CN102472125B - Valve timing regulator - Google Patents
Valve timing regulator Download PDFInfo
- Publication number
- CN102472125B CN102472125B CN200980160687.2A CN200980160687A CN102472125B CN 102472125 B CN102472125 B CN 102472125B CN 200980160687 A CN200980160687 A CN 200980160687A CN 102472125 B CN102472125 B CN 102472125B
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- CN
- China
- Prior art keywords
- retaining member
- secondary spring
- rotor
- recess
- blade
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34483—Phaser return springs
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A kind of valve timing regulator, comprising: recess, the crawler shoe of this recess and advance angle hydraulic chamber and the circumferential wall of blade are oppositely arranged, retaining member, this retaining member inserts from axial direction and is configured at recess, and secondary spring, this secondary spring is configured between the described retaining member of crawler shoe side and the described retaining member of blade-side, described rotor is exerted a force towards advance angle direction, the gap formed due to the axial length of the retaining member by being located at described blade-side and the axial length of housing is set to and is more than or equal to following values: the increasing amount sum considering the axial length increasing amount after the inclination of this retaining member produced because of the gap between described retaining member and described recess and cause because of thermal expansion, therefore, following unfavorable condition can be prevented: because of thermal expansion when oil temperature rises, the inclination of retaining member when assembling retaining member and secondary spring, the inclination etc. that working rotor and vibration produce, and make retaining member become the state bloated between the lid at two ends, make working rotor speed reduce because of friction, leakage increase etc. is made because of the wearing and tearing of lid slip surface.
Description
Technical field
The present invention relates to port timing (valvetiming) controlling device opening the automatic change of shut-in time point that a kind of operational situation according to internal-combustion engine makes outlet valve.
Background technique
This valve timing regulator comprises: camshaft, and the outlet valve of this camshaft actuated internal-combustion engine opens closedown; Housing, this housing is located on above-mentioned camshaft in the mode that can rotate freely, and is driven by the output of internal-combustion engine and rotate; Rotor, this rotor is accommodated in above-mentioned enclosure interior in the mode that can relatively rotate and is connected with camshaft; And locking member, this locking member works and retrains the relative rotation of housing and rotor under machinery force, and the constraint relief that works under from the fluid control pressure overcoming in mechanical force direction of internal hydraulic pressure indoor.
So that the valve timing regulator of this structure is applied to exhaust side as object, propose a kind of structure, at the indoor configuration secondary spring of internal hydraulic pressure as the element exerted a force towards advance angle direction to rotor.In addition, as the structure keeping this secondary spring, such as, in patent documentation 1, a kind of structure resinous retaining member insertion being located at the recess of rotor and housing is disclosed.
Prior art document
Patent documentation
Patent documentation 1: Japanese Patent Laid No. 3964207 publication
Summary of the invention
As mentioned above, in patent documentation 1, describe a pair retaining member arranging and the two ends of secondary spring are kept, but the detailed content of undeclared axial length, secondary spring patchhole entrance shape, in the use of reality, there is following technical problem: retaining member is tilted or become because of thermal expansion etc. the state bloated between the lid and shell at two ends in the interstice coverage of itself and recess, may occur in addition making because of friction working rotor speed reduce, making the unfavorable conditions such as leakage increase because lid weares and teares with the slip surface of shell.
The present invention solves the above-mentioned technical problem that causes because of the retaining member kept the secondary spring be arranged in hydraulic chamber and does, and its object is to provide a kind of valve timing regulator that can solve operating rate reduction, durability reduction etc.
