EP3821130A2 - Compresseur à spirales - Google Patents

Compresseur à spirales

Info

Publication number
EP3821130A2
EP3821130A2 EP19742309.8A EP19742309A EP3821130A2 EP 3821130 A2 EP3821130 A2 EP 3821130A2 EP 19742309 A EP19742309 A EP 19742309A EP 3821130 A2 EP3821130 A2 EP 3821130A2
Authority
EP
European Patent Office
Prior art keywords
pressure
scroll compressor
spiral element
actuator
sensor
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.)
Withdrawn
Application number
EP19742309.8A
Other languages
German (de)
English (en)
Inventor
Andreas Inhoff
Simon SCHMIDER
Thomas Hartmann
Walter Zipp
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.)
Ipetronik GmbH and Co KG
Original Assignee
Ipetronik GmbH and Co KG
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 Ipetronik GmbH and Co KG filed Critical Ipetronik GmbH and Co KG
Publication of EP3821130A2 publication Critical patent/EP3821130A2/fr
Withdrawn legal-status Critical Current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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric

Definitions

  • the present invention relates to a scroll compressor according to claim 1 and
  • Refrigerant compressors are increasingly using electrically driven refrigerant compressors.
  • the electrically driven refrigerant compressor has become the standard, particularly in hybrid vehicles and purely electrically powered vehicles. By using your own electric motor, it will
  • Auxiliary unit independent of the speed of the vehicle drive train and thus allows a wide range of control options.
  • the electrically driven refrigerant compressors that are used in passenger cars are often designed as scroll compressors.
  • Scroll compressor has two spiral elements that run into each other
  • stator spiral element remains stationary while the other spiral element, the stator spiral element
  • Rotor spiral element by a rotating electric motor and a special intermediate drive relative to the stator spiral element in an orbiting
  • the radial sealing between the spiral contours takes place via liquid oil, which is entrained by the mass flow of the gaseous refrigerant during operation.
  • the axial sealing takes place via sealing elements on the edges of the spiral contour of the rotor spiral element and its axial contact pressure.
  • the ideal value of the axial contact force depends on the operating range of the
  • Stator spiral element can also lead to the risk of wear and direct damage.
  • the aim of the invention is therefore to optimize the axial setting
  • a scroll compressor which has the following: a compressor unit with a fixed stator spiral element and a rotatable rotor spiral element which is mounted so as to be axially movable relative to the stator spiral element, the compressor unit being designed to suck in, compress and compress a fluid to be compressed from a suction area to promote in a high pressure area; a back pressure chamber, which on a side facing away from the stator spiral element
  • Rotor spiral element is arranged and can be acted upon with a back pressure to apply a pressing force in the axial direction on the rotor spiral element to exert and to press the rotor spiral element against the stator spiral element, wherein there is a fluid connection between the back pressure chamber and the suction area, and wherein there is a fluid connection between the back pressure chamber and the high pressure area; a suction pressure channel arranged in the fluid connection between the back pressure chamber and the suction area; a high pressure channel disposed in the fluid communication between the back pressure chamber and the high pressure area; wherein at least one actuator element in the high pressure channel and the suction pressure channel
  • An essential point of the invention is that the provision of the actuator elements and the thus variable cross-section of the pressure channels overcome the limitations of fixed cross-sectional relationships or mechanically acting control elements for determining the contact pressure.
  • the back pressure in the back pressure chamber can be controlled reliably, precisely and quickly by providing the actuator elements. This allows the
  • Compressor unit can be increased.
  • dynamic compression unit can be increased.
  • dynamic compression unit can be increased.
  • Rotor spiral element are suppressed along the axial direction, which would contribute to increased noise in addition to additional wear.
  • the back pressure can be quickly and reliably adapted to changing operating conditions of the scroll compressor with the present invention. This makes, for example, an adaptation to different
  • the actuator elements according to the invention are components which contain electrical signals, for example commands originating from a control computer
  • Actuator elements thus actively intervene in the process of controlling the contact pressure.
  • the actuator elements have, for example, an electrical and / or a mechanical and / or a pneumatic and / or a hydraulic
  • the actuator element of the high-pressure duct and / or the actuator element of the suction pressure duct is formed by an actuator element with an orifice geometry, a needle valve, a ball valve, a throttle valve or a shape memory wire.
  • a needle valve has a cylindrical shaft with a tapered tip. In the closed position, this conical tip sinks into a conical bore.
  • the needle tip is axially adjusted, for example, by means of a stepper motor or a current-carrying coil and gives one
  • the actuator element is designed on the principle of a ball valve.
  • a pierced ball is used as a shut-off body, which sits in a congruently shaped cavity in the pipe.
