US3804561A - Hydraulic conveying apparatus - Google Patents

Hydraulic conveying apparatus Download PDF

Info

Publication number
US3804561A
US3804561A US00264601A US26460172A US3804561A US 3804561 A US3804561 A US 3804561A US 00264601 A US00264601 A US 00264601A US 26460172 A US26460172 A US 26460172A US 3804561 A US3804561 A US 3804561A
Authority
US
United States
Prior art keywords
combination
sealing elements
passage
housing
support means
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00264601A
Other languages
English (en)
Inventor
H Kramer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19712131305 external-priority patent/DE2131305B2/de
Priority claimed from DE2211786A external-priority patent/DE2211786A1/de
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3804561A publication Critical patent/US3804561A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation

Definitions

  • An elongated housing is formed with an axial passage therethrough the surface of which is defined by a helical screw surface.
  • a cylindrical support member with a cross section smaller than that of the passage extends through the latter and engages the surface along a helical line.
  • the support member is formedwith a transverse slot therethrough in which a plurality of closely adjacent narrow sealing elements are guided movable in direction transverse to the axis of the support member and engaging with outer ends the passage surface so that during rotation of the support member and the housing relative to each other, a fluid entering the housing at one end may be pumped under pressure through an outlet at the other end of the housing.
  • the arrangement may also be used as a fluid transmission by transmitting a drive to the housing and taking up the drive from the sup port member, or vice versa.
  • the conveying apparatus should further be constructed in such a manner that it can also efficiently be operated at a slow speed, especially during conveying of liquids of high viscosity or during conveying of granulated material such as nuts, beans or the like or mixtures of liquid and solid material, as for instance small fruits suspended in juice, motar and cement before the same are hardened.
  • the conveying apparatus should be constructed in such a manner that, especially if it serves as pump for,
  • the conveying apparatus mainly comprises an elongated housing having an axis being formed withan axial passage therethrough defined by a helical screw surface, substantially cylindrical supportmeans extending in the direction of the axis through the passage and having a crosssection smaller than that of the passage and being arranged in the latter so as to, engage the aforementioned surface substantially tangentially along a helical line, and a plurality of sealing elements mounted on the support means, extending diagonally through the passage and engaging the aforementioned surface.
  • the plurality of sealing elements are arranged closely adjacent to each other in the direction of the axis and being movable relative to each otherin a direction transverse to the axis.
  • Each of the sealingelements has a width in the direction of the axis which is considerably smaller than the pitch of the screw surface.
  • the sealing elements will slide with the outer ends thereof along the surface defining the passage through the housing. Since the passage through the housing is defined by a. helical screw surface, and every cross section of this passage is eccentrically arranged with regard to the cylindrical support means, there will result a to and fro movement of the sealing elements in direction transverse to the housing axis during rotation of the cylindrical support means and the sealing elements thereon with respec'tto the housing. A liquid or a similar medium located in the passage is thereby conveyed in axial direction of the latter during rotation of the cylindrical support means and the sealing elements thereon due to the screw configuration of the inner surface of the housing.
  • the medium to be. conveyed is so to speak forwardly screwed" through the housing.
  • the sealing elements will sealeach housing cross section at two opposite points since the sealing elements will sealingly engage with the outer ends thereof the surface of the passage through the housing.
  • the helical screw surface which defines the passage through the housing extends only through a part of a single convolution of the helix, a small "conveying pressure will result, which can however be increased by extending the helical screw surface through a plurality of convolutions. Due to the positive control of the movement of the sealing elements it is possible to operate such a pump in advantageous manner at relatively low speed while still obtaining a continuous conveying of the medium passing therethrough. In this wayit is pos sible to use the conveying apparatus not only to pump liquids but also to convey granulated material or a mixture of liquids and solid bodies.
  • FIG. 1 is an axial cross section through an hydraulic conveying apparatus according to the present invention in which a relative movement between the housing and the cylindrical support means carrying the sealing elements is obtained by rotating the housing which in this case forms part of the rotor of an electrical motor;
  • FIG. 2 is a cross section along the line Il--II of FIG.
  • FIG. 3 is a longitudinal cross section through another to 3 of the'same, it will be that the hydraulic conveying apparatus in which the relative movement between the housing and the cylindrical support means carrying the sealing elements is carried out by rotating the support means with the sealing elements relative to the stationarily held housing;
