JP2002323116A - Circulating device for hydraulic fluid - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a circulating device for hydraulic fluid capable of heating hydraulic fluid itself, utilizing heat of the hydraulic fluid of a power transmission device. SOLUTION: In this circulating device for hydraulic fluid provided with a function for taking out the hydraulic fluid of the power transmission device from the power transmission device and returning the taken out hydraulic fluid to the power transmission device, a heat storage device 25 is provided for holding the hydraulic fluid taken out of the power transmission device at the external part of the power transmission device, when the temperature of the hydraulic fluid on the power transmission device side exceeds a prescribed value of temperature and for returning the hydraulic fluid held at the external part of the power transmission device to the power transmission device, when the temperature of the hydraulic fluid of the power transmission device side is below the prescribed value of temperature.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for circulating hydraulic oil of a power transmission device.

[0002]

2. Description of the Related Art Generally, in a power transmission device, for example, a hydraulic power transmission device and a hydraulically controlled transmission,
The power transmission state is controlled by the hydraulic oil. That is, the fluid power transmission device is arranged on the output side of the engine, and the fluid power transmission device includes a driving-side rotating member and a driven-side rotating member. Power is transmitted between the driving side rotating member and the driven side rotating member. On the other hand, when the hydraulic control type transmission is configured by a gear transmission mechanism and a plurality of friction engagement devices, by controlling the supply / discharge state of hydraulic pressure acting on the friction engagement devices, the input rotation member and The gear ratio between the output rotary member and the output rotary member is controlled.

[0003] The above-mentioned hydraulic oil has a characteristic that its viscosity changes with a change in temperature. Therefore, depending on the temperature, there is a possibility that the control of the power transmission state of the hydraulic power transmission device or the shift control of the transmission may be affected. Specifically, when the viscosity of the hydraulic oil used in the fluid power transmission device increases, the shear resistance at the contact surface between the drive-side rotating member and the hydraulic oil increases, and the fuel efficiency may decrease. . On the other hand, in a hydraulically controlled transmission, there is a problem in that the supply and discharge of hydraulic oil in the hydraulic circuit is delayed, and the responsiveness of the shift control is reduced.

[0004] Therefore, there has been proposed a hydraulic oil heating device capable of avoiding the above-mentioned disadvantages by warming the hydraulic oil of the power transmission device. One example of such a device is disclosed in Japanese Patent Application Laid-Open No. Hei 8-246873. Has been described. The device described in this publication has a heat storage tank having a heat insulating structure in a circuit on a cooling water outlet side of a water-cooled internal combustion engine. Then, high-temperature cooling water is sent to the heat storage tank, and the heat is stored in the heat storage tank. When cold, the engine oil and the transmission operating oil can be heated by the heat of the heat storage tank.

[0005]

Incidentally, in the fluid type power transmission device, the temperature of the hydraulic oil rises due to friction at the contact portion between the drive side rotary member and the driven side rotary member and the hydraulic oil. On the other hand, in a transmission, the temperature of the hydraulic oil increases due to meshing between gears constituting a gear transmission mechanism or slipping of a friction engagement device. However, in the device described in the above publication, there is no recognition that the heat generated on the power transmission device side is used for warming the hydraulic oil itself, and there is room for improvement in that respect. Was.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a hydraulic oil circulation device that can heat the hydraulic oil itself by utilizing the heat of the hydraulic oil of a power transmission device. I have.

[0007]

Means for Solving the Problems and Action Therefor To achieve the above object, according to the first aspect of the present invention, the hydraulic oil of the power transmission device is taken out from the power transmission device, and the taken-out hydraulic oil is taken out of the power transmission device. In a hydraulic oil circulation device having a function of returning to the power transmission device, when the temperature of the hydraulic oil on the power transmission device side exceeds a predetermined temperature, the hydraulic oil taken out of the power transmission device is supplied to the outside of the power transmission device. And a holding device for returning the working oil held outside the power transmission device to the power transmission device when the temperature of the hydraulic oil on the power transmission device side is equal to or lower than a predetermined temperature. It is characterized by the following.

According to the first aspect of the invention, when the temperature of the hydraulic oil on the power transmission device side exceeds a predetermined temperature, the hydraulic oil is sent to a location other than the power transmission device. Therefore, an increase in the internal pressure of the power transmission device is suppressed. On the other hand, when the temperature of the hydraulic oil on the power transmission device side is equal to or lower than the predetermined value temperature, the high-temperature hydraulic oil held in the holding device is returned to the power transmission device. Therefore, the increase in the viscosity of the hydraulic oil on the power transmission device side is suppressed, and the shortage of the hydraulic oil is eliminated.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, the holding device stores the hydraulic oil and operates a tank disposed in a vacuum chamber, and stores the hydraulic oil in the tank. An air passage disposed in the vacuum chamber for returning the air contained in the oil to the power transmission device side.

According to the second aspect of the invention, in addition to the same effect as the first aspect of the invention, when the hydraulic oil taken out of the power transmission device is held in the holding device, the hydraulic oil is contained in the hydraulic oil. The returned air is returned to the power transmission device side.

According to a third aspect of the present invention, in addition to the configuration of the second aspect, the air passage and a return oil passage for returning hydraulic oil held in the holding device to the power transmission device side are arranged in parallel. And a throttle portion having a flow area smaller than the flow area of the air passage is connected to a downstream side of the air pipe in the flow direction of the air.

