EP1835142A2 - Agencement de vannes, en particulier destiné à l'installation d'un courant de moyen de chauffage/refroidissement dans un véhicule automobile - Google Patents

Agencement de vannes, en particulier destiné à l'installation d'un courant de moyen de chauffage/refroidissement dans un véhicule automobile Download PDF

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Publication number
EP1835142A2
EP1835142A2 EP07004175A EP07004175A EP1835142A2 EP 1835142 A2 EP1835142 A2 EP 1835142A2 EP 07004175 A EP07004175 A EP 07004175A EP 07004175 A EP07004175 A EP 07004175A EP 1835142 A2 EP1835142 A2 EP 1835142A2
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
line
connection position
connection
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.)
Granted
Application number
EP07004175A
Other languages
German (de)
English (en)
Other versions
EP1835142A3 (fr
EP1835142B1 (fr
Inventor
Michael Humburg
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.)
Eberspaecher Climate Control Systems GmbH and Co KG
Original Assignee
J Eberspaecher GmbH and Co KG
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 J Eberspaecher GmbH and Co KG filed Critical J Eberspaecher GmbH and Co KG
Priority to PL07004175T priority Critical patent/PL1835142T3/pl
Publication of EP1835142A2 publication Critical patent/EP1835142A2/fr
Publication of EP1835142A3 publication Critical patent/EP1835142A3/fr
Application granted granted Critical
Publication of EP1835142B1 publication Critical patent/EP1835142B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105—Using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2050/00—Applications
    • F01P2050/22—Motor-cars
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/08—Cabin heater