  • FIG. 4 is a cross section taken along the line IV-IV of FIG. 3;
  • FIG. 5 isa cross section taken along the line VV in FIG. 3;
  • FIG. 7 is a transverse cross section of a modified construction in which the sealing elements cross each other;
  • FIG. 3 is a perspective view showing the construction of two crossing sealing elements
  • FIG. 9 is an axial cross section through a further modification and illustrating a conveying apparatus in which the housing is formed wit-h two oppositely convoluted helical screw surfaces;
  • FIG. 10 is an axial cross section through a further modification in which the housing as well as the cylindrical support means with the sealing elements thereon are both turnably mounted so that drive of one component will result in a rotation of the other component;
  • FIG. 11 is a transverse section of a modification of the construction shown in FIG. 1 in which one of the crossing sealing elements is constitutedby two separate parts having inner ends speced from each other;
  • FIG. 11a is an axial cross section of a modification shown in FIG. 11;
  • FIGS. 11b and 110 are modifications of an end portion of the construction shown in FIG. 1 la, drawn to an enlarged scale;
  • FIG. 11d is a cross section similar to FIG. 11 and showing a further modification
  • FIG. 12 is an axial cross section of a press form for manufacturing a screw bushing adapted to form the passage through a housing;
  • FIG. 13 is a cross section taken along the line XIII- XIII of FIG. 12;
  • FIG. 14 is an axial cross section through a further modification of a conveying apparatus in which the passage through the housing is constituted by a screw bushing;
  • FIG. 15 is a cross section taken along the line vXV-XV of FIG. 14;
  • FIG. 16 is an axial cross section of a further modification in which the passage through the housing is an annular passage constituted by two concentrically arranged screw bushings;
  • FIG. 17 is a cross section taken along the line XVII- XVII of FIG. 16;
  • FIG. 18 is a partial axial cross section of a screw bushing with a slightly elastic connecting flange
  • FIG. 19 is a partial longitudinal cross section through a central portion of a conveying apparatus in which the sealing elements are arranged in groups spaced from each other.
  • a cylindrical support member or a support means 3 extends axially through the aforementioned passage in the housing and as evident from the cross sections shown in FIGS. 46, the cylindrical support member 3 has a diameter which is smaller than the respective cross sections through the passage in the housing.
  • the cylindrical support member 3 is arranged within the passage 4 in such a manner that the periperhal surface of the cylindrical support member 3 will tangentially engage the inner housing surface 4 along a helical line, whereas opposite the line of engagement, the cylindrical support member 3 is spaced at each transverse cross section from the inner housing surface 4 so that practically successive inner surface portions of the housing are eccentrically arranged with respect to the cylindrical support member 3, whereby these eccentrically arranged sections are, in axial direction of the apparatus 1, helically displaced with respect to each other.
  • the cylindrical support member 3' is at least in the region of the helically convoluted portion of the passage through the housing formed with an axially ex tending slot 5 therethrough in which a plurality of sealing elements 6, which abut with side faces thereof against each other, are arranged for movement in transverse direction to the axis of the support member 3' and which have in this transverse direction a length L which is equal to the diameter of the axial passage through the housing.
  • the cylindrical support member 3' together with the sealing elements 6 constitute the rotor 3 of the apparatus shown in FIG. 3.
  • each sealing element in axial direction of the housing is considerably smaller and only a small fraction of the pitch of the helical screw surface defining the passage through the housing so that for each pitch of the helical screw surface a relative great number of closely adjacent sealing elements are provided which, in correspondence with the axially helically changing eccentricity of the inner surface 4 of the housing with respect to the support member 3' will be moved relative to each other in transverse direction when the rotor 3 is rotated relative to the housing.
  • each cross section of the inner surface 4 is sealed twice by the respective sealing element 6 since the latter engages with opposite ends the inner housing surface 4. This will considerably reduce any leakage losses.
  • the sealing elements 6 are arranged parallel to each sealing elements.
  • the width of the sealing elements has therefore to be chosen under consideration of both of the aforementioned factors.
  • the slot 5 formed through the cylindrical support member 3' is divided into two portions by an insert 7 located in a central portion of the slot and held therein by a screw 8 or the like in fixed position.
  • the insert 7 is dimensioned to completely fill the cross section of the slot. This will reinforcev the cylindrical support member 3', the strength of which is weakened by the slot therethrough, especially if the slot has a considerable length, and at the same time, the insert 7 will also provide an abutment or a thrust member for the group 6a of sealing elements 6 which are subjected to a certain axial force. If all sealing elements 6 of a relatively long rotor would abut only against each other, then the friction of the sealing elements produced during relative movement thereof with respect to each other might be raised to a detrimental amount.