According to the third aspect of the invention, in addition to the same effect as that of the second aspect of the invention, the time when the hydraulic oil is returned to the power transmission device and the time when the air is returned to the power transmission device are: Since the adjustment is automatically performed by the throttle portion, there is no need to provide a mechanism for adjusting the two timings in the air passage and the return oil passage.

[0013] In the invention of each claim, "the hydraulic oil of the power transmission device" means to generate a force (specifically, hydraulic pressure) for controlling the state (in other words, operation) of the components of the power transmission device. Or it refers to the fluid used to lubricate and cool the components of the power transmission.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of the present invention will be described with reference to the drawings. FIG. 2 is a diagram showing a schematic configuration of a vehicle to which the present invention is applied. In FIG. 2, an engine 1, which is a driving force source of a vehicle, is a power device that burns fuel and outputs power from a crankshaft 8. As the engine 1, an internal combustion engine, for example, a diesel engine, a gasoline engine, An LPG engine, a methanol engine, a hydrogen engine, or the like can be used. Further, a cooling device 2 that cools a cylinder block, a cylinder head, and the like that constitute the engine 1 is provided. The cooling device 2 includes a water pump 3 driven by a crankshaft 8, a fan 4 driven by the crankshaft 8, a radiator 5 through which cooling water flows, and cooling water between the engine 1 and the radiator 5. An upper hose 6 and a lower hose 7 to be circulated are provided. That is, the engine 1 is a so-called water-cooled engine in which overheating is prevented by cooling water.

On the output side of the engine 1, a hydraulic power transmission 9 is provided. Fluid power transmission 9
Is the drive-side rotating member 1 connected to the crankshaft 8
0 and a driven-side rotating member 11 capable of transmitting power by kinetic energy of hydraulic oil between the driven-side rotating member 10 and the driven-side rotating member 10. The fluid power transmission 9
May be either a torque converter having a function of amplifying torque transmitted between the driving-side rotating member 10 and the driven-side rotating member 11, or a fluid coupling having no function of amplifying torque.

A transmission 12 is provided on the output side of the hydraulic power transmission device 9. The transmission 12 controls the transmission mechanism 15 by hydraulic pressure, thereby connecting the input rotary member 13 and the output rotary member 14 to each other. This is a transmission that can change the speed ratio between the transmissions. The transmission 12 is a stepped transmission in which the speed ratio can be switched stepwise, that is, discontinuously, or a stepless transmission in which the speed ratio can be steplessly, that is, continuously switched. Any of the machines may be used. The stepped transmission includes a planetary gear mechanism and a plurality of frictional engagement devices. Examples of the continuously variable transmission include a known belt-type continuously variable transmission and a toroidal-type continuously variable transmission. Further, a hydraulic control device 16 that controls hydraulic pressure of hydraulic oil supplied to the transmission 12 and the hydraulic power transmission device 9 or controls switching of an oil passage is provided.

The hydraulic control unit 16 is pumped by an oil pan (not shown) for storing hydraulic oil and an oil pump (not shown) driven by the power of the engine 1 or another power device. Switching of a hydraulic circuit (not shown) through which hydraulic oil flows, and an oil path constituting the hydraulic circuit;
And various solenoid valves (not shown) for controlling the hydraulic pressure of the hydraulic circuit. The amount of oil in the oil pan can be checked by an occupant of the vehicle using an oil level gauge inserted into the oil filler tube 12A.

The hydraulic control device 16 is connected to an inlet pipe 17 for sending hydraulic oil of the hydraulic circuit of the hydraulic control device 16 to the radiator 5 side, and also controls the hydraulic oil sent to the radiator 5 side. An outlet pipe 18 for returning to the device 16 is provided. In addition, a control valve 19,
20 are provided separately.

Further, a supply pipe 21 branched from the control valve 19 in the inlet pipe 17 and the hydraulic control device 16 is provided, and a discharge pipe branched from the control valve 20 in the outlet pipe 18 and the hydraulic control device 16. 2
2 are provided. These supply pipe 21 and discharge pipe 22 are provided with control valves 23 and 24 separately.

The supply pipe 21 and the discharge pipe 22 are connected to a heat storage device 25. FIG. 1 is a cross-sectional view illustrating a configuration of a heat storage device 25. The heat storage device 25 includes a hollow casing 26 made of a heat insulating material, and a casing 26.
And a tank 27 housed inside. As a heat insulating material constituting the casing 26 and the tank 27,
For example, glass wool and the like can be mentioned. A vacuum chamber A1 functioning as a heat insulating layer is formed between the casing 26 and the tank 27.

The tank 27 has a top plate 28, a side plate 29 having the top plate 28 connected to the upper end thereof, and a bottom plate 30 connected to the lower end of the side plate 29. The supply pipe 21 and the discharge pipe 22 are connected to the bottom plate 30. In this way, the supply pipe 21 and the discharge pipe 22
Open to the hydraulic oil chamber B1 inside. That is, it can be said that the tank 27 is a so-called inverted thermos-type heat storage tank in which the supply pipe 21 and the discharge pipe 22 are connected to the lower part.

