JP2003286846A - Oil cooler module for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil cooler module for a transmission in which a fuel efficiency enhancement effect higher than that materialized by a rise of operating oil in an automatic transmission by an oil cooler can be attained and the number of assembling processes can be reduced and a cost is lowered as compared with a conventional oil cooler having an operating oil bypass function. <P>SOLUTION: In the oil cooler module 31, an introducing pipe 34 and a drain pipe 35 for circulating cooling water to the oil cooler and a bypass pipe 36 for allowing the cooling water to bypass are formed integrally with an oil cooler main body 32. A thermostat 29 for switching the circulation of the cooling water to the oil cooler and the bypass of the cooling water to the bypass pipe 36 is inserted from the drain pipe 35 and attached. The thermostat 29 allows the cooling water to bypass the oil cooler when the temperature of the cooling water is lower than a prescribed temperature and to circulate to the oil cooler when the temperature of the cooling water is the prescribed temperature or higher. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission oil cooler module for adjusting the temperature of hydraulic oil of a transmission to a set temperature by exchanging heat with the temperature of cooling water flowing out from a water-cooled engine.

[0002]

2. Description of the Related Art Conventionally, as a cooling device for a water-cooled engine, a technique described in Japanese Utility Model Publication No. 4-41972 is known. In the water-cooled engine cooling device described in this publication, an oil cooler that heats and cools the hydraulic oil of the transmission by using the cooling water of the engine and an air conditioner that coordinates the air in the vehicle interior are provided. It is provided.
As a result, even when the oil temperature is low, such as after the engine is started, by heating the hydraulic oil with the oil cooler,
By ensuring proper viscosity of hydraulic oil and reducing friction loss in the automatic transmission, the fuel efficiency of the vehicle is improved.

[0003]

However, the above-mentioned prior art has the following problems. That is, in a good season such as spring or autumn, the hydraulic fluid of the automatic transmission does not significantly decrease even if the engine is stopped. Furthermore, even when the air conditioner is used, since the difference between the target temperature that is considered to be set by the passenger and the outside air temperature is small, the cooling oil is used to heat the hydraulic oil while operating the air conditioner. Even if it does, fuel efficiency can be improved. However, in an environment where the outside air temperature is very low, such as in winter, the hydraulic oil of the automatic transmission becomes extremely low due to the continuation of the engine stop state. Further, the difference between the above-mentioned target temperature and the outside temperature becomes large, so that when heating the hydraulic oil and heating the vehicle interior, the energy used for heating the hydraulic oil is large, which causes air conditioning. There is a problem that the heating function of the device deteriorates and it takes time to reach the target temperature.

It is well known that operating an engine at a temperature as high as possible leads to improvement of fuel efficiency by reducing friction loss of the engine itself, but when the outside air temperature is low, it is necessary to heat the hydraulic oil. When heating is performed, there is a problem in that a rise in cooling water to the warm-up control temperature is delayed, the control time for increasing the fuel injection amount increases, and fuel consumption deteriorates.

In order to solve these problems, a bypass passage is opened in the oil circuit for circulating the hydraulic fluid of the transmission through the oil cooler, and the bypass passage is opened when the temperature of the hydraulic fluid is below a predetermined temperature. There is known an oil cooler for a transmission, which is provided with a valve that closes a bypass passage when the temperature exceeds a predetermined temperature (JP-A-6-272558). That is, when the oil temperature is equal to or lower than a predetermined temperature, the hydraulic oil is diverted to the bypass passage to avoid heat exchange with the cooling water, accelerate the rise of the water temperature, and prevent the heating function of the air conditioner from being deteriorated. At the same time, when the oil temperature exceeds a predetermined temperature, the bypass passage is closed, heat exchange between the hydraulic oil and the cooling water is executed, the hydraulic oil is raised, and friction loss of the automatic transmission is reduced. Is.

However, in the above-mentioned transmission oil cooler, since the avoidance and execution of heat exchange between the hydraulic oil and the cooling water are controlled based on the temperature of the hydraulic oil, the cooling water temperature is the warm-up control temperature. Even if it is less than this, there is a problem in that the heat exchange between the hydraulic oil and the cooling water is carried out and the temperature rise of the cooling water is hindered. Furthermore, in the above-mentioned known example, the case forming the outer circumference of the valve needs to be cut, and the assembling thereof also requires bolting work, etc., so that there is a problem that the assembling is troublesome and the cost is increased. there were.

The present invention has been made in view of the above problems, and it is possible to achieve a fuel consumption improvement effect more than the fuel consumption improvement effect due to the rise of hydraulic oil of an automatic transmission by an oil cooler and the conventional operation. It is an object of the present invention to provide an oil cooler module for a transmission, which can reduce the number of assembling steps and reduce the cost as compared with an oil cooler having an oil bypass function.

