US20020157906A1 - Vibration damper for a hydraulic brake system of a vehicle - Google Patents
Vibration damper for a hydraulic brake system of a vehicle Download PDFInfo
- Publication number
- US20020157906A1 US20020157906A1 US09/958,300 US95830001A US2002157906A1 US 20020157906 A1 US20020157906 A1 US 20020157906A1 US 95830001 A US95830001 A US 95830001A US 2002157906 A1 US2002157906 A1 US 2002157906A1
- Authority
- US
- United States
- Prior art keywords
- diaphragm
- carrier device
- vibration damper
- hydraulic fluid
- hydraulic
- 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
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Classifications
-
- 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
- B60T8/4068—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 the additional fluid circuit comprising means for attenuating pressure pulsations
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- 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
- B60T8/42—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 having expanding chambers for controlling pressure, i.e. closed systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/0006—Noise or vibration control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/02—Fluid-pressure mechanisms
- F16D2125/06—Pistons
Definitions
- the invention relates to a vibration damper for a hydraulic vehicle brake system with a diaphragm facing the hydraulic fluid that transmits the brake force and being connected to a carrier device by its edge in such manner that it is able to move toward the carrier device or away from it at least slightly in its center area.
- a vibration damper for a hydraulic vehicle brake system with a diaphragm facing the hydraulic fluid that transmits the brake force and being connected to a carrier device by its edge in such manner that it is able to move toward the carrier device or away from it at least slightly in its center area.
- vibration damper based on the generic description of claim 1 in a hydraulic brake system in order to reduce undesirable vibration in the hydraulic system and/or prevent that small vibration generated by any kind of disruptive force increases to intolerable intensity.
- a vibration damper can also be described as “pressure smoothening device.”
- spring-loaded vibration dampers can be used, which however are very extensive.
- a vibration damper as the one described in the abovementioned publication, which is equipped with a housing or carrier device with a concave recess that is sealed by a disk-shaped diaphragm comprising a spring steel sheet, is considerably simpler.
- the task of the present invention consists of presenting a remedial measure for the described problem.
- the solution of this task is characterized by the fact that the hollow chamber between the diaphragm and the carrier device that is required for the diaphragm movement is largely evaluated.
- Beneficial embodiments and further developments are the contents of the sub-claims.
- the mentioned hollow chamber between the diaphragm and the carrier device contains basically a vacuum so that in the case of a destruction of the diaphragm, which cannot be excluded one hundred percent although it is undesirable, no air can reach the hydraulic system.
- the vibration damper is no longer functional once the diaphragm has been destroyed, however at least the brake system is not impaired in its function.
- the vibrations, which can no longer be damped with a destroyed diaphragm only lead to a loss of comfort because these vibrations can be transmitted onto the chassis of the vehicle, e.g. a passenger car, in the most unfavorable case.
- a vibration damper in the hydraulic system of a vehicle brake system can become particularly necessary when the brake pressure in the hydraulic fluid is not too high, i.e. in the range of 5 bar to 20 bar.
- the diaphragm should be relatively thin and flexible.
- the vacuum existing on the side of the diaphragm facing away from the hydraulic fluid is also beneficial in light of this aspect since this way the vibration damper can take effect already starting at an absolute pressure of 1 bar.
- the relevant dimensions of the vibration damper can have such a design and the stiffness of the diaphragm be selected in such a way that the diaphragm rests completely against the surface of the carrier device facing toward it at a pressure in the range of 25 bar and more of the hydraulic fluid.
- the surface affecting the desired effect i.e. vibration damping
- the desired effect i.e. vibration damping
- the surface affecting the desired effect can therefore be enlarged e.g. with specified dimensions of the carrier device and thus the damping effect can be increased if the diaphragm has a waved or undulated shape in some areas.
- the surface of the carrier surface facing toward this area of the diaphragm can have a similar cross-sectional, i.e. basically synchronous, design.
- the carrier device can be a brake piston provided in the caliper of a vehicle brake, against whose side that faces away from the hydraulic fluid a brake lining carrier rests.
- a vibration damper for a hydraulic vehicle brake system is shown as a preferred embodiment of the invention in the only attached figure in a cross-sectional view and is described briefly in the following.
