JP2009044896A - Cooling system for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cooling system in which a refrigerant better in temperature transport efficiency is used, refrigerant piping is simple and short, and piping efficiency is better, and moreover, a plurality of heat sources to be cooled are cooled as required, without being excess and deficiency. <P>SOLUTION: The refrigerant flows to the heat sources 1, 2 to be cooled, through a pipeline 5 by a pump 4 under control of a flow-rate distribution control valve 6 after cooled by a radiator 3, then flows through the heat sources 1, 2 to cool the heat sources, and returns to the radiator 3, wherein a capsule involving a heat-accumulating material is contained in the refrigerant. A fan 3f is driven so that temperature Trout of an outlet of the refrigerant of the radiator 3 may become the temperature at which coagulation of the heat accumulating material finishes. The valve 6 is operated so that a refrigerant flow rate of the heat source 1 (2) with a high-cooling load may be increased, while the refrigerant flow rate of the heat source 2 (1) with low cooling load may be reduced; then the heat sources 1, 2 are cooled as exactly according to each required cooling load. When both the temperature Tw1out, Tw2out of the outlet of the refrigerant of the heat sources are lower than the temperature of finishing of the melting of the heat-accumulating material, a refrigerant circulation amount by the pump 4 is reduced; while conversely, when both the temperature Tw1out, Tw2out are the same or higher than the temperature of finishing of the melting of the heat-accumulating material, the circulation amount by the pump 4 is increased. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  As in the motor cooling system of a two-motor hybrid vehicle, the present invention has a plurality of cooling target heat sources to be cooled, and the plurality of cooling target heat sources and the radiator are circulated with a single common pump. It is related with the cooling device for vehicles which cooled the said some cooling object heat source by doing.

In such a vehicular cooling device, a refrigerant cooled by a radiator is directed to a plurality of heat sources to be cooled by a common pump through individual supply pipes, and passes through each heat source in a heat exchange relationship. In general, the cooled refrigerant is returned to the radiator through individual return pipes.
By the way, since piping of such a general vehicle cooling device requires refrigerant piping for each of a plurality of cooling target heat sources, there has been a problem that the piping layout of the cooling system becomes complicated.
Further, the cooling loads of the plurality of cooling target heat sources change variously according to the driving conditions and driving conditions of the vehicle, and the cooling target heat sources cannot be cooled without excess or deficiency according to individual requirements. There was also a problem.

  Therefore, conventionally, as described in Patent Document 1, for example, a refrigerant pipe in which a plurality of cooling target heat sources are in a parallel relationship with each other, a refrigerant supply line extending between the cooling target heat sources, and a refrigerant return A vehicular cooling device has been proposed in which a flow control valve is inserted in the pipe, the refrigerant supply pipe is connected to the refrigerant outlet of the radiator via a pump, and the refrigerant return pipe is connected to the refrigerant inlet of the radiator. .

  This vehicle cooling device can cool a plurality of cooling target heat sources in accordance with individual required cooling loads by operating the flow rate control valves in the refrigerant supply line and the refrigerant return line.

Conventionally, as a technique for cooling the heat source to be cooled according to the required cooling load without excess or deficiency, for example, as described in Patent Document 2, an auxiliary pump is provided, and the refrigerant supply amount according to the cooling load is provided by this auxiliary pump. Techniques to make it easier have also been proposed.
JP 2006-219083 A Japanese Patent Laid-Open No. 2004-1000095

  However, the vehicle cooling device described in Patent Document 1 can cool a plurality of cooling target heat sources without excess or deficiency according to each required cooling load by operating the flow control valve as described above. Since the cooling target heat sources are refrigerant pipes that are in parallel with each other, the refrigerant pipes are complicated and long, and flow control valves are inserted in both the refrigerant supply line and the refrigerant return line. Therefore, it was disadvantageous in terms of cost.

As a measure for shortening the refrigerant pipe, it is conceivable to use a refrigerant pipe in which a plurality of heat sources to be cooled are in series with each other.
However, in this case, although the refrigerant piping itself is efficient, a low-temperature refrigerant flows through the heat source to be cooled on the upstream side, and a refrigerant having a relatively high temperature after absorbing heat by the flow is cooled on the downstream side. Since the cooling target heat source is excessively cooled because it flows to the target heat source, and the refrigerant circulation amount is reduced to avoid this, the cooling target heat source on the downstream side tends to be insufficiently cooled. This causes another problem that the heat source to be cooled cannot be cooled in accordance with the individual required cooling load.

  Further, regardless of whether the above-described parallel piping type cooling device or series piping type cooling device is used, conventionally, the temperature transport efficiency by the refrigerant is poor, and an improvement related thereto has been desired.

The present invention first uses a refrigerant capable of improving the temperature transport efficiency by the refrigerant, and then,
The above-mentioned parallel piping type cooling device has been improved so that the above-mentioned problem is solved,
An object of the present invention is to improve the above-described series-pipe cooling device so as to eliminate the above-mentioned problems.

In order to achieve the above object with respect to the parallel pipe type cooling device, the vehicle cooling device of the present invention is configured as described in claim 1.
First, the vehicular cooling device that is the premise of the present invention is:
There are a plurality of cooling target heat sources to be cooled, and the plurality of cooling target heat sources are cooled by circulating a refrigerant with a common pump through the cooling target heat sources and the radiator. It is.

In the present invention, the refrigerant used in such a vehicular cooling device is as follows.
That is, a refrigerant in which a microscale heat storage capsule containing a heat storage material is mixed is used.
Then, the refrigerant cooled by the radiator is directed to a plurality of cooling target heat sources under the control of the flow distribution control valve by the common single pump, and the refrigerant after flowing through the cooling target heat sources is supplied to the radiator. The piping configuration is set back to.

The control mode is configured to control the refrigerant circulation amount by the pump and the flow distribution to the cooling target heat source by the flow distribution control valve according to the cooling load of the plurality of cooling target heat sources,
The radiator cooling fan is driven and controlled so that the amount of ventilation to the radiator is such that the refrigerant temperature at the refrigerant outlet of the radiator becomes the solidification end temperature of the heat storage material.

In order to achieve the above-described object with respect to the serial piping type cooling device, the vehicular cooling device of the present invention is configured as described in claim 10.
First, the vehicular cooling device that is the premise of the present invention is:
There are a plurality of cooling target heat sources to be cooled, and the plurality of cooling target heat sources are cooled by circulating a refrigerant with a common pump through the cooling target heat sources and the radiator. It is.

In the present invention, the refrigerant used in such a vehicular cooling device is as follows.
That is, a refrigerant in which a microscale heat storage capsule containing a heat storage material is mixed is used.
Then, the refrigerant cooled by the radiator is directed to a certain cooling target heat source among the plurality of cooling target heat sources by the common one pump, and the refrigerant inlet and the refrigerant of the certain cooling target heat source To the bypass pipe with a flow rate control valve that bypasses between the outlets, the refrigerant after flowing through the certain cooling target heat source is merged with the refrigerant from the bypass pipe and directed to another cooling target heat source, The piping configuration is such that the refrigerant after flowing through the other heat source to be cooled is returned to the radiator.

About the control mode, it is configured to perform branch flow control to the bypass pipe by the flow control valve according to the cooling load of the plurality of cooling target heat sources,
The refrigerant circulation amount by the pump is controlled so that the refrigerant temperature at the refrigerant outlet of the other heat source to be cooled becomes the melting end temperature of the heat storage material.

In the vehicle cooling device according to claim 1,
Since the refrigerant in which the heat storage capsule is mixed is used, heat can be efficiently transported by the heat storage effect of the heat storage material, and the circulation amount of the refrigerant by the pump can be reduced by that amount, and the heat source to be cooled It is possible to improve the cooling efficiency.

Also, the refrigerant cooled by the radiator is directed to a plurality of cooling target heat sources under the control of the flow distribution control valve by a common pump, and the refrigerant after flowing through these cooling target heat sources is returned to the radiator. Because the piping configuration is
By operating the flow rate distribution control valve, it is possible to determine distribution of refrigerant flow to a plurality of cooling target heat sources, and it is possible to cool these cooling target heat sources without excess or deficiency according to individual required cooling loads.