  • the last sealing element as viewed in the direction of movement of the medium through the conveying apparatus of one group of seal elements will abut against the insert 7 to thereby prevent an undue increase of the total friction between the side faces of the sealing elements.
  • a rotor shaft 14 integral with the cylindrical support member 3' extends through a bore in one end of the housing 2.
  • the shaft portion extending through the bore of the housing is sealed by a plurality'of sealing rings I5 which are compressed by means of a bushing threaded into the housing bore.
  • the right end, as viewed inFIG. 3, of the shaft 14 is connected by means of a coupling to a motor, only partlyshown in FIG. 3, for driving the rotor.
  • a bearing 16 is provided for the left end, as viewed in FIG. 3, of the cylindrical support member 3' and the bearing 16 is integral with a cover 17 which closes the left end, of the passage through the housing.
  • the medium inlet 12 is arranged, in the modification shown in FIG.
  • the bore 18 has a diameter which is greater thanthe width of the longitudinal slot 5.
  • Each of the sealing elements 6 may be formed of two separate parts, as indicated by the dotted lines shown in FIG. 4 through the sealing element, so that between the inner ends of the two part sealing element a gap may be provided which is transversed by the central bore 18 and which is thereby filled with the fluid me-' dium under pressure.
  • FIG. 11 shows such a modified sealing element 6a which is interrupted in its middle region 20 so that this sealing element 6a is composed of two individual parts 6b between the inner ends of which the space 20 is provided.
  • FIG. 11 illustrates also a fur ther sealing element 21a which extends transverse to the sealing element 6a, which however may also be omitted. The function of the transverse sealing element will be described later on in detail.
  • the sealing element 6a is formed of two individual parts it is advantageous to omit the transverse bore 19 mentioned above so that the two parts of the sealingelement are pressed by the fluid medium under pressure in the axial bore 18 apart, whereby even if the outer ends of the sealing element will wear, a perfect seal against the surface 4 will be obtained.
  • the thus formed closed space may be provided atone end of the axial bore 18 with a valve as shown in FIG.
  • the arrangement of such a closed space is especially advanantageous if, on the one hand, it is desired to press the outer ends of two-part sealing elements against the surface 4 and if, on the other hand, a medium is conveyed which contains solid particles or the like so that the medium is not very well adapted to be fed into the bore 18 and to provide a pressure against the inner ends of the twopart sealing elements.
  • FIG. llc it is also possible to close one end of the central bore 18 by a movable piston 81 which for instance may be under the pressure of a compression spring 82 tending to move the piston into the bore 18.
  • a movable piston 81 which for instance may be under the pressure of a compression spring 82 tending to move the piston into the bore 18.
  • this pressing apart of the two-part sealing elements is accomplished by the elastic members inserted between the inner ends of the two-part sealing elements which will assure that the outer ends of the two-part sealing elements will be pressed against the inner surface of the housing with the necessary force so that during rotation of the rotor again a positive to and fro movement of the two-part sealing elements relative to the housing is obtained.
  • FIGS. 7, 8 and 11 illustrate a modifiedv construction in which for each cross section of the passage through the housing at least two sealing elements which cross each other are arranged, as shown by the sealing elements 21 in FIGS. 7 and 8, respectively, by sealing elements 6a and 21a as shown in FIG. 11.
  • both of the sealing elements are one-piece sealing elements which have, as best shown in FIG. 8, each anintermediate portion 22 of reduced cross section which is half of the cross section of the remaining sealing element and this reduced cross section 22 of each sealing element has an appropriate length corresponding to the relative movement of the crossing sealing elements.
  • Each cross section of the passage is thereby sealed at four points, which increases the efficiency of the conveying apparatus especially during conveyance of'fluids.
  • themodification as shown in FIG.
  • one of the crossing sealing elements that is sealing element 6a, is formed, as described before, from two separate parts 6b, the inner ends of which are subjected to pressure of fluid in the central bore 18, whereas the other sealing element 21a is integral and extends through the space between the two part 6b-of the sealing element 6a.
  • FIGS. 7, 8 and l 1 Such sealing element construction as shown in FIGS. 7, 8 and l 1 may be used not only in the abovedescribed embodiment illustrated in FIG. 3 but also in the embodiments illustrated in FIGS. 1, 9 and 10 which will be described later on.
  • Adjacent sealing elements may also be formed from different metals or difierent materials especially if mediums are to be conveyed which cuase considerabld abrasion.
  • the path of the medium through the conveying apparatus is indicated for instance in FIG. 3 by the dashdotted line w and the arrows Pf.
  • the medium passes through the passage in the housing 2 along a helical path which in the projection of FIG. 3 is shown in a zigzag line in the region of the rotor.
  • FIG. 9 Aconveying apparatus construction similar to that shown in FIG. 3 is illustrated in FIG. 9.