- the so-called carrier device which here at the same time is the brake piston provided in the caliper of the otherwise conventional vehicle brake system, of the vibration damper is marked with the designation 1 .
- a brake lining carrier (not shown in the figure).
- the front side 1 c (here the upper one) opposite the front side 1 a (here the lower one) is fed in the conventional manner with the hydraulic fluid that transmits the brake force.
- a circular indentation 2 is provided in the carrier device 1 , which has at least a slightly concave design, i.e. the indentation 2 is lower in the area of the central axis 3 of the carrier device and/or further offset against the front side 1 c of the carrier device 1 than at its edge. Furthermore—as the figure shows—the surface of the carrier device 1 within this indentation 2 partially has a wave shape design. Since this—as already mentioned—involves a circular indentation 2 in the cylindrical carrier device 1 , the wave peaks 4 a and/or the wave valleys 4 b of this wave-shaped surface, of course, also define circles. (In the case of a carrier device 1 that is produced in an extrusion process, this outline can be incorporated in during the manufacturing process).
- a largely circular diaphragm 5 is provided, which is fastened by its edge to the carrier device 1 and/or to its front site 1 c in the area of the indentation 2 in such a manner that this diaphragm 5 can move at least slightly toward the carrier device 1 , i.e. toward its front side 1 c or away from it, with its area in the central axis 3 .
- the diaphragm 5 is preferably fastened to the carrier device 1 through a weided scam 6 that has been generated through an electron beam welding process.
- the diaphragm 5 If no or basically no force is applied to the surface of the diaphragm 5 that is freely accessible from the outside, i.e. the surface facing toward the hydraulic medium of the brake system, then the diaphragm 5 is located at a distance from the surface of the carrier device 1 away from its fastening area and/or fastening section, i.e. away from the welding seam 6 . Between the diaphragm 5 and the carrier device 1 a hollow chamber is located, which is largely evacuated, i.e. in this hollow chamber 7 basically a vacuum exists.
- the area or section of the diaphragm 5 located in the wave shaped area of the indentation 2 also has a wave shape and is adjusted to wave shape of the surface of the carrier device 1 in the area of the indentation 2 .
- the wave shape which is quite visible in the cross-section of the diaphragm 5 , runs parallel to that of the surface of the carrier device, i.e. these two components practically have a synchronous wave share toward each other in such a manner that the wave valleys 4 b as well as the wave peaks 4 a each rest on top of each other.
- the distance (measured in the vertical direction in the figure shown) between the diaphragm 5 that is not fed hydraulic pressure and the surface of the carrier device 1 facing toward it in the edge area of the diaphragm 5 away from its fastening section (i.e. away from the welding seam 6 ) is smaller than in the central area of the diaphragm 5 , i.e. in the environment of the central axis 3 .
- Vibrations in the hydraulic system of the vehicle brake system that affect the front side 1 c of the carrier device 1 and thus also the diaphragm 5 can only be damped successfully with the vibration damper that is formed by this diaphragm 5 and the evacuated hollow chamber 7 behind it as long as this diaphragm 5 is pressed continuously against the surface of the carrier device from the hydraulic pressure. If, however, the hydraulic pressure is lower than this value, then the pressure vibrations in the hydraulic system will try to get the diaphragm 5 to vibrate at least in its central area, i.e. from a time point of view the diaphragm 5 will move alternately toward the carrier device surface and away from it. Upon suitable coordination of the relevant dimensions this can result in an effective vibration damper.
- the thickness of the diaphragm 5 that consists for example of nickel steel or NiBe can be in the range of 0.4 mm to 0.7 mm.
- such a vibration damper will only be activated in the actually required range of the (variable) pressure that exists in the hydraulic system, e.g. in the range of about 2 bar to about 20 bar.
