JP2010065544A - Hydraulic fluid temperature control system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic fluid temperature control system controlling heating and cooling of a hydraulic fluid with a simple constitution. <P>SOLUTION: This hydraulic fluid temperature control system 1 has: a radiator circuit 9 for circulating cooling water for cooling an engine 2; a low water temperature circuit 14 for circulating the cooling water for cooling combustion air; and a hydraulic fluid heating circuit 22 for connecting the radiator circuit 9 and the low water temperature circuit 14. A switching valve 23 is arranged in a connecting part of the radiator circuit 9 and the hydraulic fluid heating circuit 22. The switching valve 23 switches a first passage where the cooling water circulating in the radiator circuit 9 passes through a hydraulic fluid heat exchanger 8 and a second passage where the cooling water circulates in the radiator circuit 9 and the cooling water circulating in the low water temperature circuit 14 passes through the hydraulic fluid heat exchanger 8. A control device 6 controls the switching valve 23 so as to heat ATF when the engine 2 warms up and cool the ATF at ordinary time. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hydraulic oil temperature control system that controls the temperature of hydraulic oil for an automatic transmission of an internal combustion engine mounted on a vehicle.

  As a first prior art, a system that heats and cools transmission oil with cooling water of a water-cooled engine is known. In this system, a heat exchanger is provided in the pipe from which the cooling water that has cooled the engine is discharged, and when the oil temperature is lower than the cooling water temperature, the oil is heated by the cooling water, and conversely, the oil temperature is lower than the cooling water temperature. When the height is too high, the oil is cooled by cooling water. In the configuration of the first conventional technique, the oil cooling performance may be insufficient.

  As a second conventional technique for solving this problem, a system for heating and cooling oil by providing a plurality of heat exchangers is known. In this system, a first heat exchanger that exchanges heat between the cooling water and oil immediately after the engine outlet is provided, and the cooling water and oil after being radiated by the radiator are built in the vicinity of the outlet of the radiator. A second heat exchanger is provided for heat exchange between the two.

In such a system, when the temperature of the oil is lower than a predetermined temperature, the oil is circulated through the first heat exchanger, and heat is exchanged with the high-temperature cooling water immediately after the engine outlet. Increase the temperature of the oil. When the oil temperature becomes equal to or higher than a predetermined temperature, the oil after passing through the first heat exchanger flows through the second heat exchanger and then returns to the transmission. Thus, when the oil temperature becomes equal to or higher than a predetermined temperature, an increase in the oil temperature is suppressed by heat exchange in the two heat exchangers (see, for example, Patent Document 1).
JP-A-11-264318

  In the second prior art system, the oil cooling performance is improved by providing a plurality of heat exchangers, but the number of parts increases because it includes a plurality of dedicated heat exchangers for cooling the oil. There is a problem of doing. The increase in the number of parts causes problems such as an increase in manufacturing cost and an increase in mass.

  Accordingly, the present invention has been made in view of the above-described problems, and an object thereof is to provide a hydraulic oil temperature control system capable of controlling heating and cooling of hydraulic oil (oil) with a simple configuration. .

  The present invention employs the following technical means in order to achieve the aforementioned object.

The invention according to claim 1 is a hydraulic oil temperature control system (1) for controlling the temperature of hydraulic oil for an automatic transmission of an internal combustion engine (2) mounted on a vehicle,
A first circulation path (9) through which cooling water for cooling the internal combustion engine circulates;
A second circulation path (14) for cooling a cooling object other than the internal combustion engine, in which cooling water having a temperature lower than that of the first circulation path circulates;
A third circulation path (22) connecting the first circulation path and the second circulation path, and cooling water that circulates through the first circulation path and passes through the inside of the internal combustion engine is determined in advance in the second circulation path. A third circulation path that passes the specific passage (19) and returns the cooling water that has passed through the specific passage to the first circulation path;
Cooling that is provided in the specific passage, has a hydraulic oil passage (20) through which hydraulic oil passes, and a cooling water passage (21) through which cooling water passes, and passes through the hydraulic oil passage and the cooling water passage. A hydraulic oil heat exchanger (8) for exchanging heat with water;
The cooling water passes through the first circulation path, the first path through which the cooling water passes through the third circulation path, the path through which the cooling water circulates through the first circulation path, and the cooling water circulates through the second circulation path. It is a hydraulic oil temperature control system characterized by including the switching means (23) which switches the 2nd path | route which forms a path | route.

