US1979622A

US1979622A - Rotary hydraulic machine

Info

Publication number: US1979622A
Application number: US652676A
Authority: US
Inventors: Hollander Aladar
Original assignee: Individual
Current assignee: Individual
Priority date: 1933-01-20
Filing date: 1933-01-20
Publication date: 1934-11-06
Anticipated expiration: 1951-11-06

Description

Nov. 6, 1934. A. HOLLANDER ROTARY HYDRAULIC MACHINE Filed Jan. 20, 1953 5 Sheets-Sheet l w? E f/ I k m .r/ a V m a H a J R I: v :5: 1 E G Nov. 6, 1 934. A. HOLLANDER 1;979,622

ROTARY HYDRAULIC MACHINE Filed Jan. 20, 1955 5 Sheets-Sheet 2 Nov. 6, 1934.

A. HOLLANDER ROTARY HYDRAULIC MACHINE Filed Jan. 20. 1933 5 Sheets-Sheet 3 Nov. 6,. 1934. A, HOLLANDER ROTARY HYDRAULIC MACHINE 5 Sheets-Sheet 4 Filed Jan. 20, 1933 .1'ltorneya Nov. 6,1934. ALHOLLANDVER 1,979,622

ROTARY HYDRAULIC MACHINE File d Jan. 2 1933 s Sheets-Sheet 5 Patented Nov. 6,1934

UNITE l) STATES PATENTQFMQE ROTARY HYDRAULIC MACHINE Aladar Hollander, Berkeley, @aiif.

Application January 20, 1933, Serial No. 652,676 18 Claims. (ct ice-es) This invention relates to a rotary hydraulicmachine adaptable for many different uses and purposes, suchas a fluid motoror a fluid pump.

When the invention is to be utilized as a fluid pump, which, for ccnvenience,.we may call a turbulence pump to distinguish it from the usual cent trifugal type of pump, it is important to provide an annular fluid channel formed of two separate parts, one the casing and the other the rotor, and to provide the channel wallsof the casingportion with a relatively rough surface to. effectively resist the fiow of the fluid through the channel and the rotor with relatively smooth ,walls to reduce to a minimum "the driving effect upon the fluid in the channel caused by the turning of the rotor.

it is one of the objects of this invention to arrange the channel walls of the casing and rotor so that the surface area of the relatively rough walls of the casing, will be equal to, or greater than the surface area of the smooth walls of the rotor, whereby the rough surface will have a greater effect upon the fluid in the channel. In fact, it is desirable to provide the greatest possible amount of rough surface, and the least amount of movable relative thereto, and to provide a suitable system of fluid inlet passages communicating with the fluid channel adjacent one end of thepiston or pistons, and a system of fluid discharge passages communicating with the channel adjacent the other end of thepiston or pistons.

A further object is to provide the turbulence pump with a plurality of pumping stages, and to angularly position the piston member of one stage with relation to the next, to effectively counterbalance the bending effect caused by the unbalanced forces of each stage.

Other'objects and advantages of the invention will become apparent as the nature of the same is more fully understood from the following description and accompanying draw ngs, wherein is set forth what is now considered to be a preferred embodiment.- It should be understood, however, that this particular embodiment of the invention is chosen principally for the purpose of exempliflcation, and that variations therefrom in "details of construction or arrangement of parts may accordingly be effected, and yet remain within the spirit and scope of the invention as the samels set forth in the appended claims. 1

In the drawings:

Figure 1 illustrates a sectionalview, taken substantially in the plane of line 1-1 of Fig. 2, of a single stage rotary double piston turbulence pump;

Figure -2 illustrates a fragmental sectional view taken substantially in the plane of line ,2-2 of Fig. 1;

Figure 3 illustrates a sectional view of 'a twostage rotary piston turbulence pump in which each rotor is provided with a single piston;

Figure 4 illustrates a sectional view of the rotor for the two-stage rotary piston type of turbulence pump, taken substantially in the plane of line 4-4 of Fig. 6; a

Figure 5 illustrates a similar view, but taken substantially in the plane of line 5--5 of Fig. 7.

