EP2553271B1 - Unité de refoulement - Google Patents

Unité de refoulement Download PDF

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Publication number
EP2553271B1
EP2553271B1 EP11708803.9A EP11708803A EP2553271B1 EP 2553271 B1 EP2553271 B1 EP 2553271B1 EP 11708803 A EP11708803 A EP 11708803A EP 2553271 B1 EP2553271 B1 EP 2553271B1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
rotor
rotors
delivery unit
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.)
Active
Application number
EP11708803.9A
Other languages
German (de)
English (en)
Other versions
EP2553271A2 (fr
Inventor
Oliver Laforsch
Dieter Amesoeder
Marian Kacmar
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2553271A2 publication Critical patent/EP2553271A2/fr
Application granted granted Critical
Publication of EP2553271B1 publication Critical patent/EP2553271B1/fr
Active 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated

Definitions

  • the invention relates to a conveyor unit according to the type of the main claim.
  • the compensating pressure often corresponds to the pressure on the pressure side of the delivery unit, which means that the forces on the rotors are significantly higher than required. This leads to increased friction in the bearings and between the rotors.
  • the back of the rotors can also be supplied via gap currents. This has the disadvantage that an undefined compensating pressure arises, which depends on the leakage flows which flow into the room or out of the room behind the rotor. In this version, too, the compensating pressure is not the ideal value for low-friction operation. From the US 6,168,404 a valve for setting a pressure in a control chamber for pressurizing a compressor element for setting a contact pressure is known.
  • the delivery unit according to the invention with the characterizing features of the main claim has the advantage that a defined compensating pressure is set on the back of the axially adjustable rotor by providing a control valve that the compensating pressure to a predetermined value between a pressure of the pressure side and a pressure of the Suction side.
  • the compensation pressure depends on the respective Operating point of the conveyor unit is set to a value that enables the conveyor unit to operate with as little friction as possible.
  • a defined force is exerted on the rotor via the pressure thus set on the rear surface on the rotor.
  • the pressure on the suction side and the pressure side exert forces on the rotors that try to drive the rotors apart. Since the pressurized areas remain the same, the ideal balancing force on the rotors is proportional to the pressure difference between the pressure side and the suction side.
  • a proportional valve is therefore well suited to compensating for the forces and thus reducing the friction between the rotors, between rotors and the housing and in the bearings. This leads to less wear and higher efficiency.
  • the compensation pressure can be used to compensate both on one rotor and on both rotors. Furthermore, different compensation pressures can be generated for the two rotors by using two proportional valves.
  • control valve has a control piston and three control chambers separated from one another by the control piston, the first control chamber of the control valve being acted upon by the pressure on the pressure side and the second control chamber being acted on by the pressure on the suction side, the third control chamber being carried out on the control piston Control channel with the first chamber or with the second chamber is fluidly connectable.
  • a compensation pressure is set which has a value between a pressure on the pressure side and a pressure on the suction side.
  • the input cross-section of the control channel can be changed depending on the position of the control piston; in this way a predetermined pressure drop is achieved.
  • control piston extends through a through-channel between the first and the second chamber, the variable inlet cross section of the control valve being achieved by partially covering the inlet cross-section with the wall of the through-channel. In this way, a predetermined pressure loss is generated at the control valve.
  • control valve is a proportional valve in which the quotient of the difference between the compensating pressure and the suction pressure and the difference between the pressure on the pressure side and the suction pressure is constant.
  • control piston is acted upon by two opposing valve springs; In this way, the control piston is returned to a predetermined starting position when the delivery unit is switched off.
  • control valve is fastened to the rotor housing of the delivery unit or is integrated in the rotor housing.
  • the pressure of the third control chamber is passed via a flow connection to the rear of the axially adjustable rotor; In this way, the compensation pressure set on the control valve reaches the rear of the rotor.
  • the drawing shows in section a partial view of the conveyor assembly according to the invention.
  • the conveyor unit is used to convey liquid or gaseous media, such as liquids or gases.
  • the conveying unit 1 has a drive rotor 2 and an output rotor 3 driven by the drive rotor 2, both of which are rotatably arranged in a rotor housing 4 and each mesh with one another via a spur toothing 5.
  • the front toothing 5 is, for example, a cycloid or trochoid toothing, but can of course also be another toothing.
  • the two rotors 2, 3 have a spherical shape in sections on their outer circumference.
  • the drive rotor 2 is driven by a motor 8, for example an electric motor.
  • a rotor bearing 9, 10 is provided for each of the rotors 2, 3.
  • the rotors 2, 3 each have one Rotor axis 6,7 which are inclined to one another, for example, that is to say not in alignment. At least one of the two rotors 2, 3 is axially adjustable. For example, this axially adjustable rotor 3 is pressed in the direction of the other rotor 2 by means of a spring element 30.
  • the spring element 30 is a compression spring, for example a plate spring or a coil spring. This ensures that the rotors 2, 3 are in contact with one another at all times.
  • both rotors 2, 3 are axially adjustable in their rotor bearings 9, 10.
  • Working spaces 11 are formed between the rotors 2, 3, in which the medium is conveyed by displacement.
  • workrooms 11, the volume of which is currently being reduced, pressure is built up.
  • This pressure also acts in the axial direction on the rotor bearings 9, 10 of the rotors 2, 3.
  • the back 2.1.3.1 of the rotor 2, 3, facing away from the other rotor 2, 3, is acted upon by a compensating pressure.
  • the compressive forces acting on the rotors 2, 3 are at least partially compensated. According to the exemplary embodiment, this takes place on both rotors 2, 3, but can of course also be implemented on only one of the rotors 2, 3.
  • a control valve 14 which adjusts the compensating pressure acting on the rear sides 2.1, 3.1 to a predetermined value between a pressure on the pressure side and a pressure on the suction side.
  • the suction side is an inlet, not shown, and the pressure side is an outlet, not shown, of the conveyor unit.
  • the compensating pressure is set to a predetermined value as a function of the respective operating point of the delivery unit, specifically to a value that enables the delivery unit to operate with as little friction as possible.
  • the control valve 14 has a control piston 15 and three control chambers 16, 17, 18 separated from one another by the control piston 15, the first control chamber 16 of the control valve 14 being pressurized on the pressure side and the second control chamber 17 being pressurized on the suction side, the third control chamber 18 can be flow-connected to the first control chamber 16 or to the second control chamber 17 via a control channel 19 on the control piston 15.
  • the control channel 19 runs in the direction of the longitudinal extent of the control piston 15.
  • An input cross section 20 in the control channel 19 can be changed depending on the position of the control piston 15.
  • the input cross section is formed by at least one input opening in the control channel 19. For example, there are several Entrance openings on the circumference of the control piston 15 executed.
  • the control piston 15 extends through a through channel 22 between the first 16 and the second control chamber 17, the variable input cross section of the control valve 14 being achieved by partially covering the input cross section with the wall of the through channel 22.
  • the control channel 19 opens into the third control chamber 18 at its end facing away from the input cross section 20.
  • the pressure of the third control chamber 18 is passed via a flow channel 24 to the rear side 2.1.3.1 of the rotors 2.3.
  • the control valve 14 can be attached to the rotor housing 4 of the delivery unit or integrated in the rotor housing 4.
  • the control valve 14 has two inlets 26, 27 for connection to the suction or pressure side of the delivery unit and an outlet 28 for connection to the flow channel 24 leading to the rear 2.1, 3.1 of the rotors 2, 3.
  • the control valve 14 is designed, for example, as a proportional valve.
  • the control piston 15 is acted upon, for example, by two opposing valve springs 23 in order to ensure a return to an initial position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (5)

