DE102015119091A1 - Valve timing controller - Google Patents

Abstract

A valve timing controller includes a first housing (20), a second housing (30), and a paddle rotor (40). An outer diameter (D1) of an open end portion (32) of the second housing is set to a predetermined value so that 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 to the lower end portion. A thickness (t1) of the reinforcing part in a radial direction is larger 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

The present disclosure relates to a valve timing controller.

A valve timing controller controls a valve timing of an intake valve and an exhaust valve by changing a rotational phase between a crankshaft and a camshaft of an internal combustion engine. The patent JP 2001-173414A describes a hydraulic valve timing controller that includes a first housing connected to a crankshaft via a chain, a second housing that is cup-shaped, and a paddle rotor attached to a camshaft. The open end portion of the second housing is attached to the first housing. When an operating oil is supplied to one of a forward chamber and a retard chamber defined by the blade rotor within the second housing, the blade rotor is relatively rotated relative to the second housing in the advance direction or the retard direction. The flow chamber and / or the delay chamber may be referred to as an oil pressure chamber.

For effectively increasing the control speed of the valve timing, the volume of the oil pressure chamber is reduced, so that the amount of the operating oil required for driving is reduced. In this case, the maximum pressure increases because a pulsation in the pressure of the operating oil increases to a high value. Thus, the pressure resistance performance of the second housing defining the oil pressure chamber needs to be improved. To increase the pressure-resistance behavior of the second housing, in addition to a material change, the thickness can also be increased.

However, if the thickness of the second housing is increased, the outer diameter of the first housing must be increased such that there is no mutual mechanical interference between a chain and the outer wall of the second housing.

In the patent JP 2001-173414 A That is, the teeth part of the first housing is made to be spaced from the second housing in the axial direction. In this case, the outer diameter of the first housing may be made small while preventing the mutual mechanical interference between the chain and the second housing. In the patent JP 2001-173414 A however, increases the length of the first housing in the axial direction.

It is an object of the present disclosure to provide a valve timing controller in which the pressure resistance performance of the second housing is increased without thereby increasing the outer diameter and the axial length of the first housing.

According to one aspect of the present disclosure, a valve timing controller disposed in a power train in which a drive power is transmitted from an input shaft to an output shaft of an internal combustion engine so as to control a valve timing of a valve that is opened by the output shaft and is closed, the following features: a first housing which has the shape of a disc which is arranged coaxially with one of the drive shaft or the output shaft and is connectable to the other of the drive shaft or the output shaft by an annular component; a second housing having the shape of a cup coaxially disposed with one of the drive shaft or the output shaft, the first housing being fixed to an open end portion of the second housing; and a blade rotor disposed in the second housing and having a blade portion that divides an inner space of the second housing into a flow chamber and a delay chamber. The paddle rotor may be fixed to one end of the one of the drive shaft or the output shaft and rotated relative to the second housing by receiving a pressure of an operating oil supplied to the flow chamber and the retard chamber.

An outer diameter of the open end portion of the second housing is set at a predetermined value so that mechanical deterioration by the annular component is prevented. The second housing has a lower end portion opposite to the open end portion and a reinforcing part which is a radially outer portion of a corner part of the flow chamber and the retard chamber adjacent to the lower end part. A thickness of the reinforcing member in a radial direction is greater than that of the other cylindrical member of the second housing. An outer diameter of the reinforcing member is greater than the predetermined value.

When the internal pressure of the oil pressure chamber is increased, the stress concentrates on the radially outer portion of the corner portion of the flow chamber and the delay chamber adjacent to the lower end portion. The radially outer portion of the second housing, where the stress concentrates, is amplified by the reinforcing member. Therefore, the pressure resistance performance of the second housing can be increased while the outer diameter of the open end portion of the second housing remains identical to that of the prior art.

In addition, the outer diameter of the open end portion of the second housing need not be changed as compared with the prior art. Even if a gear part of the first housing, around which the annular component is wound, is positioned adjacent to the open end portion of the second housing, there is no mutual mechanical interference between the annular component and the second housing. Thus, the outer diameter of the gear part of the first housing need not be increased, thereby preventing mutual mechanical interference between the annular component and the second housing. In addition, the gear part of the first housing need not be arranged so as to be spaced from the second housing in the axial direction.

Accordingly, the pressure resistance performance of the second housing is increased without having to increase the outer diameter and the axial length of the first housing.

