EP0150429A2 - Pièce intercalée à contrôle de température pour le circuit de refroidissement d'un moteur à combustion interne - Google Patents

Pièce intercalée à contrôle de température pour le circuit de refroidissement d'un moteur à combustion interne Download PDF

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Publication number
EP0150429A2
EP0150429A2 EP84115671A EP84115671A EP0150429A2 EP 0150429 A2 EP0150429 A2 EP 0150429A2 EP 84115671 A EP84115671 A EP 84115671A EP 84115671 A EP84115671 A EP 84115671A EP 0150429 A2 EP0150429 A2 EP 0150429A2
Authority
EP
European Patent Office
Prior art keywords
expansion
temperature
valve
expansion capsule
capsule
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
EP84115671A
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German (de)
English (en)
Other versions
EP0150429B1 (fr
EP0150429A3 (en
Inventor
Gerhart Huemer
Athanasios Michassouridis
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0150429A2 publication Critical patent/EP0150429A2/fr
Publication of EP0150429A3 publication Critical patent/EP0150429A3/de
Application granted granted Critical
Publication of EP0150429B1 publication Critical patent/EP0150429B1/fr
Expired legal-status Critical Current

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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
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control

Definitions

  • the invention relates to a temperature controller insert with the features according to the preamble of claim 1.
  • a known insert of this type according to DE-PS 12 95 255 has an expansion capsule which extends partially through the radiator return valve.
  • the temperature in the cooler return line influences the control temperature in the sense that the control temperature rises as the temperature of the cooler return decreases because the main part of the expansion capsule located downstream of the cooler return valve in the mixing area has to be subjected to increasing temperature, to influence the expansion capsule overall with its operating temperature. This makes it possible to achieve a constant or steadily falling control temperature of the mixed flow that is supplied to the machine as the cooler return temperature rises.
  • the limit values of the temperature control range are determined on the one hand by a maximum value of the control temperature at extremely low ambient temperature and low engine load and therefore extremely low radiator return temperature and on the other hand by a relatively low control temperature at high ambient temperature and high engine load with high radiator return temperature, the latter largely the Operating temperature of the expansion capsule corresponds.
  • the object of the invention is to develop a temperature controller insert of the known type so that it sets a control temperature which remains constant within narrow limits at part load of the machine with a correspondingly low cooler return temperature and a lower control temperature at full load of the machine with a correspondingly high cooler return temperature .
  • a regulation is to be brought about which, on the one hand, due to a high operating temperature of the machine in partial load operation, a reduced frictional power with reduced fuel consumption and, on the other hand, with full load of the machine due to a lower operating temperature, enables more intensive cooling to avoid overheating and in particular auto-ignition.
  • the expansion capsule of the first expansion element causes a uniform, relatively high control temperature and the further expansion capsule of the second expansion element overrides the function of the first from a relatively high temperature in the cooler return line. This results in a lowering of the control temperature in the area of the full load of the machine to the actuation temperature of the second expansion capsule and to the subsequent course of the cooler return temperature with the cooler return valve open and the short-circuit valve closed in accordance with the full cooling effect of the cooler.
  • the preferred actuation temperature values of the two expansion capsules are the values proposed according to the features of claim 2, which within normal limits result in a favorable high temperature level for low friction power of the machine at part load of the machine and a sufficient distance of the operating temperature from critical values at full load .
  • claims 3 to 5 show preferred structural configurations of the invention, which are closely based on the commercial structure of temperature control inserts and therefore require only minor changes to the existing production facilities for training according to the invention.
  • a temperature regulator insert 1 consists of two mutually directed expansion capsules 2 and 3 with a common piston rod 4 and a sealing cap 5 and 6, which form two expansion elements with different actuation temperatures.
  • the first expansion capsule 2 carries a radiator return valve 7 and short-circuit valve 8.
  • the radiator return valve 7 is fixed on the expansion capsule 2 and is urged together with this by a return spring 9 in the direction of a valve seat 10.
  • the short-circuit valve 8 is mounted axially displaceably against the action of a further return spring 11, so that the stroke of the expansion capsule 2 when the short-circuit valve 8 is placed on its valve seat 8 'to the short-circuit line 12 is not limited .
  • the valve seat 10 is formed on a radial fastening and closure flange 13 which is held on its outer circumference in a flange connection 14 of a thermostat housing 15. Both the return spring 9 and the second expansion capsule 3 are supported on the flange 13 and thus on the thermostat housing 15 via a respective support bracket 16 and 17.
  • the expansion capsule 3 extends into a radiator return line 18 which adjoins the thermostat housing 15 and continues in the housing 15 up to the valve seat 10.
