US2387505A - Compressor - Google Patents

Description

Oct; 23, 1945. w. FELZER ETAAL COMPRESSOR Filed Feb. 5, 1944 3 Sheets-Sheet l COMPRESSED GA S INVENTORS WILL/RM FELZER SAM W/-6RG=.

Oct. 23, 1945. w. FELZER ETAL COMPRESSOR Filed Feb. 5, 1944 INVENTORS WILL/AM FEL 25R 3 Sheets-Sheet 2 3AM -WE/NBER$ A 1 01111 I I,

""IIIIIIIIIII/ BY v W m 3* M6 Oct 23,1945. w, F LZ ETAL 2,387,505

' COMPRESSOR Filed Feb. 5, 1944 s Sheets-Sheet s 1 fig -5- 43 INVENTOR. WILL/RM FELLEA SRM WEI-E6 ma'M fl rra ENE vs Patented Oct. 23, 1945 COLIPRESSOR William Feller and Sam Weinberg, San Francisco, Calif.

Application February 5, 1944,'Serial No. 521,210

Claims. (Cl. 230-108) This invention relates to a rotary compressor.

Several objects of this invention are the provision of a simple, balanced, easily manufactured andeflicient compressor.

Another object of the invention is the provision of a compressor that is free-from objectionable overheating.

A still further object of the invention is the provision of a compressor that overcomes lubrication problems such as have heretofore been encountered in most rotary compressors.

Other objects and advantages will appear in of Fig.3.

Fig. 5 is a part-sectional, part-elevational view of a slightly different form of compressor than is shown in the preceding views.v

Fig. 6 is a sectional view taken along line 66 of Fig. 5.

Fig. 'l is a part-sectional, part-elevational view of a slightly different form of compressor than is shown in the preceding figures.

Fig. 8 is a sectional view taken along line 8-8 of Fig. 7.

Before describing the compressors of this invention in detail, it is to be understood that they are equally adapted to function as vacuum pumps,

which is the case with most compressors. a

Description of Figs. 1 to 4 In detail, the compressor illustrated in these figures comprises a face plate I (Fig. 4) having ajlat side from which an annular ring 2 prodects. This ring 2 is rigidly secured to the face plate and is flat, like an annular band, The ring I 21s formed with several radially directed openings 3 that are equally spaced from each other circumferentially of the ring. In the drawings (Fig. 3) there are three of such openings which are elongated circumferentially of the ring, and the space between each adjacent pair is of a .the specification and inthe drawings annexed hereto.

shaft ll.

length equal to the length of each opening, thereby providing an imperforate segment 4 of said ring between each such pair of openings.

On the side of face plate I opposite ring 2 is an annular chamber 5 (Fig. 4), one of the walls .of which is defined by said face-plate. The interior of this chamber communicates with the op-- posite side of the face plate by means of equally spaced, elongated, arcuately extending openings 6 (Fig. 3) that are radially outwardly of ring 2 and that are curved longitudinally to follow a circle concentric with ring 2. These openings 6 are relatively close to ring 2 and are of equal length and three in number with the space between each adjacent pair being equal to the length of each opening. The ends of each opening 6 are respectively in planes that extend radially from the axis of ring 2 and through the endsof each imperforate segment 4 that is between each adjacent pair of openings 3 in ring 2. Thus an opening 6 is just outwardly of each such imperforate segment, while the face plate I is imperforate outwardly of each opening 3.

The rotor of the compressor may comprise a plurality of blades 8 that are here represented by the webs between adjacent pairs of radially extending open-ended passageways 9 formed in a circular disk III that is centrally secured on a Shaft ll may extend at one or both ends through packing boxes l2 in one or in two opposite sides of a closed housing 13, and rods I or any other suitable means may be secured to the marginal portion of face plate I for support+ ing the face plate rigid within said housing and in the desired position relative to the rotor. The passageways Q'ma'y becylindrical or rectangular and are equally spaced from each other in an annular row concentric with the central axis of the disk l0 and "ring 2. i

The disk I0 is formed with an annular, laterally opening recess l5 that extends across the passageways 9. The ring 2 is adapted to slidably fit in said recess when the ring and recess are coaxial, and the openings 3 are arranged so as to register with a plurality of said passageways when the ring is in said recess and the face plate is in sliding engagement with one flat side of disk In (Fig. 4). In the drawings (Fig. 2), it will be' seen that three of the passageways 9 may at one time be in full registration with each of the openings 3 while the imperforate segments 4 *extend across the three openings between each set of three that are in such registration. v

For convenience and for clarity the numerals 8 will be used to refer to theso-called blades or webs between the portions of passageways 9 that are outwardly of ring 2, and these blades 'will be termed the outer impeller. The blades are webs that are between the adjacent passageways inwardly of ring 3 are designated 18 and these will be' called the "inner impeller.