Valve timing regulator of the present invention comprises: multiple crawler shoe, and these crawler shoes are formed at the inner peripheral surface of housing; Multiple blade, these blade-shaped are formed in the outer circumferential face that can be accommodated in the rotor in housing with the relative rotation, form delay angle hydraulic chamber and advance angle hydraulic chamber between itself and the circumferential two side walls of each crawler shoe; Recess, the crawler shoe of this recess and advance angle hydraulic chamber and the circumferential wall of blade are oppositely arranged; Retaining member, this retaining member inserts from axial direction and is configured at recess; And secondary spring, this secondary spring is configured between the retaining member of crawler shoe side and the retaining member of above-mentioned blade-side, rotor is exerted a force towards advance angle direction, the gap formed by the length be located on the axial length of retaining member of blade-side and the rotor axial of housing is set to and is more than or equal to following and value, should and value be following two value sums: the increasing amount considering the axial length increasing amount after because of the inclination of this retaining member of the gap generation between retaining member and recess and cause because of thermal expansion.
According to the present invention, in order to improve secondary spring assembling performance, the increasing amount sum gap that length on the rotor axial of the length be located on the rotor axial of the retaining member of blade-side and housing is formed being set to length increasing amount on the rotor axial after being more than or equal to the inclination considering this retaining member produced because of the gap between retaining member and recess and causing because of thermal expansion, therefore, even if retaining member is being located at retaining member and blade, interstice coverage between the recess of crawler shoe is tilted, or the thermal expansion (rotor produced when oil temperature rises, housing is iron type materials, linear expansion coeffcient is less than the linear expansion coeffcient of resin-made retaining member), the inclination of retaining member when assembling retaining member and secondary spring, working rotor and vibration and the inclination caused, also following unfavorable condition can reliably be prevented: retaining member becomes the state heaved between the lid and shell at two ends, make working rotor speed reduce because of friction, leakage increase etc. is made because of the wearing and tearing of lid slip surface.
Accompanying drawing explanation
Fig. 1 is the radial cross-section of the 2-2 line along Fig. 2 of the valve timing regulator of embodiment of the present invention 1.
Fig. 2 is the axial sectional view of the 1-1 line along Fig. 1 of the valve timing regulator of embodiment of the present invention 1.
Fig. 3 is the plan view representing the state being provided with secondary spring that to insert in the hole at the secondary spring of the retaining member inserting impeller recess.
Fig. 4 is the longitudinal cross-sectional side view of the 3-3 line along Fig. 3.
Embodiment
Below, in order to illustrate in greater detail the present invention, be described for implementing embodiments of the present invention with reference to the accompanying drawings.
Mode of execution 1
Fig. 1 is the radial cross-section of valve timing regulator along the 2-2 line of Fig. 2 of embodiment of the present invention 1, and Fig. 2 is the axial sectional view of valve timing regulator along the 1-1 line of Fig. 1 of embodiment of the present invention 1.
In the drawings, housing 1 is formed on the outer periphery the sprocket wheel portion 2 transmitted the driving force from not shown crank, and has the crawler shoe 3a ~ 3d forming hydraulic chamber in inner peripheral portion.Rotor 4 is configured with blade 7a ~ 7d in outside with roughly 90 ° of intervals, four hydraulic chambers that crawler shoe 3a ~ 3d by housing 1 is formed by this blade 7a ~ 7d are divided into advance side hydraulic chamber 5a ~ 5d and delay angle side hydraulic chamber 6a ~ 6d, and or the compression zone of hydraulic pressure.In this rotor 4, the gap of shaft sleeve part 9 across regulation and inner slide portion 8 sliding contact of housing 1, and there is oil seal and bearing function.
In addition, be formed with recess at the front end of blade 7a ~ 7d, and the sealing component 10 that the oil flow between being configured with each hydraulic chamber limits.In addition, rotor 4 is inserted into not shown camshaft in the inner side of shaft sleeve part 9, and is tightened by not shown bolt.As shown in Figure 2, both ends of the surface tegmentum 11 and the shell 12 of housing 1 and rotor 4 are closed, and these components are screwed by four bolts 13.
