EP1455143A1 - Dispositif de commande d'un compresseur a deplacement variable et dispositif de commande a deplacement variable d'un cycle de refrigeration - Google Patents

Dispositif de commande d'un compresseur a deplacement variable et dispositif de commande a deplacement variable d'un cycle de refrigeration Download PDF

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Publication number
EP1455143A1
EP1455143A1 EP02765373A EP02765373A EP1455143A1 EP 1455143 A1 EP1455143 A1 EP 1455143A1 EP 02765373 A EP02765373 A EP 02765373A EP 02765373 A EP02765373 A EP 02765373A EP 1455143 A1 EP1455143 A1 EP 1455143A1
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EP
European Patent Office
Prior art keywords
pressure
control
variable displacement
suction
control signal
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.)
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Application number
EP02765373A
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German (de)
English (en)
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EP1455143A4 (fr
Inventor
S. c/o ZEXEL VALEO CLIMATE CONTROL CORP. HAYASHI
S. c/o ZEXEL VALEO CLIMATE CONTROL CORP. FURUYA
Y. c/o ZEXEL VALEO CLIMATE CONTROL CORP TAKAHASHI
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Valeo Thermal Systems Japan Corp
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Zexel Valeo Climate Control Corp
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Publication date
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Publication of EP1455143A1 publication Critical patent/EP1455143A1/fr
Publication of EP1455143A4 publication Critical patent/EP1455143A4/fr
Withdrawn legal-status Critical Current

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    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/076—Details of compressors or related parts having multiple cylinders driven by a rotating swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/023—Compressor control controlling swash plate angles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet

Definitions

  • the present invention relates to a control device of a variable displacement compressor that varies the discharge capacity by controlling a pressure supplied from a discharge pressure area to a control pressure chamber and a pressure released from the control pressure chamber to a suction pressure area and also related to a variable displacement control device of a refrigerating cycle employing the variable displacement compressor.
  • Variable displacement compressors used in automotive air-conditioning systems in the related art include the one disclosed in Japanese Unexamined Patent Publication No. H 63-16177.
  • This variable displacement compressor which includes a regulating valve that regulates the state of communication between a crank chamber and a suction space, a pressure sensitive means constituted of a bellows or the like that controls the regulating valve by sensing an suction pressure and an external control means that varies a pressure control point of the pressure sensitive means by applying a variable load to the pressure sensitive means in response to an input from the outside, adjusts a pressure setting value at the pressure sensitive means with the external control means and controls the suction pressure at the compressor so as to achieve the adjusted pressure setting value.
  • Japanese Unexamined Patent Publication No. H 64-60778, Japanese Examined Patent Publication No. H 7-6503 and the like disclose variable displacement compressors that control the crank chamber pressure with an external control signal without employing the pressure sensitive means mentioned above.
  • an electromagnetic valve 202 the open/closed state of which is controlled by a control signal provided from the outside, is disposed on a passage connecting a discharge space 200 and a crank chamber 201, the crank chamber 201 and a suction space 203 are made to communicate with each other via a passage and control is implemented to achieve a desired pressure with the electromagnetic valve 202 while constantly leaking the crank chamber pressure into the suction space, as shown in FIG. 12(a).
  • the pressure control valve which includes the pressure sensitive member described first, is employed in a refrigerating cycle using carbon dioxide as a coolant in that since the pressure within the refrigerating cycle rises to a level 10 times as high as that in a conventional freon cycle, the pressure sensitive member may not have high enough pressure withstanding performance.
  • the pressure sensitive member such as a bellows, which must have a specific size in order to assure a large enough pressure receiving area, cannot be provided in a size smaller than that in the related art. For these reasons, a great deal of interest is focused on the use of a control valve, the open/closed state of which can be electrically controlled with a control signal provided from the outside as a replacement for the control valve that uses a pressure sensitive member.
  • the compressor controls the pressure on the suction side and thus, appropriate feedback control must be implemented in correspondence the suction-side pressure.
  • an object of the present invention is to provide a control device of a variable displacement compressor and a variable displacement control device of a refrigerating cycle, with which the efficiency of the compressor is improved and, at the same time, the optimal response and stability can be achieved under varying conditions by adopting a structure having a control valve controlled by a control signal provided from the outside to control a control chamber pressure without using a pressure sensitive member.
