WO2001000992A1 - Commande de capacite variable pour cycle de refrigeration - Google Patents
Commande de capacite variable pour cycle de refrigeration Download PDFInfo
- Publication number
- WO2001000992A1 WO2001000992A1 PCT/JP2000/001807 JP0001807W WO0100992A1 WO 2001000992 A1 WO2001000992 A1 WO 2001000992A1 JP 0001807 W JP0001807 W JP 0001807W WO 0100992 A1 WO0100992 A1 WO 0100992A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- chamber
- low
- valve body
- refrigeration cycle
- Prior art date
Links
Classifications
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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
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- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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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
- F04B2027/1809—Controlled pressure
- F04B2027/1818—Suction pressure
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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
- 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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
-
- 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
- F25B2700/197—Pressures of the evaporator
-
- 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
Definitions
- the present invention provides a drive swash plate that is tiltably fixed to a drive shaft, a piston that reciprocates in a compression chamber by the rotation of the drive swash plate, TECHNICAL FIELD
- the present invention relates to a variable displacement compressor for a refrigeration cycle using carbon dioxide as a refrigerant, in which a variable displacement compressor that varies a refrigerant flow through a refrigeration cycle by varying a stroke of a piston according to an inclination angle of the piston is used.
- the pressure control valve used in the variable displacement swash plate type compressor disclosed in Japanese Patent Application Laid-Open No. Hei 5-9-1913 is a first pressure control valve for opening and closing the communication between the discharge chamber and the crank chamber.
- 9-268974 discloses a valve element for opening and closing a supply passage communicating a discharge pressure region with a crank chamber.
- the valve is housed in a pressure-sensitive chamber operatively connected to one side of the valve body via a pressure-sensitive rod and communicated with a suction pressure area, and the opening degree of the air supply passage is increased with an increase in pressure in the suction pressure area.
- the pressure sensing part is displaced in a direction to decrease the opening of the air supply passage.
- the biasing force acting on the valve body by the forcible opening means and the displacement by the pressure sensing part are in the direction away from each other, so that the pressure sensing part and the valve body are separated, so that the maximum opening position of the valve body is maintained.
- the pressure-sensitive portion is a bellows, and that the pressure-sensitive portion may be a diaphragm.
- the present invention provides a variable refrigeration cycle that has sufficient pressure resistance against the pressure of a refrigeration cycle using carbon dioxide as a refrigerant and that reliably performs variable capacity control without increasing the size of a pressure control valve. It is to provide a control device. Disclosure of the invention
- a cylinder block a drive shaft provided in the cylinder block, a drive swash plate rotating with the drive shaft and having a variable inclination angle with respect to the drive shaft, provided in the cylinder block, and being parallel to the drive shaft.
- a plurality of cylinders slidably disposed in the cylinder and reciprocating in the cylinder with the rotation of the driving swash plate;
- a variable capacity compressor having at least a discharge chamber communicating with the compression chamber, a radiator for cooling the refrigerant compressed by the variable capacity compressor, and an expansion means for expanding the refrigerant cooled by the radiator.
- at least a low-pressure chamber communicating with the suction chamber and a communication with the discharge chamber.
- a high-pressure side communication port provided between the valve body, a valve body for opening and closing the low-pressure side communication port and simultaneously closing and opening the high-pressure side communication port, an electromagnetic coil for generating an electromagnetic force, and slidably inserted into the electromagnetic coil.
- a plunger that is inserted and moves by the electromagnetic force of an electromagnetic coil to move the valve element; and a variable displacement mechanism that includes a spring that urges the valve element in a direction opposite to the moving direction of the plunger;
- a pressure sensor for detecting a pressure in a low pressure line from an outlet side of the expansion means to a suction side of the variable displacement compressor; and if the low pressure detected by the pressure sensor is higher than a target pressure,
- the valve body is moved in a direction communicating with the pressure adjusting chamber and the low-pressure chamber and blocking the pressure adjusting chamber and the high-pressure chamber, and when the low-pressure pressure is lower than the target pressure,
- a control unit for controlling the electromagnetic coil so as to move the valve body in a direction of blocking the low-
- the present invention provides a pressure sensor for detecting the pressure on the low pressure side of a refrigeration cycle using carbon dioxide as a refrigerant, and a direction in which the detected value of the pressure sensor matches the target pressure, for example, the detected value is If the detected pressure is lower than the target pressure, the low pressure is decreased. Since the valve body is moved by controlling the electromagnetic coil in the direction in which it is raised, it is possible to omit a portion having low pressure resistance, such as a conventional low-pressure pressure detector, and to reduce the pressure relative to the refrigeration cycle pressure. Resistance can be increased.
