US1997061A - Rotary hydraulic machine - Google Patents

Description

April 1935. A. HOLLANDER 1,997,061

ROTARY HYDRAULIC MACHINE Original Filed Jan. 20, 1933 4 she t -sh t 1 April 9 1935.

HOLLANDER ROTARY HYDRAULIC MACHINE Original Filed Jan. 20, 1935 4 Sheets-Sheet 2 Inventor April 9, 1935. HOLLANDER I 1,997,061

ROTARY HYDRAULIC MACHINE Original Filed Jan. 20, 1933 4 Sheets- -Sheet 3 Jltorney April 9,. 19354 A. HOLLANDER ROTARY HYDRAULIC MACHINE Original: Filed Jan. 20, 1953 4 Sheets-Sheet 4 lnventar Patented Apr. 9, 1935' 1 u I 1,997,061

I UNITED STATES PATENT-OFFICE 'Aladar Hollander, Berkeley, Calif.

Original application January 20, 1933, Serial No.

652,676. Divided and this application November 6,1933, Serial No. 696,781

. 3 Claims. (01. 10396) This application is a division of my copend- Other objects and advantages of the invention ing application Serial No. 652,676 filed January Will become app as the na e O t e ame- 20, 1933, which application issu d on November is more fully understood from the'following de- 10, 1934, as Patent No. 1,979,622. scriptionand accompanying drawings wherein is 5 This invention relates to a rotary hydraulic Set forth what is now considered to be a preferred 5 machine, commonly referred t as t bulence embodiment. It should be understood, however, pump, Capable of pumping relatively small quanthat this particular embodiment of the invention tities of fluid to relatively high pressures. is chosenpri ip l r e p p x p It is an object of thi inventi to provide a, flcation, and that slight variation therefrom in turbulence pump with a rotary outer casing or minor details of construction or arrangement of. 10 rotor having a fluid channel, a-stationary. inner parts may acc d y be effected, d y casing arranged to form a closure for the fluid ainw t e sp Scope h channeLa piston member carried by the stationtion as the same is set forth in the appended ary inner casing and positioned to operatively Claims. v

project into the fluid channel, and for providing n the draw g 16 the inner casing with appropriate fluid inlet and V Figure 1 illustrates a sectional view taken .suboutlet passages communicating with the channel a in e p ane o line Fig. 01 and separated by the piston member. a single stag double p n turbulence pu p,

. A further object is to provide the fluid channel in which the pistons'remain stationary.

20 with a'plurality of blades so as to create, what Figure 2 illustrates a sectional view taken sub- 20 may be conveniently termed, a relatively rough stantially in the plane of line 2+2 of Fig. 1. i v or fluid-retarding surface for materially increas- Figure 3 illustrates on enlarged scale a fraging the resistance to the flow offluid therearound mental cross-sectional view illustrating a modiin the plane of the channel'but which will act fled form of fluid channel. 7

5 to c t wi l in th y fluid di ti b- Figure 4 illustrates a sectional view takensubstantially normal to the circular path of the stantially in the plane of line 44 of Fig. 5, of a piston member. two-stage turbulence pump in which each rotor A further object is to arrange the fluid-retardis provided with a single piston. ing surface so as to form an operative fluid seal Figure 5 illustrates a sectional View taken sub I with the piston member. stantially in the plane of line 5--5 of Fig. 4. 80

A further object is to provide the stationary As will be appreciated from a study of the inner casing with bearing means for operatively drawings, the rotary hydraulic machine of this supporting the rotary outer casing and a stuffing invention is advantageously adaptable for many box means operatively associated with the inner purposes and uses. ;In each, the rotary hydraulic and outer casings. machine operates due to the friction or drag cre- 35 A further object'is to'provide the inner casing ated between solid surfaces andifluids, and by. with two diametrically opposed piston members causing a relative movement between the'retarded. for effectively balancing the unbalanced forces fluid and a piston member. generated within the machine. In order to create a maximum friction or drag 40 A further object is to provide this turbulence between the fluid and solid surfaces, the fluid pump with two stages and to position the single may be confined in an annular channel having piston member of each stage at 180 apart so as an annular opening toward the central axis of to effectively counterbalance the bending effect thechannel, and. the three walls thereof roughcaused by the unbalanced pressures of each stage. ened or provided with projecting fluid-retarding 5' A further object is to provide a plurality of blades This fluid friction surface may be con- 5 pumping stages and to angularly position the veniently referred to as the rough or retarding piston member of each stage with relation to the surface. The annular opening of the channel piston members of the other stages so as to efiecmay be effectively sealed by a piston-carrying tively counterbalance the bending effect caused member, and the surface of this member which by the unbalanced pressures of each stage. v acts as the closing surface of the channel, may 0 A further object is to arrange the fluid-retardbe referred to as the smooth surface. The roughing vanes or blades in angular relation to the and smooth surfaces are arranged for relative. axial plane of the pump. movement, and as the smooth surface acts to A further objectis to provide axial inlet and counteract the frictionaleifect of thorough suroutlet passages. face upon the fluid, it is important that the ex-'- 55 to rotor l0,.but as illustrated in Figuresl and 2, the

