US3351360A

US3351360A - Fluid supply apparatus

Info

Publication number: US3351360A
Application number: US453003A
Authority: US
Inventors: Armand L Faccou
Original assignee: FMC Corp
Current assignee: FMC Corp
Priority date: 1965-05-04
Filing date: 1965-05-04
Publication date: 1967-11-07
Anticipated expiration: 1984-11-07

Description

1967 A. L. FACCOU FLUID SUPPLY APPARATUS 5 Sheets-Sheet 1 Filed May 4, 1965 WON owm

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IINVENTOR ARMAND L. FAOCOU ATTORNEY Nov. 7, 1957 A. L. FACCQU FLUID SUPPLY APPARATUS 5 $heets-Sheet 2 Filed y 4, 1965 mvmmaz ARMANI) L. FAcoou @P mm ATTORNEY Nov. 7, 1967 A. FACCOU FLUID SUPPLY APPARATUS 3 Sheets-Sheet 3 Filed May 4, 1965 3M MPN mwwN m 00 09w wmm 6% 3h 0mm 0mm oww N3 03 mmm mm NPN wwm wmm mwm ATTORNEY United States Patent 3,351,360 FLUID SUPPLY APPARATUS Armand L. Faccou, Santa Ana, Califi, assignor to FMC Corporation, San Jose, Calif., a corporation of Dela- Ware Filed May 4, 1965, Ser. No. 453,003 8 Claims. (Cl. 285-41) ABSTRACT OF THE DISCLOSURE A multiport rotary coupling for separately and uninterruptedly conducting a plurality of fluids at different temperatures and pressures between stationary and rotating devices.

It is well known that in various machines, roller dies are employed in producing finished products from raw or partially finished material. Such roller dies are frequently heated or cooled in their entirety as an aid in their performance of the desired operation. Consequently, these rollers have an interior cavity in which a heating or cooling medium is received for maintaining the surface area of the roller at a particular temperature.

It has proven helpful in the production of plastic sheet from pelletized raw plastic, in a machine of the general type mentioned, to employ a roller die having various surfaces areas which are maintained at different temperatures by different fluids which are supplied to different areas of the rollers interior. Fluid supplied to another surface area of the roller die is directed therefrom onto the plastic sheet. This roller die is so arranged that a certain portion of its surface area is heated by steam to a high temperature, for example three hundred and ninety five degrees F., and another portion of its surface is maintained at a relatively cooler temperature, by use of water, having a lower temperature, for example two hundred degrees F. In addition, air supplied to the roller die is discharged from its periphery onto the plastic sheet.

It is important that these fluids be supplied to the roller die through its periphery, so as to be available as close as possible to their points of use. Additionally, it is imperative that an uninterrupted supply of these fluids be maintained to the roller die. The apparatus for supplying these fluids to the roller die includes separate systems for the steam, water and air. Both the steam and water are circulated through respective areas of the roller die from separate sources and the spent fluids are preferably returned to their sources, whereas the air supplied to the roller die is discharged therefrom during its operation.

Swivel or rotary couplings are commonly used in the lines supplying fluids to roller dies. However, the requirements of supplying such diverse fluids at the temperatures and pressures required through the periphery of a roller die, while maintaining uninterrupted communication between the roller die and the fluids sources, impose certain uncommon requirements on the fluid supply apparatus.

It is, therefore, an object of the present invention to provide an improved fluid supply apparatus.

Another object is to provide improved apparatus for separately and uninterruptedly conducting a plurality of diverse fluids at different temperatures and pressures between fixed sources of supply and to the interior of a rotating roller die through the peripheral surface thereof.

Another object is to provide, in the fluid supply apparatus for a roller die, an annular, multi-passage rotary coupling assembly which encircles the periphery of the roller die and which rotatably interconnects the fluid conducting lines leading between the fluid sources and the roller die.

Another object is to provide an improved fluid handling rotary coupling.

Another object is to provide an improved fluid handling rotary coupling of annular configuration and of relatively short axial dimension.

Another object is to provide a multi-passage, fluid handling rotary coupling of annular configuration having an improved arrangement of the fluid conducting chambers between the coupling members.

Another object is to provide seal retaining means in a multi-passage, fluid handling, rotary coupling to insure retention of the seals in sealing relation in the fluid conducting chambers thereof against the effects of a relatively wide pressure differential between the pressures of the fluids therein and the pressures of the fluids in adjacent chambers or that of the atmosphere surrounding the rotary coupling.

Another object is to provide a multi-passage, fluid handling rotary coupling of annular configuration and of limited axial dimension in which only limited surface areas are present against which axial forces tending to separate the coupling members can act.

Another object is to provide a multi-passage, rotary coupling of annular configuration and limited axial dimension in which a bearing means, rotatably interconnecting the coupling members, is so located with respect to the fluid conducting chambers between the coupling members that the axial forces acting against the radial surfaces in one of said chambers and which would otherwise act to separate the coupling members are in equilibrium.

Another object is to provide a multi-passage, rotary coupling of annular configuration in which the location of the fluid conducting chambers between the coupling members is such as to enable a single bearing to interconnect the members for relative rotation and to retain the same against relative axial displacement.

These objects, together with other objects and advantages will become apparent upon reference to the following description and the accompanying drawings, in which:

FIGURE 1 is a view diagrammatically illustrating the fluid supply apparatus of the present invention, connected to the roller die of a plastic sheet producing machine and including a detail of the annular rotary coupling assembly of the apparatus, partially in axial section, encircling the roller die.

FIGURE 2 is a radial section, at reduced scale, showing one end of the rotary coupling assembly, as viewed in the direction of the arrows associated with the lines 2-2 of FIG. 1.

FIGURE 3 is a radial section, at reduced scale and with certain parts being removed, showing one rotary coupling of the rotary coupling assembly illustrated in FIG. 1, particularly disclosing the other end of the rotary coupling seen in FIG. 2, as viewed in the direction of the arrows associated with the lines 33 of FIG. 1.

FIGURE 4 is an enlarged axial section through one side of the rotary coupling shown in FIGS. 2 and 3, as viewed in'the direction of the arrows associated with the lines 44 of FIG. 2.

FIGURE 5 is a radial section, at reduced scale and with certain parts being removed, showing the other end of the rotary coupling assembly seen in FIG. 2 and particularly disclosing the other rotary coupling of the coupling assembly, as viewed in the direction of the arrows associated with the lines 55 of FIG. 1.

FIGURE 6 is an enlarged axial section through one side of the rotary coupling shown in FIG. 5, as viewed in the direction of the arrows associated with the lines 66 thereof, certain parts being revolved to the plane of the section for purposes of clarity.