  1. Unité de refoulement comprenant un rotor d'entraînement (2) et un rotor de prise de force (3) entraîné par le rotor d'entraînement (2), lesquels sont supportés de manière rotative dans un boîtier de rotor (4) et coopèrent par engrènement par le biais d'une denture frontale respective (5), au moins l'un des deux rotors (2, 3) étant déplaçable axialement et étant sollicité sur son côté arrière (2.1, 3.1) opposé à l'autre rotor (2, 3) avec une pression d'équilibrage,
    caractérisée en ce
    qu'une soupape de commande (14) est prévue, laquelle ajuste la pression d'équilibrage à une valeur prédéterminée entre une pression du côté pression et une pression du côté aspiration,
    la soupape de commande (14) présentant un piston de commande (15) et trois chambres de commande (16, 17, 18) séparées les unes des autres par le piston de commande (15), la première chambre de commande (16) de la soupape de commande (14) étant sollicitée avec la pression du côté pression et la deuxième chambre de commande (17) étant sollicitée avec la pression du côté aspiration, la troisième chambre de commande (18) pouvant être mise en liaison fluidique par le biais d'un canal de commande (19) réalisé au niveau du piston de commande (15) avec la première chambre de commande (16) ou avec la deuxième chambre de commande (17) par au moins une ouverture d'entrée au niveau de la périphérie du piston de commande (15), une section transversale d'entrée (20) du canal de commande (19), formée par l'au moins une ouverture d'entrée, pouvant être modifiée en fonction de la position du piston de commande (15) et le canal de commande (19), au niveau de son extrémité opposée à la section transversale d'entrée (20), débouchant dans la troisième chambre de commande (18), le piston de commande (15) étant sollicité par deux ressorts de soupape (23) agissant en sens inverse l'un de l'autre et la pression de la troisième chambre de commande (18) étant conduite par le biais d'une liaison fluidique (24) jusqu'au côté arrière (2.1, 3.1) des rotors (2, 3).
  2. Unité de refoulement selon la revendication 1, caractérisée en ce que le piston de commande (15) passe à travers un canal de passage (22) entre la première et la deuxième chambre de commande (16, 17), la section transversale d'entrée variable de la soupape de commande (14) étant obtenue par un recouvrement partiel de la section transversale d'entrée avec la paroi du canal de passage (22) et en ce que la pression de la troisième chambre de commande (18) est conduite par le biais d'une liaison fluidique (24) jusqu'au côté arrière (2.1, 3.1) des rotors (2, 3).
  3. Unité de refoulement selon la revendication 1, caractérisée en ce que la soupape de commande (14) est une soupape proportionnelle.
  4. Unité de refoulement selon la revendication 1, caractérisée en ce que la soupape de commande (14) est fixée au boîtier de rotor (4) de l'unité de refoulement ou est intégrée dans le boîtier de rotor (4).
  5. Unité de refoulement selon la revendication 1, caractérisée en ce que le rotor d'entraînement (2) et le rotor de prise de force (3) présentent une denture cycloïde ou trochoïde.
EP11708803.9A 2010-03-26 2011-03-11 Unité de refoulement Active EP2553271B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010003319A DE102010003319A1 (de) 2010-03-26 2010-03-26 Förderaggregat
PCT/EP2011/053693 WO2011117087A2 (fr) 2010-03-26 2011-03-11 Unité de refoulement