- the valve body when the electromagnetic coil is de-energized, the valve body is located at a position that shuts off between the low-pressure chamber and the crank chamber and communicates between the high-pressure chamber and the pressure adjustment chamber, It is desirable that the valve body moves in a direction that allows communication between the low-pressure chamber and the pressure adjustment chamber and shuts off the high-pressure chamber and the pressure adjustment chamber by the electromagnetic force of the electromagnetic coil.
- the compressor is set so that the discharge capacity of the compressor is minimized in a state where power is not supplied to the electromagnetic coil, so that the operation of the compressor in the initial stage of startup can be smoothly performed.
- valve body is formed with a small hole that communicates between the pressure adjustment chamber and the low-pressure chamber when the valve body cuts off between the pressure adjustment chamber and the low-pressure chamber. Is desirable. This allows a small amount of refrigerant to flow from the crankcase to the low pressure side, thereby preventing the temperature in the crankcase from rising.
- valve body is provided through the high-pressure chamber from the high-pressure side communication port, and transmits the biasing force of the spring to the valve body.
- a guide portion a spring storage chamber in which the spring is stored; the same pressure as that of the low-pressure chamber is supplied to the spring storage chamber; and the guide portion pressurizes the space between the spring storage chamber and the high-pressure chamber. It is shut off.
- a low pressure can be applied to both sides of the valve body, so that the operation of the valve body can be performed more smoothly than when one of the valve bodies is exposed to another pressure. Since the operating load of the valve body can be reduced, the size of the electromagnetic coil can be reduced.
- control signal supplied to the electromagnetic coil is a duty ratio signal, and its maximum voltage is desirably limited to a constant voltage by a constant voltage circuit (
- the voltage fluctuation of the battery power supply, which is the power supply is severe, so the voltage can be kept constant by the constant voltage circuit, and the power can be adjusted by the duty ratio.
- the movement of the valve can be controlled. Also, it is possible to suppress the impact sound of the valve body against the valve seat due to the generation of an excessive electromagnetic force.
- a valve stroke amount from a position where the valve element blocks the low-pressure side communication port to a position where the valve element blocks the high-pressure side communication port is 1 mm or less.
- the target pressure is calculated according to the heat load environment of the refrigeration cycle. As a result, it is possible to set the target pressure most suitable for the air conditioning conditions.
- FIG. 1 is a schematic configuration diagram of a refrigeration cycle according to an embodiment of the present invention
- FIG. 2 is a cross-sectional view of a variable displacement compressor according to an embodiment of the present invention
- FIG. FIG. 4 is a cross-sectional view showing a state of the pressure control valve according to the embodiment of the present invention when no current is applied.
- FIG. 4 shows a state of the pressure control valve according to the embodiment of the present invention when current is applied.
- FIG. 5 is a partially enlarged sectional view of a pressure control valve showing a spill groove formed in a valve body according to the embodiment of the present invention
- FIG. 3), (b), and (c) are timing charts showing control signals supplied to the electromagnetic coil of the pressure control valve.
- FIG. 1 is a schematic diagram of a refrigeration cycle 1 using carbon dioxide as a refrigerant. It is.
- the refrigeration cycle 1 includes a variable displacement compressor (hereinafter referred to as a compressor) 3 having a pressure control valve 2 for varying a discharge capacity and compressing a refrigerant to a supercritical region, and a compressor compressed to a supercritical region.
- a radiator 4 for lowering the temperature of the phase refrigerant, a high-pressure side heat exchanger 5 through which the high-pressure gas-phase refrigerant flowing out of the radiator 4 passes, and a low-pressure gas-phase refrigerant sucked into the compressor 3.
- a refrigeration cycle that absorbs heat from the air passing through the evaporator 9 disposed in the air conditioning duct of the vehicle air conditioner (not shown) and discharges the heat to the outside by the radiator 4. 1 is composed.
- a pressure sensor 12 for detecting a low pressure is provided in the low pressure line 11 between the outlet side of the expansion valve 8 and the suction side of the compressor 3.
