WO2012089501A1 - Soupape de commande de débits volumétriques - Google Patents

Soupape de commande de débits volumétriques Download PDF

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Publication number
WO2012089501A1
WO2012089501A1 PCT/EP2011/072664 EP2011072664W WO2012089501A1 WO 2012089501 A1 WO2012089501 A1 WO 2012089501A1 EP 2011072664 W EP2011072664 W EP 2011072664W WO 2012089501 A1 WO2012089501 A1 WO 2012089501A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
bypass
spring
coolant
bypass valve
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.)
Ceased
Application number
PCT/EP2011/072664
Other languages
German (de)
English (en)
Inventor
Nizar Taghouti
Georg Reeb
Harald Merz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2012089501A1 publication Critical patent/WO2012089501A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16K31/002—Actuating devices; Operating means; Releasing devices actuated by temperature variation
    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • 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
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F16K27/044—Construction of housing; Use of materials therefor of sliding valves slide valves with flat obturating members
    • F16K27/045—Construction of housing; Use of materials therefor of sliding valves slide valves with flat obturating members with pivotal obturating members
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/04—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members
    • F16K3/06—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages
    • F16K3/08—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages with circular plates rotatable around their centres

Definitions

  • Valve for controlling volume flows
  • the invention relates to a valve for controlling volume flows according to the preamble of the independent claim.
  • a cooling or heating circuit of a motor vehicle generally includes a heat source to be cooled, for example an internal combustion engine of a
  • Heat input of the heat source, the heat dissipation of any, located in the cooling circuit radiator elements and the heat capacity of the materials involved is determined.
  • a coolant is circulated in the motor vehicle, the excess heat energy of
  • Internal combustion engine absorbs and dissipates to the desired extent.
  • the heating or cooling circuit of a motor vehicle usually includes various sub-circuits, such as a cooler branch, a bypass branch and / or a Schuungs Scrileyerzweig. About an im
  • Radiator branch mounted radiator or radiator can be the superfluous
  • Amount of heat of the coolant are discharged to the ambient air.
  • a heating heat exchanger makes the available Quantity of heat of the coolant used to heat the passenger compartment.
  • the distribution of the coolant flow to the various branches of the cooling or heating circuit is usually controlled by at least one valve.
  • an electric motor is arranged in the control valve, which adjusts the position of a valve disc via a worm gear so that a desired coolant flow flows through the control valve.
  • the electric motor is not separated from the coolant flow, so that the
  • Components of the electric motor such as the rotor and the transmission, with
  • Coolants are flooded.
  • valve body is disc-shaped and a plurality of
  • valve disc of US 5, 950, 576 is by means of a shaft via a
  • Combustion engine control unit provided.
  • Valve disc by sealing elements in the form of sealing rings, as well as with
  • Adjustment of the valve disc is no longer possible, so that they can not assume a defined position. Therefore it can happen that the
  • valve disc with which a circulation of the coolant is given even in case of failure of the supply voltage.
  • the valve for controlling volume flows of a coolant in a heating and / or cooling system of a motor vehicle has a valve housing with at least one inlet channel and at least one outlet channel. At least one valve disc rotatably disposed about the axis of a shaft is present in the valve housing, which influences the connection between the at least one inlet channel and the at least one outlet channel of the valve.
  • a bypass channel and a bypass valve are further arranged, via which the at least one inlet channel and the at least one outlet channel in the event of overheating of the coolant can be connected to each other.
  • the bypass valve is designed as a spring-biased valve in which, in the case of overheating of the coolant, the spring preload is released and thereby the bypass valve can be moved automatically from a closed to an open position.
  • this results in the possibility of an instantaneous reaction in the event of overheating, while conventional thermally controlled devices either delayed or not at all respond to rising temperatures of the internal combustion engine, since they are not thermally coupled optimally to the system.
  • solenoid valves with an adjustment in the order of about 4 mm also a very low energy and space requirements for the bypass valve according to the invention can be achieved.
  • a return mechanism driven by the valve disc spends the bypass valve back into its closed position, so that the spring bias is applied to the bypass valve.
  • the application of the spring preload takes place until a
  • An unlocking pin holds the bypass valve in the closed position, wherein an addressable via a magnetic circuit armature, which is rigidly connected to the unlocking pin, the unlocking pin in the case of
  • Trigger mechanism requires only a very small triggering path.