  Moreover, in order to achieve the above-described effects, the flow rate distribution control valve need only be provided at the branching point of the piping that distributes the refrigerant flow from the pump to a plurality of heat sources to be cooled. The above-described effects can be achieved without adding or installing an auxiliary pump, which is advantageous in terms of cost, and can solve the above-described problem of the parallel-pipe cooling device related to cost.

In the control, according to the cooling load of the plurality of cooling target heat sources, the refrigerant circulation amount by the pump and the flow distribution to the cooling target heat source by the flow distribution control valve are controlled,
In order to drive and control the radiator cooling fan so that the air flow rate to the radiator is the air flow rate so that the refrigerant temperature at the refrigerant outlet of the radiator becomes the solidification end temperature of the heat storage material,
Refrigerant flow distribution to a plurality of cooling target heat sources is made according to individual cooling loads, and these cooling target heat sources can be cooled without excess or deficiency according to individual required cooling loads, and a plurality of cooling sources can be cooled. The target heat source is neither overcooled nor undercooled.

In the vehicle cooling device according to claim 10,
Since the refrigerant in which the heat storage capsule is mixed is used, heat can be efficiently transported by the heat storage effect of the heat storage material, and the circulation amount of the refrigerant by the pump can be reduced by that amount, and the heat source to be cooled In addition to the same effect as described above, it is possible to achieve the following effects.

That is, the refrigerant cooled by the radiator is directed to a certain cooling target heat source among the plurality of cooling target heat sources by the common single pump, and the refrigerant inlet and the refrigerant outlet of the certain cooling target heat source To the bypass pipe with a flow rate control valve that bypasses between them, the refrigerant that has passed through the certain cooling target heat source is merged with the refrigerant from the bypass pipe and directed to another cooling target heat source, In order to make a piping configuration that returns the refrigerant after flowing to another heat source to be cooled to the radiator,
It becomes a serial piping type cooling device, the refrigerant piping is shorter than the parallel piping type cooling device, and the piping efficiency can be increased.

In the control, according to the cooling load of the plurality of cooling target heat sources, the branch flow rate control to the bypass line by the flow rate control valve is performed,
In order to control the refrigerant circulation amount by the pump so that the refrigerant temperature at the refrigerant outlet of the other cooling target heat source becomes the melting end temperature of the heat storage material,
The upstream cooling target heat source is not cooled excessively, and the downstream cooling target heat source is not undercooled, and multiple cooling target heat sources can be cooled according to individual required cooling loads. In addition, it is possible to solve the problems of the conventional serial piping cooling device, and the plurality of cooling target heat sources are not excessively cooled or insufficiently cooled.

Hereinafter, embodiments of the present invention will be described in detail based on the embodiments shown in the drawings.
FIG. 1 shows a vehicular cooling apparatus according to an embodiment of the present invention, and reference numerals 1 and 2 denote cooling target heat sources to be cooled.
These cooling heat sources 1 and 2 are, for example, two motors of a two-motor hybrid vehicle, an engine and an automatic transmission, or a plurality (two in the illustrated example) of arbitrary heat sources to be cooled.

  These cooling target heat sources 1 and 2 are cooled by passing the refrigerant cooled by the radiator 3 in a heat exchange relationship by a common pump 4 and returning the refrigerant to the radiator 3 after passing through the refrigerant. It is assumed that the cooling is performed by the cooling air composed of the forced air generated by the fan 3f and the vehicle traveling air, and again used for cooling the heat sources 1 and 2 to be cooled.

In the present embodiment, the piping configuration for circulating the refrigerant as described above is a parallel piping type in which the heat sources 1 and 2 to be cooled have a parallel relationship as follows.
One end of the refrigerant supply pipe 5 in which the one common pump 4 is inserted is connected to the refrigerant outlet 3a of the radiator 3, and the other end of the refrigerant supply pipe 5 is connected through the flow distribution control valve 6. Connect to two branch lines 7,8.
One branch pipe 7 is connected to the refrigerant inlet 1a of the heat source 1 to be cooled, and the other branch pipe 8 is connected to the refrigerant inlet 2a of the heat source 2 to be cooled.
The refrigerant outlets 1b and 2b of the heat sources 1 and 2 to be cooled are communicated with each other through a communication line 9, and the communication line 9 and the refrigerant inlet 3b of the radiator 3 are communicated with each other through a refrigerant return line 10.

Thus, the refrigerant cooled by the radiator 3 is supplied to the flow distribution control valve 6 through the pipeline 5 by the common single pump 4, and the flow distribution control valve 6 distributes the supplied refrigerant according to the command. Then, it goes to the heat sources 1 and 2 to be cooled via the branch pipes 7 and 8.
Thereafter, the refrigerant flows through the cooling target heat sources 1 and 2, and the cooling target heat sources 1 and 2 are cooled by heat exchange during this period.
The refrigerant that has flowed through the heat sources 1 and 2 to be cooled and has risen in temperature due to the heat exchange described above is returned to the refrigerant inlet 3b of the radiator 3 through the connecting line 9 and the refrigerant return line 10, and is cooled by the radiator 3. Goes out from the refrigerant outlet 3b again and is used for cooling the heat sources 1 and 2 to be cooled.

By the way, in the present embodiment, the above refrigerant is particularly as follows.
That is, as shown in FIG. 2, a refrigerant in which a microscale heat storage capsule formed by encapsulating a heat storage material 21 such as paraffin wax in a resin capsule 22 is used.
Here, the heat storage material 21 such as paraffin wax has a melting point Tm in the vicinity of the control target temperature Tmax of the heat source 1 or 2 to be cooled. It is assumed that the heat sources 1 and 2 can be cooled and that the temperature of the radiator 3 can be reduced by heat radiation.

Incidentally, the heat storage material 21 such as paraffin wax described above has a melting characteristic as illustrated in FIG. 3 with respect to the temperature rise, and the heat storage material 21 starts to melt when it rises to the melting start temperature Tm (0). When the temperature rises to Tm (50), the melting degree becomes 50%, and when the temperature rises to the melting end temperature Tm (100), the melting degree becomes 100%.
Conversely, when the temperature drops, the heat storage material 21 has a solidification characteristic with a similar tendency to the temperature drop, but begins to solidify when it falls to the solidification start temperature Ts (0). The degree of solidification becomes 100% when the end temperature is lowered to Ts (100).

Then, the latent heat graph of the heat storage material 21 is as illustrated in FIG. 4, and while the heat storage material temperature is rising, it starts to melt from the time when it rises to the melting start temperature Tm (0), and melts as the degree of melting progresses. As the heat storage material temperature rises until the heat storage material temperature rises beyond the melting point Tm and reaches the melting end temperature Tm (100), the heat absorption amount by the heat source (the heat absorption amount from the heat sources 1 and 2) is increased. The amount of heat absorbed by melting is reduced.
In addition, while the temperature of the heat storage material is decreasing, it starts to solidify from when it decreases to the solidification start temperature Ts (0), and as the degree of solidification progresses, the amount of heat released by solidification (the amount of heat released by the radiator 3) increases. The amount of heat dissipated by solidification is reduced as the temperature of the heat storage material decreases until the temperature reaches a solidification end temperature Ts (100) after the temperature further exceeds the heat storage material temperature.

In the piping configuration as shown in FIG. 1 using the above refrigerant, the cooling control of the heat sources 1 and 2 to be cooled is performed as follows.
For this cooling control, as shown in FIG. 1, a temperature sensor 11 that detects a radiator outlet refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3, and a heat source refrigerant outlet temperature Tw1out at the refrigerant outlets 1b and 2b of the cooling target heat sources 1 and 2 , Temperature sensors 12 and 13 for individually detecting Tw2out are provided.