  • the ball valve By rotating the pierced ball through 90 ° about an axis perpendicular to the piercing, the ball valve can be transferred from a fully open state to a fully closed state.
  • the rotation can in turn be brought about, for example, by a stepper motor which is coupled to the ball valve directly or via a gear.
  • the change in the channel cross section can be achieved in that the actuator element is designed as a throttle valve.
  • the closure element can be driven by a stepper motor or by means of a current-carrying coil.
  • Other common drive concepts such as gear or worm gear are also an option
  • the actuator element can also be formed by a shape memory wire.
  • a metal wire made of a special alloy is provided in the cross section of the pressure channel, the wire changing its shape or its diameter depending on the current intensity when current is applied, in order to change the cross section of the pressure channel.
  • the actuator element of the high-pressure channel and the actuator element of the suction pressure channel is a
  • the mixing valve formed, which is connected to the high pressure channel, the suction pressure channel and the back pressure chamber.
  • the mixing valve has at least two inputs, each of which is connected to the high-pressure duct and the suction pressure duct, and at least one output, which is connected to the
  • Back pressure chamber is connected. This represents a structurally simple and robust solution for setting the back pressure in the back pressure chamber.
  • the mixing valve can be connected to at least one electrical control unit.
  • the scroll compressor has a sensor element that is designed to measure a measurement variable from which the contact pressure that can be generated by the counterpressure in the counterpressure chamber can be determined.
  • the sensor element is a
  • Pressure sensor is formed, which is designed to measure the back pressure prevailing in the back pressure chamber. This enables a conceptually simple and reliable determination of the contact pressure. Is the effective area of the
  • the pressure force can be easily calculated from the product of the measured pressure and the effective area.
  • the sensor element can be formed by a force sensor, which on a drive shaft connected to the rotor spiral element, the
  • Rotor spiral element or the stator spiral element is arranged.
  • the force sensor is designed so that it measures a force in the axial direction, so that the contact pressure can be determined directly.
  • force-correlating sensors are used, such as strain gauges or piezoelectric elements. Strain gauges change their resistance when deformed. An electrical voltage occurs in piezoelectric elements when deformed. With both sensor types, electronic detection of a force acting on the rotor spiral element or the stator spiral element is possible.
  • the scroll compressor has a control unit that is designed to control the at least one actuator element, such that the one that can be generated by the back pressure in the back pressure chamber
  • Contact pressure can be controlled, in particular as a function of the contact pressure determined by means of the sensor element.
  • a scroll compressor which has the following: a compressor unit with a stationary one
  • Stator spiral element facing away is coupled to a
  • a particular advantage of this variant of the contact pressure generation is that there is no supply of refrigerant that has already been compressed from the high pressure side back into the compression process. This means that there is almost no leakage current at the compressor unit
  • both applications are possible that directly transfer an actuator movement to the shaft, e.g. by means of a stepper motor with tappet arranged on the drive shaft, as well as indirect power transmission by means of levers or a gear.
  • An actuator is generally to be understood as a drive element which converts electrical signals, for example from control electronics, into mechanical movement.
  • the actuator is formed by a piezoelectric element. This enables a particularly precise setting of the actuator
  • the scroll compressor has a sensor element that is designed to measure a measurement variable from which the contact pressure that can be generated by the actuator can be determined. This allows more precise control of the contact pressure, with which changes in the operating state of the scroll compressor can be taken into account.
  • the sensor element is formed by a force sensor which is attached to the drive shaft, the stator spiral element or the
  • Rotor spiral element is attached. This enables direct and
  • the force-correlating sensors described above can in turn be used as force sensors.
  • the scroll compressor has a control unit which is designed to control the actuator in such a way that the Contact force that can be generated by the actuator can be controlled, in particular in
  • the scroll compressor has an oil return, which forms a fluid connection between the high pressure area and the suction area, in order to return oil located in the high pressure area to the suction area, wherein an oil return actuator element is arranged in the oil return, by means of which the cross section of the Oil return is changeable.
  • an oil return actuator element is arranged in the oil return, by means of which the cross section of the Oil return is changeable.
  • Control oil return depending on the operating state of the scroll compressor can in turn be used for the oil return actuator element.
  • a solenoid valve can be used as the oil return actuator element, which can only assume an open or closed position. The amount of oil returned can then be controlled by controlling a clock frequency with which the solenoid valve is opened and closed.
  • the scroll compressor has a fill level sensor which is designed to measure an oil fill level in the high pressure region.
