CN107848375A - The kind of refrigeration cycle of air conditioner for vehicles and the vehicle for carrying it - Google Patents
The kind of refrigeration cycle of air conditioner for vehicles and the vehicle for carrying it Download PDFInfo
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- CN107848375A CN107848375A CN201680046683.1A CN201680046683A CN107848375A CN 107848375 A CN107848375 A CN 107848375A CN 201680046683 A CN201680046683 A CN 201680046683A CN 107848375 A CN107848375 A CN 107848375A
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Classifications
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
- B60H1/3211—Control means therefor for increasing the efficiency of a vehicle refrigeration cycle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, 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
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3248—Cooling devices information from a variable is obtained related to pressure
- B60H2001/3251—Cooling devices information from a variable is obtained related to pressure of the refrigerant at a condensing unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
- B60H2001/3291—Locations with heat exchange within the refrigerant circuit itself
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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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
-
- 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
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- 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
- F25B2700/195—Pressures of the condenser
-
- 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
- F25B2700/2103—Temperatures near a heat exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
Abstract
It is an object of the invention to, on possessing the kind of refrigeration cycle of the air conditioner for vehicles of inner heat exchanger and carrying its vehicle, a kind of kind of refrigeration cycle of air conditioner for vehicles for possessing inner heat exchanger is provided and carries its vehicle, its can in a manner of not additional part rejection coefficient decline.The kind of refrigeration cycle (1) of air conditioner for vehicles of the present invention possesses：Refrigerant loop (100), it includes compressor (2), condenser (3), electric control expansion valve (4) and evaporator (5)；Inner heat exchanger (10)；Pressure sensor (31), it detects the pressure of the refrigerant between condenser and inner heat exchanger；Detect the first temperature sensor (32) of the temperature of evaporator or there is the second temperature sensor (33) of measuring point between evaporator and inner heat exchanger；Valve opening control device (40), valve opening control device is used as the degree of superheat using the value for calculating the degree of superheat, calculates the value of the degree of superheat using the detected value or the detected value of second temperature sensor and the detected value of pressure sensor of the first temperature sensor as a parameter to calculating.
Description
Technical field
The present invention relates to empty in the vehicle with inner heat exchanger (IHX=Internal Heat Exchanger)
Adjusting improves the technology of the coefficient of performance (COP=Coefficient of Performance) in the kind of refrigeration cycle of device.
Background technology
Index as the ability for representing kind of refrigeration cycle, it is known that the coefficient of performance (COP), be calculated as the refrigerating capacity of evaporator
Divided by the value that the power of driving compressor obtains.For example, by increasing refrigerating capacity, and the power of driving compressor is reduced,
The coefficient of performance can be increased.
Device as the coefficient of performance of increase kind of refrigeration cycle, it is known that inner heat exchanger is set in kind of refrigeration cycle
(IHX) structure, the of a relatively high refrigerant of temperature of the inner heat exchanger to outflow condenser and outflow evaporator
The relatively low refrigerant of temperature carries out heat exchange.
Evaporator is flowed into the state of enthalpy decline by inner heat exchanger from the refrigerant of condenser outflow, therefore increased
The big refrigerating capacity of evaporator, is advantageous to the coefficient of performance (COP) increase.On the other hand, from the refrigerant of evaporator outflow
Compressor is flowed into the state of enthalpy increase by inner heat exchanger, therefore adds the power of driving compressor, is advantageous to
The decline of the coefficient of performance.Herein, it is proposed that in the kind of refrigeration cycle of the air conditioner for vehicles with inner heat exchanger
Prevent the technology of the decline of the coefficient of performance (referring for example to patent document 1).
Patent document 1 is characterised by, by the refrigerant temperature detection means (temperature sensing tube etc.) for controlling expansion gear
Configure the path between heat exchanger and compressor internally.According to this feature, the heat based on internal heat exchange can be sought
The energy state of the refrigerant after terminating is passed in and out, controls the valve opening of expansion gear, suppresses to flow into the enthalpy of the refrigerant of compressor
Increase, prevent the decline of the coefficient of performance.
Prior art literature
Patent document
Patent document 1：JP 2008-122034 publications
The content of the invention
Invent problem to be solved
However, it is necessary to newly configure the refrigerant temperature inspection between heat exchanger and compressor internally in patent document 1
Survey device, it is impossible to avoid productive deterioration.Requirement of the vehicle in recent years to productive raising is higher, is intricately configuring
Have and temperature-detecting device is newly set in the engine room of multiple parts be significant adverse to productive raising.