Publications (2)

Publication Number Publication Date
EP2553271A2 EP2553271A2 (fr) 2013-02-06
EP2553271B1 true EP2553271B1 (fr) 2020-06-17

Family

ID=44503739

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11708803.9A Active EP2553271B1 (fr) 2010-03-26 2011-03-11 Unité de refoulement

Country Status (6)

Country Link
US (1) US20130089455A1 (fr)
EP (1) EP2553271B1 (fr)
CN (1) CN103026070B (fr)
BR (1) BR112012024212A2 (fr)
DE (1) DE102010003319A1 (fr)
WO (1) WO2011117087A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011084828B4 (de) * 2011-10-19 2024-02-15 Robert Bosch Gmbh Förderaggregat

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080041472A1 (en) * 2006-08-15 2008-02-21 Tbk Co., Ltd. Tandem pump valve structure

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2431817A (en) * 1944-04-22 1947-12-02 Christa Smith H Fluid displacement device of the gear type
US6168404B1 (en) * 1998-12-16 2001-01-02 Tecumseh Products Company Scroll compressor having axial compliance valve
JP4070391B2 (ja) * 2000-06-15 2008-04-02 カヤバ工業株式会社 ベーンポンプの圧力調整装置
EP1527256B1 (fr) 2002-08-02 2013-05-22 Robert Bosch GmbH Machine a piston rotatif avec enveloppe interne mobile
DE102008003240B4 (de) * 2008-01-04 2024-02-15 Robert Bosch Gmbh Förderaggregat
DE102008023475A1 (de) * 2008-05-14 2009-11-19 Robert Bosch Gmbh Hydromaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080041472A1 (en) * 2006-08-15 2008-02-21 Tbk Co., Ltd. Tandem pump valve structure

Also Published As

Publication number Publication date
EP2553271A2 (fr) 2013-02-06
CN103026070A (zh) 2013-04-03
WO2011117087A3 (fr) 2013-02-14
WO2011117087A2 (fr) 2011-09-29
BR112012024212A2 (pt) 2016-07-05
CN103026070B (zh) 2016-03-16
DE102010003319A1 (de) 2011-09-29
US20130089455A1 (en) 2013-04-11

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