WO2017190917A1 - Procédé de commande d'un circuit de pompe à chaleur incluant un moteur électrique d'un groupe compresseur, et circuit de pompe à chaleur - Google Patents

Procédé de commande d'un circuit de pompe à chaleur incluant un moteur électrique d'un groupe compresseur, et circuit de pompe à chaleur Download PDF

Info

Publication number
WO2017190917A1
WO2017190917A1 PCT/EP2017/058602 EP2017058602W WO2017190917A1 WO 2017190917 A1 WO2017190917 A1 WO 2017190917A1 EP 2017058602 W EP2017058602 W EP 2017058602W WO 2017190917 A1 WO2017190917 A1 WO 2017190917A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
rotor
bearing
machine
electric machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2017/058602
Other languages
German (de)
English (en)
Inventor
Thomas Schniedertoens
Simon Klink
Martin Viereckel
Nils Giesselmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
BD Kompressor GmbH
Original Assignee
Robert Bosch GmbH
BD Kompressor GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH, BD Kompressor GmbH filed Critical Robert Bosch GmbH
Publication of WO2017190917A1 publication Critical patent/WO2017190917A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0292—Stop safety or alarm devices, e.g. stop-and-go control; Disposition of check-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/90—Braking
    • F05D2260/903—Braking using electrical or magnetic forces

