WO2006009080A1 - 車両のトランスミッションの潤滑油供給制御装置 - Google Patents
車両のトランスミッションの潤滑油供給制御装置 Download PDFInfo
- Publication number
- WO2006009080A1 WO2006009080A1 PCT/JP2005/013068 JP2005013068W WO2006009080A1 WO 2006009080 A1 WO2006009080 A1 WO 2006009080A1 JP 2005013068 W JP2005013068 W JP 2005013068W WO 2006009080 A1 WO2006009080 A1 WO 2006009080A1
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- WIPO (PCT)
- Prior art keywords
- lubricating oil
- transmission
- control
- controller
- oil passage
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0446—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control the supply forming part of the transmission control unit, e.g. for automatic transmissions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
Definitions
- the present invention relates to an apparatus for controlling supply of lubricating oil to a transmission of a vehicle.
- Patent Document 1 to be described later describes an invention for supplying a necessary amount of lubricating oil to the transmission according to the operating state of the planetary gear type transmission.
- Patent Document 1 That is, in Patent Document 1, the object is achieved by the following means.
- the first pressure regulating valve regulates the hydraulic pressure of the pressure oil discharged from the hydraulic pump to the line pressure and outputs it to the line pressure oil passage.
- a line pressure oil path is connected to the second control valve, and a lubrication signal pressure oil path is connected to the second control valve, and the second control valve is supplied from the line pressure oil path.
- the spool With the line pressure as the base pressure, the spool is operated according to the lubrication signal pressure supplied from the lubrication signal pressure oil passage, and the lubrication pressure is output to the upstream side of the orifice.
- Patent Document 1 JP-A-10-141480
- the present invention has been made in view of such a situation, and when constructing a lubricating oil supply control device for a transmission, it is not necessary to add a new sensor, and the arithmetic processing performed by the controller is a simple process. Therefore, it is an object of the present invention to make it possible to construct a control device with a simple configuration and to construct it at a low cost.
- the first invention is a first invention
- An engine controller that controls the engine
- a transmission controller for controlling the transmission
- Hydraulic pump force Lubricating oil supply oil passage for guiding discharged lubricating oil to the transmission, A bypass oil passage for guiding the lubricating oil in the lubricating oil supply oil passage to the tank;
- a relief valve that discharges the lubricating oil in the lubricating oil supply oil passage to the tank through the bypass oil passage, and operates according to a control electric signal
- a throttle provided on the outlet side or the inlet side of the relief valve
- a controller for controlling the lubricant supply which receives engine controller control information and / or transmission controller control information, generates a control electric signal for operating the relief valve based on the control information, and outputs it.
- the second invention is:
- An engine controller that controls the engine
- a transmission controller for controlling the transmission
- a hydraulic pump force a lubricating oil supply oil passage that guides the discharged lubricating oil to the transmission, a bypass oil passage that guides the lubricating oil in the lubricating oil supply oil passage to the tank,
- a control valve that adjusts the amount of lubricating oil introduced to the transmission through the lubricating oil supply oil passage and the amount of lubricating oil introduced from the lubricating oil supply oil passage to the tank through the bypass oil passage;
- a control valve that operates in response to a control electrical signal;
- a lubricant supply control controller that receives engine controller control information and / or transmission controller control information and generates and outputs a control electrical signal for operating the control valve based on the control information;
- the third invention provides
- a hydraulic pump force a lubricating oil supply oil passage that guides the discharged lubricating oil to the transmission, a bypass oil passage that guides the lubricating oil in the lubricating oil supply oil passage to the tank,
- a relief valve that discharges lubricating oil in the lubricating oil supply oil path to the tank via the bypass oil path.
- a relief valve that operates in response to a control electrical signal;
- a throttle provided on the outlet side or the inlet side of the relief valve
- a lubricant supply control controller that outputs a control electric signal for operating the relief valve
- the fourth invention is:
- a hydraulic pump force a lubricating oil supply oil passage that guides the discharged lubricating oil to the transmission, a bypass oil passage that guides the lubricating oil in the lubricating oil supply oil passage to the tank,
- a control valve that adjusts the amount of lubricating oil introduced to the transmission through the lubricating oil supply oil passage and the amount of lubricating oil introduced from the lubricating oil supply oil passage to the tank through the bypass oil passage;
- a control valve that operates in response to a control electrical signal;
- a lubricant supply control controller that outputs a control electric signal for operating the control valve
- the lubricating oil supply control device for the transmission 3 of the first invention includes an engine controller 30 for controlling the engine 1, a transmission controller 40 for controlling the transmission 3, and a lubricant Lubricating oil supply passage 17 for guiding the lubricating oil discharged from the hydraulic pump 9 to the transmission 3, bypass oil passages 21 and 23 for guiding the lubricating oil in the lubricating oil supply passage 17 to the lubricating oil tank 8, and lubrication A relief valve 22 for discharging the lubricating oil in the oil supply oil passage 17 to the lubricating oil tank 8 through the bypass oil passages 21 and 23, and a relief valve 22 that operates according to the control electric signal i, and a relief valve
- the control information of the throttle 28 provided at the outlet 22 and the control information of the engine controller 30 and / or the control information of the transmission controller 40 are input, and the relief is performed based on the control information. 22 generates a control electric signal i for operating, constituted by a lubric
- step 1 When the control electric signal i for operating the relief valve 22 is output from the lubricant supply control controller 50 (YES in step 102 or 103 in FIG. 3, step 1) 04) The relief valve 22 is activated and opened.
