Source: https://patents.google.com/patent/EP2441985B1/en
Timestamp: 2020-08-07 18:56:16
Document Index: 322429379

Matched Legal Cases: ['art 5', 'art 11', 'art 5', 'art 11', 'art 11', 'art 5', 'art 11', 'art 5', 'art 5', 'art 11', 'art 36', 'art 36', 'art 42', 'art 42', 'art 36', 'art 42', 'art 35', 'art 42', 'art 42', 'art 36', 'art 42', 'art 36', 'art 42', 'art 42', 'art 36', 'art 42', 'art 36', 'art 36', 'art 42', 'art 42', 'art 42', 'art 36', 'art 36', 'art 42', 'art 42']

EP2441985B1 - Oil supply system of automatic transmission - Google Patents
Oil supply system of automatic transmission Download PDF
EP2441985B1
EP2441985B1 EP20100192873 EP10192873A EP2441985B1 EP 2441985 B1 EP2441985 B1 EP 2441985B1 EP 20100192873 EP20100192873 EP 20100192873 EP 10192873 A EP10192873 A EP 10192873A EP 2441985 B1 EP2441985 B1 EP 2441985B1
EP20100192873
EP2441985A2 (en
EP2441985A3 (en
Wonjune Sung
2010-10-12 Priority to KR1020100099188A priority Critical patent/KR20120037623A/en
2010-11-29 Application filed by Hyundai Motor Co filed Critical Hyundai Motor Co
2012-04-18 Publication of EP2441985A2 publication Critical patent/EP2441985A2/en
2012-07-04 Publication of EP2441985A3 publication Critical patent/EP2441985A3/en
2013-07-31 Publication of EP2441985B1 publication Critical patent/EP2441985B1/en
230000001105 regulatory Effects 0.000 claims description 38
230000003134 recirculating Effects 0.000 claims description 6
230000001050 lubricating Effects 0.000 description 7
F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
The present application claims priority to Korean Patent Application Number 10-2010-0099188 filed October 12, 2010 .
The present invention relates to an oil supply system of an automatic transmission, and more particularly, to an oil supply system of an automatic transmission that supply oil from an oil reservoir to a high-pressure part for operating a clutch and to a low-pressure part for cooling and lubricating, using an oil pump.
As the oil price increases and the regulation for exhaust gas (CO2) is enhanced over the world in recent years, it is very important to improve fuel efficiency and consider eco-friendly factors in developing vehicles and the advanced car manufacturers have devoted all their strength to come up with technologies for saving fuel in order to achieve those objects.
Improving power transmission efficiency the transmission is necessary to improve fuel efficiency in automatic transmission vehicles, but the oil pump in the automatic transmission is a part reducing the power transmission efficiency, such that the power transmission efficiency of the transmission can be considerably increased, if unnecessary power consumption of the oil pump can be reduced.
The output flow rate of the oil pump is composed of the flow rate of the high-pressure part for operating the clutch, the flow rate of the low-pressure part for cooling and lubricating, and the recirculation flow rate retuning the flow rate left after generating desired oil pressure from a regulating valve to the inlet of the oil pump, however, the oil supply systems discharges the entire oil on the basis of the high-pressure part used to control the clutch in the related art, such that the oil pump consumes a large amount of power and accordingly the power transmission efficiency of transmissions is reduced.
That is, according to an oil supply system of the related art, as shown in FIG 1, an inlet 1a of an oil pump 1 is connected with an oil reservoir 3 through an oil supply channel 2, an outlet 1b of oil pump 1 is connected to a high-pressure part 5 for operating a clutch through a high-pressure part channel 4, high-pressure channel 4 is connected with a high-pressure regulating valve 8 and a reducing valve 9 through a first valve channel 6 and a second valve channel 7, respectively, reducing valve 9 is connected to a low-pressure part 11 for cooling and lubricating through a low-pressure part channel 10, and high-pressure regulating valve 8 and reducing valve 9 are connected with oil supply channel 2 through a first return channel 12 and a second return channel 13, respectively.
