CN104955693A - Master brake cylinder for a hydraulic motor vehicle brake system - Google Patents
Master brake cylinder for a hydraulic motor vehicle brake system Download PDFInfo
- Publication number
- CN104955693A CN104955693A CN201480006468.XA CN201480006468A CN104955693A CN 104955693 A CN104955693 A CN 104955693A CN 201480006468 A CN201480006468 A CN 201480006468A CN 104955693 A CN104955693 A CN 104955693A
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- junction device
- master brake
- brake cylinder
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- 238000000034 method Methods 0.000 claims description 17
- 238000004519 manufacturing process Methods 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 239000000463 material Substances 0.000 claims description 3
- 238000003825 pressing Methods 0.000 claims description 3
- 239000007769 metal material Substances 0.000 claims description 2
- 230000000977 initiatory effect Effects 0.000 abstract 1
- 238000007789 sealing Methods 0.000 abstract 1
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007717 exclusion Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000012958 reprocessing Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
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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
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/232—Recuperation valves
-
- 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
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/236—Piston sealing arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Transmission Of Braking Force In Braking Systems (AREA)
Abstract
The invention relates to a master brake cylinder (1), in particular a tandem master brake cylinder for a hydraulic motor vehicle brake system, which is impinged upon preferably by a pneumatic brake booster (2), comprising at least one piston (4,5) which is displaceable in a housing (3) and has in each case a plurality of follow-up connections (14,15), said follow-up connections allowing a hydraulic connection between the pressure chamber (6,7) and a pressureless follow-up chamber (16,17) at the start of a braking operation. According to the invention, at least some of the follow-up connections (14,15) are configured as axial grooves and are formed in an outer lateral surface of at least one piston (4), lead with one end to the piston edge (8) and with another end in each case to a control edge (18) in the lateral surface in a main plane E1, which is arranged in parallel and at a distance (S1) to the piston edge (8) and the overtravel thereof by the sealing collar (12) defines a closure path of the piston (4). In order to allow a smooth, quiet and yet sufficiently reliable braking initiation, it is proposed according to the invention that the piston (4) comprises further follow-up connections (14) which are configured as axial grooves and are formed in the outer lateral surface of the piston (4), lead with one end to the piston edge (8) and with another end in each case to a control edge (18) in the lateral surface of the piston (4) in at least one further plane (E2), which is arranged in parallel to the main plane (E1) and in an offset manner relative to the piston edge (8).
Description
Technical field
The present invention relates to a kind of fluid pressure type tandem brake master cylinder (THz) for hydraulic motor vehicle brake system according to claim 1 preamble, be especially configured to two circuit tandem brake master cylinder.Mostly be connected with Pneumatic brake booster in the upstream of this master brake cylinder (THz), described Pneumatic brake booster can realize braking force enlarging function.The unit that master cylinder and brake servo unit are formed is commonly called brake equipment and is the component part of motor vehicle braking systems.
Background technology
Tandem brake master cylinder is known.For the true(-)running of tandem brake master cylinder, need the hydraulic connecting not only being braked the initial position in state and ensureing between pressure chamber and pressure medium container in other words in neutral position but also when piston movement starts in other words when braking procedure starts in short time.In addition, be devoted to keep slack of pedal short as far as possible in known brake system, set up to realize fast speed braking force after time delay short as far as possible.
DE102009054695 discloses a kind of secondary piston of plunger tpe tandem brake master cylinder, described secondary piston has the ring of axial groove for this purpose in its outer peripheral face, and described axial groove starts from a unique public plane misplaced abreast with piston ridge backward towards the end of piston against piston operation direction and controls seamed edge in other words and lead to piston end surface.
Shortcoming
What be mainly regarded as the shortcoming in known systems is, the short slack of pedal of this system and precipitous pressure then raise and such as can cause serious traveling comfort loss due to hard uncomfortable pedal sense, or control the brake servo unit piston connected with THz of housing or the unexpected deceleration/braking of diaphragm owing to having and cause higher noise development.
Known, if the hydraulic pressure closing stroke in THz increases due to the slow down hydraulic column in the hydraulic effect opposing THz chamber of causing of the inner component of Pneumatic brake booster after being crossed by piston, when the air volume flowed into temporarily reaches static, described hydraulic effect can cause noise.Produce so-called impact noise.