  According to the first aspect of the present invention, when switching to the first path, the cooling water that has passed through the internal combustion engine flows through the cooling water passage of the hydraulic oil heat exchanger. Therefore, the temperature of the hydraulic oil can be controlled by the cooling water that has passed through the internal combustion engine. Moreover, when switching to a 2nd path | route, the cooling water which circulates through a 2nd circulation path flows into the cooling water path of a hydraulic oil heat exchanger. Therefore, the temperature of the hydraulic oil can be controlled by the cooling water circulating through the second circulation path. In addition, since the objects to be cooled are different from each other in the first circulation path and the second circulation path, the temperatures of the circulating cooling water are different from each other, and the cooling water in the second circulation path is lower in temperature. Therefore, by switching between the first path and the second path, the cooling water circulating through different flow paths can be circulated to the hydraulic oil heat exchanger, and the temperature of the hydraulic oil can be heated and cooled. In addition, since the first circulation path and the second circulation path can utilize the existing circulation path mounted on the vehicle, the hydraulic oil temperature control system of the present invention is simply provided by newly providing the third circulation path and the switching means. Can be realized. The operation and effect as described above can be achieved by the hydraulic oil temperature control system having such a simple configuration.

Further, the invention according to claim 2 further includes control means (6) for controlling the switching means,
The control means controls the switching means to the first path during warm-up when the cooling water circulating through the first circulation path is equal to or lower than a predetermined temperature.

  According to the second aspect of the present invention, the cooling water circulating through the first circulation path is at a higher temperature than the cooling water circulating through the second circulation path. The cooling water can be circulated through the cooling water passage of the hydraulic oil heat exchanger. As a result, the hydraulic oil can be heated in a short time during warm-up. Thereby, the fuel consumption of the vehicle can be improved.

  Furthermore, the invention according to claim 3 is characterized in that the control means controls the switching means to the second path when the cooling water circulating through the first circulation path is normal above a predetermined temperature.

  According to the third aspect of the present invention, since the cooling water in the first circulation path is higher than the predetermined temperature, the low-temperature cooling water circulating in the second circulation path is exchanged with hydraulic oil by controlling to the second path. Can be circulated through the cooling water passage of the vessel. By cooling the hydraulic oil in this way, it is possible to prevent the hydraulic oil from becoming hot at normal times.

Furthermore, in the invention according to claim 4, the object to be cooled is combustion air sucked into the internal combustion engine,
A main radiator (10) provided in the first circulation path, for exchanging heat between the cooling water circulating in the first circulation path and the outside air;
An intercooler (18) provided in the second circulation path for exchanging heat between the cooling water circulating in the second circulation path and the combustion air;
It further includes a sub-radiator (15) provided in the second circulation path and exchanging heat between the cooling water circulating in the second circulation path and the outside air.

  According to the fourth aspect of the present invention, the hydraulic oil temperature control system further includes a main radiator, a sub-radiator, and an intercooler. In such a hydraulic oil temperature control system, since the cooling water for cooling the internal combustion engine is higher in temperature than the cooling water for cooling the combustion air, the cooling water circulating in the first circulation path circulates in the second circulation path. It is hotter than the cooling water. Therefore, the hydraulic oil temperature control system of the present invention can achieve the operations and effects as described above.

