WO2014102133A1 - Compressed-gas bypass valven - Google Patents

Compressed-gas bypass valven Download PDF

Info

Publication number
WO2014102133A1
WO2014102133A1 PCT/EP2013/077346 EP2013077346W WO2014102133A1 WO 2014102133 A1 WO2014102133 A1 WO 2014102133A1 EP 2013077346 W EP2013077346 W EP 2013077346W WO 2014102133 A1 WO2014102133 A1 WO 2014102133A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressed
gas bypass
armature
bypass valve
valve
Prior art date
Application number
PCT/EP2013/077346
Other languages
French (fr)
Inventor
Xiangguang CAO
Guangrui SUN
Russell M. Modien
Jiaqiang Chen
Longsheng ZHAO
Original Assignee
Continental Automotive Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2014102133A1 publication Critical patent/WO2014102133A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/16—Control of the pumps by bypassing charging air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/029—Electromagnetically actuated valves
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0668—Sliding valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present utility model relates to the field of machinery, in particular to a compressed-gas bypass valve for a turbocharged engine .
  • the compressed-gas bypass valve of the present utility model has the following advantages with respect to the prior art: based on mature solenoid valve technology in the prior art, a com ⁇ pressed-gas bypass valve with a smaller size, a simple structure, and even better performance is designed, using the electro ⁇ magnetic force produced by a solenoid valve to replace a vacuum as a driving force.
  • Fig. 3 shows schematically an exploded view of the components of an embodiment of the compressed-gas bypass valve.
  • Fig. 4 shows schematically a graph comparing the performance curves of a solenoid valve with a magnetically permeable sleeve and a solenoid valve with no magnetically permeable sleeve.
  • Fig. 5 shows a schematic view of the coil in an embodiment of the solenoid valve.
  • Fig. 6 shows a graph comparing the performance curves of a completely sealed coil and a non-sealed coil.
  • Fig. 7 shows a schematic diagram of a floating connection between a valve head and an armature, established by means of a DGBB bearing.
  • Fig. 8 shows a schematic diagram of a floating connection between a valve head and an armature, established by means of a snap-fit.
  • Fig. 1 shows the structure and layout of a compressed-gas back-flow pipeline having a compressed-gas bypass valve ac ⁇ cording to the present utility model.
  • a compressed-gas back-flow pipeline connected in parallel with the air compressor is provided upstream of the compressed-air intercooler, to enable compressed gas to flow from the air compressor outlet back to the air compressor inlet.
  • the back-flow of compressed gas can prevent a surge in the gas flow, and thereby prevent damage to the turbine blades caused by a surge jitter.
  • the back-flow of compressed gas can also allow the turbine to keep rotating to reduce turbine lag during acceleration and protect the throttle valve.
  • a compressed-gas bypass valve is provided in the compressed-gas back-flow pipeline.
  • the periphery of the bowl-shaped connection element 25 is connected to the valve head 2, and there is a through-hole in the center of the bowl-shaped connection element 25, the armature 3 being snap-fitted in the through-hole.
  • the elastic component 4 may be a helical compression spring.
  • a bushing 7 is provided around the periphery of the armature 3, the bushing 7 being used as a guiding structure for the movement of the armature 3.
  • the compressed-gas bypass valve 1 further comprises a wire reel 5 which at least partially surrounds the bushing 7.
  • a coil 6 is wound on the wire reel 5.
