CN105673115B - Valve timing controller - Google Patents
Valve timing controller Download PDFInfo
- Publication number
- CN105673115B CN105673115B CN201510894417.1A CN201510894417A CN105673115B CN 105673115 B CN105673115 B CN 105673115B CN 201510894417 A CN201510894417 A CN 201510894417A CN 105673115 B CN105673115 B CN 105673115B
- Authority
- CN
- China
- Prior art keywords
- shell
- reinforcement part
- chamber
- valve timing
- driven shaft
- 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
Links
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
-
- 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
- F01L1/02—Valve drive
- F01L1/022—Chain drive
-
- 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
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/34433—Location oil control valves
-
- 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
- F01L2001/34469—Lock movement parallel to camshaft axis
-
- 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
- F01L2001/34479—Sealing of phaser devices
-
- 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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A kind of valve timing controller, including first shell (20), second shell (30) and blade rotor (40).The outer diameter of second shell open end portion (32) be arranged to predetermined value to avoid with annular element (93) mechanical interference.Second shell has the bottom part and reinforcement part (34) opposite with open end portion, which is the radially outer of the corner part (p1) adjacent with bottom part of advance chamber and delay chamber.The radial thickness (t1) of reinforcement part is greater than the radial thickness of other cylindrical portions of second shell.The outer diameter (D2) of reinforcement part is greater than the predetermined value.
Description
Technical field
The present invention relates to a kind of valve timing controllers.
Background technique
The rotation phase that valve timing controller passes through between the crank axle and camshaft that change internal combustion engine controls air inlet
The valve timing of door and exhaust valve.JP2001-173414A describes a kind of hydraulic valve timing controller comprising passes through chain
First shell, the second shell of cupuliform and the blade rotor for being fixed on camshaft of item and crank axis connection.Second shell
Open end portion is fixed on first shell.When operation oil be inhaled into the advance chamber limited by second shell intracorporal blade rotor with
For the moment, blade rotor is relative to second shell along direction in advance or retarding direction rotation for delay chamber.Advance chamber and/or delay chamber
It can be referred to as hydraulic chamber.
In order to improve the control speed of valve timing, reduce the volume of hydraulic chamber effectively to reduce the required behaviour of driving
Make the dosage of oil.In this case, since the pulsation in the pressure of operation oil becomes larger, maximum pressure is also become larger.Therefore, it is necessary to
Improve the compressive property for limiting the second shell of hydraulic chamber.In addition to the change on material, thickness can also be increased to improve
The compressive property of two shells.
However, if the thickness of second shell increases, since chain cannot mechanically interfere the outer wall of second shell, first
The outer diameter of shell must also increase.
In JP2001-173414A, the teeth portion of first shell is spaced apart along axial with second shell.In this case,
The outer diameter of first shell can be made smaller, while avoid the mechanical interference between chain and second shell.However, In
In JP2001-173414A, the axial length of first shell is elongated.
Summary of the invention
The object of the present invention is to provide a kind of valve timing controllers, wherein not increasing first shell outer diameter and axial length
The compressive property of second shell can be improved in the case where degree.
It is an aspect of this invention to provide that the passing to driving force from driving shaft of internal combustion engine is arranged in valve timing controller
In the powertrain of driven shaft, to control the valve timing of the valve opened and closed by driven shaft, the valve timing
Controller includes: the first shell of dish type, coaxially arranged with one in driving shaft and driven shaft, and by annular element with
It is in driving shaft and driven shaft the other is attachable；Described in the second shell of cupuliform, with driving shaft and driven shaft
One coaxially arranged, and first shell is fixed on the open end portion of second shell；And blade rotor, it is arranged in second shell
In and there is blade-section, the inner space of second shell is divided into advance chamber and delay chamber by the blade-section.Blade rotor
The one end one of being capable of fixing described in the driving shaft and driven shaft, and receiving the operation for being supplied to advance chamber and delay chamber
It can be rotated relative to second shell under the pressure of oil.
The outer diameter of second shell open end portion be arranged to predetermined value to avoid with annular element mechanical interference.Second shell
With the bottom part and reinforcement part opposite with open end portion, the reinforcement part is advance chamber and delay chamber and bottom part
The radially outer of adjacent corner part.Reinforcement part is greater than the thickness of other cylindrical parts of second shell in radial thickness.