Definitions

  • the present invention relates to a valve arrangement, in particular for adjusting a heating medium / coolant flow in a motor vehicle, comprising a first valve member, which is adjustable in response to a prevailing between a first line and a second line pressure difference between a first connection position and a second connection position , As well as a second valve member which varies depending on the temperature flow through the first valve member, wherein when positioning the first valve member in the second connection position, a flow connection between the first conduit and a third conduit is substantially released and when positioning the first valve member in the first connection position the Flow connection between the first line and the third line is temperature-dependent variable from the second valve member.
  • FIG. 1 shows schematically the structure of this known valve assembly or its integration into the heating / cooling system of a vehicle.
  • the generally designated 10 valve assembly is connected via three in Fig. 1 only schematically indicated lines 12, 14, 16 in connection with the overall system 18.
  • the first line 12 establishes a connection between the valve assembly 10 and the coolant jacket of an internal combustion engine 20 ago.
  • the second line 14 establishes a connection between the valve arrangement 10 and a heat exchanger 22, in which heat can be transmitted to the air to be introduced into the vehicle interior.
  • the valve assembly 10 is in communication with the heat exchanger portion 24 of a fuel heater to be operated vehicle heater 26.
  • this heat exchanger assembly 24 performs another Line 28 away, in the direction of the heat exchanger 22 leading to the second line 14.
  • From the heat exchanger 22 performs a line 30 away.
  • this line 30 branches into a line 34 which leads via a check valve 36 and a line 37 to the third line 16 and thus also to the heat exchanger portion 24 of the vehicle heater 26, and in a line 38, which leads to the drive unit or the internal combustion engine 20 and the coolant jacket thereof leads.
  • the feed pump 40 is associated with the vehicle heater 26 and conveys the incoming fluid from the lines 16 and 37 via the line 28 and the line 14 to the heat exchanger 22.
  • the feed pump 42 is associated with the coolant jacket of the internal combustion engine 20 and promotes that via the line 30 and the line 38 incoming fluid into the conduit 12 and thus to the valve assembly 10th
  • the valve assembly 10 shown only schematically includes slidably received in a valve housing 44, a first valve member 46. This can be moved between the first connection position shown in FIG. 1 by a solid line and the second connection position shown in Fig. 1 with a dashed line. This shift takes place under the pressures prevailing at the two end regions of the valve housing 44, ie primarily in the lines 12 and 14, or the pressure difference that arises. If the pressure P1 in the second line 14 is higher than the pressure P2 in the first line 12, then the first valve member 46 moves into the first connecting position shown by a solid line or remains in this connecting position. If the pressure P2 in the first line 12 is higher than the pressure P1 in the second line 14, the first valve member 46 moves in the second connecting position drawn with dashed lines.
  • a second valve member 48 is further included in the first valve member 46. This can shift in the first valve member 46, between the illustrated in Fig. 1 by a solid line first bridging position and the illustrated in Fig. 1 with dashed line second bridging position.
  • the displacement of the second valve member 48 in the first valve member 46 between its two bridging positions is temperature-dependent.
  • a thermally active actuator such as a built-up of shape memory material element exists, which at above a certain switching temperature increasing temperature in the region of the first valve member 46 and the second valve member 48 of this second valve member 48 against the biasing force a return spring moves from the first bridging position shown by a solid line in the shown in dashed line second bridging position. If the temperature drops below the switching temperature again, the second valve member 48 moves back into the first bridging position.
  • this system 18 is as follows: If at a first start or cold start first the feed pump 40 is put into operation and also the vehicle heater 26 is activated, then the fluid which absorbs heat in the heat exchanger area 24 is transferred by the conveying action of the feed pump 40 the line 28 delivered. It also passes via the line 14 into the interior of the valve housing 44, so that there on the one hand, a certain pressure P1 is generated, which acts on the first valve member 46 in the direction of its first connection position. On the other hand, the above-mentioned thermally active actuating element, which is responsible for the movement of the second valve member 48, comes into contact with this increasingly warming fluid.
  • the temperature is not sufficiently high, that is still below the switching temperature, so that the second valve member 48 is in its first bridging position.
  • the funded by the feed pump 40 fluid flows through the heat exchanger 22 and passes through the line 30, the line 34, the check valve 36 and the line 37 back to the feed pump 40 and the heat exchanger area 24. Since in this phase of operation, the feed pump 42 is not operated and thus the pressure P2 generated in the line 12 is below the pressure P1, the first valve member 46 assumes the already mentioned first connection position. In this first connection position, the connection between the first line 12 and the third line 16 is blocked due to the fact that the second valve element 48 is also in its first bridging position shown by a solid line, whereby possibly a certain leakage flow may be present.
  • the fluid which is increasingly heated in the heater 26, flows primarily only via the heat exchanger 22 and thus contributes to heating the air to be conducted into the vehicle interior and thus preheating the vehicle interior.
  • the fluid After a certain period of time, the fluid reaches a sufficiently high temperature and has sufficiently heated the region of the first valve member or the thermally active element present there, so that the latter will move the second valve member 48 to its second bridging position shown by a dotted line in FIG ,
  • the first valve member 46 remains due to the initially still unchanged pressure conditions in its first connection position.
  • the flow connection between the first line 12 and the third line 16 is then basically released, so that when the feed pump 42 is still not activated, the coolant jacket of the internal combustion engine 20 is released for flow through.
  • a flow connection between the two lines 12 and 14 possibly interrupted except for a leakage flow explained below.
  • the still circulating fluid so for example water or other liquid coolant, enter from the line 12 into the valve housing 44 and there will branch into a partial flow, via the line 16 and the deactivated feed pump 40 to the second line 14th enters, as well as in a partial flow, which passes through the addressed leakage path through the first valve member 46 directly to the second line 14.
  • a valve arrangement in particular for adjusting a heating medium / coolant flow in a motor vehicle, comprising a first valve member which, depending on a second valve member, the temperature dependent on the flowability of the first valve member changes, wherein positioning of the first valve member in the second connection position, a flow connection between the the first line and a third line is substantially released and when positioning the first valve member in the first connection position, the flow connection between the first line and the third line is temperature-dependent changed by the second valve member; characterized by a bypass flow path which, when the first valve member is positioned in the second connection position, provides a temperature-independent flow connection between the first line and the second line.
  • valve arrangement according to the invention it is therefore ensured that even when the first valve member is in its second connecting position, a leakage flow is made possible, specifically independently of the prevailing temperatures. This is particularly important in incorporation of such a valve arrangement into a system as described above with reference to FIG. 1, since in the phase in which only the feed pump associated with the internal combustion engine is operated, a flow path with a comparatively small throttle effect can be provided.
