WO2011117087A2 - Förderaggregat - Google Patents
Förderaggregat Download PDFInfo
- Publication number
- WO2011117087A2 WO2011117087A2 PCT/EP2011/053693 EP2011053693W WO2011117087A2 WO 2011117087 A2 WO2011117087 A2 WO 2011117087A2 EP 2011053693 W EP2011053693 W EP 2011053693W WO 2011117087 A2 WO2011117087 A2 WO 2011117087A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- control
- rotors
- rotor
- delivery unit
- Prior art date
Links
- 230000001419 dependent effect Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
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 is based on a delivery unit according to the preamble of the main claim.
- the balancing pressure often corresponds to the pressure of the delivery side of the delivery unit, whereby 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 flows. This has the disadvantage that it sets an undefined balance pressure, which depends on the leakage flows that flow into the room or from the space behind the rotor. Also with this
- the balancing pressure does not have the ideal value for low-friction operation.
- Main claim has the advantage that a defined compensation pressure on the back of the axially adjustable rotor is adjusted by a control valve is provided which sets the compensation pressure to a predetermined value between a pressure of the pressure side and a pressure of the suction side.
- the balancing pressure is dependent on the respective Operating point of the delivery unit set, and that to a value that allows the lowest possible operation of the delivery unit.
- a defined force is exerted on the rotor via the thus set pressure on the rear surface on the rotor.
- the pressure of the suction side and the pressure side exert forces on the rotors which try to dislodge the rotors. Since the pressure areas remain the same, the ideal balancing force on the rotors is proportional to
- the compensation pressure can be used compensating both on a rotor and on both rotors. Furthermore, different balancing pressures can be generated for the two rotors by the use of two proportional valves.
- control valve has a control piston and three by the control piston separate control chambers, wherein the first control chamber of the control valve is acted upon by the pressure of the pressure side and the second control chamber with the pressure of the suction side, wherein the third control chamber via a on the control piston executed control channel with the first chamber or with the second chamber
- a balance pressure is set, which has a value between a pressure of the pressure side and a pressure of the suction side.
- the input cross-section of the control channel is variable depending on the position of the control piston, since in this way a predetermined pressure loss is achieved.
- control piston protrudes through a passage between the first and the second chamber, wherein the variable input cross-section of the control valve by a partial overlap of the input cross section with the wall of the
- control valve is a proportional valve in which the quotient of the difference between the compensation pressure and the suction pressure to the difference between the pressure-side pressure and the suction pressure is constant. It is also advantageous if the control piston of two counteracting each other
- Valve springs is acted upon, since in this way a provision of the control piston is achieved in a predetermined starting position when switching off the delivery unit.
- control valve is attached to the rotor housing of the delivery unit or integrated in the rotor housing.
- the drawing shows in section a partial view of the delivery unit according to the invention.
- the delivery unit serves to convey liquid or gaseous media, for example liquids or gases.
- the delivery unit 1 has a drive rotor 2 and driven by the drive rotor 2 output rotor 3, both of which are rotatably arranged in a rotor housing 4 and cooperate via a respective spur gearing 5 meshing.
- the spur gearing 5 is for example a cycloid or Trochoidenvertechnikung, but may of course be another gearing.
- the two rotors 2, 3 according to the exemplary embodiment have a spherical shape in sections on their outer circumference.
- Drive rotor 2 is driven by a motor 8, for example an electric motor.
- a motor 8 for example an electric motor.
- the rotors 2,3 each have a rotor bearing 9,10 is provided.
- the rotors 2, 3 each have one Rotor axis 6.7, for example, are inclined to each other, so do not align.
- At least one of the two rotors 2, 3 is axially adjustable.
- this axially adjustable rotor 3 is pressed by means of a spring element 30 in the direction of the other rotor 2.
- the spring element 30 is a compression spring, for example a plate spring or a
- both rotors 2, 3 are axially adjustable in their rotor bearings 9, 10. Between the rotors 2,3 working chambers 11 are formed, in which the medium through
- a control valve 14 which controls the pressure acting on the backs 2.1.3.1 balance pressure to a predetermined value between a pressure of
- the suction side is an unillustrated input and the pressure side of an unillustrated output of the delivery unit.
- the compensation pressure is adjusted to a predetermined value depending on the respective operating point of the delivery unit, and indeed to a value that allows a possible low-friction operation of the delivery unit.
- the control valve 14 has a control piston 15 and three by the control piston 15 separate control chambers 16,17,18, wherein the first control chamber 16 of the control valve 14 is acted upon by the pressure of the pressure side and the second control chamber 17 with the pressure of the suction side, said third control chamber 18 via a control piston 19 running on the control piston 19 with the first control chamber 16 or with the second control chamber 17 is strömungsverbindbar.