In this configuration, oil 14 in oil reservoir 3 is supplied to inlet 1a of oil pump 1 through oil filter 15 and oil pump 1 is operated by power from an engine 16.
Therefore, as oil pump 1 is operated by the power from engine 16, oil 14 in oil reservoir 3 flows into inlet 1a and the oil discharged from outlet 1b to high-pressure part channel 4 is controlled at high pressure by high-pressure regulating valve 8 and supplied to high-pressure part 5.
Some of the oil in high-pressure part channel 4 is supplied to reducing valve 9 through second valve channel 7, reducing valve 9 reduces high pressure of the oil to low pressure, and the oil at the low pressure reduced by reducing valve 9 is supplied to low-pressure part 11.
Further, the oil left from the oil increased in pressure by high-pressure regulating valve 8 recirculates to inlet 1a of oil pump 1 through first return channel 12 and oil supply channel 2 and the oil left from the oil decreased in pressure by reducing valve 9 recirculates to inlet 1a of oil pump 1 through second return channel 13 and oil supply channel 2.
In general, since low-pressure part 11 is used to cooling and lubricating the transmission, it needs a lot of flow rate, while since high-pressure part 5 is used to control the clutch, it needs a smaller amount of flow rate than low-pressure part 11.
Therefore, according to the oil supply system having the configuration of the related art, oil pump 1 discharges the entire flow rate on the basis of high-pressure part 5, such that oil pump 1 requires a large amount power. For example, assuming that high-pressure part 5 requires pressure of 20kgf/cm2 and flow rate of 51pm, low-pressure part 11 requires pressure of 8kgf/cm2 and flow rate 101pm, and the recirculation flow rate is 151pm, the consuming power of oil pump 1 of the system according to the related art is defined by "consuming power = high-pressure part pressure x entire discharged amount", and substituting values in the equation, "20kgf/cm2 x 301pm = 980W", that is, the consuming power of oil pump 1 is 980W.
The consuming power 980W of oil pump 1 is relatively large and the large consuming power of oil pump 1, as described above, considerably reduces the power transmission efficiency of the transmission, such that the fuel efficiency of the vehicle reduces. Further, excessive load is applied to oil pump 1, such that durability of oil pump 1 is reduced and large noise is caused. Pressure vibration is excessively generated by cavitation when oil pump 1 operates at high speed.
JP2009-287688 A discloses the preamble of claim 1.
The present invention has been made in an effort to provide an oil supply system of an automatic transmission that has an improved configuration by making the oil pump discharge the entire flow rate on the basis of a low-pressure part for cooling and lubricating and controlling the pressure of only some of the oil for a high-pressure part at high pressure and then supplying the oil to the high-pressure part, to reduce a large amount of power consumed by the oil pump, improves fuel efficiency by largely improving power transmission efficiency of the transmission, and improves durability and reduces noise and pressure vibration by reducing the load applied to the oil pump.
One aspect of the present invention provides an oil supply system of an automatic transmission which supplies oil from an oil reservoir to a high-pressure part and a low-pressure part, using an oil pump, and includes a first oil pump pumping up oil from the oil reservoir and supplying the oil to the low-pressure part, a low-pressure regulating valve connected to a low-pressure part channel connecting the first oil pump with the low-pressure part, and controlling the pressure of the oil discharged from the first oil pump at pressure required by the low-pressure part, a second oil pump receiving the oil of which the pressure is controlled through the low-pressure regulating valve and supplying the oil to the high-pressure part, and a high-pressure regulating valve connected to a high-pressure part channel connecting the second oil pump with the high-pressure part and controlling the pressure of the oil discharged from the second oil pump at pressure required by the high-pressure part.
Further, the oil supply system of an automatic transmission further includes a first return channel recirculating the oil left after generating the low-pressure oil through the low-pressure regulating valve to the inlet of the first oil pump, a second return channel recirculating the oil left after generating the high-pressure oil through the high-pressure regulating valve to the inlet of the second oil pump, a connection channel connecting the low-pressure part channel with the high-pressure part channel, and a one-way check valve allowing for oil flow from the low-pressure part channel to the high-pressure part channel and preventing oil flow in the opposite direction.
