CN105673115A

CN105673115A - Valve timing controller

Info

Publication number: CN105673115A
Application number: CN201510894417.1A
Authority: CN
Inventors: 满谷哲朗
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2014-12-08
Filing date: 2015-12-08
Publication date: 2016-06-15
Anticipated expiration: 2035-12-08
Also published as: JP6467896B2; DE102015119091B4; CN105673115B; JP2016109055A; DE102015119091A1

Abstract

A valve timing controller includes a first housing (20), a second housing (30) and a bladed rotor (40). An outer diameter (D1) of an open end portion (32) of the second housing is adjusted to a predetermined value, that a mechanical interference with an annular component (93) can be prevented. The second housing has a lower end portion opposite to the open end portion and a reinforcing part (34), which is a radially outer portion of a corner part (p1) of a flow chamber and a delay chamber adjacent the lower end portion. A thickness (t1) of the reinforcing part in a radial direction is greater than that of the other cylindrical part of the second housing. An outer diameter (D2) of the reinforcing member is greater than the predetermined value.

Description

Valve timing controller

Technical field

The present invention relates to a kind of valve timing controller.

Background technology

Valve timing controller controls the valve timing of inlet valve and blast gate by the rotation phase changed between the crank axle of oil engine and camshaft. JP2001-173414A describes a kind of hydraulic valve timing controller, it blade rotor comprising the first housing being connected with crank axle by chain, the 2nd cup-shaped housing and being fixed on camshaft. The open end portion of the 2nd housing is fixed on the first housing. Being inhaled into the advance chamber limited by the blade rotor in the 2nd housing and delay chamber when process oil for the moment, blade rotor rotates along direction in advance or retarding direction relative to the 2nd housing. Advance chamber and/or delay chamber can be referred to as hydraulic chamber.

In order to improve the control speed of valve timing, the volume effectively reducing hydraulic chamber is to reduce the consumption of the process oil needed for driving. In this case, owing to the pulsation in the pressure of process oil becomes big, peak pressure also becomes big. Consequently, it is desirable to improve the compressive property of the 2nd housing limiting hydraulic chamber. Except the change on material, it is also possible to increase thickness to improve the compressive property of the 2nd housing.

But, if the thickness of the 2nd housing increases, owing to the outer wall of the 2nd housing can not mechanically be interfered by chain, the external diameter of the first housing also must increase.

In JP2001-173414A, the teeth portion of the first housing separates vertically and between the 2nd housing. In this case, the external diameter of the first housing can obtain smaller, avoids the mechanical interference between chain and the 2nd housing simultaneously. But, in JP2001-173414A, the axial length of the first housing is elongated.

Summary of the invention

It is an object of the invention to provide a kind of valve timing controller, wherein can improve the compressive property of the 2nd housing when not increasing the first housing external diameter and axial length.

According to an aspect of of the present present invention, valve timing controller is arranged on the power train that motivating force passes to driven shaft from main drive shaft of oil engine, to control the valve timing of the valve opened and closed by driven shaft, this valve timing controller comprises: the first housing of dish type, one in itself and main drive shaft and driven shaft coaxially arranged, and can be connected with another in main drive shaft and driven shaft by annular element; In the 2nd cup-shaped housing, itself and main drive shaft and driven shaft described one coaxially arranged, the first housing is fixed on the open end portion of the 2nd housing; And blade rotor, it is arranged in the 2nd housing and has blade-section, and the internal space of the 2nd housing is divided into advance chamber and delay chamber by described blade-section.One end that blade rotor one of can be fixed on described in main drive shaft and driven shaft, and can rotate relative to the 2nd housing under the pressure receiving the process oil being supplied to advance chamber and delay chamber.

The external diameter of the 2nd shell nozzle end portion is arranged to preset value to avoid and annular element mechanical interference. 2nd housing has the bottom part contrary with open end portion and reinforcement portion, and described reinforcement portion is the radially outer of the corner part adjacent with bottom part of advance chamber and delay chamber. Reinforcement portion is greater than the thickness of other cylindrical parts of the 2nd housing at the thickness of radial direction. The external diameter in reinforcement portion is greater than described preset value.

When the interior voltage rise height of hydraulic chamber, stress concentrates on the radially outer of the corner part adjacent with bottom part of advance chamber and delay chamber. This radially outer utilizing reinforcement portion that the stress of the 2nd housing is concentrated is strengthened. Accordingly, it may be possible to improve the compressive property of the 2nd housing, the simultaneously external diameter of the 2nd shell nozzle end portion and of the prior art identical.