  • Another object of the present invention is to provide a variable displacement control device of a refrigerating cycle 'capable of implementing appropriate feedback control when electrically controlling the control valve.
  • a control device of the variable displacement compressor comprises a means for pressure detection that detects the pressure on the suction pressure area side, a means for control signal calculation that calculates the control signal for the means for pressure control so as to set the pressure detected by the means for pressure detection to a target pressure and a means for gain adjustment that adjusts a gain in an arithmetic expression used to calculate the control signal in correspondence to a physical quantity that affects the air conditioning state.
  • the gain in the arithmetic expression used to calculate the control signal for the means for pressure control is adjusted based upon a volume representing a physical quantity that affects the air conditioning state and, as a result, the optimal response and stability are achieved under varying conditions.
  • the means for pressure control may be constituted as a single control valve that simultaneously adjusts the state of communication between the control pressure chamber and the discharge pressure area and the state of communication between the control pressure chamber and the suction pressure area, or it may be constituted with a first switching control valve disposed on a pressure supply passage connecting the discharge pressure area with the control pressure chamber and a second switching control valve disposed on a pressure release passage connecting the control pressure chamber with the suction pressure area.
  • variable displacement compressor be a so-called swash plate variable displacement compressor comprising a drive shaft disposed within a cylinder block, a drive swash plate that rotates together with the drive shaft and allows the angle of inclination formed relative to the drive shaft to be varied freely, a cylinder disposed within the cylinder block and having an axis extending parallel to the drive shaft, a piston slidably disposed within the cylinder which makes a reciprocal movement inside the cylinder as the drive swash plate rotates, a compression space formed by the cylinder and the piston, a crank chamber constituting the control pressure chamber formed at the piston on the side opposite from the compression space side, a suction space that constitutes the suction pressure area coming into communication with the compression space during a suction stroke of the piston and a discharge space that constitutes the discharge pressure area coming into communication with the compression space during the compression stroke of the piston.
  • a variable displacement control device to be adopted in conjunction with a refrigerating cycle having at least a variable displacement compressor that includes a means for pressure control enabling a pressure supply from a discharge pressure area to a control pressure chamber and a pressure release from the control pressure chamber to a suction pressure area and adjusts the pressure in the control pressure chamber by controlling the means for pressure control with a control signal provided from the outside so as to reduce the discharge capacity as the pressure in the control pressure chamber rises and to increase the discharge capacity as the pressure in the control pressure chamber becomes lower, a radiator that cools a coolant having been compressed at the variable displacement compressor, an expansion device that depressurizes the coolant having been cooled at the radiator and an evaporator that evaporates the depressurized coolant at the expansion device, comprises a means for pressure detection that detects the pressure on the suction pressure area side, a means for control signal calculation that calculates the control signal for the means for pressure control so as to set the pressure detected by the means for pressure detection to a target pressure
  • the gain in the arithmetic expression used to calculate the control signal for the means for pressure control is adjusted in correspondence to a physical quantity that affects the air conditioning state and, as a result, the optimal response and stability are assured under varying conditions.
  • a variable displacement control device to be adopted in conjunction with a refrigerating cycle having at least a variable displacement compressor that includes a means for pressure control enabling a pressure supply from a discharge pressure area to a control pressure chamber and a pressure release from the control pressure chamber to a suction pressure area and adjusts pressure in the control pressure chamber by controlling the means for pressure control with a control signal provided from the outside so as to reduce the discharge capacity as the pressure in the control pressure chamber rises and to increase the discharge capacity as the pressure in the control pressure chamber becomes lower, a radiator that cools a coolant having been compressed at the variable displacement compressor, an expansion device depressurizes the coolant having been cooled at the radiator and an evaporator that evaporates the depressurized coolant at the expansion device, comprises a means for pressure detection that detects the pressure on the suction pressure area side, a means for control signal calculation that calculates the control signal for the means for pressure control so as to set the pressure detected by the means for pressure detection to a target pressure,
  • control is implemented to achieve the target pressure on the suction pressure area side of the compressor to ultimately control the outlet-side air temperature at the evaporator so as to achieve the target temperature and thus, the control performance can be improved.