Definitions

  • the invention relates to a method for controlling a heat pump cycle according to claim 1 and a heat pump cycle according to
  • Compressor with a compressor rotor and an electric machine includes.
  • the electric machine drives the compressor rotor.
  • the electric machine is de-energized so that the compressor rotor expires.
  • Electrical machine can be provided by that Compressor rotor of the compressor system is driven at a predefined speed of the electric machine, wherein the electric machine is switched to a freewheeling operation, wherein in the freewheeling operation of the compressor rotor of the compressor system expires, wherein the rotational speed of the compressor rotor is detected, wherein the rotational speed is compared with a target rotational speed, when falling below the target speed by the speed, the electric machine is switched to a short-circuit operation.
  • This embodiment has the advantage that the compressor rotor is brought to a standstill faster than when the compressor rotor only expires. Further, a time in which a fluid bearing is operated in sliding operation is reduced, so that a mechanical friction work is reduced in the fluid bearing. As a result, wear of the fluid bearing is avoided.
  • the electric machine is de-energized after standstill of the compressor rotor, and preferably the
  • Compressor rotor stored fluid-dynamically and / or being below the
  • Target speed of the compressor rotor is slidably mounted.
  • a pressure difference between an input side of the compressor and an output side is reduced in time between the falling below the target speed by the rotational speed and the short circuit of the electric machine, advantageously canceled.
  • Machine rotor of the electric machine with which the machine rotor comes to a standstill, determined relative to a machine stator of the electric machine, wherein at a timed to the standstill of the machine rotor of the electric machine starting operation of the machine rotor of the electric machine, the electrical machine in dependence of the determined Angle position is controlled.
  • the startup process can be carried out particularly quickly.
  • an output stage of a control circuit of the control unit is completely switched into the short circuit.
  • Switching element which is connected to a positive supply voltage potential, turned off and at least a second switching element, which is connected to a negative supply voltage potential turned on.
  • a first switching element connected to a positive supply voltage potential is turned on, and at least a second switching element connected to a negative one
  • Supply voltage potential is connected, switched off.
  • the heat pump cycle has a first heat exchanger, a second heat exchanger, a heat transfer medium and a control unit.
  • the compressor system includes a compressor and an electric machine.
  • the compressor comprises a compressor rotor and the electric machine comprises a machine rotor.
  • the compressor rotor is
  • Heat exchanger is fluidly connected to an input side of the compressor.
  • the first heat exchanger is fluidly connected to an output side of the compressor.
  • the compressor rotor is designed to promote the heat transfer medium between the first heat exchanger and the second heat exchanger in the circuit.
  • the control unit is designed, the
  • the compressor system comprises a
  • the storage device comprises at least one
  • the compressor rotor can be mounted rotatably in a particularly low-friction manner.
  • the bearing element is preferably a fluid-dynamic fluid bearing, in particular a gas-dynamic fluid bearing.
  • the Bearing element has a limit speed. Above the limit speed, a contact between a rotating bearing surface of the bearing element and a stationary bearing surface is canceled.
  • the setpoint speed corresponds to the limit speed or the setpoint speed is greater than the limit speed.
  • Compressor rotor can be reduced without shorting the electrical machine.
  • the compressor is designed as a turbocompressor, wherein the setpoint speed has a value, wherein the value is in a range of 15,000 to 60,000 rpm, preferably in a range of 20,000 to 40,000 rpm.
  • Figure 1 is a schematic representation of a heat pump cycle
  • FIG. 2 shows a longitudinal section through an exemplary structural design of a compressor system of the heat pump cycle
  • FIG. 3 shows a cross section along a sectional plane A-A shown in FIG. 2 through an electric machine of the compressor system
  • FIG. 4 shows a cross section along a sectional plane B-B shown in FIG. 2 through a bearing device of the compressor system;
  • Figure 5 is a schematic circuit diagram of a control circuit of a
  • FIG. 6 shows a flow diagram of a method for operating the
  • Figure 7 is a graph of a rotational speed of a compressor rotor plotted against time
  • FIG. 8 shows a diagram of a rotational energy of a rotor of FIG
  • Figure 9 is a plot of a phase current versus time plot
  • Figure 10 is a graph of a current waveform plotted against time.
  • Figure 1 1 is a diagram of a rotor angle of the electric machine
  • FIG. 1 shows a schematic representation of a heat pump cycle 10.