Here, it is an object of the present invention on possessing the kind of refrigeration cycle of the air conditioner for vehicles of inner heat exchanger
And carry its vehicle, there is provided a kind of kind of refrigeration cycle of air conditioner for vehicles for possessing inner heat exchanger and carry its car
, its can in a manner of not additional part rejection coefficient decline.
For solving the technical scheme of problem
The kind of refrigeration cycle of air conditioner for vehicles of the present invention possesses：Refrigerant loop, it utilizes pipe arrangement connection pressure
Contracting machine, condenser, electric control expansion valve and evaporator, make refrigerant circulation；Inner heat exchanger, it is in the first heat exchange department and
The heat exchange of the refrigerant is carried out between two heat exchange departments, is exported from the condenser to the refrigerant of the electric control expansion valve
First heat exchange department is flowed through, is exported from the evaporator to the cold-producing medium stream of the suction side of the compressor through described second
Heat exchange department；Pressure sensor, it detects the pressure of the refrigerant between the condenser and the inner heat exchanger；
Either one in first temperature sensor and second temperature sensor, first temperature sensor detect the evaporator
Temperature or the air for passing through the evaporator temperature, the second temperature sensor hands in the evaporator and the internal heat
There is measuring point between parallel operation；Valve opening control device, it is based on the institute between the inner heat exchanger and the compressor
The degree of superheat of refrigerant is stated, controls the valve opening of the electric control expansion valve；The valve opening control device is using the calculating degree of superheat
Value as the degree of superheat, the value for calculating the degree of superheat utilizes the detected value and described second of first temperature sensor
The detected value of either one and the pressure sensor in the detected value of temperature sensor is as a parameter to calculate.
In the kind of refrigeration cycle of air conditioner for vehicles of the present invention, following form is included, i.e. the valve opening control
Device processed has the calculating part calculated the calculating degree of superheat,
The value of the temperature of the refrigerant to be converted according to the detected value of the pressure sensor is set to a [DEG C], by institute
The detected value for stating the first temperature sensor is set to b [DEG C], and the detected value of the second temperature sensor is set into c [DEG C], by institute
The difference for stating the detected value c and detected value b is set to α [DEG C], and the hot of the inner heat exchanger that (formula 1) will be utilized to derive is handed over
When changing the value of efficiency and being set to Elow, the calculating part uses (formula 2) or (formula 3) to estimate described inner heat exchanger and the compression
The temperature X [DEG C] of the refrigerant between machine, according to the poor or described of temperature X [DEG C] value and the detected value b [DEG C]
Temperature X [DEG C] value and the difference of (detected value c [DEG C]-α), the value of the calculating degree of superheat is calculated,
[formula 1]
In formula 1, T1 is the actual measurement temperature value of the refrigerant of the entrance side of first heat exchange department, and T3 is described
The actual measurement temperature value of the refrigerant of the outlet side of second heat exchange department, T4 are the systems of the entrance side of second heat exchange department
The actual measurement temperature value of cryogen.
[formula 2]
[formula 3]
In the kind of refrigeration cycle of air conditioner for vehicles of the present invention, it is preferable that the calculating part is in the temperature X
The detected value c [DEG C] of the second temperature sensor is used in the presumption of [DEG C], in the calculating of the value of the calculating degree of superheat
Use the detected value b [DEG C] of first temperature sensor.The overheat of the refrigerant of compressor suction can more correctly be estimated
Degree, as a result, being capable of the decline of more reliably rejection coefficient.
Vehicle of the present invention possesses the kind of refrigeration cycle of air conditioner for vehicles of the present invention.Can be not make life
The mode that production property deteriorates, there is provided possess the vehicle of the air conditioner for vehicles of high-performance coefficient.
The effect of invention
The present invention relates to the kind of refrigeration cycle for the air conditioner for vehicles for possessing inner heat exchanger and the vehicle for carrying it, energy
A kind of kind of refrigeration cycle of air conditioner for vehicles for possessing inner heat exchanger is enough provided and carries its vehicle, it can be with not
The decline of the mode rejection coefficient of additional part.
Brief description of the drawings
Fig. 1 is the system diagram of an example of the kind of refrigeration cycle for representing air conditioner for vehicles of the present embodiment.
Fig. 2 is an example of the control process for the valve opening for representing the electric control expansion valve that valve opening control device is carried out
Flow chart.