  • cascade control is achieved by a major controller that controls the air temperature at the evaporator on the outlet side and a minor controller that controls the pressure on the suction pressure area side and, by using the outlet-side air temperature at the evaporator as a control variable of the major controller, the target pressure on the suction pressure area side, which is a target value for the minor controller as an operation variable of the major controller, the pressure on the suction pressure area side as a control variable of the minor controller and the control signal provided to the means for pressure control as an operation variable of the minor controller, faster control response is achieved.
  • variable displacement control device may further include a means for control signal calculation gain adjustment that adjusts a gain in an arithmetic expression used to calculate the control signal in correspondence to a physical quantity that affects the air conditioning state to be utilized in conjunction with such cascade control, or a means for target pressure calculation gain adjustment that adjusts a gain in an arithmetic operation used to calculate the target pressure on the suction pressure area side in correspondence to a physical quantity that affects the air conditioning state to be utilized in conjunction with the cascade control.
  • a means for control signal calculation gain adjustment that adjusts a gain in an arithmetic expression used to calculate the control signal in correspondence to a physical quantity that affects the air conditioning state to be utilized in conjunction with such cascade control
  • target pressure calculation gain adjustment that adjusts a gain in an arithmetic operation used to calculate the target pressure on the suction pressure area side in correspondence to a physical quantity that affects the air conditioning state to be utilized in conjunction with the cascade control.
  • the means for pressure control may be constituted as a single control valve that simultaneously adjusts the state of communication between the control pressure chamber and the discharge pressure area and the state of communication between the control pressure chamber and the suction pressure area, or it may be constituted with a first switching control valve disposed on a pressure supply passage connecting the discharge pressure area with the control pressure chamber and a second switching control valve disposed on a pressure release passage connecting the control pressure chamber with the suction pressure area.
  • the control efficiency of the compressor may be improved by providing a means for comparison that compares the air temperature at the evaporator on the outlet outside with a target temperature and, in such a case, the first switching control valve should be fully closed if the air temperature on the outlet side of the evaporator is higher than the target temperature so as to control the second switching control valve alone with the control signal or the second switching control valve should be fully closed if the air temperature on the outlet side of the evaporator is equal to or lower than the target temperature so as to control the first switching control valve alone with the control signal.
  • these control measures may be adopted in combination or control may be implemented to control the first switching control valve and the second switching control valve with the control signal if the air temperature at the evaporator on the outlet side is equal to or lower than the target temperature.
  • variable displacement compressor used in the refrigerating cycle described above be a so-called swash plate variable displacement compressor comprising a drive shaft disposed within a cylinder block, a drive swash plate that rotates together with the drive shaft and allows the angle of inclination formed relative to the drive shaft to be varied freely, a cylinder disposed within the cylinder block and having an axis extending parallel to the drive shaft, a piston slidably disposed within the cylinder, which makes a reciprocal movement inside the cylinder as the drive swash plate rotates, a compression space formed by the cylinder and the piston, a crank chamber constituting the control pressure chamber formed at the piston on the side opposite from compression space side, a suction space that constitutes the suction pressure area coming into communication with the compression space during a suction stroke of the piston and a discharge space that constitutes the discharge pressure area coming into communication with the compression space during the compression stroke of the piston, and the variable displacement control device is ideal in an application in a refrigerating cycle in which carbon dioxide
  • the physical quantity that affects the air conditioning state described above may be a measured value (external information) detected with a sensor such as the outlet-side air temperature at the evaporator, the external air temperature, the cabin internal temperature, the discharge pressure at the compressor, the suction pressure at the compressor, the coolant pressure at the outlet of the evaporator, the rotational speed of the compressor or the vehicle speed, or an arithmetic value (internal information) such as a target rotational speed of the blower fan (i.e., a target air flow), a target pressure for the low-pressure line in the refrigerating cycle or a target air temperature on the outlet side of the evaporator calculated at a control unit.
  • a target rotational speed of the blower fan i.e., a target air flow
  • a target pressure for the low-pressure line in the refrigerating cycle a target air temperature on the outlet side of the evaporator calculated at a control unit.
  • the refrigerating cycle 1 comprises a variable displacement compressor (hereafter referred to as a compressor) 3 having a pressure control valve 2 used to adjust a discharge capacity and capable of compressing a coolant to a supercritical range, a radiator 4 that cools the coolant, an expansion device 5 that lowers the pressure of the coolant and an evaporator 6 that evaporates the coolant.
