EP3256726B1 - Method for stopping a hermetic refrigerant compressor and control system for same - Google Patents

Method for stopping a hermetic refrigerant compressor and control system for same Download PDF

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Publication number
EP3256726B1
EP3256726B1 EP16703334.9A EP16703334A EP3256726B1 EP 3256726 B1 EP3256726 B1 EP 3256726B1 EP 16703334 A EP16703334 A EP 16703334A EP 3256726 B1 EP3256726 B1 EP 3256726B1
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EP
European Patent Office
Prior art keywords
crankshaft
braking torque
reciprocating piston
refrigerant compressor
electric motor
Prior art date
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Revoked
Application number
EP16703334.9A
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German (de)
French (fr)
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EP3256726A1 (en
Inventor
Per Tranekjer Petersen
Ulrich Gries
Fabian Brune
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Secop GmbH
Original Assignee
Nidec Global Appliance Germany GmbH
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Application filed by Nidec Global Appliance Germany GmbH filed Critical Nidec Global Appliance Germany GmbH
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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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • 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
    • 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
    • F04B49/103—Responsive to speed
    • 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
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/127—Braking parameters
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0204—Frequency of the electric current

Definitions

  • the present invention relates to methods for stopping a hermetically sealed refrigerant compressor with a hermetically sealed housing, arranged therein a crankshaft comprising a reciprocating cylinder unit and a crankshaft driving electric motor, and a control unit controlling the electric motor, wherein the control unit, the electric motor in the presence of a Operating signal, preferably a frequency signal operates.
  • the present invention relates to a hermetically sealed refrigerant compressor having a control system with an electronic control unit.
  • Hermetically sealed refrigerant compressors which are used in cooling circuits of various systems and devices, especially in household appliances such as refrigerators and compress refrigerant by means of a reciprocating cylinder unit, are known.
  • the reciprocating cylinder unit comprises a crankshaft which is driven by an electric motor to periodically suck gaseous refrigerant into a cylinder of the reciprocating cylinder unit by means of a reciprocating piston of the reciprocating cylinder unit to compress and eject again from the cylinder. Due to the periodic compression processes, there is a reaction torque of the reciprocating cylinder unit, which has peaks according to the maximum occurring compressions. Correspondingly accompanied mechanical vibrations and noise, which are typically attenuated by suspension of the reciprocating cylinder unit to springs in a (hermetically sealed) housing of the refrigerant compressor.
  • the first group While the first group is switched on reaching a triggering temperature in the volume to be cooled (for example, the refrigerator of a refrigerator) and turned off again when the desired target temperature is reached, in the second group better control is possible because of the different speeds provided different cooling capacities can be.
  • a triggering temperature in the volume to be cooled for example, the refrigerator of a refrigerator
  • variable-speed refrigerant compressors are operated by means of an electronic control unit which controls the refrigerant compressor, specifically the electric motor, as a function of an operating signal.
  • the operating signal is usually generated by a device that is in operative connection with the refrigerant compressor, such as a refrigerator or a freezer. In principle, this can be any signal, with a frequency signal very often being used in practice.
  • the existence of the operating signal is used to signal the electronic control unit that cooling capacity is requested, the electric motor of the refrigerant compressor must be activated.
  • the height of the frequency serves as a measure of the required speed. It represents, as it were, a setpoint for the speed that is generated as a function of the target temperature.
  • the operating signal is detected by the electronic control unit, which controls the electric motor according to this specification.
  • variable-speed refrigerant compressors The problem with such variable-speed refrigerant compressors is usually the stopping process. Such is initiated, for example, when the volume to be cooled has reached its target temperature. It is initiated by first no longer generating an operating signal from the device, ie. the existing operating signal goes out. This process is detected by the electronic control unit and initiated the stopping process, with the aim of stopping the refrigerant compressor, ie. to bring the crankshaft to a standstill.
  • the stalling process is a critical process in terms of noise and mechanical damage to the compressor.
  • the reciprocating cylinder units including crankshaft and electric motor are mounted within the hermetically sealed housing by means of springs, as already described above, in order to compensate for vibrations occurring during operation can.
  • oscillating system is designed so that in normal operation is driven supercritical, ie. the natural frequency of the system, which can lead to leading to the destruction of the refrigerant compressor vibrations must be traversed both at startup, but especially when stopping.
  • the reciprocating cylinder unit continues to run due to the inertia and the kinetic energy for some time, which usually continues to compression processes that contribute significantly to the successive reduction of kinetic energy. Accordingly, the speed and thus the frequency of the compression processes decrease, which in turn can be connected in the housing particularly large deflections of the reciprocating cylinder unit, which can even lead to a striking of the piston-cylinder unit on the housing. Finally, leakage will eventually result in insufficient kinetic energy to complete the compression process.
  • the pressure of the compressed gas in the cylinder then causes a sudden reversal of the rotational movement of the crankshaft, which results in a particularly strong deflection of the piston-cylinder unit is connected in the housing and can also lead to striking the piston-cylinder unit on the housing. Overall, this results in a particularly large noise, with even mechanical damage can occur.
  • the piston-cylinder unit can be selectively braked by the crankshaft is subjected to a braking torque.
  • Different methods are known.
  • the rotational speed of the crankshaft has to be continuously measured and evaluated, i. be compared with a predetermined value. Since the speed measurement system and cost can only be done with a relatively inaccurate resolution (depending on the number of poles of the electric motor), an exact vote of the system with this solution is not possible. In addition, the method described there does not make it possible to take into account other parameters which may be relevant for the moment of application of the braking torque.
  • a stopping method of a refrigerant compressor is known that is intended to prevent breakage of pipes due to vibration.
  • the refrigerant compressor is first decelerated to a first speed V1, which is smaller than Vp, and then to zero speed after a certain period of time.
  • the stopping process is triggered by the detection of a stop signal.
  • the speed of the crankshaft during the stopping process is therefore no longer a relevant parameter for the stopping process itself. Rather, the refrigerant compressor, specifically, the reciprocating cylinder unit is actively controlled during the period, thus driven by the electric motor and therefore the time duration and the reduction rate can be chosen such that it does not cause the refrigeration compressor to accelerate when passing through the critical speeds associated with noise and wear and tear disadvantages.
  • the operating signal is a desired value for the rotational speed of the crankshaft or that a desired value for the rotational speed of the crankshaft can be generated from the operating signal.
  • the rotational speed of the crankshaft is known on the basis of the last operating signal before initiating the stopping process or it is assumed that the electronic control unit controls the electric motor in accordance with this desired value, so that a further measurement of the rotational speed of the crankshaft during the stopping process is no longer necessary according to the invention.
  • the time period can therefore be selected in the case of this preferred embodiment depending on the last known setpoint speed before the stopping process.
  • the determination of the time duration takes place either by calculation or by selection from at least one table, preferably stored in a memory of the control unit.
  • the electronic control unit can calculate an optimal period of time by using an algorithm adapted to the respective refrigerant compressor type or access values already determined in advance, for example in the laboratory.
  • At least one further operating parameter is taken into account in the calculation of the time duration or that the at least one table from which the selection of the time duration takes contains values at least during its generation another operating parameter was taken into account.
  • the at least one further operating parameter can be, for example, the temperature of the refrigerant compressor inside the housing and / or the gas pressure of the refrigerant on the suction side and / or pressure side and / or the outside temperature and / or the total operating hours of the refrigerant compressor.
  • the time duration can be determined more precisely and the stopping process can be optimized in terms of noise and wear technology.
  • the total operating hours can also be taken into account, as a result of which aging processes of the springs and concomitant changes in the spring constants can also influence the duration of time.
  • a braking torque is additionally applied to the crankshaft. Independent of Speed is thus used as the triggering event for the application of the braking torque to the crankshaft, the time elapsed since the operation signal was extinguished.
  • the position of the lifting piston is detected and the braking torque is applied in dependence on the position of the lifting piston of the reciprocating cylinder unit to the crankshaft.
  • the application of the braking torque is not (only) in function of the time duration but in dependence of the piston position after the expiration of the period.
  • the noise or the wear behavior could be further improved, in addition to the end of the period, the braking torque is applied to the crankshaft only when the reciprocating piston is in exactly that position at which was found by experiments that the accelerations / deflections of the housing during the further stopping operation during which the braking torque is applied are a minimum.
  • the position of the lifting piston, at which the braking torque is applied is around that position Position is, in which the reciprocating piston has the lowest speed relative to a complete revolution of the crankshaft.
  • the lowest speed is understood as the lowest measurable speed depending on the method of measurement. Since the piston speed is directly related to the speed of the crankshaft, in most cases the speed of the crankshaft will be measured to determine the position at which the piston has the lowest speed relative to a complete revolution of the crankshaft.
  • the velocity measurement provided in the poles of the stator of the electric motor by the rotation of the rotor connected to the crankshaft is provided as the speed measurement.
  • the accuracy of the speed measurement in this case is limited by the number of poles.
  • the smallest measurable speed (corresponding to the smallest measurable reciprocating piston speed) relative to a complete revolution of the crankshaft can be used as the triggering moment for the application of the braking torque.
  • the position at which the brake torque is applied may also be in a range that is within a crank angle of +/- 25 degrees measured from the position where the reciprocating piston has the lowest speed to a complete revolution of the crankshaft.
  • crankshaft is exposed to the braking torque for a certain period of time, which is preferably between 0.15 s and 0.45 s long. This can be ensured that the stopping process can be safely stopped or the critical speeds can be traversed braked.
  • the period of time can be selected according to a further preferred embodiment of the invention from a, preferably stored in the memory of the control unit table.
  • a great variety of parameters can be stored for the stored time values, in particular operating parameters as above be considered, and so the stopping process to be optimized.
  • the crankshaft is exposed to the braking torque longer than the crankshaft would require at the time of triggering the braking torque for one revolution.
  • the electric motor To generate the braking torque can be used in a conventional manner, the electric motor.
  • the current direction can be reversed by windings of the electric motor compared to the normal operation.
  • the windings may be shorted so that the current generated or induced due to the rotational motion of the electric motor produces a torque opposite the prevailing rotational motion.
  • the latter method is sometimes referred to as "zero vector braking" and generates a dependent on the speed braking torque.
  • Fig. 1 schematically shows a hermetically sealed refrigerant compressor 1, as it is used for example in household appliances, such as refrigerators.
  • the refrigerant compressor 1 comprises a reciprocating cylinder unit 2 with a reciprocating piston 9, which can move up and down in a cylinder (not shown).
  • the reciprocating piston 9 is thereby moved via a crankshaft 3, which is driven by means of an electric motor 4.
  • gaseous refrigerant is sucked into the cylinder, compressed there by means of the reciprocating piston 9 and discharged again from the cylinder.
  • the inlet and outlet of the refrigerant is usually controlled by means of a valve plate mounted on a cylinder head of the cylinder with valves for the inlet and the outlet (not shown).
  • the electric motor 4 is controlled by means of a, preferably electronic control unit 5, which forms part of a control system for the refrigerant compressor 1.
  • the electronic control unit 5 obtains information about the currently desired cooling capacity from the apparatus (e.g., a refrigerator) in which the refrigerant compressor 2 is used.
  • the device preferably sends to the electronic control unit 5 an operating signal, particularly preferably in the form of a frequency signal, wherein in the latter case the required cooling power is proportional to the frequency. If no cooling capacity is required because, for example, a target temperature is reached in a volume to be cooled, no operating signal is generated. The absence of an operating signal is detected by the electronic control unit 5, whereupon it initiates the stopping process.
  • the control unit 5 is connected to a power supply 6, and supplies the electric motor 4 with electrical energy.
  • the power supply 6 is usually the low-voltage network to which the device, preferably household appliance is connected, in which device the refrigerant compressor 1 is used.
  • the reciprocating cylinder unit 2 is arranged in a hermetically sealed housing 7 of the refrigerant compressor 1 and stored therein by means of springs 8.
  • the springs 8 serve to dampen vibrations or deflections of the reciprocating cylinder unit 2 and thus to minimize noise development and to avoid mechanical damage.
  • the vibrations are caused in particular by the repetitive compression processes. Due to the periodic compression processes, there is a reaction torque M R of the reciprocating cylinder unit 2, which has peaks corresponding to the maximum occurring compressions.
  • a speed V of the crankshaft 3 by means of the electric motor 4 is reduced at a reduction rate, the duration ⁇ depending on the value of the last operating signal before Extinguishment is determined.
  • the speed V of the crankshaft 3 is reduced in a controlled manner by the electric motor 4 over the period of time ⁇ .
  • the reduction rate is achieved by a known per se control of the electric motor 4, for example by means of the control unit 5, the supply voltage of the electric motor 4 is reduced by means of a pulse width modulation method.
  • the last operating signal specifically from the value of the last operating signal
  • the current speed of the refrigerant compressor at the time of extinction of the operating signal is closed, i. closed at the initiation of the stopping process, without having to measure this speed.
  • the period of time ⁇ within which the refrigerant compressor controlled by the electric motor 4 with a predetermined reduction rate, which is preferably constant, but in principle can vary over the period of time ⁇ is shut down, can either be recalculated at each stop depending on the duration ⁇ , However, it is particularly preferably read as a function of the time duration ⁇ from a table which is stored in a memory of the electronic control unit.
  • operating parameters such as, for example, the temperature of the refrigerant compressor in the interior of the housing and / or the gas pressure of the refrigerant on the suction side and / or pressure side and / or the outside temperature and / or the total operating hours of the refrigerant compressor can additionally be taken into account in order to reduce noise and wear Optimization of the stopping process to achieve.
  • operating parameters such as, for example, the temperature of the refrigerant compressor in the interior of the housing and / or the gas pressure of the refrigerant on the suction side and / or pressure side and / or the outside temperature and / or the total operating hours of the refrigerant compressor can additionally be taken into account in order to reduce noise and wear Optimization of the stopping process to achieve.
  • values for the period of time ⁇ can be determined, which are then stored in the table.
  • a further optimization of the method according to the invention for stopping a hermetically sealed refrigerant compressor can be achieved by applying a braking torque after the time period ⁇ has elapsed and a defined position of the reciprocating piston 9 is detected.
  • a braking torque after the time period ⁇ has elapsed and a defined position of the reciprocating piston 9 is detected.
  • the position of the reciprocating piston 9 at which the braking torque is applied is the position at which the housing 7 experiences the lowest acceleration values in the course of the further stopping operation in comparison to other reciprocating positions of a complete revolution of the crankshaft 3, in particular the acceleration values are parallel and perpendicular to the crankshaft axis for inferring the optimum reciprocating piston position. Low acceleration values of the housing during the further stopping process at this point cause a slight deflection of the same during the further stopping process.
  • This optimal position of the reciprocating piston 9 is in advance, for example on a prototype of a particular refrigerant compressor type determined by standardized measurement methods in which the acceleration and deflection of the housing, preferably parallel and perpendicular to the crankshaft axis from the time of application of the braking torque to the standstill of the crankshaft starting from different Hubkolbenpositionen a complete crankshaft revolution is measured. It should be noted that this optimum position is refrigerant type specific and may depend on a variety of operating parameters, but in any case can best be determined empirically according to the invention.
  • the optimum position of the reciprocating piston 9 determined from the tests can be stored in a memory of the electronic control unit 5 and the achievement of this position in operation serves as a triggering event for the application of the braking torque. It should be noted at this point that the position determination of the piston in variable speed refrigerant compressors is possible due to the structure of the electric motor 4 due to the voltages induced in the individual poles of the stator by the rotation of the rotor. In principle, however, other methods for determining the position of the reciprocating piston 9 in the cylinder are also suitable.
  • the optimal reciprocating piston position also corresponds to that position of the reciprocating piston 9, in which the reciprocating piston 9 has the lowest speed relative to a complete revolution of the crankshaft 3 or 25 ° before or after this position.
  • This embodiment has the advantage that the speed of the reciprocating piston 9 can be determined via the rotational speed of the crankshaft 3 during normal operation and thereby determines that position at which the reciprocating piston 9 the lowest speed relative to a complete revolution of the crankshaft 3 at any time can be.
  • Fig. 2 shows by way of example a time profile of the speed V of the crankshaft 3 when using the method according to the invention for stopping the refrigerant compressor 1.
  • the speed V is at a predetermined by the operating signal, corresponding to a required cooling power value v 1 (eg 4000 min -1 ), which corresponds to a certain operating state of the refrigerant compressor 1.
  • v 1 eg 4000 min -1
  • the speed V decreases over the entire time period ⁇ .
  • the period of time ⁇ is preferably selected from stored tables in order to take into account the operating state present until immediately before time t 0 .
  • the reduction rate is also preferably taken from stored tables, which have been obtained analogously to the tables for ⁇ , wherein the reduction rate over the time period ⁇ can also vary.
  • Duration ⁇ and the reduction rate are in any case so coordinated that a noise and wear technology optimal stopping process can be driven.
  • Period ⁇ and reduction rate are then coordinated so that it is ensured that the application of the braking torque takes place at a time in which Compressor is still operated in a supercritical state.
  • the operating parameters influencing this can be included in the time period ⁇ and / or in the reduction rate, as well as by the choice of the time duration ⁇ and / or the reduction rate or tuning of the same noise and wear optimization.
  • the application of the braking torque is carried out by driving the electric motor 4 by the electronic control unit 5 in a conventional manner, so that this ⁇ after the expiration of the time period generates a braking torque to which the crankshaft 3 is exposed.
  • the braking torque is applied over a certain period .DELTA.t.
  • the time period .DELTA.t is also selected from stored tables in order to take into account a wide variety of operating situations.
  • the period ⁇ t is sufficiently long, it can thus be guaranteed that after the expiry of the period .DELTA.t, the crankshaft 3 is no longer rotating.
  • the time .DELTA.t for this is in a range of 0.15 s to 0.45 s.
  • Figure 4 shows that particularly preferred variant of the invention, according to which after the time period ⁇ and before applying the braking torque within a time period ⁇ 1 nor the optimal piston position is detected.
  • the duration of this period depends on the Hubkolbenposition after the expiry of the time ⁇ and the required rotational angle of the crankshaft 3 until reaching the optimum piston position.
  • Fig.2 shows the solid line drawn over the period .DELTA.t the case that the crankshaft 3 comes to a standstill exactly at the expiration of the period .DELTA.t.
  • the dashed line over the period .DELTA.t illustrates the case that the crankshaft 3 is no longer rotating even before the expiration of the period .DELTA.t.
  • the dash-dotted line in Fig. 2 serves to Illustrating that - avoidable by a suitable choice of ⁇ t - If the crankshaft 3 continues to rotate even after the time span ⁇ t has elapsed.

