CN101896723A - Liquid pump - Google Patents

Liquid pump Download PDF

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Publication number
CN101896723A
CN101896723A CN2008801205800A CN200880120580A CN101896723A CN 101896723 A CN101896723 A CN 101896723A CN 2008801205800 A CN2008801205800 A CN 2008801205800A CN 200880120580 A CN200880120580 A CN 200880120580A CN 101896723 A CN101896723 A CN 101896723A
Authority
CN
China
Prior art keywords
pump
pressure
sealing unit
liquid pump
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.)
Granted
Application number
CN2008801205800A
Other languages
Chinese (zh)
Other versions
CN101896723B (en
Inventor
D·弗希
M·霍赫德费尔
H·赫尔曼
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 CN101896723A publication Critical patent/CN101896723A/en
Application granted granted Critical
Publication of CN101896723B publication Critical patent/CN101896723B/en
Expired - Fee Related 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
    • 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
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Abstract

The invention relates to a liquid pump (10) comprising a pump housing (12), a pump unit (14) for generating an operating pressure (pB), a drive shaft (16) used to drive the pump unit (14) and guided out of the pump housing (12) on a drive/output side, and a sealing unit (18) sealing the passage. When the liquid pump (10) is subjected to an admission pressure (pv), the pressurised liquid generates, in the region of the sealing unit (18), at least one pressure field (20) facing the sealing unit (18) and at least one pressure field (22) facing away from the sealing unit (18). According to the invention, an asymmetrical arrangement of the pressure fields (20, 22) is provided.