The outer diameter of reinforcement part is greater than the predetermined value.
When the internal pressure of hydraulic chamber increases, stress concentrates on the corner part adjacent with bottom part of advance chamber and delay chamber
Radially outer.It is strengthened using the radially outer that reinforcement part concentrates the stress of second shell.Therefore, it can be improved
The compressive property of two shells, at the same the outer diameter of second shell open end portion with it is in the prior art identical.
In addition, being not necessarily to change the outer diameter of second shell open end portion compared with the prior art.Even if being twined by annular element
Around first shell teeth portion be arranged to it is adjacent with the open end portion of second shell, will not be in annular element and second shell
Between generate mechanical interference.It therefore, there is no need to increase the outer diameter of the teeth portion of first shell to avoid annular element and second shell
Between mechanical interference.Furthermore, it is not necessary that the teeth portion of first shell is arranged to and second shell is axially spaced.
Therefore, in the case where not increasing the outer diameter and axial length of first shell, it can be improved the resistance to compression of second shell
Performance.
Detailed description of the invention
From detailed description with reference to the accompanying drawing, above and other objects, features and advantages of the invention will become more
Add intuitive.Wherein:
Fig. 1 shows the schematic cross section of the valve timing controller according to first embodiment；
Fig. 2 shows the cross-sectional views of the line II-II in Fig. 1；
Fig. 3 shows the cross-sectional view of the line III-III in Fig. 2；And
Fig. 4 is the cross-sectional view of the second shell and blade rotor according to the valve timing controller of second embodiment.
Specific embodiment
Hereinafter, embodiment will be described according to attached drawing.Identical or equivalent part uses in the accompanying drawings in following embodiments
Identical appended drawing reference.
(first embodiment)
As shown in Figure 1, according to the valve timing controller 10 of first embodiment by making 92 phase of camshaft of internal combustion engine 90
Crank axle 91 is rotated to control the valve timing of the inlet valve (not shown) opened and closed using camshaft 92.Valve is just
When controller 10 be arranged in from crank axle 91 to the powertrain of camshaft 92.Crank axle 91 can correspond to driving shaft, convex
Wheel shaft 92 can correspond to driven shaft.
Valve timing controller 10 is explained referring to Figures 1 and 2.As depicted in figs. 1 and 2, valve timing controller 10 includes
First shell 20, second shell 30 and blade rotor 40.Second shell 30 and blade rotor 40 are illustrated only in Fig. 2.
First shell 20 is dish type, is arranged to coaxial with camshaft 92.First shell 20 is assemblied in the axis of camshaft 92
To end.In the present embodiment, first shell 20 is sprocket, has the outside teeth portion 21 that can be engaged with chain 93.First
Shell 20 can be connect by chain 93 with crank axle 91.When crank axle 91 rotates, first shell 20 is with 91 turns of crank axle
It is dynamic.Chain 93 can correspond to annular element from beginning to end.
Second shell 30 is cupuliform, is arranged to coaxial with camshaft 92.Second shell 30 has multiple radially-inwardly
The lug boss 31 of protrusion.First shell 20 is fixed on the open end portion 32 of second shell 30 by bolt 15.
Blade rotor 40 can be rotated relative to second shell 30, have 41 He of shaft sleeve part being located in second shell 30
Multiple blade parts 42.Shaft sleeve part 41 is fixed on camshaft 92 by the sleeve bolt 51 of oil passage control valve 50.Blade part 42 from
Shaft sleeve part 41 projects radially outward, and the space between the lug boss 31 of the inner space of second shell 30, that is, adjacent is divided into
Advance chamber 43 and delay chamber 44.In rotational direction, delay chamber 44 is located at 42 front of blade part.In rotational direction, advance chamber 43
Behind blade part 42.The pressure of the operation oil of advance chamber 43 and delay chamber 44,40 energy of blade rotor are supplied to by receiving
It is enough to be rotated relative to second shell 30.