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

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft Verfahren zum Anhalten eines hermetisch gekapselten Kältemittelverdichters mit einem hermetisch dichten Gehäuse, darin angeordnet eine eine Kurbelwelle umfassende Hubkolben-Zylinder-Einheit und ein die Kurbelwelle antreibender Elektromotor, sowie eine den Elektromotor steuernde Steuereinheit, wobei die Steuereinheit den Elektromotor bei Vorliegen eines Betriebssignals, vorzugsweise eines Frequenzsignals, betreibt.The present invention relates to methods for stopping a hermetically sealed refrigerant compressor with a hermetically sealed housing, arranged therein a crankshaft comprising a reciprocating cylinder unit and a crankshaft driving electric motor, and a control unit controlling the electric motor, wherein the control unit, the electric motor in the presence of a Operating signal, preferably a frequency signal operates.

Weiters betrifft die vorliegende Erfindung einen hermetisch gekapselten Kältemittelverdichter mit einem Steuerungssystem mit einer elektronische Steuereinheit.Furthermore, the present invention relates to a hermetically sealed refrigerant compressor having a control system with an electronic control unit.

STAND DER TECHNIKSTATE OF THE ART

Hermetisch gekapselte Kältemittelverdichter, die in Kühlkreisläufen diverser Anlagen und Geräte, insbesondere in Haushaltsgeräten wie Kühlschränken zum Einsatz kommen und mittels einer Hubkolben-Zylinder-Einheit Kältemittel verdichten, sind bekannt. Üblicherweise umfasst die Hubkolben-Zylinder-Einheit eine Kurbelwelle, die mittels eines Elektromotors angetrieben wird, um periodisch gasförmiges Kältemittel in einen Zylinder der Hubkolben-Zylinder-Einheit einzusaugen, mittels eines Hubkolbens der Hubkolben-Zylinder-Einheit zu komprimieren und wieder aus dem Zylinder auszustoßen. Aufgrund der periodischen Kompressionsvorgänge kommt es zu einem Reaktionsdrehmoment der Hubkolben-Zylinder-Einheit, welches entsprechend der maximal auftretenden Kompressionen Spitzen aufweist. Entsprechend einher gehen mechanische Vibrationen und eine Geräuschentwicklung, welche typischerweise durch eine Aufhängung der Hubkolben-Zylinder-Einheit an Federn in einem (hermetisch dichten) Gehäuse des Kältemittelverdichters gedämpft werden sollen.Hermetically sealed refrigerant compressors, which are used in cooling circuits of various systems and devices, especially in household appliances such as refrigerators and compress refrigerant by means of a reciprocating cylinder unit, are known. Typically, the reciprocating cylinder unit comprises a crankshaft which is driven by an electric motor to periodically suck gaseous refrigerant into a cylinder of the reciprocating cylinder unit by means of a reciprocating piston of the reciprocating cylinder unit to compress and eject again from the cylinder. Due to the periodic compression processes, there is a reaction torque of the reciprocating cylinder unit, which has peaks according to the maximum occurring compressions. Correspondingly accompanied mechanical vibrations and noise, which are typically attenuated by suspension of the reciprocating cylinder unit to springs in a (hermetically sealed) housing of the refrigerant compressor.

Grundsätzlich zu unterscheiden ist zwischen Kältemittelverdichtern, die mit fixer Drehzahl arbeiten und jenen, die mit variabler Drehzahl betrieben werden können.A fundamental distinction should be made between refrigerant compressors, which operate at fixed speed and those that can be operated at variable speed.

