EP2304238A1 - Procédé de commande du fonctionnement d'un compresseur - Google Patents

Procédé de commande du fonctionnement d'un compresseur

Info

Publication number
EP2304238A1
EP2304238A1 EP09765657A EP09765657A EP2304238A1 EP 2304238 A1 EP2304238 A1 EP 2304238A1 EP 09765657 A EP09765657 A EP 09765657A EP 09765657 A EP09765657 A EP 09765657A EP 2304238 A1 EP2304238 A1 EP 2304238A1
Authority
EP
European Patent Office
Prior art keywords
compressor
temperature
cooling function
location
temperature estimate
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
EP09765657A
Other languages
German (de)
English (en)
Other versions
EP2304238B1 (fr
Inventor
Marek Engelhardt
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP2304238A1 publication Critical patent/EP2304238A1/fr
Application granted granted Critical
Publication of EP2304238B1 publication Critical patent/EP2304238B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/08—Cylinder or housing parameters
    • F04B2201/0801—Temperature

Definitions

  • the invention relates to a method referred to in the preamble of claim 1 for controlling the operation of a compressor.
  • compressors are frequently used in which a gaseous or liquid medium can be brought to a pressure which is above the ambient pressure.
  • the gaseous or liquid medium is often used as a control pressure medium, for example, actuators, in particular piston-cylinder arrangements, can be acted upon.
  • Piston compressors formed.
  • relatively small compressors are increasingly used, which are thermally significantly burdened in a possibly longer-lasting operation, so that components can heat unacceptably high. If the thermal load is too high, the exhaust valve or the piston seal of a reciprocating compressor will usually be damaged first. digt, which can ultimately lead to a failure of the compressor and thus the level control system.
  • Compressor varies, serve the heat transfer conditions that prevail between the compressor and the surrounding air.
  • the duty ratio may be varied depending on the air temperature and the air flow velocity prevailing in the vicinity of the compressor such that the duty ratio is shortened as the ambient temperature increases and is prolonged as it decreases.
  • the ambient temperature can be based on a Model calculation from the current vehicle outside air temperature and / orggymotoransaug Kunststofftemperatur be determined.
  • the disadvantage here is that the known method as all duty cycle methods is consistently inaccurate because it does not take into account the thermodynamic properties of the compressor itself. For example, the controller does not influence the temperature range in which the compressor is ultimately operated.
  • a method for temperature-controlled control of a compressor for air suspension of a motor vehicle is known, which is designed as an estimation method and manages without a separate temperature sensor on the compressor.
  • the compressor is switched off by a control unit when a temperature estimate calculated by the latter exceeds an upper threshold value, or is switched on or is allowed to be switched on if a lower threshold value is undershot.
  • the respective last temperature estimated value is increased by a certain temperature jump when the compressor is switched on, the extent of which depends on the height of the last estimated value.
  • the estimated value is increased during a compressor operation in a predetermined manner and lowered at standstill of the compressor in a predetermined manner.
  • the disadvantage here is that the underlying for the process linear relationships in practice are generally not present because at high temperature differences, the temperature changes are greater than at small temperature differences. The temperature jump also does not take place in reality immediately, so that in this area, the control technology availability of the compressor is disadvantageously reduced.
  • EP 1 644 640 B1 discloses a method of the type in question for controlling the operation of the compressor, in which the compressor is switched off by a thermal damage control unit when a temperature estimate calculated by the controller exceeds an upper threshold.
  • the control unit calculates, using the temperature estimate as the state variable, a cooling function which represents the time course of the cooling of the compressor.
  • the invention has the object of developing a method referred to in the preamble of claim 1 species so that the cooling function can be determined more precisely.
  • the invention is based on the finding that the cooling function in a case in which the compressor has been operated so that it has heated up, for example, only in one area of the outlet valve, but otherwise is not completely or largely "thoroughly warmed", another Course has as in a case in which the compressor has been operated so that it is not only strongly heated, for example, in the area of the exhaust valve, but is completely or largely "warm-through”. Proceeding from this, the invention is based on the idea of determining the cooling function on the basis of a temperature gradient between the temperatures at at least two locations of the compressor spaced apart from one another.
  • the invention provides that the control unit determines the cooling function on the basis of at least one first and one second temperature estimate associated with spatially spaced locations of the compressor, such that the cooling function is based on a temperature difference between the first temperature estimate and the second temperature estimate is determined. In this way, the cooling function can be determined much more accurately.
  • the compressor has been operated so that it has heated predominantly at a location associated with the first temperature estimate, for example in the region of its outlet valve, while at a location associated with the second temperature estimate, for example, an outer surface of the housing of the Compressor corresponds, has heated less, so the temperature gradient between the used points of the compressor is relatively high. Accordingly, the compressor will cool relatively quickly after switching off by heat dissipation to the environment, so that the controller calculates a cooling function that corresponds to such a relatively rapid cooling.
  • the compressor has been operated such that it is associated both at a location associated with the first temperature estimate and at a value associated with the second temperature estimate Point has relatively strongly heated, the temperature gradient between the considered points of the compressor is lower. In such a case, the compressor will cool down relatively slowly due to heat dissipation to the environment. Accordingly, the controller calculates a cooling function corresponding to a slower cooling of the compressor.
  • the reaction speed of the control of the operation of the compressor is increased according to the invention.
  • the reaction possibilities of the controller during operation of the compressor are extended. For example, it is possible to immediately restart the compressor after a relatively rapid cooling when, for example, a level control system of a motor vehicle for the protection of pedestrians requires a lowering of the body of the motor vehicle.