FIGURE 7 is a fragmentary elevation of the rotary coupling seen in FIG. 5, shown at reduced scale and as viewed in the direction of the arrows associated with the lines 7-7 of FIG. 6, illustrating the connection of the fluid lines to the particular rotary coupling.

Referring specifically to FIGURE 1, the fluid supply apparatus 10 of the present invention is employed in supplying steam, water and compressed air to the roller die 12 of a machine 14, the machine 14 being employed in producing plastic sheet from pelletized raw plastic. The roller die 12 is of generally cylindrical configuration and is rotatably mounted by a bearing 16, on a support frame 18 of the machine. Since the details of the machine 14 in general and its operation are unimportant to the present disclosure, only a fragment of the machine and the roller die 12 thereof have been illustrated. A sprocket 20, secured in fixed relation to the rotary die 12, is connected by a drive chain 22 to a source of rotary power (not shown) to rotate the roller die.

Separate fluid supply systems S, W and A for supplying steam, water and air, respectively, to the roller die 12 are connected thereto by means of a rotary coupling assembly 24, included in the fluid supply apparatus 10. The steam and water are employed in heating and cooling different areas of the roller die 12 while the compressed air is discharged from the roller die adjacent the surface of the plastic sheet to aid in its handling.

The rotary coupling assembly 24 is of annular configuration (FIGS. 2 and 5) and includes two

annular rotary couplings

30 and 32, which are connected to each other in fixed coaxial relation by a spacer sleeve 33. The rotary coupling assembly 24 is operatively mounted in the machine 14, in a manner to be described later, in such a position as to encircle the roller die -12. In this way, the fluids, which are conducted to the rotating die through the

rotary couplings

30 and 32, can enter the roller die at appropriate locations along its periphery, as close as possible to their points of use.

The rotary coupling 30 (FIGS. 1 and 4) of the fluid supply system S includes two annular members, i.e., a stator 34 and a rotor 36, that are rotatably interconnected in coaxial relation by a bearing 38, which retains them against relative axial displacement.

The stator 34 comprises first and second

annular coupling portions

40 and 42 which are connected to each other in fixed relation. The first coupling portion 40 has an inwardly facing cylindrical surface 44 of limited axial dimension and an annular radial end face 46, which joins one end of the surface 44 and extends outward therefrom to the outer cylindrical surface 48 of the coupling portion 40. An annular radial surface 50 joins the other end of the cylindrical surface 44 and extends inward therefrom and joins a relatively short, outwardly facing cylindrical surface 52. The surface 52 is spaced inwardly from and is in confronting coaxial relation with the surface 44. A relatively narrow radial face 54 ext-ends between the surface 52 and the inner cylindrical surface '56 of the coupling portion 40, the surface 56 being concentric with the

surfaces

44 and 52. A radial surface 58, extending between the inner and outer

cylindrical surfaces

48 and 56, comprises the annular outer face of the coupling portion 40.

The second portion 42 is also annular, having coaxial inner and outer

cylindrical surfaces

64 and 66 and opposite, inner and outer

radial faces

68 and 70. The inner cylindrical surface 64 is provided with an annular concave raceway 72, forming part of the bearing 38. A bore 74 (FIG. 4), extending radially through the coupling portion 42, in alignment with the raceway 72, threadedly receives a ball retainer plug 76, the purpose for which will be described more fully.

A circular array of capscrews 78 (FIGS. 3 and 4), extending in an axial direction through the second cou- 4 pling portion 42, are threaded into the radial end face 46 and clamp an annular gasket 80 between the same and the radial face 68. In this way, the first and

second coupling portions

40 and 42 are separably but rigidly interconnected in fluid tight relation to make up the annular coupling member or stator 34 of the rotary coupling 30.

It will be noted in FIGURES 1 and 4 that the inner cylindrical surface 64 of the second coupling portion 42 is of relatively smaller diameter than the cylindrical surface 44 of the coupling portion 40. Therefore, when the first and

second coupling portions

40 and 42 are interconnected so as to have the relationship shown in FIGURES l and 4, the inner part of the portion 42 projects radially inward from the surface 44, with the projecting part of the radial face 68 being in parallel confronting relation with the radial surface 50. Thus, it will be apparent (see FIGS. 1 and 4) that the annular surfaces, i.e., the

cylindrical surfaces

44 and 64, of the annular coupling member or stator 34 are at right angles to the annular surfaces, i.e., the radial surface 50 and the radial face 54. Furthermore, the inwardly projecting part of the inner radial face 68 in cooperation with the cylindrical surface 44 defines an annular groove G in the annular member or stator 34 that adjoins another annular groove G, defined by the cylindrical surface 52 in cooperation with the radial surface 50.

The rotor or annular member 36 of the rotary coupling 30 (FIGS. 1 and 4) has an outer cylindrical surface 82 of approximately the same diameter as that of the surface 64. The inner surface 84 of the rotor 36 is also cylindrical and has a diameter similar to that of the surface 56 of the stator 34. An annular outer end face 86 of the rotor 36 extends radially between and joins the inner and outer

cylindrical surfaces

82 and 84 and a radial inner face 88 joins the surface 84.

The rotor 36 includes an annular radial flange 90, projecting outward from the cylindrical surface 82, and a cylindrical flange 92, projecting from the radial end surface 88. The radial flange 90 has opposite annular radial sides 94 and 96 and an outer edge which includes an annular concave channel 98 between opposite cylindrical shoulders 100 that join the sides 94 and 96. It is to be noted that the radial side 96 of the flange 90 is coplanar with and forms an effective extension of the end surface 88.

The cylindrical flange 92 has outer and inner

cylindrical surfaces

102 and 104, the outer surface 102 being coplanar with and forming an effective extension of the surface 82. A bevel 106 is provided on the cylindrical flange 92, connecting the radial edge thereof and the surface 104.

An annular concave raceway 114, similar to the raceway 72, is provided in the surface 82 of the rotor 36. The raceway 114 is so spaced with relation to the radial surface 88 and to the adjacent side 94 of the radial flange 90 that the flange 90 of the assembled rotary coupling 30 is substantially centered between the face 68 and the surface 50 of the stator 34, when the

raceways

72 and 114 of the stator 34 and the rotor 36 of the assembled rotary coupling 30 are opposite each other. Additionally, when the stator 34 and rotor 36 are so positioned, the face 54 and the surface 88 lie close to each other, in confronting relation.

Balls 116, introduced into the confronting

raceways

72 and 114 through the bore 74, are retained in the raceways by the ball retainer plug 78. In this way, the annular members i.e., the stator 34 and the rotor 36 of the rotary coupling 30 are mounted for relative coaxial rotation and are retained against axial displacement with respect to each other.