  • the construction shown in FIG. 9 differs from the above-described construction illustrated in FIG. 3 mainly in that the passage through the housing is constituted by two oppositely convoluted helical screw surfaces 9a and 9b, and in which medium inlets 12 are provided at the ends 10 and 11" of the two helical screw surfaceswhich face away from each other, whereas a single outlet 13 is provided between the adjacent ends of the aforementioned surfaces.
  • a common rotor 3a is coaxially arranged in the interior of the two aforementioned helical screw surfaces 9a and 9b and the rotor is again provided with sealing elements as described before in connection with FIG. 3.
  • a shaft 14 integral with the rotor 30 projects through the bore in the right end, as viewed in FIG. 9, of the housing 2a and sealing means 15 are provided in this bore which seal the shaft against the housing.
  • the shaft 14 is connected to a motor, not shown in FIG. 9, to rotate the rotor 3a relative to the stationary held housing 2a. Since the two portions 9a and 9b of the passage through the housing are convoluted in opposite directions, the axial forces produced on the rotor will equalize each other. However, in this construction it may also be advantageous to provide a central bore 18' and an additinal bore 118 through the rotor 3a which respectively communicate with the interior of the passages at different pressure regions through transverse bores 19 and 119 as shown in FIG. 9.
  • FIGS. 1 and 2 A further embodiment of a converging apparatus according to the present invention is illustrated in FIGS. 1 and 2.
  • the cylindrical support member 23, which corresponds to the member 3' of the rotor 3 of the embodiment shown in FIG. 3 which carries in an axial slot therethrough the sealing elements 6, is arranged stationarily, whereas the surrounding outer housing 23a provided with the axial passage therethrough which is defined by a helical screw surface is surrounded by and fixed to a rotor 24 of an electromotor 25.
  • the rotor 24 of the electromotor is separated by an annular gap 26 from the surrounding stator 27.
  • the stator is provided with the usual stator winding 28 and surrounded by the motor housing 29.
  • the inlet 12a and the outlet 13a are arranged coaxially with the axis of the cylindrical support member 23.
  • the inlet and the outlet are provided in the covers 30 and 31 which are connected by screws 32 to the motor housing 29 and which close respectively axial openings in the housing which substantially correspond to the inner diameter of the rotor of the electromotor, so that the complete rotor may be easily assembled with anddisassembled from the other components of the apparatus.
  • annular spaces 34 and 35 are provided in the region of the inlet and the outlet, which spaces are traversed by the medium to be conveyed and which are connected with each other through the annular gap 26 between rotor 24 and stator 27.
  • the aforementioned annular spaces 34 and 35 are connected respectively downstream of the i inlet 12a with the latter by a transverse passage 36 and upstream of the outlet 13a by a corresponding transverse passage 36 so that the fluid medium may circulate through the annular spaces 34 and 35 and the annular gap 26 as indicated by the arrow Pf 2 and Pf 3.
  • the medium under pressure passes through the passage 36 adjacent to the outlet 13a and at high pressure into the annular space 35 and then through the annular gap 26 into the annular space 34 and back through the other cross passage 36 into the main passage. Due to the continuous stream of fluid medium through the annular gap 26 an advantageous cooling of the motor is obtained.
  • FIG. 10 A further embodiment is illustrated in FIG. 10.
  • the cylindrical support member 43 which carries the sealing elements 6 in an axially extending slot, as described before, as well as the outer housing 42 provided with the central passage therethrough the surface of which is defined by a helical screw surface are both turnably mounted, whereby either the housing or the rotor, constituted by the member 43 with the sealing elements 6, are connected to a drive 44, whereas the other of the two aforementioned components is provided with means 45 to take up a drive therefrom.
  • the cylindrical support member 43 which carries the sealing elements 6 in an axially extending slot, as described before, as well as the outer housing 42 provided with the central passage therethrough the surface of which is defined by a helical screw surface are both turnably mounted, whereby either the housing or the rotor, constituted by the member 43 with the sealing elements 6, are connected to a drive 44, whereas the other of the two aforementioned components is provided with means 45 to take up a drive therefrom.
  • the rotor constituted by the cylindrical support member 43 and the sealing elements 6 are driven from a motor 44 by means of a shaft'44a, whereas the housing 32 carries a coupling disk 45 provided for instance with two coupling pins 46 so that the housing may be connected to a member to be driven.
  • the housing 42 part of the housing which defines the helical screw surface 4 is formed from a different material than the remainder of the housing.
  • the helical screw surface which defines the passage of the housing is formed by a thin walled tube or a screw bushing, as shown at 5 4 in the embodiment illustrated in FIG. 14.
  • FIGS. 12 and 13 schematically illustrate the manner in which such a screw bushing 54 may be formed from a tube 55.
  • the apparatus 56 illustrated in FIGS. 12 and 13 comprises a form 'having a central portion 57 formed with a central passage therethrough having an inner surface corresponding to the outer surface of the screw bushing 54 to be produced.