  • the heat pump cycle 10 comprises a compressor system 15, a control unit 20, a first heat exchanger 25, a second heat exchanger 30 and a throttle 35.
  • the compressor system 15 includes an electric machine 40 and a
  • Compressor 45 on.
  • the electric machine 40 serves to drive the compressor 45.
  • the compressor 45 is designed as a turbomachine.
  • the compressor 45 has an input side 50 and an output side 55.
  • the output side 55 of the compressor 45 is connected to an input side of the first heat exchanger 25 by means of a first fluidic connection 60.
  • the first heat exchanger 25 is connected to the throttle 35 by means of a second fluidic connection 65.
  • the throttle 35 is connected to an input side of the second heat exchanger 30 by means of a third fluidic connection 70.
  • An output side of the second heat exchanger 30 is connected to the input side 50 of the compressor 45 by means of a fourth fluidic connection 75. Furthermore, the
  • a heat transfer medium 80th Das Heat transfer medium 80 may include propane, butane and / or CO2, for example.
  • the control unit 20 has an interface 90, a control device 95 and a memory 100.
  • the memory 100 is preferably as a predefined
  • Threshold a target speed ns of the compressor rotor 130 is stored.
  • the nominal rotational speed ns has a value which lies in a range of 15,000 to 60,000 rpm, preferably in a range of 20,000 to 40,000 rpm.
  • the interface 90 is connected to the control device 95 by means of a first electrical connection 105.
  • the memory 100 is connected to the control device 95.
  • Interface 90 is connected by means of a third electrical connection 1 15 with the electric machine 40. Furthermore, the control unit 20 comprises a
  • Speed sensor 120 The speed sensor 120 is disposed on the compressor 45.
  • the speed sensor 120 is connected to the interface 90 of the controller 20 by means of a fourth electrical connection 125.
  • the compressor 45 conveys the heat transfer medium 80 from the input side 50 to the output side 55 and thereby compresses the heat transfer medium 80.
  • the heat transfer medium 80 is conveyed via the first fluidic connection 60 to the first heat exchanger 25.
  • the first heat exchanger 25 serves as an evaporator and thereby absorbs heat W1, for example, from an environment 85 on.
  • the heat transfer medium 80 is via the second fluidic connection
  • Heat transfer medium 80 reduced.
  • the heat transfer medium 80 flows with reduced pressure via the third fluidic connection 70 to the second
  • Heat exchanger 30 The second heat exchanger 30 serves as a capacitor.
  • the heat transfer medium 80 heat W2.
  • the emitted heat W2 can serve, for example, for heating a building.
  • a further heat transfer medium for example in a buffer memory of a heating system, can be heated by means of the second heat exchanger 30.
  • the heat transfer medium 80 is guided back to the input side 50 of the compressor 45 via the fourth fluidic connection 75.
  • Figure 2 shows a longitudinal section through an exemplary constructive
  • the compressor 45 is formed in the embodiment by way of example as a radial compressor.
  • Compressor 45 conceivable.
  • the compressor 45 is designed as an axial compressor.
  • the compressor 45 has a compressor rotor 130.
  • the compressor rotor 130 is rotatably supported about a rotation axis 135.
  • the input side 50 is arranged radially inwardly with respect to the axis of rotation 135, whereas the output side 55 of the compressor 45 is radially outwardly of the
  • Rotary shaft 135 is arranged.
  • the electric machine 40 has a machine rotor 140 and a
  • Machine stator 145 on.
  • the machine stator 145 is rotationally fixed.
  • the machine rotor 140 is torque-coupled by means of a coupling shaft 150 by way of example with the compressor rotor 130 and rotatable about the
  • Rotary shaft 135 stored.
  • a clutch and / or a translation device or other devices are provided between the machine rotor 140 and the compressor rotor 130, for example, a clutch and / or a translation device or other devices are provided to couple the compressor rotor 130 with the machine rotor 140. Also can be dispensed with the coupling shaft 150.
  • the compressor system 15 comprises a bearing device 155. Die
  • Bearing device 155 has a first bearing element 160, a second
  • the first bearing element 160 is designed as a thrust bearing.
  • the second and third bearing element 165, 170 are formed as a radial bearing element.
  • the first bearing member 160 serves to set an axial position of the compressor rotor 130, the engine rotor 140 and the coupling shaft 150.
  • the second and third bearing members 165, 170 rotatably support the compressor rotor 130, the engine rotor 140, and the coupling shaft 150 about the rotation axis 135.
  • all bearing elements 160, 165, 170 are as
  • fluid dynamic fluid bearing preferably as a dynamic gas bearings formed.
  • the bearing elements 160, 165, 170 are formed as a fluid dynamic bearing. Due to the design of the bearing element 160, 165, 170 as a fluid-dynamic fluid bearing, the bearing of the compressor rotor 130 and the machine rotor 140 can be performed with particularly low friction, in particular at high speed.
  • the bearing elements 160, 165, 170 are arranged on the coupling shaft 150. Also, another arrangement of the bearing members 160, 165, 170 at others