On the other hand, an air pipe 31 opening to the hydraulic oil chamber B 1 is attached to the top plate 28, and this air pipe 31 is connected to the discharge pipe 22. This air pipe 3
Most of 1 is arranged in the vacuum chamber A1. An atmosphere opening pipe 32 is connected to a portion of the air pipe 31 corresponding to the vacuum chamber A1. The open-to-atmosphere pipe 32 is open to the outside of the casing 26. A control valve 33 is provided at a connection point between the air pipe 31 and the atmosphere open pipe 32. The control valve 33 is a three-way valve.

Further, a throttle portion C1 is formed at a connection portion between the air pipe 31 and the discharge pipe 22. The flow area (in other words, the opening diameter) of the constricted portion C1 and the region 35 other than the constricted portion C1 in the air pipe 31 are different. That is, the flow area of the narrowed portion C1 is equal to the area 35.
Is set to be smaller than the distribution area.

FIG. 3 is a block diagram showing a control circuit of the system shown in FIGS. That is, an electronic control unit 36 is provided, and the electronic control unit 36 includes an arithmetic processing unit (CPU or MPU) and a storage unit (RO).
M, RAM) and a microcomputer having an input / output interface.

The electronic control unit 36 receives a signal from a cooling water temperature sensor 37 for detecting the temperature of the cooling water on the cooling device 2 side,
The signal of the transmission oil temperature sensor 38 for detecting the operating oil temperature on the hydraulic control device 16 side, the signal of the heat storage tank oil temperature sensor 39 for detecting the temperature of the operating oil in the tank 27, and the signal of the operating oil in the tank 27 A signal of a hydraulic oil amount detection sensor 40 for detecting the amount, a signal of a vehicle speed sensor 41, a signal of an accelerator opening sensor 42, and the like are input. From the electronic control unit 36,
Control signals for the control valves 19, 20, 23, 24, and 33, control signals for the hydraulic control device 16, and the like are output. In FIG. 2, a cooler 5A driven by power other than the power of the engine 1 can be used instead of the cooling device 2.

FIG. 4 shows an embodiment in which a part of the system shown in FIG. 2 is modified. In FIG. 4, the cooling device 2 of FIG.
, A cooler 104 is provided. Cooler 104
Is connected to the discharge pipe 101 and the return pipe 102,
0. Discharge pipe 101 and return pipe 102
Is connected to a cooling water flow passage (not shown) of the engine 1, and a discharge pipe 101 and a return pipe 102 are connected by a heat exchange unit 100. Other configurations in FIG.
Since the configuration is the same as that in FIG. 2, the same reference numerals as those in FIG. For the system of FIG.
Control system can be applied.

Here, the correspondence between the configuration shown in FIGS. 1 to 4 and the configuration of the present invention will be described. The hydraulic power transmission 9 and the transmission 12 correspond to the power transmission of the present invention. , Discharge pipe 22 and outlet pipe 18
Correspond to the return oil passage of the present invention, and the air pipe 31 corresponds to the air passage of the present invention.

Next, control applied to the system shown in FIGS. 1 to 4 will be described. First, the system of FIG. 2 will be described. When the engine 1 is operated, the water pump 3 is driven by the power of the crankshaft 8,
The cooling water circulates through the cooling water flow path in the cooling device 2, and the cooling water to which the heat of the engine 1 is transmitted is sent to the radiator 5. On the radiator 5 side, the airflow generated by the running and the airflow generated by the fan 4 are generated, and the heat of the cooling water is transmitted to the pipes, and heat exchange is performed by forced convection at the contact surface between the pipes and the atmosphere. Is taken away, and the cooling water is returned to the engine 1 side.

On the other hand, the power of the engine 1 is transmitted to the transmission 12 via the hydraulic power transmission device 9. And
Based on a signal from the vehicle speed sensor 41, a signal from the accelerator opening sensor 42, and data stored in advance in the electronic control unit 36, a control signal to the hydraulic control unit 16 is output, and shift control of the transmission 12 is performed. . At the time of this shift control, the heat generating portion of the speed change mechanism 15 is lubricated and cooled by the hydraulic oil. As a result, the temperature of the hydraulic oil increases. Further, in the hydraulic power transmission device 9, when power is transmitted between the driving side rotating member 10 and the driven side rotating member 11 by the kinetic energy of hydraulic oil, the driving side rotating member 10 and the driven side rotating member The temperature of the hydraulic oil rises due to the frictional heat of the contact surface between 11 and the hydraulic oil.

On the other hand, in the system of FIG. 4, the cooling water of the engine 1 is subjected to heat exchange by forced convection at a contact surface between the pipe and the atmosphere, and heat of the cooling water is taken away. Cooling water is returned to the engine 1 side. "

Next, various controls based on the temperature of the hydraulic oil will be described. Various controls are performed when the temperature of the hydraulic oil on the hydraulic control device 16 side is equal to or lower than the first predetermined temperature (case A).
And a case where the temperature exceeds the first predetermined temperature (case B).

* Case A In this case A, the operation oil is further stored in the heat storage device 25 (in other words, stored or held),
Or, even when the hydraulic oil is stored in the heat storage device 25, the temperature of the hydraulic oil stored in the heat storage device 25 is lower than the temperature of the hydraulic oil on the hydraulic control device 16 side (case a1).
And the case where the temperature of the hydraulic oil stored in the heat storage device 25 is higher than the temperature of the hydraulic oil on the hydraulic control device 16 side (case a2).