  • the short-circuit line 12 opening into the housing 15 opposite ends at the valve seat 8 ′ for the short-circuit valve 8.
  • the interior of the housing 15 forms a mixing chamber 15 'for coolant components from the short-circuit line 12 and the cooler return line 18 between the valve seats 8' and 10.
  • a return line 19 leads from the mixing chamber 15 'to the coolant pump 20 of the machine 21.
  • the short-circuit line 12 and a radiator supply line 22 to a cooler 23 with the subsequent cooler return line 18 close the two parallel line branches of the cooling circuit between the machine 21 and the mixing chamber 15 '.
  • the coolant pump 20 conveys the coolant, which is initially cold after a cold start, exclusively through the short-circuit line 12 with the short-circuit valve 8 open and the cooler return valve 7. Since a cooling effect of the cooler 23 is excluded, the temperature of the coolant quickly reaches the actuation temperature of the expansion capsule 2, which is predominantly arranged in the mixing chamber 15 'through which flow.
  • the expansion material contained therein expands very strongly at its actuation temperature by changing its physical state from solid to liquid in a low temperature range of, for example, 90 to 105.degree. As a result, a stroke of the expansion capsule 2 together with the radiator return valve and the short-circuit valve 8 is generated in this temperature range, which opens the radiator return valve 7 at 90 ° C.
  • the common piston rod 4 of the two expansion capsules 2 and 3 is thereby displaced by the volume change of the expansion material in the expansion capsule 2 against the action of the return spring 9 and is supported via a stop ring 4 'against the second expansion capsule 3.
  • the stop ring 4 ' forms a fixed support for the piston rod 4, the position of which remains unaffected by the change in volume of the expansion material in the second expansion capsule 3 below the start of its actuation temperature range of, for example, 70 to 85 ° C.
  • This curve 24 of the control temperature solely from the function of the expansion capsule 2 passes in a previously known manner according to the broken line 24 'directly into the curve 25 of the cooler outlet temperature T KA with a full flow through the cooler 23 and a short-circuit line 12 not flowed through.
  • the control temperature and thus the machine inlet temperature T ME according to the course 24-24 'in FIG. 2 is selected to be relatively high at approximately 100 ° C. in order to achieve an operating temperature that is advantageously high for low frictional power, this leads to this with a given high ambient temperature and machine full load in the region 24 'at the same time as a risk of overheating and auto-ignition of the machine.
  • the one arranged in the cooler return line 18 and the cooler according to FIG outlet temperature T KA of the coolant exposed second expansion capsule 3 a lowering curve 27 of the control temperature and thus the engine inlet temperature T ME only from the beginning of the operating temperature range of, for example, 70 to 85 ° C of this second expansion capsule 3, which is only in high machines Partial and full load and at the same time high ambient temperature is reached. Due to the increase in volume of the expansion material in the second expansion capsule 3, the piston rod 4 is moved out of the sealing head 6 and thus also the first expansion capsule 2 together with the radiator return valve 7 and the short-circuit valve 8 in the sense of an increasing opening and closing of the first the latter moves.
  • the expansion capsule 3 achieves a stroke of the piston rod 4 which is sufficient only for the radiator return valve 7 to open fully and for the full Closing the short-circuit valve 8 corresponds.
  • the first expansion capsule 2 is also subjected exclusively to the radiator return temperature T KA from the radiator return line 18 at approximately 85 ° C., so that the piston rod 4 has its starting position relative to the first expansion capsule 2 and the position of the valves 7 and 8 thus is dependent solely on the stroke of the piston rod 4 from the second expansion capsule 3.
  • the control temperature and thus the machine inlet temperature T ME fall in the range of the operating temperature from 70 to 85 ° C. of the second expansion capsule 3 from its horizontal course 24, which is determined by the function of the first expansion capsule 2 increasing cooler outlet temperature T KA on the course 25 of the cooler outlet temperature T KA with only flow through the cooler 23.
  • the operating temperature then rises further, the cooling output of the cooling circuit, and in particular the cooler size, being decisive for the temperature values of this increase after the course 25.
  • the course of the coolant temperature that can be achieved by the invention in cooperation with tuning the entire cooling circuit allows a particularly high operating temperature for internal combustion engines for high efficiency in part-load operation and a lower operating temperature for safe full-load operation with extremely low construction costs for the achieve temperature controller use according to the invention. It is also possible in a simple manner to replace a previously used temperature regulator insert on internal combustion engines with mixed thermostats for a temperature regulator insert according to the invention which is matched to the respective internal combustion engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
EP84115671A 1983-12-24 1984-12-18 Pièce intercalée à contrôle de température pour le circuit de refroidissement d'un moteur à combustion interne Expired EP0150429B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3347002 1983-12-24
DE3347002A DE3347002C1 (de) 1983-12-24 1983-12-24 Temperaturregler-Einsatz fuer den Kuehlkreis fluessigkeitsgekuehlter Brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0150429A2 true EP0150429A2 (fr) 1985-08-07
EP0150429A3 EP0150429A3 (en) 1986-10-08
EP0150429B1 EP0150429B1 (fr) 1988-08-10