  In addition, the code | symbol in the bracket | parenthesis of each above-mentioned means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

  Hereinafter, a plurality of embodiments for carrying out the present invention will be described with reference to the drawings. Portions corresponding to the matters described in the preceding forms in each embodiment are denoted by the same reference numerals, and overlapping description may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic diagram illustrating an overall configuration of a hydraulic oil temperature control system 1 according to the first embodiment. The hydraulic oil temperature control system 1 according to the present embodiment is applied to a vehicle (automobile) using the engine 2 as a driving source for traveling. The hydraulic oil temperature control system 1 includes an engine cooling device 3 for cooling the engine 2, a supply air cooling device 4 for cooling combustion air and hydraulic oil, and the engine cooling device 3 and the supply air cooling device 4. A coupling device 5 to be coupled and a control device 6 are included.

  The engine 2 is a water-cooled internal combustion engine. The engine 2 is provided with an automatic transmission (not shown) that automatically operates the clutch and the transmission. In the automatic transmission, an ATF circulation circuit 7 for circulating hydraulic oil for automatic transmission (hereinafter also referred to as “ATF”) is formed. The ATF circulation circuit 7 is provided with an ATF pump (not shown) for circulating ATF. The ATF pump is an engine direct-coupled pump that rotates by receiving the driving force of the engine 2. The ATF circulation circuit 7 is provided with an ATF temperature sensor (not shown) for detecting the temperature of the circulating ATF. The temperature information detected by the ATF temperature sensor is given to the control device 6. The ATF circulation circuit 7 is provided with a hydraulic oil heat exchanger 8 through which the ATF circulating through the ATF circulation circuit 7 flows.

  The engine cooling device 3 includes a radiator circuit 9, a main radiator 10, a bypass passage 11, a main water pump 12, and a thermostat 13. The radiator circuit 9 is a first circulation path that is connected to the engine 2 and through which cooling water for cooling the engine 2 circulates. The radiator circuit 9 is provided with a main radiator 10, a thermostat 13 and a main water pump 12. The main water pump 12 is a pump for circulating cooling water, and is an engine direct-coupled pump that rotates by receiving the driving force of the engine 2. Further, the radiator circuit 9 is provided with a cooling water temperature sensor (not shown) for detecting the temperature of the circulating cooling water. The temperature information detected by the cooling water temperature sensor is given to the control device 6.

  The main radiator 10 cools the cooling water circulating through the radiator circuit 9 by heat exchange with the outside air by the main water pump 12. The radiator circuit 9 is provided with a bypass passage 11 for bypassing the main radiator 10 and circulating cooling water.

  The thermostat 13 adjusts the amount of cooling water flowing through the main radiator 10 and the amount of cooling water flowing through the bypass passage 11 according to the temperature of the cooling water. Specifically, when the cooling water temperature is equal to or lower than a predetermined cooling water temperature, the thermostat 13 closes the flow path to the radiator circuit 9 side so that the cooling water circulates only in the bypass passage 11. When the cooling water temperature exceeds a predetermined cooling water temperature, the thermostat 13 opens a flow path toward the radiator circuit 9 so that the cooling water circulates in both the bypass passage 11 and the radiator circuit 9.

  The supply air cooling device 4 includes a low water temperature circuit 14, a sub radiator 15, a sub water pump 16, a check valve 17 and an intercooler 18. The low water temperature circuit 14 is a second circulation path through which cooling water for cooling the combustion air sucked into the engine 2 circulates. The low water temperature circuit 14 is provided with a sub water pump 16, a sub radiator 15, an intercooler 18, a check valve 17, and a hydraulic oil heat exchanger 8. The sub water pump 16 is a pump for circulating cooling water. The sub-water pump 16 is controlled by the control device 6 in an activated state and a stopped state.

  The sub radiator 15 cools the cooling water circulating in the low water temperature circuit 14 by the sub water pump 16 through heat exchange with the outside air. The intercooler 18 cools the combustion air by heat exchange with the cooling water circulating in the low water temperature circuit 14 by the sub water pump 16. Further, the intercooler 18 is provided with a combustion air temperature sensor (not shown) for detecting the temperature of the combustion air passing therethrough. The temperature information detected by the combustion air temperature sensor is given to the control device 6.

