EP0636791A1 - Seitenkanalpumpenregelung - Google Patents

Seitenkanalpumpenregelung Download PDF

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Publication number
EP0636791A1
EP0636791A1 EP94305264A EP94305264A EP0636791A1 EP 0636791 A1 EP0636791 A1 EP 0636791A1 EP 94305264 A EP94305264 A EP 94305264A EP 94305264 A EP94305264 A EP 94305264A EP 0636791 A1 EP0636791 A1 EP 0636791A1
Authority
EP
European Patent Office
Prior art keywords
fluid
inlet
pump
stripper
flow
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.)
Withdrawn
Application number
EP94305264A
Other languages
English (en)
French (fr)
Inventor
John Scott Kidger
Roger John Cumming
John Charles Gibbons
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.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of EP0636791A1 publication Critical patent/EP0636791A1/de
Withdrawn legal-status Critical Current

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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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/005—Varying behaviour or the very pump the pumps being of the circumferential flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps

Definitions

  • This invention relates to regenerative pumps.
  • Regenerative pumps comprise a housing with a fluid inlet and a fluid outlet, and an impeller rotatably mounted within the housing and having a plurality of vanes spaced angularly around the axis of rotation of the impeller and accommodated within a flow channel within the housing extending between the inlet and outlet, the vanes serving to induce a spiral or helical flow of fluid along the length of the flow channel as the impeller is rotated.
  • the spiral flow is induced by the centrifugal and frictional effects of the vanes on the fluid and causes the fluid to be re-circulated repeatedly across a plurality of the vanes between the inlet and outlet, thereby progressively increasing the fluid pressure.
  • a stripper block is located between the inlet and outlet and has sufficient clearance with the impeller and vanes to allow them to pass but to restrict direct fluid flow from the higher pressure fluid outlet to the lower pressure fluid inlet.
  • an annular core is provided in the flow channel and the fluid flows in said spiral path about the core.
  • the vanes project from the impeller into the flow channel and either terminate just short of a fixed core or are connected to the core so that the core rotates with the rotor.
  • the vanes may have an aerofoil cross-section to enhance the fluid flow effects, and means may be provided to assist the initial spiral flow of fluid at the inlet.
  • An example of such a regenerative pump is shown in British Patent No. 2068461.
  • British Patent No. 2074242 discloses a regenerative pump in which fluid flows in a spiral path about a core between an inlet and outlet, and which incorporates a stripper block between the inlet and outlet that serves to preserve the annular motion of the fluid as it passes with the vanes of the impeller through the stripper block. This is achieved by providing a fluid flow loop in the stripper block which intersects the path of the rotation of the vanes.
  • the fluid flow loop may comprise one or more closed loops each of which is formed by a separate duct which re-circulates the fluid through the vanes, or may comprise a single quasi-helical loop formed by a succession of ducts between the outlet and inlet side of the stripper block. In the latter arrangement, the quasi-helical flow loop serves to preserve the annular motion of the fluid to a maximum extent so as to maintain increased pump efficiency and pressure rise.
  • Regenerative pumps of the aforesaid kind are mechanically simple and reliable and are capable of operating at high speed and have low specific weight. Regenerative pumps are also capable of generating high pressures and high flows, the pressure generally being proportional to the square of the impeller speed, and the flow generally being proportional to the impeller speed. However, in some applications, for example, as engine driven fuel pumps for aviation gas turbine engines, this pressure/ flow speed characteristic can be a problem at some operating conditions. Thus a regenerative fuel pump may be designed to produce a desired fuel pressure and flow at low speed, engine light-up conditions, but the fuel pressure, and/or flow at some maximum engine speed may then be excessive, resulting in fuel heating and high Delta T because of the high energy input of the pump.
  • An object of the present invention is to provide a regenerative pump in which the aforesaid problem of excess pressure and/or excess flow at higher speeds can be reduced or avoided.
  • the present invention consists in a regenerative pump comprising a housing with a fluid inlet and a fluid outlet, an impeller rotatably mounted within the housing and having a plurality of vanes spaced angularly around the axis of rotation of the impeller and accommodated within a flow channel within the housing extending between the inlet and outlet, and a flow stripper located between the inlet and outlet and through which the vanes pass, characterised in that a second fluid inlet is provided in the housing to open into the flow channel between said fluid inlet and fluid outlet, and in that control means is provided to control the supply of fluid selectively to one or the other, or one or both of said fluid inlets, thereby to vary the output of the pump.
  • the effective length of the flow channel is shortened and thus the pressure rise generated in the flow channel is reduced for any particular output flow. That portion of the flow channel between the stripper and the second inlet becomes redundant, but a reduced pressure is produced therein which can cause vaporisation if the fluid pumped is a liquid, and thereby reduces the drag on the impeller.
  • the pressure rise and output flow are each reduced, but to a lesser extent compared with that when only the second inlet is used.
  • three or more circumferentially spaced fluid inlets may be provided along the length of the flow channel, and the inlet supply of fluid connected to these selectively either as alternatives or in combination.
  • the invention therefore gives the ability to vary the output of a regenerative pump by controlling the supply of fluid to alternative inlets, and thereby provides a wide possible choice of pump outputs.
  • the particular outputs produced will be dependent upon the relative positions of the inlets and outlets along the length of the channel.
  • the stripper is adapted to preserve the annular motion of the fluid as it passes through the stripper, and may incorporate a fluid flow loop in the stripper which intersects the path of rotation of the vanes.
  • the first fluid inlet is preferably spaced downstream of the stripper block rather than being located immediately after the stripper block, thereby allowing the annular flow of fluid from the stripper block to establish itself before it meets the flow through the inlet.
  • An optimum location is preferably determined to ensure that the helical flow has not dissipated by the time it reaches the inlet and to allow the maximum possible flow channel length after the inlet.
  • the centre of the inlet is located within an angular range of 15° to 90° from the fluid exit port of the stripper block, and preferably within the angular range of 45° to 75° from the exit port.
  • the present invention consists in a regenerative pump comprising a housing with a fluid inlet and a fluid outlet, an impeller rotatably mounted within the housing and having a plurality of vanes spaced angularly around the axis of rotation of the impeller and accommodated within a flow channel within the housing extending between the inlet and outlet, and a flow stripper located between the inlet and outlet and through which the vanes pass, characterised in that said fluid inlet is spaced downstream of the stripper block, thereby allowing the annular flow of fluid from the stripper block to establish itself before it meets the flow through the inlet.
