US3895893A - Rotary piston pump - Google Patents

Rotary piston pump Download PDF

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US3895893A
US3895893A US311816A US31181672A US3895893A US 3895893 A US3895893 A US 3895893A US 311816 A US311816 A US 311816A US 31181672 A US31181672 A US 31181672A US 3895893 A US3895893 A US 3895893A
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vanes
channel
rotary piston
piston pump
pump according
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Manfred Sommer
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/02—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees

Definitions

  • a rotary piston pump comprises vanes mounted on [52] US. Cl.
  • Control means is provided for turning the vanes about radial [56] References C'ted axes so as to position the vanes approximately perpen- UNITED STATES PATENTS dicular to their direction of movement while passing 94,892 9/1869 Keith 418/226 through the forwarding portion of the nn d t 185,069 12/1876 Birum 418/233 turn them approximately 90 so as to pass through the 249,345 11/1881 l-lalstead 418/226 sealing portion of the channel in an edgewise position.
  • the invention relates to rotary piston pumps and in particular to pumps having a plurality of vanes traveling around an annular channel provided with inlet and outlet ports.
  • the pump is suitable for pumping almost any fluid medium and especially suitable for pumping either viscous or non-viscous liquids which may or may not contain solid pieces or particles.
  • a pump in accordance with the invention is particularly useful in handling beverages, food stuffs and chemicals.
  • the pump in accordance with the invention makes possible smooth operation comparable to that of a centrifugal pump and moreover minimizes crushing or turbulence in the medium being pumped. It is almost wholly insensitive to foreign bodies protected against dry running and is wear resistant. Moreover, it can be operated in either direction.
  • a rotary piston pump having a pump chamber in the form of an annular channel having a forwarding or pumping portion of circular cross section and a sealing portion of restricted cross section.
  • Disc-like vanes mounted on shafts extending from a hub rotatably concentrically with the annular channel are disposed in the channel and travel circumferentially around it as the hub rotates.
  • the vanes are rotatable about their axes radial of the hub and the turning of the vanes is cyclically controlled so that the vanes pass edgewise through the sealing portion of the channel while being turned approximately perpendicular to their direction of movement in the forwarding or pumping portion of the channel.
  • Inlet and outlet passages are provided respectively at opposite ends of the forwarding portion of the channeLSuitable means provides fluid tight seals between the relatively moving parts of the pump.
  • the distance between two adjacent vanes and the length of the sealing portion of the channel are coordinated so that the next following vane has entered the sealing portion of the channel to provide a complete seal before the preceding vane has passed out of the sealing portion of the channel.
  • the circumferential edges of the vanes are rounded so as to permit free turning of the vanes while maintaining a close seal between the vanes and the channel walls.
  • an inclined ramp or entrance surface which is engageable successively with the vanes as they approach the sealing channel and may be used as means for turning the vanes so as to enter the sealing channel in an edgewise position.
  • the entrance surfaces and/or the vanes are formed wholly or in part of elastic material so as to avoid impact shocks.
  • the advantages of a piston pump and of a centrifugal pump are combined in a single pump wherein the vanes traveling around the annular pump channel approach the piston pump system but, instead of rectilinear back and forth movement of the piston in a piston pump, the piston like vanes travel in a circular path and carry the pumped medium with them in the spaces between successive vanes. After turning to an edgewise position, the vanes pass through a restricted sealing part of the channel between pressure and suction zones and after passing through the sealing channel portion they are turned back to operating position upon entering the forwarding or pumping portion of the channel.
  • the pump in accordance with the invention is particularly suitable for the beverage and food industry and above all for the wine producing industry for the transportation of the mash which is produced by a crushing mill and provides the base material for production of wine.
  • the pump in accordance with the invention is also suitable for other thinner liquids and also for liquids containing coarse particles, for example in the chemical industry. No objects such as berries can become lodged in the rotatable vanes as is the case with sliding vanes of a vane cell rotary pump. Rotary vanes can be sealed essentially better than sliding vanes.
  • the circular vanes can, if desired, be sealed with piston rings although for most purposesit is undesirable to have movable elements on the vane circumference since a good seal can be-obtained with the rounded form of the vanes.
