DE1269390B - Centrifuge for high speeds - Google Patents

Description

FEDERAL REPUBLIC OF GERMANY

GERMAN

PATENT OFFICE

EDITORIAL

Int. Cl .:

B 04b

German class: 421-6 / 01

Number: 1269 390

File number: P 12 69 390.2-52

Filing date: March 7, 1963

Open date: May 30, 1968

In centrifuges with continuous flow, it is known that the centrifuge rotor is the liquid in such a way that the rotor forms a face-to-face seal with a tube which is coaxial is arranged to the axis of rotation of the rotor and flows through the liquid to be supplied will. A known arrangement uses a tubular seal for this purpose, the one having radial flange which is attached to a cup-shaped part of the supply pipe surrounding the pipe end attached to its edge (British Patent 434 008).

It is also known in centrifuges through U.S. Patent 2,837,237 for fluid delivery a spring-loaded, axially displaceable sealing sleeve into the rotating rotor axis use, which is sealed in the fixed supply pipe and with its end face against a on the hollow rotor shaft arranged sleeve presses.

According to an older proposal by the proprietor of the property right, a continuously flowing Centrifuge for high speeds has a single-ended rotor on a shaft that revolves with it Has liquid outlet lines and inlet lines, which in the axial direction of go out at the other end of the shaft and which have lines that pass through a non-rotating part, via a surface-to-surface seal formed between the parts containing the two groups of lines, whose sealing surface extends radially to the axis of rotation, are in connection.

The invention aims to provide a face-to-face seal in a centrifuge arrangement of this type under an axial pressure that is automatically adjusted depending on the pressure in the centrifuge Applying applied pressure changes. So it will be with low sealing pressure and accordingly low heat generation and low seal wear if this is the case Allow pressure ratios of the liquid subjected to the centrifugation process, on the other hand the bearing pressure of the face-to-face seal increases when there are high fluid pressures in the centrifuge require this.

A centrifuge with continuous flow for high speeds with a single-ended one Runner on a shaft that has fluid outlet and inlet lines running around it, which extend in the axial direction from the other shaft end and which with lines that a enforce non-rotating part, via one between the two groups of lines Centrifuge for high speeds

Applicant:

Beckman Instruments, Inc., Fullerton, Calif.

(V. St. A.)

Representative:

Dr. phil. G. B. Hagen, patent attorney,

8000 Munich-Solln, Franz-Hals-Str. 21

Named as inventor:

Richard C. Stallman, San Carlos, Calif .;

Edward G. Pickels, Atherton, Calif. (V. St. A.)

Claimed priority:

V. St. v. America March 27, 1962 (182 813)

Parts formed face-to-face seal are in connection, characterized according to the Invention characterized in that the non-circumferential part penetrated by lines slides in the axial direction arranged displaceably and on the circumferential part having the moving lines pressed on by means of a device which can be extended in the axial direction under the influence of fluid pressure which is between a fixed point of the centrifuge frame and that of lines interspersed non-encircling part is housed.

A preferred embodiment of the invention provides that the automatic adjustment of the on the seal acting pressure provided, extendable in the axial direction from a device Piston device consists, the piston of which is guided axially displaceably within two cylinders, one of which is the cylinder of the flow supplying the liquid to be centrifuged to the rotor is traversed, while the other cylinder of the flow emerging from the rotor is flowed through, the one cylinder being supported against a fixed frame part of the centrifuge is, but the other cylinder transfers its pressure axially to the one surface sealing part. At this Arrangement is expedient from the yet