- a part of the lubricating oil guided to the lubricating oil supply oil passage 17 passes through the relief valve 22 via the bypass oil passage 21.
- the lubricating oil that has passed through the relief valve 22 is discharged to the lubricating oil tank 8 through the bypass oil passage 23 and the throttle 28.
- the lubricant supply control controller 50 when the load on the engine 1 is low or the load on the transmission 3 is low (YES in step 102 or YES in step 103), the lubricant supply control controller 50 The control electric signal i is output from the engine (step 104), and a part of the lubricating oil to be supplied to the transmission 3 is discharged to the lubricating oil tank 8, so that the mechanical friction of the transmission 3 is reduced. While cooling, the components of the transmission 3 can be protected, and an excessive supply of lubricating oil can be prevented to reduce power loss in the transmission 3, thereby improving the fuel consumption of the engine 1 and saving energy.
- the control information of the engine controller 30 and the control information of the transmission controller 40 are input to the lubricant supply control controller 50, and the control electric signal i is output based on the control information. Therefore, the control of the lubrication oil supply by operating the relief valve 22 is performed, so that the control system can be simplified by using the existing control information used by the existing engine controller 30 and transmission controller 40. It can be constructed at low cost. In other words, it is not necessary to add a new sensor to acquire the control information. In addition, the sensor detection signal must be processed by the controller and converted into engineering units required for arithmetic processing. In addition, it is not necessary for the controller to newly calculate the engine load or transmission load based on the detection values of various sensors. Therefore, the processing performed by the controller can be simplified as illustrated in FIG.
- the relief valve 22 is operated and the lubricating oil in the lubricating oil supply oil passage 17 is transferred to the lubricating oil tank 8 via the bypass oil passage 21, the relief valve 22, and the bypass oil passage 23. Since the hydraulic circuit is configured to discharge, only the valve body and piping for discharging the lubricating oil in the lubricating oil supply oil passage 17 are added to the existing lubricating oil supply oil passage 17 in the hydraulic circuit. so Therefore, when constructing a hydraulic system, the configuration of the valve body and the handling of the hydraulic piping can be simplified, and the cost can be reduced.
- a control valve 60 having the same function is used instead of the relief valve 22 and the throttle 28 of the first invention. That is, as shown in FIG. 6, the control valve 60 is connected to the lubrication 3 guided to the transmission 3 through the lubricating oil supply oil passage 17 in accordance with the control electric signal i output from the lubricating oil supply control controller 50. The amount of oil and the amount of lubricating oil introduced from the lubricating oil supply oil passage 17 to the lubricating oil tank 8 through the bypass oil passage 23 are adjusted.
- the control information of the engine controller 30 and the transmission controller 40 is input to the lubricant supply control controller 50 to control the supply of lubricant, but the engine controller 30
- the lubricant supply controller 50 may control the lubricant supply based on information other than the control information of the transmission controller 40 (third invention, fourth invention).
- FIG. 1 is a diagram showing a configuration of a power transmission path of the wheel loader 100.
- FIG. 2 is a diagram showing a configuration of the lubricating oil supply circuit of the wheel loader 100.
- the lubricating oil supply control device for the transmission 3 of the present embodiment is largely discharged from the engine controller 30 that controls the engine 1, the transmission controller 40 that controls the transmission 3, and the lubricating hydraulic pump 9.
- Lubricating oil supply oil passage 17 for guiding the lubricating oil to the transmission 3 bypass oil passages 21 and 23 for guiding the lubricating oil in the lubricating oil supply oil passage 17 to the lubricating oil tank 8, and in the lubricating oil supply oil passage 17
- Relief valve 22 that discharges lubricating oil to lubricating oil tank 8 through bypass oil passages 21 and 23, provided on the outlet side of relief valve 22 that operates according to control electric signal i, and relief valve 22
- the control information of the throttle 28, the engine controller 30 and the control information of the transmission controller 40 are input, and the relief valve 22 is operated based on the control information. Generate and output control electrical signal i And a controller 50 for lubricating oil supply control.
- the output shaft of the engine 1 of the wheel loader 100 is connected to the PTO shaft 7.
- the PTO shaft 7 is connected to the torque converter 2.
- the output of the engine 1 is transmitted to the drive wheels 5 through the PTO shaft 7, the torque converter 2, the transmission 3, and the differential gear 4.
- An accelerator pedal 6 is provided in the cab of the wheel loader 100.
- An operation amount (depression amount) is detected by a stroke sensor 6 a provided on the accelerator pedal 6, and a signal indicating the operation amount is input to the engine controller 30.
- the engine controller 30 controls the engine 1 based on the input signal of the stroke sensor 6a so that the rotational speed of the engine 1 becomes a target rotational speed corresponding to the operation amount of the accelerator pedal 6.