Extending over the outer open ends of the passageways 9 outwardly of the outer impeller are held stationary. The water or liquid 23 that is in the housing i3 is drawn into the compressor through central opening 26 in face plate I and then is moved outwardly under centrifugal force through passageways 9;

At posltion 30 (Fig. 2) where one of the segments 4 has just closed one of the passageways 9 to how of liquid therethrough from the inner impeller to the outer, it will be noted that said passageway is filled with the liquid. However,

. due to centrifugal force, the liquid in the outer ings are in an annular row concentric with the ring and they are adapted to register with openings 6 in face plate i and to be scanned by the imperforate portions between said openings (3 upon rotation of shaft ii and disk It.

The disk id is formed with an annular row of passageways at extending transversely therethrough, each of which communicates at one end with the passageway .9 of the inner impeller inwardly of ring 2, while the opposite end of each such passageway 2i opens outwardly of disk it. Each such passageway 28 is relatively small in diameter as compared with openings 2|] or with passageways 9.

The disk i may also be formed with an annular row of radially extending outwardly opening ducts 22 that open at their inner ends into recess it. These ducts may be alongside each passageway 9 and each web 8 of the outer impeller.

The compressor may be mounted vertically within the housing It as seen in Fig. l, or in any other desired position, such as horizontal. In whatever position the compressor is mounted the liquid 23, which may be water, oil, or other free flowing liquid, covers same, and a gas pipe or conduit 24 extends from chamber out of the liquid and housingto the atmosphere or to any desired source of gas. A check valve 25 is provided in said conduit.

The inner ends of passageways 9 in the inner impeller are in communication with the liquid 23 through an opening 26 in face plate i and preferably a plurality of equally spaced blades 27 may extend inwardly in continuation of the inner ends of some of the blades'or webs I8, these blades 21 being part of the inner impeller and extending past the edges of the opening 26 toward the shaft ii. They function to prevent swishing of the liquid and direct the same into the passageways 9 when the disk ill is rotated.

In Fig. 2 the liquid is indicated by dash lines and the gas is indicated by stipples. The solid heavy black arcuate lines indicate the segments 4 while the open spaces in continuation of and connecting said black lines indicate the openines 3.

In the compressor illustrated and described,

' there are three complete cycles from intake of gas to compression performed simultaneously. The number of passageways 9, and the number of openings 6 greatly determine the number of such cycles.

In describing the operation, Fig. 3 will be employed and only one cycle will be described, it being understood that the shaft 9 of the rotor is revolved by any desired means, such as a motor 28 (Fig. i). 4

Referring back to Fig. 2, it will be assumed that the rotor, which is disk It, is rotated clockwise. The ring 2 having openings 3 and segments 4 is impeller will be moved outwardly in the outer impeller to produce a negative pressure or suction adjacent ring 2. As the opening 6 is in communication with the passageway 9 of the'outer impeller at position 30 and at the next succeeding positions 3i, 32 the gas or atmospheric air, indicatech by stippling, will be drawn into the outer impeller to fill the void thus produced. In the meantime the liquid in the inner impeller at positions iii, 32, or in passageway 9 of the inner impeller will be restrained by segment 4 from following the liquid and gas in the-outer impeller, but just as soon as the passageway 9 advances beyond segment 4 this liquid in the inner impeller ispermitted to rush out following the air that is entrapped in the outer passageway 9 of the outer impeller, as indicated in positions 33, M35, the said air being compressed and ejected into the liquid 23 in housing l3 for rising into the compressed air space 36 at the,

top of the housing (Fig. 1). At positions 33, as, 35 the outer impeller is, of course, out of communication with the gas source or with'the atmosphere since the opening 6 terminates just Following position 35, the

beyond position 32. same cycle is repeated, and, as already explained, three such cycles are simultaneously carried out with each 120 movement of the rotor, or nine complete cycles are produced with each full revolution of the rotor that is herein illustrated.

. With a larger rotor a greater number of such cycles is possible.