Below, the oily path being formed at rotor 4 is described.There is the advance side path 17a ~ 17d and the delay angle side path 18a ~ 18d that also run through formation with the not shown oily communication being formed at camshaft diametrically in the shaft sleeve part 9 of rotor 4, these advance side path 17a ~ 17d and delay angle side path 18a ~ 18d are communicated with advance side hydraulic chamber 5a ~ 5d and delay angle side hydraulic chamber 6a ~ 6d, respectively so that working oil is supplied to hydraulic chamber.
The crawler shoe 3b of housing 1 is formed the hole 21 run through diametrically, stop pin 23 can be contained in this hole 21 in the axial direction movably, this stop pin 23 by chimeric with the embedding hole 22 of the shaft sleeve part 9 being formed at rotor 4, can when starting reference position and most advanced angle position limitation rotor 4.Stop pin 23 is exerted a force towards chimeric direction by spring 24, and limited 25, spring 24 keeps.In addition, utilize and apply delay angle side hydraulic pressure at delay angle side oil path 26 pairs of stop pins 23 of the bottom opening of embedding hole 22, owing to being under pressure at front end, therefore stop pin 23 overcomes spring 24 and draws back towards footpath foreign side, thus can remove the restriction of rotor 4.
Then, the secondary spring 27 exerted a force towards advance angle direction by rotor 4 is described.The blade 7a (~ 7d) of rotor 4 and the crawler shoe 3a (~ 3d) of housing 1 are formed with the recess 28,29 run through in the axial direction respectively, in this recess 28,29, are inserted with resinous retaining member 30,31 respectively.Secondary spring 27 inserts the secondary spring patchhole 32,33 being formed at retaining member 30,31 side.
Like this, secondary spring 27 is configured in advance side hydraulic chamber.In illustrated example, in each hydraulic chamber, be configured with two secondary springs 27 respectively, be configured with eight secondary springs 27 altogether.At secondary spring 27, the longest most advanced angle position of length is set, consider that assembling performance is easily can insert the assembly body of a pair retaining member and secondary spring 27 by machinery, and shorter and make secondary spring 27 offset the object of distortion diametrically than arranging length for the bearing length avoided because of retaining member, configure secondary spring 27 as the crow flies.That is, in FIG, the bottom surface P of the retaining member 30 and bottom surface Q of retaining member 31 is parallel to each other.
Arrange the shortest most delay angle position of length at secondary spring 27, secondary spring 27 is configured to the arc-shaped of lateral bend in device.In addition, form in the opening edge of recess 28 of the blade 7a (~ 7d) being located at the rotor-side of carrying out spinning movement the tapering 35 that opening is narrowed and be used as anti-shedding part, as shown in Figure 4, the tapering 34 abutted with tapering 35 is formed in the bi-side of retaining member 30.By such setting, even if when rotor action, also can prevent retaining member 30 from departing from recess 28 mistakenly.
The object arranging retaining member 30,31 is, multiple secondary spring 27 can be located in hydraulic chamber in this fancy shapes space, thus make its assembling performance become easy.Therefore, between retaining member 30,31 and recess 28,29, the gap of regulation is set, easily to insert retaining member.Due to the existence in this gap, retaining member 30,31 can be rocked in recess 28,29, retaining member 30,31 is in the amount corresponding to gap that longitudinally, transversely tilt.
At this, because retaining member 30,31 is by ester moulding, its linear expansion coeffcient is larger than the linear expansion coeffcient of the housing 1 (being preferably the sintering metal system of iron class in 1) forming the space of inserting for retaining member, therefore, the device axial dimension of retaining member 30,31 is set to shorter than the device axial dimension of housing 1, the difference in size Δ T that short amount produces for the difference of linear expansion coeffcient, bloats when thermal expansion to avoid retaining member 30,31 in housing 1.
But when producing the inclination of above-mentioned retaining member 30, as shown in Figure 3, the device axial dimension of retaining member 30,31 looks large than the device axial dimension under vertical situation, and due to this dimension enlargement, retaining member 30,31 bloats in housing 1.If there is this state in rotor-side, then frictional force can rise, and this can become the reason that operating rate reduces and lid 11, shell 12 wear and tear.