- the engine 1 is a diesel engine, and its output is controlled by adjusting the injection amount injected into the cylinder. This adjustment is done by changing the stroke of the engine 1 fuel injection pump plunger using the control rack of the electric governor.
- the engine controller 30 inputs the actual engine speed, the control rack position, etc., and sends a control electric signal to the electric governor so that the difference between the target speed and the actual speed is eliminated. Output to control the control rack position of the electric governor.
- control electrical signal output from the engine controller 30 is sent to the lubricant supply control controller 50 via the electrical signal line 31 as control information indicating the load (fuel injection amount) of the engine 1. Is output.
- the transmission 3 is composed of, for example, a planetary gear type transmission.
- a planetary gear type transmission is composed of multiple sets of hydraulic clutches and multiple sets of planetary gear mechanisms. Change gears. Multiple sets of hydraulic clutches include forward hydraulic clutch, reverse hydraulic clutch, speed stage hydraulic clutch, that is, first speed hydraulic clutch, second speed hydraulic clutch, third speed hydraulic clutch, fourth speed (maximum speed stage) ) Hydraulic clutch force Shifting is performed by selecting whether the hydraulic clutch is! / Or not.
- the transmission 3 is provided with an electromagnetic proportional control valve for each hydraulic clutch.
- a control electrical signal (control information) applied to the electromagnetic proportional control valve pressure oil is supplied to the corresponding hydraulic clutch, and the hydraulic clutch is engaged.
- the transmission controller 40 inputs the operation position of the operation lever for driving, the vehicle speed, etc., and selects either the forward hydraulic clutch or the reverse hydraulic clutch and also selects whether the speed stage clutch is shifted or not. Then, a control electric signal for engaging the selected hydraulic clutch is output to the electromagnetic proportional pressure control valve of the corresponding hydraulic clutch.
- control electric signal output from the transmission controller 40 is used as control information indicating the load (speed stage) of the transmission 1, and the controller for lubricating oil supply control via the electric signal line 41. Output to 50.
- the transmission 3 includes a speed change mechanism unit configured by a planetary gear mechanism (squeezing gear mechanism).
- the clutch (friction engagement element) force is also configured.
- Lubricating oil needs to be supplied to the transmission mechanism, clutch, and the like of the transmission 3 to reduce mechanical friction, cool down, prevent fouling, and the like.
- a lubricating oil tank 8 that forms a part of the case of the transmission 3 is provided at the lower part of the transmission 3.
- a drive shaft of a lubricating hydraulic pump 9 is connected to the PTO shaft 7.
- the output of the engine 1 is transmitted to the lubricating hydraulic pump 9 via the PTO shaft 7, and the lubricating hydraulic pump 9 is driven.
- the suction port 9 a of the lubricating hydraulic pump 9 communicates with the lubricating oil tank 8 via the suction oil passage 10.
- the suction oil passage 10 is provided with a strainer 12.
- the discharge port 9b of the lubricating hydraulic pump 9 communicates with the inlet port of the main relief valve 13 via the pump discharge oil passage 11.
- the outlet port of the main relief valve 13 is the oil passage 1
- An oil passage 15 communicates with the oil passage 14.
- the oil passage 15 is provided with a throttle 15a.
- the outlet of the torque converter 2 communicates with the inlet of the oil cooler 16.
- the lubricating oil passing through the oil cooler 16 is cooled by the flow of wind formed by a cooling fan (not shown).
- the discharge pressure oil from the lubricating hydraulic pump 9 is also used as the original pressure of the pressure oil supplied to the hydraulic clutch.
- the lubricating oil supply oil passage 17 communicates with the bypass oil passage 21.
- the bypass oil passage 21 communicates with the inlet port 22a of the relief valve 22.
- An outlet port (tank port) 22 b of the relief valve 22 communicates with the bypass oil passage 23.
- a throttle 28 is provided in the bypass oil passage 23. The downstream side of the throttle 28 communicates with the lubricating oil tank 8.
- One end of a panel 22c for determining a set relief pressure is brought into contact with one end of the spool or ball of the relief valve 22.
- the pressure receiving surface at the other end of the spool or ball of the relief valve 22 (the side opposite to the panel 22 2c) communicates with the inlet port 22a through the pilot oil passage 24.
- the other end of the spool or ball of the relief valve 22 (the side opposite to the panel 22c) is provided with a pilot port 22d to which a pilot pressure Pc is applied.
- the pump discharge oil passage 11 branches into a pilot oil passage 25.
- the pilot oil passage 25 communicates with the inlet port 26c of the electromagnetic control valve 26! /.
- the outlet port 26d of the electromagnetic control valve 26 communicates with the pilot port 22d of the relief valve 22 via the pilot oil passage 27! /.
- the tank port 26f of the electromagnetic control valve 26 communicates with the lubricating oil tank 8 via the oil passage 29.
- the electromagnetic solenoid 26e of the electromagnetic control valve 26 is electrically connected to the lubricant supply control controller 50 via the electric signal line 51.
