Abstract:
A cooling medium circulating apparatus includes first and second flow paths configured to circulate a cooling medium, and a flow path switchover unit for connecting or disconnecting between the first and second flow paths. A method for controlling a cooling medium circulating apparatus includes detecting temperatures of the cooling medium flowing through the flow paths. The method further includes calculating a temperature difference between temperatures of the cooling medium flowing through the first and second flow paths. In the cooling medium circulating apparatus and method, a prescribed cycle is set, and connecting and disconnecting periods are set. The connecting and disconnecting periods are periods for connecting and disconnecting, respectively, between the flow paths in the prescribed cycle. The flow path switchover unit is controlled based on the connecting and disconnecting periods. The prescribed cycle becomes shorter as the temperature difference becomes larger.

Description:
TECHNICAL FIELD 
     The present invention relates to a cooling medium circulating apparatus, an air conditioning apparatus for a vehicle, and a method for controlling a cooling medium circulating apparatus. 
     BACKGROUND ART 
     An air conditioning apparatus is disclosed in JP05-65018A, wherein when an air is heated by means of a heater core by using a cooling water which is used to cool down an engine, a temperature of the heater core is adjusted at around an intended temperature by switchover of a flow path of the cooling water flowing into a heater core by ON/OFF of a valve device with a certain duty ratio. 
     SUMMARY OF INVENTION 
     In the technology mentioned above, the flow path is switched over in such a way that when the valve device is ON, the cooling water may flow into the heater core after it is heated up while going through the engine, whereas when the valve device is OFF, the cooling water may not go through the engine so that it may flow into the heater core without being heated up by the engine. 
     In the air conditioning apparatus as mentioned above, when the state that the cooling water flows into the heater core without going through the engine is switched over to the state that the cooling water heated up by the engine flows into the heater core by means of the valve device, the situation that a temperature difference of the cooling water before and after the switchover of the flow path becomes large can happen. When the temperature difference of the cooling water is large, if the valve device is controlled with the same condition as that of the case that the temperature difference of the cooling water is small, massive amount of the cooling water with the large temperature difference may flow into the heater core whereby increasing the variation of the temperature of the heater core as compared with the case that the temperature difference of the cooling water is small, so that there may be a risk to cause hunting of the air temperature blown out from the air conditioning apparatus. 
     The present invention was made in order to solve the problem as mentioned above; and therefore, an object of the present invention is to suppress the hunting of the air temperature blown out from the air conditioning apparatus. 
     One aspect of the present invention is directed to a cooling medium circulating apparatus. The cooling medium circulating apparatus includes a first flow path configured to circulate a cooling medium, a second flow path configured to circulate the cooling medium, a flow path switchover unit configured to connect or disconnect between the first flow path and the second flow path, a first temperature detecting unit configured to detect a temperature of the cooling medium flowing through the first flow path, a second temperature detecting unit configured to detect a temperature of the cooling medium flowing through the second flow path, a temperature difference calculating unit configured to calculate a temperature difference between the temperature of the cooling medium flowing through the first flow path and the temperature of the cooling medium flowing through the second flow path, a flow path switchover time setting unit configured to set a prescribed cycle, a connecting period and a disconnecting period, the connecting period being a period for connecting between the first flow path and the second flow path in the prescribed cycle, the disconnecting period being a period for disconnecting between the first flow path and the second flow path in the prescribed cycle and a controlling unit configured to control the flow path switchover unit on the basis of the connecting period and the disconnecting period which are set by the flow path switchover time setting unit, and wherein the flow path switchover time setting unit is configured to make the prescribed cycle shorter when the temperature difference is larger. 
     Another aspect of the present invention is directed to a method for controlling a cooling medium circulating apparatus. The cooling medium circulating apparatus includes a first flow path configured to circulate a cooling medium, a second flow path configured to circulate the cooling medium, and a flow path switchover means configured to connect or disconnect between the first flow path and the second flow path. The method includes detecting a temperature of the cooling medium flowing through the first flow path, detecting a temperature of the cooling medium flowing through the second flow path, calculating a temperature difference between the temperature of the cooling medium flowing through the first flow path and the temperature of the cooling medium flowing through the second flow path, setting a prescribed cycle, a connecting period and a disconnecting period, the prescribed cycle being made shorter as the temperature difference is larger, the connecting period being a period for connecting between the first flow path and the second flow path in the prescribed cycle, the disconnecting period being a period for disconnecting between the first flow path and the second flow path in the prescribed cycle, and controlling the flow path switchover means on the basis of the connecting period and the disconnecting period. 
