CN100580250C - Compressor volume control system and refrigeration cycle system - Google Patents

Compressor volume control system and refrigeration cycle system Download PDF

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Publication number
CN100580250C
CN100580250C CN200610068089A CN200610068089A CN100580250C CN 100580250 C CN100580250 C CN 100580250C CN 200610068089 A CN200610068089 A CN 200610068089A CN 200610068089 A CN200610068089 A CN 200610068089A CN 100580250 C CN100580250 C CN 100580250C
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Prior art keywords
pressure
compressor
control
value
high side
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Expired - Fee Related
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CN200610068089A
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CN1837612A (en
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今津正琢
久米祥隆
长谷川敦
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Denso Corp
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Denso Corp
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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
    • 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
    • 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
    • F04B2027/185—Discharge pressure
    • 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
    • F04B2027/1859—Suction pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1206—Rotational speed of a rotating inclined plate
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/01—Pressure before the pump inlet
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • 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
    • F25B2700/17—Speeds
    • F25B2700/171—Speeds of the compressor
    • 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
    • F25B2700/1931—Discharge 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
    • F25B2700/19—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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices

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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)
  • Air Conditioning Control Device (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

A control device controlling a displacement control means of a compressor is provided. The control device establishes first control pressure value and second control pressure value higher than first control pressure valve by predetermined value as control pressure value relating to high pressure. The controller regulates a capacity control unit when the maximum pressure exceeds a first pressure control value, reducing the discharge capacity while the maximum pressure reaches the first control pressure value. The controller then stops the operation of a compressor when the maximum pressure exceeds the second control pressure value.

Description

Compressor volume control system and cooling cycle system
Technical field
The present invention relates to the capacity control system and the cooling cycle system that is preferred for vehicle air conditioner of variable displacement compressor.
Background technique
Past is being used for the cooling cycle system of vehicle air conditioning, and compressor is designed to drive by vehicle motor, and compressor speed can not be controlled like this.Therefore, the various systems of capacity control drive have been proposed to be provided with, described capacity control drive can change the discharge capacity of compressor by motorized adjustment, thereby controls the emission performance (for example, referring to Japan Patent publication (A) No.2003-129956) of compressor by the control discharge capacity.
Japan Patent publication (A) No.2003-129956 discloses a kind of swash plate (swash plate) type variable volume compressor; described slant plate type variable volume compressor changes the angle of inclination of swash plate to change stroke of piston; change discharge capacity thus, wherein whether the protection of compressor control is necessary by judging with the value of the velocity correlation of compressor and the practical operation information of compressor.
In addition, in the predetermined high-speed region of compressor, when compressor is in high serviceability (highoperating state), the discharge capacity of compressor is controlled to and reduces side, even simultaneously in the predetermined high serviceability of compressor, in the time of in compressor is in low serviceability, the discharge capacity of compressor is controlled to and reduces side.
But, according to Japan Patent publication (A) No.2003-129956, the refrigeration agent flow velocity is based on current value, circulation high pressure and the out of Memory indirect Estimation of compressor speed, capacity control drive, the operation moment of torsion estimates that based on this refrigeration agent flow velocity, speed and out of Memory whether compressor is under the high serviceability is judged based on this operation moment of torsion.
Therefore, the judgement of the high serviceability of compressor is carried out based on the estimation in a plurality of stages.The result; the judgement of the high serviceability of compressor departs from end with the actual load condition from compressor; the result; the protection control (for the control that reduces the discharge capacity side) of compressor can not be performed when protection control actual demand; conversely; the protection control of compressor but finishes to carry out when not needing protection control, and other inconvenience takes place.
Summary of the invention
The objective of the invention is accurately to carry out the volume controlled of compressor protection.
In order to realize this purpose, according to a first aspect of the invention, a kind of compressor volume control system that is used to control the cooling cycle system of variable volume compressor 10 is provided, and described system is designed to continuously change discharge capacity by the capacity control device 10b of motorized adjustment, and described system is provided with:
High side pressure detection device 22, be used to detect refrigeration cycle high side pressure and
Control system 25, the testing signal of high side pressure detection device 22 are imported into described control system 25, and according to high side pressure control capacity control device 10b,
Control system 25 with the first pilot pressure value Pd1 and the second pilot pressure value Pd2 that is higher than the predetermined value of the described first pilot pressure value Pd1 be provided as the pilot pressure value that is used for described high side pressure and
Control system 25 control capacity control device 10b when high side pressure surpasses the first pilot pressure value Pd1, reduce discharge capacity, and high side pressure near the first pilot pressure value Pd1 and
When high side pressure surpasses the second pilot pressure value Pd2, compressor 10 is set to idling conditions (idling state).
In view of the above, the high pressure side pressure that detects by high pressure side pressure detection device 22 is directly used in the compressor discharge capacity that reduces side that is controlled to, when needs, can carry out the control of the discharge capacity that prevents the rising of compressor in high side pressure when needed reliably like this.
Thus, the compressor discharge capacity does not have big reducing when not needing the protection control of compressor discharge capacity.Therefore, compressor performance can be used to realize cooling performance effectively.
In addition, even when controlling the discharge capacity of compressor 10, when high side pressure has surpassed (ends up exceeding) second pilot pressure value Pd2, promptly, when high side pressure greatly surpassed (greatly overshoot), compressor 10 can be stopped to force to reduce high side pressure.Therefore, just can prevent the rising of compressor high side pressure more reliably.
In addition, do not taking place under the above-mentioned common operational condition that surpasses, high side pressure can be controlled within the second pilot pressure value Pd2 by the discharge capacity of control compressor 10, and compressor 10 can continuous running under non-stop situation like this.For this reason, the cooling down operation of refrigeration cycle system can keep continuously, and the inconvenience of rising that is discharged into the temperature of the fluctuation of temperature of the air in the object that is cooled off or passenger accommodation like this can be suppressed.
Owing to can keep the cooling down operation of cooling cycle system so continuously and carry out the protection control of compressor; when the continuous variable capacity type compressor of the big capacity of preparation; if use big capacity compressor like this; even in having the cooling cycle system of less cooling capacity, also can keep cooling down operation also to carry out the protection of compressor in an identical manner continuously.Therefore, common compressor can be used to handle from big capacity cooling cycle system to little and anything of capacity cooling cycle system.
Please note, except the operation that stops compressor 10 fully, " stopping compressor 10 " in the present invention comprise the discharge capacity with compressor 10 be set near 0% minimum capacity with the emission performance with compressor 10 be arranged on substantially with stop identical state in.
