CN102086859A - Piston pump and hydraulic device of vehicle brake system, and vehicle brake system - Google Patents
Piston pump and hydraulic device of vehicle brake system, and vehicle brake system Download PDFInfo
- Publication number
- CN102086859A CN102086859A CN2010105782384A CN201010578238A CN102086859A CN 102086859 A CN102086859 A CN 102086859A CN 2010105782384 A CN2010105782384 A CN 2010105782384A CN 201010578238 A CN201010578238 A CN 201010578238A CN 102086859 A CN102086859 A CN 102086859A
- Authority
- CN
- China
- Prior art keywords
- piston
- reciprocating pump
- ring
- pumping cylinder
- low pressure
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—Pistons
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4031—Pump units characterised by their construction or mounting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0448—Sealing means, e.g. for shafts or housings
Abstract
The invention relates to a piston pump and a hydraulic device of a vehicle brake system, and a vehicle brake system. The piston pump (10) of the vehicle brake system comprises a pumping cylinder (12) and a piston (14) capable of performing mobile support in the pumping cylinder (12). The piston is sealed relative to the pumping cylinder (12) in a fluid-tight manner through sealing devices (18) which can be divided into high-pressure sealing members (20) and low-pressure sealing member (22).
Description
Technical field
The present invention relates to a kind of reciprocating pump of motor vehicle braking system, the piston that described reciprocating pump has pumping cylinder and supports movably in described pumping cylinder, described piston seals by means of seal arrangement in a fluid tight manner with respect to its driving side.The invention still further relates to a kind of the have hydraulic pressure installation that is used for motor vehicle braking system of this reciprocating pump and motor vehicle braking system with this reciprocating pump.
Background technique
Hydraulic pressure installation is a constituent element of modern vehicle braking system, and described hydraulic pressure installation is applied on motor vehicle such as car or the load-carrying vehicle, is used to the retardation pressure that provides controlled.For retardation pressure is measured, described hydraulic pressure installation has the pump that comprises a plurality of pump elements.Usually each pump element is configured to reciprocating pump, in described reciprocating pump, piston is bearing in the pumping cylinder movably.Driving to piston realizes that by eccentric wheel described eccentric wheel is installed in by on the electric motor driven axle.Described piston along vertical shift-in of described piston with shift out, is carried out delivery stroke and suction stroke thus continuously in conveyor chamber.
Gap by the structural type decision is arranged between piston and pumping cylinder, and described gap must be sealed by means of Sealing, to avoid leakage.Sealing need be installed, the sealing part separates the conveyor side of piston and the driving side of piston in pumping cylinder in a fluid tight manner for this reason.In order to realize piston frictionless motion as far as possible in pumping cylinder, described piston slides along guiding element on fluid film.Along with the fluid that the suction stroke motion is brought into is failed back by means of the resiliently deformable of Sealing in reciprocal delivery stroke motion usually.In the motion of this delivery stroke, in conveyor chamber and on Sealing, produce high pressure thus.Described Sealing must be determined size according to this high pressure.
In addition, the motion of piston also can little by little cause the wear phenomenon on Sealing, and described wear phenomenon shows as crack or the gap between Sealing and the piston.These cracks and gap may be flow through by fluid subsequently, and described thus fluid arrives driving side from conveyor side.This leakage current causes damage with the function of a kind of mode that is not hoped to reciprocating pump.
Described piston also may can apply heat load to Sealing then owing to particularly generating heat in the frictional force on eccentric shaft bearing on the driving side, thereby described Sealing is damaged.
Summary of the invention
Task of the present invention is, overcomes above-mentioned defective and a kind of reciprocating pump that is used for motor vehicle braking system is provided, and described reciprocating pump makes the possibility that creates with the low-cost parts of the utilization of known piston pump simplified in comparison.
Task of the present invention is to solve by the reciprocating pump according to claim 1.Described task is also by being solved according to the hydraulic pressure installation of claim 9 and according to the motor vehicle braking system of claim 10.Dependent claims is described favourable improvement project of the present invention.
