WO2013069101A1 - Dispositif de commutation d'état de fonctionnement pour pompe à capacité variable - Google Patents

Dispositif de commutation d'état de fonctionnement pour pompe à capacité variable Download PDF

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Publication number
WO2013069101A1
WO2013069101A1 PCT/JP2011/075787 JP2011075787W WO2013069101A1 WO 2013069101 A1 WO2013069101 A1 WO 2013069101A1 JP 2011075787 W JP2011075787 W JP 2011075787W WO 2013069101 A1 WO2013069101 A1 WO 2013069101A1
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WIPO (PCT)
Prior art keywords
flow rate
operation state
discharge flow
variable displacement
displacement pump
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PCT/JP2011/075787
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English (en)
Japanese (ja)
Inventor
恵以地 西山
章宏 柴原
三千夫 小島
俊和 畝山
知朗 石川
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本田技研工業株式会社
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Priority to PCT/JP2011/075787 priority Critical patent/WO2013069101A1/fr
Publication of WO2013069101A1 publication Critical patent/WO2013069101A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • F04C2270/205—Controlled or regulated

Definitions

  • the present invention relates to a variable displacement pump that discharges oil sucked from a plurality of suction ports from a plurality of discharge ports, and a total capacity in which the plurality of discharge ports are completely cut off from the plurality of suction ports.
  • the present invention relates to an operation state switching device for a variable displacement pump comprising an operation state or an operation state switching means for switching to a partial capacity operation state in which at least one of the plurality of discharge ports communicates with at least one of the plurality of suction ports.
  • Patent Document 1 discloses that such a variable displacement pump operating state switching device is used for the purpose of supplying oil to an automobile transmission.
  • the displacement flow rate of a positive displacement pump such as a vane pump is proportional to the rotation speed, so when trying to secure the required discharge flow rate in a region where the engine rotation speed is low, There is a problem in that the discharge flow rate becomes excessive in a region where the engine speed is high, the power for driving the variable displacement pump is wasted, and the fuel consumption of the engine increases.
  • Patent Document 1 operates the variable displacement pump in a full capacity operation state in a region where the engine speed is less than a predetermined value, and operates the variable displacement pump in half capacity in a region where the engine speed is a predetermined value or more. By operating in the driving state, the fuel consumption of the engine is reduced.
  • Japanese Unexamined Patent Publication No. 2011-163258 Japanese Unexamined Patent Publication No. 2011-163258
  • variable displacement pump may be able to be in a half displacement operation state depending on the operation state of the vehicle. There was a problem that energy was wasted because the pump was uniformly operated at full capacity.
  • the present invention has been made in view of the above circumstances, and aims to save energy by setting the variable displacement pump to a partial displacement operation state as much as possible while ensuring the necessary discharge flow rate of the variable displacement pump.
  • a variable displacement pump that discharges oil sucked from a plurality of suction ports from a plurality of discharge ports, and the variable displacement pump, the plurality of discharge ports include the plurality of discharge ports.
  • Variable capacity comprising operating state switching means for switching to a full capacity operating state completely shut off from the suction port or a partial capacity operating state in which at least one of the plurality of discharge ports communicates with at least one of the plurality of suction ports
  • a pump operating state switching device a partial capacity operating state discharge flow rate calculating means for calculating a discharge flow rate of the variable capacity pump when in the partial capacity operating state, and the pump set according to the operating state of the vehicle
  • a required discharge flow rate calculating means for calculating a required discharge flow rate of the variable displacement pump, and the operating state switching means is the partial capacity operation state.
  • variable displacement pump If the difference between the discharge flow rate calculated by the discharge flow rate calculation means and the required discharge flow rate calculated by the required discharge flow rate calculation means is greater than or equal to a predetermined determination threshold, switching the variable displacement pump to the partial capacity operation state is not allowed.
  • An operation state switching device for a variable displacement pump as one feature is proposed.
  • the required discharge flow rate calculating means includes a flow rate required for shifting the transmission, a flow rate leaking from the hydraulic circuit of the transmission, and a flow rate required for lubricating the transmission.
