US2609672A - Unitized centrifugal refrigerating machine - Google Patents

Description

Sept. 9, 1952 N. B. WALES UNITIZED CENTRIFUGAL REFRIGERATING'MACHINE 2 SHEETS-SHEET 1 Filed May 4, 1951 1 J l/ mm U Q 7 Q J a w g mm M m w MN a 5 NW Q W J l Q U a w R y M A M Q MN I N\ I m 1 N N T m v 1 mi Su H Q\ ct H H HL nmkxm IIWENTOR. rm

Patented Sept. 9, 1952 UNIIETIZ'ED? STATES PATENT OFFICE H TIZEQDENTRH A REFRIGEBATmQf MACHI NathaniehBrwalesyNew York, N.- =Y'.; assignor 'to I Industrial. Patent Corporation, New York,

Application May 4,1951, Serial No. 224,531,

17, This inventiona-relates -to a unitized *hermet icaliy sealed centrifugal refrigeration machine .6 Claims; '(Cl. (52 -1175) using :a radial-multi-stage compressor wherein v the alternate stages thereof are-stationary and the interleaving'stages' 'revolve-withthe shell or unitizedcasing of the machine.

The stationarypompression stagescomposed of Q vanes or bucketsrare formed on a disc 'journaled within' tliecasing-coincident with its axis of rotation: One segment of this disc is weightedto oppose its rotation as induced by the work of compression. 1

Usingtrichlorethylene, gCzHGlz; as the refrigerantuin this machine, which'requires only (4') pounds gauge pressure difference between "a temperature of -123 degi; Frin the-sumpand 20 deg. F. in the -vaporiz'edto obtain achange of state, the casing-of this machine of approximately sixteen (16) inchesin diameter and directly connected to a standard 1725 R. P. M. motor requires a counterweight in the disc, including an adequate margin of weight, totaling about fifteen (15) pounds ltoxmaintain it stationary, the compressor displacing i'cubicgrfeetirof itrichlorethylene :gas perxminuteio. give .s-atrefrigerating :effect of approximatelyfifidpounds ofmeltingice equivalent of; refrigeration per. 24 hours.

'I'hehermeticaheasing oi: thistinvention may be.

formedrlikei'atdumbbellt one end thereof cooperatingfino; formlthe multi stage radial centrifugal compressor,;: while the othernenlarged end forms the vaporizing chamber; In;the compressor end,

means; are provided .1 to; enhance angular .yelocity a of the gaseous refrigerant-,whiie in the vaporizing end; meansizareiprcvided xto' minimize or destroy angularurvelocityeso lithe gaseous refrigerant :in I

order toxohtainiraliquefaction in the compressor envelopewith'out creatingsufii'cient angular acceleration of 'thergases in the vaporizing portion ofithe :envelopebr -in other Words; a centrifugal field sufiicient to, militate against-g me liquid refrigerants vaporization therein. at desirable low vaporizing temperatures.

(3) A centrifugal compressor completely. en.-

closed within a hermetical revolving envelope wherein alternate stages of centrifugal compression are produced by stationary buckets secured l to and supported by an internally-positioned BC? centrically-weighted element gjournaledn coinci:

dent with the axis of jrotationof. the. rev lv ng.

envelope (4') Stationary duct means within .a rotating centrifugal compression refrigerating machine to continuously return the liquid refrigerant accumulating by its condensation within the periphery of the rotating "hermetically-sealed centrifugal compressor casing and conveying such; liquid;

refrigerant diametrically towards the axis of roe tation and then conveyingit axially into an ,expansion nozzlein-the unitary revolving vapor,

izing chamber;

(5) A. silent low 'unitized centrifugal refrigerating system hermeticallyk-contfii lfid in a H revolving envelope. 1

(6) A low-cost refrigeratingsystem ofthe type (7) Other objects are "implicit in the subse: quent drawings and specifications.

Referring to the drawings Figure -1 is aside elevation partially in section of myinventiom Figure 2 is er section taken along, line 2+2 in Figure 1.

Figure 3 is a -m0dificati0n-of Figure 1.

