US20110186158A1 - Delivery unit - Google Patents

Delivery unit Download PDF

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Publication number
US20110186158A1
US20110186158A1 US13/121,699 US200913121699A US2011186158A1 US 20110186158 A1 US20110186158 A1 US 20110186158A1 US 200913121699 A US200913121699 A US 200913121699A US 2011186158 A1 US2011186158 A1 US 2011186158A1
Authority
US
United States
Prior art keywords
control
inlet
delivery unit
outlet
rotation
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.)
Abandoned
Application number
US13/121,699
Other languages
English (en)
Inventor
Thomas Steidten
Ingo Samerski
Ingo Nowitzky
Niccolo Haegele
Jens Schrader
Guido Daimer
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
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SAMERSKI, INGO, HAEGELE, NICCOLO, STEIDTEN, THOMAS, NOWITZKY, INGO, DAIMER, GUIDO, SCHRADER, JENS
Publication of US20110186158A1 publication Critical patent/US20110186158A1/en
Abandoned 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
    • 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
    • F04C3/085—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 the axes of cooperating members being on the same plane
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85978—With pump

Definitions

  • a delivery unit is known already from DE 10 2004 026 048 A1 comprising a drive rotor and an output rotor driven by the drive rotor which are mounted in a housing, interact in a meshing manner via a respective spur toothing and draw fluid through at least one inlet and push said fluid out through an outlet, wherein the inlet and the outlet are separated from each other by two separating webs.
  • a rotational speed control In order to control the flow rate through the delivery unit, a rotational speed control, a bypass control or, for gases, a suction throttling can, for example, be carried out.
  • a rotational speed control is energy-efficient but very expensive as an electric motor must be used, the rotational speed of which can be controlled.
  • bypass control the fluid is delivered from the outlet via a bypass back to the inlet, which however is unfavorable in energy terms and is associated with hydraulic losses.
  • the delivery unit according to the invention has the advantage that on the inlet side the flow rate can be controlled very easily and with few hydraulic losses and on the outlet side the inner compression can be controlled in the event of the delivery of gases, by virtue of the fact that at least one of the separating webs has at least one control opening, the opening cross section of which can be controlled by a control slide.
  • the design according to the invention in contrast to the prior art, requires less space for the volume flow control, is more cost-effective and is more energy-efficient.
  • Working chambers with a volume that increases in the region of the inlet in the direction of rotation and decreases in the region of the outlet in the direction of rotation are formed between the spur toothings of the rotors, the maximum volume of the working chambers being formed at a first transition point in the region of a first separating web and the minimum volume being formed at a second transition point in the region of a second separating web.
  • At least one control opening connected to the inlet side is arranged in a region of the first separating web which lies behind the first transition point in the direction of rotation, as the respective working chambers are in this way variably fluidly connected to the inlet via the point of their maximum volume.
  • At least one control opening connected to the outlet side is arranged in a region of the first separating web which lies behind the first transition point in the direction of rotation, as in this way the inner sealing of the delivery unit can be controlled.
  • FIG. 1 shows in section a delivery unit to which the invention could be applied
  • FIG. 2 shows a sectional view of a rotor housing according to the invention according to FIG. 1 in a first exemplary embodiment
  • FIG. 3 shows a three-dimensional view of the rotor housing according to FIG. 1 and FIG. 2 .
  • FIG. 4 shows a sectional view of a rotor housing according to the invention according to FIG. 1 in a second exemplary embodiment.
  • FIG. 1 shows in section a delivery unit to which the invention could be applied.
  • the delivery unit 1 has a drive rotor 2 and an output rotor 3 driven by the drive rotor 2 which are both mounted in a rotor housing 4 .
  • the drive rotor 2 is driven by a motor 5 , for example an electric motor, via a driveshaft.
  • the two rotors 2 , 3 each have a spur toothing 6 , for example a cycloidal spur toothing, which interact with each other in a meshing manner and draw fluid in through at least one inlet 7 in the rotor housing 4 and push said liquid out through an outlet 8 in the rotor housing 4 following the positive displacement principle.
  • Working chambers 14 are formed between the spur toothings 6 of the rotors 2 , 3 .
  • the axes of rotation of the two rotors 2 , 3 extend obliquely to each other and thus enclose an angle other than 180 degrees so that the volume of the working chambers 14 alternately increases and decreases during a revolution of the drive rotor 2 .
  • the volume of the chambers 14 increases in the direction of rotation and decreases at the outlet 8 in the direction of rotation so that fluid is drawn into the working chambers 14 at the inlet and is pushed out of the working chambers 14 at the outlet.
  • the rotor housing 4 is enclosed by a pump housing 15 .
  • the inlet 7 and the outlet 8 of the rotor housing 4 are sealed relative to each other inside the pump housing 15 , for example by means of separating walls 16 , 17 or other sealing means.