  • the compressed-gas bypass valve 1 further comprises a housing 16 which surrounds the coil 6, an outer encapsulating element 17 which surrounds the housing 16, and a protective cover 18 around the valve head 2.
  • the housing 16 is made of a magnetically permeable material to enhance the magnetic force, and together with the coil 6 forms a completely sealed coil structure.
  • a sealing element for sealing such as an O-ring 19, is provided between the outer encapsulating element 17 and the protective cover 18.
  • a sealing element such as a V-ring 21 is provided between the protective cover 18 and the valve head 2.
  • the armature 3 of the com ⁇ pressed-gas bypass valve 1 is cylindrical.
  • a lubricating layer is provided on an inner peripheral wall of the bushing 7 to facilitate guiding of the armature 3, while also reducing resistance to movement.
  • the bushing 7 is made of a magnetically permeable material, so that the magnetic force of the solenoid valve is increased and performance is boosted.
  • a sleeve 8 is fitted between the bushing 7 and the wire reel 5; installation of the sleeve 8 may for example be accomplished by means of an interference fit.
  • Such a structure helps to increase the magnetic force of the com ⁇ pressed-gas bypass valve 1, thereby optimizing performance.
  • the sleeve 8 is made of a magnetically permeable material. Not only can this give more room for optimizing the stator structure, but the use of a magnetically permeable material for the sleeve itself also plays a definite role in terms of improving performance. Fig.
  • FIG. 4 shows sche- matically a graph comparing the performance curves of a solenoid valve with a magnetically permeable sleeve and a solenoid valve with no magnetically permeable sleeve. It can be seen from Fig. 4 that under the same conditions, with the size of the solenoid valve remaining unchanged, the magnetic force can be increased by about 53.8% overall. Correspondingly, under the same magnetic force supply conditions, the dimensions of the compressed-gas bypass valve 1 can be reduced.
  • the armature 3 is hollow and has a vent hole 20, to prevent a vacuum (which would hinder movement) from forming during movement.
  • the vent hole 20 is located halfway along the length of the armature 3.
  • Fig. 5 shows a schematic view of the coil 6 in an advantageous embodiment of the solenoid valve. It can be seen from Fig. 5 that the coil 6 has a completely sealed structure.
  • Fig. 6 shows a graph comparing the performance curves of a completely sealed coil and a non-sealed coil. It can be seen from Fig. 6 that a coil with a completely sealed structure is not only conducive to an increased magnetic force, but also more stable than a non-sealed coil in terms of performance.
  • the compressed-gas bypass valve 1 further comprises an electronic component 9 for absorbing pulse energy.
  • the provision of the electronic component 9 for absorbing pulse energy can protect the valve body from being damaged by a sudden change in external voltage, such as a pulse.
  • the electronic component 9 for absorbing pulse energy can absorb energy produced by the valve body, protecting the customer's electricity supply terminal from damage and satisfying the EMC requirements of the automobile industry.
  • the elec ⁇ tronic component for absorbing pulse energy may be various electronic components known to those skilled in the art, such as a diode.
  • the compressed-gas bypass valve 1 can take the form of a diverse range of products, ensuring that it is suited to different customer requirements.
  • the wire reel 5 is made by injection molding. On the wire reel 5 are provided multiple, preferably 2, annular ribs, so as to prevent plastic from entering and filling crevices during injection molding of the plastic, causing valve failure.