Description

Liquid pump
Technical field
The present invention relates to a kind of according to independent claims 1 liquid pump as described in the preamble.
Background technique
Usually, the liquid pump that is designed to gear pump comprises the live axle that is provided with rotationally, and this live axle puts in the pump case of liquid pump.Be provided with the pump unit that has at least one gear in pump case, this gear produces pump function.Live axle only passes and will drive energy transfer to above-mentioned at least one gear in a side of pump case.This passes and must seal by the sealing unit that for example is designed to the radial axle seal ring.If liquid pump produces working pressure pB or liquid pump is loaded initial pressure pv, the sealing unit bears the thrust load of generation by making pump case with respect to external world's sealing.This thrust load F by the initial pressure pv of the sealed diameter D of axle and existence according to formula F=pv*D 2* calculate π/4.
DE 19924057A1 shows a kind of liquid pump, and it comprises pump case and is arranged on the pump assembly that being used in this pump case produces liquid working pressure.For the driven pump assembly, be provided with the live axle that passes from pump case at driving side/outlet side, this live axle is bearing in the pump case by bearing unit.This passes by sealing unit and seals.When liquid pump was loaded, the liquid that is under the pressure acted on the sealing unit at least one towards the pressure field of sealing unit and at least one pressure field of sealing unit dorsad in the region generating of sealing unit.
Summary of the invention
In contrast to this, have the following advantages according to the described liquid pump of the present invention of the feature of independent claims 1: described pressure field is designed to be asymmetric layout.Therefore, the surface that is loaded by initial pressure varies in size.By the asymmetric layout of the pressure field relevant with initial pressure, the axial force that produces when liquid pump is loaded initial pressure can be cancelled in liquid pump.On live axle, form equilibrium of forces.The bearing unit of liquid pump only needs bearing radial force, and this has simplified bearing unit and has provided cost savings thus.Advantageously, reduced pressure loading on sealing unit.Because sealing unit only need bear less pressure, sealing unit can on cost obvious cheaper mode design.
By described measure and improvement project in the dependent claims, can advantageously carry out favourable improvement to the liquid pump that in independent claims, provides.
In order to obtain the asymmetric layout of pressure field, be preferably greater than the pressure field of sealing unit dorsad towards the pressure field of sealing unit.Therefore, obtained the optimum sealing of pump case with respect to the external world.If the pump unit has a plurality of gears, the area of these pressure fields can be assigned on each gear.
Particularly advantageously be, towards the pressure field of sealing unit than the pressure field of seal element dorsad big the cross sectional area of live axle.
Advantageously, can be simply and realize expansion by the groove in a sealing surface of liquid pump inexpensively towards the pressure field of sealing unit.Therefore, the surface that is loaded by initial pressure varies in size.Produced stress-free surface here, with respect to sealing unit.
Preferably, the pressure field relevant with the working pressure of liquid pump is designed to be symmetric arrangement.Therefore, the pressure field acting in conjunction with initial pressure forms equilibrium of forces on live axle.
Because the pressure field of the sealing unit dorsad of initial pressure is designed to be designed to symmetry less than pressure field towards the pressure field of live axle and working pressure, has produced the stress-free surface with respect to sealing unit.In order to make this stress-free surface unloading in mode simple and with low cost, a passage preferably is set, this passage is used for connecting groove and the chamber that is positioned at the pump unit.
This pump unit is a gear drive.Advantageously, the above-mentioned chamber in the pump unit is the chamber between the tooth of two gears, just so-called inter-lobe clearance.Preferably, utilize adjacent inter-lobe clearance after the summit, the expansion by the gap produces negative pressure thus.
In addition, in order to make the unloading of stress-free surface, a passage can be set also, this passage is used to connect groove and an apotheca, and this pipeline makes it possible to simply and realize inexpensively unloading equally.
Accompanying drawing shows favourable mode of execution of the present invention, below described.In the accompanying drawings, identical reference character represents to carry out the parts or the element of same or similar function.
Description of drawings
Fig. 1 shows the signal longitudinal sectional view of liquid pump of the present invention.
Fig. 2 shows the schematic transverse sectional view of liquid pump of the present invention.
Embodiment
Fig. 1 shows liquid pump 10 of the present invention, and the form of this liquid pump is the gear pump with pump case 12, and this pump case has inner chamber 46, and this inner chamber comprises the inlet 48 and the outlet on the pressure side 50 of suction side.By the shaft through-hole of needs sealing, the live axle 16 of She Zhiing extends in the pump case 12 rotationally, and this drive shaft is arranged on the pump unit 14 in the inner chamber 46 of pump case 12.
Pump unit 14 is used for that is to say under the condition that produces corresponding high fluid pressure level, is producing working pressure p BCondition under carry liquid.Here, liquid is pumped into liquid pump 10 on the pressure side from the suction side of liquid pump 10 usually.For this reason, pump unit 14 preferably has gear drive, and this gear drive generally includes at least two gears 38,40 as Fig. 2, and one of them gear drives by live axle 16.According to the layout and the size of these gears, at this preferably external gear pump, crescent gear pump, Gerotor pump or volute pump.Liquid pump 10 is carried the liquid for the treatment of pumping usually equably.Working pressure p BPressure field 30,32 be symmetric arrangement.
Live axle 16 is rotatably supported in the pump case 12 by bearing unit 52,54.Between shaft through-hole and live axle 16, be provided with the sealing unit 18 that is designed to Simmer ring, with outside canned pump housing 12 to external world in other words on live axle 16.Simmer ring 18 is arranged in the recess of pump case 12 by drive fit.Preferably, this Simmer ring 18 is designed to the radial axle seal ring, and this radial direction seal ring radially is pressed onto on the surface of live axle 16.Simmer ring 18 must be according to being applied to the initial pressure pv on the liquid pump 10 and producing working pressure p in pump case 12 BDesign, that is to say, Simmer ring 18 must apply enough big radial force according to stress level, to carry out its function.When liquid pump 10 was loaded initial pressure pv, the liquid that is under the pressure acted on the sealing unit 18 at least one towards the pressure field 20 of sealing unit 18 and at least one pressure field 22 of sealing unit 18 dorsad in the region generating of sealing unit 18.
In order directly in liquid pump 10, to offset the axial force F that causes by initial pressure pv, pressure field 20,22 is designed to be asymmetric layout according to the present invention.In the present embodiment, towards the pressure field 20 of sealing unit 18 greater than the pressure field 22 of sealing unit 18 dorsad.Preferably, towards the pressure field 20 of sealing unit 18 than the pressure field 22 of sealing unit 18 dorsad big the area of cross section 24 of live axle 16.
According to Fig. 2, realized expansion towards the pressure field 20 of sealing unit 18 by the groove 26 in a sealing surface 28 of liquid pump 10.In order to make these groove 26 unloadings that form no pressure surface, be provided with a passage 34, this passage is used for connecting this groove 26 and the chamber 36 that is positioned at pump unit 14.Preferably, this chamber 36 that is arranged in pump unit 14 chamber between the tooth of two gears 38,40 preferably.In addition, in order to make no pressure surface 26 unloadings that are designed to groove, also be provided with a pipeline 42, this pipeline is used to connect this groove and an apotheca 44.Certainly, these measures that are used to unload also can be provided with individually.

Claims (9)