  • the turning of the vanes about a radial axis of rotation in order to lie in a circumferentially extending plane makes possible'an advantageous bearing in a driven hub portion.
  • the elastic entrance faces avoid hard impact and guide the vanes in a noise-free manner and avoid damage through foreign bodies or hard objects in the medium being pumped.
  • the elastic form of the vanes the running characteristics not only with respect to noise but also with respect to dry running is essentially improved. The resilience of these parts avoids impact. Above all foreign bodies in the medium being pumped cause no disturbance.
  • Two identical ramps or entrance faces, whether they engage the vanes only locally or on the entire side edge, are advantageously provided at both inlet and outlet connections of the pump so that the channel has a symmetrical profile and the pump can be run in either direction. This is particularly convenient for transferring media back and forth between two containers and represents an important advantage of these pumps.
  • the pressure faces of the vanes can be formed in four manners. In order to obtain a high capacity and minimize losses, the vanes are made as thin as possible.
  • the pressure faces of the vanes may be formed curved in order to take the stresses acting in the location of the hearing or to make the profile form conform to the loading. This requires corresponding profiling of the cross section of the channel in the sealing zone. With a view to easy production and good sealing characteristics it is however desirable to select plane pressure faces for the vanes which are advantageously parallel to one another although they can, if desired, be slightly inclined with respectto one another.
  • the formation of the pressure faces of the vanes depends on the strength and characteristics of the material of the vanes and of their bounding parts.
  • the guiding of the vanes can likewise be effected in various ways and indeed either in the pump chamber and/or on the bearing element.
  • a control system comprising a cam, levers and sliding elements acts on the bearing shafts of the vanes.
  • This mode of control is indeed more expensive than the pure internal control but has the advantage of providing an exact and above all noiseless movement of the vanes. If it is desired to alter the delivery of the pump while keeping the same speed of rotation, this can be achieved by changing the position of the vanes in the conveying portion of the pump channel. Thus if the vanes are somewhat inclined instead of being perpendicular to the direction of movement, only a portion of the stream will be delivered to the pressure zone while another portion is bypassed.
  • the vane axes lie in a single plane, all except the oneof the connecting members between the vanes of a pair are laterally offset to opposite sides to avoid interference with one another.
  • the pump is particularly suitable for handling media containing coarse particles, it is desirable to make the connection between the vanes of a pair somewhat elastic sorthat on engagement with a hard unfavorably positioned object orforeign body, the vane can temporarily deflect and then spring back to its proper position.
  • the elastic connection can advantageously be formed of spring steel wire.
  • the entrance face to the sealing portion of the channel locally engages only a singleportion of the vanes.
  • the entrance surface to conform in profile exactly to the corresponding developed profile of the vanes so that the entrance surface engages the entire side edge of the vanes.
  • Another advantageous form is for the entrance faces to be formed of small rods which provide openings between them and the channel wall for the passage of the medium and coarse particles contained therein. A clamping of the pump'parts and the medium being pumped is thereby avoided in a simple manner.
  • the profiled parts which form the entrance face not only can be made of, or covered with elastic, plastic material but also can be made of correspondingly profiled spring steel sheet metal.
  • the vanes can be made of rubber or also of other elastic high strength plastic materials such as polyamides or the like.
  • a desirable constructive form for the bearing and guiding of the vanes is provided when the vanes are provided with inwardly projecting bearing shafts which are rotatably received in openings in a rotatable hub which is coaxial withthe annular pump channel. Suitable seals are provided between the rotating parts and the housing. If the pump housing is preferably made of two parts which are joined together with a suitable sealing gasket in the central plane of the pump channel, the pump can be easily produced and can easily be assembled and disassembled, as the entire hub portion together with the vanes can be taken off with one part of the pump housing.
  • bearing stubs can be provided eccentrically on the inner ends of the bearing shafts of the vanes.
  • a particular reliable and very quiet running arrangement' is provided when these stubs are linked to connecting rods which extend generally in the direction of the axis of rotation of the pump rotor and their ends engage an inclined face of a control member coaxial with the axis of rotation so that the vanes after leaving the sealing portion of the channel are turned to a position perpendicular to the direction of movement and upon running on to the entrance faces to the sealing portion of the channel they are turned so as to lie in the direction of their movement.