That is, when using such as glass etc. as adding material in retaining member 30 to suppress the supporting surface of secondary spring 27 to wear and tear, the wearing and tearing of the other side's material can become remarkable.Herein, in mode of execution 1, also consider the assembly axis size increasing amount Δ C upwards produced because of the inclination of this retaining member 30, retaining member 30,31 and lid 11, gap between shell 12 are set as more than (Δ T+ Δ C).The thermal expansion amount Δ T of retaining member 30 is 40 μm to the maximum, and inclination amount Δ C is 90 μm to the maximum.By such setting, also can not bloat in housing 1 even if retaining member 30,31 rocks, thus stable device workability and durability can be obtained.
In addition, as shown in Figure 4, the tapering 36 of width Lh than the wire spacing Ls large (Lh > Ls) of the secondary spring 27 of most advanced angle position is formed with at secondary spring patchhole 32,33 entrance of retaining member 30,31.By such setting, along with rotor 4 is from most advanced angle position towards the action of delay angle direction, secondary spring 27 is deformed into arc-shaped gradually on one side while compression (secondary spring wire spacing diminishes), but secondary spring wire rod can not be stuck in the entrance part edge of retaining member 30, can stably keep secondary spring 27.
Then, the action of device is described.First, when engine start, idle running time etc. valve timing regulator when being controlled to reference position and most advanced angle position, be not energized in not shown oil control valve, supply hydraulic pressure via advance side path in not shown motor towards advance side hydraulic chamber 5, thus rotor 4 is fixed on most advanced angle position.Now, bottom surface P, Q of retaining member 30,31 are parallel, and as shown in Figure 1, secondary spring 27 becomes straight.In addition, stop pin 23 is chimeric with embedding hole 22.
Then, when sending the instruction of delay angle work because of rotating speed rising etc. to valve timing regulator, oil control valve is passed into the electric current of regulation to open the output port of delay angle side, and via delay angle side path in not shown motor, first the delay angle side oil path 26 towards valve timing regulator supplies oil supply, owing to bearing pressure by the front end of stop pin 23, therefore stop pin 23 overcomes the force of spring 24 and moves towards direction outside footpath, and depart from embedding hole 22, thus remove the restriction of rotor 4.
At this, under the state that stop pin 23 is chimeric, delay angle side path 18a ~ 18d is blocked by the shoe portion of housing 1, can not supply hydraulic pressure towards delay angle side hydraulic chamber 6.When unlock pin 23 time, the effect lower rotor part 4 replacing torque at cam vibrates, and is opened by blocked delay angle side path, thus towards delay angle side hydraulic chamber for oil supply.
When present dynasty delay angle side hydraulic chamber is for oil supply, the rotating torques of angular direction that rotor 4 is delayed, the cam torque on this rotating torques and delay angle direction is combined, and overcomes the secondary spring torque on advance angle direction and starts action.Now, even if produce because of the vibration etc. of motor in the interstice coverage of recess 28,29 at retaining member 30,31, and along with the rotation of motor the working fluid of valve timing regulator and engine oil be heated to about roughly 100 DEG C and make retaining member 30,31 thermal expansion when, retaining member 30,31 also can not bloat in housing 1, and rotor 4 can normally work.
As mentioned above, according to this mode of execution 1, because the object arranging retaining member is to improve the assembling performance of secondary spring, therefore, between the recess of retaining member and blade, crawler shoe, be provided with the gap of regulation, retaining member can be tilted in this interstice coverage.But, owing to adopting this structure, because of thermal expansion (rotor when oil temperature rises, housing is iron type materials, linear expansion coeffcient is less than the linear expansion coeffcient of resin-made retaining member), the inclination of retaining member when assembling retaining member and secondary spring, working rotor and vibration and produce inclination etc., there will be following unfavorable condition: retaining member becomes the state bloated between the lid and shell at two ends, make working rotor speed reduce because of friction, leakage increase etc. is made because of the wearing and tearing of lid slip surface, but the gap formed due to the axial length of the retaining member by being located at blade-side and the axial length of housing is set greater than and equals following values, therefore, can reliably prevent above-mentioned unfavorable condition, wherein, above-mentioned value considers the axial length increasing amount after because of the inclination of this retaining member of the gap generation between retaining member and recess and the increasing amount sum caused because of thermal expansion.