The foregoing and other aspects, features, and advantages of the present disclosure will become more apparent from the following detailed description made with reference to the accompanying drawings. Show it:

1 a schematic cross-sectional view illustrating a valve timing controller according to a first embodiment;

2 a cross-sectional view taken along a line II-II of 1 has been created;

3 a cross-sectional view taken along a line III-III of 2 has been created; and

4 a cross-sectional view illustrating a second housing and a blade rotor of a valve timing controller according to a second embodiment.

The following is a description of embodiments with reference to the drawings. Identical or corresponding portions of the respective embodiments listed below are identified by the same reference numerals in the drawings.

First Embodiment

As in 1 is shown controls a valve timing controller 10 According to a first embodiment, a valve timing of an intake valve (not shown) passing through a camshaft 92 by turning the camshaft 92 relative to the crankshaft 91 the internal combustion engine 90 opened and closed. The valve timing controller 10 is in a drivetrain from the crankshaft 91 to the camshaft 92 arranged. The crankshaft 91 can correspond to a drive shaft, and the camshaft 92 can correspond to an output shaft.

The valve timing controller 10 is referring to 1 and 2 explained in more detail. As in 1 and 2 is shown includes the valve timing controller 10 a first housing 20 , a second housing 30 and a paddle wheel 40 , Only the second case 30 and the paddle wheel 40 are in 2 shown.

The first case 20 is disc-shaped and coaxial with the camshaft 92 arranged. The first case 20 is at the axial end portion of the camshaft 92 attached. In this embodiment, the first housing is 20 around a sprocket that has an outer toothing part 21 has, with which a chain 93 Can take action. The first case 20 can with the crankshaft 91 over the chain 93 get connected. If the crankshaft 91 turns, turns the first case 20 with the crankshaft 91 , The chain 93 may correspond to an annular component that is endless.

The second housing 30 is cup-shaped and coaxial with the camshaft 92 arranged. The second housing 30 has several projection parts 31 which protrude inward in the radial direction. The first case 20 is with the screw 15 at the open end portion 32 of the second housing 30 attached.

The paddle wheel 40 may be relative to the second housing 30 turn and has a hub part 41 and several scoop parts 42 within the second housing 30 on. The hub part 41 is on the camshaft 92 with a sleeve screw 51 from an oil line control valve 50 attached. The blade part 42 stands from the hub part 41 in the radial direction outwards and divides the interior of the second housing 30 ie the space between the adjacent projection parts 31 , in the supply chamber 43 and in the delay chamber 44 , The delay chamber 44 is in front of the bucket part 42 arranged in the direction of rotation. The flow chamber 43 is behind the blade part 42 arranged in the direction of rotation. The paddle wheel 40 may be relative to the second housing 30 by receiving a pressure of the operating oil, that of the flow chamber 43 and the delay chamber 44 is fed, turn.

The oil line control valve 50 is at the middle part of the vane rotor 40 arranged. The oil line control valve 50 includes the sleeve screw 51 and the slider 59 , The Fixing bolt 51 points between the head 52 and the screw part 53 the sleeve part 54 on. The sleeve part 54 has a flow channel 55 on that with the supply chamber 43 via the supply oil line 45 of the vane rotor 40 communicates, a delay channel 56 that with the delay chamber 44 over the delay oil line 46 of the vane rotor 40 communicates, a feed channel 57 , with the discharge channel of the oil pump 95 through the feed oil line 54 the camshaft 52 communicates, and a discharge channel 58 that with the oil storage part 97 through the discharge oil line 96 the camshaft 92 communicated.

The slider 59 can be inside the sleeve part 54 in the axial direction reciprocate, and the channels of the sleeve part 54 can according to the axial position of the slider 59 be connected to each other. In particular, the slider can 59 the delay channel 56 and the discharge channel 58 connect together while the flow channel 55 and the feed channel 57 connected to each other. In addition, the slider can 59 the flow channel 55 with the discharge channel 58 connect while the delay channel 56 and the feed channel 57 connected to each other.

A stop plate 61 is inside the head 52 the sleeve screw 41 attached. The slider 59 is by the spring 62 towards the stop plate 61 biased. The axial position of the slider 59 is due to a balance between the biasing force of the spring 62 and a force of a linear solenoid 63 who is facing the slider 59 via the stop plate 61 is arranged, determined.