  • Such a combination of control by the entrance faces and the linkage and cam arrangement makes it possible to vary the play between the entrance faces and the control member disposed outside of the pump chamber. This is important for the practical realization of a quiet dependable pump.
  • FIG. 1 is a central section through a first embodiment of a pump in accordance with the invention, the section being taken on the line 1-1 in FIGS. 2 and 4;
  • FIG. 2 is a plan view of the pump shown in FIG. 1;
  • FIG. 3 is a partial section taken along the line 3-3 in FIG. 1;
  • FIG. 4 is an enlarged cross section of the pump taken along the line 4-4 in FIG. 1;
  • FIG. 5 is a schematic side elevation showing a vane of the pump in successive phases of its movement
  • FIGS. 6a and 6b are a developed sectional view of the path of a vane and its guiding cams
  • FIG. 7 is a vertical section of a further embodiment taken on the line 77 in FIG. 9;
  • FIG. 8 is a horizontal section of the pump taken on the line 8-8 in FIG. 7;
  • FIG. 9 is an enlarged cross section of the pump taken on the line 99 in FIG. 7;
  • FIG. 10 is a central section through a further embodiment of the pump taken on the line 10-10 in FIGS. 1 1 and 13;
  • FIG. 11 is a section taken along the line 11-11 in FIGS. 10 and 13;
  • FIG. 12 shows half of a developed view of the pump channel with different vane positions
  • FIG. 13 is an enlarged and more detail cross section taken along the line 13-13 in FIGS. 10 and 11.
  • FIGS. 1 to 6 there is shown a pump 20 in accordance with the present invention having a pump casing 21 which is formed of two casing portions 22 and 23 which are divided along the central plane E of the pump and are united by bolts 25 passing through apertures 26 in eyes 27 provided at the periphery of the pump casing parts.
  • a fluid tight connection between the casing parts is provided by an O-ring gasket 24.
  • an annular channel 30 which as seen particularly in FIG. 4, is of circular cross section with a radius r.
  • Connecting passageways 31 and 32 open tangentially into the channel 30 and are provided with flanges '33 for connection with inlet and outlet lines of the pump.
  • the connecting passage 31 will for convenience be designated as the inlet or suction connection and the connecting passage 32 as the outlet or pressure connection. They operate in this manner when the pump is rotated in a clockwise direction as indicated by the arrow 34 in FIG. 1.
  • a plurality of vanes 35 in the form of circular discs run around in the annular channel 30.
  • Six such vanes 35 are shown by way of example in the drawings, the vanes being equally spaced and thus disposed 60 from one another.
  • the vanes 35 are fixed on stub shafts 36 which extend into the vanes from bearing shafts 37 and are fixed to the vanes by pins 38.
  • the bearing shafts 37 are rotatable in bushings 39. They are rotatable about axes SA which are disposed in the central plane E of the pump and extend radially from the axis of rotation DA of the pump.
  • the bearing bushings 39 fit in radial holes provided in an annular hub portion 40 which is formed as a flange-like projection on a driving sleeve 41 and leaves a central space 42 free inside of the hub.
  • the hub portion 40 is sealed with respect to the casing by means of O-ring gaskets 43 which slidably engage cylindrical sealing and bearing faces 44 of the pump casing 21.
  • Shaft packings 45 are provided for further sealing the driving sleeve 41.
  • the driving shaft (not shown) is rotationally connected with the sleeve 41 by means of a key fitting in an axially extending groove 46 provided in the interior of the sleeve.
  • the inwardly extending bearing shafts 37 of pairs of diametrically opposite vanes 35 are rotationally but elastically connected with one another by means of connecting rods 47, 48 and 49.
  • These rods are formed, for example, of spring steel wire so as to provide torsional elasticity permitting resilient relative angular displacement of the two vanes of a pair.
  • the rod 47 connecting the two vanes 35 appearing in FIG. 4 is offset to the right. It is thereby possible for all of the three pairs of vanes to be turned independently of one another. As seen in FIG. 1 the two vanes 35 of each pair are turned relative to one another.
  • the vanes have a thickness d. Stop collars 50 provided at the inner ends of the bearing shafts 37 prevent axial displacement of the shafts and hence the vanes.
