WO2015104169A1 - Schnellentlüftungsventilvorrichtung für pneumatische aktuatoren von pneumatischen einrichtungen sowie pneumatische einrichtung mit einer solchen schnellentlüftungsvorrichtung - Google Patents
Schnellentlüftungsventilvorrichtung für pneumatische aktuatoren von pneumatischen einrichtungen sowie pneumatische einrichtung mit einer solchen schnellentlüftungsvorrichtung Download PDFInfo
- Publication number
- WO2015104169A1 WO2015104169A1 PCT/EP2014/078684 EP2014078684W WO2015104169A1 WO 2015104169 A1 WO2015104169 A1 WO 2015104169A1 EP 2014078684 W EP2014078684 W EP 2014078684W WO 2015104169 A1 WO2015104169 A1 WO 2015104169A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- flow
- active surface
- diaphragm
- pneumatic
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/024—Pressure relief 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
- B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
- B60T15/02—Application and release valves
- B60T15/36—Other control devices or valves characterised by definite functions
- B60T15/52—Other control devices or valves characterised by definite functions for quick release of brakes, e.g. for influencing counter- pressure in triple valve or recirculating air from reservoir or brake cylinder to brake pipe
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/202—Externally-operated valves mounted in or on the actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2215/00—Fluid-actuated devices for displacing a member from one position to another
Definitions
- the invention is based on a quick exhaust valve device for pneumatic actuators of pneumatic devices according to claim 1 and of a pneumatic device including at least one such quick exhaust valve device according to claim 10.
- air suspension devices or pneumatic clutch and / or transmission devices also include actuators, e.g. Air bellows, which must be ventilated and vented within a short time or with a certain gradient.
- actuators e.g. Air bellows
- ABS, ASR or ESP are on board, high demands are placed on the dynamics of pneumatic brake cylinders.
- the pneumatic brake pressure in the brake cylinders is usually controlled by a relay valve, which is precontrolled by a control pressure of an electromagnetic inlet / outlet valve combination.
- the relay valve can provide the required ventilation gradients and ventilation times, in some cases the bleeding requirements may not be met. In this case, a quick exhaust valve device is helpful, which is placed between the working output of the relay valve and the brake cylinder.
- the present invention is therefore an object of the invention to provide a quick exhaust device available, which as fast as possible Venting a pneumatic actuator allows a pneumatic device and it is simple in construction.
- a quick exhaust device should also be arranged or used in a pneumatic device.
- the invention is the first time a quick exhaust valve device for pneumatic actuators of pneumatic devices, with
- a membrane valve disposed in the housing, which comprises at least one membrane acting together with a valve seat, wherein in an open position of the diaphragm valve, in which the membrane is lifted from the valve seat, a pressure sink is connected to the first port and in a closed position of the Diaphragm valve, in which the membrane is sealingly seated on the valve seat, this connection is interrupted, and wherein
- a second active surface of the membrane which urges the diaphragm valve in the closed position under pressure, is loaded by a prevailing in the reduced flow cross-section at the constriction or throttle second pressure or by a in a second portion of the flow channel between the second port and the constriction or Throttling prevailing first pressure, and the diaphragm is urged by compression spring means in the closed position, wherein
- the first active surface, the second active surface, the compression spring means and the flow cross sections in the first section, in the second section and at the constriction or throttle point of the flow channel are designed such that
- the opening forces acting on the first effective surface originating at least from the third pressure, counteract the effect of the second pressure acting on the second effective surface, or from the first pressure as well as from the forces resulting from the compression springs closing forces keep the diaphragm valve in the open position or bring.
- the second active surface of the membrane is loaded by the second pressure prevailing in the reduced flow cross-section at the constriction or throttling point.
- the second active surface of the membrane is loaded by the first pressure prevailing between the second connection and the constriction or throttling point.
- Both variants of the invention make use of the effect that, in the case of a flow through a flow channel, starting from a flow cross section through a contrasting smaller flow cross section at a constriction or throttle point according to the law of continuity at the constriction or throttle point, the flow velocity and thus the dynamic dynamic pressure increase. But the static pressure is reduced. Furthermore, the effect is used that results in the flow through the constriction or throttle point losses of flow energy, which in a
- first, second and third pressures are essentially static pressures.
- the expert can, on the basis of his specialist knowledge, determine the first effective area, the second effective area, the compression spring means and the flow cross sections in the first section, in the second section and at the constriction or throttle point. Design and dimension seistelle of the flow channel suitable for the desired effects described above occur.