  • FIG. 3 shows a cross section along a sectional plane A-A shown in FIG. 2 through the electric machine 40 of the compressor system 15 shown in FIG. 2.
  • the electric machine 40 in the embodiment is designed in an exemplary three-phase manner.
  • the electric machine 40 may be designed as a synchronous motor, asynchronous motor or reluctance machine.
  • the machine stator 145 has, for example, a plurality of circumferentially offset windings 175, 180, 185.
  • the windings 175, 180, 185 are connected to a terminal 190.
  • Each winding 175, 180, 185 is connected via the connection with a fifth, sixth and seventh electrical connection 186, 187, 188 to the interface 90.
  • the first winding 175 is, for example, with a first phase U
  • the third winding 185 by way of example with a third phase
  • the machine rotor 140 has a fourth winding 195, which is electrically connected to the interface 90 via a further connection (not shown).
  • the fourth winding 195 is in operation of the electrical
  • Machine 40 is energized so that the fourth winding 195 a
  • FIG. 4 shows a cross section along a sectional plane B-B shown in FIG. 2 through the third bearing element 170 of the bearing device 155 of FIG
  • the third bearing element 170 is explained by way of example. The explanations should in this case also apply to the first and / or second bearing element 160, 165.
  • the third bearing element 170 has on a inner circumferential surface a first non-rotatably arranged bearing surface 200 and on an outer peripheral surface of the coupling shaft 150, a second bearing surface 205.
  • the second bearing surface 205 is arranged to extend on a circular path about the rotation axis 135.
  • the first bearing surface 200 extends around a circular path about a bearing axis 210.
  • the rotational axis 135 is arranged eccentrically to the bearing axis 210. In this case, the axis of rotation 135 is arranged in the direction of gravity below the bearing axis 210.
  • the second bearing surface 205 rotates about the rotation axis 135.
  • the second bearing surface 205 causes the heat transfer medium 80 in the third bearing element 170 in the circumferential direction in rotation.
  • a supporting force FA which is to support parallel in the direction of gravity
  • a damping force FD which is aligned perpendicular to supporting force FA support.
  • Bearing surface 205 while the counter to the direction of gravity acting bearing force FL and acting perpendicular to the bearing force FL tangential force FT is constructed by a pressure pad 220 of the heat transfer medium 80 in the gap 215.
  • Pressure pad 220 strong enough the force acting against the direction of gravity bearing force FL is temporarily greater than the supporting force FA ISL SO that a Touch contact between the first and the second bearing surface 200, 205 is repealed.
  • the gap 215 below the rotational axis 135 is wider with increasing rotational speed of the second bearing surface 205. With increasing width of the gap 215, the bearing force FL increases until an equilibrium state and the bearing force FL equal to the
  • Supporting force FA is.
  • the rotation axis 135 approaches the bearing axis 210 from below. Due to the support force FA to be supported via the second bearing surface 205, however, the rotation axis 135 is never arranged above the bearing axis 210.
  • Storage area 200 is arranged. Depending on the speed n of the second bearing surface 205, the gap 215 is formed differently wide.
  • the bearing force FL is smaller than the support force FA to be supported via the third bearing element 170, so that the second
  • Storage surface 205 has a contact contact with the first bearing surface 200.
  • the coupling shaft 150 is thus slidingly mounted in the bearing element 165, 170.
  • FIG. 5 shows a schematic circuit diagram of a control circuit 300 of the control device 20.
  • the control circuit 300 has an output stage 305, a
  • Rectifier 310 and a power connector 315 on.
  • the power supply 315 is electrically connected to the rectifier 310.
  • the rectifier 310 provides a positive supply voltage T + and a negative supply voltage T- relative to a ground point 320. Between the negative
  • Supply voltage potential T + may be provided parallel to the rectifier 310 connected intermediate circuit capacitor 321.
  • the output stage 305 comprises the switching elements 325a to 325f in the form of
  • Circuit breakers which with individual phases U, V, W of the electric Machine 40, are connected.
  • the phases U, V, W are either against the positive supply voltage potential T + or the negative
  • Supply voltage potential T + connected switching elements 325a to 325c are also called “high-side switch” and the negative
  • the switching elements 325a to 325f may be embodied, for example, as Insulated Gate Bipolar Transistor (IGBT) or as Metal Oxide Semiconductor Field Effect Transistor (MOSFET)
  • the output stage 305 further includes a plurality of free wheeling diodes 330a to 330f respectively arranged in parallel to one of the switching elements 325a to 325f.
  • the switching elements 325a and 325d, 325b and 325e, and 325c and 325f each form a half bridge 335a, 335b and 335c, respectively each one of the phases U, V, W of the electric machine 40 are assigned.