Figure 4is asectiontaken-throughline 5--5' in Figure 3:

Referring to the drawings; similar; numerals refer to similar parts:-

Numerals la,---Ib-and *Ic comprise the casing or hermetical shell of the unit-ized refrigerating machine. The portionIa enclosesthe multi-stage centrifugal compressor composed of moving blade series I3, I4 and Band stationary'blade series II and I2: Portion Ib formsthe connecting gas duct between portions Ia and* lcand 1 contains a Graphitar self-lubricating'sleeve I I- which forms the bearing for stationary sleeve I 6 connected to disc S-on which the stationaryseries of blades I l and I2 are secured as wellas supporting counterweight "23 and tube 1 B through the "medium of disc 6. Portion I0 is the vaporizing chamb-erinto which stationary tube- It and its extension I 8a convey liquid refrigerant from-sump -9 in portion 4 I a through'capillary expansion valve I 9 discharg ing liquid refrigeranti 9a therein. The shellportions la, lb and lo are sustained through axial support member i to the shaft 3 of electric motor 2. Motor 2 is suitably mounted on pedestal 5.

In the portion la of the hermetical shell, three radial series of moving buckets or vanes are shown, respectively l3, l4 and l5, which are secured to and revolve with shell la. Interposed between these buckets, see Figure 2, are the two stationary series of vanes or buckets I! and I2, forming thereby a multi-stage radial centrifugal compressor wherein the gas is accelerated by the first radial series of vanes l3, causing a gaseous induction from vaporizer portion lc through portion lb, and the gas then contacts the stationary vanes I l, whereby it is deflected and its angular velocity partially converted into pressure and so on through the complete series of moving and stationary buckets. All of these radially-formed buckets are shown in Figure 2 as having a straight radial geometry but these buckets may have suitably curved gas inlet and discharge edges as is well known in the multi-stage compressor art.

Turning to Figure 1, the stationary disc 6 journaled by sleeve It on bearing ll supports the counterweight 23 seen in Figures 1 and 2. In Figure 2 it is shown at 23 together with pipe l8 in a position as they would normally assume when the machine is not operating and at 2311 and [8a respectively in a position displaced by the torque generated by the work of compression and friction when the shell la, lb and lo are in rotation. In this operative position the liquefied refrigerant 36, see Figure 1, partially collects in the annular sump 9 formed by the circumferentially extended portion l of disc 6 and by the annular lip 8. The gaseous refrigerant as it is compressed in the compressor to its critical change-of-state pressure, which is dictated by the mean temperature of the aerated and cooled shell la, in its rotation deposits liquid refrigerant also on the inner peripherial surface of shell la as shown by numeral 31. Means are provided by scoop element II) which is attached to the stationary rim 1 of disc 6 to deflect any predetermined residual volume of this liquefied refrigerant from the inner peripherial surface of la and discharges it through orifice 24 into annular sump 9 to make it available for transfer through pipe l8 which enters into stationary annular sump 9, whereby the liquid refrigerant is conveyed through pipe l8 to the approximate axial center of the machine and enters expansion valve l3 and is thereby discharged at Illa into vaporizing chamber 22 by virtue of the pressure head existing between the comparative low pressure existing in vaporizing chamber 22 due to its evacuation by the suction of the multi-stage compressor in portion la through the open duct portionlb as compared with the pressure existant in annular stationary sump 9, which is approximately a pressure differential of four pounds gauge.

'It is to be noted that the comparatively long Graphitar self-lubricating bearing l'l forms a seal between the space 38 in la and the vaporizer space 22, but its sealing factor is largely effected by the annular bushing 50, see Figure 2, secured to sleeve it, which forms a seal against the edge of graphite sleeve l! by virtue of the pressure difference exerted axially on sleeve l6 between chamber 38 and vaporizing chamber 22.

Suitable ducts such as 25, 26, 27, 28 and 29 may surround the shell la, lb and lo to define and direct the cold or heated air streams passing therethrough due to the windage caused by the 4 geometry of said revolving shell. Struts 28 in sub-atmospheric vaporizing chamber 22 serve to prevent distortion of the walls of portion lc due to atmospheric pressure.

