CN102472125A - Valve timing regulator - Google Patents
Valve timing regulator Download PDFInfo
- Publication number
- CN102472125A CN102472125A CN2009801606872A CN200980160687A CN102472125A CN 102472125 A CN102472125 A CN 102472125A CN 2009801606872 A CN2009801606872 A CN 2009801606872A CN 200980160687 A CN200980160687 A CN 200980160687A CN 102472125 A CN102472125 A CN 102472125A
- Authority
- CN
- China
- Prior art keywords
- retaining member
- rotor
- recess
- holding member
- secondary spring
- 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.)
- Granted
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Classifications
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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
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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 valve timing regulator is equipped with a recess which is provided to face the peripheral wall surface of the shoe and vane of an advance oil pressure chamber, a holding member which is inserted into the recess from the axial direction and arranged in place, and an assist spring arranged between the holding member on the shoe side and the holding member on the vane side in order to urge the rotor in the advancing direction, wherein the clearance formed by the axial length of the holding member provided on the vane side and the axial length of the case is set equal to or larger than the sum of an increment in the axial length in which the inclination of the holding member caused by the gap between the holding member and the recess is taken into account and an increment caused by thermal expansion. Since a state in which the holding member is stretched between the covers at the opposite ends is brought about by thermal expansion during oil temperature rise, inclination of the holding member when the holding member and the assist spring are attached, or inclination caused by operation or vibration of the rotor, malfunction such as increase in leakage due to drop in operating speed of the rotor caused by friction or abrasion of the sliding surface of a cover can be prevented.
Description
Technical field
The present invention relates to port timing (valve timing) controlling device that the shut-in time point changes automatically of opening that a kind of operational situation according to internal-combustion engine makes outlet valve.
Background technique
This port timing controlling device comprises: camshaft, and the outlet valve of this camshaft actuated internal-combustion engine is opened and is closed; Housing, this housing to be can free rotation mode being located on the above-mentioned camshaft, and driven and rotate by the output of internal-combustion engine; Rotor, this rotor is accommodated in above-mentioned enclosure interior with the counterrotating mode of ability and is connected with camshaft; And locking member, this locking member is worked under the mechanical application of force and is retrained the relative rotation of housing and rotor, and work comes constraint relief under the fluid control pressure on the mechanical application of force direction in overcome indoor from internal hydraulic pressure.
Port timing controlling device with this structure is applied to exhaust side as purpose, has proposed a kind of structure, at the indoor configuration secondary spring of internal hydraulic pressure as to the element of rotor towards the advance angle direction application of force.In addition, as the structure that keeps this secondary spring, for example, in patent documentation 1, a kind of structure of resinous retaining member being inserted the recess of being located at rotor and housing is disclosed.
The existing technology document
Patent documentation
Patent documentation 1: No. 3964207 communique of Japanese Patent Laid
Summary of the invention
As stated; In patent documentation 1; Put down in writing a pair of retaining member that the two ends to secondary spring keep has been set; But the detailed content of undeclared axial length, secondary spring patchhole entrance shape; In the use of reality, have following technical problem: retaining member becomes the state that between the lid at two ends and shell, bloats in the interstice coverage tilt of itself and recess or because of thermal expansion etc., may occur in addition reducing because of friction makes working rotor speed, make unfavorable conditions such as leaking increase because of the slip surface wearing and tearing of lid and shell.
The present invention does for solving the above-mentioned technical problem that causes because of the retaining member that the secondary spring that is arranged in the hydraulic chamber is kept, and its purpose is to provide a kind of port timing controlling device that can solve operating rate reduction, durability reduction etc.
Port timing controlling device of the present invention comprises: a plurality of crawler shoes, and these crawler shoes are formed at the inner peripheral surface of housing; A plurality of blades, these blade-shaped are formed in the outer circumferential face that can be accommodated in the rotor in the housing with the relative rotation, its with the circumferential two side walls of each crawler shoe between formation delay angle hydraulic chamber and advance angle hydraulic chamber; 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 insert from axial direction and are disposed at recess; And secondary spring; This secondary spring is disposed between the retaining member of retaining member and above-mentioned blade-side of crawler shoe side; With rotor towards the advance angle direction application of force; The gap that will be formed by the axial length of the axial length of the retaining member of being located at blade-side and housing is set for more than or equal to following and value, should and value be following two value sums: considered the increasing amount that causes because of the axial length increasing amount after the inclination of this retaining member of the generation of the gap between retaining member and the recess and because of thermal expansion.
