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EP2304238B1 - Method for controlling the operation of a compressor - Google Patents

Method for controlling the operation of a compressor Download PDF

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Publication number
EP2304238B1
EP2304238B1 EP09765657.3A EP09765657A EP2304238B1 EP 2304238 B1 EP2304238 B1 EP 2304238B1 EP 09765657 A EP09765657 A EP 09765657A EP 2304238 B1 EP2304238 B1 EP 2304238B1
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EP
European Patent Office
Prior art keywords
compressor
temperature value
temperature
estimated temperature
controller
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.)
Active
Application number
EP09765657.3A
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German (de)
French (fr)
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EP2304238A1 (en
Inventor
Marek Engelhardt
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Continental Teves AG and Co OHG
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Continental Teves AG and Co OHG
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Publication of EP2304238A1 publication Critical patent/EP2304238A1/en
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Publication of EP2304238B1 publication Critical patent/EP2304238B1/en
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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.
  • An application in motor vehicles results from the need to supply the air springs of a level control system with compressed air such that it brings the body of the vehicle in a driving situation equitable distance to the road surface. Since such a level control system does not constantly provide for a height adjustment of the body of the vehicle, an associated compressor is required only ever put into operation if the need exists.
  • the corresponding compressors are usually designed as electric motor driven piston compressors. In order to minimize the cost of the compressors used 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 is usually damaged first, which can ultimately lead to failure of the compressor and thus the level control system.
  • 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.
  • EP 1 644 640 B1 For example, there is known a method of the type in question for controlling the operation of the compressor, wherein the compressor is shut down by a thermal damage control controller when a temperature estimate calculated by the controller exceeds an upper threshold.
  • the control unit calculates, using the temperature estimated value 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.
  • the cooling function can be determined much more accurately. For example, if 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 Compressor corresponds, has heated less, so the temperature gradient between the used points of the compressor is relatively high.
  • 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. In this way, the reliability of a vehicle equipped with such a level control system motor vehicle is substantially increased.
  • the basic way of determining the cooling function is the expert from the EP 1 644 640 B1 is known and will therefore not be explained here.
  • the locations of the compressor spatially assigned to the first and the second temperature estimation values can be selected within wide limits in accordance with the respective requirements, constructional conditions and operating conditions of the compressor. Starting from the idea that a cooling of the compressor takes place mainly by heat removal to the environment, an advantageous development of the teaching according to the invention provides that a location of the compressor spatially assigned to the second temperature estimate is closer to an area 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 off and restarting the control unit, the same is determined by using the determined cooling function and the time between switching off and restarting, at which time a lower temperature threshold value is exceeded and the compressor can be switched on again ,
  • the compressor is first subjected to various operating conditions in a test setup, in particular with regard to the duration of its operation, the ambient temperature, the compressor voltage and the pre-pressure and counterpressure of the compressor.
  • a first temperature sensor by means of a first temperature sensor, 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 is arranged in the region of the cylinder head of the compressor in this embodiment.
  • 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, which represents the time course of the cooling of the compressor after a shutdown.
  • 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 calculated on the basis of the temperature estimates determined for the time of switch-off as soon as the control unit is switched on again, so for example when switching on the ignition of the motor vehicle. Based on the determined cooling function and the time between switching off the compressor and the reconnection of the control unit past time, the controller can then determine at what time a lower threshold value of the temperature of the compressor is exceeded and the compressor can be switched on again accordingly.
  • the cooling function can be determined more precisely, since, according to the invention, it is not determined on the basis of a single temperature estimate, but on the basis of a temperature difference between two temperature estimates.

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

Description

Die Erfindung betrifft ein Verfahren der im Oberbegriff des Anspruchs 1 genannten Art zur Steuerung des Betriebs eines Kompressors.The invention relates to a method referred to in the preamble of claim 1 for controlling the operation of a compressor.

In Kraftfahrzeugen werden häufig Kompressoren verwendet, in denen ein gasformiges oder flüssiges Medium auf einen Druck bringbar ist, der über dem Umgebungsdruck liegt. Das gasförmige oder flüssige Medium wird häufig als Steuerdruckmedium genutzt, mit dem beispielsweise Aktuatoren, insbesondere Kolben-Zylinder-Anordnungen, beaufschlagbar sind.In motor vehicles, 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.