When the stator 34 and the rotor 36 are so assembled in making up the coupling 30, the inner

cylindrical surfaces

56 and 84 thereof are in alignment and comprise the inner cylindrical surface 85 of the rotary coupling 30.

With particular reference to FIGURE 4, it will be apparent that the

surfaces

44 and 68, defining the groove G, in cooperation with the

surfaces

50, 82 and 102 define the axially extending leg R of an annular L-shaped recess R provided between the stator 34 and the rotor 36. Similarly, the

surfaces

50 and 52, defining the groove G, in cooperation with the surfaces 88 and 96 define the radial leg R" of the annular recess R. It will be an aid in visualizing the configuration of the annular recess R, if it is understood that in effect the adjacent ends of the legs R and R overlap each other.

Referring again to FIGURES 1 and 4, it will be noted that at the distal end of the axially extending leg R of the annular recess R, the radial side 94 of the flange 90, the cylindrical surface 82 of the rotor 36, and the projecting portion of the radial face 68 of the second coupling portion 42, which adjoin each other, cooperate to provide an annular seal retaining channel 122. Similarly, the radial side 96 of the flange 90 and the cylindrical surface 102 of the cylindrical flange 92 of the rotor 36, and the radial surface 50 of the stator 34, which adjoin each other, cooperate to define an annular seal retaining channel 124 in the annular recess R Where the legs R and R thereof join. Another seal retaining channel, i.e., annular channel 126, located in the annular recess R at the distal end of the radial leg R, is defined by the adjoining

surfaces

50 and 52 of the stator 34 and the surface 88 of the rotor 36.

If the temperature of the fluid or fluids handled by the rotary coupling 30 is not excessively high, elastomeric seals of an appropriate type may be used in the

channels

122, 124, and 126. However, it has been found that if the working temperature of the fluid or fluids is high, seals of the type disclosed in United States application Ser. No. 379,083 of Landis H. Perry may be advantageously used. The above mentioned application is assigned to the assignee of the present application. For this reason

annular seals

130, 132 and 134, of the type disclosed in the above-mentioned United States application, have been used in the rotary coupling 30, as shown in the

seal retaining channels

122, 124 and 126, respectively.

In general, each of the

seals

130, 132 and 134 comprises a U-shaped annular envelope of Teflon or the like having a cylindrical bight portion 136 and radial side walls 138 and 140. The side walls 138 and 140 are forced against the radial surfaces of the respective

seal retaining channels

122, 124 and 126 by an energizer 142 and the cylindrical bight portion 136 is forced against the cylindrical surface of the respective channel by a coiled, annular tension spring 144, inside the energizer.

The seals 130 and 132, disposed in the annular leg R of the recess R, cooperate with the various adjoining surfaces defining the

channels

122 and 124, respectively, to provide a fluid tight, axially extending annular chamber C in the leg R. Similarly, the seal 134, disposed in the distal end of the radial leg R" and the seal 132, which, in effect, is in both the legs R and R, cooperate with the various adjoining surfaces defining the

channels

124 and 126, respectively, to provide a fluid tight, axially extending annular chamber C in the leg R.

Communication between the chamber C and the outside of the stator 34 is maintained through diametrically opposite passageways or ports 148 (FIGS. 1, 2 and 4), each of which extends through the coupling portions 40 between a threaded opening 150 in the radial face 58 and an inner opening 152 in the surface 44 of the chamber C, at a location opposite the concave channel 98 in the radial flange 90. Diametrically opposite passageways or ports 154 (FIGS. 1, 2 and 4), communicate between the chamber C and the outside of the rotor 36. Each passageway 154 includes one port 156 which extends a limited distance axially of the rotor 36 from a threaded opening 158 in the end face 86 thereof.

Another port 160 of the passage 156 extends radially of the rotor 36 from an opening 162 in the concave channel 6 98 of the radial flange 90, into the port 156. Since, in the present instance, only one pair of

ports

148, 154 is used to maintain communication through the rotary coupling 30 by way of chamber C, plugs 164 and 166 are threaded into one set of the openings and 158.

Communication between the chamber C and the outside of the stator 34 is maintained through diametrically opposite passages or ports 170 (FIGS. 2 and 4), each of which extends through the coupling portion 40 between a threaded opening 172 in the radial face 58 and an inner opening 174 (FIG. 4) in the surface 50 of the chamber C. Dimetrically opposite passageways or ports 176 (FIGS. 3 and 4) communicate between the chamber C and the outside of the rotor 36. Each passageway 176 includes one port 178 which extends a limited distance axially of the rotor 36 from a threaded opening 180 in the end face 86 thereof. Another port 182 of the passage 176 extends radially of the rotor 36 from a threaded opening 184 in the concave channel 98 of the radial flange 90 and into the port 178. A plug 186 is threaded into the opening 184 to block communication between the chamber C and the port 176. The final leg of the passageway 176 is provided by an axially extending port 188 leading between an opening 190 in the surface 88 of the chamber C and the port 182. It will be noted in FIGURE 4 that in forming the port 188 it is extended across the surface 104 of the cylindrical flange 92 between the surface '88 to the distal edge of the flange, thereby providing a groove 188a across the surface 104. The port 188 and the port 170 are of the same diameter and are spaced the same distance from the axis of the rotary coupling 30 so that normally a portion of the opening 174 of port 170 is in confronting relation with a portion of the edge of the cylindrical flange 92.

In the disclosed embodiment, only one pair of

ports

170, 176 is used to maintain communication through the rotary coupling 30 by way of the chamber C; therefore, plugs 192 and 194 (FIGS. 2 and 3) are threaded into one set of the

openings

172 and 180, respectively.

Thus it may be understood that a plurality of uninterrupted paths are provided through the stator 34 and the rotor 36 for conducting fluid supplies separately through the rotary coupling 30 regardless of Whether both the stator and rotor thereof are stationary or whether there is relative rotation therebetween. One such path includes the

ports

148 and 154 which extend between the annular chamber C and the outside of the rotary coupling 30 through the

coupling members

34 and 36. Another path includes the

ports

170 and 176, which extend between the chamber C and the outside of the rotary coupling 30, through the coupling members 34 and 3 6.

In operatively mounting the rotary coupling assembly 24 in the machine 14, the rotary coupling 30 is positioned With the inner peripheral surface 85 thereof in encircling, uniformly spaced relation about the roller die 12 (FIGS. 2 and 3) adjacent one end thereof. The radial face 58 of the stator 34 is in confronting relation with the inner face 200 of a radial flange 202, which forms a fixed part of the support frame 18. Each of a circular array of capscrews 204 (FIGS. 1 and 2), extending through the flange 202, is threaded into the radial face 58 of the stator 34 to rigidly connect the same to the support frame 18 in substantially coaxial relation to the roller die 12. In this way, the rotor '36 is positioned so that the end face 86 thereof is in confronting relation with the adjacent face 206 of an annular radial flange 208, provided on the roller die 12. Each of an annular series of capscrews 210, extending through the flange 208, is threaded into the end face 86 of the rotor 36 to securely connect the same to the roller die 12 for rotation therewith.

