced cooling fins 106.
Extending inwardly and axially of end 82 or 156 ls the ~; annular flange 88 which has formed on the lnner surface : thereof the annular recess 90 ln whlch ls mounted the 30 outer race 92 of bearlng 94. It can then be appreciated that friction discs 28 and 102 are not directly interconnected together, but are only interconnected together ~hrough thelr separate lnterconnection to housing 15C according to the teachings of the present 35 invention. Therefor, no vlbratlon ls transferred between the power source shaft received in hub 100 of frlction 132732l~
1 disc 102 and output shaft 10 due to off center mounting of clutch-brake A. Vibration may cause noise and premature component wear. Thus, rubber coating of splines 36 and/or 38 or other techniques to compensate 5 for vibration are not necessary, reducing the cost of manufacture of clutch-brake A according to the teachings of the present invention.
Housing end 82 or 156 lncludes provisions for mounting housing 150 and clutch-brake A to the motor or 10 other source of power such as by a female C-face 222 and by cap screws received in circumferentially spaced, axially extending apertures 224. End 154 includes provisions for mounting housing 150 and clutch-brake A to the output apparatus such as a gear reducer such as by a 15 male C-face 226 and by circumferentially spaced, axially extending, apertures 123 for receipt of bolts extending from the gear reducer. Shaft 10 may also be keyed to a sheave, a sprocket, a coupling or the like for actuation thereof. -It will be seen that with no air pressure in cylinderC and upon introducing fluid pressure into cylinder C~ by a source (not shown) connected to port 182, piston 48 moves towards end 154 whereby disc 28 is made to contact lining 79 and through hub 34 brake shaft 10. With no air 25 pressure in cylinder C' a~d upon introducing fluld pressure into cylinder C by a source ~not shown) connected to inlet 24, piston 48 moves away from end 154 whereby disc 28 ls separated from lining 79 and as a result there ls no braking of shaft 10, and friction 30 llning 32 contacts face 104 of live friction disc 102 whereby shaft 10 ls clutched ln.
Now that the basic csnstruction and operation of preferred ~mbodiments according to the teachings of the present lnvention have been set forth, subtle features 35 and advantages of the present invention can be set forth and appreciated. A first difference between clutch-brake 132~32 `:
1 A disclosed herein and clutch-brake A disclosed in U.S.
Patent 4,534,454 is that no springs are utilized in the present construction in moving piston 48 whereas springs are utilized for moving the piston in the construction 5 described in U.S. Patent 4,534,454. Separate fluid ~ cylinders C and C~ as in the present invention allow more ;~ torque capacity in the engagement of the clutch or brake in clutch-brake A. Further, faster actuation of the ; clutch in clutch-brake A of the present invention is ' 10 possible because it is not necessary to compress springs as in U.S. Patent 4,534,454. However, it should also be appreciated that clutch-brake A of the present invention obtains many of the advantages gained by clutch-brake A
of U.S. Patent 4,534, 454 including prevention of :i 15 simultaneous clutching and braking of output shaft 10.
A further ma;or difference between clutch-brake A of ~, the present invention and U.S. Patent 4,534,454 is the !~ houslng construction. It should then be noted that housing 150 according to the teachings of the present ; 20 invention is of a modular, interchangeable component type. Specifically, housing ends of different types and constructlons may be utilized and interchanged with a ~` common body portion 152. For example, as shown in Figure 2, housing ends 154M and 156M may be utilized with a body , ~ 25 portion 152 for interconnection between a power source 3 and output apparatus utilizing metric standard interconnections. Similarly, housing ends 154N and 156N
may be utilized wlth the same body portion 152 for interconnection between a power source and output 30 apparatus utilizing NEMA ~inch) standard ~';; lnterconnections. It can then further be appreciated that it ls even possible to mismatch housing ends 154 and 1 156 between metric and NEMA standards.
'~ Furthermore, it should be appreciated that since body 35 portion 152 is identical for either metric or NEMA type interconnections, it is then only necessary to :
.
1 manufacture and keep on inventory a single type of body portion 152 rather than separate housing constructions for each type of industry interconnections such as metric or NEMA standards.
Similarly, according to the teachings of the present invention, the remaining components are of identical constructions such as piston 48, friction disc 28, bearings 46 and 94, friction linings 79 and 32 and the like or may be machined from a common casting to either a 10 metric, NEMA, or other industry standard such as shaft lo and hub 100, and housing ends. Therefore, machining from a common casting greatly reduces the number of casting molds and the capital expenditures required to manufacture clutch-brake A for interconnection with other 15 components of varying industrial standards according to the teachings of the present invention. Further, it is then only necessary to manufacture and keep in inventory a significantly reduced number of components while having clutch-brakes A which fit both metric and NEMA industry 20 standards.
It should be further noted that the preferred construction of cylindrical body portion 152 according to the teachings of the present invention is further advantageous. First, body portion 152 is adaptable for 25 easy casting. Further, the provision of fins 176 allows for the dissipation of heat from clutch-brake A according to the teachings of the present invention without requiring cores during casting. Furthermore, fins 176 structurally reinforce mounting flange 170 and annular 30 member 160.
Further, in the preferred embodiment of Flgures 1 and 2, mounting flange 17~ lies between the mold interface and divide~ the draft angles of cylindrical body port1on 152. Further, the provlsio~ of fins 174 allows for the 35 dissipation of heat from clutch-brake A accordlng to the teachings of the present invention without re~uiring 132732~
cooling air apertures requiring window cores during casting. Furthermore, fins 174 structurally reinforce mounting flange 170.
Similarly, stationary input housing 82 of Figures 3 5 and 4 according to the teachings of the present invention is further advantageous. First, stationary input housing 82 is adaptable for easy casting. Specifically, openings 84 of stationary input housing 82 are formed by fingers 80 and thus do not require window cores during casting.
. 10 Further, the interface interaction locations which are the major source of heat generation are positioned axially within stationary input housing 82 to allow rapid ` heat dissipation as the result of the axial openings in interface element 25 and friction disc 103, cutouts 23a, 15 openings 84 and fins 106.
Additionally, housing 150 and clutch-brake A
according to the teachings of the present invention are particularly advantageous when it is necessary to disassemble clutch-brake A for installation and 20 maintenance, such as when the C-face is larger than the bore circle of apertures 224. Specifically, clutch-brake A according to the teachings of the present invention can be se~arated into two major components, a first component including housing end 82 or 156 and friction disc 102 and 25 a second component including body portion 152, housing end 154, friction disc 28, and piston 48 held together by the interconnection of body portio~ 152 and housing end 154 by bolts 200. Housing end 82 or 156 may then be interconnected to the power source by bolts extending 30 through apertures 224 and body portlon 152 may be interconnected to housing end 82 or 156 by bolts 216, with housing end 154 belng lnterconnected to the output appar~tus utllizlng bolts receiYed in apertures 123 either before or after the interconnection of body 35 portion 152 to housing end 82 or 156.