Embodiment
The form of the present invention is illustrated referring to the drawings.Embodiments described below is the reality of the present invention
Example is applied, the invention is not restricted to following embodiment.It should be noted that the reference in this specification and accompanying drawing corresponds to
During identical composed component, same part is mutually referred to.As long as the effect of the present invention can be realized, you can carry out various form changes
More.
Fig. 1 is the system diagram of an example of the kind of refrigeration cycle for representing air conditioner for vehicles of the present embodiment.
As shown in figure 1, the kind of refrigeration cycle 1 of air conditioner for vehicles of the present embodiment possesses：Refrigerant loop 100, it is utilized
Pipe arrangement 61~66 connects compressor 2, condenser 3, electric control expansion valve 4 and evaporator 5, makes refrigerant circulation；Inner heat exchanger
10, it carries out the heat exchange of refrigerant between the first heat exchange department 11 and the second heat exchange department 12, is exported from condenser 3 to electricity
The cold-producing medium stream of expansion valve 4 is controlled through the first heat exchange department, is exported from evaporator 5 to the cold-producing medium stream warp of the suction side of compressor 2
Second heat exchange department；Pressure sensor 31, it detects the pressure of the refrigerant between condenser 3 and inner heat exchanger 10；The
Either one in one temperature sensor 32 and second temperature sensor 33, the first temperature sensor detect the temperature of evaporator 5
The temperature of degree or air by evaporator 5, second temperature sensor has between evaporator 5 and inner heat exchanger 10 to be surveyed
Fixed point；Valve opening control device 40, its degree of superheat based on the refrigerant between inner heat exchanger 10 and compressor 2, control
The valve opening of electric control expansion valve 4, valve opening control device 40, as the degree of superheat, calculate the degree of superheat using the value for calculating the degree of superheat
Value utilizes either one in the detected value of the first temperature sensor 32 and the detected value of second temperature sensor 33 and pressure
The detected value of sensor 31 is as a parameter to calculate.
Refrigerant loop 100 is to connect compressor 2, condenser 3, electric control expansion valve 4 and evaporator 5 using pipe arrangement 61~66
Loop, refrigerant internally circulates.For example, refrigerant is the freon-type materials such as R134a, HFO-1234yf or dioxy
Change carbon.
Compressor 2 is by the driving force from engine (not shown), or is received through the motor of driven by power and (does not scheme
Show) driving force, compress the refrigerant of the vaporized state of low-temp low-pressure, become the refrigeration of the vaporized state of HTHP
Agent.Compressor 2 can be fixed capacity type or variable capacity type.
Condenser 3 is heat exchanger, for the refrigerant for the vaporized state of HTHP discharged from compressor 2, is passed through
Traveling wind, the wind from cooling fan 7 or both cooled down, become the refrigerant of the liquefaction of HTHP.
Cooling fan 7 can be the special fan of condenser 3, or simultaneously to the radiator of the configuration on the downside of the wind of condenser 3
The fan that (not shown) is cooled down.
Electric control expansion valve 4 makes the refrigerant decompression/expansion condensed by condenser 3, becomes low temperature by throttling action
The vaporific refrigerant (refrigerant of gas-liquid mixed shape) of low pressure, while carry out the adjustment of the flow of refrigerant.
Evaporator 5 is heat exchanger, makes the refrigerant vapor for becoming gas-liquid mixed shape in electric control expansion valve 4, using now
Steam heat, to carrying out cooling and dehumidifying by the wind pushing air of evaporator 5.
Inner heat exchanger 10 is configured on refrigerant loop 100.Inner heat exchanger 10 has the first heat exchange department 11
With the second heat exchange department 12, exported from condenser 3 to the cold-producing medium stream of electric control expansion valve 4 through the first heat exchange department, from evaporator 5
Export to the cold-producing medium stream of the suction side of compressor 2 through the second heat exchange department, flowing through the relatively-high temperature of the first heat exchange department 11
Refrigerant and flow through the second heat exchange department 12 relative low temperature refrigerant between carry out heat exchange.
