WO2016128405A1 - Procédé d'arrêt d'un compresseur frigorifique enfermé hermétiquement et système de commande de celui-ci - Google Patents

Procédé d'arrêt d'un compresseur frigorifique enfermé hermétiquement et système de commande de celui-ci Download PDF

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Publication number
WO2016128405A1
WO2016128405A1 PCT/EP2016/052736 EP2016052736W WO2016128405A1 WO 2016128405 A1 WO2016128405 A1 WO 2016128405A1 EP 2016052736 W EP2016052736 W EP 2016052736W WO 2016128405 A1 WO2016128405 A1 WO 2016128405A1
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WO
WIPO (PCT)
Prior art keywords
crankshaft
braking torque
electric motor
refrigerant compressor
operating signal
Prior art date
Application number
PCT/EP2016/052736
Other languages
German (de)
English (en)
Inventor
Per Tranekjer Petersen
Ulrich Gries
Fabian Brune
Original Assignee
Secop Gmbh
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Application filed by Secop Gmbh filed Critical Secop Gmbh
Priority to EP16703334.9A priority Critical patent/EP3256726B1/fr
Publication of WO2016128405A1 publication Critical patent/WO2016128405A1/fr

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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 Operational signal, preferably a frequency signal, operates and detects the extinction of the operating signal.
  • a Operational signal preferably a frequency signal
  • the present invention relates to a control system for a hermetically sealed refrigerant compressor with a hermetically sealed housing, arranged therein a reciprocating cylinder unit with a crankshaft and an electric motor for driving the crankshaft, the control system comprising an electronic control unit for operating the electric motor in the presence of a Operating signal, preferably a frequency signal, and for detecting the extinction of the operating signal.
  • a Operating signal preferably a frequency signal
  • Hermetically sealed refrigerant compressors which are used in cooling circuits of various systems and devices, in particular in household appliances such as refrigerators, and which 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.
  • 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 reciprocating 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 leads to 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 braking torque is not instantaneous, i. After applying the stopping process preliminary extinction of the operating signal, but initially only wegzupier the drive torque of the electric motor, so that the crankshaft alone, due to the stored kinetic energy continues to rotate until the rotational speed of the reciprocating cylinder unit or the crankshaft under a has reduced 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. Accordingly, during stoppage, the rotational speed of the crankshaft has to be continuously measured and evaluated, i. be compared with a predetermined value.
  • This object is achieved by a method of stopping a hermetic-type refrigerant compressor having a hermetically sealed housing therein including a reciprocating cylinder unit including a crankshaft and an electric motor driving the crankshaft, and a control unit controlling the electric motor, the control unit providing the electric motor an operating signal, preferably a frequency signal, operating and detecting the extinguishment of the operating signal, achieved in that, after the detection of the extinction of the operating signal over a period of time, a speed of the crankshaft is reduced by means of the electric motor at a, preferably constant, reduction rate, the time period in Dependence of the last operating signal is determined before its extinction. The speed of the crankshaft during the stopping process is therefore no longer a relevant parameter for the stopping process itself.
  • 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 due to the last operating signal before the initiation of the stopping process or it is assumed that the electronic Control unit controls the electric motor according to this target value, so that a further measurement of the rotational speed of the crankshaft during the stopping process according to the invention is no longer necessary.
  • 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 place contains at least one additional one Operating parameters 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
  • the duration can be determined more precisely and the stopping process noise and wear technology to be optimized.
  • 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 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.
  • Fig. 1 is a schematic representation of a hermetically sealed
  • Fig. 2 is a diagram crankshaft speed vs. Time according to one
  • Fig. 3 is a diagram crankshaft speed vs. Time according to one
  • Fig. 4 is a diagram crankshaft speed vs. Time according to one
  • Fig. 5 is a diagram of a reaction torque of a reciprocating cylinder unit vs. angle of rotation
  • Fig. 1 shows schematically a hermetically sealed refrigerant compressor 1, as it is for example also in household appliances, e.g. Refrigerators, is used.
  • 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.
  • the reciprocating cylinder unit 2 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.
  • 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 receives information about the currently desired cooling capacity from the device (eg 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 alswei steaks according to the maximum compression occurring peaks.
  • Such a profile of the reaction torque M R during operation is plotted in FIG. 5 against the angle of rotation C of the crankshaft 3.
  • 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 OC of about 180 ° or just before.
  • Refrigerant compressor 1 to a particularly high
  • 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. It is the last operating signal, specifically from the value of the last operating signal, the operating state of the
  • 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 x has expired and a defined position of the reciprocating piston 9 is detected.
  • a braking torque after the time period x has expired and a defined position of the reciprocating piston 9 is detected.
  • the elapsed time x for the time of application of the braking torque relevant but a certain, optimal for the noise and wear technical improvement Hubkolbenposition.
  • 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 inference to the optimal Hubkolbenposition.