The cooling control is performed based on the control program shown in FIG.
First, in step S1, it is checked whether or not the radiator outlet refrigerant temperature Trout is equal to or higher than the solidification end temperature Ts (100) of the heat storage material 21.
If the radiator outlet refrigerant temperature Trout is equal to or higher than the solidification end temperature Ts (100) of the heat storage material 21, the rotation speed of the radiator cooling fan 3f is increased in step S2, and conversely, the radiator outlet refrigerant temperature Trout ends the solidification of the heat storage material 21. If the temperature is lower than Ts (100), the rotational speed of the radiator cooling fan 3f is decreased in step S3.
The rotation control of the radiator fan 3f is performed so that the amount of cooling air supplied to the radiator 3 is adjusted so that the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 becomes the solidification end temperature Ts (100) of the heat storage material 21. This leads to controlling the rotation speed of the cooling fan 3f.

  In step S4, it is checked whether or not the heat source refrigerant outlet temperatures Tw1out and Tw2out at the refrigerant outlets 1b and 2b of the cooling target heat sources 1 and 2 are both equal to or higher than the melting end temperature Tm (100) of the heat storage material 21. In step S5 and step S6, which of the heat source refrigerant outlet temperatures Tw1out and Tw2out is higher than the melting end temperature Tm (100) (thus which is lower than the melting end temperature Tm (100), or both are the melting end temperatures) Check if it is less than Tm (100).

When it is determined in step S5 that the heat source refrigerant outlet temperature Tw1out is equal to or higher than the melting end temperature Tm (100) (and therefore, the heat source refrigerant outlet temperature Tw2out is lower than the melting end temperature Tm (100)), in step S7, the melting end temperature is determined. Cooling target corresponding to the heat source refrigerant outlet temperature Tw2out whose refrigerant flow rate of the heat source 1 corresponding to the heat source refrigerant outlet temperature Tw1out that has become Tm (100) or higher has increased to be less than the melting end temperature Tm (100) The flow distribution control valve 6 is operated so that the refrigerant flow rate of the heat source 2 decreases.
As a result, the refrigerant flow rate of the cooling target heat source 1 having a large cooling load is increased, and the refrigerant flow rate of the cooling target heat source 2 having a small cooling load is decreased, and these are cooled in accordance with individual required cooling loads. be able to.

When it is determined in step S6 that the heat source refrigerant outlet temperature Tw2out is equal to or higher than the melting end temperature Tm (100) (and therefore, the heat source refrigerant outlet temperature Tw1out is lower than the melting end temperature Tm (100)), in step S8, the melting end temperature is determined. Cooling target corresponding to the heat source refrigerant outlet temperature Tw1out whose refrigerant flow rate of the heat source 2 corresponding to the heat source refrigerant outlet temperature Tw2out that has become Tm (100) or more has increased to be less than the melting end temperature Tm (100) The flow distribution control valve 6 is operated so that the refrigerant flow rate of the heat source 1 decreases.
As a result, the refrigerant flow rate of the cooling target heat source 2 having a large cooling load is increased, and the refrigerant flow rate of the cooling target heat source 1 having a small cooling load is decreased, and these are cooled in accordance with each required cooling load. be able to.

When it is determined in step S4 that both the heat source refrigerant outlet temperatures Tw1out and Tw2out are equal to or higher than the melting end temperature Tm (100) of the heat storage material 21 (insufficient in the cooling capacity), the load on the pump 4 is increased in step S9. Increase the circulation rate of the refrigerant.
As a result, the cooling capacity is increased by the increase of the refrigerant circulation amount, so that the cooling capacity shortage can be solved and both the cooling target heat sources 1 and 2 can be prevented from being insufficiently cooled.

When it is determined in steps S5 and S6 that both the heat source refrigerant outlet temperatures Tw1out and Tw2out are lower than the melting end temperature Tm (100) of the heat storage material 21 (the cooling capacity is excessive), the load on the pump 4 is reduced in step S10. This reduces the amount of refrigerant circulation.
As a result, the cooling capacity is reduced by the amount of the refrigerant circulation reduction, and it is possible to eliminate the excessive cooling capacity and prevent the cooling target heat sources 1 and 2 from being overcooled together.

After the above control, in step S11, it is checked whether or not the engine ignition switch is turned off, and the above loop is repeatedly executed by returning the control to step S1 unless the engine ignition switch is turned off.
When it is determined in step S11 that the engine ignition switch has been turned off, the control program in FIG. 5 is terminated and the cooling control is terminated.

In the vehicle cooling device of the first embodiment described above,
Since the refrigerant in which the heat storage capsule described above with reference to FIG. 2 is used, heat can be efficiently transported by the heat storage effect of the heat storage material 21, and the circulation amount of the refrigerant by the pump 4 is reduced accordingly. It is possible to improve the cooling efficiency of the heat sources 1 and 2 to be cooled.

In addition, the refrigerant cooled by the radiator 3 is directed to a plurality of cooling target heat sources 1 and 2 by a common pump 4 under the control of the flow distribution control valve 6, and is passed to these cooling target heat sources 1 and 2. Because it is a piping configuration that returns the refrigerant after flowing back to the radiator 3,
By operating the flow distribution control valve 6, it is possible to determine the distribution of the refrigerant flow to the plurality of cooling target heat sources 1 and 2, and the cooling target heat sources 1 and 2 can be determined according to the individual required cooling load. Can be cooled.

  In addition, in order to achieve the above-described effects, it is only necessary to provide the flow distribution control valve 6 at the branching point of the pipe that distributes the refrigerant flow from the pump 4 to the plurality of heat sources 1 and 2 to be cooled. The above-mentioned effects can be achieved without adding a control valve or an additional auxiliary pump, which is advantageous in terms of cost, and eliminates the problem of the above-described parallel-pipe cooling device related to cost. it can.

In the control, according to the cooling load of the plurality of cooling target heat sources 1 and 2, the refrigerant circulation amount by the pump 4 and the flow distribution to the cooling target heat source by the flow distribution control valve 6 are controlled,
In order to drive and control the radiator cooling fan 3f so that the cooling air amount to the radiator 3 is the cooling air amount so that the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 becomes the solidification end temperature Ts (100) of the heat storage material,
The distribution of the refrigerant flow to the plurality of cooling target heat sources 1 and 2 corresponds to each cooling load, and the cooling target heat sources 1 and 2 can be cooled without excess or deficiency according to each required cooling load. At the same time, the plurality of heat sources 1 and 2 to be cooled are not excessively cooled or insufficiently cooled.

FIG. 6 shows a control program for the vehicular cooling device according to the second embodiment of the present invention.
In this embodiment, the same piping configuration as shown in FIG. 1 is used, but the temperature sensors 12 and 13 individually detect the wall surface temperatures Th1 and Th2 in the refrigerant outlet passages 1b and 2b of the cooling target heat sources 1 and 2. Using the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2 and the radiator outlet refrigerant temperature Trout detected by the temperature sensor 11, cooling control is performed as follows.

  In steps S1 to S3, processing similar to that indicated by the same reference numerals in FIG. 5 is performed, and the amount of cooling air to the radiator 3 is changed to the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 by the solidification end temperature Ts of the heat storage material 21. The rotation speed of the radiator cooling fan 3f is controlled so that the amount of cooling air becomes (100).

  In step S14, it is checked whether the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the cooling target heat sources 1 and 2 are both equal to or higher than the control target temperature Tmax of the cooling target heat sources 1 and 2. If not, step S15 and step S16 are performed. , It is checked which of the heat source refrigerant outlet passage wall surface temperatures Th1 and Th2 is equal to or higher than the control target temperature Tmax (thus which is lower than the control target temperature Tmax or both are lower than the control target temperature Tmax).

When it is determined in step S15 that the heat source refrigerant outlet passage wall surface temperature Th1 is equal to or higher than the control target temperature Tmax (thus, the heat source refrigerant outlet passage wall surface temperature Th2 is lower than the control target temperature Tmax), in step S7, the control target temperature Tmax is equal to or higher. The refrigerant flow rate of the cooling target heat source 1 corresponding to the heat source refrigerant outlet passage wall surface temperature Th1 increases, and the refrigerant flow of the cooling target heat source 2 corresponding to the heat source refrigerant outlet passage wall surface temperature Th2 that is less than the control target temperature Tmax. The flow distribution control valve 6 is operated so that the flow rate decreases.
As a result, the refrigerant flow rate of the cooling target heat source 1 having a large cooling load is increased, and the refrigerant flow rate of the cooling target heat source 2 having a small cooling load is decreased, and these are cooled in accordance with individual required cooling loads. be able to.