  • the pumping or forwarding portion 54 of the annular channel 30 i.e., the lower portion between the inlet 31 and outlet 32 is completely free and is hence of circular cross section except for an annular opening at the inner periphery of the channel through which the shaft 36 enters.
  • the upper sealing portion 55 of the channel is reduced to the thickness d of the vanes 35.
  • sealing pieces 56 and 57 are inserted in the annular channel which otherwise is of circular cross section throughout its circumferential extent.
  • the sealing piece 56 has at its left end as viewed in FIG. 1 an inclined entrance face or ramp 58, the developed profile of which is a gradual rectilinear incline as seen in FIG. 6a.
  • cross section it conforms to the circular curvature of the vanes so as continually to engage one entire side edge of the vane as the vane is progressively rotated.
  • the cross sectional contour accordingly varies progressively from approximately semicircular at the upstream end to approximately flat at the downstream end.
  • This form can also be seen somewhat in FIGS. 1 and 3.
  • the sealing piece 56 extends through the entire sealing part 55 of the channel 30 to the inlet 31 and ends there in a slightly inclined end face 59.
  • the sealing piece 56 On the outer side engaging the channel wall the sealing piece 56 has an arcuate cross section as seen in FIG. 4 while on the inner side the leading face 58 merges into a plane sealing face 60 which is spaced from the central plane E of the pump a distance equal to half the thickness d of the vanes 35.
  • a like but mirror image sealing piece 57 lies in the right hand part of the sealing portion 55 of the channel 30 as seen in FIG. 4.
  • the entry face 58 of the sealing piece 57 is located at the inlet 31 of the pump while the end face 59 lies at the outlet 32.
  • This symmetrical arrangement permits the pump to run in either direction.
  • a sealing constriction 61 which corresponds in profile to the vanes 35 turned in a direction circumferential of the channel.
  • the peripheral edges 62 of the vanes 35 are curved with the radius r so that in all positions there is obtained a free bearing and sealing arrangement between the vanes 35 and the walls of the channel 30.
  • the pump casing 21 may be made of stainless steel, bronze, gray cast iron, etc., and also of cast steel.
  • the sealing pieces 56 and 57 may also be produced from hardenable alloy steel or also from plastic with corresponding properties.
  • the vanes 35 can be made either from suitable resilient plastic material or advantageously from a rubber compound having corresponding physiologically uncontaminating qualities. They can moreover have a metal core covered with an appropriate rubber or plastic material. Thereby the expected wear will be concentrated almost wholly on the cheaply produced and easily replaceable vanes.
  • the sealing pieces 56 and 57 can be formed as profiled sheet steel stampings which are set into the casing in such manner as to provide a fluid tight seal.
  • FIGS. 5, 6a and 6b of which FIGS. 6a and 6b are an extension of one another.
  • the ends A and EN Of FIG. 6a join respectively with the ends A and EN of FIG. 6b to form a continuous circuit.
  • the hub 40 is rotated in the direction of the arrows 34 by a motor through a shafts fitting into the sleeve 41, all of the vanes 35 are carried around with the hub through their respective shafts 36, 37.
  • the vanes are perpendicular to the circumferential direction of movement. lnth isposition the vanes push ahead of them the fluid to be pumped until they reach the position B.
  • the vanes Shortly thereafter the vanes reach the entry face 58 of the sealing piece 56 and, as shown in dotted lines in FIG. 6a, they are thereupon engaged by the face 58 so that theyare slowly turned about their axes SA until shortly before the position D are disposed in the direction of movement and are-thereby ready to engage the sealing faces 60. They then'pass the outlet passage 32.
  • the outlet 32 appears in FIG. 6a as a recess in the sealing face 56 because, on account of its round shape and the transistion to a flat sides passage, a lateral recessing of the sealing face 56 is necessary in order to obtain free flow of the medium being pumped.
  • the vanes Upon further rotation of the rotor, the vanes enter the sealing part of the channel which is formed between two opposite sealing pieces 56 and 57 and has a width which is only equal to the thickness d of the vanes from the outlet 32 to the end face 59 of the sealing piece 57 at the inlet 31.
  • the preceding vane As will be seen from the following description of FIG. 7, is still a small distance from the exit end of the sealing canal part 55 so that a continuous seal is provided between the outlet 32 and inlet 31.