In addition, compared to prior art without the need to changing the external diameter of the 2nd shell nozzle end portion. Even if the teeth portion of the first housing being wound around by annular element is arranged to adjacent with the open end portion of the 2nd housing, also mechanical interference can not be produced between annular element and the 2nd housing. Therefore, it is not necessary to the external diameter of teeth portion increasing the first housing is to avoid the mechanical interference between annular element and the 2nd housing. In addition, it is not necessary to the teeth portion of the first housing is arranged to the 2nd housing axially spaced.

Therefore, when not increasing external diameter and the axial length of the first housing, it is possible to improve the compressive property of the 2nd housing.

Accompanying drawing explanation

Below in conjunction with, in the detailed description of accompanying drawing, the above and other object of the present invention, feature and advantage will become more directly perceived. Wherein:

Fig. 1 shows the schematic cross section of the valve timing controller according to the first embodiment;

Fig. 2 shows the cross-sectional view along the line II-II in Fig. 1;

Fig. 3 shows the cross-sectional view along the line III-III in Fig. 2; And

Fig. 4 is the 2nd housing of the valve timing controller according to the 2nd embodiment and the cross-sectional view of blade rotor.

Embodiment

Hereinafter, according to accompanying drawing, embodiment will be described. Part identical or equivalent in each embodiment below adopts identical Reference numeral in the accompanying drawings.

(the first embodiment)

As shown in Figure 1, according to the valve timing controller 10 of the first embodiment, by making, the camshaft 92 of oil engine 90 rotates the valve timing of the inlet valve (not shown) controlling to utilize camshaft 92 to open and close relative to crank axle 91. Valve timing controller 10 is arranged in from crank axle 91 to the power train of camshaft 92. Crank axle 91 may correspond in main drive shaft, and camshaft 92 may correspond in driven shaft.

Valve timing controller 10 is explained with reference to Fig. 1 and Fig. 2. As depicted in figs. 1 and 2, valve timing controller 10 comprises the first housing 20, the 2nd housing 30 and blade rotor 40. Fig. 2 illustrate only the 2nd housing 30 and blade rotor 40.

First housing 20 is dish type, and it is arranged to camshaft 92 coaxial. First housing 20 is assemblied in the axial end portion of camshaft 92. In the present embodiment, the first housing 20 is the chain gear teeth, has the outside teeth portion 21 that can engage with chain 93. First housing 20 can be connected with crank axle 91 by chain 93. When crank axle 91 rotates, the first housing 20 rotates along with crank axle 91.Chain 93 may correspond in annular element from beginning to end.

2nd housing 30 is cup-shaped, and it is arranged to camshaft 92 coaxial. 2nd housing 30 has multiple lug boss 31 radially-inwardly protruded. First housing 20 is fixed on the open end portion 32 of the 2nd housing 30 by bolt 15.

Blade rotor 40 can rotate relative to the 2nd housing 30, and it has the shaft sleeve part 41 and multiple blade part 42 that are positioned at the 2nd housing 30. Shaft sleeve part 41 is fixed on camshaft 92 by the sleeve bolt 51 of oil passage control valve 50. Blade part 42 radially outward protrudes from shaft sleeve part 41, and the space between the internal space of the 2nd housing 30 and adjacent lug boss 31 is divided into advance chamber 43 and delay chamber 44. In rotational direction, delay chamber 44 is positioned at before blade part 42. In rotational direction, advance chamber 43 is positioned at after blade part 42. The pressure of the process oil being supplied to advance chamber 43 and delay chamber 44 by receiving, blade rotor 40 can rotate relative to the 2nd housing 30.

Oil passage control valve 50 is arranged on the central part of blade rotor 40. Oil passage control valve 50 comprises 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, should be connected with advance chamber 43 by the oil circuit 45 in advance of blade rotor 40 by port 55 in advance; Postponing port 56, this delay port 56 is connected with delay chamber 44 by the delay oil circuit 46 of blade rotor 40; Supply port 57, this supply port 57 is connected with the relief outlet of oil pump 95 by the supply oil circuit 94 of camshaft 92; And discharge port 58, this discharge port 58 is connected with oil storage portion 97 by the oil path 96 of putting of camshaft 92.

Spool 59 can to-and-fro movement vertically inside sleeve part 54, the port of sleeve part 54 can be connected to each other according to the axial location of spool 59. Especially, when port 55 is connected with supply port 57 in advance, spool 59 can connect delay port 56 and discharge port 58. In addition, when postponing port 56 and be connected with supply port 57, spool 59 can connect port 55 and discharge port 58 in advance.