809 557/215

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more detailed reasons for discussion between shown) works with (also not shown) a compression spring is arranged on the two cylinders. appropriate control means together, so that the Ab-In In a further embodiment of the invention, the locking plate 16 can be releasably locked. the Centrifuge be provided with a shaft that serves to support the upper bearing and the end plate the rotor protrudes upwards and to take up with its upper 5 sealing arrangement 20. The end is rotatably mounted in a bearing, which have in the side walls of the rotor housing

a block body is arranged, the resilient to cylindrical steel part 21, which is used as protection for the is attached to a fixed part of the centrifuge case that it is due to the centrifugal and so lower movements of the rotor and the forces at the comparatively high rotational speed bearings as a result of vibrations or the like allows and dampens io dities in which the rotor is operated, occurring stresses to breakage or further details and advantages of the invention a flying apart of the runner. At in connection with exemplary embodiments, part 21 is explained by the bottom are completed below with reference to the pulling wall 22, which are made in the same way dependent description. Of the 15 a relatively resistant material Figures shows is made. The side walls 21 and the floor F i g. 1, partially in section, a side view wall 22 thus forming a steel safety chamber, a centrifuge for continuous liquid flow- The interior of the safety chamber can be equipped with cooling, mitttelverdarnpferwicklungen 23 be provided, the

F i g. 2, on an enlarged scale, shows a cross section 20 for cooling the interior of the chamber, through the upper bearing and sealing arrangement between the bottom wall 22 and the bearing

according to line 2-2 of FIG. 1, shaft or spindle 14 going outwards into the chamber

Fig. 3 shows a cross-section along the line 3-3 protrudes in order to support the runner there and to pull it against it i g. 2, ben, a suitable vacuum seal is formed.

F i g. Fig. 4 is a cross-section along line 4-4 of Fig. 25. The spindle 14 is preferably made of compliant F i g. 2, made of material and protrudes with its lower

F i g. 5 shows, on an enlarged scale, a partial section at the end which is in an oil-filled bearing arrangement 26 taken by the centrifuge rotor, the feed shaft and, down over. The camp 26 the coupling of the shaft with the rotor, is arranged by spaced apart

F i g. 6 a cross section of a somewhat modified 30 arms 27 carried, which are supported by a resilient Coupling the feed shaft with the runner, supported base plate 28 from extending downwards.

F i g. 7 on an enlarged scale is a view of the spindle or shaft 14 is driven with a for supplying and removing liquid to an um- belt pulley 31 and is revolving over this The feed shaft is driven towards and away from this by means of a drive belt 32, which is driven over the Nende running surface seal, 35 drive pulley 33 of a motor 34 is running. The reason-

8 shows a cross section along the line 8-8 in plate 28, for example by means of springs 37 F i g. 7, the platform 36 rest. In or on the housing

9 is a view taken along line 9-9 in FIG. 9, means (not shown) may be attached to F i g. 7 to evacuate chamber 17.

Fig. 10 is a cross-section along the line 10-10 in 40. As Fig. 5 shows, the rotor can be a cylindri-F i g. 5, see coat 41 included, like at its ends

11 shows a view of the arrangement for the areas 42 and 43 indicated, provided with threads load on the running surface seal. The lower end of the jacket 41 is through

12 shows a partially sectioned side view of a screwed-in base 44 closed. In a somewhat modified arrangement with a 45 the bottom a recess 46 is provided which upper bearing and a seal that can accommodate the upper end of the spindle. In the

F i g. 13 shows a view, on an enlarged scale, of pins 47 and 48 arranged from one another according to the line 13-13 in Fig. 12, which the barrel can in corresponding recesses on the surface sealing arrangement engage in their assignment to the side of the spindle to create a form-fitting upper bearing and sealing arrangement of the 50-sige connection between the spindle and the Fig. 12 shows the bottom 44, by means of which the rotor is driven

Figure 14 is a cross-section taken along line 14-14 in Figure 14 to provide.

