EP0609408B1 - Rotating actuator - Google Patents
Rotating actuator Download PDFInfo
- Publication number
- EP0609408B1 EP0609408B1 EP93915687A EP93915687A EP0609408B1 EP 0609408 B1 EP0609408 B1 EP 0609408B1 EP 93915687 A EP93915687 A EP 93915687A EP 93915687 A EP93915687 A EP 93915687A EP 0609408 B1 EP0609408 B1 EP 0609408B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- outlet
- boundary
- rotating actuator
- longitudinal axis
- branch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 230000007704 transition Effects 0.000 claims abstract description 9
- 238000002485 combustion reaction Methods 0.000 claims abstract description 4
- 238000011144 upstream manufacturing Methods 0.000 claims 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M3/00—Idling devices for carburettors
- F02M3/06—Increasing idling speed
- F02M3/07—Increasing idling speed by positioning the throttle flap stop, or by changing the fuel flow cross-sectional area, by electrical, electromechanical or electropneumatic means, according to engine speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/12—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit
- F02D9/16—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit the members being rotatable
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M3/00—Idling devices for carburettors
- F02M3/06—Increasing idling speed
- F02M2003/067—Increasing idling speed the valve for controlling the cross-section of the conduit being rotatable, but not being a screw-like valve
Definitions
- the invention relates to a rotary actuator according to the preamble of the main claim.
- a turntable is already known (see, for example, WO 91/14090, US-A-2449833), but in which undesirable noise can occur as a result of eddies, especially when using suction pipes and suction pipe connections made of plastic.
- the turntable according to the invention with the characterizing features of the main claim has the advantage that a disturbing noise that occurs when flowing through the rotary valve housing is counteracted by reducing the vortex formation.
- FIG. 1 shows a longitudinal section through a turntable designed according to the invention
- FIG. 2 shows a view of the inlet connection of the turntable
- FIG. 3 shows a section along line III-III in FIG. 2.
- a rotary actuator 1 for controlling the idle speed of an internal combustion engine which has a rotary valve housing 2 with a cup-shaped receiving opening 3, into which a servomotor 4 is inserted, which can be acted upon by a speed-dependent control signal.
- a rotary valve housing 2 On the rotary valve housing 2, an inlet connector 5 and an outlet connector 6 are formed laterally, which open into a bore 7 running in the rotary valve housing 2 and coaxial with the receiving opening 3.
- the servomotor 4 of the rotary actuator 1 is connected via a shaft 9, which is mounted, for example, in two roller bearings 10, 11, to a rotary valve 12, which is concentrically rotatable in the bore 7, and which assumes an angle of rotation position corresponding to the control signal of the servomotor 4.
- the rotary slide valve housing 2 In the area of the mouth of the inlet connection 5 into the bore 7, the rotary slide valve housing 2 has a throttle opening 13, which is more or less closed by the rotary slide valve 12 in accordance with an angular position of the servomotor 4.
- the throttle opening 13 is opposite in the Bore 7 an outlet opening 14 is arranged, which opens into the outlet port 6.
- Inlet pipe 5 and outlet pipe 6 are connected via connecting lines 15, 16 to an intake pipe 17 in such a way that they form a bypass line 18 which bypasses a throttle valve 19 arranged in the intake pipe 17, the operating means in the bypass line 18 in the direction of the arrow when the throttle opening 13 is open 20 can flow to the internal combustion engine.
- the connecting lines 15, 16 and the suction pipe 17 can be made of metal and / or plastic.
- the inlet connector 5 has a longitudinal axis 22 and the outlet connector 6 has a longitudinal axis 23 which lie on a line and run at right angles to the shaft 9.
- the longitudinal axes 22, 23 are laterally offset so that they run past the shaft 9 and do not cut it (Fig. 3).
- the inlet connection 5 and the outlet connection 6 are shown in FIG. 1 shifted into the plane of the drawing.
- the flow cross-section of the bypass line 18 has a slight, truncated cone-shaped narrowing 24 from the mouth of the connecting line 15 into the inlet connection 5 in the flow direction.
- the flow cross section is formed by flat boundary surfaces 25 which run parallel to the longitudinal axis 22 and which enclose a square.
- a steady, streamlined transition is provided between the frustoconical constriction 24 and the boundary surfaces 25.