- the lubricant supply control controller 50 is electrically connected to the engine controller 30 via the electric signal line 31.
- the lubricant supply control controller 50 is electrically connected to the transmission controller 40 via the electric signal line 41 !.
- the lubricating oil supply control controller 50 is shown as a separate body from the engine controller 30 and the transmission controller 40. However, the lubricating oil supply control controller 50 is replaced with the engine controller 30. It may be configured integrally with 30. Also, the lubricant supply control controller 50 may be configured so as to be integrated with the transmission controller 40.
- the electromagnetic control valve 26 is a two-position switching valve having two valve positions 26A and 26B. One end of a panel 26g is in contact with the opposite side of the electromagnetic control valve 26 spool to the electromagnetic solenoid 26e side.
- the electromagnetic control valve 26 is switched between the valve positions 26A and 26B according to the control electric signal i applied to the electromagnetic solenoid 26e.
- FIG. 3 is a flow chart showing the procedure of processing performed by the lubricant supply control controller 50.
- the program corresponding to this flowchart is installed in the lubricant supply control controller 50.
- Control information of the engine controller 30 is sent to the lubricant supply control controller 50 via the electric signal line 31.
- the control information of the transmission controller 40 is sent to the lubricant supply control controller 50 via the electric signal line 41.
- a data frame signal according to a predetermined protocol is sent between each controller.
- control information inside the engine controller 30 is described in the data frame signal and is sent to the electric signal line 31.
- the transmission controller 40 the control information inside the transmission controller 40 is described in the data frame signal and is transmitted to the electric signal line 41.
- the input control information of the data frame signal force engine controller 30 and the control information of the transmission controller 40 are read (step 101).
- step 102 and 103 it is determined whether or not the load on the engine 1 and the load on the transmission 3 are low. If the load on 1 is low or the load on transmission 3 is low (YES in step 102 or YES in step 103), it is determined that the lubricant supplied to transmission 3 is excessive and should be reduced. To do. In other words, in the case of light loads, a small amount of oil is sufficient to reduce the mechanical friction and cool down with the lubricating oil to protect the components of Transmission 3, and conversely, If the above oil is supplied, it will become resistance when the planetary gear etc. rotates, causing power loss and worsening the fuel efficiency of engine 1.
- step 104 the process returns to step 101.
- the threshold value a c can be set to 70% of the maximum torque, for example (step 102).
- the speed stage ⁇ force currently selected in the transmission 3 is a light speed speed stage ⁇ cTC, that is, whether or not the transmission 3 is operating at a low load.
- the light load speed stage ⁇ c is set to, for example, “forward 4th speed” which is the maximum forward speed stage. “Forward 4th speed” is selected when the forward hydraulic clutch and the 4th speed hydraulic clutch are engaged (step 103).
- step 102 and 103 If the determinations in steps 102 and 103 are both NO, it is determined that the lubricating oil supplied to the transmission 3 should be increased. In other words, in the case of a high load, a large amount of oil is required to reduce mechanical friction and cool the lubricating oil to protect the components of the transmission 3. For this reason, the load is high and is supplied to the transmission 3. Control electric signal i for reducing the lubricating oil supplied to the transmission 3 so that the lubricating oil supplied to the transmission 3 is not reduced. The process returns to step 101 with the power off.
- control electric signal i is the electromagnetic solenoid of the electromagnetic control valve 26. 26e is not added, and the electromagnetic control valve 26 is switched to the lubricating oil supply position 26A by the panel power of the panel 26g.
- Lubricating oil in the lubricating oil tank 8 is sucked from the suction port 9a of the lubricating hydraulic pump 9 through the suction oil passage 10, and is discharged from the discharge port 9b of the lubricating hydraulic pump 9 to the pump discharge oil passage 11. Discharged.
- Lubricating oil which is pump discharge pressure oil, is supplied to the torque converter 2 via the pump discharge oil passage 11, the main relief valve 13, and the oil passage 14. The lubricating oil supplied to the torque converter 2 is used as hydraulic oil for driving force transmission in the torque converter 2.
- the lubricating oil guided to the oil passage 14 is supplied to the PTO shaft 7 via the oil passage 15 and the throttle 15a provided in the oil passage 15. This lubricates the components of the PTO shaft 7.
- the lubricating oil that has lubricated the PTO shaft 7 is discharged to the lubricating oil tank 8.
- the lubricating oil that has passed through the torque converter 2 is guided to the lubricating oil supply oil passage 17 via the oil cooler 16.
- the lubricating oil guided to the lubricating oil supply oil passage 17 is supplied to the transmission 3. This lubricates transmission 3.
- the lubricating oil that has lubricated the transmission 3 is discharged to the lubricating oil tank 8.
- the lubricating oil guided to the pump discharge oil passage 11 is supplied as pilot pressure oil (pilot pressure Pc) to the inlet port 26c of the electromagnetic control valve 26 via the pilot oil passage 25.
- the electromagnetic control valve 26 since the electromagnetic control valve 26 is switched to the lubricating oil supply position 26A, the pilot pressure oil supplied to the inlet port 26c is blocked at the inlet port 26c of the electromagnetic control valve 26. .
