EP2359008B1 - Rolling fluid pump - Google Patents

Rolling fluid pump Download PDF

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Publication number
EP2359008B1
EP2359008B1 EP09810836.8A EP09810836A EP2359008B1 EP 2359008 B1 EP2359008 B1 EP 2359008B1 EP 09810836 A EP09810836 A EP 09810836A EP 2359008 B1 EP2359008 B1 EP 2359008B1
Authority
EP
European Patent Office
Prior art keywords
pump
rotor
replenishing
shaft
vane
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.)
Not-in-force
Application number
EP09810836.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2359008A2 (en
Inventor
Miroslav Sedlacek
Karel Brada
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.)
Czech Technical University In Prague
Original Assignee
Czech Technical University In Prague
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
Application filed by Czech Technical University In Prague filed Critical Czech Technical University In Prague
Publication of EP2359008A2 publication Critical patent/EP2359008A2/en
Application granted granted Critical
Publication of EP2359008B1 publication Critical patent/EP2359008B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D11/00—Other rotary non-positive-displacement pumps

Definitions

  • the invention relates to fluid pumps which consist of a cylindrical or conical stator, in which a rotor of a rotary shape is mounted on a shaft.
  • the rotor touches the stator and can roll along its inner wall.
  • fluid pumps based on the dynamic principle that comprise of a stator; their working element is rotating blade or a rotating blade cascade.
  • Displacement pumps with a piston-shaped working element are also known.
  • the state of the art technology includes viscosity pumps based on the principle applied also in fluid dynamic radial and axial bearings, i.e. using the lifting force generated in the wedge-shaped gap of the cylindrical or planar plug or runner suspension bearing.
  • This principle is also used for rolling pumps, e.g. in the Czech patent No. 284483 called “Fluid Rolling Machine” and the European patent EP1015760 B1 called “Rolling Fluid Machine”.
  • the current technical practice knows a pump comprising a fluid storage tank provided with an inlet and at least with one outlet nozzle, where a rolling rotor of a rotary shape is mounted on a supporting device in the area of the outlet nozzle.
  • This machine can then operate not only as a turbine, but also in reverse as a rolling fluid pump, where the increase of the pressure of the flowing fluid is achieved by centrifugal forces as well as by viscosity forces in the wedge-shaped gap between the rolling rotor and the stator.
  • the flow in the wedge-shaped gap is analogous to the well-known Taylor vortices in a concentric cylindrical gap.
  • the solution of the rolling fluid motor designed according to the Czech utility model No. 7606 Hydraulic Motor and the European patent EP1082538 B1 Hydraulic Motor can be used for fluid transport.
  • the solution under the Czech patent No. 294708 called "Rolling Fluid Turbine” is known as a fluid pump if the turbine is equipped with a rotary drive unit.
  • the pumps briefly mentioned in the previous paragraph have a principal disadvantage because they are very complicated.
  • some types do not achieve, in some marginal areas of parameters such as very small flow rates and in particular small transport heads, as favourable ratio of energy input and output as rolling fluid machines in the pump mode.
  • rolling fluid pumps are less efficient and increasing revolutions do not lead to an adequate improvement of parameters and their efficiency.
  • the fluid supply to the working space is associated with energy losses, i.e. declining pressure and the ensuing imperfect filling of the wedge-shaped working space.
  • the goal of the proposed technical solution is to adjust the rolling pump to increase its efficiency, i.e. to make sure that the supplied input mechanical energy is transformed into hydraulic energy with higher efficiency and higher outputs.
  • a rolling fluid pump comprising a stator, fitted with at least one fluid inlet opening and at least one fluid outlet opening, where at least one rolling rotor is lodged on a shaft in the rotary-shaped stator; the rotor comprises a rotary-shaped body based on this invention, whose essence comprises in the fact that a replenishing vane is located on the shaft using a locking device to accelerate and guide the fluid in the needed direction to the gap between the stator and the rotor.
  • the setting of the replenishing vane in the hydraulically controlled space is possible at standstill through adjusting the locking device on the shaft and fixing another position of the replenishing vane.
  • Adjustment of the locking device allows the altitudinal positioning of the replenishing vane relative to the gap between the rotor and the stator, the tilting of its longitudinal axis from the longest perpendicular line from the longitudinal axis of the shaft to the inner wall of the pump casing in the direction to or from the rotor as well as the turning of the replenishing vane in or against the rotor rolling direction.
  • the shaft is firmly attached to the driver and the rolling rotor with the shaft form a freely rotating unit.
  • the advantage of the proposed solution is that the replenishing vane supplies the fluid so that it increases the motive element of fluid speed in the rotor rolling direction when the fluid is channelled to the gap between the rotor and the stator.
  • the replenishing vane also prevents cavitations' to a large extent, occurring when the fluid enters the working space and around the rolling rotor with precessional movement.
  • the advantage of the presented solution consists in the organized flow of the fluid entering the working space, which allows greater machine output at a higher efficiency of transformation of mechanical energy into hydraulic energy.