Furthermore, due to the preferred construction of ' 132732il `~:
s -16-1 housing end 82 and body portion 152 of Figures 3 and 4 according to the teachings of the present invention, easy ::~ access is allowed to friction lining ring 79 due to the x offset nature of mounting flange 170 from body portion 72 to allow radial removal from between backing portion 68 ~ and friction interface member 25 without dismantling .~ friction interface member 25 from the second component including body portion 152, housing end 154, and piston 48. Thus, clutch-brake A according to the teachings of 10 the present invention is advantageous in the ease of maintenance and specifically the replacement of friction lining rings ~2 and 79 and particularly does not require reaching radially inward of a closed housing for lining ~` replacement.
It should be additionally noted that the preferred I construction of friction disc 28 of Figures 3 and 4 according to the teachings of the present invention is further advantageous. Specifically, friction disc 28 is adaptable for easy casting without requiring casting 20 cores. Specifically, one piece friction disc 28 of the type of U.S. Patent 4,534,454 required spaced cutouts 23a ~, be formed by using cores located between the cavities ~; which formed the flat ring portions of the friction disc 28, greatly increaslng the cost of the molds as well as 25 the casting. The two pie~e construction of friction disc 28 and specifically the construction of friction ~,~ interface element 25 eliminates the requirement for casting cores for disc heat ventilation as webs 27 which ' space ring portion ~3b and 25a to allow for heat 30 ventilation are formed on and upstand from the rear face of flat ring portion 25a. Flat ring portion 23b need not be cast and may be slmply cut or stamped from sheet r~ material, greatly reducing the cost of manufacture.
k Furthermore, during maintenance of clutch-brake A and 35 specifically the replacement of friction lining rings 32 ahd 79, it should be noted that friction disc 28 of r h~ ~
~ ' t ' 132732~
; l F~ gures 3 and 4 according to the teachings of the present invention is also of an advantageous construction.
Specifically, flange 170 is located axially inward of end 164 and of friction lining 79 secured to annular body 5 portion 72. Thus, after housing end 82 is removed by removing bolts 216, bolts 29 may be removed which secure friction lining ring 32 and flat ring portion 23b to friction interface element 25. After removal of ring 32 and portion 23b, easy access is allowed to bolts 81 10 through openings 95 to allow removal of friction lining ring 79 and in particular it is not necessary to reach through ring portions 23b and 25a and cutouts 23a.
Further, the use of bushings 208 in housing end 154 in Figures 1 and 2 according to the teachings of the 15 present invention is particularly advantageous over utilization of ball bearings. Specifically, bushings 208 are clearly less expensive than ball bearings. Further, the fabrication of end 1~4 and its assembly with bushings 208 and output shaft lO according to the teachings of the 20 present invention is easier and less expensive.
Furthermore, the axial length required for bushings 208 is considerably shorter than for ball bearings allowing clutch-brake A according to the teachings of the present invention to be axially shorter and friction disc 28 to 25 be axially closer to the output apparatus than when roller bearings are utilized. Thus, although roller bearings are more capable of recelving overhang and radial loa~s, the construction of clutch-brake A
according to the teachings of the present invention and 30 the direct lnterconnection of housing end 154 to the output apparatus allows use of bushlngs 208 whlch reduces the overall cost of clutch-brake 10.
Now that the basic teachings of the present invention have been explained, maQy extensions and variations will 35 be obvious to one having ordinary skill in the art. For example, although housing 150 in th~ preferred form of s 132732~
~ -18~
,'~ 1 the present ~nvention in Figures 1 and 2 does not include cooling air apertures and is believed to be advantageous, such cooling air apertures or other cooling provisions may be provided in addition to and/or instead of fins 174 and 176 such as provided in Figures 3 and 4.
Further, although securement of housing ends 82 or 156 and housing end 154 to body portion 152 is shown in the preferred embodiment including bolts 200 and bolts 216 and associated structure, other forms of 10 securement may be apparent to one skilled in the art after the teachings of the present invention are known.
., Although shown as formed of one piece, friction lining ring 32 may be formed in a manner as friction 15 lining ring 79 of Figures 3 and 4 to allow interchangability and component inventory and iS manufacture reduction.
i~ Although air pressure on both sides of piston 48 is utilized to activate clutch-brake A in the preferred 20 form, other forms and types of activation may be utilized in ac~ordance with the present invention.
:, i 25 ;
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.;
1:
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The present invention solves these and other '~ deficiencies and problems in rotational control apparatus by providing easily and inexpensively cast or otherwise formed components which can be easily assembled into a 10 unit which in turn can be easily installed and l maintained. In particular, an improved housing is provided including first and second housing ends secured ; to a cylindrical body portion. The cylindrical body portion includes an integral interface member extending 15 radially inwardly and an integral mounting flange extending radially outwardly of an axially extending annular member. The first housing end is removably I secured to the cylindrical body portion and the second !~ housing end is removably secured to the integral mounting '! 20 flange allowing the apparatus to be readily disassembled into first and second major components which are particularly advantageous for installation and maintenance.
Further, in another aspect, the interface disc 25 having first ~nd second lnterface surfaces is formed of a first, flat ring portion and a cast interface element including a second, integral flat ring portlon. The first, flat ring portlon is held in a spaced condition for heat ventilation by upstanding , 30 webs cast on the second ring portion eliminating casting cores. Further, the removability of the first ring portion allows better access to the friction lining rin~ securement to allow removal thereof without requiring dismantling of the cast interface 35 element from the remaining components.
It is thus an aim of the present invention to provide a novel apparatus for controlling rotation of an ' :
; .
~', 132732`il . -3-output.
It is further an aim of the present invention to ;~ provide such a novel rotational control apparatus having r~` an improved housing.
It is further an aim of the present invention to provide such a novel rotational control apparatus having an improved interface disc having first and second interface surfaces.
It is further an aim of the present invention to 10 provide such a novel rotational control apparatus which can be separated into two major components for installation and maintenance.
It is further an aim of the present invention to provide such a novel rotational control apparatus having 15 more torque capacity.
It is further an aim of the present invention to provide such a novel rotational control apparatus having faster actuation.
It is further an aim of the present invention to 20 provide such a novel rotational control apparatus utilizing modular, interchangeable components.
t is further an aim of the present invention to provide such a novel rotational control apparatus ~; utilizing common castings for varying industrial 25 interconnections.
It is further an aim of the present invention to provide such a novel rotational control apparatus utilizing components which may be easily and ` inexpensively cast.
These and further aims and advantages of the present invention will become clearer in light of the following detailed description of illustrative embodlments of this invention described in connection with tAe drawing~.
35 DESCRIPTI~N OF THE DRAWINGS
The illustrative embodiments may best be described by :'~
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~ 1 reference to the accompanying drawings where:
,~ Figure 1 shows a cross sectional view of a clutch-brake ac~ording to the preferred teachings of the ~f present invention.