Ein Anwendungsfall in Kraftfahrzeugen ergibt sich aus der Notwendigkeit, die Luftfedern einer Niveauregulierungsanlage derart mit Druckluft zu versorgen, dass diese die Karosserie des Fahrzeugs in einen fahrsituationsgerechten Abstand zur Fahrbahnoberfläche bringt. Da eine solche Niveauregulierungsanlage nicht ständig für eine Höhenverstellung der Karosserie des Fahrzeugs sorgt, wird ein zugehöriger Kompressor bedarfsgerecht immer nur dann in Betrieb genommen, wenn die Notwendigkeit dazu besteht. Die entsprechenden Kompressoren sind in der Regel als elektromotorisch betriebene Kolbenkompressoren ausgebildet. Zur Minimierung der Kosten für die verwendeten Kompressoren werden verstärkt relativ kleine Kompressoren eingesetzt, die bei einem ggf. länger dauernden Betrieb thermisch erheblich belastet werden, so dass sich Bauteile unzulässig hoch erwärmen können. Bei zu starker thermischer Beanspruchung wird in der Regel zuerst das Auslassventil oder die Kolbendichtung eines Kolbenkompressors beschädigt, was letztlich zu einem Ausfall des Kompressors und damit der Niveauregulierungsanlage führen kann.An application in motor vehicles results from the need to supply the air springs of a level control system with compressed air such that it brings the body of the vehicle in a driving situation equitable distance to the road surface. Since such a level control system does not constantly provide for a height adjustment of the body of the vehicle, an associated compressor is required only ever put into operation if the need exists. The corresponding compressors are usually designed as electric motor driven piston compressors. In order to minimize the cost of the compressors used 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 is usually damaged first, which can ultimately lead to failure of the compressor and thus the level control system.

Zur Vermeidung derartiger Schäden ist es beispielsweise durch DE 15 03 446 A1 , DE 19 43 936 A1 und EP 1 253 321 A2 bekannt, die Temperatur des Kompressors im Bereich der thermisch stark belasteten Bauteile direkt zu messen und bei einer thermischen Überlastung den Kompressor zur Abkühlung abzuschalten. Nachteilig hierbei ist, daß die notwendigen Temperatursensoren vergleichsweise teuer und bei kleinen Kompressoren aufgrund des beengten Bauraums im interessierenden Bereich nur schwer unterzubringen sind. Zwar deutet EP 1 253 321 A2 an, dass die Steuerung des Kompressorbetriebs auch ohne Temperatursensoren auf der Basis eines thermischen Modells erfolgen kann. Der Inhalt eines solchen Mess- bzw. Steuerungsverfahrens wird dabei jedoch nicht näher definiert.To avoid such damage, it is for example by DE 15 03 446 A1 . DE 19 43 936 A1 and EP 1 253 321 A2 It is known to directly measure the temperature of the compressor in the area of the components subjected to high thermal stress and, in the event of thermal overload, to switch off the compressor for cooling. The disadvantage here is that the necessary temperature sensors are relatively expensive and are difficult to accommodate in small compressors due to the cramped space in the area of interest. Although indicates EP 1 253 321 A2 assume that the control of the compressor operation can also take place without temperature sensors on the basis of a thermal model. However, the content of such a measurement or control method is not defined in more detail.