  • the mounting angle of the replenishing blade in relationship the pump shaft centreline is perpendicular and in direction to the inner side of the pump casing and the replenishing blade angle in relationship to the pump rotor rotating plane can be twisted between 0 to 35° while the angle between two perpendicular lines of the pump shaft and the replenishing blade centreline in direction to the pump casing can deviate from the true 90° line in direction towards rolling motor 0 to 50° or can deviate from the true 90° line in direction away from the rolling motor 0 to 60°.
  • the replenishing vane has the shape of a warped surface whose end at the pump casing has the same radius as the inner wall of the pump casing and its width is 10% to 99% of the distance between the shaft and the pump casing, and its longitudinal axis can be tilted using the adjustable locking device from the longest perpendicular line leading from the longitudinal axis of the shaft to the inner wall of the cabinet in the direction to the rotor at an angle of 0° to 35° and from the rotor at an angle of 0° to 50° and can be turned in or against the rotor rolling direction at an angle of 0° to 60°.
  • the replenishing vane has the shape of a propeller blade whose width is 10% to 99% of the distance between the shaft and the pump casing and its longitudinal axis can be tilted using the locking device from the longest perpendicular line leading from the longitudinal axis of the shaft to the inner wall of the pump casing in the direction to the rotor at an angle of 0° to 35° and from the rotor at an angle of 0° to 50° and can be turned in or against the rotor rolling direction at an angle of 0° to 60°.
  • the replenishing vane has the shape of a part of a spiral surface with a variable helix angle of ⁇ 10° to 50° and its width is 10% to 99% of the distance between the shaft and the pump casing.
  • the replenishing vane is, at least on part of its surface, equipped with protrusions 0.1mm to 0.35mm high and/or dimples 0.1mm to 15mm deep, and the diameter of the protrusions and/or dimple base is 0.1mm to 45mm.
  • Figure 1 shows the first embodiment of the rolling fluid pump with a partial cross-section in side view, where the replenishing vane has the shape of a warped surface.
  • Figure 2 shows the second embodiment of the rolling fluid pump with a partial cross-section in side view, where the replenishing vane has the shape propeller blade.
  • Figure 3 shows the embodiment of the replenishing vane with a partial cross-section in side view, where the replenishing vane has the shape of a part of a spiral surface with a variable helix angle.
  • Figure 4 shows the embodiment of the replenishing vane with a partial cross-section in side view, where the replenishing vane is at fitted with protrusions or dimples on at least a part of its surface.
  • the rolling fluid pump consists of the drive housing 10 , which is composed of a hollow cylinder with the inner diameter of 165mm, closed with a removable cover on the upper end; its lower end is formed by the cover of the pump casing 1.
  • a rotary-shaped ring stator 2 is placed in the central part of the pump casing 1 ; the stator also forms the route for the freely rotating bearing of the rolling rotor 3 coupled with the outer shell of the bearing 8 of the rotor 3 positioned on the rolling rotor 3 .
  • the rotary-shaped ring stator 2 is conical and has an inlet diameter of 134mm; its length is 115mm and its peak angle 15°.
  • the rolling rotor 3 has the shape of a regular hollow hemisphere with the outer diameter of 120mm.
  • the shaft 4 passes through the pump's casing cover 1 , where it can tilt in a ball joint 5 , positioned in the centre of the pump's casing cover 1 .
  • the lower end of the 4 shaft is located in the bearing 8 of the rolling rotor 3 and the upper end of the shaft 4 is lodged in the positioner 13 of the input shaft 11 .
  • the positioner 13 of input shaft 11 connected to the input shaft 11 positioned in the suspension bearing 12 of the input shaft 11 , which is part of the drive housing 10 , provides for non-rotating and symmetrical connection of the pump shaft 4 and the input shaft 11 , which leads to an even number of revolutions of the pump shaft 4 and the input shaft 11 .
  • the input shaft 11 and the positioner 13 of the input shaft 11 , the ball joint 5 and the pump shaft 4 are dimensioned to make sure that the rolling rotor 3 touches the stator 2 .
  • the replenishing vane 9 has the shape of a warped surface and is adjustably positioned, using the locking device 14 , on the pump shaft 4 above the gap between the rotor 3 and the stator 2 .
  • the suspension bearing of the pump shaft 4 in the bearing 8 of the rolling rotor 3 results in the rolling of the rolling rotor 3 along the inner wall of the stator 2 , which results in the movement of the fluid through the inlet 6 to the space between the rotor 3 and the stator 2 in the pump and in discharging the fluid out through the outlet 7 of the pump.
  • the replenishing vane 9 in the shape of warped surface has the width of 50% of the distance between the pump shaft 4 and the pump casing 1 and is locked above the gap between the rotor 3 and the stator 2 ; its longitudinal axis is tilted from the longest perpendicular line leading from the longitudinal axis of the pump shaft 4 to the inner wall of the pump casing 1 in the direction of the rotor 3 at an angle of 30° and at the same time is rotated in the rolling direction of the rotor 3 at an angle of 28°.
  • This arrangement of the replenishing vane 9 helps the flow of the fluid through the active space between the rotor 3 and the stator 2 so that it increases the motive element of speed at the edge of the gap between the rotor 3 and the stator 2 in the rolling direction of the rotor 2 when it enters the gap between the rotor 3 and the stator 2 .
  • This replenishing vane 9 also slows down cavitation that occurs at the fluid inlet to the working space between the rotor 3 and the stator 2 so that the speed of the supplied fluid at the beginning of the gap between the rotor 3 and the stator 2 is increased more by the replenishing vane 9 due to its turning in the rolling direction of the rotor 3 than in other places above the gap between the rotor 3 and the stator 2 .