* Case a1 The case a1 will be described separately for a case (case) corresponding to the system of FIG. 2 and a case (case) for the system of FIG. In this case, when the cooling water temperature is equal to or lower than the hydraulic oil temperature on the hydraulic control device 16 side (case-
1) and the case where the cooling water temperature exceeds the hydraulic oil temperature on the hydraulic control device 16 side (case-2).

* Case In the case of the system of FIG. 2, the control valves 19, 20,
Control for closing 23 and 24 is performed. When this control is performed, the hydraulic oil is trapped in the transmission 12, the hydraulic power transmission device 9, and the hydraulic control device 16 side.
Therefore, as described above, the temperature of the hydraulic oil increases due to the frictional heat of the hydraulic power transmission device 9 and the transmission 12, and the warming-up of the hydraulic power transmission device 9 and the transmission 12 is promoted.

By the way, in recent years, by gradually changing the hydraulic pressure of the hydraulic chamber involved in the shift control of the transmission 12, the shock at the time of shifting can be reduced and the shift feeling can be improved. 2. Description of the Related Art Various types of solenoid valves have been increasing for the purpose of controlling the engagement pressure of a lock-up clutch provided in a power transmission device with high accuracy and improving fuel efficiency. For this reason, the valve body to which these solenoid valves are attached and which is provided with a hydraulic circuit tends to be large. As described above, as the size of the valve body increases, the total length of the hydraulic circuit increases accordingly, and it is necessary to increase the amount of hydraulic oil flowing into the hydraulic circuit.

However, from the viewpoint of mountability on a vehicle, it is difficult to make the oil pan for storing the hydraulic oil deep, and the amount of the hydraulic oil may be insufficient. here,
This is not a problem when the outside air temperature is high, but when the outside air temperature is low, the viscosity of the hydraulic oil increases and its flow resistance increases, so the hydraulic oil pumped from the oil pan by the oil pump is returned to the oil pan. It takes a long time to return to, and air in the oil pan may be sucked into the hydraulic circuit side. As a result, there is a problem that the responsiveness of the shift control performed on the transmission 12 side is reduced.

Therefore, in the system provided with the hydraulic control device 16 having a large valve body, control for closing the control valves 19, 20, and 23 and opening the control valves 24 and 33 in the above case is performed. When this is done, the hydraulic oil in the tank 27 is pushed out to the discharge pipe 22 by the atmospheric pressure, and the pushed out hydraulic oil is supplied to the hydraulic control device 16 side.

As a result, the shortage of the hydraulic oil amount on the hydraulic control device 16 side is resolved, and a decrease in the responsiveness of the shift control can be suppressed. Note that the temperature of the hydraulic oil in the heat storage device 25 is lower than the temperature of the hydraulic oil on the hydraulic control device 16 side, and the operating oil in the heat storage device 25 warms the hydraulic oil on the hydraulic control device 16 side. Since the required amount of hydraulic oil is sent out from the heat storage device 25 by the hydraulic control device 16, the control valves 24 and 33 are also closed. In this way, the temperature of the hydraulic oil is increased on the side of the transmission 12 and the hydraulic power transmission device 9 to promote warm-up.

* Case -1 In case -1 in the system of FIG.
Control for closing all of 0, 23, and 24 is performed. When this control is performed, all the pipes connecting the hydraulic control device 16, the cooling device 2, and the heat storage device 25 are shut off,
The hydraulic oil is confined in the transmission 12, the hydraulic power transmission 9, and the hydraulic control 16. Therefore, as described above, the temperature of the hydraulic oil increases due to the frictional heat of the hydraulic power transmission device 9 and the transmission 12, and the warming-up of the hydraulic power transmission device 9 and the transmission 12 is promoted.

* Case-2 In this case-2, control is performed to open the control valves 19 and 20 and close the control valves 23 and 24. When this control is performed, the hydraulic oil on the hydraulic control device 16 side becomes
The cooling water on the engine 1 side is sent to the heat exchange unit 100 via the discharge pipe 101 while being sent to the heat exchange unit 100 via the inlet pipe 17. Then, the heat exchange unit 1
At 00, the heat of the cooling water is transmitted to the hydraulic oil side, so that the temperature of the hydraulic oil increases and the temperature of the cooling water decreases. The warmed hydraulic oil is returned to the hydraulic control device 16 via the outlet pipe 18. In this way, warming up of the hydraulic power transmission device 9 and the transmission 12 is promoted. The cooling water whose temperature has decreased in the heat exchange unit 100 is
It is returned to the engine 1 via the return pipe 102.

* Case a2 The case a2 will be described separately for a case (case) corresponding to the system of FIG. 2 and a case (case) for the system of FIG.

* Case In the case of the system shown in FIG. 2, when the control valve 24 is opened and the control valve 33 is controlled to communicate the hydraulic oil chamber B1 with the atmosphere, the control valves 19, 20, and Close 23. Then, the hydraulic oil stored in the heat storage device 25 is sent to the hydraulic control device 16 side, and the hydraulic oil on the hydraulic control device 16 side is warmed. Heat is generated inside the fluid power transmission device 9, and warming up of the transmission 12 and the fluid power transmission device 9 is promoted.