  • the scroll compressor has one
  • Speed sensor which is designed to a speed of the
  • the scroll compressor has a rotary drive control which is designed to rotate the
  • the scroll compressor has a high-pressure sensor which is designed to measure a pressure in the
  • the high pressure sensor is preferably a
  • Highly dynamic pressure sensor with low hysteresis which is designed to measure the maximum pressure of the fluid to be compressed in the high pressure chamber in the direction of flow of the fluid in front of an outlet in the high pressure chamber.
  • the rotary drive control is designed to control the control of the rotary drive as a function of the pressure in the compressor unit. This can cause a pressure surge in the
  • Compressor unit a sudden increase in the speed of the
  • Rotor spiral element are compensated, which is caused by the fact that the speed increases sharply with a constant torque of the rotary drive in the event of a pressure drop in the compressor unit. This can actively reduce rotary shocks during operation of the scroll compressor.
  • the scroll compressor has a temperature sensor which is designed to measure a temperature of the fluid to be compressed in the high pressure region, preferably directly at an outlet of the
  • this can be provided as a safety measure to prevent the scroll compressor from exceeding one
  • the State of matter of the fluid to be compressed in the high pressure area can be determined. In this way it can be determined whether liquid refrigerant can be present in the compressor unit. Accordingly, it is then possible that
  • control unit is designed to:
  • the axial force can be controlled.
  • the axial force can be directly applied to the changed one
  • the wear of the compressor unit can be reduced and the service life of the compressor unit can be increased, the efficiency of the scroll compressor can be further improved and the excitation of oscillations and vibrations by a periodic axial movement of the rotor spiral element during the
  • Invention for a scroll compressor for cars can then be dispensed with conventional measures for reducing vibrations such as corresponding mechanical decouplings, bearings, damping elements, the integration of additional masses or the like.
  • Fig. 1 shows a section of a scroll compressor according to a first
  • FIG. 2 shows a modification of the scroll compressor according to FIG. 1 with a modified one
  • FIG. 3 shows a modification of the scroll compressor according to FIG. 2 with a
  • FIG. 4 shows a modification of the scroll compressor according to FIG. 3 with a
  • FIG. 5 shows a modification of the scroll compressor according to FIG. 1 with a
  • FIG. 6 shows a further modification of the scroll compressor according to FIG. 1 with a further alternative for a sensor element
  • FIG. 7 shows a further modification of the scroll compressor according to FIG. 1 with a further alternative for a sensor element
  • Fig. 8 shows a section of a scroll compressor according to a second
  • FIG. 9 shows a modification of the scroll compressor according to FIG. 8.
  • Fig. 10 shows a section of a scroll compressor according to another
  • FIG. 11 shows a modification of the scroll compressor according to FIG. 8 with a
  • FIG. 12 shows a modification of the scroll compressor according to FIG. 11 with a
  • Oil recirculation actuator element shows a modification of the scroll compressor according to FIG. 12 with a level sensor
  • FIG. 14 shows a modification of the scroll compressor according to FIG. 13 with a
  • FIG. 15 shows a modification of the scroll compressor according to FIG. 14 with a
  • FIG. 16 shows a modification of the scroll compressor according to FIG. 15 with a
  • FIG. 1 shows a section of a scroll compressor according to a first
  • the scroll compressor has a housing 50 with a substantially cylindrical shape.
  • the cylinder axis Z of the housing 50 is shown with a dash-dotted line.
  • the direction parallel to the cylinder axis Z of the housing 50 is referred to below as the axial direction.
  • the housing 50 has a fluid inlet 51 on the lateral surface, through which fluid to be compressed can be introduced into the scroll compressor.
  • the fluid is introduced into a suction region 30 via the fluid inlet 51.
  • a compressor unit 20 adjoins the suction area 30 in the axial direction, into which fluid is sucked in from the suction area 30 when the scroll compressor is in operation and compressed there.
  • a high-pressure region 40 connects to the compressor unit 20 in the axial direction, into which the fluid compressed in the compressor unit 20 is conveyed and from which it flows out through a fluid outlet 52 in the housing 50 of the scroll compressor.
  • the functional units of the scroll compressor are described in detail below.
  • a drive shaft 23 is arranged in the suction area 30 and is rotatably supported by means of two bearings 24a, 24b.
  • the drive shaft 23 is rotatably connected to a rotor 24 of an electric motor, which is surrounded by a stator 25 of the electric motor.
  • the drive shaft 23 can by means of electric motor are driven in rotation.
  • the electronics required for controlling the electric motor are accommodated in an electronics housing 70 which is arranged adjacent to the housing 50 of the scroll compressor.
  • the suction area 30 is connected via a compressor feed line 27 to the
  • the compressor unit 20 connected.