- a branch channel branches off from the first section of the flow channel, preferably in the vertical direction, which communicates at least with a part of the first active surface of the membrane.
- the first effective area of the membrane is at least partially set below the third pressure which prevails between the first connection and the constriction or throttling point 25.
- a partial flow of the vent flow through the flow channel and another partial stream of the vent flow over the branch channel to the pressure sink is formed accordingly.
- the venting of the pneumatic actuator takes place on the one hand via the flow channel in the direction of the second port and the pressure source to and on the other hand via the branch channel and the pressure sink.
- the vent partial flow which is passed through the flow channel and the second port, can then be vented in particular via a vent disposed between the second port and the compressed air source.
- a relay valve is arranged between the second connection and the pressure source, then the partial ventilation stream conducted via the flow channel can be vented by means of the venting conventionally associated with such a relay valve.
- the second effective area of the membrane under second pressure according to the first variant or under the first pressure according to the first variant can be set, for example, a limited by the second active surface of the membrane chamber by means of a connecting channel according to the first variant with the constriction or Throttle or according to the second variant with the second portion of the flow channel in connection.
- the connecting channel can be arranged substantially perpendicular to the second section of the flow channel or to constricting or throttling point in order to control as possible only a static first or second pressure to the second effective surface of the membrane.
- the membrane is held at its radially outer edge in the housing, for example between two housing halves of the housing, and cooperates via an axially movable radially inner portion with the valve seat.
- the valve seat is formed as an edge of an orifice of a vent channel connected to the pressure sink in the housing, wherein the vent channel may for example be arranged perpendicular to the flow channel.
- the vent channel may for example be arranged perpendicular to the flow channel.
- arbitrary orientations of the venting channel or the central axis of the diaphragm valve with respect to the flow channel or its center axis are possible.
- the invention also relates to a pneumatic or electro-pneumatic device of a vehicle which includes at least one high-speed ventilation valve device described above.
- a pneumatic or electro-pneumatic device of a vehicle which includes at least one high-speed ventilation valve device described above.
- Such a device can be, for example, a pneumatic or electro-pneumatic brake device, an air suspension device or a pneumatically actuated
- Act 15 clutch and / or transmission device of a vehicle Of course, this list is not exhaustive, as one or more pneumatic actuators of any pneumatic or electro-pneumatic device can be vented by means of the quick-release device according to the invention.
- the device is particularly preferably a pneumatic or electro-pneumatic brake device, wherein at least one clip-type ventilation device described above is arranged between a working connection of a relay valve and at least one brake cylinder, the first connection being provided with a ventilatable and brake chamber of the brake
- the quick exhaust device separately, ie formed with its own housing or integrated into the housing of the brake cylinder.
- the housing of the quick exhaust device can be designed as at least two-part housing, in which case the edge of the membrane of the diaphragm valve can be clamped between the two housing parts.
- FIG. 1 is a side sectional view of a preferred embodiment of a first variant of the invention
- FIG. 2 shows the lateral sectional view of Figure 1 with symbolized by arrows ventilation flow and venting flow.
- FIG 3 is a side sectional view of a preferred embodiment of a second variant of the invention.
- a preferred embodiment of a first variant of a quick exhaust valve device 1 shown in FIG. 1 is preferably used for rapid venting of a pneumatic brake cylinder (not shown here for reasons of scale) of a pneumatic or electro-pneumatic brake device of a vehicle, in particular of a commercial vehicle.
- the quick exhaust valve device 1 here preferably forms a separate device with its own housing 2, a connectable with a ventilated and ventable brake chamber of the brake cylinder first port 4 and connected to a working port of a relay valve not shown here second port 6.
- the relay valve is part of a in electro-pneumatic braking devices well-known pressure control module and is connected via a supply connection to a compressed air source, in particular with a compressed air reservoir and controls depending on the pending at its pneumatic control port, generated by an inlet / outlet valve control pressure working or braking pressure to its working port ,
- a here preferably cylindrical and straight flow channel 8 is formed between the first port 4 and the second port 6, which is narrowed at a constriction or throttle point 10 by a reduced flow cross-section.
- the flow channel 8 in a first flow channel section 12 between the first port 4 and the constriction or throttle point 10 and in a second flow channel section 14 between the constriction or throttle point 10 and the second port 6 each have a larger flow cross-section than at the Constriction or throttle point 10.