  • the force required for the unlocking pin is very low, so that a necessary magnetic circuit is very small, easy and inexpensive to implement. Since this magnetic circuit can be activated via a short trigger pulse, the energy requirement for the bypass valve according to the invention drops to almost zero.
  • the unlocking pin engages in an opening of a rigidly connected to a valve disk of the bypass valve valve piston, to which the
  • unlocking pin holds a spring biased toggle lever, which is operatively connected to a valve plate of the bypass valve, in a defined position, so that the toggle can buckle in the case of release by the release pin.
  • bypass valve is designed as a rotary slide valve, the unlocking pin holding the spring-biased rotary valve in the closed position, and the rotary valve in case of release by the unlocking pin as a result of acting through a pivot spring preload by means of a rotary motion opens around the fulcrum.
  • the rotary valve can also be
  • Linear slide valve are used, which operates accordingly.
  • Fig. 1 shows a first embodiment of a valve in a
  • FIG. 3 shows a second embodiment of the valve of Figure 1 in a further sectional view
  • FIG. 6 is a schematic representation of a second embodiment of the bypass valve according to the invention.
  • FIG. 7 is a schematic representation of a third embodiment of the bypass valve according to the invention.
  • Fig. 8 is a schematic representation of a fourth embodiment of the bypass valve according to the invention.
  • Fig. 1 shows an example of a valve 1 in an overview.
  • the valve 1 according to the embodiment in Fig. 1 has a housing 10 with a
  • the lower housing part 12 is substantially cup-shaped, as shown in Figures 2 and 3, and allows in its interior the formation of a valve chamber for receiving a valve element.
  • the upper housing part 14 may also be cup-shaped or merely be formed as a kind of cover in the lower housing part 12. Formed on the housing base 12 is the neck of a
  • the inlet channel 18 or the nozzle can in particular be integrally formed with the housing lower part 12, for example, be formed in plastic.
  • valve 1 Inlet duct 18 and the first and second outlet channel 20, 22 are opened, closed and varied as desired.
  • valve 1 still has an actuator 24 for adjusting the valve element, which will be described in more detail in connection with FIG. 3 and its own Drive housing 25 which is bolted to the housing 10, in particular the housing upper part 14 of the valve 1.
  • Fig. 2 shows a first section through the valve 1, which extends approximately perpendicular to the plane of the drawing of FIG.
  • a valve disc 28 is arranged as a valve element.
  • An output shaft 30 of the actuator 24 shown in more detail in Fig. 3 engages in a central opening 32 of the valve disc 28 a.
  • the valve disc 28 is rotatably mounted on the output shaft 30, so that this shaft as the drive shaft of
  • Valve disc 28 is used.
  • the securing of the valve disk on the shaft 30 can be effected for example by a screw connection or latching shown in FIG. 2, or else by a compression of the shaft 30 in the central opening 32 of the valve disk 28.
  • sealing means for example a sealing ring 36, are provided between the lower housing part 12 and the upper housing part 14, sealing means, for example a sealing ring 36, are provided in order to provide a fluid-tight connection between the two housing parts 12, 14 of the valve housing 10
  • Fig. 3 shows a second schematic sectional view of the valve 1 in a further embodiment.
  • Outlet ducts 20 are arranged offset from one another here.
  • the rotor 38 has a rotor shaft 42, on which a worm gear 44 is arranged in a first region and a laminated core 46 in a second region.
  • Sheet metal of the laminated core 46 while radially comprise the rotor shaft 42 and are limited axially by two sheet metal sleeves 48.
  • the laminated core 46 at least one magnet 50 is arranged.
  • the laminated core 46 is in its spatial
  • Helical gear 44 through a radial bearing receptacle 54 and the therein arranged first radial bearing element 56 separated.
  • Bearing elements 58, 60 rest, in this case have a higher degree of hardness than the other surfaces of the rotor shaft 42.
  • the axial bearing elements 58, 60 are plate-shaped, wherein the first axial bearing element 58 in the
  • the rotor 38 has at the ends of the rotor shaft 42 in each case a starting mushroom 64, which serves to support the bearing forces on the axial bearing elements 58, 60.
  • the stator 40 has at least one coil 62 with a plurality of windings and laminated cores, not shown.
  • the coils 62 generate a voltage applied to the magnetic field, which the rotor 38 in rotation around the
  • the coils 62 can in this case with
  • AC voltage can be operated or electronically commutated.
  • the valve disk 28 has at least one opening 70, wherein the opening 70 is rotated in front of the outlet channel 20 by rotating the valve disk 28. Depending on the position of the opening 70 in front of the outlet channel 20, the flow area of the valve disc 28 is regulated.
  • the opening 70 is arranged offset with its longitudinal axis to the axis of rotation 31 of the shaft 30 and the valve disc 28.
  • valve housing 10 in particular in the upper housing part 14, a bypass channel 72 and a bypass valve 74 are arranged between the inlet channel 18 and the outlet channel 20, not shown, via which the inlet channel 18 and the outlet channel 20 in the event of overheating of the coolant can be connected to each other.