According to the present invention; In order to improve the secondary spring assembling performance; The increasing amount sum that causes more than or equal to the axial length increasing amount after the inclination of this retaining member of having considered to produce because of the gap between retaining member and the recess with because of thermal expansion is set in the gap that the axial length of the axial length of the retaining member of being located at blade-side and housing is formed for; Therefore; Even if the interstice coverage tilt of retaining member between the recess of being located at retaining member and blade, crawler shoe; Or the thermal expansion (rotor, housing are iron type materials, and linear expansion coeffcient is littler than the linear expansion coeffcient of resin system retaining member) when producing the oil temperature and rising, inclination, working rotor and vibration and the inclination that causes of retaining member when assembling retaining member and secondary spring, also can prevent following unfavorable condition reliably: retaining member becomes the state of between the lid at two ends and shell, heaving; Reduce because of friction makes working rotor speed, leak increase etc. because of the wearing and tearing of lid slip surface make.
Description of drawings
Fig. 1 is the radial cross-section along the 2-2 line of Fig. 2 of the port timing controlling device of embodiment of the present invention 1.
Fig. 2 is the axial sectional view along the 1-1 line of Fig. 1 of the port timing controlling device of embodiment of the present invention 1.
Fig. 3 is the insert in the hole plan view of state that secondary spring is installed of the secondary spring that is illustrated in the retaining member that inserts the impeller recess.
Fig. 4 is the vertical profile side view along the 3-3 line of Fig. 3.
Embodiment
Below, in order to illustrate in greater detail the present invention, the mode of execution that is used for embodiment of the present invention is described according to accompanying drawing.
Mode of execution 1
Fig. 1 is the radial cross-section of the port timing controlling device of embodiment of the present invention 1 along the 2-2 line of Fig. 2, and Fig. 2 is the axial sectional view of the port timing controlling device of embodiment of the present invention 1 along the 1-1 line of Fig. 1.
In the drawings, housing 1 is formed with the sprocket wheel portion 2 to transmitting from the driving force of not shown crank in periphery, and has the crawler shoe 3a～3d that forms hydraulic chamber in interior perimembranous.Rotor 4 has blade 7a～7d in the outside with 90 ° of arranged spaced roughly; Four hydraulic chambers that this blade 7a～7d will be formed by the crawler shoe 3a～3d of housing 1 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, shaft sleeve part 9 is across inner slide portion 8 sliding contacts of predetermined gap and housing 1, and has oil seal and bearing function.
In addition, be formed with recess at the front end of blade 7a～7d, and dispose the sealing component 10 that the oil flow between each hydraulic chamber is limited.In addition, rotor 4 is inserted into not shown camshaft in the inboard of shaft sleeve part 9, and is tightened by not shown bolt.As shown in Figure 2, the both ends of the surface tegmentum 11 of housing 1 and rotor 4 and shell 12 sealings, these members are screwed by four bolts 13.
Below, the oily path that is formed at rotor 4 is described.In the shaft sleeve part 9 of rotor 4, have the advance side path 17a～17d and the delay angle side path 18a～18d that are communicated with and run through diametrically formation with the not shown oily path that is formed at camshaft; 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.
On the crawler shoe 3b of housing 1, be formed with the hole of running through diametrically 21; Stop pin 23 can be contained in this hole 21 in the axial direction movably; This stop pin 23 is through chimeric with the embedding hole 22 of the shaft sleeve part that is formed at rotor 49, can be when starting the advance angle position limit rotor 4 in reference position.Towards the chimeric direction application of force, 24 limited 25 on spring keeps stop pin 23 by spring 24.In addition, the 26 pairs of stop pins 23 of delay angle side oil path that are utilized in the bottom opening of embedding hole 22 apply delay angle side hydraulic pressure, owing to be under pressure at front end, so stop pin 23 overcomes spring 24 foreign sides draw back towards the footpath, thereby can remove the restriction of rotor 4.
Then, to the secondary spring 27 of rotor 4 towards the advance angle direction application of force described.The blade 7a of rotor 4 (～7d) with the crawler shoe 3a of housing 1 (～be formed with the recess 28,29 that runs through in the axial direction respectively on 3d), in this recess 28,29, be inserted with resinous retaining member 30,31 respectively.Secondary spring 27 inserts the secondary spring patchhole 32,33 that is formed at retaining member 30,31 sides.
