The present invention relates to variable valve mechanisms that switch the drive state of valves according to the operating condition of an internal combustion engine.
There is a variable valve mechanism 90 of a first conventional example shown in
[Patent Document 1] Japanese Patent Application Publication No. 2010-31788 (JP 2010-31788 A)
In such a three-stage variable valve mechanism 90, the inventors of the present invention desired to increase the lift amount and decrease the working angle when in the medium lift state in order to achieve high performance, and desired to suppress the lift amount and increase the working angle when in the high lift state in order to achieve higher fuel efficiency (Atkinson cycle etc.).
In the variable valve mechanism 90, however, both left and right sub arms 98, 99 are coupled to the central main arm 97 when in the high lift state. The main arm 97 therefore swings according to the cam profile of one of the medium and high lift cams 93, 94 which has a larger lift amount. Accordingly, as shown by solid lines in
It is an object of the present invention to increase design flexibility of cam profiles by allowing two lift curves such as medium and high lift curves to cross.
In order to achieve the above object, a variable valve mechanism of an internal combustion engine of the present invention includes: a main arm that is capable of swinging and that drives a valve when swinging; a first sub arm that is provided on one side in the lateral direction of the main arm and that swings when driven by a first cam provided on a camshaft so as to protrude from the camshaft; a second sub arm that is provided on the other side in the lateral direction of the main arm and that swings when driven by a second cam provided on the camshaft so as to protrude from the camshaft; and a switch device that performs switching between a first coupled state where only the first sub arm of the first and second sub arms is coupled to the main arm so as to be non-swingable relative to the main arm and the main arm thus swings according to a cam profile of the first cam, and a second coupled state where only the second sub arm of the first and second sub arms is coupled to the main arm so as to be non-swingable relative to the main arm and the main arm thus swings according to a cam profile of the second cam.
According to this configuration, a first lift curve showing a lift amount of the valve relative to a rotation angle of the cam shaft when in the first coupled state can be made to cross a second lift curve showing the lift amount of the valve relative to the rotation angle of the cam shaft when in the second coupled state. This can increase design flexibility of the cam profiles of the first and second cams. Preferably, the first lift curve and the second lift curve cross each other, although the present invention is not particularly limited to this.
The form of the switch device is not particularly limited. However, it is preferable that the switch device include a first coupling pin that extends across a boundary between the main arm and the first sub arm when in the first coupled state and that does not extend across the boundary between the main arm and the first sub arm when in the second coupled state, and a second coupling pin that extends across a boundary between the main arm and the second sub arm when in the second coupled state and that does not extend across the boundary between the main arm and the second sub arm when in the first coupled state.
The switch device may perform switching only between the first coupled state and the second coupled state. However, it is preferable that the switch device perform switching among a non-coupled state where neither the first sub arm nor the second sub arm is coupled to the main arm so as to be non-swingable relative to the main arm, the first coupled state, and the second coupled state, because the switching can be performed in three stages. The following forms [i] and [ii] are shown as examples in the non-coupled state.
[i] A form in which the cam shaft is provided with a third cam having a smaller lift amount than the first and second cams, and when in the non-coupled state, the main arm swings according to a cam profile of the third cam.
[ii] A form in which when in the non-coupled state, the main arm does not swing at all and rests.
The form of the switch device in the case of such three-stage switching is not particularly limited. However, it is preferable that the switch device include a first coupling pin that extends across a boundary between the main arm and the first sub arm when in the first coupled state and that does not extend across the boundary between the main arm and the first sub arm when in the non-coupled state and the second coupled state, and a second coupling pin that extends across a boundary between the main arm and the second sub arm when in the second coupled state and that does not extend across the boundary between the main arm and the second sub arm when in the non-coupled state and the first coupled state.
More specifically, it is preferable that the switch device include: a first interposed pin that is provided in the main arm so as to contact the first coupling pin; a second interposed pin that is provided in the main arm so as to contact the second coupling pin; a non-coupling hydraulic mechanism that is provided in the main arm and that uses an oil pressure to press the first coupling pin into the first sub arm via the first interposed pin and to press the second coupling pin into the second sub arm via the second interposed pin when in the non-coupled state; a return spring that is provided in the first sub arm and that uses a restoring force to press the first coupling pin to a position where the first coupling pin extends across a boundary between the first sub arm and the main arm and to press the second coupling pin into the second sub arm via the first coupling pin, the first interposed pin, and the second interposed pin, when in the first coupled state; and a coupling hydraulic mechanism that is provided in the second sub arm, and that uses an oil pressure to press the second coupling pin to a position where the second coupling pin extends across a boundary between the second sub arm and the main arm and to press the first coupling pin into the first sub arm via the second coupling pin, the second interposed pin, and the first interposed pin, when in the second coupled state. This configuration allows one common switch device to be used in the three-stage switching structure, whereby compact, light arms can be achieved.