  • the compressor unit is essentially formed by two spiral elements, namely a stator spiral element 21 mounted immovably in the housing and a rotor spiral element 22 movably mounted relative to the stator spiral element 21.
  • Both spiral elements have a base plate 21a, 22a, each of which extends perpendicular to the cylinder axis Z of the scroll compressor ,
  • a spiral wall 21b, 22b extends from the base plates 21a, 22a of the spiral elements in each case parallel to the cylinder axis Z.
  • the spiral elements are arranged in the compressor unit 20 such that the spiral walls 21b, 22b interlock.
  • the spiral walls of each spiral element extend to the bottom plate of the opposite spiral element.
  • sealing elements are arranged, which are shown in FIG. 1 as black squares. The sealing elements serve to mutually seal the spiral elements in the axial direction.
  • the rotor spiral element 22 is offset from the stator spiral element 21 perpendicular to the cylinder axis Z.
  • the rotor spiral element 22 is rotatably mounted on the drive shaft 23 by means of a bearing 24c, the rotor spiral element 22 being arranged eccentrically with respect to the drive shaft 23, as shown in FIG. 1.
  • Sickle-shaped pockets are formed between the spiral walls 21b, 22b, which migrate in the direction of the center of the spirals during the orbiting movement of the rotor spiral element 22, the volume of which decreases. Thereby the fluid introduced into the compressor unit 20 radially from the outside via the compressor feed line 27 is compressed during the orbiting movement of the rotor spiral element 22.
  • the compressor unit 20 has a hot gas valve 26 on the side facing the high pressure region 40 near the cylinder axis Z, through which compressed fluid flows from the compressor unit 20 into a high pressure chamber 41 in the
  • the hot gas valve 26 is a
  • Compressor unit 20 in the high pressure chamber 41 allows and a
  • the compressed fluid flows out of the high pressure chamber 41 via a
  • Overflow channel 43 in an oil separation chamber 42 for lubricating the electric motor in the suction area 30 and for radially sealing the
  • Spiral elements in the compressor unit 20 contain liquid oil in the suction area 30, which is in contact with the components of the electric motor and is entrained during the operation of the scroll compressor via the mass flow of the gaseous fluid in the suction area 30 when sucking into the compressor unit 20.
  • the oil discharged into the high-pressure region 40 is separated in the oil separation chamber 42 in that the overflow channel 43 is formed in such a way that the passing mixture of oil and fluid substantially tangentially enters the oil separation chamber 42, which is cylindrical.
  • the combination of tangential overflow channel 43 and cylindrical oil separation chamber 42 acts as a centrifugal separator.
  • Oil separation chamber 42 are directed back into the suction area 30.
  • the movably mounted rotor spiral element 22 In order to achieve the sealing required for the compression process in the axial direction, the movably mounted rotor spiral element 22 must be subjected to a pressing force in the axial direction in order to
  • a counter pressure chamber 10 is arranged on the side of the rotor spiral element 22 facing away from the stator spiral element 21.
  • Back pressure chamber 10 is on one side of the bottom plate 22a of the
  • Rotor spiral element 22 limited. If the back pressure chamber 10 is pressurized, this causes a pressing force on the
  • Stator spiral element 21 is pressed.
  • the back pressure chamber 10 is in fluid communication with a mixing chamber 105.
  • the mixing chamber 105 is in fluid communication with the suction area 30 and the high pressure area 40.
  • the fluid connection with the suction area 30 is established through a suction pressure channel 103.
  • High-pressure area 40 is produced by a high-pressure channel 104.
  • the suction pressure channel 103 and the high pressure channel 104 are designed as bores in the housing 50.
  • Fluid flows into the mixing chamber 105 through the suction pressure channel 103 with a suction pressure prevailing in the suction region 30.
  • Compressed fluid flows into the mixing chamber 105 at high pressure level via the high pressure channel 104.
  • a counterpressure thus arises in the mixing chamber 105, which is derived from the proportions of suction and high pressure results. This pressure level also arises in the
  • Suction pressure channel 103 and the high pressure channel 104 variable. This is achieved in that a first actuator element 101 is arranged in the suction pressure channel 103 and a second actuator element 102 is arranged in the high pressure channel 104. Depending on the cross sections of the two pressure channels 103 and 104, which are set by means of the actuator elements 101 and 102, the back pressure in the Back pressure chamber 10, and thus the contact pressure for the rotor spiral element 22 can be adjusted.
  • the actuator elements 101 and 102 are each shown in FIG. 1 connected to a stepper motor.
  • the stepper motor of the actuator elements 101 and 102 generates a rotary movement which is transmitted to an actuator element which is arranged in the pressure channels and which changes the cross section of the respective pressure channel due to its movement.