- the transition from the respective larger flow cross section of the first flow channel section 12 and the second flow channel section 14 on the contrast smaller flow cross section of the constriction or throttle point 10 is preferably carried out here in a stepped manner. Alternatively, this transition can also be continuous and continuous.
- a diaphragm valve 16 is arranged, which comprises at least one valve seat 18 with a cooperating membrane 20, wherein in an open position of the diaphragm valve 16, in which the membrane 20 is lifted from the valve seat 18, a pressure sink 22 with the first Terminal 4 is connected and in a closed position of the diaphragm valve 16, in which the membrane 20 is sealingly seated on the valve seat 18, this connection is interrupted, as can be easily imagined with reference to FIG.
- the example circular-shaped membrane 20 is held at its radially outer edge in the housing 2 and clamped, for example, between two housing halves 2A, 2B of the housing 2.
- the diaphragm 20 cooperates with the valve seat 18 via an axially movable radially inner portion and has a first active surface 24 and a second active surface 26 facing away from it.
- the valve seat 18 is formed as an edge of an orifice of a connected to the pressure sink 22, for example, the atmosphere vent passage 28 in the housing 2, wherein the vent passage 28 is arranged for example perpendicular to the flow channel 8.
- the vent channel 28 is formed for example in the here lower half of the housing 2B, in which also the valve seat 18 and the vent channel 28 are formed, wherein during assembly of the diaphragm valve 16, the membrane is placed on the lower half of the housing 2B under contact of the valve seat and then for fixing the membrane, the upper half of the housing 2A is mounted on the lower half of the housing 2B, with the interposition of the edge of the membrane 20th
- the third pressure p3 can act on this annular surface 30 of the first active surface 24 of the membrane, branches from the first flow channel section 12 from a puncture channel 32, preferably in an initially vertical direction and then inclined at an acute angle to the vertical with respect to the flow channel 8, which is in communication with an annular chamber 34, which is bounded by the annular surface 30 of the first active surface 24 of the membrane 20.
- the pressure forces based on the third pressure p3 therefore act against the first active surface 24 in the opening direction of the diaphragm valve 16.
- this second active surface 26 is loaded by a second pressure p2 prevailing in the reduced flow cross section at the constriction or throttle point 10. So that the second active surface 26 of the membrane 20 can be set below the second pressure p2, for example, one is through the second active surface 26th
- This connecting channel 40 is preferably arranged perpendicular to the flow channel 8, so that of the prevailing in the constriction or throttling point 10 total pressure (static pressure and dynamic dynamic pressure) substantially only
- the diaphragm 20 is urged by a compression spring 42 in the closed position, which is supported on the one hand centrally on the diaphragm 20 and on the other hand at the bottom of the chamber 38, in which the connecting channel 40 opens.
- the compression spring 42 is then, in order to exert compressive forces on the diaphragm 20 25 in the closing direction, installed between the bottom of the chamber 38 and the diaphragm 20 and the valve seat 18 supporting this biased. Consequently, the compressive forces acting on the second active surface 26 of the diaphragm 20 resulting from the compression spring 42 as well as the second pressure p2 urge the diaphragm 20 against the valve seat 18 to bring or hold the diaphragm valve in its closed position.
- the flow cross section in the first flow channel section 12 may be slightly larger than the flow cross section in the second flow channel section 14.
- these flow cross sections may equally well be the same or the inverse conditions exist.
- the operation of the quick exhaust device 1 according to the first variant of FIG. 1 is as follows:
- the first active surface 24, the second active surface 26, the compression spring 42 and the flow cross sections in the first flow channel section 12, in the second flow channel section 14 and at the constriction or throttling point 10 of the flow channel 8 are designed such that when starting from the second port 6 for first port 4 directed towards, in Fig.2
- 2 p forms the static pressure, with: v flow velocity, p pressure, and p density of the fluid.
- the venturi effect describes that the flow velocity v of a fluid flowing through a flow channel is inversely proportional to a changing tube cross section. This means that the flow velocity v of the fluid increases at cross-sectional constrictions because, according to the law of continuity, the same amount of fluid has to be discharged from any flow cross-section of a flow channel that has been introduced into it.
- the effect is used that results in the flow through the necking or throttling point 10 losses of flow energy, which compared with the static pressure p1 or p3 before the constriction or throttling point 10 in passing after passing through the 15th ligation or throttling point 10 reduced static pressure p1 or p3 result.