* Case In the case of the system shown in FIG. 4, when the control valves 19, 20,
24 is opened, the control valve 23 is closed, and the control valve 33 is controlled to communicate the hydraulic oil chamber B1 with the atmosphere. Then, the hydraulic oil stored in the heat storage device 25 is sent to the hydraulic control device 16 side to warm the hydraulic oil on the hydraulic control device 16 side, and the hydraulic oil on the hydraulic control device 16 side passes through the inlet pipe 17. Then, the coolant is sent to the heat exchange unit 100, and the cooling water on the engine 1 side is sent to the heat exchange unit 100 via the discharge pipe 101. As a result, the heat of the cooling water is transmitted to the hydraulic oil, and after the temperature of the hydraulic oil increases, the hydraulic oil is returned to the hydraulic control device 16 via the outlet pipe 18. In this way, the warm-up of the transmission 12 and the hydraulic power transmission 9 is promoted.

* Case B The case (case) corresponding to the system of FIG. 2 and the case (case) corresponding to the system of FIG. 4 will be described separately.

* Case: The control valves 19, 20, 23, and 24 are opened, and the control of the control valve 33 allows the air pipe 31 to communicate with the hydraulic oil chamber B1. Then, a part of the hydraulic oil on the hydraulic control device 16 side is sent to the tank 27 of the heat storage device 25 via the supply pipe 21, and the high-temperature hydraulic oil is stored in the heat storage device 25. Here, since the tank 27 is formed of a heat insulating material, the vacuum chamber A1 is formed, and the casing 26 is formed of a heat insulating material, the heat of the hydraulic oil in the tank 27 is transferred to the outside of the heat storage device 25. And the temperature of the hydraulic oil in the tank 27 is prevented from lowering. Also, the hydraulic control device 16
A part of the hydraulic oil is cooled by being sent to the cooling device 2 side via the inlet pipe 17 and then cooled by the outlet pipe 1.
The control returns to the hydraulic control device 16 via the control unit 8. In this way, overheating of the hydraulic oil is suppressed.

* Case: The control valves 19, 20, 23, and 24 are opened, and the air pipe 31 and the hydraulic oil chamber B1 are communicated under the control of the control valve 33. Then, a part of the hydraulic oil on the hydraulic control device 16 side is sent to the tank 27 of the heat storage device 25 via the supply pipe 21, and the high-temperature hydraulic oil is stored in the heat storage device 25. A part of the hydraulic oil of the hydraulic control device 16 is sent to the heat exchange unit 100 via the inlet pipe 17 and is cooled by the cooling water on the engine 1 side. Then, the process returns to the hydraulic control device 16. In this way, overheating of the hydraulic oil is suppressed. As described above, in the system of FIG. 4, the hydraulic oil on the hydraulic control device 16 side can be heated or cooled by the cooling water on the engine 1 side. That is, the cooler 103 is a heat exchanger having a function as a warmer and a function as a cooler.

FIG. 5 shows an example in which a part of the system shown in FIG. 1 is modified. In FIG. 5,
The flow area of the air pipe 31 is set to be the same over the entire length, and the flow area of the connection area between the discharge pipe 22 and the air pipe 31 is formed to be smaller than the flow area of the discharge pipe 22. Have been. The discharge pipe 22
In this case, the flow area of the area other than the throttle section D1 is set to be larger than the flow area of the throttle section D1.

The system shown in FIG. 5 can be applied to the system shown in FIG. 2 or FIG. 4 to perform the above-described various controls. In FIG. 5, the return action of the air returned from the air pipe 31 to the hydraulic control device 16 side is based on the differential pressure corresponding to the difference between the flow area of the air pipe 31 and the flow area of the throttle D1. Other than as facilitated, an effect similar to that of the system of FIGS. 1-4 occurs.

As described above, according to the systems shown in FIGS. 1 to 5, when the temperature of the hydraulic oil on the hydraulic control device 16 side is high, the hydraulic oil is stored in the heat storage device 25 so that the hydraulic power The amount of hydraulic oil on the transmission device 9, the transmission 12, and the hydraulic control device 16 side can be reduced, and the pressure inside the oil pan is suppressed from increasing. Therefore,
Hydraulic oil can be prevented from blowing out from the oil filler tube 12A and the like, and it may not be necessary to provide a breather plug or the like for releasing air into the atmosphere in the oil pan on the hydraulic control device 16 side.

Further, when the hydraulic oil on the hydraulic control device 16 side is at a low temperature, the high-temperature hydraulic oil stored in the heat storage device 25 is returned to the hydraulic control device 16 so that the hydraulic oil on the hydraulic control device 16 side is returned. Of the hydraulic oil is prevented from increasing due to an increase in the temperature of the hydraulic oil. Therefore, in the fluid type power transmission device 9, an increase in the shear resistance of the contact surface between the hydraulic oil and the drive-side rotating member 10 is suppressed, an increase in the engine load can be suppressed, and a decrease in fuel efficiency can be prevented.

Further, when the temperature is low, the hydraulic oil stored in the heat storage device 25 is supplied to the hydraulic control device 16 side, and a decrease in the amount of hydraulic oil in the oil pan is suppressed. Therefore, the phenomenon that the air in the oil pan is sucked by the oil pump can be prevented, and the time required for the hydraulic oil pumped from the oil pan to return to the oil pan is reduced, and the responsiveness of the shift control due to a shortage of the hydraulic oil is reduced. Can be prevented beforehand.