When it is determined in step S16 that the heat source refrigerant outlet passage wall surface temperature Th2 is equal to or higher than the control target temperature Tmax (thus, the heat source refrigerant outlet passage wall surface temperature Th1 is lower than the control target temperature Tmax), in step S8, the control target temperature Tmax or higher. The refrigerant flow rate of the cooling target heat source 2 corresponding to the heat source refrigerant outlet passage wall surface temperature Th2 increases, and the refrigerant flow of the cooling target heat source 1 corresponding to the heat source refrigerant outlet passage wall surface temperature Th1 that is less than the control target temperature Tmax. The flow distribution control valve 6 is operated so that the flow rate decreases.
As a result, the refrigerant flow rate of the cooling target heat source 2 having a large cooling load is increased, and the refrigerant flow rate of the cooling target heat source 1 having a small cooling load is decreased, and these are cooled in accordance with each required cooling load. be able to.

When it is determined in step S14 that both the heat source refrigerant outlet passage wall surface temperatures Th1 and Th2 are equal to or higher than the control target temperature Tmax (insufficient cooling capacity), the refrigerant circulation amount is increased by increasing the load of the pump 4 in step S9. Increase.
As a result, the cooling capacity is increased by the increase of the refrigerant circulation amount, so that the cooling capacity shortage can be solved and both the cooling target heat sources 1 and 2 can be prevented from being insufficiently cooled.

When it is determined in steps S15 and S16 that both the heat source refrigerant outlet passage wall surface temperatures Th1 and Th2 are lower than the control target temperature Tmax (excess cooling capacity), the refrigerant flow is reduced by reducing the load of the pump 4 in step S10. Reduce circulation.
As a result, the cooling capacity is reduced by the amount of the refrigerant circulation reduction, and it is possible to eliminate the excessive cooling capacity and prevent the cooling target heat sources 1 and 2 from being overcooled together.

After the above control, in step S11, it is checked whether or not the engine ignition switch is turned off, and the above loop is repeatedly executed by returning the control to step S1 unless the engine ignition switch is turned off.
When it is determined in step S11 that the engine ignition switch has been turned off, the control program in FIG. 6 is terminated and the cooling control is terminated.

In the vehicle cooling device of the present embodiment, in addition to achieving the same operational effects as in the above-described embodiment,
The refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2 to be cooled are monitored, and the refrigerant circulation amount control by the pump 4 and the flow distribution control valve 6 are performed so that these become the control target temperature Tmax of the heat sources 1 and 2 to be cooled. In order to control the flow distribution to the cooling target heat sources 1 and 2,
The refrigerant outlet passage wall surface temperature Th1, Th2 that best represents the temperature of the cooling target heat sources 1, 2 is controlled to be the control target temperature Tmax of the cooling target heat sources 1, 2, and the cooling temperature control is based on the above-described embodiment. Can be made even more accurate.

FIG. 7 shows a control program for a vehicular cooling device according to a third embodiment of the present invention. This control program adds steps S21 to S23 between step S2 and step S3 of FIG. 5 and step S4. It is a thing.
Also in this embodiment, using the same piping configuration as shown in FIG. 1, the following heat source refrigerant outlet temperatures Tw1out, Tw2out detected by the temperature sensors 12, 13 and the radiator outlet refrigerant temperature Trout detected by the temperature sensor 11 are as follows. So as to carry out the cooling control.

  In steps S1 to S3, processing similar to that indicated by the same reference numerals in FIG. 5 is performed, and the amount of cooling air to the radiator 3 is changed to the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 by the solidification end temperature Ts of the heat storage material 21. The rotation speed of the radiator cooling fan 3f is controlled so that the amount of cooling air becomes (100).

In step S21, the size of the cooling load for the cooling target heat sources 1 and 2 is determined by comparing the heat source refrigerant outlet temperatures Tw1out and Tw2out.
Therefore, step S21 corresponds to the heat source cooling load comparison means in the present invention.
If it is determined in step S21 that the heat source refrigerant outlet temperature has a relationship of Tw1out ≧ Tw2out (the cooling load of the cooling target heat source 1 is larger than the cooling load of the cooling target heat source 2), the cooling load is large in step S22. The flow rate distribution control valve 6 is operated so that the refrigerant flow rate to the cooling target heat source 1 determined increases and the refrigerant flow rate to the cooling target heat source 2 determined to have a small cooling load decreases.
If it is determined in step S21 that the heat source refrigerant outlet temperature has a relationship of Tw1out <Tw2out (the cooling load of the cooling target heat source 2 is larger than the cooling load of the cooling target heat source 1), the cooling load is large in step S23. The flow rate distribution control valve 6 is operated so that the refrigerant flow rate to the cooling target heat source 2 determined increases and the refrigerant flow rate to the cooling target heat source 1 determined to have a small cooling load decreases.

  In steps S4 to S11, processing similar to that indicated by the same reference numerals in FIG. 5 is performed, and the refrigerant temperatures Tw1out and Tw2out at the refrigerant outlets 1b and 2b of the heat sources 1 and 2 to be cooled are the melting end temperatures Tm of the heat storage material 21. The refrigerant circulation amount by the pump 4 and the flow distribution to the cooling target heat sources 1 and 2 by the flow distribution control valve 6 are controlled so as to be (100).

In the vehicle cooling device of the present embodiment, in addition to achieving the same operational effects as in the first embodiment described above with reference to FIGS.
In steps S21 to S23, the magnitude of the heat source refrigerant outlet temperatures Tw1out and Tw2out is compared to determine the size of the cooling load for the heat sources 1 and 2 to be cooled, and the flow distribution control valve 6 is operated according to the determination result to determine the cooling load. In order to increase the refrigerant flow rate to the cooling target heat source 1 or 2 determined to be large and reduce the refrigerant flow rate to the cooling target heat source 2 or 1 determined to have a small cooling load,
In steps S4 to S11, the refrigerant circulation amount and the flow distribution control by the pump 4 are performed so that the refrigerant temperatures Tw1out and Tw2out at the refrigerant outlets 1b and 2b of the heat sources 1 and 2 to be cooled become the melting end temperature Tm (100) of the heat storage material 21. In combination with controlling the flow distribution to the heat sources 1 and 2 to be cooled by the valve 6, the heat sources 1 and 2 can be efficiently cooled.

FIG. 8 shows a control program for a vehicular cooling device according to a fourth embodiment of the present invention. This control program adds steps S31 to S33 between step S2 and step S3 of FIG. 6 and step S14. It is a thing.
In the present embodiment, the same piping configuration as that shown in FIG. 1 is used. However, as in the second embodiment of the present invention shown in FIG. 6, the temperature sensors 12 and 13 in FIG. The wall surface temperatures Th1 and Th2 in the passages 1b and 2b are individually detected, and the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2 and the radiator outlet refrigerant temperature Trout detected by the temperature sensor 11 are as follows. Perform cooling control.

  In steps S1 to S3, processing similar to that indicated by the same reference numerals in FIG. 6 is performed, and the amount of cooling air supplied to the radiator 3 is set so that the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 is equal to the solidification end temperature Ts of the heat storage material 21. The rotation speed of the radiator cooling fan 3f is controlled so that the amount of cooling air becomes (100).

In step S31, the size of the cooling load for the cooling target heat sources 1 and 2 is determined by comparing the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2.
Therefore, step S31 corresponds to the heat source cooling load comparison means in the present invention.
If it is determined in step S31 that the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2 are Th1 ≧ Th2 (the cooling load of the cooling target heat source 1 is larger than the cooling load of the cooling target heat source 2), step S32 The flow distribution control valve 6 is operated so that the refrigerant flow rate to the cooling target heat source 1 determined to have a large cooling load increases and the refrigerant flow rate to the cooling target heat source 2 determined to have a low cooling load decreases. .
When it is determined in step S31 that the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the heat sources 1 and 2 are Th1 <Th2 (the cooling load of the cooling target heat source 2 is larger than the cooling load of the cooling target heat source 1), step S33 The flow distribution control valve 6 is operated so that the refrigerant flow rate to the cooling target heat source 2 determined to have a large cooling load increases and the refrigerant flow rate to the cooling target heat source 1 determined to have a low cooling load decreases. .