According to a second aspect of the invention, provide a kind of compressor control system of cooling cycle system of a first aspect of the present invention, also be provided with:
Rotation detecting 24 is used to detect the value of information with the velocity correlation of compressor 10, and testing signal is inputed to control system 25,
Control system 25 is provided with first pilot pressure value Pd1 conduct and is used for the pilot pressure value of high side pressure in the low low-speed region of the first control rate Nx of ratio piston compressor 10, and the 3rd pilot pressure value Pd3 is set in the high-speed region of the first control rate Nx that is higher than compressor 10.
The 3rd pilot pressure value Pd3 is the pressure that is lower than the first pilot pressure value Pd1, and descends according to the rising of the speed of compressor 10, and
In the time of in the speed of compressor 10 is in than the high high-speed region of the first control rate Nx, if high side pressure surpasses the 3rd pilot pressure value Pd3, capacity control device 10b is controlled, and discharge capacity is reduced, and high side pressure is near the 3rd pilot pressure value Pd3.
In view of the above, when the speed of compressor 10 was in the low-speed region that is lower than the first control rate Nx, high side pressure can be controlled near the first pilot pressure value Pd1 by the discharge capacity of control compressor 10.
Please note, the load that is applied on the internal mechanism of compressor 10 not only increases along with the increase of pressure loading substantially, and along with the increase of the speed of compressor 10 and increase, if like this as in addition at high-speed region the first pilot pressure value Pd1 is set in low-speed region, in high-speed region, be easy to cause overload with respect to the internal mechanism of compressor 10.
Therefore, when the speed of compressor 10 is in the high-speed region that is higher than the first control rate Nx, be provided as the pressure that is lower than the first pilot pressure value Pd1 and along with the rising of the speed of compressor 10 and the 3rd pilot pressure value Pd3 that descends, and pass through the control of the discharge capacity of compressor 10, high side pressure is controlled near the 3rd pilot pressure value Pd3.
Therefore, in high-speed region, high side pressure can be controlled to low pressure according to the rising of the speed of compressor 10.Because this even follow the increase load of speed to increase, also can carry out the protection control of compressor, the protection of the compressor in the high-speed region can more accurately be carried out like this.
According to a third aspect of the invention we, provide a kind of compressor control system of cooling cycle system of a first aspect of the present invention, also be provided with:
Low-pressure lateral pressure detection device 23, be used to detect the low-pressure lateral pressure of refrigeration cycle and testing signal is input in the control system 25 and
Speed detector 24 is used to detect with the value of information of the velocity correlation of compressor 10 and this testing signal is input to control system 25,
Described control system 25 is provided for the predetermined control pressure value P s4 of low-pressure lateral pressure, and
The control capacity control device, when the speed of compressor 1 is in the high-speed region that is higher than predetermined speed Ny and low-pressure lateral pressure descend from expectant control pressure value P s4, discharge capacity is reduced, and low-pressure lateral pressure is near expectant control pressure value P s4.
Notice that if the circulation low-pressure lateral pressure too descends, the difference between circuit high pressure and the low pressure will increase, the load that is applied on the internal mechanism of compressor 10 will increase.
Therefore, in a third aspect of the present invention, when the speed of compressor 10 is in the height zone that is higher than expectant control speed Ny, if low-pressure lateral pressure descends from expectant control pressure value P s4, discharge capacity is reduced, and low-pressure lateral pressure is near expectant control pressure value P s4.
Because this just can suppress the undue decline in the circulation low-pressure lateral pressure in the high-speed region, and carry out compressor protection control more exactly.
Please note, when freezing medium leakage, also caused the undue phenomenon that descends of low-pressure lateral pressure, but in a third aspect of the present invention, in the high-speed region of compressor 10, carry out and judge, so just often, just can be in undue decline by discharge capacity control low-pressure lateral pressure in the amount that is sealed in described intrasystem refrigeration agent.
According to a forth aspect of the invention, provide a kind of compressor control system of cooling cycle system of a second aspect of the present invention, also be provided with:
Low-pressure lateral pressure detection device 23 is used to detect the low-pressure lateral pressure of refrigeration cycle and testing signal is input in the control system 25,
Control system 25 is provided for the predetermined control pressure value P s4 of low-pressure lateral pressure, and the second control rate Ny is set than the lucky high predetermined amount of the first control rate Nx, and
Control described capacity control device 10b, when the speed of compressor 1 be within the high-speed region that is higher than the second control rate Ny and low-pressure lateral pressure when predetermined control pressure value P s4 descends, discharge capacity is reduced, and low-pressure lateral pressure is near predetermined control pressure value P s4.
Because this just can carry out compressor protection control with the third aspect more exactly by making up of the present invention first, second.
According to a fifth aspect of the invention, a kind of compressor volume control system that is used to control the cooling cycle system of variable volume compressor 10 is provided, described system is designed to continuously change discharge capacity by the capacity control device 10b of motorized adjustment, and described system is provided with:
High side pressure detection device 22 is used to detect the high side pressure of refrigeration cycle,
Speed detector 24, be used to detect with the value of information of the velocity correlation of compressor 10 and
Control system 25, the testing signal of high side pressure detection device 22 and speed detector 24 is transfused to control system 25, and according to the speed controlling capacity control device 10b of high side pressure and compressor 10,
Control system 25 is provided with the first pilot pressure value Pd1 and the 3rd pilot pressure value Pd3 as the pilot pressure value that is used for high side pressure, in the lower low-speed region of the predetermined control speed Nx that the described first pilot pressure value Pd1 is used for ratio piston compressor 10, in the higher high-speed region of the predetermined control speed Nx that described the 3rd pilot pressure value Pd3 is used for ratio piston compressor 10
The 3rd pilot pressure value Pd3 is designed to be lower than the pressure of the first pilot pressure value Pd1 and along with the rising of the speed of compressor 10 and descend, and
Control capacity control device 10b, when the speed of compressor 10 is in the low-speed region that is lower than predetermined speed Nx, and high side pressure reduces discharge capacity near the first pilot pressure value Pd1, and high side pressure surpass the first pilot pressure value Pd1 and
Control capacity control device 10b, in the time of in the speed of compressor 10 is in than the high high-speed region of expectant control speed Nx, and high side pressure surpasses the 3rd pilot pressure value Pd3, and discharge capacity is reduced, and high side pressure is near the 3rd pilot pressure value Pd3.
In view of the above, the mode identical with a second aspect of the present invention in high-speed region, can control to low pressure with high side pressure according to the rising of the speed of compressor 10.Therefore, increase even consider the rising load of following this speed, also can carry out the protection control of compressor, the protection of the compressor in the high-speed region can be carried out more exactly like this.