The fluid system S of the fluid supply apparatus 10, in addition to the swivel joint 30, includes a source of steam, such as a steam generator 216, capable of supplying saturated steam having a pressure of 220 psi. and a temperature of three hundred and ninety-five degrees F. A line 218, in which a valve 220 is provided, runs from the steam generator 216 to the port 148 of the rotary coupling 30, whece the adjacent end of the line 218 is screwed into the threaded opening 150 of the stator 34 to supply steam to the chamber C. Steam thus supplied to the annular chamber C is discharged therefrom through the port 154 into a line 222, which is screwed at one end into the threaded opening 158 and at the other end into a fitting 224 (FIGS. 1 and 2) in the roller die 12. The steam supplied in this way to the roller die 12 through its periphery is directed by appropriate interior construction (not shown) to those areas of the roller die which are to be heated. As the steam is cooled during operation of the roller die 12, condensate is formed therein which is conducted to a second fitting 226 (FIG. 3) in the periphery of the roller die and from which a line 228 leads to the port 176 of the rotary coupling 30. The line 228 is screwed into the threaded opening 180 of the port 176 which leads to the chamber C. Condensate, conducted in this way into the annular chamber C, is discharged therefrom through the port 170 into a line 230, which is screwed into the threaded opening 172 of the port 17 and leads therefrom back to the steam generator 216. Movement of the condensate back to the steam generator 216, through the line 230, can be regulated as desired by a valve 232 therein.

The steam, which is routed to the roller die 12 through the chamber C, is of suflicient pressure to aid in energizing the seals 130 and 132 therein. However, in the chamber C, the seal 134 is energized primarily by the energizer 142 since the condensate conducted therethrough is of relatively lower pressure than the steam in chamber C.

The rotary coupling 32 (FIGS. 1 and 6) of the water and air supply systems W and A in the fluid supply apparatus 10 includes two annular members, i.e., a stator 240 and a rotor 242, that are rotatably interconnected in coaxial relation by

bearings

244 and 246 which retain the same against relative axial displacement.

The annular member or stator 240 has inwardly and outwardly facing concentric

cylindrical surfaces

248 and 250, respectively, and opposite annular end faces 252 and 254. The end faces 252 and 254 are provided with annular concave raceways 256 and 258, respectively, which are spaced equal distances from the axis of the stator 240 and form parts of the

bearings

244 and 246.

Similar

annular grooves

262 and 264 are provided in the inner cylindrical surface 248 at locations which are near but which are spaced axially inward from the end faces 252 and 254, respectively. There are also three relatively narrow

annular grooves

266, 268 and 270 in the surface 248 between the

grooves

262 and 264, which are approximately the same depth as the

grooves

262 and 264 and are spaced therefrom and from each other approximately equal distances. Narrow annular bevels b are provided along the grooves, there being a bevel between the surface 248 and the adjacent side of each groove.

The rotor or annular member 242 of the rotary coupling 32 (FIGS. 1 and 6) comprises first and second

annular coupling portions

272 and 273 which are connected to each other in fixed relation. The first annular coupling portion 272 has coaxial inner and outer cylindrical surfaces 274 and 276, respectively, the axial dimension of the surface 276 being only slightly greater than that of the stator 240. One end of the annular portion 272 is provided with an annular radial flange 278 having inner and outer radial faces 280 and 281. The inner face 280 extends into confronting relation with the end face 252 of the stator 240 and includes an annular step having a radial face 280a which joins the cylindrical surface 276. The outer face 281 extends radially outward from the surface 274 to the edge of the flange 278. The radial face 280 is provided with an annular concave raceway 282, having the same diameter a that of the raceway 256 and comprises part of the bearing 244. An annular bevel 284 on the periphery of the flange 278 and joining the radial face 280 is provided for a purpose to be explained later. The other end of the annular portion 272 has a radial face 8 286 joining the inner and outer cylindrical surfaces 274 and 2767 The coupling portion 272 also includes similar annular

radial flanges

288 and 290 or abutment means projecting from the cylindrical surface 276 at locations which are near but which are spaced axially inward thereof from the opposite radial faces 280a and 286. The radial flange 288 has opposite annular radial sides 292 and 294 and an outer edge which includes an annular concave channel 296 between opposite cylindrical shoulders 298 that join the sides 292 and 294. Similarly, the radial flange 290 is provided with opposite annular

radial sides

300 and 302 and an outer edge which includes an annular concave channel 304 between opposite cylindrical shoulders 306 that join the

sides

300 and 302. It is to be noted that the concave channels 296 and 304 have substantially the same width as the

annular grooves

262 and 264 of the stator 240.

In addition to the

flanges

288 and 290, the rotor is also provided with three relatively narrow annular radial flanges or abutment means 308, 310 and 312 on the surface 276 between the

flanges

288 and 290, which are spaced therefrom and from each other approximately equal distances. All of the

flanges

288, 290, 308, 310 and 312 have substantially the same radial dimension.

The second coupling portion 273 is also annular, having an inner cylindrical surface 314 and opposite radial faces 316 and 318, the surface 314 being the same diameter as the surface 274. An annular bevel 319 on the outer periphery of the portion 273 and joining the radial face 316 is provide for purposes to be explained later. The face 316 includes an annular concave raceway 330, having the same diameter as the raceways 256 and 258 and comprises part of the bearing 246. Each capscrew 332 of a circular array thereof (FIGS. 1 and 6), extend in an axial direction through the second coupling portion 273 and is threaded into the radial face 286 to clamp the

portions

272 and 273 to each other, as mentioned earlier. When the coupling portions are so connected, the surfaces 274 and 314 thereof are in alignment and comprise the inner cylindrical surface 324 of the rotary coupling 32 and the radially projecting part of the coupling portion 273 comprises a second flange 325 of the rotor 242. It will be noted (FIG. 1) that the surface 324 has substantially the same diameter as the surface of the rotary coupling 30.

Balls 326 of the

bearings

244 and 246, introduced between the confronting raceway thereof during assembly of the rotary coupling 32, mount the stator 240 and the rotor 242 thereof for relative coaxial rotation and retain the same against displacement with respect to each other.

One of two similar O-ring seals 327, of a rubber-like composition, is disposed under tension between the bevel 284 on the flange 278 of the rotor 242 and the adjacent end face 252 of the stator 240 of the assembled coupling members. The other O-ring seal 327 is disposed under tension between the bevel 319 on the coupling portion 273 of the rotor 242 and the adjacent end face 254 of the stator 240. When the O-ring seals 327 are thus positioned they prevent the entry of dirt between the closely spaced surfaces of stator 240 and the rotor 242 and into the

bearings

244 and 246.