[0008]

According to a first aspect of the present invention, an oil cooler main body that circulates hydraulic fluid for a transmission is provided.
A cooling water flowing out of the water-cooled engine is separated from the working oil circulating in the oil cooler main body, an introduction path for introducing heat exchange with the working oil into the oil cooler main body, and a discharge path for discharging the cooling water to the outside. A bypass path connecting the introduction path and the discharge path to bypass the cooling water; a water temperature detecting means for detecting the water temperature of the cooling water; a circulation of the cooling water to an oil cooler; and a bypass path to the bypass path. Possible switching means, and switching control means for controlling switching of the switching means,
In the transmission oil cooler for adjusting the temperature of the hydraulic fluid of the transmission by heat exchange with the cooling water, the introduction path,
An exhaust passage and a bypass passage are formed integrally with the oil cooler body, and the water temperature detection means, the switching control means and the switching means are provided inside the introduction passage, the discharge passage or the bypass passage,
The switching control means outputs a command to the switching means to prohibit circulation of cooling water to the oil cooler when the detected water temperature is lower than a preset temperature, and the detected water temperature is equal to or higher than a preset temperature. When it becomes, a command for permitting the circulation of the cooling water to the oil cooler is set to be output to the switching means.

According to a second aspect of the invention, in the oil cooler module for a transmission according to the first aspect, the switching means is located at a confluence of the introduction path or the discharge path and the bypass path, and is preset. A switching valve that opens the bypass passage and closes the introduction passage or the discharge passage when the temperature is lower than a predetermined temperature, and closes the bypass passage and opens the introduction passage or the discharge passage when the temperature becomes equal to or higher than a preset temperature. To do.

According to a third aspect of the invention, in the oil cooler module for a transmission according to the first or second aspect, the water temperature detecting means, the switching control means and the switching means are switched by reaching a preset temperature. It is characterized in that it is a slide type switching valve using a thermostat.

According to a fourth aspect of the present invention, in the oil cooler module for a transmission according to the first to third aspects, a pipe in which the introduction passage, the discharge passage and the bypass passage are projected from the oil cooler body to the outside. It is characterized by

[0012]

In the oil cooler module for a transmission according to the present invention, there is provided switching means capable of switching between circulation of cooling water to the oil cooler and bypass to the bypass passage. Then, in the switching control means, when the detected water temperature is lower than the preset set temperature, a command for prohibiting the circulation of the cooling water to the oil cooler is output to the switching means, and the detected water temperature is preset. When the temperature is equal to or higher than the set temperature, it is controlled to output a command for permitting circulation of the cooling water to the oil cooler to the switching means. That is,
When the water temperature is lower than the set temperature, the water temperature can be raised faster and the engine can be operated at the highest temperature, so that it is possible to obtain more fuel efficiency improvement effects due to the increase in the hydraulic oil of the transmission by the oil cooler. As a result, it is possible to improve fuel efficiency, especially when the engine is started.

Further, in the oil cooler module for a transmission of the present invention, the introduction passage, the discharge passage and the bypass passage are formed integrally with the oil cooler main body, and the water temperature detection means, the switching means and the switching control means are provided in the introduction passage, the discharge passage. It is provided inside the road or bypass road. Therefore, assembling to the transmission housing etc. is completed simply by fixing the oil cooler main body, so compared to the oil cooler with the conventional cooling water bypass structure, the number of assembling steps can be reduced and the cost can be reduced. it can.

Further, the switching means is located at a confluence of the introduction passage or the discharge passage and the bypass passage, and when the temperature is lower than a preset temperature, the bypass passage is opened and the introduction passage or the discharge passage is closed, and the preset means is set. A switching valve that closes the bypass passage and opens the introduction passage or the discharge passage when the temperature exceeds a certain temperature may be used.

Further, the water temperature detecting means, the switching control means and the switching means may be a slide type switching valve which is controlled by a thermostat. With such a configuration, the water temperature detection means, the switching means, and the switching control means can be integrated to reduce the size of the system, and the assembly to the oil cooler becomes easy.

Further, the introduction passage, the discharge passage and the bypass passage may be pipes protruding outside the oil cooler body. With such a configuration, it is possible to avoid that the cooling water diverted to the bypass passage is deprived of heat by the oil cooler main body, and the water temperature can be raised more quickly.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in more detail below.

FIG. 1 is an explanatory view showing a cooling device for a water-cooled engine to which the transmission oil cooler module of the embodiment is applied. As shown in FIG. 1, the cooling device 1 has cooling water flowing out from a water-cooled engine (hereinafter, simply referred to as an engine) 2 via a cooling water circuit (cooling water distribution pipe) 3 arranged between headers 4 and 5. A radiator 7 as a heat exchanger for cooling the cooling water by circulating the cooling water in the tube 6.
Is provided.