According to a sixth aspect of the invention, a kind of compressor volume control system that is used to control the cooling cycle system of variable volume compressor 10 is provided, described system is designed to continuously change discharge capacity by motorized adjustment capacity control device 10b, and described system is provided with:
Low-pressure lateral pressure detection device 23 is used to detect the low-pressure lateral pressure of refrigeration cycle,
Speed detector 24, be used to detect with the value of information of the velocity correlation of compressor 10 and
Control system 25, the testing signal of low-pressure lateral pressure detection device 23 and speed detector 24 is transfused to described control system 25, and according to the speed controlling capacity control device 10b of low-pressure lateral pressure and compressor 10,
Described control system 25 is provided for the predetermined control pressure value P s4 of low-pressure lateral pressure, and
Control capacity control device 10b, when the speed of compressor 10 is in the high-speed region that is higher than predetermined speed Ny, and low-pressure lateral pressure reduces discharge capacity near expectant control pressure value P d4, and low-pressure lateral pressure drops to and is lower than expectant control pressure value P d4.
Identical with the mode of third and fourth aspect of the present invention, can suppress the undue decline in the circulation low-pressure lateral pressure in the high-speed region, and carry out compressor protection control more exactly.
In a seventh aspect of the present invention, the compressor volume control system of arbitrary cooling cycle system of first to the 5th aspect of the present invention is provided, and described system regulates the change degree of discharge capacity according to the difference between the high side pressure and the first pilot pressure value Pd1.
In view of the above, when differing greatly between the high side pressure and the first pilot pressure value Pd1, the change degree of discharge capacity can increase to allow high side pressure quickly near the first pilot pressure value Pd1.Conversely, the difference between the high side pressure and the first pilot pressure value Pd1 hour, the change degree of discharge capacity can reduce, the fluctuation or the room temperature that blow to the temperature of the air in the passenger accommodation like this can become littler.
According to an eighth aspect of the invention, provide according to of the present invention second or the compressor volume control system of the 5th aspect cooling cycle system, described system regulates the change degree of discharge capacity according to the difference between high side pressure and the 3rd pilot pressure value Pd3.
In view of the above, when differing greatly between high side pressure and the 3rd pilot pressure value Pd1, the change degree of discharge capacity can increase to allow high side pressure quickly near the 3rd pilot pressure value Pd3.Conversely, the difference between high side pressure and the 3rd pilot pressure value Pd3 hour, the change degree of discharge capacity can reduce, the fluctuation or the room temperature that blow to the temperature of the air in the passenger accommodation like this can become littler.
According to a ninth aspect of the invention, the compressor volume control system of the arbitrary cooling cycle system in first to the 5th aspect according to the present invention is provided, and described system makes the second pilot pressure value Pd2 be higher than the first pilot pressure value Pd1 value of 0.01MPa at least.
According to a ninth aspect of the invention, according to the setting of the second pilot pressure value Pd2, high side pressure can be controlled within the second pilot pressure value Pd2 usually, and can avoid the braking of compressor by compressor capacity control.
According to the tenth aspect of the invention, provide a kind of cooling cycle system, be provided with
Vaporizer 19 is used for making the refrigeration agent evaporation from cooled air is absorbed heat,
Compressor 10 is used to hold and compress the refrigeration agent that passes through vaporizer 19,
Capacity control device 10b, but described capacity control device 10b motorized adjustment be arranged on compressor 10 places, and can change the discharge capacity of compressor 10 continuously,
High side pressure detection device 22 is used to detect the high side pressure of refrigeration cycle, and
Control system 25, the testing signal of high side pressure detection device 22 are input to described control system 25, and according to high side pressure control capacity control device 10b,
Control system 25 with the first pilot pressure value Pd1 and the second pilot pressure value Pd2 that is higher than the described first pilot pressure value Pd1 predetermined value be provided as the pilot pressure value that is used for high side pressure and
Control system 25 control capacity control device 10b when high side pressure surpasses the first pilot pressure value Pd1, reduce discharge capacity, and high side pressure near the first pilot pressure value Pd1 and
When high side pressure surpasses the second pilot pressure value Pd2, compressor 10 is arranged in the idling conditions.
Like this, a tenth aspect of the present invention has covered the cooling cycle system of a first aspect of the present invention, and has shown effect and the effect similar with effect to the effect of a first aspect of the present invention.
According to the 11st aspect of the present invention, a kind of cooling cycle system is provided, be provided with
Vaporizer 19 is used for making the refrigeration agent evaporation from cooled air is absorbed heat,
Compressor 10 is used to hold and compress the refrigeration agent that passes through vaporizer 19,
Capacity control device 10b, but described capacity control device 10b motorized adjustment be arranged on compressor 10 places, and can change the discharge capacity of compressor 10 continuously,
High side pressure detection device 22 is used to detect the high side pressure of refrigeration cycle,
Speed detector 24, be used to detect with the value of information of the velocity correlation of compressor 10 and
Control system 25, the testing signal of high side pressure detection device 22 and speed detector 24 is input to described control system 25, and according to the described capacity control device 10b of the speed controlling of high side pressure and compressor 10,
Control system 25 will use the 3rd pilot pressure value Pd3 that uses in the high-speed region of first pilot pressure value Pd1 in the low velocity zone of the predetermined control speed Nx that is lower than compressor 10 and the predetermined control speed Nx that is higher than compressor 10 to be provided as the pilot pressure value that high side pressure is used
The 3rd pilot pressure value Pd3 be designed to be lower than the first pilot pressure value Pd1 pressure and along with the speed of compressor 10 rise and descend and
Control capacity control device 10b, when the speed of compressor 10 is in the low-speed region that is lower than expectant control speed Nx, and high side pressure reduces discharge capacity above the first pilot pressure value Pd1, and the speed of compressor 10 near the first pilot pressure value Pd1 and
Control capacity control device 10b, when the speed of compressor 10 is in the high-speed region that is higher than expectant control speed Nx and high side pressure when surpassing the 3rd pilot pressure value Pd3, discharge capacity is reduced, and high side pressure is near the 3rd pilot pressure value Pd3.
Like this, the 11st aspect of the present invention has covered the cooling cycle system of a fifth aspect of the present invention, and can show effect similar to a fifth aspect of the present invention and effect.
According to the 12nd aspect of the present invention, a kind of cooling cycle system is provided, be provided with
Vaporizer 19 is used for making the refrigeration agent evaporation from cooled air is absorbed heat,
Compressor 10 is used to hold and compress the refrigeration agent that passes through vaporizer 19,
Capacity control device 10b, but described capacity control device 10b motorized adjustment be arranged on compressor 10 places, and can change the discharge capacity of compressor 10 continuously,
Low-pressure lateral pressure detection device 23 is used to detect the low-pressure lateral pressure of refrigeration cycle,
Speed detector 24, be used to detect with the value of information of the velocity correlation of compressor 10 and
Control system 25, the testing signal input control system 25 of low-pressure lateral pressure detection device 23 and speed detector 24, and according to the low-pressure lateral pressure and the speed controlling capacity control device of compressor 10,
Described control system 25 be provided for described low-pressure lateral pressure scheduled pressure value Ps4 and
Control capacity control device 10b, in the time of in the speed of compressor 10 is in than the higher high-speed region of expectant control speed Ny, and low-pressure lateral pressure is fallen under the expectant control pressure value P d4, and discharge capacity is reduced, and low-pressure lateral pressure is near expectant control pressure value P d4.