The central portion of blade rotor 40 is arranged in oil passage control valve 50.Oil passage control valve 50 includes sleeve bolt 51 and spool
59.Sleeve bolt 51 has the sleeve part 54 being arranged between head 52 and threaded portion 53.Sleeve part 54 has port 55 in advance,
This shifts to an earlier date port 55 and is connected to by the oil circuit 45 in advance of blade rotor 40 with advance chamber 43；Delayed port 56, the delayed port 56
It is connected to by the delay oil circuit 46 of blade rotor 40 with delay chamber 44；Supply port 57, the supply port 57 pass through camshaft 92
Supply oil circuit 94 be connected to the outlet of oil pump 95；And discharge port 58, the discharge port 58 are put by camshaft 92
Oily access 96 is connected to oil storage unit 97.
Spool 59 can move axially in reciprocal fashion on the inside of sleeve part 54, and the port of sleeve part 54 can be according to spool 59
Axial position is connected to each other.Particularly, when port 55 is connected with supply port 57 in advance, spool 59 being capable of connection delay port
56 and discharge port 58.In addition, spool 59 can connect 55 He of port in advance when delayed port 56 is connected with supply port 57
Discharge port 58.
Baffle 61 is fixed on 52 inside of head of sleeve bolt 51.Spool 59 is biased towards baffle 61 by spring 62.Pass through
Make to reach axial position of the balance to determine spool 59 between the bias force of spring 62 and the active force of linear solenoid 63, wherein
The linear solenoid 63 is reversed via baffle 61 and spool 59.
When the rotation phase of camshaft 92 to second shell 30 deviates a desired value on the retard side, controlled by oil circuit
Valve 50 will postpone oil circuit 46 and be connected with access 96 of draining the oil, and oil circuit 45 will be connected in advance with supply oil circuit 94.Whereby, delay chamber
44 operation oil is discharged to oil storage unit 97, while operating oil and being supplied to advance chamber 43 from oil pump 95, so that blade rotor 40 is mentioning
Front side is rotated relative to second shell 30.
When the rotation phase of camshaft 92 to second shell 30 deviates a desired value on side in advance, controlled by oil circuit
Valve 50 oil circuit 45 will be connected with access 96 of draining the oil in advance, and delay oil circuit 46 is connected with supply oil circuit 94.Whereby, advance chamber
43 operation oil is discharged to oil storage unit 97, while operating oil and being supplied to delay chamber 44 from oil pump 95, so that blade rotor 40 is prolonging
Slow side is rotated relative to second shell 30.
It, will in advance by oil passage control valve 50 when the rotation phase of camshaft 92 to second shell 30 is consistent with desired value
Room 43 and delay chamber 44 are closed, to keep the rotation phase.
Valve timing controller 10 is explained further referring to figs. 1 to Fig. 3.As shown in Figure 1 to Figure 3, second shell 30 is open
The outer diameter D 1 of end part 32 is set as predetermined value to avoid the mechanical interference with chain 93.
The bottom part 33 of second shell 30 integrally has reinforcement part 34.The reinforcement part 34 increases second shell 30
The radial thickness t1 of radially outer, wherein the radially outer of the second shell 30 is located at the adjacent of advance chamber 43 and delay chamber 44
The radially outer of the corner part p1 of bottom part 33.In other words, reinforcement part 34 is a part of second shell 30, is located at the
The radial outside of the outer circumference surface of the open end portion 32 of two shells 30.The outer diameter D 2 of the reinforcement part 34 of second shell 30, which is greater than, to be opened
The outer diameter D 1 of mouth end part 32, outer diameter D 1 is the predetermined value set to avoid the mechanical interference with chain 93.
As shown in Fig. 2, reinforcement part 34 is formed as circumferentially at least Chong Die with advance chamber 43 and delay chamber 44.In the present embodiment
In, reinforcement part 34 is not formed in a part of corresponding position with the lug boss 31 of second shell 30.That is, circumferentially local
Ground forms reinforcement part 34.
As shown in figures 1 and 3, from corner part p1 to reinforcement part the 34 axial end p2 adjacent to first shell 20 axial direction
Length L is greater than or equal to the axial width t2 of 30 bottom 35 of second shell, and is less than or equal to the axis of 30 bottom 35 of second shell
To 1.5 times of thickness t2.In other words, the axial direction of the 34 end p2 adjacent to first shell 20 is long from corner part p1 to reinforcement part
Degree L is 1-1.5 times of the axial width t2 of 30 bottom 35 of second shell.