An electric pump 8 is provided which is driven independently of the engine 2 and circulates cooling water between the engine 2 and the radiator 7. Although only the electric pump 8 is used in the present embodiment, the present invention is not limited to this configuration, and another configuration may be used as long as the circulation amount of the cooling water can be adjusted. For example, by using an electric pump as the main pump, combining a normal water pump driven by the engine as the sub pump, and adjusting the flow rate of the main pump based on the engine speed,
The configuration may be such that the circulation amount of the entire cooling water is adjusted.

Further, a temperature sensor 9 as a temperature detecting means for detecting the temperature of the cooling water in the engine 2 and a room temperature sensor 9a for detecting the room temperature are provided. In addition, a cooling water circuit 10 is provided in the middle of which an electric pump 8 is interposed to allow cooling water to flow from the radiator 7 to the engine 2. In addition, the fan 11 that blows air to the tube 6 of the radiator 7
A rotary drive motor 12 is provided. Also,
An electrically controllable thermostat that diverts the cooling water, which is interposed in the cooling water circuit 3 and is sent from the engine 2 toward the radiator 7, to the suction side of the electric pump 8 via the bypass circuit 13 according to the cooling water temperature. 14 are provided. Further, a control device 15 is provided which controls the drive output of the electric pump 8 and the rotation speed of the rotary drive motor 12 based on the detection value detected by the temperature sensor 9.

Further, the cooling water circuit 24 has an air conditioner 25.
Is provided in parallel with the cooling water circuit 24a. The cooling water circuit 24a includes an oil circulation path 28a for circulating oil with the automatic transmission 30, and an oil cooler 28 that exchanges heat with the oil of the automatic transmission 30.
An oil cooler module 31 integrally provided with a thermostat 29 for switching the communication of the cooling water circuit 24a to be connectable and disconnectable is provided. The oil cooler module 31 permits the cooling water to circulate in the oil cooler 28 when the temperature is higher than the warm-up control temperature (for example, 80 ° C.), and circulates the cooling water in the oil cooler 28 when the temperature is lower than the warm-up control temperature. Is set to prohibit. Therefore, when the cooling water is lower than 80 ° C., the automatic transmission oil is not cooled by the oil cooler 28, and when the cooling water is 80 ° C. or higher, the automatic transmission oil is cooled. The structure of the oil cooler module 31 will be described later.

A cooling water flow passage 23 is formed in the engine 2 so as to communicate with the cylinder head 21 and the cylinder block 22. The cooling water circuit 10 is connected to the end of the cooling water flow passage 23 on the cylinder head 21 side so as to communicate therewith. On the other hand, at the end of the cooling water flow passage 23 on the cylinder block 22 side, the cooling water circuit 3 described above is provided.
Are connected so that they communicate with each other. That is, the cooling water delivered by the electric pump 8 is set so as to enter from the cylinder head 21 side and be delivered from the cylinder block 22 side.

The radiator 7 is provided with, for example, headers 4 and 5 which are vertically spaced apart from each other, and a large number of tubes 6 which are arranged parallel to each other between the headers 4 and 5, so-called a longitudinal flow. However, a radiator having a so-called transverse flow structure may be used. The tube 6 is appropriately provided with heat exchange plate fins, corrugated fins, and the like.

The cooling water circuit 3 connected to the end of the cooling water flow passage 23 on the cylinder block 22 side is connected to the upper header 4 of the radiator 7. An electrically controllable thermostat 14 is provided in the middle of the cooling water circuit 3, and the flow rate WR flowing through the cooling water circuit 3 and the bypass circuit 1
The ratio WR: WB with the flow rate WB flowing through 3 is, for example, 100
℃ to 105 ℃, depending on the temperature of the cooling water 0:10
It is set to gradually change from 0 to 100: 0. The thermostat 14 is arranged in the middle of the cooling water circuit 10 that connects the lower header 5 and the engine 2, and the ratio WK of the flow rate WK flowing through the cooling water circuit 10 to the flow rate WB flowing through the bypass passage 13: It may be set to control WB.

Further, a rotary drive motor 12 in which a fan 11 for blowing air is attached to the tube 6 of the radiator 7.
Is connected to the control device 15 and is configured to control its rotation speed based on the rotation speed control signal Sr from the control device 15.

The electric pump 8 is configured to operate based on the flow velocity control signal Sv from the control device 15 to change the flow velocity of the cooling water.

The temperature sensor 9 is arranged so as to detect the temperature in the vicinity of the terminal end of the cooling water flow passage 23 of the cylinder block 22. In the present embodiment,
Although the detection end of the temperature sensor 9 is inserted and arranged in the cylinder block 22, the temperature near the outlet of the cooling water flow passage 23 may be detected.