  • the locations of the compressor spatially assigned to the first and the second temperature estimate can be selected within wide limits in accordance with the respective requirements, constructional conditions and operating conditions of the compressor.
  • a spatially associated with the second temperature estimate point of the compressor is closer to a region located at ambient temperature than a location spatially associated with the first temperature estimate. In this way, the precision in determining the cooling function is further elevated.
  • the locations assigned to the temperature estimates are selected here, for example and in particular, such that a high temperature gradient results between these points in the case of a predominantly local heating of the compressor, for example in the region of the outlet valve.
  • This temperature gradient is particularly high when the first temperature estimate is associated with a location of the compressor at which the compressor heats up relatively quickly during operation and / or when the second temperature estimate is associated with a location of the compressor where the Compressor heats up relatively slowly during operation, as provide advantageous developments of the teaching of the invention.
  • expedient developments of the invention provide for the first location to be arranged in the region of an outlet valve or a piston seal of the compressor and / or the second point in the region of an outer surface of the housing of the compressor, in particular in the region of its cylinder head, is arranged.
  • the controller can determine the cooling function using any other state variables.
  • An advantageous development of the invention provides insofar as the control unit determines the cooling function using further state variables, in particular the ambient temperature and / or the compressor voltage and / or a pre-pressure and counter-pressure of the compressor.
  • Another advantageous development of the invention provides that, after switching on and restarting the control unit, the same is determined by using the determined cooling function and between switching on and restarting, at which time a lower temperature threshold is exceeded and the compressor can be switched on again.
  • the compressor is first subjected in a test setup various operating conditions, in particular with regard to the duration of its operation, the ambient temperature, the compressor voltage and the bias and back pressure of the compressor.
  • various operating conditions in particular with regard to the duration of its operation, the ambient temperature, the compressor voltage and the bias and back pressure of the compressor.
  • the time profile of the temperature of the compressor at a first location which is arranged in the region of an outlet valve of the compressor in this embodiment, measured and stored, in particular during the cooling of the compressor in the off state.
  • the time profile of the temperature of the compressor is measured at a second location, which in this
  • Embodiment is arranged in the region of the cylinder head of the compressor.
  • the temperature profiles determined in this way for different operating states are stored and fed into a software of the control unit of the compressor, so that in the installed state of the compressor, for example on a level control system of a motor vehicle, temperature estimates can be determined by the control unit, and accordingly in the installed state of the Compressor a temperature sensor is not required.
  • the same is controlled by the controller such that the controller shuts off the compressor to prevent thermal damage when a calculated by the controller temperature estimate exceeds an upper threshold.
  • the controller calculates, in a continuous manner or at intervals by software, a first temperature estimate associated with a location in the exhaust valve portion of the compressor in the embodiment, and a second temperature estimate associated with a location is assigned in the region of the cylinder head of the compressor.
  • the control unit additionally calculates a cooling function that determines the time course of the cooling of the
  • control unit determines the Cooling function according to the invention, starting from the first and the second temperature estimate, such that the cooling function is determined based on the temperature difference between the first temperature estimate and the second temperature estimate.
  • the controller shuts off the compressor to prevent thermal damage. If the control unit remains switched on after switching off the compressor, it calculates, based on the temperature estimates, the cooling function, from which it can be deduced, at which time the compressor can be switched on again, without thermal damage occurring in the compressor. If the temperature difference between the first and the second temperature estimated value is relatively large, this means that the compressor is heated relatively high, above all locally in the area of its outlet valve, without the compressor being relatively "warmed up". This results in a cooling function, which corresponds to a faster cooling, so that a lower threshold of the temperature is reached relatively quickly and thus the compressor can be switched on again relatively quickly.
  • control unit determines that the temperature difference between the first and the second temperature estimated value is relatively small, it follows that the compressor is not heated relatively strongly only in the region of its outlet valve, but is rather heavily "warmed up".
  • the cooling function is determined on the basis of the determined for the time of switching off
  • the cooling function can be determined more precisely, since according to the invention it is not determined on the basis of a single temperature estimation value but on the basis of a temperature difference between two temperature estimates.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un procédé de commande du fonctionnement d'un compresseur. Afin d'éviter les dommages thermiques, le compresseur est coupé par un appareil de commande lorsque la valeur de température estimée par l'appareil de commande dépasse une valeur de seuil supérieure. Pour ce faire, l'appareil de commande calcule, sur la base de la valeur de température estimée, une fonction de refroidissement constituant une grandeur d'état qui représente l'allure dans le temps du refroidissement du compresseur. Selon l'invention, l'appareil de commande calcule la fonction de refroidissement en partant d'au moins une première et une deuxième valeur de température estimée qui correspondent à des endroits du compresseur séparés dans l'espace, afin que la fonction de refroidissement soit déterminée à partir de la différence de température entre la première et la deuxième valeur de température estimée.
EP09765657.3A 2008-06-17 2009-04-15 Procédé de commande du fonctionnement d'un compresseur Active EP2304238B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008028781A DE102008028781A1 (de) 2008-06-17 2008-06-17 Verfahren zur Steuerung des Betriebs eines Kompressors
PCT/EP2009/054431 WO2009153077A1 (fr) 2008-06-17 2009-04-15 Procédé de commande du fonctionnement d'un compresseur