- the diaphragm 5 rests completely on the carrier device 1 so that no influence on the braking behavior of the overall system must be feared. If the diaphragm 5 is destroyed, beneficially no air will be able to reach the hydraulic system, however it should be pointed out that the design can certainly include a plurality of details that deviate from the example shown in the embodiment without deviating from the contents of the patent claims.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Braking Arrangements (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a vibration damper for a hydraulic vehicle brake system with a diaphragm facing the hydraulic fluid that transmits the braking force and being fastened to a carrier device by its edge in such manner that it is able to move toward the carrier device or away from it at least slightly in its center area. Based on the invention, the hollow chamber between the diaphragm and the carrier device, which is required for the movement of the diaphragm, has been largely evacuated. The stiffness of the diaphragm is preferably selected in such a manner that the diaphragm rests completely against the surface of the carrier device facing toward it at a pressure of the hydraulic fluid in the range of 25 bar and more. In some areas, the diaphragm can have a wave-shape cross-sectional design as can the surface of the carrier device facing toward the diaphragm. In a preferred version, the carrier device is a brake piston that is incorporated in the caliper of a vehicle brake, against whose side that faces away from the hydraulic fluid a brake lining carrier rests.
Description
- The invention relates to a vibration damper for a hydraulic vehicle brake system with a diaphragm facing the hydraulic fluid that transmits the brake force and being connected to a carrier device by its edge in such manner that it is able to move toward the carrier device or away from it at least slightly in its center area. We would lose to refer to DE 195 44 223 A1 for the known state of the art.
- It may be required to provide a vibration damper based on the generic description of claim 1 in a hydraulic brake system in order to reduce undesirable vibration in the hydraulic system and/or prevent that small vibration generated by any kind of disruptive force increases to intolerable intensity. Such a vibration damper can also be described as “pressure smoothening device.” For this purpose, for example, spring-loaded vibration dampers can be used, which however are very extensive. A vibration damper as the one described in the abovementioned publication, which is equipped with a housing or carrier device with a concave recess that is sealed by a disk-shaped diaphragm comprising a spring steel sheet, is considerably simpler. These diaphragms, which are fed on the outside with the hydraulic fluid of the brake system, is welded together with the carrier device on the edge, and the hollow chamber between the diaphragm and the abovementioned recess is filled with air. Pressure vibration generated in the hydraulic system causes the diaphragm to move into the hollow chamber with its central area and then move away again from the carrier device, which can have a vibration damping effect if appropriately designed.
- It has been proven that in particular when the diaphragm is relatively thin and therefore weak it can rupture in the most unfavorable case so that the air from the hollow chamber between the diaphragm and the carrier device can reach the hydraulic system. Air pockets in the hydraulic system of a hydraulic vehicle brake system however are known to be extremely undesirable because this can cause a soft braking actuation, caused by the compression of the trapped air.
- The task of the present invention consists of presenting a remedial measure for the described problem. The solution of this task is characterized by the fact that the hollow chamber between the diaphragm and the carrier device that is required for the diaphragm movement is largely evaluated. Beneficial embodiments and further developments are the contents of the sub-claims.
- In accordance with the invention, the mentioned hollow chamber between the diaphragm and the carrier device contains basically a vacuum so that in the case of a destruction of the diaphragm, which cannot be excluded one hundred percent although it is undesirable, no air can reach the hydraulic system. Of course, the vibration damper is no longer functional once the diaphragm has been destroyed, however at least the brake system is not impaired in its function. The vibrations, which can no longer be damped with a destroyed diaphragm, only lead to a loss of comfort because these vibrations can be transmitted onto the chassis of the vehicle, e.g. a passenger car, in the most unfavorable case.
- It has been proven that a vibration damper in the hydraulic system of a vehicle brake system can become particularly necessary when the brake pressure in the hydraulic fluid is not too high, i.e. in the range of 5 bar to 20 bar. In order to achieve effective damping, the diaphragm should be relatively thin and flexible. The vacuum existing on the side of the diaphragm facing away from the hydraulic fluid is also beneficial in light of this aspect since this way the vibration damper can take effect already starting at an absolute pressure of 1 bar. In order to prevent the diaphragm from being destroyed at higher brake pressure—it can increase up to about 200 bar—the relevant dimensions of the vibration damper can have such a design and the stiffness of the diaphragm be selected in such a way that the diaphragm rests completely against the surface of the carrier device facing toward it at a pressure in the range of 25 bar and more of the hydraulic fluid.
- The surface affecting the desired effect, i.e. vibration damping, can therefore be enlarged e.g. with specified dimensions of the carrier device and thus the damping effect can be increased if the diaphragm has a waved or undulated shape in some areas. In order to prevent a destruction of the diaphragm as well, caused by exceptionally high hydraulic pressure, even with such a diaphragm design, the surface of the carrier surface facing toward this area of the diaphragm can have a similar cross-sectional, i.e. basically synchronous, design. For firmness reasons it may be recommended with such a diaphragm design to select the geometric dimensions in such a manner that the distance between the diaphragm without hydraulic pressure and the surface of the carrier device facing toward the diaphragm in the edge area of the diaphragm away from the fastening section (with which it is fastened to the carrier device) it is smaller than in the central diaphragm area.