  • a compressor variable displacement compressor
  • a pressure control valve 2 used to adjust a discharge capacity and capable of compressing a coolant to a supercritical range
  • a radiator 4 that cools the coolant
  • an expansion device 5 that lowers the pressure of the coolant
  • an evaporator 6 that evaporates the coolant.
  • the discharge side of the compressor 3 is connected to the expansion device 5 via the radiator 4 and the path extending from the discharge side of the compressor 3 through the inflow side of the expansion device 5 constitutes a high-pressure line 7.
  • the outflow side of the expansion device 5 is connected to the evaporator 6, the outflow side of the evaporator 6, in turn, is connected to the suction side of the compressor 3 and the path extending from the outflow side of the expansion device 5 to the suction side of the compressor 3 constitutes a low-pressure line 8.
  • the coolant constituted of carbon dioxide (CO2) is compressed at the compressor 3 enters the radiator 4 as a high-temperature, high-pressure coolant in a supercritical state, radiates heat and thus becomes cooled at the radiator 4 and is then supplied to the expansion device 5 without becoming liquefied.
  • the coolant is depressurized at the expansion device 5 and, as a result, it becomes a low temperature, low pressure moist steam. It then exchanges heat with the air passing through the evaporator 6 and thus becomes gaseous at the evaporator 6. Subsequently, it is returned to the compressor 3.
  • Reference numeral 9 indicates a pressure sensor provided in the low-pressure line 8 to detect a low level pressure Ps, and a signal output by the pressure sensor 9 is input to a control unit 16 together with signals provided by various sensors such as an external air temperature sensor 10 which detects the outside air temperature, an internal cabin temperature sensor 11 which detects the cabin internal temperature, a solar radiation sensor 12 that detects a solar radiation quantity and an outlet air temperature sensor 14 disposed on the evaporator outlet side to detect the temperature of air supplied from a fan 13 and passing through the evaporator 6 and signals provided through an operation panel 15 to set a target temperature in the cabin and the like.
  • various sensors such as an external air temperature sensor 10 which detects the outside air temperature, an internal cabin temperature sensor 11 which detects the cabin internal temperature, a solar radiation sensor 12 that detects a solar radiation quantity and an outlet air temperature sensor 14 disposed on the evaporator outlet side to detect the temperature of air supplied from a fan 13 and passing through the evaporator 6 and signals provided through an operation panel 15 to set a target
  • the control unit 16 is constituted with an input circuit through which the various types of signals described above are input as data, a memory unit which includes a read only memory (ROM) and a random access memory (RAM), a central processing unit (CPU) that processes the data and calculates control data by using a program called up from the memory unit, a duty ratio calculation circuit that calculates the duty ratio for the control signal based upon the control data calculated at the central processing unit, a control signal output circuit that outputs the control signal with the duty ratio calculated at the duty ratio calculation circuit to the pressure control valve 2.
  • ROM read only memory
  • RAM random access memory
  • CPU central processing unit
  • a duty ratio calculation circuit that calculates the duty ratio for the control signal based upon the control data calculated at the central processing unit
  • a control signal output circuit that outputs the control signal with the duty ratio calculated at the duty ratio calculation circuit to the pressure control valve 2.
  • a peripheral block 20 of the compressor 3 which may be, for instance, a swash plate variable displacement compressor such as that shown in FIG. 2, includes a front block 21 that defines a crank chamber 24, a central block 22 at which a plurality of cylinders 25 are defined and a rear block 23 that defines a suction space 26 and a discharge space 27.
  • a drive shaft 28 passing through the peripheral block 20 is rotatably held at the front block 21 and the central block 22 via bearings 29a and 29b respectively.
  • the drive shaft 28 is connected with a driving engine (not shown) via a belt, a pulley and an electromagnetic clutch, and as the electromagnetic clutch is engaged, the rotation of the engine is communicated to cause the drive shaft 28 to rotate.
  • a swash plate 30 which is caused to rotate as the drive shaft 28 rotates and is allowed to a tilt freely relative to the drive shaft 28 is provided at the drive shaft 28.
  • a plurality of cylinders 25 formed at the central block 22 over specific intervals around the drive shaft 28 each assumes a cylindrical shape having a central axis extending parallel to the axis of the drive shaft 28.
  • the swash plate 30 rotates with a predetermined angle of inclination and, as a result, the end of the swash plate 30 is caused to rock over a specific range along the axis of the drive shaft 28.