The controller 15 controls the flow velocity generated by the electric pump 8, in particular, the pipe flow velocity of the radiator 7 and the rotation speed of the rotary drive motor 12 of the fan 11. In particular, by specifying the characteristics of the cooling water flowing through the pipe inside the radiator 7 under high load, power loss is reduced, and it is possible to achieve a significant improvement in fuel consumption.

Next, the structure of the oil cooler unit 31 will be described. FIG. 2 is a perspective view showing the oil cooler unit 31. In the figure, 32 is an oil cooler body, which is formed by laminating a plurality of plates. A flange portion 32a in which a bolt hole 32b is formed is projected from the lower portion of the oil cooler body 32.
Is fixed near the automatic transmission 30 by mounting bolts 30a.

On the upper surface of the oil cooler body 32, an oil inlet 33a for inflowing automatic transmission oil, an oil outlet 33b for outflowing automatic transmission oil, and cooling water from the cooling water circuit 24a are supplied to the oil cooler body. An introduction pipe 34 that is introduced into the inside 32 and a discharge pipe 35 that discharges the cooling water to the cooling water circuit 24a are provided in a protruding manner, respectively, and these are integrally formed with the oil cooler body 32. A cooling water inlet 34a is opened at the upper end of the introduction pipe 34, and a cooling water outlet 35a is opened at the upper end of the discharge pipe 35.

Between the introduction pipe 34 and the discharge pipe 35, a bypass pipe 36 that bypasses the cooling water is integrally formed. In addition, at the confluence portion of the discharge pipe 35 with the bypass pipe 36, the thermostat mounting hole 35
b is formed, and the thermostat 29 is inserted into the discharge pipe 35 through the thermostat mounting hole 35b, and then the fixing screw lid 35c closes the thermostat mounting hole 35b.

Next, the structure of the thermostat 29 will be described with reference to FIG. The thermostat 29 has a predetermined temperature,
For example, shape memory resin 29a that deforms when reaching 80 ° C
And a switching valve 29b of a slide type by a spring 29c
It has a structure that switches. This switching valve 29b is
When the temperature of the shape memory resin 29a is lower than 80 ° C., the bypass pipe 36 is opened and the discharge pipe 35 is closed by the spring 29c, as shown in FIG.

When the temperature of the shape memory resin 29a rises above 80 ° C., the shape memory resin 29a is deformed against the biasing force of the spring 29c as shown in FIG.
The bypass pipe 36 is closed and the discharge pipe 35 is opened. The shape resin 29a is 80
When the temperature returns to less than ° C, the shape memory resin 29a is deformed, and the switching valve 29b returns to the state of Fig. 3A due to the urging force of the spring 29c.

Before describing the control and operation of the cooling system 1 for a water-cooled engine in the present embodiment, the relationship between the water side Reynolds number in the radiator 7, the fan wind speed, and the power required for cooling is shown in FIG. Will be explained.

The graph shown in FIG. 6 shows that the core portion (heat dissipation portion) has a lateral dimension of 691.5 mm, a longitudinal dimension of 360 mm, and a depth dimension of 16 mm, when a high load is applied to a general longitudinal flow radiator (cooling water temperature is It is a figure which shows the power required for cooling in the state which reached 105 degreeC and the cooling water is circulating through the radiator 7). In the figure, the horizontal axis represents the water side Reynolds number of the radiator 7 and the fan wind speed (m / sec), and the vertical axis represents the power (W) required for cooling. As shown in FIG.
When the water side Reynolds number of the radiator 7 increases, the power of the electric pump 8 also increases accordingly. Then, when the fan wind speed increases, the fan power, that is, the power of the rotary drive motor 12 increases accordingly.

The sum of the pump power and the fan power, that is, the power required for cooling is low when the water side Reynolds number is 1800 to 6000, as shown in FIG. In the region where the power required for cooling is low, the flow state of the cooling water flowing in the tube 6 of the radiator 7 is a transition region between laminar flow and turbulent flow, and a turbulent flow region near this transition region. It extends to. In such a radiator, when the load is high, the electric pump 8 is controlled so that the Reynolds number is in the 1800 to 6000 region, and the fan 11 is controlled to be in the wind velocity region of 2.8 to 3.3 m / sec, which is necessary for cooling. It is possible to keep the power consumption low, which means that the fuel efficiency is improved at this time.

Incidentally, in terms of the performance of the radiator 7, the performance improvement of the fins formed on the outside of the tube 6 and the increase of the air volume are the points of performance improvement, but the Reynolds number on the water side of the cooling water decreases and turbulent flow occurs. When it disappears, the cooling performance of the cooling water deteriorates extremely, so it is important to use it in turbulent flow as much as possible.

Here, the optimum design for cooling will be described from the viewpoint of energy. In engine cooling with a radiator, we verify whether the balance of cooling water temperature, fan air volume, etc. is most suitable by calculating the energy required for cooling.