Summary of the invention
Object:
Therefore the object of the present invention is to provide the motor vehicle braking systems of improvement, described motor vehicle braking systems realizes soft, slight but enough failure-free brakings inexpensively and introduces when avoiding aforesaid drawbacks of the prior art.
Technical scheme and advantage:
According to the present invention, described object is realized by the master brake cylinder with Feature Combination according to claim 1.Dependent claims and drawings illustrate other favourable form of implementation and expanded configuration.
Described object realizes like this: anti-backflow junction device is configured to the axial groove be arranged in the outer peripheral face of piston, wherein, anti-backflow junction device ends at the control seamed edge in the side face of piston respectively with an end, described control seamed edge be arranged so that on side face described control seamed edge be not be all in unique around line in other words in a plane, but be distributed in staggering in multiple plane, thus, when piston movement, the control seamed edge staggered in groups is crossed by seal ring with following one another, and this causes groove little by little to close lentamente.
At this, depending on the closing characteristics of expectation, control seamed edge interval to each other and can be specified to larger or less interval, to realize optimizing according to hydraulic consumers device and brake equipment dynamic in total closing stroke and pressure gradient.
Preferably axially groove is provided with the control seamed edge being in diverse location, is preferably arranged at least three planes misplaced toward each other.
In the present invention, groove not only can be provided with straight control seamed edge, and can be provided with the control seamed edge at rounded angle.
Interval preferably between the first plane and last plane (the 3rd, the fourth class, depending on form of implementation) can be in the scope between 0.5mm and 3mm.
In a particularly preferred form of implementation, the interval between the first plane and last plane is in the scope between 0.9mm and 1.5mm.
Particularly advantageously, there is the piston of groove by plastic material and with injecting method or drawing method manufacture.
The piston with groove also can with pressing method manufacture.
Especially can be realized by preceding feature:
-in master brake cylinder, mildly set up hydraulic pressure, especially close to (gradient reduced at the first hole plane period of contact cross-sectional plane is smooth) at the end of closing stroke,
-compensate the less desirable dynamic effect that may cause noise,
-manufacture inexpensively and weight saving, avoid cutting process, avoid chip thus completely and simplify scale removal process.
Accompanying drawing explanation
Combine by dependent claims the explanation carried out by means of accompanying drawing and obtain other details of the present invention, feature, advantage and application possibility.Corresponding parts and structural constituent arrange identical Reference numeral as far as possible.In accompanying drawing:
Fig. 1 illustrates the cross section view of a form of implementation according to master brake cylinder of the present invention.
Fig. 2 illustrates the lateral plan according to the first form of implementation of the present invention of piston 4.
Fig. 3 illustrates the lateral plan according to another form of implementation of the present invention of piston 4.
Fig. 4 illustrates and is configuring with the corresponding of each plane according to anti-backflow junction device 14 in the form of implementation of Fig. 2.
Fig. 5 illustrates and middlely to configure with the corresponding of each plane according to anti-backflow junction device 14 in the form of implementation of Fig. 3.
Fig. 6 illustrates the three-dimensional detailed view (a, b) of two different forms of implementation of piston 4.
Fig. 7 illustrates the comparison relevant to piston stroke of the accumulation cross-sectional plane of anti-backflow junction device 14 on piston according to the present invention with known piston.
Detailed description of the invention
Fig. 1
The cross section view of the first form of implementation according to master brake cylinder 1 of the present invention has been shown in Fig. 1.Master brake cylinder 1 is configured to plunger piston type tandem main cylinder.Because the mode of operation of this master brake cylinder is fully known, so only inquire into the attribute for particular importance of the present invention below.
Two pistons 4 (secondary piston) and 5 (primary piston) can be arranged on slidingly back and forth each other master brake cylinder 1 in housing 3.At this, piston 4 in housing 3 restriction pressure medium fill pressure chamber 6 and seal by means of seal ring 12 relative to described pressure chamber; Piston 5 limit also with pressure medium fill pressure chamber 7 and seal by means of seal ring 13 relative to described pressure chamber.Not only piston 4 but also piston 5 are substantially configured to can-like and point to towards limited pressure chamber 6 or 7 respectively with the piston ridge of its correspondence (piston end surface) 8 or 9.In pressure chamber 6,7, producible brake-pressure is transferred to unshowned car side brake by unshowned brake piping.
Seal ring 12,13 is positioned in the circular groove 10,11 in housing 3 respectively.