When the stator 240 and the rotor 242 are so assembled in operative relation, an annular recess T is provided in the rotary coupling 32 between the radially spaced

cylindrical surfaces

248 and 276 and the axially spaced radial faces 280a and 316 of the flanges 278 and 325. It will be noted that the radial face 280a has substantially the same radial dimension as the recess T. In the recess T the

radial flanges

288 and 290 of the rotor 242 are opposite the

annular grooves

262 and 264, respectively, of the stator 240 and the

flanges

308, 310 and 312 are opposite the

grooves

266, 268 and 270.

With reference to FIGURES 1 and 6, it will be noted that the confronting radial sides of the adjacent ones of the

flanges

288, 290, 308, 310 and 312, as well as the confronting radial face 280 and the adjacent radial side 292 of the flange 288 and the confronting radial face 316 and the adjacent radial side 302 of the flange 290 in cooperation with the cylindrical surface 276 define a plurality of annular seal retaining channels 328(1-328 in the recess T between the confronting

cylindrical surfaces

248 and 276.

Since the temperature of the fluids handled by the rotary coupling 32 are relatively lower than those handled by the rotary coupling 30, elastomeric, annular cup seal 330a-330f of simple, well known construction are used in this rotary coupling 30, as shown in the seal retaining channels 32842-3281, respectively. It is to be understood, however, that seals of the type used in the rotary coupling 30 can be used in the rotary coupling 32, if desired.

The adjacent ones of the seals in the recess T cooperate with the confronting

cylindrical surfaces

248 and 276 thereof to provide a fluid tight, axially extending chamber D therebetween. Thus, a chamber D1 is provided in the recess T between the adjacent seals 330a and 33012, a

chamber D2 between seals 33012 and 3300 and so on, thereby providing chambers D1-D5.

Communication between the chamber D1 (FIG. 1) and the outside of the stator 240 is maintained through a radially extending passageway or port 336 which extends through the stator from a threaded opening 338 in the surface 250 and into the annular groove 262. A passageway or port 348 is provided in the rotor 242 through which to maintain communication through the same between the chamber D1 and the outside of the rotor 242. The passageway 340 includes one port 342 which extends a limited distance axially of the rotor 242 from a threaded opening 344 in the radial face 281 of the coupling portion 272. Another port 346 of the passageway 346 extends radially of the rotor 242 from an opening 348 in the conopening 344 in the radial face 281 of the coupling portion 342.

Similarly, communication between the chamber D (FIG. 6) and the outside of the stator 240 is maintained through a radially extending passageway or port 346 which extends through the stator 240 from a threaded opening 348 in the surface 250 and into the annular groove 264. A passageway or port 350 (FIG. 6) is provided in the coupling portion 272 of the rotor 242 through which to maintain communication between the chamber D5 and the outside of the rotor. The passageway 350 includes one port 352 which extends a limited distance axially of the portion 272 to a point adjacent the radial face 286, from a threaded opening 354 in the radial face 281. Another port 356 of the passageway 35%} extends radially of the rotor 242 from an opening 358 in the concave channel 304 of the radial flange 290, into the port 352. Preferably, the

ports

340 and 350 in the rotor 242 are spaced one hundred and eighty degrees apart, as clearly shown in FIG. 5.

Communication between the chambers D2, D3 and D4 (FIG 6) and the outside of the stator 240 is maintained through radially extending passageways or

ports

358, 360 and 362 which extend through the stator from threaded

openings

358a, 360a and 362a, respectively, in the surface 250 and into the

annular grooves

266, 268 and 270, respectively. Three passageways 364 (FIG. 5), only one of which is shown in dotted lines in FIG. 6, are provided in the coupling portion 272 by which to maintain communication between the chambers D2, D3 and D4 and the outside of the rotor 242. Each passageway 364 includes one port 366 which extends a limited distance axially of the rotor 242 from a threaded opening 368 in. the radial face 281 of the coupling portion 272. Three ports or

passageways

370, 372, and 374 extend radially of the rotor 242 from an opening (not shown) in the cylindrical edges of the

radial flanges

308, 310 and 312 respectively, and into each of the ports 366.

Thus, it may be understood that a plurality of uninter- 10 rupted paths are provided rotor 242 for conducting fluid supplies separately through the rotary coupling 32 regardless of whether both the stator and rotor are stationary or whether there is relative rotation therebetween. A first path includes the

ports

336 and 340 which extend between the chamber D1 and the outside of the rotary coupling 32 through the coupling members. A second path includes the

ports

346 and 350 which extend between the chamber D5 and the outside of the rotary coupling 32, through the coupling members. A third path includes the

ports

358, 360 and 362 collectively, and the ports 364 collectively which extend between the chambers D2, D3 and D4 and the outside of the rotary coupling 32 through the stator 240 and the rotor 242.

It is to be understood that, if desired, separate fluid paths can be maintained through the stator 240 and rotor 242 by way of the chambers D2, D3 and D4 by providing separate ports which extend from each of the chambers D2, D3 and D4, through the rotor 242 to the outside thereof. In this way, five separate fluid paths can be provided through the swivel joint 32 instead of the three paths described above and shown in FIGS. 1 and 6.

In completing the mounting of the rotary coupling assembly 24 in the machine 14 and in order to operatively mount the rotary coupling 32, this coupling (FIG. 1) is positioned in encircling relations about the roller die 12, and is spaced axially inward thereof with respect to the rotary coupling 30. The edge portions of the previously mentioned spacer sleeve 33 overlap the adjacent end portions of the

stators

34 and 240 of the rotary couplings 3t) and 32 to which they are rigidly connected by circumferentially spaced

cap screws

376 and 378, respectively. As best shown in FIG. 1, the cap screws 376 pass radially through the spacer sleeve 33 and are screwed into the surface 66 of the coupling portion 42 to rigidly connect the sleeve to the stator 34 of the rotary coupling 30. Similarly, the cap screws 378 pass radially through the spacer sleeve 33 and are screwed into the surface 250 of the stator 240 to rigidly connect the same to the sleeve. The rotary coupling 32 is thus positioned in the machine 14 in axially spaced relation to the rotary coupling 30, and the stator 240 is secured against rotation by its connection to the radial flange 202 of the support frame 18 through the sleeve 33 and the stator 34 of the rotary coupling 30.