Durch DE 39 19 407 A1 und DE 40 30 475 A1 ist es bekannt, die thermische Belastung eines Kompressors über die elektrische Leistungsaufnahme und/oder die Betriebsdauer des zu dem Kompressor gehörenden Elektromotors zu ermitteln. In eine ähnliche Richtung geht der aus DE 43 33 591 A1 bekannt gewordene Vorschlag, die Steuerung eines Kompressors durch Aufsummieren von dessen Einzeleinschaltzeiten und Einzelabschaltzeiten zu beeinflussen. Die Einzeleinschalt- und Abschaltzeiten stellen jeweils einen von mehreren Einflussfaktoren im Hinblick auf die thermische Belastung des Kompressors dar. Durch DE 198 12 234 C2 ist es bekannt, dass ein Kompressor hinsichtlich seiner Ein- und Ausschaltzeiten variabel betrieben werden kann. Dabei soll die jeweils aktuelle Einschaltdauer an die aktuellen Betriebsbedingungen des Kompressors angepasst werden. Als Parameter, in dessen Abhängigkeit die Einschaltdauer des Kompressors variiert wird, dienen die Wärmeübertragungsbedingungen, die zwischen dem Kompressor und der diesen umgebenden Luft herrschen. Dabei kann die Einschaltdauer beispielsweise in Abhängigkeit von der in der Umgebung des Kompressors herrschenden Lufttemperatur und Luftströmungsgeschwindigkeit derart variiert werden, dass die Einschaltdauer verkürzt wird, wenn die Umgebungstemperatur zunimmt, und verlängert wird, wenn sie abnimmt. Die Umgebungstemperatur kann dabei anhand einer Modellrechnung aus der aktuellen Fahrzeugaußenlufttemperatur und/oder der Fahrzeugmotoransauglufttemperatur bestimmt werden. Nachteilig ist hierbei, dass das bekannte Verfahren wie alle Einschaltdauermethoden durchweg ungenau ist, weil es die thermodynamischen Eigenschaften des Kompressors selbst nicht berücksichtigt. Die Steuerung nimmt dabei beispielsweise keinen Einfluss darauf, in welchem Temperaturband der Kompressor letztlich betrieben wird.By DE 39 19 407 A1 and DE 40 30 475 A1 It is known to determine the thermal load of a compressor on the electrical power consumption and / or the operating time of belonging to the compressor electric motor. In a similar direction goes out DE 43 33 591 A1 become known proposal to influence the control of a compressor by summing its individual Einschaltzeiten and Einzelabschaltzeiten. The individual switch-on and switch-off times each represent one of several influencing factors with regard to the thermal load of the compressor DE 198 12 234 C2 It is known that a compressor can be operated variably in terms of its on and off times. The respective current duty cycle should be adapted to the current operating conditions of the compressor. As a parameter, depending on the duty cycle of the compressor is varied, serve the heat transfer conditions that prevail between the compressor and the surrounding air. For example, 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 / or Fahrzeugmotoransauglufttemperatur 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.

Durch DE 196 21 946 C2 ist ein Verfahren zur temperaturgestützten Steuerung eines Kompressors für eine Luftfederung eines Kraftfahrzeugs bekannt, das als Schätzverfahren ausgestaltet ist und ohne einen gesonderten Temperatursensor am Kompressor auskommt. Dazu ist vorgesehen, dass der Kompressor von einem Steuergerät abgeschaltet wird, wenn ein von diesem berechneter Temperatur-Schätzwert einen oberen Schwellenwert überschreitet, oder eingeschaltet wird bzw. ein Einschalten gestattet wird, wenn ein unterer Schwellenwert unterschritten wird. Dazu wird der jeweils letzte Temperatur-Schätzwert beim Einschalten des Kompressors um einen bestimmten Temperatursprung erhöht, dessen Maß von der Höhe des letzten Schätzwertes abhängig ist. Weiterhin wird der Schätzwert während eines Kompressorbetriebes in vorgegebener Weise erhöht und bei Stillstand des Kompressors in vorgegebener Weise abgesenkt. Nachteilig ist hierbei, dass die für das Verfahren zugrunde gelegten linearen Zusammenhänge in der Praxis in der Regel nicht vorliegen, da bei großen Temperaturdifferenzen die Temperaturänderungen größer sind als bei kleinen Temperaturdifferenzen. Der Temperatursprung findet außerdem in der Realität nicht augenblicklich statt, so daß in diesem Bereich auch die steuerungstechnische Verfügbarkeit des Kompressors nachteilig herabgesetzt ist.By DE 196 21 946 C2 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. For this purpose it is provided that 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. For this purpose, 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. Furthermore, 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, since 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.

Durch EP 1 644 640 B1 ist ein Verfahren der betreffenden Art zur Steuerung des Betriebs des Kompressors bekannt, bei dem der Kompressor von einem Steuergerät zur Vermeidung thermischer Schäden dann abgeschaltet wird, wenn ein von dem Steuergerät berechneter Temperatur-Schätzwert einen oberen Schwellenwert überschreitet. Bei dem bekannten Verfahren berechnet das Steuergerät unter Heranziehung des Temperatur-Schätzwertes als Zustandsgröße eine Abkühlfunktion, die den zeitlichen Verlauf der Abkühlung des Kompressors repräsentiert.By EP 1 644 640 B1 For example, there is known a method of the type in question for controlling the operation of the compressor, wherein the compressor is shut down by a thermal damage control controller when a temperature estimate calculated by the controller exceeds an upper threshold. In the known method, the control unit calculates, using the temperature estimated value as the state variable, a cooling function which represents the time course of the cooling of the compressor.