In Figures 3 and 4 a slight modification is shown of the invention as disclosed in Figures 1 and 2. In Figures 1 and 2 the pendulous counterweight 23 is shown in the compressor portion la in order to locate this weight as close to the shell-supporting bearings of motor 2 whereas in Figures 3 and 4 bearings are provided at both ends of shell portions la, lb and lo, as is seen by pedestals .33 and 3| and outboard shaft 33 secured to portion I0 and journaled in bearing 34 on pedestal 3l.

By the'positioning of the counterweight 35 in Figure 4 in vaporizing chamber 22, it is possible to rotate the entire shell la, lb and In at a higher R. P. M. to reduce the diameter of the machine for a given necessary compression ratio between chambers 38 and 22 due to the deaccelerative action of the stationary surface of counterweight 35 opposing angular velocity of the gases entrained by the higher rotation of chamber 22, see arrows 39 in vaporizer 22, Figure 4, which permits attaining low temperatures in the vaporizing chamber 22 by minimizing the centrifugal effect of the entrained gas therein and permitting an effective change-of-state of the liquid refrigerant at a lower pressure therein and hence lower temperature than would otherwise occur.

Due to the counter-flow occurring in portion lb, that is, the relatively cold gases leaving the vaporizing chamber 22 by the induction of the suction of the multi-stage compressor in portion la and the countercurrent of the liquid refrigerant l9a flowing in pipe l8 and Ilia to expansion valve IS, an efficient heat interchange occurs therebetween. V

' Operation The operation of my invention is briefiy as follows: On energizing motor 2, shell portions la, lb and I0 are revolved by shaft 3 of motor'2 to which they are secured and supported. The bucket series l3, l4 and. I5 rotate with shell portion la, to which'they are secured, while the bucket series ll and I2 remain stationary due to their securance to disc element 6, which is pendulously counterweighted by weight 23 and journaled on Graphitar bearing ll formed 00- incident with the axis of rotation of shell la, lb and lo. In this manner, the respective series of movingand stationary buckets form a multistage compressor which achieves the required pressure differential to liquefy the gaseous refrigerant at relatively'low R. P. M. in respect to the diameter of shell portion la. As the refrigerants gas is liquefied near the outer periphery of shell 1a, which is effectively air-cooled by its rotation, the liquid refrigerant is deposited partially in the stationary circumferential sump 9 and partially on the interior surface of shell portion la about its inner periphery. As this liquid refrigerant accumulates to a predetermined amount scoop lll secured through the wall I of sump 9 formed about the outer periphery of stationary disc 6 lifts the liquid refrigerant into sump 9 through the raised lipped orifice 24, see Figure 2, and fills the lower segment of the sta tionary sump 9. A stationary pipe' I!) secured to disc 6 and in open connection to the floor of sump 9 in this lower segment of sump 9, conveys the liquid refrigerant under the pressure head 7" celeration of the vaporized gases therein induced by the skin friction of said revolving shell of said third portion.

6. A centrifugal compression refrigeration machine comprising a symmetrical hermetical shell, a refrigerant in said shell, journal means on which to rotate said shell about its axis of symmetry, motor-actuated means to rotate said shell, said shell divided into three portions, the first portion containing a moving stage of buckets secured to said shell to generate acceleration of the gas of said refrigerant, the third portion containing expansion means to gasify said liquid refrigerant and gaseous deceleration means whereby to offset the centrifugal field generated by the frictional contact of said gaseous refrigerant with the interior thereof, the second portion forming a communicating passagebetween the axes of said first and said third portions, an element in said first portion journalled in said second portion and maintained stationary 8 by a pendulous weight, said stationary element sustaining a stage of buckets cooperating with said moving stage of buckets in said first portion to compress the gas of said refrigerant whereby to cause its liquefaction, and collection and conveyance means sustained by said stationary element to collect and convey the refrigerant liquefied in said first portion through said second portion into said expansion means in said third portion.

NATHANIEL B. WALES.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,315,282 Carpenter Sept, 9, 1919 Brockway s Feb.. 9, 1932

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