CN101793249A - Gear pump - Google Patents
Gear pump Download PDFInfo
- Publication number
- CN101793249A CN101793249A CN200910246875A CN200910246875A CN101793249A CN 101793249 A CN101793249 A CN 101793249A CN 200910246875 A CN200910246875 A CN 200910246875A CN 200910246875 A CN200910246875 A CN 200910246875A CN 101793249 A CN101793249 A CN 101793249A
- Authority
- CN
- China
- Prior art keywords
- bearing
- gear
- pump
- live axle
- gear pump
- 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.)
- Pending
Links
- 238000007789 sealing Methods 0.000 claims abstract description 11
- 239000007788 liquid Substances 0.000 claims abstract description 5
- 238000003825 pressing Methods 0.000 claims description 5
- 238000010276 construction Methods 0.000 abstract 1
- 230000005540 biological transmission Effects 0.000 description 10
- 239000012530 fluid Substances 0.000 description 7
- 238000013461 design Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000881 depressing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
Images
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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- 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
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The present invention provides a gear pump (10), especially a gear pump for generating brake pressure in a motor vehicle hydraulic braking system. In the known gear pump, a through hole (16) for a drive shaft (22) of a gear pump (10) is sealed by a sealing element (30) in a pump housing (12). If the gear pump (10) is exerted by a primary pressure of liquid, the sealing element (30) is also exerted by the pressure and the through hole (16) must be sealed effectively by a corresponding structure. Therefore, an expensive sealing element (30) with corresponding complex structure is needed. According to the present invention, the pressure loads of the sealing element (30) can be reduced, therefore, the sealing element (30) is capable of performing construction at a low cost and effectively sealing a gear pump exerted by a primary pressure relative to the external environment.
Description
Technical field
The present invention relates to a kind of gear pump, especially for the gear pump that in automotive hydraulic brake system, produces retardation pressure with anti-skidding control function, this gear pump has: pump case and be contained in the gearing of this pump case inside, and this gearing is made up of a small gear and a gear that is driven by this small gear that is arranged on the live axle at least; The bearing means of live axle, this bearing means are made up of a clutch shaft bearing and one second bearing at least; And the through hole that in pump case, seals by seal element, live axle passes this through hole and extends to the outside.
Background technique
Up to now, the hydraulic braking sytem with anti-skidding control function often is equipped with hydraulic pressure installation, and this hydraulic pressure installation is equipped with radial piston pump (referring to for example EP 1687532A1) for this reason.Yet radial piston pump is to be made of and owing to their periodic duty is easy to produce operational noise many parts.In addition, be relatively costly and install complicated at manufacture view in order to drive the necessary device of radial piston pump.Therefore the important research and development difficult point in this technical field is to reduce operational noise and make product cost low as far as possible.
Recently for the above reasons, gear pump as pressure generator, wherein not only can be adopted internal gear pump also can adopt external gear pump by more and more.In principle, gear pump since their continuous operation compare noise with radial piston pump lower and can construct more simply and compact more drive unit is an outstanding feature.
The basic structure of gear pump for example discloses in DE102006034386A1 fully.The gear pump of describing in this document has pump case, and the live axle that is rotatably supported in the pump case passes in this pump case.On live axle, be provided with small gear, this small gear and a gear engagement in not relatively turnable mode.By driving torque is delivered on this gear from small gear, will the hydraulic transmission fluid in backlash be transported to and be positioned on high-tension side pump discharge from the pump intake that is positioned at low voltage side.The through hole that live axle passes the hydraulic seal that is arranged in pump case extends to the outside.Sealing is produced by seal element, and the sealing element is particularly had to when gear pump is loaded the liquid first pressing with respective degrees ground radially by pretension, so that the pump inner chamber is sealed reliably with respect to external environment condition.The like this special design of seal element causes it to make expensive and the main andfrictional conditions of influence on live axle.In addition, the transmission largely to be easy to causing more serious wearing and tearing and can to promote inevitable operational noise by the seal element of pretension.