1. liquid pump (10), it comprises pump case (12), be used to produce the pump unit (14) of working pressure (pB), the live axle (16) that is used to drive described pump unit (14) that passes from described pump case (12) at driving side/outlet side, and this is passed the sealing unit (18) that seals, wherein, when liquid pump (10) is loaded initial pressure (pV), the liquid generation in the zone of described sealing unit (18) that is under the pressure acts at least one pressure field towards described sealing unit (18) (20) on the described sealing unit (18) and the pressure field (22) of at least one described dorsad sealing unit (18), it is characterized in that, described pressure field (20,22) is asymmetric layout.
2. liquid pump as claimed in claim 1 is characterized in that, towards the pressure field (20) of described sealing unit (18) greater than the pressure field (22) of described sealing unit (18) dorsad.
3. liquid pump as claimed in claim 1 or 2 is characterized in that, towards the pressure field (20) of described sealing unit (18) than the pressure field (22) of described sealing unit (18) dorsad big the area of cross section (24) of described live axle (16).
4. as each described liquid pump in the claim 1 to 3, it is characterized in that, in a sealing surface (28), be provided with groove (26).
5. each described liquid pump in the claim as described above is characterized in that the pressure field (30,32) of described working pressure (pB) is symmetric arrangement.
6. each described liquid pump in the claim as described above is characterized in that be provided with a passage (34), this passage is used for connecting described groove (26) and the chamber (36) that is positioned at described pump unit (14).
7. each described liquid pump in the claim as described above is characterized in that described pump unit (14) is a gear drive.
8. liquid pump as claimed in claim 1 is characterized in that, the chamber (36) that is arranged in described pump unit (14) is the chamber between the tooth of two gears (38,40).
9. liquid pump as claimed in claim 1 is characterized in that, is provided with a pipeline (42), and this pipeline is used to connect a described groove (26) and an apotheca (44).
CN2008801205800A 2007-12-17 2008-10-23 Liquid pump Expired - Fee Related CN101896723B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007060758A DE102007060758A1 (en) 2007-12-17 2007-12-17 liquid pump
DE102007060758.1 2007-12-17
PCT/EP2008/064384 WO2009077248A1 (en) 2007-12-17 2008-10-23 Liquid pump

Publications (2)

Publication Number Publication Date
CN101896723A true CN101896723A (en) 2010-11-24
CN101896723B CN101896723B (en) 2013-05-01

Family

ID=40525085

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2008801205800A Expired - Fee Related CN101896723B (en) 2007-12-17 2008-10-23 Liquid pump

Country Status (6)

Country Link
US (1) US20100316520A1 (en)
EP (1) EP2235375B1 (en)
JP (1) JP5583025B2 (en)
CN (1) CN101896723B (en)
DE (1) DE102007060758A1 (en)
WO (1) WO2009077248A1 (en)

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* Cited by examiner, † Cited by third party
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US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
FR1241958A (en) * 1958-11-15 1960-09-23 Bosch Gmbh Robert Hydraulic machine
US3050010A (en) * 1960-02-23 1962-08-21 Thompson Ramo Wooldridge Inc Pressure loaded pump
DE1553133A1 (en) * 1966-12-23 1970-07-30 Maag Zahnraeder & Maschinen Ag High pressure gear pump
JPS4965805U (en) * 1972-09-22 1974-06-08
DE2403319A1 (en) * 1974-01-24 1975-07-31 Bosch Gmbh Robert GEAR MACHINE
DE2610827A1 (en) * 1976-03-15 1977-09-29 Bosch Gmbh Robert GEAR MACHINE (PUMP OR MOTOR)
JPS6097391U (en) * 1983-12-08 1985-07-03 三菱重工業株式会社 rotating fluid machine
US4737087A (en) * 1984-12-10 1988-04-12 Barmag Ag Drive shaft seal for gear pump and method
CN1006321B (en) * 1987-03-05 1990-01-03 江苏工学院 Balance unit for pump axial force
US5022837A (en) * 1989-11-13 1991-06-11 Sta-Rite Industries, Inc. Seal arrangement for a gear machine
US5180297A (en) * 1991-03-22 1993-01-19 The Gorman-Rupp Company Fluid transfer pump with shaft seal structure
US6213173B1 (en) * 1998-04-15 2001-04-10 K. J. Manufacturing Co. Engine air purge apparatus and method
KR100298356B1 (en) * 1998-11-13 2001-11-22 윤종용 ATM 2 processing apparatus and method of ATM network
US6149415A (en) * 1999-02-11 2000-11-21 Viking Pump, Inc. Internal gear pump having a feed groove aligned with the roots of the idler teeth
DE19924057A1 (en) 1999-05-26 2000-11-30 Bosch Gmbh Robert Gearwheel machine for hydrostatic drives has two axially displaceable component parts pressing axially onto side faces of gearwheels with different sized forces
JP2002147368A (en) * 2000-11-09 2002-05-22 Fuji Heavy Ind Ltd Internal rotor type fluid device
AU2003294889A1 (en) * 2002-12-19 2004-07-14 Haldex Hydraulics Gmbh Gear-type machine comprising lateral axial plates
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control

Also Published As

Publication number Publication date
JP2011506837A (en) 2011-03-03
EP2235375A1 (en) 2010-10-06
EP2235375B1 (en) 2013-12-11
JP5583025B2 (en) 2014-09-03
WO2009077248A1 (en) 2009-06-25
DE102007060758A1 (en) 2009-06-18
US20100316520A1 (en) 2010-12-16
CN101896723B (en) 2013-05-01

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CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20130501

Termination date: 20201023

CF01 Termination of patent right due to non-payment of annual fee