Publications (2)

Publication Number Publication Date
EP2304238A1 true EP2304238A1 (fr) 2011-04-06
EP2304238B1 EP2304238B1 (fr) 2015-01-07

Family

ID=40823612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09765657.3A Active EP2304238B1 (fr) 2008-06-17 2009-04-15 Procédé de commande du fonctionnement d'un compresseur

Country Status (4)

Country Link
US (1) US9932978B2 (fr)
EP (1) EP2304238B1 (fr)
DE (1) DE102008028781A1 (fr)
WO (1) WO2009153077A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010017654A1 (de) * 2010-06-30 2012-01-05 Continental Teves Ag & Co. Ohg Höhenabhängige Kompressorsteuerung

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334808A (en) 1965-10-24 1967-08-08 Lennox Ind Inc Compressor lubrication arrangement
DE1943936A1 (de) 1969-08-29 1971-03-18 Danfoss As Schutzanordnung fuer einen Verdichter
DE3919407A1 (de) 1988-07-14 1990-01-18 Eco Air Drucklufttechnik Gmbh Verfahren zum steuern eines verdichters und steuerungseinrichtung
JPH03118719A (ja) 1989-09-29 1991-05-21 Seikosha Co Ltd モータの制御方法
DE4333591A1 (de) 1993-10-01 1995-04-06 Bayerische Motoren Werke Ag Steuergerät zum bedarfsgerechten Ein- und Ausschalten des elektrischen Antriebsmotors, insbesondere eines Luftkompressors
US5584675A (en) * 1995-09-15 1996-12-17 Devilbiss Air Power Company Cylinder sleeve for an air compressor
DE19621946C2 (de) 1996-05-31 2002-05-29 Daimler Chrysler Ag Luftfederung
DE19812234C2 (de) 1998-03-20 2002-07-18 Daimler Chrysler Ag Luftfederungsanlage für Fahrzeuge
DE10120206A1 (de) 2001-04-24 2002-10-31 Wabco Gmbh & Co Ohg Verfahren zur Steuerung eines Kompressors
DE10330121A1 (de) 2003-07-04 2005-02-03 Continental Aktiengesellschaft Verfahren zur Steuerung des Betriebs eines Kompressors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009153077A1 *

Also Published As

Publication number Publication date
US20110052422A1 (en) 2011-03-03
WO2009153077A1 (fr) 2009-12-23
DE102008028781A1 (de) 2009-12-24
US9932978B2 (en) 2018-04-03
EP2304238B1 (fr) 2015-01-07

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