EP0097924A2 - Turbine-pompe - Google Patents

Turbine-pompe Download PDF

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Publication number
EP0097924A2
EP0097924A2 EP83106165A EP83106165A EP0097924A2 EP 0097924 A2 EP0097924 A2 EP 0097924A2 EP 83106165 A EP83106165 A EP 83106165A EP 83106165 A EP83106165 A EP 83106165A EP 0097924 A2 EP0097924 A2 EP 0097924A2
Authority
EP
European Patent Office
Prior art keywords
pump
turbine
impeller
blade
side channel
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.)
Granted
Application number
EP83106165A
Other languages
German (de)
English (en)
Other versions
EP0097924A3 (en
EP0097924B1 (fr
Inventor
Friedrich Schweinfurter
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.)
Assunzione O Variazione Mandato marchi & Mittler S
Original Assignee
Schweinfurter Friedrich
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 Schweinfurter Friedrich filed Critical Schweinfurter Friedrich
Priority to AT83106165T priority Critical patent/ATE29552T1/de
Publication of EP0097924A2 publication Critical patent/EP0097924A2/fr
Publication of EP0097924A3 publication Critical patent/EP0097924A3/de
Application granted granted Critical
Publication of EP0097924B1 publication Critical patent/EP0097924B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset

Definitions

  • the invention relates to a turbine pump, consisting of a turbine part, which absorbs hydraulic energy from a fluid stream and emits it as rotational energy, and a pump part which works inversely for this purpose, which absorbs rotational energy and emits hydraulic energy, at least one impeller being provided.
  • turbine pumps which use Pelton turbines or volute casing pumps as drive systems, the pump and turbine parts being arranged on a common shaft, which results in an extremely compact design.
  • a turbine pump is known in which a propeller impeller serves as a turbine impeller and drives the conveying impeller directly via a common shaft.
  • the object of the present invention is to show a turbine pump which enables a high efficiency of the drive part with low volume flows and high pressure drop with simple design features.
  • a turbine pump according to the preamble of the main claim which is characterized in that the turbine part has a "reverse" running side channel pump with an impeller and with blade cells separated by blade webs and opposite flow channel.
  • the blade webs are preferably arranged obliquely or curved in the form of a logarithmic or arithmetic spiral with respect to the radial direction of the impeller.
  • the turbine pump is at least during the start-up process from an external energy source, for. B. an electric motor, rotated so that a circulating flow can develop through the resulting centrifugal force field, as is known to be necessary for the energy transfer by pulse exchange between blade cells and volume flow.
  • an external energy source for. B. an electric motor
  • the side channel turbine operates with high efficiency and can with very low pressure flows very high pressure drops between Remove inlet and outlet.
  • the pressure gradient that can be achieved with single-stage side channel pumps is absolutely unattainable with a low volume flow.
  • the inclined blade webs of the conveyor cells result in a substantial reduction in the hydraulic losses of the circulation flow in comparison to straight, non-tilted blade webs and thus increase the efficiency of energy transmission, both in the turbine and in the pump operation. Furthermore, a kind of "freewheeling" of the turbine is achieved by the inclination if, for. B. during the start-up process, the medium to be reduced in its pressure has a flow velocity which is too low for the impeller speed. If the blade webs were just employed, the turbine would then work with the same efficiency as a pump and supply energy to the volume flow from which energy is to be extracted. Due to the inclined blades, however, the efficiency in the "turbine direction" is significantly higher than that in the "pump direction", so that the rotational energy of the turbine impeller is only released to a small extent to the volume flow.