It will be noted that a plurality of circumferentially spaced openings 379 are provided in the sleeve 33, thereby leaving relatively narrow connections 380 between the opposite edge portions thereof. This enables the heat, conducted into the sleeve from the rotary coupling 30, to be dissipated more quickly than if the sleeve were solid. Furthermore, the narrow connections 380, between the opposite edge portions of the sleeve, reduce to a near minimum the amount of heat that can be conducted to the relatively cool rotary connection 32 from the heated coupling 30.

When the rotary coupling 32 is so positioned axially of the roller die 12, the radial face 281 of its rotor 242 is in contact with the adjacent radial surface of the previously mentioned sprocket 20. Each bolt 382 of an annular series thereof passing in an axial direction through the sprocket 20 is screwed into the end face 281 of the rotor 242 to rigidly connect the latter to the sprocket 20 for rotation with the roller die 12, relatively to the stator 240. When the rotary coupling 32 is mounted in the machine 14 in the manner disclosed, the inner peripheral surface 324 is in spaced, substantially coaxial relation to the surface of the roller die 12.

The fluid system W (FIG. 1), of which the rotary coupling 32 is a part, includes a source 386 of water that is capable of supplying the water at predetermined pressure and temperature, preferably at one hundred psi. and two-hundred degrees F. A line 388, in which a valve 390 is provided, runs from the water source 386 to the through the stator 240 and the p port 336 of the swivel joint 332, where it is screwed into the threaded opening 338 of the stator 240 to supply water to the chamber D1. Water, thus supplied to the chamber D1 is discharged therefrom through the port 340 into a line 392, which is screwed at one end into the threaded opening 344 of the port 340 and at the other end into a fitting 394 (FIGS. 1 and S) in the periphery of the roller die 12. The water supplied by the system W to the roller die 12 in this way, is directed by appropriate interior construction thereof (not shown) to those areas which are to be maintained at a relatively cooler temperature than the areas to which steam is supplied by the system S. The water, which absorbs heat as it is circulated in the roller die 12, is conducted to another fitting 396 (FIG. in the periphery of the roller die and from which a line 398 leads to the port 350 of the rotary coupling 32. The line 398 is screwed into the threaded opening 354 of the port 350 which leads to the chamber D5. The heated water, conducted in this way into the chamber D5, is discharged therefrom through the port 346 into a line 400 which is screwed into the threaded opening 348 and preferably leads therefrom back to the water source 386. The flow of water back to the source 386, through the line 400, can be regulated as desired by a valve 402 therein.

The fluid system A, of which the rotary coupling 32 is also a part, includes a compressor 408 capable of supplying an appropriate volume of air at a desirable pressure, preferably 1 p.s.i. A line 410, in which valve 412 is provided, runs from the compressor 408 to supply compressed air to the roller die 12. The line 410 includes three

branch lines

410a, 410b, and 410a which are screwed into the threaded

openings

358a, 360a and 362a of

ports

358, and 360 and 362 to direct compressed air from the line 410 into the chambers D2, D3 and D4. Air thus supplied to the chambers D2, D3 and D4 is discharged therefrom through the three ports 364 into three lines 414 (FIG. 5), each of which is screwed at one end into the threaded opening 368 of the respective port 364 and at the other end into one of three similar fittings 416 (FIGS. 1 and 5) in the periphery of the roller die 12. Air supplied by the system A to the roller die 12 in this way is directed by appropriate interior construction thereof (not shown) to those areas of the die from which the air is discharged against the surface of the sheet plastic to aid in its handling.

During preparation for the production of plastic sheet by use of the machine 14, various controls, in common use in fluid systems such as the present steam, water and compressed air systems S, W and A of the fluid supply apparatus 10, are set so as to supply these fluids at the desired pressures and/or temperatures to the roller die 12 by way of the rotary coupling assembly 24. Thus, steam supplied by the system S, having a pressure of two-hundred twenty p.s.i. and a temperature of threehundred ninety-five degrees F. is conducted through the rotary coupling 30 by way of the annular chamber C enroute to the roller die 12, which is rotated by the drive chain 22 during production. Condensate and steam enroute back to the steam generator 216 of the system S from the roller die 12 are also conducted through the rotary coupling 30 but by way of the annular chamber C.

The water, supplied by the system W, having a pressure of one hundred p.s.i. and a temperature of twohundred degrees F. is conducted through the rotary coupling 32 by way of the annular chamber D1 enroute to the roller die 12. After the water performs its cooling effect in the roller die 12 and is enroute back to the source 386 of water it is again conducted through the rotary coupling 32, this time through the annular chamber D5.

The air which, as mentioned above, is discharged from the roller die 12, is supplied by the compressor 408 at one p.s.i. and, enroute to the die, is conducted through the rotary coupling 32 by way of the annular chambers D2, D3, and D4.

The compression of the seals 330a330f between the

surfaces

248 and 276 is sufficient to effectively seal the chambers D2 and D3 against the escape of air past the seals 3300 and 330d therein since the air in these chambers is at too low a pressure to do so. However, the seals 330a, 3301) and 330e, 330 in the chambers D1 and D5 are energized by the pressure of the water conducted therethrough to seal these chambers.

It will be recognized that the ultimate reduction in the axial dimension of a multi-passage, fluid handling rotary coupling of annular configuration would be attained by constructing such a rotary coupling so that the annular fluid conducting chambers thereof adjoin each other in radial alignment, between the relatively rotating coupling members. In a rotary coupling having such construction, nearly all the forces exerted by the pressurized fluids conducted therethrough would be directed axially. Therefore, with fluids under high pressure, the forces exerted on the bearings interconnecting the coupling members for relative rotation are great and the wear of the bearing parts is proportional. It will be noted that in the rotary coupling 30 (FIGS. 1 and 4), the adjoining fluid conducting chambers C and C provided in the annular recess R between the

coupling members

34 and 36 are arranged so that one chamber, i.e., chamber C is disposed in an axial direction at right angles to the other or radially disposed chamber C. Therefore, because of this arrangement or disposition of the chambers C and C in the coupling 30, the axial forces tending to separate the coupling members are less than would be the case if the chambers were arranged in radial alignment. Additionally, the rotary coupling 30 is of relatively shorter axial dimension than if the chambers were in alignment in an axial direction. Due to the construction of the rotary coupling 30, only a single bearing need be used therein to interconnect the

coupling members

34 and 36 thereof for relative rotation, and the life of this hearing is longer than it would be in a swivel joint or rotary coupling where the annular chambers were in alignment radially of the coupling.