Figure 2 shows an exploded, perspective view of the , improved housing of the clutch-brake of Figure 1 illustrating the modular interchangeability thereof.
, Figure 3 shows a cross sectional view of an alternate embodiment of a clutch-brake according to the preferred ~; 10 teachings of the present invention.
Figure 4 shows an exploded, perspective view of the `~ clutch-brake of Figure 3.
All figures are drawn for ease of explanation of the basic teachings of the present invention only; the 15 extensions of the Figures with respect to number, ;~ position, relationship, and dimensions of the parts to form the preferred embodiment will be explained or will t be within the skill of the art after the following ' teachings of the present invention have been read and 20 understood. Further, the exact dimensions and dimensional proportions to conform to specific force, weight, strength, and similar requirements will likewise be within the ~kill of the art after the following teachings of the present invention have been read and `~ 25 understood.
Where used in the various figures of the drawings, the same numerals designate the same or similar parts.
Furthermore, when the terms "top", "bottom", "inward", "outward", "first", "second", "inside", "outside", 30 "radially", "axlally", "circumferentially", and similar terms are used herein, it should be understood that these terms have reference only to the structure shown ln the drawings ~s it would appear to a person viewing the drawings and are utilized only to facilitate describing 35 the invention.
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132732 ~
Apparatus for providing rotational control of an output with an input and a housing according to the ~i teachings of the present invention is shown in the i~Z drawings and is generally designated A. In the most 5 preferred embodiments of the present invention, apparatus , A is a clutch-brake and is an improvement of the type 'f shown and described in U.S. Patent No. 4,534,454. For purpose of explanation of the basic teachings of the 10 present invention, the same numerals designate the same , or similar parts in the present figures and the figures ' of U.S. Patent No. 4,534,454. The description of the t common numerals and the clutch-brake A may be found Z herein and in U.S. Patent No. 4,534,454.
Referring to the drawings in detail, the clutch-brake A includes the driven rotatable output shaft 10. Further provided is the interface dlsc shown in its preferred form as friction disc 28. In the preferred embodiment ' of Figures 1 and 2, mounted by means of bolts 29 on the ! 20 flrst face 30 of friction disc 28 is the first interface surface shown as friction lining ring 32. In the preferred embodiment of Figures 3 and 4, frictlon disc ~ 28 includes a flat ring portion 23b and a friction l~ interface element 25. Friction lnterface element 25 1~
~ 25 includes a flat ring portion 25a havlng Z circumferentlally spaced, radlally extending webs 27 ~ upstanding from the face opposite to the lnterface Z surface thereof. ~xlally extending openings 9S of the type shown and descrlbed in U.S. Patent No. 4,078,637 30 are formed in the flat ring portlon 25a lntermedlate ~; webs 27. Webs 27 include axially extendlng shoulders 27a for receipt of the radially inward axially extending opening of flat ring portlon 23b. Bolts 29 threadably received in webs 27 extend through and secure friction 35 llning rlng 32 and the flat rlng portion 23b to frlction interface element 25 with the face opposite ~ ,~
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1 to the interface surface of ring portion 23b abutting ~ with the free ends of webs 27 and spaced from the face of : ring portion 25a to form spaced cutouts 23a for heat - venting.
Disc 28 terminates radially inwardly in the hollow hub 34 formed with splines 36 slidably engaged with splines 38 of shaft 10. Formed on the hub 34 is the annular recess 40 forming the shoulder 42. Mounted in ; the recess 40 and against the shoulder 42 is the inner 10 race 44 of bearing 46.
The numeral 48 designates an annular piston which i includes the axially disposed annular flange portion 50.
The outer race 54 of bearing 46 is mounted on the inner : surface of piston flange portion 50 and against the 15 shoulder 56 thereby rotatably mounting shaft 10 and a portion of hub 34 within piston 48.
~: Clutch-brake A according to the teachings of the present invention includes a housing 150 of an ~; improved construction including modular, : 20 interchangeable components 82 or 156, 152, and 154.
Specifically, housing 150 includes a cylindrical body portion 152 having a first, generally axially :~ extending annular member 158 which intersects with a second, generally radially extending annular member 25 160. Member 158 includes a first, free annular end 164 and a second, free annular end 168. In the most preferred form, annular recess 186 is provided in the ~:~ radially inward diameter of annular member 158 and ad~acent end 168 for allowlng ease of assembly.
Member 160 lncludes an integral, annular body portion 72 located radially inwardly of annular member 15~ and extending toward its s~cond end 168. Annular body portion 72 includes a backing portion 68 for mounting thereon the ~econd, fixed interface member ; 35 shown as friction lining ring 79 opposite frictlon disc ;~:
:~:
132732~
,, ~, 1 28. Friction lining ring 79 in the preferred form shown ~, in Figures 3 and 4 is formed of two, half-moon pieces to allow radial removal without removing friction interface 5'` element 25. Lining 79 is secured by bolts 81 to backing 5 portion 68.
Member 160 further includes an annular, radially .~ extending mounting flange 170 having circumferentially :~ spaced, axially extending apertures 172. Flange 170 is generally located such that body portion 72 is ,~ 10 slightly offset from flange 170.
. Body portion 152 further includes in its most preferred form, integral, axially extending, circumferentially spaced fins 176 extending from annular ; member 158 from flange 170 to a point slightly axially 15 spaced inwardly of end 168. Axially extending, circumferentlally spaced mounting shoulders 178 are further provided in the preferred embodiment extending from annular member 158 from flange 170 to end 168 and circumferentially spaced from fins 176. One of the 20 shoulders 178 in the preferred embodiment includes a port enlargement 180 including axially spaced, radially extending air ports 24 and 182.
Housing end 154 is generally planar and circular in configuration having a diameter larger than annular 25 member 158 of cylindrical body portion 152. End 154 includes axially extending, integral projection 23 having radially intermediate axially extending surface 188 and radially outward axially extending surface 190 in its most preferred form. Surface 190 has a 30 dlameter generally equal to recess 186 and for receipt therein. End 154 is removably secured to cylindrical body portion 152 in its most preferred form by bolts 200 extendlng through circumferentially spaced, axially extending apertures 202 formed in end 154 and 35 threadably received in mounting shoulders 178 of cyl1ndr~cal body portlon 152. IA the most preferred ~ 132732~
1 form, apertures 202 include counter sunk entries for . receipt of the heads of bolts 200. suitable fluid sealing provisions 192 such as an 0-rlng is provided in the preferred embodiment between surface 190 of 5 projection 23 of end 154 and cylindrical body portion 152.
In the preferred form of Figures 1 and 2, annular flange portion 50 of piston 48 has formed on the outer surface thereof adjacent to its first end the annular 10 groove 58 in which is positioned the O-ring 60 which ~; makes sliding and sealing contact with surface 188 of projection 23. An annular portion 52 extends radially outwardly from annular flange potion 50. The second, free end of annular portion 52 of piston 48 has formed , 15 therein the groove 62 in which is positioned the 0-ring 64 which makes sliding and sealing contact with the radially inward surface of annular member 158 of i housing 150.