Another aspect of the present invention provides an oil supply system of an automatic transmission which supplies oil from an oil reservoir to a high-pressure part and a low-pressure part, using an oil pump, and includes a first oil pump pumping up oil from the oil reservoir and supplying the oil to the low-pressure part, a low-pressure regulating valve connected to a low-pressure part channel connecting the first oil pump with the low-pressure part, and controlling the pressure of the oil discharged from the first oil pump at pressure required by the low-pressure part, a second oil pump receiving the oil of which the pressure is controlled through the low-pressure regulating valve and supplying the oil to the high-pressure part, a high-pressure regulating valve connected to a high-pressure part channel connecting the second oil pump with the high-pressure part and controlling the pressure of the oil discharged from the second oil pump at pressure required by the high-pressure part, a first return channel recirculating the oil left after generating the low-pressure oil through the low-pressure regulating valve to the inlet of the first oil pump, and a second return channel recirculating the oil left after generating the high-pressure oil through the high-pressure regulating valve to the inlet of the first oil pump.
Further, the oil supply system of an automatic transmission further includes a connection channel connecting the low-pressure part channel with the high-pressure part channel, and a one-way check valve disposed in the connection channel to allow for oil flow from the low-pressure part channel to the high-pressure part channel and prevent oil flow in the opposite direction.
According to various aspects of the present invention, an oil supply system of an automatic transmission can remarkably reduce the total consuming power of oil pumps, by discharging the entire oil on the basis of a low-pressure part and controlling only some of the oil, which is required by a high-pressure part, at high pressure, and then supplying the oil to high-pressure part, can considerably improve power transmission efficiency of the transmission, and can improve fuel efficiency and durability of the oil pumps and reduce loss of power, noise, and pressure vibration.
FIG. 1 is a diagram illustrating an oil supply system of an automatic transmission of the related art.
FIG. 2 is a diagram illustrating an exemplary oil supply system of an automatic transmission according to the present invention.
FIG. 3 is a diagram illustrating an exemplary oil supply system of an automatic transmission according to the present invention.
FIG. 2 shows an oil supply system according to various embodiments of the present invention, where oil 32 is stored in an oil reservoir 31, oil reservoir 31 is connected with an inlet 34a of a first oil pump 34 through an oil supply channel 33, outlet 34b of first oil pump 34 is connected to a low-pressure part 36 for cooling and lubricating through a low-pressure part channel 35, a low-pressure regulating valve 38 is connected to low-pressure part channel 35 through a first valve channel 37, such that low-pressure regulating valve 38 controls the pressure of oil discharged to low-pressure part channel 35 from outlet 34b of first oil pump 34 at a level required by low-pressure part 36.
Further, a sub-channel 40 diverging from low-pressure part channel 35 to supply the oil of which the pressure is controlled through low-pressure regulating valve 38 to a second oil pump 39 is connected with inlet 39a of second oil pump 39, an outlet 39b of second oil pump 39 is connected to a high-pressure part 42 for operating a clutch through a high-pressure part channel 41, and a high-pressure regulating valve 44 is connected to high-pressure part channel 41 through a second valve channel 43, such that high-pressure regulating valve 44 controls the pressure of the oils discharged to high-pressure channel 41 from outlet 39b of second oil pump 39 at a level (high pressure) required by high-pressure part 42.
The oil supply system according to various embodiments of the present invention includes a first return channel 45 connecting an oil intake channel 33 with low-pressure regulating valve 38 to recirculate the oil left after generating the low-pressure oil through low-pressure regulating valve 38 to inlet 34a of first oil pump 34, and a second return channel 46 connecting sub-channel 40 with high-pressure regulating valve 44 to recirculate the oil left after generating the high-pressure oil through high-pressure regulating valve to inlet 39a of second oil pump 39.