When the rotational phase of the camshaft 92 to the second housing 30 is on a delay side of a desired value, the delay oil line 46 and the discharge oil line 96 interconnected, and the supply oil line 45 and the feed oil line 94 be through the oil line control valve 50 connected with each other. As a result, the operating oil of the delay chamber 44 to the oil storage part 97 discharged, while the operating oil of the flow chamber 43 from the oil pump 95 is fed so that the paddle rotor 40 a relative rotation to the second housing 30 on the front page.

When the rotational phase of the camshaft 92 to the second housing 30 is on a forward side of a desired value, the supply oil line 45 and the discharge oil line 96 interconnected, and the delay oil line 46 and the feed oil line 94 be through the oil line control valve 50 connected with each other. Thus, the operating oil of the flow chamber 43 to the storage oil part 97 dissipated while the operating oil of the delay chamber 44 from the oil pump 95 is fed so that the paddle rotor 40 a relative rotation to the second housing 30 on the delay side.

When the rotational phase of the camshaft 92 to the second housing 30 matches a desired value, the flow chamber 43 and the delay chamber 44 through the oil line control valve 50 closed, so that the rotational phase is maintained.

The valve timing controller 10 is referring to 1 to 3 explained in more detail. As in 1 to 3 is shown, the outer diameter D1 of the open end portion 33 of the second housing 30 set to a predetermined value, leaving a mechanical interference with the chain 93 is prevented.

The lower end section 33 of the second housing 30 has an integral reinforcement part 34 on. The reinforcement part 34 The radial thickness t1 extends the radially outer portion of the second housing 30 located on the radially outer side of the corner part t1 of the flow chamber 43 and the delay chamber 44 next to the lower end section 33 located. In other words, the delay part 34 a section of the second housing 30 located on the radially outer side of the outer peripheral surface of the open end portion 32 of the second housing 30 located. The outer diameter D2 of the reinforcing member 34 is larger than the outer diameter D1 of the open end portion 32 of the second housing 30 ie, the predetermined value set to cause mechanical damage to the chain 93 can be prevented.

As in 2 is shown, is the reinforcing member 34 designed so that it at least the flow chamber 43 and the delay chamber 44 overlaps in the circumferential direction. In this embodiment, the reinforcing member 34 not formed at a position that is a part of the projecting part 31 of the second housing 30 equivalent. More specifically, the reinforcing part 34 partially formed in the circumferential direction.

As in 1 and 3 is shown, the axial length L is from the corner part p1 to the axial end p2 of the reinforcing part 34 next to the first case 20 greater than or equal to the axial thickness t2 of the underside 35 of the second housing 30 and is less than or equal to 1.5 times the axial thickness t2 of the underside 35 of the second housing 30 , In other words, the length L is in the axial direction from the corner part p1 to the end p2 of the reinforcing part 34 next to the first case 20 in a range of 1 to 1.5 times the thickness t2 second bottom 35 of the second housing 30 in the axial direction.

The bottom 35 is a part of the lower end section 33 of the second housing 30 and propagates perpendicular to the axial direction. The end p2 of the reinforcement part 34 next to the first case 20 is gently bevelled so that the reinforcing part 34 with the other cylindrical part of the second housing 30 is connected.

According to the first embodiment, the outer diameter D1 is open end portion 33 of the second housing 30 so adjusted to the predetermined value that a mechanical impairment with the chain 93 is prevented. The lower end section 33 of the second housing 30 has the reinforcing part 34 on where the thickness t1 compared to the other cylindrical part of the second housing 30 increases in the radial direction. The reinforcement part 34 is located on the radially outer side of the corner part t1 of the flow chamber 43 and delay chamber 44 next to the lower end section 33 , The outer diameter D2 of the reinforcing part 34 is greater than the predetermined value, which is set to cause mechanical damage to the chain 93 is prevented.

When the internal pressure in the flow chamber 43 or the delay chamber 44 is increased, the stress concentrates on the radially outer portion of the corner portion p1. In the first embodiment, a part of the lower end portion 33 of the second housing 30 where the stress concentrates, with the reinforcement part 34 strengthened. Therefore, the pressure resistance behavior of the second housing 30 are increased while the outer diameter D1 of the open end portion 32 of the second housing 30 compared to a comparative example in which a second housing has a constant outer diameter remains the same.