- the control channel 19 extends in the direction of the longitudinal extent of the control piston 15th
- An input cross-section 20 in the control channel 19 is dependent on the position of the
- Control piston 15 changeable.
- the input cross section is defined by at least one
- Input opening formed in the control channel 19 For example, several Input openings on the circumference of the control piston 15 executed.
- the control piston 15 extends through a passage 22 between the first 16 and the second control chamber 17, wherein the variable input cross section of the control valve 14 is achieved by a partial overlap of the input cross section with the wall of the passage channel 22.
- the control channel 19 opens at its end facing away from the input cross section 20 in the third control chamber 18.
- the pressure of the third control chamber 18 is passed through a flow channel 24 to the back 2.1.3.1 of the rotors 2.3.
- the control valve 14 may be attached to the rotor housing 4 of the delivery unit or in
- the control valve 14 has two inputs 26,27 for connection to the suction and pressure side of the delivery unit and an output 28 for connection to the flow channel 24 leading to the rear side of the rotors 2.1,3.1 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 counter-acting valve springs 23 in order to ensure a return to a starting position.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BR112012024212A BR112012024212A2 (pt) | 2010-03-26 | 2011-03-11 | agregado de distribuição |
CN201180021004.2A CN103026070B (zh) | 2010-03-26 | 2011-03-11 | 输送设备 |
US13/637,393 US20130089455A1 (en) | 2010-03-26 | 2011-03-11 | Delivery unit |
EP11708803.9A EP2553271B1 (de) | 2010-03-26 | 2011-03-11 | Förderaggregat |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010003319A DE102010003319A1 (de) | 2010-03-26 | 2010-03-26 | Förderaggregat |
DE102010003319.7 | 2010-03-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2011117087A2 true WO2011117087A2 (de) | 2011-09-29 |
WO2011117087A3 WO2011117087A3 (de) | 2013-02-14 |
Family
ID=44503739
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2011/053693 WO2011117087A2 (de) | 2010-03-26 | 2011-03-11 | Förderaggregat |
Country Status (6)
Country | Link |
---|---|
US (1) | US20130089455A1 (de) |
EP (1) | EP2553271B1 (de) |
CN (1) | CN103026070B (de) |
BR (1) | BR112012024212A2 (de) |
DE (1) | DE102010003319A1 (de) |
WO (1) | WO2011117087A2 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011084828B4 (de) * | 2011-10-19 | 2024-02-15 | Robert Bosch Gmbh | Förderaggregat |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10335939A1 (de) | 2002-08-02 | 2004-04-08 | Cor Pumps + Compressors Ag | Innengehäuse für Drehkolbenmaschinen |
Family Cites Families (6)
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 |
JP5007085B2 (ja) * | 2006-08-15 | 2012-08-22 | 株式会社Tbk | タンデムポンプのバルブ構造 |
DE102008003240B4 (de) * | 2008-01-04 | 2024-02-15 | Robert Bosch Gmbh | Förderaggregat |
DE102008023475A1 (de) * | 2008-05-14 | 2009-11-19 | Robert Bosch Gmbh | Hydromaschine |
-
2010
- 2010-03-26 DE DE102010003319A patent/DE102010003319A1/de not_active Withdrawn
-
2011
- 2011-03-11 BR BR112012024212A patent/BR112012024212A2/pt active Search and Examination
- 2011-03-11 US US13/637,393 patent/US20130089455A1/en not_active Abandoned
- 2011-03-11 CN CN201180021004.2A patent/CN103026070B/zh active Active
- 2011-03-11 WO PCT/EP2011/053693 patent/WO2011117087A2/de active Application Filing
- 2011-03-11 EP EP11708803.9A patent/EP2553271B1/de active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10335939A1 (de) | 2002-08-02 | 2004-04-08 | Cor Pumps + Compressors Ag | Innengehäuse für Drehkolbenmaschinen |
Also Published As
Publication number | Publication date |
---|---|
DE102010003319A1 (de) | 2011-09-29 |
CN103026070B (zh) | 2016-03-16 |
EP2553271B1 (de) | 2020-06-17 |
CN103026070A (zh) | 2013-04-03 |
US20130089455A1 (en) | 2013-04-11 |
WO2011117087A3 (de) | 2013-02-14 |
BR112012024212A2 (pt) | 2016-07-05 |
EP2553271A2 (de) | 2013-02-06 |
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