- the abovementioned laws for the ventilation flow 44 mean that the flow velocity vi, which prevails in the second flow channel section 14, at the inlet.
- the flow velocity decreases from v2 to v3.
- the third pressure p3 in the first flow channel section 12 no longer reaches the outlet pressure p1 in the second flow channel section 14 due to flow diversions and friction. Due to this relatively large energy loss, the third pressure p3 in the first flow channel section 12 is then even smaller than the second pressure p2 at the constriction or throttling point 10 and p3 ⁇ p2.
- the relatively low third pressure p3 prevailing in the first flow channel section 12 can then act on the annular surface 30 of the first active surface 24 of the membrane 20 via the branch channel 32 and the annular chamber 34. Together with the compressive forces, which are loaded on the inner part 36 of the first effective surface and derived from the atmospheric pressure, the rela ⁇ tively low third pressure p3 but not, the diaphragm valve 16 against the action of acting on the second effective surface 26th to open from the relatively high second pressure p2 as well as from the forces resulting from the compression spring closing forces (with appropriate design), so that this remains in its secured by the compression spring 42 closed position or placed in this.
- the above-described laws for the vent flow 46 taking place in the opposite direction mean that the flow velocity v3 prevailing in the first flow channel section 12 increases at the constriction or throttling point 10 to the comparatively greater flow velocity v2, and that in the first flow channel.
- the purge flow 46 is p2 ⁇ p3.
- This relatively low second pressure p2 is then applied via the connecting channel 40 to the second active surface 26 of the membrane 20.
- the example shows that the ratio between the second pressure p2 and the third pressure p3 depends on the direction in which the flow channel 8 flows through and thus is different or countercurrent to the vent flow 44 and the vent flow 46.
- the pneumatic brake device has a relay valve arranged between the second port 6 and the pressure source.
- the partial deaeration stream 46A directed via the flow channel 8 can be deaerated by means of the deaeration usually associated with such a relay valve.
- the second active surface 26 is not acted upon by the second pressure p 2 but by the first pressure p 1 via a connecting channel 40, which is formed between the second flow channel section 14 and the chamber 38. Also, this connection channel 40 is preferably arranged perpendicular to the flow channel 8.
- the second active surface 26 of the diaphragm 20 of the first pressure p1 and the pressure forces of the compression spring 42 in the closing direction and the first Wirkflä- che 24 still burdened by the third pressure p3 and the atmospheric pressure in the opening direction.
- the first active surface 24, the second active surface 26, the compression spring 42 and the flow cross sections in the first flow channel section 12, in the second flow channel section 14 and at the constriction or throttling point 10 of the flow channel 8 are designed such that when starting from the second port 6 for The first connection 4 directed toward Ventilation io flow for ventilation of the brake cylinder acting on the second active surface 26, from the first pressure p1 and from the spring 42 resulting from the compression forces against the action of acting on the first active surface 24, from the third pressure p3 and the atmospheric pressure resulting opening forces keep the diaphragm valve 16 in the closed position or brin-
- the prevailing in the first flow channel section 12 relatively low third i o pressure p3 can then act on the puncture channel 32 and the annular chamber 34 on the annular surface 30 of the first active surface 24 of the diaphragm 20.
- This relatively low first pressure p1 is then applied to the second active surface 26 of the membrane 20 via the connecting channel 25.