- the bypass line 18 From the outlet opening 14, the bypass line 18 has a slight, frustoconical extension 27 up to the mouth of the outlet nozzle 6 in the connecting line 16.
- the throttle opening 13 located in the inlet port 5 is formed by two opposite longer boundary edges 28 and two opposite shorter boundary edges 29 which are formed in a known manner approximately rectangular or approximately parallelogram-shaped to each other and dotted obliquely to the axis of the indicated wave 9 lie.
- the boundary surfaces 25 (Fig. 1) are arranged so that they run through the corresponding boundary edges (28, 29) and are approximately parallel to each other.
- the outlet opening 14 opposite the throttle opening 13 in the rotary valve housing 2, indicated by dashed lines in FIG. 2 has a larger cross section than the throttle opening 13 and has a straight boundary edge 30 on its side facing away from the shaft 9, which runs approximately parallel to the longitudinal axis of the shaft 9. Outside the straight boundary edge 30, the outlet opening 14 has a boundary edge 31 with a curved course, which can be circular, for example, in the projection.
- FIG. 3 shows the bore 7 arranged in the rotary valve housing 2, in which the shaft 9 is concentrically arranged, with which the rotary valve 12 is connected in a rotationally fixed manner.
- the rotary valve 12 has an outer surface 33 which corresponds to the diameter of the bore 7 and closes the throttle opening 13 more or less depending on the rotational angle position of the shaft 9, so that the amount of operating fluid flowing in the direction of arrow 20 can be controlled by rotating the shaft 9.
- the inlet connection 5 has the frustoconical constriction 24, which is adjoined by an area 40 with a concave course arched towards the longitudinal axis 22, which merges into an area 41 with a convex course.
- the area 41 adjoins the area 21 with the flat boundary surfaces 25 which run through the boundary edges 28, 29. This results in an approximately S-shaped course of the transition from the frustoconical constriction 24 to the boundary surfaces 25.
- the flow cross section is delimited by the opposing boundary surfaces 25, which each run through the longer boundary edges 28 .
- the boundary surfaces 25 assigned to the shorter boundary edges 29 can be shorter than approximately one third of the length of the inlet connection 5, viewed in the flow direction.
- the outlet connection 6 Starting from the outlet opening 14, starting from the straight boundary edge 30 in the flow direction, the outlet connection 6 initially runs along a flat boundary surface 26 which touches the boundary edge 30 and is directed approximately parallel to the longitudinal axis 23. After about a third of its length, the outlet connection 6 has in a region 42 a convex course that is curved away from the longitudinal axis 23, so that the flow cross section in region 42 is increasingly widening in the direction of flow. Adjoining the area 42, approximately halfway through the length of the outlet connection 6, is followed by a concave area 43 which is curved against the longitudinal axis 23 of the outlet connection 6, so that the flow cross section in the area 43 widens as seen in the flow direction. The region 43 is adjoined by the frusto-conical extension 27, which extends approximately over the last third of the outlet nozzle 6.
- the configuration of the flow profile in the rotary actuator according to the invention results in less swirling of the operating medium, as a result of which the noise development, in particular in the case of suction pipes and suction pipe connections made of plastic, is reduced.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
- Air-Flow Control Members (AREA)
Abstract
Description
Die Erfindung geht aus von einem Drehsteller nach der Gattung des Hauptanspruchs. Es ist schon ein Drehsteller bekannt (siehe z.B. WO 91/14090, US-A-2449833), bei dem es aber infolge von Wirbelbildungen, insbesondere bei Verwendung von Saugrohren und Saugrohranschlüssen aus Kunststoff, zu einer unerwünschten Geräuschentwicklung kommen kann.The invention relates to a rotary actuator according to the preamble of the main claim. A turntable is already known (see, for example, WO 91/14090, US-A-2449833), but in which undesirable noise can occur as a result of eddies, especially when using suction pipes and suction pipe connections made of plastic.
