CN100585133C - Valve timing regulation device - Google Patents
Valve timing regulation device Download PDFInfo
- Publication number
- CN100585133C CN100585133C CN200680031090.4A CN200680031090A CN100585133C CN 100585133 C CN100585133 C CN 100585133C CN 200680031090 A CN200680031090 A CN 200680031090A CN 100585133 C CN100585133 C CN 100585133C
- Authority
- CN
- China
- Prior art keywords
- hole
- axle
- valve timing
- rotation
- helical 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.)
- Expired - Fee Related
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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
-
- 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
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34456—Locking in only one position
-
- 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
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34473—Lock movement perpendicular to camshaft axis
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
- Y10T29/49293—Camshaft making
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A valve timing regulation device having a first rotating body co-rotating with a crankshaft; a second rotating body integrally fixed to an intake or exhaust camshaft; a first hole radially penetrating through a shoe formed inside the first rotating body; a second hole formed in the shoe, intersecting with the first hole; a coil spring pressing a lock pin received in the first hole to engage the lock pin with a recess formed in the outer periphery of the second rotating body; and a shaft inserted in the second hole for preventing jumping out of the coil spring.
Description
Technical field
The valve timing adjustment device (valve timing regulationdevice) that the switching time of the intake valve of a kind of internal-combustion engine to motor etc. (below be called motor) or exhaust valve of the present invention relates to is controlled.
Background technique
Valve timing adjustment device in the past comprises: first solid of rotation, protecgulum and bonnet that this first solid of rotation has the crawler shoe (shoe) of a plurality of overshooting shapes with the inboard and form the housing of hydraulic chamber, the described hydraulic chamber of sealing between this crawler shoe are fixed into one, and rotate with the bent axle one; And second solid of rotation, this second solid of rotation has a plurality of blades that described hydraulic chamber are divided into advance angle hydraulic chamber and retardation angle hydraulic chamber respectively, can relatively rotate with predetermined angular at described first a rotating body, and fix with the integrated camshaft of air inlet or exhaust, oil pump to motor sliding parts fuel feeding is supplied with, the discharging oil pressure, and utilizes this oil pressure to control the relative position of second solid of rotation with respect to first solid of rotation.
In said structure, when engine start, there is not the occasion of oil pressure, the blade repeated butt of the crawler shoe of first solid of rotation and second solid of rotation, separate, can produce Strike note.Therefore, first hole that radially connects is set on described crawler shoe, the stop pin that is accommodated in this first hole is pushed with the helical spring that is inserted in this hole, thereby for example at second rotation position during in maximum retardation angle position, this stop pin is engaged with recess on the outer circumferential face that is arranged on this second solid of rotation, the relative position of first solid of rotation and second solid of rotation is fixed, thereby suppressed the generation of Strike note.In addition, this stop pin moves towards removing direction because of the oil pressure that overcomes the helical spring application of force.When this was mobile, stop pin back pressure was behind discharged to the outside.
At this moment, need be used to the lock structure that prevents that helical spring from flying out.As this lock structure, there were four kinds in the past.
First kind, using the limit position part that is inserted into the cylindrical member in the stop pin reception hole from radial outside to block the occasion that helical spring flies out, use towards the axle that inserts with the direction of stop pin reception hole quadrature to fix limit position part.But, adopt this structure and since with the direction of stop pin reception hole quadrature on the axle reception hole diameter that forms become path, therefore the axle reception hole needs cutting separately.Therefore, the production process number increases, and cost rises.In addition, in order to block helical spring flying out, need limit position part and two parts of axle.
Second kind, shown in patent documentation 1, with the direction of stop pin reception hole quadrature on insert tabular limit position part in the groove that forms and block the helical spring occasion that flies out, the processing of groove needs high machining accuracy.In addition and since after radial outside inserts stop pin and helical spring in the reception hole with tabular limit position part insertion groove, so assembling is poor.