  • valve arrangement according to the invention can be distinguished by a valve housing which displaceably receives the first valve member between the first connection position and the second connection position, the bypass flow path comprising a channel arrangement which leads past the first valve member when positioned in the second connection position.
  • valve housing has a first housing member receiving the first valve member in positioning in the first connection position, the inner dimension substantially corresponds to the outer dimension of the first valve member, and receiving the first valve member when positioned in the second connection position second housing portion, which has a larger inner dimension than the outer dimension of the first valve member to provide the channel arrangement.
  • a guide arrangement for guiding the first valve member into and out of the second connection position is provided in the second housing section.
  • the guide arrangement comprises a plurality of guide projections provided on the second housing section.
  • the channel arrangement can then be formed between these guide projections.
  • a biasing arrangement is provided for biasing the first valve member in the first connection position.
  • the present invention further relates to a vehicle heating system comprising a valve arrangement according to the invention, wherein the first line establishes a connection between the coolant jacket of a drive unit and a valve housing of the valve arrangement, the second line establishes a connection between the valve housing and a coolant heat exchanger and the third line connects between the valve housing and a heat exchanger area of a vehicle heater manufactures.
  • Fig. 2 can be seen the essential for the explanation of the present invention system areas of generally designated 18 in Fig. 1 heating system, namely the valve assembly 10, the heat exchanger portion 24 of the heater 26 and the feed pump 40.
  • the others, not in Fig. 2 System areas shown further, may be constructed or cooperate with each other, as shown in Fig. 1 and already described generally with reference to FIG. 1.
  • the valve housing 44 which, as explained below, here two housing sections 50, 52 has. Both housing sections 50, 52 are substantially tube-like, but have the difference that they provide different internal dimensions.
  • the first valve member 46 is positioned when it is in its first connection position, this first connection position is substantially predetermined by an annular housing portion 54 provided in the housing portion 50.
  • a biasing spring 56 presses the first valve member 56 into abutment therewith Investment area 54.
  • the first valve member 46 is substantially formed as a hollow body and has an opening 58 on its front side facing the first conduit 12. This is basically closed by the second valve member 48.
  • a provided in the first valve member 48 biasing spring 60 which is supported on a support member 62 also provided in the first valve member 46, presses the second valve member in its first bridging position, that is the position in which the opening 58 is closed.
  • the support element 62 Since the support element 62 is open, the fluid flowing in through the line 28 or the line region 14 provided here for example as part of the second housing section 52 and heated in the heat exchanger region 24 can enter the interior of the first valve element 46 and thus into heat transfer contact with a helical spring-like manner trained temperature-sensitive actuator 64 come. This has due to its shape memory property on a certain switching temperature, the exceeding of which has the consequence that it expands to move the second valve member 48 against the biasing action of the spring 56 in its second bridging position. In this second bridging position, the opening 58 is then released so that through the interior of the first valve member 46 and through one or more provided in the first valve member 46 openings 66 then the fluid from the first conduit 12 into the third conduit 16 and thus to the feed pump 40 can flow.
  • the second valve member 48 Since in the second bridging position, the second valve member 48 is axially supported on the support member 62, but no tight completion of the openings provided in the support member 62 is generated, also in this phase, a flow possibility for the supplied via the line 28 fluid is still present. Also, the fluid flowing in via the first conduit 12 may flow into the conduit 14 through the interior of the first valve member 46, which, upon activation of the delivery pump 42 seen in FIG. 1, will increase due to the fact that the pressure P2 will exceed the pressure P1. also the case will be.
  • This bypass flow path establishes a connection between the first line 12 and the second line 14 or the line 28.
  • This connection via the bypass flow path 68 or the channel arrangement 70 is always given when positioning the first valve member 46 in its second connecting position, regardless of whether the second valve member 48 is in its first bridging position, as shown in FIG. or in its second bridging position, so through the interior of the first Ventilorgangs 46 through an additional flow path is created.
  • valve arrangement 44 with the bypass flow path 68 has the result that when the feed pump 42 is in operation and the pressure P2 exceeds the pressure P1, a significantly larger proportion of the pumped fluid via the second line 14 to the heat exchanger 22 passes and not via the feed pump 40 and the heat exchanger region 24th flows into the conduit 28. This is especially advantageous in those operating phases in which the setpoint operating temperature is reached and the feed pump 40 is no longer operated.
  • additional flow path namely on the channel assembly 70, created so that a much more efficient flow through the entire system is obtained.
  • this bypass flow path 68 can be provided by the valve housing 44 being designed to widen. While the first housing portion 50 is dimensioned so that it can absorb and guide the first valve member 46, but with the least possible loss of leakage, the second housing portion 52 adjoining, for example, in a stepped expansion area is larger, so that the bypass flow path 68 at the outside of the first valve member 46 passes. Nevertheless, in order to be able to move the first valve member 46 back and forth between its two connecting positions without the risk of jamming, a guide arrangement in the form of a plurality of rib-like projections 72 is provided in the second housing section 52.
  • These rib-like projections 72 extend approximately in the longitudinal direction, ie also displacement direction of the first valve member 46 and form with their inwardly directed surface regions a guide structure which connects substantially flush and steplessly to the inner surface in the first housing portion 50.
  • a guide structure which connects substantially flush and steplessly to the inner surface in the first housing portion 50.
  • four such rib-like projections that not only ensure the defined guidance of the first valve member 46, but also define channels of the channel arrangement 70 between them.
  • a further support member 74 may be held between these projections 72, which provides an abutment for the biasing spring 56.
  • the overall system described above and shown in FIG. 1 can also be advantageously used above all when an integral construction of the valve arrangement 10 with the delivery pump 40 or possibly the heater 26 is obtained.
  • the feed pump 40 with this valve arrangement 10 as an assembly into an overall system and thereby achieve the previously described functionality with a compact size.
  • the system does not necessarily have to be provided with the extensive functionality described above become.
  • conventional functionality of vehicle heating may be achieved by not routing the conduit 12 to the valve assembly 10, as indicated in FIG.
  • valve assembly 10 is basically superfluous, but because of the not very significant additional production costs whose presence can be accepted, especially because it provides the opportunity, subsequently by appropriate switching the line connections also to ensure the more extensive functionality.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Multiple-Way Valves (AREA)
  • Sliding Valves (AREA)
  • Motor Or Generator Cooling System (AREA)
EP07004175A 2006-03-16 2007-02-28 Agencement de vannes, en particulier destiné à l'installation d'un courant de moyen de chauffage/refroidissement dans un véhicule automobile Active EP1835142B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07004175T PL1835142T3 (pl) 2006-03-16 2007-02-28 Układ zaworu, w szczególności do regulacji strumienia przepływu środka grzewczego/środka chłodzącego w pojeździe mechanicznym