In the preferred form of Figures 3 and 4, annular 20 piston 48 is generally Z-shaped and includes a second, axially disposed annular flange portion 51 and annular portion 52 extending radially between the ends of portions 50 and 51. The radlally outer surface of g~: portion 51 is complementary to and for sliding receipt ~:~ 25 within cylindrical body portion 152 and includes sultable sealing provlsions therebetween such as 0-ring 64 received within groove 62 formed in the radially outer . surface of portion 51. The radially inner surface of ` portion 51 is complementary to and for sliding receipt on 30 surface 188 of pro~ection 23 and includes suitable sealin~ p~ovisions therebetween such as 0-ring 60 .~ received within groove 58 formed in surface 188 of ~ pro~ectio~ 23.
The radially outer surface of portion 50 is ; 35 compleme~tary to and for sliding receipt within radially inward, axially extending surface 198 of body portion 72 and incl~des suitable sealing provisions tharebetween :
132732~
i g 1 such as 0-ring 196 received within groove 194 formed in surface 198 of body portion 72.
It will be seen that piston ~8, bearing 46, hub 34 and friction disc 28 thereof are all slidable on shaft 5 10. It will be further seen that the void defined by piston 48, cylindrical body portion 152, and end 154 forms a cylinder C to which there is communication by air port 24. It will be further seen that the void defined by piston 48, cylindrical body portion 152, and body 10 portion 72 forms a cylinder C' to which there is communication by air port 182. For rotatably relating piston 48 to housing 150, an antirotation pin 20~ shown in its preferred form as a spring pin is secured through the first end of annular flange portion 50 and is 15 slidably received in an aperture 206 formed in end 154 in the preferred form of Figures 1 and 2 and is secured in end 154 and is slidably received in an aperture 206 formed in the free end of annular flange portion 51 of : piston 48 in the preferred form of Figures 3 and 4. It :20 can then be appreciated that the particular arrangement of pin 204 and its interrelationship to piston 48 and housing end 154 are advantageous in regard to formation of the apertures for receiving pin 204 wlthout wall break through.
~: 2s In the preferred form of Flgures 1 and 2, clutch-brake A includes first and second, L-shaped bushlngs 208 which are oppositely directed with the free ends of the flrst legs being contiguous and with the first legs of the first and second L-shaped bushings 30 belng received on output shaft 10. Bushings 208 ~re prevented from axially movin~ on shaft 10 by a shoulder 21~ formed on shaft 10 and by a retaining ring 212 secured o~ shaft 10. In the most preferred form, bushings 20a are formed of Ollite Bronze. The second 35 legs o~ bushings 2Q8 capture an annular shoulder 19 formed in circular opening 18 of end 154 for axially ' ~` 132732~
1 securing bushings 208 in end 154.
In the preferred form of Figures 3 and 4, mounted on shaft 10 are the inner races 12 of bearings 14 and 14a with the outer races 16 mounted in the circular opening 5 18 of housing end 154. In the preferred form of Figures 3 and 4, opening 18 is formed by projection 23 which is of a two step form. Races 12 and 16 of bearings 14 and 14a are retained by a shoulder 210 formed on shaft lo, by retaining rings 211 secured in opening 18 of housing end 10 154, and by retaining ring 212 secured on shaft 10.
In the preferred form of Figures 1 and 2, member 158 includes a first cylindrical portion 162 having the first, free annular end 164 and having a second end integrally attached to a first end of a second 15 cylindrical portion 166 having the second, free annular end 168. The radlally inward diameter of cyllndrical j portion 162 is generally equal to the radially outward f, ' diameter of cylindrical portion 166. Annular recess 184 is provided in the radially lnward diameter of 20 cylindrical portion 162 ad~acent end 164 for allowing ease of assembly. Body portion 152 further includes in ;~ the preferred form of Figures 1 and 2, integral, axially -~ extending, circumferentially spaced, heat dissipating fins 174 extendlng from cylindrical portion 162 from 25 flange 170 to a point slightly axially spaced inwardly of end 16~.
The inner race 96 of bearing 94 is mounted in recess 98 formed on hub 100 of frlction disc 102 having frlction face 104. Hub 100 is keyed to the live input shaft of a .30 motor or other source of power by means of keyway 110.
Thus, as the power source shaft rotates so does disc 102.
In the preferred embodiment of Figures 1 and 2, housing end 156 is generally planar and circular in configuration having a diamet2r larger than cyllndrical 35 body portlon 152. End 156 lncludes integral, axially extending shoulder 214 having a diameter generally equal , 13273~1 1 to recess 184 and for receipt therein. End 156 is removably secured to housing body 150 in its most preferred form by studs 216 extending through apertures 172 and threadably received in end 156. A jam nut 218 . 5 may be provided threadably received on stud 216 and abutting with end 156. Further, a lock washer and nut 220 may be provided threadably received on stud 216 and abutting with flange 170.
: In the preferred embodiment of Figures 3 and 4, 10 axially extending fingers 80 of housing end 82 shown in its preferred form as stationary input housing define openings 84 for air cooling and the fingers 80 terminate at their outer e~ge in the ring like and radially disposed outer end wall 86. The lnner diameter of 15 fingers 80 is greater than the outer diameter of axially extending annular member 158. The inner edge of fingers 80 includes an annular recess 184 provided in the inner diameter of fingers 80 of a size and shape complementary to and for slidable receipt on an axially extending 20 shoulder 185 integrally formed on mounting flange 170 of ~:~: free end 164 of cylindrical body portion 152. Stationary input housing 82 is removably secured to body portion 152 in its most preferred form by bolts 216 extending through apertures 172 and threadably received in the inner edge 25 of fingers 80. Disc 102 of Figures 3 and 4 is equipped with the spaced cooling fins 106.
Extending inwardly and axially of end 82 or 156 ls the ~; annular flange 88 which has formed on the lnner surface : thereof the annular recess 90 ln whlch ls mounted the 30 outer race 92 of bearlng 94. It can then be appreciated that friction discs 28 and 102 are not directly interconnected together, but are only interconnected together ~hrough thelr separate lnterconnection to housing 15C according to the teachings of the present 35 invention. Therefor, no vlbratlon ls transferred between the power source shaft received in hub 100 of frlction 132732l~
1 disc 102 and output shaft 10 due to off center mounting of clutch-brake A. Vibration may cause noise and premature component wear. Thus, rubber coating of splines 36 and/or 38 or other techniques to compensate 5 for vibration are not necessary, reducing the cost of manufacture of clutch-brake A according to the teachings of the present invention.