posed area of the smooth surface be reduced to as small an area as is possible. The piston carried by the member projects into the fiuidchan nel and forms With the rough surface an opera- .tive fluid seal, that is, during the relative move- 'ment between the piston and rough surface, the

piston so closely fits the contour ofthe rough surface that an effective fiuid seal is formed between the piston and rough surface, so that leakage communicate with the fluidchannel at'the sucpastthe piston is practically eliminated. An appropriate fluid inlet passage may be formed the piston-carrying, member, and arranged to tion end of the: piston, and an appropriate fluid outlet passage may be formed in the piston-carrying'member and arranged to communicate with and finally forced out of the discharge passage due to .the relative motion between the piston and the rough;surface.; r

The invention may take the form of a turbulencepump in which the outer casing may be the rotating member, while the inner piston-cari y ing casingmay be the stationary member. This form of -,the invention is illustrated in Figs. 1 and-2.

1 1 The term turbulence may be used to conven iently' distinguish this form of pumpfroma centrifugal or turbine pump.

' and may include a frame I having centralbores The turbulence pump illustrated in Figs. 1 and 2, may be of the single impeller double piston type,

land 3 of slightly different diameters, for receiving and supporting the hub 4 of the stationary inner casing 5. The outer end of bore 2 may closed by the end plate Gsuitably fastened to the frameby means of bolts 1, and the inner :casing hub 4 may be clamped to the endplate as by means "of the stud 8 andnut 9. An outer casing l0, which in this case forms the rotor of .the machine, may be journalled upon the inner casing hub 4, and maybe providedwith a removable driving flange ll suitably retained in operative position by means of a nut l2 screw- 7 threaded into gthe rotor and the locking screw i3.

A'fluid channel 14 may be formed directly in the 7 channel l4 may be preferably'formed in an auxiliary ring member l5, which in turn may be suitably mounted in the rotor as by clamping the:

channel ring between the rotor 10 and the driv- 'ing flange 'l l-. A set screw l6 may beprovided for locking the channel ring against rotation.

The walls of channel l4 may be roughenedin any suitable way, as by providing a plurality of equally spaced blades I1. The blades I! may be cast integral with the channel ring or the. channel ring-may be slotted and the blades inserted. The blades l1 may be arranged to leave the center portion [8 of the fluid channel unobstructed, in order to permit the pistons I!) to travel therein. The pistons !9 may be of such size as to. closely fit the ends of. the blades I! in the center portion [8 of the channel, so as to form therewith a fluid seal, but not so close as to interfere with the travel offthe blades past the pistons. The pistons may be formed integral with or suitably fastened to the periphery of the inner casing 5, as by means of rivets 20. The periphery 2| of the inner casing nicely flts the inner diameter of the channel ring inorder to form therewith an operative fluid seal, but does not interfere with the free rotation of the rotor. Also to assist in the sealing of the fluid channel, the rotor may be made to closely fit, and thereby form a fluid seal, with each side V of the inner casing adjacent the periphery there of, as at 22 and 23. The peripheral surface of 'fore, to provide amaximum of rough surface area and a minimum of smooth surface area,

which is accomplished by forming the fluid channel entirely withinthe rotor, and providing the walls of the channel withthe rough surface, and byclosing the channel with, the smooth sur- The function of the rough the inner casing Which forms the closing wall for face 24 of the inner casing; The shape of the fluid channel,- in cross-section, maybe of any desired form, as for example, the channel may be rectangular as illustrated in Figures land 2, or it may be oval, or roundas illustrated in Figure 3.

trated in Figures 1 and 2, the depth of the chan nel may be considerably greater than itswidth,

whereby a relatively large, rough surface area is obtainable, while the surface area of the smooth closing wall of the channel will be relatively small,

thus the surface area of the rough surfacewill greatly exceed the surfacearea of the smooth surface.