Während die erste Gruppe bei Erreichen einer Auslösetemperatur im zu kühlenden Volumen (beispielsweise der Kühlraum eines Kühlschranks) eingeschalten und bei Erreichen der gewünschten Zieltemperatur wieder ausgeschalten werden, ist bei der zweiten Gruppe eine bessere Regelung möglich, da aufgrund der unterschiedlichen Drehzahlen verschiedene Kühlleistungen zur Verfügung gestellt werden können.While the first group is switched on reaching a triggering temperature in the volume to be cooled (for example, the refrigerator of a refrigerator) and turned off again when the desired target temperature is reached, in the second group better control is possible because of the different speeds provided different cooling capacities can be.

Dabei ist es in der Praxis vorgesehen, dass derartige Kältemittelverdichter mit variabler Drehzahl mittels einer elektronischen Steuereinheit betrieben werden, die in Abhängigkeit eines Betriebssignals den Kältemittelverdichter, konkret den Elektromotor, steuert. Das Betriebssignal wird in der Regel von einem Gerät generiert, das in Wirkverbindung mit dem Kältemittelverdichter steht, beispielsweise von einem Kühlschrank oder einer Gefriertruhe. Es kann sich dabei grundsätzlich um ein beliebiges Signal handeln, wobei in der Praxis sehr oft ein Frequenzsignal zum Einsatz kommt. Die Existenz des Betriebssignals dient dazu der elektronischen Steuereinheit zu signalisieren, dass Kälteleistung angefordert wird, der Elektromotor des Kältemittelverdichters aktiviert werden muss. Die Höhe der Frequenz dient als Maß für die geforderte Drehzahl. Sie stellt sozusagen einen Sollwert für die Drehzahl dar, der in Abhängigkeit von der Zieltemperatur generiert wird. Das Betriebssignal wird von der elektronischen Steuereinheit detektiert, die den Elektromotor entsprechend dieser Vorgabe steuert.In practice, it is provided that such variable-speed refrigerant compressors are operated by means of an electronic control unit which controls the refrigerant compressor, specifically the electric motor, as a function of an operating signal. The operating signal is usually generated by a device that is in operative connection with the refrigerant compressor, such as a refrigerator or a freezer. In principle, this can be any signal, with a frequency signal very often being used in practice. The existence of the operating signal is used to signal the electronic control unit that cooling capacity is requested, the electric motor of the refrigerant compressor must be activated. The height of the frequency serves as a measure of the required speed. It represents, as it were, a setpoint for the speed that is generated as a function of the target temperature. The operating signal is detected by the electronic control unit, which controls the electric motor according to this specification.

Problematisch bei derartigen Kältemittelverdichtern mit variabler Drehzahl ist in der Regel der Anhaltevorgang. Ein solcher wird beispielsweise dann eingeleitet, wenn das zu kühlende Volumen seine Zieltemperatur erreicht hat. Er wird eingeleitet indem zunächst vom Gerät kein Betriebssignal mehr generiert wird, dh. das bestehende Betriebssignal erlischt. Dieser Vorgang wird von der elektronischen Steuereinheit erkannt und der Anhaltevorgang eingeleitet, mit dem Ziel, den Kältemittelverdichter anzuhalten, dh. die Kurbelwelle zum Stillstand zu bringen.The problem with such variable-speed refrigerant compressors is usually the stopping process. Such is initiated, for example, when the volume to be cooled has reached its target temperature. It is initiated by first no longer generating an operating signal from the device, ie. the existing operating signal goes out. This process is detected by the electronic control unit and initiated the stopping process, with the aim of stopping the refrigerant compressor, ie. to bring the crankshaft to a standstill.

Der Anhaltevorgang ist jedoch ein kritischer Vorgang hinsichtlich Geräuschentwicklung und mechanischer Beschädigung des Kompressors.However, the stalling process is a critical process in terms of noise and mechanical damage to the compressor.

Grundsätzlich sind die Hubkolben-Zylinder-Einheiten samt Kurbelwelle und Elektromotor innerhalb des hermetisch dichten Gehäuses mittels Federn gelagert, wie dies bereits weiter oben beschrieben wurde, um während des Betriebs auftretende Vibrationen ausgleichen zu können. Das sich aus diesem Umstand ergebende, schwingende System ist so ausgelegt, dass im Normalbetrieb überkritisch gefahren wird, dh. die Eigenfrequenz des Systems, bei welcher es zu bis zur Zerstörung des Kältemittelverdichters führenden Vibrationen kommen kann, muss sowohl beim Hochfahren, insbesondere aber auch beim Anhalten durchfahren werden.Basically, the reciprocating cylinder units including crankshaft and electric motor are mounted within the hermetically sealed housing by means of springs, as already described above, in order to compensate for vibrations occurring during operation can. The resulting from this circumstance, oscillating system is designed so that in normal operation is driven supercritical, ie. the natural frequency of the system, which can lead to leading to the destruction of the refrigerant compressor vibrations must be traversed both at startup, but especially when stopping.

Schaltet man den Elektromotor beim Anhalten einfach ab, läuft die Hubkolben-Zylinder-Einheit aufgrund der Massenträgheit und der vorhandenen kinetischen Energie noch eine Zeitlang weiter, wobei es in der Regel weiterhin zu Kompressionsvorgängen kommt, welche maßgeblich zur sukzessiven Reduktion der kinetischen Energie beitragen. Entsprechend nehmen die Drehzahl und damit auch die Frequenz der Kompressionsvorgänge ab, womit wiederum besonders große Auslenkungen der Hubkolben-Zylinder-Einheit im Gehäuse verbunden sein können, die sogar zu einem Anschlagen der Hubkolben-Zylinder-Einheit am Gehäuse führen können. Auch führt das Auslaufenlassen schließlich dazu, dass irgendwann nicht mehr genug kinetische Energie vorhanden ist, um den Kompressionsvorgang vollständig auszuführen. Durch den Druck des im Zylinder komprimierten Gases kommt es dann zu einer ruckartigen Umkehrung der Drehbewegung der Kurbelwelle, was mit einer besonders starken Auslenkung der Kolben-Zylinder-Einheit im Gehäuse verbunden ist und ebenfalls zum Anschlagen der Kolben-Zylinder-Einheit am Gehäuse führen kann. Insgesamt ergibt sich dadurch eine besonders große Geräuschentwicklung, wobei sogar mechanische Schäden auftreten können.If you turn off the electric motor when stopping simply, the reciprocating cylinder unit continues to run due to the inertia and the kinetic energy for some time, which usually continues to compression processes that contribute significantly to the successive reduction of kinetic energy. Accordingly, the speed and thus the frequency of the compression processes decrease, which in turn can be connected in the housing particularly large deflections of the reciprocating cylinder unit, which can even lead to a striking of the piston-cylinder unit on the housing. Finally, leakage will eventually result in insufficient kinetic energy to complete the compression process. The pressure of the compressed gas in the cylinder then causes a sudden reversal of the rotational movement of the crankshaft, which results in a particularly strong deflection of the piston-cylinder unit is connected in the housing and can also lead to striking the piston-cylinder unit on the housing. Overall, this results in a particularly large noise, with even mechanical damage can occur.

Um dies zu verhindern, kann die Hubkolben-Zylinder-Einheit gezielt abgebremst werden, indem die Kurbelwelle einem Bremsmoment ausgesetzt wird. Dabei sind unterschiedliche Verfahren bekannt.To prevent this, the piston-cylinder unit can be selectively braked by the crankshaft is subjected to a braking torque. Different methods are known.

Aus der EP 2669519 A1 bzw. US 2014072451 A1 ist es beispielsweise bekannt, das Bremsmoment nicht sofort, d.h. nach dem den Anhaltevorgang einleitenden Erlöschen des Betriebssignals anzulegen, sondern zunächst lediglich das Antriebsmoment des Elektromotors wegzuschalten, so dass die Kurbelwelle alleine, aufgrund der gespeicherten kinetischen Energie so lange weiterdreht, bis sich die Drehgeschwindigkeit der Hubkolben-Zylinder-Einheit bzw. der Kurbelwelle unter einen vorgegebenen Drehgeschwindigkeitswert reduziert hat. Erst wenn dieser Wert unterschritten ist, wird das Bremsmoment mittels des Elektromotors an die Kurbelwelle angelegt und der Anhaltevorgang abgeschlossen.From the EP 2669519 A1 or. US 2014072451 A1 For example, it is known not to apply the braking torque immediately, ie after the stopping process initiating extinction of the operating signal, but initially only wegzuschalten the drive torque of the electric motor, so that the crankshaft alone continues to rotate due to the stored kinetic energy until the rotational speed of the Has reduced reciprocating cylinder unit or the crankshaft below a predetermined rotational speed value. Only when this value is undershot, the braking torque is applied by means of the electric motor to the crankshaft and the stopping process is completed.

Entsprechend muss während des Anhaltens laufend die Drehgeschwindigkeit der Kurbelwelle gemessen und ausgewertet, i.e. mit einem vorgegebenen Wert verglichen werden. Da die Drehzahlmessung system- und kostenbedingt nur mit einer relativ ungenauen Auflösung erfolgen kann (abhängig von der Polzahl des Elektromotors), ist eine exakte Abstimmung des Systems mit dieser Lösung nicht möglich. Darüberhinaus ermöglicht es das dort beschriebene Verfahren nicht, auch andere Parameter zu berücksichtigen, die für den Zeitpunkt des Anlegens des Bremsmomentes relevant sein können.Accordingly, during stoppage, the rotational speed of the crankshaft has to be continuously measured and evaluated, i. be compared with a predetermined value. Since the speed measurement system and cost can only be done with a relatively inaccurate resolution (depending on the number of poles of the electric motor), an exact vote of the system with this solution is not possible. In addition, the method described there does not make it possible to take into account other parameters which may be relevant for the moment of application of the braking torque.

Aus der Bedienungsanleitung " Secop XV Controllers Attached Electronic Unit Operating Instructions (November 2014 )" ist es bekannt, beim Anhalten eines einen Elektromotor aufweisenden Kältemittelverdichters nach dem Erlöschen eines Betriebssignals die Drehzahl des Elektromotors mit einer konstanten Verringerungsrate zu verringern, wobei der Kältemittelverdichter hierbei aktiv angetrieben wird.From the manual " Secop XV Controllers Attached Electronic Unit Operating Instructions (November 2014 ) "it is known when stopping an electric motor having Refrigerant compressor after the cessation of an operating signal to reduce the rotational speed of the electric motor at a constant rate of reduction, wherein the refrigerant compressor is actively driven in this case.

Aus der EP 2759788 A1 ist ein Anhalteverfahren eines Kältemittelkompressors bekannt, das brechende Leitungen in Folge von Vibrationen vermeiden soll. Bei diesem Anhalteverfahren wird der Kältemittelkompressor ausgehend von einer Geschwindigkeit Vp im Betriebszustand zunächst auf eine erste Geschwindigkeit V1, die kleiner ist als Vp, abgebremst und anschließend nach einer gewissen Zeitspanne auf Geschwindigkeit null. Dabei wird das Anhalteverfahren durch die Detektion eines Stop-Signals ausgelöst.From the EP 2759788 A1 For example, a stopping method of a refrigerant compressor is known that is intended to prevent breakage of pipes due to vibration. In this stopping method, starting from a speed Vp in the operating state, the refrigerant compressor is first decelerated to a first speed V1, which is smaller than Vp, and then to zero speed after a certain period of time. The stopping process is triggered by the detection of a stop signal.