  • the vanes Upon exiting from the sealing channel 55, the vanes pass the inlet 31 and continue along the exit face 58 of the sealing piece 57.
  • the vanes In passing from the position F through the position G to the position H the vanes are turned from a position in line with the direction of movement to a position perpendicular to the direction of movement by engagement of the diametrically opposite vanes with which they are connected by the connecting rods 47, 48 and 49 with the entrance face 58 of the sealing piece 56. If, however, a. vane encounters a hard piece in the liquid being pumped, the resilience of the connecting rod permits the vane to deflect angularly relative to the opposite vane until the obstacle is cleared. During their movement through the forwardly part 54 of the channel 30 the vanes are held in a position perpendicular to the direction of movement by the connected opposite vanes being held between the opposite sealing faces of the sealing portion 55 of the channel. There is thus achieved an automatic control of proper orientation of the vanes as they circulate around the annular channel.
  • the vane which has just been turned to a position perpendicular to the direction of movement will draw the medium being pumped from the inlet 31 and when the following vane is likewise turned to a position perpendicular to the direction of movement, a constant volume of space is defined in the forwarding channel part 54 between the two vanes.
  • the portion of medium thus confined in the forwarding portion of the canal 54 between successive vanes is carried along without any compression and when the leading vane reaches the entrance face 58 and is turned so as to lie in the direction of movement, the greater part of the medium is discharged through the outlet 32.
  • a small part of the medium will, however, in this embodiment be carried through the sealing part 55 between the vanes turned in the direction of movement.
  • the pump works in the manner of a piston pump, it is self priming. However, as it is built as a rotary pump there is a very uniform discharge practically without pulsations.
  • FIGS. 7 to 9 like parts are designated by the same reference numerals.
  • the pump is basically exactly like that illustrated in FIGS. 1 to 6b and it also works in the same manner.
  • the control of the individual vanes as they travel around the channel is effected by cams and not by coupling with opposite vanes and by entrance ramps.
  • the bearing shafts 37 extend into the central hollow space 42 of the hub portion 40 and are provided at their inner ends with eccentrically arranged positioning stub shafts 65. These engage in a cam track 66 which is provided in a control member 67 disposed concentrically with the axis of rotation of the pump.
  • the cam track 66 is shaped to provide the desired turning of the vanes 35 v as they travel around the annular channel 30.
  • the control member 67 is secured against rotation to a cover 69 which in turn is secured to the left casing member 22 and closes the control space 42.
  • This embodiment likewise has six vanes. However, as the vanes are independently controlled by engagement of the control shafts 65 in the cam track 66 the vanes can be more closely spaced so that the losses through the sealing space can be limited; The number of vanes can be increased or decreased as desired.
  • FIGS. 10 to .13 there is shown a further example of a rotary piston pump which operates on the same principle as the foregoingexamples and differs from .these primarily only in the form of the control of the vanes.
  • Likeparts are designated by the same reference numerals asin the preceding figures.
  • vanes 135 which are likewise of circular disc form up to the partjin the region of the bearing shafts 137.
  • the pump housing consists likewise of two essentially symmetrical housing parts 121 and 122 which, except for the slightly different form of the inlet and outlet, differ primarily in that instead of the inserted sealing pieces to limit the sealing portion 55 of the channel, two housing parts 121 and 12 2 are formed with corresponding thickenings to define a sealing channel portion of the thickness d.
  • 'Also'the end faces 159 are not formed in any particular manner although theycan also be profiled.
  • the entrance face 58 at the junction of the forwarding portion of the'channel with the sealing portion is here formed as a separate inserted entrance piece 158 which consists, for example, of a bar or strip comprising a steel core with covering of a relatively elastic material, in particular an oil and chemical resistant elastomeric plastic material with a Shore hardness of about 80 to 85, for example a material sold by Wegriken Bayer AG under the name VULKOL- LAN.
  • the entrance piece thus formed is resilient.
  • Each of the entrance pieces 158 is provided with an opening 162 which permits discharge from the channel
  • the bearing shafts 137 are, for example, rotatable in.
  • each shaft is provided with two needle bearings 139 and between these bearings the shaft is provided with an annular groove in which tangential pins 181 engage to secure the shaft against axial movement.