The third is using the limit position part that is pressed in the stop pin reception hole from radial outside to block the occasion that helical spring flies out, and may cause because of the centrifugal force in the high speed rotating zone coming off, or cause coming off because of vibration waits relaxing of causing.In addition, also need the power that is pressed into and the engineering management that is pressed into size.
The 4th kind, shown in patent documentation 2, block the occasion that helical spring flies out at trough wall surface with housing, must with helical spring under compressive state and stop pin insert together and keep out of the way in the slot part, so assembling is poor.
Patent documentation 1: Japanese patent laid-open 11-101107 communique
Patent documentation 2: the Japan Patent spy opens the 2005-002952 communique
Because valve timing adjustment device in the past as above constitutes, therefore used and blocked the various lock structures that helical spring flies out, but there are the problems such as engineering management that relax and cause coming off, need be pressed into power and be pressed into size that the high machining accuracy of needs, assembling are poor, can cause coming off or cause because of vibration etc. because of the centrifugal force in the high speed rotating zone respectively in these lock structures.
Summary of the invention
In view of the above problems, the objective of the invention is to obtain that a kind of use can reduce machining accuracy, improves processing and assembling, shape is simple and make the valve timing adjustment device that is easy to engaging part.
Valve timing adjustment device of the present invention comprises: first solid of rotation, the housing that this first solid of rotation has the crawler shoe of a plurality of overshooting shapes with the inboard and form hydraulic chamber between this crawler shoe is fixed into one with the protecgulum and the bonnet of the described hydraulic chamber of sealing, and rotates with the bent axle one; Second solid of rotation, this second solid of rotation has a plurality of blades that described hydraulic chamber are divided into advance angle hydraulic chamber and retardation angle hydraulic chamber respectively, can relatively rotate with predetermined angular at described first a rotating body, and fix with the integrated camshaft of air inlet or exhaust; Oil pressure is supplied with and is discharged parts, and this oil pressure is supplied with the discharge parts can carry out the supply and the discharge of working oil to described advance angle hydraulic chamber and retardation angle hydraulic chamber; First hole, this first hole radially connect on described crawler shoe; Second hole, this second hole is opened on the described crawler shoe across with respect to described first hole; Helical spring, this helical spring are to being accommodated in stop pin in described first hole and pushing and this stop pin is engaged with recess on the outer circumferential face that is arranged on described second solid of rotation; And axle, this axle is in order to prevent described helical spring and to fly out and being inserted in described second hole.
Adopt the present invention, because with being inserted in and taking in spool blocking helical spring and fly out in second hole arranged in a crossed manner of stop pin and helical spring first hole, therefore the size of approach locking pin reception hole diameter can be made in the hole of inserting for axle, can carry out Mould Machining, need not to carry out hole processing by cutting.Consequently, has the effect that can obtain the good valve timing adjustment device of making property.In addition, big for a diameter in the hole of inserting, this can reduce dimensional accuracy, and can improve processing and assembling, and because axle can use the simple shape of substantial cylindrical shape, so the making of axle is also easy.
Description of drawings
Fig. 1 is the figure of internal structure of the valve timing adjustment device of expression the invention process form 1, is the longitudinal section of second rotation position when maximum retardation angle position.
Fig. 2 is the sectional elevation along the A-A line of Fig. 1.
Fig. 3 is the longitudinal section along the B-B line of Fig. 2.
The longitudinal section of the valve timing adjustment device that Fig. 4 is second rotation position when advance angle position.
Fig. 5 is the amplification sectional elevation of major component that expression has locked the state of second solid of rotation.
Fig. 6 is the amplification longitudinal section of major component that expression has locked the state of second solid of rotation.
Fig. 7 is the amplification sectional elevation of major component of the state of the expression locking of having removed second solid of rotation.
Fig. 8 is the amplification longitudinal section of major component of the state of the expression locking of having removed second solid of rotation.