Like this, secondary spring 27 is disposed in the advance side hydraulic chamber.In illustrated example, in each hydraulic chamber, dispose two secondary springs 27 respectively, disposed eight secondary springs 27 altogether.At secondary spring 27 the longest advance angle position of length is set; Consider that assembling performance inserts the assembly body of a pair of retaining member and secondary spring 27 with machinery easily; And, dispose secondary spring 27 as the crow flies from avoiding bearing length to lack the purpose that makes secondary spring 27 squint diametrically and be out of shape than length is set because of retaining member.That is, in Fig. 1, the bottom surface P of retaining member 30 and the bottom surface Q of retaining member 31 are parallel.
The purpose that retaining member 30,31 is set is, can a plurality of secondary springs 27 be located in the hydraulic chamber in this peculiar shape space, thereby make its assembling performance become easy.Therefore, at retaining member 30,31 and recess 28, set predetermined gap between 29, easily to insert retaining member.Because the existence in this gap makes retaining member 30,31 in recess 28,29, to rock, retaining member 30,31 vertically, transversely tilt and measure accordingly in the gap.
At this; Because retaining member 30,31 is by ester moulding; Its linear expansion coeffcient is bigger than the linear expansion coeffcient of the housing 1 (in this mode of execution 1, being the sintering metal system of iron class) that forms the space that supplies the retaining member insertion, therefore, the device axial dimension of retaining member 30,31 is set for 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 in housing 1 when the thermal expansion to avoid retaining member 30,31.
Yet as shown in Figure 3 when producing the inclination of above-mentioned retaining member 30, the device axial dimension of retaining member 30,31 looks greatly that than the device axial dimension under the vertical situation because this size enlarges, retaining member 30,31 bloats in housing 1.If this state occurs in rotor-side, then frictional force can rise, this can become operating rate reduce and cover 11, the reason of shell 12 wearing and tearing.
That is, for example use in retaining member 30 for the supporting surface wearing and tearing that suppress secondary spring 27 glass etc. as the situation of adding material under, it is remarkable that the wearing and tearing of the other side's material can become., in mode of execution 1, also consider the size increasing amount Δ C that assembly axis that the inclination because of this retaining member 30 produces makes progress here, the gap between retaining member 30,31 and lid 11, the shell 12 is set at more than (Δ T+ Δ C).The thermal expansion amount Δ T of retaining member 30 is 40 μ m to the maximum, and inclination amount Δ C is 90 μ m to the maximum.Through such setting, can in housing 1, not bloat even if retaining member 30,31 rocks also, thereby can obtain stable device workability and durability.
In addition, as shown in Figure 4, be formed with width Lh than the big (tapering 36 of Lh＞Ls) of the wire spacing Ls of the secondary spring 27 of advance angle position at the secondary spring patchhole of retaining member 30,31 32,33 inlets.Through such setting; Along with rotor 4 moves towards the delay angle direction from advance angle position; Secondary spring 27 is deformed into circular-arc one side compression (the secondary spring wire spacing diminishes) on one side gradually; But the secondary spring wire rod can not be stuck in the entrance part edge portion of retaining member 30, can stably keep secondary spring 27.
Then, the action to device describes.At first; When engine start, when idle running etc. the port timing controlling device be controlled under the situation of advance angle position, reference position; Not energising in not shown oil control valve; Supply with hydraulic pressure via advance side path in the not shown motor towards advance side hydraulic chamber 5, thereby rotor 4 is fixed in advance angle position.At this moment, bottom surface P, the Q of retaining member 30,31 are parallel, as shown in Figure 1, and secondary spring 27 becomes straight.In addition, stop pin 23 is chimeric with embedding hole 22.
Then; When the port timing controlling device being sent the instruction of delay angle work because of rotating speed rising etc.; Oil control valve is fed the output port that predetermined electric current is opened delay angle side, and, at first supply with oil towards the delay angle side oil path 26 of port timing controlling device via delay angle side path in the not shown motor; Because the front end by stop pin 23 bears pressure; Therefore stop pin 23 overcomes the application of force of spring 24 and outer direction moves towards the footpath, and breaks away from embedding hole 22, thus the restriction of releasing rotor 4.