Der erfindungsgemäße Drehsteller mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß einer beim Durchströmen des Drehschiebergehäuses auftretenden störenden Geräuschentwicklung durch Verringerung der Wirbelbildung entgegengewirkt wird.The turntable according to the invention with the characterizing features of the main claim has the advantage that a disturbing noise that occurs when flowing through the rotary valve housing is counteracted by reducing the vortex formation.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Drehstellers möglich. Besonders vorteilhaft ist die Ausbildung einer parallel zur Strömungsrichtung liegenden Begrenzungsfläche und eines strömungsgünstigen Übergangs mit einem konkaven und sich daran anschließenden konvexen Bereich im Ausgangsstutzen des Drehschiebergehäuses, wodurch die beim Durchströmen des Drehschiebergehäuses auftretende Geräuschentwicklung weiter reduzierbar ist.The measures listed in the subclaims enable advantageous developments and improvements of the rotary actuator specified in the main claim. The formation of a boundary surface lying parallel to the direction of flow and a flow-favorable transition with a concave and adjoining convex area in the outlet port of the rotary valve housing, whereby the noise generated when flowing through the rotary valve housing can be further reduced.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch einen erfindungsgemäß ausgestalteten Drehsteller, Figur 2 eine Ansicht auf den Eingangsstutzen des Drehstellers und Figur 3 einen Schnitt gemäß Linie III-III in Figur 2.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. FIG. 1 shows a longitudinal section through a turntable designed according to the invention, FIG. 2 shows a view of the inlet connection of the turntable and FIG. 3 shows a section along line III-III in FIG. 2.
In Figur 1 ist ein Drehsteller 1 zur Regelung der Leerlaufdrehzahl einer Brennkraftmaschine gezeigt, der ein Drehschiebergehäuse 2 mit einer napfförmigen Aufnahmeöffnung 3 hat, in die ein Stellmotor 4 eingesetzt ist, der mit einem drehzahlabhängigen Steuersignal beaufschlagbar ist. Am Drehschiebergehäuse 2 sind seitlich ein Eingangsstutzen 5 und ein Ausgangsstutzen 6 ausgebildet, die in eine im Drehschiebergehäuse 2 koaxial zur Aufnahmeöffnung 3 verlaufende Bohrung 7 münden.In Figure 1, a
Der Stellmotor 4 des Drehstellers 1 ist über eine Welle 9, die beispielsweise in zwei Wälzlagern 10, 11 gelagert ist, mit einem Drehschieber 12 verbunden, der konzentrisch in der Bohrung 7 drehbar angeordnet ist, und eine dem Steuersignal des Stellmotors 4 entsprechende Drehwinkelstellung einnimmt. Im Bereich der Mündung des Eingangsstutzens 5 in die Bohrung 7 weist das Drehschiebergehäuse 2 eine Drosselöffnung 13 auf, die entsprechend einer Drehwinkelstellung des Stellmotors 4 vom Drehschieber 12 mehr oder weniger geschlossen wird. Der Drosselöffnung 13 gegenüberliegend ist in der Bohrung 7 eine Austrittsöffnung 14 angeordnet, die in den Ausgangsstutzen 6 mündet. Eingangsstutzen 5 und Ausgangsstutzen 6 sind über Anschlußleitungen 15, 16 mit einem Ansaugrohr 17 derart verbunden, daß sie eine Bypassleitung 18 bilden, die eine im Ansaugrohr 17 angeordnete Drosselklappe 19 umgeht, wobei bei geöffneter Drosselöffnung 13 das Betriebsmittel in der Bypassleitung 18 in Richtung des Pfeiles 20 zur Brennkraftmaschine strömen kann. Die Anschlußleitungen 15, 16 und das Ansaugrohr 17 können aus Metall und/oder Kunststoff hergestellt sein.The servomotor 4 of the
Der Eingangsstutzen 5 hat eine Längsachse 22 und der Ausgangsstutzen 6 hat eine Längsachse 23, die auf einer Linie liegen und rechtwinklig zur Welle 9 verlaufen. Dabei sind die Längsachsen 22, 23 seitlich so versetzt, daß sie an der Welle 9 vorbeilaufen und diese nicht schneiden (Fig. 3). Aus Gründen der Darstellbarkeit sind in Figur 1 der Eingangsstutzen 5 und der Ausgangsstutzen 6 in die Zeichenebene verschoben gezeigt.The