Fig. 9 is the amplification sectional elevation of the major component of expression stop pin and helical spring assembling condition.
Figure 10 is that explanation second solid of rotation is with respect to first solid of rotation amplification sectional elevation of major component in relative rotation.
Figure 11 is the amplification longitudinal section of the major component that can't assemble with respect to first solid of rotation of explanation second solid of rotation.
Figure 12 is the axle of expression cylindrical shape and the amplification longitudinal section of the major component of the assembling condition of the stop pin of band step cylindrical shape.
Embodiment
Below, in order to illustrate in greater detail the present invention, describe being used to implement best example of the present invention with reference to accompanying drawing.
Example 1.
What accompanying drawing was represented is the internal structure of the valve timing adjustment device of the invention process form 1, Fig. 1 is the longitudinal section of the valve timing adjustment device of second rotation position when maximum retardation angle position, Fig. 2 is the sectional elevation along the A-A line of Fig. 1, Fig. 3 is the longitudinal section along the B-B line of Fig. 2, the longitudinal section of the valve timing adjustment device that Fig. 4 is second rotation position when advance angle position.
As Fig. 1～shown in Figure 4, the valve timing adjustment device 1 of this example 1 roughly comprises: the bent axle (not shown) by chain (not shown) and motor (not shown) is first solid of rotation 1 of rotation synchronously; And be provided in this first solid of rotation 1 and with fixing all-in-one-piece second solid of rotation 3 of the end face of air inlet or exhaust cam shaft (below be called camshaft) 2.
First solid of rotation 1 comprises: have the sprocket wheel 4a of the rotary driving force of accepting bent axle (not shown) in the outside and have in the inboard towards the housing 4 of the outstanding a plurality of crawler shoe 4b of radially inner side; And the protecgulum 5 and the bonnet 6 that seal the inner space of this housing 4, the three utilizes bolt 7 to be fixed into one.
Second solid of rotation 3 is made of rotor 10, and this rotor 10 comprises: across packing ring 8 utilize bolt 9 one be attached on the end face of camshaft 2 protuberance 10a and from the peripheral part of this protuberance 10a towards the outstanding a plurality of blade 10b of radial outside.A plurality of inner spaces that the blade 10b of this rotor 10 will be formed by the crawler shoe 4b of housing 4 are divided into: in a plurality of advance angle hydraulic chamber 11 that makes rotor 10 accept when advance side is rotated relatively that oil pressure supplies with respect to first solid of rotation 1 and in a plurality of retardation angle hydraulic chamber 12 that makes rotor 10 accept with respect to first solid of rotation 1 that oil pressure supplies with when the retardation angle side is rotated relatively.In each advance angle hydraulic chamber, be communicated with supply, the discharging oil pressure advance angle oil circuit 13, in each retardation angle hydraulic chamber, be communicated with supply, the discharging oil pressure retardation angle oil circuit 14.
On the crawler shoe 4b of housing 4, be formed with the reception hole (first hole) 15 that radially connects.Being equipped with from the radial outside insertion in this reception hole 15 can be along this roughly columned stop pin 16 that radially moves back and forth.In addition, on the direction of intersecting with reception hole 15 of crawler shoe 4b (rotor 10 axially), be formed with roughly columned hole (second hole) 4b-1, be inserted in the roughly columned axle 17 that the rear end of the rear end of the helical spring 18 in the described reception hole 15 and stop pin 16 is inserted in the described hole 4b-1 with the form of urge lock pin 16 and block.
Peripheral part at the protuberance 10a of rotor 10 is formed with engaging recessed part 19, when rotor 10 was positioned at maximum retardation angle position with respect to the relative position of housing 4, the front end of described stop pin 16 engaged before radially inner side and then with described engaging recessed part 19 under the application of force of helical spring 18.In addition, on this engaging recessed part 19, be communicated with releasing oil circuit 20.
Below action is described.