Family

ID=6218088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115671A Expired EP0150429B1 (fr) 1983-12-24 1984-12-18 Pièce intercalée à contrôle de température pour le circuit de refroidissement d'un moteur à combustion interne

Country Status (4)

Country Link
US (1) US4606302A (fr)
EP (1) EP0150429B1 (fr)
JP (1) JPS60173307A (fr)
DE (2) DE3347002C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3765773A4 (fr) * 2018-03-14 2021-08-25 Scania CV AB Dispositif thermostatique pour un système de refroidissement et système de refroidissement comprenant ce dispositif thermostatique

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS639622A (ja) * 1986-06-30 1988-01-16 Fuji Heavy Ind Ltd エンジンの冷却装置
DE3700582C1 (de) * 1987-01-10 1988-03-03 Bayerische Motoren Werke Ag Temperatur-Regelvorrichtung fuer den Kuehlkreis fluessigkeitsgekuehlter Brennkraftmaschinen
US4883082A (en) * 1988-05-16 1989-11-28 Pirkle Fred L Temperature-responsive valve
US5181656A (en) * 1991-12-16 1993-01-26 Schwerdt Gerald N Water recirculating apparatus
US5275231A (en) * 1992-07-28 1994-01-04 Yoshikazu Kuze Cooling system for an automotive engine
DE4324178A1 (de) * 1993-07-19 1995-01-26 Bayerische Motoren Werke Ag Kühlanlage für einen Verbrennungsmotor eines Kraftfahrzeuges mit einem Thermostatventil, das ein elektrisch beheizbares Dehnstoffelement enthält
DE4401620A1 (de) * 1994-01-20 1995-07-27 Bayerische Motoren Werke Ag Kühlanlage für einen Verbrennungsmotor eines Kraftfahrzeuges mit einem Thermostatventil, das ein elektrisch beheizbares Dehnstoffelement enthält
US5410991A (en) * 1994-05-05 1995-05-02 Standard-Thomson Corporation Coolant fill housing with integral thermostat
GB9411617D0 (en) * 1994-06-09 1994-08-03 Rover Group A thermostat assembly
FR2739468B1 (fr) * 1995-10-02 2003-03-07 Inst Francais Du Petrole Procede et dispositif de regulation de la temperature d'un fluide
US5642691A (en) * 1996-01-30 1997-07-01 Brunswick Corporation Thermostat assembly for a marine engine with bypass
DE19637818C1 (de) * 1996-09-17 1998-04-16 Laengerer & Reich Gmbh & Co Thermostatventileinheit
DE19814252B4 (de) * 1998-03-31 2014-10-09 Behr Thermot-Tronik Gmbh Thermostatventil
JP4498636B2 (ja) 2001-04-27 2010-07-07 日本サーモスタット株式会社 サーモスタット装置
DE10144844B4 (de) * 2001-09-06 2014-06-05 Behr Thermot-Tronik Gmbh Thermostatventil
DE102009012534A1 (de) * 2009-03-10 2010-09-16 Audi Ag Selbstregelndes Thermostatventil sowie Kühlsystem für ein Brennkraftmaschine
IN2012DN01865A (fr) * 2009-12-04 2015-07-17 Toyota Motor Co Ltd
SE536466C2 (sv) * 2012-04-05 2013-11-26 Scania Cv Ab Termostatanordning och kylsystem
JP6576702B2 (ja) * 2015-06-18 2019-09-18 ダイハツ工業株式会社 車両用内燃機関の冷却水制御装置
SE540327C2 (en) * 2016-10-21 2018-06-26 Scania Cv Ab A thermostat device for a cooling system and a cooling system comprising said thermostat device
TR201800656A2 (tr) * 2018-01-17 2019-07-22 Kirpart Otomotiv Parcalari Sanayi Ve Ticaret A S Soğutma si̇stemi̇ üzeri̇ndeki̇ farkli motor algilama noktalarinin sicaklik değerleri̇ne uyumlu olacak şeki̇lde eşzamanli akti̇ve edi̇len termostati̇k valf
KR102123112B1 (ko) * 2019-10-15 2020-06-15 조대원 병원용 자산 관리 시스템 및 방법
KR102216885B1 (ko) * 2020-01-31 2021-02-17 임시원 정신건강의학의 병원용 자산 관리를 위한 방법 및 장치