F i g. 4. There is a cam 45 on the top of the base 44

In detail, the in F i g. 1 provided to accommodate a rotor core 49 Centrifuge assembly has an outer housing 11 that 55 is capable of. This core 49 is also exceptionally Includes drive means and the rotor housing. provided to the upper ends of the tenons At the top of the housing 11 an opening 47 and 48 is to be received so that it is also form-12 provided through which the rotor 13 is guided and driven by the drive spindle, the can to it inside the rotor housing on the top of the cylindrical rotor shell 41

the drive shaft 14 to be arranged as below 60 is threaded at 42 so that a is described. Cover 52 can be screwed into an end plate 16. Between the the upper bearing and seal assembly 17, shoulder 54 formed on shell 41, and screwed on. The end plate 16 is with rollers the underside of the lid 52 is an O-shaped 18 provided, the spaced apart ring 53 inserted. The lid is also provided with a are and in correspondingly distant channels 19 lau- 65 series of channels extending in the radial direction fen, which are attached to the side of the housing 11, so 56 provided with slots 58 in connection that this can be easily opened and you are standing on the top of the core piece 49 gedas Enclosed. A ratchet device (does not form. The liquid flows along the

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Slots 58 through the channels 56 in the outer tubing of the other, so that the degree of mixing is reduced the rotor chamber, as indicated by the arrows 59. The subdivisions also lead to a

is indicated. Decrease in the mixture that occurs when the The top of the core piece 49 has an after liquid is continuously fed to the rotor and outwardly protruding ring 61, which is removed from in FIG.

Lid 52 formed cavity 62 is added. In Fig. Fig. 6 is another possibility of means of an O-shaped ring 63 is shown for a flow arrangement for the supply and removal of liquid seal between the rim 61 and the speed to and from the rotor. The head piece adjoining part 52 is taken care of. In the ring 61 can 83 a is provided with a passage 101 , the NEN openings 66 are provided, which serve to guide io ring liquid formed between the tubes 78 and 79 to the core. space with the adjacent slot 58 connects. The core piece is spaced apart by a number. The liquid is then arranged from one another through the central tube 79 and is returned in a radial direction. The liquid is accordingly provided in the openings 71 extending into the device, supplied by the rotor via the annular space and via the liquid taken from the chamber between the core 15 central tube.

piece and the jacket 41 is formed in the axial In Fig. 2 it can be seen how the guide part 76 bore 72 and from there in the arrangement for the upward direction through the flange part 106 to supply and discharge of liquid, the subsequently passed through, which is written screwed to the end plate 16, to be allowed to arrive. is. By means of a thread 74 arranged at a distance from one another, the cover 52 receives 20 bolts 108. On the flange part 106, the support part 76 in which the flexible shaft assembly housing 107 is fastened. On its underside, the housing for the supply and discharge of liquid has recesses 109 into which a sleeve is located. The shaft 77 contains an outer tube 78 which engages 111 , which surrounds the part 76 and together concentrically encloses a hollow body 79. The shaft 77, an isolation ring 112 with the recesses 109, is enclosed within the part 76 by means of a 25. The insulation ring 112 is mounted with a circular groove bushing 80. Arranged at a distance from one another, which receives an O-shaped ring 113 , arranged O-shaped rings 81 and 82 form a suitable seal between the O-shaped ring 113. The end of the shaft is received by a flange part 106 and a head piece 83 of the insulating ring 112. About one in the vacuum seal created. An O-shaped ring head piece provided channel 84 consists of a connection 30 116 serves to seal between the insulating bond to the axial bore 72 in the core piece 49, ring 112 and the housing 107. Between the outer tube 78 and the through, the bolts are tightened accordingly Head piece 83 of space 85 is formed. The outer 108 is formed between the interior of the housing and tube 78 contains passages 86 so that the fluids and surrounding parts at the lower end of the housing, as indicated by arrows 87, are vacuum sealed in the annular housing. The space between the hollow inner line 79 and housing 107 is provided with a ball bearing 116 ^ 4, the outer tube 78 can flow. As will be described below, the bearing tube 79 is the liquid in the head piece is 116 ^ 4 with the part 76 so long not in contact, conducted. The lower end of the tube 79 is in contact until the rotor begins to vibrate too much, and the connection with the channel 40 formed in the head piece then only serves as a buffer to the deflections 89. The channel 89 in turn serves to connect the shaft limit.

with the adjacent slots 58 and the further The sleeve 111 is formed so that its upper