(Contribution rate of water amount / air amount in radiator alone) The heat radiation amount of the radiator is obtained by the following formula. (Formula 1) Q = κAΔT However, Q: Radiator heat dissipation (W), κ: Radiator heat transfer rate (W / mm ² K)

The K value is displayed by substituting the radiator performance, and is determined by the following factors. (Formula 2) 1 / κ = 1 / (αw · Aw / A) + d / (λt · Aw /
A) + 1 / αa · ηa (Formula 3) 1 / κ = 11 (%) + 0.1 (%) + 88.9 (%)

As shown in FIG. 7, λt is the tube conductivity (W / mK), and αa is the heat transfer coefficient on the air side (W / m ^2).
K), αw is water side heat transfer coefficient, ηa is fin integration efficiency (%), Aw is water side heat radiation area (mm ² ), A is air side heat radiation area (mm ² ), d is tube plate thickness (mm) Is. Also,
Formula 3 represents the contribution ratio of each term in Formula 2, and in the calculation, the core part (heat dissipation part) has a horizontal dimension of 691.5 mm, a vertical dimension of 360 mm, and a depth dimension of 16 mm. Using the one provided, a flow rate of 40 liters / second (Reynolds number 3500) and a wind speed of 3 m / second were used.

The relationship between the K value and the water side Reynolds number is shown in the graph of FIG. FIG. 8 also shows the flow state of the cooling water that changes with the water-side Reynolds number. From FIG. 8, the region where the power required for cooling is low in FIG. 6 described above, that is, the region where the Reynolds number of the cooling water in the tube is 1800 to 6000, is the cooling water flowing in the tube 6 of the radiator 7. It can be seen that the flow state of is extending over the transition region between the laminar flow and the turbulent flow and the turbulent flow region near the transition region.

In this state, the contribution rate to the performance on the water and air side is larger on the air side (88.9%) than on the water side (11%), as in the above mathematical formula 3. Therefore, when the required amount of supplementary heat is increased, it is possible to cool the engine with less power by fixing the amount of water and increasing the air amount of the fan (on the air side). In this way, by determining the Reynolds number of the cooling water in the range in which the power required for cooling is optimized, optimum control is possible in radiators of various forms. The present invention can be applied to a heat exchanger (of a water-cooled engine) including a heater core of any form in which cooling water flows in a pipe.

That is, the Reynolds number Re is Da, a mass velocity of cooling water is G, a viscosity coefficient is G, and a coefficient of viscosity is Da, which is obtained by multiplying a value obtained by dividing the cross-sectional area of water passage by the wet edge length (inner circumferential length) by 4. Μ
Then, it is represented by DaG / μ (equivalent diameter × mass velocity / viscosity coefficient), and if this Reynolds number Re is the same,
The flows are mechanically similar and have equal thermal conductivity. Therefore, by controlling the Reynolds number of the cooling water flowing through the various radiators 7 to fall within the range of 1800 to 6000 as described above, the power required for cooling the engine 2 (the sum of the pump power and the fan power). ) Can be the lowest. As a result, the power load can be reduced and the fuel efficiency of the engine can be significantly improved.

(Optimal Air Energy Balance for Cooling Radiator) Next, similarly to the radiator 7, the core portion (heat dissipation portion) has a lateral dimension of 691.5 mm, a longitudinal dimension of 360 mm, and a depth dimension of 16 mm. With a vertical flow radiator,
Radiator performance (radiator heat dissipation Q) and air volume (wind speed V)
The relationship between a) and the cooling water flow rate (Gw) is shown in the graph of FIG. The vertical axis represents the radiator heat radiation amount, and the horizontal axis represents the wind speed. In addition, Table 1 below shows the wind speed (V) for obtaining the same performance (radiator heat dissipation) (Q) with the same radiator.
The combination of a) and the cooling water flow rate (Gw) is shown. In this way, the same radiator heat dissipation flow rate of 3.4 × 104W
It is possible to appropriately select the combination of the wind speed and the flow rate of the cooling water for producing

[0046]

[Table 1] (Amount of Energy Required for Cooling) Next, when the required energies are compared using the theoretical power represented by the following formula 4 on both the air side and the cooling water side, the results shown in the table below are obtained. (Formula 4) P = ρgQH where P: power (W), ρ: fluid density (kg / m ³ ),
g: Gravitational acceleration (m / s ² ), Q: Flow rate (m ³ / s), H: Pressure difference (m)

[0047]

[Table 2] In Table 2 above, the total required power is the minimum at 280 W, and the Reynolds number at that time is 2600, and the Reynolds number range (1800 to 600) that minimizes the power required for cooling described above.
You can confirm that it is in 0).

By the way, the air-side contribution to the radiator performance is large, but the water-side contribution is small. Therefore, as for the amount of energy, the amount of energy required to cool the engine can be reduced by decreasing the flow rate of the cooling water and increasing the air flow rate. However, if the flow rate of the cooling water decreases to the laminar flow region, the performance on the water side is extremely deteriorated, which is not preferable.