In this embodiment, the tank 27
Since the air pipe 31 is disposed in the vacuum chamber A1, the heat of the working oil sent to the tank 27 can be suppressed from being transmitted to the air pipe 31. Therefore, the heat storage device 2
The heat stored in the heat storage device 5 can be suppressed from being radiated to the outside via the air pipe 31, and the heat storage function of the heat storage device 25 is further improved.

Further, in this embodiment, since the air pipes 31 are provided with the constrictions C1 and D1, the flow area (cross-sectional area) of the air pipe 31 and the flow area (cross-sectional area) of the constrictions C1 and D1 are provided. The discharge of air is promoted by the differential pressure corresponding to

Further, in this embodiment, the aperture portion C
1, D1, the hydraulic oil is transmitted to the power transmission device hydraulic control device 1
6 and the time when the air is returned to the hydraulic control device 16 are automatically adjusted. Therefore, it is not necessary to separately provide a control valve or the like for adjusting the two timings in the air pipe 31 and the return pipe 22, and it is possible to suppress an increase in the number of parts. Therefore, the size and size of the device can be reduced, and the on-board performance is improved.

FIG. 6 is a diagram showing another system to which the present invention is applied. 6, the same components as those of the system shown in FIG. 2 are denoted by the same reference numerals as those in FIG. 2, and description thereof will be omitted. FIG. 7 shows the configuration of the heat storage device 60 used in FIG. The heat storage device 60 has a casing 61 made of a heat insulating material, and a tank 62 is provided inside the casing 61. The tank 62 has a bottle shape. The tank 62 has a cylindrical body 63, a bottom 64 formed at one end of the body 63, and an inclined portion 65 formed at the other end of the body 63. have. here,
The material of the casing 61 is the same as the casing 26 shown in the figure, and the material of the tank 62 is the tank 27 shown in FIG.
It is the same as the material.

The inclined portion 65 has an opening 66, and the opening 6
One end of an inlet pipe 67 is attached to 6, and the other end of the inlet pipe 67 is attached to a case 68 of the hydraulic control device 16. Thus, the other end of the inlet pipe 67 is opened to the inside E1 of the oil pan. A control valve 6 is provided in the middle of the inlet pipe 67.
9 are provided. The control valve 69 includes an internal E
A thermal valve that is automatically opened and closed based on the temperature of the hydraulic oil in 1, a solenoid valve controlled by an electronic control unit, and the like.

On the other hand, the inclined portion 65 is provided inside the tank 62.
A valve body 70 is provided which comes into contact with the inner surface of the valve body. This valve body 70 is formed in an annular shape. Further, an outlet pipe 71 is provided which passes through the inside of the case 62 and the inside of the inlet pipe 67 and is arranged over the inside E1 of the oil pan. The valve body 60 is attached to the outer periphery of the outlet pipe 71 so as to be relatively movable in the axial direction of the valve body 60.

Further, a vacuum chamber F1 is formed between the casing 61 and the tank 62, and an air pipe 72 which penetrates the casing 61 and is disposed in the vacuum chamber F1. One end of the air pipe 72 is
It is attached to the bottom 64 of the tank 62 and opens to the hydraulic oil chamber G1 inside the tank 62. Also, air piping 7
The other end of 2 penetrates the case 68 and opens into the interior E1 of the oil pan. A control valve 73 is provided in the middle of the air pipe 72. Thus, the heat storage device 60 shown in FIG. 6 is also a so-called inverted thermos type heat storage device in which the opening 66 of the tank 62 is directed downward.

The control system circuit shown in FIG. 3 can be used for the systems shown in FIGS. That is, a signal of the coolant temperature sensor 37, a signal of the transmission oil temperature sensor 38,
The signal of the hydraulic oil amount detection sensor 40 for detecting the hydraulic oil amount on the 6 side, the signal of the oil temperature sensor 39 for the heat storage tank for detecting the temperature of the hydraulic oil in the heat storage device 60, the signal of the vehicle speed sensor 41, the accelerator opening sensor 42 Is input. From the electronic control unit 36, a signal for controlling the control valves 69 and 73, a signal for controlling the hydraulic control unit 16, and the like are input. Here, the correspondence between the configuration of FIG. 7 and the configuration of the present invention will be described. The air pipe 72 corresponds to the air passage, and the outlet pipe 71 corresponds to the return oil path of the present invention.

In the systems shown in FIGS. 6 and 7, the same operations as those shown in FIGS. In the systems of FIGS. 6 and 7, when the hydraulic oil temperature on the hydraulic control device 16 side is equal to or lower than the predetermined temperature THO2, the control valve 69 is closed and the control valve 73 is opened. Then, the air pressure in the inside E1 of the oil pan is increased via the air pipe 72 to the inside G1 of the tank 62.
And the high-temperature hydraulic oil stored in the tank 62 is supplied to the oil pan via the outlet pipe 71. Therefore, an increase in the viscosity of the hydraulic oil is suppressed on the hydraulic control device 16 side. Therefore, in the fluid type power transmission device 9, an increase in the shear resistance of the contact surface between the hydraulic oil and the drive-side rotating member 10 is suppressed, an increase in the engine load can be suppressed, and a decrease in fuel efficiency can be prevented. The casing 61 is made of a heat insulating material, and
Since the tank 62 is made of a heat insulating material and the vacuum chamber F1 is formed, the transfer of the heat of the hydraulic oil in the tank 62 to the outside of the heat storage device 60 is suppressed.
It is possible to suppress a decrease in the temperature of the working oil in the inside.