Figure 6 illustrates a sectional view taken substantially in the plane of line 6-6 of Fig. 4;

Figure 'l'illustrates a. sectional view taken sub stantially in the plane of line '7--7 of Fig. 5;

Figure 8 illustrates a sectional view of the rotor taken substantially in the plane of line 8-8 of Fig. 7; s H

Figure 9 illustrates a sectional view taken substantially in the plane of line 9-9 of Fig. 10, of a double impeller turbulence pump;

Figure 10 illustrates a sectional view taken substantially in the plane of line 10-10 of Fig. 9.

As will be appreciated from a study of the drawings, the rotary hydraulic machine of this invention is advantageously adaptable for many purposes and uses. In each, the rotary hydraulic' machine operates due to the friction or drag created between solid surfaces and fluids, and by causing a relative movement between the retarded fluid and a piston member.

In order to create a maximum friction or drag between the fluid and solid surfaces, the'fluid may be confined in an annular channel having an annular opening toward the central axis of the channel, and the three walls thereof roughened or provided with projecting fluid retarding blades. This fluid friction surface may be conveniently referred to as the rough or retarding surface. The annular opening of the channel may be eifectively sealed by a-piston carrying member, and the surface of this member which acts as the closing surface of the channel, may be referred to as the smooth surface. The rough and smooth s rfaces are arranged for relative movement, and as the smoothsurface acts to counteract the frictional effect of the rough surface upon the fluid, it is important that the exposed area of the smooth surface be reduced to as small, an area as pressure or suction end thereof.

is possible. The piston carried by. the member, projects into the fluid channel and forms with the rough surface an operative fluid seal, that is,

surface, so that leakage past the piston is practically eliminated. An appropriate fluid inlet passage may be formed in the piston carrying member, and arranged to communicate with the fluid channel at the suction end of the piston, and an appropriate fluid outlet passage may be formed in the piston carrying member and arranged to communicate with .the fluid channel at the discharge end of the piston. Thus fluid may be drawn into the fluid channel at the suction end of the piston acted upon by the rough surface to retard or resist the motion of the fluid relative to the rough surface, and finally forced out of the discharge passage due to the relative motion between the piston and the rough surface.

The turbulence pump illustrated in Figs. 1 and 2 is of the type in which the annular fluid channel with'its rough or fluid retarding surface remains stationary while the pistons carried by the rotor are driven through the retarded fluid contained in the channel, to thereby obtain the relative motion between the retarded fluid and pistons toproduce the pumping effect.

This form of turbulence pump may be referred to as the rotary piston type of turbulence pump to distinguish it from the form of turbu in that the inltpassage has considerable centrifugal pumping effect and thus assists in keeping the pump primed.

The rotary piston form of pump as illustrated in Figures 1 and 2, may include briefly: an outer casing formed of two halves 61 and 62, andhaving an open cavity 63 between the halves, for

receiving a channel ring-64 and the rotor or impeller 65. The half portions of the outer casing may be securely bolted toegther bythe cap screws 66, and to thereby firmly clamp the channel ring. 64 therebetween. The channel ring 64 may be provided with an annular fluid channel 67, and may be slotted with a plurality of slots 68 in each of which slots a friction or fluid retarding blade may be mounted.