According to the present invention, a kind of reciprocating pump of motor vehicle braking system has been proposed, the piston that described reciprocating pump has pumping cylinder and supports movably in described pumping cylinder, described piston seals by means of seal arrangement in a fluid tight manner with respect to its driving side, wherein, described seal arrangement is divided into high-pressure sealing ring and low pressure seal spare.
According to the present invention, described seal arrangement is designed to be made from multiple components, promptly as high-pressure sealing ring and low pressure seal spare.At the reciprocating pump run duration, can very high pressure appear at the input side (suction side) of pump in some riding manipulations.These high pressure exert an influence to seal arrangement towards the driving side direction of pump.These high pressure have guaranteed that the sealing lip of high pressure sealing ring is pressed on the hole wall.Therefore, the space between low pressure seal spare and the high-pressure sealing ring is separated by fluid-tight ground.Therefore, described high-pressure sealing ring preferably is made of a kind of material that can resist high pressure and simultaneously can be reliably conveyor side and driving side be separated in a fluid tight manner.On the contrary, described low pressure seal spare is designed to, and is used for when low pressure appears in the suction side at pump, avoids fluid not pass the arrival driving side from the suction side of pump with not being hoped.Because the high pressure of delivery stroke does not act on the low pressure seal spare, so described low pressure seal spare can be advantageously by cheaply, the material that is usually used in the conventional seals part constitutes.To i.e. sealing under high pressure of these two kinds of different tasks and sealing under low pressure, utilize a kind of solution of multi-part type seal arrangement to make the use of more low-cost parts become possibility according to the present invention, described more low-cost parts can also be assembled more simply.
First of reciprocating pump kind of favourable improvement project according to the present invention, with the high-pressure sealing ring fixed-site be fixed on the piston.
Be installed in to fixed-site high-pressure sealing ring on the piston in the movement process of piston along with described piston motion.For this reason, described high-pressure sealing ring for example is pressed on the described piston.Yun Dong high-pressure sealing ring can seal the gap between piston and the pumping cylinder in the following way like this: described high-pressure sealing ring (for example being configured to labyrinth) abuts against the parts (for example prolongation on the filter screen) of an other encirclement piston vertically.This axially near carrying out especially, that is to say that part at the high discharge pressure of the generation of piston stroke when the delivery stroke motion finishes.Described axially near also preventing high-pressure sealing ring generation wear phenomenon, make the longer service life of whole sealing device thus.
Second of reciprocating pump kind of favourable improvement project according to the present invention, described high-pressure sealing ring be configured to be arranged on with having fixed-site the ring-type element on the piston and on described ring-type element, be shaped be close to sealing lip on the pumping cylinder.
The zone that high-pressure sealing ring is configured to ring-type element is connected high-pressure sealing ring with piston, specifically power transmission connects.Can form this power transmission especially simply connects.Described ring-type element can also be configured for guide ring or the supporting ring of piston in pumping cylinder simultaneously.Form sealing lip on ring-type element, described sealing lip covers the gap that needs sealing, and is close on the pumping cylinder in the periphery.If fluid is exerted pressure to sealing lip during delivery stroke, then described sealing lip radially is pressed against on the pumping cylinder.Gap between piston and the pumping cylinder is closed in a fluid tight manner thus.Described sealing lip is advantageously made by the high-strength material that can resist high pressure.Thus, the working life that can reduce the wearing and tearing of sealing lip and improve whole high-pressure sealing ring.That is to say that described ring-type element leads to piston and under high pressure is close on the wall of described pumping cylinder in pumping cylinder.
The third favourable improvement project of reciprocating pump according to the present invention is configured to have the ring that cross section is an O shape with described low pressure seal spare.
Because according to the present invention, the high pressure that is produced by delivery stroke acts on the high-pressure sealing ring, determine so advantageously low pressure seal spare is carried out size, thereby make it sustain the low pressure of driving side separately.For such low pressure is sealed, can use the ring of commercial general cross section, promptly so-called O shape ring as O shape.Therefore, can be with very low cost realization piston and the clearance seal between the pumping cylinder.