Further, the oil supply system according to various embodiments of the present invention further includes a connection channel 47 that connects low-pressure part channel 35 with high-pressure part channel 41, and a one-way check valve 48 that allows for oil flow from low-pressure part channel 35 to high-pressure part channel 41 and prevents oil flow in the opposite direction is disposed in connecting channel 47.
In this configuration, one end of connecting channel 47 is connected with the line between low-pressure regulating valve 38 and low-pressure part 36 in low-pressure part channel 35, while the other end is connected with the line between high-pressure regulating valve 44 and high-pressure part 42 in high-pressure part channel 41.
Further, one-way check valve 48 is a valve opening connection channel 47, only when the oil pressure of high-pressure part channel 41 is lower than the oil pressure of low-pressure part channel 35.
Sometimes, the pressure of the high-pressure part may need to be lower than the pressure of the low-pressure part while the vehicle travels under small load, in which second oil pump 39 stops and the oil is supplied from low-pressure part 35 to high-pressure part 42 through connection channel 47 and high-pressure part channel 41 by one-way check valve 48.
If the vehicle travels under high load (traveling at high speed, accelerating, traveling on a slope, or shifting etc.), the high-pressure part 42 requires high-pressure oil, because large load is applied thereto, in which second oil pump 39 and high-pressure regulating valve 44 operate.
Accordingly, the oil pressure of high-pressure part channel 41 increases larger than the oil pressure of low-pressure part channel 35, such that one-way check valve 48 is kept closed. Therefore, the connection channel 47 connecting low-pressure part channel 35 with high-pressure part channel 41 is closed by one-way check valve 48, and low-pressure oil and high pressure oil start to be supplied to low-pressure part 36 and high-pressure part 42, respectively.
Further, the low-pressure part oil is supplied through one-way check valve 48 in a failsafe condition in which second oil pump 39 fails to normally operate, thereby implementing emergency operation.
According to various embodiments of the present invention, both of first oil pump 34 and second oil pump 39 may be mechanical oil pumps that are operated by power from an engine.
Alternatively, first oil pump 34 may be a mechanical oil pump that is operated by the power from an engine and second oil pump 39 may be an electric oil pump that is operated by power from an electric motor.
In this case, the electric motor is operated by electric signals from an oil pump control unit, and the parameters that are inputted to the oil pump control unit to control the operation of the electric motor may be the number of revolution (rpm) of the engine, engine torque, vehicle speed, shifting, oil temperature etc.
Alternatively, according to various embodiments of the present invention, both of first oil pump 34 and second oil pump 39 may be electric oil pumps that are operated by power from an electric motor.
The operation of the oil supply system according to various embodiments of the present invention is described hereafter.
Oil 32 in oil reservoir 31 flows into inlet 34a of first oil pump 34 through an oil filter 49 by the operation of first oil pump 34.
The oil discharged to low-pressure part channel 35 through outlet 34b of first oil pump 34 decreases in pressure by low-pressure regulating valve 38 and then supplied to low-pressure part 36.
Further, the oil left after generating the low-pressure oil through low-pressure regulating valve 38 recirculates to inlet 34a of first oil pump 34 through first return channel 45 and oil supply channel 33.
Further, some of the low-pressure oil generated through low-pressure regulating valve 38 is supplied to inlet 39a of second oil pump 39 through sub-channel 40 while the low-pressure oil discharged to high-pressure part channel 41 through outlet 39b of second oil pump 39 is controlled at the pressure (high pressure) required by high-pressure part 42 by high-pressure regulating valve 44 and then supplied to high-pressure part 42.
Further, the oil left after generating the high-pressure oil through high-pressure regulating valve 44 recirculates to inlet 39a of second oil pump 39 through second return channel 46 and sub- channel 40.
Since low-pressure part 36 is used to cooling and lubricating the transmission, it needs a lot of flow rate, while since high-pressure part 42 is used to control the clutch, it needs a smaller amount of flow rate than low-pressure part 36.