  • the rolling fluid pump in this case consists of the drive housing 10 , which is composed of a hollow cylinder, closed with a removable cover on the upper end; its lower end is formed by the cover of the pump casing 1 .
  • a rotary-shaped ring stator 2 is placed in the central part of the pump casing 1 of the router for the freely rotating suspension bearing of the rolling rotor 3 coupled with the shell of the bearing 8 of the rotor 3 positioned on the rolling rotor 3 .
  • the rotary-shaped ring stator 2 is conical and has an inlet diameter of 134mm; its length is 115mm and its peak angle 15°.
  • the rolling rotor 3 has the shape of a hollow truncated cone whose biggest diameter is 120mm and peak angle 20°.
  • the shaft 4 passes through the pump's casing cover 1 , where it can tilt in a ball joint 5 , positioned in the centre of the pump's casing cover 1 .
  • the lower end of the 4 shaft is located in the bearing 8 of the rolling rotor 3 and the upper end of the shaft 4 is lodged in the locator 13 of the input shaft 11 .
  • the positioner 13 of the input shaft 11 connected to the input shaft 11 positioned in the suspension bearing 12 of the input shaft 11 , which is part of the drive housing 11 , provides for non-rotating and symmetrical connection of the pump shaft 4 and the input shaft 11 , which leads to an even number of revolutions of the pump shaft 4 and the input shaft 11 .
  • the input shaft 11 and the locator 13 of the input shaft 11 , the ball joint 5 and the shaft 4 are dimensioned to make sure that the rolling rotor 3 touches the stator 2 .
  • the replenishing vane 9 in the shape of a propeller blade has the width of 60% of the distance between the pump shaft 4 and the pump casing 1 .
  • the suspension of the pump shaft 4 in the bearing 8 of the rolling rotor 3 results in the rolling of the rotor 3 along the inner wall of the stator 2 , which results in the movement of the fluid through the inlet 6 to the space between the rotor 3 and the stator 2 in the pump and in pushing the fluid out through the outlet 7 of the pump.
  • the replenishing vane 9 in the shape of a propeller blade has the width of 60% of the distance between the pump shaft 4 and the pump casing 1 and is locked with the locking device 14 above the gap between the rotor 3 and the stator 2 ; its longitudinal axis is tilted from the longest perpendicular line leading from the longitudinal axis of the pump shaft 4 to the inner wall of the pump casing 1 in the direction of the rotor 3 at an angle of 9° and at the same time it is rotated in the rolling direction of the rotor 3 with respect to the total active surface, which is in this case smaller than for the replenishing vane 9 of the warped surface shape in the previous embodiment, at an angle of 36°.
  • This arrangement of the replenishing vane 9 helps the flow of the fluid through the active space between the rotor 3 and the stator 2 as in the previous embodiment so that it increases the motive element of speed at the edge of the gap between the rotor 3 and the stator 2 in the rolling direction of the rotor 2 when it enters the gap between the rotor 3 and the stator 2 .
  • this replenishing vane 9 also reduces cavitation that occurs at the fluid inlet to the working space between the rotor 3 and the stator 2 so that the speed of the supplied fluid at the beginning of the gap between the rotor 3 and the stator 2 is increased more by the replenishing vane 9 due to its turning in the rolling direction of the rotor 3 than in other places above the gap between the rotor 3 and the stator 2 .
  • FIG. 3 Another specific embodiment of the replenishing vane 9 is shown schematically in figure 3 .
  • the solution of the fluid pump based on the invention is identical with the embodiment shown in figure 1 , where the rotor 3 has the shape of a hollow hemisphere, but with the difference that the replenishing vane 9 has the shape of a part of a spiral surface with a variable helix angle of 15° and its width is 23% of the distance between the shaft 4 and the pump casing 1 .
  • this replenishing vane 9 in the shape of a part of a spiral surface faces the gap between the rotor 3 and the stator 2 and influences the supply of fluid in the gap between the rotor 3 and the stator 2 so that the motive element of the speed of the fluid increases on a long section above the hydraulically active space between the rotor 3 and the stator 2 , unlike in the previous embodiments.
  • this replenishing vane 9 reduces cavitation especially at smaller working revolutions of the rolling pump, when the diameter of the rotary-shaped ring stator 2 on the route of the freely rotating suspension bearing of the rolling rotor 3 does not exceed 1.116 times the diameter of the rolling rotor 3 .
  • FIG 4 Yet another specific embodiment of the replenishing vane 9 is shown in figure 4 .
  • the solution of the fluid pump based on the invention is identical with the embodiment shown in figure 1 , where the rotor 3 has the shape of a hollow hemisphere, but with the difference that the replenishing vane 9 with the shape of a warped surface is fitted with two dimples 15 on its surface facing the rotor 3 and with two protrusions 16 on its surface facing away from the rotor 3 ; their base has a circular shape with a diameter of 7mm.
  • the depth of the dimples 15 is 3mm and the height of the protrusions 16 4mm.
  • This modified replenishing vane 9 especially allows an efficient pumping of different think sludge mixtures, when the dimples 15 and the protrusions 16 help homogenize the pumped materials, facilitating their flow through the gap between the rotor 3 and the stator 2 .
  • the pump as shown in this invention can be used to pump fluids, especially liquids, but also various fluid mixtures. It is also suitable for transporting thick consistencies, such as sludge and sludge mixtures.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP09810836.8A 2008-12-10 2009-12-09 Rolling fluid pump Not-in-force EP2359008B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CZ2008-796A CZ306714B6 (cs) 2008-12-10 2008-12-10 Tekutinové odvalovací čerpadlo
PCT/CZ2009/000148 WO2010066210A2 (en) 2008-12-10 2009-12-09 Rolling fluid pump