  In steps S14 to S16 and steps S7 to S10, processing similar to that indicated by the same reference numerals in FIG. 6 is performed, and the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the cooling target heat sources 1 and 2 are changed to the cooling target heat sources 1 and 2. The refrigerant circulation amount by the pump 4 and the flow distribution to the cooling target heat sources 1 and 2 by the flow distribution control valve 6 are controlled so that the control target temperature Tmax is reached.

In the vehicle cooling device of the present embodiment, in addition to achieving the same operational effects as in the second embodiment shown in FIGS.
In steps S31 to S33, the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the cooling target heat sources 1 and 2 are compared to determine the size of the cooling load for the cooling target heat sources 1 and 2, and the flow distribution control is performed according to the determination result. Operate valve 6 to increase the refrigerant flow rate to cooling target heat source 1 or 2 that has been determined to have a large cooling load, and reduce the refrigerant flow rate to cooling target heat source 2 or 1 that has been determined to have a low cooling load. For,
In steps S14 to S16 and steps S7 to S10, the refrigerant circulation amount and flow rate by the pump 4 so that the refrigerant outlet passage wall surface temperatures Th1 and Th2 of the cooling target heat sources 1 and 2 become the control target temperature Tmax of the cooling target heat sources 1 and 2, respectively. In combination with controlling the flow distribution to the heat sources 1 and 2 to be cooled by the distribution control valve 6, the heat sources 1 and 2 can be efficiently cooled.

9 and 10 show a vehicular cooling apparatus according to a fifth embodiment of the present invention. In FIG. 9, the same reference numerals as those in FIG. 1 denote the same parts as in FIG.
As shown in FIG. 9, in this embodiment, the piping configuration for passing the refrigerant cooled by the radiator 3 to the cooling target heat sources 1 and 2 through a common pump 4 in a heat exchange relationship is shown. It is assumed that the heat sources 1 and 2 are connected in series so that they are in series as follows.

That is, one end of the refrigerant supply line 5 in which the one common pump 4 is inserted is connected to the refrigerant outlet 3a of the radiator 3, and the other end of the refrigerant supply line 5 is connected to the heat source 1 to be cooled on the upstream side. Connected to the refrigerant inlet 1a.
The refrigerant outlet 1b of the upstream cooling target heat source 1 and the refrigerant inlet 2a of the downstream cooling target heat source 2 are connected to each other by the connecting pipe 14, and between the refrigerant supply pipe 5 and the connecting pipe 14. A bypass pipe 15 that extends and bypasses between the refrigerant inlet 1a and the refrigerant outlet 1b of the upstream cooling target heat source 1 is provided, and the flow control valve 16 is inserted into the bypass pipe 15.
A refrigerant return pipe 10 connects the refrigerant outlet 2b of the downstream heat source 2 to be cooled and the refrigerant inlet 3b of the radiator 3.

Thus, the refrigerant cooled by the radiator 3 passes through the pipe line 5 by the common single pump 4 to the refrigerant inlet 1a of the upstream heat source 1 to be cooled, and the bypass pipe according to the opening degree of the flow control valve 16. Also supplied to the road 15.
The refrigerant that has flowed through the heat exchange relationship to the upstream cooling target heat source 1 and cooled the heat source 1 merges with the refrigerant from the bypass pipe 15, and passes through the communication pipe 14 to the refrigerant inlet of the downstream cooling target heat source 2. Head for 2a.
The refrigerant that has flowed while cooling the downstream cooling target heat source 2 is returned to the refrigerant inlet 3b of the radiator 3 through the refrigerant return pipe 10, cooled by the radiator 3, and then cooled again. In order to cool them.

  In this embodiment as well, the above-mentioned refrigerant is formed by encapsulating the heat storage material 21 such as paraffin wax described above with reference to FIG. 2 (having a melting point Tm near the control target temperature Tmax of the heat sources 1 and 2 to be cooled) in the resin capsule 22. A refrigerant in which microscale heat storage capsules are mixed is used.

In the piping configuration as shown in FIG. 9 using such a refrigerant, cooling control of the heat sources 1 and 2 to be cooled is performed as follows.
For this cooling control, as shown in FIG. 9, the temperature sensor 11 for detecting the radiator outlet refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 and the wall surface temperature Th1 in the refrigerant outlet passage 1b of the upstream cooling target heat source 1 are individually set. A temperature sensor 12 for detecting and a temperature sensor 13 for detecting the heat source refrigerant outlet temperature Tw2out at the refrigerant outlet 2b of the downstream cooling target heat source 2 are provided.

The cooling control is performed based on the control program shown in FIG.
First, in step S41, it is checked whether or not the radiator outlet refrigerant temperature Trout is equal to or higher than the solidification end temperature Ts (100) of the heat storage material 21.
If the radiator outlet refrigerant temperature Trout is equal to or higher than the solidification end temperature Ts (100) of the heat storage material 21, the rotation speed of the radiator cooling fan 3f is increased in step S42, and conversely, the radiator outlet refrigerant temperature Trout ends the solidification of the heat storage material 21. If the temperature is less than Ts (100), the rotational speed of the radiator cooling fan 3f is decreased in step S43.
The rotation control of the radiator fan 3f is performed so that the amount of cooling air supplied to the radiator 3 is adjusted so that the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 becomes the solidification end temperature Ts (100) of the heat storage material 21. This leads to controlling the rotation speed of the cooling fan 3f.

In step S44, it is checked whether or not the refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2 is lower than the melting end temperature Tm (100) of the heat storage material 21, that is, whether or not the cooling capacity is excessive.
When it is determined in step S44 that Tw2out <Tm (100) is excessive, whether or not the refrigerant outlet passage wall surface temperature Th1 of the upstream cooling target heat source 1 is lower than the control target temperature Tmax of the cooling target heat sources 1 and 2 in step S45. To check whether the upstream heat source 1 to be cooled is undercooled or undercooled.
When the upstream cooling target heat source 1 determined as Th1 <Tmax in step S45 is overcooled, the circulation amount of the refrigerant is reduced by reducing the load of the pump 4 in step S46.
As a result, the cooling capacity is reduced by the amount of decrease in the refrigerant circulation amount, so that the overcooling of the upstream cooling target heat source 1 can be eliminated and the excessive cooling capacity can be eliminated.
When the upstream cooling target heat source 1 determined to be Th1 ≧ Tmax in step S45 is insufficiently cooled, the degree of opening of the bypass line 15 (the opening degree of the flow control valve 16) is reduced in step S47, so that the upstream cooling target The amount of heat absorbed here is increased by increasing the refrigerant flow rate to the heat source 1.
The insufficient cooling of the upstream cooling target heat source 1 can be resolved by increasing the refrigerant flow rate to the upstream cooling target heat source 1 (increasing the amount of heat absorbed by the heat source 1).

When the cooling capacity is determined to be Tw2out ≧ Tm (100) in step S44, whether or not the refrigerant outlet passage wall surface temperature Th1 of the upstream cooling target heat source 1 is lower than the control target temperature Tmax of the cooling target heat sources 1 and 2 in step S48. To check whether the upstream heat source 1 to be cooled is undercooled or undercooled.
When the upstream cooling target heat source 1 determined as Th1 <Tmax in step S48 is overcooled, the upstream cooling target is increased by increasing the degree of opening of the bypass line 15 (the opening degree of the flow control valve 16) in step S49. The refrigerant flow rate to the heat source 1 is reduced to reduce the amount of heat absorbed here.
The cooling of the upstream cooling target heat source 1 can be eliminated by the decrease in the refrigerant flow rate to the upstream cooling target heat source 1 (the decrease in the amount of heat absorbed by the heat source 1).
When the upstream cooling target heat source 1 determined as Th1 ≧ Tmax in step S48 is insufficiently cooled, the refrigerant circulation rate is increased by increasing the load of the pump 4 in step S50.
As a result, the cooling capacity is increased by the amount of increase in the refrigerant circulation amount, so that the insufficient cooling of the upstream cooling target heat source 1 can be solved and the insufficient cooling capacity can be solved.