AUFGABE DER ERFINDUNGOBJECT OF THE INVENTION

Es ist daher Aufgabe der vorliegenden Erfindung, ein alternatives, vereinfachtes Verfahren zum Anhalten von hermetisch gekapselten Kältemittelverdichtern sowie ein Steuerungssystem für diese zur Verfügung zu stellen, welche weniger fehleranfällig sind und darüberhinaus auch die Möglichkeit schaffen, den Anhaltevorgang geräusch- und verschleißtechnisch zu optimieren, in dem auch verschiedenste Betriebsparameter berücksichtigt werden können.It is therefore an object of the present invention to provide an alternative, simplified method for stopping hermetically sealed refrigerant compressors and a control system for these are available, which are less prone to error and also create the opportunity to optimize the stopping process noise and wear, in which also various operating parameters can be considered.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Diese Aufgabe wird durch ein Verfahren gemäß Anspruch 1 gelöst.This object is achieved by a method according to claim 1.

Die Drehzahl der Kurbelwelle während des Anhaltevorgangs ist somit für den Anhaltevorgang selbst kein relevanter Parameter mehr. Vielmehr wird der Kältemittelverdichter, konkret, die Hubkolben-Zylinder-Einheit während der Zeitdauer aktiv gesteuert, somit vom Elektromotor angetrieben und kann daher die Zeitdauer und die Verringerungsrate derart gewählt werden, dass es beim Durchfahren der kritischen Drehzahlen nicht zu einem Aufschaukeln des Kältemittelverdichters und den damit verbundenen geräusch- und verschleißtechnischen Nachteilen kommt.The speed of the crankshaft during the stopping process is therefore no longer a relevant parameter for the stopping process itself. Rather, the refrigerant compressor, specifically, the reciprocating cylinder unit is actively controlled during the period, thus driven by the electric motor and therefore the time duration and the reduction rate can be chosen such that it does not cause the refrigeration compressor to accelerate when passing through the critical speeds associated with noise and wear and tear disadvantages.

Gemäß einer besonders bevorzugten Ausführungsvariante der Erfindung ist es vorgesehen, dass es sich bei dem Betriebssignal um einen Sollwert für die Drehzahl der Kurbelwelle handelt bzw. dass aus dem Betriebssignal ein Sollwert für die Drehzahl der Kurbelwelle generiert werden kann bzw. wird. Die Drehzahl der Kurbelwelle ist aufgrund des letzten Betriebssignals vor dem Einleiten des Anhaltevorgangs bekannt bzw. wird angenommen, dass die elektronische Steuereinheit den Elektromotor entsprechend dieses Sollwertes steuert, so dass eine weiterführende Messung der Drehzahl der Kurbelwelle während des Anhaltevorgangs erfindungsgemäß nicht mehr notwendig ist. Die Zeitdauer kann daher im Falle dieser bevorzugten Ausführungsvariante in Abhängigkeit der letzten bekannten Solldrehzahl vor dem Anhaltevorgang gewählt werden.According to a particularly preferred embodiment of the invention, it is provided that the operating signal is a desired value for the rotational speed of the crankshaft or that a desired value for the rotational speed of the crankshaft can be generated from the operating signal. The rotational speed of the crankshaft is known on the basis of the last operating signal before initiating the stopping process or it is assumed that the electronic control unit controls the electric motor in accordance with this desired value, so that a further measurement of the rotational speed of the crankshaft during the stopping process is no longer necessary according to the invention. The time period can therefore be selected in the case of this preferred embodiment depending on the last known setpoint speed before the stopping process.

Erfindungsgemäß ist es vorgesehen, dass die Bestimmung der Zeitdauer entweder durch Berechnung erfolgt oder durch Auswahl aus zumindest einer, vorzugsweise in einem Speicher der Steuereinheit hinterlegten, Tabelle. Dadurch kann die elektronische Steuereinheit durch Anwendung eines auf den jeweiligen Kältemittelverdichtertyp angepassten Algorithmus, eine optimale Zeitdauer berechnen bzw. auf bereits im Vorfeld, beispielsweise im Labor bestimmte Werte zugreifen.According to the invention, it is provided that the determination of the time duration takes place either by calculation or by selection from at least one table, preferably stored in a memory of the control unit. As a result, the electronic control unit can calculate an optimal period of time by using an algorithm adapted to the respective refrigerant compressor type or access values already determined in advance, for example in the laboratory.

Gemäß einer weiteren bevorzugten Ausführungsvariante der Erfindung kann es dabei vorgesehen sein, dass bei der Berechnung der Zeitdauer zumindest ein weiterer Betriebsparameter berücksichtigt wird bzw. dass die zumindest eine Tabelle, aus welcher die Auswahl der Zeitdauer erfolgt, Werte enthält, bei deren Erstellung zumindest ein weiterer Betriebsparameter berücksichtigt wurde. Konkret kann es sich bei dem zumindest einen weiteren Betriebsparameter beispielsweise um die Temperatur des Kältemittelverdichters im Inneren des Gehäuses handeln und/oder um den Gasdruck des Kältemittels saugseitig und/oder druckseitig und/oder die Außentemperatur und/oder die Gesamtbetriebsstunden des Kältemittelverdichters. Durch Berücksichtigung weiterer Betriebsparameter kann die Zeitdauer noch exakter bestimmt werden und der Anhaltevorgang geräusch- und verschleißtechnisch optimiert werden. Neben den üblichen physikalischen Messgrößen können dabei auch die Gesamtbetriebsstunden berücksichtigt werden, wodurch auch Alterungsprozesse der Federn und damit einhergehende Veränderungen der Federkonstanten die Zeitdauer beeinflussen können.In accordance with a further preferred embodiment variant of the invention, it can be provided that at least one further operating parameter is taken into account in the calculation of the time duration or that the at least one table from which the selection of the time duration takes contains values at least during its generation another operating parameter was taken into account. Specifically, the at least one further operating parameter can be, for example, the temperature of the refrigerant compressor inside the housing and / or the gas pressure of the refrigerant on the suction side and / or pressure side and / or the outside temperature and / or the total operating hours of the refrigerant compressor. By taking into account further operating parameters, the time duration can be determined more precisely and the stopping process can be optimized in terms of noise and wear technology. In addition to the usual physical measured variables, the total operating hours can also be taken into account, as a result of which aging processes of the springs and concomitant changes in the spring constants can also influence the duration of time.

Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist es vorgesehen, dass nach Ablauf der Zeitdauer zusätzlich ein Bremsmoment an die Kurbelwelle angelegt wird. Unabhängig von der Drehzahl wird damit die seit des Erlöschens des Betriebssignals vergangene Zeit als auslösendes Ereignis für das Anlegen des Bremsmomentes an die Kurbelwelle herangezogen. In Kombination mit den zuvor beschriebenen Vorteilen, kann dadurch eine weitere geräusch- und verschleißtechnische Optimierung des Anhaltevorgangs vorgenommen werden.According to a further preferred embodiment of the invention, it is provided that, after the time has elapsed, a braking torque is additionally applied to the crankshaft. Independent of Speed is thus used as the triggering event for the application of the braking torque to the crankshaft, the time elapsed since the operation signal was extinguished. In combination with the advantages described above, a further noise and wear optimization of the stopping process can be carried out.

Gemäß einer besonders bevorzugten Ausführungsvariante der Erfindung ist es vorgesehen, dass die Position des Hubkolbens detektiert wird und das Bremsmoment in Abhängigkeit der Position des Hubkolbens der Hubkolben-Zylinder-Einheit an die Kurbelwelle angelegt wird. Gemäß dieser besonders bevorzugten Ausführungsvariante der Erfindung erfolgt das Anlegen des Bremsmomentes nicht (nur) in Abhängigkeit der Zeitdauer sondern in Abhängigkeit der Kolbenposition nach Ablauf der Zeitdauer. Dadurch ist eine weitere geräusch- und verschleißtechnische Optimierung des Anhaltevorgangs möglich. Herauszustreichen ist an dieser Stelle, dass jene Kolbenposition, die zum Zeitpunkt des Anlegens des Bremsmomentes von Hubkolben eingenommen wird, einen ganz wesentlichen Einfluss auf die Geräusch- und Verschleißentwicklung des Kältemittelverdichters hat und das Anlegen des Bremsmomentes in Abhängigkeit der Hubkolbenposition unabhängig von den anderen in dieser Anmeldung beschriebenen Verfahrensschritten, insbesondere das Anlegen des Bremsmomentes in Abhängigkeit von am Gehäuse gemessenen Beschleunigungswerten bzw. minimalen Kolbengeschwindigkeiten, wie weiter unten im Detail beschrieben, eine wesentliche Verbesserung gegenüber den aus dem Stand der Technik bekannten Verfahren mit sich bringt.According to a particularly preferred embodiment of the invention, it is provided that the position of the lifting piston is detected and the braking torque is applied in dependence on the position of the lifting piston of the reciprocating cylinder unit to the crankshaft. According to this particularly preferred embodiment of the invention, the application of the braking torque is not (only) in function of the time duration but in dependence of the piston position after the expiration of the period. As a result, a further noise and wear optimization of the stopping process is possible. It should be emphasized at this point that that piston position, which is assumed at the time of application of the braking torque of the reciprocating piston, has a very significant influence on the noise and wear development of the refrigerant compressor and the application of the braking torque depending on the reciprocating position independently of the others in this Application described method steps, in particular the application of the braking torque as a function of measured at the housing acceleration values or minimum piston speeds, as described in detail below, brings about a significant improvement over the known from the prior art method.

Erfindungsgemäß ist es dabei gemäß einer weiteren bevorzugten Ausführungsvariante vorgesehen, dass es sich bei der Position des Hubkolbens, bei welcher das Bremsmoment angelegt wird, um jene Position handelt, bei welcher das Gehäuse im Zuge des weiteren Anhaltevorgangs im Vergleich zu anderen Hubkolbenpositionen einer vollständigen Umdrehung der Kurbelwelle die geringsten Beschleunigungswerte erfährt.According to the invention, it is provided according to a further preferred embodiment, that it is at the position of the reciprocating piston, in which the braking torque is applied to that position at which the housing in the course of further stopping compared to other Hubkolbenpositionen a complete revolution of the Crankshaft experiences the lowest acceleration values.