- this relatively small first pressure p1 together with the compression spring forces of the compression spring 42 can not prevent the membrane 20, due to the pressure forces acting in the opposite direction from the then relatively large third pressure p3 and the atmospheric pressure.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Transportation (AREA)
- Fluid-Driven Valves (AREA)
- Details Of Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2936275A CA2936275A1 (en) | 2014-01-09 | 2014-12-19 | Quick-action bleeder valve device for pneumatic actuators of pneumatic systems, and pneumatic system having a quick-action bleeder valve device of this type |
MX2016008932A MX2016008932A (es) | 2014-01-09 | 2014-12-19 | Dispositivo de valvula de purga rapida para actuadores neumaticos de sistemas neumaticos y sistema neumatico teniendo semejante dispositivo de valvula de purga rapida. |
US15/110,631 US20160327068A1 (en) | 2014-01-09 | 2014-12-19 | Quick-action bleeder valve device for pneumatic actuators of pneumatic systems, and pneumatic system having a quick-action bleeder valve device of this type |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014100187.7 | 2014-01-09 | ||
DE102014100187.7A DE102014100187A1 (de) | 2014-01-09 | 2014-01-09 | Schnellentlüftungsventilvorrichtung für pneumatische Aktuatoren von pneumatischen Einrichtungen sowie pneumatische Einrichtung mit einer solchen Schnellentlüftungsvorrichtung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015104169A1 true WO2015104169A1 (de) | 2015-07-16 |
Family
ID=52134204
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/078684 WO2015104169A1 (de) | 2014-01-09 | 2014-12-19 | Schnellentlüftungsventilvorrichtung für pneumatische aktuatoren von pneumatischen einrichtungen sowie pneumatische einrichtung mit einer solchen schnellentlüftungsvorrichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US20160327068A1 (de) |
CA (1) | CA2936275A1 (de) |
DE (1) | DE102014100187A1 (de) |
MX (1) | MX2016008932A (de) |
WO (1) | WO2015104169A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106812750A (zh) * | 2015-12-01 | 2017-06-09 | 北汽福田汽车股份有限公司 | 一种可避免零件受高压冲击的阀、液压系统及车辆 |
CN106762922B (zh) * | 2016-12-22 | 2018-03-16 | 常州科研试制中心有限公司 | 单轨吊制动油缸用的液压快排阀 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2089480A (en) * | 1980-12-13 | 1982-06-23 | Bendix Ltd | Valve assemblies |
US4596265A (en) * | 1984-11-15 | 1986-06-24 | Allied Corporation | Quick release valve |
EP0431383A1 (de) * | 1989-12-05 | 1991-06-12 | Knorr-Bremse Ag | Gleitschutzventil für druckluftgebremste Fahrzeuge |
USRE37617E1 (en) * | 1995-01-26 | 2002-04-02 | John C. Sherman | Ball valve with integrated removable flow venturi, flow balancing means, and pipe union means |
WO2004078546A1 (en) * | 2003-03-05 | 2004-09-16 | Bendix Commercial Vehicle Systems Llc | Pneumatic valve with an enhanced exhaust flow control feature |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2718897A (en) * | 1953-04-03 | 1955-09-27 | Bendix Westinghouse Automotive | Quick release valve |
BE793582A (fr) * | 1972-01-03 | 1973-04-16 | North American Rockwell | Valve |
US4187764A (en) * | 1972-07-12 | 1980-02-12 | The United States Of America As Represented By The United States Department Of Energy | Fast-acting valve actuator |
DE59402560D1 (de) * | 1993-10-29 | 1997-05-28 | Siemens Ag | Stellmotor, insbesondere für ein schnellschlussventil |
US20040107990A1 (en) * | 2002-12-06 | 2004-06-10 | Thanh Ho | Enhanced exhaust flow control feature |
DE102010003463B4 (de) * | 2010-03-30 | 2013-11-14 | Haldex Brake Products Gmbh | Pneumatische Baueinheiten für Luftfederungsanlagen |
-
2014
- 2014-01-09 DE DE102014100187.7A patent/DE102014100187A1/de not_active Ceased
- 2014-12-19 WO PCT/EP2014/078684 patent/WO2015104169A1/de active Application Filing
- 2014-12-19 US US15/110,631 patent/US20160327068A1/en not_active Abandoned
- 2014-12-19 CA CA2936275A patent/CA2936275A1/en not_active Abandoned
- 2014-12-19 MX MX2016008932A patent/MX2016008932A/es unknown
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2089480A (en) * | 1980-12-13 | 1982-06-23 | Bendix Ltd | Valve assemblies |
US4596265A (en) * | 1984-11-15 | 1986-06-24 | Allied Corporation | Quick release valve |
EP0431383A1 (de) * | 1989-12-05 | 1991-06-12 | Knorr-Bremse Ag | Gleitschutzventil für druckluftgebremste Fahrzeuge |
USRE37617E1 (en) * | 1995-01-26 | 2002-04-02 | John C. Sherman | Ball valve with integrated removable flow venturi, flow balancing means, and pipe union means |
WO2004078546A1 (en) * | 2003-03-05 | 2004-09-16 | Bendix Commercial Vehicle Systems Llc | Pneumatic valve with an enhanced exhaust flow control feature |
Also Published As
Publication number | Publication date |
---|---|
CA2936275A1 (en) | 2015-07-16 |
DE102014100187A1 (de) | 2015-07-09 |
US20160327068A1 (en) | 2016-11-10 |
MX2016008932A (es) | 2016-09-16 |
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