  • the pump and turbine part can advantageously be provided in a single impeller and if necessary, the two parts each have two or more stages, which results in very high pressure digits combined with a particularly compact design and maximum efficiency.
  • the turbine pump shown in Figures 1 and 2 is multi-stage and double-flow and consists of a housing 10 and two impellers 27 and 27 '.
  • the housing 10 is composed of a housing ring 11 with inlet openings 12 and 13 and outlet openings 14 and 15, a housing cover 16 with a side channel 17, a double-sided flow channel housing 18 with the side channels 17 'and 20', and a flow channel housing 19 with a side channel 20
  • Bearing cover 21 and a housing cover 16 are fastened to the housing ring 11 with housing screws 22 and sealed by O-rings 23.
  • a shaft 25 which is sealed to the outside by packing rings 24, is arranged, which is set in rotation in the direction of the arrow by a drive motor, not shown, for example an electric motor.
  • a drive motor not shown, for example an electric motor.
  • the impellers 27 and 27 ′ are fastened by means of feather keys 26 and sealed from one another on the shaft 25 and in the double-sided flow channel housing 18 by mechanical seals 28 and 29.
  • a locking ring 30 with a spacer disk 31 serves to axially secure the impellers 27 and 27 ′.
  • the impellers 27 and 27 ′ which are designed as stepped disks, are provided with blade ring cells 32 and 33, which are separated from one another by spirally curved blade webs 35 and 36. Opposite the blade rings, side channels 17, 17 'or 20 and 20' are incorporated into the flow channel housings 18 and 19 and 16 in the housing cover.
  • the volume flow of lower energy state entering the housing 10 through the inlet opening 13 experiences an energy transfer through an exchange of momentum between the circulation flow formed by the centrifugal force from the blade cells 32 'and 33' and the volume flow in the side channels 20 and 20 '.
  • the medium flows through the delivery part of the turbine pump, starting from a suction opening 34, first via the smallest diameter blade ring 32 'of the delivery impeller 27', flows via the conduit 37 into the next larger blade ring 33 'and then leaves the housing 10 of the turbine pump through the outlet opening 14 in an increased energy state.
  • the volume flow entering the inlet opening 12 of the housing 10 with a higher energy state passes through the inlet opening 38 in the outer, double-sided blade ring 33 of the rotating turbine wheel 27, the side channels 17 and 17 'being dimensioned in their cross sections such that the flow rate of the volume flow in the side channels is substantially higher than the rotating speed of the blade rings 32 and 33 of the turbine wheel 27.
  • the centrifugal forces in the blade cells 33 of the inevitably rotating turbine impeller 27 form a displacer flow, which alternately enters the faster flowing volume flow in the side channels from the blade cells of the blade rings and thereby the energy by impulse exchange from the volume flow of higher energy state on the blade webs 35 and 36 of the turbine impeller 27 as rotational energy.
  • the slowed, somewhat throttled volume flow passes via the overhead line duct 39 into the smaller, double-sided blade rings 32 with opposing side ducts 17 and 17 'distributed over a smaller circle, where in the same way as in the previous stage a further energy reduction or Throttling occurs.
  • the volume flow of reduced energy state throttled in two stages leaves the turbine pump through the double-sided side channel outlet openings 40 and the outlet opening 15 in the housing 10.
  • FIGS. 3 and 4 show a multi-stage flow channel housing with side channels and side channel inlet openings 34 and outlet openings 38.
  • the flow channel interrupters 41 and 42 in each case prevent the medium from flowing over to the opposite side.
  • the overhead line channel 37 connects the flow channels of the two stages.