  • the member 57 is preferably a two-part member 57a and 57b, as clearly shown in FIG. 13, and a pair of covers 59 and 60 abut against the end faces of the central member 57 and are pressed thereagainst by bolts and nuts as clearly illustrated in FIG. 12.
  • the cover 59 is provided with a central bore 61 through which a fluid under high pressure to the motor 44 and to provide a coupling on the member 43.
  • the ends of the tube are sealingly engaged by the inner surfaces of the aforementioned covers or at least one or a plurality of ventilating passages 78 are provided to permit air surrounding-the outer surface of the tube 55 to escape to the exterior of the form.
  • the tube 55 which is shown in FIGS. 12 and 13 in undeformed condition, is deformed under the influence of the pressure medium 62 passed into the interior of the tube to the configuration as indicated in dotted lines in FIG. 12. In this manner, an exact configurated screw bushing 54 with excellent surface quality at its inner face 4 may be obtained.
  • screw bushing Due to the thin wall of the screw bushing a relatively expensive material for forming the same may be used without unduly increasing the price thereof.
  • Another possibility to form the screw'bushing is to form the same from hard metal alloys for inseance from sintered or preferably cast hard metal alloys.
  • Such screw bushings may for instance be cast according to the lost wax method with sufficient precision and they will have a very high resistance against abrasion, which is especially advantageous during conveying of cement paste, whereby the cost of such a screw bushing inserted for instance in an outer housing 102, as shown in FIG. 14, is relatively small.
  • the outer surface of the screw bushing 54 is surrounded by a helical passage 72 which is encompassed by a corresponding portion of the housing 102 of the conveying apparatus illustrated in FIG. 14.
  • the helical passage 72 is adapted to receive or to be flown through by, a fluid'medium which will impart an outer pressure and/or to serve to cool, respectively to heat the screw bushing 54.
  • an inlet and outlet 73 and 74 are provided in the outer housing 102 which surrounds the screw bushing.
  • the outer housing 102 is provided with an axial bore 110 the diameter of which is so dimensioned that the screw bushing 54 will engage and thereby be supported along a helical line in the bore 110 of the housing.
  • TI-Ie screw bushing is preferably provided at its left end, as viewed in FIG. 14, and as also shown in the partial view of FIG. 18 with a radially extending attaching flange 11 1.
  • This flange 111 is in axial direction slightly yeildable so as to compensate for different axial expansions of the screw bushing and the surrounding housing 102 which will especially occur when the screw housing and the outer housing have different temperatures.
  • Such flange 111 may be provided on opposite ends of the screw bushing 54 but, advantageously, and as shown in FIG. 14, only one end of the screw bushing is provided with a flange 111 whereas the other end, shown in FIG. 14 as the right end, is cylindrically formed so as to be movable in axial direction along a sealing ring 112 located in an annular groove of the outer housing 102 and surrounding in a sealed manner the cylindrical end of the screw bushing.
  • FIGS. 16 and 17 A further embodiment according to the present invention is illustrated in longitudinal and transverse cross-sections in FIGS. 16 and 17.
  • the conveying space forthe medium to be conveyed by the apparatus is in the form of an annular space having inner and outer surfaces, formed by a pair of coaxial screw bushings 154 and 254.
  • a likewise annular support member or support means 103 which carries the sealing elements 6 is coaxially and rotatably arranged within the thus formed annular space 120.
  • the support means 103 has a cross section in form of a hollow cylinder and is provided in the region 6 with axial extending transverse slots in which the sealing elements 106 are guided in the manner as described before. As evident from FIGS.
  • the annular support means 103 is provided at the sides thereof facing the suction side of the conveying apparatus 101 with an endwall 121 from which a drive shaft 122 extends in axial direction for turning the support means 103 about its axis.
  • the endwall 121 is provided with a plurality of passages 124 for passage of p the medium to be conveyed therethrough.
  • the medium to be conveyed enters the apparatus through the inlet 121, and as indicated by the arrows Pf 60and Pjfil, the medium to be conveyed may pass .in the region radially outwardly of the support means 103 as wellas through the passages 124 into the region 126 which is located radially inwardly of the support means.
  • the medium passes therefore in two streams through the apparatus whereby one stream, that is the inner stream in the region 126 is adjacent the screw bushing 254 and the other outer stream in the region 127 is adjacent the outer screw bushing 154, as clearly shown in FIGS. 16 and 17.
  • the support means 103 may be mounted only at one end thereof, for instance at the end shown as the left end in FIG. 16, by means of the shaft 122 in the region of the suction side of the conveying apparatus 101.
  • the support means 103 is mounted in an additional bearing on the pressure outlet side of the apparatus in the neighborhood of the outlet 130.
  • an annular bearing 301 is provided which is fastened to the housing 102 and which is formed with an annular groove 302 in which the right end of the support means 103 is turnably mounted. This will assure proper mounting and sealing of the support medium means 103.