Therefore, since the entire oil is discharged on the basis of low-pressure part 36 and only some of the oil which is required by high-pressure part 42 is controlled at high pressure and supplied to high-pressure part 42 in the oil supply system according to various embodiments of the present invention the power consumed by the oil pump is largely reduced as compared with the configuration of the related art, which is shown in FIG. 1.
That is, assuming that, as in the example of the related art, high-pressure part 42 needs pressure of 20kgf/cm2 and flow rate of 51pm, low-pressure part 36 needs pressure of 8kgf/cm2 and flow rate of 101pm, and the recirculation flow rate is 151pm, the total consuming power of first and second oil pumps 34, 39 of the present invention is defined by "consuming power = {[pressure of low-pressure part × entire discharged amount]+[pressure of high-pressure part - pressure of low-pressure part] × discharged amount of high-pressure part}.
Substituting values into the equation, "{[8kgf/cm2 × 301pm] + [(20kgf/cm2 - 8kgf/cm2) × 51pm]}= 490W", that the total consuming power of first and second oil pumps 34, 39 of the present invention is 490W, such that it is possible to reduce approximately 50% of the consuming power, 980W, of the oil pump of the related art, which has been described with reference to FIG. 1.
As the total consuming power of the oil pumps is remarkably reduced by the configuration of the present invention, the factors reducing power transmission efficiency of a transmission is considerably decreased, such that the power transmission efficiency of the transmission is largely improved and the fuel efficiency can be further improved.
Further, as the total consuming power of the oil pumps reduces, the load exerted in the oil pumps can be decreased, such that it is possible to improve durability of the oil pumps and reduce noise and pressure vibration.
FIG. 3 shows an oil supply system according to various embodiments of the present invention. Comparing the configuration shown in FIG. 3 with the configuration shown in FIG. 2, it is different that a second return channel 460 is connected to an oil supply channel 33 to recirculate the oil left after generating high-pressure oil through a high-pressure regulating valve 44 to an inlet 34a of a first oil pump 34, and the others are all the same as those shown in FIG. 2.
Therefore, in the configuration shown in FIG. 3, the entire oil is discharged on the basis of a low-pressure part 36 and only some of the oil which is required by a high-pressure part 42 is controlled at high pressure and then supplied to high-pressure part 42, as in that shown in FIG. 2. Accordingly, the total consuming power of the oil pumps can be considerably reduced, as compared with the configuration of the related art shown in FIG. 1, and the detailed description is not provided.
An oil supply system of an automatic transmission which supplies oil (32) from an oil reservoir (31) to a high-pressure part (42) and a low-pressure part (36), the oil supply system comprising:
a first oil pump (34) pumping up oil (32) from the oil reservoir (31) and supplying the oil (32) to the low-pressure part (36);
a low-pressure regulating valve (38) connected to a low-pressure part channel (35) connecting the first oil pump (34) with the low-pressure part (36), and controlling oil pressure discharged from the first oil pump (34) at a first pressure required by the low-pressure part (36);
a second oil pump (39) receiving the oil (32) of which the first pressure is controlled by the low-pressure regulating valve (38) and supplying the oil (32) to the high-pressure part (42);
a high-pressure regulating valve (44) connected to a high-pressure part channel (41) connecting the second oil pump (39) with the high-pressure part (42) and controlling oil pressure discharged from the second oil pump (39) at a second
pressure required by the high-pressure part (42); characterized by a connection channel (47) connecting the low-pressure part channel (35) with the high-pressure part channel (41), wherein one end of the connection channel (47) is connected to the low-pressure part channel (35) and the other end of the connection channel (47) is connected to the high-pressure part channel (41); and
a one-way check valve (48) disposed in the connection channel (47) to allow for oil flow from the low-pressure part channel (35) to the high-pressure part channel (41) and prevent oil flow in the opposite direction;
wherein the one-way check valve (48) is a valve opening the connection channel (47) only when an oil pressure of the high-pressure part channel (41) is lower than an oil pressure of the low-pressure part channel (35).