  • a variable displacement pump operating state switching device having a second feature of calculating the required discharge flow rate from at least one of the above is proposed.
  • the operation state switching means fixes the variable displacement pump to the full capacity operation state when the engine speed is less than a predetermined value.
  • a variable displacement pump operating state switching device having the third feature is proposed.
  • the operation state switching means fixes the variable displacement pump to the partial displacement operation state when the engine speed is a predetermined value or more.
  • a variable displacement pump operating state switching device having the fourth feature is proposed.
  • the operation state switching means fixes the variable displacement pump to the partial displacement operation state when the transmission oil temperature is lower than a predetermined value.
  • a variable displacement pump operating state switching device having the fifth feature is proposed.
  • the operation state switching means may be configured to switch the variable displacement pump when the transmission oil temperature is equal to or higher than a predetermined value and the engine speed is lower than the predetermined value.
  • a variable displacement pump operating state switching device having a sixth feature of fixing to the full capacity operating state is proposed.
  • the first suction port 16A and the second suction port 16B of the embodiment correspond to the suction port of the present invention
  • the first discharge port 17A and the second discharge port 17B of the embodiment correspond to the discharge port of the present invention
  • the oil pump OP of the embodiment corresponds to the variable displacement pump of the present invention
  • the half capacity operation state discharge flow rate calculation means M1 of the embodiment corresponds to the partial capacity operation state discharge flow rate calculation means of the present invention.
  • the half capacity operation state of the form corresponds to the partial capacity operation state of the present invention.
  • the partial capacity operation state discharge flow rate calculating means calculates the discharge flow rate when the variable displacement pump is in the partial capacity operation state, and the required discharge flow rate calculation means is responsive to the driving state of the vehicle.
  • the operation state switching means calculates the difference between the discharge flow rate calculated by the partial capacity operation state discharge flow rate calculation means and the required discharge flow rate calculated by the required discharge flow rate calculation means. Since the variable displacement pump is switched to the partial displacement operation state when the predetermined judgment threshold is exceeded, the variable displacement pump can be driven by operating the variable displacement pump as much as possible while ensuring the minimum required discharge flow rate. Energy can be saved.
  • the required discharge flow rate calculation means calculates the required discharge flow rate from the flow rate required for shifting the transmission, the flow rate leaking from the transmission hydraulic circuit, or the flow rate required for lubricating the transmission. Therefore, it is possible to calculate an appropriate required discharge flow rate.
  • the operating state switching means fixes the variable displacement pump to the full capacity operating state when the engine speed is less than a predetermined value, so that the minimum lubrication of the lubrication target portion is required. It is possible to secure an oil flow rate that makes it possible.
  • the operating state switching means fixes the variable displacement pump to the partial displacement operating state when the engine speed is greater than or equal to a predetermined value, so that the discharge pressure becomes excessive and the variable displacement It is possible to prevent erosion from occurring in the pump.
  • the operating state switching means fixes the variable displacement pump to the partial displacement operating state when the transmission oil temperature is lower than a predetermined value, so that the oil viscosity becomes high and it is difficult to flow.
  • the variable displacement pump it is possible to prevent the variable displacement pump from entering the full capacity operation state and generating aeration.
  • the operation state switching means fixes the variable displacement pump to the full displacement operation state when the transmission oil temperature is equal to or higher than a predetermined value, so that the oil viscosity is lowered and the pump efficiency is reduced.
  • the full flow operation state can be established to ensure the necessary flow rate.
  • the partial capacity operation state is enabled without being fixed to the full capacity operation state. It is possible to avoid the transmission oil temperature from rising excessively while being fixed in the operating state.
  • FIG. 1 is a diagram showing a hydraulic circuit of a transmission.
  • FIG. 2 is a block diagram of a control system of the operating state switching device.
  • FIG. 3 is a diagram for explaining the operation of the oil pump during full capacity operation.
  • FIG. 4 is a diagram for explaining the operation of the oil pump during half capacity operation.
  • FIG. 5 is a map for searching a full capacity / half capacity switchable area.