Further, at a low temperature, the hydraulic oil stored in the heat storage device 60 is supplied to the hydraulic control device 16 to suppress a decrease in the amount of hydraulic oil in the oil pan. The phenomenon that air is sucked can be prevented. Therefore, the time required for the hydraulic oil pumped from the oil pan to return to the oil pan is shortened, and it is possible to prevent a reduction in the responsiveness of the shift control due to a shortage of the hydraulic oil. In a state where the own weight of the hydraulic oil is acting on the valve body 70, the valve body 70 is pressed against the inner surface of the inclined portion 65 and the opening 66 is closed.
The working oil inside does not flow to the inlet pipe 67 side.

On the other hand, when the operating oil temperature on the hydraulic control device 16 side is equal to or higher than the predetermined temperature THO1 + α, the internal E1 becomes high pressure. Here, the predetermined temperature THO1 is higher than the predetermined temperature THO2, and “α” indicates a phenomenon in which the control valve 69 is alternately and frequently switched between an open state and a closed state, that is, a hunting phenomenon occurs. Hysteresis that does not occur. Then, the control valve 73 is closed and the control valve 69 is opened, and the operating oil in the inside E1 of the oil pan acts on the valve body 70 via the inlet pipe 67, and the valve body 70 is pressed toward the bottom 64. Then, the opening 66 is opened.

In this way, the working oil in the inside E1 is stored in the working oil chamber G1. When the hydraulic oil is stored in the hydraulic oil chamber G1, the own weight of the hydraulic oil acts on the valve body 70 and the opening 66 is closed, so that the hydraulic oil stored in the hydraulic oil chamber G1 flows through the opening 66. There is no backflow to the inside E1 side via the. Also, when the engine 1 stops and the temperature rise of the hydraulic oil on the hydraulic control device 16 side is suppressed, and the supply pressure of the hydraulic oil supplied from the hydraulic control device 16 side to the tank 62 side decreases, the valve body 70 Is lowered by its own weight and the opening 66 is closed, so that the hydraulic oil stored in the hydraulic oil chamber G1
There is no backflow to the inside E1 side via the opening 66.

As described above, also in the system shown in FIGS. 6 and 7, when the temperature of the hydraulic oil on the hydraulic control device 16 side is high, the hydraulic oil is stored in the heat storage device 70.
It is possible to reduce the temperature of the hydraulic oil on the hydraulic power transmission device 9, the transmission 12, and the hydraulic control device 16 side,
A high pressure inside the oil pan is suppressed. Therefore, it is possible to suppress the hydraulic oil on the hydraulic control device 16 side from being blown out from the oil filler tube 12A or the like, and to provide a breather plug or the like on the hydraulic control device 16 side for releasing the air in the interior E1 into the atmosphere. Nor.

In FIG. 7, the outlet pipe 7
The open end of No. 1 is set lower than the lowest oil level H1 shown by the solid line. Further, the opening and closing of the control valve 73 is controlled based on the signal of the hydraulic oil amount detection sensor 40 so that the highest oil level J1 of the hydraulic oil and the opening end of the air pipe 72 are at the same height. Further, also in the embodiment of FIG. 7, since the air pipe 72 is provided facing the vacuum chamber F1,
The heat of the working oil stored in the tank 62 can be suppressed from being transmitted to the outside of the casing 61 via the air pipe 72, and the heat storage function of the heat storage device 60 is further improved. In the embodiments shown in FIGS. 1, 2, 6, and 7, a heater (not shown) may be added to the heat storage device to heat the working oil stored in the tank by the heater. it can.

FIG. 8 is a conceptual diagram showing another embodiment.
In FIG. 8, the same configuration as the embodiment of FIG.
The same reference numerals as in FIG. 2 are assigned and the description is omitted. A cooling device driven by the engine 1 or another power device,
In other words, the heat exchanger 2 has the radiator 5. Also, an inlet pipe 17 and an outlet pipe 18
Is provided with a control valve 80. And
The heat exchanger 2 has a part of the inlet pipe 17 and a part of the outlet pipe 18, that is, a region including the control valve 80. Thus, in the heat exchanger 2, heat can be exchanged between the cooling water on the engine 1 side and the hydraulic oil on the hydraulic control device 16 side.

In the embodiment shown in FIG. 8, the engine 1 rotates independently by repeating known four steps, that is, an intake stroke, a compression stroke, a combustion process (expansion stroke), and an exhaust stroke. Here, when the cooling water temperature is equal to or lower than the predetermined temperature, so-called homogeneous combustion in which fuel is injected into the combustion chamber during the intake stroke can be performed. Further, when the cooling water temperature exceeds a predetermined temperature, so-called stratified combustion can be performed in which fuel is injected into the combustion chamber and burned in the compression stroke. Here, stratified combustion consumes less fuel than homogeneous combustion, and stratified combustion can improve fuel efficiency.

By the way, during the operation of the engine 1, the cooling water is always circulated to the heat exchanger 2 side, and the hydraulic oil of the hydraulic control device 12 is circulated to the heat exchanger 2 side, so that the heat of the cooling water is Is transmitted to the working oil and the working oil is heated by the cooling water, the warm-up of the engine 1 is delayed, and the timing of switching from the homogeneous combustion to the stratified combustion is delayed, making it difficult to improve the fuel efficiency.