- In accordance with a beneficial combination of functions, the carrier device can be a brake piston provided in the caliper of a vehicle brake, against whose side that faces away from the hydraulic fluid a brake lining carrier rests. Such a vibration damper for a hydraulic vehicle brake system is shown as a preferred embodiment of the invention in the only attached figure in a cross-sectional view and is described briefly in the following.
- The so-called carrier device, which here at the same time is the brake piston provided in the caliper of the otherwise conventional vehicle brake system, of the vibration damper is marked with the designation1. Against the front side 1 a (the lower one shown in the figure) of this cylindrical brake piston 1 or carrier device 1, which runs in a cylinder that is not shown with its cylinder shell area 1 b and can be moved, rests as usual a brake lining carrier (not shown in the figure). The front side 1 c (here the upper one) opposite the front side 1 a (here the lower one) is fed in the conventional manner with the hydraulic fluid that transmits the brake force.
- On the front side1 c a
circular indentation 2 is provided in the carrier device 1, which has at least a slightly concave design, i.e. theindentation 2 is lower in the area of thecentral axis 3 of the carrier device and/or further offset against the front side 1 c of the carrier device 1 than at its edge. Furthermore—as the figure shows—the surface of the carrier device 1 within thisindentation 2 partially has a wave shape design. Since this—as already mentioned—involves acircular indentation 2 in the cylindrical carrier device 1, thewave peaks 4 a and/or thewave valleys 4 b of this wave-shaped surface, of course, also define circles. (In the case of a carrier device 1 that is produced in an extrusion process, this outline can be incorporated in during the manufacturing process). - Additionally a largely
circular diaphragm 5 is provided, which is fastened by its edge to the carrier device 1 and/or to its front site 1 c in the area of theindentation 2 in such a manner that thisdiaphragm 5 can move at least slightly toward the carrier device 1, i.e. toward its front side 1 c or away from it, with its area in thecentral axis 3. At its edge thediaphragm 5 is preferably fastened to the carrier device 1 through aweided scam 6 that has been generated through an electron beam welding process. - If no or basically no force is applied to the surface of the
diaphragm 5 that is freely accessible from the outside, i.e. the surface facing toward the hydraulic medium of the brake system, then thediaphragm 5 is located at a distance from the surface of the carrier device 1 away from its fastening area and/or fastening section, i.e. away from thewelding seam 6. Between thediaphragm 5 and the carrier device 1 a hollow chamber is located, which is largely evacuated, i.e. in thishollow chamber 7 basically a vacuum exists. - The area or section of the
diaphragm 5 located in the wave shaped area of theindentation 2 also has a wave shape and is adjusted to wave shape of the surface of the carrier device 1 in the area of theindentation 2. The wave shape, which is quite visible in the cross-section of thediaphragm 5, runs parallel to that of the surface of the carrier device, i.e. these two components practically have a synchronous wave share toward each other in such a manner that thewave valleys 4 b as well as the wave peaks 4 a each rest on top of each other. - As far as the dimension of the evacuated
hollow chamber 7 is concerned, which is largely determined by the concavity of the surface of the carrier device 1 in the area of theindentation 2, the distance (measured in the vertical direction in the figure shown) between thediaphragm 5 that is not fed hydraulic pressure and the surface of the carrier device 1 facing toward it in the edge area of thediaphragm 5 away from its fastening section (i.e. away from the welding seam 6) is smaller than in the central area of thediaphragm 5, i.e. in the environment of thecentral axis 3. - Vibrations in the hydraulic system of the vehicle brake system that affect the front side1 c of the carrier device 1 and thus also the
diaphragm 5 can only be damped successfully with the vibration damper that is formed by thisdiaphragm 5 and the evacuatedhollow chamber 7 behind it as long as thisdiaphragm 5 is pressed continuously against the surface of the carrier device from the hydraulic pressure. If, however, the hydraulic pressure is lower than this value, then the pressure vibrations in the hydraulic system will try to get thediaphragm 5 to vibrate at least in its central area, i.e. from a time point of view thediaphragm 5 will move alternately toward the carrier device surface and away from it. Upon suitable coordination of the relevant dimensions this can result in an effective vibration damper. E.g. the thickness of thediaphragm 5 that consists for example of nickel steel or NiBe can be in the range of 0.4 mm to 0.7 mm. - In a beneficial version, such a vibration damper will only be activated in the actually required range of the (variable) pressure that exists in the hydraulic system, e.g. in the range of about 2 bar to about 20 bar. In the case of higher hydraulic pressure, the
diaphragm 5 rests completely on the carrier device 1 so that no influence on the braking behavior of the overall system must be feared. If thediaphragm 5 is destroyed, beneficially no air will be able to reach the hydraulic system, however it should be pointed out that the design can certainly include a plurality of details that deviate from the example shown in the embodiment without deviating from the contents of the patent claims.