Like this, the 12nd aspect of the present invention has covered the cooling cycle system of a sixth aspect of the present invention, and can show effect identical with a sixth aspect of the present invention and effect.
Notice that the reference identification after different devices has shown that the device with specific is corresponding in following embodiment.
Description of drawings
These and/or other purpose of the present invention and advantage will and become clearer in conjunction with the accompanying drawings from embodiment's following explanation, wherein:
Fig. 1 is the view of structure that has shown the whole system of embodiments of the invention;
Fig. 2 is the curve according to definite method of the volume controlled current value of embodiment's variable volume compressor;
Fig. 3 is according to the volume controlled electric current of embodiment's variable volume compressor and the curve of the relation between the target low-pressure lateral pressure;
Fig. 4 is the curve according to the control of the capacity control drive of embodiment's variable volume compressor;
Fig. 5 is the flow chart of the volume controlled in the embodiment;
Fig. 6 is the flow chart of embodiment's inner capacities control;
Fig. 7 is the operating curve of the relation between the interior compressor speed of refrigerant pressure and embodiment;
The volume controlled that Fig. 8 A, 8B are based on embodiment has been explained the view of the behavior of high side pressure and low-pressure lateral pressure.
Embodiment
Below, will be based on the description of drawings embodiments of the invention.Fig. 1 has shown refrigeration cycle and its control system of vehicle according to the invention air-conditioning system.The present invention relates to a kind of air-conditioning system of using in the bus at a large amount of seats that is used for settling especially on the length direction of passenger's indoor vehicle.The compressor 10 of refrigeration cycle has the magnetic clutch 10a that is formed for breaking away from cooperation and cooperates the clutch device of driving force.Compressor 10 by this magnetic clutch 10a, be with 11 etc. by vehicle motor 12 drivings and suction and compressed refrigerant.
Compressor 10 is to continuously change the transfiguration compressor types of discharge capacity by the control signal from the outside, and is provided with electromagnet-type capacity control drive 10b.
At the waste side place of compressor 10, be provided with the electronic cooling fan 16 of condenser 13, refrigeration agent container 14, subcooler 15 and formation condensation unit 17.Condenser 13 is by blowing next air cooling and the condensation high-pressure gas refrigerant from compressor 1 discharging from electronic cooling fan 16 (outside air).
The liquid and vapor capacity refrigeration agent that refrigeration agent container 14 separates in the outlet port of condenser, and towards subcooler 15 guiding liquids refrigeration agents.It is at place, the bottom side storage excess liquid refrigeration agent of the box-shaped inside of refrigeration agent container 14.Air (outside air) cooling of subcooler 15 by blowing from electronic cooling fan 16 is used for supercooling from the liquid refrigerant (saturated solution) of refrigeration agent container 14.
At the outlet side place of subcooler 15, be provided with the expansion valve 18 that forms decompressor.This expansion valve 18 has reduced pressure at the outlet side place high pressure liquid refrigerant of subcooler 15 (cross cold refrigeration agent) to low-pressure gas-liquid two-phase state.The opening degree of expansion valve 18 can be controlled automatically by known mechanism, so the overheated predetermined value that is maintained at of the refrigeration agent in the outlet port of vaporizer 19.
Vaporizer 19 is that heat exchanger is used in cooling, and described heat exchanger is in electric fan 20 is placed in the housing (not shown) of cooling unit 21.Air in the passenger accommodation of electric fan 20 suction buses also sends it to vaporizer 19.In vaporizer 19, low-pressure gas-liquid two phase refrigerant absorbs from the heat of the air that is blowed and evaporation.Because this, the air that is blowed is cooled with cooling air.This cooling air supplies in the cooling pipe (not shown) that is placed in the indoor place, top of bus rider.Cooling air is blown into the inside of passenger accommodation from the cooling air port of cooling pipe.
The coolant channel at the waste side place of compressor 10 is provided with high side pressure sensor 22, is used to detect high side pressure Pd.In addition, the coolant channel at the suction side place of compressor 10 is provided with low-pressure lateral pressure sensor 23, is used to detect low-pressure lateral pressure Ps.Because the change of refrigerant pressure, pressure transducer 22,23 changes resistance value continuously, and changes voltage continuously based on this.
The velocity transducer 24 that in the housing of compressor 10, holds compressor 10.Rotation by the magnetic rotatable portion in the compressor 10 produces the pulse type output voltage to this velocity transducer 24 at the electromagnetic coil place, the speed of the corresponding compressor of frequency.These sensors 22,23 and 24 testing signal are transfused to air-conditioner control system 25.In addition, at the inlet side place of air-conditioner control system 25, connect room temperature sensor 26 and other sensor and the Air-Conditioning Control Panel 27 of the chamber in the temperature T r be used to detect bus.Air-Conditioning Control Panel 27 is settled near indoor object palette, and allows different air-conditioning operation signals to be input to air-conditioner control system 25 based on driver's manual operations.
Especially, Air-Conditioning Control Panel 27 is provided with temperature switch 27a and air quantity switch 27b is set, described temperature is provided with switch 27a and is used for manually being provided with indoor temperature required Tset, and described air quantity switch 27b is used for manually being provided with the air-flow of the electric fan 6 of cooling unit 21 grades.
Air-conditioner control system 25 comprises microcomputer and peripheral circuit thereof etc.It carries out predetermined processing according to preset program, with the operation of control aircondition.For this reason, the outlet side of air-conditioner control system 25 have the magnetic clutch 10a of compressor 10 and capacity control drive 10b, condensation unit 17 electronic cooling fan 16, cooling unit 21 electric fan 20 and be connected to its other aircondition.These airconditions are controlled by the operation of air-conditioner control system 25.
Then, variable volume compressor 10 will be described in more detail.The variable volume compressor 10 of present embodiment is known as slant plate type compressor (for example, referring to Japan Patent publication (A) No.11-78510).
Be applied to the control current value I of electromagnetic capacity control valve 10b by change, the pilot pressure Pc of swash plate is changed.Because this, the change at the angle of inclination of swash plate becomes the change of the stroke of piston, and becomes the change of discharge capacity successively.Herein, discharge capacity is that refrigeration agent is inhaled into and the geometric cpacity of the working space that compresses.Especially, it is the top dead of stroke of piston and the volume of the cylinder between the bottom dead center.