Housing end 82 or 156 lncludes provisions for mounting housing 150 and clutch-brake A to the motor or 10 other source of power such as by a female C-face 222 and by cap screws received in circumferentially spaced, axially extending apertures 224. End 154 includes provisions for mounting housing 150 and clutch-brake A to the output apparatus such as a gear reducer such as by a 15 male C-face 226 and by circumferentially spaced, axially extending, apertures 123 for receipt of bolts extending from the gear reducer. Shaft 10 may also be keyed to a sheave, a sprocket, a coupling or the like for actuation thereof. -It will be seen that with no air pressure in cylinderC and upon introducing fluid pressure into cylinder C~ by a source (not shown) connected to port 182, piston 48 moves towards end 154 whereby disc 28 is made to contact lining 79 and through hub 34 brake shaft 10. With no air 25 pressure in cylinder C' a~d upon introducing fluld pressure into cylinder C by a source ~not shown) connected to inlet 24, piston 48 moves away from end 154 whereby disc 28 ls separated from lining 79 and as a result there ls no braking of shaft 10, and friction 30 llning 32 contacts face 104 of live friction disc 102 whereby shaft 10 ls clutched ln.
Now that the basic csnstruction and operation of preferred ~mbodiments according to the teachings of the present lnvention have been set forth, subtle features 35 and advantages of the present invention can be set forth and appreciated. A first difference between clutch-brake 132~32 `:
1 A disclosed herein and clutch-brake A disclosed in U.S.
Patent 4,534,454 is that no springs are utilized in the present construction in moving piston 48 whereas springs are utilized for moving the piston in the construction 5 described in U.S. Patent 4,534,454. Separate fluid ~ cylinders C and C~ as in the present invention allow more ;~ torque capacity in the engagement of the clutch or brake in clutch-brake A. Further, faster actuation of the ; clutch in clutch-brake A of the present invention is ' 10 possible because it is not necessary to compress springs as in U.S. Patent 4,534,454. However, it should also be appreciated that clutch-brake A of the present invention obtains many of the advantages gained by clutch-brake A
of U.S. Patent 4,534, 454 including prevention of :i 15 simultaneous clutching and braking of output shaft 10.
A further ma;or difference between clutch-brake A of ~, the present invention and U.S. Patent 4,534,454 is the !~ houslng construction. It should then be noted that housing 150 according to the teachings of the present ; 20 invention is of a modular, interchangeable component type. Specifically, housing ends of different types and constructlons may be utilized and interchanged with a ~` common body portion 152. For example, as shown in Figure 2, housing ends 154M and 156M may be utilized with a body , ~ 25 portion 152 for interconnection between a power source 3 and output apparatus utilizing metric standard interconnections. Similarly, housing ends 154N and 156N
may be utilized wlth the same body portion 152 for interconnection between a power source and output 30 apparatus utilizing NEMA ~inch) standard ~';; lnterconnections. It can then further be appreciated that it ls even possible to mismatch housing ends 154 and 1 156 between metric and NEMA standards.
'~ Furthermore, it should be appreciated that since body 35 portion 152 is identical for either metric or NEMA type interconnections, it is then only necessary to :
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1 manufacture and keep on inventory a single type of body portion 152 rather than separate housing constructions for each type of industry interconnections such as metric or NEMA standards.
Similarly, according to the teachings of the present invention, the remaining components are of identical constructions such as piston 48, friction disc 28, bearings 46 and 94, friction linings 79 and 32 and the like or may be machined from a common casting to either a 10 metric, NEMA, or other industry standard such as shaft lo and hub 100, and housing ends. Therefore, machining from a common casting greatly reduces the number of casting molds and the capital expenditures required to manufacture clutch-brake A for interconnection with other 15 components of varying industrial standards according to the teachings of the present invention. Further, it is then only necessary to manufacture and keep in inventory a significantly reduced number of components while having clutch-brakes A which fit both metric and NEMA industry 20 standards.
It should be further noted that the preferred construction of cylindrical body portion 152 according to the teachings of the present invention is further advantageous. First, body portion 152 is adaptable for 25 easy casting. Further, the provision of fins 176 allows for the dissipation of heat from clutch-brake A according to the teachings of the present invention without requiring cores during casting. Furthermore, fins 176 structurally reinforce mounting flange 170 and annular 30 member 160.
Further, in the preferred embodiment of Flgures 1 and 2, mounting flange 17~ lies between the mold interface and divide~ the draft angles of cylindrical body port1on 152. Further, the provlsio~ of fins 174 allows for the 35 dissipation of heat from clutch-brake A accordlng to the teachings of the present invention without re~uiring 132732~
cooling air apertures requiring window cores during casting. Furthermore, fins 174 structurally reinforce mounting flange 170.
Similarly, stationary input housing 82 of Figures 3 5 and 4 according to the teachings of the present invention is further advantageous. First, stationary input housing 82 is adaptable for easy casting. Specifically, openings 84 of stationary input housing 82 are formed by fingers 80 and thus do not require window cores during casting.
. 10 Further, the interface interaction locations which are the major source of heat generation are positioned axially within stationary input housing 82 to allow rapid ` heat dissipation as the result of the axial openings in interface element 25 and friction disc 103, cutouts 23a, 15 openings 84 and fins 106.
Additionally, housing 150 and clutch-brake A
according to the teachings of the present invention are particularly advantageous when it is necessary to disassemble clutch-brake A for installation and 20 maintenance, such as when the C-face is larger than the bore circle of apertures 224. Specifically, clutch-brake A according to the teachings of the present invention can be se~arated into two major components, a first component including housing end 82 or 156 and friction disc 102 and 25 a second component including body portion 152, housing end 154, friction disc 28, and piston 48 held together by the interconnection of body portio~ 152 and housing end 154 by bolts 200. Housing end 82 or 156 may then be interconnected to the power source by bolts extending 30 through apertures 224 and body portlon 152 may be interconnected to housing end 82 or 156 by bolts 216, with housing end 154 belng lnterconnected to the output appar~tus utllizlng bolts receiYed in apertures 123 either before or after the interconnection of body 35 portion 152 to housing end 82 or 156.
Furthermore, due to the preferred construction of ' 132732il `~:
s -16-1 housing end 82 and body portion 152 of Figures 3 and 4 according to the teachings of the present invention, easy ::~ access is allowed to friction lining ring 79 due to the x offset nature of mounting flange 170 from body portion 72 to allow radial removal from between backing portion 68 ~ and friction interface member 25 without dismantling .~ friction interface member 25 from the second component including body portion 152, housing end 154, and piston 48. Thus, clutch-brake A according to the teachings of 10 the present invention is advantageous in the ease of maintenance and specifically the replacement of friction lining rings ~2 and 79 and particularly does not require reaching radially inward of a closed housing for lining ~` replacement.