  • FIG. 6 is an explanatory diagram of a method for calculating the surplus flow rate.
  • FIG. 7 is a block diagram for explaining the control of the embodiment.
  • FIG. 8 is a flowchart for explaining the control of the embodiment.
  • FIG. 1 shows a part of a hydraulic circuit of a transmission for a vehicle including, for example, a belt type continuously variable transmission.
  • a variable capacity oil pump OP comprising a vane pump connected to a mission shaft and operated by the driving force of a traveling engine rotates an elliptical cam ring 11, a rotor 12 disposed inside the cam ring 11, and the rotor 12.
  • a pump shaft 13 that is freely supported, a plurality of vanes 14 that are slidably supported in the radial direction around the rotor 12 and that are in sliding contact with the inner surface of the cam ring 11, and the cam ring 11, the rotor 12, and the vanes 14.
  • the first and second discharge ports that can communicate with the plurality of working chambers 15, the first and second suction ports 16A and 16B that can communicate with the working chamber 15 with an increased volume, and the working chamber 15 with a reduced volume. Ports 17A and 17B.
  • An oil passage P1 extending from the oil tank 18 branches into bifurcated oil passages P2 and P3, one oil passage P2 is connected to the first suction port 16A, and the other oil passage P3 is connected to the second suction port 16B. Is done.
  • Oil passages P4 and P5 extending from the first discharge port 17A are connected to a hydraulic actuator 19 such as a transmission pulley oil chamber, a hydraulic clutch, and a hydraulic brake, and the oil pump OP discharges between the oil passage P4 and the oil passage P5.
  • a regulator valve 20 for adjusting the pressure to the line pressure is interposed.
  • the pump shift valve 21 includes a spool 23 biased by a spring 22, a port 21a connected to an oil passage P6 to which a modulator pressure is transmitted via a shift solenoid valve 24, and a port connected to an oil passage P1 via an oil passage P7. 21b, a port 21c connected to the second discharge port 17B via the oil passage P8, a port 21d connected to the oil passage P4 via the oil passage P9, and a port 21e connected to the oil passage P10 to which the modulator pressure is transmitted.
  • the electronic control unit U that switches the operation state of the oil pump OP between the full capacity operation state and the half capacity operation state includes the half capacity operation state discharge flow rate calculation means M1, the required discharge flow rate calculation means M2, And operating state switching means M3.
  • the oil pump OP is in a half capacity operation state based on the engine speed detected by the engine speed sensor Sa and the transmission oil temperature detected by the transmission oil temperature sensor Sb.
  • the oil discharge flow rate is calculated.
  • the required discharge flow rate calculation means M2 calculates the required discharge flow rate of the oil pump OP that is currently required based on the specifications of the vehicle and the driving state of the vehicle.
  • the operation state switching means M3 compares the discharge flow rate of the oil pump OP calculated by the half capacity operation state discharge flow rate calculation means M1 with the required discharge flow rate of the oil pump OP calculated by the required discharge flow rate calculation means M2. By controlling the shift solenoid valve 24 based on the result, the operation state of the oil pump OP is switched to the full capacity operation state or the half capacity operation state.
  • the electronic control unit U when the oil pump OP operates at full capacity, the electronic control unit U outputs an OFF signal so that the shift solenoid valve 24, which is a normally open solenoid valve, is demagnetized and opened.
  • the modulator pressure is transmitted to the port 21a at the right end of the valve 21.
  • the modulator pressure is also transmitted to the left end port 21 e of the pump shift valve 21, but the spool 23 of the pump shift valve 21 moves to the left by the elastic force of the spring 22.
  • the port 21c and the port 21d communicate with each other, and the second discharge port 17B of the oil pump OP communicates with the oil path P4 through the path of the oil path P8 ⁇ port 21c ⁇ port 21d ⁇ oil path P9.
  • the oil discharged from the first and second discharge ports 17A and 17B merges in the oil passage P4 and is supplied to the hydraulic actuator 19 and the lubricated portion via the regulator valve 20 and the oil passage P5.