  • Specific possible embodiments for actuator elements are, for example, orifices, needle valves, ball valves or throttle valves.
  • a motor-operated actuator element other devices can be used that allow a controlled change in cross-section of the pressure channels.
  • FIG. 2 shows a modification of the scroll compressor according to FIG. 1.
  • the mixing chamber 105 is omitted.
  • the high-pressure duct 104 and the intake duct 103 are connected directly to the counter-pressure chamber 10 via a bore.
  • FIG. 3 shows a further modified exemplary embodiment of the scroll compressor according to FIGS. 1 and 2.
  • the actuator elements 101 and 102 are replaced by an actuator element which is formed by a mixing valve 101a.
  • the two inputs of the mixing valve 101a are each with the high pressure channel 104 and the
  • Mixing valve 101a generates a medium pressure from the proportional inflows of suction and high pressure at the valve outlet, which is connected to the back pressure chamber 10.
  • the mixing valve 101a is in turn connected to a motor via which the valve position can be adjusted.
  • FIG. 4 shows an exemplary embodiment of a scroll compressor according to the invention, modified from the exemplary embodiment of FIG. 3, in which a sensor element in the form of a pressure sensor 110 is provided.
  • Pressure sensor 110 is arranged in the back pressure chamber 10 and is designed to measure the back pressure prevailing in the back pressure chamber 10. The value of the back pressure determined in this way is multiplied by the size of the area of the base plate 22a of the rotor spiral element 22 which is in direct contact with the back pressure chamber 10, that is to say an effective area of the base plate 22a on which the back pressure determined by the pressure sensor 110 acts to the pressing force that acts on the rotor spiral element 22.
  • Fig. 5 shows a modification of the embodiment of Fig. 1.
  • the sensor element is formed by a force sensor 111, which on the
  • Rotor spiral element 22 facing away from the end of the drive shaft 23 is arranged.
  • the force sensor 111 is decoupled from the drive shaft 23 or its rotational movement by an axial sliding bearing 112. Since the force sensor 111 is arranged near the axial end of the housing 50 on which the electronics housing 70 is located, this is necessary for the operation of the force sensor 111
  • the force sensor 111 is arranged to measure a force that is in
  • the force sensor 111 can be formed by a piezoelectric element, in which one
  • Element leads to the occurrence of an electrical voltage, the amount of which is proportional to the amount of deformation.
  • Corresponding characteristic curve which can be determined in advance and can be stored in purple in the force sensor electronics, the force acting on the force sensor 111 can be determined, from which the contact pressure can in turn be inferred with a suitable calibration of the system. This modification can
  • FIG. 6 and FIG. 7 show further possible designs for a force sensor as a modification of the exemplary embodiment from FIG. 1. These modifications can also be applied to the exemplary embodiments of FIGS. 2 or 3.
  • the force sensor 111 is a strain gauge formed, which is attached to the bottom plate 21a of the stator spiral element 21 on the side facing the rotor spiral element 22, see FIG. 6, or on the bottom plate 21a of the stator spiral element 21 on the
  • the pressing force determined in real time can now be used as a control variable in a control circuit in order to control the actuator elements in such a way that the pressing force is set to a predetermined value in order to achieve the optimum contact pressure at any operating point or load point of the scroll compressor Adjust actuator elements controllable back pressure.
  • the control circuit required for this is not shown in FIGS. 4 to 7. It can be present in the electronics housing 70 or can be accommodated in a separate control device. Alternatively, the control circuit can also be present in an existing vehicle intelligence, if the
  • Scroll compressor is used in a car.
  • Fig. 8 shows a section of a scroll compressor according to a second
  • Embodiment of the present invention differs from the exemplary embodiments shown in FIGS. 1 to 7 in the constructive solution for generating the contact pressure. Same
  • the drive shaft in 23 in Fig. 8 serves as in the previous ones
  • Embodiment is mounted in the scroll compressor movable in the axial direction. This can be achieved, for example, in that the bearings 24a, 24b are designed as floating bearings.
  • the compressor feed line 27, the Suction area 30 fluidly connects to the compressor unit 20 is also provided.
  • the suction pressure and high pressure channels, however, are not available.
  • the contact pressure is generated in that an actuator 120 is provided which is designed to generate a
  • the actuator 120 is arranged on the axial end of the drive shaft 23 facing away from the compressor unit 20.
  • the actuator 120 is of the
  • Actuator electronics 112a which is required for actuating the actuator 120, are in the electronics housing 70
  • the integration of the actuator 120 along the axis of rotation of the drive shaft 23 makes it possible to convert a control signal for the actuator 120 into mechanical movement.