Der Erfindung liegt die Aufgabe zugrunde, ein Verfahren der im Oberbegriff des Anspruchs 1 genannten Art so weiterzubilden, dass die Abkühlfunktion präziser ermittelbar ist.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.

Diese Aufgabe wird durch die im Anspruch 1 angegebene Lehre gelöst.This object is achieved by the teaching defined in claim 1.

Der Erfindung liegt die Erkenntnis zugrunde, dass die Abkühlfunktion in einem Falle, in dem der Kompressor so betrieben wurde, dass er sich beispielsweise ausschließlich in einem Bereich des Auslassventiles stark erwärmt hat, im übrigen jedoch nicht vollständig oder weitgehend "durchgewärmt" ist, einen anderen Verlauf hat als in einem Falle, in dem der Kompressor so betrieben wurde, dass er beispielsweise nicht nur im Bereich des Auslassventiles stark erwärmt ist, sondern vollständig oder weitgehend "durchgewärmt" ist. Hiervon ausgehend liegt der Erfindung der Gedanke zugrunde, die Abkühlfunktion ausgehend von einem Temperaturgradienten zwischen den Temperaturen an wenigstens zwei zueinander räumlich beabstandeten Stellen des Kompressors zu ermitteln. Dementsprechend sieht die Erfindung vor, dass das Steuergerät die Abkühlfunktion ausgehend von wenigstens einem ersten und einem zweiten Temperatur-Schätzwert ermittelt, die räumlich zueinander beabstandeten Stellen des Kompressors zugeordnet sind, derart, daß die Abkühlfunktion ausgehend von einer Temperaturdifferenz zwischen dem ersten Temperatur-Schätzwert und dem zweiten Temperatur-Schätzwert ermittelt wird. Auf diese Weise lässt sich die Abkühlfunktion wesentlich genauer ermitteln. Ist der Kompressor beispielsweise so betrieben worden, dass er sich überwiegend an einer dem ersten Temperatur-Schätzwert zugeordneten Stelle erwärmt hat, beispielsweise im Bereich seines Auslassventiles, während er sich an einer dem zweiten Temperatur-Schätzwert zugeordneten Stelle, die beispielsweise einer Außenfläche des Gehäuses des Kompressors entspricht, weniger stark erwärmt hat, so ist der Temperaturgradient zwischen den herangezogenen Stellen des Kompressors relativ hoch. Dementsprechend wird sich der Kompressor nach dem Abschalten durch Wärmeabfuhr an die Umgebung relativ schnell abkühlen, so dass das Steuergerät eine Abkühlfunktion berechnet, die einer solchen relativ schnellen Abkühlung entspricht. Ist demgegenüber der Kompressor so betrieben worden, dass er sich sowohl an einer dem ersten Temperatur-Schätzwert zugeordneten Stelle als auch an einer dem zweiten Temperatur-Schätzwert zugeordneten Stelle relativ stark erwärmt hat, so ist der Temperaturgradient zwischen den betrachteten Stellen des Kompressors geringer. In einem solchen Fall wird sich der Kompressor durch Wärmeabfuhr an die Umgebung relativ langsam abkühlen. Dementsprechend berechnet das Steuergerät eine Abkühlfunktion, die einer langsameren Abkühlung des Kompressors entspricht.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. Accordingly, 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. For example, if 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 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. In contrast, 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.