  • the shift solenoid valve 24 which is a normally open solenoid valve, is energized and closed when the electronic control unit U outputs an ON signal. Since the transmission of the modulator pressure to the port 21a of the valve 21 is cut off, the modulator pressure transmitted to the port 21e at the left end of the pump shift valve 21 overcomes the elastic force of the spring 22 and the spool 23 moves to the right.
  • the port 21b and the port 21c communicate with each other, and the second discharge port 17B of the oil pump OP communicates with the oil path P1 through the path of the oil path P8 ⁇ port 21c ⁇ port 21b ⁇ oil path P7.
  • the oil discharged from the second discharge port 17B is returned to the first and second suction ports 16A and 16B, and only the oil discharged from the first discharge port 17A is supplied to the oil passage P4.
  • the hydraulic pressure generated by the half-capacity operation of the oil pump OP is supplied to the hydraulic actuator 19 and the lubrication target portion in the same manner as the hydraulic pressure generated by the full-capacity operation.
  • the region where the oil pump OP is operated at full capacity and the region where the oil pump OP is operated at half capacity are the engine speed detected by the engine speed sensor Sa and the transmission oil temperature detected by the transmission oil temperature sensor Sb. It is determined by the map used as a parameter.
  • the oil pump OP speed decreases and the oil discharge flow rate decreases, so that the seized portion of the transmission is not seized.
  • the oil pump OP is fixed in the full capacity operation state so that the oil can be supplied.
  • Oil pump OP parts that come into contact with oil by erosion caused by cavitation may occur due to the increase in the rotation speed of oil pump OP in the high rotation half-capacity operation fixed region where the engine speed is greater than or equal to a predetermined value.
  • the oil pump OP is fixed to a half capacity operation state so that the motor is not damaged.
  • the oil viscosity may increase and it may be difficult to flow smoothly through the hydraulic circuit, and the function of the oil pump OP is maintained by suppressing the occurrence of aeration. Therefore, the oil pump OP is fixed to the half capacity operation state.
  • full capacity operation is performed in areas other than the low rotation full capacity fixed area, the high rotation half capacity fixed area, the low temperature half capacity fixed area, and the high temperature full capacity fixed area, that is, in the remaining full capacity / half capacity switchable area. If the required discharge flow rate is obtained even in the half-capacity operation state, the half-capacity operation state is set. If the required discharge flow rate cannot be obtained in the half-capacity operation state, the full-capacity operation state is established. And
  • the half capacity operation state discharge flow rate calculation means M1 calculates the discharge flow rate when the oil pump OP is in the half capacity operation state based on the engine speed and the transmission oil temperature.
  • the required discharge flow rate calculation means M2 calculates the required discharge flow rate of the oil pump OP required by the transmission from the specifications of the vehicle and the driving state of the vehicle.
  • the required discharge flow rate is the flow rate required to change gears by changing the drive pulley of the transmission and the side pressure of the drive pulley, the flow rate corresponding to the amount of oil leakage from the hydraulic circuit of the transmission, and the lubricated part of the transmission. It consists of the flow rate required for lubrication.
  • the operation state switching means M3 calculates a surplus flow by subtracting a necessary flow rate that is the sum of the three flow rates from a discharge flow rate when the oil pump OP is in a half capacity operation state, and the surplus flow rate is equal to or greater than a preset threshold value. If so, the oil pump OP is controlled to the half capacity operation state, and if less than the threshold value, the oil pump OP is controlled to the full capacity operation state.
  • the “function protection, full / half capacity determination block” performs the processing described in FIG. 5, and based on the engine speed and transmission oil temperature, the low rotation full capacity fixed area and the high rotation half capacity fixed. In the case of the low rotation full capacity fixed area and the high temperature full capacity fixed area, the area, the low temperature half capacity fixed area, the high temperature full capacity fixed area, and the full capacity / half capacity switchable area (normal area) are separated. The discharge capacity of the oil pump OP is fixed at the full capacity operation state.
  • the oil pump OP discharge capacity is fixed at the half capacity operation state, and the total capacity /
  • the operation state of the oil pump OP is set to either the full capacity operation state or the half capacity operation state.