(Control Method of Embodiment) The control method and operation of the cooling device 1 for the water-cooled engine will be described with reference to the flowchart shown in FIG. 4 and the diagram showing the relationship between the water temperature and the fan air flow and the water flow shown in FIG. To do. Output data of the electric pump 8 corresponding to the optimum water side Reynolds number shown in FIG. 6 is stored in a memory unit (not shown) provided in the control device 15,
The output data of the rotary drive motor 12 corresponding to the fan wind speed are stored.

In step 101, the electric pump 8 is operated at a flow rate as low as possible (hereinafter, lower limit flow rate) that does not cause local boiling of the cooling water in the engine, for example, 10 L / min.

In step 102, the water temperature detected by the temperature sensor 9 is read.

In step 103, it is judged whether or not the air conditioner switch is turned on. When it is turned on, the process proceeds to step 104, and when it is not turned on, the step 1 is performed.
Go to 20.

At step 104, the detected value detected by the room temperature sensor 9a and the set target temperature are read, and the routine proceeds to step 105.

In step 105, it is judged whether or not the read detection value of the room temperature sensor 9a is higher than the target temperature. If it is higher than the target temperature, the process proceeds to step 120, and if it is lower than the target temperature, the process proceeds to step 106.

In step 106, cooling water is caused to flow into the heater core 26 so that the water side Reynolds number in the tube becomes 2600, and the process proceeds to step 107.

In step 107, it is judged whether or not the water temperature is higher than 80 ° C. If it is higher than 80 ° C., the process proceeds to step 108, and if it is 80 ° C. or lower, the process proceeds to step 109.

In step 108, warm water is flown through the oil cooler 28 and the process proceeds to step 112. Also in the oil cooler 28, it is desirable that the Reynolds number on the cooling water side be near 2600.

At step 109, the cooling water is prevented from flowing through the oil cooler 28, and the routine proceeds to step 110.

In step 110, the fan 11 is prevented from driving.

In step 111, the thermostat 14
The cooling water passage 3 is fully closed, and the bypass circuit 13 is fully opened.

In step 112, it is judged whether or not the water temperature is higher than 105 ° C. If the temperature is high, the process proceeds to step 113, and if it is low, the process proceeds to step 117.

In step 113, the thermostat 14
The cooling water circuit 3 is fully opened, the bypass circuit 13 is fully closed, and the routine proceeds to step 114.

In step 114, it is determined whether or not the electric pump 8 is driven so that the water side Reynolds number of the radiator 7 is 2600. If so, the process proceeds to step 115, otherwise the process proceeds to step 116. .

In step 115, the drive of the fan 11 is increased.

In step 116, the electric pump 8 is driven so that the water side Reynolds number of the radiator 7 becomes 2600.

In step 117, the thermostat 14
Is the flow rate WR flowing through the cooling water circuit 3 and the bypass circuit 1
The ratio WR: WB with the flow rate WB flowing through 3 is gradually changed from 0: 100 to 100: 0 depending on the temperature of the cooling water, and is flowed.

That is, immediately after the engine is started, the electric pump 8 is driven at a flow rate of 10 L / min (corresponding to FIG. 5).
At this time, the circulation of the cooling water to the oil cooler 28 is prohibited. Then, the cooling water flows through the cooling water flow passage 23 of the cylinder head 21 and the cylinder block 22. Along with this, the temperature sensor 9 starts detecting the temperature in the cooling water flow passage 23 of the cylinder block 22. In the thermostat 14, until the temperature of the circulating cooling water reaches, for example, 100 ° C., the cooling water is circulated to the bypass circuit 13 so as to bypass the radiator 7.

Next, it is judged whether or not the air conditioner is switched on. Here, when the switch is not turned on, the temperature value detected by the temperature sensor 9 is 80
It is determined whether the temperature is higher than ℃. If the cooling water temperature is higher than 80 ° C. in this determination, warm water is flowed through the oil cooler 28 (corresponding to FIG. 5).

On the other hand, in step 105, it is determined whether or not the vehicle interior temperature is higher than the target temperature of the air conditioner 25. When the vehicle interior temperature is lower than the target temperature, the electric pump 8 is driven so that the Reynolds number of the hot water flowing through the tube of the heater core 26 becomes 2600.

When the temperature of the cooling water coming out of the cylinder block 22 rises to 80 ° C. with the operation of the engine 2, the thermostat 29 opens the cooling water circuit 24a and causes the cooling water to flow to the oil cooler 28 (see FIG. 5). Equivalent to).

Next, in step 112, when the cooling water temperature is lower than 105 ° C., the thermostat 14 determines the flow rate WR through the cooling water circuit 3 and the flow rate WB through the bypass circuit 13 according to the cooling water temperature. The ratio of is gradually changed and distributed.