Above already mentioned channels 56. O-shaped end cooperates with the support ring 117 , the

Rings are used to seal between the head piece on the guide part 76 is screwed when the

and the shaft assembly 77. The O-shaped 45 bearing and seal assembly are raised

Ring 91 creates a seal between the core and the rotor out of the chamber through the with

piece 49 and the head piece 83 made. The threaded ones formed in the end plate

Upper O-shaped ring 92 is used to seal between the opening is lifted. Therefore, if the upper bearing

between the head piece and the guide 76. arrangement is removed, the sleeve 111 serves to

The liquid thus flows down the central 50 to the rotor in relation to the flange part

rohres79, then supported outwards through the opening 106.

openings 89, the slots 58 and the channels 56 in the The shaft arrangement 77 protrudes in the upward direction between the core piece 49 and the cylindrical through the opening 118, the space formed in the support housing outer jacket of the rotor 41. The 117 is formed, is then inwardly through the channels 71 further characterized by the recess 119, fluid that is provided in the member 120 55, and by the axial bore 72, the channel 84 and through the designated bearing assembly 121. The ring bearing 121 formed between the tubes 78 and 79 includes a sleeve 122 which urges an annular clearance space. take 123 has. In the bearing assembly 121 a The core 49 has longitudinal slots 94, inserted into bearing sleeve 124th The sleeve 124 forms to which wings 96 are received. The wings 60 together with the annular recess 123 protrude outward in the radial direction, with their chambers 125, the outer edges of which are in contact with the jacket 41 with a coolant for cooling. The wing of the camp is fed. The temperature of the bearing divide the interior of the rotor, which can be influenced in this way, so that the liquid in the rotor is accelerated if the feed or vanes and the rotor are set in rotation to no impairment 65 Withdrawal arrangement, liquid flowing through the rotor at the prescribed speed. Speed is to be brought between the sleeve 124 and the shaft. This leads to a displacement of the arranged porous sleeve 126 , which is supplied with oil via part of the amount of liquid in relation to line 127. Thus, the

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Bearing assembly 121 for rotatably receiving the seal member 162 is in a downward direction upper end of the flexible shaft assembly 77, by the pressure of the processed liquid in a for lubrication and as a vacuum seal pressed between the sealing contact layer. This bearing force the shaft and the surrounding parts. is based on a loading sleeve, which is shown in Fig. 11 in the

Between the parts 107 and 120, an individual is shown. The sleeve assembly yields Vacuum seal is provided, which maintains a piston 181, which plunges into cylinders 183 and has yielding sleeve 131, which protrudes in its position through 184, which is formed in the parts 186 and 187 a clock spring 132 is held. are. O-shaped rings 188 and 189 form the

The bearing assembly 121 is from the part 120 piston rings. The fluid absorbed by the centri and worn. The part 120 (see Fig. 2 io joint flows, must penetrate into the pipe 191. You and 3) is with extending in the radial direction- then flows into the rotor and arrives at the fingers 133, each of which will return from the runner to tube 193 Stainless steel insert 134 has. Opposite the use in hereupon in contact with the other end of the A stainless steel piston 181 is attached to part 120 in part 107 and flows over tube 194 set 136 attached. The inserts are hollow 15 onwards. Usually it is the one entering at 191 broach which has a larger diameter liquid under high pressure, while those at 193 have as a trunnion 137; the exit liquid entering the cavities as a result of pressure engagement and the part 120 at three different drains everything in the barrel it is under lower pressure. Occasionally, however, it is necessary to adjust the flow ratio to the part 107 can hold. to reverse direction; in this case the

Inwardly protruding at the lower end of the piston 181 formed on the part 107 Tongues 142 carry a ring 141 which is applied to the pressure to expand the assembly. Of the gene is fastened by means of the screws 143. The after fluid pressure leads to an expansion or to outwardly protruding tongues of the part 120 lie between a pressing of the two ends of the see the tongues extending inward. At 35 seal arrangement. The lower end 186 works for everyone Ring 141 are spaced apart from one another, but together with a ball, which in turn attaches itself to arranged rubber parts 144 attached, which engages in ab- the part 175 and pushes it downwards, so extend inwardly and the upper ends of the that the fixed · sealing surface of the circumferential stainless steel inserts 134 record. is assigned to the sealing surface in a sealing manner. That