  • the pistons 31 secured to the front end of the swash plate 30 along the radial direction move reciprocally along the axis of the drive shaft 28 to change the volumetric capacity of a compression space 32 defined within the cylinder 25 so that the coolant is taken in from the suction space 26 via an suction port 34 having a suction valve 33 and the compressed coolant is discharged into the discharge space 27 via a discharge port 36 having a discharge valve 35.
  • the discharge capacity of the compressor 3 is determined by the stroke of the pistons 31, which, in turn, is determined in correspondence to the pressure difference between the pressure applied to the front surfaces of the pistons 31, i.e., the pressure in the compression spaces 32, and the pressure applied to the rear surfaces of the pistons, i.e., the pressure within the crank chamber 24 (the crank chamber pressure Pc).
  • the pressure Pc in the crank chamber 24 is controlled with the pressure control valve 2 disposed at the rear block 23 or the like of the compressor 3.
  • the pressure control valve 2 used in this structure which is capable of simultaneously adjusting the state of communication between the crank chamber 24 and the discharge space 27 and the state of communication between the crank chamber 24 and the suction space 26 may adopt a structure in the known art such as that disclosed in Japanese Unexamined Patent Publication No. 2001-12358. It is electrically controlled with a control signal provided by the control unit 16 and controls the discharge capacity by adjusting the crank chamber pressure Pc so as to set the low level pressure Ps detected with the pressure sensor 9 to a target pressure Pset.
  • FIG. 3 presents a flowchart of an example of a control operation that may be executed in the compressor control by the control unit 16, and an example of the control operation executed for the compressor 3 is explained below in reference to the flowchart.
  • the control unit 16 enters a target air temperature Tset for the evaporator outlet side.
  • Tset may be entered by directly setting the target air temperature through the operation panel 15 or it may be calculated based upon various types of heat load information such as the external air temperature and the cabin internal temperature.
  • step 52 the air temperature T on the evaporator outlet side detected with the outlet air temperature sensor 14 is entered, and in the following step 54, gains A, B and C in an arithmetic expression (mathematical expression 1 below) used to calculate the target value Pset for the low level pressure are determined.
  • A is a proportional gain by which the proportional term is multiplied
  • B is an integral gain by which the integral term is multiplied
  • C is a differential gain by which the differential term is multiplied.
  • the individual gains (A, B and C) are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 4 (a).
  • Tset is smaller than a predetermined value T0
  • Tset is greater than the predetermined value T0
  • the target value Pset for the low level pressure is calculated by using mathematical expression 1, based upon the difference between the target air temperature Tset for the evaporator outlet side and the actual temperature T detected on the evaporator outlet side. More specifically, as shown in FIG. 5, a proportional component Pp, an integral component Pi and a differential component Pd are individually calculated based upon the difference between the target air temperature Tset for the evaporator outlet side and the actual air temperature T on the evaporator outlet side (steps 560 through 564), and then, in step 566, the individual components are multiplied by the corresponding gains to calculate the target value Pset for the low level pressure.
  • the target value Pset for the low level pressure is set to a lower value (so as to increase the discharge capacity of the compressor 3), whereas when T is lower than Tset, the target value Pset is set to a higher value (so as to reduce the discharge capacity of the compressor 3).
  • step 58 the lower level pressure Ps is detected and entered, and in the following step 60, gains D, E and F in an arithmetic expression (mathematical expression 2 below) used to calculate the control signal DL to be provided to the pressure control valve 2 are determined.
  • D is a proportional gain by which the proportional term is multiplied
  • E is an integral game by which the integral term is multiplied
  • F is a differential gain by which the differential term is multiplied.
  • DL D(Pset - Ps) + E ⁇ (Pset - Ps) dt + Fd (Pset - Ps) /dt ...
  • the individual gains are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 4(b).
  • Tset is smaller than a predetermined value T1
  • Tset is greater than the predetermined value T1
  • step 62 the control signal DL to be provided to the pressure control valve 2 is calculated by using mathematical expression 2 based upon the difference between the target pressure Pset for the low level pressure and the actual low level pressure Ps detected with the pressure sensor 9.
  • a proportional component Dp, an integral component Di and a differential component Dd are individually calculated based upon the difference between the target pressure Pset for the low level pressure and the actual low level pressure Ps (steps 620 through 624), and the individual components are multiplied by the corresponding gains in step 626 to calculate the control signal DL for the pressure control valve 2, as shown in FIG. 6.