According to the present invention, the first lift curve showing the lift amount of the valve relative to the rotation angle of the cam shaft when in the first coupled state can be made to cross the second lift curve showing the lift amount of the valve relative to the rotation angle of the cam shaft when in the second coupled state. This can increase design flexibility of the cam profiles of the first and second cams, thereby facilitating optimal cam profile design. For example, high performance can be ensured during low to medium speed rotation, and fuel efficiency can be improved during high speed rotation.
A variable valve mechanism 9 of an embodiment shown in
[Drive Unit 10]
The drive unit 10 is formed by a camshaft 11 extending in the lateral direction and rotating according to rotation of the internal combustion engine, a low lift cam 12 provided on the camshaft 11 so as to protrude therefrom, a medium lift cam 13 provided on the camshaft 11 at a position on the right side of the low lift cam 12 so as to protrude from the camshaft 11, and a high lift cam 14 provided on the camshaft 11 at a position on the left side of the low lift cam 12 so as to protrude from the camshaft 11. In
[Main Arm 20]
The main arm 20 is an arm extending in the longitudinal direction, and has in its rear end portion a shaft hole 27 extending therethrough in the lateral direction. A rocker shaft 29 extending in the lateral direction is inserted through the shaft hole 27, whereby the rear end portion is supported so as to be swingable about the shaft. The tip end portion of the main arm 20 is widened in the lateral direction, and pressing portions 24, 24 that press the valves 7, 7 are provided on the lower surface of the right and left ends of the tip end portion. When swinging, the main arm 20 drives the valves 7, 7 by pressing down the valves 7, 7 with the pressing portions 24, 24. A roller 21 contacting the low lift cam 12 is rotatably supported in the upper part of an intermediate portion in the longitudinal direction of the main arm 20 via a roller shaft 22 and bearings 23. A pin hole 25 is formed in the lower part of the intermediate portion in the longitudinal direction of the main arm 20 so as to extend therethrough in the lateral direction.
[First Sub Arm 30]
The first sub arm 30 is an arm provided on the right side of the main arm 20 and extending in the longitudinal direction, and has in its rear end portion a shaft hole 37 extending therethrough in the lateral direction. The rocker shaft 29 is inserted through the shaft hole 37, whereby the rear end portion is supported so as to be swingable about the shaft. A roller 31 contacting the medium lift cam 13 is rotatably supported in the upper part of the front end portion of the first sub arm 30 via a roller shaft 32 and bearings (not shown). A pin hole 35 is formed in the lower part of the front end portion of the first sub arm 30 so as to extend therethrough in the lateral direction. A lost motion protrusion 38 contacting a lost motion spring 39 is provided on the lower surface of the front end portion of the first sub arm 30.
[Second Sub Arm 40]
The second sub arm 40 is an arm provided on the left side of the main arm 20 and extending in the longitudinal direction, and has in its rear end portion a shaft hole 47 extending therethrough in the lateral direction. The rocker shaft 29 is inserted through the shaft hole 47, whereby the rear end portion is supported so as to be swingable about the shaft. A roller 41 contacting the high lift cam 14 is rotatably supported in the upper part of the tip end portion of the second sub arm 40 via a roller shaft (not shown) and bearings (not shown). A pin hole 45 that opens to the right is formed in the lower part of the front end portion of the second sub arm 40. A lost motion protrusion 48 contacting a lost motion spring 49 is provided on the lower surface of the front end portion of the second sub arm 40.
[Switch Device 50]
The switch device 50 is a device that switches the lift state among a low lift state (non-coupled state), a medium lift state (first coupled state), and a high lift state (second coupled state). The low lift state (non-coupled state) is a state where neither the first sub arm 30 nor the second sub arm 40 is coupled to the main arm 20 so as to be non-swingable relative to the main arm 20. The medium lift state (first coupled state) is a state where only the first sub arm 30 of the first and second sub arms 30, 40 is coupled to the main arm 20 so as to be non-swingable relative to the main arm 20 and the second sub arm 40 is not coupled to the main arm 20 so as to be non-swingable relative to the main arm 20. The high lift state (second coupled state) is a state where only the second sub arm 40 of the first and second sub arms 30, 40 is coupled to the main arm 20 so as to be non-swingable relative to the main arm 20 and the first sub arm 30 is not coupled to the main arm 20 so as to be non-swingable relative to the main arm 20. This switch device 50 includes a first coupling pin 51, a second coupling pin 54, a first interposed pin 52, a second interposed pin 53, a return spring 58, a non-coupling hydraulic mechanism 61, and a coupling hydraulic mechanism 66, which will be described below.