After the above control, in step S51, it is checked whether or not the engine ignition switch is turned off, and the above loop is repeatedly executed by returning the control to step S41 unless the engine ignition switch is turned off.
When it is determined in step S51 that the engine ignition switch has been turned off, the control program of FIG. 10 is terminated and the cooling control is terminated.

In the vehicle cooling device of the fifth embodiment described above,
Since the refrigerant in which the heat storage capsule described above with reference to FIG. 2 is used, heat can be efficiently transported by the heat storage effect of the heat storage material 21, and the circulation amount of the refrigerant by the pump 4 is reduced accordingly. It is possible to improve the cooling efficiency of the heat sources 1 and 2 to be cooled.

Further, in this embodiment, as shown in FIG. 9, the refrigerant cooled by the radiator 3 is directed to the upstream cooling target heat source 1 by a common pump 4, and the refrigerant inlet of the upstream cooling target heat source 1 is also provided. Direct to the bypass line 15 with the flow rate control valve 16 that bypasses between the refrigerant outlet 1b and the refrigerant outlet 1b, and merge the refrigerant after flowing into the heat source 1 to be cooled with the refrigerant from the bypass line 15 downstream To make the piping configuration to return to the radiator 3 the refrigerant after flowing to the cooling target heat source 2 and flowing through the downstream cooling target heat source 2,
It becomes a serial piping type cooling device, the refrigerant piping is shorter than the parallel piping type cooling device, the piping efficiency can be increased, and the cooling flow rate can be reduced by increasing the cooling efficiency.

In the control, according to the cooling load of the cooling target heat sources 1, 2 determined from the refrigerant outlet passage wall surface temperature Th1 of the upstream cooling target heat source 1 and the refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2, the flow control valve 16 Perform branch flow control to bypass line 15,
In order to perform branch flow control to the bypass line 15 by the flow control valve 16 so that the refrigerant outlet passage wall surface temperature Th1 of the upstream cooling target heat source 1 becomes the control target temperature Tmax,
In addition, in order to perform the refrigerant circulation amount control by the pump 4 so that the refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2 becomes the melting end temperature Tm (100) of the heat storage material 21,
Cooling target heat sources 1 and 2 can be cooled according to the individual required cooling load without the upstream cooling target heat source 1 being excessively cooled or the downstream cooling target heat source 2 being insufficiently cooled. In addition, it is possible to solve the above-described problems of the conventional serial piping cooling device, and neither the heat source 1 or 2 to be cooled is excessively cooled or insufficiently cooled.

FIG. 11 shows a control program for a vehicular cooling device according to a sixth embodiment of the present invention, which is obtained by replacing steps S45 and S48 in FIG. 10 with steps S55 and S58, respectively.
Also in this embodiment, the same piping configuration as shown in FIG. 9 is used, but the temperature sensor 12 detects the refrigerant temperature Tw1out in the refrigerant outlet passage 1b of the upstream cooling target heat source 1, and this upstream cooling target heat source 1 using the refrigerant outlet temperature Tw1out, the refrigerant temperature Tw2out in the refrigerant outlet passage 2b of the downstream cooling target heat source 2 detected by the temperature sensor 13, and the radiator outlet refrigerant temperature Trout detected by the temperature sensor 11 as follows: Carry out cooling control.

  In steps S41 to S43, processing similar to that shown by the same reference numerals in FIG. 10 is performed, and the amount of cooling air to the radiator 3 is changed to the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 by the solidification end temperature Ts of the heat storage material 21. The rotation speed of the radiator cooling fan 3f is controlled so that the amount of cooling air becomes (100).

When the cooling capacity is excessively determined as Tw2out <Tm (100) in step S44, it is determined in step S55 whether or not the refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1 is lower than the melting end temperature Tm (100) of the heat storage material 21. Then, it is checked whether the heat source 1 to be cooled on the upstream side is undercooled or undercooled.
When the upstream side cooling target heat source 1 is determined to be Tw1out <Tm (100) in step S55, the refrigerant circulation amount is reduced by reducing the load of the pump 4 in step S46.
As a result, the cooling capacity is reduced by the amount of decrease in the refrigerant circulation amount, so that the overcooling of the upstream cooling target heat source 1 can be eliminated and the excessive cooling capacity can be eliminated.
When the upstream cooling target heat source 1 determined to be Tw1out ≧ Tm (100) in step S55 is insufficiently cooled, the degree of opening of the bypass line 15 (the opening degree of the flow control valve 16) is reduced in step S47. The refrigerant flow rate to the side cooling target heat source 1 is increased to increase the heat absorption amount here.
The insufficient cooling of the upstream cooling target heat source 1 can be resolved by increasing the refrigerant flow rate to the upstream cooling target heat source 1 (increasing the amount of heat absorbed by the heat source 1).

When the cooling capacity is determined to be insufficient in step S44 as Tw2out ≧ Tm (100), it is determined in step S58 whether or not the refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1 is lower than the melting end temperature Tm (100) of the heat storage material 21. Then, it is checked whether the heat source 1 to be cooled on the upstream side is undercooled or undercooled.
When the upstream cooling target heat source 1 is determined to be Tw1out <Tm (100) in step S58, the degree of opening of the bypass line 15 (the opening degree of the flow control valve 16) is increased in step S49 to increase the upstream The refrigerant flow rate to the side cooling target heat source 1 is reduced to reduce the heat absorption amount here.
The cooling of the upstream cooling target heat source 1 can be eliminated by the decrease in the refrigerant flow rate to the upstream cooling target heat source 1 (the decrease in the amount of heat absorbed by the heat source 1).
When the upstream cooling target heat source 1 determined as Tw1out ≧ Tm (100) in step S58 is insufficiently cooled, the circulation amount of the refrigerant is increased by increasing the load of the pump 4 in step S50.
As a result, the cooling capacity is increased by the amount of increase in the refrigerant circulation amount, so that the insufficient cooling of the upstream cooling target heat source 1 can be solved and the insufficient cooling capacity can be solved.

  The above control continues until it is determined in step S51 that the engine ignition switch is turned off, and when the engine ignition switch is turned off, the control program of FIG. 11 is terminated.

In the vehicle cooling device of the sixth embodiment described above, the same operational effects as in the fifth embodiment described above with reference to FIGS. 9 and 10 can be obtained,
The flow control valve 16 branches to the bypass line 15 according to the cooling load of the cooling target heat sources 1 and 2 determined from the refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1 and the refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2. Flow control,
In order to control the branch flow rate to the bypass line 15 by the flow rate control valve 16 so that the refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1 becomes the melting end temperature Tm (100) of the heat storage material 21,
In addition, in order to perform the refrigerant circulation amount control by the pump 4 so that the refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2 becomes the melting end temperature Tm (100) of the heat storage material 21,
Cooling target heat sources 1 and 2 can be cooled according to the individual required cooling load without the upstream cooling target heat source 1 being excessively cooled or the downstream cooling target heat source 2 being insufficiently cooled. In addition, it is possible to solve the above-described problems of the conventional serial piping cooling device, and neither the heat source 1 or 2 to be cooled is excessively cooled or insufficiently cooled.

12 and 13 show a vehicular cooling device according to a seventh embodiment of the present invention. In this embodiment, as shown in FIG. 12, a pipe configuration similar to that in FIG. 9 is used as shown in FIG. The temperature sensor 12 detects the refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1, and as other temperature sensors, the refrigerant after flowing through the upstream cooling target heat source 1 and the refrigerant from the bypass line 15 Is provided with a temperature sensor 17 for detecting the temperature Twtotal of the combined refrigerant.
The refrigerant is a microscale heat storage capsule in which a heat storage material 21 such as paraffin wax described above with reference to FIG. 2 (having a melting point Tm near the control target temperature Tmax of the heat sources 1 and 2 to be cooled) is encapsulated in a resin capsule 22. Use mixed refrigerant.