Summary of the invention
In order to overcome the above-mentioned shortcoming of prior art, the present invention proposes a kind of gear pump as type as described in starting, small gear is relatively rotating but can axially movable mode be arranged on the live axle, and the live axle that has small gear can rest on second bearing close seal element that is used for the through hole of live axle in described pump case (12) of this second bearing effectively along its longitudinal axis hydraulic pressure.
Gear pump of the present invention is that with respect to the advantage that prior art has in this gear pump, the pressure load that acts on the seal element that is used for the sealing drive shaft through hole in pump case has reduced.Therefore, even in the gear pump of just depressing work, also can use the seal element that designs in mode simple more and that cost is lower.In addition, the influence that the andfrictional conditions on the live axle is produced of this seal element is very little and producing actively favourable effect aspect undesirable operational noise transmission.
In a kind of preferred implementation of the present invention, live axle has at least one convex shoulder, this convex shoulder and the annular flange flange acting in conjunction that is provided with on second bearing.Preferably, annular flange flange is designed in the side of second bearing away from small gear.
Advantageously, the annular flange flange on second bearing is designed to preferably vertically radially inwardly upright.
In another kind of preferred implementation of the present invention, the clutch shaft bearing of bearing means and second bearing are sliding bearings.
In addition advantageously, gear pump is applied in the liquid first pressing.
Other advantages of the present invention or preferred improvement project can be by drawing in the following description.
Description of drawings
Be described in the drawings a specific embodiment of the present invention and in the following description it done elaboration at length.
Unique accompanying drawing shows the present invention by means of the longitudinal section of gear pump of the present invention, and wherein this longitudinal section is to pass pump case to dissect in the zone of the bearing means of live axle.
Embodiment
In the accompanying drawings, the pump case of gear pump 10 is represented with reference character 12.This pump case 12 is at cavity 14 of its inner formation, and each gear of gear pump 10 is arranged in this cavity rotationally.The through hole 16 that forms in pump case 12 for example vertically feeds in this cavity 14.
Accompanying drawing only illustrates the small gear 20 that is the actuation gear of gear pump 10.Driven gear is covered so can't see.But can draw thus, small gear 20 meshes with the relative engaging piece of driven gear with the engaging piece that it forms on its periphery.Opposite with simplicity of illustration in the accompanying drawings, the size of cavity 14 be configured to and the size of the gear that is meshing with each other particularly width match.Therefore when small gear 20 is driven, in the backlash of each gear, hydraulic transmission fluid is transported to from the pump intake that is positioned at low voltage side and is positioned on high-tension side pump discharge.Pump intake and pump discharge design on pump case 10 in sightless in the drawings mode.Carry out the extruding of transmission fluid and carry out supercharging in transmission fluid whereby by the intermeshing tooth of each gear.
For driving pinion 20, this small gear is arranged on the live axle 22 in the mode that can not relatively rotate and not have axial force.The supporting of no axial force refers to a kind of like this supporting, and promptly live axle 22 can be carried out relative movement with respect to small gear 20 along its longitudinal axis.Therefore small gear 20 and live axle 22 can move relative to each other.Under operating conditions, the opposite action of hydraulic force of identical size but action direction is on two outsides of small gear 20.Above-mentioned power is cancelled out each other, thus small gear 20 in cavity 14 inside by centering.
Through hole 16 internal diameters own are set to obviously greater than the desired size of the external diameter of second drive shaft section 22.2.Produce annular space 24 thus, in this annular space, be provided with seal element 30.This seal element 30 be designed to the annular and driven shaft part 22.2 pass.Seal element 30 firmly is pressed in the through hole 16 of pump case 12 in all sides.Preferably use traditional radial axle seal ring as seal element 30.