The oil supply system of an automatic transmission as defined in claim 1, further comprising a first return channel (45) recirculating the oil (32) through the low-pressure regulating valve (38) to an inlet (34a) of the first oil pump (34).
The oil supply system of an automatic transmission as defined in claim 2, further comprising a second return channel (46) recirculating the oil (32) through the high-pressure regulating valve (44) to an inlet (39a) of the second oil pump (39).
The oil supply system of an automatic transmission as defined in claim 1, further comprising an oil pump control unit generating control signals to stop the second oil pump (39) when the oil pressure of the high-pressure part channel (41) is lower than that of the low-pressure part channel (35).
The oil supply system of an automatic transmission as defined in claim 1, wherein the first oil pump (34) and the second oil pump (39) are both mechanical oil pumps that are operated by power from an engine.
The oil supply system of an automatic transmission as defined in claim 1, wherein the first oil pump (34) is a mechanical oil pump that is operated by power from an engine, and
the second oil pump (39) is an electric oil pump that is operated by power from an electric motor.
The oil supply system of an automatic transmission as defined in claim 1, wherein the first oil pump (34) and the second oil pump (39) are both electric oil pumps that are operated by power from an electric motor.
EP20100192873 2010-10-12 2010-11-29 Oil supply system of automatic transmission Active EP2441985B1 (en)
KR1020100099188A KR20120037623A (en) 2010-10-12 2010-10-12 Oil supply system of automatic transmission
EP2441985A2 EP2441985A2 (en) 2012-04-18
EP2441985A3 EP2441985A3 (en) 2012-07-04
EP2441985B1 true EP2441985B1 (en) 2013-07-31
ID=45098763
EP20100192873 Active EP2441985B1 (en) 2010-10-12 2010-11-29 Oil supply system of automatic transmission
US (1) US8512008B2 (en)
EP (1) EP2441985B1 (en)
JP (1) JP5558316B2 (en)
KR (1) KR20120037623A (en)
CN (1) CN102444679B (en)
US9121460B2 (en) * 2012-03-23 2015-09-01 GM Global Technology Operations LLC Transmission control fluid diffuser
KR101338455B1 (en) * 2012-09-03 2013-12-10 현대자동차주식회사 Oil pressure supply system of automatic transmission
KR101394040B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101394038B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101865716B1 (en) * 2012-09-03 2018-06-11 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101394039B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101338454B1 (en) * 2012-09-03 2013-12-10 현대자동차주식회사 Oil pressure supply system of automatic transmission
KR20140032033A (en) 2012-09-03 2014-03-14 현대자동차주식회사 Oil pressure supply system of automatic transmission
EP2716912A1 (en) 2012-10-08 2014-04-09 Magna International Japan Inc. Balanced pressure dual pump
KR101405192B1 (en) * 2012-11-05 2014-06-10 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101405207B1 (en) * 2012-11-06 2014-06-10 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101438607B1 (en) * 2012-12-12 2014-09-05 현대자동차 주식회사 Oil pressure supply system of automatic transmission