In addition, in rotor-side, the Drop-proof element of retaining member is set to the structure preventing retaining member from tilting owing to have employed, therefore, when can prevent from carrying out advance angle action fast when rotor is at such as high hydraulic pressure, retaining member is not followed and such unfavorable condition that comes off.
In addition, because the width in the tapering of the secondary spring patchhole entrance by being located at retaining member sets larger than secondary spring wire spacing when being located at most advanced angle position, therefore, even if shrinking along with the action of rotor because of the inclination of retaining member, secondary spring, when making secondary spring wire rod cross the entrance part of retaining member, secondary spring wire rod also can not be stuck in the edge of retaining member entrance part, can produce correct secondary spring load, and retaining member also can be suppressed to tilt.And, can suppress because of the outside of spring loaded wire rod and entrance friction and the wearing and tearing produced.
In addition, be maximum most advanced angle position owing to arranging length at secondary spring, by secondary spring straight configuration, therefore, can secondary spring and retaining member be stably set, thus rock (inclination) of retaining member during assembling can be suppressed to inferior limit.In addition, maximum, least stable and under holding yielding state, secondary spring is set straight owing to arranging length at secondary spring, therefore, secondary spring can be prevented to be deformed into U-shaped.
Industrial utilizability
Valve timing regulator of the present invention is installed on the exhaust side camshaft of internal-combustion engine, can effectively be applicable to control the shut-in time point of opening of outlet valve.
Claims (4)
1. a valve timing regulator, comprising:
Camshaft, the valve of this camshaft actuated internal-combustion engine opens cut out;
Housing, this housing within it side face has multiple crawler shoe, is located on described camshaft in the mode that can rotate freely, and is driven by the output of described internal-combustion engine and rotate; And
Rotor, this rotor has multiple blade at its outer circumferential face, to be accommodated in described housing in the mode that can relatively rotate and to be connected with described camshaft, wherein, described multiple blade forms delay angle hydraulic chamber and advance angle hydraulic chamber between itself and the circumferential two side walls of each described crawler shoe, it is characterized in that
Described valve timing regulator comprises:
Recess, the described crawler shoe of this recess and described advance angle hydraulic chamber and the circumferential wall of described blade are oppositely arranged;
Retaining member, this retaining member inserts from the axial direction of described rotor and is configured at described recess; And
Secondary spring, between the described retaining member that this secondary spring is configured at described crawler shoe side and the retaining member of described blade-side, by described rotor towards advance angle direction force,
The retaining member being located at described blade-side to be set in the gap that the length axially of described rotor is formed at the length axially of described rotor and housing and to be more than or equal to following and value, should and value be following two value sums: consider the length increasing amount axially at described rotor after the inclination of this retaining member that produce because of the gap between described retaining member with described recess, in the plane parallel relative to the axle of described rotor, and the increasing amount caused because of thermal expansion.
2. valve timing regulator as claimed in claim 1, is characterized in that,
The anti-shedding part that opening is narrowed is set at the recess of the circumferential wall being located at blade, and on retaining member, forms the first tapering abutted with described anti-shedding part.
3. valve timing regulator as claimed in claim 1, is characterized in that,
The second tapering being located at the secondary spring patchhole entrance of retaining member is set to larger than secondary spring wire spacing when being located at most advanced angle position at secondary spring width axially.