The 4th of reciprocating pump the kind of favourable improvement project according to the present invention is configured to have the ring that cross section is a C shape with described low pressure seal spare.
According to this improvement project, the cross section of described low pressure seal spare is c-shaped.By this shape, described low pressure seal spare can be advantageously seals the stroke distances of the length of piston, and need not to occupy the volume with the corresponding O shape ring of its radius.When piston motion, perhaps need this volume is compressed, this may cause the increase of crooked merit.Described design proposal has advantageously realized more compact structure of reciprocating pump of the present invention.In addition, described C shape the heat between piston and the housing is isolated also is favourable.
The 5th of reciprocating pump the kind of favourable improvement project according to the present invention, described low pressure seal spare is radially supported at intervals with the side of piston.
According to the present invention, between low pressure seal spare and piston face, have at interval.This interval separates described low pressure seal spare and piston side.If described piston during movement generates heat owing to for example frictional force on eccentric shaft bearing, then can not proceed to the direct heat transmission on the low pressure seal spare.Got rid of the possibility that low pressure seal spare is subjected to undesirable heat load thus.The friction of piston on low pressure seal spare also avoided at described interval, avoided thus being damaged by wearing and tearing.
The 6th of reciprocating pump the kind of favourable improvement project is provided with spring element according to the present invention, and by this spring element, cross section is that the ring of C shape can be resisted against on the pumping cylinder by radially outside pretension.
Described cross section is the ring of C shape, and promptly so-called C shape ring is constructed to have an internal cavities.According to the present invention, spring element is arranged in this cavity.Described spring element advantageously is configured to described C shape is encircled the annular spring that radially outwards presses on the pumping cylinder inwall.Described pumping cylinder can advantageously have step on this inwall, described C shape ring is bearing on the described step vertically.This invention similarly comprises such step design on piston, wherein, is supported by this step so described C shape is encircled vertically.Annular spring can also advantageously be constructed forming V-shape on cross section, also C shape is encircled vertically by pretension thus.Cross section be C shape low pressure seal spare can by means of spring element of the present invention advantageously not only radially but also axially by pretension, thus, during stroke, guaranteed optimum sealing effect.
The 7th of reciprocating pump the kind of favourable improvement project according to the present invention is arranged for low pressure seal spare vertically and seals between piston and pumping cylinder.
The described low pressure seal spare that radially is resisted against on the pumping cylinder inwall by pretension preferably is close to design vertically on the step and high-pressure sealing ring on the pumping cylinder.If piston moves at suction stroke together with high-pressure sealing ring, then described low pressure seal spare is crushed between step and high-pressure sealing ring vertically.Thus, described low pressure seal spare is pressed towards the seal clearance between high-pressure sealing ring and pumping cylinder, and described seal clearance is thus by the sealing of fluid-tight ground.The low pressure seal spare of axial seal can advantageously be configured to commercial general seal ring, and this can simplify assembling and reduce cost.
Advantageously be equipped with this reciprocating pump of the present invention for hydraulic pressure installation of the present invention.Task of the present invention is also solved by the motor vehicle braking system with such reciprocating pump of the present invention.
Description of drawings
Below will be to being described in detail by means of the embodiment of schematic figures to solution of the present invention.Accompanying drawing shows reciprocating pump of the present invention with longitudinal sectional view.
Embodiment
Reciprocating pump 10 has been shown in the accompanying drawing, and described reciprocating pump comprises housing pumping cylinder 12 and at the described housing piston 14 of mobile-bearing in the pumping cylinder in other words in other words.Between pumping cylinder 12 and piston 14 gapped 16.This gap 16 is sealed in a fluid tight manner by means of seal arrangement 18.Described seal arrangement 18 comprises that high-pressure sealing ring 20 and low pressure seal spare 22 are as seal element.The sliding movement of piston 14 is substantially by guide ring 24 guiding.