Da sich die Abkühlfunktion mittels des erfindungsgemäßen Verfahrens präziser ermitteln lässt, ist erfindungsgemäß die Reaktionsschnelligkeit der Steuerung des Betriebs des Kompressors erhöht. Insbesondere ist es möglich, den Kompressor relativ schnell wieder einzuschalten, wenn die ermittelte Abkühlfunktion einer schnelleren Abkühlung entspricht. Dadurch sind die Reaktionsmöglichkeiten der Steuerung beim Betrieb des Kompressors erweitert. Beispielsweise ist es möglich, den Kompressor nach einer relativ schnellen Abkühlung sofort wieder in Betrieb zu nehmen, wenn beispielsweise eine Niveauregulierungsanlage eines Kraftfahrzeugs zum Schutz von Fußgängern eine Absenkung der Karosserie des Kraftfahrzeugs erfordert. Auf diese Weise ist die Betriebssicherheit eines mit einer solchen Niveauregulierungsanlage ausgestatteten Kraftfahrzeugs wesentlich erhöht. Die grundsätzliche Art und Weise der Ermittlung der Abkühlfunktion ist dem Fachmann aus der EP 1 644 640 B1 bekannt und wird daher hier nicht näher erläutert.Since the cooling function can be determined more precisely by means of the method according to the invention, the reaction speed of the control of the operation of the compressor is increased according to the invention. In particular, it is possible to restart the compressor relatively quickly, if the determined cooling function corresponds to a faster cooling. As a result, 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. In this way, the reliability of a vehicle equipped with such a level control system motor vehicle is substantially increased. The basic way of determining the cooling function is the expert from the EP 1 644 640 B1 is known and will therefore not be explained here.

Die dem ersten und dem zweiten Temperatur-Schätzwert räumlich zugeordneten Stellen des Kompressors sind entsprechend den jeweiligen Anforderungen, baulichen Gegebenheiten und Betriebszuständen des Kompressors innerhalb weiter Grenzen wählbar. Ausgehend von dem Gedanken, dass sich eine Abkühlung des Kompressors vor allem durch Wärmeabfuhr an die Umgebung vollzieht, sieht eine vorteilhafte Weiterbildung der erfindungsgemäßen Lehre vor, dass eine dem zweiten Temperatur-Schätzwert räumlich zugeordnete Stelle des Kompressors näher an einem auf Umgebungstemperatur befindlichen Bereich liegt als eine dem ersten Temperatur-Schätzwert räumlich zugeordnete Stelle. Auf diese Weise ist die Präzision bei der Ermittlung der Abkühlfunktion weiter erhöht. Die den Temperatur-Schätzwerten zugeordneten Stellen werden hierbei beispielsweise und insbesondere so gewählt, dass sich zwischen diesen Stellen bei einer vorwiegend lokalen Erwärmung des Kompressors, beispielsweise im Bereich des Auslassventiles, ein hoher Temperaturgradient ergibt.The locations of the compressor spatially assigned to the first and the second temperature estimation values can be selected within wide limits in accordance with the respective requirements, constructional conditions and operating conditions of the compressor. Starting from the idea that a cooling of the compressor takes place mainly by heat removal to the environment, an advantageous development of the teaching according to the invention provides that a location of the compressor spatially assigned to the second temperature estimate is closer to an area 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.

Dieser Temperaturgradient ist dann besonders hoch, wenn der erste Temperatur-Schätzwert einer Stelle des Kompressors zugeordnet ist, an der sich der Kompressor im Betrieb relativ schnell erwärmt und/oder wenn der zweite Temperatur-Schätzwert einer Stelle des Kompressors zugeordnet ist, an der sich der Kompressor im Betrieb relativ langsam erwärmt, wie dies vorteilhafte Weiterbildungen der erfindungsgemäßen Lehre vorsehen.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.

Da sich der Kompressor erfahrungsgemäß im Bereich seines Auslassventiles oder seiner Kolbendichtung am schnellsten und an einer Außenfläche seines Gehäuses relativ langsam erwärmt, sehen zweckmäßige Weiterbildungen der Erfindung vor, dass die erste Stelle im Bereich eines Auslassventiles oder einer Kolbendichtung des Kompressors angeordnet ist und/oder dass die zweite Stelle im Bereich einer Außenfläche des Gehäuses des Kompressors, insbesondere im Bereich seines Zylinderkopfes, angeordnet ist. Das Steuergerät kann die Abkühlfunktion unter Heranziehung beliebiger weiterer Zustandsgrößen ermitteln. Eine vorteilhafte Weiterbildung der Erfindung sieht insoweit vor, dass das Steuergerät die Abkühlfunktion unter Heranziehung weiterer Zustandsgrößen, insbesondere der Umgebungstemperatur und/oder der Kompressorspannung und/oder eines Vor- und Gegendruckes des Kompressors, ermittelt. Eine andere vorteilhafte Weiterbildung der Erfindung sieht vor, dass nach einem Ausschalten und Wiedereinschalten des Steuergerätes dasselbe unter Heranziehung der ermittelten Abkühlfunktion und der zwischen dem Ausschalten und Wiedereinschalten vergangenen Zeit ermittelt, zu welchem Zeitpunkt ein unterer Temperatur-Schwellenwert unterschritten wird und der Kompressor wiedereingeschaltet werden kann.Since, according to experience, the compressor heats up relatively quickly in the region of its outlet valve or its piston seal and on an outer surface of its housing, 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 off and restarting the control unit, the same is determined by using the determined cooling function and the time between switching off and restarting, at which time a lower temperature threshold value is exceeded and the compressor can be switched on again ,