  The check valve 17 is provided downstream of the intercooler 18 and between the intercooler 18 and the hydraulic oil heat exchanger 8. When the cooling water flows through the low water temperature circuit 14, the check valve 17 is allowed to flow from the intercooler 18 to the hydraulic oil heat exchanger 8, and prevents the flow to the reverse side.

  The hydraulic oil heat exchanger 8 is provided in the specific passage 19 downstream of the check valve 17 and upstream of the sub water pump 16. The hydraulic oil heat exchanger 8 has a hydraulic oil passage 20 through which hydraulic oil passes and a cooling water passage 21 through which cooling water passes. Therefore, both ends of the cooling water passage 21 are connected to the specific passage 19. In other words, the cooling water flowing into the cooling water passage 21 is the cooling water flowing down the specific passage 19. The cooling water flowing down the cooling water passage 21 flows into the specific passage 19. Since the hydraulic oil heat exchanger 8 is provided in the ATF circulation circuit 7 as described above, the heat exchanger exchanges heat between the ATF circulating in the ATF circulation circuit 7 and the cooling water flowing in the low water temperature circuit 14. It is.

  Thus, the radiator circuit 9 is a circulation path for cooling the engine 2 which is an internal combustion engine. The low water temperature circuit 14 is a circulation path for cooling the combustion air. Therefore, the radiator circuit 9 and the low water temperature circuit 14 have different cooling objects, and therefore the temperatures of the circulating cooling water are also different from each other. In the present embodiment, the cooling water that cools the engine 2 is hotter than the cooling water that cools the combustion air, so the cooling water circulating in the radiator circuit 9 is higher than the cooling water circulating in the low water temperature circuit 14. It is.

  Next, the connection device 5 that connects the engine cooling device 3 and the supply air cooling device 4 will be described. The coupling device 5 includes a hydraulic oil heating circuit 22 and a switching valve 23. First, a configuration for connecting the radiator circuit 9 and the low water temperature circuit 14 will be described. The bypass passage 11 is provided with a hydraulic oil heating circuit 22 that is a third circulation path. The hydraulic oil heating circuit 22 has an outflow passage 24 branched from the bypass passage 11 and joined to the low water temperature circuit 14, and an inflow passage 25 branched from the low water temperature circuit 14 and joined to the bypass passage 11. The joining position of the outflow passage 24 and the low water temperature circuit 14 is between the check valve 17 of the low water temperature circuit 14 and the hydraulic oil heat exchanger 8. Therefore, the cooling water flowing into the low water temperature circuit 14 from the outflow passage 24 flows to the hydraulic oil heat exchanger 8 without flowing back by the check valve 17. The branch position between the inflow passage 25 and the low water temperature circuit 14 is between the hydraulic oil heat exchanger 8 of the low water temperature circuit 14 and the sub water pump 16.

  A switching valve 23 is provided at a connecting portion that connects the radiator circuit 9 and the hydraulic oil heating circuit 22. The switching valve 23 is configured such that the cooling water passing through the bypass passage 11 passes through the hydraulic oil heat exchanger 8 via the hydraulic oil heating circuit 22, and the cooling water circulates in the radiator circuit 9. This is switching means for switching between the second path through which the coolant circulating in the circuit 14 passes through the hydraulic oil heat exchanger 8. Specifically, the switching valve 23 includes a radiator and a first path through which cooling water flowing through the bypass passage 11 flows in the outflow passage 24 and cooling water flowing through the low water temperature circuit 14 flows in the inflow passage 25 in the connection portion. In the circuit 9 and the low water temperature circuit 14, the second path through which the cooling water circulates is switched. Therefore, when the switching valve 23 is controlled to the first path, the cooling water flowing through the hydraulic oil heat exchanger 8 is not the cooling water that has passed through the intercooler 18 but the cooling water that has passed through the inside of the engine 2. When the switching valve 23 is controlled to the second path, the cooling water flowing through the bypass passage 11 is the cooling water that has passed through the inside of the engine 2, and the cooling water that passes through the hydraulic oil heat exchanger 8 is Cooling water that has passed through the cooler 18. Such a switching valve 23 is controlled by the control device 6.