If desired, .the edges of the retarding blades which project into the fluid channel, may be beveled to form a knife edge at their front faces, so as to present a relatively sharp sealing surface tothe rotary pistons 69. The pistons 69 closely approach but do not touch the retarding The clearance between the pistons and blades. the retarding blades should be so close as to effectively prevent fluid leaking from the high pressure end of the piston to ,the low The pistons 69 may be suitably mounted upon the rotor in opposed relation, and the rotor may form an operative seal with the channel ring, so as to effectively prevent leakage of fluid from the channel, but yet not so close as to bind dur- 'ingits rotation. The periphery 70 of the rotor,

which forms the closure for the fluid cha n l.

comprises the total smooth surface of the machine, and as the smooth surface only equals the extent of one of the narrow walls of the fluid channel, the surface area of the smooth surface is relatively small in comparison to the surface area of the rough walls, which include the three remaining walls of the fluid channel. And therefore, the driving effect of the smooth surface upon the fluid will be very little as compared to the retarding action of the far greater area of rough surface. The rotor 65 may be suitably mounted upon a driving shaft 71 as by means of the shaft flange 72, and the screws 73, and the shaft in turn may be journalled in the outer casing by means of bearing 74,-and sealed against fluid leakage by means of a standard form of stuffing box 75. Appropriate fluid inlet and discharge passages may be provided to communicate with the fluid channel adjacent the opposite ends of the pistons, as for example, the fluid inlet passage 76 may be provided in the outer casing 60, and arranged to communicate with one end of the central bore 77 of the rotor, and a suitable wearing ring 78 may be provided for forming a fluid seal between the housing passage 76 and the rotor bore 77. The other end of the rotor bore 77 may communicate with the suction passage 78 formed in and extending radially through the rotor and extending through the periphery of the rotor at diametrically opposite points so as to communicate with the fluid channel directly adjacent the suction. or inlet ends of the pistons 69. The discharge passages 79 may be formed in the rotor, and each extended through the periphery of the rotor so as to communicate with the fluid channel directly adjacent the discharge end of the pistons. The inner end of each of the discharge passages 79 communicates with the discharge ports 80 which .open into the annular bore 81 from which the fluid may discharge into the discharge passage 82 formed in the outer casing 60. A suitable wearing ring 83 may be provided to form a fluid seal between the annular rotor bore 81 and the passage 82 of the casing 60.

As may be observed from Figure 2, the suction and discharge ends of pistons 69 may be appropriately shaped to facilitate a smooth entrance discharge ofthe fluid being pumped to and from the channel, and in some instances, it may be desirable to extend the ends of the pistons to overlap the inlet and outlet passages.'

The rotor may be provided with a single pis-- ton having appropriate fluid inlet and outlet passages, in which case the pump when operating at the same speed would deliver substantially one-half the volume of fluid attwice the pressure. However, such an arrangement would produce a very undesirable bending moment in the rotor shaft due to the unbalanced pressures generated in the fluid channel acting upon the periphery of the rotor. This unbalanced state of fluid pressure is generated by the rotor acting upon the fluid in the channel, whereby the fluid received at the suction end of the rotor piston is gradually increased in pressure until it is finally discharged through the outlet passage at the discharge end of the piston at a maximum pressure. vThus the fluid pressure at the sue- I from the suction end of the piston to the mid point may be 25 pounds per square inch, while the averagepressiire' from the mid point to the dischargeL-end Bi' the piston may be pounds per square inch, or a'pressure difference of 50 pounds per square inch in favor of the section from the mid point to the discharge end of the piston; and by multiplying the exposed areaof the inner casing fromthe mid point to the discharge end of the piston by the differential pressure of 50 pounds per square inch, the resultant unbalanced force-may be ,obtained, which force acts to force the rotor and easing apart in a direction away'from the high pressure section, and this unbalanced force will cause a bending moment to be resisted by the shaft and bearings. This bending. of the rotor shaft causes undue wear, binding, and also makes it practically impossible to maintain the stufllng box in condition to effectively seal the rotor against leakage. By the opposed piston arrangement, the fluid pressures are counter-balanced, thus eliminating the unbalanced pressure condition where only one piston is used. 9 In operation, therotary piston form of turbulence pump may be provided with a suitable source of fluid supply which will travel through the inlet passages, and as the rotor revolves, will be played into the fluid channel by the inlet passages 78 at the suction end: of the pistons, whereupon the rough fluid retarding surface will act to retard the fluid while the pistons traveling at a relatively high speed will scoop up and force the retarded fluid out the discharge passages. f

Should a' higher pressure be desired from the same'diameter pump operating at the same speed,

any number of stagesmay be provided, which stages would be serially connected with the appropriate fluid passages. In Figures 3 to 8, a two-stage rotary piston turbulence pump is illustrated, which may be substantially identical with the single stage pump except that provision is made for the extra stage with its appropriate fluid passages, and that each rotor is provided.

with one piston only.