  • a fluid tight seal is provided by shaft gaskets 182.
  • Flat vane-holding portions 136 extend outwardly from each of the bearing shafts 137 and, as seen in FIG. 13, are profiled so as to fit into the vanes 135 which are secured on the shaft portions 136 by screws 138. While the bearing shafts 137 and their holding portions 136 are formed of steel or of rust free metal, the vanes 135 are made of plastic, for example a polyamide. As in the previously described embodiments, the circumferential edges 62 of the vanes are of parti-spherical form with a radius r.
  • control stub shafts 65 On the inner ends of the bearing shafts 137 which extend into the central control space 42, there are provided control stub shafts 65 which, as in the embodiment of FIG. 9, are eccentric to the turning axis SA of the bearing shaft.
  • Connecting rods 185 are pivotally connected with the eccentric stub shafts 65.
  • the connecting rods 185 have slightly tapered conical end portions 186 and are formed of steel. They extend slidably and rotatably into pushing casings 187 and are disposed essentially in the direction of the axis of rotation DA, i.e., any deviation from this direction is due only to the eccentricity.
  • the pushing casings 187 are slidable in the direction of the axis of rotation DA in a guiding flanged cover 188 secured to the right hand casing part as viewed in FIG. 13.
  • the pushing casings have rounded ends 189 which run over an inclined surface 190 of a control disc 191 which is tiltably arranged in a control disc chamber 192 formed in a cap-form cover 193.
  • This cover 193 is preferably formed of a high strength plastic for example polyamide.
  • the control disc 191 has a central spherical recess 194 by means of which the disc 19] is easily tiltable on the rounded inner end of a supporting stem 195 which is received in the recess 194.
  • the supporting stem 195 is provided with an external threaded portion and is screwed into a threaded opening in the cover 193 so that it can be axially adjustable. It is held in adjusted position by a lock nut 197.
  • the guiding cover 188 and cap 193 are secured in place by means of screws of which only the center lines are indicated in the drawings.
  • Small pistons 200 which are slidable in the push casings 187 bear on the ends 201 of the connecting rods 185. Between these pistons 200 and the internal bearing faces 202 of the casings 187 there are spring elements 203 which are formed of an elastic plastic or rubber of very good quality and good spring characteristics, for example the above mentioned material VULKOLLAN. These spring elements provide a not too soft elastic connection between the control stubs 65 of the shafts 137 and the inclined face 190 of the control disc 191 so as to provide very quient running and good control of the pump.
  • bars 199 which lie in the central plane E of the pump and serve to guide the medium being pumped and to hold back any hard solids to prevent them from contacting and possibly damaging the vanes of the pump.
  • the supporting stem 195 cana be adjustably screwed outwardly so as to give the control disc 19] more play.
  • the vanes 135 are thereby positioned at a slightly inclined angle while passing through the forwarding portion 54 of the channel so that they do not provide a complete seal and thereby permit a certain backflow of the medium being pumped.
  • control disc 191 being tiltably supported by the support rod 195 it can be replaced by a fixed control piece having a correspondingly inclined control face on which the rounded ends 189 of the connecting rods slide.
  • control face instead of being flat can under proper circumstances be given a profiled form in order better to suit the geometrical structure, although with the construction shown in the drawings the necessary equalization is well taken care of through the spring elements and the play between the connecting rods and the control disc.
  • control can be provided by any appropriate means that permits the vanes to pass through the sealing portion of the channel while being held at the desired angle of incidence through the forwarding portion of the channel.
  • the pump is self-priming and has the same suction characteristics as a piston pump. It is capable of automatically removing air from the suction space.
  • the liquid flow is laminar so that the pump operates smoothly like a rotary pump without crushing the medium being pumped and without turbulence. Even at low speed the pump works uniformly and quietly.
  • the pump is insensitive to foreign bodies and large solids in the medium being pumped. It is protected against running dry. This characteristic is improved .through the possibility of-making the vanes elastic.
  • the pump is also suitable for viscous media and media containing solid particles.
  • the pump can be made very resistant to wear, erosion and corrosion.
  • the pump can be run in either direction.