  • the common outlet 130 is provided at the pressure end of the conveying apparatus 101 and the pressure medium passes through an annular space 131 into the outlet 130.
  • the apparatus preferably includes further a cylindrical member 132 projecting in axial direction from the cover which closes the housing 102 at the right end, as viewed in FIG. 16, and which carries the screw bushing 254.
  • each of the sealing elements 6 may be formed of two parts of equal length as evident from the parting line 206 in FIGS. 14 and 15.
  • the parting line 206 is located in the region of the bore 18 which is filled with a fluid under pressure.
  • the bore 18 does not necessarily extend over the whole axial length of the screw bushing and be closed at one end as shown in FIG. 14, but the central bore 18 may also communicate through a cross bore 19 with the space of higher pressure, as for instance shown in FIG. 3. It is also possible to arrange two or more such bores through the support means which are separated from each other. This is shown in FIG. 9 for the separate bores 18 with the outlet 19, and 118 with the outlet 119.
  • the medium to be conveyed can pass with the pressure prevailing in the region of the outlet 13 through the bores 18 to the bore outlets 19 which are located in the region of an intermediate pressure,-and the sealing elements 6 which are located between.
  • these bores 19 and the outlet 13 will therefore, in the region of their gaps 206, be impinged with relative high pressure.
  • the sealing elements 6 shown in FIG. 9 are made in this arrangement also as two part sealing elements 6a and 6b as described in connection with FIG. 14. Such an impingement of the sealing elements with high pressure fluid would cause in the region of the inlets l2 unnecessarily high friction between bushing and sealing elements and wear at the outer ends of the latter. Therefore, a second bore 118 is provided which has its inlet 119 in the region of medium pressure and its outlet at the region of the low pressure so that the sealing elements between the transverse bores 119 and the inlets 12 of the apparatus are impinged at the inner ends thereof with a lower pressure.
  • FIG. 19 illustrates a further advantageous modification of the apparatus according to the present invention.
  • the sealing elements 6 are divided in three separate groups 306, 307 and 308.
  • the sealing elements are arranged closely adjacent to each other so that side faces of the sealing elements engage .each other and they are guided for movement in direction transverse to the axis of the apparatus in axially extending transverse slots through the cylindrical support means3.
  • these slots 5 may be constructed as a sin gle, axially extending slot which is divided into separate portions by inserts 7a and 7b which are held in the slots by transverse screws or the like as illustrated for instance in FIG. 5.
  • the essential advantage of dividing the sealing elements in individual groups 306, 307 and 308 resides in the fact that the pressure of the medium to be conveyed and acting on a sealing element 6 is not transmitted in axial direction through all sealing elements.
  • the pressure of the medium to be conveyed and acting on a sealing element 6 is not transmitted in axial direction through all sealing elements.
  • This pressure will, however, not be transmitted to the sealing elements of the other two groups since the rightmost sealing element of the group 306 abuts at 309 against the insert 7a.
  • the pressure on the sealing elements of the group 308 of sealing elements may for instance be between 0-7 atm. as indicated at P 7.
  • the sealing elements of the group 307 are therefore sub jected to axial pressures between 14 and 7 atm. and the sealing elements of the group 308 will be subjected to a pressure between 7 and 0 atm.
  • the individual sealing elements will therefore be subjected only to partial pressures of the total pressure acting in axial direction so that they are subjected to less friction and less wear. It is mentioned at this occasion that the relative movement of adjacent sealing elements is usually relatively small which will reduce the wear on the side faces of the sealing. elements.
  • the conveying apparatus has the advantage that the apparatus can be operated with a high as well as a low rotational speed depending on the medium to be conveyed. Especially for mediums of low viscosity it is possible, depending on the axial length of the apparatus, to obtain relatively very high pumping pressures. This is especially the case if a great number of sealing elements 106 is provided as for instance shown in the embodiment of FIGS. 16 and 17. This embodiment is especially advantageous if relatively great amounts of mediums have to be conveyed. On thetother hand, it is also possible with the apparatus according to the present invention, espe cially with the embodiment shown in FIG. 14, to con vey mediums of very high viscosity, for instance cement paste. Thereby it is advantageous if the elements which are subjected to greatest wear may be easily exchanged without disassembling the whole apparatus and in which for instance the passage for the medium through the housing is formed bya separate screw bushing or bushings.