The heat exchanger effectiveness Elow of inner heat exchanger 10 is each inner heat exchanger each intrinsic value, by following
(formula 1) defines.In formula 1, T1 is the actual measurement temperature value of the refrigerant of the entrance 10a sides of the first heat exchange department 11, and T3 is
The actual measurement temperature value of the refrigerant of the outlet 10d sides of second heat exchange department 12, T4 are the entrance 10c of the second heat exchange department 12
The actual measurement temperature value of the refrigerant of side.For example, before kind of refrigeration cycle 1 is assembled into air conditioner for vehicles, respectively
The entrance 10a of one heat exchange department 11, the outlet 10d of the second heat exchange department 12 and the second heat exchange department 12 entrance 10c set temperature
The measuring point of sensor is spent, determines T1, T3 and T4.
[formula 1]
Pipe arrangement 61 directly or indirectly connects the outlet of compressor 2 and the entrance of condenser 3.Pipe arrangement 62 is directly or indirectly
Connect outlet and the entrance 10a of the first heat exchange department 11 of condenser 3.Pipe arrangement 63 directly or indirectly connects the first heat exchange department
11 outlet 10b and the entrance of electric control expansion valve 4.Pipe arrangement 64 directly or indirectly connects the outlet and evaporation of electric control expansion valve 4
The entrance of device 5.Pipe arrangement 65 directly or indirectly connects outlet and the entrance 10c of the second heat exchange department 12 of evaporator 5.Pipe arrangement 66
Directly or indirectly connect the outlet 10d of the second heat exchange department 12 and the entrance of compressor 2.
Pressure sensor 31 is the device of the pressure for the refrigerant that detection is flowed out from condenser 3, is existing kind of refrigeration cycle
In the device that has set.For example, the measuring point of pressure sensor 31 (is not schemed in a manner of with refrigerant contact installed in mounting hole
Show), the mounting hole is arranged on the refrigerant outlet pipe (not shown) or pipe arrangement 62 of condenser 3.In existing kind of refrigeration cycle, example
Such as, the detected value of pressure sensor 31 is used in the safety device of refrigerant loop 100.More specifically, due to automatically controlled expansion
Failure of valve 4 etc., the refrigerant flowed out from condenser 3 does not flow according to plan, from compressor 2 to the refrigerant of electric control expansion valve 4
When the pressure in loop 100 exceedes setting value, stop the driving of compressor 2, carry out preventing that refrigerant loop 100 is mechanically damaged
Control.In the present embodiment, the detected value of pressure sensor 31 goes back quilt in addition to being used in existing kind of refrigeration cycle
It is used in the control of the valve opening of electric control expansion valve 4.By using the detected value of pressure sensor 31, flowed using from condenser 3
The high-pressure refrigerant energy hole valve opening gone out, it is thus possible to enough consider the internal circulating load of refrigerant and the heat exchange of condenser 3
Amount, can carry out the control of the higher valve opening of precision.
First temperature sensor 32 is the device of the temperature for the temperature or air for passing through evaporator 5 for detecting evaporator 5, is
The device set in existing kind of refrigeration cycle.When first temperature sensor 32 detects the temperature of evaporator 5, for example, the first temperature
The measuring point for spending sensor 32 is arranged on the fin at the position that temperature is minimum in evaporator 5.Moreover, the first temperature sensor 32 is examined
When surveying the temperature by the air of evaporator 5, for example, the measuring point of the first temperature sensor 32 is installed with existing known structure
The downstream space at the minimum position of temperature in evaporator 5.In existing kind of refrigeration cycle, for example, the first temperature sensor
32 detected value is used in the switch control of the compressor 2 of fixed capacity type.More specifically, the temperature of evaporator 5 or passing through
When the temperature of the air of evaporator 5 exceedes setting value, compressor 2, the temperature of evaporator 5 or the air by evaporator 5 are driven
Temperature when being less than setting value, enter to exercise the control of the stopping of compressor 2.Or it is used in the row of the compressor 2 of variable capacity type
Output controls.More specifically, when the temperature of evaporator 5 or the temperature for the air for passing through evaporator 5 exceed setting value, increase compression
When the temperature of the discharge rate of machine 2, the temperature of evaporator 5 or the air for passing through evaporator 5 is less than setting value, enter to exercise compressor 2
Discharge rate reduction control.The measuring point of first temperature sensor 32 is arranged on the position that temperature is minimum in evaporator 5
Purpose is, detects freezing for evaporator 5 earlier.The minimum position of temperature is freezed in refrigerant loop 100 in evaporator 5
The position that the degree of superheat minimum or the degree of superheat of agent are zero.In the present embodiment, the detected value of the first temperature sensor 32 except
It is used in outside existing kind of refrigeration cycle, is also used in the control of the valve opening of electric control expansion valve 4.First temperature sensor
32 detected value is to reflect in-car air themperature and from blower fan to the value of the air output of evaporator 5.Therefore, lead to
The detected value using the first temperature sensor 32 is crossed, in the control of valve opening, additionally it is possible to consider in-car air themperature and
From blower fan to the factor of the air output of evaporator 5, the control of the higher valve opening of precision can be carried out.