The bottom 35 is a part of the bottom part 33 of second shell 30, is extended perpendicular to axially direction.
The end p2 adjacent to first shell 20 of reinforcement part 34 is chamfered, thus by other tubulars of reinforcement part 34 and second shell 30
Part is smoothly connected.
According to first embodiment, the outer diameter D 1 of the open end portion 32 of second shell 30 be arranged to predetermined value to avoid with chain
The mechanical interference of item 93.The bottom part 33 of second shell 30 has reinforcement part 34, compared to other tubulars of second shell 30
Part, radial thickness t1 increase.The reinforcement part 34 is located at the turning adjacent to bottom part 33 of advance chamber 43 and delay chamber 44
The radial outside of corner p1.The outer diameter D 2 of reinforcement part 34 avoids making a reservation for the described of 93 mechanical interference of chain greater than set
Value.
When the internal pressure of advance chamber 43 or delay chamber 44 increases, stress concentrates on the radially outer of corner part p1.In this reality
It applies in example, stress concentrates on a part of the bottom part 33 of second shell 30, and the part is by 34 reinforcement of reinforcement part.Therefore,
The compressive property of two shells 30 improves, while the outer diameter D 1 of 30 open end portion 32 of second shell is identical as in comparative example, In
In the comparative example, second shell has constant outer diameter.
In addition, having no need to change the outer diameter D 1 of 30 open end portion 32 of second shell compared to comparative example.Even if by chain
The teeth portion 21 of the first shells 20 of 93 windings is arranged to adjacent with the open end portion 32 of second shell 30, can also be limited in chain
Mechanical interference is generated between 93 and second shell 30.It therefore, there is no need to increase the outer diameter of the teeth portion 21 of first shell 20 to avoid
Mechanical interference between chain 93 and second shell 30.Furthermore, it is not necessary that by the teeth portion 21 of first shell 20 and second shell 30
In axially spaced arrangement.
Therefore, according to first embodiment, in valve timing controller 10, in the outer diameter and axis for not increasing first shell 20
In the case where length, the compressive property of second shell 30 can be improved.
According to first embodiment, reinforcement part 34 is formed along circumferential position at least Chong Die with advance chamber 43 and delay chamber 44
Place.Therefore, the part that all stress are concentrated in second shell 30 can be sufficiently intensified.
According to first embodiment, reinforcement part 34 is circumferentially formed locally.Therefore, the weight of second shell 30 is not excessive
Increase, while compressive property increases sufficiently to required degree.
According to first embodiment, the axial direction of the 34 end p2 adjacent to first shell 20 is long from corner part p1 to reinforcement part
Degree L is 1-1.5 times of the axial width t2 of 30 bottom 35 of second shell.Therefore, the weight of second shell 30 does not increase excessively,
Compressive property increases sufficiently to required degree simultaneously.(second embodiment)
In a second embodiment, as shown in figure 4, reinforcement part 81 is formed in whole circumferential directions of second shell 80.According to
Two embodiments can obtain the effect being identical with the first embodiment.The second shell 80 is easy to process, because not having on its external wall
There is recess.
(other embodiments)
In other embodiments, annular element can be belt to replace chain.First shell can be to be wrapped thereon
The belt pulley of belt.
In other embodiments, the axial length of the end adjacent to first shell from corner part to reinforcement part can be big
In 1.5 times of second shell bottom axial width.In this case, although the weight of second shell increases, compressive property
Improved.
In other embodiments, oil passage control valve can be provided in outside valve timing controller and be not arranged in blade and turn
The central portion of son.
In other embodiments, valve timing controller can control the exhaust valve of internal combustion engine and/or the opening of inlet valve
And closure timings.
The changes and improvements will be understood as in the scope of the present invention being defined by the following claims.