Abstract

A compressed-gas bypass valve (1) for a turbocharged engine, comprising: a moveable valve core, comprising a valve head (2) and an armature (3) in a floating connection with the valve head (2); an elastic component (4) for pressing the valve head (2) into a non-actuated position; a bushing (7) provided around the periphery of the armature (3), the bushing (7) being used to guide the movement of the armature (3); and a wire reel (5) at least partially surrounding the bushing (7), a coil (6) being wound on the wire reel (5). The compressed-gas bypass valve of the present utility model uses the electromagnetic force produced by a solenoid valve as a driving force, and has a smaller size, a simple structure, and even better performance.

Description

Description
Compressed-gas bypass valven Technical Field
The present utility model relates to the field of machinery, in particular to a compressed-gas bypass valve for a turbocharged engine .
Background art
There are already a large number of electronic valves applied in the technical field of automobiles. Of these, the vacuum valve is one of the more commonly used types. The shortcomings of such a vacuum valve are that it has a large size and structural complexity due to the need for auxiliary parts such as a vacuum channel and valve . Another shortcoming of the vacuum valve is that it has a long response time.
Content of the utility model
The problem solved by the present utility model is to provide a compressed-gas bypass valve, wherein the compressed-gas bypass valve has a simple structure and improved performance while being of smaller dimensions.
To solve the above problem, the compressed-gas bypass valve provided by the present utility model comprises: a moveable valve core, comprising a valve head and an armature in a floating connection with the valve head; an elastic component for pressing the valve head into a non-actuated position; a bushing provided around the periphery of the armature, the bushing being used to guide the movement of the armature; and a wire reel at least partially surrounding the bushing, a coil being wound on the wire reel. The compressed-gas bypass valve of the present utility model uses the electromagnetic force produced by a solenoid valve as a driving force, and has a smaller size, a simple structure, and even better performance.
The compressed-gas bypass valve of the present utility model has the following advantages with respect to the prior art: based on mature solenoid valve technology in the prior art, a com¬ pressed-gas bypass valve with a smaller size, a simple structure, and even better performance is designed, using the electro¬ magnetic force produced by a solenoid valve to replace a vacuum as a driving force.
Description of the accompanying drawings
Fig. 1 shows the structure and layout of a compressed-gas back-flow pipeline having a compressed-gas bypass valve according to the present utility model.
Fig. 2 shows schematically a sectional view of an embodiment of the compressed-gas bypass valve according to the present utility model.
Fig. 3 shows schematically an exploded view of the components of an embodiment of the compressed-gas bypass valve. Fig. 4 shows schematically a graph comparing the performance curves of a solenoid valve with a magnetically permeable sleeve and a solenoid valve with no magnetically permeable sleeve. Fig. 5 shows a schematic view of the coil in an embodiment of the solenoid valve.
Fig. 6 shows a graph comparing the performance curves of a completely sealed coil and a non-sealed coil. Fig. 7 shows a schematic diagram of a floating connection between a valve head and an armature, established by means of a DGBB bearing. Fig. 8 shows a schematic diagram of a floating connection between a valve head and an armature, established by means of a snap-fit.
Fig. 9 shows a partial magnified schematic diagram of the direct floating connection between the valve head and the armature in Fig. 2.
Particular embodiments
Compressed-gas bypass valves according to embodiments of the present invention are described below with reference to the accompanying drawings. In the description which follows, many specific details are expounded to give those skilled in the art a more comprehensive understanding of the present utility model. However, it will be clear to those skilled in the art that some of these specific details could be omitted in the implementation of the present utility model. Moreover, it should be appreciated that the present utility model is by no means limited to the specific embodiments presented. On the contrary, it would be possible to realize the present utility model using any com¬ bination of the following features and key elements, regardless of whether they relate to different embodiments. Therefore, the following aspects, features, embodiments and advantages serve the sole purpose of illustration, and should not be regarded as key elements or definitions of the claims, unless clearly mentioned in the claims.