In order to counter-balance the unbalanced forces created by the pressure differences in each of the rotors, the piston of one rotor is arranged 180 degrees ahead of the other piston, whereby the full width of the channel ring and acts as the unbalanced forces developed by the pressure differences of one rotor will act to counterbalance or neutralize the unbalanced forces of the other roto'i'.

The two-stage rotary piston turbulence pump has-many parts which may be identical with the corresponding partsof the single stage rotary piston pum and therefore these parts have been given the same number with symbol a afiixed thereto. The outer casing half 61a may be made so as to provide a deeper cavity 73a, so as to accommodate the two stages. A channel ring may be mounted in the cavity 73a and may be provided. with two spaced fluid channels 86 and87, and the ring 85 may also be provided with a plurality of radial slots 88, in each of which slots a single retarding blade 89 may be mounted. Each retarding blade may be arranged to project an equal distance into each channel to form the rough friction or retarding surface thereof. The channel ring 85 may be provided with a diaphragm 90 for separating the stages. The impeller may include a first stage rotor 91 and a second stage rotor 92, and

the periphery of each rotor may be-arranged to form an operative seal with its respective fluid channel and also with the adjacent sides of the outer casing and channel ring diaphragm. A first stage piston 93 may be'suitably mounted upon the first stage rotor, while a second stage piston 94 may be suitably m unted upon the second stage rotor 92, and the pistons positioned 180 apart in order that the unbalanced forces of each rotor may be substantially I counterbalanced. Appropriate fluid passages may be provided for serially communicating the stages of the pump, as for example, the impeller bore We may at one end communicate withthe fluid inlet passage formed in the outer casing, and

a suitable wearing ring 78a may be provided for forming a fluid seal between the casing passage and the rotor bore. The opposite end of bore 77a communicates with the first stage suction or inlet passage 95, which passage is formed in the flrst stage rotor and extends through the periphery thereof to communicate with the fluid channel adjacent the suction end of the flrst stage piston 93. The discharge passage 96 is likewise formed in the first stage rotor, and at its outer end extends through the periphery thereof to communicate with the fluid channel adjacent the discharge ,end of the flrst stage piston 93, while the discharge passage at its inner end communicates, with transfer passage 97. The transfer passage 97 in turn communicates with the inlet or suction assage 98 formed in and extending through second-stage impeller 92 to communicate with the second-stage fluid channel adjacent the suction end of the second stage piston 94. second-stage discharge passage 99 may be formed in the second-stage rotor, and arranged to extend through the periphery thereof-to communicate with thesecond-stage fluid channel adjacent the discharge end of the second-stage piston 94, and to communicate with the annular discharge port 100 from which the fluid passes into the discharge passage82a formed in the outer casing from which the pressure fluid may be conveniently taken. A wearing ring 83a may be provided to form a fluicr'seal betweenthe secondhe periphery of the stage annular discharge port and the discharge passage of the outer casing. Y

It may be well to note that in this two-stage pump, that each retarding blade extends across the rough surface for the channels, and also that the channel ring is provided with a diaphragm which assists in sealing off interstage leakage. It should be appreciated that the chan- Thenel rings for each of the pumps described may rotors. I