  • 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.
  • 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.
  • 2 shows, by way of example, a time profile of the rotational speed V of the crankshaft 3 when using the method according to the invention for stopping the refrigerant compressor 1.
  • the rotational speed V is at a value Vi predetermined by the operating signal, corresponding to a required cooling power (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.
  • 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 duration ⁇ and / or in the reduction rate, as well as by the choice of the time duration x and / or the reduction rate or tuning thereof to each other 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 it generates after the expiration of the time x a braking torque to which the crankshaft 3 is exposed.
  • the braking torque is applied over a certain period of time At.
  • the time period At is also selected from stored tables in order to take into account the most diverse operating situations. By the time period At is sufficiently long, so it can be guaranteed that after the expiry of the period At the crankshaft 3 is no longer rotating. Typically, the period At is in a range of 0.15 s to 0.45 s.
  • Braking torque within a time period Xi nor the optimum piston position is detected.
  • the duration of this period depends on the Hubkolbenposition after the expiration of the time period X and the required rotational angle of the crankshaft 3 until reaching the optimum piston position.
  • the solid line drawn over the period ⁇ t shows the case that the crankshaft 3 comes to a standstill exactly at the end of the period ⁇ t.
  • the line drawn by dashed lines over the period At illustrates the case where the crankshaft 3 no longer rotates before the expiration of the time period At.
  • the dashed line in Fig. 2 is used for Illustrating that - avoidable by a suitable choice of At - if the crankshaft 3 continues to rotate even after the time span At has expired.
  • Refrigerant compressor (1) with a hermetically sealed housing (7), arranged therein a reciprocating cylinder unit (2) with a crankshaft (3) and an electric motor (4) for driving the crankshaft (3), the control system comprising an electronic control unit (5) for operating the electric motor (4) in the presence of an operating signal, preferably a frequency signal, and for detecting the extinguishment of the operating signal, characterized in that the electronic control unit (5) is designed after the detection of the extinction of the operating signal over a period of time (x) To reduce a speed (V) of the crankshaft (3) by means of the electric motor (4) with a reduction rate, wherein the time period (X) is determined in dependence on the last operating signal before its extinction.
  • Control system characterized in that the electronic control unit (5) is designed to carry out the determination of the time duration either by calculation or by selection from at least one table, preferably stored in a memory of the control unit (4).
  • Control system characterized in that the electronic control unit (5) is adapted to process the operating signal as a setpoint for the rotational speed of the crankshaft (3).
  • Control system according to one of Claims 19 to 21, characterized in that the electronic control unit (5) is designed to take into account at least one further operating parameter when calculating the time duration (X).
  • Control system characterized in that the at least one table, from which the selection of the time duration (X) takes place, contains values in which Creation of at least one further operating parameter was taken into account.
  • Control system characterized in that it is the at least one further operating parameter to the temperature of the refrigerant compressor inside the housing or the gas pressure of the refrigerant suction side or pressure side or the outside temperature or the total operating hours of the
  • Control system characterized in that the electronic control unit (5) is adapted to apply after the time period (X), preferably via the electric motor (4), acting on the crankshaft (3) braking torque.
  • Control system characterized in that the electronic control unit (5) is adapted to detect the position of the reciprocating piston and to apply the braking torque as a function of the position of the reciprocating piston of the reciprocating cylinder unit (2) to the crankshaft (3).
  • Control system characterized in that the electronic control unit (5) is adapted to apply the braking torque at a position of the lifting piston (9), at which position the housing (7) in the course of the further stopping operation in comparison to other Hubkolbenpositionen a complete revolution of Crankshaft (3) the lowest acceleration values, preferably in parallel and perpendicular to the crankshaft axis learns.
  • Control system characterized in that the electronic control unit (5) is adapted to apply the braking torque at a position of the lifting piston (9), at which position the housing (7) in the course of the further stopping operation in comparison to other Hubkolbenpositionen a complete revolution of Crankshaft (3) not more than 120% of the lowest acceleration values, preferably in parallel and perpendicular to the crankshaft axis learns.
  • Control system characterized in that the electronic control unit (5) is adapted to the braking torque at a Position of the reciprocating piston (9) create at which position the reciprocating piston (9) has the lowest speed, based on a complete revolution of the crankshaft (3).
  • Control system characterized in that the electronic control unit (5) is adapted to apply the braking torque at a position of the reciprocating piston (9) which is within a crankshaft rotation angle of +/- 25 °, measured from that position at which the reciprocating piston ( 9) has the lowest speed, based on a complete revolution of the crankshaft (3).
  • Control system characterized in that the electronic control unit (5) is adapted to apply the braking torque only a certain period of time (At), which is preferably between 0.15 s and 0.45 s long.
  • Control system characterized in that the electronic control unit (5) is adapted to apply the braking torque longer than the crankshaft (3) would require at the time of initiation of the braking torque for one revolution.
  • Control system characterized in that the electronic control unit (5) is designed to keep the reduction rate constant over the time period (x).