In addition, in swash plate type variable volume compressor 10, pilot pressure Pc can be adjusted changing the angle of inclination of swash plate continuously, and from 100% maximum capacity discharge capacity is changed to minimum capacity near about 0% continuously thus.
The control current value I that is applied to electromagnetic capacity control valve 10b is provided with the function of the difference between the setting temperature Tset of switch 27a and determines by room temperature Tr (detected temperatures of room temperature sensor 26) and temperature as shown in Figure 2.Herein, temperature difference (Tr-Tset) is big more, and cooling load is big more, so temperature difference (Tr-Tset) is the indicator of cooling load (value of information).Temperature difference (Tr-Tset) is big more, and it is big more that the control current value I increases.
In electromagnet-type capacity control drive 10b, the value of control valve electric current I is used to change the electromagnetic force of electromagnetic coil and regulates the valve position that is used to control described pilot pressure Pc, as shown in Figure 3, when the value of control electric current I increased, the target low-pressure lateral pressure of refrigeration cycle (target suction pressure) was set to lower.
In addition, the valve position of the capacity control drive 10b of electromagnet-type is regulated according to target low pressure, and pilot pressure Pc is conditioned thus, and discharge capacity changes.Because this of discharge capacity changes, the actual low-pressure lateral pressure of refrigeration cycle is conditioned to mate with the target low-pressure lateral pressure.
Therefore, the increase of temperature difference (Tr-Tset) increase, target low-pressure lateral pressure that cause controlling current value I descend, the operating condition of the increase of the increase at the angle of inclination of the decline of pilot pressure Pc, swash plate and discharge capacity.If reduce temperature difference (Tr-Tset), operating condition in contrast to this takes place, and reduce discharge capacity.
The Current Control of capacity control drive 10b specifically is the duty ratio control of shortwave shape output as shown in Figure 5.Therefore, the adjusting of control electric current I refers to the adjusting of duty ratio.Duty ratio=t/t0.Note that and also can not utilize this duty ratio control, but directly continuously change the value (with simulated mode) of control electric current I.
Then, the specific example of controlling according to this embodiment's compressor capacity is described with reference to Fig. 5,6.Fig. 5,6 has shown by the performed control program of air-conditioner control system 25.When vehicle transmitter 12 operation and air-conditioning system 25 were supplied to power, the control program of Fig. 5 started.At first, different sensor 22-24 and 26 different operating signal etc. and Air-Conditioning Control Panel 27 are read (S10).
Then, judge whether compressor speed Nc is the first control rate Nx or bigger (S20).Herein, the first control rate Nx be describe high voltage control zone A and as shown in Figure 7 first protect the speed of control area B at a high speed, and for example be 3000rpm.In addition, high voltage control zone A is the zone that only is used for the protection control of compressor 10 by high side pressure Pd.Relative therewith, first to protect at a high speed the control area be the zone that is used for the protection control of compressor 10 according to high side pressure Pd and speed Nc.
Note that in this embodiment the top speed of the use of compressor speed Nc approximately is 6500rpm, such first control rate Nx is the speed of 1/2 degree that is higher than the top speed of use a little.
The coordinate indication refrigerant pressure of Fig. 7.In the present embodiment, R134a is as the refrigeration agent of refrigeration cycle, and therefore at the refrigerant pressure near 0.3MPa, refrigerant temperature becomes near 0 ℃.
When compressor speed Nc less than the first control rate Nx, step 20 place judges whether, and the control processing of the high voltage control logic L1 of execution graph 5.Relative therewith, when compressor speed Nc is the first control rate Nx or bigger, being judged as of S20 place be, and execution graph 5 first protect control logic L2 at a high speed.
At first, explain high voltage control logic L1, at first, judge that whether the high side pressure Pd that detected by high side pressure sensor 22 is the first pilot pressure value Pd1 or bigger (S30) as shown in Figure 7.Herein, the first pilot pressure value Pd1 is the pressure that starts compressor protection control, is used to reduce the pressure loading on the compressor internal mechanism.In the present embodiment, the first pilot pressure value Pd1 is set to for example 2.7MPa (referring to Fig. 7).
In contrast, the second pilot pressure value Pd2 is the force value that is higher than the lucky predetermined value Pdd of the first pilot pressure value Pd1, and is to be used for stopping immediately the stress level of compressor with the protection compressor.In the present embodiment, predetermined value Pdd is set to 0.1MPa, and the second pilot pressure value Pd2 is set to 2.8MPa (referring to Fig. 7) simultaneously.Herein, owing to following reason, predetermined value Pdd should be set to 0.01MPa or bigger.
According to inventor's test and research, even under common drive condition, surpass (overshoot) that surpass the high pressure of the first pilot pressure value Pd1 takes place at the compressor capacity control period sometimes.If surpass is the degree of being scheduled to or littler, does not need to restart the compressor protection control that is used to stop compressor.What being not enough to like this started compressor protection control surpasses degree according to the application of refrigeration cycle and difference, and so thus being not enough to starts surpassing degree and can reducing setting to each application of compressor protection control.Described degree or this degree that adds safe clearance can be set to predetermined value Pdd as above.
From then on viewpoint, predetermined value Pdd can be set to such as 0.01MPa or bigger.In addition, as in present embodiment, predetermined value Pdd can be set to 0.1MPa or bigger.For example, the degree of predetermined value Pdd can be set up, and makes the first pilot pressure Pd1 add predetermined value Pdd in the above value and becomes and be not more than high-voltage value with being avoided, even interim.
Add predetermined value Pdd by allowing the value of the second pilot pressure value Pd2 equal the first pilot pressure value Pd1, it just can be set to handle the pressure that compressor must be stopped immediately.In addition, the first pilot pressure value Pd1 is set up and is lower than the just value Pdd for being scheduled to of the second pilot pressure value Pd2, and consider needs in the zone of under the common operational condition of the refrigeration cycle first pilot pressure value Pd1, have and make and realize and the height of the degree of adjusting compressor performance.
If high side pressure Pd is less than as the high pressure (1) of Fig. 7, the first pilot pressure value Pd1 in (2), so compressor protection control not necessarily, compressor capacity is normally controlled (S40) like this.This normal control is to change the discharge capacity of compressor 10 to regulate the control of low-pressure lateral pressure according to the change of cooling load.
Especially, as showing in Fig. 2 above-mentioned, the control current value I of electromagnet-type capacity control drive 10b is provided with the function of the temperature difference (Tr-Tset) between the setting temperature Tset of switch 27a and determines by room temperature Tr and temperature.This control current value I is used to determine the target low-pressure lateral pressure of refrigeration cycle as shown in Figure 3.