Described piston 14 is in operation and is driven by eccentric wheel 26.Therefore, described eccentric wheel 26 is pressed on the end face of piston 14 for this reason, thus described piston is advanced vertically housing bore in other words in the pumping cylinder 12, and carries out delivery stroke thus.For the suction stroke of following after delivery stroke, described piston 14 is released from pumping cylinder 12 vertically by the spring force of spring (not shown).Thus, at the fluid that the conveyor side suction of piston 14 need be carried, be brake fluid in the embodiment shown.
In order to ensure the motion of piston 14 low frictions, described piston has fluid film.Described piston 14 on fluid film that this fluid of being carried by needs constitutes along the housing bore wall in other words pumping cylinder 12 slide.Therefore, the fluid of described needs conveying is along with each suction stroke of piston 14 also passes through up to arriving on the high-pressure sealing ring 20 on guide ring 24 next doors with very little amount.
High-pressure sealing ring 20 comprises ring-type element 30 and sealing lip 32.Described high-pressure sealing ring 20 is connected with piston 14 power transmission on the side 28 of described piston by means of described ring-type element 30.Connect based on this, described high-pressure sealing ring 20 is motion together along with each motion of piston.Described sealing lip 32 is designed on the ring-type element 30, and described sealing lip extends to the housing hole wall in other words on the pumping cylinder 12 from ring-type element 30 always.Therefore, gap 16 is sealed by high-pressure sealing ring 20 fluid-tight ground.Only stay narrow seal clearance 34 at this in other words between the pumping cylinder 12 at sealing lip 32 and housing.
In the embodiment shown, low pressure seal spare 22 is designed to the ring that cross section is a C shape, described ring radial outward sealing, and radial inward is opened wide.Therefore, described C shape ring has central cavity, and described cavity one side is sealed by ring-type element 30, and opens wide at the opposite side towards eccentric wheel 26.The spring element that is designed to metal spring 36 is arranged in this cavity.Described metal spring 36 is resisted against the radially outside pretension of described low pressure seal spare 22 on the pumping cylinder.Here, described low pressure seal spare 22 radially with piston 14 separately, thereby make the described piston neither can also can be to low pressure seal spare 22 with thermal energy transfer with frictional force.It is V-arrangement that described metal spring 36 is designed on cross section, and be arranged on like this in the low pressure seal spare 22, thus the parts that described metal spring also are resisted against described low pressure seal spare 22 pretensions vertically be close to promptly a side be that ring-type element 30 opposite sides are on the pumping cylinder 12.Described low pressure seal spare 22 is close on the step 38 of pumping cylinder 12 vertically and is close on the high-pressure sealing ring 20.At this, described low pressure seal spare 22 covers seal clearance 34.
22 of this low pressure seal spares that is surrounded are compressed vertically in other words when reciprocating pump 14 motions and are crowded together vertically.At this, described metal spring 36 is taking place when this axial orientation is out of shape low pressure seal spare 22 to be resetted by its spring force.
In delivery stroke, a part of fluid arrives in the space 40 that is surrounded by pumping cylinder 12, piston 14, guide ring 24 and high-pressure sealing ring 20.Because high-pressure sealing ring 20 is with piston 14 motion, so this can impel the fluid that gathers in space 40 is failed back on the one hand.On the other hand, the pressure in space 40 is particularly exerted pressure to high-pressure sealing ring 20.This pressure radially outwards presses housing in other words on the pumping cylinder 12 with the sealing lip 32 of high-pressure sealing ring 20.Described pressure is determined size by described sealing lip 32 suitable moulding, thereby makes high-pressure sealing ring 20 stop escape of liquid as much as possible.
In suction stroke, described piston 14 shifts out the pumping cylinder 12 in other words from housing vertically.At this, described piston 14 applies power by means of the low pressure seal spare 22 that 20 pairs of high-pressure sealing rings are arranged between described high-pressure sealing ring 20 and the step 38.Already mentioned as mentioned, described low pressure seal spare 22 and the metal spring 36 that is arranged on wherein deform by this power.Described low pressure seal spare 22 is close between step 38 and the high-pressure sealing ring 20 by described distortion, thereby is closed with making described seal clearance 34 fluid-tight.Described in addition metal spring 36 outwards is pressed against described low pressure seal spare 22 on the pumping cylinder 12 vertically, thereby described seal clearance 34 fluid-tight ground is sealed.