In housing 3, directly before circular groove 10,11, be provided with return passage 16 and 17 around piston 4,5 on direction of operating B, described return passage is configured with the circular groove of the sidewall cut sth. askew in the direction towards circular groove 10,11 respectively.Return passage 16,17 is continued to be connected by return flow line 21,22 with the unshowned chamber without pressure/uninflated pressure medium container and therefore also keeps without pressure.
Piston 4,5 has multiple anti-backflow junction device 14 or 15, although there is seal ring 14,15, therefore described anti-backflow junction device not by the hydraulic connecting also allowed in the initial position that operates between corresponding pressure chamber 6,7 and stress-free return passage 16,17, and supports brake system pressure balance and exhaust shown.
In braking procedure, two retracing springs 19 and 20 are compressed by the movement of piston 4 or 5 on direction of operating B, and for making after terminating at braking procedure two pistons 4,5 reset to it not by the initial position that operates.
Piston 5 is operated by the press rods (parts are in addition not shown) of Pneumatic brake booster 2.In braking procedure, brake servo unit 2 loads piston 5 with power and described piston is not moved towards the direction of piston 4 from it by the initial position that operates on direction of operating B.In the process, piston 4 first due to retracing spring 20 rigidity and then by pressure chamber 7 set up brake-pressure and to a great extent with piston 5 synchronously in the same direction together with move.In the process, anti-backflow junction device 14,15 is little by little by being crossed by seal ring 12,13 and opening with return passage 16,17 points, and can be prevented from from pressure chamber 6,7 exclusion to the flowing of the pressure medium return passage 16,17, thus, can brake-pressure be set up in pressure chamber 6,7.The shift motion of piston when anti-backflow junction device 14,15 and return passage 16,17 are opened by seal ring 12,13 points is commonly called closing stroke.
If such as too suddenly interrupted in emergency brake operations in the process with the hydraulic connecting of return passage 16,17, then this movable parts quick deceleration undesirably of Pneumatic brake booster 2 that usually can cause piston 5 and be connected with piston 5 by piston rod, and cause the air stream of brake servo unit 2 inside disturbed.High noise development can be produced thus, i.e. so-called impact noise.In addition, piston slows down suddenly and causes hard and uncomfortable pedal sense.
The improvement according to the present invention of above-mentioned characteristic is explained especially by figure below.
Fig. 2
Multiple anti-backflow junction device 14 is arranged on piston 4 as shown in the figure.Anti-backflow junction device 14 is configured to axial groove, and described axial groove is formed in the outer peripheral face of piston 4, leads to piston ridge 8 and ends at the control seamed edge 18 in side face respectively with another end respectively to pass into end 23.At this, control seamed edge 18 and arrange at a distance of different interval S1, S2, S3 in multiple groups and piston ridge 8, thus, each group is in the plane E1 parallel with piston ridge 8, E2 or E3.The closing stroke of piston 8 is determined at this with the principal plane E1 of piston ridge 8 lie farthest away.
Piston 4 is shown as and is in it not by the initial position that operates relative to seal ring 12.At this, all control before seamed edge 18 is in seal ring 12 on direction of operating B, and hydraulic connecting all between anti-backflow junction device 14 authorized pressure chamber 6 and stress-free return passage 16 and pressure medium circulate.
Now, if piston 4 moves on direction of operating B when introducing brake operating, then first seal ring 12 is crossed a group of being arranged in plane E3 and is controlled seamed edge 18
3.Thus, remaining through flow cross section, hydraulic connecting namely between pressure chamber 6 and return passage 16 still by the accumulation cross-sectional plane of whole anti-backflow junction device 14 decrease the cross-sectional plane of the anti-backflow junction device 14 separated with return passage 16.When the enough rapid movement of piston 4, in pressure chamber 6, start pressure soft slowly raise.Along with the further moving displacement stroke in other words of piston 4, one group in plane E2 controls seamed edge 18
2and the then control seamed edge 18 of principal plane E1
1in succession crossed.When principal plane E1 is crossed, all still remaining anti-backflow junction device 14 separates with return passage 16, and pressure chamber 6 completely cuts off with bar pressure, and closing stroke is reached, and brake-pressure is set up to be similar to now and carried out like that in traditional braking master cylinder 1.
Illustrate in detail the anti-backflow junction device 14 of shown form of implementation below in the diagram in a tabular form or control the accurate radial distribution of seamed edge 18 and configure with each plane E1, the corresponding of E2, E3.
In shown form of implementation, piston 4 has 30 anti-backflow junction device 14 altogether, but also allows different quantity in the present invention.