In the foregoing description of the operation it will be apparent that the gas supply is at a higher pressure than the space or void that is produced by the liquid being thrown out of the outer impeller by the centrifugal force, and normally such higher pressure is normal pressure or atmospheric pressure so that the gas will flow into said space and there is a negative or less than atmospheric pressure in said space,

The liquid in;the inner impeller is at a greater pressure than the pressure of the liquid 23 in the housing due to centrifugal force imparted theret by rotation of the rotor. Inasmuch as the gas drawn into the outer impeller is at a lower pressure-than the pressure on the liquid in the housing and in the inner impeller, as soon as the liquid in the inner impeller is released the gas is compressed by equilization of pressures.

The centrifugal force that is imparted to the liquid in the rotor is determined by the R. P. M. thereof, the size ofthe rotor and the densityand viscosity of the liquid. The guide vanes 69 are, of course, important for converting the velocity of the liquid discharged-into pressure energy.

In order to prevent any possible objectionable leakage of water or liquid past ring 2 and into the outer impeller during the time when the segments e interrupt theflow of liquid through passageways a, we provide the passageways 22, which passageways open at their inner ends into recess is at points between the outer edge of ring 2 and the passageways 9. Thus any liquid 'erable time.

' trally apertured for passage of such gas.

' peller will flow out of the passageways 22 before reaching the passageways 9 that are'in the outer impeller.

Inasmuch as compression takes place between the liquid bodies in the outer impeller, one v of which bodies is in communication with the liquid 23 in housing l3, it will be seen that heat transmitted to said liquid is immediately dissipated in the large body of liquid in said housing, since the liquid in the outer impeller of the compressor is discharged into said housing and may not be re circulated through the compressorfor a consid- Thus isothermal compression is effected.

Inasmuch asthe-degree of compression of the gas supply in housing I3 is dependent upon the capacity of the rotor to draw gas into the outer impeller, and which latter capacity is dependent noon the centrifugal force being adequate to overcome the pressure of the liquid in housing I3, it will be seen that the work stroke of the compressor is the suction stroke and not the compression stroke.

As to lubrication, which is a serious problem in the usual sliding-vane-type compressors, no such problem is here presented, since water itself if used as the liquid 23 is a suflicient lubricant, orv

oil may be used'as the liquidif desired.

, The rotor constitutes the only moving part of the compressor and this may be fabricated in one or several pieces and face plate I, ring 2, and the walls of chamber may be made in one or several pieces if desired. In the drawings the several parts of the compressor, such as those above mentioned, are shown as being integralwhere they plate 4| is disk 44 of the rotor, which disk is centrally secured on shaft 45 for rotation, the latter being connected with any suitable source of power for causing such rotation.

The face plate 48 carries the ring 2 which is identical in every respect with the ring 2 of Figs. 1 to 4, having openings 3 therein with imperforate segments 4 therebetween (Fig. 5).

rupt the flow of liquid in passageways 8, I provide openings 2| as described, that will relieve such hammer, which ports relieve the sudden shock by venting 'into the main body of liquid in the housing.

Description of Figs. 5 and 6 The main difference between the compressor illustrated in these figures and the Preceding ones is that in the present instance there is no centrifugal force exerted on the liquid forcing it into the outer impeller. The movement of liquid into the outer impeller is due to the difference in pressure between the liquid in the housing I! and the gas that is admitted into the outer impeller before compression thereof.

A common feature between the compressor of Figs. 1 to 4 and the compressor of Figs. 5, 6 is the ring 2, which will bear the same number in Figs. 5, 6. 'Other features are similar although not identical.

In Figs. 5, 6 a pair-of stationary face plates 48, 4| are provided in spaced opposed relation, and a chamber 42 at the outer side of plate 40 and centrally thereof is provided for admission of gas to The inner and outer impeller of Flags. 5, 6 respectively comprise an inner annular row of equally spaced radially extending blades 48 (Fig. 5) secured to the rotor disk 44, and an outer annular row of equally spaced radially extending blades 41 also secured to disk 44. The ring 2 is disposed between the adjacent edges of the blades 46 and blades 41.