     Other aspect of the present invention is directed to A cooling medium circulating apparatus includes a first flow path and a second flow path configured to circulate a cooling medium, a connecting flow path configured to connect between the first flow path and the second flow path, a valve device capable of disconnecting a flow of the cooling medium in the connecting flow path, a first temperature sensor arranged in the first flow path, and a second temperature sensor arranged in the second flow path, wherein the valve device is configured to repeatedly connect or disconnect the cooling medium flow in the connecting flow path with a prescribed cycle, and the prescribed cycle is shorter as a temperature difference between a temperature of the cooling medium flowing through the first flow path and a temperature of the cooling medium flowing through the second flow path is larger. 
     According to these aspects, the prescribed cycle is made shorter as the temperature difference between the temperature of the cooling medium flowing through the first flow path and the temperature of the cooling medium flowing through the second flow path is larger. Thereby, massive flow of the cooling medium with a large temperature difference into the first flow path can be suppressed, so that hunting of the temperature of the cooling medium flowing through the first flow path can be suppressed. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a block diagram of a system of an air conditioning apparatus of an electrically driven vehicle in a first embodiment, 
         FIG. 2  is a flow chart showing an air control in the first embodiment, 
         FIG. 3  is a map showing a relationship between a deviation and a basic cycle, 
         FIG. 4  is a figure showing a relationship among a target blowing-out temperature, a temperature of a second cooling water at an exit of a radiator, a temperature of the second cooling water flowing into a heater core, a connecting period ratio, and a disconnecting period ratio, 
         FIG. 5  is a block diagram of a system of an air conditioning apparatus of an electrically driven vehicle in a second embodiment, 
         FIG. 6  is a flow chart showing an air control in the second embodiment, 
         FIG. 7  is a map showing a relationship between a maximum flow rate and an amended cycle. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Hereunder, the air conditioning apparatus  1  in the first embodiment of the present invention will be explained with referring to the drawings.  FIG. 1  is the block diagram of the system of the air conditioning apparatus  1  of an electrically driven vehicle. 
     The air conditioning apparatus  1  is comprised of the cooling medium cycle  2  through which a cooling medium circulates, the low-temperature water cycle  3  through which a first cooling water circulates, the high-temperature water cycle  4  through which a second cooling water (cooling medium) circulates, and the controller  5 . The first cooling water and the second cooling water are composed of for example, a non-freezing solution. 
     The cooling medium cycle  2  is comprised of the compressor  10 , the condenser  11 , the evaporator  12 , the cooling medium-water heat exchanger  13 , the first electromagnetic valve  14 , the first expansion valve  15 , the second electromagnetic valve  16 , and the second expansion valve  17 . 
     The compressor  10  pressurizes the cooling medium to make it a high temperature and high pressure gas. The compressor  10  is driven by the electric power supplied from the battery  20  mentioned later. 
     The condenser  11  exchanges the heat between the cooling medium pressurized by the compressor  10  and the second cooling water circulating the high-temperature cycle  4  to cool down the cooling medium whereby heating up the second cooling water. By so doing, the cooling medium is liquefied. 
     The evaporator  12  evaporates the cooling medium which is cooled down by the condenser  11 . During the time when the cooling medium is evaporated, an air outside the evaporator  12  is cooled down. The cooling medium which is made to the gas by the evaporator  12  is pressurized again by the compressor  10 . The air which is cooled down by the evaporator  12  is used in the air conditioning of the vehicle during a cooling (drying) mode. 
     The first expansion valve  15  is a temperature-type expansion valve and has a temperature-perceiving cylindrical tube at the exit side of the evaporator  12  (not shown by the drawing), wherein the opening degree thereof is controlled in accordance with the superheat (degree of superheat of the cooling medium) at the exit side of the evaporator  12  in such a way that the cooling medium may be ejected into the evaporator  12  in accordance with the opening degree. 
     The first electromagnetic valve  14  opens or closes on the basis of the signal from the controller  5 . 
     The cooling medium-water heat exchanger  13  evaporates the cooling medium which is cooled down by the condenser  11  by the heat of the first cooling water. The first cooling water flows inside the cooling medium-water heat exchanger  13 , and the first cooling water is cooled down when the cooling medium is evaporated. The cooling medium which becomes a gas by the cooling medium-water heat exchanger  13  is pressurized again by the compressor  10 . 