Der Strömungsquerschnitt der Bypassleitung 18 weist ab der Mündung der Anschlußleitung 15 in den Eingangsstutzen 5 in Strömungsrichtung gesehen eine leichte, kegelstumpfförmige Verengung 24 auf. In einem vor der Drosselöffnung 13 liegenden Abschnitt 21 des Eingangsstutzens 5 wird der Strömungsquerschnitt von ebenen, parallel zur Längsachse 22 verlaufenden Begrenzungsflächen 25 gebildet, die ein Viereck einschließen. Zwischen der kegelstumpfförmigen Verengung 24 und den Begrenzungsflächen 25 ist erfindungsgemäß ein stetiger, strömungsgünstiger Übergang vorgesehen. Ab der Austrittsöffnung 14 weist die Bypassleitung 18 bis zur Mündung des Ausgangsstutzen 6 in die Anschlußleitung 16 eine leichte, kegelstumpfförmige Erweiterung 27 auf.The flow cross-section of the
In Figur 2 ist erkennbar, daß die im Eingangsstutzen 5 befindliche Drosselöffnung 13 von zwei einander gegenüberliegenden längeren Begrenzungskanten 28 und zwei einander gegenüberliegenden kürzeren Begrenzungskanten 29 gebildet wird, die in bekannter Weise etwa rechteckförmig bzw. etwa parallelogrammförmig zueinander ausgebildet sind und schräg zur Achse der gepunktet angedeuteten Welle 9 liegen. Die Begrenzungsflächen 25 (Fig. 1) sind dabei so angeordnet, daß sie durch die entsprechenden Begrenzungskanten (28, 29) verlaufen und etwa parallel zueinander liegen. Die der Drosselöffnung 13 im Drehschiebergehäuse 2 gegenüberliegende, in Figur 2 gestrichelt angedeutete Austrittsöffnung 14 weist gegenüber der Drosselöffnung 13 einen größeren Querschnitt auf und hat an ihrer, der Welle 9 abgewandten Seite eine gerade Begrenzungskante 30, die etwa parallel zur Längsachse der Welle 9 verläuft. Außerhalb der geraden Begrenzungskante 30 hat die Austrittsöffnung 14 eine Begrenzungskante 31 mit einem gewölbten Verlauf, der beispielsweise in der Projektion kreisförmig sein kann.In Figure 2 it can be seen that the
Figur 3 zeigt die im Drehschiebergehäuse 2 angeordnete Bohrung 7, in der konzentrisch die Welle 9 angeordnet ist, mit der der Drehschieber 12 drehfest verbunden ist. Der Drehschieber 12 hat eine Außenfläche 33, die dem Durchmesser der Bohrung 7 entspricht und die Drosselöffnung 13 je nach Drehwinkelstellung der Welle 9 mehr oder weniger schließt, so daß die in Richtung des Pfeiles 20 strömende Betriebsmittelmenge durch Verdrehen der Welle 9 steuerbar ist. Durch Drehung der Welle 9 im Uhrzeigersinn kann der Strömungsquerschnitt an der Drosselöffnung 13 vollständig geöffnet werden, durch Drehung der Welle 9 entgegen dem Uhrzeigersinn kann der Strömungsquerschnitt an der Drosselöffnung 13 vollständig geschlossen werden.FIG. 3 shows the bore 7 arranged in the
Bei zumindest teilweise geöffneter Drosselöffnung 13 gelangt das Betriebsmittel über die kegelstumpfförmige Verengung 24 zur Drosselöffnung 13, wobei der Übergang auf den verkleinerten Strömungsquerschnitt der Drosselöffnung 13 ohne abrupte Querschnittsänderung in strömungsgünstiger Weise erfolgt. Der Eingangsstutzen 5 weist etwa in seinem ersten Drittel die kegelstumpfförmige Verengung 24 auf, an die sich ein Bereich 40 mit einem zur Längsachse 22 hin gewölbten konkaven Verlauf anschließt, der in einen Bereich 41 mit konvexem Verlauf übergeht. An den Bereich 41 schließt sich der Bereich 21 mit den ebenen Begrenzungsflächen 25 an, die durch die Begrenzungskanten 28, 29 verlaufen. Damit ergibt sich ein etwa S-förmiger Verlauf des Überganges von der kegelstumpfförmigen Verengung 24 zu den Begrenzungsflächen 25. Ab etwa dem letzten Drittel der Länge des Eingangsstutzens 5 wird der Strömungsquerschnitt durch die einander gegenüberliegenden Begrenzungsflächen 25 begrenzt, die jeweils durch die längeren Begrenzungskanten 28 verlaufen. Die den kürzeren Begrenzungskanten 29 zugeordneten Begrenzungsflächen 25 können in Strömungsrichtung gesehen kürzer als etwa ein Drittel der Länge des Eingangsstutzens 5 sein.When the