The number of blades 41 may vary, although in Fig. 5 they correspond to the number of blades or ribs 8 of Figs. 3, 4 and as the edges of their blades opposite plate 4| are in substantially sliding contact with the face plate 40. they coaot with the latter face plate and with plate 4| and with each.

other to provide radially extending passageways inner ends are at ring 2. Thus upon rotation of disk 44 the inner ends of the passageways will be intermittently opened and closed by segments 4 andopenings 3 in exactly the same manner as passageways 9 of the outer impeller in Figs. 3, 4 are opened and closed.

Both plates 40, 4| are provided with openings 49 therein that are in opposed relation and that correspond with openings 6 in Figs. 3, 4 in number and position. I

Inasmuch as the compressor of Figs. 5, 6 is to be mounted in a liquid in a closed housing in the same manner as the compressor of Fig. 1, it will be seen that as the rotor disk 44 is rotated, the liquid will be drawn through openings .49 into passageways 48 for ejecting radially outwardly from the latter. Such admission to said passageways is only during those times when blades 41 are scanning the openings 49, and at such times the inner ends of passageways are closed.

Extending over the outer ends of passageways 48 are deflector vanes 50 that function the same as the'vanes IQ of Figs. 1 to 4.

In operation, upon rotation of disk 44 by any suitable means, the liquid in which the compressor is immersed will be thrown outwardly by centrifugal force due to revolution of the blades 41 of the outer impeller, thus creating a low pres-. sure zone adjacent ring 2 that will be filled by gas from the inner impeller at the points where the openings 3 occur. The liquid for compression of said gas will fiow into said outer impeller laterally through openings 49 as soon as the blades.

come 'to said openings, and at which time the imperforate segments 4 close the inner ends of the passageways 48 Descriptionof Figs. 7 and 8 The invention as disclosed in these illustrations differs mainly from the other forms of the invention in that the liquid may be thrown out of the outer impeller laterally instead of by centrifugal force, and also the gas may move laterally in the rotor instead of radially. This form of the invention is particularly suitable for producing a relatively large volume per minute of relatively low pressure gas, but gas at a pressure above normal.

The same interrupter ring 2 with openings 3 preceding forms.

. and imperforate segments 4 may be used as in the The ring 2 is rigid-with a face plate 60, said plate being formed with openings 6| therein that correspond with openings 6 or 48, and an annular chamber 62 having a. gas line 63 in communication therewith is provided for supplying gas to be compressed to said openings.

The rotor comprises a disk 64 that carries an annular row of angularly set blades 65 outwardly of ring 2 and positioned to scan openings Bl, said blades being of the blower type and adapted to move fluid axially of the row thereof the same as the blades of a fan. The blades'65 alsov scan the openings 3 in ring 2, and inwardly of the ring 2 are radially extending blades 66 secured to disk 64 for movement with the latter.

A central opening 68 in face plate so admits liquid to the inner impeller blades 66 for movement radially outwardly through openings 3 in ring 2 to the outer impeller.

As in the preceding views, the imperforate segments 4 between openings 3 in the ring 2 are positioned to extend the length of the openings in the face plate. Thus upon revolution of the rotor 64 tl-e liquid admitted to the inner impeller will be thrown outwardly by centrifugal force and upon interrupting this outward movement a pace of negative pressure will occur outwardly of ring the liquid confined in the inner impeller by the imperforate segments 4 will be released to follow the air, upon which an equilization of pressure in the gas relative to the liquid will occur and the compressed air will be released in housing I3, or the like, for building up the gas pressure therein.

Instead of the deflecting vanes previously used, we provide stationary, radially extending blades 10 for slowing down the velocity of the fluid ejected from the rotor and for removing the whirl velocity component so as to straighten out the flow.

It is obvious, of course, that the gas could be admitted to the inner impeller and the liquid to the outer impeller, although in such an instance it might be desirable to provide inlet guide blades like blades 10 at the side of the face plate as well as-at their present positions.

Comparison of all forms of invention illustrated A comparison between all forms of the invention herein described and illustrated will show a common principle of utilizing two fluids of different densities, one of which is compressed between bodies of the other and then released under pressure for storage or use. In all forms of the inventiong there is an alternate admission of fluid of different pressures from separate paths into a single path in alternate relationship in the latter path wherein equalization of pressures occur. Also in all forms of the invention dynamic pressure in a liquid as well as the static pressure thereof is transmitted to successive charges of gas in said liquid for gradually building up the pressure in accumulated charges of such gas.

Other similarities than those mentioned herein will be obvious.