  • the inlet is located in an optimum position within the range 15° to 90° downstream of the exit port of the stripper block, or within the preferred range of 45° to 75° downstream of the exit port.
  • the regenerative pump illustrated in Figures 1 to 3 comprises a housing 1 formed in two sections 2, 3 which are connected face-to-face and define an internal cavity 4 therebetween to receive an impeller 5 which is mounted on a drive shaft 6 supported in the housing by combined journal and thrust bearings 7.
  • One end of the shaft 6 is received in a blind bore 8 in an end plate 9, and the other end of the shaft 6 is sealed in the housing by a mechanical shaft seal 10 and is formed with internal splines 11 for driving connection to a power source.
  • the impeller 5 comprises an inner annular body 12 and an outer toroidal ring 14 with a plurality of radially projecting curved section vanes 13 connected therebetween.
  • the body 12 of the impeller 5 is a close fit with the inner walls 15 of the cavity 4 in the housing 1, but the vanes 13 and toroidal ring 14 project radially into an enlarged peripheral portion of the cavity 4 in the form of a toroidal chamber 16 concentric with the shaft 6 and symmetrical with the impeller 5 about the radially extending dividing plane along which the housing sections 2,3 meet.
  • a flow stripper block 17 is located within the toroidal chamber 16 and comprises a pair of blocks 18 which are secured in opposed recesses in the housing sections 2,3 and have inner faces which cooperate to closely surround the vanes 13 and the toroidal ring 14, as shown in Figure 1.
  • a first inlet port 19 is provided in the housing section 2 so as to open into the toroidal chamber 16 adjacent to the downstream side of the stripper block 17, given that the impeller 5 rotates in the direction of arrow R, as shown in Figure 2.
  • An outlet port 20 is provided in the housing section 2 so as to open into the toroidal chamber 16 adjacent to the upstream side of the stripper block.
  • the chamber 16 between these inlet and outlet ports 19,20 forms a flow channel in which the impeller induces a helical flow of fluid about the toroidal ring 14 as it is rotated, passing repeatedly through the vanes 13 and being progressively raised in pressure.
  • the flow stripper block 17 serves to separate the high pressure outlet end of the flow channel 16 from the lower pressure inlet end of the flow channel 16 and limits the direct flow of fluid between the two.
  • the stripper block is formed with an internal helical flow channel or loop 22 which advances in the same sense as the helical fluid flow about the toroidal ring 14 in flow channel 16, as shown in Figure 3.
  • the upstream end of the helical flow loop 22 opens into the outlet end of the flow channel 16 at a shaped port 23, and the downstream end of the helical loop 22 opens into the inlet end of the flow channel 16 at a shaped exit port 29.
  • the exit port 29 directs the flow of fluid from the loop 22 circumferentially of the toroidal ring 14 through the vanes 13 into the inlet end of the flow channel 16.
  • the fluid supplied to the loop 22 therefore flows in a helical path through the loop and tends to continue in the same helical path within the flow channel 16 after leaving the exit port 29.
  • This circumferentially directed jet of fluid from the exit port 29 tends to induce a helical flow of fluid in the region of the inlet port 19, and thereby serves to enhance the pressure rise in the flow channel 16 caused by the repeated passage of the fluid through the vanes 13.
  • the pump has a fluid inlet port 19 and a fluid outlet port 20.
  • the pump also has a second fluid inlet port 33 which opens into the flow channel 16 approximately half way along its length between the inlet port 19 and the outlet port 20.
  • Both of these inlet ports 19,33 are connected to a diverter valve 34, as shown in Figure 4, which is adapted to switch a supply of fluid from inlet 35 to either inlet port 19,33, or to divide the inlet supply of fluid in any selected ratio between the two inlet ports 19,33.
  • the diverter valve 34 also serves to connect the two inlet ports 19,33 together so as to allow recirculation of fluid through the valve 34 between the two inlet ports under certain flow conditions.
  • the length of the flow channel between the inlet ports 19 and 33 becomes redundant, but the drag exerted on the impeller by the fluid when this is a liquid, is reduced by vaporisation of the liquid in the channel caused by the reduced pressure due to the continued pumping action of the impeller.
  • the output of the pumps is as shown by curve E in Figure 8, with the output flow Q increased at all pressure rise values ⁇ P as compared with the output shown by curve C when only the second inlet port 33 is used, but the pressure rise ⁇ P reduced at most flow values Q compared with the output shown by curve A when only the first inlet port 19 is used as shown in Figure 7.
  • the pressure rise ⁇ P of the pump with twin inlet supplies, shown in Figure 5 is higher than that of the pump using just the first inlet port 19, shown in Figure 7.
  • Figure 9 illustrates an alternative embodiment of the invention in which the diverter valve 34 controlling fluid flow to the two inlet ports 19,33, is replaced by a variable restrictor valve 35 in the inlet connection 36 to the port 19 and a non-return valve 37 in the inlet connection 38 to the port 33.
  • a fluid supply connection 41 supplies fluid to a connection 40 between the restrictor valve 35 and non-return valve 37 so as to supply fluid in parallel to both of them.
  • the non-return valve 37 prevents re-circulation of fluid through connection 40 between the higher pressure second inlet port 33 and the lower pressure first inlet port 19, but is responsive to a pressure demand signal produced at the inlet port 33 by the setting of the variable restrictor valve 36.
  • the pressure generated at the second inlet port 33 by the impeller will be a maximum and will close or limit opening of the non-return valve 38 so that there is zero or a minimum flow of fluid through the second inlet port 33.
  • the restrictor valve 36 is only partially opened, a lower pressure will be generated at the second inlet port 33, and therefore the non-return valve 37 will open more to increase the flow of fluid through the second inlet port 33.
  • the restrictor valve 35 is closed, the non-return valve 38 will open to a maximum extent to supply fluid to the second inlet port 33.
  • the particular outputs produced by the pump will depend upon the relative position of the inlets 19,33 or 19,33,42 and outlet 20 along the length of the flow channel 16.
  • an improved output is obtained if the first inlet 19 is spaced downstream of the stripper block 17, as shown in Figure 2, rather than being located immediately after the stripper block.
  • This downstream spacing of the inlet 19 may serve to allow the helical flow of fluid from the exit port 29 to establish itself before it meets the flow through the inlet 19.
  • the downstream spacing is too large, the helical flow may dissipate and, for a fixed position of the outlet port 20, the effective length of the flow channel 16 will be reduced.
  • An optimum position of the inlet 19 lies within the range 15° to 90° downstream of the exit port 29, or the preferred range 45° to 75° downstream of the exit port 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP94305264A 1993-07-28 1994-07-18 Seitenkanalpumpenregelung Withdrawn EP0636791A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB939315630A GB9315630D0 (en) 1993-07-28 1993-07-28 Pumps
GB9315630 1993-07-28