Fluid may be fedinto'the fluid channel'adja;

cent the suction or inlet side of the pistons, by any suitable port or passage. means, as for example, the inner casing hub may be provided with bore 25 communicating at one end with an inlet passage- 26 formed in the frame I, while the 5;, V

opposite'end of bore 25 may communicate with a pair of opposed inlet passages 21 extending through the inner casing, and each having a port opening through the periphery thereof so as to communicate with thefluid channel at a point adjacent the, suction end of their pistons.

respective The fluid may be discharged through any. suitable port or passage means, as for example, a pair of opposed discharge passages 28 may each com:-

municate at oneend with the fiuidchannel at the discharge end of their respective pistons, while the opposite ends of the opposed discharge passages may communicate withlan annular pas-v sage 29 formed inthe hub 4 ofthe inner casing, which passage in turn may communicate with the frame discharge passage 30. s 1

Any suitable form of stufling box means 3 I ma be provided'for sealing the bearing end of the rotor against fluid leakage; While the driving disc l l ofthe rotor may be suitably connectedto a driving m'eans'as for exampla the driving disc Il may be provided with a boss 32' having a ta pered bore 33 in'which a driving shaft 34 may be secured as by means of the threaded end of the shaft and the nut 35 and locked against slippage v by means of key 36. The; drive shaft 34'may be driven by an electric motor or other suitable means not shown, and may be supported adjaiii! In the rectangular form of channel illuscent the rotor in a suitable bearing, 31 carried by a subframe 38, only partially shown.

As may be observed from Figure 2, the suction and discharge ends of pistons l9 may be appropriately shaped as at 3.9, to facilitate a'srnooth entrance and discharge of the fluid being pumped, and. in some instances, it may be desirable to extend or overlap the inletor outlet passages with the end39 of the pistons. The inner casing may be provided with a single piston i9 having appropriate inlet and outlet passages, in which case the pump would operate to deliver substantially one-half the volume or" fluid,,but at twice the pressure. However, such an arrangementproduces a very undesirable bending 'moment between the rotor and inner casing, caused by the unbalanced pressures createdin the fluid channel. This unbalanced condition of fluid pressure iscreated by the rotation of the rotor, whereby the fluid received at the suction end ofthe piston is gradually increased in pressure until the fluid is discharged from the discharge end of the piston. Thus the fluid pressure at the suction end of the piston may be, for the purpose of.illus- I tration, at pressure, while at the discharge end of the piston, at a pressure of 100 lbs. per square inch, and therefore, at a point midway between the suction and discharge passages the fluid pressure may be 50 lbs. per square inch. The average fluid pressure from the suction end of the piston to the mid point may be. 25 lbs. per square-inch, while the average pressure from the mid point to the discharge end of the piston, may be- '75 lbs. per square inch, or a pressure difference of 50 lbs.

. per square inch in favor ofthe section from the resulting in undue wear, binding, and besides charge passage.

makes it practically impossible to maintain the stufling box in condition to effectively seal the rotor against leakage. By the opposed piston arrangement, the fluid pressures are counterbalanced, thus eliminating the unbalanced pressure condition where only one piston is used.-

The operation of the pump may be substantially as follows: Fluid supply and discharge pipes may be connected to the pump; the rotor set in motion, and due to the rough surface of the channel, the fluid contained therein willbe carried or urged toward the discharge end of the stationary piston; as the fluid moves from the suction port towarddischarge port, the rough surfaces of the channel act upon a greater and greater length of fluid, and thus create an increasing rise in the. pressure of the fluid until finally the fluid is forced out of the discharge port by the piston at its channel from thesuction passage, and the piston may be shaped to assist in directing the fluid along a streamline course as it flows from the inlet passage to the channel. 1 As will be appreciated in this form of turbulencepump, there'is. created a relative'motion between the rough surface and the fluidzon'one hand and the pistonson the other hand, whereby the pumping action is effected: i

When it is desired to pump fluids to a higher pressure than. is possible with the turbulence to obtain the desired pressure and volume output In Figure 4 is illustrated a turbulence pump similar to the pump illustrated inFigure 1, except:

ing that the pump of Figure i has been provided with two fluid channels connected inseries, or as may be conveniently expressed, a two-stage pump. The tWo-stagepump of Figure' l will deliver substantially four times the pressure of the pump of Figure l, for the same size pump operating at the same speed, because the two channels are connected in series andonlya single piston is mounted in each, thus the effective length of the'rough surface from suction to discharge, is substantially four times as vgreatasin-the case of the.

single stage pump of Figure 1, in the fluid channel I of which two opposed pistons are ,operatively mounted, thus reducingthe length of the rough surface to substantially one-half its total length.

It should be noted however, that these pumps are reversible, that is, the suction and discharge respectively, for one direction'of rotation, will be come discharge and suctionrespectlvlyrfor the opposite rotation. The pressures produced by the two opposite rotations, may be equal or different, depending upon whether the resistance of the rough surfaces are equalor differentfor theopposite directions of flow.