     The second expansion valve  17  is a temperature-type expansion valve and has a temperature-perceiving cylindrical tube at the exit side of the cooling medium-water heat exchanger  13  (not shown by the drawing); and the opening degree thereof is controlled in accordance with the superheat at the exit side of the cooling medium-water heat exchanger  13  in such a way that the cooling medium may be ejected into the cooling medium-water heat exchanger  13  in accordance with the opening degree. 
     The second electromagnetic valve  16  opens or closes on the basis of the signal from the controller  5 . 
     The second electromagnetic valve  16 , the second expansion valve  17 , and the cooling medium-water heat exchanger  13  are arranged in parallel to the first electromagnetic valve  14 , the first expansion valve  15 , and the evaporator  12 . 
     The low-temperature water cycle  3  is comprised of the battery  20 , the cooling medium-water heat exchanger  13 , and the first water pump  21 . 
     The first water pump  21  circulates the first cooling water through the battery  20  and the cooling medium-water heat exchanger  13  in this order. The ejection amount of the first water pump  21  is determined on the basis of the signal from the controller  5 . Meanwhile, the flow rate of the first water pump  21  may be changed with plural stages in such a way that the flow rate of the first cooling water may be increased as the stage becomes larger. 
     The battery  20  is the secondary battery to supply the electric power to the motor  38  etc. of the electrically driven vehicle, wherein heat is generated during it is charged and discharged. The battery  20  is cooled down by the first cooling water which is circulating by the first water pump  21 . 
     The first cooling water whose temperature is raised by cooling down the battery  20  flows inside the cooling medium-water heat exchanger  13 , and the heat thereof is absorbed when the cooling medium is evaporated by the cooling medium-water heat exchanger  13 , so that the temperature thereof is lowered. 
     The high-temperature water cycle  4  is comprised of the first cycle  7 , the second cycle  8 , the connecting flow path  32 , and the three-way valve  30 . The first cycle  7  and the second cycle  8  are connected by the connecting flow path  32 , wherein the first cycle  7  and the second cycle  8  become connected or disconnected by switchover of the three-way valve  30 . 
     The first cycle  7  is comprised of the condenser  11 , the main heater  33 , the heater core  34 , the second water pump  35 , and the first flow path  36 . 
     The first flow path  36  is made up such that the second cooling water may flow through the second water pump  35 , the condenser  11 , the main heater  33 , and the heater core  34  in this order. 
     The main heater  33  warms up the second cooling water by the heat generated by the electric power supplied from the battery  20 . 
     The heater core  34  undergoes a heat exchange with the cooling medium by the condenser  11 ; and thereafter, a heat exchange is made between the second cooling water whose temperature is raised by heating with the main heater  33  and the air around the heater core  34 , so that the air may be warmed up. The air which is warmed up by the heater core  34  is used for air conditioning of the cabin during a warming mode. When warming is OFF, the air mix door  42  prohibits the air from hitting the heater core  34 , so that warming-up of the air may be prohibited. Meanwhile, a by-pass flow path may be arranged such that the air may by-pass the heater core  34 . 
     The second water pump  35  is driven by the electric power supplied from the battery  20 , wherein the rotation speed thereof is constant while it is driven so that the flow rate thereof may be constant. When the first cycle  7  and the second cycle  8  are disconnected by the three-way valve  30 , the second water pump  35  circulates the second cooling water through the condenser  11 , the main heater  33 , and the heater core  34  in this order. When the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 , the second water pump  35  lets the second cooling water flow into the radiator  37  to cool down the second cooling water. 
     The second cycle  8  is comprised of the radiator  37 , the motor  38 , the inverter  39 , the third water pump  40 , and the second flow path  41 . 
     The second flow path  41  is made up such that the second cooling water may flow through the third water pump  40 , the inverter  39 , the motor  38 , and the radiator  37  in this order. 
     The radiator  37  undergoes the heat exchange between the flowing outside air and the second cooling water to cool down the second cooling water. 
     The inverter  39  transforms between the direct current and the alternate current with each other; and it controls the electric power supplied to the motor  38  from the battery  20  or the electric power supplied to the battery  20  from the motor  38 . The inverter  39  is cooled down by the second cooling water. 
     The motor  38  is the three-phase AC motor which functions as an electric motor by the electric power supplied from the battery  20 , and functions as a dynamo during such a time as deceleration of the vehicle. The motor  38  is cooled down by the second cooling water. 