Die Erfindung wird nachfolgend anhand eines Ausführungsbeispieles näher erläutert.The invention will be explained in more detail with reference to an embodiment.

Bei einem erfindungsgemäßen Verfahren zur Steuerung des Betriebs eines Kompressors wird der Kompressor zunächst in einem Prüfaufbau verschiedenen Betriebszuständen, insbesondere hinsichtlich der Dauer seines Betriebes, der Umgebungstemperatur, der Kompressorspannung und des Vor- und Gegendruckes des Kompressors, unterworfen. Hierbei wird mittels eines ersten Temperatursensors der zeitliche Verlauf der Temperatur des Kompressors an einer ersten Stelle, die bei diesem Ausführungsbeispiel im Bereich eines Auslassventiles des Kompressors angeordnet ist, gemessen und abgespeichert, insbesondere während der Abkühlung des Kompressors im ausgeschalteten Zustand. Darüber hinaus wird mittels eines zweiten Temperatursensors der zeitliche Verlauf der Temperatur des Kompressors an einer zweiten Stelle gemessen, die bei diesem Ausführungsbeispiel im Bereich des Zylinderkopfes des Kompressors angeordnet ist. Die auf diese Weise für verschiedene Betriebszustände ermittelten Temperaturverläufe werden abgespeichert und in eine Software des Steuergerätes des Kompressors eingespeist, so dass im Einbauzustand des Kompressors, beispielsweise an einer Niveauregulierungsanlage eines Kraftfahrzeuges, von dem Steuergerät Temperatur-Schätzwerte ermittelt werden können, und dementsprechend im Einbauzustand des Kompressors ein Temperatursensor nicht erforderlich ist.In a method according to the invention for controlling the operation of a compressor, the compressor is first subjected to various operating conditions in a test setup, in particular with regard to the duration of its operation, the ambient temperature, the compressor voltage and the pre-pressure and counterpressure of the compressor. Here, by means of a first temperature sensor, 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. In addition, by means of a second temperature sensor, the time profile of the temperature of the compressor is measured at a second location, which is arranged in the region of the cylinder head of the compressor in this embodiment. 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.

Im Einbauzustand des Kompressors wird derselbe durch das Steuergerät derart gesteuert, dass das Steuergerät den Kompressor zur Vermeidung thermischer Schäden dann abschaltet, wenn ein von dem Steuergerät berechneter Temperatur-Schätzwert einen oberen Schwellenwert überschreitet.In the installed state of the compressor, 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.

Während des Betriebs des Kompressors errechnet das Steuergerät zeitlich kontinuierlich oder in Intervallen anhand seiner Software einen ersten Temperatur-Schätzwert, der bei dem Ausführungsbeispiel einer Stelle im Bereich des Auslassventiles des Kompressors zugeordnet ist, und einen zweiten Temperatur-Schätzwert, der bei dem Ausführungsbeispiel einer Stelle im Bereich des Zylinderkopfes des Kompressors zugeordnet ist. Ausgehend von diesen Temperatur-Schätzwerten berechnet das Steuergerät zusätzlich eine Abkühlfunktion, die den zeitlichen Verlauf der Abkühlung des Kompressors nach einem Abschalten repräsentiert. Hierbei ermittelt das Steuergerät die Abkühlfunktion erfindungsgemäß ausgehend von dem ersten und dem zweiten Temperatur-Schätzwert, derart, dass die Abkühlfunktion ausgehend von der Temperaturdifferenz zwischen dem ersten Temperatur-Schätzwert und dem zweiten Temperatur-Schätzwert ermittelt wird.During operation of the compressor, 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. On the basis of these temperature estimates, the control unit additionally calculates a cooling function, which represents the time course of the cooling of the compressor after a shutdown. In this case, 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.