In addition, the valve position of electromagnet-type capacity control drive 10b is regulated according to target low voltage side voltage (electromagnetic force of electromagnetic coil) and actual low pressure.Because this regulates pilot pressure Pc and changes discharge capacity.Discharge capacity is changed to regulate actual low-pressure lateral pressure to mate with the target low-pressure lateral pressure.
Owing to determine by the low-pressure lateral pressure of refrigeration cycle in the refrigeration agent evaporating temperature at vaporizer 19 places, change discharge capacity with regulate low-pressure lateral pressure make it possible to control vaporizer 19 cooling performance be controlled to the performance suitable with cooling load.
On the other hand, when high side pressure Pd surpasses the first pilot pressure value Pd1, shown in the high pressure (3) of Fig. 7, be to judge whether high side pressure Pd is the second pilot pressure value Pd2 or bigger (S50) being judged as of S30 place for example.When not being judged as not, at the S60 place based on pressure difference Δ Pa, the controlled high voltage control that is used for of capacity.
Especially, obtain the pressure difference Δ Pa=first pilot pressure value Pd1-actual high-voltage side pressure Pd.Based on this pressure difference Δ Pa, find control electric current regulated value.This control electric current regulated value is the regulating degree of current relatively (previous calculations) control electric current.
But, when Pd surpasses Pd1, carry out the high voltage control of S60, that is, in the negative region of pressure difference Δ Pa, the decrease (decrease of duty ratio) of controlling electric current I like this is definite above the amount of the first pilot pressure value Pd1 according to the high side pressure Pd of reality.
In view of the above, actual high side pressure Pd surpasses the amount big more (pressure difference Δ Pa is big more) of the first pilot pressure value Pd1, and the amount that the control electric current I can form is big more, like this discharge capacity to reduce degree big more.As a result, high side pressure Pd can reduce rapidly towards the first pilot pressure value Pd1.
In contrast, the amount that surpasses the first pilot pressure value Pd1 as the high side pressure Pd of reality is less, the decrease of control electric current I becomes littler, discharge capacity to reduce degree less, it is that fluctuation and the interior fluctuation of room temperature in turn that is blown into the temperature of the air in the passenger accommodation can keep less that individual advantage is arranged like this, can suppress any injury effect for the air-conditioning sensation.
Please note; under normal vehicle operation conditions; the high voltage control of above-mentioned S60 makes high side pressure Pd be suppressed to less than the second pilot pressure value Pd2, and shown in the solid line among Fig. 8 A, the protection of compressor 10 control can be performed ceaselessly continuous running air-conditioning system simultaneously like this.Therewith, the inconvenience that just can avoid room temperature to raise and follow the fluctuation of the temperature that the protection control of compressor 10 blows.
On the other hand, if the high voltage control of above-mentioned S60 the term of execution undue operating lag (surpassing) takes place in volume controlled, high side pressure Pd will rise too big sometimes, and surpass the second pilot pressure value Pd2 (referring to the high pressure (3) of Fig. 7 and the dotted line of Fig. 8 A).When for example high outside air temperature causes the refrigerant cools decreased performance of condensation unit 17 and vehicle to slow down rapidly, be easy to take place such volume controlled operating lag, the speed of vehicle transmitter 12 rises rapidly, and the speed of compressor 10 also rises rapidly.
In this case, to become be that the S70 place that operates in of refrigeration cycle stops to the judgement at the S50 place.Especially, be cut off and compressor 10 is stopped to the power of the magnetic clutch 10a of compressor 10.Meanwhile, condensation unit cooling fan 16 is stopped.Because the operation of compressor 10 is stopped, the overload of compressor internal mechanism can be easy to eliminate, and compressor 10 is protected.Note that electric fan 20 continuous runnings of cooling unit 21, even when stopping refrigeration cycle, air is blown in the passenger accommodation continuously like this.
Then, the judgement of explanation at S20 place become be and situation that first high speed of Fig. 5 protects the control processing of control logic L2 to be performed.In this control processing, at first, judge whether high side pressure Pd is the 3rd pilot pressure value Pd3 or bigger (S80).
Herein, similar to the first pilot pressure value Pd in the high voltage control logic L1, the 3rd pilot pressure value Pd3 is the pressure that starts compressor protection control, is used to reduce the pressure loading on the compressor internal mechanism.But as shown in Figure 7, the 3rd pilot pressure value Pd3 is determined to descend from the level of the first pilot pressure value Pd1 (2.7MPa) gradually according to the rising in the compressor speed Nc, promptly drops to the right side.These are different with the first pilot pressure value Pd1.
Next the reason of determining the 3rd pilot pressure value Pd3 like this will describe.That is, the load that influences the reliability of compressor 10 can be replaced by pressure difference between high side pressure and the low-pressure lateral pressure and speed.That is, the difference between height and the low-pressure lateral pressure is big more, and the pressure loading that acts on the compressor internal mechanism is big more.In addition, compressor speed Nc is high more, and the temperature of the friction portion of compressor internal mechanism rises big more.Owing to these reasons etc., the actual load of compressor 10 further rises.Correspondingly, determine the 3rd pilot pressure value Pd3 with along with the rise and fall of compressor speed Nc to the right.
In addition, if actual high side pressure Pd, does not need compressor protection control less than the 3rd pilot pressure value Pd3 shown in the high pressure (1) of Fig. 7, carry out common control (S90) like this.This common control is identical with S40.It is the control of regulating discharge capacity according to the change of cooling load.
On the other hand; when the high side pressure Pd of reality surpasses the 3rd pilot pressure value Pd3 of high pressure (2) as shown in Figure 7, need compressor protection control, program advances to S100 like this; at described S100 place, judge whether high side pressure Pd is the second pilot pressure value Pd2 or bigger.When high side pressure Pd less than the second pilot pressure value Pd2, program advances to S110, at described S110 place, carries out the first protection control at a high speed.
This first similar control of high voltage control of protecting control to be and to rise at a high speed.It obtains the high side pressure Pd of pressure difference Δ Pb=the 3rd pilot pressure value Pd3-reality, and controls the capacity that is used for high voltage control based on this pressure difference Δ Pb.
Especially, the high voltage control of S110 is carried out within the negative region of pressure difference Δ Pd, and the decrease (decrease of duty ratio) of controlling electric current I like this is definite above the amount of the 3rd pilot pressure value Pd3 according to the high side pressure Pd of reality.
In view of the above, it is big more that actual high side pressure Pd surpasses the 3rd pilot pressure value Pd3, and the decrease of control electric current I is big more, so just can increase reducing degree and reducing high side pressure Pd towards the 3rd pilot pressure value Pd1 rapidly of discharge capacity.