The part 120 is thus both through the ring 141 30 upper part 187 cooperates with a ball 198, as well as by means of the pin 137 through the part 107 on which an adjusting screw 199 engages, which is after stored, while still extending enough clearance for the bottom through the housing 201, which the Deflection or vibration of the upper shaft includes upper bearings and the seal assembly is available, although it is in the closet. The advantage of the structure described is in it

ken are held. 35 to see that the pressure on the sealing surface is a

The upper support piece 120 carries the guide 150 is a direct function of the pressure with which the flues for the tread seal. Enters the runner at the end of the flexibility. The highest sealing seed shaft is the rotating part 151; the rotary pressure is only applied with the highest occurring fluid surface sealing (see. Fig. 2 and 7) attached. The liquidity pressures exercised when the need for it on Seal includes a first part 153 that is largest on the 40th. At lower pressures the dichroic tube 79 is attached. The part 153 is reduced with a frictional pressure, so that unnecessary frictional majority at a distance from each other and avoiding abrasion losses in the seal who-Kanälel54 provided with an annular groove 155 in the. To the runner even in the absence of Connection that is at the top of the same liquid that otherwise flows through the runner, or is formed. With these channels, the fluid circulates between 45 in the absence of pressure To be able to form the inner and outer flexible shafts, a spring 195 is provided which dete annulus in connection. To seal the clamped between two shoulder pieces, the is formed between the sealing member 153 and the housing on the outside of the cylinders 183 and 184 160 formed chamber is an O-shaped ring seal, so that there is always a minimum of sealing intended. The pipe 79 is in connection 50 pressure is available.

with that located in the sealing part 153 over the entire arrangement is an insulating

Passage 156. Completed. The conclusion can be insulation

The fixed part of the circumferential seal is made of material 200, such as styrofoam holds an outer cylindrical shell 161 attached to shell 202. The Ummantedas Sealing part 162 receives and together with 55 ment can be divided into two sections and how this forms a cooling chamber, the coolant to the in F i g. 4 shown at 203 with a hinge ver-cooling the tread seal can accommodate. be seen. The jacket can be inlet and outlet through O-rings 166 and 167 contain the chamber drain coaxial lines 204 and 205, around the sealed. The sealing part 162 stands with the separated liquid and coolant in the end of the gel Part 153 in sealing contact and 60 housing, as shown schematically in FIGS. 2 and 4 is provided with a plurality of channels, which are indicated.

extend upward and into an annular ring. The bearing and seal assembly includes keyway 165 open, which in turn with the channel 168 in tel, to the tread seal during the connection which is driven to an outlet pipe 169, for example a jet 206, is closed. The central shaft 79 stands with the axial 65, which serves to direct water onto the tread opening 171 in connection, in turn, with the tion to spray. The water from the seal Opening 172 and the supply pipe 173 connected, flows between the parts and overflows that is. an outlet 207, which at the same time as an outlet for

other liquids can serve, which penetrate into the arrangement.

It can be seen that in this way a bearing and sealing arrangement is created which serves to to form part of the vacuum containment for the rotor, and in turn the upwardly extending one flexible shaft. The arrangement contains means to ensure that the force of the Circumferential seal is comparable to the pressure of the liquid, which causes leakage losses be kept to a minimum. Places where heat is generated or places with which the Liquid is in contact, are cooled so that they are kept essentially at the same temperature and thus destruction or decomposition of the same can be avoided. In the overall arrangement the shaft is mounted in such a way that it can bend, so as to cause vibrations in itself to be able to absorb balanced runners, which as a result of an imbalance of the load or disturbances occur in the separated liquid. The resilient arrangement carries helps to dampen any vibrations that may occur. The arrangement allows the supply and Discharge of liquids at air pressure in a runner, which is rotatably arranged in a vacuum chamber is.