  • the control signal DL obtained as described above is output from the control unit 16 to the pressure control valve 2 in step 64.
  • the low-level pressure Ps is higher than the target pressure Pset, the duty ratio increases and thus, a control signal with the higher duty ratio is provided to the pressure control valve 2 to increase the discharge volume.
  • the low-level pressure Ps is lower than the target pressure Pset, the duty ratio becomes lower and thus, a control signal with the lower duty ratio is provided to the pressure control valve 2 to reduce the discharge volume.
  • the gains in the arithmetic expression used to calculate Pset are determined based upon the external information indicating a physical quantity that affects the air-conditioning state in block 70, and in the next block 72, Pset is calculated with mathematical expression 1 based upon the difference between Tset and T ( Tset error) by using the gains thus determined so as to set the Tset error to 0.
  • the gains in the arithmetic expression used to calculate DL are determined in block 74 based upon the external information through the external control described above, and in the next block 76, DL is calculated with mathematical expression 2 based upon the difference between Pset and Ps ( Ps error) by using the gains thus determined, so as to set the Ps error to 0. Then, DL is provided to the pressure control valve 2 of the compressor 3 in the air-conditioning system.
  • the gains (A, B and C) in the arithmetic expression used to calculate Pset and the gains (D, E and F) in the arithmetic expression used to calculate DL are adjusted based upon the external information indicating a physical quantity that affects the air conditioning state, and, as a result, it is possible to prevent deterioration of the response and the stability which may occur when the gains are fixed at specific values. In other words, the optimal response and stability can be assured under varying conditions.
  • control described above achieves cascade control implemented with a major controller that uses the air temperature T on the evaporator outlet side as a control variable and the target value Pset for the low-level pressure as an operation variable and a minor controller that uses the operation variable of the major controller as a target value, the low level pressure Ps as a control variable and the control signal DL provided to the pressure control valve 2 as an operation variable.
  • feedback control for converging the air temperature T on the evaporator outlet side to the target temperature Tset can be implemented in a desirable manner to ultimately control the air temperature T on the evaporator outlet side by controlling the suction-side pressure which can be directly controlled with the compressor 3 in the structure described above, which does not include a pressure sensitive member such as a bellows and adopts an electrically controlled pressure control valve 2, while also achieving faster control response.
  • FIG. 8 presents another structural example that may be adopted. While the basic structures of the refrigerating cycle 1 and the compressor 3 are similar to those in the previous structural example, this example differs in that the pressure control valve 2 at the compressor 3 is constituted with a first switching control valve (Pd-Pc valve) 2a, which is an electromagnetic valve disposed on a pressure supply passage connecting the discharge space 27 with the crank chamber 24 and a second switching control valve (Pc - Ps valve) 2b, which is an electromagnetic valve disposed on a pressure release passage connecting the crank chamber 24 with the suction space 26 and in that the control unit 16 implements control on these switching control valves. Since other structural features are similar to those in the previous example, the same reference numerals are assigned to corresponding parts to preclude the necessity for a repeated explanation thereof.
  • step 80 the control unit 16 enters a target air temperature Tset for the evaporator outlet side.
  • Tset may be entered by directly setting the target air temperature through the operation panel 15 or it may be calculated based upon various types of heat load information such as the external air temperature and the cabin internal temperature.
  • step 82 the air temperature T on the evaporator outlet side detected with the outlet air temperature sensor 14 is entered, and in the following step 84, the actual air temperature T on the evaporator outlet side is compared with the target air temperature Tset for the evaporator outlet outside. If Tset ⁇ T, it is necessary to lower the air temperature, i.e., it is necessary to increase the discharge volume of the compressor 3, and accordingly, the first switching control valve 2a and the second switching control valve 2b are controlled as described below.
  • a full close signal is output for the first switching control valve (Pd - Pc valve) 2a to set it in a fully closed state and thus, the pressure supply from the discharge space 27 to the crank chamber 24 is stopped completely (step 86).
  • the gains A, B and C in the arithmetic expression (mathematical expression 1) used to calculate the target value Pset for the low level pressure are determined in step 88 in the control implemented on the second switching control valve (Pc - Ps valve) 2b.
  • the individual gains are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 10(a).