Versuche unter standardisierten, reproduzierbaren Bedingungen haben gezeigt, dass jene Hubkolbenposition, bei welcher das Bremsmoment angelegt wird, ganz wesentlichen Einfluss auf die Geräuschentwicklung während des Anhaltevorgangs hat. Je nach Hubkolbenposition kommt es zu unterschiedlichen Beschleunigungen des Gehäuses und damit einhergehend, Auslenkungen des Gehäuses und damit wiederum einhergehend zu stärkerer bzw. geringerer Geräuschentwicklung. Es wurde weiters festgestellt, dass sich für jeden Kältemittelverdichtertyp eine Hubkolbenposition (optimale Hubkolbenposition) bestimmen lässt, bei welcher im Vergleich zu anderen Hubkolbenpositionen einer kompletten Umdrehung, während des angelegten Bremsmomentes die geringste Beschleunigung/Auslenkung des Gehäuses auftritt. In Folge konnte daher die Geräuschentwicklung bzw. das Verschleißverhalten nochmals verbessert werden, in dem zusätzlich zum Ablauf der Zeitdauer, das Bremsmoment erst dann an die Kurbelwelle angelegt wird, wenn sich der Hubkolben in genau jener Position befindet, bei welcher durch Versuche herausgefunden wurde, dass die Beschleunigungen/Auslenkungen des Gehäuses während des weiteren Anhaltevorgangs, während welchem das Bremsmoment angelegt ist, ein Minimum sind.Experiments under standardized, reproducible conditions have shown that the position of the piston at which the braking torque is applied has a very significant effect on the Noise during the stopping process has. Depending on the Hubkolbenposition it comes to different accelerations of the housing and concomitantly, deflections of the housing and thus in turn to greater or lesser noise. It has also been found that for each refrigerant compressor type, a reciprocating position (optimum reciprocating position) can be determined in which the lowest acceleration / displacement of the housing occurs compared to other reciprocating positions of a complete revolution during the applied braking torque. As a result, therefore, the noise or the wear behavior could be further improved, in addition to the end of the period, the braking torque is applied to the crankshaft only when the reciprocating piston is in exactly that position at which was found by experiments that the accelerations / deflections of the housing during the further stopping operation during which the braking torque is applied are a minimum.

Alternativ dazu ist es gemäß einer bevorzugten Ausführungsvariante der Erfindung vorgesehen, dass es sich bei der Position des Hubkolbens, bei welcher das Bremsmoment angelegt wird, um eine jener Positionen handelt, in welchen das Gehäuse im Zuge des weiteren Anhaltevorgangs im Vergleich zu anderen Hubkolbenpositionen einer kompletten Umdrehung der Kurbelwelle nicht mehr als 120% der geringsten Beschleunigungswerte erfährt. Die durchgeführten Versuche haben ergeben, dass bei geringen Abweichungen um die optimale Hubkolbenposition, dennoch im Vergleich zu den verbleibenden Hubkolbenpositionen eine deutlich merkbare geräuschtechnische Verbesserung während des Anhaltevorgangs erzielbar ist.Alternatively, it is provided according to a preferred embodiment of the invention, that it is at the position of the reciprocating piston, in which the braking torque is applied to one of those positions in which the housing in the course of further stopping operation compared to other Hubkolbenpositionen a complete Rotation of the crankshaft does not experience more than 120% of the lowest acceleration values. The tests carried out have shown that, with slight deviations around the optimum reciprocating piston position, a clearly noticeable noise improvement during the stopping process can still be achieved in comparison with the remaining reciprocating piston positions.

Anzumerken ist an dieser Stelle, dass in den Versuchen die Beschleunigungswerte des Gehäuses parallel und senkrecht zur Kurbelwellenachse als besonderen Einfluss auf die Geräuschentwicklung und den mechanischen Verschleiß habend, erkannt wurden.It should be noted at this point that in the tests, the acceleration values of the housing parallel and perpendicular to the crankshaft axis as a special influence on the noise and the mechanical wear having recognized.

Gemäß einer alternativen, besonders bevorzugten Ausführungsvariante der Erfindung ist es vorgesehen, dass es sich bei der Position des Hubkolbens, bei welcher das Bremsmoment angelegt wird, um jene Position handelt, bei welcher der Hubkolben die geringste Geschwindigkeit bezogen auf eine komplette Umdrehung der Kurbelwelle aufweist. Unter der geringsten Geschwindigkeit wird in Abhängigkeit der Messmethode die geringste messbare Geschwindigkeit verstanden. Da die Kolbengeschwindigkeit unmittelbar mit der Drehzahl der Kurbelwelle zusammenhängt, wird in den meisten Fällen die Drehzahl der Kurbelwelle gemessen werden, um jene Position zu ermitteln, bei welcher der Hubkolben die geringste Geschwindigkeit bezogen auf eine komplette Umdrehung der Kurbelwelle aufweist. Darüberhinaus bietet sich bei Kältemittelverdichtern mit variabler Geschwindigkeit als Geschwindigkeitsmessung die in den Polen des Stators des Elektromotors durch die Umdrehung des mit der Kurbelwelle verbundenen Rotors induzierten Spannungen an. Es versteht sich, dass die Genauigkeit der Geschwindigkeitsmessung in diesem Fall durch die Polzahl limitiert ist. In diesem Fall kann erfindungsgemäß eben die kleinste messbare Drehzahl (entspricht der kleinesten messbaren Hubkolbengeschwindigkeit) bezogen auf eine komplette Umdrehung der Kurbelwelle als Auslösezeitpunkt für das Anlegen des Bremsmomentes herangezogen werden.According to an alternative, particularly preferred embodiment variant of the invention, it is provided that the position of the lifting piston, at which the braking torque is applied, is around that position Position is, in which the reciprocating piston has the lowest speed relative to a complete revolution of the crankshaft. The lowest speed is understood as the lowest measurable speed depending on the method of measurement. Since the piston speed is directly related to the speed of the crankshaft, in most cases the speed of the crankshaft will be measured to determine the position at which the piston has the lowest speed relative to a complete revolution of the crankshaft. Moreover, in variable speed refrigerant compressors, the velocity measurement provided in the poles of the stator of the electric motor by the rotation of the rotor connected to the crankshaft is provided as the speed measurement. It is understood that the accuracy of the speed measurement in this case is limited by the number of poles. In this case, according to the invention, the smallest measurable speed (corresponding to the smallest measurable reciprocating piston speed) relative to a complete revolution of the crankshaft can be used as the triggering moment for the application of the braking torque.

Anstelle der Position mit der geringsten Geschwindigkeit kann die Position, bei welcher das Bremsmoment angelegt wird, auch in einem Bereich liegen, der sich innerhalb eines Kurbelwellendrehwinkels von +/-25° befindet, gemessen ab jener Position, bei welcher der Hubkolben die geringste Geschwindigkeit bezogen auf eine komplette Umdrehung der Kurbelwelle aufweist.Instead of the lowest speed position, the position at which the brake torque is applied may also be in a range that is within a crank angle of +/- 25 degrees measured from the position where the reciprocating piston has the lowest speed to a complete revolution of the crankshaft.

Gemäß einer weiteren bevorzugten Ausführungsvariante der Erfindung ist es vorgesehen, dass die Kurbelwelle dem Bremsmoment eine bestimmte Zeitspanne ausgesetzt wird, die vorzugsweise zwischen 0,15 s und 0,45 s lang ist. Damit kann sichergestellt werden, dass der Anhaltevorgang sicher beendet werden kann bzw. die kritischen Drehzahlen gebremst durchfahren werden können.According to a further preferred embodiment of the invention, it is provided that the crankshaft is exposed to the braking torque for a certain period of time, which is preferably between 0.15 s and 0.45 s long. This can be ensured that the stopping process can be safely stopped or the critical speeds can be traversed braked.

Die Zeitspanne kann gemäß einer weiteren bevorzugten Ausführungsvariante der Erfindung aus einer, vorzugsweise im Speicher der Steuereinheit hinterlegten Tabelle gewählt werden. Auch hier können bei den hinterlegten Werten für die Zeitspanne verschiedenste Parameter, insbesondere Betriebsparameter wie oben beschrieben, berücksichtigt werden und so der Anhaltevorgang optimiert werden.The period of time can be selected according to a further preferred embodiment of the invention from a, preferably stored in the memory of the control unit table. Here as well, a great variety of parameters can be stored for the stored time values, in particular operating parameters as above be considered, and so the stopping process to be optimized.

Gemäß einer weiteren bevorzugten Ausführungsvariante der Erfindung ist es vorgesehen, dass die Kurbelwelle dem Bremsmoment länger ausgesetzt ist, als die Kurbelwelle zum Zeitpunkt der Auslösung des Bremsmomentes für eine Umdrehung benötigen würde. Damit kann, je nach Beginn des Bremsvorganges, sichergestellt werden, dass der Bremsvorgang nicht in einem Kompressionszyklus endet, wo das Reaktionsdrehmoment ein Maximum haben kann.According to a further preferred embodiment of the invention, it is provided that the crankshaft is exposed to the braking torque longer than the crankshaft would require at the time of triggering the braking torque for one revolution. Thus, depending on the beginning of the braking operation, it can be ensured that the braking operation does not end in a compression cycle where the reaction torque can have a maximum.

Zur Erzeugung des Bremsmoments kann dabei in an sich bekannter Weise der Elektromotor verwendet werden. Beispielsweise kann die Stromrichtung durch Windungen des Elektromotors im Vergleich zum normalen Betrieb umgekehrt werden. Oder es können die Windungen kurzgeschlossen werden, sodass der Strom, der aufgrund der Drehbewegung des Elektromotors erzeugt bzw. induziert wird, ein der vorherrschenden Drehbewegung entgegengesetztes Drehmoment erzeugt. Letzteres Verfahren wird manchmal auch als "zero vector braking" bezeichnet und erzeugt ein von der Drehzahl abhängiges Bremsmoment.To generate the braking torque can be used in a conventional manner, the electric motor. For example, the current direction can be reversed by windings of the electric motor compared to the normal operation. Or the windings may be shorted so that the current generated or induced due to the rotational motion of the electric motor produces a torque opposite the prevailing rotational motion. The latter method is sometimes referred to as "zero vector braking" and generates a dependent on the speed braking torque.

Bei Einsatz des Elektromotors zwecks anlegen des Bremsmomentes kann es durch die oben beschriebenen, erfindungsgemäßen Maßnahmen auch sichergestellt werden, dass die beim Erzeugen des Bremsmoments auftretenden Ströme und Magnetfelder nicht zu einer unerwünschten Entmagnetisierung des Elektromotors bzw. von dessen Teilen führen, da zum Zeitpunkt des Anlegens des Bremsmomentes der Kältemittelverdichter bereits kontrolliert mit einer entsprechend geringen Drehzahl betrieben wird.When using the electric motor in order to create the braking torque, it can also be ensured by the above-described inventive measures that the currents and magnetic fields occurring during generation of the braking torque do not lead to an undesired demagnetization of the electric motor or its parts, since at the time of application the braking torque of the refrigerant compressor is already controlled with a correspondingly low speed is operated.

Analog zu den obigen Ausführungen wird die der Erfindung zugrundeliegende Aufgabe auch durch ein entsprechendes Steuerungssystem gelöst, welches in der Lage ist, das beschriebene Verfahren durchzuführen.Analogously to the above explanations, the object underlying the invention is also achieved by a corresponding control system which is capable of carrying out the described method.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die Erfindung wird nun anhand von Ausführungsbeispielen näher erläutert. Die Zeichnungen sind beispielhaft und sollen den Erfindungsgedanken zwar darlegen, ihn aber keinesfalls einengen oder gar abschließend wiedergeben.The invention will now be explained in more detail with reference to exemplary embodiments. The drawings are exemplary and should be the Although set out the idea of the invention, it does not restrict or even reproduce it in any way.