Claims (5)
1. Vibration damper for a hydraulic vehicle brake system with a diaphragm (5) facing the hydraulic fluid that transmits the braking force and being fastened to a carrier device (1) by its edge in such manner that it is able to move toward the carrier device or away from it at least slightly in its center area,
wherein the hollow chamber (7) between the diaphragm (5) and the carrier device (1) that is required for the movement of the diaphragm is largely evacuated.
2. Vibration damper in accordance with claim 1 ,
wherein the stiffness of the diaphragms (5) is selected in such a manner that the diaphragm rests completely against the surface of the carrier device (1) facing toward it at a pressure of the hydraulic fluid in the range or 25 bar and more.
3. Vibration damper in accordance with claim 1 or 2,
wherein in some areas, the diaphragm (5) has a wave shape in its cross-section as does, in this area, the surface of the carrier device (1) that faces toward the diaphragm.
4. Vibration damper in accordance with one of the previous claims,
wherein the distance between the diaphragm (5) to which no hydraulic pressure is applied and the surface of the carrier device (5) facing toward it in the edge area of the diaphragm away from the fastening section is smaller than in the central diaphragm area.
5. Vibration damper in accordance with one of the previous claims,
wherein the carrier device (1) is the brake piston that is incorporated in the caliper of a vehicle brake, against whose side (1 a) facing away from the hydraulic fluid a brake lining carrier rests.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10005588 | 2000-02-09 | ||
DE10005588.5 | 2000-02-09 | ||
DE10005588A DE10005588A1 (en) | 2000-02-09 | 2000-02-09 | Vibration damper for a hydraulic vehicle brake system |
Publications (2)
Publication Number | Publication Date |
---|---|
US6471016B1 US6471016B1 (en) | 2002-10-29 |
US20020157906A1 true US20020157906A1 (en) | 2002-10-31 |
Family
ID=7630265
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/958,300 Expired - Lifetime US6471016B1 (en) | 2000-02-09 | 2001-01-13 | Vibration damper for a hydraulic brake system of a vehicle |
Country Status (5)
Country | Link |
---|---|
US (1) | US6471016B1 (en) |
EP (1) | EP1169580B1 (en) |
JP (1) | JP2003522664A (en) |
DE (2) | DE10005588A1 (en) |
WO (1) | WO2001059319A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110017332A1 (en) * | 2008-02-18 | 2011-01-27 | Continental Teves Ag & Co. Ohg | Pulsation damping capsule |
CN104632948A (en) * | 2013-11-14 | 2015-05-20 | 罗伯特·博世有限公司 | Block-shaped housing of a hydraulic unit of a vehicle brake system |
US20160195084A1 (en) * | 2013-09-26 | 2016-07-07 | Continental Automotive Gmbh | Damper For A High-Pressure Pump |
US10364890B2 (en) * | 2015-01-16 | 2019-07-30 | Continental Teves Ag & Co. Ohg | Double cup-shaped piston for a disc brake |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10327408B4 (en) * | 2002-10-19 | 2017-10-26 | Robert Bosch Gmbh | Device for damping pressure pulsations in a fuel system of an internal combustion engine |
US7188529B2 (en) * | 2005-01-25 | 2007-03-13 | Yokogawa Electric Corporation | Differential pressure measuring apparatus |
US20080116742A1 (en) * | 2006-11-20 | 2008-05-22 | Lipski Mark C | Brake modulation device and method |