In some instances, it may be desirable to arrange a double rotor turbulence pump in parallel be formed of two halves split on a radial plane 7 to enable the channel rings to be placed over the same speeds. The double rotor turbulence pump arranged im parallel, may be of the stationary or movable piston types, but as the movable' piston type is the more simple, it has been chosenfor illustration in Figures9 and 10. The double 7 rotor turbulence pump of the rotary pistorr type as illustrated in Figures 9 and l0,-may include" briefly, two outer casings 101 and 102 suitably fastened together as by-bolts 103, and each casing may be provided with a

rotor cavity

104 and 105. A channel ring 106 having two spaced fluid channels 107 and .108, maybe mountedin the cavities104 and 105, and each channel may be provided with a suitable fluid retarding means such as the blades 109.

A pair of back-to-hack rotors 110 and .111 may be operatively mounted in the rotor cavities by means of the drive shaft 112, which shaft may besupported in suitable bearings 113 exterior of the pump casings, and a suitable stufling box 114 may be provided in each'casing where the shaft 112 passes the'rethrough, so as to seal the shaft against fluid leakage. The periphery of each rotor may form a fluid seal with its respective fluid channel, and each may be provided with a piston arranged to project into/its respective fluid channel and therein to closely fit the rough surface thereof, so as to form an operative fluid seal for preventing undue leakage of the fluid from the pressure end to the suction end of each piston, It is. important to counter-balance the unbalanced pressure forces developed in each rotor, and therefore the piston of one rotor may be located at 180 from the piston of the other rotor. L

An important advantage resulting from the back-to-back arrangement of the rotors is the balancing of the axial thrust or forces created by the suction and discharge pressures acting upon the rotors and shaft. As the inlet and discharge passages are identical for each rotor, these passages will be described for, only one of the rotors, namely, rotor 110 operating in casing 101'.

A-suction or inlet passage 115 may be provided in casing 101 and arranged to communicate with the bore 116 of the rotor 110. A wearing ring 117 may be provided to form an operative fluid seal between the.casing and rotor at the junction of passage 115 and bore 116. An inlet passage 118 may be formed in and extending through the periphery of the rotor, and may communicate at its inner end with bore 116 while at its opposite end it may communicate with the fluid channel 107 adjacent the suction end of the piston.

fhe discharge passage will be described in connection with rotor 111, and casing 102, wherein it shows more clearly. The discharge passage 119 may be formed in the rotor 111 and may'at' one end extend through the periphery of the rotor to communicate with the fluid channel adjacent the discharge end of the piston while the opposite end of the discharge passage'may communicate with one section of the annulanpassage 120, which in turn communicates with the dis-- charge passage 121 formed in the outer casing 102. The casing 102 may beprovided with a wearing ring 122 for forming a fluid seal with the rotor 111 at the junction of the annular passage 120 and the casing discharge passage 121. If desired, the two suction or inlet passages may be connected together by means of a suitable yoke pipe fitting, not shown, and likewise, the

two discharge passages may be connected to- It may be well to note that in this type of pump the two bearings are arranged exterior to the pump .casings,.which is a material advantage as the bearings may be of suiflcient isize and adequately lubricated. e

It will-be understood that these pumps are reversible, that is, the suction and discharge passages respectively, for one direction of rotation, will become the discharge and suction passages respectively, for the opposite rotation. The pressures produced by the two opposite rotations may be equal or diiferent, depending upon whether the resistance of the rough surfaces are equal or different for the opposite directions of flow; and also the pump of this invention may be utilized as a fluid turbine by connecting a suitable source of pressure fluid thereto.

It is to be understood that the term fluid is to mean any liquid whether easy flowing or viscous, and that the pumps, by properly proportioning the areas of the several parts, may be'readily utilized for pumping air, vapor, steam or gas; in other words, may actas a compressor.

It will be appreciated that the fluid inlet and outlet passages may be appropriately curved-or otherwise shaped instead of being radially disposed as illustrated in the several figures, whereby the pumping action of the inlet passage may be of a maximum value, while the turbine action of the outlet passage may be of a minimum value, thereby increasing the effective head and. emciency of the pump.