Claims (2)
1. a kind of valve timing controller is arranged and driving force is passed to driven shaft from driving shaft (91) in internal combustion engine (90)
(92) in powertrain, to control the valve timing of the valve opened and closed by the driven shaft, the valve is just
When controller include:
First shell (20), it is coaxially arranged with one in disc-like shape, with the driving shaft and the driven shaft, it is described
First shell can be connected to another in the driving shaft and the driven shaft by annular element (93)；
Second shell (30), with one coaxially arranged in cup-like shape, with the driving shaft and the driven shaft,
The first shell is fixed on the open end portion (32) of the second shell；And
Blade rotor (40) is arranged in the second shell and has blade-section (42), and the blade-section will be described
The inner space of second shell is divided into advance chamber (43) and delay chamber (44), and the blade rotor is capable of fixing in the active
One one end in axis and the driven shaft, and the blade rotor can be supplied to the advance chamber by receiving
With the operating oily pressure of the delay chamber relative to second shell rotation, wherein
The outer diameter (D1) of the open end portion of the second shell be arranged to predetermined value to avoid with the annular element machine
Tool interference,
The second shell has the bottom part and reinforcement part (34) opposite with the open end portion, and the reinforcement part is
The radially outer of the corner part (p1) adjacent with the bottom part of the advance chamber and the delay chamber,
The radial thickness (t1) of the reinforcement part is greater than the radial thickness of other cylindrical portions of the second shell,
The outer diameter (D2) of the reinforcement part is greater than the predetermined value, and
The reinforcement part (34) is configured to reinforce when the internal pressure in the advance chamber (43) or the delay chamber (44) increases
The bottom part (33) at the concentrated place of stress, wherein
The reinforcement part is located at position circumferentially at least Chong Die with the advance chamber and the delay chamber, the reinforcement part
(34) it is formed locally along the circumferential direction.
2. valve timing controller as described in claim 1, wherein
The axial length (L) of the end (p2) adjacent to the first shell from the corner part (p1) to the reinforcement part is
1-1.5 times of the axial width (t2) of the bottom (35) of the second shell.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-248092 | 2014-12-08 | ||
| JP2014248092A JP6467896B2 (en) | 2014-12-08 | 2014-12-08 | Valve timing adjustment device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105673115A CN105673115A (en) | 2016-06-15 |
| CN105673115B true CN105673115B (en) | 2019-11-26 |
Family
ID=55974294
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510894417.1A Expired - Fee Related CN105673115B (en) | 2014-12-08 | 2015-12-08 | Valve timing controller |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6467896B2 (en) |
| CN (1) | CN105673115B (en) |
| DE (1) | DE102015119091B4 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009257256A (en) * | 2008-04-18 | 2009-11-05 | Mitsubishi Electric Corp | Valve timing adjusting device |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09250310A (en) * | 1996-03-14 | 1997-09-22 | Toyota Motor Corp | Valve timing changing device for internal combustion engine |
| JP2000008814A (en) * | 1998-06-22 | 2000-01-11 | Toyota Motor Corp | Valve timing regulation device of internal combustion engine |
| JP4158185B2 (en) * | 1999-12-15 | 2008-10-01 | 株式会社デンソー | Valve timing adjustment device |
| JP2004060591A (en) * | 2002-07-31 | 2004-02-26 | Mikuni Corp | Valve timing changing device |
| DE102004035035B4 (en) | 2003-07-24 | 2022-04-14 | Daimler Ag | Camshaft adjusters for internal combustion engines |
| JP4229464B2 (en) * | 2006-08-23 | 2009-02-25 | 株式会社日立製作所 | Phase variable device and camshaft phase variable device for internal combustion engine |
| JP5660405B2 (en) * | 2012-09-28 | 2015-01-28 | 株式会社デンソー | Valve timing adjustment device |
| JP5835261B2 (en) * | 2013-03-29 | 2015-12-24 | 株式会社デンソー | Manufacturing apparatus and manufacturing method of valve timing adjusting device |
-
2014
- 2014-12-08 JP JP2014248092A patent/JP6467896B2/en active Active
-
2015
- 2015-11-06 DE DE102015119091.5A patent/DE102015119091B4/en active Active
- 2015-12-08 CN CN201510894417.1A patent/CN105673115B/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009257256A (en) * | 2008-04-18 | 2009-11-05 | Mitsubishi Electric Corp | Valve timing adjusting device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6467896B2 (en) | 2019-02-13 |
| DE102015119091A1 (en) | 2016-06-09 |
| JP2016109055A (en) | 2016-06-20 |
| CN105673115A (en) | 2016-06-15 |
| DE102015119091B4 (en) | 2022-03-10 |
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Granted publication date: 20191126 Termination date: 20211208 |