Second temperature sensor 33 is the device of the temperature for the refrigerant that detection is flowed out from evaporator 5, is existing refrigeration
The device set in circulation.For example, the measuring point of second temperature sensor 33 is arranged on the system of evaporator 5 in a contact fashion
The periphery of cryogen outlet (not shown) or the periphery of pipe arrangement 65.In existing kind of refrigeration cycle, for example, second temperature sensor
33 detected value is used in the valve opening control of electric control expansion valve 4.More specifically, the valve opening of control electric control expansion valve 4, with
The value of the degree of superheat of the refrigerant outlet for the evaporator 5 for making to be provided with the measuring point of second temperature sensor 33 is changed into desired value.
In the present embodiment, instead of the measuring point that is provided with second temperature sensor 33 evaporator 5 refrigerant outlet overheat
Degree, based on the degree of superheat of the refrigerant between inner heat exchanger 10 and compressor 2, the valve opening of control electric control expansion valve 4.
The detected value of second temperature sensor 33 is more slightly higher than the detected value of the first temperature sensor 32.Second temperature sensor
Internal circulating loads of the poor α according to refrigerant of the detected value of 33 detected value and the first temperature sensor 32, the air-supply by evaporator 5
The temperature or air output of air, the setting position of the first temperature sensor 32 or second temperature sensor 33 or electric control expansion valve 4
Setting value (outflow evaporator 5 refrigerant the degree of superheat target temperature) etc. difference, still, e.g. 2~6 DEG C.
Kind of refrigeration cycle 1 of the present embodiment can possess 33 liang of the first temperature sensor 32 and second temperature sensor
Person, or do not possess either one in the first temperature sensor 32 or second temperature sensor 33.Passed by possessing the first temperature
Both sensor 32 and second temperature sensor 33, can more correctly estimate the degree of superheat.Moreover, passed by not possessing the first temperature
Either one in sensor 32 or second temperature sensor 33, can reduce components number.Do not possess the first temperature sensor 32 or
During either one in second temperature sensor 33, it is preferable that omit second temperature sensor 33.
Preferably, valve opening control device 40 has：The calculating part 41 calculated calculating the degree of superheat；Based on calculating
The valve control unit 42 of the valve opening of temperature adjustment electric control expansion valve 4.Calculate the overheat that the degree of superheat is the refrigerant for sucking compressor 2
The presumed value of degree.Preferably, valve opening control device 40 is equipped on conditioning control unit (not shown), or is equipped on the system of being equipped with
The control unit of engine (not shown) of the vehicle of SAPMAC method 1.Can neatly tackle the design philosophy of vehicle, memory size or
The various key elements such as cost.
Fig. 2 is an example of the control process for the valve opening for representing the electric control expansion valve that valve opening control device is carried out
Flow chart.Preferably, the control process of valve opening has：Estimate the refrigerant between inner heat exchanger 10 and compressor 2
Temperature X [DEG C] process (step S1)；The process (step S2) calculated the value for calculating the degree of superheat；Control the work of valve opening
Sequence (step S3).
(step S1)
In step sl, the calculating part 41 of valve opening control device uses (formula 2) or (formula 3) to calculate inner heat exchanger 10
The temperature X [DEG C] of the refrigerant between compressor 2 presumed value.In formula 2 or formula 3, Elow is to utilize (formula 1) advance
The heat exchanger effectiveness for the inner heat exchanger 10 derived, it is the intrinsic value of inner heat exchanger 10.A [DEG C] is from pressure sensing
The value of the temperature of the detected value conversion of device 31.Because refrigerant is saturation state between condenser 3 and inner heat exchanger 10,
The value of the pressure detected according to pressure sensor 31 uniquely draws temperature a [DEG C].B [DEG C] is the inspection of the first temperature sensor 32
Measured value.C [DEG C] is the detected value of second temperature sensor 33.α [DEG C] is the detected value c [DEG C] and the of second temperature sensor 33
The detected value b [DEG C] of one temperature sensor 32 difference.α [DEG C] is to be based on the first temperature sensor 32 and second temperature sensor 33
The value that calculates of actual measured value, or the internal circulating load based on refrigerant, by the temperature of the wind pushing air of evaporator 5 or send
Setting value (the outflow of air quantity, the setting position of the first temperature sensor 32 or second temperature sensor 33 or electric control expansion valve 4
The presumed value of the calculating such as the target temperature of the degree of superheat of the refrigerant of evaporator 5.In step sl, make in temperature X presumption
During with the detected value b of the first temperature sensor 32, using formula 2.The inspection of second temperature sensor 33 is used in temperature X presumption
During measured value c, using formula 3.