In addition, the amount that surpasses described value as high side pressure Pd is less, and the decrease of control electric current I also becomes less, and the decrease of discharge amount is less, be blown into like this air in the passenger accommodation temperature fluctuation and successively the fluctuation in the room temperature can reduce.
Note that common high side pressure Pd can be suppressed to less than the second pilot pressure value Pd2 by the high voltage control of carrying out S110, shown in the solid line of Fig. 8 A, so just can carry out the protection control ceaselessly continuous running air-conditioning system of while of compressor 10.
But, if because the unexpected rising of compressor speed or the cause of other specific factor, the high voltage control of S110 the term of execution the undue operating lag (surpassing) of volume controlled taken place, high side pressure Pd will finish (with reference to the high pressure (3) of figure 7 and the dotted line of Fig. 8 A) sometimes to surpass the second pilot pressure value Pd2.
In this case, to become be that refrigeration cycle stops at the S120 place in the judgement of S100.Especially, be cut off to the power of the magnetic clutch 10a of compressor 10, compressor 10 is stopped.Meanwhile, the cooling fan 16 of condensation unit 17 is stopped.Because stopping of the operation of compressor 10, the overload of compressor internal mechanism can be eliminated reliably, and compressor 10 can be protected.
Meanwhile, the operation of the electric fan 20 of cooling unit continues.Note that high side pressure Pd surpasses the 3rd pilot pressure value Pd3, be easy to generation when higher and motor operate in outside air temperature on high speed as the state of the high pressure (2) of Fig. 7.
Then, explanation second high speed is as shown in Figure 6 protected control logic L3.Process judges from the S130 that the S110 of Fig. 5 advances to Fig. 6 whether compressor speed Nc is the second control rate Ny.Herein, the second control rate Ny is that second high speed of describing is as shown in Figure 7 protected the speed of control area C, and is the speed that fully is higher than the first control rate Nx, for example is 5000rpm.It is the zone that is used for the protection control of compressor 10 by low-pressure lateral pressure Ps and speed Nc that this second high speed is protected control area C.
If compressor speed Nc is the second control rate Ny or bigger, judgement at the S130 place becomes, then at S140, judge whether actual low-pressure lateral pressure Ps (checkout value of the 4th pilot pressure value Ps4) is the 4th pilot pressure value Ps4 or littler then.Herein, the 4th pilot pressure value Ps4 is 0.05MPa for example.Low low-pressure lateral pressure value like this (from the pressure of the negative region of external pressure) only takes place under such as low outside air temperature and the specific condition near the high speed operation of the top speed of using.
When in the high-speed region of the second control rate Ny or higher, actual low-pressure lateral pressure Ps is the 4th pilot pressure value Ps4 or littler, and shown in the low pressure (4) of Fig. 7, process advances to S150, at described S150 place, second at a high speed protection control and be performed.
This second high speed protection control is to be used for changing the control control of current I, and Shi Ji low-pressure lateral pressure Ps becomes the 4th pilot pressure value Ps4 or bigger like this.Especially, the control electric current I is reduced to the minimum value of this control range.Because this, the compressor discharge capacity is controlled to the minimum capacity volume forcibly.
By reducing to control electric current I like this and reducing discharge capacity, actual low-pressure lateral pressure Ps can be elevated to the 4th pilot pressure Ps4 or bigger, shown in Fig. 8 B.
Please note; the second high speed protection of S150 is controlled at first of S110 and protects control to be performed afterwards execution once more at a high speed, and the little person of the control electric current I of determining at two control processing places of S110 and S150 is selected for the control electric current I (duty ratio) that finally is identified for capacity control drive 10b like this.
In view of the above, owing to be controlled to less level based on two control procedure discharge capacity of S110 and S150, first and second protect the purpose of control to realize at a high speed.
When being judged as not at S130 and S140 place; the second not execution of protection control at a high speed of S150; when it is identified for the control electric current I (duty ratio) of capacity control drive 10b, adopt " decrease of control electric current I " of protecting control according to first of S110 at a high speed like this.
Other embodiment
Note that the invention is not restricted to the embodiments described, and can in following mode, make amendment, for example:
(1) in the above-described embodiment; illustrated that will control electric current I is reduced to the example that second of S150 protects the minimum value in the interior control range of control at a high speed; but control similar to the high voltage control of S60 and the first high speed protection of S110; also can obtain the low-pressure lateral pressure Ps of pressure difference Δ Pc=the 4th pilot pressure value Ps4-reality; and the decrease (decrease of duty ratio) of determining the control electric current I is with when pressure difference Δ Pc becomes bigger and become bigger; that is, the amount fallen under the 4th pilot pressure value Ps4 of Shi Ji low-pressure lateral pressure Ps is big more.
(2) in the above-described embodiment, variable volume compressor 10 is provided with magnetic clutch 10a, power to magnetic clutch 10a is cut off to break away from magnetic clutch 10a when handling, the refrigeration cycle (S70 and S120) that is used for stopping Fig. 5 is to stop compressor 10, but swash plate type variable volume compressor 10 makes the angle of inclination of swash plate continuously change, and the maximum capacity of discharge capacity from 100% continuously changes the minimum capacity near about 0%, so also can be when stopping the refrigeration cycle of Fig. 5 (S70 and S120) discharge capacity be reduced to force and reduces, to allow compressor 10 stop substantially near about 0% minimum capacity.
By like this, just can eliminate the magnetic clutch 10a of variable volume compressor 10, compressor 10 can become the no-clutch structure like this.
(3) the invention is characterized in the volume controlled of variable volume compressor 10, be not limited to the structure of variable volume compressor 10, so also can use with the variable volume compressor except the swash plate type.
(4) in the above-described embodiment, explained the example of the variable volume compressor 10 that is provided with velocity transducer 24, but the velocity correlation of the speed of variable volume compressor 10 and vehicle transmitter 12 connection so just can be based on the speed of the speed calculation variable volume compressor 10 of vehicle transmitter 12.Especially, variable volume compressor 10 is actuated to be rotated by pulley and band by vehicle transmitter 12, and compressor speed can calculate by following formula (1) like this:
Compressor speed=transmitter speed x (sender side diameter of pulley/compressor side diameter of pulley) (1)
(5) in the above-described embodiment, the low target value of low-pressure lateral pressure Ps when the compressor high speed, promptly the 4th pilot pressure value Ps4 becomes fixed value, except having the low-pressure lateral pressure sensor 23 that sensor output value changes continuously according to pressure, also can use pressure switch like this by the 4th pilot pressure value Ps4 operation.