At first, when rotor 10 was positioned at Fig. 1～Fig. 3 and Fig. 5, maximum retardation angle position shown in Figure 6 with respect to the relative position of housing 4, stop pin 16 engaged (state is locked and fastened) with engaging recessed part 19 under the application of force of helical spring 18.Under this state, if make stop pin front end 16a pressurized to engaging recessed part 19 supply oil pressure by removing oil circuit 20, then stop pin 16 overcomes the application of force of helical spring 18 and slides towards radial outside in stop pin reception hole 15, is disengaged with engaging of engaging recessed part 19.At this moment, the oil of stop pin back pressure side is discharged from the space that is arranged between stop pin reception hole 15 and the axle 17.As Fig. 7, shown in Figure 8, by in advance angle hydraulic chamber 11, supply with oil via advance angle oil circuit 13, and the oil in the retardation angle hydraulic chamber 12 are discharged via retardation angle oil circuit 14, as shown in Figure 4, the rotor 10 that stop pin 16 has been removed locking relatively rotates towards advance side.
In addition, is the occasion of advance angle position at rotor 10 with respect to the relative position of housing 4, oily by in retardation angle hydraulic chamber 12, supplying with via retardation angle oil circuit 14, and the oil in the advance angle hydraulic chamber 11 are discharged via advance angle oil circuit 13, rotor 10 relatively rotates towards the retardation angle side.If rotor 10 turns to maximum retardation angle position with respect to the relative position of housing 4, then stop pin 16 engages with engaging recessed part 19 sliding towards radially inner side in reception hole 15 under the application of force of helical spring 18.
As mentioned above, adopt this example 1, owing to diameter is approached take in hole and this reception hole of the diameter of stop pin and helical spring reception hole to be formed on the crawler shoe across, and the axle that inserts the substantial cylindrical shape in this hole blocks helical spring flying out, so can make big footpath for the hole of this insertion and also can make of mould, can be with the also disposable formation in hole when forming housing by casting etc.Therefore, need not to carry out hole processing, can cut down fabricating cost by cutting.In addition,, therefore need not cutting because axle can use the parts of the simple shape of substantial cylindrical shape, can be by disposable formation such as castings.Consequently, can cut down fabricating cost, can reduce dimensional accuracy, and can improve processing and assembling.
Example 2.
Fig. 9 is the sectional elevation of the major component of expression example 2, and the diameter of axle 17 constitutes less than the diameter of stop pin reception hole and the diameter of helical spring 18.Adopt this structure, the assembly fixture 21 that can use the U font with the two fork sheet 21a that pass the gap (space) 22 that forms between stop pin reception hole 15 and the axle 17 is towards radial compression helical spring 18.Consequently, can easily axle 17 be inserted among the hole 4b-1 that is provided with vertically, can improve assembling.In addition, after assembling, after having pulled down assembly fixture 21, be arranged on stop pin reception hole 15 and the gap 22 of axle between 17 and can play and be used to make the oil drainage hole that oil discharges to stop pin back pressure side or the effect of oil-discharge trough.
Example 3.
Example as shown, axle 17 for example constitutes D tee section shape in order to have helical spring at least one the plane seat surface 17a of carrying on the axial direction of outer circumferential face, and set each size, with the end face that causes axle 17 arc surface and stop pin in mistake when relative because of axle 17 assembly directions, made the end face of stop pin and the arc surface butt of axle 17 before in stop pin is received into reception hole 15 fully, make the front end of stop pin outstanding from the interior week of housing 4 all the time.Consequently, as shown in figure 11, rotor 10 can't insert towards direction shown in the arrow, and perhaps as shown in figure 10, rotor 10 can't rotate, and therefore can know it is loading error, can prevent the outflow of wrong assembly parts reliably.