  • bypass valve 74 Normal operation, the bypass valve 74 is closed ( Figures 4a and 4b). A valve disk 76 of the bypass valve 74 which is connected to a valve piston 75 and has a flexible valve seal 77 is displaced into a sealing seat 78 in accordance with FIG. If the coolant due to a blocking of the valve disc 28 in closed condition overheated, the bypass valve 74 is opened according to FIG. 4c, so that the coolant can flow through the bypass channel 72 into the outlet channel 20.
  • a return mechanism 80 for the bypass valve 74 comprises a rotationally fixed to the shaft 30 of the valve 1 verbünd enen driver 82.
  • the driver 82 has a radial bulge 84, which outside the control range of the valve 1 to a displacement of the return mechanism 80 in the direction of Bypass valve 74 leads.
  • a spring element 86 in particular a spiral spring 88, presses the return mechanism 80 against the driver 84 in order to ensure a permanent frictional contact between the return mechanism 80 and
  • Control range " is understood that the opening 70 of the valve disc 28 is in a position in which the volume flow of the coolant between
  • Inlet port 18 and outlet port 20, 22 is interrupted.
  • Fig. 5 shows a first embodiment of the bypass valve 74 according to the invention.
  • the bypass valve 74 is shown in the closed position and in Fig. 5b in the open position.
  • the connection to the bypass channel 72 of the valve 1 is effected by means of acting on the valve plate 76 spring 92, in particular an axially acting coil spring, a leaf spring or the like, a spring bias of the bypass valve 74 in the closed state (ie the valve seal 77 rests in the sealing seat 78).
  • the valve piston 75 which is rigidly connected to the valve disk 76, is held in the closed position of the bypass valve 74 via an opening 94 provided therein and an unlocking pin 96 engaging therein during normal operation of the valve 1.
  • bypass valve 74 If there is an overheating of the coolant, the bypass valve 74 is moved from its closed to the open position for the emergency operation of the valve 1, so that the coolant via the bypass channel 72 in the outlet channel 20, 22 can flow.
  • a magnetic circuit 102 consisting of a winding element 98 and a magnetic armature 100 is briefly actuated by means of a voltage pulse such that the magnet armature 100 rigidly connected to the unlocking pin 96 releases the opening 94 of the valve armature 75, so that the valve disk 76 opens in accordance with FIG Fig. 5b moves due to the spring bias of the spring 92 automatically from the closed to the open position.
  • the bypass valve 74 can be returned to its closed position by means of the return mechanism 80. Due to the spring force of the force acting on the armature 100 spring 104, the unlocking pin 96 can then engage again in the opening 94 of the valve piston 75 and the bypass valve 74 in the
  • FIG. 6 An alternative embodiment of the bypass valve 74 according to the invention is shown in FIG. 6. Instead of an opening in the valve piston 75, the latter is now connected via a valve
  • the unlocking pin 96 prevents buckling of the toggle lever 106 in the closed state of the bypass valve 74 in normal operation of the valve 1.
  • the unlocking pin 96 is retracted by the magnetic circuit 102 so that the toggle lever 102 may buckle and the bypass valve 74 due to Spring bias of the spring 92 from its closed (Fig. 6a) in the open position (Fig. 6b) slides.
  • a movement of the bypass valve 74 in its closed state then takes place again in the normal operation of the valve 1 via the return mechanism 80th
  • Fig. 7 illustrates an alternative to the toggle lever 106 by being replaced by a bending spring 108. However, the operation is identical to that of the toggle lever 106, so that should be dispensed with a more detailed description.
  • bypass valve 74 as a
  • Rotary valve 110 with a rotatable about an axis of rotation 112
  • Spring bias of a spring 112 in particular a tangentially acting spiral spring, a scroll spring or the like, standing valve plate 114 in the opening 90 to the bypass channel 72 occlusive position.
  • the rotary valve valve 110 opens due to acting on the pivot point of the axis of rotation 112
  • Valve plate 114 acts. Instead of the rotary valve can also be
  • Linear slide valve are used, which operates accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne une soupape (1) servant à commander des débits volumétriques d'un fluide de refroidissement dans un système de chauffage et/ou de refroidissement d'un véhicule à moteur, comprenant un carter de soupape (10, 12, 14, 25) pourvu d'au moins un canal d'entrée (18) et d'au moins un canal de sortie (20, 22), ledit carter de soupape (10, 12, 14) abritant au moins un disque de soupape (28) qui est monté rotatif autour de l'axe (31) d'un arbre (30) et qui influe sur la liaison entre ledit au moins un canal d'entrée (18) et ledit au moins un canal de sortie (20, 22) de la soupape (1). Un canal de dérivation (72) et une soupape de dérivation (74, 110) sont agencés dans le carter de soupape (10, 12, 14) entre ledit au moins un canal d'entrée (18) et ledit au moins un canal de sortie (20, 22) et permettent de raccorder ces derniers en cas de surchauffe du fluide de refroidissement. Selon l'invention, la soupape de dérivation (74, 110) se présente sous la forme d'une soupape précontrainte par un ressort, la précontrainte du ressort étant relâchée en cas de surchauffe du fluide de refroidissement, ce qui permet à la soupape de dérivation (74, 110) de passer automatiquement d'une position fermée à une position ouverte.
PCT/EP2011/072664 2010-12-29 2011-12-13 Soupape de commande de débits volumétriques Ceased WO2012089501A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010064309A DE102010064309A1 (de) 2010-12-29 2010-12-29 Ventil zur Steuerung von Volumenströmen
DE102010064309.2 2010-12-29