JP5171190B2 (en) * | 2007-09-28 | 2013-03-27 | 京セラ株式会社 | Liquid discharge head |
DE102009046578A1 (en) * | 2009-11-10 | 2011-05-12 | BSH Bosch und Siemens Hausgeräte GmbH | Pulsation damper for hot beverage preparation device, particularly coffee machine, has damper base with base plate with upper surface with inlet and outlet, connections, support and elastic membrane |
DE102019210649A1 (en) * | 2019-07-18 | 2021-01-21 | Robert Bosch Gmbh | Brake system damping device with a passage |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS63100262A (en) * | 1986-10-16 | 1988-05-02 | Aisan Ind Co Ltd | Pulsation damping device for fuel feed system |
JPH01188793A (en) * | 1988-01-19 | 1989-07-28 | Power Reactor & Nuclear Fuel Dev Corp | Device for protecting bellows type pipe joint |
DE3821726A1 (en) * | 1988-06-28 | 1990-01-04 | Klaus Kronwald Chemo Consult | Pulsation damper |
US5205309A (en) | 1990-05-07 | 1993-04-27 | Cardenas Richard A | Adjustable pressure control device for hydraulic brake systems |
JPH0587168A (en) * | 1991-09-24 | 1993-04-06 | Aisin Seiki Co Ltd | Disc brake |
US5540486A (en) * | 1993-12-07 | 1996-07-30 | Kelsey-Hayes Company | Anti-lock brake system noise attenuator |
DE4418701A1 (en) | 1994-05-28 | 1995-11-30 | Bayerische Motoren Werke Ag | Vehicle disc brake piston |
US5820227A (en) * | 1995-08-24 | 1998-10-13 | Spero; Theodore P. | Brake equalizer with housing enclosing piston and shock absorber |
DE19539780A1 (en) * | 1995-10-26 | 1997-04-30 | Bosch Gmbh Robert | Damper to suppress brake fluid oscillations in motor vehicle's brake system |
DE19544223B4 (en) | 1995-11-28 | 2005-11-24 | Robert Bosch Gmbh | Vibration damper for damping fluid vibrations in a hydraulic, slip-controlled braking system of motor vehicles |
-
2000
- 2000-02-09 DE DE10005588A patent/DE10005588A1/en not_active Withdrawn
-
2001
- 2001-01-13 JP JP2001558628A patent/JP2003522664A/en active Pending
- 2001-01-13 WO PCT/EP2001/000371 patent/WO2001059319A1/en active IP Right Grant
- 2001-01-13 DE DE50109379T patent/DE50109379D1/en not_active Expired - Lifetime
- 2001-01-13 EP EP01903645A patent/EP1169580B1/en not_active Expired - Lifetime
- 2001-01-13 US US09/958,300 patent/US6471016B1/en not_active Expired - Lifetime
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110017332A1 (en) * | 2008-02-18 | 2011-01-27 | Continental Teves Ag & Co. Ohg | Pulsation damping capsule |
US8757212B2 (en) | 2008-02-18 | 2014-06-24 | Continental Teves Ag & Co. Ohg | Pulsation damping capsule |
US20160195084A1 (en) * | 2013-09-26 | 2016-07-07 | Continental Automotive Gmbh | Damper For A High-Pressure Pump |
US9828988B2 (en) * | 2013-09-26 | 2017-11-28 | Continental Automotive Gmbh | Damper for a high-pressure pump |
CN104632948A (en) * | 2013-11-14 | 2015-05-20 | 罗伯特·博世有限公司 | Block-shaped housing of a hydraulic unit of a vehicle brake system |
US10364890B2 (en) * | 2015-01-16 | 2019-07-30 | Continental Teves Ag & Co. Ohg | Double cup-shaped piston for a disc brake |
Also Published As
Publication number | Publication date |
---|---|
US6471016B1 (en) | 2002-10-29 |
EP1169580A1 (en) | 2002-01-09 |
DE50109379D1 (en) | 2006-05-18 |
JP2003522664A (en) | 2003-07-29 |
EP1169580B1 (en) | 2006-03-29 |
WO2001059319A1 (en) | 2001-08-16 |
DE10005588A1 (en) | 2002-03-28 |
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