At this time, when the temperature detected by the temperature sensor 9 does not reach the predetermined target temperature of 105 ° C., the rotary drive motor 12 is not normally driven and the fan 1
No. 1 is not rotating, and the cooling water passing through the tube 6 only exchanges heat with the traveling outside air. In step 108, it is determined whether or not the fan 11 is driven, and if the fan 11 is not driven, the detection of the cooling water temperature is continued. When the fan 11 is driven, the fan 11 is controlled so that the cooling water temperature in the cooling water flow passage 23 of the cylinder block 22 becomes 105 ° C.
Controls the number of revolutions of to be low and continues to detect the cooling water temperature.

The cooling water discharged from the header 5 is supplied to the electric pump 8
And is sent to the cooling water flow passage 23 of the cylinder head 21 via the cooling water circuit 10. When the air conditioner 25 is operating, a fan air volume may be generated according to a request from the air conditioner 25 side.

The cooling water temperature, that is, the temperature sensor 9
If the detected temperature of is higher than 105 ℃, thermostat 1
4, the bypass circuit 13 is fully closed, the cooling water circuit 3 is fully opened, and the cooling water is circulated to the radiator 7.

Then, in step 114, the electric pump 8 determines whether or not the water side Reynolds number of the tube 6 is 2600. When the water side Reynolds number is 2600, the controller 15 outputs the rotation speed control signal Sr to the rotary drive motor 12 so that the cooling water temperature in the cooling water flow passage 23 of the cylinder block 22 becomes 105 ° C. The fan 11 is controlled to increase its rotation. On the other hand, when the water-side Reynolds number is not 2600, the drive of the electric pump 8 is controlled so that the water-side Reynolds number is 2600, and the temperature sensor 9
The detection of the cooling water temperature is continued (corresponding to FIG. 5).

(Operation and Effect of Embodiment) In the water-cooled engine cooling device of the embodiment, the water temperature detected by the temperature sensor 9 is a preset temperature (80 ° C.).
When the temperature is less than, the circulation of cooling water to the oil cooler 28 is stopped by the thermostat 29, and when the water temperature is equal to or higher than a preset temperature (80 ° C.), the cooling water is circulated to the oil cooler 28 by the thermostat 29. To be controlled. That is, when the water temperature is lower than the set temperature, the water temperature rises quickly to the warm-up control temperature and the engine is operated at a temperature as high as possible to reduce friction loss of the engine itself and increase the fuel injection amount control time. By shortening, it becomes possible to obtain a fuel consumption improvement effect that is higher than the fuel consumption improvement effect due to an increase in hydraulic oil of the automatic transmission 30 by the oil cooler 28, and in particular, it is possible to improve fuel consumption at the time of engine start.

When the air conditioner is switched on and the room temperature is lower than the target temperature, the circulation of the cooling water to the oil cooler 28 is stopped. That is, in an environment where the outside air temperature is extremely low, such as in winter, the difference between the outside air temperature and the target temperature in the passenger compartment set by the passenger is large, so that heating of the hydraulic oil and air conditioning are performed. As a result, the energy used for heating the hydraulic oil is large, the heating function of the air conditioner deteriorates, and it takes time to reach the target temperature.
However, the cooling water temperature is 80 ℃ until the target warm-up is achieved.
In case of less than, by prohibiting the operation of the oil cooler,
Stable air conditioning can be achieved without deteriorating the heating function of the air conditioning apparatus.

An air conditioner for circulating cooling water is provided in the tube, and the flow state of the cooling water in the tube is set to at least one of the transition region between the laminar flow region and the turbulent flow region and the turbulent flow region adjacent to this transition region. The distribution means may be controlled within a range including one of the areas. That is, the heat exchange efficiency of the air conditioner is improved, and the time for achieving the target temperature can be shortened.

Further, although the embodiment has been described by taking the example in which the preset temperature is set to 80 ° C., the present invention is not limited to this, and the increase control of the fuel injection amount at the time of starting is performed. It suffices if the temperature is equal to or higher than the predetermined temperature (warm-up control temperature).

Further, in the embodiment, the thermostat 14 is set so as to gradually change from 0: 100 to 100: 0 depending on the cooling water temperature, for example, between 100 ° C and 105 ° C. Although the present invention is not limited to this, the set temperature may be changed according to the characteristics of the engine, and the set temperature is variable according to the load state of the engine. Is also good.

The oil cooler module 31 includes the introduction pipe 34, the discharge pipe 35 and the bypass pipe 3.
6 is integrally formed with the oil cooler main body 32 that covers the oil cooler 28, and the thermostat 29 is attached by being inserted into the inside from the thermostat attachment hole 35 b of the discharge pipe 35.