In the present invention, also allow two pistons 4,5 to have the anti-backflow junction device 14,15 being configured to axial groove according to above-mentioned principle.
Fig. 3
Different from the piston 4 according to Fig. 2, the control seamed edge 18 of the anti-backflow junction device 14 in shown form of implementation is divided into 4 groups instead of 3 groups, and corresponding configuration is to four plane E1, E2, E3, E4.Thus, compared with above-mentioned form of implementation, the thinner classification that can realize through flow cross section reduces in other words gradually.Also allow to be arranged in the present invention in the plane of 5 or more.
Fig. 4
What Fig. 4 showed each anti-backflow junction device 14 in form of implementation shown in Fig. 2 and plane E1 ~ E3 in the table is correspondingly configured to and distribution on the periphery of piston 4.Generally speaking, piston has 30 anti-backflow junction device 14, and described anti-backflow junction device is evenly distributed on the periphery of piston 4 with the angle intervals of 12 °.
Can see, principal plane E1 and the second plane E2 is corresponding is respectively configured with 5 anti-backflow junction device 14 be evenly distributed in the angle intervals of 72 ° on the periphery of piston, and the control seamed edge of described anti-backflow junction device is in corresponding plane.The anti-backflow junction device 14 of plane E2 is between the anti-backflow junction device 14 that this is accurately in principal plane E1 diametrically respectively.Remaining 20 anti-backflow junction device 14 correspondence configures to plane E3 and is arranged on adjacent to each other in couples on remaining periphery.
This set has following effect: when introducing braking and piston 4 crosses closing stroke, when braking introducing and starting, through flow cross section reduces about 67% first fast, and remaining through flow cross section slowly reduces with the level of 2 formed objects subsequently, until completely closed on principal plane 1.Especially " hard " pedal sense is significantly offset when snap catch thus.
Fig. 5
Illustrate in Fig. 5 and configured according to each anti-backflow junction device 14 distribution on piston 4 in the form of implementation of Fig. 3 and correspondence.The closed of through flow cross section carries out in principle with according to the form of implementation of Fig. 4 similarly, but more uniformly distribute in whole closing stroke by adding another plane E4: be first that two-stage type reduces the through flow cross section on plane E4 and E3 lenitively relatively, the cross-sectional plane respectively with every grade about 37% disconnects; Same two-stage type closes subsequently, and the cross-sectional plane respectively with about 13% disconnects.Thus, the change curve of pressure gradient than in above-mentioned layout evenly.
Combination shown in Figure 4 and 5 and layout are absolutely not interpreted as exclusiveness.By changing anti-backflow junction device 14 and plane E1, E2, E3 in the present invention ... quantity, interval and size, the almost arbitrary change curve expected especially pressure gradient structurally being determined for the braking introducing stage and also determine pedal sense thus.
Fig. 6
Fig. 6 shows the different form of implementation of two of piston 4 with view a and b.Have substantially straight control seamed edge 18 according to the control seamed edge 18 in the form of implementation of view a, described control seamed edge is arranged abreast relative to piston ridge 8.
And be configured to be rounded according to the control seamed edge 18 in the form of implementation of view b, thus, not whole control seamed edge but the tangent line of described control seamed edge is in the plane parallel with piston ridge 8.
The piston of such structure can preferably abnormal cost be cheap and effectively manufacture with deformation method or manufacturing process, does not need thus or only needs little reprocessing, and the cutting working method of the costliness avoided trouble.Preferred piston 4 can be manufactured by plastic material with injecting method or drawing method, but also can be manufactured by metallic material with pressing method.
Fig. 7
On piston stroke in other words moving displacement (X-axis), by comparison show the reduction (Y-axis) of through flow cross section in the figure 7.Solid line representative have according to the piston 4 of the layout of Fig. 4 according to form of implementation of the present invention, represented by dotted arrows all controls known traditional piston that seamed edge 18 is in single plane.The change curve of solid line is obviously seen 3 levels, and described level is the appearance when crossing plane E3 (at 0.6mm place), E2 (at 0.8mm place) and E1 (closed at 1.2mm place) respectively.
In addition the important advantage according to piston of the present invention is seen, by moderately reducing cross-sectional plane when piston stroke starts, must close close to through flow cross section only still little at the end of closing displacement, thus, pressure gradient only improves indistinctively relative to the situation of known piston, thus, avoid piston at the end of closing displacement and slow down suddenly, therefore the danger of impact noise significantly reduces.In addition, the rising of counter-force brake pedal experienced is evenly and more comfortable for chaufeur.