- the pilot port 22d of the relief valve 22 communicates with the lubricating oil tank 8 via the pilot oil passage 27, the outlet port 26d of the electromagnetic control valve 26, the tank port 26f, and the oil passage 29. Therefore, the pressure acting on the pilot port 22d of the relief valve 22 becomes the tank pressure, and the relief valve 22 does not reach the set relief pressure and is closed by the panel force of the panel 22c.
- the inlet port 26c and the outlet port 26d of the electromagnetic control valve 26 communicate with each other, and the pilot pressure oil (pilot pressure Pc) supplied to the inlet port 26c becomes the outlet port 26d of the electromagnetic control valve 26 and the pilot oil. Via line 27, it is added to pilot port 22d of relief valve 22.
- pilot pressure Pc acting on the pilot port 22d of the relief valve 22 is equal to or higher than the set relief pressure of the relief valve 22, and the force corresponding to the pilot pressure Pc overcomes the panel force of the panel 22c, and the relief valve 22 is opened.
- a part of the lubricating oil guided to the lubricating oil supply oil passage 17 passes through the relief valve 22 via the bypass oil passage 21.
- the lubricating oil that has passed through the relief valve 22 is discharged to the lubricating oil tank 8 through the bypass oil passage 23 and the throttle 28.
- the lubricating oil discharge flow rate that is discharged from the lubricating oil supply oil passage 17 through the relief valve 22 to the lubricating oil tank 8, and the lubricating oil supply flow amount that is supplied from the lubricating oil supply oil passage 17 to the transmission 3 This ratio can be adjusted depending on the size of the opening area of the throttle 28 provided on the outlet side of the relief valve 22.
- control information of the engine controller 30 and the control information of the transmission controller 40 are input to the lubricant supply control controller 50, and the control electric signal i is controlled based on the control information. Since the control of the lubricating oil supply is performed by operating and generating the relief valve 22, the existing control information used by the existing engine controller 30 and transmission controller 40 is added to the vehicle control system. By using it, the control system can be constructed easily and at low cost. That is, it is not necessary to add a new sensor in order to acquire control information. In addition, it is not necessary to process the sensor detection signal with the controller and convert it into engineering units required for arithmetic processing. In addition, it is not necessary for the controller to newly calculate the engine load or transmission load based on the detection values of various sensors. Therefore, the processing performed by the controller can be simplified as shown in Fig. 3.
- the relief valve 22 is operated to feed the lubricating oil in the lubricating oil supply oil passage 17 through the bypass oil passage 21, the relief valve 22, and the bypass oil passage 23.
- Discharged The hydraulic circuit is configured so that the valve body and piping for draining the lubricating oil in the lubricating oil supply oil passage 17 can be added to the existing lubricating oil supply oil passage 17 in the hydraulic circuit. Therefore, when constructing a hydraulic system, the configuration of the valve body and the handling of the hydraulic piping can be simplified, and the cost can be reduced.
- both the control information of the engine controller 30 and the control information of the transmission controller 40 are input to the lubricant supply control controller 50.
- the control information of the engine controller 30 or the transmission controller 40 Only one of the control information may be input. In this case, in the process of FIG. 3, one of steps 102 and 103 is omitted.
- the relief valve is operated on condition that the load on engine 1 is low and the load on transmission 3 is low (YES in step 102 and YES in step 103). It is also possible to output a control electric signal i for operating 22 (step 104).
- the control electric signal output from the engine controller 30 to the electric governor of the engine 1 is input to the lubricant supply control controller 50 as control information.
- the detected value of the stroke sensor 6a input to the engine controller 30, that is, the operation amount of the accelerator pedal 6, may be input to the controller 50 for supplying lubricant as control information indicating the load of the engine 1. Good.
- the lubricant supply control controller 50 when the operation amount of the accelerator pedal 50 is equal to or less than the predetermined operation amount, it may be determined that the load on the engine 1 is small.
- a throttle 28 is provided in the bypass oil passage 23 on the outlet side of the relief valve 22.
- the lubricating oil is discharged to the lubricating oil tank 8 at a flow rate corresponding to the opening area of the throttle 28, but instead of providing the throttle 28 in the non-pass oil passage 23, the bypass on the inlet side of the relief valve 22 is used. It may be provided in the oil passage 21. Further, the throttle 28 may be provided in the bypass oil passage 23 on the outlet side of the relief valve 22 and the bypass oil passage 21 on the inlet side of the relief valve 22, respectively.
- the pilot pressure oil (pilot pressure Pc) output from the electromagnetic control valve 26 is applied to the pilot port 22d of the relief valve 22 to open the relief valve 22. According to this configuration, it is possible to reduce the size of the electromagnetic solenoid to which the control electric signal i is applied (the electromagnetic solenoid 26e of the electromagnetic control valve 26).
- control electrical signal i output from the lubricating oil supply control controller 50 is applied directly to the relief valve 22 via the electrical signal line 51. May be configured.
- FIG. 5 (A) is a hydraulic circuit diagram corresponding to FIG. Components not shown in Fig. 5 (A) are the same as those shown in Fig. 2 unless otherwise specified.