The bearing means of live axle 22 is made up of two axially spaced bearings 32.1 and 32.2.Two bearings 32 are held on the periphery of the drive shaft section 22.1 with big external diameter and are implemented as sliding bearing.Clutch shaft bearing 32.1 away from seal element 30 constitutes floating bearing in this bearing pack zoarium.This floating bearing is implemented as the structure of hollow circle tube.Near second bearing 32.2 of seal element 30 its near have on seal element 30 distolateral vertically radially to inner process, around annular flange flange 34.The size of this annular flange flange 34 is configured to match with the size of the convex shoulder 22.3 of live axle 22, makes the size of the internal diameter that limited by annular flange flange 34 less times greater than the external diameter of second drive shaft section 22.2.
Be pressed into to fixed-site second bearing 32.2 in the through hole 16 of pump case 12 and will load axial force transmission to live axle 22 on pump case 12.These axial forces for example act on the end face of first drive shaft section 22.1 and the hydraulic pressure first pressing that maybe may be existed by the hydraulic pressure in pump case 12 internal actions produces.These axial forces make live axle 22 move with respect to small gear 20 in pump case 12 inside, rest on effectively on the annular flange flange 34 of second bearing 32.2 until convex shoulder 22.3 hydraulic pressure of live axle.Effectively be interpreted as about hydraulic pressure, make at this second bearing 32.2 and the annular space 24 that exists between with the seal element 30 of through hole 16 sealing separates on hydraulic pressure with pump inner chamber remaining part by putting.Therefore can not form the high stress level of pump inner chamber and the hydraulic pressure load of seal element 30 in this annular space 24 is reduced.Thereby employed seal element 30 needn't seal to such an extent that be about the overvoltage of 140bar (crust) and so even can be applied in the gear pump 10 that there is the liquid first pressing in its suction side as the order of magnitude that may occur in short-term in gear pump 10.
Has the device that second bearing 32.2 of annular flange flange 34 can fail back transmission fluid when being provided in live axle 22 rotational motions on its interior week and on the inboard of annular flange flange 34 at it.These devices preferably crooked twist, inwardly that is the groove that opens wide towards live axle 22, select cross section, groove depth and the pitch between their helixes of these grooves, make when drive shaft turns the pressure drop that produces the direction of pointing to pump case inside.This effect makes the transmission fluid leakage of second bearing 32.2 reach minimum.Simultaneously, the transmission fluid that imports in the groove that opens wide forms lubricating film, and this lubricating film reduces the friction between second bearing 32.2 and the live axle 22 and suppress live axle 22 to cause that the vibration transfer of noise is on pump case 12.
Certainly, can expect NM other modifications or favourable improvement project, and can not break away from basic design of the present invention above-mentioned specific embodiment.
Claims (6)
1. especially for the gear pump that produces retardation pressure in the automotive hydraulic brake system with anti-skidding control function, this gear pump has:
Pump case (12) and be contained in the inner gearing of this pump case (12), this gearing is made up of a small gear (20) and the gear by this small gear (20) driving that is arranged on the live axle at least,
The bearing means of described live axle (22), this bearing means are made up of a clutch shaft bearing (32.1) and one second bearing (32.2) at least, and
By the through hole (16) of seal element (30) sealing, described live axle (22) passes this through hole and extends to the outside in described pump case (12),
It is characterized in that:
Described small gear (20) is relatively rotating but can axially movable mode be arranged on the described live axle (22), and
The described live axle (22) that has described small gear (20) can rest on described second bearing (32.2) effectively along its longitudinal axis hydraulic pressure, and described second bearing is near the described seal element (30) that is used for the through hole (16) of live axle (22) in described pump case (12).
2. by the described gear pump of claim 1, it is characterized in that:
Described live axle (22) has at least one convex shoulder (22.3), this convex shoulder and annular flange flange (34) acting in conjunction of going up setting at described second bearing (32.2).
3. by claim 1 or 2 described gear pumps, it is characterized in that:
Described annular flange flange (34) is designed in the side of described second bearing (32.2) away from described small gear (20).