List of numerals
1 master brake cylinder
2 brake servo units
3 housings
4 pistons
5 pistons
6 pressure chambers
7 pressure chambers
8 piston ridge
9 piston ridge
10 circular grooves
11 circular grooves
12 seal rings
13 seal rings
14 anti-backflow junction device
15 anti-backflow junction device
16 return passages
17 return passages
18 control seamed edge
19 retracing springs
20 retracing springs
21 return flow lines
22 return flow lines
23 pass into end
B direction of operating
E1 principal plane
E2 plane
E3 plane
E4 plane
S1 piston ridge is to the interval of plane E1
S2 piston ridge is to the interval of plane E2
S3 piston ridge is to the interval of plane E3
S4 piston ridge is to the interval of plane E4
Claims (13)
1. the master brake cylinder for hydraulic motor vehicle brake system (1), especially tandem brake master cylinder, described master brake cylinder is preferably loaded by Pneumatic brake booster (2), described master brake cylinder has at least one can at the piston (4 of movement in housing (3), 5), described piston limits pressure chamber (6 in described housing (3), 7), and have towards described pressure chamber (6, 7) piston ridge (8 pointed to, 9) and by means of the circular groove (10 being arranged on described housing (3), 11) seal ring (12 in, 13) relative to described pressure chamber (6, 7) seal, at described piston (4, 5) multiple anti-backflow junction device (14 is respectively arranged with in, 15), described anti-backflow junction device allows the described pressure chamber (6 when braking procedure starts, 7) with stress-free return passage (16, 17) hydraulic connecting between, wherein, at least some anti-backflow junction device (14) is configured to axial groove, be formed in the outer peripheral face of at least one piston (4), lead to described piston ridge (8) with an end and in principal plane (E1), end at the control seamed edge (18) in described side face with another end, described principal plane is parallel to described piston ridge (8) with interval (S1) and arranges, and described principal plane is crossed by described seal ring (12) the closing stroke determining described piston (4), it is characterized in that: described piston (4) has other anti-backflow junction device (14), described other anti-backflow junction device is configured to axial groove, be formed in the outer peripheral face of described piston (4), lead to described piston ridge (8) with an end and at least one other plane (E2), end at the control seamed edge (18) in the side face of described piston (4) with another end, described other plane and described principal plane (E1) are arranged to misplace towards the direction of described piston ridge (8) relative to described principal plane (E1) abreast.
2. master brake cylinder according to claim 1, it is characterized in that: described control seamed edge (18) is arranged to be distributed at least three plane (E1, E2, E3) on, wherein, described plane (E2, E3) direction be arranged to abreast towards described piston ridge (8) with described principal plane (E1) is staggered, thus, described plane is crossed by described seal ring (12) prior to described principal plane (E1) by during operation at described piston (4).
3. master brake cylinder according to claim 1 and 2, is characterized in that: at least three anti-backflow junction device (14) control seamed edge (18) accordingly with it and end in described principal plane (E1).
4. master brake cylinder according to claim 1 and 2, is characterized in that: control seamed edge (18) with anti-backflow junction device (14) as much ended in described principal plane (E1) or the anti-backflow junction device (14) fewer than it accordingly with it and end in described second plane (E2).
5. master brake cylinder according to claim 1 and 2, is characterized in that: each plane (E1, E2, E3, E4) has the anti-backflow junction device (15) of equal number.
6. master brake cylinder according to claim 1 and 2, it is characterized in that: the cross-sectional configuration ending at each single anti-backflow junction device (14) in described principal plane (E1) becomes identical or larger than it with the cross-sectional plane size ending at the single anti-backflow junction device (14) in all other plane (E2, E3).
7. master brake cylinder according to claim 1 and 2 (1), it is characterized in that: the summation ending at the cross-sectional plane of the whole anti-backflow junction device (14) in described principal plane (E1) is identical or larger than it with the summation size of the cross-sectional plane ending at the whole anti-backflow junction device (14) in each single other plane (E2, E3).
8. master brake cylinder according to claim 1 and 2 (1), is characterized in that: the interval between described primary principal plane (E1) and last plane is in the scope between 0.5mm and 3mm.
9. master brake cylinder according to claim 1, is characterized in that: described control seamed edge (18) is configured to be parallel to described piston ridge (8).