It is to be understood that the invention is not to be limited to the details herein set' forth for the sake of illustration, but is of the full scope of the following claims.

I claim:

1. In a rotary hydraulic machine arr annular" channel having rough walls, a casing means arranged to form an operative fluid seal for closing the annular channel and provided with a smooth surface facing said chann'elm. piston carried by said casing and arranged to project into 4 the fluid channel and to form an operative fluid seal with the rough surface thereof, a fluid inlet passage formed in the casing and arranged to communicate with the fluid channel adjacent the suction end of the piston, a fluid outlet passage formed in' the casing'andmrranged to communicate with the fluid channel adjacent the discharge end of the piston, and means for causing a relative movement between the channel and easing.-

2. In a turbulence pump, a stationary outer casing, an annular channel ring mounted there in and provided with a fluid'channe'l, a plurality of fluid retarding blades mounted in the channel ring and arranged to project from the fluid channel so as to form therein a relatively roughsurface, a rotor rotatably mounted in the casing and arranged to form an operative fluid seal with the channel ring for effectively sealing the fluid channel, a piston mounted upon the rotor and arranged to project into the fluid channel and to form an operative fluid seal with the retarding blades therein, said rotor provided with an appropriate inlet passage communicating with the fluidchannel adjacent the one end of thepiston and an appropriate discharge passage communicavity and arranged to form an operative fluid seal with the channel ring for effectively aling the fluid channel, a piston means mounte upon the rotor and arra'ngedto project into the fluid '145 face, 'a rotor operatively mounted in the rotor- V fluid retarding means; said rotor having an appropriate inlet passage communicating the fluid channel adjacent one end of the piston with the g inlet passage formed in the casing and an aptill propriate-discharge passage communicating the fluid channel adjacent the other end of the piston with the discharge passage formed in the easing, and meansfor rotating the rotor.

a; In a turbulence pump, a stationary casing having a fluid channel, a rotor operatively mounted in said casing and arranged to form an operative fluid seal for said channel, a piston carried by the rotor and arranged to project intothe fluid channel and to form an operative fluid seal with the walls thereof, said rotor having anappropriate inlet passage communicating with the fluid channel adjacent one end ofthe piston and an appropriate discharge passage communicating with the fluid channel adjacent the other end of said piston, and said stationary casing having fluid inlet and outlet passages'communicab ing with the related passages of the rotor.

5. In a turbulence pump, a stationary casing provided with a fluid channel having relatively rough walls, a rotor operatively mounted in said casing and arranged to operatively seal said channel, a piston carried by the rotorand arranged to project into the fluid channel and to form an operative fluid seal with the rough walls thereof, said rotor having an appropriate inlet passage communicating with thefluid channel adjacent one end of the piston and an appropriate discharge passage communicating with the fluid channel adjacent the other end of said piston, and said stationary casing having fluid inlet and outlet passages communicating with the related passages of the rotor. o

6. In a turbulence pump, a stationary casing provided with a fluid channel having relatively rough walls, a rotor operatively mounted in said casing and arranged to operatively seal said channel, a pair of diametrically opposed pistons carried by the rotor andeach of said pistons arranged to project into the fluid channel and to form an operative fluid seal with'the rough walls thereof, said rotor having an appropriate sys- I tom oi inlet passages communicating with the fluid channel adjacent one end of each of said pistons and an appropriate system of discharge passages communicating with the fluid channel, and said stationary casing having fluid inlet and outlet passages communicating with the related passages of the rotor.

7. In a turbulence pump, a stationary casing provided with a fluid channel having relatively to walls, a rotor operatively mounted in the casing and arranged to operatively seal said channel, a piston carried by the rotor and arranged to project into the fluid channel and to form with the rough walls an eflective fluid seal, said rotor having an appropriate inlet passage communicating with the fluid channel adjacent one end of the piston and an appropriate discharge passage, communicating with the fluid channel adjacent the other end of the piston, each end of 1 said piston overlapping in spaced relation the adprovided with a fluid channel, having relatively iacent fluid passages, and said stationary casing having fluid inlet and outlet passages communicating with their related passages of the rotor.