- the arrangement of the electromagnetic control valve 26, the pilot oil passages 25 and 27, and the discharge oil passage 29 provided in the hydraulic circuit of FIG. 2 is omitted.
- the relief valve 22 is provided with an electromagnetic solenoid 22e instead of the pi port 22d shown in FIG.
- the relief valve 22 is used as a control valve, and the lubricating oil is discharged to the lubricating oil tank 8 via the no-pass circuits 21 and 23.
- a control valve other than the relief valve 22 it is possible to discharge the lubricating oil using a control valve other than the relief valve 22. That is, the amount of lubricating oil guided to the transmission 3 via the lubricating oil supply oil passage 17 and the amount of lubricating oil guided from the lubricating oil supply oil passage 17 to the lubricating oil tank 8 via the bypass oil passage 23
- Any control valve may be used as long as it is a control valve that adjusts.
- FIG. 6 is a hydraulic circuit diagram of the present embodiment and corresponds to FIG. Components not shown in FIG. 6 are the same as those in FIG. 2 unless otherwise specified.
- a control valve 60 configured as a two-position switching valve is provided.
- the outlet of the oil cooler 16 communicates with the lubricating oil supply oil passage 17.
- the lubricating oil supply oil passage 17 communicates with the inlet port 60c of the control valve 60.
- the outlet port 60d of the control valve 60 communicates with the transmission 3 and supplies lubricating oil to the transmission mechanism, clutch, and the like of the transmission 3.
- the tank port 60f of the control valve 60 communicates with the bypass oil passage 23.
- the bypass oil passage 23 communicates with the lubricating oil tank 8.
- the control valve 60 is a two-position switching valve having two valve positions 60A (lubricating oil supply position) and 60B (lubricating oil discharge position).
- the control valve 60 is switched between valve positions 60A and 60B in accordance with the pilot pressure Pc applied to the pilot port 60e.
- the pilot port 60e communicates with the outlet port 26d of the electromagnetic control valve 26 through the noroil oil passage 27.
- One end of the panel 60g is in contact with the side of the spool of the control valve 60 opposite to the pilot port 60e side.
- the pressure receiving surface of the control valve 60 spool on the pilot port 60e side (opposite to the panel 60g) communicates with the inlet port 60c via the pilot oil passage 24! /.
- the lubricating oil discharge flow rate that is discharged from the lubricating oil supply oil passage 17 through the control valve 60 to the lubricating oil tank 8, and the lubricating oil supply flow rate that is supplied from the lubricating oil supply oil passage 17 to the transmission 3 This ratio can be adjusted by adjusting the ratio of the opening area of the restrictor 63 and the opening area of the restrictor 62 provided in the control valve 60.
- the lubricating oil that has passed through the torque converter 2 is guided to the lubricating oil supply oil path 17 via the oil cooler 16.
- the lubricating oil introduced into the lubricating oil supply oil passage 17 is supplied to the inlet port 60c of the control valve 60.
- the lubricating oil guided to the pump discharge oil passage 11 is supplied as pilot pressure oil (pilot pressure Pc) to the inlet port 26c of the electromagnetic control valve 26 via the pilot oil passage 25.
- the electromagnetic control valve 26 since the electromagnetic control valve 26 is switched to the lubricating oil supply position 26A, the pilot pressure oil supplied to the inlet port 26c is blocked at the inlet port 26c of the electromagnetic control valve 26.
- the pilot port 60e of the control valve 60 communicates with the lubricating oil tank 8 via the pilot oil passage 27, the outlet port 26d of the electromagnetic control valve 26, the tank port 26f, and the oil passage 29.
- the pressure acting on the pilot port 60e of the control valve 60 becomes the tank pressure, and the control valve 60 is positioned at the lubricant supply position 60A by the panel force of the panel 60g. Therefore, the entire amount of the lubricating oil introduced to the lubricating oil supply oil passage 17 passes through the throttle 60d of the control valve 60, and is supplied to the transmission 3.
- the entire amount of the lubricating oil guided to the lubricating oil supply oil passage 17 is supplied to the transmission 3 without being discharged to the lubricating oil tank 8 via the bypass oil passage 23.
- pilot pressure oil (pilot pressure Pc) supplied to 6c is the outlet port 26d of the electromagnetic control valve 26.
- a part of the lubricating oil guided to the lubricating oil supply oil passage 17 is discharged to the lubricating oil tank 8 via the throttle 63 of the control valve 60 and the bypass oil passage 23. Further, the remainder of the lubricating oil introduced to the lubricating oil supply oil passage 17 is supplied to the transmission 3 through the throttle 62 of the control valve 60.
- the pilot pressure oil (pilot pressure Pc) output from the electromagnetic control valve 26 is applied to the pilot port 60e of the control valve 60, and the control valve 60 is switched. According to this configuration, it is possible to reduce the size of the electromagnetic solenoid to which the control electric signal i is applied (the electromagnetic solenoid 26e of the electromagnetic control valve 26).