Therefore, in the embodiment shown in FIG. 8, the cooling water temperature on the engine 1 side is a temperature at which stratified combustion can be executed, and the cooling water temperature is higher than the hydraulic oil temperature on the hydraulic control device 16 side. Is higher, the control valve 80 is opened to send the hydraulic oil of the hydraulic control device 16 to the heat exchanger 2 via the inlet pipe 17, and then to the hydraulic control device 16 via the outlet pipe 18. Perform return control. That is, if the operating oil temperature is higher than the cooling water temperature, or if the cooling water temperature has not reached a temperature at which stratified combustion can be performed, the control valve 80 is closed.

By performing such control,
The problem that "the heat of the operating oil in the high temperature state is transmitted to the cooling water in the low temperature state and the temperature of the hydraulic oil decreases to increase its viscosity" can be prevented beforehand, and FIGS. The same effect as that of the second embodiment can be obtained. Further, since the warm-up of the engine 1 is promoted, the switching from the homogeneous combustion to the stratified combustion can be achieved at an early stage, and the fuel efficiency can be improved. In addition, even when the control valve 80 is provided in the middle of the inlet pipe 17, the same operation and effect as described above can be obtained. In addition, a bimetal or the like is used instead of the control valve 80, and the inlet pipe 1
7 can be opened and closed.

[0071]

As described above, according to the first aspect of the present invention,
When the temperature of the hydraulic oil on the power transmission device side exceeds a predetermined temperature, the hydraulic oil is sent to a location other than the power transmission device.
Therefore, an increase in the internal pressure of the power transmission device is suppressed, and it is possible to prevent the hydraulic oil inside the power transmission device from spouting to the outside, and it is not necessary to provide an air release device for discharging the air inside the power transmission device to the outside. Becomes

On the other hand, when the temperature of the hydraulic oil on the power transmission device side is equal to or lower than the predetermined temperature, the high-temperature hydraulic oil held in the holding device is returned to the power transmission device. Therefore, the increase in the viscosity of the hydraulic oil on the power transmission device side is suppressed, and the deterioration of fuel efficiency of the driving force source connected to the power transmission device can be suppressed, and the shortage of hydraulic oil in the power transmission device is eliminated. As a result, it is possible to avoid a decrease in the power transmission function of the power transmission device due to insufficient hydraulic oil.

According to the second aspect of the invention, in addition to obtaining the same effect as the first aspect of the invention, when the hydraulic oil taken out of the power transmission device is held in the holding device, the hydraulic oil is included in the hydraulic oil. The returned air is returned to the power transmission device side.

According to the third aspect of the invention, in addition to obtaining the same effects as the second aspect of the invention, the timing at which the hydraulic oil is returned to the power transmission device and the timing at which the air is returned to the power transmission device are different. Since it is automatically adjusted by the throttle unit, there is no need to provide a mechanism for adjusting the two timings in the air pipe and the return pipe.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a heat storage device used in the present invention.

FIG. 2 is a conceptual diagram showing an example of a vehicle to which the present invention is applied.

FIG. 3 is a block diagram showing a control system of the vehicle shown in FIG.

FIG. 4 is a conceptual diagram showing an embodiment in which a part of the system of FIG. 2 is modified.

FIG. 5 is a sectional view showing a configuration example in which a part of the heat storage device of FIG. 1 is changed.

FIG. 6 is a conceptual diagram showing another example of a vehicle to which the present invention is applied.

FIG. 7 is a sectional view showing another embodiment of the heat storage device used in the present invention.

FIG. 8 is a conceptual diagram showing another embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Engine, 9 ... Fluid power transmission device, 12 ... Transmission, 16 ... Hydraulic control device, 18, 71 ... Outlet piping, 22 ... Discharge piping, 25, 60 ... Heat storage device, 27, 62 ... Tank, 31, 72 ... air piping,
32: open air tube, A1, F1: vacuum chamber, C1,
D1 ... Aperture section.

 ──────────────────────────────────────────────────の Continued on the front page F term (reference) 3J063 AA01 AB00 AB41 AB53 AC03 BA15 BA17 BA20 CA01 CD70 3J552 MA01 MA06 MA12 NA01 NB01 PA20 PA59 QA36A QA42A QA44A VA48W

Claims (3)

[Claims] 1. A hydraulic oil circulation device having a function of extracting hydraulic oil of a power transmission device from the power transmission device and returning the extracted hydraulic oil to the power transmission device. When the temperature of the hydraulic oil exceeds the predetermined temperature, the hydraulic oil taken out of the power transmission device is held outside the power transmission device, and when the temperature of the hydraulic oil on the power transmission device side is equal to or lower than the predetermined temperature, And a holding device for returning the working oil held outside the power transmission device to the power transmission device. 2. The holding device stores the hydraulic oil,
And, having a tank arranged inside the vacuum chamber, and an air passage arranged in the vacuum chamber for returning air contained in hydraulic oil stored in the tank to the power transmission device side The hydraulic oil circulation device according to claim 1, wherein: 3. The air passage and a return oil passage for returning hydraulic oil held in the holding device to the power transmission device side are arranged in parallel, and the air passage in the air flow direction in the air pipe is arranged in parallel. The hydraulic oil circulation device according to claim 2, wherein a throttle portion having a flow area smaller than a flow area of the air passage is connected to the downstream side.