On the other hand, when the end face of the D of axle 17 shape planar surface portion 17a and stop pin 16 is relative, this D shape planar surface portion 17a compression helical spring 18 of 17 and make stop pin 16 outstanding from reception hole 15, but because each size was set for before the D shape planar surface portion 17a butt of the end face of stop pin and axle 17 and stop pin 16 can be pushed in the reception hole 15 fully, but therefore regular event.
In addition, because the seat surface of helical spring 18 or screw pin 16 directly push axle 17, therefore the D shape planar surface portion 17a of axle 17 is compensated by the rotation of axle 17 in shaft insertion hole with respect to the meeting of inclination slightly of the glide direction of helical spring 18.
Example 4.
Fig. 8 is the figure of expression example 4, with the protecgulum 5 of the end butt of axle 17 and the either party in the bonnet 6 or both sides' (only being protecgulum 5 among Fig. 8) on be formed with the location indentations 5a that engages with shaft end.Adopting this structure, is the occasion of D tee section shape at axle 17 for example, by in advance location indentations 5a being formed D tee section shape, can prevent the loading error of axle 17, and can prevent to cause axle 17 rotations because of vibration.
Example 5.
Figure 12 is the sectional elevation of the major component of expression example 5, and axle 17 constitutes cylindrical shape, and stop pin 16 constitutes cylindrical shape with the level.The arc surface butt of one end of the seat surface of helical spring 18 and axle 17, the stepped part butt of the other end and stop pin 16 forms around the minor diameter part of stop pin.In addition, the end face of stop pin 16 minor diameter part sides when the stop pin release with the axle the arc surface butt, thereby prevent helical spring being close to.
Adopt this structure, owing to can make helical spring diameter and take between the aperture roughly the samely, so reception hole 15 becomes guide when helical spring stretches, play the effect that prevents to tilt.
In addition, as the example of this example in the seat surface of helical spring 18 occasion with the arc surface butt of axle 17, in order to prevent the distortion of seat surface portion, two circle or three circles of reeling of helical spring seat surface portion can being reeled.
Industrial utilizability
As mentioned above, the present invention can be widely used in use processing and the assembling that is arranged in engine etc. The valve timing adjustment device of good engaging part.
Claims (7)
1. a valve timing adjustment device is characterized in that, comprising:
The housing that first solid of rotation, this first solid of rotation have the crawler shoe of a plurality of overshooting shapes with the inboard and form hydraulic chamber between this crawler shoe is fixed into one with the protecgulum and the bonnet of the described hydraulic chamber of sealing, and rotates with the bent axle one;
Second solid of rotation, this second solid of rotation has a plurality of blades that described hydraulic chamber are divided into advance angle hydraulic chamber and retardation angle hydraulic chamber respectively, and can relatively rotate with predetermined angular at described first a rotating body, and fixes with the integrated camshaft of air inlet or exhaust;
Oil pressure is supplied with and is discharged parts, and this oil pressure is supplied with the discharge parts can carry out the supply and the discharge of working oil to described advance angle hydraulic chamber and retardation angle hydraulic chamber;
First hole, this first hole radially connect on described crawler shoe;
Second hole, this second hole is opened on the described crawler shoe across with respect to described first hole;
Helical spring, this helical spring are to being accommodated in stop pin in described first hole and pushing and this stop pin is engaged with recess on the outer circumferential face that is arranged on described second solid of rotation; And
Axle, this axle is in order to prevent described helical spring and to fly out and being inserted in described second hole.
2. valve timing adjustment device as claimed in claim 1 is characterized in that, the diameter of axle is less than the diameter in first hole.
3. valve timing adjustment device as claimed in claim 1 is characterized in that, the diameter of axle is less than helical spring diameter.
4. valve timing adjustment device as claimed in claim 1 is characterized in that, has the helical spring plane of carrying seat surface on the part of the outer circumferential face of axle.
5. valve timing adjustment device as claimed in claim 4 is characterized in that, axle is a D tee section shape.
6. valve timing adjustment device as claimed in claim 1 is characterized in that, with the protecgulum of the end butt of axle and either party in the bonnet or both sides on be formed with location indentations.