10. master brake cylinder according to claim 1 and 2, is characterized in that: described control seamed edge (18) is configured to be rounded and one of at least tangent with described plane (E1, E2, E3).
11. master brake cylinders according to claim 1, is characterized in that: described anti-backflow junction device (14,15) is configured to axial groove on two pistons (4,5).
12. master brake cylinders according to claim 1,2 or 11, is characterized in that: described piston (4) is by plastic material and with injecting method or drawing method manufacture.
13. master brake cylinders according to claim 1,2 or 11, is characterized in that: described piston (4) is by metallic material and with pressing method manufacture.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013201560.7 | 2013-01-30 | ||
| DE102013201560 | 2013-01-30 | ||
| PCT/EP2014/051854 WO2014118301A1 (en) | 2013-01-30 | 2014-01-30 | Master brake cylinder for a hydraulic motor vehicle brake system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104955693A true CN104955693A (en) | 2015-09-30 |
Family
ID=50064567
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480006468.XA Pending CN104955693A (en) | 2013-01-30 | 2014-01-30 | Master brake cylinder for a hydraulic motor vehicle brake system |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN104955693A (en) |
| DE (1) | DE102014201699A1 (en) |
| WO (1) | WO2014118301A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10272892B2 (en) | 2015-06-30 | 2019-04-30 | Continental Teves Ag & Co. Ohg | Hydraulic unit for producing brake pressure for a motor-vehicle brake system |
| JP2020055398A (en) * | 2018-10-01 | 2020-04-09 | 株式会社アドヴィックス | Master cylinder |
| DE102020102540A1 (en) | 2020-01-31 | 2021-08-05 | Schwäbische Hüttenwerke Automotive GmbH | Fluid supply system with control valve for supplying one or more fluid consumers |
| CN113446336B (en) * | 2021-06-30 | 2022-12-27 | 采埃孚商用车系统(青岛)有限公司 | Double-piston spring brake air chamber |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1005013A (en) * | 1949-11-23 | 1952-04-07 | Pneumatic vibrator without neutral point with spring torsion bar, or compressed fluid which can be specially adapted to vibrating tables or to various machines | |
| US20050103010A1 (en) * | 2003-10-08 | 2005-05-19 | Atsushi Yasuda | Master cylinder |
| US20050172626A1 (en) * | 2001-07-13 | 2005-08-11 | Pierre Lebret | Penetration master cylinder with reduced backlash and application thereof |
| DE102009054695A1 (en) * | 2009-12-15 | 2011-06-16 | Continental Teves Ag & Co. Ohg | Master cylinder for a regulated braking system |
| DE102011075359A1 (en) * | 2011-05-05 | 2012-11-08 | Continental Teves Ag & Co. Ohg | Master cylinder, in particular for a regulated braking system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2969086B1 (en) * | 2010-12-21 | 2016-04-29 | Bosch Gmbh Robert | TANDEM MASTER CYLINDER PRIMER PISTON AND MASTER TANDEM MASTER CYLINDER EQUIPPED WITH SUCH A PRIMARY PISTON |
-
2014
- 2014-01-30 DE DE102014201699.1A patent/DE102014201699A1/en active Pending
- 2014-01-30 WO PCT/EP2014/051854 patent/WO2014118301A1/en active Application Filing
- 2014-01-30 CN CN201480006468.XA patent/CN104955693A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1005013A (en) * | 1949-11-23 | 1952-04-07 | Pneumatic vibrator without neutral point with spring torsion bar, or compressed fluid which can be specially adapted to vibrating tables or to various machines | |
| US20050172626A1 (en) * | 2001-07-13 | 2005-08-11 | Pierre Lebret | Penetration master cylinder with reduced backlash and application thereof |
| US20050103010A1 (en) * | 2003-10-08 | 2005-05-19 | Atsushi Yasuda | Master cylinder |
| DE102009054695A1 (en) * | 2009-12-15 | 2011-06-16 | Continental Teves Ag & Co. Ohg | Master cylinder for a regulated braking system |
| DE102011075359A1 (en) * | 2011-05-05 | 2012-11-08 | Continental Teves Ag & Co. Ohg | Master cylinder, in particular for a regulated braking system |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014201699A1 (en) | 2014-07-31 |
| WO2014118301A1 (en) | 2014-08-07 |
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Application publication date: 20150930 |
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| RJ01 | Rejection of invention patent application after publication |