  The control device 6 is a control means and comprises a microcomputer and its peripheral circuits. The control device 6 performs arithmetic processing for controlling each unit in accordance with a preset program. The control device 6 controls the sub water pump 16 and the switching valve 23 based on temperature information detected by the cooling water temperature sensor, the ATF temperature sensor, and the combustion air temperature sensor. The control device 6 controls the switching valve 23 and the sub water pump 16 so as to heat the ATF when the engine 2 is warmed up and cool the ATF at the normal time after warming up. Here, the warm-up time is a predetermined period from the start-up of the engine 2, and the cooling water circulating through the radiator circuit 9 is in a state of a predetermined temperature (for example, 60 degrees) or less. Further, the normal time is a period after warm-up, and the cooling water circulating through the radiator circuit 9 is in a state higher than a predetermined temperature. In other words, the normal time is during normal vehicle travel.

  Next, control of the switching valve 23 of the control device 6 will be described. FIG. 2 is a flowchart showing a procedure for determining the flow path of the switching valve 23 of the control device 6. FIG. 3 is a schematic diagram of the hydraulic oil temperature control system 1 showing the flow of cooling water in the first path. FIG. 4 is a schematic diagram of the hydraulic oil temperature control system 1 showing the flow of cooling water in the case of the second path. This flow is repeatedly executed in a short time while warming up and in a state where electric power is supplied to the control device 6.

  In step a1, if the ATF temperature is lower than the cooling water temperature circulating in the radiator circuit 9, the process proceeds to step a2, and if not, the process proceeds to step a4. In step a2, if the combustion air temperature is lower than the preset temperature, the process proceeds to step a3, and if not, the process proceeds to step a4. The set temperature of such combustion air is determined based on whether or not the combustion air needs to be cooled. Therefore, when the combustion air temperature is equal to or higher than the set temperature, it is necessary to cool the combustion air.

  In step a3, since the ATF temperature is lower than the cooling water temperature circulating in the radiator circuit 9 and the combustion air temperature is lower than the set temperature, the switching valve 23 is controlled to the first path (see FIG. 3), and the sub-water pump 16 is set to a stop state, and this flow is finished. In step a4, since the ATF temperature is not lower than the cooling water temperature circulating through the radiator circuit 9 or the combustion air temperature is not lower than the set temperature, the switching valve 23 is controlled to the second path (see FIG. 4), The sub-water pump 16 is activated and this flow ends.

  As shown in FIG. 3 according to the above-described flow, when the sub-water pump 16 is switched to the first path and the sub-water pump 16 is stopped, the cooling water flowing out from the inside of the engine 2 sequentially includes the bypass passage 11, the outflow passage 24, and the specific passage. Circulates through the passage 19, the hydraulic oil heat exchanger 8, the specific passage 19, the inflow passage 25, the bypass passage 11, the thermostat 13, the main water pump 12, and the engine 2. Therefore, the cooling water that has passed through the engine 2 and has cooled the engine 2 and has risen in temperature passes through the hydraulic oil heat exchanger 8. Thus, the temperature of the cooling water heated by the engine 2 is higher than the ATF temperature as shown in step a1. Thus, when the cooling water temperature is larger than the ATF temperature, it is a case of warm-up. Therefore, the ATF can be heated by setting the first path during warm-up.

  Further, when the combustion air temperature is lower than the set temperature, it is not necessary to cool the combustion air with the cooling water circulating in the low water temperature circuit 14, so there is no problem even if the sub water pump 16 is stopped. Therefore, the sub water pump 16 can be stopped and the cooling water heated by the engine 2 can be controlled to pass through the hydraulic oil heat exchanger 8.