  • the output stage 305 determines the power and operating mode of the electric machine 40 and is controlled via the control unit 95 via the interface 90.
  • the electric machine 40 is designed in the illustrated embodiment, three-phase, but may also have fewer or more than three phases. Accordingly, the control circuit 300 may also include fewer or more than three half-bridges 335.
  • the current sensor 340a, 340b, 340c each associated with a phase U, V, W.
  • the current sensor 340a, 340b, 340c may be in the form of a
  • the current sensor 340a, 340b, 340c is configured to detect the current or at least a current-characteristic quantity flowing between the windings 175, 180, 185 and the switching elements 325a to 325f.
  • the current sensor 340a, 340b, 340c is connected to the
  • Interface 90 of the controller 20 is connected.
  • the current sensor 340a, 340b, 340c is a function of the current detected in each case for a phase U, V, W a corresponding signal of the interface 90 and the interface 90 of the controller 95 ready.
  • the control device 95 controls via the interface 90, the switching elements 325 a to 325 f such that the windings 175, 180, 185 generate a rotating field in the electric machine 40, wherein by means of the intensity of the rotating field and frequency of the rotating field of the machine rotor 140 about the rotation axis 135th generates a torque and drives the compressor rotor 130.
  • the rotary field or the control of the individual windings 175, 180, 185 via the half bridges 335a, 335b, 335c can be effected by means of pulse width modulation.
  • FIG. 6 shows a flowchart of a method of the heat pump cycle 10.
  • FIG. 7 shows a diagram of a rotational speed n of the compressor rotor 130 plotted against the time t.
  • Figure 8 shows a plot of rotational energy erot plotted over time.
  • FIG. 9 shows a diagram of a course of a
  • FIG. 10 shows a diagram of the current lu of the phase U plotted against the time t.
  • FIG. 11 shows a diagram of a rotor angle of the machine rotor 140 with respect to the machine stator 145 of the electric machine 40 plotted against the time t.
  • control device 95 controls the electric machine 40 in such a way that the electric machine 40
  • Compressor rotor 130 with a predefined speed nv preferably constant drive over a predefined time interval.
  • the predefined speed nv is thereby, preferably by at least a factor of 1, 5, greater than that
  • the final stage 305 is switched in a second method step 405 via the control device 95 such that the electric machine 40 is operated in a freewheeling operation.
  • the switching elements 325a to 325f are all opened so that the Windings 175, 180, 185 are electrically isolated from the power supply 315.
  • the compressor rotor 130 and the engine rotor 140 continue to rotate.
  • the rotational speed n of the compressor rotor 130 drops in a first time interval 600 (see FIG. after Stromlossciens the windings 175, 180, 185 from.
  • Control device 95 detects the speed n of the compressor rotor 130 by means of the speed sensor 120 in a third method step 410.
  • a fourth method step 415 which follows the second method step 405 and the third method step 410, the control device 95 compares the detected speed n with the setpoint speed ns. If the rotational speed n exceeds the target rotational speed ns, a fifth method step 420 is continued.
  • a predefined time interval is awaited.
  • the predefined time interval may correspond, for example, to a clock frequency of the control device 95. It is also conceivable that the memory 100, the predefined time interval is stored.
  • control device 95 continues with the fourth method step 415.
  • the control device 95 controls the compressor 45 such that the compressor 45 reduces a pressure of the heat carrier medium 80 between the input side 50 and the output side 55. This can be done, for example, by opening a bypass in the compressor 45 on the basis of a control signal of the control device 95, which connects the input side 50 to the output side 55.
  • a seventh method step 430 which takes place in the sixth method step 425, the control device 95 switches the output stage 305 into a
  • the fourth winding 195 for the magnetic field is further energized.
  • a current lu, lv, lw is induced in the first to third windings 175, 180, 185.
  • the induced current lu, lv, lw is short-circuited via the switching elements 325a to 325f.
  • the respectively induced in the windings 175, 180, 185 induced current lu, lv, lw generates a magnetic field via a short-circuit torque M, which against the
  • Rotary movement of the engine rotor 140 acts and thus the engine rotor 140, the compressor rotor 130 and the coupling shaft 150 decelerates.
  • all the switching elements 325a to 325f are simultaneously turned on.
  • all high-side switches 325a to 325c are turned off, while at the same time all low-side switches 325d to 325f are turned on.
  • the short-circuit mode is done exclusively via the low-side switches 325d to 325f.
  • all high-side switches 325a to 325c of all motor phases are switched on, while at the same time all low-side switches 325d to 325f of all motor phases are switched off. In this case, the short circuit occurs via the high-side switches 325a to 325c.