Ab der Austrittsöffnung 14 verläuft der Ausgangsstutzen 6 ausgehend von der geraden Begrenzungskante 30 in Strömungsrichtung gesehen zunächst entlang einer die Begrenzungskante 30 berührenden ebenen Begrenzungsfläche 26, die etwa parallel zur Längsachse 23 gerichtet ist. Nach etwa einem Drittel seiner Länge hat der Ausgangsstutzen 6 in einem Bereich 42 einen von der Längsachse 23 weg gewölbten konvexen Verlauf, so daß sich der Strömungsquerschnitt im Bereich 42 in Strömungsrichtung zunehmend erweitert. Anschließend an den Bereich 42, etwa nach der Hälfte der Länge des Ausgangsstutzens 6 schließt sich ein entgegen der Längsachse 23 des Ausgangsstutzens 6 gewölbter konkaver Bereich 43 an, so daß sich der Strömungsquerschnitt im Bereich 43 in Strömungsrichtung gesehen abnehmend erweitert. An den Bereich 43 grenzt die sich etwa über das letzte Drittel des Ausgangsstutzens 6 erstreckende, kegelstumpfförmige Erweiterung 27 an.Starting from the outlet opening 14, starting from the
Außerhalb der geraden Begrenzungskante 30 beginnt die kegelstumpfförmige Erweiterung 27 direkt an der kreisförmigen Begrenzungskante 31. Sämtliche Längenangaben beziehen sich dabei jeweils auf die in der Zeichnung dargestellte Schnittebene. Außerhalb dieser Schnittebene verkürzen sich die Längen der Übergänge entsprechend ihrem Abstand von einer der Längsachsen 22, 23.Outside the
Durch die erfindungsgemäße Ausgestaltung des Strömungsverlaufs im Drehsteller ergibt sich eine geringere Verwirbelung des Betriebsmittels, wodurch die Geräuschentwicklung, insbesondere bei Saugrohren und Saugrohranschlüssen aus Kunststoff, verringert wird.The configuration of the flow profile in the rotary actuator according to the invention results in less swirling of the operating medium, as a result of which the noise development, in particular in the case of suction pipes and suction pipe connections made of plastic, is reduced.
Claims (5)
- Rotating actuator, in particular a rotating actuator for controlling a throttling cross-section of an internal combustion engine flow conduit carrying an operating medium, with a housing (2) and an actuating motor (4) which, by way of a shaft (9), drives a rotary slide (12) which acts as a throttling element, is arranged centrally in a hole (7) of the housing (2) and can be rotated, the operating medium to be controlled passing through an inlet branch (5) with a quadrilateral throttling opening (13) with in each case two mutually opposite longer boundary edges (28) and shorter boundary edges (29) and via an outlet opening (14) into an outlet branch (6), and the inlet branch (5) and the outlet branch (6) have longitudinal axes (22, 23) which lie on one line, characterized in that, in the upstream direction, starting from the throttling opening (13) the inlet branch has formed in it at least two boundary surfaces (25) which run through the mutually opposite longer boundary edges (28) and are arranged parallel to the longitudinal axis (22) of the inlet branch (5), and the transitions of the flow cross-section from the boundary surfaces (25) to the upstream part of the inlet branch (5) are each formed by a convex region (41) arching away from the longitudinal axis (22) and an adjoining concave region (40) arching towards the longitudinal axis (22).
- Rotating actuator according to Claim 1, characterized in that a frustoconical constriction (24) extending in the direction of flow is provided in the inlet branch (5) directly upstream of the concave region (40).
- Rotating actuator according to Claim 1, characterized in that the outlet opening (14) has a straight boundary edge (30) through which there runs a boundary surface (26) running parallel to the longitudinal axis (23) of the outlet branch (6), and the transition to the flow cross-section of the outlet branch (6) is formed by a convex region (42) arching away from the longitudinal axis (23) and an adjoining concave region (43) arching towards the longitudinal axis (23).