  • this impeller can be operated as a turbine or as a pump, depending on the direction of flow. In reverse operation, the inlet openings 34 then naturally become outlet openings, and the outlet openings 38 become inlet openings.
  • FIGS. 8 and 9 A further preferred embodiment can be seen from FIGS. 8 and 9, in which single-stage impellers are used.
  • the turbine impeller 67 in this case has axially and radially open blade cells with side channels 69 and 69 'arranged opposite one another, while the impeller 63 has only axially open blade cells with side channels 62 and 62' arranged opposite one another.
  • the flow channel housing 61 from FIG. 8 is shown in more detail in FIGS. 10 and 11.
  • the pumped medium enters through the side channel inlet opening 65 and flows through the side channel 62 to the outlet opening 64, repeatedly entering the pumping cells of the impeller, which in this way transmits its rotational energy to the pumped medium.
  • the side channel is interrupted between the inlet and outlet openings by the interruption point 66, as a result of which an overflow of the conveyed medium from the outlet to the inlet, that is to say a “short circuit”, is prevented.
  • the single-stage delivery impeller 63 to the flow channel housing 61 from FIG. 8 is shown in FIGS. 12 and 13.
  • the axial feed cells are spiral curved blade webs separated.
  • the housing cover 68 from FIG. 8 is shown in more detail in FIGS. 14 and 15 and has an incorporated side channel 69 which extends from the inlet opening 72 to the outlet opening 71 with the side channel interrupter 70 lying in between.
  • the volume flow of higher energy state entering at 72 experiences an energy reduction when flowing through this turbine stage in that the faster flowing volume flow repeatedly enters the blade cells and communicates a torque to them.
  • the volume flow thus throttled then leaves the turbine stage with a lower energy state through the outlet opening 71.
  • the turbine impeller 67 from FIG. 8 is shown in FIGS. 16 and 17 and has blade cells which are open radially and axially and are separated from one another by blade vanes which are also spirally curved.
  • the preferred embodiment shown in FIG. 18 is a turbine pump, in which a multi-stage side channel pump with vanes or star impellers in a link construction by means of a double-flow turbine wheel with several radially separated ones Stages is supported or driven.
  • the turbine pump consists of a turbine housing 79 with flow duct housings 77 and 78 and a turbine impeller 75, as well as a bearing cover 80 with a common shaft 73 sealed therein by packing rings 74.
  • the common shaft 73 is additionally supported at the end of the side channel link stages with its extension in a slide bearing 89 in the foot housing 91.
  • the individual housing members are held together by housing screws 87 and nuts 88.
  • the volume flow of higher energy state intended for energy recovery enters through the inlet opening 81 in the turbine housing 79 and flows through the outer, larger-diameter blade ring stage on the turbine impeller 75 via its side channels arranged opposite to it, through the turbine to the inner, smallest-diameter blade ring stage, the volume flow being one experienced significant energy reduction.
  • This energy absorbed by the impeller blade webs of the blade cells is transferred directly to the multi-stage side channel feed pump, which runs on the same shaft with the same direction of rotation and speed.
  • the side channel pump is sealed from the turbine part by the shaft sealing rings 76.
  • the pumped delivery flow enters through the housing opening 83 and flows through the individual side channel delivery stages up to the outlet opening 90 in the foot housing 91.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Valve Device For Special Equipments (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP83106165A 1982-06-25 1983-06-23 Turbine-pompe Expired EP0097924B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83106165T ATE29552T1 (de) 1982-06-25 1983-06-23 Turbinenpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3223868 1982-06-25
DE19823223868 DE3223868A1 (de) 1982-06-25 1982-06-25 Turbinenpumpe