- the low pressure Ps detected by the pressure sensor 12 is a temperature sensor 13 for detecting the outside air temperature Ta, a temperature sensor 14 for detecting the vehicle interior temperature Tinc, and a temperature setting device for an operation panel (not shown).
- the temperature setting signal Tset from 15 and the solar radiation Q sun detected by the solar radiation detection sensor 16 are input to the controller 17.
- the controller 17 includes an input circuit 18 for inputting the above-described various signals as data, a memory unit 19 including a read-only memory (ROM) and a random access memory (RAM), and a memory unit 19 stored in the memory unit 19.
- a central processing unit (CPU) 20 that calls a program to process the data or saves the data to the memory unit 19 to calculate control data.
- Output circuit 21 that outputs the duty ratio of the control signal based on the control data calculated by the control device 20, a constant voltage circuit 23 that produces a desired constant voltage from the battery power supply 22, and this constant voltage circuit 2 3
- a duty ratio control circuit 24 that outputs a control signal having a duty ratio output by the output circuit 21.
- the compressor 3 is, for example, a variable capacity swash plate type compressor as shown in FIG. 2, and an outer peripheral block 30 of the compressor 3 includes a front block 31 defining a crank chamber 34, and a plurality of compressors. It comprises a central block 32 defining a cylinder 35 and a rear block 33 defining a suction space 36 and a discharge space 37.
- the drive shaft 38 penetrating through the outer peripheral block 30 is held by the front block 31 and the central block 32 via the bearings 39a and 39b so as to rotate independently.
- the drive shaft 38 is connected to a traveling engine (not shown) via a belt, a pulley, and an electromagnetic clutch. When the electromagnetic clutch is turned on, the rotation of the engine is transmitted to rotate.
- the drive shaft 38 is provided with a swash plate 40 that rotates with the rotation of the drive shaft 38 and is tiltable with respect to the drive shaft 38.
- the cylinder 35 formed in the center block 32 is formed at a predetermined interval around the drive shaft 38, and has a cylindrical shape having a central axis parallel to the axis of the drive shaft 38.
- a biston 41 whose one end is held by the swash plate 40 is slidably inserted.
- the displacement of the compressor 3 is determined by the stroke of the piston 41, and the stroke is determined by the pressure applied to the front of the piston 41, the pressure of the compression chamber 42, and the pressure applied to the back of the piston, the pressure It is determined by the pressure difference from the pressure in the crank chamber 34. Specifically, if the pressure in the crank chamber 34 is increased, the differential pressure between the compression chamber 42 and the crank chamber 34 becomes smaller, so that the stroke of the piston 41 becomes smaller and the discharge capacity becomes smaller. If the pressure in the crank chamber 34 is reduced, the differential pressure between the compression chamber 42 and the crank chamber 34 increases, so that the stroke of the piston 41 increases and the discharge capacity increases.
- a pressure control valve 2 is provided in the rear block 33 of the compressor 3.
- the pressure control valve 2 is shown in FIG. 3 and FIG. 4, and is composed of a driving section 60, a central block section 70, and a valve body section 80.
- the drive section 60 is a cylindrical case 61 that is caulked and fixed to one end of the central block section 70, and is housed in the case 61 and fixed to one end of the central block section 70.
- a plunger 64 having one end face in contact with the body drive port 68 and the other end face in which a spring mounting hole 65 is formed; and one end contacting the plunger 64 when inserted into the spring mounting hole 65
- a cover 6 7 fixed to the other end of the case 61 so as to hold the other end of the spring 66 and to seal the other end of the cylinder 63. It is constituted by and.
- the central block 70 has, at one end, a columnar projection 7 1 a for fixing the cylinder 63 and an outer ring 7 lb to which the case 61 is fixed by caulking.
- a cylindrical block 71 which is formed with the columnar projection 71a, and through which the valve element drive port 68 is slidably penetrated; It has a low-pressure chamber 73 formed in the center in a cylindrical shape, and a plurality of low-pressure communication holes 72 extending radially from the low-pressure chamber 73. Since the plurality of low-pressure communication holes 72 communicate with the suction space 36 of the compressor 3 via the first groove 75 formed in the rear block 33, the low-pressure chamber 73 has The pressure substantially matches the pressure in the low pressure line of the refrigeration cycle 1.