It should be additionally noted that the preferred I construction of friction disc 28 of Figures 3 and 4 according to the teachings of the present invention is further advantageous. Specifically, friction disc 28 is adaptable for easy casting without requiring casting 20 cores. Specifically, one piece friction disc 28 of the type of U.S. Patent 4,534,454 required spaced cutouts 23a ~, be formed by using cores located between the cavities ~; which formed the flat ring portions of the friction disc 28, greatly increaslng the cost of the molds as well as 25 the casting. The two pie~e construction of friction disc 28 and specifically the construction of friction ~,~ interface element 25 eliminates the requirement for casting cores for disc heat ventilation as webs 27 which ' space ring portion ~3b and 25a to allow for heat 30 ventilation are formed on and upstand from the rear face of flat ring portion 25a. Flat ring portion 23b need not be cast and may be slmply cut or stamped from sheet r~ material, greatly reducing the cost of manufacture.
k Furthermore, during maintenance of clutch-brake A and 35 specifically the replacement of friction lining rings 32 ahd 79, it should be noted that friction disc 28 of r h~ ~
~ ' t ' 132732~
; l F~ gures 3 and 4 according to the teachings of the present invention is also of an advantageous construction.
Specifically, flange 170 is located axially inward of end 164 and of friction lining 79 secured to annular body 5 portion 72. Thus, after housing end 82 is removed by removing bolts 216, bolts 29 may be removed which secure friction lining ring 32 and flat ring portion 23b to friction interface element 25. After removal of ring 32 and portion 23b, easy access is allowed to bolts 81 10 through openings 95 to allow removal of friction lining ring 79 and in particular it is not necessary to reach through ring portions 23b and 25a and cutouts 23a.
Further, the use of bushings 208 in housing end 154 in Figures 1 and 2 according to the teachings of the 15 present invention is particularly advantageous over utilization of ball bearings. Specifically, bushings 208 are clearly less expensive than ball bearings. Further, the fabrication of end 1~4 and its assembly with bushings 208 and output shaft lO according to the teachings of the 20 present invention is easier and less expensive.
Furthermore, the axial length required for bushings 208 is considerably shorter than for ball bearings allowing clutch-brake A according to the teachings of the present invention to be axially shorter and friction disc 28 to 25 be axially closer to the output apparatus than when roller bearings are utilized. Thus, although roller bearings are more capable of recelving overhang and radial loa~s, the construction of clutch-brake A
according to the teachings of the present invention and 30 the direct lnterconnection of housing end 154 to the output apparatus allows use of bushlngs 208 whlch reduces the overall cost of clutch-brake 10.
Now that the basic teachings of the present invention have been explained, maQy extensions and variations will 35 be obvious to one having ordinary skill in the art. For example, although housing 150 in th~ preferred form of s 132732~
~ -18~
,'~ 1 the present ~nvention in Figures 1 and 2 does not include cooling air apertures and is believed to be advantageous, such cooling air apertures or other cooling provisions may be provided in addition to and/or instead of fins 174 and 176 such as provided in Figures 3 and 4.
Further, although securement of housing ends 82 or 156 and housing end 154 to body portion 152 is shown in the preferred embodiment including bolts 200 and bolts 216 and associated structure, other forms of 10 securement may be apparent to one skilled in the art after the teachings of the present invention are known.
., Although shown as formed of one piece, friction lining ring 32 may be formed in a manner as friction 15 lining ring 79 of Figures 3 and 4 to allow interchangability and component inventory and iS manufacture reduction.
i~ Although air pressure on both sides of piston 48 is utilized to activate clutch-brake A in the preferred 20 form, other forms and types of activation may be utilized in ac~ordance with the present invention.
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Claims (26)
1. In an apparatus for providing rotational control of an output including an interface disc having first and second interface surfaces, a housing, a first interface member formed on an input for interfacing with the first interface surface of the interface disc, a second interface member formed on the housing for interfacing with the second interface surface of the interface disc, with the improvement comprising an improved housing comprising, in combination: a cylindrical body portion; a first housing end having a generally circular shape; a second housing end; with the cylindrical body portion including an axially extending annular member having a free annular end, with the second interface member being integral with and extending radially inwardly of the axially extending annular member; a mounting flange extending radially outwardly of the axially extending annular member slightly offset from the second interface member; means for removably securing the first housing end to the free annular end of the axially extending annular member; and means accessible outside of the axially extending annular member of the cylindrical body portion for removably securing the second housing end to the mounting flange of the cylindrial body portion.
2. The apparatus of claim 1 further comprising an improved interface disc comprising, in combination:
a first, flat ring portion including the first interface surface, a first face opposite to the first interface surface, and a radially inward axially extending opening;
an interface element including a second ring portion and means for connecting the second ring portion for rotation with the output, with the second ring portion including the second interface surface and a second face opposite the second interface surface; circumferentially spaced webs upstanding from the second face of the interface element, with the webs having free ends; and means for securing the first, flat ring portion to the interface element with the first face abutting with the free ends of the webs and spaced from the second face of the interface element forming spaced cutouts for heat venting.
a first, flat ring portion including the first interface surface, a first face opposite to the first interface surface, and a radially inward axially extending opening;
an interface element including a second ring portion and means for connecting the second ring portion for rotation with the output, with the second ring portion including the second interface surface and a second face opposite the second interface surface; circumferentially spaced webs upstanding from the second face of the interface element, with the webs having free ends; and means for securing the first, flat ring portion to the interface element with the first face abutting with the free ends of the webs and spaced from the second face of the interface element forming spaced cutouts for heat venting.
3. The apparatus of claim 2 further comprising, in combination: at least a first axially extending opening formed in the second ring portion of the interface element and located intermediate the circumferentially spaced webs for access to the second interface member.
4. The apparatus of claim 2 further comprising, in combination: axially extending shoulders formed on the free ends of the webs for receipt of the radially inward axially extending opening of the first, flat ring portion to aid in positioning of the first, flat ring portion relative to the interface element.
5. The apparatus of any one of claims 1-4 wherein the free annular end has a diameter; and wherein the apparatus further comprises, in combination: an axially extending projection integrally formed on the first housing end having a radially outward axially extending surface with a diameter generally equal to and for receipt within the diameter of the free annular end of the axially extending annular member.
6. The apparatus of claim 5 further comprising, in combination: a piston; means for interconnecting the piston for axial movement with the interface disc and for rotation relative to the interface disc; and means for reciprocally mounting the piston within the housing comprising, in combination: a radially inward axially extending surface formed on the axially extending projection of the first housing end; an axially extending surface formed on the second interface member of the cylindrical body portion; with the piston comprising, in combination: an axially disposed annular flange portion;
with the piston abutting with and for reciprocal movement within the axially extending annular member, with the piston being slideable on the radially inward axially extending surface formed on the axially extending projection of the first housing end, and with the axially disposed annular flange portion of the piston being slideable on the axially extending surface formed on the second interface member of the cylindrical body portion.
with the piston abutting with and for reciprocal movement within the axially extending annular member, with the piston being slideable on the radially inward axially extending surface formed on the axially extending projection of the first housing end, and with the axially disposed annular flange portion of the piston being slideable on the axially extending surface formed on the second interface member of the cylindrical body portion.