Publications (1)

Publication Number Publication Date
EP0636791A1 true EP0636791A1 (de) 1995-02-01

Family

ID=10739581

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94305264A Withdrawn EP0636791A1 (de) 1993-07-28 1994-07-18 Seitenkanalpumpenregelung

Country Status (3)

Country Link
EP (1) EP0636791A1 (de)
JP (1) JPH07167083A (de)
GB (1) GB9315630D0 (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19725249A1 (de) * 1997-06-14 1998-12-24 Mannesmann Vdo Ag Förderpumpe
US7198455B2 (en) 2003-11-21 2007-04-03 The Boc Group Plc Vacuum pumping arrangement
CN106968958A (zh) * 2017-03-30 2017-07-21 河北技投机械设备有限公司 一种应用于金属内衬渣浆泵内的可调节的高效耐磨盘装置
WO2019087134A1 (en) 2017-11-03 2019-05-09 Fisher & Paykel Healthcare Limited Regenerative blower
US11230979B2 (en) 2019-03-08 2022-01-25 Pratt & Whitney Canada Corp. Aircraft engine fuel system and method
US11280342B2 (en) 2019-04-05 2022-03-22 Pratt & Whitney Canada Corp. Rotodynamic pump and method
US11459958B2 (en) 2019-03-22 2022-10-04 Pratt & Whitney Canada Corp. Rotodynamic pump having a body defining a body cavity with a first and second housing portion defining a portion of an impeller cavity and disposed within the body cavity wherein the body cavity extends at least in part around the second housing portion and the housing portions defining an impeller clearance
US20230193907A1 (en) * 2015-07-17 2023-06-22 Gardner Denver Deutschland Gmbh Side-channel machine (compressor, vacuum pump or blower) having an extraction duct in the stripper