At this, under the chimeric state of stop pin 23, delay angle side path 18a～18d is stopped up by the shoe portion of housing 1, can not supply with hydraulic pressure towards delay angle side hydraulic chamber 6.When unlocking pin 23, the effect lower rotor part 4 that replaces torque at cam vibrates, and blocked delay angle side path is opened, thereby supplied with oil towards the delay angle side hydraulic chamber.
When present dynasty delay angle side hydraulic chamber is supplied with oil, on rotor 4, produce the rotating torques of delay angle direction, the cam torque on this rotating torques and the delay angle direction lumps together, and overcomes the secondary spring torque on the advance angle direction and begins to move.At this moment; Even if in the interstice coverage of recess 28,29 in the generation inclinations such as vibration of retaining member 30,31 because of motor; And along with the rotation of motor is that engine oil is heated to roughly about 100 ℃ and makes under the situation of retaining member 30,31 thermal expansions with the working fluid of port timing controlling device; Retaining member 30,31 can not bloat in housing 1 yet, and rotor 4 can normally be worked.
As stated, according to this mode of execution 1, because the purpose that retaining member is set is to improve the assembling performance of secondary spring, therefore, between the recess of retaining member and blade, crawler shoe, be provided with predetermined gap, retaining member can be in this interstice coverage tilt.Yet; Owing to adopt this structure; (rotor, housing are iron type materials in thermal expansion when rising because of the oil temperature; Linear expansion coeffcient is littler than the linear expansion coeffcient of resin system retaining member), inclination, working rotor and the vibration of the retaining member when assembling retaining member and secondary spring and produce inclination etc.; Following unfavorable condition can occur: retaining member becomes the state that between the lid at two ends and shell, bloats, reduces because of friction makes working rotor speed, increase etc. because of the wearing and tearing of lid slip surface make to leak; But be set at more than or equal to following value owing to will be located at the gap of axial length formation of axial length and housing of the retaining member of blade-side, therefore, can prevent above-mentioned unfavorable condition reliably; Wherein, above-mentioned value is the axial length increasing amount and the increasing amount sum that causes because of thermal expansion after the inclination of this retaining member of having considered to produce because of the gap between retaining member and the recess.
In addition; Owing to adopted the Drop-proof element that retaining member is set in rotor-side to prevent the structure that retaining member tilts; Therefore, can prevent that retaining member is not followed and such unfavorable condition that comes off when rotor carries out the advance angle action during at high hydraulic pressure for example fast.
In addition; Because it is big to be located at the secondary spring wire spacing that the width setup in tapering of the secondary spring patchhole inlet of retaining member must be when being located at advance angle position, therefore, even if shrink along with the action of rotor at inclination, secondary spring because of retaining member; Make when the secondary spring wire rod crosses the entrance part of retaining member; The secondary spring wire rod can not be stuck in the edge portion of retaining member entrance part yet, can produce correct secondary spring load, can suppress retaining member yet.And, can suppress the outside and the wearing and tearing that enter the mouth and rub and produce because of the spring loaded wire rod.
In addition,,, therefore, secondary spring and retaining member can be set stably, thereby rock (inclination) of the retaining member can will assemble the time is suppressed to inferior limit with the secondary spring straight configuration owing to length is set for maximum advance angle position at secondary spring.In addition,, set secondary spring straight, therefore, can prevent that secondary spring is deformed into U word shape owing to be provided with under the state of length maximum, least stable and easy deformation at secondary spring.
Utilizability in the industry
Port timing controlling device of the present invention is installed on the exhaust side camshaft of internal-combustion engine, can be applicable to effectively the shut-in time point of opening of outlet valve is controlled.
Claims (4)
1. port timing controlling device comprises:
Camshaft, the valve of this camshaft actuated internal-combustion engine opens and cuts out;
Housing, this housing its inner peripheral surface has a plurality of crawler shoes, can free rotation mode being located on the said camshaft, and being driven and rotates by the output of said internal-combustion engine; And
Rotor; This rotor has a plurality of blades at its outer circumferential face; Is connected can counterrotating mode to be accommodated in the said housing and with said camshaft, wherein, said a plurality of blades are formation delay angle hydraulic chamber and advance angle hydraulic chamber between the circumferential two side walls of itself and each said crawler shoe; It is characterized in that
Said port timing controlling device comprises:
Recess, the said crawler shoe of this recess and said advance angle hydraulic chamber and the circumferential wall of said blade are oppositely arranged;
Retaining member, this retaining member insert from axial direction and are disposed at said recess; And
Secondary spring, this secondary spring are disposed between the retaining member of said retaining member and said blade-side of said crawler shoe side, with said rotor towards the advance angle direction application of force,
The gap that the axial length of the axial length of the retaining member of being located at said blade-side and housing forms is set for more than or equal to following and value, should and value be following two value sums: considered the increasing amount that causes because of the axial length increasing amount after the inclination of this retaining member of the generation of the gap between said retaining member and the said recess and because of thermal expansion.