Publications (1)

Publication Number Publication Date
WO2012089501A1 true WO2012089501A1 (fr) 2012-07-05

Family

ID=45350761

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/072664 Ceased WO2012089501A1 (fr) 2010-12-29 2011-12-13 Soupape de commande de débits volumétriques

Country Status (2)

Country Link
DE (1) DE102010064309A1 (fr)
WO (1) WO2012089501A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5950576A (en) 1998-06-30 1999-09-14 Siemens Canada Limited Proportional coolant valve
US20030070714A1 (en) * 2001-10-11 2003-04-17 Eaton Corporation Servo operated rotary valve with emergency bypass and method of making same
DE102006053307A1 (de) 2006-11-13 2008-05-15 Robert Bosch Gmbh Ventil zur Steuerung von Volumenströmen
DE102006053310A1 (de) 2006-11-13 2008-05-15 Robert Bosch Gmbh Ventil zur Steuerung von Volumenströmen
DE102008029706A1 (de) * 2008-06-24 2009-12-31 Murrplastik Systemtechnik Gmbh Ventil zur Steuerung eines Fluidstroms in einer Kraftfahrzeug-Heizungs- und/oder Klimaanlage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5950576A (en) 1998-06-30 1999-09-14 Siemens Canada Limited Proportional coolant valve
US20030070714A1 (en) * 2001-10-11 2003-04-17 Eaton Corporation Servo operated rotary valve with emergency bypass and method of making same
DE102006053307A1 (de) 2006-11-13 2008-05-15 Robert Bosch Gmbh Ventil zur Steuerung von Volumenströmen
DE102006053310A1 (de) 2006-11-13 2008-05-15 Robert Bosch Gmbh Ventil zur Steuerung von Volumenströmen
DE102008029706A1 (de) * 2008-06-24 2009-12-31 Murrplastik Systemtechnik Gmbh Ventil zur Steuerung eines Fluidstroms in einer Kraftfahrzeug-Heizungs- und/oder Klimaanlage

Also Published As

Publication number Publication date
DE102010064309A1 (de) 2012-07-05

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