Baffle plate 61 is fixed on inside the head 52 of sleeve bolt 51. Spool 59 is biased to baffle plate 61 by spring 62. By making to reach the axial location that balance determines spool 59 between the bias force of spring 62 and the reactive force of linear solenoid 63, wherein said linear solenoid 63 is arranged via baffle plate 61 is contrary with spool 59.

When camshaft 92 offsets an expected value on the retard side to the rotation phase of the 2nd housing 30, by oil passage control valve 50, by delay oil circuit 46, oil path 96 is connected with putting, and oil circuit 94 is connected with supplying will to shift to an earlier date oil circuit 45. Whereby, the process oil of delay chamber 44 is discharged to oil storage portion 97, and process oil is fed to advance chamber 43 from oil pump 95 simultaneously, thus blade rotor 40 rotates relative to the 2nd housing 30 in side in advance.

When camshaft 92 offsets an expected value to the rotation phase of the 2nd housing 30 in advance side, oily path 96 is connected with putting will shift to an earlier date oil circuit 45 by oil passage control valve 50, and oil circuit 94 is connected with supplying by delay oil circuit 46. Whereby, the process oil of advance chamber 43 is discharged to oil storage portion 97, and process oil is fed to delay chamber 44 from oil pump 95 simultaneously, thus blade rotor 40 rotates relative to the 2nd housing 30 in delay side.

When camshaft 92 is consistent with expected value to the rotation phase of the 2nd housing 30, by oil passage control valve 50, advance chamber 43 and delay chamber 44 is closed, thus keep this rotation phase.

Valve timing controller 10 is explained further referring to figs. 1 through Fig. 3. As shown in Figure 1 to Figure 3, the outer diameter D 1 of the 2nd housing 30 open end portion 32 is set as that preset value is to avoid and the mechanical interference of chain 93.

The bottom part 33 of the 2nd housing 30 has reinforcement portion 34 overallly. This reinforcement portion 34 increases the radial thickness t1 of the radially outer of the 2nd housing 30, and the radially outer of wherein said 2nd housing 30 is positioned at the radially outer of the corner part p1 that adjacent bottom part 33 of advance chamber 43 and delay chamber 44. In other words, reinforcement portion 34 is a part for the 2nd housing 30, and it is positioned at the radial outside of the outer circumference surface of the open end portion 32 of the 2nd housing 30. The outer diameter D 2 in the reinforcement portion 34 of the 2nd housing 30 is greater than the outer diameter D 1 of open end portion 32, and outer diameter D 1 is the described preset value of setting to avoid the mechanical interference with chain 93.

As shown in Figure 2, reinforcement portion 34 is formed as circumferentially at least overlapping with advance chamber 43 and delay chamber 44. In the present embodiment, reinforcement portion 34 is not formed in the corresponding position of the part of the lug boss 31 with the 2nd housing 30. That is, reinforcement portion 34 circumferentially it is formed locally.

As shown in figures 1 and 3, the axial length L adjacent to the axial end p2 of the first housing 20 from corner part p1 to reinforcement portion 34 is more than or equal to the axial thickness t2 of bottom the 2nd housing 30 35, and is less than or equals 1.5 times of the axial thickness t2 of bottom the 2nd housing 30 35. In other words, the axial length L adjacent to the end p2 of the first housing 20 from corner part p1 to reinforcement portion 34 be the axial thickness t2 of bottom the 2nd housing 30 35 1-1.5 doubly.

Described bottom 35 is a part for the bottom part 33 of the 2nd housing 30, and it extends in direction perpendicular to axial direction. The end p2 chamfering adjacent to the first housing 20 in reinforcement portion 34, thus by smoothing junction for other cylindrical portions of reinforcement portion 34 and the 2nd housing 30.

According to the first embodiment, the outer diameter D 1 of the open end portion 32 of the 2nd housing 30 is arranged to preset value to avoid and the mechanical interference of chain 93. The bottom part 33 of the 2nd housing 30 has reinforcement portion 34, and compared to other cylindrical portions of the 2nd housing 30, its radial thickness t1 increases. This reinforcement portion 34 is positioned at the radial outside of the corner part p1 adjacent to bottom part 33 of advance chamber 43 and delay chamber 44. The outer diameter D 2 in reinforcement portion 34 is greater than set avoiding and the described preset value of chain 93 mechanical interference.

When the interior voltage rise height of advance chamber 43 or delay chamber 44, stress concentrates on the radially outer of corner part p1. In the present embodiment, stress concentrates on a part for the bottom part 33 of the 2nd housing 30, and this part is by strengthening portion 34 reinforcement. Therefore, the compressive property of the 2nd housing 30 improves, and the outer diameter D 1 of the 2nd housing 30 open end portion 32 is identical with comparative example simultaneously, and in this comparative example, the 2nd housing has constant external diameter.