     The third water pump  40  is driven by the electric power supplied from the battery  20 , wherein the rotation speed thereof is constant while it is driven so that the flow rate thereof may be constant while it is driven. When the first cycle  7  and the second cycle  8  are disconnected by the three-way valve  30 , the third water pump  40  circulates the second cooling water through the inverter  39 , the motor  38 , and the radiator  37  in this order. When the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 , the third water pump  40  lets the second cooling water flow into the heater core  34 . 
     The three-way valve  30  switches over the flow paths on the basis of a basic cycle, a connecting period, and a disconnecting period, so that the first cycle  7  and the second circle  8  may be connected or disconnected. 
     The controller  5  is comprised of main memory devices such as CPU and RAM as well as a memory medium memorized with a program which can be read out by a computer. When CPU reads out the program memorized in the memory medium and executes it, each function of the controller  5  is expressed. The memory medium which can be read out by a computer means a magnetic disk, an optical magnetic disk, CD-ROM, DVD-ROM, a semiconductor memory, and the like. 
     The controller  5  controls the three-way valve  30  on the basis of the signal from the first temperature sensor  50  for detection of the outside temperature and the signal from the second temperature sensor  51  for detection of the temperature of the cooling medium flowing into the heater core  34 . 
     The first temperature sensor  50  is arranged between the front grill and the radiator  37 . The second temperature sensor  51  is arranged between the main heater  33  and the heater core  34 . 
     Next, the air control in the first embodiment will be explained by using the flow char of  FIG. 2 . 
     In the step S 100 , the controller  5  detects the outside temperature on the basis of the signal from the first temperature sensor  50  and estimates the temperature of the second cooling water at the exit of the radiator  37  on the basis of the outside temperature. 
     In the step S 101 , the controller  5  detects the temperature of the second cooling water flowing into the heater core  34  on the basis of the signal from the second temperature sensor  51 . 
     In the step S 102 , the controller  5  calculates the deviation between the temperature of the second cooling water flowing into the heater core  34  and the temperature of the second cooling water at the exit of the radiator  37 . 
     In the step S 103 , on the basis of the deviation the controller  5  calculates the basic cycle (prescribed cycle) from the map in  FIG. 3 .  FIG. 3  is the map showing the relationship between the deviation and the basic cycle. The basic cycle becomes shorter when the deviation becomes larger; and it becomes the lower limit when the deviation becomes more than a certain prescribed value. The lower limit thereof is set on the basis of the motion guarantee of the three-way valve  30 . Meanwhile, this basic cycle means the cycle when the disconnecting motion (disconnection between the first flow path  36  and the second flow path  41 ) and the connecting motion (connection between the first flow path  36  and the second flow path  41 ) are repeated in the three-way valve  30 . 
     In the step S 104 , the controller  5  calculates the connecting period ratio and the disconnecting period ratio from the map of  FIG. 4  on the basis of the temperature of the second cooling water at the exit of the radiator  37 , the temperature of the second cooling water flowing into the heater core  34 , and the target blowing-out temperature of the air conditioning apparatus  1 .  FIG. 4  shows the relationship among the target blowing-out temperature, the temperature of the second cooling water at the exit of the radiator  37 , the temperature of the second cooling water flowing into the heater core  34 , the connecting period ratio, and the disconnecting period ratio. When the temperature of the second cooling water flowing into the heater core  34  is higher than the target blowing-out temperature, as the temperature of the second cooling water flowing into the heater core  34  is getting closer to the target blowing-out temperature, the connecting period ratio becomes lower and the disconnecting period ratio becomes higher. Meanwhile, when the target blowing-out temperature is equal to or lower than the temperature of the second cooling water at the exit of the radiator  37 , the disconnecting period ratio becomes zero; and when the target blowing-out temperature is equal to or higher than the temperature of the second cooling water flowing into the heater core  34 , the connecting period ratio becomes zero. 
     In the step S 105 , the controller  5  calculates the connecting period and the disconnecting period on the basis of the basic cycle, the connecting period ratio, and the disconnecting period ratio. The controller  5  calculates the connecting period and the disconnecting period by portioning out the basic cycle in accordance with the connecting period ratio and the disconnecting period ratio. When the basic cycle becomes longer in a certain connecting period ratio and disconnecting period ratio, each of the connecting period and the disconnecting period becomes longer. When the connecting period ratio becomes higher in a certain basic cycle, the connecting period becomes longer. Specifically, in a certain basic cycle, when the temperature of the second cooling water flowing into the heater core  34  is higher than the target blowing-out temperature, as the temperature of the second cooling water flowing into the heater core  34  is getting closer to the target blowing-out temperature, the connecting period becomes shorter and the disconnecting period becomes longer. 