In certain cases it may be desirable to mount the upper shaft somewhat more rigidly and to provide different inlet and outlet channels. FIGS. 12 and 13 show such a modified arrangement. Parts of Figures 12 and 13 have the same reference numerals as corresponding parts previously described. The part 76 a serves to receive a rigid shaft 211 which protrudes upwards and is sealed against the sleeve 212, for example by O-shaped rings 213 in a suitable manner. On the part 212 a plurality of channels 214 are provided which are in communication with the space 216 , which in turn is connected to the openings 154 a in the circumferential part 153 ″ of the tread seal. The inner shaft is fastened in a suitable manner to the circumferential sealing part 153 a, for example by a sealing part 215. The shaft 79 α protrudes downwards into the head piece described above. The rigid shaft 211 and the flexible shaft 79 α cooperate so that they form inlet and outlet channels. The annular space serves as the one channel, the hollow shaft 79 a as the second passage. The bearing arrangement is similar to that previously described. The part 219 is, however, rigidly attached to a rigid ring 141 a, while the flexibility is established by means of a rubber sleeve 221 which is arranged between the bearing part 122 and the carrier 219.

With regard to all further details, the arrangement is essentially constructed as that before and bears corresponding reference numerals.

Claims (10)

Patent claims: 1. A centrifuge with continuous flow for high speeds with a single-ended rotor on a shaft that has fluid outlet and inlet lines running around with ilir, which extend in the axial direction from the other end of the shaft and which have lines that pass through a non-rotating part via a The face-to-face seal formed between the parts containing the two line groups is connected, characterized in that the non-circumferential part (162) penetrated by lines (168, 172) is slidably slidable in the axial direction and to which the accompanying lines (78, 79) having circumferential part (151) is pressed by means of a device (186, 187) which can be extended under the influence of liquid pressure and which is located between a fixed point (181, 198) of the centrifuge frame (201) and that of lines (168, 172) penetrated non-circumferential part (162) is housed. 2. Centrifuge according to claim 1, characterized in that the extendable device (186, 187) is connected to the line (169, 173) for the liquid to be centrifuged. 3. Centrifuge according to claim 2, characterized in that the extendable device (186, 187) has a piston (181) , the opposite ends of which are guided in cylinders (183,184) , and that the one cylinder (183) of the rotor ( 41) supplied liquid to be centrifuged and the other cylinder (184) is flowed through by the centrifuged liquid emerging from the rotor (41). 4. Centrifuge according to claim 3, characterized in that the two cylinders (183, 184) are biased away from each other by a compression spring (195). 5. Centrifuge according to claim 1, characterized in that the extendable device (186, 187) of a ball-and-socket mounting (198) is connected to the centrifuge frame (201) . 6. Centrifuge according to claim 1, characterized in that the upper end (77) of the rotor shaft is rotatably mounted in a bearing (121) which is arranged in a block (120) fastened resiliently to a stationary part (107). 7. Centrifuge according to claim 6, characterized in that the stationary centrifuge part (107 ) carries the block (120) by means of radial tongues (142) with the interposition of elastomeric parts (144). 8. Centrifuge according to claim 6, characterized in that the block (120) is connected to the stationary centrifuge part (107) by means of a plurality of deflectable pins (137) extending parallel to the shaft (78). 9. Centrifuge according to claim 6, characterized in that the block (120) has cooling lines and a chamber (125) which has a cooling medium flowing through it and surrounding the bearing (127). 10. Centrifuge according to claim 6, characterized in that a line (206) is provided on the block (120) , through the opening of which the jet of a coolant is directed onto the face-to-face seal (151, 161) . Considered publications:
German Patent No. 551477;
British Patent No. 434 008. For this purpose 2 sheets of drawings 809 557/215 5.68 © Bundesdruckerei Berlin