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1295255B (de) * 1965-03-27 1969-05-14 Bayerische Motoren Werke Ag Thermostatisch gesteuertes Mischventil, insbesondere fuer Umlaufkuehlungen von fluessigkeitsgekuehlten Brennkraftmaschinen mit Luftkuehler und Kurzschlussleitung
DE1451669A1 (de) * 1963-06-20 1970-02-12 Daimler Benz Ag Thermostat fuer verschieden hohe OEffnungstemperaturen bzw. OEffnungshuebe,insbesondere an Kraftfahrzeug-Brennkraftmaschinen
FR2087791A5 (fr) * 1970-03-06 1971-12-31 Ammus Sytytin Oy
DE2320447A1 (de) * 1973-04-21 1974-11-07 Daimler Benz Ag Kuehlwasserregelventil, insbesondere zur regelung der kuehlwassertemperatur von kraftfahrzeugen
DE2755465A1 (de) * 1977-12-13 1979-06-21 Daimler Benz Ag Regelthermostat fuer die einhaltung eines im wesentlichen konstanten sollwertes der betriebstemperatur eines fluessigen kuehlmittels einer brennkraftmaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE861937C (de) * 1949-11-29 1953-01-08 Daimler Benz Ag Vorrichtung zur Temperaturregelung an Brennkraftmaschinen
US3768731A (en) * 1971-08-25 1973-10-30 Altair Inc Fail safe thermostatic switch
DE2314301C3 (de) * 1973-03-22 1978-07-20 Bayerische Motoren Werke Ag, 8000 Muenchen Unilaufkiihlvorrichtung für Kolbenbrennkraftmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1451669A1 (de) * 1963-06-20 1970-02-12 Daimler Benz Ag Thermostat fuer verschieden hohe OEffnungstemperaturen bzw. OEffnungshuebe,insbesondere an Kraftfahrzeug-Brennkraftmaschinen
DE1295255B (de) * 1965-03-27 1969-05-14 Bayerische Motoren Werke Ag Thermostatisch gesteuertes Mischventil, insbesondere fuer Umlaufkuehlungen von fluessigkeitsgekuehlten Brennkraftmaschinen mit Luftkuehler und Kurzschlussleitung
FR2087791A5 (fr) * 1970-03-06 1971-12-31 Ammus Sytytin Oy
DE2320447A1 (de) * 1973-04-21 1974-11-07 Daimler Benz Ag Kuehlwasserregelventil, insbesondere zur regelung der kuehlwassertemperatur von kraftfahrzeugen
DE2755465A1 (de) * 1977-12-13 1979-06-21 Daimler Benz Ag Regelthermostat fuer die einhaltung eines im wesentlichen konstanten sollwertes der betriebstemperatur eines fluessigen kuehlmittels einer brennkraftmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3765773A4 (fr) * 2018-03-14 2021-08-25 Scania CV AB Dispositif thermostatique pour un système de refroidissement et système de refroidissement comprenant ce dispositif thermostatique
US11578641B2 (en) 2018-03-14 2023-02-14 Scania Cv Ab Thermostat device for a cooling system and a cooling system comprising said thermostat device

Also Published As

Publication number Publication date
EP0150429B1 (fr) 1988-08-10
JPH0231213B2 (fr) 1990-07-12
DE3347002C1 (de) 1985-05-15
EP0150429A3 (en) 1986-10-08
DE3473322D1 (en) 1988-09-15
JPS60173307A (ja) 1985-09-06
US4606302A (en) 1986-08-19

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