  • a combination comprising elongated housing means having an axis being formed with an axial passage there through defined by a helical screwsurface; substantially cylindrical support means extending in the direction of said axis through said passage and having across section smaller than that of the passage, said support means being arranged in said passage soas to engage said surface substantially tangentially along a helical line; and a plurality of sealing elements mounted on said support means and extending; diagonally through said passage and engaging said surface, said plurality of sealing elements being arranged closely adjacent to each other in the direction of said axis and being movable relative to each other in a direction transverse to said axis, each of said sealing elements havinga width in the direction of said axis which is considerably smaller than the pitch of said screw surface.
  • said elongated housing means is closed at one and open at the other end thereof and including a bearing for said cylindrical support means at the closed end of said housing means, a drive shaft extending through the other end of said housing means and being connected to said cylindrical support means, and sealing means around said drive shaft in said other end of said housing means.
  • each of said sealing elements comprises two parts having inner ends located in said slots spaced from each other and resilient means sandwiched between said inner ends of said two parts for biasing the latter away from each other.
  • said support means is provided with two axially extending slots tberethrough arranged at an angle with respect to each other, said sealing elements being arranged in said two slots so that adjacent sealing elements in one slot cross corresponding sealing elements in the other slot, each of said sealing elements having in the region where it crosses the other sealing element a portion of reduced thickness so that the combined thickness of the crossing portion is equal to the thickness of the remainder of each sealing element, the length of the portion of reduced thickness corresponding to the relative movement of the crossing sealing elements.
  • said support means is provided with at least two axially extending slots arranged at an angle with respect to each other, said sealing elements being arranged in said slots so that adjacent sealing elements in one slot cross corresponding sealing elements in the other slot, at least one of each of the crossing sealing elements being made from two parts having inner ends spaced from the corresponding crossing sealing element, and means for biasing said inner ends away from each other.
  • sealing elements have parallel side faces and are arranged in said slots so that the parallel side faces of adjacent sealing elements engage each other.
  • said passage surface is defined by two oppositely convoluted screw surfaces aligned along a common axis and spaced in axial direction from each other, and including a pair of fluid inlet means respectively arranged at the ends of said screw surfaces which face away from each other and a common fluid outlet means communicating with said passage at the space between the facing ends of the two screw surfaces.
  • cylindrical support means is formed with an axial bore having a diameter greater than the thickness of said sealing elements, each of said sealing elements being formed of two parts having inner ends in said bore, and including a fluid medium under pressure in said bore acting on said inner ends of the two-part sealing elements for pressing the outer ends against said surface.
  • said housing means comprises outer annularwall means and a bushing located within said outer annular wall means, said passage with said helical screw surface being formed by said bushing.
  • said bushing has a thin wall of substantially uniform thickness and being provided at the outer periphery thereof with a surface corresponding to the inner surface thereof to form between the inner surface of the outer wall means and the outer surface of said bushing a passage adapted to receive fluid for providing pressure on the outer surface of said bushing, respectively for cooling or heating the latter.
  • annular wall means has an inner cylindrical surface and wherein the outer surface of said bushing engages said inner cylindrical surface along a helical line.
  • said passage through said housing means comprises an annular passage the inner and outer surfaces thereof being defined by helical screw surfaces, said support means comprising an annular cylindrical member coaxially arranged in said passage.
  • said housing means comprises two coaxial bushings on which said inner and outer surfaces are provided and wall means supporting said bushings.
  • annular cylindrical member is provided with at least one axially extending slot therethrough, said sealing elements extending through and being guided in said slot for movement in said transverse direction.
  • annular cylindrical member is provided with a plurality of axially extending slots therethrough which are angularly displaced from each other and a plurality of axially adjacent sealing elements extending through each of said slots and being guided therein for movement in said transverse direction.
  • said housing means has a pair of end walls one of which is provided with inlet means and including a connecting channel at the end of said passage adjacent to the other end wall and communicating with outlet means provided in said other end wall.
  • annular cylindrical member has at one end thereof a' transverse endwall formed with openings therethrough for the passage of the medium to be conveyed into an inner region of said axial passage through said housing means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US00264601A 1971-06-24 1972-06-20 Hydraulic conveying apparatus Expired - Lifetime US3804561A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19712131305 DE2131305B2 (de) 1971-06-24 1971-06-24 Rotationskolbenpumpe
DE2211786A DE2211786A1 (de) 1972-03-11 1972-03-11 Foerdervorrichtung, insbesondere foerderpumpe