8.'-In a turbulence pump, a stationary casing rough walls, a rotor operatively mounted in the casing and arranged to operatively seal said channel, diametrically opposed pistons carried by the rotor and each arranged to project into the fluid channel and to form with the rough walls thereof an effective fluid seal-said rotorihaving an appropriate system of'inlet passages communicating with the fluid channel adjacent one end of each piston and an appropriate system of discharge passages communicating with the fluid channel adjacent the other ends of the pistons, the ends of each piston arranged to overlap in spaced relation the adjacent fluid passage, and said stationary casing having fluid inlet and outlet passages communicating with their related rotor passages.

9. In a turbulence pump, a stationary casing .provi dedwith a fluid channel having relatively; rough walls, a. rotor operatively mounted in said,

casing and arranged to operatively seal said channel, a plurality of pistons spaced equally around said rotor and each arranged to project into the fluid channel and to form an operative fluid seal with the rough walls thereof, said rotor having an appropriate system of inlet passages communicating with the fluid channel a fiacent one end of each of said pistons and an appropriate system of discharge passages communicating with the fluid channel adjacent the other end of each piston, and said stationary casing having fluid inlet and outlet passages communicating with their related rotor passages. 7

10.- In a turbulence pump, a stationary outer casing provided with a fluid channel having relatively rough walls and said casing also provided with appropriate inlet and discharge passages, a rotor operatively mounted in said casing and arranged to operatively seal said channel, a plurality of pistons spaced equally around said rotor and each arranged to project into the fluid channel and to form an operative fluid seal with the rough walls thereof,'and said rotor having an appropriate system of inlet passages communieating the fluid channel adjacent the suction end of each of said pistons with the casing inlet passage and an appropriate system of discharge passages con'imunicating the fluid-channel adjacent thedischarge end of each of said pistons with the casing discharge passage.

11. In a turbulence pump, a stationary outer casing having a rotor cavity and appropriate inlet and discharge passages, an annular channel ring mounted in the rotor cavity and provided with a fluid channel, fluid retarding means formed in the fluid channel to provide therein a relatively rough surface, a rotor operatively mounted in the rotor cavity and arranged to form an operative fluid seal with the channel ring for effectively sealing the fluid channel, a plurality of pistons equally spaced around'said rotor and each arranged to project into the fluid channel and to form an operative fluid seal with the rough walls thereof, and said rotor having an appropriate system of inlet passages communicating the fluid channel'adjacent the suction end of each of said pistons with the casing inlet passage and an appropriate system of discharge passages communicating the'fluid channel adjacent the discharge end of each of said pistons withthe casing discharge passage:

12. In a multistage turbulence pump, a stationary outer casing having alrotor cavity and a propriate inlet and discharge passages, an annular channel ring mounted in the rotor cavity and provided with a plurality of fluid channels, fluid retarding means formed in each of said fluid channels to provide therein a relatively rough surface, a plurality of rotors, meansoperatively mounted in the rotor cavity and each arranged to form'an operative fluid seal with one of said channel rings for effectively sealing the fluid channel thereof, a piston carried by each rotor so of, and said rotor means having an appropriate fluid channel arranged to communicate the inlet passage of the casing with the initial fluid chan-, 'nel adjacent the suction end of the piston therefor and intermediate fluid passages arranged for serially communicating the discharge end of' the piston of one fluid channel with the suction'end of the piston of the next succeeding fluid channel and a final discharge passage arranged to communicate the flnal fluid channel adjacent thedischarge end of the piston therefor with the casing discharge passage.