Überschreitet der erste Temperatur-Schätzwert einen oberen Schwellenwert, so schaltet das Steuergerät den Kompressor zur Vermeidung thermischer Schäden ab. Bleibt das Steuergerät nach dem Abschalten des Kompressors eingeschaltet, so errechnet es ausgehend von den Temperatur-Schätzwerten die Abkühlfunktion, aus der abgeleitet werden kann, zu welchem Zeitpunkt der Kompressor wieder eingeschaltet werden kann, ohne dass thermische Schäden in dem Kompressor entstehen. Ist die Temperaturdifferenz zwischen dem ersten und dem zweiten Temperatur-Schätzwert relativ groß, so bedeutet dies, dass der Kompressor vor allem lokal im Bereich seines Auslassventiles relativ stark erwärmt ist, ohne dass der Kompressor relativ stark "durchgewärmt" ist. Daraus ergibt sich eine Abkühlfunktion, die einer schnelleren Abkühlung entspricht, so dass ein unterer Schwellenwert der Temperatur relativ schnell unterschritten wird und der Kompressor dementsprechend relativ schnell wieder eingeschaltet werden kann.If the first temperature estimate exceeds an upper threshold, 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.

Ermittelt das Steuergerät demgegenüber, dass die Temperaturdifferenz zwischen dem ersten und dem zweiten Temperatur-Schätzwert relativ gering ist, so ergibt sich daraus, dass sich der Kompressor nicht ausschließlich im Bereich seines Auslassventiles relativ stark erwärmt, sondern relativ stark "durchgewärmt" ist.On the other hand, if the 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".

Daraus ergibt sich eine Abkühlfunktion, die einer relativ langsamen Abkühlung entspricht, so dass der untere Schwellenwert, bei dem der Kompressor wieder eingeschaltet werden kann, erst nach einer längeren Zeit unterschritten wird.This results in a cooling function, which corresponds to a relatively slow cooling, so that the lower threshold, at which the compressor can be switched on again, is not reached after a long time.

Wird das Steuergerät beim oder kurz nach dem Abschalten des Kompressors abgeschaltet, beispielsweise beim Ausschalten der Zündung des Kraftfahrzeugs, so wird die Abkühlfunktion ausgehend von den für den Zeitpunkt des Abschaltens ermittelten Temperatur-Schätzwerten berechnet, sobald das Steuergerät wieder eingeschaltet wird, also beispielsweise beim Einschalten der Zündung des Kraftfahrzeuges. Ausgehend von der ermittelten Abkühlfunktion und der zwischen dem Ausschalten des Kompressors und dem Wiedereinschalten des Steuergerätes vergangenen Zeit kann das Steuergerät dann ermitteln, zu welchem Zeitpunkt ein unterer Schwellenwert der Temperatur des Kompressors unterschritten ist und der Kompressor dementsprechend wieder eingeschaltet werden kann.If the control unit is switched off during or shortly after switching off the compressor, for example when the ignition of the motor vehicle is switched off, then the cooling function is calculated on the basis of the temperature estimates determined for the time of switch-off as soon as the control unit is switched on again, so for example when switching on the ignition of the motor vehicle. Based on the determined cooling function and the time between switching off the compressor and the reconnection of the control unit past time, the controller can then determine at what time a lower threshold value of the temperature of the compressor is exceeded and the compressor can be switched on again accordingly.

Aufgrund der erfindungsgemäßen Lehre kann die Abkühlfunktion präziser ermittelt werden, da sie erfindungsgemäß nicht ausgehend von einem einzigen Temperatur-Schätzwert, sondern ausgehend von einer Temperaturdifferenz zwischen zwei Temperatur-Schätzwerten ermittelt wird.On the basis of the teaching according to the invention, the cooling function can be determined more precisely, since, according to the invention, it is not determined on the basis of a single temperature estimate, but on the basis of a temperature difference between two temperature estimates.

Die Vorteile der erfindungsgemäßen Lehre ergeben sich bereits dann, wenn ausschließlich die Differenz zwischen zwei Temperaturwerten ermittelt wird. Es ist erfindungsgemäß jedoch auch möglich, die Abkühlfunktion ausgehend von wenigstens zwei Temperaturdifferenzen aus wenigstens drei Temperatur-Schätzwerten zu ermitteln. Eine Heranziehung von zwei oder mehreren Temperaturdifferenzen ermöglicht entsprechen den jeweiligen Anforderungen noch genauere Aussagen über die räumliche Wärmeverteilung in dem Kompressor.The advantages of the teaching according to the invention already arise when only the difference between two temperature values is determined. However, it is also possible according to the invention to determine the cooling function from at least two temperature differences from at least three temperature estimated values. An attraction of two or more temperature differences allows more precise statements about the spatial heat distribution in the compressor according to the respective requirements.