- the valve body 80 has a substantially cylindrical outer case 81 and an inner case 82 attached to the outer case 81, and a pressure adjustment chamber is provided on the central block side of the outer case 81.
- An opening / closing portion 91 of the valve body 90 is accommodated therein, and the sliding portion 93 of the valve body 90 is slidably inserted into the inner case 82 together with the valve body 9.
- a high-pressure chamber 84 is defined between the small-diameter portion 92 and the small-diameter portion 92.
- the pressure regulating chamber 86 communicates with the crank chamber 34 through a crank chamber communication hole 85 opened in the outer case 81 and a second groove 95 formed in the rear block 33.
- the high-pressure chamber 84 passes through the outer case 81 and the inner case 82, a communication hole 83 formed through the outer case 81, and a third groove 96 formed in the rear block 33. It communicates with 7.
- the inner diameter of the pressure adjusting chamber 86 is formed larger than the inner diameter of the low-pressure chamber 73, and the inner diameter of the inner case 82 is formed smaller than the inner diameter of the pressure adjusting chamber 86.
- a low pressure side valve seat 76 is formed between the low pressure chamber 73 and the pressure adjustment chamber 86, and a high pressure side valve seat 7 is provided between the high pressure chamber 84 and the pressure adjustment chamber 86. 7 is formed.
- the opening / closing portion 91 of the valve body 90 housed in the pressure adjusting chamber 86 sits on the low-pressure side valve seat 76 or the high-pressure side valve seat 77 to communicate therewith. / Interruption is to be performed.
- a low-pressure space 87 is formed between the end of the sliding portion 93 of the valve element 90 and the inner case 82, and fixes the inner case 82 to the outer case 81. It communicates with the suction space 36 via a communication hole 88 formed in the lid 89 and a communication space 97 formed in the rear block 33.
- a spring 94 is provided in the low-pressure space 87 to urge the first-stage valve body 90 against the low-pressure side valve seat 76. Since the urging force of the spring 94 is set to be larger than the urging force of the spring 66, when the electromagnetic coil 63 is not energized, the opening / closing section 91 is connected to the low-pressure side valve. It is in a state of being pressed by the seat 76.
- the opening / closing section 91 of the valve element 90 communicates the pressure regulating chamber 86 with the low-pressure chamber 73 when the opening / closing section 91 is seated on the low-pressure side valve seat 76.
- a plurality of spill grooves 98 are formed. This allows the refrigerant in the crank chamber 34 to escape to the low pressure side, so that the temperature in the crank chamber 34 can be suppressed from rising.
- the pressure in the refrigeration cycle 1 is high because low pressure is high because equilibrium pressure of high pressure and low pressure is applied. Since there is no current flow as shown, the discharge space 37 and the crank chamber 34 are in communication with each other, and the pressure in the crank chamber 34 is the same as the high pressure. In this case, since the pressure difference between the high pressure and the low pressure is small, the discharge capacity is small and the driving load of the compressor 3 is reduced, so that the compressor 3 can be started smoothly.
- the electromagnetic coil 63 of the pressure control valve 2 is energized, and the plunger 64 is connected to the electromagnetic coil. Attracted by 6 3, to the force of the spring 9 4
- the valve block 90 is moved via the valve drive rod 68, the opening / closing portion 91 is separated from the low-pressure valve seat 76 and seats on the high-pressure valve seat 77, as shown in FIG. State.
- the crank chamber 34 communicates with the suction space 36 through the pressure adjusting chamber 86 and the low-pressure chamber 73, and has the same pressure as the low-pressure pressure. The stroke amount increases, and the discharge capacity of the compressor 3 increases.
- the pressure control valve 2 After the operation of the compressor 3 is stabilized, if the detected pressure Ps of the pressure sensor 12 is higher than the target pressure Psa, the pressure control valve 2 is moved in a direction to increase the discharge capacity of the compressor 3. When the pressure Ps detected by the pressure sensor 12 is smaller than the target pressure Psa, the pressure control valve 2 is controlled so as to reduce the discharge capacity of the compressor 3.
- K 1 ⁇ F (T a) + K 2-F (Tine) + K 3 ⁇ F (Q s un)-K 4-F (Ts et) + K 5 ⁇ ⁇ P sa K 6 ⁇ F (cho) + 7 ⁇ .
- 1, 1 ⁇ 2, 1 ⁇ 3, 1 ⁇ 4, and K6 are operation constants, and K5 and ⁇ 7 are correction terms.