Dabei zeigt:

Fig. 1
eine schematische Darstellung eines hermetisch gekapselten Kältemittelverdichters
Fig. 2
ein Diagramm Kurbelwellendrehzahl vs. Zeit gemäß einer Ausführungsvariante der Erfindung
Fig. 3
ein Diagramm Kurbelwellendrehzahl vs. Zeit gemäß einer alternativen Ausführungsvariante der Erfindung
Fig. 4
ein Diagramm Kurbelwellendrehzahl vs. Zeit gemäß einer weiteren alternativen Ausführungsvariante der Erfindung
Fig. 5
ein Diagramm eines Reaktionsdrehmoments einer Hubkolben-Zylinder-Einheit vs. Drehwinkel
Showing:
Fig. 1
a schematic representation of a hermetically sealed refrigerant compressor
Fig. 2
a diagram of crankshaft speed vs. Time according to an embodiment of the invention
Fig. 3
a diagram of crankshaft speed vs. Time according to an alternative embodiment of the invention
Fig. 4
a diagram of crankshaft speed vs. Time according to another alternative embodiment of the invention
Fig. 5
a diagram of a reaction torque of a reciprocating cylinder unit vs.. angle of rotation

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS FOR CARRYING OUT THE INVENTION

Fig. 1 zeigt schematisch einen hermetisch gekapselten Kältemittelverdichter 1, wie er beispielsweise auch in Haushaltsgeräten, z.B. Kühlschränken, zum Einsatz kommt. Der Kältemittelverdichter 1 umfasst eine Hubkolben-Zylinder-Einheit 2 mit einem Hubkolben 9, der sich in einem Zylinder (nicht dargestellt) auf und ab bewegen kann. Der Hubkolben 9 wird dabei über eine Kurbelwelle 3 bewegt, die mittels eines Elektromotors 4 angetrieben wird. Fig. 1 schematically shows a hermetically sealed refrigerant compressor 1, as it is used for example in household appliances, such as refrigerators. The refrigerant compressor 1 comprises a reciprocating cylinder unit 2 with a reciprocating piston 9, which can move up and down in a cylinder (not shown). The reciprocating piston 9 is thereby moved via a crankshaft 3, which is driven by means of an electric motor 4.

Mittels der Hubkolben-Zylinder-Einheit 2 wird gasförmiges Kältemittel in den Zylinder gesaugt, dort mittels des Hubkolbens 9 komprimiert und wieder aus dem Zylinder ausgestoßen. Der Einlass und Auslass des Kältemittels wird dabei üblicherweise mittels einer an einem Zylinderkopf des Zylinders montierten Ventilplatte mit Ventilen für den Einlass und den Auslass (nicht dargestellt) gesteuert.By means of the reciprocating cylinder unit 2 gaseous refrigerant is sucked into the cylinder, compressed there by means of the reciprocating piston 9 and discharged again from the cylinder. In this case, the inlet and outlet of the refrigerant is usually controlled by means of a valve plate mounted on a cylinder head of the cylinder with valves for the inlet and the outlet (not shown).

Der Elektromotor 4 wird mittels einer, vorzugsweise elektronischen Steuereinheit 5 angesteuert, die einen Teil eines Steuerungssystems für den Kältemittelverdichter 1 bildet. Üblicherweise erhält die elektronische Steuereinheit 5 vom Gerät (z.B. ein Kühlschrank), in welchem der Kältemittelverdichter 2 zum Einsatz kommt, Informationen über die aktuell gewünschte Kühlleistung. Vorzugsweise sendet hierzu das Gerät an die elektronische Steuereinheit 5 ein Betriebssignal, besonders bevorzugt in Form eines Frequenzsignals, wobei in letzterem Fall die geforderte Kühlleistung proportional zur Frequenz ist. Ist keine Kühlleistung erforderlich, weil beispielsweise eine Zieltemperatur in einem zu kühlenden Volumen erreicht ist, wird kein Betriebssignal generiert. Das Fehlen eines Betriebssignals wird von der elektronischen Steuereinheit 5 detektiert, worauf diese den Anhaltevorgang einleitet.The electric motor 4 is controlled by means of a, preferably electronic control unit 5, which forms part of a control system for the refrigerant compressor 1. Usually, the electronic control unit 5 obtains information about the currently desired cooling capacity from the apparatus (e.g., a refrigerator) in which the refrigerant compressor 2 is used. For this purpose, the device preferably sends to the electronic control unit 5 an operating signal, particularly preferably in the form of a frequency signal, wherein in the latter case the required cooling power is proportional to the frequency. If no cooling capacity is required because, for example, a target temperature is reached in a volume to be cooled, no operating signal is generated. The absence of an operating signal is detected by the electronic control unit 5, whereupon it initiates the stopping process.

Im in Fig. 1 dargestellten Ausführungsbeispiel ist die Steuereinheit 5 mit einer Stromversorgung 6 verbunden, und versorgt den Elektromotor 4 mit elektrischer Energie. Bei der Stromversorgung 6 handelt es sich üblicherweise um das Niederspannungsnetz, an welches das Gerät, vorzugsweise Haushaltsgerät angeschlossen wird, in welchem Gerät der Kältemittelverdichter 1 Verwendung findet.Im in Fig. 1 illustrated embodiment, the control unit 5 is connected to a power supply 6, and supplies the electric motor 4 with electrical energy. In the power supply 6 is usually the low-voltage network to which the device, preferably household appliance is connected, in which device the refrigerant compressor 1 is used.

Die Hubkolben-Zylinder-Einheit 2 ist in einem hermetisch dichten Gehäuse 7 des Kältemittelverdichters 1 angeordnet und in diesem mittels Federn 8 gelagert. Die Federn 8 dienen dazu, Vibrationen bzw. Auslenkungen der Hubkolben-Zylinder-Einheit 2 zu dämpfen und somit eine Geräuschentwicklung möglichst gering zu halten und mechanische Beschädigung zu vermeiden. Die Vibrationen werden insbesondere durch die sich wiederholenden Kompressionsvorgänge verursacht. Aufgrund der periodischen Kompressionsvorgänge kommt es zu einem Reaktionsdrehmoment MR der Hubkolben-Zylinder-Einheit 2, welches entsprechend der maximal auftretenden Kompressionen Spitzen aufweist.The reciprocating cylinder unit 2 is arranged in a hermetically sealed housing 7 of the refrigerant compressor 1 and stored therein by means of springs 8. The springs 8 serve to dampen vibrations or deflections of the reciprocating cylinder unit 2 and thus to minimize noise development and to avoid mechanical damage. The vibrations are caused in particular by the repetitive compression processes. Due to the periodic compression processes, there is a reaction torque M R of the reciprocating cylinder unit 2, which has peaks corresponding to the maximum occurring compressions.

Ein solcher Verlauf des Reaktionsdrehmoments MR während des Betriebs ist in Fig.5 gegen den Drehwinkel a der Kurbelwelle 3 aufgetragen. Der Drehwinkel α=0° wird dabei durch die Position des Hubkolbens 9 in einem unteren Totpunkt definiert. Die maximale Kompression des gasförmigen Kältemittels und damit einhergehend eine Spitze im Verlauf des Reaktionsdrehmoments MR der Hubkolben-Zylinder-Einheit 2 liegen entsprechend bei einem Drehwinkel α von ca. 180° bzw. knapp davor.Such a course of the reaction torque M R during operation is in Figure 5 applied against the angle of rotation a of the crankshaft 3. The rotation angle α = 0 ° is defined by the position of the reciprocating piston 9 in a bottom dead center. The maximum compression of the gaseous refrigerant and, consequently, a peak in the Course of the reaction torque M R of the reciprocating cylinder unit 2 are correspondingly at a rotational angle α of about 180 ° or just before.

Wie weiter oben bereits ausführlich beschrieben wurde, kann es insbesondere beim Herunterfahren bzw. Anhalten des Kältemittelverdichters 1 zu einer besonders hohen Geräuschentwicklung bzw. auch zu mechanischen Schäden kommen. Um dies zu verhindern wird nach dem Detektieren des Erlöschens des Betriebssignals durch die elektronische Steuereinheit 5 über eine Zeitdauer τ hinweg eine Drehzahl V der Kurbelwelle 3 mittels des Elektromotors 4 mit einer Verringerungsrate verringert, wobei die Zeitdauer τ in Abhängigkeit des Wertes des letzten Betriebssignals vor dessen Erlöschen bestimmt wird. Mit anderen Worten wird durch den Elektromotor 4 die Drehzahl V der Kurbelwelle 3 kontrolliert verringert und zwar über die Zeitdauer τ. Die Verringerungsrate wird durch eine an sich bekannte Ansteuerung des Elektromotors 4 erzielt, beispielsweise indem mittels der Steuereinheit 5 die Versorgungsspannung des Elektromotors 4 mittels eines Pulsweiten-Modulations-Verfahrens reduziert wird.As has already been described in detail above, especially during shutdown or stopping of the refrigerant compressor 1, particularly high noise development or also mechanical damage can occur. To prevent this, after detecting the extinction of the operating signal by the electronic control unit 5 over a period of time τ a speed V of the crankshaft 3 by means of the electric motor 4 is reduced at a reduction rate, the duration τ depending on the value of the last operating signal before Extinguishment is determined. In other words, the speed V of the crankshaft 3 is reduced in a controlled manner by the electric motor 4 over the period of time τ. The reduction rate is achieved by a known per se control of the electric motor 4, for example by means of the control unit 5, the supply voltage of the electric motor 4 is reduced by means of a pulse width modulation method.

Dabei wird vom letzten Betriebssignal, konkret aus dem Wert des letzten Betriebssignals, auf den Betriebszustand des Kältemittelverdichters bei Einleitung des Anhaltevorgangs geschlossen, insbesondere wird dabei auf die aktuelle Drehzahl des Kältemittelverdichters zum Zeitpunkt des Erlöschens des Betriebssignals geschlossen, i.e. bei Einleitung des Anhaltevorgangs geschlossen, ohne diese Drehzahl messen zu müssen.In this case, it is concluded from the last operating signal, specifically from the value of the last operating signal, on the operating state of the refrigerant compressor at the initiation of the stopping process, in particular, the current speed of the refrigerant compressor at the time of extinction of the operating signal is closed, i. closed at the initiation of the stopping process, without having to measure this speed.

Die Zeitdauer τ innerhalb welcher der Kältemittelverdichter kontrolliert mittels des Elektromotors 4 mit einer vorgegebenen Verringerungsrate, die bevorzugt konstant ist, grundsätzlich aber auch über die Zeitdauer τ variieren kann, heruntergefahren wird, kann dabei entweder bei jedem Anhaltevorgang in Abhängigkeit der Zeitdauer τ neu berechnet werden, wird aber besonders bevorzugt in Abhängigkeit der Zeitdauer τ aus einer Tabelle ausgelesen, die in einem Speicher der elektronischen Steuereinheit hinterlegt ist.The period of time τ within which the refrigerant compressor controlled by the electric motor 4 with a predetermined reduction rate, which is preferably constant, but in principle can vary over the period of time τ is shut down, can either be recalculated at each stop depending on the duration τ, However, it is particularly preferably read as a function of the time duration τ from a table which is stored in a memory of the electronic control unit.