In the piping configuration as shown in FIG. 12 using such a refrigerant, the cooling control of the heat sources 1 and 2 to be cooled is performed as follows.
In steps S61 to S63, the same processing as in steps S41 to S43 in FIG. 10 is performed, and the amount of cooling air to the radiator 3 is set so that the refrigerant temperature Trout at the refrigerant outlet 3a of the radiator 3 is the solidification end temperature Ts ( The rotation speed of the radiator cooling fan 3f is controlled so that the cooling air volume becomes 100).

In step S64, the size of the cooling load for the cooling target heat sources 1 and 2 is determined by comparing the heat source refrigerant outlet temperatures Tw1out and Tw2out.
Therefore, step S64 corresponds to the heat source cooling load comparison means in the present invention.
When it is determined in step S64 that the heat source refrigerant outlet temperature has a relationship of Tw1out <Tw2out (the cooling load of the downstream cooling target heat source 2 is larger than the cooling load of the upstream cooling target heat source 1), the cooling load is determined in step S65. It is determined whether or not the downstream cooling target heat source 2 is insufficiently cooled depending on whether or not the heat source refrigerant outlet temperature Tw2out of the downstream cooling target heat source 2 determined to be large is equal to or higher than the melting end temperature Tm (100) of the heat storage material 21. To do.

  If it is determined in step S65 that Tw2out ≧ Tm (100), that is, if the downstream cooling target heat source 2 having a large cooling load is in an insufficient cooling state, the combined refrigerant temperature Twtotal is set to 50% melting degree of the heat storage material 21 in step S66. It is checked whether the melting point Tm is less than the corresponding melting point. If it is less, the circulation amount of the refrigerant is increased by increasing the load of the pump 4 in step S67. By increasing the degree of opening (opening of the flow control valve 16), the refrigerant branch flow rate through the bypass line 15 is increased, the refrigerant flow rate to the upstream cooling target heat source 1 is decreased, and the combined refrigerant temperature Twtotal is stored. The material 21 is controlled to be less than the melting point Tm corresponding to the 50% melting degree.

  On the other hand, if it is determined in step S65 that Tw2out <Tm (100), that is, if the downstream cooling target heat source 2 having a large cooling load is in a supercooled state, in step S69, the refrigerant load is reduced by reducing the load on the pump 4. The amount of circulation is reduced to avoid a supercooling state of the heat source 2 to be cooled on the downstream side.

  When it is determined in step S64 that the heat source refrigerant outlet temperature has a relationship of Tw1out ≧ Tw2out (the cooling load of the upstream cooling target heat source 1 is larger than the cooling load of the downstream cooling target heat source 2), the cooling load is determined in step S71. Whether or not the upstream cooling target heat source 1 is insufficiently cooled is determined by whether or not the heat source refrigerant outlet temperature Tw1out of the upstream cooling target heat source 1 determined to be large is equal to or higher than the melting end temperature Tm (100) of the heat storage material 21. To do.

  When it is determined in step S71 that Tw1out ≧ Tm (100), that is, when the upstream cooling target heat source 1 having a large cooling load is in an insufficient cooling state, the combined refrigerant temperature Twtotal is set to 50% melting degree of the heat storage material 21 in step S72. It is checked whether or not the corresponding melting point Tm is exceeded, and if it is above, the circulation amount of the refrigerant is increased by increasing the load of the pump 4 in step S73. By reducing the opening degree (the opening degree of the flow control valve 16), the refrigerant branch flow rate through the bypass line 15 is decreased, the refrigerant flow rate to the upstream cooling target heat source 1 is increased, and the combined refrigerant temperature Twtotal is The heat storage material 21 is controlled to have a melting point Tm or higher corresponding to the 50% melting degree.

  On the other hand, when it is determined in step S71 that Tw2out <Tm (100), that is, when the upstream cooling target heat source 1 having a large cooling load is in a supercooled state, in step S75, the refrigerant load is reduced by reducing the load on the pump 4. The amount of circulation is reduced to avoid a supercooled state of the upstream cooling target heat source 1.

After the above control, in step S76, it is checked whether or not the engine ignition switch is turned off, and the above loop is repeatedly executed by returning the control to step S61 unless the engine ignition switch is turned off.
When it is determined in step S76 that the engine ignition switch has been turned off, the control program in FIG. 13 is terminated and the cooling control is terminated.

Also in the vehicle cooling device of the seventh embodiment described above,
Since the refrigerant in which the heat storage capsule described above with reference to FIG. 2 is used, heat can be efficiently transported by the heat storage effect of the heat storage material 21, and the circulation amount of the refrigerant by the pump 4 is reduced accordingly. It is possible to improve the cooling efficiency of the heat sources 1 and 2 to be cooled,
As shown in FIG. 12, the heat sources 1 and 2 to be cooled are serially connected refrigerant pipes that are serially correlated, and the refrigerant pipes are shorter than those of the parallel pipe type so that the pipe efficiency can be improved. The flow path can be shortened to increase the cooling efficiency.

In the control, when the cooling load of the upstream cooling target heat source 1 is smaller than the cooling load of the downstream cooling target heat source 2, the combined refrigerant temperature Ttotal is less than the melting point Tm that is a temperature indicating 50% melting of the heat storage material 21. The branch flow rate increase control to the bypass line 15 is performed by the flow rate control valve 16,
When the cooling load of the downstream cooling target heat source 2 is larger than the cooling load of the upstream cooling target heat source 2, the flow rate control is performed so that the combined refrigerant temperature Ttotal is equal to or higher than the melting point Tm, which is a temperature indicating 50% melting of the heat storage material 21. Since the branch flow rate drop control to the bypass line 15 is performed by the valve 16,
The use of the latent heat of the heat storage material 21 is increased at the cooling target heat source having a large cooling load, and the cooling efficiency can be improved by suppressing the refrigerant circulation amount.

For example, when the cooling load of the upstream cooling target heat source 1 is smaller than the cooling load of the downstream cooling target heat source 2, the combined refrigerant temperature Ttotal is less than the melting point Tm, which is a temperature indicating 50% melting of the heat storage material 21, By increasing the branch flow rate to the bypass line 15 by the flow control valve 16, more latent heat can be used in the downstream heat source 2 to be cooled with a large cooling load, and the apparent specific heat of the refrigerant increases and cooling is performed. Efficiency is improved, and the refrigerant circulation flow rate can be reduced accordingly.
Further, when the cooling load of the downstream cooling target heat source 2 is larger than the cooling load of the upstream cooling target heat source 2, the combined refrigerant temperature Ttotal is equal to or higher than the melting point Tm, which is a temperature indicating 50% melting of the heat storage material 21. By reducing the branch flow rate to the bypass line 15 by the flow control valve 16, more latent heat can be used in the upstream cooling target heat source 1 having a large cooling load, and the apparent specific heat of the refrigerant is increased and cooling is performed. Efficiency is improved, and the refrigerant circulation flow rate can be reduced accordingly.

It is a schematic system diagram which shows the refrigerant | coolant piping structure of the cooling device for vehicles which becomes one Example of this invention. It is sectional drawing of the thermal storage capsule mixed with the refrigerant | coolant used with the cooling device for vehicles of the Example. It is a melting degree change characteristic view which shows the relationship between temperature and a melting degree of the thermal storage material enclosed in the thermal storage capsule. It is a calorie | heat amount change characteristic view which shows the relationship between the temperature of the thermal storage material enclosed in the thermal storage capsule, the amount of heat absorption, and the amount of heat dissipation. It is a flowchart which shows the cooling control program in the cooling device for vehicles of the Example. 6 is a flowchart similar to FIG. 5, showing a cooling control program for a vehicle cooling device according to a second embodiment of the present invention. 6 is a flowchart similar to FIG. 5, showing a cooling control program for a vehicle cooling device according to a third embodiment of the present invention. 6 is a flowchart similar to FIG. 5, showing a cooling control program for a vehicle cooling device according to a fourth embodiment of the present invention. FIG. 6 is a schematic system diagram showing a refrigerant piping configuration of a vehicle cooling device according to a fifth embodiment of the present invention. It is a flowchart which shows the cooling control program in the cooling device for vehicles of the Example. FIG. 11 is a flowchart similar to FIG. 10, showing a cooling control program for a vehicle cooling device according to a sixth embodiment of the present invention. FIG. 10 is a schematic system diagram showing a refrigerant piping configuration of a vehicle cooling device according to a seventh embodiment of the present invention. It is a flowchart which shows the cooling control program in the cooling device for vehicles of the Example.