- the duty ratio Ds of the control signal supplied to the electromagnetic coil 63 is calculated from the low pressure Ps and the target low pressure Psa according to Equation 1 below.
- A is a proportional constant
- B is an integral constant
- C is a correction term.
- the pressure control valve since the pressure sensor for detecting the low pressure is provided separately from the pressure control valve, the pressure control valve itself has a pressure resistance against the pressure of the refrigeration cycle using carbon dioxide as the refrigerant. Since the low-pressure portion does not exist, the life of the pressure control valve can be prolonged, and stable operation can be performed.
- the pressure control valve can be controlled under a certain condition, so that the desired discharge capacity of the compressor can be obtained. Can be reliably obtained.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Magnetically Actuated Valves (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP00911336A EP1188925B1 (en) | 1999-06-24 | 2000-03-24 | Variable-capacity control for refrigerating cycle |
US09/980,499 US6585494B1 (en) | 1999-06-24 | 2000-03-24 | Variable-capacity control for refrigerating cycle without using a large pressure control valve |
DE60007125T DE60007125T2 (de) | 1999-06-24 | 2000-03-24 | Regelung der variablen kapazität eines kühlkreislaufes |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP17803699A JP4392631B2 (ja) | 1999-06-24 | 1999-06-24 | 冷凍サイクルの可変容量制御装置 |
JP11/178036 | 1999-06-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001000992A1 true WO2001000992A1 (fr) | 2001-01-04 |
Family
ID=16041475
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2000/001807 WO2001000992A1 (fr) | 1999-06-24 | 2000-03-24 | Commande de capacite variable pour cycle de refrigeration |
Country Status (5)
Country | Link |
---|---|
US (1) | US6585494B1 (ja) |
EP (1) | EP1188925B1 (ja) |
JP (1) | JP4392631B2 (ja) |
DE (1) | DE60007125T2 (ja) |
WO (1) | WO2001000992A1 (ja) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002250278A (ja) * | 2001-02-23 | 2002-09-06 | Zexel Valeo Climate Control Corp | 可変容量型圧縮機及びこの可変容量型圧縮機を備える冷房システム |
JP3903851B2 (ja) * | 2002-06-11 | 2007-04-11 | 株式会社デンソー | 熱交換器 |
JP2004354017A (ja) * | 2003-05-30 | 2004-12-16 | Sanyo Electric Co Ltd | 冷却装置 |
NL1026728C2 (nl) * | 2004-07-26 | 2006-01-31 | Antonie Bonte | Verbetering van koelsystemen. |
JP2006291765A (ja) * | 2005-04-07 | 2006-10-26 | Saginomiya Seisakusho Inc | 容量可変型圧縮機用制御弁および容量可変型圧縮機および冷凍サイクル装置 |
EP1867873B1 (en) * | 2005-04-08 | 2012-07-11 | Eagle Industry Co., Ltd. | Capacity control valve |
US20080289350A1 (en) * | 2006-11-13 | 2008-11-27 | Hussmann Corporation | Two stage transcritical refrigeration system |
DE102007029523A1 (de) * | 2007-06-25 | 2009-01-02 | Obrist Engineering Gmbh | Kraft/Arbeitsmaschine und Expander-Wärmeübertrager-Einheit |
JP2010048498A (ja) * | 2008-08-22 | 2010-03-04 | Tgk Co Ltd | 冷凍サイクル |
KR102346627B1 (ko) * | 2015-09-30 | 2022-01-05 | 엘지전자 주식회사 | 공기조화기 및 그 제어방법 |
US10543737B2 (en) | 2015-12-28 | 2020-01-28 | Thermo King Corporation | Cascade heat transfer system |