Turbocharged engines, i.e. engines with a turbocharger, are being used in ever increasing numbers in modern motorized vehicles, to improve energy efficiency. In turbocharged engines, exhaust gases drive the turbocharger turbine disposed in the exhaust pipeline, thereby simultaneously making an air compressor „
connected to the turbine compress incoming air. The air that has undergone compression (hereinafter referred to as compressed air) passes through a compressed-air intercooler to arrive at the throttle valve, thereby entering the engine cylinder for combustion.
Fig. 1 shows the structure and layout of a compressed-gas back-flow pipeline having a compressed-gas bypass valve ac¬ cording to the present utility model. According to the present utility model, a compressed-gas back-flow pipeline connected in parallel with the air compressor is provided upstream of the compressed-air intercooler, to enable compressed gas to flow from the air compressor outlet back to the air compressor inlet. The back-flow of compressed gas can prevent a surge in the gas flow, and thereby prevent damage to the turbine blades caused by a surge jitter. Moreover, the back-flow of compressed gas can also allow the turbine to keep rotating to reduce turbine lag during acceleration and protect the throttle valve. As Fig. 1 shows, a compressed-gas bypass valve is provided in the compressed-gas back-flow pipeline. When not energized, the compressed-gas bypass valve keeps the back-flow pipeline closed. This being the case, compressed air passes through the com¬ pressed-air intercooler, throttle valve and intake manifold to enter the engine cylinders. When energized, the compressed-gas bypass valve opens the back-flow pipeline, and compressed air can flow back to the intake end of the air compressor via the compressed-gas bypass valve. Figs. 2 and 3 show schematically a sectional view and an exploded view, respectively, of an embodiment of the compressed-gas bypass valve according to the present utility model. As Figs. 2 - 3 show, the compressed-gas bypass valve 1 comprises a moveable valve core and an elastic component 4 for pressing the moveable core into a non-actuated position, the moveable core comprising a valve head 2 and an armature 3. As Figs. 2 and 9 show, a direct floating connection can be established between the valve head 2 and armature 3. A spherical structure which facilitates floating of the valve head 2 and armature 3 can be clearly seen in Fig. 9 ; the spherical structure should be a protrusion on that side of the valve head 2 which faces the armature 3. Alternatively, as shown in Fig. 7, a floating connection can be established between the valve head 2 and armature 3 by means of a support device, such as a DGBB bearing 15 (deep groove ball bearing) . The DGBB bearing is snap-connected to the valve head 2; the connection between the DGBB bearing and the armature 3 is accomplished by means of an interference fit. Floating of the valve head 2 and armature 3 relative to one another can be achieved by adjusting the clearance of the DGBB bearing. Alternatively, as shown in Fig. 8, a floating connection is established between the valve head 2 and armature 3 by a snap-fit. Specifically, a bowl-shaped connection element 25 can be used to establish a floating connection between the valve head 2 and armature 3 by a snap-fit. The periphery of the bowl-shaped connection element 25 is connected to the valve head 2, and there is a through-hole in the center of the bowl-shaped connection element 25, the armature 3 being snap-fitted in the through-hole. For example, the elastic component 4 may be a helical compression spring. When power is cut off from the compressed-gas bypass valve 1, the valve head 2 presses downwards on a valve seat (not shown) under the action of gravity and of the elastic component 4, thereby closing the gas passage.
A bushing 7 is provided around the periphery of the armature 3, the bushing 7 being used as a guiding structure for the movement of the armature 3. The compressed-gas bypass valve 1 further comprises a wire reel 5 which at least partially surrounds the bushing 7. A coil 6 is wound on the wire reel 5.
In addition, multiple stators for enhancing the magnetic force of the compressed-gas bypass valve 1 may be provided, e.g. a first stator 10 disposed above the armature 3, and an annular second stator 11 arranged around the armature. Each stator is made of magnetically permeable material.
When the compressed-gas bypass valve 1 is energized, a magnetic circuit is formed by the first stator 10, the second stator 11 and the armature 3, and under the action of the electromagnetic force produced by the coil 6, the armature 3 moves upwards, simultaneously driving the valve head 2 upwards, opening the compressed-gas bypass valve 1 and thereby opening the gas passage.