7. valve timing adjustment device as claimed in claim 1 is characterized in that, axle is by forging disposable formation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP249868/2005 | 2005-08-30 | ||
| JP2005249868 | 2005-08-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101248255A CN101248255A (en) | 2008-08-20 |
| CN100585133C true CN100585133C (en) | 2010-01-27 |
Family
ID=37808552
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680031090.4A Expired - Fee Related CN100585133C (en) | 2005-08-30 | 2006-05-22 | Valve timing regulation device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20100089349A1 (en) |
| JP (1) | JP4290754B2 (en) |
| CN (1) | CN100585133C (en) |
| DE (1) | DE112006002222T5 (en) |
| WO (1) | WO2007026449A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5376227B2 (en) * | 2009-05-25 | 2013-12-25 | アイシン精機株式会社 | Valve timing control device |
| JP5029671B2 (en) * | 2009-10-15 | 2012-09-19 | 株式会社デンソー | Valve timing adjustment device |
| DE102010035182A1 (en) * | 2010-08-24 | 2012-03-01 | Schaeffler Technologies Gmbh & Co. Kg | Camshaft adjuster arrangement and camshaft adjuster |
| JP5321925B2 (en) * | 2011-02-18 | 2013-10-23 | アイシン精機株式会社 | Valve timing control device |
| US8544434B2 (en) | 2011-11-23 | 2013-10-01 | Toyota Motor Engineering & Manufacturing North America, Inc. | Lock pin for variable valve timing mechanism |
| JP5781910B2 (en) * | 2011-12-09 | 2015-09-24 | 日立オートモティブシステムズ株式会社 | Valve timing control device for internal combustion engine |
| JP5991091B2 (en) * | 2012-09-04 | 2016-09-14 | アイシン精機株式会社 | Valve timing control device |
| US11306626B2 (en) * | 2020-06-02 | 2022-04-19 | Schaeffler Technologies AG & Co. KG | Camshaft phaser with target wheel washer |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3812691B2 (en) * | 1996-12-24 | 2006-08-23 | アイシン精機株式会社 | Valve timing control device |
| JP4503195B2 (en) * | 2001-03-05 | 2010-07-14 | 三菱電機株式会社 | Valve timing adjustment device |
| JP2002303106A (en) * | 2001-04-09 | 2002-10-18 | Mitsubishi Electric Corp | Valve timing adjusting device |
| JP3935704B2 (en) * | 2001-10-16 | 2007-06-27 | 三菱電機株式会社 | Valve timing adjustment device |
| JP2003227320A (en) * | 2002-01-31 | 2003-08-15 | Mitsubishi Electric Corp | Valve timing adjusting device |
| JP2003097229A (en) * | 2002-09-11 | 2003-04-03 | Toyota Motor Corp | Valve timing control unit for internal combustion engine |
| JP2004263643A (en) * | 2003-03-03 | 2004-09-24 | Mitsubishi Electric Corp | Valve timing adjusting device |
-
2006
- 2006-05-22 JP JP2007533123A patent/JP4290754B2/en not_active Expired - Fee Related
- 2006-05-22 WO PCT/JP2006/310155 patent/WO2007026449A1/en active Application Filing
- 2006-05-22 US US11/989,743 patent/US20100089349A1/en not_active Abandoned
- 2006-05-22 DE DE112006002222T patent/DE112006002222T5/en not_active Withdrawn
- 2006-05-22 CN CN200680031090.4A patent/CN100585133C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| US20100089349A1 (en) | 2010-04-15 |
| WO2007026449A1 (en) | 2007-03-08 |
| JP4290754B2 (en) | 2009-07-08 |
| DE112006002222T5 (en) | 2008-06-05 |
| CN101248255A (en) | 2008-08-20 |
| JPWO2007026449A1 (en) | 2009-03-05 |
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