The parts of the two-stage pump of Figure 4, which correspond to the like parts of the :single stage pump of Figure l, have been, given the same number with the additionof the symbol a. The principal difference be'tweeen the single and twostage pumps, resides in; providing a rotor 10a having a greater width, for accommodating a channel' ring member 4i! having two fluid channels 4! and 42. be slotted as at 43, to receive the blades 44 for forming the rough surface in the channel. of the fluid channels may be operatively closed by one of the inner casings 45 and 46, so as to form a fluid seal with the channel ring. The inner casing 45 may be provided with the piston 41, while the inner casing. to may be provided with the pieton 58. The pistons may be arranged to project into their respective fluid channels and closely fit the edges of the'blades '44, so as to form therewith an operative fluid seal for effectively preventing the pressure fluid from leaking past the pistons from the high to the low pressure ends thereof.

Appropriate fluid passages may be provided for serially connecting the fluid channels, which passages rnay include the inlet or suction passage Zt-a formed in the frame member !a, to which one end of the hub bore 25-a communicates, while the other end of the hub bore may communicate with one end of the inlet passage 49,

Each end of the channel ring 40 may Each ' 10 r i inlet passage 52 may be formed in the inner caswhich'passage may extend through inner casing 4B and through the periphery thereof so as to communicate with the fluid channel 42 adjacent the suction end of piston 48. r g

A discharge passage 50 maybe formed in the inner casing 46 and may communicate the fluid channel 42' adjacent the discharge endof piston 48; with a transfer passage 5|, whichtransfer passage communicates with one end of a suction or inlet passage 52 of the inner casing 45. The

j ing 45, and extendsthrough the periphery thereof,

so as to communicate with the fluid channel, 42 adjacent the inletend of the piston 41, while the discharge passage 53 formed in the inner casing 45, may communicate the fluid channel 4| adjacent the discharge end of the piston 41 with the discharge passage 29-a, and thence to the pump outlet passage 30a formed in the pump frame member l-a.

In order to counterbalance the unbalanced forces created by the pressure difierences in each of the rotors, the pistons 41 and 48 are set 180 apart, so that the unbalanced forces created by the pressure differences of one rotor, will act tocounterbal'ance or neutralize the unbalanced forces of the other rotor.

ItWillbe readily appreciated that the pumps of this invention may be utilized as fluid turbines by connecting a-suitable source of pressurefluid gthereto. I 7 1 i It'is to be understood that the term fluid is to mean any liquid whether easy flowing or vicious"; and that the pumps, by properly proportioning the areas of the several parts, may be readily utilized for'purnping air, vapor, steam or gas: in other words, may act as a compressor.

The invention is not to be limited to the details herein set forth'forthe sake of illustration, but is'ofthe full scope of the following claims. "Iclaim: r C

1 1f. In a rotary hydraulic machine, a frame having :fluid inlet and outlet passages, astationary 'inner'casing having fluid inlet and outlet passages, a cylindrical bearing surface forming a 7 connecting member between the frame and inner casing and having fluid inlet and outlet passages communicating the related passages of said frame and casing, a rotary outer casing journaled' upon said bearing surface, a stufling box forming an operative fluid seal between the frame and outer casing, said outer casing having a fluid channel, piston means carried by the innercasing and arranged to operatively project'into the said fluid channel, said inner. casing being arranged to form an operative fluid seal for the channel and having its fluid-inlet and outlet passages communicating with the channel adjacent the opposite ends of the piston, and means for rotating the outer casing. a

2. In'a rotary hydraulic machine, a frame having fluid inlet and outlet passages, a stationary inner casing having fluid inlet and outlet passages, a cylindrical bearing surface forming a connecting member between theframe and inner casing and having fluid inlet and outlet passages communicating the related passages of said frame and casing, a rotary outer casing journaled upon" said bearing surface andhaving a fluid channel, a stufling box forming an operative fluid seal between the frame and outer casing, diametrically opposed piston means carried by the inner casing and arranged toloperatively project into the said fluid channel, said inner casing being arranged to form an operative fluid seal for the channel and having itsfluid inlet and outlet passages communicating with thechanneladj acent the related opposite ends of thepiston 'means, and means for rotating the outer'casing. A 3. In a rotary hydraulic machine, a frame havihg flllid inlet and outlet passages, a stationary to form an operative fluid seal for the channels and having its fluid inlet and outlet'passages ser? the related ends of the piston means, and means for rotating the outer casing.

ALADAR HOLLANDER.

ially communicating with the channels adjacent r

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