  • a rotary piston pump comprising a casing having an annular channel therein, a hub rotatable in said casing concentric with said annular channel, said hub comprising a shaft portion rotatably supported in said casing and an overhanging annular flange portion at an inner end of said shaft portion and-having a central space inside said shaft portion and having a central space inside said annular flange portion, said flange portion being disposed wholly radially inwardly of said annular channel of the casing, means providing a fluid tight seal between said hub and said casi'rig', means for rotating said hub, a plurality of circumferentially spaced generally radial shafts extending through and rotatably supported by said annular flange portion of said hub, a flat circular disc-shaped vane mounted on the outer end of each of said shafts and disposed in said annular channel whereby upon rotation of said hub, said vanes are carried around in said annular channel, said channel having an arcuate pumping portion of uniform circular cross section
  • a rotary piston pump according to claim 1 comprising means for varying the angle of said vanes while in said pumping channel portion to provide different delivery rates of the medium being pumped while the speed of rotation of the pump is the same.
  • a rotary piston pump according to claim 1, wherein said actuating means comprises stationary cam means disposed in said central space in said hub and engaged by said eccentric portions as the hub rotates to control the rotational positioning of said shafts and the respective vanes.
  • a rotary piston pump according to claim 1 wherein said channel and said inlet and outlet openings are symmetrical about a diametrical line midway between said openings so that opposite halves are mirror images of one another, whereby said pump is reversible.
  • a rotary piston pump according to claim 1 comprising means in at least said inlet opening for guiding the medium being pumped into said channel and for holding back excessively large solid objects in said medium.
  • a rotary piston pump according to claim 1, wherein said hub comprises a cylindrical body portion rotatable in said casing and adapted to be connected to a motor for driving said hub and an annular flange portion extending axially from said body portion and rotatably supporting said shafts.
  • sealing means comprises packing rings providing a seal between said body portion of the hub and said casing and sealing rings providing a seal between the periphery of said flange portion and a surrounding portion of said casing on opposite sides of said channel.
  • a rotary piston pump according to claim 1 further comprising ramp means disposed upstream of said sealing channel portion and engageable successively with one side of each of said vanes.
  • a rotary piston pump according to claim 11, wherein said ramp means comprises at least one bar with an opening between the bar and the wall of said channel for the passage of objects in the medium being pumped.
  • a rotary piston pump according to claim 1, wherein said actuating means comprises connecting rod means connected to each said eccentric portion and extending approximately parallel to the axis of said hub and guided for endwise movement, and a control member having an inclined face engageably by the ends of said connecting rod means.
  • a rotary piston pump according to claim 17, comprising means for adjustably moving said control member axially of the hub shaft axis to vary the play between said connecting rod means and said inclined face and thereby provide play of a selected amount in the connection between said vanes.
  • each of said connecting rod means comprises two telescopically disposed members with elastic means therebetween to provide selected longitudinal resiliency.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US311816A 1971-12-03 1972-12-04 Rotary piston pump Expired - Lifetime US3895893A (en)

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DE19712160162 DE2160162C2 (de) 1971-12-03 1971-12-03 Rotationskolbenpumpe
AT933272A AT326486B (de) 1971-12-03 1972-11-02 Rotationskolbenpumpe

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US (1) US3895893A (fr)
CA (1) CA968222A (fr)
CH (1) CH545417A (fr)
FR (1) FR2164257A5 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3947164A (en) * 1973-11-02 1976-03-30 Compresseurs S.A. Rotatable machine operating as a compressor or a motor
US4082485A (en) * 1975-12-08 1978-04-04 Helmut Wolf Rotary vane-type pump
US4465445A (en) * 1980-12-06 1984-08-14 Ursula Sommer geb. Heyd Rotary pivoted vane pump
US5033429A (en) * 1990-01-11 1991-07-23 Groves James L Internal combustion engine
US5156541A (en) * 1991-05-07 1992-10-20 Lew Hyok S Revolving vane pump-motor-meter with a toroidal working chamber
GB2312249A (en) * 1996-04-20 1997-10-22 Manfred Sommer Rotary pivoted-vane pump
GB2319063A (en) * 1996-11-06 1998-05-13 David Richard Chance Rotary Fluid pump or motor
US20100119358A1 (en) * 2008-09-23 2010-05-13 Van Der Meijden Hendrikus Johannes Fluid-powered motors and pumps
US20190040867A1 (en) * 2017-08-02 2019-02-07 Poolstar Canada Limited Hydraulic rotary drive

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US94892A (en) * 1869-09-14 Edmund keith
US185069A (en) * 1876-12-05 Iiviprovement in rotary force-pumps
US249345A (en) * 1881-11-08 Rotary steam-engine
US307842A (en) * 1884-11-11 Island
US415953A (en) * 1889-11-26 Rotary engine
US453128A (en) * 1891-05-26 Water or other motor
US1263639A (en) * 1915-11-16 1918-04-23 George A Bertsch Reversible rotary motor.