US9777828B2 (en) 2012-12-17 2017-10-03 Tbk Co., Ltd. Fluid supply device
US9671013B2 (en) 2013-02-26 2017-06-06 Honda Motor Co., Ltd. Hydraulic pressure supply apparatus
KR101510331B1 (en) * 2013-04-01 2015-04-07 현대자동차 주식회사 Pump motor control system for automatic transmission and method thereof
KR101484194B1 (en) * 2013-04-02 2015-01-16 현대자동차 주식회사 Hydraulic pressure supply system of automatic transmission
KR101461876B1 (en) 2013-04-02 2014-11-13 현대자동차 주식회사 Hydraulic pressure supply system of automatic transmission
JP6204063B2 (en) * 2013-05-21 2017-09-27 トーヨーエイテック株式会社 Oil pump system
CN103277495B (en) * 2013-06-17 2016-02-10 太重（天津）滨海重型机械有限公司 Low-pressure anti-seepage device of gearbox
JP5632049B1 (en) * 2013-07-10 2014-11-26 川崎重工業株式会社 Hydraulic circuit for control of continuously variable transmission
KR101490915B1 (en) * 2013-07-29 2015-02-06 현대자동차 주식회사 Oil pressure supply system of automatic transmission
JP6207368B2 (en) * 2013-09-11 2017-10-04 現代自動車株式会社Ｈｙｕｎｄａｉ Ｍｏｔｏｒ Ｃｏｍｐａｎｙ Hydraulic supply system for automatic transmission for vehicles
KR101461894B1 (en) * 2013-09-16 2014-11-13 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR20150032128A (en) * 2013-09-17 2015-03-25 현대자동차주식회사 Oil pressure supply system of automatic transmission
KR101509697B1 (en) * 2013-09-17 2015-04-07 현대자동차 주식회사 Oil pressure supply system of automatic transmission
KR101566728B1 (en) * 2013-12-18 2015-11-06 현대자동차 주식회사 Oil pressure supply system of automatic transmission
JP6180356B2 (en) * 2014-04-08 2017-08-16 本田技研工業株式会社 Hydraulic control device
KR101601072B1 (en) * 2014-06-16 2016-03-08 현대자동차주식회사 Oil pump for automatic transmission
KR101601105B1 (en) * 2014-07-01 2016-03-08 현대자동차 주식회사 Oil pressure supply system of automatic transmission
DE102014215646A1 (en) * 2014-08-07 2016-02-11 Robert Bosch Gmbh Device and system for pressurizing a fluid and corresponding use
JP6187415B2 (en) * 2014-08-22 2017-08-30 トヨタ自動車株式会社 Lubrication control device
KR101755484B1 (en) 2015-12-09 2017-07-10 현대자동차 주식회사 Apparatus for controlling oil pump of automatic transmission and method thereof
CN105774516A (en) * 2016-05-20 2016-07-20 中国第汽车股份有限公司 Dual-power coupling device for hybrid powered automatic transmission hydraulic system
JP6535365B2 (en) * 2017-05-26 2019-06-26 本田技研工業株式会社 Hydraulic control unit
JP6594381B2 (en) * 2017-08-10 2019-10-23 本田技研工業株式会社 Hydraulic control device
DE2855085C2 (en) * 1978-08-18 1986-04-24 S.R.M. Hydromekanik Ab, Stockholm, Se
JPH0223901Y2 (en) * 1985-04-30 1990-06-29
JPH0754981A (en) 1993-08-18 1995-02-28 Tochigi Fuji Ind Co Ltd Belt type continuously variable transmission
JPH07190157A (en) 1993-12-27 1995-07-28 Tochigi Fuji Ind Co Ltd Belt type continuously variable transmission
NL1001279C2 (en) * 1995-09-25 1997-03-26 Doornes Transmissie Bv Continuously variable transmission.
JP3629906B2 (en) 1997-07-22 2005-03-16 日本精工株式会社 Toroidal continuously variable transmission
NL1010144C2 (en) * 1998-09-21 2000-03-22 Doornes Transmissie Bv Continuously variable transmission.