     As discussed above, the controller  5  calculates the basic cycle on the basis of the deviation, so that the connecting period and the disconnecting period in this calculated basic cycle may be calculated. 
     In the step S 106 , the controller  5  switches over the three-way valve  30  on the basis of the basic cycle, the connecting period, and the disconnecting period. By so doing, in the basic cycle, after the first cycle  7  and the second cycle  8  are connected during the connecting period whereby flowing the second cooling water which is cooled down by the radiator  37  into the heater core  34 , the first cycle  7  and the second cycle  8  are disconnected by the three-way valve  30  during the disconnecting period. 
     The effects of the first embodiment of the present invention will be explained. 
     As the deviation between the temperature of the second cooling water flowing into the heater core  34  and the temperature of the second cooling water at the exit of the radiator  37  is getting larger, the basic cycle is made shorter. By so doing, when the second cooling water which is cooled down by the radiator  37  flows into the heater core  34 , massive flow of the second cooling water which is cooled down by the radiator  37  into the heater core  34  can be suppressed, so that hunting of the blowing-out temperature of the air which is warmed up by the heater core  34  against the target blowing-out temperature can be suppressed. In addition, as the deviation between the temperature of the second cooling water flowing into the heater core  34  and the temperature of the second cooling water at the exit of the radiator  37  is getting smaller, the basic cycle is made longer. By so doing, number of switchover of the three-way valve  30  can be reduced, so that durability of the three-way valve  30  can be enhanced. 
     When the temperature of the second cooling water flowing into the heater core  34  is higher than the target blowing-out temperature, as the temperature of the second cooling water flowing into the heater core  34  is getting closer to the target blowing-out temperature, the connecting period becomes shorter and the disconnecting period becomes longer. When the temperature of the second cooling water flowing into the heater core  34  comes close to the target blowing temperature, by decreasing the flow rate of the second cooling water flowing into the heater core  34 , the second cooling water being cooled down by the radiator  37 , the blowing-out temperature of the air which is warmed up by the heater core  34  can be made to come close to the target blowing-out temperature. 
     By estimating the temperature of the second cooling water at the exit of the radiator  37  on the basis of the signal from the first temperature sensor  50  capable of detecting the outside air temperature, the temperature of the second cooling water at the exit of the radiator  37  can be detected by using an existing temperature sensor without newly installing a temperature sensor. 
     By detecting the temperature of the second cooling water immediately before flowing into the heater core  34  by using the second temperature sensor  51 , the temperature of the heater core  34  can be detected correctly. 
     Next, the second embodiment of the present invention will be explained with referring to  FIG. 5 . 
       FIG. 5  is the block diagram of the system of the air conditioning apparatus  1  of an electrically driven vehicle of the second embodiment. Here, mainly the items different from those of the first embodiment will be explained. 
     The air conditioning apparatus  1  of the second embodiment is provided with the flow rate sensor  52 . The flow rate sensor  52  is installed at the place where detection of the flow rate of the second cooling water flowing into the heater core  34  becomes possible when the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 . Specifically, the flow rate sensor  52  is installed between the main heater  33  and the condenser  11 . 
     The controller  5  controls the three-way valve  30  on the basis of the signal from the first temperature sensor  50 , the signal from the second temperature sensor  51 , and the signal from the flow rate sensor  52 . 
     The third water pump  40  can change the rotation speed thereof in accordance with the load of the motor  38  etc., so that the flow rate of the second cooling water can be changed. 
     Next, control of the air conditioning in the second embodiment will be explained by using the flow chart shown in  FIG. 6 . 
     Controls from the step S 200  to the step S 203  are the same as the controls from the step S 100  to the step S 103  in the first embodiment; and therefore, the explanation thereof is omitted here. 
     In the step S 204 , the controller  5  calculates the amended cycle from the map of  FIG. 7  on the basis of the memorized maximum flow rate. The maximum flow rate is the maximum flow rate during the previous control when the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 .  FIG. 7  is the map showing the relationship between the maximum flow rate and the amended cycle. The amended cycle becomes longer as the maximum flow rate becomes higher. 
     In the step S 205 , the controller  5  subtracts the amended cycle from the basic cycle thereby calculating the final cycle (prescribed cycle). The longer the amended cycle is, namely, the higher the maximum flow rate is, the shorter the final cycle becomes. When the first cycle  7  and the second cycle  8  are connected and the flow rate of the second cooling water flowing into the heater core  34  is higher, the time for the second cooling water whose temperature is lowered by the radiator  37  to reach the heater core  34  becomes shorter. Because of this, the temperature change of the heater core  34  becomes larger. Accordingly, the final cycle is made shorter when the maximum flow rate is higher. 