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006012212A DE102006012212A1 (de) 2006-03-16 2006-03-16 Ventilanordnung, insbesondere zur Einstellung einer Heizmittel/Kühlmittel-Strömung in einem Kraftfahrzeug

Publications (3)

Publication Number Publication Date
EP1835142A2 true EP1835142A2 (fr) 2007-09-19
EP1835142A3 EP1835142A3 (fr) 2008-06-25
EP1835142B1 EP1835142B1 (fr) 2012-09-12

Family

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EP07004175A Active EP1835142B1 (fr) 2006-03-16 2007-02-28 Agencement de vannes, en particulier destiné à l'installation d'un courant de moyen de chauffage/refroidissement dans un véhicule automobile

Country Status (3)

Country Link
EP (1) EP1835142B1 (fr)
DE (1) DE102006012212A1 (fr)
PL (1) PL1835142T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013225098A1 (de) 2013-12-06 2015-06-11 Eberspächer Climate Control Systems GmbH & Co. KG Ventilanordnung
DE102014203085A1 (de) 2014-02-20 2015-08-20 Eberspächer Climate Control Systems GmbH & Co. KG Ventilanordnung, insbesondere zur Einstellung einer Wärmeträgermediumströmung im Wärmeträgermediumkreislauf eines Fahrzeugs
CN106870098A (zh) * 2017-03-29 2017-06-20 安徽江淮汽车集团股份有限公司 一种发动机冷却系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012220789B4 (de) 2012-11-14 2021-06-24 Eberspächer Climate Control Systems GmbH Wärmetauscheranordnung, insbesondere für ein Fahrzeugheizgerät

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10359293A1 (de) 2003-12-17 2005-07-21 J. Eberspächer GmbH & Co. KG Ventilanordnung, insbesondere zur Einstellung der Heizmittel-/Kühlmittelströmung in einem Kraftfahrzeug

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FR869652A (fr) * 1939-03-18 1942-02-11 Bmw Flugmotorenbau Gmbh Dispositif de lubrification pour moteurs d'avions
US2813545A (en) * 1955-06-17 1957-11-19 Galland Henning Mfg Company Inline control valve
ATE4340T1 (de) * 1979-09-28 1983-08-15 Caterpillar Tractor Co. Fluidfolge-umlaufapparat.
DE3824412C1 (fr) * 1988-07-19 1989-08-24 Mtu Friedrichshafen Gmbh
DE3843827A1 (de) * 1988-12-24 1990-07-05 Kloeckner Humboldt Deutz Ag Brennkraftmaschine mit zwei hydraulischen fluessigkeitskreislaeufen
CZ288737B6 (cs) * 1993-07-21 2001-08-15 J. Eberspächer Gmbh & Co. Topení vozidla
DE10128634B4 (de) * 2001-06-13 2004-08-05 Itw Henschel Gmbh Thermostatventil
US6915958B2 (en) * 2002-05-22 2005-07-12 Tesma International Inc. Linear proportional valve

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10359293A1 (de) 2003-12-17 2005-07-21 J. Eberspächer GmbH & Co. KG Ventilanordnung, insbesondere zur Einstellung der Heizmittel-/Kühlmittelströmung in einem Kraftfahrzeug

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013225098A1 (de) 2013-12-06 2015-06-11 Eberspächer Climate Control Systems GmbH & Co. KG Ventilanordnung
DE102013225098B4 (de) 2013-12-06 2021-08-12 Eberspächer Climate Control Systems GmbH Fahrzeugheizsystem
DE102014203085A1 (de) 2014-02-20 2015-08-20 Eberspächer Climate Control Systems GmbH & Co. KG Ventilanordnung, insbesondere zur Einstellung einer Wärmeträgermediumströmung im Wärmeträgermediumkreislauf eines Fahrzeugs
CN106870098A (zh) * 2017-03-29 2017-06-20 安徽江淮汽车集团股份有限公司 一种发动机冷却系统

Also Published As

Publication number Publication date
DE102006012212A1 (de) 2007-09-20
EP1835142A3 (fr) 2008-06-25
EP1835142B1 (fr) 2012-09-12
PL1835142T3 (pl) 2013-03-29

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