The compressed-gas bypass valve 1 further comprises a housing 16 which surrounds the coil 6, an outer encapsulating element 17 which surrounds the housing 16, and a protective cover 18 around the valve head 2. Preferably, the housing 16 is made of a magnetically permeable material to enhance the magnetic force, and together with the coil 6 forms a completely sealed coil structure. A sealing element for sealing, such as an O-ring 19, is provided between the outer encapsulating element 17 and the protective cover 18. A sealing element such as a V-ring 21 is provided between the protective cover 18 and the valve head 2.
In one advantageous embodiment, the armature 3 of the com¬ pressed-gas bypass valve 1 is cylindrical.
In one advantageous embodiment, a lubricating layer is provided on an inner peripheral wall of the bushing 7 to facilitate guiding of the armature 3, while also reducing resistance to movement. With such a design, there is no need to plate the armature 3 itself with a lubricating layer separately, and so costs are reduced.
In one advantageous variation, the bushing 7 is made of a magnetically permeable material, so that the magnetic force of the solenoid valve is increased and performance is boosted.
In one advantageous variation, a sleeve 8 is fitted between the bushing 7 and the wire reel 5; installation of the sleeve 8 may for example be accomplished by means of an interference fit. Such a structure helps to increase the magnetic force of the com¬ pressed-gas bypass valve 1, thereby optimizing performance. In one advantageous variation, the sleeve 8 is made of a magnetically permeable material. Not only can this give more room for optimizing the stator structure, but the use of a magnetically permeable material for the sleeve itself also plays a definite role in terms of improving performance. Fig. 4 shows sche- matically a graph comparing the performance curves of a solenoid valve with a magnetically permeable sleeve and a solenoid valve with no magnetically permeable sleeve. It can be seen from Fig. 4 that under the same conditions, with the size of the solenoid valve remaining unchanged, the magnetic force can be increased by about 53.8% overall. Correspondingly, under the same magnetic force supply conditions, the dimensions of the compressed-gas bypass valve 1 can be reduced.
In one advantageous embodiment, the armature 3 is hollow and has a vent hole 20, to prevent a vacuum (which would hinder movement) from forming during movement. Preferably, the vent hole 20 is located halfway along the length of the armature 3. Preferably, the fewer the vent holes 20, the better; the smaller the size thereof, the better.
Fig. 5 shows a schematic view of the coil 6 in an advantageous embodiment of the solenoid valve. It can be seen from Fig. 5 that the coil 6 has a completely sealed structure. Fig. 6 shows a graph comparing the performance curves of a completely sealed coil and a non-sealed coil. It can be seen from Fig. 6 that a coil with a completely sealed structure is not only conducive to an increased magnetic force, but also more stable than a non-sealed coil in terms of performance. In one advantageous embodiment, as Figs. 2 - 3 show, the compressed-gas bypass valve 1 further comprises an electronic component 9 for absorbing pulse energy. In such an embodiment, the provision of the electronic component 9 for absorbing pulse energy can protect the valve body from being damaged by a sudden change in external voltage, such as a pulse. In addition, the electronic component 9 for absorbing pulse energy can absorb energy produced by the valve body, protecting the customer's electricity supply terminal from damage and satisfying the EMC requirements of the automobile industry. Moreover, the elec¬ tronic component for absorbing pulse energy may be various electronic components known to those skilled in the art, such as a diode. Thus the compressed-gas bypass valve 1 can take the form of a diverse range of products, ensuring that it is suited to different customer requirements.
Finally, in one advantageous embodiment, the wire reel 5 is made by injection molding. On the wire reel 5 are provided multiple, preferably 2, annular ribs, so as to prevent plastic from entering and filling crevices during injection molding of the plastic, causing valve failure. Although the present utility model has been disclosed above by way of preferred embodiments, it is by no means defined thereby. Any changes or modifications made by any person skilled in the art without departing from the spirit and scope of the present utility model should be included within the scope of protection thereof. Thus the scope defined by the claims should be regarded as the scope of protection of the present utility model.