  • the discharge flow rate in the half capacity operation state of the oil pump OP is calculated.
  • the discharge flow rate of the oil pump OP can be calculated by the product of the engine speed, the efficiency of the oil pump OP, and the discharge flow rate per one rotation of the engine.
  • the required discharge flow rate of the oil pump OP is calculated.
  • the required discharge flow rate is composed of a flow rate required for shifting, a flow rate corresponding to the amount of oil leakage, and a flow rate required for lubrication of the lubricated part, and the sum of these is the required discharge flow rate.
  • the flow rate required for shifting is calculated as the product of the piston area of the drive pulley and driven pulley and the stroke amount of the piston per unit time.
  • the flow rate corresponding to the amount of oil leakage is searched by applying the current PH pressure and oil temperature of the hydraulic circuit to a three-dimensional map determined from design specifications.
  • the flow rate required for lubrication of the lubricated part is calculated by the product of the search value of the three-dimensional map of transmission ratio-engine speed measured for each oil temperature and the lockup clutch pressure coefficient.
  • the marginal flow rate is obtained by subtracting the required discharge flow rate from the discharge flow rate in the half capacity operation state of the oil pump OP calculated as described above, and processing the difference with a low-pass filter.
  • the “flow rate balance determination block” it is determined whether or not the driving state of the vehicle is in a stable state. That is, when any one of the following conditions is satisfied, it is determined that the stable condition is not satisfied (unstable), and the oil pump OP is set to the full capacity operation state.
  • the oil pump OP Since the relationship between the flow balance calculation and the actual machine is deviated, the oil pump OP is set to the full capacity operation state. When the condition (12) is satisfied, it is difficult to ensure the accuracy of the flow balance calculation, and therefore the oil pump OP is set to the full capacity operation state.
  • the full capacity operation state and the half capacity operation state are switched by comparing the surplus flow rate with a threshold value. That is, when the oil pump OP is currently in the full capacity operation state, the surplus flow rate exceeds the end threshold value, and when the surplus flow rate exceeds the start threshold value (> end threshold value), the full capacity operation state of the oil pump OP is ended. . When the oil pump OP is currently in the half capacity operation state, the half capacity operation state of the oil pump OP is ended when the surplus flow rate is less than the end threshold value.
  • the timer is started when the switching signal between the full capacity operation state and the half capacity operation state is input from the “Flow Balance Determination Block”, and the state is stable after a predetermined time. Is confirmed, the oil pump OP is switched to the full capacity operation state or the half capacity operation state.
  • step S1 the discharge flow rate in the half capacity operation state of the oil pump OP is calculated.
  • step S2 the required discharge flow rate is calculated according to the vehicle operation state.
  • step S3 the discharge flow rate in the half capacity operation state is calculated.
  • a surplus flow rate is calculated as a flow rate balance obtained by subtracting the discharge flow rate.
  • step S4 if the engine speed and transmission oil temperature are in the low rotation full capacity fixed region, the oil pump OP is fixed to the full capacity operation state, and in step S5, the engine speed and transmission oil temperature are fixed in the high rotation half capacity fixed region. If so, the oil pump OP is fixed in the half capacity operation state. If the engine speed and the transmission oil temperature are in the low temperature half capacity fixed region in step S6, the oil pump OP is fixed in the half capacity operation state. If the rotational speed and the transmission oil temperature are in the high temperature full capacity fixed region, the oil pump OP is fixed to the full capacity operation state.
  • step S8 the flow rate balance (surplus flow rate) is compared with the threshold value, and if the balance is negative and the surplus flow rate is insufficient, the oil pump OP is set to the full capacity operation state. If the balance is positive and the surplus flow rate is not insufficient in step S8, the oil pump OP is set to a half capacity operation state after confirming that the state has stabilized after a predetermined time in step S9.
  • the difference between the discharge flow rate calculated by the half capacity operation state discharge flow rate calculation unit M1 and the required discharge flow rate calculated by the required discharge flow rate calculation unit M2 is equal to or greater than a predetermined determination threshold value.