  • the movement of the actuator 120 is transmitted to the drive shaft 23.
  • the contact pressure between the rotor spiral element 22 and the stator spiral element 21 can thus be generated via the mechanical movement of the actuator 120.
  • the actuator 120 can be formed, for example, by a stepper motor with a plunger.
  • An advantage of the generation of contact pressure by an actuator 120 acting on the drive shaft 23 is that no return of already compressed fluid from the high pressure region 40 back into the
  • FIG. 9 shows a modification of the scroll compressor according to FIG. 8.
  • Stop 113 is provided, which limits the movement of the drive shaft 23 in the axial direction, regardless of a minimal actuator movement.
  • Various actuators do not behave linearly with their actual working area with a minimal degree of control. Because the actuator 120 must first carry out a certain stroke or a certain movement before it touches the drive shaft 23, it comes into its linear effective range, which enables precise and reproducible control.
  • the stop 113 is provided for the drive shaft. 9 also illustrates a coupling of the actuator 120 to the drive shaft 23 via a gear 122.
  • Fig. 10 shows a scroll compressor with an alternative design of the actuator 120.
  • actuators in the usual sense for the application of the pressing force is also the generation of an axial force on the drive shaft 23 with a
  • the drive shaft 23 acts as an armature in a coil 130.
  • the electronics of the coil 130 can in turn be accommodated in the electronics housing 70 in this embodiment.
  • the corresponding deflection of the drive shaft 23 can be excited via the energization of the coil 130, which in turn generates the contact pressure between the rotor spiral element 22 and the stator spiral element 21.
  • Spacers 131 can be provided for mounting and for adjusting a distance between the drive shaft 23, which acts as a rotor, and the coil 130.
  • Drive shaft 23 arranged and measures the force applied to the drive shaft 23 by the actuator 120.
  • Force sensor electronics 121a can in turn be arranged in electronics housing 70.
  • the contact pressure determined by the force sensor 121 can be used in a control circuit analogously to the first exemplary embodiment and its modifications, in order to make the contact pressure dependent on the current one Optimally set operating conditions and conditions of the scroll compressor.
  • the positions and designs of the force sensor shown in FIGS. 6 and 7 can also be used for this purpose.
  • FIG. 12 shows a modification of the scroll compressor according to FIG. 11.
  • an oil return actuator element 61 is provided in the oil return 60.
  • the cross section of the oil return 60 can be varied and the return of the oil can thus be configured actively and independently of a load point.
  • Actuator elements are used which are also used in actuator elements 101, 102 of the first exemplary embodiment.
  • the use of a solenoid valve is also possible, which is only the open or the
  • a corresponding control can be provided in the oil return actuator element 61.
  • the amount of oil in the high-pressure area 40 or a measurement variable proportional to it must be available. 13 shows a corresponding one
  • a fill level sensor 62 is arranged at the lower end of the oil separation chamber 42, with which the amount of oil in the
  • Oil separation chamber 42 separated oil can be determined. On the basis of these measured values, the oil return can be regulated by controlling the oil return actuator element 61. This means that an optimal amount of circulating oil can be set, which in turn can contribute to an increase in efficiency.
  • FIG. 14 shows a modification of the scroll compressor according to FIG. 13.
  • a speed sensor 123 is provided in this exemplary embodiment, which measures the speed of the drive shaft 23.
  • the speed sensor 123 can be arranged on the axial end of the drive shaft 23, on which the actuator 120 is also located.
  • the speed sensor 123 can also be provided on the end of the suction region 30 facing the compressor unit 20.
  • the speed sensor 123 can either on the outer surface of the
  • Drive shaft 23 may be aligned or alternatively axially on the top surface of the rotor 24.
  • An incremental encoder with optical or magnetic mode of action can be used as the speed sensor 123, for example.
  • Speed sensor electronics 123a required for the operation of the speed sensor 123 can in turn, as shown in FIG. 14, be accommodated in the electronics housing 70.
  • the speed sensor 123 With the speed sensor 123, the instantaneous speed of the drive shaft 23, and thus also a rotational nonuniformity of the drive shaft 23, which may arise due to the compression process, can be detected.
  • Compression process follows, or when there is a maximum or a minimum of rotational nonuniformity, allows measures to actively influence or compensate for these irregular rotational movements.
  • the determined speed in the control of the contact pressure can be adjusted accordingly
  • a falling speed can be compensated for by reducing the pressing force and vice versa.
  • An advantage of controlling the contact pressure taking into account the rotational speed or rotational non-uniformity is that the generation of vibrations in the scroll compressor can be prevented by reducing the rotational non-uniformity.