- the control electrical signal i output from the lubricant supply control controller 50 is directly transmitted via the electrical signal line 51. It may be configured to act on the electromagnetic solenoid 60h of the control valve 60.
- control valve 60 is binary-switched according to the determination result of whether or not the load is small.
- the position of the valve 60 may be changed continuously.
- the controller 50 for lubricating oil supply control changes the control valve 60 to a position corresponding to the magnitude of the load based on the control information of the magnitude of the load of the engine 1 or the load of the transmission 3.
- the control valve 60 is gradually moved from the lubricating oil discharge position B side to the lubricating oil supply position A side, and as the load decreases.
- Control may be performed so that the control valve 60 is gradually moved from the lubricating oil supply position A side to the lubricating oil discharge position B side.
- a wheel loader is assumed as a vehicle
- a diesel engine is assumed as an engine
- a planetary gear type transmission is assumed as a transmission.
- the present invention can be applied regardless of the structure. In other words, not only construction machinery but also vehicles other than construction machinery are equipped with a parallel shaft gear type transmission that does not use a hydraulic clutch and that can be applied to vehicles equipped with gasoline engines that may be applied to the present invention. The present invention may be applied to such vehicles.
- FIG. 1 is a configuration diagram of a vehicle according to an embodiment.
- FIG. 2 is a hydraulic circuit diagram of the first embodiment.
- FIG. 3 is a flowchart illustrating a processing procedure performed by the controller of the embodiment.
- FIG. 4 is a flowchart showing a processing procedure different from FIG.
- FIGS. 5 (A) and 5 (B) are hydraulic circuit diagrams of a second embodiment and a fourth embodiment, respectively.
- FIG. 6 is a hydraulic circuit diagram of a third embodiment.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Control Of Transmission Device (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112005000055T DE112005000055B4 (de) | 2004-07-16 | 2005-07-14 | Schmierölzuführung-Steuervorrichtung für ein Wechselgetriebe |
US10/572,282 US8005599B2 (en) | 2004-07-16 | 2005-07-14 | Lubricating oil supply control device for transmission of vehicle |
JP2006526818A JP4653095B2 (ja) | 2004-07-16 | 2005-07-14 | 車両のトランスミッションの潤滑油供給制御装置 |
SE0600505A SE529229C2 (sv) | 2004-07-16 | 2006-03-08 | Regleranordning för smörjoljetillförsel för ett fordons transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004210366 | 2004-07-16 | ||
JP2004-210366 | 2004-07-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006009080A1 true WO2006009080A1 (ja) | 2006-01-26 |
Family
ID=35785193
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/013068 WO2006009080A1 (ja) | 2004-07-16 | 2005-07-14 | 車両のトランスミッションの潤滑油供給制御装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US8005599B2 (ja) |
JP (1) | JP4653095B2 (ja) |
DE (1) | DE112005000055B4 (ja) |
SE (1) | SE529229C2 (ja) |
WO (1) | WO2006009080A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007303519A (ja) * | 2006-05-10 | 2007-11-22 | Komatsu Ltd | 変速機 |
EP2085655A1 (en) * | 2008-01-29 | 2009-08-05 | GM Global Technology Operations, Inc. | Automatic transmission |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
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US7985154B2 (en) * | 2007-10-26 | 2011-07-26 | GM Global Technology Operations LLC | Method and apparatus to control hydraulic pressure for component lubrication in an electro-mechanical transmission |
JP5215780B2 (ja) * | 2008-09-03 | 2013-06-19 | 三菱重工業株式会社 | 増速機の潤滑装置及び方法 |
US7976419B2 (en) * | 2008-12-11 | 2011-07-12 | Ford Global Technologies, Llc | Control of the flow rate in a transmission oil cooler |
GB2470349B (en) * | 2009-05-12 | 2014-07-23 | Gm Global Tech Operations Inc | Fluid supply system and method of operating a fluid supply system |
JP2011108838A (ja) * | 2009-11-17 | 2011-06-02 | Fujitsu Ten Ltd | 電子制御装置 |