Explanation of symbols

1 Cooling target heat source 2 Cooling target heat source
1a, 2a Refrigerant inlet
1b, 2b Refrigerant outlet 3 Radiator
3a Refrigerant outlet
3b Refrigerant inlet
3f Cooling fan 4 Pump 5 Refrigerant supply line 6 Flow distribution control valve 7 Branch line 8 Branch line 9 Connection line
10 Refrigerant return line
11 Radiator refrigerant outlet temperature sensor
12 Heat source refrigerant outlet temperature sensor
13 Heat source refrigerant outlet temperature sensor
14 Connection pipeline
15 Bypass line
16 Flow control valve
17 Combined refrigerant temperature sensor
21 Heat storage material
22 Resin capsule

Claims (14)

A vehicle in which there are a plurality of cooling target heat sources to be cooled, and the plurality of cooling target heat sources are cooled by circulating a refrigerant with a common single pump to the plurality of cooling target heat sources and the radiator. Cooling equipment for
The refrigerant is a refrigerant in which a microscale heat storage capsule containing a heat storage material is mixed,
The refrigerant cooled by the radiator is directed to the plurality of cooling target heat sources under the control of the flow distribution control valve by the common single pump, and the refrigerant after flowing through the cooling target heat sources is supplied to the radiator. No piping configuration to return to
The refrigerant circulation amount by the pump and the flow distribution to the cooling target heat source by the flow distribution control valve are controlled according to the cooling load of the plurality of cooling target heat sources,
The radiator cooling fan is driven and controlled so that the amount of ventilation to the radiator is such that the refrigerant temperature at the refrigerant outlet of the radiator becomes the solidification end temperature of the heat storage material. Cooling system. In the vehicle cooling device according to claim 1,
The refrigerant circulation amount by the pump and the flow distribution to the cooling target heat source by the flow distribution control valve are determined such that the refrigerant temperature at the refrigerant outlet of the plurality of cooling target heat sources becomes the melting end temperature of the heat storage material. A vehicular cooling device. In the vehicle cooling device according to claim 2,
Among the plurality of cooling target heat sources, the refrigerant temperature at the refrigerant outlet of a certain cooling target heat source is lower than the melting end temperature of the heat storage material, and the refrigerant temperature at the refrigerant outlet of another cooling target heat source is the end of melting of the heat storage material. When the temperature is equal to or higher than the temperature, the flow rate distribution control valve is configured to operate so as to decrease the refrigerant supply amount to the certain cooling target heat source and increase the refrigerant supply amount to the other cooling target heat source. Vehicle cooling device. In the vehicle cooling device according to claim 2 or 3,
When the refrigerant temperatures at the refrigerant outlets of the plurality of cooling target heat sources are all equal to or higher than the melting end temperature of the heat storage material, the refrigerant circulation amount by the pump is increased, and the refrigerant temperatures at the refrigerant outlets of the plurality of cooling target heat sources are increased. When the temperature is lower than the melting end temperature of the heat storage material, the vehicle cooling device is configured to operate the pump so as to reduce the refrigerant circulation rate by the pump. In the vehicle cooling device according to claim 1,
The refrigerant circulation amount by the pump and the flow distribution to the cooling target heat source by the flow distribution control valve are controlled so that the wall surface temperature in the refrigerant outlet passage of the plurality of cooling target heat sources becomes the control target temperature. A vehicular cooling device. In the vehicle cooling device according to claim 5,
Among the plurality of cooling target heat sources, when the wall surface temperature in the refrigerant outlet passage of a certain cooling target heat source is lower than the control target temperature and the wall surface temperature in the refrigerant outlet passage of another cooling target heat source is equal to or higher than the control target temperature, A vehicular cooling device configured to operate the flow rate distribution control valve so as to decrease a refrigerant supply amount to the certain cooling target heat source and increase a refrigerant supply amount to the other cooling target heat source. In the vehicle cooling device according to claim 5 or 6,
When the wall surface temperatures in the refrigerant outlet passages of the plurality of cooling target heat sources are all equal to or higher than the control target temperature, the refrigerant circulation amount by the pump is increased, and the wall surface temperatures in the refrigerant outlet passages of the plurality of cooling target heat sources are all A vehicular cooling device characterized in that when the temperature is lower than the control target temperature, the pump is operated so as to reduce the amount of refrigerant circulating by the pump. In the vehicle cooling device according to any one of claims 1 to 4,
A heat source cooling load comparison means for determining the size of the cooling load for the plurality of cooling target heat sources is provided,
A vehicular cooling device characterized in that the flow rate distribution control valve is operated so as to increase a refrigerant flow rate to a cooling target heat source determined to have a large cooling load by the means. In the vehicle cooling device according to any one of claims 1, 5 to 7,
A heat source cooling load comparison means for determining the size of the cooling load for the plurality of cooling target heat sources is provided,
A vehicular cooling device characterized in that the flow rate distribution control valve is operated so as to increase a refrigerant flow rate to a cooling target heat source determined to have a large cooling load by the means. A vehicle in which there are a plurality of cooling target heat sources to be cooled, and the plurality of cooling target heat sources are cooled by circulating a refrigerant with a common single pump to the plurality of cooling target heat sources and the radiator. Cooling equipment for
The refrigerant is a refrigerant in which a microscale heat storage capsule containing a heat storage material is mixed,
The refrigerant cooled by the radiator is directed to a certain cooling target heat source among the plurality of cooling target heat sources by the one common pump, and between the refrigerant inlet and the refrigerant outlet of the certain cooling target heat source. The refrigerant after flowing through the certain cooling target heat source is merged with the refrigerant from the bypass pipe to the other cooling target heat source, and the other. A piping configuration that returns the refrigerant after flowing through the cooling target heat source to the radiator,
In accordance with the cooling load of the plurality of cooling target heat sources, the flow rate control valve is configured to perform branch flow rate control to the bypass pipe line,
A vehicular cooling device configured to control a refrigerant circulation amount by the pump so that a refrigerant temperature at a refrigerant outlet of the other heat source to be cooled becomes a melting end temperature of the heat storage material. In the vehicle cooling device according to claim 10,
A vehicular cooling device configured to perform branch flow rate control to a bypass line by the flow rate control valve so that a wall surface temperature in a refrigerant outlet passage of the heat source to be cooled becomes a control target temperature. In the vehicle cooling device according to claim 10,
Cooling for a vehicle, wherein the flow rate control valve controls the branch flow rate to the bypass line so that the refrigerant temperature at the refrigerant outlet of the cooling target heat source becomes the melting end temperature of the heat storage material. apparatus. In the vehicle cooling device according to claim 10,
A heat source cooling load comparison means for determining the size of the cooling load for the plurality of cooling target heat sources is provided,
According to the cooling load size determination of the heat source to be cooled by the means, the flow rate is set so that the temperature of the combined refrigerant of the refrigerant after flowing through the certain heat source to be cooled and the refrigerant from the bypass pipe becomes a predetermined value. A vehicular cooling device characterized in that a branch flow rate control to a bypass pipe line is performed by a control valve. In the vehicle cooling device according to claim 13,
When the cooling load of the certain cooling target heat source is smaller than the cooling load of the other cooling target heat source by the heat source cooling load comparison means, the temperature of the combined refrigerant becomes less than the temperature indicating 50% melting of the heat storage material. The branch flow rate increase control to the bypass line is performed by the flow rate control valve,
When the cooling load of the certain cooling target heat source is larger than the cooling load of the other cooling target heat source by the heat source cooling load comparison means, the temperature of the combined refrigerant becomes equal to or higher than the temperature indicating 50% melting of the heat storage material. As described above, the vehicle cooling device is configured to perform branch flow rate drop control to the bypass pipe by the flow rate control valve.

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