13. In a multistage turbulence pump, a stationary outer casing having a rotor cavity and appropriate inlet and discharge passages, an annu lar channel ring mounted in the rotor cavity and provided with two fluid channels and having a plurality of blade slots intersecting said channels, removable fluid retarding blades mounted in said channel ring slots and arranged so that each single blade forms the fluid retarding means for both of the fluid channels,- two associated, rotors operatively mounted in the casing rotor cavity and each arranged to form an operative fluid seal with the channel ring for effectively sealing the fluid channels, a piston carried by each rotor in diametrically, opposed relation and each piston arranged to project into its respectivefluid channel and to form an operative fluid seal with the fluid retarding blades thereof, and said rotors having appropriate systems of fluid channels arranged to communicate the inlet passage of the casing with first stage fluid channeladjacent the suction end of the piston therefor and a transfer passage arranged to communicate the first stage fluid channel adjacent the discharge end of piston with the second stage fluid channel adjacent the suction end of the piston therefor and flnal discharge passage arranged to communicate the last stage fluid channel adjacent the discharge end of the piston with the casingdischarge passage.

14. In a' multistage turbulence pump, a stationary casing provided with a plurality of fluid channels and each of said channels having relatively rough walls, rotor means operatively mounted in said casing and arranged to operatively seal said channels, a piston means for each fluid channel carried by said rotor means in oppositely disposed relation and each piston arranged to project into its respective fluid channel and to form an operative fluid seal with rough walls thereof, said rotor means having an appropriate system of fluid passages forserially communicating the fluid channels, and said stationary casing having inlet and outlet passages appropriately communicating with the system of fluid passages formed in the rotor.

l5p In a multistage turbulence pump, a stationary casing provided with a plurality of fluid channels and each of said channels having relatively rough walls, rotor means operatively mounted in said casing and arranged to operatively seal said channels, a piston means for each fluid channel carried by the rotor means in oppositely disposed relation and each piston arranged to project into its respective fluid channel and to form an operative fluid seal with the rough walls thereof, said rotor means having an appropriate system of fluid passages for. serially communicating the fluid channels and the ends of each piston being arranged to overlap in spaced relation the adjacent fluid passages, and said stationary casing having inlet and outlet passages appropriately communicating with the system of fluid'passages'formed in the rotor.

16. In a turbulence pump, casing means having spaced fluid channels, fluid retarding means formed in each of said channels, a rotor for each channel operatively mounted in the casing in back-to-back relation and each rotor arranged to operatively seal its respective fluid channel, a piston carried by each rotor and arranged so that one piston will be degrees in advance of the other piston, and each of said rotors having an appropriate inlet passage communicating with the fluid channeladjacent the suction end of its piston, an appropriate discharge passage communicating with the fluid channel adjacent the discharge end of the piston, and said casing having fluid inlet and outlet passages communicating with the related passages of each rotor.

17. In a turbulence pump, casing means hav-, ing spaced fluid channels anda pair of appro-- priate inlet and outlet passages, fluid retardin means for each of said channels, a rotor for each channel operatively mounted in the casing in back-to-back relation and each rotor arranged to operatively seal its respective fluid channel, a

piston carried by each rotor and arranged so that one of said pistons will be 180 degrees in advance-of the other of said pistons, and each rotor having an appropriate inlet passage communicating its respective fluidchannel adjacent the suction end of its piston with one of said casing inlet passages and an appropriate discharge passage communicating its respective fluid 1 channel adjacent the discharge end of its piston with one of said casing discharge passages.

18. In a rotary hydraulic machine, an outer casing having an annular fluid channel, a plurality of removable blades mounted in said channel tq form a relatively rough surface, an inner casing arranged to form an operative fluid seal for closing the channel and provided with a smooth surface facing said channel, a piston carried by said casing and arranged to project into the fluid channel andto form an operative fluid seal with the removable blades mounted therein, a fluid inlet passage formed in the inner casing and arranged to communicate with the fluid ALADAR HOLLANDER.