JP4576714B2 (en) * 2000-12-28 2010-11-10 アイシン・エィ・ダブリュ株式会社 Oil pump drive control device
DE10125260A1 (en) * 2001-05-23 2002-11-28 Zahnradfabrik Friedrichshafen Transmission for a motor vehicle drive comprises hydraulic lines connected to a common feed leading away from a transmission oil pump whose working pressure is produced as required
DE10327406A1 (en) * 2003-06-18 2005-02-03 Zf Friedrichshafen Ag Hydraulic system for power shift transmission has low and high pressure pumps with switch over valve for shift elements to set hydraulic circuit
JP4299068B2 (en) * 2003-07-14 2009-07-22 トヨタ自動車株式会社 Electric oil pump function expansion type variable speed drive for vehicle
JP4661078B2 (en) 2004-04-26 2011-03-30 アイシン精機株式会社 Hydraulic supply device
JP4457746B2 (en) 2004-05-10 2010-04-28 日本精工株式会社 Toroidal continuously variable transmission
US7281904B2 (en) * 2004-07-20 2007-10-16 General Motors Corporation Transmission pump and filter
DE602004024721D1 (en) * 2004-08-13 2010-01-28 Bosch Gmbh Robert Step-free gearbox with a set of hydraulic pumps
DE102005013137A1 (en) * 2005-03-22 2006-09-28 Zf Friedrichshafen Ag Method and device for controlling an oil supply for an automatic transmission and a starting element
EP1722121A1 (en) 2005-05-09 2006-11-15 HOERBIGER Antriebstechnik GmbH Hydraulic double clutch
US8322252B2 (en) * 2006-09-29 2012-12-04 Caterpillar Inc. Step-change transmission having charge and variable displacement pumps
JP5081714B2 (en) 2008-05-08 2012-11-28 トヨタ自動車株式会社 Continuously Variable Transmission
JP5012667B2 (en) * 2008-05-29 2012-08-29 トヨタ自動車株式会社 Power transmission device
2010-10-12 KR KR1020100099188A patent/KR20120037623A/en not_active Application Discontinuation
2010-11-09 JP JP2010250866A patent/JP5558316B2/en active Active
2010-11-24 US US12/954,235 patent/US8512008B2/en active Active
2010-11-29 EP EP20100192873 patent/EP2441985B1/en active Active
2010-12-03 CN CN201010578017.7A patent/CN102444679B/en active IP Right Grant
JP2012082947A (en) 2012-04-26
EP2441985A2 (en) 2012-04-18
KR20120037623A (en) 2012-04-20
CN102444679B (en) 2015-08-19
CN102444679A (en) 2012-05-09
US20120085441A1 (en) 2012-04-12
JP5558316B2 (en) 2014-07-23
EP2441985A3 (en) 2012-07-04
US8512008B2 (en) 2013-08-20
JP3921220B2 (en) 2007-05-30 Hydraulic supply device
JP5306974B2 (en) 2013-10-02 Electric oil pump
US7951043B2 (en) 2011-05-31 Method and device for controlling the oil supply of an automatic gearbox and a starting element
JP6018255B2 (en) 2016-11-02 Boost Assist System
US8186154B2 (en) 2012-05-29 Rotary flow control valve with energy recovery
JP4296887B2 (en) 2009-07-15 Driving force transmission system
US7481053B2 (en) 2009-01-27 Hydraulic pressurizer system
JP5266111B2 (en) 2013-08-21 Hydraulic transmission device for automatic transmission
JP6150989B2 (en) 2017-06-21 Hydraulic control device for automatic transmission
WO2012111096A1 (en) 2012-08-23 Control device for vehicle oil supply device
JP6112789B2 (en) 2017-04-12 Hydraulic control device and method for automatic transmission
DE102010033758A1 (en) 2011-02-17 Methods and systems for assisted direct start control
JP4565343B2 (en) 2010-10-20 Hydraulic supply device and vehicle drive device
US9080503B2 (en) 2015-07-14 Hydraulic turbo accelerator apparatus
EP1893896B1 (en) 2010-01-20 Drive control device of an automatic gearbox for a motor vehicle and method therefor
KR101197366B1 (en) 2012-11-05 Hybrid propulsion system
KR101566728B1 (en) 2015-11-06 Oil pressure supply system of automatic transmission
JP3835007B2 (en) 2006-10-18 Working fluid supply device for automatic transmission
US20080308355A1 (en) 2008-12-18 Oil supply system for vehicle
2012-04-18 AX Request for extension of the european patent to:
2012-07-04 RIC1 Information provided on ipc code assigned before grant
Ipc: F16H 61/00 20060101AFI20120525BHEP
Owner name: HYUNDAI MOTOR COMPANY
Ref document number: 624849
Ref document number: 602010009000