(6) in the above embodiments, the second pilot pressure value Pd2 also is constant value, no matter and compressor speed Nc, but also the second pilot pressure value Pd2 can be set to the feature that the 3rd pilot pressure value Pd3 in compressor speed Nc is the first control rate Nx or bigger high-speed region falls into the right.For this reason, in the first control rate Nx or bigger high-speed region, just can move forward when stopping compressor rising with speed.
(7) in the above-described embodiment, the low target value of low-pressure lateral pressure Ps when the compressor fair speed, promptly the 4th pilot pressure value Ps4 becomes steady state value, rises to the feature that compressor speed Nc is the right in the second control rate Ny or the bigger high-speed region but also it can be set to.Because this just can move forward when being used for the volume controlled of low voltage control in the rising with speed.
(8) in the above-described embodiment, the cooling cycle system that is used for vehicle air conditioning has been described, but the present invention can similarly be applied to the cooling cycle system of the application except vehicle air conditioning, as long as they are the cooling cycle systems that are provided with variable volume compressor 10.
Although with reference to the certain embodiments selected for purpose of explanation be illustrated, those of ordinary skill is appreciated that under the situation that does not deviate from basic conception of the present invention and scope of the present invention, can carry out multiple modification to the present invention.

Claims (8)

1. compressor volume control system that is used to control the cooling cycle system of variable volume compressor (10), the capacity control device (10b) that described system is designed to by motorized adjustment continuously changes discharge capacity, and described system is provided with:
High side pressure detection device (22), be used to detect refrigeration cycle high side pressure and
Control system (25), the testing signal of described high side pressure detection device (22) is imported into described control system (25), and controls described capacity control device (10b) according to described high side pressure,
Described control system (25) with the first pilot pressure value (Pd1) and the second pilot pressure value (Pd2) that is higher than the predetermined value of the described first pilot pressure value (Pd1) be provided as the pilot pressure value that is used for described high side pressure and
Described control system (25) control capacity control device (10b) when described high side pressure surpasses the described first pilot pressure value (Pd1), reduces described discharge capacity, and described high side pressure near the described first pilot pressure value (Pd1) and
When described high side pressure surpasses the described second pilot pressure value (Pd2), described compressor (10) is set to idling conditions.
2. the compressor volume control system of cooling cycle system according to claim 1 also is provided with:
Rotation detecting (24) is used for detecting the value of information with the velocity correlation of described compressor (10), and testing signal is input in the described control system (25),
Described control system (25) is provided with the first pilot pressure value (Pd1) as the described pilot pressure value that is used for high side pressure in than the low low-speed region of first control rate (Nx) of described compressor (10), and the 3rd pilot pressure value (Pd3) is set in the high-speed region of first control rate (Nx) that is higher than described compressor (10)
Described the 3rd pilot pressure value (Pd3) is the pressure that is lower than the described first pilot pressure value (Pd1), and descends according to the rising of the speed of described compressor (10), and
In the time of in the speed of described compressor (10) is in than the high high-speed region of described first control rate (Nx), if described high side pressure surpasses described the 3rd pilot pressure value (Pd3), (10b) is controlled for described capacity control device, described discharge capacity is reduced, and described high side pressure is near described the 3rd pilot pressure value (Pd3).
3. the compressor volume control system of cooling cycle system according to claim 1 also is provided with:
Low-pressure lateral pressure detection device (23), be used to detect the low-pressure lateral pressure of refrigeration cycle and testing signal is input in the described control system (25) and
Speed detector (24), the value of information that is used for the velocity correlation of detection and compressor (10) also is input to described control system (25) with this testing signal,
Described control system (25) is provided for the predetermined control force value (Ps4) of described low-pressure lateral pressure, and
Control described capacity control device, when the speed of described compressor (1) is in the high-speed region that is higher than predetermined speed (Ny), and described low-pressure lateral pressure descends from described expectant control force value (Ps4), described discharge capacity is reduced, and described low-pressure lateral pressure is near expectant control force value (Ps4).
4. the compressor volume control system of cooling cycle system according to claim 2 also is provided with:
Low-pressure lateral pressure detection device (23) is used to detect the low-pressure lateral pressure of refrigeration cycle and testing signal is input in the described control system (25),
Described control system (25) is provided for the predetermined control force value (Ps4) of described low-pressure lateral pressure, and second control rate (Ny) is set than the lucky high predetermined amount of described first control rate (Nx), and
Control described capacity control device (10b), when the speed of described compressor (1) is within the high-speed region that is higher than described second control rate (Ny), and described low-pressure lateral pressure descends from described predetermined control force value (Ps4), described discharge capacity is reduced, and described low-pressure lateral pressure is near predetermined control force value (Ps4).
5. according to the compressor volume control system of the arbitrary described cooling cycle system of claim 1-4, described system regulates the change degree of described discharge capacity according to the difference between described high side pressure and the described first pilot pressure value (Pd1).
6. the compressor volume control system of cooling cycle system according to claim 2, described system regulates the change degree of described discharge capacity according to the difference between described high side pressure and described the 3rd pilot pressure value (Pd3).
7. according to the compressor volume control system of the arbitrary described cooling cycle system of claim 1-4, described system makes that the described second pilot pressure value (Pd2) is to be higher than the first pilot pressure value (Pd1) value of 0.01MPa at least.
8. a cooling cycle system is provided with
Vaporizer (19) is used for making the refrigeration agent evaporation from cooled air is absorbed heat,
Compressor (10) is used to hold and compress the refrigeration agent that passes through described vaporizer (19),
Capacity control device (10b) is arranged on described compressor (10) to described capacity control device (10b) motorized adjustment and locates, and can change the discharge capacity of described compressor (10) continuously,
High side pressure detection device (22) is used to detect the high side pressure of refrigeration cycle, and
Control system (25), the testing signal of described high side pressure detection device (22) is input to described control system (25), and controls described capacity control device (10b) according to described high side pressure,
Described control system (25) with the first pilot pressure value (Pd1) and the second pilot pressure value (Pd2) that is higher than described first pilot pressure value (Pd1) predetermined value be provided as the pilot pressure value that is used for high side pressure and
Described control system (25) is controlled described capacity control device (10b), when described high side pressure surpasses the described first pilot pressure value (Pd1), described discharge capacity is reduced, and described high side pressure near the described first pilot pressure value (Pd1) and
When described high side pressure surpasses the described second pilot pressure value (Pd2), described compressor (10) is arranged on idling conditions.
CN200610068089A 2005-03-24 2006-03-24 Compressor volume control system and refrigeration cycle system Expired - Fee Related CN100580250C (en)

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JP2005085576A JP2006266172A (en) 2005-03-24 2005-03-24 Compressor displacement control device and refrigeration cycle device

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