  • the diagram of FIG. 7 shows a first graph 500, a second graph 505 and a third graph 510.
  • the first graph 500 shows a rotational speed profile of the compressor rotor 130 when the graph of FIG.
  • Compressor rotor 130 in a switching state of the control circuit 300 as is done in the second step 405 and the windings 175, 180, 185 are not short-circuited.
  • the rotational speed n drops slowly over a time t in a second time interval 605.
  • the pressure pad 220 of the heat transfer medium 80 in the bearing element 160, 165, 170 too weak to prevent Berrindrome the second bearing surface 205 with the first bearing surface 200.
  • the second bearing surface 205 slides on the first bearing surface 200 in a third time interval 610. This leads to an increased wear of the bearing surfaces 200, 205.
  • the rotational energy E ro t by friction in the bearing element 160, 165, 170 degraded.
  • the bearing element 160, 165, 170 has a particularly low manufacturing tolerance.
  • the tolerance of the bearing element 160, 165, 170 is worn out by mechanical wear, in particular during operation of the bearing element 160, 165, 170 below the limit speed nG.
  • the second graph 505 and also the third graph 510 show one
  • Speed curve of the speed n over time after switching the control circuit 300 in the short-circuit operation (seventh step 430). Due to the short-circuit operation, the rotational speed n is reduced very rapidly compared to the first graph 500 in a fourth time interval 615. In particular, a large part of the rotational energy E ro t is compared to a leakage of the
  • Compressor rotor 130 (as in the first graph 500) degraded into heat energy through the windings 175, 180, 185 and the switching elements 325a to 325f.
  • the fourth time interval has different lengths. The faster reduction of the rotational energy ER 0 t compared with the running out of the compressor rotor 130 is shown in FIG. 8 with a fourth graph 515
  • the setpoint speed ns has a value which is significantly greater, preferably greater by a factor of 2, than that
  • the short-circuit torque M can be generally compared with the general
  • ⁇ is constant.
  • U is a voltage of the electric machine 40
  • R is an electrical machine 40 resistance
  • ⁇ is the magnetic flux.
  • Machine 40 and ⁇ angular frequency of the machine rotor 140 are identical to Machine 40 and ⁇ angular frequency of the machine rotor 140.
  • the current lu, lv, lw induced in the windings 175, 180, 185 is preferably detected parallel to the seventh method step 430 in an eighth method step 435 by the current sensor 340a, 340b, 340c (see FIG.
  • the control device 95 determines the rotor angle ⁇ of the machine rotor 140 relative to the machine stator 145 based on the detected induced current lu, lv, lw (see FIG. Of course, it is also conceivable that the rotor angle ⁇ is determined differently, for example by means of a Hall sensor.
  • FIG. 10 shows the currents lu, lv, lw during the braking process over time.
  • the total current I determined from the currents lu, lv, lw is shown as an example by a solid line.
  • a dashed line shows a determined current profile from the current lu, lv, lw.
  • FIG. 11 shows the determined rotor angle ⁇ based on the determined current profile based on FIG.
  • a ninth method step 440 the control device 95 checks whether the detected rotational speed n is greater than 0 and whether the compressor rotor 130 thus rotates.
  • control device 95 continues with the seventh and eighth process steps 430, 435. If the rotational speed n of the compressor rotor 130 is equal to 0, then the control device 95 drives with one tenth
  • Step 445 continues.
  • control device 95 switches all
  • Switching elements 325a to 325f off and lifts the short circuit operation. It is advantageous if the control device 95 waits for another predefined time interval. This has the advantage that before canceling the short-circuit operation at a standstill restarting the compressor rotor 130 at unfavorable Conditions, in particular at a pressure between the input side 50 and the output side 55 of the compressor 45, reliably by the in
  • Short circuit operation generated short-circuit torque of the electric machine 140 can be avoided.
  • the control device 95 determines a standstill rotor angle Bs of the machine rotor 140 with which it came to a standstill during deceleration on the basis of the rotor angle erf detected in the eighth method step 435.
  • the standstill rotor angle Bs is stored in the memory 100.
  • the control device 95 takes into account the shutdown rotor angle Bs stored in the memory 100 in a twelfth method step 460 when the switching elements 325a to 325f are actuated, by correspondingly driving the switching elements 325a to 325f to a stop rotor angle Bs Rotary field for starting the engine rotor 140 to produce.
  • a swinging of the engine rotor 140 to the rotating field can be avoided and a starting operation of the electric machine 40 for starting up the compressor system 15 can be shortened.
  • a sliding friction within the bearing device 155 is kept particularly short.
  • Process steps 400 to 460 is dispensed with.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Abstract