Claims (8)

  1. Method for controlling the operation of a compressor,
    in which the compressor is switched off by a controller in order to avoid thermal damage if an estimated temperature value calculated by the controller exceeds an upper threshold value, and
    in which the controller, utilizing the estimated temperature value as a state variable, calculates a cooling function which represents the course over time of the cooling of the compressor after the compressor has been switched off,
    characterized in that
    the controller determines the cooling function, on the basis of at least a first and a second estimated temperature value which are associated with points on the compressor at a spatial distance from one another, in such a manner that the cooling function is determined on the basis of at least one temperature difference between the first and the second estimated temperature value.
  2. Method according to Claim 1, characterized in that a point on the compressor spatially associated with the second estimated temperature value is located closer to a region which is at ambient temperature than a point associated spatially with the first estimated temperature value.
  3. Method according to Claim 1, characterized in that the first estimated temperature value is associated with a point on the compressor at which the compressor heats up relatively quickly in operation.
  4. Method according to Claim 1, 2 or 3, characterized in that the second estimated temperature value is associated with a point on the compressor at which the compressor heats up relatively slowly in operation.
  5. Method according to any one of the preceding claims, characterized in that the first estimated temperature value is associated with a point which is arranged in the region of a discharge valve or a piston seal of the compressor.
  6. Method according to any one of the preceding claims, characterized in that the second estimated temperature value is associated with a point which is arranged in the region of an outer surface of the housing of the compressor, in particular a cylinder head of the compressor.
  7. Method according to any one of the preceding claims, characterized in that the controller determines the cooling function while taking account of further state variables, in particular the ambient temperature and/or the compressor voltage and/or an admission pressure and/or back pressure of the compressor.
  8. Method according to any one of the preceding claims, characterized in that, after the controller has been switched off and switched on again, the controller determines, while taking account of the cooling function determined and the time which has elapsed between the switching off and switching on again of the controller, the time at which the temperature has fallen below a lower threshold value and at which the compressor can be switched on again.
EP09765657.3A 2008-06-17 2009-04-15 Method for controlling the operation of a compressor Active EP2304238B1 (en)

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DE102008028781A DE102008028781A1 (en) 2008-06-17 2008-06-17 Method for controlling the operation of a compressor
PCT/EP2009/054431 WO2009153077A1 (en) 2008-06-17 2009-04-15 Method for controlling the operation of a compressor

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Publication number Priority date Publication date Assignee Title
US3334808A (en) 1965-10-24 1967-08-08 Lennox Ind Inc Compressor lubrication arrangement
DE1943936A1 (en) 1969-08-29 1971-03-18 Danfoss As Protection arrangement for a compressor
DE3919407A1 (en) 1988-07-14 1990-01-18 Eco Air Drucklufttechnik Gmbh METHOD FOR CONTROLLING A COMPRESSOR AND CONTROL DEVICE
JPH03118719A (en) 1989-09-29 1991-05-21 Seikosha Co Ltd Motor control
DE4333591A1 (en) 1993-10-01 1995-04-06 Bayerische Motoren Werke Ag Controller for switching the electric drive motor, in particular of an air compressor, on and off to match the demand
US5584675A (en) * 1995-09-15 1996-12-17 Devilbiss Air Power Company Cylinder sleeve for an air compressor
DE19621946C2 (en) 1996-05-31 2002-05-29 Daimler Chrysler Ag air suspension
DE19812234C2 (en) 1998-03-20 2002-07-18 Daimler Chrysler Ag Air suspension system for vehicles
DE10120206A1 (en) 2001-04-24 2002-10-31 Wabco Gmbh & Co Ohg Method for controlling a compressor
DE10330121A1 (en) 2003-07-04 2005-02-03 Continental Aktiengesellschaft Method for controlling the operation of a compressor

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DE102008028781A1 (en) 2009-12-24
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US9932978B2 (en) 2018-04-03
US20110052422A1 (en) 2011-03-03

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