  • the entry of vibrations into the vehicle can be reduced or reduced.
  • the speed of the drive shaft 23 can also be varied in that the energization of the motor driving the drive shaft 23, ie the energization of the stator 25 is controlled, in particular as a function of the speed or rotational irregularity determined by the speed sensor 123. Falling speeds can be compensated for by increasing the drive current for the stator 25 and vice versa.
  • the control of the electric motor with the stator 25 can also be done in combination with the control of the pressing force.
  • FIG. 15 shows a modification of the scroll compressor according to FIG. 14.
  • a high-pressure sensor 124 is provided, which is designed to measure the pressure prevailing in the compressor unit 20.
  • the high pressure sensor 124 is immediately adjacent to the hot gas valve 26
  • Compressor unit 20 to measure.
  • the pressing force and / or the speed of the drive shaft 23 enable a large number of control scenarios with which the operation of the scroll compressor can be optimized with regard to various aspects.
  • Rotational non-uniformity detected by the detection of the speed sensor 123 the phenomenon can be counteracted in such a way that the rotating field, which sets the drive shaft 23 in rotation, is weakened as soon as, for example, the compression has taken place and the torque load on the
  • Drive shaft 23 decreases briefly until the next pressure maximum. This is accomplished by appropriate control of the drive current for the stator 25.
  • the high-pressure sensor 124 is arranged in front of the hot gas valve 26 in relation to the direction of flow of the fluid to be compressed and supplies a pressure signal.
  • This pressure signal can be used to counter the sudden increase in the drive shaft speed after opening the hot gas valve 26 due to constant electrical drive power with reduced mechanical resistance in the compressor unit 20. This can actively reduce rotary shocks that occur when the Scroll compressor occur.
  • the control used for this purpose can in particular be designed as a self-learning controller with combined feedback / feed forward control.
  • Compression process can also be developed using a
  • Control unit or can be present in an existing vehicle intelligence.
  • the speed sensor 123 can also be used for more extensive
  • the energization of the electric motor driving the drive shaft 23 can be interrupted if the rotational speed exceeds a preset limit value.
  • a shutdown of the scroll compressor can also be set if the high-pressure sensor 124 measures a pressure value in the compressor unit 20 that lies above a preset high-pressure limit value. Damage to the scroll compressor can thus be effectively suppressed.
  • Contact pressure can be controlled depending on the angle of rotation.
  • Input variable of the control can also be used the pressure value determined by the high pressure sensor 124 upstream of the hot gas valve 26.
  • Rotor spiral element 22 the pressing force can be controlled or readjusted. With the help of a prematurely falling high pressure, an internal leak due to insufficient contact pressure can be detected and avoided at the next cycle.
  • the scroll compressor If the scroll compressor is started under these conditions by energizing the stator 25, it may happen that the scroll compressor cannot displace the liquid fluid and therefore does not start. In this situation, the scroll compressor according to the present
  • the rotor spiral element 22 can be moved in a targeted manner in the direction of the suction region 30 and thus a desired internal leakage is generated in the compressor unit 20. This enables the scroll compressor to start. As soon as the scroll compressor has started up, the rotor spiral element 22 can be brought into tight axial engagement with the stator spiral element 21 again by means of the actuator 120 and the compression operation can be started again.
  • the application of the contact pressure can be time or pressure controlled.
  • Scroll compressor can be ensured even when the fluid is in an unfavorable state of aggregation, the maximum current consumption of the scroll compressor is also reduced, and the load on the materials is reduced and the service life of the scroll compressor is increased.
  • FIG. 16 shows a modification of the scroll compressor from FIG. 15.
  • a temperature sensor 125 is provided, which is designed to measure a temperature of the fluid in the high-pressure region.
  • the temperature sensor 125 is provided, which is designed to measure a temperature of the fluid in the high-pressure region.
  • Temperature sensor 125 in the immediate vicinity of the output of the
  • Hot gas valve 26 attached.
  • the aggregate state of the fluid in the high-pressure region 40 can be determined, taking into account corresponding material data that are stored on a control unit. In this way, it can be determined when liquid fluid is present in the compressor unit 20 or the high pressure region 40 adjoining it. Accordingly, the control of that described with reference to FIG. 15 can be performed
  • the temperature sensor 125 can of course also be used as another
  • the scroll compressor can be switched off when a preset maximum temperature is reached.
  • the possibility of pushing the drive shaft 23 axially in the direction of the electronics housing and thus causing a targeted leakage in the axial direction in the compressor unit 20 can suddenly supply a large amount of cold suction gas to the hot fluid in the compressor unit 20 due to the axial leakage , This can cause damage to the
  • control measures described above can be combined with one another in a suitable manner in order to optimally adapt the control of the scroll compressor to given conditions. Since the principle of operation of the scroll compressors for applications in the automotive sector and in stationary technology is basically the same, all of the features described here could be used both in a scroll compressor for cars and also applied to stationary technology.