Publications (3)

Publication Number Publication Date
EP0097924A2 true EP0097924A2 (fr) 1984-01-11
EP0097924A3 EP0097924A3 (en) 1984-11-28
EP0097924B1 EP0097924B1 (fr) 1987-09-09

Family

ID=6166898

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83106165A Expired EP0097924B1 (fr) 1982-06-25 1983-06-23 Turbine-pompe

Country Status (3)

Country Link
EP (1) EP0097924B1 (fr)
AT (1) ATE29552T1 (fr)
DE (2) DE3223868A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001071193A1 (fr) * 2000-03-21 2001-09-27 Siemens Aktiengesellschaft Pompe de circulation
WO2011089025A3 (fr) * 2010-01-20 2011-10-27 Gardner Denver Deutschland Gmbh Turbine de détente pour la détente d'un gaz
EP2426313A1 (fr) * 2010-09-07 2012-03-07 Chun-Chieh Chen Convertisseur comprenant des roues centrifuges
WO2012113700A1 (fr) * 2011-02-22 2012-08-30 Gardner Denver Deutschland Gmbh Configuration de machine à canaux latéraux

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10019911A1 (de) * 2000-04-20 2001-10-25 Mannesmann Vdo Ag Förderpumpe
US7074016B1 (en) * 2002-05-24 2006-07-11 Massachusetts Institute Of Technology Planar turbopump assembly
DE102010064450B3 (de) * 2010-01-20 2015-01-08 Gardner Denver Deutschland Gmbh Entspannungs-Turbine zur Entspannung von Gas
DE102010064441B3 (de) * 2010-01-20 2015-03-26 Gardner Denver Deutschland Gmbh Entspannungs-Turbine zur Entspannung von Gas
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
EP2699268A2 (fr) 2011-04-21 2014-02-26 Seattle Genetics, Inc. Nouveaux conjugués liant-principe actif (adc) et leur utilisation
DE102015209561A1 (de) * 2015-05-26 2016-12-01 Mahle International Gmbh Pumpvorrichtung und Kurbelgehäuseentlüftungseinrichtung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2724338A (en) * 1949-05-19 1955-11-22 Roth Co Roy E Combination centrifugal-turbine pump
US2936714A (en) * 1956-07-18 1960-05-17 Crane Co Turbine driven pump
DE1403579A1 (de) * 1961-03-04 1969-07-17 Obermaier & Cie Turbogeblaese
DE2112762A1 (de) * 1971-03-17 1972-10-12 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe
GB1402713A (en) * 1971-06-30 1975-08-13 Lintott Eng Ltd Vortex compressor
DE2920683A1 (de) * 1979-05-22 1980-11-27 Rudolf Dr Wieser Turbinenpumpe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2724338A (en) * 1949-05-19 1955-11-22 Roth Co Roy E Combination centrifugal-turbine pump
US2936714A (en) * 1956-07-18 1960-05-17 Crane Co Turbine driven pump
DE1403579A1 (de) * 1961-03-04 1969-07-17 Obermaier & Cie Turbogeblaese
DE2112762A1 (de) * 1971-03-17 1972-10-12 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe
GB1402713A (en) * 1971-06-30 1975-08-13 Lintott Eng Ltd Vortex compressor
DE2920683A1 (de) * 1979-05-22 1980-11-27 Rudolf Dr Wieser Turbinenpumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001071193A1 (fr) * 2000-03-21 2001-09-27 Siemens Aktiengesellschaft Pompe de circulation
WO2011089025A3 (fr) * 2010-01-20 2011-10-27 Gardner Denver Deutschland Gmbh Turbine de détente pour la détente d'un gaz
EP2426313A1 (fr) * 2010-09-07 2012-03-07 Chun-Chieh Chen Convertisseur comprenant des roues centrifuges
WO2012113700A1 (fr) * 2011-02-22 2012-08-30 Gardner Denver Deutschland Gmbh Configuration de machine à canaux latéraux
CN103403357A (zh) * 2011-02-22 2013-11-20 加德纳·丹佛德国股份有限公司 侧通道设备型装置
CN103403357B (zh) * 2011-02-22 2017-02-15 加德纳·丹佛德国股份有限公司 侧通道设备型装置
US9677561B2 (en) 2011-02-22 2017-06-13 Gardner Denver Deutschland Gmbh Side channel machine arrangement
KR101875797B1 (ko) * 2011-02-22 2018-07-06 가드너 덴버 도이칠란트 게엠베하 측면 채널 머신 장치

Also Published As

Publication number Publication date
DE3373511D1 (en) 1987-10-15
EP0097924A3 (en) 1984-11-28
DE3223868A1 (de) 1983-12-29
EP0097924B1 (fr) 1987-09-09
ATE29552T1 (de) 1987-09-15

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