2. port timing controlling device as claimed in claim 1 is characterized in that,
The anti-shedding part that opening is narrowed down in the recess setting of the circumferential wall of being located at blade, and on retaining member, form the tapering with said anti-shedding part butt.
3. port timing controlling device as claimed in claim 1 is characterized in that,
Secondary spring wire spacing when the width setup in the tapering of being located at retaining member is become than is located at advance angle position is big.
4. port timing controlling device as claimed in claim 1 is characterized in that,
At secondary spring the maximum advance angle position of length is set, 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 true CN102472125A (en) | 2012-05-23 |
| CN102472125B 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) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104334840A (en) * | 2012-06-06 | 2015-02-04 | 舍弗勒技术有限两合公司 | Rotor for a hydraulic camshaft adjuster |
| CN104685166A (en) * | 2012-09-26 | 2015-06-03 | 舍弗勒技术股份两合公司 | Camshaft adjuster |
| CN105332759A (en) * | 2014-07-30 | 2016-02-17 | 舍弗勒技术股份两合公司 | Camshaft phase adjuster and method of assembling the same |
| CN110159384A (en) * | 2018-02-12 | 2019-08-23 | 伊希欧1控股有限公司 | Camshaft adjuster with compensation supporting part |
| CN112074656A (en) * | 2018-08-31 | 2020-12-11 | 株式会社电装 | Valve timing adjusting device |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020043231A1 (en) * | 2000-08-09 | 2002-04-18 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting apparatus for internal combustion engine |
| 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 |
| 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 |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
-
2009
- 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 CN CN200980160687.2A patent/CN102472125B/en active Active
- 2009-09-25 DE DE112009005364.5T patent/DE112009005364B4/en active Active
Patent Citations (9)
| 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 |
| US20020043231A1 (en) * | 2000-08-09 | 2002-04-18 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting apparatus for internal combustion engine |
| CN1619112A (en) * | 2003-11-21 | 2005-05-25 | 三菱电机株式会社 | Valve timing adjusting device |
| JP2005155373A (en) * | 2003-11-21 | 2005-06-16 | Mitsubishi Electric Corp | Valve timing adjusting 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 |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104334840A (en) * | 2012-06-06 | 2015-02-04 | 舍弗勒技术有限两合公司 | Rotor for a hydraulic camshaft adjuster |
| CN104685166A (en) * | 2012-09-26 | 2015-06-03 | 舍弗勒技术股份两合公司 | Camshaft adjuster |
| CN104685166B (en) * | 2012-09-26 | 2017-06-20 | 舍弗勒技术股份两合公司 | Camshaft adjuster |
| CN105332759A (en) * | 2014-07-30 | 2016-02-17 | 舍弗勒技术股份两合公司 | Camshaft phase adjuster and method of assembling the same |
| CN110159384A (en) * | 2018-02-12 | 2019-08-23 | 伊希欧1控股有限公司 | Camshaft adjuster with compensation supporting part |
| CN110159384B (en) * | 2018-02-12 | 2021-07-09 | 伊希欧1控股有限公司 | Camshaft adjuster with compensating bearing |
| CN112074656A (en) * | 2018-08-31 | 2020-12-11 | 株式会社电装 | Valve timing adjusting device |
| CN112074656B (en) * | 2018-08-31 | 2022-05-24 | 株式会社电装 | Valve timing adjusting device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112009005364B4 (en) | 2016-06-09 |
| US20120167846A1 (en) | 2012-07-05 |
| JPWO2011036720A1 (en) | 2013-02-14 |
| JP5335094B2 (en) | 2013-11-06 |
| CN102472125B (en) | 2016-04-20 |
| WO2011036720A1 (en) | 2011-03-31 |
| DE112009005364T5 (en) | 2013-03-28 |
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