[formula 2]
[formula 3]
(step S2)
In step s 2, the calculating part 41 of valve opening control device uses detected value b [DEG C] or detected value c [DEG C] and temperature
X [DEG C] value, the value for calculating the degree of superheat is calculated.In the present embodiment, the refrigerant saturation temperature of evaporator 5 is subtracted
The calculating degree of superheat is considered as internal heat exchange by the value for going that the refrigerant temperature of compressor 2 will be sucked as the degree of superheat is calculated
The degree of superheat of refrigerant between device 10 and compressor 2.Here, during using detected value b [DEG C], as described above, the first temperature
The refrigerant that sensor 32 detects degree of superheat minimum (or the degree of superheat is zero) in refrigerant loop 100, therefore, by its detected value
B [DEG C] is considered as refrigerant saturation temperature, and during using detected value c [DEG C], (c- α) [DEG C] is considered as into refrigerant saturation temperature.Moreover,
The temperature that compressor 2 will be sucked is the X [DEG C] tried to achieve in step S1.So to calculating the degree of superheat, carried out by formula 4 or formula 5
Calculate.
(formula 4) calculates the degree of superheat=X-b
(formula 5) calculates the degree of superheat=X- (c- α)
(step S3)
In step s3, the valve control unit 42 of valve opening control device 40 is based on the calculating degree of superheat calculated in step S2
Value, control the valve opening of electric control expansion valve 4.
In the kind of refrigeration cycle 1 of air conditioner for vehicles of the present embodiment, it is preferable that calculating part 41 is in temperature X
The detected value c [DEG C] of second temperature sensor 33 is used in the presumption of [DEG C], the is used in the calculating of value of the degree of superheat is calculated
The detected value b [DEG C] of one temperature sensor 32.Due to using formula 3 in temperature X [DEG C] presumption, the value of the degree of superheat is being calculated
Formula 4 is used in calculating, it is not necessary to be modified using correction value α, can more correctly estimate the refrigerant of compressor suction
The degree of superheat, as a result, being capable of the decline of more reliably rejection coefficient.
The kind of refrigeration cycle 1 of air conditioner for vehicles of the present embodiment can estimate the refrigerant for flowing into compressor 2
Energy (degree of superheat), be reflected in the control of the refrigerant flow of expansion valve.In addition, as valve opening control parameter,
Using either one in the detected value of the first temperature sensor 32 and the detected value of second temperature sensor 33 and in the past just
For the detected value of the pressure sensor 31 of air-conditioning device, therefore, it is possible to provide the inhibition in a manner of not additional new part
The air-conditioning device of the decline of energy coefficient.
Vehicle of the present embodiment possesses the kind of refrigeration cycle 1 of air conditioner for vehicles of the present embodiment.Energy
Enough in a manner of deteriorating productivity, there is provided possess the vehicle of the air conditioner for vehicles of high-performance coefficient.