Publications (1)

Publication Number Publication Date
US3804561A true US3804561A (en) 1974-04-16

Family

ID=25761317

Family Applications (1)

Application Number Title Priority Date Filing Date
US00264601A Expired - Lifetime US3804561A (en) 1971-06-24 1972-06-20 Hydraulic conveying apparatus

Country Status (3)

Country Link
US (1) US3804561A (enrdf_load_stackoverflow)
FR (1) FR2143500B1 (enrdf_load_stackoverflow)
IT (1) IT956647B (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4558991A (en) * 1985-01-10 1985-12-17 Barr Robert A Wave pump assembly
WO2014094715A3 (de) * 2012-12-19 2014-12-04 Netzsch Pumpen & Systeme Gmbh Mehrfachpumpe
WO2016198037A1 (de) * 2015-06-12 2016-12-15 Netzsch Pumpen & Systeme Gmbh Pumpengehäuse für eine exzenterschneckenpumpe und damit ausgestattete exzenterschneckenpumpe
WO2022122858A1 (de) * 2020-12-09 2022-06-16 Volkswagen Aktiengesellschaft Pumpenvorrichtung für ein hydraulisches system eines kraftfahrzeugs, hydraulisches system
US20250237214A1 (en) * 2021-10-25 2025-07-24 Graco Minnesota Inc. Progressive cavity pump with pump radially within electric motor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZA79440B (en) * 1978-02-10 1980-09-24 Oakes Ltd E T Drive arrangement
EP0184938B1 (en) * 1984-12-12 1990-03-28 Robert A. Barr Wave pump assembly
BE1000978A5 (fr) * 1988-01-18 1989-05-30 Dragages Decloedt & Fils Sa Motopompe integree a moteur electrique et pompe rotative.

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2585406A (en) * 1947-08-04 1952-02-12 Benjamin N Tager Solid cross vane rotary pump
US3203350A (en) * 1962-11-05 1965-08-31 Robbins & Myers Helical multiple pump

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2585406A (en) * 1947-08-04 1952-02-12 Benjamin N Tager Solid cross vane rotary pump
US3203350A (en) * 1962-11-05 1965-08-31 Robbins & Myers Helical multiple pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4558991A (en) * 1985-01-10 1985-12-17 Barr Robert A Wave pump assembly
WO2014094715A3 (de) * 2012-12-19 2014-12-04 Netzsch Pumpen & Systeme Gmbh Mehrfachpumpe
CN104822942A (zh) * 2012-12-19 2015-08-05 耐驰泵及系统有限公司 多头泵
JP2016505756A (ja) * 2012-12-19 2016-02-25 ネッチュ プンペン ウント システーメ ゲーエムベーハーＮｅｔｚｓｃｈ Ｐｕｍｐｅｎ ＆ Ｓｙｓｔｅｍｅ Ｇｍｂｈ 多連ポンプ
AU2013362364B2 (en) * 2012-12-19 2016-07-07 Netzsch Pumpen & Systeme Gmbh Multiple pump arrangement
WO2016198037A1 (de) * 2015-06-12 2016-12-15 Netzsch Pumpen & Systeme Gmbh Pumpengehäuse für eine exzenterschneckenpumpe und damit ausgestattete exzenterschneckenpumpe
CN107743548A (zh) * 2015-06-12 2018-02-27 耐驰泵及系统有限公司 用于偏心螺杆泵的泵壳和装备有该泵壳的偏心螺杆泵
CN107743548B (zh) * 2015-06-12 2019-05-17 耐驰泵及系统有限公司 用于偏心螺杆泵的泵壳和装备有该泵壳的偏心螺杆泵
US10767646B2 (en) 2015-06-12 2020-09-08 Netzsch Pumpen & Systeme Gmbh Pump housing for an eccentric screw pump and an eccentric screw pump equipped therewith
WO2022122858A1 (de) * 2020-12-09 2022-06-16 Volkswagen Aktiengesellschaft Pumpenvorrichtung für ein hydraulisches system eines kraftfahrzeugs, hydraulisches system
US20250237214A1 (en) * 2021-10-25 2025-07-24 Graco Minnesota Inc. Progressive cavity pump with pump radially within electric motor

Also Published As

Publication number Publication date
FR2143500B1 (enrdf_load_stackoverflow) 1973-07-13
IT956647B (it) 1973-10-10
FR2143500A1 (enrdf_load_stackoverflow) 1973-02-02

Similar Documents

Publication Publication Date Title
US3817664A (en) Rotary fluid pump or motor with intermeshed spiral walls
US3203350A (en) Helical multiple pump
US3216362A (en) Flexible ring pump drive device
US4551080A (en) Variable displacement sliding vane pump/hydraulic motor
US3034446A (en) Hydraulic pump or motor
US1964330A (en) rotary pump
US3810721A (en) Rotary piston machine with bypass regulation
US3804561A (en) Hydraulic conveying apparatus
CA1102178A (en) Eccentric disc pump
US3690793A (en) Gear pump with lubricating means
US3539282A (en) Gear pump or motor
US932033A (en) Johannes krone
US3870437A (en) Planetary gear pump
US2880677A (en) Variable volume vane pump
US3473437A (en) Rotary slide valve for fluid motors and pumps
US2446194A (en) Pump construction
US3619089A (en) Fluid-pressure device
US1793577A (en) Rotary machine
US7192264B2 (en) Hyrdraulic motor
US3106897A (en) Fixed displacement variable discharge pump
US4484870A (en) Planetary hydraulic motor with irregularly arranged valving parts
US1670229A (en) Combined variable-capacity and constant-volume pump
US2336344A (en) Rotary pump
US2662481A (en) Priming means for centrifugal pumps
US3363577A (en) Shaft sealing for spinning pump