7. The apparatus of claim 6 further comprising, in combination: means for sealing between the radially outward axially extending surface formed on the axially extending projection of the first housing end and the free annular end of the axially extending annular member;
means for sealing between the piston and the axially extending annular member; means for sealing between the piston and the radially inward axially extending surface formed on the axially extending projection of the first housing end; means for sealing between the axially disposed annular flange of the piston and the axially extending surface formed on the second interface member of the cylindrical body portion, with a first pressure cylinder defined by the piston, the axially extending projection of the first housing end, and the axially extending annular member, with a second pressure cylinder defined by the piston, the second interface member, and the axially extending annular member; means for introducing fluid pressure into the first pressure cylinder; and means for introducing fluid pressure into the second pressure cylinder.
means for sealing between the piston and the axially extending annular member; means for sealing between the piston and the radially inward axially extending surface formed on the axially extending projection of the first housing end; means for sealing between the axially disposed annular flange of the piston and the axially extending surface formed on the second interface member of the cylindrical body portion, with a first pressure cylinder defined by the piston, the axially extending projection of the first housing end, and the axially extending annular member, with a second pressure cylinder defined by the piston, the second interface member, and the axially extending annular member; means for introducing fluid pressure into the first pressure cylinder; and means for introducing fluid pressure into the second pressure cylinder.
8. The apparatus of claim 5 further comprising, in combination: circumferentially spaced heat dissipating fins integrally formed with and extending axially from the axially extending annular member and integrally formed with and extending axially from the radially extending mounting flange.
9. The apparatus of claim 8 wherein the means for removably securing the second housing end to the mounting flange comprises, in combination: axially extending studs having a first end threadably received in the second housing end and having a second end secured to the radially extending mounting flange.
10. The apparatus of claim 9 wherein the output and the first interface member are rotatably mounted with respect to the housing and independent of each other allowing the apparatus to be readily disassembled into first and second major components for apparatus installation, with the first major component including the first interface member and the second housing end and with the second major component including the output, the cylindrical body portion, and the first housing end.
11. The apparatus of claim 10 further comprising, in combination: first and second L-shaped bushings having first and second legs, with the first legs having free ends, with the first and second L-shaped bushings being oppositely directed with the free ends of the first legs being contiguous, with the first legs of the first and second L-shaped bushings being rotatably received on the output; an annular shoulder formed in a circular opening of the first housing end, with the annular shoulder being captured between the second legs of the first and second L-shaped bushings; and means for preventing axial movement of the first legs of the first and second L-shaped bushings on the output.
12. The apparatus of any one of claims 1 to 4, 6 and 7 further comprising, in combination: circumferentially spaced heat dissipating fins integrally formed with and extending axially from the axially extending annular member and integrally formed with and extending axially from the radially extending mounting flange.
13. The apparatus of claim 12 wherein the means for removably securing the second housing end to the mounting flange comprises, in combination: axially extending studs having a first end threadably received in the second housing end and having a second end secured to the radially extending mounting flange.
14. The apparatus of claim 13 wherein the output and the first interface member are rotatably mounted with respect to the housing and independent of each other allowing the apparatus to be readily disassembled into first and second major components for apparatus installation, with the first major component including the first interface member and the second housing end and with the second major component including the output, the cylindrical body portion, and the first housing end.
15. The apparatus of claim 14 further comprising, in combination: first and second L-shaped bushings having first and second legs, with the first legs having free ends, with the first and second L-shaped bushings being oppositely directed with the free ends of the first legs being contiguous, with the first legs of the first and second L-shaped bushings being rotatably received on the output; an annular shoulder formed in a circular opening of the first housing end, with the annular shoulder being captured between the second legs of the first and second L-shaped bushings; and means for preventing axial movement of the first legs of the first and second L-shaped bushings on the output.
16. The apparatus of any one of claims 1 to 4, 6 and 7 wherein the means for removably securing the second housing end to the mounting flange comprises, in combination: axially extending studs having a first end threadably received in the second housing end and having a second end secured to the radially extending mounting flange.
17. The apparatus of claim 16 wherein the output and the first interface member are rotatably mounted with respect to the housing and independent of each other allowing the apparatus to be readily disassembled into first and second major components for apparatus installation, with the first major component including the first interface member and the second housing end and with the second major component including the output, the cylindrical body portion, and the first housing end.
18. The apparatus of claim 17 further comprising, in combination: first and second L-shaped bushings having first and second legs, with the first legs having free ends, with the first and second L-shaped bushings being oppositely directed with the free ends of the first legs being contiguous, with the first legs of the first and second L-shaped bushings being rotatably received on the output; an annular shoulder formed in a circular opening of the first housing end, with the annular shoulder being captured between the second legs of the first and second L-shaped bushings; and means for preventing axial movement of the first legs of the first and second L-shaped bushings on the output.
19. The apparatus of any one of claims 1 to 4, 6 and 7 wherein the output and the first interface member are rotatably mounted with respect to the housing and independent of each other allowing the apparatus to be readily disassembled into first and second major components for apparatus installation, with the first major component including the first interface member and the second housing end and with the second major component including the output, the cylindrical body portion, and the first housing end.
20. The apparatus of claim 19 further comprising, in combination: first and second L-shaped bushings having first and second legs, with the first legs having free ends, with the first and second L-shaped bushings being oppositely directed with the free ends of the first legs being contiguous, with the first legs of the first and second L-shaped bushings being rotatably received on the output; an annular shoulder formed in a circular opening of the first housing end, with the annular shoulder being captured between the second legs of the first and second L-shaped bushings; and means for preventing axial movement of the first legs of the first and second L-shaped bushings on the output.
21. The apparatus of any one of claims 1 to 4, 6 and 7 further comprising, in combination: first and second L-shaped bushings having first and second legs, with the first legs having free ends, with the first and second L-shaped bushings being oppositely directed with the free ends of the first legs being contiguous, with the first legs of the first and second L-shaped bushings being rotatably received on the output; an annular shoulder formed in a circular opening of the first housing end, with the annular shoulder being captured between the second legs of the first and second L-shaped bushings; and means for preventing axial movement of the first legs of the first and second L-shaped bushings on the output.
22. An interface disc for an output having first and second interface surfaces, comprising a first, flat ring portion including the first interface surface, a first face opposite to the first interface surface, and a radially inward axially extending opening; an interface element including a second ring portion and means for connecting the second ring portion for rotation with the output, with the second ring portion including the second interface surface and a second face opposite the second interface surface; circumferentially spaced webs upstanding from the second face of the interface element, with the webs having free ends, with the second ring portion, the connecting means, and the webs being integrally cast as a single element; and bolts threadably received in the webs and extending through and removably securing the first, flat ring portion to the interface element with the first face abutting with the free ends of the webs and spaced from the second face of the interface element forming spaced cutouts for heat venting.
23. The interface disc of claim 22 further comprising, in combination: at least a first axially extending opening formed in the second ring portion of the interface element and located intermediate the circumferentially spaced webs.
24. The interface disc of any one of claims 22 and 23 further comprising, in combination: axially extending shoulders formed on the free ends of the webs for receipt of the radially inward axially extending opening of the first, flat ring portion to aid in positioning of the first, flat ring portion relative to the interface element.