In addition, compared to comparative example, it is not necessary to change the outer diameter D 1 of the 2nd housing 30 open end portion 32. Even if the teeth portion 21 of the first housing 20 being wound around by chain 93 is arranged to adjacent with the open end portion 32 of the 2nd housing 30, also can be limited between chain 93 and the 2nd housing 30 and produce mechanical interference. Therefore, it is not necessary to the external diameter of teeth portion 21 increasing the first housing 20 is to avoid the mechanical interference between chain 93 and the 2nd housing 30. In addition, it is not necessary to by the teeth portion 21 of the first housing 20 and the 2nd housing 30 in axially spaced layout.

Therefore, according to the first embodiment, in valve timing controller 10, when not increasing external diameter and the axial length of the first housing 20, it is possible to improve the compressive property of the 2nd housing 30.

According to the first embodiment, reinforcement portion 34 is formed in circumferentially at least overlapping with advance chamber 43 and delay chamber 44 position. Therefore, the part that all stress is concentrated in the 2nd housing 30 can be sufficiently intensified.

According to the first embodiment, reinforcement portion 34 is circumferentially formed locally. Therefore, the weight of the 2nd housing 30 does not too much increase, and compressive property is fully increased to required degree simultaneously.

According to the first embodiment, the axial length L adjacent to the end p2 of the first housing 20 from corner part p1 to reinforcement portion 34 is 1-1.5 times of the axial thickness t2 of bottom the 2nd housing 30 35. Therefore, the weight of the 2nd housing 30 does not too much increase, and compressive property is fully increased to required degree simultaneously. (the 2nd embodiment)

In a second embodiment, as shown in Figure 4, reinforcement portion 81 is formed in whole circumferences of the 2nd housing 80. According to the 2nd embodiment, it is possible to obtain the effect identical with the first embodiment. 2nd housing 80 is easy to processing, because not having recess on its external wall.

(other embodiments)

In other embodiments, annular element can be that belt is to replace chain. First housing can be the belt pulley being wrapped belt on it.

In other embodiments, 1.5 times of the axial thickness of the 2nd housing bottom can be greater than from corner part to the axial length of the end adjacent to the first housing in reinforcement portion. In this case, although the weight of the 2nd housing increases, but compressive property improves.

In other embodiments, can be provided in valve timing controller outside and be not arranged on the central part of blade rotor for oil passage control valve.

In other embodiments, valve timing controller can the blast gate of controlling combustion engine and/or the opening and closing timing of inlet valve.

Described changes and improvements are by the scope being understood to be in the present invention being defined by the following claims.

Claims

1. a valve timing controller, it is arranged on the power train that motivating force passes to driven shaft (92) from main drive shaft (91) of oil engine (90), to control the valve timing of valve opened and closed by described driven shaft, described valve timing controller comprises:

First housing (20), it has disc-like shape, coaxially arranged with in described main drive shaft and described driven shaft, and described first housing can pass through another that annular element (93) is connected in described main drive shaft and described driven shaft;

2nd housing (30), it has cup-like shape, with in described main drive shaft and described driven shaft described one coaxially arranged, described first housing is fixed on the open end portion (32) of described 2nd housing; And

Blade rotor (40), it is arranged in described 2nd housing and has blade-section (42), the internal space of described 2nd housing is divided into advance chamber (43) and delay chamber (44) by described blade-section, one end of described blade rotor can be fixed in described main drive shaft and described driven shaft described one, and described blade rotor can by receive be supplied to described advance chamber and described delay chamber process oil pressure and relative to described 2nd housing rotate, wherein

The external diameter (D1) of the described open end portion of described 2nd housing is arranged to preset value to avoid and described annular element mechanical interference,

Described 2nd housing has the bottom part contrary with described open end portion and reinforcement portion (34), and described reinforcement portion is the radially outer of the corner part adjacent with described bottom part (p1) of described advance chamber and described delay chamber,

The radial thickness (t1) in described reinforcement portion is greater than the radial thickness of other cylindrical portion of described 2nd housing, and

The external diameter (D2) in described reinforcement portion is greater than described preset value.

2. valve timing controller as claimed in claim 1, wherein

Described reinforcement portion is positioned at circumferentially at least overlapping with described advance chamber and described delay chamber position.

3. valve timing controller as claimed in claim 1 or 2, wherein

The axial length (L) adjacent to the end (p2) of described first housing from described corner part (p1) to described reinforcement portion is 1-1.5 times of the axial thickness (t2) of the bottom (35) of described 2nd housing.