  • step 90 the target value Pset for the low level pressure is calculated based upon the difference between the target air temperature Tset for the evaporator outlet side and the actual temperature T detected on the evaporator outlet side by using mathematical expression 1 as in the processing shown in FIG. 5 explained earlier.
  • step 92 the lower level pressure Ps is detected and entered, and in the following step 94, the gains D, E and F in the arithmetic expression (mathematical expression 2 presented earlier) used to calculate the control signal DL to be provided to the pressure control valve 2 are determined.
  • the individual gains are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 10(b).
  • Tset is smaller than a predetermined value T1
  • Tset is greater than the predetermined value T1
  • step 96 the control signal DL to be provided to the pressure control valve 2 is calculated based upon the difference between the target pressure Pset for the low level pressure and the actual low level pressure Ps by using mathematical expression 2 as in the processing shown in FIG. 6 explained earlier, and in step 98, the control signal DL is output from the control unit 16 to the second switching control valve (Pc - Ps valve) 2b.
  • step 84 If, on the other hand, it is judged in step 84 that Tset ⁇ T, the air temperature is too low, i.e., it is necessary to reduce the discharge volume at the compressor 3, and accordingly, the discharge capacity is reduced by controlling the first switching control valve 2a and the second switching control valve 2b as described below.
  • the gains A, B and C in the arithmetic expression (mathematical expression 1) used to calculate the target value Pset for the low level pressure are determined in step 100.
  • the individual gains are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 10(a).
  • step 102 the target value Pset for the low level pressure is calculated based upon the difference between the target air temperature Tset for the evaporator outlet side and the actual temperature T detected on the evaporator outlet side by using mathematical expression 1 as in the processing shown in FIG. 5 explained earlier.
  • step 104 the lower level pressure Ps is detected and entered, and in the following step 106, the gains D, E and F in the arithmetic expression (mathematical expression 2 presented earlier) used to calculate the control signal DL to be provided to the pressure control valve 2 are determined.
  • the individual gains are adjusted in correspondence to a value representing a physical quantity that affects the air conditioning state, e.g., the target air temperature Tset for the evaporator outlet side, input as external information, as indicated in FIG. 10(b).
  • step 108 the control signal DL to be provided to the pressure control valve 2 is calculated based upon the difference between the target pressure Pset for the low level pressure and the actual low level pressure Ps by using mathematical expression 2 as in the processing shown in FIG. 6 explained earlier, and in step 110, the control signal DL is output from the control unit 16 to the first switching control valve (Pd - Pc valve) 2a.
  • control similar to that executed in steps 88 through 98 is implemented on the second switching control valve (Pc - Ps valve) 2b in steps 112 to 122.
  • the gains (A, B and C) in the arithmetic expression used to calculate Pset and the gains (D, E and F) in the arithmetic expression used to calculate DL are adjusted based upon the external information indicating a physical quantity that affects the air conditioning state.
  • the control implemented on the individual switching control valves 2a and 2b described above constitutes cascade control achieved with a major controller that uses the air temperature T on the evaporator outlet side as a control variable and the target value Pset for the low-level pressure as an operation variable and a minor controller that uses the operation variable of the major controller as a target value, the low level pressure Ps as a control variable and the control signal DL provided to the pressure control valves as an operation variable.
  • feedback control for converging the air temperature T on the evaporator outlet side to the target temperature Tset can be implemented in a desirable manner to ultimately control the air temperature T on the evaporator outlet side by controlling the suction-side pressure which can be directly controlled with the compressor 3 in the structure described above, which does not include a pressure sensitive member such as a bellows and adopts electrically controlled switching control valves 2a and 2b, while also achieving faster control response.
  • the discharge volume is adjusted simply by regulating the release quantity with the pressure supply to the crank chamber from the discharge space stopped altogether and thus, the crank chamber pressure can be utilized effectively.
  • open/close control was implemented on the first switching control valve (Pd - Pc valve) 2a as well, it would be necessary to release extra pressure from the crank chamber to the suction space in correspondence to the pressure supplied from the discharge space to the crank chamber in order to achieve the desired crank chamber pressure Pc, which would result in poorer compressor efficiency.
  • the crank chamber pressure is controlled simply by controlling the second switching control valve (Pc - Ps valve) 2b when increasing the discharge capacity as described above, the crank chamber pressure can be adjusted with a high degree of efficiency to improve the efficiency of the compressor itself.