US11549729B2 (en) | 2018-07-23 | 2023-01-10 | Samsung Electronics Co., Ltd. | Cool air supplying apparatus and refrigerator having the same |
WO2020204132A1 (ja) | 2019-04-03 | 2020-10-08 | イーグル工業株式会社 | 容量制御弁 |
WO2020204134A1 (ja) | 2019-04-03 | 2020-10-08 | イーグル工業株式会社 | 容量制御弁 |
WO2020218284A1 (ja) * | 2019-04-24 | 2020-10-29 | イーグル工業株式会社 | 容量制御弁 |
WO2020218285A1 (ja) | 2019-04-24 | 2020-10-29 | イーグル工業株式会社 | 容量制御弁 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63148062A (ja) * | 1986-12-08 | 1988-06-20 | 株式会社豊田自動織機製作所 | 可変容量圧縮機の制御方法 |
JPH02135680U (ja) * | 1989-04-13 | 1990-11-13 | ||
JPH0599136A (ja) * | 1991-10-23 | 1993-04-20 | Sanden Corp | 可変容量型斜板式圧縮機 |
JPH05231312A (ja) * | 1992-02-26 | 1993-09-07 | Hitachi Ltd | 可変容量形片斜板式圧縮機 |
JPH07151261A (ja) * | 1993-11-26 | 1995-06-13 | Aisin Seiki Co Ltd | 電磁比例式圧力制御弁 |
JPH09151847A (ja) * | 1995-12-04 | 1997-06-10 | Nippon Soken Inc | 斜板型圧縮機 |
JPH10318405A (ja) * | 1997-05-14 | 1998-12-04 | Toyota Autom Loom Works Ltd | 圧縮機の制御弁 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4481042C2 (de) * | 1994-07-13 | 1999-02-11 | Toyoda Automatic Loom Works | Taumelscheibenkompressor mit variabler Verdrängung |
JP3678824B2 (ja) | 1995-12-14 | 2005-08-03 | 株式会社テージーケー | 容量可変圧縮機の容量制御装置 |
JPH09250452A (ja) | 1996-03-19 | 1997-09-22 | Toyota Autom Loom Works Ltd | 圧縮機における潤滑構造 |
JPH10141242A (ja) | 1996-11-15 | 1998-05-26 | Toyota Autom Loom Works Ltd | 可変容量型圧縮機 |
FR2763376B1 (fr) * | 1997-05-14 | 2002-11-01 | Toyoda Automatic Loom Works | Soupape de commande d'un compresseur a deplacement variable pour climatiseur d'air de vehicule, et compresseur comprenant une telle soupape |
JP4160669B2 (ja) * | 1997-11-28 | 2008-10-01 | 株式会社不二工機 | 可変容量型圧縮機用制御弁 |
JP4045654B2 (ja) * | 1998-07-15 | 2008-02-13 | 株式会社日本自動車部品総合研究所 | 超臨界冷凍サイクル |
-
1999
- 1999-06-24 JP JP17803699A patent/JP4392631B2/ja not_active Expired - Fee Related
-
2000
- 2000-03-24 US US09/980,499 patent/US6585494B1/en not_active Expired - Fee Related
- 2000-03-24 EP EP00911336A patent/EP1188925B1/en not_active Expired - Lifetime
- 2000-03-24 WO PCT/JP2000/001807 patent/WO2001000992A1/ja active IP Right Grant
- 2000-03-24 DE DE60007125T patent/DE60007125T2/de not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63148062A (ja) * | 1986-12-08 | 1988-06-20 | 株式会社豊田自動織機製作所 | 可変容量圧縮機の制御方法 |
JPH02135680U (ja) * | 1989-04-13 | 1990-11-13 | ||
JPH0599136A (ja) * | 1991-10-23 | 1993-04-20 | Sanden Corp | 可変容量型斜板式圧縮機 |
JPH05231312A (ja) * | 1992-02-26 | 1993-09-07 | Hitachi Ltd | 可変容量形片斜板式圧縮機 |
JPH07151261A (ja) * | 1993-11-26 | 1995-06-13 | Aisin Seiki Co Ltd | 電磁比例式圧力制御弁 |
JPH09151847A (ja) * | 1995-12-04 | 1997-06-10 | Nippon Soken Inc | 斜板型圧縮機 |
JPH10318405A (ja) * | 1997-05-14 | 1998-12-04 | Toyota Autom Loom Works Ltd | 圧縮機の制御弁 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1188925A4 * |
Also Published As
Publication number | Publication date |
---|---|
DE60007125T2 (de) | 2004-05-27 |
US6585494B1 (en) | 2003-07-01 |
EP1188925A1 (en) | 2002-03-20 |
EP1188925B1 (en) | 2003-12-10 |
JP4392631B2 (ja) | 2010-01-06 |
EP1188925A4 (en) | 2002-09-04 |
JP2001012358A (ja) | 2001-01-16 |
DE60007125D1 (de) | 2004-01-22 |
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