Publications (2)

Publication Number Publication Date
EP2359008A2 EP2359008A2 (en) 2011-08-24
EP2359008B1 true EP2359008B1 (en) 2018-11-14

Family

ID=42243106

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09810836.8A Not-in-force EP2359008B1 (en) 2008-12-10 2009-12-09 Rolling fluid pump

Country Status (3)

Country Link
EP (1) EP2359008B1 (cs)
CZ (1) CZ306714B6 (cs)
WO (1) WO2010066210A2 (cs)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191412038A (en) * 1914-05-15 1915-05-13 William Edward Proctor Improvements in or relating to Propellers, Rotary Fans, Pumps and the like.
US2107090A (en) * 1935-01-10 1938-02-01 Borg Warner Water pump
US2773453A (en) * 1952-09-12 1956-12-11 Gemeinhardt William Rotary pumps
DE1453763A1 (de) * 1962-12-24 1969-01-09 Wilhelm Goldau Schleuderrohrsaug- und Druckpumpe
IT1160266B (it) * 1978-11-27 1987-03-11 Sempio Primo Perfezionamenti alla pompa centrifuga stagna senza organi di tenuta in rotazione
FR2629142A1 (fr) * 1988-03-24 1989-09-29 Carrouset Pierre Machine rotative a deplacement non positif utilisable comme pompe, compresseur, propulseur ou turbine motrice
SU1701971A1 (ru) * 1989-12-26 1991-12-30 Войсковая часть 27177 Гидродвигатель
RU2185525C2 (ru) * 1996-10-17 2002-07-20 Мирослав СЕДЛАЧЕК Гидравлическая машина
CZ97297A3 (cs) * 1997-03-28 1998-12-16 Miroslav Ing. Csc. Sedláček Odvalovací tekutinový stroj
CZ7606U1 (cs) 1998-05-22 1998-07-10 Miroslav Ing. Csc. Sedláček Hydromotor
CZ11469U1 (cs) * 2001-05-31 2001-09-03 Sedláček Miroslav Odvalovací tekutinový stroj
CZ294708B6 (cs) * 2001-09-13 2005-02-16 Miroslav Ing. Csc. Sedláček Odvalovací kapalinová turbína
CZ14104U1 (cs) * 2004-01-23 2004-03-02 Miroslav Šimera Odvalovací tekutinový stroj, zejména s rozstřikováním kapaliny na výstupu

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CZ2008796A3 (cs) 2010-06-23
WO2010066210A2 (en) 2010-06-17
EP2359008A2 (en) 2011-08-24
WO2010066210A3 (en) 2010-11-04
CZ306714B6 (cs) 2017-05-24

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