As most clearly understood by reference to FIG. 4, the

cylindrical surfaces

64 and 102 of the rotor 36 may be considered to define an imaginary cylinder which is coaxial with the

coupling members

34 and 36 and is substantially coincident with the centers of the balls 116 in the bearing 38. It will be noted that the entire chamber C is disposed to one side of this imaginary cylinder and is completely within one member of the rotary coupling 30. As a consequence, the axial forces exerted by the high pressure steam against the portions of the

surfaces

68 and 50 defining the opposite ends of the chamber C are in equilibrium. These forces have no tendency to cause relative axial separation between the

coupling members

34 and 36 and, therefore, are not resisted by the bearing 38. As a result, only the axial forces exerted against those portions of the

surfaces

50 and 88, defining the axially opposite surfaces of the chamber C, are resisted by the bearing 38 in retaining the

coupling members

34 and 36 against relative axial displacement.

With reference to the chamber C of the rotary coupling 30 shown in FIG. 4, the

seal retaining channels

122 and 124 thereof are of such axial dimension as to snugly fit the seals and 132 therein so that sealing relation is always maintained between the relatively

rotatable members

34 and 36 and the seals 130 and 132. Movement of the seals 130 and 132 radially in the

channels

122 and 124 is possible, however, without destroying the sealing relation mentioned above. This enables fluid to be conducted through the rotary coupling by way of the chamber C at a relatively lower pressure than the pressure of the atmosphere surrounding the rotary coupling 30 or the pressure in the chamber C, without dislodging the seals 130 and 132 from their sealing relation with the

channels

122 and 124. Additionally, the seals 130 and 132 cannot move to a position in the chamber C wherein 13 they might block the flow of fluid therethrou-gh by way of the

ports

148 and 154.

'If a partial vacuum should momentarily form in the chamber C, the seal 134 therein might in a certain area or areas move radially outward from its seating relation in the channel 126. Even though the seal 134, when in such a position, might contact the surface 194 (FIG. 4) of the cylindrical flange 92, the

ports

170 and 188 cannot be blocked due to the provision of the groove 188a across the cylindrical surface 104 and the relative position of the

parts

170 and 188 to the flange 92. Furthermore, the bevel 106 on the cylindrical flange 92 and the groove 188a assure that fluid can communicate at all times with the interior of the seal 134 to force the same into seated position in the channel 126. Under such a condition as that described above relating to the seal 134, the radial side walls 138 and 140 of the seal retain their sealing relation with the

sides

50 and 88 of the chamber C.

With reference to FIG. 6, it will be noted that the seals 330:2-330 cannot move in the seal retaining channels 328a-328f out of sealing relation between the confronting

surfaces

248 and 276 of the rotary coupling 32. Moreover, the seals 32811-3287, due to the annular

radial flanges

288, 290, 308, 310 and 312, cannot move to a position in the chambers D1-D5 wherein they could block the fluid flow through the rotary coupling 32 by way of these chambers.

From the foregoing it is further evident that the fluid supply apparatus of the present invention provides for the separate and uninterrupted conducting of a plurality of diverse fluid at different temperatures and pressures between fixed sources of supply and the interior of a rotating roller die through the periphery thereof, and that the rotary coupling assembly employed in the apparatus encircles the periphery of the rotary die to which the fluid conducting lines of the apparatus are connected by way of the rotary coupling assembly.

Although a preferred embodiment of the present invention has been shown and described, it will be understood that various changes and modifications may be made in the details thereof without departing from the spirit and scope of the appended claims.

Having described the invention, what is claimed and desired to be protected by Letters Patent is:

1. In combination, a roller die adapted to have different fluids supplied to different internal areas thereof through its periphery, said roller die being mounted for rotation in a support frame, a rotary coupling assembly comprising first and second annular multi-passage rotary couplings, each rotary coupling having an annular rotor and an annular stator interconnected for relative rotation, the annular stators of said rotary couplings being rigidly interconnected, means mounting said rotary coupling assembly in encircling relation to about said roller die with said stators fixed to said support frame to retain said stators against rotation, means connecting said rotors to said rotatable roller die for rotation therewith, a first stationary fluid source, means connecting said first fluid source to said first rotary coupling, said first rotary coupling having fluid conducting means interconnecting said first source to one interior area of said rotatable roller die through the periphery thereof by way of separate passages through said first annular multi-passage rotary coupling to uninterruptedly circulate fluid supplied by said first source between said first source said one area of said rotatable roller die, a second stationary fluid source, said second coupling having fluid conducting means interconnecting said second fluid source and a second interior area of said rotatable roller die through the periphery thereof by way of separate passages through said second annular multi-passage rotary coupling to uninterruptedly circulate fluid supplied by said second source between said second source and said second area of said rotatable roller die.

2. The combination of claim 1 wherein the fluids supplied to said roller die by said first and second rotary couplings are of different temperatures and said stators of said first and second rotary couplings are rigidly interconnected in axially spaced relation by a cylindrical sleeve having a peripherally spaced openings therethrough leaving relatively narrow connections therebetween interconnecting opposite ends of said sleeve to thereby restrict the conduction of heat through said sleeve between said interconnected rotary coupling.

3. An annular rotary coupling assembly comprising: (A) a first fluid handling rotary coupling including (1) a first annular coupling member having a cylindrical surface and opposite radial end faces,

(2) a second annular coupling member having a cylindrical surface and opposite radially projecting end flanges, each end flange including a radial inner surface in confronting relation with the adjacent radial end face of said first coupling member,

(3) bearing means between the inner surface of each radial end flange and the adjacent end face of said first coupling member and mounting said coupling members for relative rotary motion while retaining the same against relative axial displacement with the cylindrical surfaces of said coupling members in coaxial radially spaced confronting relation providing an annular axially extending recess between said cylindrical surfaces thereof,

(4) seal means interposed the cylindrical surfaces of said coupling members in the annular axially extending recess and providing in the recess in conjunction with said cylindrical surfaces a fluid-tight annular chamber and (5) means establishing communication through both of said coupling members between said chamber and the outside of the rotary coupling; and

a second fluid handling rotary coupling including (1) a first annular coupling member having adjoining annular surfaces disposed at right angles to each other,

(2) a second annular coupling member having adjoining annular surfaces disposed at right angles to each other and arranged in spaced confronting relation to the adjoining annular surfaces of said first coupling member of said second rotary coupling, the confronting surfaces of said coupling member of said second rotary coupling defining an L-shaped recess between said members, said recess having leg portions disposed at right angles to each other,

(3) seal means interposed between the spaced confronting surfaces defining the annular recess 7 of said second rotary coupling and providing in cooperation with said spaced confronting surfaces thereof fluid-tight chambers in the leg portions of the recess,

(4) bearing means between the coupling members of said second rotary coupling and mounting said members for rotary motion relatively to each other,

(5) separate means establishing communication through both of said coupling members of said second rotary coupling between each chamber thereof and the outside of the second rotary coupling, and

(6) means rigidly interconnecting one coupling member of one rotary coupling and one coupling member of the other rotary coupling in coaxial relation.