Description of reference numerals
The kind of refrigeration cycle of 1 air conditioner for vehicles
2 compressors
3 condensers
4 electric control expansion valves
5 evaporators
7 cooling fans
10 inner heat exchangers
The entrance of the heat exchange departments of 10a first
The outlet of the heat exchange departments of 10b first
The entrance of the heat exchange departments of 10c second
The outlet of the heat exchange departments of 10d second
11 first heat exchange departments
12 second heat exchange departments
31 pressure sensors
32 first temperature sensors
33 second temperature sensors
40 valve opening control devices
41 calculating parts
42 valve control units
61~66 pipe arrangements
100 refrigerant loops
Claims (4)
1. a kind of kind of refrigeration cycle of air conditioner for vehicles, it is characterised in that possess：
Refrigerant loop, it makes refrigerant circulation using pipe arrangement connection compressor, condenser, electric control expansion valve and evaporator；
Inner heat exchanger, it carries out the heat exchange of the refrigerant between the first heat exchange department and the second heat exchange department, from
The condenser is exported to the cold-producing medium stream of the electric control expansion valve through first heat exchange department, from the evaporator export to
The cold-producing medium stream of the suction side of the compressor is through second heat exchange department；
Pressure sensor, it detects the pressure of the refrigerant between the condenser and the inner heat exchanger；
Either one in first temperature sensor and second temperature sensor, first temperature sensor detect the steaming
The temperature of device or the temperature for the air for passing through the evaporator are sent out, the second temperature sensor is in the evaporator and the inside
There is measuring point between heat exchanger；
Valve opening control device, its overheat based on the refrigerant between the inner heat exchanger and the compressor
Degree, control the valve opening of the electric control expansion valve；
The valve opening control device is utilized using the value for calculating the degree of superheat as the degree of superheat, the value for calculating the degree of superheat
Either one in the detected value of first temperature sensor and the detected value of the second temperature sensor and the pressure
The detected value of force snesor is as a parameter to calculate.
2. the kind of refrigeration cycle of air conditioner for vehicles as claimed in claim 1, it is characterised in that
The valve opening control device has the calculating part calculated the calculating degree of superheat,
The value of the temperature of the refrigerant to be converted according to the detected value of the pressure sensor is set to a [DEG C], by described
The detected value of one temperature sensor is set to b [DEG C], and the detected value of the second temperature sensor is set into c [DEG C], by the inspection
Measured value c and the detected value b difference are set to α [DEG C], will utilize the heat exchange for the inner heat exchanger that (formula 1) derive to imitate
When the value of rate is set to Elow, the calculating part use (formula 2) or (formula 3) estimate described inner heat exchanger and the compressor it
Between the refrigerant temperature X [DEG C], according to the poor or described temperature X of temperature X [DEG C] value and the detected value b [DEG C]
The value of [DEG C] and the difference of (detected value c [DEG C]-α), the value of the calculating degree of superheat is calculated,
[formula 1]
<mrow>
<mi>E</mi>
<mi>l</mi>
<mi>o</mi>
<mi>w</mi>
<mo>=</mo>
<mn>100</mn>
<mo>&times;</mo>
<mfrac>
<mrow>
<mi>T</mi>
<mn>3</mn>
<mo>-</mo>
<mi>T</mi>
<mn>4</mn>
</mrow>
<mrow>
<mi>T</mi>
<mn>1</mn>
<mo>-</mo>
<mi>T</mi>
<mn>4</mn>
</mrow>
</mfrac>
</mrow>
In formula 1, T1 is the actual measurement temperature value of the refrigerant of the entrance side of first heat exchange department, and T3 is described second
The actual measurement temperature value of the refrigerant of the outlet side of heat exchange department, T4 are the refrigerants of the entrance side of second heat exchange department
Actual measurement temperature value,
[formula 2]
<mrow>
<mi>X</mi>
<mo>=</mo>
<mfrac>
<mrow>
<mi>E</mi>
<mi>l</mi>
<mi>o</mi>
<mi>w</mi>
<mo>&times;</mo>
<mo>{</mo>
<mi>a</mi>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mi>b</mi>
<mo>+</mo>
<mi>&alpha;</mi>
<mo>)</mo>
</mrow>
<mo>}</mo>
</mrow>
<mn>100</mn>
</mfrac>
<mo>+</mo>
<mrow>
<mo>(</mo>
<mi>b</mi>
<mo>+</mo>
<mi>&alpha;</mi>
<mo>)</mo>
</mrow>
</mrow>
[formula 3]
<mrow>
<mi>X</mi>
<mo>=</mo>
<mfrac>
<mrow>
<mi>E</mi>
<mi>l</mi>
<mi>o</mi>
<mi>w</mi>
<mo>&times;</mo>
<mrow>
<mo>(</mo>
<mi>a</mi>
<mo>-</mo>
<mi>c</mi>
<mo>)</mo>
</mrow>
</mrow>
<mn>100</mn>
</mfrac>
<mo>+</mo>
<mi>c</mi>
<mo>.</mo>
</mrow>
3. the kind of refrigeration cycle of air conditioner for vehicles as claimed in claim 2, it is characterised in that
The calculating part uses the detected value c [DEG C] of the second temperature sensor in the presumption of the temperature X [DEG C], in institute
State the detected value b [DEG C] that first temperature sensor is used in the calculating for the value for calculating the degree of superheat.