     In the step S 206 , the controller  5  calculates the connecting period ratio and the disconnecting period ratio from the map of  FIG. 4  on the basis of the temperature of the second cooling water at the exit of the radiator  37 , the temperature of the second cooling water flowing into the heater core  34 , and the target blowing-out temperature. 
     In the step S 207 , the controller  5  calculates the connecting period and the disconnecting period on the basis of the final cycle, the connecting period ratio, and the disconnecting period ratio. 
     In the step S 208 , the controller  5  switches over the three-way valve  30  on the basis of the final cycle, the connecting period, and the disconnecting period. 
     In the step S 209 , in the case that the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 , the controller  5  detects the flow rate of the second cooling water flowing into the heater core  34  on the basis of the signal from the flow rate sensor  52  and memorizes the maximum flow rate. This memorized maximum flow rate is used in the next control. Meanwhile, when the maximum flow rate is newly calculated, the memorized maximum flow rate is deleted. 
     Next, the effects of the second embodiment will be explained. 
     In the case that the first cycle  7  and the second cycle  8  are connected, the higher the maximum flow rate of the second cooling water flowing into the heater core  34  is, the shorter the final cycle is made. By so doing, the flow rate of the second cooling water cooled down by the radiator  37  during the final cycle and flowing into the heater core  34  can be made lower; and as a result, the hunting of the blowing-out temperature of the air against the target blowing-out temperature can be suppressed. Especially, lowering of the blowing-out temperature of the air against the target blowing-out temperature can be suppressed. 
     The embodiments of the present invention has been explained in the above, wherein the above-mentioned embodiments show merely a part of the application examples of the present invention; and therefore, this does not mean that the technical scope of the present invention is limited to the specific composition of these embodiments. 
     In the second embodiment, the amended cycle is calculated by using the maximum flow rate when the first cycle  7  and the second cycle  8  were connected by the three-way valve  30  in the previous control; however, the amended cycle may be calculated by estimating the flow rate of the third water pump  40  from the load of the motor  38  and so forth whereby estimating the maximum flow rate when the first cycle  7  and the second cycle  8  are connected by the three-way valve  30 . 
     In the second embodiment, the flow rate of the third water pump  40  was made variable; however, the flow rate of the second water pump  35  may be made variable, or the flow rate of the second water pump  35  as well as the flow rate of the third water pump  40  may be made variable. 
     In the second embodiment, the amended cycle was calculated on the basis of the maximum flow rate; however, by calculating the average flow rate, the amended cycle may be calculated on the basis of this average flow rate. 
     There may be a difference in the flow rate of the second cooling water depending on the type of the vehicles. In this case, the basic cycle of the air conditioning apparatus for the basic electrically driven vehicle is established; and then, in the case that the flow rate of the second cooling water is different from that of the basic air conditioning apparatus, the amended cycle for each air conditioning apparatus may be established by the way used in the second embodiment, whereby the final cycle suitable for each air conditioning apparatus may be set. 
     In the above-mentioned embodiments, the air conditioning apparatus  1  of an electrically driven vehicle has been explained; however, this may be applied to the air conditioning apparatus of a hybrid vehicle as well. 
     In the above-mentioned embodiments, explanation has been made by using the three-way valve  30 ; however, two control valves in place of one three-way valve  30  may be used, wherein the first cycle  7  and the second cycle  8  may be connected and disconnected by controlling these two control valves. 
     In the above-mentioned embodiments, the temperature of the second cooling water at the exit of the radiator  37  was estimated from the outside air temperature; however, the temperature of the second cooling water at the exit of the radiator  37  may be detected by a temperature sensor. 
     In the above-mentioned embodiments, the cooling medium cycle  2 , the low-temperature water cycle  3 , and the high-temperature water cycle  4  were controlled by one controller  5 ; however, different controllers may be used for these controls. 
     In the low-temperature water cycle  3 , not limiting to the first cooling water, any cooling medium regardless of a liquid and a gaseous medium may be used. In addition, in the high-temperature water cycle  4 , not limiting to the second cooling water, a liquid and a gaseous medium may be used. 
     This application claims priority from Japanese Patent Application No. 2013-7787, filed Jan. 18, 2013, which is incorporated herein by reference in its entirety.