L'invention concerne un procédé de commande d'un groupe compresseur ainsi qu'un groupe compresseur, ledit procédé consistant à entraîner le rotor du compresseur du groupe compresseur à une vitesse de rotation prédéfinie au moyen du moteur électrique, à commuter le moteur électrique en mode roue libre, ce qui entraîne un fonctionnement par inertie du rotor du compresseur du groupe compresseur, et une réduction de sa vitesse de rotation par rapport à la vitesse de rotation prédéfinie, à mesurer la vitesse de rotation du rotor du compresseur et à la comparer à une vitesse de rotation de consigne, et si la vitesse de rotation est inférieure à la vitesse de rotation de consigne, à commuter le moteur électrique en mode court-circuit.
PCT/EP2017/058602 2016-05-02 2017-04-11 Procédé de commande d'un circuit de pompe à chaleur incluant un moteur électrique d'un groupe compresseur, et circuit de pompe à chaleur Ceased WO2017190917A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016207493.8A DE102016207493A1 (de) 2016-05-02 2016-05-02 Verfahren zur Steuerung eines Wärmepumpenkreislaufs mit einer elektrischen Maschine eines Verdichtersystems und Wärmepumpenkreislauf
DE102016207493.8 2016-05-02

Publications (1)

Publication Number Publication Date
WO2017190917A1 true WO2017190917A1 (fr) 2017-11-09

Family

ID=58640823

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/058602 Ceased WO2017190917A1 (fr) 2016-05-02 2017-04-11 Procédé de commande d'un circuit de pompe à chaleur incluant un moteur électrique d'un groupe compresseur, et circuit de pompe à chaleur

Country Status (2)

Country Link
DE (1) DE102016207493A1 (fr)
WO (1) WO2017190917A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023120370A1 (de) * 2023-08-01 2025-02-06 Bitzer Kühlmaschinenbau Gmbh Verdichter-/Expandermaschine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117526774A (zh) 2018-12-04 2024-02-06 丹佛斯（天津）有限公司 一种控制压缩机制动的方法、变频器及变频压缩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999005779A1 (fr) * 1997-07-24 1999-02-04 Zexel Corporation Procede et dispositif de commande de l'entrainement d'un conditionneur d'air
US5897299A (en) * 1995-05-23 1999-04-27 Daikin Industries, Ltd. Anti-reverse rotation apparatus of compressor
US20080110685A1 (en) * 2006-11-09 2008-05-15 Gm Global Technology Operations, Inc. Turbocompressor shutdown mechanism
JP2014171370A (ja) * 2013-03-05 2014-09-18 Mitsubishi Electric Corp モータ駆動制御装置、空気調和機、換気扇およびヒートポンプ式給湯器
EP2921709A1 (fr) * 2014-03-19 2015-09-23 Kabushiki Kaisha Toyota Jidoshokki Machine à fluide de type turbo
DE102014217005A1 (de) * 2014-08-26 2016-03-03 BSH Hausgeräte GmbH Verfahren zum Bremsen eines Verdichters und Verdichter eines Kältegerätes, Klimageräts oder einer Wärmepumpe sowie Kältegerätes, Klimageräts oder Wärmepumpe damit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004127385A (ja) * 2002-09-30 2004-04-22 Mitsumi Electric Co Ltd 光ディスク装置及び光ディスク装置のブレーキ制御方法
DE102012208762B4 (de) * 2012-05-24 2022-05-05 Robert Bosch Gmbh Verfahren zum Abbremsen einer Strömungsmaschine mit einer Synchronmaschine
DE102013217261A1 (de) * 2013-08-29 2015-03-05 Robert Bosch Gmbh Kompressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5897299A (en) * 1995-05-23 1999-04-27 Daikin Industries, Ltd. Anti-reverse rotation apparatus of compressor
WO1999005779A1 (fr) * 1997-07-24 1999-02-04 Zexel Corporation Procede et dispositif de commande de l'entrainement d'un conditionneur d'air
US20080110685A1 (en) * 2006-11-09 2008-05-15 Gm Global Technology Operations, Inc. Turbocompressor shutdown mechanism
JP2014171370A (ja) * 2013-03-05 2014-09-18 Mitsubishi Electric Corp モータ駆動制御装置、空気調和機、換気扇およびヒートポンプ式給湯器
EP2921709A1 (fr) * 2014-03-19 2015-09-23 Kabushiki Kaisha Toyota Jidoshokki Machine à fluide de type turbo
DE102014217005A1 (de) * 2014-08-26 2016-03-03 BSH Hausgeräte GmbH Verfahren zum Bremsen eines Verdichters und Verdichter eines Kältegerätes, Klimageräts oder einer Wärmepumpe sowie Kältegerätes, Klimageräts oder Wärmepumpe damit