In beiden Fällen können dabei Betriebsparamater wie beispielsweise die Temperatur des Kältemittelverdichters im Inneren des Gehäuses und/oder der Gasdruck des Kältemittels saugseitig und/oder druckseitig und/oder die Außentemperatur und/oder die Gesamtbetriebsstunden des Kältemittelverdichters zusätzlich berücksichtigt werden, um eine geräusch- und verschleißtechnische Optimierung des Anhaltevorgangs zu erzielen. Dabei können zuvor, in Versuchen, mittels standardisierter Messmethoden Werte für die Zeitdauer τ ermittelt werden, die dann in der Tabelle hinterlegt werden.In both cases, operating parameters such as, for example, the temperature of the refrigerant compressor in the interior of the housing and / or the gas pressure of the refrigerant on the suction side and / or pressure side and / or the outside temperature and / or the total operating hours of the refrigerant compressor can additionally be taken into account in order to reduce noise and wear Optimization of the stopping process to achieve. In this case, previously, in tests, by means of standardized measuring methods values for the period of time τ can be determined, which are then stored in the table.

Eine weitere Optimierung des erfindungsgemäßen Verfahrens zum Anhalten eines hermetisch dichten Kältemittelverdichters kann durch Anlegen eines Bremsmomentes erfolgen, nachdem die Zeitdauer τ abgelaufen ist und eine definierte Position des Hubkolbens 9 detektiert wird. Mit anderen Worten ist in diesem Fall nicht (nur) die abgelaufene Zeitdauer τ für den Zeitpunkt des Anlegens des Bremsmomentes relevant sondern eine bestimmte, für die geräusch- und verschleißtechnische Verbesserung optimale Hubkolbenposition.A further optimization of the method according to the invention for stopping a hermetically sealed refrigerant compressor can be achieved by applying a braking torque after the time period τ has elapsed and a defined position of the reciprocating piston 9 is detected. In other words, in this case not (only) the elapsed time τ relevant for the time of application of the braking torque but a certain, optimal for the noise and wear technical improvement Hubkolbenposition.

Diese bestimmt sich besonders bevorzugt nach der Auslenkung des Gehäuses 7 des Kältemittelverdichters. Konkret handelt es sich bei der Position des Hubkolbens 9, bei welcher das Bremsmoment angelegt wird, um jene Position, bei welcher das Gehäuse 7 im Zuge des weiteren Anhaltevorgangs im Vergleich zu anderen Hubkolbenpositionen einer kompletten Umdrehung der Kurbelwelle 3 die geringsten Beschleunigungswerte erfährt, wobei insbesondere die Beschleunigungswerte parallel und senkrecht zur Kurbelwellenachse für den Rückschluss auf die optimale Hubkolbenposition sind. Geringe Beschleunigungswerte des Gehäuses während des weiteren Anhaltevorgangs bewirken an dieser Stelle eine geringe Auslenkung desselben während des weiteren Anhaltevorgangs. Diese optimale Position des Hubkolbens 9 ist im Vorfeld, beispielsweise an einem Prototypen eines bestimmten Kältemittelverdichtertyps mittels standardisierter Messmethoden ermittelbar, in dem die Beschleunigung und Auslenkung des Gehäuses, vorzugsweise parallel und senkrecht zur Kurbelwellenachse vom Zeitpunkt des Anlegen des Bremsmomentes bis zum Stillstand der Kurbelwelle ausgehend von unterschiedlichen Hubkolbenpositionen einer kompletten Kurbelwellenumdrehung gemessen wird. Es ist anzumerken, dass diese optimale Position kältemittelverdichtertypspezifisch ist und von einer Vielzahl an Betriebsparametern abhängen kann, jedenfalls am besten gemäß der Erfindung empirisch ermittelt werden kann. Die aus den Versuchen ermittelte optimale Position des Hubkolbens 9 kann in einem Speicher der elektronischen Steuereinheit 5 hinterlegt werden und das Erreichen dieser Position im Betrieb als auslösendes Ereignis für das Anlegen des Bremsmomentes herhalten. Anzumerken ist an dieser Stelle, dass die Positionsbestimmung des Kolbens bei Kältemittelverdichtern mit variabler Drehzahl aufgrund des Aufbaus des Elektromotors 4 möglich ist, aufgrund der durch die Drehung des Rotors in den einzelnen Polen des Stators induzierten Spannungen. Grundsätzlich eignen sich aber auch andere Methoden zur Bestimmung der Position des Hubkolbens 9 im Zylinder.This is determined particularly preferably after the deflection of the housing 7 of the refrigerant compressor. Concretely, the position of the reciprocating piston 9 at which the braking torque is applied is the position at which the housing 7 experiences the lowest acceleration values in the course of the further stopping operation in comparison to other reciprocating positions of a complete revolution of the crankshaft 3, in particular the acceleration values are parallel and perpendicular to the crankshaft axis for inferring the optimum reciprocating piston position. Low acceleration values of the housing during the further stopping process at this point cause a slight deflection of the same during the further stopping process. This optimal position of the reciprocating piston 9 is in advance, for example on a prototype of a particular refrigerant compressor type determined by standardized measurement methods in which the acceleration and deflection of the housing, preferably parallel and perpendicular to the crankshaft axis from the time of application of the braking torque to the standstill of the crankshaft starting from different Hubkolbenpositionen a complete crankshaft revolution is measured. It should be noted that this optimum position is refrigerant type specific and may depend on a variety of operating parameters, but in any case can best be determined empirically according to the invention. The optimum position of the reciprocating piston 9 determined from the tests can be stored in a memory of the electronic control unit 5 and the achievement of this position in operation serves as a triggering event for the application of the braking torque. It should be noted at this point that the position determination of the piston in variable speed refrigerant compressors is possible due to the structure of the electric motor 4 due to the voltages induced in the individual poles of the stator by the rotation of the rotor. In principle, however, other methods for determining the position of the reciprocating piston 9 in the cylinder are also suitable.

Messungen haben ergeben, dass auch Hubkolbenpositionen in der unmittelbaren Umgebung dieser optimalen Hubkolbenposition, etwa im Bereich +/- 25° immer noch einen geräusch- und verschleißtechnisch gegenüber herkömmlichen Kältemittelverdichtern optimierten Anhaltevorgang ermöglichen, so dass es sich bei der Position des Hubkolbens 9, bei welcher das Bremsmoment angelegt wird, auch um eine jener Positionen handeln kann, in welchen das Gehäuse 7 im Zuge des weiteren Anhaltevorgangs im Vergleich zu anderen Hubkolbenpositionen einer kompletten Umdrehung der Kurbelwelle 3 nicht mehr als 120% der geringsten Beschleunigungswerte erfährt.Measurements have shown that even piston positions in the immediate vicinity of this optimum reciprocating position, for example in the range +/- 25 °, still allow a noise and wear technology over conventional refrigerant compressors optimized stopping process, so that it is at the position of the reciprocating piston 9, in which the braking torque is applied, can also act to one of those positions in which the housing 7 in the course of the further stopping operation in comparison to other Hubkolbenpositionen a complete revolution of the crankshaft 3 does not learn more than 120% of the lowest acceleration values.

Alternativ dazu entspricht die optimale Hubkolbenposition auch jener Position des Hubkolbens 9, bei welcher der Hubkolben 9 die geringste Geschwindigkeit bezogen auf eine komplette Umdrehung der Kurbelwelle 3 aufweist bzw 25° vor oder nach dieser Position. Diese Ausführungsvariante hat den Vorteil, dass die Geschwindigkeit des Hubkolbens 9 über die Drehzahl der Kurbelwelle 3 auch während des normalen Betriebs bestimmt werden kann und dadurch jene Position, bei welcher der Hubkolben 9 die geringste Geschwindigkeit bezogen auf eine komplette Umdrehung der Kurbelwelle 3 aufweist jederzeit bestimmt werden kann.Alternatively, the optimal reciprocating piston position also corresponds to that position of the reciprocating piston 9, in which the reciprocating piston 9 has the lowest speed relative to a complete revolution of the crankshaft 3 or 25 ° before or after this position. This embodiment has the advantage that the speed of the reciprocating piston 9 can be determined via the rotational speed of the crankshaft 3 during normal operation and thereby determines that position at which the reciprocating piston 9 the lowest speed relative to a complete revolution of the crankshaft 3 at any time can be.

Fig. 2 zeigt beispielhaft einen zeitlichen Verlauf der Drehzahl V der Kurbelwelle 3 bei Anwendung des erfindungsgemäßen Verfahrens zum Anhalten des Kältemittelverdichters 1. Zunächst befindet sich die Drehzahl V auf einem durch das Betriebssignal, korrespondierend zu einer geforderten Kühlleistung, vorgegebenen Wert v 1 (z.B. 4000 min-1), der einem gewissen Betriebszustand des Kältemittelverdichters 1, entspricht. Eine tatsächliche Bestimmung der Drehzahl V ist nicht erforderlich. Fig. 2 shows by way of example a time profile of the speed V of the crankshaft 3 when using the method according to the invention for stopping the refrigerant compressor 1. First, the speed V is at a predetermined by the operating signal, corresponding to a required cooling power value v 1 (eg 4000 min -1 ), which corresponds to a certain operating state of the refrigerant compressor 1. An actual determination of the speed V is not required.

Zum Zeitpunkt t0 erlischt das Betriebssignal. Die Detektion des Erlöschens des Betriebssignals leitet nun das Anhalten des Kältemittelverdichters 1 ein. Es sei bemerkt, dass zwar im gezeigten Ausführungsbeispiel die Drehzahl V vor dem Zeitpunkt t0 als konstant dargestellt ist, jedoch selbstverständlich auch eine variierende Drehzahl V - entsprechend einer variierenden Kühlleistungsanforderung - möglich ist.At time t 0, the operating signal goes out. The detection of the extinction of the operating signal now initiates the stopping of the refrigerant compressor 1. It should be noted that although in the illustrated embodiment, the speed V is shown as constant before the time t 0 , but of course also a varying speed V - in accordance with a varying cooling power requirement - is possible.

Ab dem Zeitpunkt t0 nimmt die Drehzahl V über die gesamte Zeitdauer τ ab. Im gezeigten Ausführungsbeispiel liegt während der Zeitdauer τ eine lineare Drehzahlabnahme vor - entsprechend einer konstanten Verringerungsrate. Die Zeitdauer τ wird vorzugsweise aus hinterlegten Tabellen ausgewählt, um dem bis unmittelbar vor dem Zeitpunkt t0 vorliegenden Betriebszustand Rechnung zu tragen.From time t 0 , the speed V decreases over the entire time period τ. In the exemplary embodiment shown, there is a linear speed decrease during the time period τ - corresponding to a constant rate of reduction. The period of time τ is preferably selected from stored tables in order to take into account the operating state present until immediately before time t 0 .

Auch die Verringerungsrate wird bevorzugt aus hinterlegten Tabellen entnommen, welche analog zu den Tabellen für τ gewonnen worden sind, wobei die Verringerungsrate über der Zeitdauer τ auch variieren kann.The reduction rate is also preferably taken from stored tables, which have been obtained analogously to the tables for τ, wherein the reduction rate over the time period τ can also vary.

Zeitdauer τ und die Verringerungsrate sind jedenfalls so aufeinander abgestimmte, dass ein geräusch- und verschleißtechnisch optimaler Anhaltevorgang gefahren werden kann.Duration τ and the reduction rate are in any case so coordinated that a noise and wear technology optimal stopping process can be driven.