JP5578127B2 (ja) * | 2011-03-30 | 2014-08-27 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド駆動装置 |
KR101461876B1 (ko) * | 2013-04-02 | 2014-11-13 | 현대자동차 주식회사 | 차량용 자동변속기의 유압공급시스템 |
DE102015204834A1 (de) * | 2015-03-18 | 2016-09-22 | Zf Friedrichshafen Ag | Ölversorgungsanordnung und Verfahren zur Ölversorgung |
JP6274293B1 (ja) * | 2016-11-09 | 2018-02-07 | マツダ株式会社 | 油圧作動式変速機 |
JP6274292B1 (ja) | 2016-11-09 | 2018-02-07 | マツダ株式会社 | 油圧作動式変速機 |
US10309522B2 (en) * | 2017-01-23 | 2019-06-04 | Borgwarner Inc. | Transfer case pump with multiple flow paths to internal components |
FR3107560B1 (fr) * | 2020-02-21 | 2022-02-04 | Safran Aircraft Engines | Isolement d’un echangeur thermique de turbomachine en cas de fuite par un distributeur electrique et hydromecanique |
CN113917115B (zh) * | 2020-07-08 | 2023-09-01 | 广州汽车集团股份有限公司 | 变速器润滑油含气量检测系统、方法、装置及存储介质 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62199562U (ja) * | 1986-06-09 | 1987-12-18 | ||
JPH0626565A (ja) * | 1992-07-08 | 1994-02-01 | Nissan Motor Co Ltd | 無段変速機の油圧制御装置 |
JP2001330107A (ja) * | 2000-05-23 | 2001-11-30 | Honda Motor Co Ltd | 車両用自動変速機における潤滑油量制御装置 |
JP2002195371A (ja) * | 2000-12-28 | 2002-07-10 | Toyota Motor Corp | トロイダル型無段変速機 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6191658A (ja) | 1984-10-11 | 1986-05-09 | Mitsubishi Paper Mills Ltd | ハロゲン化銀写真感光材料の処理方法 |
JPS6191658U (ja) * | 1984-11-22 | 1986-06-13 | ||
CH670228A5 (ja) | 1986-02-27 | 1989-05-31 | Schweizerische Lokomotiv | |
JPH01169161A (ja) | 1987-12-22 | 1989-07-04 | Honda Motor Co Ltd | 変速機の潤滑圧制御バルブ |
JPH01242872A (ja) | 1988-03-22 | 1989-09-27 | Nissan Motor Co Ltd | 自動変速機の潤滑流量制御装置 |
JPH05106732A (ja) | 1991-10-15 | 1993-04-27 | Hitachi Constr Mach Co Ltd | Hst油圧走行駆動装置 |
JPH05263895A (ja) | 1992-03-19 | 1993-10-12 | Nissan Motor Co Ltd | 自動変速機の潤滑流量制御装置 |
JP3322072B2 (ja) * | 1994-08-12 | 2002-09-09 | トヨタ自動車株式会社 | 動力伝達機構の潤滑装置 |
US5522476A (en) * | 1994-11-30 | 1996-06-04 | Dana Corporation | Lubrication system for vehicle transmission |
JP4029945B2 (ja) | 1996-11-07 | 2008-01-09 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の潤滑油制御装置 |
JP3711688B2 (ja) * | 1997-03-22 | 2005-11-02 | マツダ株式会社 | トロイダル式無段変速機 |
JP3635190B2 (ja) * | 1997-07-09 | 2005-04-06 | 日産自動車株式会社 | 自動変速機の油圧制御装置 |
JP3592093B2 (ja) * | 1998-08-10 | 2004-11-24 | ジヤトコ株式会社 | トロイダル型無段自動変速機の潤滑構造 |
JP3512724B2 (ja) | 2000-09-05 | 2004-03-31 | 本田技研工業株式会社 | 車両用自動変速機の油圧制御装置 |
JP2002181175A (ja) * | 2000-12-19 | 2002-06-26 | Aisin Aw Co Ltd | 無段変速機の油圧制御装置 |
JP3622689B2 (ja) * | 2001-04-24 | 2005-02-23 | トヨタ自動車株式会社 | 動力伝達装置用作動油温の制御装置 |
DE10308502B4 (de) | 2003-02-26 | 2018-02-01 | Volkswagen Ag | Verfahren zur Steuerung eines automatisierten Kfz-Getriebes |
-
2005
- 2005-07-14 US US10/572,282 patent/US8005599B2/en not_active Expired - Fee Related
- 2005-07-14 WO PCT/JP2005/013068 patent/WO2006009080A1/ja active Application Filing
- 2005-07-14 DE DE112005000055T patent/DE112005000055B4/de not_active Expired - Fee Related
- 2005-07-14 JP JP2006526818A patent/JP4653095B2/ja not_active Expired - Fee Related
-
2006
- 2006-03-08 SE SE0600505A patent/SE529229C2/sv not_active IP Right Cessation
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62199562U (ja) * | 1986-06-09 | 1987-12-18 | ||
JPH0626565A (ja) * | 1992-07-08 | 1994-02-01 | Nissan Motor Co Ltd | 無段変速機の油圧制御装置 |
JP2001330107A (ja) * | 2000-05-23 | 2001-11-30 | Honda Motor Co Ltd | 車両用自動変速機における潤滑油量制御装置 |
JP2002195371A (ja) * | 2000-12-28 | 2002-07-10 | Toyota Motor Corp | トロイダル型無段変速機 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007303519A (ja) * | 2006-05-10 | 2007-11-22 | Komatsu Ltd | 変速機 |
EP2085655A1 (en) * | 2008-01-29 | 2009-08-05 | GM Global Technology Operations, Inc. | Automatic transmission |
Also Published As
Publication number | Publication date |
---|---|
US8005599B2 (en) | 2011-08-23 |
DE112005000055T5 (de) | 2006-09-21 |
JP4653095B2 (ja) | 2011-03-16 |
DE112005000055B4 (de) | 2013-11-07 |
US20080234903A1 (en) | 2008-09-25 |
SE529229C2 (sv) | 2007-06-05 |
SE0600505L (sv) | 2006-05-11 |
JPWO2006009080A1 (ja) | 2008-05-01 |
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