  Further, as shown in FIG. 4, in the state where the path is switched to the second path by the switching valve 23 and the sub water pump 16 is activated, the cooling water circulates in the radiator circuit 9 and the low water temperature circuit 14 respectively. Since the ATF temperature is not lower than the cooling water temperature as shown in step a1, the ATF is not heated by the cooling water circulating through the radiator circuit 9 because the switching to the second path is performed in this way. In such a case, since it is a normal time after the warm-up operation is finished, as described above, the coolant circulating in the low water temperature circuit 14 which is lower in temperature than the coolant circulating in the radiator circuit 9 is used as the hydraulic oil heat exchanger 8. The ATF can be cooled by supplying to.

  Further, the switching to the second path is performed when the combustion air temperature is not lower than the set temperature as shown in step a2. Therefore, it is necessary to cool the combustion air. In such a case, the combustion air can be cooled by starting the sub water pump 16 and circulating the cooling water in the low water temperature circuit 14 as described above.

  As described above, when the hydraulic oil temperature control system 1 of the present embodiment is switched to the first path, the cooling water that has passed through the engine 2 flows through the cooling water passage 21 of the hydraulic oil heat exchanger 8. Therefore, the temperature of the ATF can be controlled by the cooling water that has passed through the engine 2. Further, when switching to the second path, the cooling water circulating in the low water temperature circuit 14 flows in the cooling water passage 21 of the hydraulic oil heat exchanger 8. Therefore, the temperature of the ATF can be controlled by the cooling water circulating in the low water temperature circuit 14. In addition, since the objects to be cooled are different from each other in the radiator circuit 9 and the low water temperature circuit 14, the temperatures of the circulating cooling water are different from each other. The control device 6 can heat and cool the temperature of the ATF by circulating each cooling water circulating through different flow paths to the hydraulic oil heat exchanger 8. Further, the radiator circuit 9 and the low water temperature circuit 14 are existing circulation paths mounted on the vehicle, so that the hydraulic oil temperature control system 1 can be installed by simply providing the hydraulic oil heating circuit 22 and the switching valve 23 as the connecting device 5. Can be realized. The operation and effect as described above can be achieved by the hydraulic oil temperature control system 1 having such a simple configuration.

  Further, in the present embodiment, the cooling water circulating through the radiator circuit 9 is hotter than the cooling water circulating through the low water temperature circuit 14, so that the high-temperature cooling water is activated by controlling to the first path when warming up. The oil heat exchanger 8 can be circulated through the cooling water passage 21. This makes it possible to heat the ATF in a short time when warming up. Thereby, the fuel consumption of the vehicle can be improved.

  Further, in the present embodiment, the low-temperature cooling water circulating in the low water temperature circuit 14 can be circulated through the cooling water passage 21 of the hydraulic oil heat exchanger 8 by controlling to the second path at normal times. By cooling the hydraulic oil in this way, it is possible to prevent the hydraulic oil from becoming hot at normal times.

  In the present embodiment, hydraulic oil temperature control system 1 includes main radiator 10, sub-radiator 15, and intercooler 18. In such a hydraulic oil temperature control system 1, the cooling water that cools the engine 2 is hotter than the cooling water that cools the combustion air, so the cooling water circulating in the radiator circuit 9 circulates in the low water temperature circuit 14. It is hotter than the cooling water. Therefore, the hydraulic oil temperature control system 1 of the present invention can achieve the operations and effects as described above.

  In the present embodiment, the intercooler 18 is not air-cooled but water-cooled. In the case of an air-cooled intercooler, the place where the air-cooled intercooler is installed is limited to the vicinity of the radiator. However, in the present embodiment, since the water-cooled intercooler 18 is used, a configuration in which an air-cooled intercooler is provided near the radiator. As a result, the distance between the intercooler 18 and the engine 2 can be shortened. As a result, the piping for supplying air to the engine 2 can be shortened, the air supply resistance can be reduced, and the space can be saved. Further, by shortening the piping, the turbo lag can be shortened and the response can be improved.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In the first embodiment described above, the object to be cooled other than the engine 2 is combustion air, but is not limited to combustion air, and may be another object to be cooled, such as exhaust gas.