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023120370A1 (de) * 2023-08-01 2025-02-06 Bitzer Kühlmaschinenbau Gmbh Verdichter-/Expandermaschine

Also Published As

Publication number Publication date
DE102016207493A1 (de) 2017-11-02

Similar Documents

Publication Publication Date Title
DE102006030362A1 (de) Motor/Verfahren und System zum Starten eines sensorlosen Motors
EP0945973B1 (fr) Dispositif de commande pour un moteur synchrone monophase
EP2715932A2 (fr) Procédé et dispositif permettant de faire fonctionner un moteur sans balais
DE102016102789A1 (de) Motorbetriebener Verdichter
WO2017190917A1 (fr) Procédé de commande d'un circuit de pompe à chaleur incluant un moteur électrique d'un groupe compresseur, et circuit de pompe à chaleur
WO2012025904A2 (fr) Procédé d'excitation d'un petit moteur monophasé à courant continu sans balai
DE602004012158T2 (de) Anlasssystem für einen einphasen-induktionsmotor
EP1812714B1 (fr) Ensemble comprenant un ventilateur et une pompe
EP2714489B1 (fr) Procédé et dispositif permettant de faire fonctionner un moteur sans balais
EP3400645B1 (fr) Entraînement de pompe à vide avec commutation étoile-triangle
EP0957570A2 (fr) Dispositif pour commander un moteur synchrone monophasé
EP1418664A2 (fr) Moteur synchrone
DE102014116689A1 (de) Vorrichtung und Verfahren zum Sichern einer Antriebssteuerung gegen Versorgungsspannungsausfälle
DE102006026560A1 (de) Anlaufverfahren für einen sensor- und bürstenlosen Gleichstrommotor
EP2854140A1 (fr) Module de résistance pour l'augmentation du couple de démarrage pour un rotor d'une machine électrique dotée d'un enroulement rotorique
DE102005035451B3 (de) Elektronisch kommutierter Motor, insbesondere Lüftermotor, und Verfahren zur Ansteuerung des Motors
DE102013009518A1 (de) Kraftfahrzeug mit einer Kraftstoff-Heizeinrichtung
EP2982035B1 (fr) Procédé de mise en marche d'un moteur électrique à vitesse variable
DE4413802C2 (de) Verfahren und Vorrichtung zum Steuern der Drehzahl eines elektrischen Dreiphasen-Asynchronmotors
EP1443635A1 (fr) Procédé de contrôle d'un angle de déclenchement
EP3449564B1 (fr) Procédé et dispositif de commande d'une machine électrique
DE4017442A1 (de) Einzelspindelantrieb fuer eine arbeitsstelle einer spinnereimaschine
EP3676951B1 (fr) Commande d'un moteur de ventilateur pour l'amélioration de la compatibilité électromagnétique
DE102014100572A1 (de) Verfahren zum Betreiben eines BLDC-Motors mit sensorloser Kommutierung
EP2223131B1 (fr) Procédé pour faire fonctionner sans capteur une machine électrique à commutation électronique

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17720014

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 17720014

Country of ref document: EP

Kind code of ref document: A1