- Rotating actuator according to Claim 3, characterized in that a frustoconical widening (27) running in the direction of flow is provided in the outlet branch (6) directly downstream of the concave region (43).
- Rotating actuator according to Claim 4, characterized in that the outlet opening (14) is bounded to the outside of the straight boundary edge (30) by a boundary edge (31) which is circular in its projection, and the frustoconical widening (27) of the outlet branch (6) emanates from this circular boundary edge (31).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4227951A DE4227951A1 (en) | 1992-08-22 | 1992-08-22 | Turntable |
| DE4227951 | 1992-08-22 | ||
| PCT/DE1993/000687 WO1994004811A1 (en) | 1992-08-22 | 1993-08-05 | Rotating actuator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0609408A1 EP0609408A1 (en) | 1994-08-10 |
| EP0609408B1 true EP0609408B1 (en) | 1996-11-20 |
Family
ID=6466216
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP93915687A Expired - Lifetime EP0609408B1 (en) | 1992-08-22 | 1993-08-05 | Rotating actuator |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5476246A (en) |
| EP (1) | EP0609408B1 (en) |
| JP (1) | JPH07500658A (en) |
| DE (2) | DE4227951A1 (en) |
| WO (1) | WO1994004811A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103917772A (en) * | 2011-11-07 | 2014-07-09 | 株式会社三国 | Flow control valve |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6026845A (en) * | 1996-04-24 | 2000-02-22 | Bighorn Valve, Inc. | Flow, split Venturi, axially-rotated valve |
| US6109293A (en) | 1996-04-24 | 2000-08-29 | Big Horn Valve, Inc. | Split venturi, axially-rotated valve |
| FR2814501B1 (en) * | 2000-09-25 | 2002-12-27 | Internova Int Innovation | AIR INTAKE DEVICE FOR A HEAT ENGINE |
| CN100366965C (en) * | 2001-07-10 | 2008-02-06 | 日本电产三协株式会社 | Valve drive device |
| JP2006057763A (en) * | 2004-08-20 | 2006-03-02 | Nidec Sankyo Corp | Valve driving device |
| GB2430992A (en) * | 2005-10-05 | 2007-04-11 | South Bank Univ Entpr Ltd | Rotary plug valve |
| ITBS20060221A1 (en) * | 2006-12-18 | 2008-06-19 | Enolgas Bonomi S P A | INTERCEPTING VALVE |
| JP2009115271A (en) * | 2007-11-09 | 2009-05-28 | Yamatake Corp | Flow rate measurement valve |
| CN102740810B (en) * | 2010-01-29 | 2015-06-17 | 医研比赫国际股份公司 | A drainage valve and a collection bag assembly comprising said valve |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2449833A (en) * | 1945-09-11 | 1948-09-21 | Julius L Barnes | Valve |
| DE3926910A1 (en) * | 1989-08-16 | 1991-02-21 | Bosch Gmbh Robert | IDLE TURNTABLE |
| DE4007260A1 (en) * | 1990-03-08 | 1991-09-12 | Bosch Gmbh Robert | Rotating flow control valve |
-
1992
- 1992-08-22 DE DE4227951A patent/DE4227951A1/en not_active Withdrawn
-
1993
- 1993-08-05 JP JP6505748A patent/JPH07500658A/en active Pending
- 1993-08-05 EP EP93915687A patent/EP0609408B1/en not_active Expired - Lifetime
- 1993-08-05 DE DE59304542T patent/DE59304542D1/en not_active Expired - Lifetime
- 1993-08-05 WO PCT/DE1993/000687 patent/WO1994004811A1/en active IP Right Grant
- 1993-08-05 US US08/211,126 patent/US5476246A/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103917772A (en) * | 2011-11-07 | 2014-07-09 | 株式会社三国 | Flow control valve |
| CN103917772B (en) * | 2011-11-07 | 2016-10-26 | 株式会社三国 | Flow control valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07500658A (en) | 1995-01-19 |
| WO1994004811A1 (en) | 1994-03-03 |
| US5476246A (en) | 1995-12-19 |
| DE4227951A1 (en) | 1994-02-24 |
| EP0609408A1 (en) | 1994-08-10 |
| DE59304542D1 (en) | 1997-01-02 |
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