  • the first switching control valve (Pd - Pc valve) 2a when the crank chamber pressure is released, i.e., when it is judged that Tset ⁇ T and it is necessary to increase the discharge volume at the compressor in order to increase the cooling capability, the first switching control valve (Pd - Pc valve) 2a is set in a fully closed state in the control described above.
  • the second switching control valve (Pc - Ps valve) 2b may be set in a fully closed state and duty ratio control may be implemented on the first switching control valve (Pd - Pc valve) 2a when supplying the crank chamber pressure, i.e., when it is judged that Tset ⁇ T and the discharge volume at the compressor needs to be reduced in order to lower the cooling capability.
  • the first switching control valve (Pd - Pc valve) 2a may be set in a fully closed state (step 86) and then duty ratio control may be implemented on the second switching control valve (Pc - Ps valve) 2b (steps 88 through 98) as in the control shown in FIG. 9, whereas if it is judged that Tset ⁇ T, the second switching control valve (Pc - Ps valve) 2b may be first set in a fully closed state (step 124) and then duty ratio control may be implemented on the first switching control valve (Pd - Pc valve) 2a (steps 100 through 110), as shown in FIG. 11.
  • the gains may be adjusted in conformance to any of measured values (external information) detected with sensors such as the outlet-side air temperature T at the evaporator 6, the external air temperature Ta, the cabin internal air temperature Tinc, the discharge pressure Pd at the compressor, the suction pressure Ps at the compressor, the coolant pressure at the evaporator outlet, the rotational speed of the compressor and the vehicle speed or any of arithmetic values (internal information) calculated at the control unit 16 such as the target rotational speed (i.e., the target air flow rate) for the blower fan 13, the target pressure Pset for the low-pressure line 8 in the refrigeration cycle 1 and the target air temperature Tset for the evaporator outlet side.
  • the gains may be adjusted by using some of the values listed above in combination.
  • the gains are adjusted over two stages in the control described above, they may be instead adjusted over three stages or more, or they may be adjusted continuously.
  • PID control is adopted in the examples explained above, the gains may be adjusted in a similar manner based upon a physical quantity that affects the air conditioning state in conjunction with another control mode such as PI control.
  • a control device of the variable displacement compressor and a variable displacement control device of a refrigerating cycle with optimal response and stability assured under varying conditions while improving the efficiency of the compressor are provided.
  • control signal to be provided to the means for pressure control is calculated so as to set the pressure detected by the means for pressure detection to the target pressure and the target pressure for the suction pressure area side is calculated so as to set the outlet-side air temperature at the evaporator to the target temperature
  • the outlet-side air temperature at the evaporator which is the ultimate control target, can be controlled with a high degree of effectiveness by adopting cascade control to achieve feedback control, which is ideal in an application in which control is implemented with an electrically controlled control valve without providing a pressure sensitive member such as a bellows.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP02765373A 2001-10-25 2002-08-29 Dispositif de commande d'un compresseur a deplacement variable et dispositif de commande a deplacement variable d'un cycle de refrigeration Withdrawn EP1455143A4 (fr)

Applications Claiming Priority (3)

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JP2001328023 2001-10-25
JP2001328023 2001-10-25
PCT/JP2002/008722 WO2003036184A1 (fr) 2001-10-25 2002-08-29 Dispositif de commande d'un compresseur a deplacement variable et dispositif de commande a deplacement variable d'un cycle de refrigeration

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EP1455143A4 EP1455143A4 (fr) 2011-11-16

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JP2006329447A (ja) * 2005-05-23 2006-12-07 Mitsubishi Heavy Ind Ltd 空気調和装置
JP2009229012A (ja) * 2008-03-24 2009-10-08 Daikin Ind Ltd 冷凍装置
JP2010000964A (ja) * 2008-06-23 2010-01-07 Denso Corp 空調装置
JP5463190B2 (ja) * 2010-04-09 2014-04-09 三菱重工業株式会社 定数設定装置及び方法並びにプログラム
CN110464444B (zh) * 2019-08-14 2023-03-31 心诺普医疗技术（北京）有限公司 一种温度可控的冷冻消融系统
CN113587363B (zh) * 2021-08-04 2022-07-26 广东美的暖通设备有限公司 压缩机故障检测方法、装置、计算设备及存储介质

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