25. The interface disc of claim 24 further comprising, in combination: a friction lining ring, with the friction lining ring being removably secured to the first interface surface of the first, flat ring portion by the bolts removably securing the first, flat ring portion to the interface element.
26. The interface disc of any one of claims 22 and 23 further comprising, in combination: a friction lining ring, with the friction lining ring being removably secured to the first interface surface of the first, flat ring portion by the bolts removably securing the first, flat ring portion to the interface element.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US906,973 | 1986-09-12 | ||
| US06/906,973 US4750595A (en) | 1986-09-12 | 1986-09-12 | Rotational control apparatus |
| US011,778 | 1987-02-06 | ||
| US07/011,778 US4766986A (en) | 1987-02-06 | 1987-02-06 | Rotational control apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1327324C true CA1327324C (en) | 1994-03-01 |
Family
ID=26682774
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000545801A Expired - Lifetime CA1327324C (en) | 1986-09-12 | 1987-09-01 | Rotational control apparatus |
Country Status (12)
| Country | Link |
|---|---|
| JP (1) | JP2927429B2 (en) |
| AU (1) | AU627318B2 (en) |
| BE (1) | BE1000841A4 (en) |
| BR (1) | BR8704578A (en) |
| CA (1) | CA1327324C (en) |
| DE (1) | DE3730621C2 (en) |
| ES (1) | ES2005310A6 (en) |
| FR (1) | FR2603964B1 (en) |
| GB (1) | GB2197416B (en) |
| IT (1) | IT1218683B (en) |
| NL (1) | NL193389C (en) |
| SE (2) | SE501872C2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3827127A1 (en) * | 1988-08-10 | 1990-02-22 | Gehr Kunststoffwerk Kg | Clutch |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2197232A (en) * | 1936-01-18 | 1940-04-16 | Clarence G Wood | Clutch plate |
| US2674356A (en) * | 1950-09-06 | 1954-04-06 | Ind Clutch Corp | Air operated clutch-brake mechanism |
| GB731048A (en) * | 1952-12-12 | 1955-06-01 | Singer Mfg Co | Actuating mechanism for electric clutch-brake motor |
| US3250353A (en) * | 1963-07-10 | 1966-05-10 | Horton Mfg Co Inc | Clutch and brake with stationary fluid motor |
| US3378120A (en) * | 1965-05-28 | 1968-04-16 | Gen Automated Machinery Corp | Clutch and brake with non-rotatable fluid operator |
| GB1147604A (en) * | 1965-07-15 | 1969-04-02 | Mullard Ltd | Improvements in or relating to television transmission systems |
| CH466828A (en) * | 1967-12-04 | 1968-12-15 | Fischer Ag Georg | Drive unit, in particular for weaving machines |
| US3468402A (en) * | 1968-04-04 | 1969-09-23 | Francis P Edwards | Clutch and brake |
| US3623579A (en) * | 1969-09-26 | 1971-11-30 | Kelsey Hayes Co | Fabricated rotor for a disk brake assembly |
| BE759766A (en) * | 1970-03-16 | 1971-06-02 | Horton Mfg Co Inc | COMBINED BRAKE-CLUTCH |
| US3924715A (en) * | 1974-04-17 | 1975-12-09 | Force Control Ind | Clutch-brake unit |
| JPS5248283Y2 (en) * | 1974-05-20 | 1977-11-02 | ||
| JPS5225949A (en) * | 1975-08-23 | 1977-02-26 | Shimadzu Corp | Brake-loaded oil pressure motor |
| US4078637A (en) | 1976-05-07 | 1978-03-14 | Horton Manufacturing Co. Inc. | Fluid disengaged and spring urged brake |
| JPS559992U (en) * | 1978-07-06 | 1980-01-22 | ||
| US4534454A (en) * | 1981-11-30 | 1985-08-13 | Horton Manufacturing Co., Inc. | Combination clutch-brake |
| US4530680A (en) * | 1982-06-01 | 1985-07-23 | Dayco Corporation | Belt pulley and method of making the same |
| US4630718A (en) * | 1985-02-01 | 1986-12-23 | Horton Manufacturing Co., Inc. | Coupling clutch/brake and housing |
-
1987
- 1987-09-01 CA CA000545801A patent/CA1327324C/en not_active Expired - Lifetime
- 1987-09-02 SE SE8703412A patent/SE501872C2/en not_active IP Right Cessation
- 1987-09-03 BR BR8704578A patent/BR8704578A/en not_active IP Right Cessation
- 1987-09-08 GB GB8721101A patent/GB2197416B/en not_active Expired - Fee Related
- 1987-09-09 NL NL8702143A patent/NL193389C/en not_active IP Right Cessation
- 1987-09-10 ES ES8702608A patent/ES2005310A6/en not_active Expired
- 1987-09-11 FR FR878712636A patent/FR2603964B1/en not_active Expired
- 1987-09-11 DE DE3730621A patent/DE3730621C2/en not_active Expired - Fee Related
- 1987-09-11 BE BE8701024A patent/BE1000841A4/en not_active IP Right Cessation
- 1987-09-11 JP JP62228229A patent/JP2927429B2/en not_active Expired - Lifetime
- 1987-09-11 IT IT67778/87A patent/IT1218683B/en active
-
1990
- 1990-06-01 AU AU56235/90A patent/AU627318B2/en not_active Ceased
-
1991
- 1991-06-12 SE SE9101800A patent/SE507655C2/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| SE9101800D0 (en) | 1991-06-12 |
| SE507655C2 (en) | 1998-06-29 |
| GB2197416A (en) | 1988-05-18 |
| SE501872C2 (en) | 1995-06-12 |
| SE8703412D0 (en) | 1987-09-02 |
| NL193389C (en) | 1999-08-03 |
| ES2005310A6 (en) | 1989-03-01 |
| BE1000841A4 (en) | 1989-04-18 |
| DE3730621A1 (en) | 1988-03-17 |
| NL193389B (en) | 1999-04-01 |
| DE3730621C2 (en) | 1999-01-28 |
| AU5623590A (en) | 1991-12-05 |
| BR8704578A (en) | 1988-04-26 |
| FR2603964B1 (en) | 1989-08-25 |
| JPS63106166A (en) | 1988-05-11 |
| SE9101800L (en) | 1991-06-12 |
| AU627318B2 (en) | 1992-08-20 |
| AU592888B2 (en) | 1990-01-25 |
| JP2927429B2 (en) | 1999-07-28 |
| FR2603964A1 (en) | 1988-03-18 |
| SE8703412L (en) | 1988-03-13 |
| GB8721101D0 (en) | 1987-10-14 |
| IT8767778A0 (en) | 1987-09-11 |
| AU7775787A (en) | 1988-03-17 |
| GB2197416B (en) | 1991-06-05 |
| IT1218683B (en) | 1990-04-19 |
| NL8702143A (en) | 1988-04-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |
Effective date: 20110301 |