In addition, there is no need for the outer diameter D1 of the open end portion 32 of the second housing 30 to change compared to the comparative example. Even if the gearing part 21 of the first housing 20 to that the chain 93 is wound, next to the open end section 32 of the second housing 30 is positioned, a mutual mechanical impairment between the chain 93 and the second housing 30 prevented. Thus, the outer diameter of the toothing part 21 of the first housing 20 not be enlarged, causing mutual mechanical damage between the chain 93 and the second housing 30 to be able to prevent. In addition, the gearing part must 21 of the first housing 20 not be arranged so that it from the second housing 30 is spaced in the axial direction.

Thus, according to the first embodiment, the pressure resistance performance of the second housing 30 be increased without the outer diameter and the axial length of the first housing 20 in the valve timing controller 10 must be increased.

According to the first embodiment, the reinforcing member 34 so formed at a position that it is at least the flow chamber 43 and the delay chamber 44 overlaps in the circumferential direction. Thus, all sections where the stress concentrates can be in the second housing 30 be intensified.

According to the first embodiment, the reinforcing member 34 partially formed in the circumferential direction. This will prevent the weight of the second housing 30 increases too much, while the compressive strength behavior is sufficiently increased to the necessary extent.

According to the first embodiment, the axial length L is from the corner part p1 to the end p2 of the reinforcing part 34 next to the first case 20 in a range of 1 to 1.5 times the axial thickness t2 of the underside 35 of the second housing 30 , This will prevent the weight of the second housing 30 increases too much, while the compressive strength behavior is sufficiently increased to a necessary level.

Second Embodiment

In a second embodiment, as in 4 is shown, is the reinforcing member 81 along the entire circumference of the second housing 80 educated. According to the second embodiment, the same effect as in the first embodiment can be obtained. The second housing 80 is easy to work, since the outer wall has no recess.

Other Embodiments

In another embodiment, an annular component may be a belt instead of the chain. The first housing may be a pulley around which a belt is wound.

In another embodiment, an axial length from the corner portion to the end of the reinforcement portion adjacent the first housing may be greater than 1.5 times the axial thickness of the bottom surface of the second housing. Even if the weight of the second housing is higher, in this case, the pressure resistance performance improves.

In another embodiment, an oil line control valve may be used instead of the middle part of the vane rotor may be provided outside of the valve timing controller.

In another embodiment, the valve timing controller may control an opening and closing timing of an exhaust valve and / or an intake valve of an internal combustion engine.

Such changes and modifications are to be understood as included within the scope of the invention as defined by the appended claims.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 2001-173414 A [0002, 0005, 0005]

Claims (3)

Valve timing controller, which is arranged in a drive train in which a driving force from a drive shaft ( 91 ) on an output shaft ( 92 ) of an internal combustion engine ( 90 ), so as to control a valve timing of a valve that is opened and closed by the output shaft, the valve timing controller comprising: a first housing (10); 20 ) which is in the form of a disc coaxial with one of the drive shaft or the output shaft, the first housing having the other of the drive shaft or the output shaft by an annular component ( 93 ) is connectable; a second housing ( 30 ) which is in the form of a cup which is coaxially arranged with the one of the drive shaft and the output shaft, the first housing at an open end portion ( 33 ) of the second housing is fixed; and a paddle rotor ( 40 ), which is arranged in the second housing and a blade part ( 42 ) having an interior of the second housing in a flow chamber ( 43 ) and a delay chamber ( 44 ), wherein the paddle rotor can be fixed at one end of the one of the drive shaft or the output shaft and can be rotated relative to the second housing by receiving a pressure of an operating oil, which is supplied to the flow chamber and the delay chamber, wherein an outer diameter (D1) of the open end portion of the second housing is set to a predetermined value so that mechanical interference with the annular component 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 portion (p1) of the flow chamber and the retard chamber adjacent to the lower end portion, a thickness (t1) of the reinforcing portion in a radial direction is larger than that of the other cylindrical portion of the second housing, and an outer diameter (D2) of the amplifying part is greater than the predetermined value. The valve timing controller according to claim 1, wherein the reinforcing member is disposed at a position to overlap at least the pre-flow chamber and the retard chamber in a circumferential direction. A valve timing controller according to claim 1 or 2, wherein a length (L) in an axial direction from the corner portion (p1) to an end (p2) of the reinforcing member adjacent to the first housing is in a range of 1 to 1.5 times a thickness (t2) an underside ( 35 ) of the second housing is in the axial direction.

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