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR902803A (fr) * 1943-01-27 1945-09-13 Hermes Patentverwertungs Gmbh Pompe à gaz annulaire à sec
GB864168A (en) * 1958-10-03 1961-03-29 Westinghouse Electric Corp Improvements in or relating to rotary fluid pumps
GB1561000A (en) * 1977-03-16 1980-02-13 Stieger H Pumps
GB2068461A (en) * 1980-02-01 1981-08-12 Utile Eng Co Ltd Regenerative turbo machines
GB2074242A (en) * 1980-03-20 1981-10-28 Secr Defence Axial-flow rotary compressor
FR2575234A1 (fr) * 1984-12-21 1986-06-27 Webasto Werk Baier Kg W Soufflante a canal lateral, notamment pour appareils de chauffage de vehicules

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR902803A (fr) * 1943-01-27 1945-09-13 Hermes Patentverwertungs Gmbh Pompe à gaz annulaire à sec
GB864168A (en) * 1958-10-03 1961-03-29 Westinghouse Electric Corp Improvements in or relating to rotary fluid pumps
GB1561000A (en) * 1977-03-16 1980-02-13 Stieger H Pumps
GB2068461A (en) * 1980-02-01 1981-08-12 Utile Eng Co Ltd Regenerative turbo machines
GB2074242A (en) * 1980-03-20 1981-10-28 Secr Defence Axial-flow rotary compressor
FR2575234A1 (fr) * 1984-12-21 1986-06-27 Webasto Werk Baier Kg W Soufflante a canal lateral, notamment pour appareils de chauffage de vehicules

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19725249A1 (de) * 1997-06-14 1998-12-24 Mannesmann Vdo Ag Förderpumpe
US6152688A (en) * 1997-06-14 2000-11-28 Mannesmann Vdo Ag Fuel pump
DE19725249C2 (de) * 1997-06-14 2002-05-02 Siemens Ag Förderpumpe
US7198455B2 (en) 2003-11-21 2007-04-03 The Boc Group Plc Vacuum pumping arrangement
US20230193907A1 (en) * 2015-07-17 2023-06-22 Gardner Denver Deutschland Gmbh Side-channel machine (compressor, vacuum pump or blower) having an extraction duct in the stripper
CN106968958A (zh) * 2017-03-30 2017-07-21 河北技投机械设备有限公司 一种应用于金属内衬渣浆泵内的可调节的高效耐磨盘装置
CN106968958B (zh) * 2017-03-30 2023-03-31 河北技投机械设备有限公司 一种应用于金属内衬渣浆泵内的可调节的高效耐磨盘装置
EP3704384A4 (de) * 2017-11-03 2021-07-28 Fisher & Paykel Healthcare Limited Regenerativgebläse
JP2021501851A (ja) * 2017-11-03 2021-01-21 フィッシャー アンド ペイケル ヘルスケア リミテッド 渦流ブロワ
AU2018361976B2 (en) * 2017-11-03 2021-10-14 Fisher & Paykel Healthcare Limited Regenerative blower
US11371515B2 (en) 2017-11-03 2022-06-28 Fisher & Paykel Healthcare Limited Regenerative blower
CN111373156A (zh) * 2017-11-03 2020-07-03 费雪派克医疗保健有限公司 再生鼓风机
WO2019087134A1 (en) 2017-11-03 2019-05-09 Fisher & Paykel Healthcare Limited Regenerative blower
US11230979B2 (en) 2019-03-08 2022-01-25 Pratt & Whitney Canada Corp. Aircraft engine fuel system and method
US11459958B2 (en) 2019-03-22 2022-10-04 Pratt & Whitney Canada Corp. Rotodynamic pump having a body defining a body cavity with a first and second housing portion defining a portion of an impeller cavity and disposed within the body cavity wherein the body cavity extends at least in part around the second housing portion and the housing portions defining an impeller clearance
US11280342B2 (en) 2019-04-05 2022-03-22 Pratt & Whitney Canada Corp. Rotodynamic pump and method

Also Published As

Publication number Publication date
JPH07167083A (ja) 1995-07-04
GB9315630D0 (en) 1993-09-08

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