Claims (10)
1. the reciprocating pump of a motor vehicle braking system (10), the piston (14) that described reciprocating pump has pumping cylinder (12) and supports movably in described pumping cylinder, described piston seals with respect to pumping cylinder (12) in a fluid tight manner by means of seal arrangement (18), it is characterized in that described seal arrangement (18) is divided into high-pressure sealing ring (20) and low pressure seal spare (22).
2. according to the described reciprocating pump of claim 1, it is characterized in that, be fixed on the piston (14) to described high-pressure sealing ring (20) fixed-site.
3. according to the described reciprocating pump of claim 2, it is characterized in that, described high-pressure sealing ring (20) be constructed to be arranged on with having fixed-site on the piston (14) ring-type element (30) and be shaped on the described ring-type element and be close to sealing lip (32) on the pumping cylinder (12).
4. according to any described reciprocating pump in the claim 1 to 3, it is characterized in that described low pressure seal spare (22) is constructed to have the ring that cross section is an O shape.
5. according to any described reciprocating pump in the claim 1 to 3, it is characterized in that described low pressure seal spare (22) is constructed to have the ring that cross section is a C shape.
6. according to any described reciprocating pump in the claim 1 to 5, it is characterized in that described low pressure seal spare (22) is radially supported at intervals with the side (28) of piston (14).
7. according to any described reciprocating pump in the claim 1 to 6, it is characterized in that, be provided with spring element (36), described cross section is that the ring of C shape can be resisted against on the pumping cylinder (12) by radially outside pretension by described spring element.
8. according to any described reciprocating pump in the claim 1 to 7, it is characterized in that described low pressure seal spare (22) is arranged for sealing vertically between described piston (14) and described pumping cylinder (12).
9. the hydraulic pressure installation of a motor vehicle braking system is characterized in that, described hydraulic pressure installation has according to any described reciprocating pump (10) in the claim 1 to 8.
10. a motor vehicle braking system is characterized in that, described motor vehicle braking system has according to any described reciprocating pump (10) in the claim 1 to 8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009047590.7A DE102009047590B4 (en) | 2009-12-07 | 2009-12-07 | Piston pump with a sealing arrangement |
| DE102009047590.7 | 2009-12-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102086859A true CN102086859A (en) | 2011-06-08 |
Family
ID=43971983
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010105782384A Pending CN102086859A (en) | 2009-12-07 | 2010-12-03 | Piston pump and hydraulic device of vehicle brake system, and vehicle brake system |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102086859A (en) |
| DE (1) | DE102009047590B4 (en) |
| FR (1) | FR2953567A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104508300A (en) * | 2012-08-03 | 2015-04-08 | 罗伯特·博世有限公司 | Low pressure sealing ring for a pump element of a hydraulic unit |
| CN106460758A (en) * | 2014-02-17 | 2017-02-22 | 罗伯特·博世有限公司 | Piston fuel pump for an internal combustion engine |
| CN110945239A (en) * | 2017-07-20 | 2020-03-31 | 罗伯特·博世有限公司 | Piston pump |