  • Embodiment can be applied.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur à spirales comprenant les caractéristiques suivantes : une unité de compresseur (20) ayant un élément en spirale de stator (21) fixe et un élément en spirale de rotor rotatif (22) supporté de manière mobile axialement par rapport à l'élément en spirale de stator (21). L'unité de compresseur (20) est adaptée pour aspirer un fluide à comprimer d'une zone d'aspiration (30), le comprimer et le transporter dans une zone haute pression (40); une chambre de contre-pression (10) qui est disposée sur un côté de l'élément en spirale de rotor (22) opposé à l'élément en spirale de stator (21) et qui peut être soumise à une contre-pression pour exercer une force de contact dans la direction axiale sur l'élément en spirale de rotor (22) et pour appuyer l'élément en spirale de rotor (22) contre l'élément en spirale de stator (21). Il existe une communication de fluide entre la chambre de contre-pression (10) et la zone d'aspiration (30), et il existe une communication de fluide entre la chambre de contre-pression (10) et la partie haute pression (40); un canal de pression d'aspiration (103) disposé dans la communication de fluide entre la chambre de contre-pression (10) et la zone d'aspiration (30); un canal haute pression (104) disposé dans la liaison fluide entre la chambre de contre-pression (10) et la zone haute pression (40). Au moins un élément d'actionnement (101, 102, 101a) est disposé dans le canal haute pression (104) et le canal de pression d'aspiration (103), au moyen duquel la section transversale du canal haute pression (102) et du canal de pression d'aspiration (103) est variable.
EP19742309.8A 2018-07-10 2019-07-09 Compresseur à spirales Withdrawn EP3821130A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018116630.3A DE102018116630A1 (de) 2018-07-10 2018-07-10 Scrollverdichter
PCT/EP2019/068363 WO2020011769A2 (fr) 2018-07-10 2019-07-09 Compresseur à spirales

Publications (1)

Publication Number Publication Date
EP3821130A2 true EP3821130A2 (fr) 2021-05-19

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EP19742309.8A Withdrawn EP3821130A2 (fr) 2018-07-10 2019-07-09 Compresseur à spirales

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EP (1) EP3821130A2 (fr)
DE (1) DE102018116630A1 (fr)
WO (1) WO2020011769A2 (fr)

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Publication number Priority date Publication date Assignee Title
GB2592657A (en) * 2020-03-05 2021-09-08 Edwards Ltd Scroll pump apparatus and method
GB2592658A (en) * 2020-03-05 2021-09-08 Edwards Ltd Scroll pump and apparatus and method
DE102021101627B4 (de) * 2021-01-26 2023-05-04 Sanden International (Europe) GmbH Spiralverdichter mit direkter Ölrückführung von einem Ölabscheider in einen Kompressionsabschnitt
CN113530816A (zh) * 2021-07-28 2021-10-22 合肥墨研涡旋科技有限公司 具有背压腔压力采集功能的电动涡旋压缩机
CN114033676A (zh) * 2021-12-23 2022-02-11 广州广涡压缩机有限公司 一种增压式涡旋空气压缩机
EP4269800A1 (fr) * 2022-04-29 2023-11-01 Dabir Surfaces, Inc. Pompe à spirales avec système de contrôle de charge axiale
US20250270995A1 (en) * 2024-02-26 2025-08-28 Mahle International Gmbh Electric compressor with passive pressure system between high and low pressure regions

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JPS5776291A (en) * 1980-10-31 1982-05-13 Hitachi Ltd Scroll fluid machine
JP2005016379A (ja) * 2003-06-25 2005-01-20 Denso Corp スクロール型流体機械
DE102011121365B4 (de) * 2011-12-19 2013-12-19 Robert Bosch Gmbh Spiralverdichter mit axial verschiebbarem Spiralblatt
KR101509290B1 (ko) * 2012-09-17 2015-04-07 한라비스테온공조 주식회사 스크롤 압축기
US9541084B2 (en) * 2013-02-06 2017-01-10 Emerson Climate Technologies, Inc. Capacity modulated scroll compressor
CN105298838A (zh) * 2015-11-23 2016-02-03 珠海格力节能环保制冷技术研究中心有限公司 一种涡旋压缩机及其调节控制方法

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WO2020011769A3 (fr) 2020-03-12
WO2020011769A2 (fr) 2020-01-16

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