Alternativ dazu kann, wie in Fig.3 dargestellt, vorgesehen sein, den Kompressor durch das zusätzliche Anlegen eines Bremsmomentes anzuhalten. Zeitdauer τ und Verringerungsrate sind dann so aufeinander abzustimmen, dass sichergestellt wird, dass das Anlegen des Bremsmomentes zu einem Zeitpunkt erfolgt, in welchem der Kompressor immer noch in einem überkritischen Zustand betrieben wird. Die darauf Einfluss habenden Betriebsparameter können in die Zeitdauer τ und/oder in die Verringerungsrate einfließen, ebenso wie durch die Wahl der Zeitdauer τ und/oder der Verringerungsrate bzw. Abstimmung derselben aufeinander geräusch- und verschleißtechnische Optimierung erfolgen kann.Alternatively, as in Figure 3 illustrated, be provided to stop the compressor by the additional application of a braking torque. Period τ and reduction rate are then coordinated so that it is ensured that the application of the braking torque takes place at a time in which Compressor is still operated in a supercritical state. The operating parameters influencing this can be included in the time period τ and / or in the reduction rate, as well as by the choice of the time duration τ and / or the reduction rate or tuning of the same noise and wear optimization.

Das Anlegen des Bremsmomentes erfolgt durch Ansteuerung des Elektromotors 4 durch die elektronische Steuereinheit 5 in an sich bekannter Weise, sodass dieser nach Ablauf der Zeitdauer τ ein Bremsmoment erzeugt, welchem die Kurbelwelle 3 ausgesetzt wird.The application of the braking torque is carried out by driving the electric motor 4 by the electronic control unit 5 in a conventional manner, so that this τ after the expiration of the time period generates a braking torque to which the crankshaft 3 is exposed.

Um vorzugsweise sicherzustellen, dass die Hubkolben-Zylinder-Einheit 2 bzw. die Kurbelwelle 3 hierdurch tatsächlich zum Stillstand kommt, ohne ständig die aktuelle Drehzahl V zu messen, wird das Bremsmoment über eine bestimmte Zeitspanne Δt angelegt. Vorzugsweise wird die Zeitspanne Δt ebenfalls aus hinterlegten Tabellen ausgewählt, um den unterschiedlichsten Betriebssituationen Rechnung zu tragen. Indem die Zeitspanne Δt hinreichend lang ist, kann also garantiert werden, dass sich nach Ablauf der Zeitspanne Δt die Kurbelwelle 3 nicht mehr dreht. Typischerweise liegt die Zeitspanne Δt hierfür in einem Bereich von 0,15 s bis 0,45 s.In order to preferably ensure that the piston-cylinder unit 2 or the crankshaft 3 thereby actually comes to a standstill, without constantly measuring the current speed V, the braking torque is applied over a certain period .DELTA.t. Preferably, the time period .DELTA.t is also selected from stored tables in order to take into account a wide variety of operating situations. By the period Δt is sufficiently long, it can thus be guaranteed that after the expiry of the period .DELTA.t, the crankshaft 3 is no longer rotating. Typically, the time .DELTA.t for this is in a range of 0.15 s to 0.45 s.

Fig.4 zeigt jene besonders bevorzugte Variante der Erfindung, gemäß welcher nach Ablauf der Zeitdauer τ und vor Anlegen des Bremsmomentes innerhalb einer Zeitspanne τ1 noch die optimale Kolbenposition detektiert wird. Die Dauer dieser Zeitspanne richtet sich nach der Hubkolbenposition nach Ablauf der Zeitdauer τ und dem erforderlichen Drehwinkel der Kurbelwelle 3 bis zum Erreichen der optimalen Kolbenposition. Figure 4 shows that particularly preferred variant of the invention, according to which after the time period τ and before applying the braking torque within a time period τ 1 nor the optimal piston position is detected. The duration of this period depends on the Hubkolbenposition after the expiry of the time τ and the required rotational angle of the crankshaft 3 until reaching the optimum piston position.

In Fig.2 zeigt die über der Zeitspanne Δt eingezeichnete durchgezogene Linie den Fall, dass die Kurbelwelle 3 genau mit Ablauf der Zeitspanne Δt zum Stillstand kommt. Die über der Zeitspanne Δt strichliert eingezeichnete Linie illustriert den Fall, dass die Kurbelwelle 3 bereits vor Ablauf der Zeitspanne Δt sich nicht mehr dreht. Die strichpunktierte Linie in Fig. 2 dient zur Veranschaulichung jenes - durch geeignete Wahl von Δt vermeidbaren - Falls, dass sich die Kurbelwelle 3 auch nach Ablauf der Zeitspanne Δt noch kurz weiter dreht.In Fig.2 shows the solid line drawn over the period .DELTA.t the case that the crankshaft 3 comes to a standstill exactly at the expiration of the period .DELTA.t. The dashed line over the period .DELTA.t illustrates the case that the crankshaft 3 is no longer rotating even before the expiration of the period .DELTA.t. The dash-dotted line in Fig. 2 serves to Illustrating that - avoidable by a suitable choice of Δt - If the crankshaft 3 continues to rotate even after the time span Δt has elapsed.

BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS

11
KältemittelverdichterRefrigerant compressor
22
Hubkolben-Zylinder-EinheitReciprocating piston-cylinder unit
33
Kurbelwellecrankshaft
44
Elektromotorelectric motor
55
Steuereinheitcontrol unit
66
Stromversorgungpower supply
77
Gehäusecasing
88th
Federfeather
99
Hubkolbenreciprocating
vv
Drehzahl der KurbelwelleSpeed of the crankshaft
ττ
Zeitdauer für VerringerungsrateDuration of reduction rate
τ1 τ 1
Zeitdauer zur Bestimmung der optimalen KolbenpositionTime to determine the optimal piston position
Δt.delta.t
Zeitspanne für Wirken des BremsmomentsTime span for the braking torque
αα
Drehwinkel der KurbelwelleAngle of rotation of the crankshaft
MR M R
Reaktionsdrehmoment der Hubkolben-Zylinder-EinheitReaction torque of the reciprocating cylinder unit
t0 t 0
Zeitpunkt des Erlöschens eines BetriebssignalsTime of extinction of an operating signal

Claims (19)

  1. Method for stopping a hermetically encapsulated refrigerant compressor (1) having a hermetically sealed housing (7), arranged therein a reciprocating piston-cylinder unit (2) comprising a crankshaft (3) and an electric motor (4) driving the crankshaft (3), and a control unit (5) controlling the electric motor (4), wherein the control unit (5) operates the electric motor (4) in the presence of an operating signal, preferably a frequency signal, characterized in that the control unit (5) detects the termination of the operating signal and in that, after the detection of the termination of the operating signal, over a time duration (τ) a rotational speed of the crankshaft is reduced by means of the electric motor at a reduction rate, the piston-cylinder unit being actively driven by the electric motor (4) during the time duration (τ), wherein the time duration (τ) is determined as a function of the last operating signal before its termination, wherein the determination of the time duration (τ) is carried out either by calculation or by selection from at least one table which is preferably stored in a memory of the control unit (5).
  2. Method according to claim 1, characterized in that the operating signal is a target value for the rotational speed of the crankshaft and/or in that a target value for the rotational speed of the crankshaft can be generated from the operating signal.
  3. Method according to claim 1 or 2, characterized in that at least one further operating parameter is taken into account when calculating the time duration (τ).
  4. Method according to claim 1 or 2, characterized in that the at least one table, from which the selection of the time duration (τ) takes place, contains values, during the preparation of which at least one further operating parameter was taken into account.
  5. Method according to one of claims 3 to 4, characterized in that the at least one further operating parameter is the temperature of the refrigerant compressor inside the housing and/or the gas pressure of the refrigerant on the suction side and/or on the pressure side and/or the outside temperature and/or the total operating hours of the refrigerant compressor.
  6. Method according to one of claims 1 to 5, characterized in that a braking torque is applied to the crankshaft (3) after the time duration (τ) has elapsed.
  7. Method according to one of claims 1 to 6, characterized in that the position of the reciprocating piston is detected and the braking torque is applied to the crankshaft (3) as a function of the position of the reciprocating piston of the reciprocating piston-cylinder unit (2).
  8. Method according to claim 7, characterized in that the position of the reciprocating piston (9) in which the braking torque is applied is the position in which the housing (7) experiences the lowest acceleration values, preferably parallel and perpendicular to the crankshaft axis, in the course of the further stopping operation in comparison with other reciprocating piston positions of a complete revolution of the crankshaft (3).
  9. Method according to claim 7, characterized in that the position of the reciprocating piston in which the braking torque is applied is one of those positions in which the housing (7), in the course of the further stopping operation, does not experience more than 120% of the lowest acceleration values, preferably parallel and perpendicular to the crankshaft axis, in comparison with other reciprocating piston positions of a complete revolution of the crankshaft (3).
  10. Method according to claim 7, characterized in that the position of the reciprocating piston (9) in which the braking torque is applied is the position in which the reciprocating piston (9) has the lowest speed relative to a complete revolution of the crankshaft (3).
  11. Method according to claim 7, characterized in that the position of the reciprocating piston (9) in which the braking torque is applied is a range within a crankshaft rotation angle of +/-25° measured from the position in which the reciprocating piston (9) has the lowest speed relative to a complete revolution of the crankshaft (3).
  12. Method according to one of claims 6 to 11, characterized in that the crankshaft (3) is subjected to the braking torque for a certain time period (Δt), which is preferably between 0.15 s and 0.45 s long.
  13. Method according to claim 12, characterized in that the time period (Δt) is selected from tables, preferably stored in the memory of the control unit.
  14. Method according to one of claims 6 to 13, characterized in that the crankshaft (3) is exposed to the braking torque for longer than the crankshaft (3) would need for one revolution at the time the braking torque is triggered.
  15. Method according to one of claims 6 to 14, characterized in that the braking torque is generated by means of the electric motor (4).
  16. Method according to one of claims 1 to 15, characterized in that the reduction rate is constant over the time duration (τ).
  17. Method according to one of claims 1 to 16, characterized in that the operating signal is generated by an appliance, preferably a domestic appliance, which is operatively connected to the refrigerant compressor.
  18. Hermetically encapsulated refrigerant compressor (1) having a control system with an electronic control unit (5) adapted to carry out a method according to one of claims 1 to 17.
  19. Appliance, preferably domestic appliance, preferably refrigerator or freezer, comprising a hermetically encapsulated refrigerant compressor (1) according to claim 18.
EP16703334.9A 2015-02-09 2016-02-09 Method for stopping a hermetic refrigerant compressor and control system for same Revoked EP3256726B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP15154373.3A EP3054158A1 (en) 2015-02-09 2015-02-09 Method for stopping a hermetic refrigerant compressor and control system for same
PCT/EP2016/052736 WO2016128405A1 (en) 2015-02-09 2016-02-09 Method for stopping a hermetically encapsulated refrigerant compressor, and control system therefor

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EP3256726B1 true EP3256726B1 (en) 2019-09-04

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EP3054158A1 (en) 2016-08-10
WO2016128405A1 (en) 2016-08-18

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