4. by claim 2 or 3 described gear pumps, it is characterized in that:
Described annular flange flange (34) on described second bearing (32.2) is designed to preferably vertically radially inwardly upright.
5. by one of claim 1 to 4 described gear pump, it is characterized in that:
The described clutch shaft bearing (32.1) and described second bearing (32.2) of described bearing means are sliding bearings.
6. by one of claim 1 to 5 described gear pump, it is characterized in that:
Described gear pump (10) is applied in the liquid first pressing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008054419.1 | 2008-12-09 | ||
| DE200810054419 DE102008054419A1 (en) | 2008-12-09 | 2008-12-09 | Gear pump, particularly for generating brake pressure in slip controllable hydraulic brake system of motor vehicle, has pump housing and gear wheel arrangement accommodated inside pump housing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101793249A true CN101793249A (en) | 2010-08-04 |
Family
ID=42145305
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910246875A Pending CN101793249A (en) | 2008-12-09 | 2009-12-04 | Gear pump |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN101793249A (en) |
| DE (1) | DE102008054419A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104956087A (en) * | 2013-01-29 | 2015-09-30 | 罗伯特·博世有限公司 | Internal gear pump |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2089990U (en) * | 1991-01-18 | 1991-12-04 | 程樱 | Double direction floating gear pump |
| CN2283146Y (en) * | 1997-04-30 | 1998-06-03 | 于光 | Special-shaped bearing |
| CN1598314A (en) * | 2004-09-20 | 2005-03-23 | 徐福刚 | Hydraulic gear pump |
| CN2773351Y (en) * | 2005-01-04 | 2006-04-19 | 刘远军 | Local hydraulic compensated gear pump |
| CN2900865Y (en) * | 2006-03-31 | 2007-05-16 | 吴涛慧 | Inside engaged gear pump |
| US20080166254A1 (en) * | 2006-09-28 | 2008-07-10 | Martin Jordan | Hydraulic device |
| CN201121581Y (en) * | 2007-11-02 | 2008-09-24 | 邢台市小龙王精密液压泵业有限公司 | High pressure-resistant anti-overloading gear pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10353834A1 (en) | 2003-11-18 | 2005-06-16 | Robert Bosch Gmbh | Multi-piston pump |
| JP2006170089A (en) * | 2004-12-16 | 2006-06-29 | Hitachi Ltd | Pump device |
| DE102006034386B4 (en) | 2006-07-25 | 2017-10-26 | Robert Bosch Gmbh | gear pump |
| DE102007054401A1 (en) * | 2007-11-14 | 2009-05-20 | Robert Bosch Gmbh | liquid pump |
-
2008
- 2008-12-09 DE DE200810054419 patent/DE102008054419A1/en not_active Withdrawn
-
2009
- 2009-12-04 CN CN200910246875A patent/CN101793249A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2089990U (en) * | 1991-01-18 | 1991-12-04 | 程樱 | Double direction floating gear pump |
| CN2283146Y (en) * | 1997-04-30 | 1998-06-03 | 于光 | Special-shaped bearing |
| CN1598314A (en) * | 2004-09-20 | 2005-03-23 | 徐福刚 | Hydraulic gear pump |
| CN2773351Y (en) * | 2005-01-04 | 2006-04-19 | 刘远军 | Local hydraulic compensated gear pump |
| CN2900865Y (en) * | 2006-03-31 | 2007-05-16 | 吴涛慧 | Inside engaged gear pump |
| US20080166254A1 (en) * | 2006-09-28 | 2008-07-10 | Martin Jordan | Hydraulic device |
| CN201121581Y (en) * | 2007-11-02 | 2008-09-24 | 邢台市小龙王精密液压泵业有限公司 | High pressure-resistant anti-overloading gear pump |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104956087A (en) * | 2013-01-29 | 2015-09-30 | 罗伯特·博世有限公司 | Internal gear pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102008054419A1 (en) | 2010-06-10 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20100804 |