  • the operation state switching means M3 switches the variable displacement pump OP to the half displacement operation state, the variable displacement pump OP is operated by half capacity as much as possible while ensuring the necessary minimum discharge flow rate. The driving energy of the pump OP can be saved.
  • the required discharge flow rate calculation means M2 calculates the required discharge flow rate from the flow rate required for transmission shifting, the flow rate leaking from the hydraulic circuit of the transmission, and the flow rate required for lubrication of the transmission. be able to.
  • variable displacement pump of the present invention is not limited to the vane pump of the embodiment, and may be a gear pump or a trochoid pump.
  • partial capacity operation state of the present invention is not limited to the half capacity operation state, and may be an operation state having a smaller capacity than the full capacity operation state.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)

Abstract

Selon l'invention, un moyen de calcul du débit volumique de refoulement de l'état de fonctionnement à demi-capacité (M1) calcule le débit volumique de refoulement lorsqu'une pompe à capacité variable (OP) est dans l'état de fonctionnement à demi-capacité et un moyen de calcul du débit volumique de refoulement requis (M2) calcule un débit volumique de refoulement requis pour la pompe à capacité variable (OP), qui est réglé en fonction de l'état de fonctionnement du véhicule. Lorsque la différence entre le débit volumique de refoulement calculé par le moyen de calcul du débit volumique de refoulement d'état de fonctionnement à demi-capacité (M1) et le débit volumique de refoulement requis calculé par le moyen de calcul du débit volumique de refoulement requis (M2) est égale ou supérieure à une valeur seuil de détermination prescrite, un moyen de commutation d'état de fonctionnement (M3) commute la pompe à capacité variable (OP) sur l'état de fonctionnement à demi-capacité, de telle sorte que la pompe à capacité variable (OP) travaille à demi-capacité autant que possible tout en maintenant le débit volumique de refoulement requis minimum, en permettant ainsi d'économiser sur l'énergie d'entraînement pour la pompe à capacité variable (OP). Le moyen de calcul du débit volumique de refoulement requis (M2) calcule le débit volumique de refoulement requis sur la base du débit volumique requis pour changer les rapports au moyen de la transmission, du débit volumique de la fuite du circuit hydraulique de la transmission et du débit volumique requis pour lubrifier la transmission, et il est ainsi possible de calculer un débit volumique de refoulement requis précis.
PCT/JP2011/075787 2011-11-09 2011-11-09 Dispositif de commutation d'état de fonctionnement pour pompe à capacité variable WO2013069101A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016183579A (ja) * 2015-03-25 2016-10-20 富士重工業株式会社 オイルポンプの吐出量切替装置
JP2017155875A (ja) * 2016-03-03 2017-09-07 本田技研工業株式会社 車両の油圧制御装置
JP2019199929A (ja) * 2018-05-17 2019-11-21 株式会社Ｓｕｂａｒｕ オイルポンプの固着検知装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0533857A (ja) * 1991-07-26 1993-02-09 Fuji Heavy Ind Ltd 無段変速機の油圧制御装置
JPH1089430A (ja) * 1996-08-26 1998-04-07 Van Doornes Transmissie Bv 連続可変変速機
JP2001140771A (ja) * 1999-11-18 2001-05-22 Honda Motor Co Ltd 容量切換型作動油供給装置
JP2011163258A (ja) * 2010-02-12 2011-08-25 Honda Motor Co Ltd 可変容量ポンプの運転状態判定装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0533857A (ja) * 1991-07-26 1993-02-09 Fuji Heavy Ind Ltd 無段変速機の油圧制御装置
JPH1089430A (ja) * 1996-08-26 1998-04-07 Van Doornes Transmissie Bv 連続可変変速機
JP2001140771A (ja) * 1999-11-18 2001-05-22 Honda Motor Co Ltd 容量切換型作動油供給装置
JP2011163258A (ja) * 2010-02-12 2011-08-25 Honda Motor Co Ltd 可変容量ポンプの運転状態判定装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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