Claims

Patent claims
A compressed-gas bypass valve (1) for a turbocharged engine, characterized in that it comprises:
a moveable valve core, comprising a valve head
(2) and an armature
(3) in a floating connection with the valve head (2) ; an elastic component
(4) for pressing the valve head (2) into a non-actuated position;
a bushing (7) provided around the periphery of the armature (3), the bushing (7) being used to guide the movement of the armature (3); and
a wire reel
(5) at least partially surrounding the bushing (7), a coil
(6) being wound on the wire reel (5).
The compressed-gas bypass valve as claimed in claim 1, characterized in that the armature (3) is cylindrical.
The compressed-gas bypass valve as claimed in claim 1, characterized in that a lubricating layer is provided on an inner peripheral wall of the bushing (7) .
The compressed-gas bypass valve as claimed in claim 1, characterized in that the bushing (7) is made of magnetically permeable material.
The compressed-gas bypass valve as claimed in claim 1, characterized in that a sleeve (8) is fitted between the bushing (7) and the wire reel (5) .
The compressed-gas bypass valve as claimed in claim 5, characterized in that there is an interference fit between the bushing (7) and the sleeve (8) .
7. The compressed-gas bypass valve as claimed in claim 5, characterized in that the sleeve (8) is made of a magnetically permeable material.
8. The compressed-gas bypass valve as claimed in claim 1, characterized in that the armature (3) has a hollow structure and a vent hole (20) is provided in the armature (3) .
9. The compressed-gas bypass valve as claimed in claim 8, characterized in that the vent hole is located halfway along the length of the armature.
10. The compressed-gas bypass valve as claimed in claim 1, characterized in that it further comprises a housing (16) which surrounds the coil, the housing (16) and the coil (6) forming a completely sealed structure.
11. The compressed-gas bypass valve as claimed in claim 1, characterized in that the compressed-gas bypass valve (1) further comprises an electronic component (9) for absorbing pulse energy.
12. The compressed-gas bypass valve as claimed in claim 11, characterized in that the electronic component (9) for absorbing pulse energy is a diode.
13. The compressed-gas bypass valve as claimed in claim 1, characterized in that at least 2 annular ribs are provided on the wire reel (5) .
14. The compressed-gas bypass valve as claimed in claim 1, characterized in that a floating connection is established between the valve head (2) and the armature (3) by means of a protrusion on that side of the valve head (2) which faces the armature (3) .
15. The compressed-gas bypass valve as claimed in claim 1, characterized in that a floating connection is established between the valve head (2) and the armature (3) by means of a deep groove ball bearing (15) , the deep groove ball bearing (15) being snap-connected to the valve head (2), and the connection between the deep groove ball bearing (15) and the armature (3) being accomplished by means of an interference fit .
16. The compressed-gas bypass valve as claimed in claim 1, characterized in that a floating connection between the valve head (2) and the armature (3) by means of a bowl-shaped connection element (25), the periphery of the bowl-shaped connection element (25) being connected to the valve head (2), a through-hole being provided in the center of the bowl-shaped connection element (25), and the armature (3) being snap-fitted in the through-hole.
PCT/EP2013/077346 2012-12-28 2013-12-19 Compressed-gas bypass valven WO2014102133A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201220741540.1 2012-12-28
CN2012207415401U CN203009035U (en) 2012-12-28 2012-12-28 Compressed gas bypass valve

Publications (1)

Publication Number Publication Date
WO2014102133A1 true WO2014102133A1 (en) 2014-07-03

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Country Link
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WO (1) WO2014102133A1 (en)

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WO2016026721A1 (en) * 2014-08-21 2016-02-25 Continental Automotive Gmbh Valve core for electronic valve and electronic valve comprising the valve core
WO2016041659A1 (en) 2014-09-19 2016-03-24 Pierburg Gmbh Adjustment element for an overrun air recirculation valve
WO2017005657A1 (en) * 2015-07-09 2017-01-12 Continental Automotive Gmbh Blow-off valve
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CN204476550U (en) 2015-03-12 2015-07-15 大陆汽车电子(芜湖)有限公司 A kind of Spool assembly and pressurized gas bypass valve
CN105370390A (en) * 2015-11-25 2016-03-02 重庆普什机械有限责任公司 Supercharged inter-cooling internal combustion engine gas intake bypass control device
CN109113947B (en) * 2017-06-26 2020-08-25 比亚迪股份有限公司 Electric oil pump assembly, steering system and lubricating system

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WO2009105405A1 (en) * 2008-02-19 2009-08-27 Continental Automotive Systems Us, Inc. Lift lock assembly feature for air bypass valve
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JP2017527757A (en) * 2014-08-21 2017-09-21 コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツングＣｏｎｔｉｎｅｎｔａｌ Ａｕｔｏｍｏｔｉｖｅ ＧｍｂＨ Valve core for electronic valve and electronic valve having valve core
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JP2017531140A (en) * 2014-09-19 2017-10-19 ピールブルク ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ ＧｍｂＨ Adjustment mechanism used for blow-off valves
US10393273B2 (en) 2014-09-19 2019-08-27 Pierburg Gmbh Adjustment element for an overrun air recirculation valve
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CN107735553A (en) * 2015-07-09 2018-02-23 大陆汽车有限责任公司 Turn of tidal stream valve
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DE102016118341A1 (en) 2016-09-28 2018-03-29 Pierburg Gmbh Adjusting element for a diverter valve
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