4. valve timing regulator as claimed in claim 1, is characterized in that,
Arrange the maximum most advanced angle position of length at secondary spring, the bottom surface of the retaining member of crawler shoe side is parallel with the bottom surface of the retaining member of blade-side.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2009/004859 WO2011036720A1 (en) | 2009-09-25 | 2009-09-25 | Valve timing regulator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102472125A CN102472125A (en) | 2012-05-23 |
| CN102472125B true CN102472125B (en) | 2016-04-20 |
Family
ID=43795493
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980160687.2A Active CN102472125B (en) | 2009-09-25 | 2009-09-25 | Valve timing regulator |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20120167846A1 (en) |
| JP (1) | JP5335094B2 (en) |
| CN (1) | CN102472125B (en) |
| DE (1) | DE112009005364B4 (en) |
| WO (1) | WO2011036720A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012209532A1 (en) * | 2012-06-06 | 2013-12-12 | Schaeffler Technologies AG & Co. KG | Rotor for a hydraulic camshaft adjuster |
| DE102012217394A1 (en) * | 2012-09-26 | 2014-03-27 | Schaeffler Technologies Gmbh & Co. Kg | Phaser |
| CN105332759B (en) * | 2014-07-30 | 2019-07-16 | 舍弗勒技术股份两合公司 | Camshaft phase adjuster and its assemble method |
| DE102018103029A1 (en) * | 2018-02-12 | 2019-08-14 | ECO Holding 1 GmbH | Camshaft adjuster with compensation bearing |
| JP7001023B2 (en) * | 2018-08-31 | 2022-01-19 | 株式会社デンソー | Valve timing adjuster |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6450138B1 (en) * | 2000-01-25 | 2002-09-17 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting device |
| US6591799B1 (en) * | 2000-07-10 | 2003-07-15 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting device |
| CN1619112A (en) * | 2003-11-21 | 2005-05-25 | 三菱电机株式会社 | Valve timing adjusting device |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002122009A (en) * | 2000-08-09 | 2002-04-26 | Mitsubishi Electric Corp | Valve timing adjusting device |
| JP4166631B2 (en) * | 2003-06-05 | 2008-10-15 | 三菱電機株式会社 | Valve timing adjustment device |
| JP4327047B2 (en) * | 2004-08-27 | 2009-09-09 | 三菱電機株式会社 | Valve timing adjustment device |
| JP2006083785A (en) * | 2004-09-17 | 2006-03-30 | Hitachi Ltd | Valve timing control device of internal combustion engine |
| JP2007023953A (en) * | 2005-07-20 | 2007-02-01 | Denso Corp | Valve timing adjustment device |
| JP2007291889A (en) * | 2006-04-21 | 2007-11-08 | Mitsubishi Electric Corp | Valve timing adjustment device |
| WO2009019814A1 (en) * | 2007-08-08 | 2009-02-12 | Mitsubishi Electric Corporation | Valve timing adjusting device, and its assembling method |
-
2009
- 2009-09-25 CN CN200980160687.2A patent/CN102472125B/en active Active
- 2009-09-25 JP JP2011532802A patent/JP5335094B2/en active Active
- 2009-09-25 WO PCT/JP2009/004859 patent/WO2011036720A1/en active Application Filing
- 2009-09-25 US US13/376,101 patent/US20120167846A1/en not_active Abandoned
- 2009-09-25 DE DE112009005364.5T patent/DE112009005364B4/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6450138B1 (en) * | 2000-01-25 | 2002-09-17 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting device |
| US6591799B1 (en) * | 2000-07-10 | 2003-07-15 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting device |
| CN1619112A (en) * | 2003-11-21 | 2005-05-25 | 三菱电机株式会社 | Valve timing adjusting device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2011036720A1 (en) | 2013-02-14 |
| WO2011036720A1 (en) | 2011-03-31 |
| CN102472125A (en) | 2012-05-23 |
| US20120167846A1 (en) | 2012-07-05 |
| DE112009005364T5 (en) | 2013-03-28 |
| JP5335094B2 (en) | 2013-11-06 |
| DE112009005364B4 (en) | 2016-06-09 |
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