  The switching means is realized by the switching valve 23, but is not limited to the switching valve 23, and other configurations for switching between the first path and the second path, for example, an on-off valve is provided for each pipe, and the switching valve 23 may be configured to perform the same operation as that in FIG.

It is a mimetic diagram showing the whole hydraulic oil temperature control system 1 composition of a 1st embodiment. 4 is a flowchart showing a procedure for determining a flow path of a switching valve 23 of the control device 6. It is a schematic diagram of the hydraulic-oil temperature control system 1 which shows the flow of the cooling water in the case of a 1st path | route. It is a schematic diagram of the hydraulic-oil temperature control system 1 which shows the flow of the cooling water in the case of a 2nd path | route.

Explanation of symbols

1 ... Hydraulic oil temperature control system 2 ... Engine (internal combustion engine)
DESCRIPTION OF SYMBOLS 3 ... Engine cooling device 4 ... Supply air cooling device 5 ... Connection device 6 ... Control apparatus (control means)
7 ... ATF circuit 8 ... Hydraulic oil heat exchanger 9 ... Radiator circuit (first circuit)
DESCRIPTION OF SYMBOLS 10 ... Main radiator 11 ... Bypass passage 14 ... Low water temperature circuit (2nd circuit)
DESCRIPTION OF SYMBOLS 15 ... Sub-radiator 18 ... Intercooler 19 ... Specific passage 20 ... Hydraulic oil passage 21 ... Cooling water passage 22 ... Hydraulic oil heating circuit (3rd circuit)
23 ... Switching valve 24 ... Outflow passage 25 ... Inflow passage

Claims (4)

A hydraulic oil temperature control system (1) for controlling the temperature of hydraulic oil for an automatic transmission of an internal combustion engine (2) mounted on a vehicle,
A first circulation path (9) through which cooling water for cooling the internal combustion engine circulates;
A second circulation path (14) for cooling a cooling object other than the internal combustion engine, in which cooling water having a temperature lower than that of the cooling water in the first circulation path circulates;
A third circulation path (22) connecting the first circulation path and the second circulation path, wherein the cooling water circulating through the first circulation path and passing through the internal combustion engine is A third circulation path that passes a predetermined specific passage (19) of the two circulation paths and returns the cooling water that has passed through the specific passage to the first circulation path;
The hydraulic oil and the cooling which are provided in the specific passage, have a hydraulic oil passage (20) through which the hydraulic oil passes and a cooling water passage (21) through which the cooling water passes, and pass through the hydraulic oil passage. A hydraulic oil heat exchanger (8) for exchanging heat with the cooling water passing through the water passage;
A first path through which the cooling water passing through the first circulation path passes through the cooling water path via the third circulation path, a path through which the cooling water circulates through the first circulation path, and the second circulation. And a switching means (23) for switching between a second path that forms a path through which the cooling water circulates in the path. And further includes control means (6) for controlling the switching means,
2. The hydraulic oil according to claim 1, wherein the control unit controls the switching unit to the first path when the cooling water circulating in the first circulation path is warmed up to a predetermined temperature or less. Temperature control system.   3. The hydraulic oil temperature according to claim 2, wherein the control unit controls the switching unit to the second path when the cooling water circulating in the first circulation path is normal higher than the predetermined temperature. Control system. The object to be cooled is combustion air sucked into the internal combustion engine,
A main radiator (10) provided in the first circulation path, for exchanging heat between the cooling water circulating in the first circulation path and outside air;
An intercooler (18) provided in the second circulation path for exchanging heat between the cooling water circulating in the second circulation path and the combustion air;
The sub-radiator (15), which is provided in the second circulation path and circulates through the second circulation path and exchanges heat with outside air, further includes: The hydraulic-oil temperature control system as described in any one of these.

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