Therefore, the thermostat 29 is inserted into the inside of the thermostat mounting hole 35b of the discharge pipe 35, and is closed with the fixing screw lid 35c, and the oil cooler main body 32 is closed.
Since the assembly to the automatic transmission housing is completed only by fastening the flange portion 32a of the above with the mounting bolt 30a, the number of assembling steps can be reduced and the cost can be reduced as compared with the conventional product.

Although the present embodiment has been described above, the specific configuration of the present invention is not limited to the present embodiment, and any design change that does not depart from the gist of the invention is included in the present invention.

[Brief description of drawings]

FIG. 1 is a schematic explanatory view showing a water-cooled engine cooling device to which an oil cooler module of an embodiment is applied.

FIG. 2 is a perspective view showing the oil cooler module of the embodiment.

FIG. 3 is a longitudinal sectional view of an essential part of an oil cooler module.

FIG. 4 is a flowchart showing the content of control in the embodiment.

FIG. 5 is a diagram showing a relationship between an engine water temperature, a fan air volume, and a water flow rate in the embodiment.

FIG. 6 is a graph showing the relationship between the power required for cooling, the radiator water side Reynolds number, the fan wind speed, and the relationship between the fan power and the pump power in the embodiment.

FIG. 7 is an explanatory diagram showing a cooling water flowing in the tube and a heat transfer system.

FIG. 8 is a graph showing a relationship between a K value, a water side Reynolds number, and a fan wind speed.

FIG. 9 is a graph showing the relationship between radiator heat radiation and fan wind speed.

[Explanation of symbols]

1 Cooling device 2 engine 3 Cooling water circuit 4,5 header 6 tubes 7 radiator 8 electric pumps 9 Temperature sensor 9a Room temperature sensor 10 Cooling water circuit 11 fans 12 rotation drive motor 13 Bypass circuit 14 Thermostat 15 Control device 16 cylinder head 17 cylinder block 23 Cooling water flow passage 24 Hot water flow passage 24a Cooling water circuit 24b thermostat circuit 25 Air conditioner 26 heater core 27 Electromagnetic valve 28 oil cooler 29 Thermostat 29a shape memory resin 29b switching valve 29c spring 30 automatic transmission 31 Oil cooler module 32 Oil cooler body 32a Flange part 32b bolt hole 33a Oil inlet 33b Oil outlet 34 Introduction pipe 34a Cooling water inlet 35 discharge pipe 35a Cooling water discharge port 35b Thermostat mounting hole 35c Fixing screw lid 36 Bypass pipe

─────────────────────────────────────────────────── ─── Continued Front Page (51) Int.Cl. ⁷ Identification Code FI Theme Coat (Reference) F28F 27/00 511 F28F 27/00 511D

Claims (4)

[Claims] Claim: What is claimed is: 1. An oil cooler body for circulating operating oil of a transmission and cooling oil flowing out of a water-cooled engine are separated from the operating oil for circulating in the oil cooler body and exchange heat with the operating oil in the oil cooler body. An introduction path that can be introduced and a discharge path that discharges the cooling water to the outside, a bypass path that connects the introduction path and the discharge path to bypass the cooling water, and a water temperature detection unit that detects the water temperature of the cooling water, The transmission includes a switching unit that can switch between circulation of the cooling water to an oil cooler and bypass to a bypass passage, and switching control unit that controls switching of the switching unit, and a transmission by heat exchange with the cooling water. In an oil cooler for a transmission for adjusting the temperature of hydraulic oil, the introduction passage, the discharge passage and the bypass passage are formed integrally with the oil cooler body, and the water temperature detection means, the switching control means and the switching means are provided. The switching control means is provided inside the introduction path, the discharge path or the bypass path, and the switching control means is provided to the switching means with a command to prohibit the circulation of the cooling water to the oil cooler when the detected water temperature is lower than a preset temperature. An oil cooler for a transmission characterized in that a command for permitting circulation of cooling water to the oil cooler is output to the switching means when the detected water temperature exceeds a preset temperature. module. 2. The transmission oil cooler module according to claim 1, wherein the switching means is located at a confluence of the introduction path or the discharge path and the bypass path, and is lower than a preset temperature. An oil cooler for a transmission, which is a switching valve that opens the bypass passage and closes the introduction passage or the discharge passage, and closes the bypass passage and opens the introduction passage or the discharge passage when the temperature exceeds a preset temperature. module. 3. The oil cooler module for a transmission according to claim 1, wherein the water temperature detecting means, the switching control means, and the switching means are a slide type using a thermostat that switches when a preset temperature is reached. An oil cooler module for a transmission, which is characterized by being a switching valve. 4. The oil cooler module for a transmission according to claim 1, wherein the introduction passage, the discharge passage, and the bypass passage are pipes protruding from the oil cooler body to the outside. Transmission oil cooler module.