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

Abstract

L'invention concerne un procédé d'arrêt d'un compresseur frigorifique (1), enfermé hermétiquement, qui comprend un boîtier (7) hermétiquement étanche dans lequel sont disposés une unité piston-cylindre (2), comportant un vilebrequin (3), et un moteur électrique (4), entraînant le vilebrequin (3), et une unité de commande (5) commandant le moteur électrique (4), l'unité de commande (5) commandant le moteur électrique (4) en présence d'un signal de commande, de préférence d'un signal de fréquence, et détectant la défaillance du signal de commande. Selon l'invention, après la détection de la défaillance du signal de commande au-delà d'une durée (I), la vitesse de rotation (V) du vilebrequin (3) est réduite avec un taux de réduction au moyen du moteur électrique (4), la durée (I) étant déterminée en fonction du dernier signal de commande avant la défaillance de celui-ci.
PCT/EP2016/052736 2015-02-09 2016-02-09 Procédé d'arrêt d'un compresseur frigorifique enfermé hermétiquement et système de commande de celui-ci WO2016128405A1 (fr)

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EP16703334.9A EP3256726B1 (fr) 2015-02-09 2016-02-09 Procédé d'arrêt d'un compresseur hermétique de réfrigérant et son système de commande

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EP15154373.3A EP3054158A1 (fr) 2015-02-09 2015-02-09 Procédé d'arrêt d'un compresseur hermétique de réfrigérant et son système de commande
EP15154373.3 2015-02-09

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WO2016128405A1 true WO2016128405A1 (fr) 2016-08-18

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EP2759788A1 (fr) * 2013-01-29 2014-07-30 LG Electronics, Inc. Dispositif pour réduire les vibrations dans un compresseur et son procédé de commande

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US6051952A (en) * 1997-11-06 2000-04-18 Whirlpool Corporation Electric motor speed and direction controller and method
EP2669519A1 (fr) 2011-01-26 2013-12-04 Whirlpool S.A. Système et procédé de commande pour compresseurs alternatifs
US20140072451A1 (en) * 2011-01-26 2014-03-13 Whirlpool S.A. Control system and method for reciprocating compressors
EP2759788A1 (fr) * 2013-01-29 2014-07-30 LG Electronics, Inc. Dispositif pour réduire les vibrations dans un compresseur et son procédé de commande

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EP3256726A1 (fr) 2017-12-20
EP3256726B1 (fr) 2019-09-04
EP3054158A1 (fr) 2016-08-10

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