  • the separating walls 16 , 17 lie, for example, in the region of the separating webs 9 , 10 .
  • the working chambers 14 must be fluidly connected either to the inlet 7 or to the outlet 8 so that no closed chambers 14 are created in which the incompressible liquid is compressed by a reduction in the volume of the chambers 14 and an unacceptably high elevated pressure occurs which could damage the delivery unit.
  • the rotors 2 , 3 are also mounted in such a way that in the event of a predetermined elevated pressure they are pressed apart from each other in such a way that the elevated pressure is relieved by a short circuit with the adjacent working chambers. Closed working chambers 14 are acceptable for the delivery of gases as gases are compressible and a so-called inner compression is desired inside the closed chambers 14 .
  • FIG. 2 shows a sectional view of the rotor housing according to the invention according to FIG. 1 in a first exemplary embodiment.
  • parts which are identical or function in an identical fashion to those in the view according to FIG. 1 have the same reference numerals.
  • the inlet 7 and the outlet 8 are separated from each other in the circumferential direction of the rotor housing 4 by two separating webs 9 , 10 .
  • At least one of the separating webs 9 , 10 has at least one control opening 12 , the opening cross section of which can be modified by a movably mounted control slide 13 .
  • a plurality of control openings 12 are, for example, arranged behind one another in the direction of rotation of the rotors 2 , 3 .
  • the control opening 12 is, for example, a slot-shaped through-opening.
  • the control slide 13 can, for example, be adjusted electrically, pneumatically or hydraulically and interacts with the at least one control opening 12 to open or close it.
  • a control opening 12 that is not completely covered by the control slide 13 is fluidly connected to the inlet 7 or the outlet 8 and opens into one of the working chambers 14 depending on the position of the rotors.
  • the control slide 13 can be adjusted in or counter to the direction of rotation of the rotors 2 , 3 and/or axially with respect to one of the axes of rotation.
  • the maximum volume of the working chambers 14 is formed at a first transition point A in the region of the first separating web 9 and the minimum volume is formed at a second transition point B in the region of the second separating web 10 .
  • the separating webs 9 , 10 cover a predetermined angular range around the transition points A, B. Viewed in the direction of rotation, the volume of the chambers 14 decreases from the first transition point A to the second transition point B and increases from the second transition point B to the first transition point A.
  • the at least one control opening 12 is arranged on the first separating web 9 , in front of the separating wall 16 , viewed in the direction of rotation of the rotors 2 , 3 , in such a way that it is fluidly connected in the open state to the inlet 7 .
  • the at least one control opening 12 is, for example, arranged in such a way that it lies in a region of the first separating web 9 which lies behind the first transition point A in the direction of rotation.
  • the respective working chambers 14 can be connected to the inlet 7 variably via the control opening 12 over the first transition point A, so that by reducing the volume of the respective working chamber 14 a part of the fluid drawn out of the working chamber 14 is pushed back again into the inlet 7 . Because of the “late” closing of the inlet 7 , the amount delivered per revolution decreases, effecting a simple and energy-efficient volume flow control on the inlet side.
  • the at least one control opening 12 can alternatively also be designed on the first separating web 9 , in front of the first transition point A in the direction of rotation of the rotors 2 , 3 .
  • the volume flow control is effected by the “early” closing of the working chambers 14 at the inlet 7 , as a result of which the working chambers 14 are not completely filled and the hydraulic throttle losses are reduced in comparison to the “late” closing of the inlet 7 .
  • one or more control openings 12 can also be provided in front of the first transition point A, and one or more control openings 12 behind the first transition point A in the direction of rotation.
  • FIG. 3 shows a three-dimensional view of the rotor housing according to FIG. 1 and FIG. 2 .
  • parts which are identical or function in an identical fashion to those in the view according to FIG. 1 and FIG. 2 have the same reference numerals.
  • FIG. 4 shows a sectional view of the rotor housing according to the invention according to FIG. 1 in a second exemplary embodiment.
  • parts which are identical or function in an identical fashion to those in the view according to FIG. 1 to FIG. 3 have the same reference numerals.
  • the at least one control opening 12 is also arranged on the first separating web 9 , but it is fluidly connected in the open state to the outlet 8 by being designed on the first separating web 9 behind the separating wall 16 , viewed in the direction of rotation.
  • it is not the volume flow but the inner sealing that is controlled by means of the control openings 12 and optimal operation of the delivery unit in terms of energy is thereby achieved. Because of the inner sealing, the second embodiment is suited only for the delivery of gases.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US13/121,699 2008-10-02 2009-09-10 Delivery unit Abandoned US20110186158A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200810042564 DE102008042564A1 (de) 2008-10-02 2008-10-02 Förderaggregat
DE102008042564.8 2008-10-02
PCT/EP2009/061739 WO2010037620A2 (de) 2008-10-02 2009-09-10 Förderaggregat