US1892345A (en) * 1929-07-05 1932-12-27 Hughes Cecil Pump, compressor, engine, and the like
US2151484A (en) * 1938-05-09 1939-03-21 Fred M Nordling Rotary motor and pump
US2487449A (en) * 1944-12-21 1949-11-08 Bendix Aviat Corp Rotor and drive shaft with frangible coupling
US2584582A (en) * 1945-03-23 1952-02-05 Cleburne B Hatfield Fluid pump or motor
US2843049A (en) * 1954-01-29 1958-07-15 Sherwood Brass Works Resilient rotor pump or motor

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US94892A (en) * 1869-09-14 Edmund keith
US185069A (en) * 1876-12-05 Iiviprovement in rotary force-pumps
US249345A (en) * 1881-11-08 Rotary steam-engine
US307842A (en) * 1884-11-11 Island
US415953A (en) * 1889-11-26 Rotary engine
US453128A (en) * 1891-05-26 Water or other motor
US1263639A (en) * 1915-11-16 1918-04-23 George A Bertsch Reversible rotary motor.
US1892345A (en) * 1929-07-05 1932-12-27 Hughes Cecil Pump, compressor, engine, and the like
US2151484A (en) * 1938-05-09 1939-03-21 Fred M Nordling Rotary motor and pump
US2487449A (en) * 1944-12-21 1949-11-08 Bendix Aviat Corp Rotor and drive shaft with frangible coupling
US2584582A (en) * 1945-03-23 1952-02-05 Cleburne B Hatfield Fluid pump or motor
US2843049A (en) * 1954-01-29 1958-07-15 Sherwood Brass Works Resilient rotor pump or motor

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3947164A (en) * 1973-11-02 1976-03-30 Compresseurs S.A. Rotatable machine operating as a compressor or a motor
US4082485A (en) * 1975-12-08 1978-04-04 Helmut Wolf Rotary vane-type pump
US4465445A (en) * 1980-12-06 1984-08-14 Ursula Sommer geb. Heyd Rotary pivoted vane pump
US5033429A (en) * 1990-01-11 1991-07-23 Groves James L Internal combustion engine
US5156541A (en) * 1991-05-07 1992-10-20 Lew Hyok S Revolving vane pump-motor-meter with a toroidal working chamber
GB2312249B (en) * 1996-04-20 1999-12-29 Manfred Sommer Rotary swing-vane pump
GB2312249A (en) * 1996-04-20 1997-10-22 Manfred Sommer Rotary pivoted-vane pump
GB2319063A (en) * 1996-11-06 1998-05-13 David Richard Chance Rotary Fluid pump or motor
GB2319063B (en) * 1996-11-06 2000-12-06 David Richard Chance Rotary pump
US20100119358A1 (en) * 2008-09-23 2010-05-13 Van Der Meijden Hendrikus Johannes Fluid-powered motors and pumps
US8845276B2 (en) * 2008-09-23 2014-09-30 Zodiac Pool Systems, Inc. Fluid-powered motors and pumps
US20140356136A1 (en) * 2008-09-23 2014-12-04 Zodiac Pool Systems, Inc. Fluid-powered motors and pumps
AU2009295565B2 (en) * 2008-09-23 2015-01-22 Zodiac Pool Systems, Inc. Fluid-powered motors and pumps
US20190040867A1 (en) * 2017-08-02 2019-02-07 Poolstar Canada Limited Hydraulic rotary drive

Also Published As

Publication number Publication date
CH545417A (de) 1973-12-15
FR2164257A5 (fr) 1973-07-27
CA968222A (en) 1975-05-27

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