| CN110945241A (en) * | 2017-07-20 | 2020-03-31 | 罗伯特·博世有限公司 | Piston pump, in particular high-pressure fuel pump for an internal combustion engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014104050A1 (en) * | 2014-03-24 | 2015-09-24 | Netzsch-Feinmahltechnik Gmbh | Homogenizer with a high pressure and a low pressure chamber |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5007276A (en) * | 1990-05-09 | 1991-04-16 | Teledyne Industries, Inc. | Seal arrangement for use in a press assembly |
| CN2366598Y (en) * | 1998-08-19 | 2000-03-01 | 李祥龙 | 'C' type sealing means for piston |
| DE19850560A1 (en) * | 1998-11-03 | 2000-05-04 | Mannesmann Sachs Ag | Actuator cylinder for hydraulic system is used for clutch mechanism in vehicle and has axially movable seal |
| US6494465B1 (en) * | 1996-07-02 | 2002-12-17 | John Wentworth Bucknell | Seals for hydraulic assemblies |
| US20080122184A1 (en) * | 2006-11-23 | 2008-05-29 | Elringklinger Ag | Sealing arrangement |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2056770A (en) | 1969-10-08 | 1972-04-13 | Uss Engineers And Consultants, Inc | A sealing assembly fora pump |
| DE19641778A1 (en) | 1996-10-10 | 1998-04-16 | Bosch Gmbh Robert | Piston pump |
| DE19904926A1 (en) * | 1999-02-06 | 2000-08-10 | Bosch Gmbh Robert | Pump unit for a slip-controlled, hydraulic vehicle brake system |
| JP2005299808A (en) | 2004-04-13 | 2005-10-27 | Nok Corp | Seal for pump |
| US8011289B2 (en) * | 2006-01-13 | 2011-09-06 | Bwi Company Limited S.A. | Half-sleeved and sleeveless plastic piston pumps |
| DE102007052664A1 (en) | 2007-11-05 | 2009-05-07 | Robert Bosch Gmbh | Guide ring for a piston pump and piston pump |
| DE102008003454A1 (en) * | 2008-01-08 | 2009-07-09 | Robert Bosch Gmbh | Hydraulic fluid pump with a sealing element |
-
2009
- 2009-12-07 DE DE102009047590.7A patent/DE102009047590B4/en active Active
-
2010
- 2010-12-03 FR FR1060065A patent/FR2953567A1/en not_active Withdrawn
- 2010-12-03 CN CN2010105782384A patent/CN102086859A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5007276A (en) * | 1990-05-09 | 1991-04-16 | Teledyne Industries, Inc. | Seal arrangement for use in a press assembly |
| US6494465B1 (en) * | 1996-07-02 | 2002-12-17 | John Wentworth Bucknell | Seals for hydraulic assemblies |
| CN2366598Y (en) * | 1998-08-19 | 2000-03-01 | 李祥龙 | 'C' type sealing means for piston |
| DE19850560A1 (en) * | 1998-11-03 | 2000-05-04 | Mannesmann Sachs Ag | Actuator cylinder for hydraulic system is used for clutch mechanism in vehicle and has axially movable seal |
| US20080122184A1 (en) * | 2006-11-23 | 2008-05-29 | Elringklinger Ag | Sealing arrangement |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104508300A (en) * | 2012-08-03 | 2015-04-08 | 罗伯特·博世有限公司 | Low pressure sealing ring for a pump element of a hydraulic unit |
| CN106460758A (en) * | 2014-02-17 | 2017-02-22 | 罗伯特·博世有限公司 | Piston fuel pump for an internal combustion engine |
| CN106460758B (en) * | 2014-02-17 | 2019-04-05 | 罗伯特·博世有限公司 | Piston fuel pump for internal combustion engine |
| US10393112B2 (en) | 2014-02-17 | 2019-08-27 | Robert Bosch Gmbh | Piston fuel pump for an internal combustion engine |
| CN110945239A (en) * | 2017-07-20 | 2020-03-31 | 罗伯特·博世有限公司 | Piston pump |
| CN110945241A (en) * | 2017-07-20 | 2020-03-31 | 罗伯特·博世有限公司 | Piston pump, in particular high-pressure fuel pump for an internal combustion engine |
| US11261853B2 (en) | 2017-07-20 | 2022-03-01 | Robert Bosch Gmbh | Piston pump |
| CN110945239B (en) * | 2017-07-20 | 2022-04-26 | 罗伯特·博世有限公司 | Piston pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102009047590B4 (en) | 2022-05-19 |
| DE102009047590A1 (en) | 2011-06-09 |
| FR2953567A1 (en) | 2011-06-10 |
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Application publication date: 20110608 |