4. The rotary coupling assembly of claim 3 wherein the seal means in the annular axially extending recess of the first rotary coupling provide at least three annular 15 chambers therein, the outer seal means being seated against said flanges, and wherein the first rotary coupling includes separate means establishing communication through both of said'coupling members between each chamber and the outside of said first rotary coupling, and annular flange means on one of said coupling members projecting radially from the cylindrical surface there- 'of into the annular recess between said coupling members and providing abutment means for engagement by the seal means defining the inner ends of the two outer annular chambers and restricting said seal means against inward movement in the recess in a direction axially of said first rotary coupling, said flange means adapting said first rotary coupling to handle fluids of relatively high pressure in said two outer chambers.

5. The rotary coupling assembly of claim 4 wherein an annular groove provided in the cylindrical surface of the other of said coupling members of said first rotary coupling is located opposite said radial flange means and intersects the means establishing communication between the respective chamber and the outside of said other of said coupling members, and wherein the means establishing communication between said chamber and the outside of said one of said coupling members enters said chamber through said annular radial flange means opposite the annular groove.

6. The rotary coupling assembly of claim 3 wherein the seal means in the annular axially extending recess of the first rotary coupling provide at least three annular chambers therein, the outer seal means being arranged to be seated against said flanges, and wherein the first rotary coupling includes separate means establishing communication through both of said coupling members between each chamber and the outside of the rotary coupling, and annular flange means provided on one of said joint members projecting radially from the cylindrical surface thereof into the end chambers and providing abutment means for engagement by the seal means defining the ends of the outer chambers and restricting said seal means against movement toward each other in the end chambers in a direction axially of the rotary coupling, the annular flange means in said end chambers 16 adapting the rotary coupling to handle fluids of relatively low pressure in said end chambers.

7. The rotary coupling assembly of claim 6 wherein an annular groove is provided in the cylindrical surface of the other of said coupling members of said first rotary coupling is located opposite said radial flange means in each of said end chambers and intersects the means establishing communication between the respective end chamber and the outside of said other of said coupling members, and wherein the means establishing communication between each of said end chambers and the outside of said one of said coupling members enters the respective end chamber through said annular radial flange means therein.

8. The annular rotary coupling assembly of claim 3 wherein one coupling member of one rotary coupling and one coupling member of the other rotary coupling are rigidly interconnected in coaxially spaced relation by a cylindrical sleeve having peripherally spaced openings therethrough leaving relatively narrow connections therebetween which connect opposite ends of said sleeve to thereby restrict the conduction of heat through said sleeve between said interconnected couplings.

References Cited UNITED STATES PATENTS 2,343,491 3/1944 Bard et al. 285-275 X 2,458,343 1/1949 Carleton 285-275 X 2,557,498 6/1951 Collender 285-136 2,662,785 12/1953 Fawick 285-136 2,768,843 10/1956 Zeilman 285-275 X 2,877,026 3/1959 Payne et al. 285-275 X 2,943,868 7/1960 Hanback 285- X 3,175,849 3/1965 Kelly 285-190 FOREIGN PATENTS 759,098 10/ 1956 Great Britain. 859,491 1/ 1961 Great Britain.

EDWARD C. ALLEN, Primary Examiner.

THOMAS P. CALLAGHAN, Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,351,360 November 7, 1967 Armand L. Faccou ppears in the above identified It is certified that error a ehy corrected as patent and that said Letters Patent are her shown below:

Column 6, line 12, "Dimetrically" should read Diametrical Column 7, line 2, "whece" should read where Column 9, lines 38 and 39, cancel "opening 344 in the radial face 281 of the coupling portion 342. and insert cave channel 296 of the'radial flange 288, into the port 342. Column 13, line 54, cancel "to"; line 65, after "source", second occurrence,

insert and Signed and sealed this 24th day of February 1970.

V (SEAL) Edward M. Fletcher, J r.

Attest:

WILLIAM E. SCHUYLER, IR;

Attesting Officer Commissioner of Patents

Claims

1. IN COMBINATION, A ROLLER DIE ADAPTED TO HAVE DIFFERENT FLUID SUPPLIED TO DIFFERENT INTERNAL AREAS THEREOF THROUGH ITS PERIPHERY, SAID ROLLER DIE BEING MOUNTED FOR ROTATION IN A SUPPORT FRAME, A ROTARY COUPLING ASSEMBLY COMPRISING FIRST AND SECOND ANNULAR MULTI-PASSAGE ROTARY COUPLINGS, EACH ROTARY COUPLING HAVING AN ANNULAR ROTOR AND AN ANNULAR STATOR INTERCONNECTED FOR RELATIVE ROTATION, THE ANNULAR STATORS OF SAID ROTARY COUPLINGS BEING RIGIDLY INTERCONNECTED, MEANS MOUNTING SAID ROTARY COUPLING ASSEMBLY IN ENCIRCLING RELATION TO ABOUT SAID ROLLER DIE WITH SAID STATORS FIXED TO SAID SUPPORT FRAME TO RETAIN AND STATORS AGAINST ROTATION, MEANS CONNECTING SAID ROTORS TO SAID ROTATABLE ROLLER DIE FOR ROTATION THEREWITH, A FIRST STATIONARY FLUID SOURCE, MEANS CONNECTING SAID FIRST ROTARY SOURCE TO SAID FIRST ROTARY COUPLING, FIRST ROTARY COUPLING HAVING FLUID CONDUCTING MEANS INTERCONNECTING SAID FIRST SOURCE TO ONE INTERIOR AREA OF SAID ROTATABLE ROLLER DIE THROUGH THE PERIPHERY THEREOF BY WAY OF SEPARATE PASSAGES THROUGH THE FIRST ANNULAR MULTI-PASSAGE ROTARY COUPLING TO UNINTERRUPTEDLY CIRCULATE FLUID SUPPLIED BY SAID FIRST SOURCE BETWEEN SAID FIRST SOURCE SAID ONE AREA OF SAID ROTATABLE ROLLER DIE, A SECOND STATIONARY FLUID SOURCE, SAID SECOND COUPLING HAVING FLUID CONDUTING MEANS INTERCONNECTING SAID SECOND FLUID SOURCE AND A SECOND INTERIOR AREA OF SAID ROTATABLE ROLLER DIE THROUGH THE PERIPHERY THEREOF BY WAY OF SEPARATE PASSAGES THROUGH SAID SECOND ANNULAR MULTI-PASSAGE ROTARY COUPLING TO UNINTERRUPTEDLY CIRCULATE FLUID SUPPLIED BY SAID SECOND SOURCE BETWEEN SAID SECOND SOURCE AND SAID SECOND AREA OF SAID ROTATABLE ROLLER DIE.