A kind of 4. vehicle, it is characterised in that
Possesses the kind of refrigeration cycle of the air conditioner for vehicles in claims 1 to 3 described in any one.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-225057 | 2015-11-17 | ||
| JP2015225057A JP2017088137A (en) | 2015-11-17 | 2015-11-17 | Refrigeration cycle of vehicular air conditioner and vehicle mounted with the same |
| PCT/JP2016/083960 WO2017086343A1 (en) | 2015-11-17 | 2016-11-16 | Refrigeration cycle for vehicular air-conditioning device, and vehicle equipped therewith |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107848375A true CN107848375A (en) | 2018-03-27 |
Family
ID=58718118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680046683.1A Pending CN107848375A (en) | 2015-11-17 | 2016-11-16 | The kind of refrigeration cycle of air conditioner for vehicles and the vehicle for carrying it |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2017088137A (en) |
| CN (1) | CN107848375A (en) |
| DE (1) | DE112016005264T5 (en) |
| WO (1) | WO2017086343A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112248744A (en) * | 2020-09-30 | 2021-01-22 | 广西玉柴机器股份有限公司 | Control system of vehicle air conditioner |
| CN112440665A (en) * | 2019-08-29 | 2021-03-05 | 法雷奥日本株式会社 | Air conditioner for vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102165062B1 (en) * | 2019-01-08 | 2020-10-13 | 대우조선해양 주식회사 | Temperature Control System And Method Of Insulation Box For Ship |
| DE102020115274A1 (en) * | 2020-06-09 | 2021-12-09 | Stiebel Eltron Gmbh & Co. Kg | Method for operating a compression refrigeration system |
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| JP2001001754A (en) * | 1999-06-24 | 2001-01-09 | Japan Climate Systems Corp | Air conditioner for vehicle |
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| CN102419024A (en) * | 2010-09-24 | 2012-04-18 | 松下电器产业株式会社 | Refrigeration cycle apparatus and hot-water heating apparatus |
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| JPH1163624A (en) * | 1997-08-21 | 1999-03-05 | Matsushita Refrig Co Ltd | Air conditioner |
| JP6136231B2 (en) * | 2012-12-18 | 2017-05-31 | 富士電機株式会社 | Refrigerant flow control device |
-
2015
- 2015-11-17 JP JP2015225057A patent/JP2017088137A/en active Pending
-
2016
- 2016-11-16 CN CN201680046683.1A patent/CN107848375A/en active Pending
- 2016-11-16 DE DE112016005264.2T patent/DE112016005264T5/en not_active Withdrawn
- 2016-11-16 WO PCT/JP2016/083960 patent/WO2017086343A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001001754A (en) * | 1999-06-24 | 2001-01-09 | Japan Climate Systems Corp | Air conditioner for vehicle |
| JP2004061061A (en) * | 2002-07-31 | 2004-02-26 | Matsushita Electric Ind Co Ltd | Freezing cycle device and its operation method |
| JP2008209028A (en) * | 2007-02-23 | 2008-09-11 | Denso Corp | Ejector type refrigeration cycle |
| CN104964496A (en) * | 2007-10-08 | 2015-10-07 | 艾默生环境优化技术有限公司 | System and method for monitoring overheat of a compressor |
| JP2009109157A (en) * | 2007-11-01 | 2009-05-21 | Toyota Industries Corp | Refrigerant circulation circuit |
| CN101842645A (en) * | 2007-11-30 | 2010-09-22 | 三菱电机株式会社 | Refrigeration cycle device |
| CN102419024A (en) * | 2010-09-24 | 2012-04-18 | 松下电器产业株式会社 | Refrigeration cycle apparatus and hot-water heating apparatus |
| CN102410693A (en) * | 2011-12-08 | 2012-04-11 | 合肥美的荣事达电冰箱有限公司 | Refrigerating system of refrigerator, refrigerator provided with same and control method of refrigerator |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112440665A (en) * | 2019-08-29 | 2021-03-05 | 法雷奥日本株式会社 | Air conditioner for vehicle |
| CN112248744A (en) * | 2020-09-30 | 2021-01-22 | 广西玉柴机器股份有限公司 | Control system of vehicle air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2017086343A1 (en) | 2017-05-26 |
| JP2017088137A (en) | 2017-05-25 |
| DE112016005264T5 (en) | 2018-08-02 |
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