The first coupling pin 51 is inserted in the pin hole 35 of the first sub arm 30. In the medium lift state, the first coupling pin 51 is advanced out of the pin hole 35 of the first sub arm 30 to the left and extends across the boundary between the pin hole 35 and the pin hole 25 of the main arm 20. In the low lift state and the high lift state, the first coupling pin 51 is withdrawn into the pin hole 35 of the first sub arm 30 and does not extend across the boundary between the pin hole 35 and the pin hole 25 of the main arm 20. The second coupling pin 54 is inserted in the pin hole 45 of the second sub arm 40. In the high lift state, the second coupling pin 54 is advanced out of the pin hole 45 of the second sub arm 40 to the right and extends across the boundary between the pin hole 45 and the pin hole 25 of the main arm 20. In the low lift state and the medium lift state, the second coupling pin 54 is withdrawn into the pin hole 45 of the second sub arm 40 and does not extend across the boundary between the pin hole 45 and the pin hole 25 of the main arm 20.
The first interposed pin 52 is inserted in the right part of the pin hole 25 of the main arm 20. The right end face of the first interposed pin 52 is in contact with the left end face of the first coupling pin 51. The second interposed pin 53 is inserted in the left part of the pin hole 25 of the main arm 20. The left end face of the second interposed pin 53 is in contact with the right end face of the second coupling pin 54. The return spring 58 is a spring interposed between the left side surface of a retainer 59 attached to the right opening of the pin hole 35 of the first sub arm 30 and the right end face of the first coupling pin 51.
The non-coupling hydraulic mechanism 61 is a mechanism that changes the oil pressure in the pin hole 25 of the main arm 20. The non-coupling hydraulic mechanism 61 is formed by a non-coupling shaft oil passage 62 formed in the right part of the rocker shaft 29, a non-coupling arm oil passage 63 formed in the main arm 20 to supply the oil pressure in the non-coupling shaft oil passage 62 to the region between the first interposed pin 52 and the second interposed pin 53 in the pin hole 25, and a non-coupling hydraulic device (not shown) that supplies an oil pressure to the non-coupling shaft oil passage 62. The coupling hydraulic mechanism 66 is a mechanism that changes, the oil pressure in the pin hole 45 of the second sub arm 40. The coupling hydraulic mechanism 66 is formed by a coupling shaft oil passage 67 formed in the left part of the rocker shaft 29, a coupling arm oil passage 68 formed in the second sub arm 40 to supply the oil pressure in the coupling shaft oil passage 67 to the region between the inner bottom surface of the pin hole 45 and the second coupling pin 54 in the pin hole 45 of the second sub arm 40, and a coupling hydraulic device (not shown) that supplies an oil pressure to the coupling shaft oil passage 67. The non-coupling shaft oil passage 62 on the right side is separated from the coupling shaft oil passage 67 on the left side by a partition pin 64 inserted in the rocker shaft 29.
Switching of the drive state of the valves 7, 7 by the variable valve mechanism 9 will be described below with respect to the case of [1] the low lift state, [2] the medium lift state, and [3] the high lift state.
[1] In the Low Lift State (Non-Coupled State)
As shown in
[2] In the Medium Lift State (First Coupled State)
As shown in
[3] In the High Lift State (Second Coupled State)
As shown in
Accordingly, when switching the lift state from the low lift state to the medium lift state, the first coupling pin 51 and the first interposed pin 52 are shifted from the right side to the left side, and the second interposed pin 53 and the second coupling pin 54 are not shifted. On the contrary, when switching the lift state from the medium lift state to the low lift state, the first coupling pin 51 and the first interposed pin 52 are shifted from the left side to the right side, and the second interposed pin 53 and the second coupling pin 54 are not shifted. When shifting the lift state from the medium lift state to the high lift state, all of the four pins 51, 52, 53, and 54 are shifted from the left side to the right side. On the contrary, when shifting the lift state from the high lift state to the medium lift state, all of the four pins 51, 52, 53, and 54 are shifted from the right side to the left side.
The following advantageous effects [A] to [C] can be obtained according to the present invention.
[A] In the medium lift state, only the first sub arm 30 that is driven by the medium lift cam 13 is coupled to the main arm 20 so as to be non-swingable relative to the main arm 20. In the high lift state, only the second sub arm 40 that is driven by the high lift cam 14 is coupled to the main arm 20 so as to be non-swingable relative to the main arm 20. Accordingly, unlike the conventional example, the medium lift curve C1 does not necessarily constantly exceed the high lift curve C2. This increases design flexibility of the cam profiles of the medium lift cam 13 and the high lift cam 14, thereby facilitating optimal cam profile design.
[B] As shown in
[C] The switch device 50 serves both as one switch device that couples and decouples the first sub arm 30 to and from the main arm 20 and as another switch device that couples and decouples the second sub arm 40 to and from the main arm 20. The switch devices can thus be integrated into one, whereby a compact, light variable valve mechanism 9 can be obtained.
The present invention is not limited to the above embodiment, and may be modified as appropriate without departing from the spirit and scope of the invention, as in, e.g., a first modification described below.
The low lift cam 12 may be eliminated, or the low lift cam 12 may be replaced with a resting cam having a true circular shape in section, so that the low lift state is replaced with a resting state where driving of the valves 7, 7 is suspended.
Number | Date | Country | Kind |
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2012-254619 | Nov 2012 | JP | national |