The invention as illustrated in Figs. 1 to 4 is particularly suitable for high pressures, and in all forms of the invention it is obvious that a plurality of compressors can be used on a single drive shaft, and also single units having several rotors for compressing gas in several stages can be employed. The invention as herein illustrated and described is intended to be merely illustrative of the invention, and not restrictive thereof.

Having described our invention, we claim:

1. A compressor of the character described comprising a closed housing containing abody of liquid and a space for gas under pressure, an annular row of impeller blades immersed in said body of liquid and supported for revolving about the central axis of said row, means so supporting said row of blades, a plurality of spaced inlets for admitting liquid in said housing to the blades of said row at spaced points for propulsion by said blades upon such revolution of said blades, means obstructing the admission of such liquid to said blades between said spaced points, means for admitting gas to said blades between said spaced points only, and said impeller blades being exposed to discharging liquid admitted thereto into said housing at all points during revolution of said blades about said axis, aplurality of deflector vanes positioned in the path of the liquid adapted to be discharged by said impeller blades for converting the velocity of the discharged liquid into pressure head, one of the ends of each of said vanes being closely adjacent said blades and said vanes extending from said ends progressively increased distances outwardly of said blades in the direction of travel of the latter.

2. A compressor of the character described comprising a closed housing containing a liquid and a space for gas under pressure, an inner annular row of impeller blades immersed in saidliquid and supported for revolving about the central axis of said row, said blades being arranged radially about said axis with their inner ends communicating with said liquid for moving said spaced openings for said discharge of such liquid therethrough, an outer annular row of radially arranged impeller blades concentric with said inner row and around the outer side of said ring, means supporting the blades of said inner row and outer row for simultaneous rotation in the same-direction about their common axis, means for admitting gas into the annular path of movement of the outer row of blades at points where said interrupter ring closes the inner row of blades to said discharge, said blades of said outer row being open to discharge into said housing at their outer ends, and means extending over'the outer ends of the blades of said outer row and spaced therefrom for reducing the velocity of liquid discharged from said outer row, said means being deflector vanes, and one of the ends of each of said vanes being closely adjacent the outer ends of said blades and said vanes extending from their said ends progressively increased distances outwardly of said blades in the direction of travel of the latter.

3. A compressor of the character described comfor admitting a gas at normal pressure into said part behind said remainder during said rotation of said rotor, and means for simultaneously releasing the said interrupted portion and causing the same to i'ollow said remainder and stopping said admission of gas to behind said portion, said means for interrupting said portion and for releasing the portion so interrupted comprising a ring formed withimperiorate segments and openly of said rotor from one of their ends respec I tively.

4. A gas compressor of the character described comprising a closed housing containing a body of liquid and enclosing a space over said body for gas under pressure, a rotor wholly immersed insaid body of liquid, said rotor comprising a pair of concentrically arranged annular coplanar rows or radially extending impeller blades providing an inner and an outer row thereof, means supporting said rows of blades for rotation together in the same direction about their common axis. a central inlet for admitting the liquid of said body to the inner row of impeller blades for outward movement of said liquid by centrifugal force upon said rotation'ot said rotor, equally spaced imperforate stationary segments of a ring positioned between said rows of blades for interrupting said movement of said'llquid from said inner,

row of blades to said outer row of blades, means for admitting gas from outside said housing into the path of travel of said outer-blades adjacent said segments and for their full lengths, said outer into said body,

blades terminating in said body or liquid for ejection of the liquid and and deflectors respectively extend= ing progressively outwardly of the said outer row of blades and over the outer ends thereof for re ducing the velocity of the said liquid ejected from said outer row. v

5. A compressor of the character described comprising an annular inner row and an annular outer row of radially disposed impeller blades,

' said rows of blades being coplanar and concentrio, and means supporting said blades for movement together about their common axis, a housing enclosing said blades formed. with a central inlet for admitting fluid to the inner ends of the blades oi said inner row, a stationary interrupter ring positioned between said rows formed with alternate perforate and mperforate sections for opening and closing communication between the said rows of blades periodically as said blades are revolved, openings formed in said housing for permitting continuous circulation of fluid through the inner impeller blades at all times independently of said ring, and means for admitting fluid diiferent than that adapted to be admitted to said inner row tothe inner ends of the impeller of said outer row at said points where the imperforate'sections oisaid ring'extend between said rows, and the outer ends of the blades of said outer row being open to discharge of fluid outwardly thereof at all times.

FELZER. SAM WEINBRG.

gas between them directly

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