Publications (1)

Publication Number Publication Date
US20110186158A1 true US20110186158A1 (en) 2011-08-04

Family

ID=41794756

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/121,699 Abandoned US20110186158A1 (en) 2008-10-02 2009-09-10 Delivery unit

Country Status (6)

Country Link
US (1) US20110186158A1 (pt)
EP (1) EP2331822A2 (pt)
CN (1) CN102171457B (pt)
BR (1) BRPI0920534A2 (pt)
DE (1) DE102008042564A1 (pt)
WO (1) WO2010037620A2 (pt)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1482807A (en) * 1921-08-31 1924-02-05 Westinghouse Electric & Mfg Co Regulator for rotary pumps and motors
US2190812A (en) * 1937-05-17 1940-02-20 Gunnar A Wahlmark Hydraulic motor or pump
US2316107A (en) * 1941-09-02 1943-04-06 Ruben Zorro David Engine
US3273341A (en) * 1963-04-29 1966-09-20 Wildhaber Ernest Positive-displacement thermal unit
CH449428A (de) * 1966-02-21 1967-12-31 Wildhaber Ernest Verdrängungsmaschine
US5351657A (en) * 1992-09-28 1994-10-04 Buck Erik S Modular power unit
US5404849A (en) * 1991-12-11 1995-04-11 Fenton; John W. Spherical engine
US7249936B2 (en) * 2001-06-01 2007-07-31 Lg Electronics Inc. Dual capacity compressor
US20070253851A1 (en) * 2004-05-25 2007-11-01 Felix Arnold Leakage Loss Flow Control

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1472291A (en) * 1974-12-24 1977-05-04 Blything W Rotary positive displacement unit

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1482807A (en) * 1921-08-31 1924-02-05 Westinghouse Electric & Mfg Co Regulator for rotary pumps and motors
US2190812A (en) * 1937-05-17 1940-02-20 Gunnar A Wahlmark Hydraulic motor or pump
US2316107A (en) * 1941-09-02 1943-04-06 Ruben Zorro David Engine
US3273341A (en) * 1963-04-29 1966-09-20 Wildhaber Ernest Positive-displacement thermal unit
CH449428A (de) * 1966-02-21 1967-12-31 Wildhaber Ernest Verdrängungsmaschine
US5404849A (en) * 1991-12-11 1995-04-11 Fenton; John W. Spherical engine
US5351657A (en) * 1992-09-28 1994-10-04 Buck Erik S Modular power unit
US7249936B2 (en) * 2001-06-01 2007-07-31 Lg Electronics Inc. Dual capacity compressor
US20070253851A1 (en) * 2004-05-25 2007-11-01 Felix Arnold Leakage Loss Flow Control

Also Published As

Publication number Publication date
BRPI0920534A2 (pt) 2015-12-29
CN102171457A (zh) 2011-08-31
DE102008042564A1 (de) 2010-04-08
EP2331822A2 (de) 2011-06-15
CN102171457B (zh) 2014-12-31
WO2010037620A3 (de) 2010-07-22
WO2010037620A2 (de) 2010-04-08

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Legal Events

Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:STEIDTEN, THOMAS;SAMERSKI, INGO;NOWITZKY, INGO;AND OTHERS;SIGNING DATES FROM 20110222 TO 20110314;REEL/FRAME:026046/0109

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION