JP2007224733A - Oil passage of variable valve mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil passage of a variable valve mechanism which can minimize an installation space and reduce the number of processing steps. <P>SOLUTION: The oil passage of a variable valve mechanism comprises a #3 main oil passage 51 having a hydraulic pressure supply path connected to the downstream side of a hydraulic pressure source so as to supply an operating fluid from the hydraulic pressure source to a valve stop mechanism 21 for switching the operation and stop of an intake valve IV and an exhaust valve EV, an intake valve side branch oil passage 50 and an exhaust valve side branch oil passage 52 that are branched from the #3 main oil passage 51 so as to open in inner peripheral surfaces of lifter holes 47 as an intake valve side hydraulic pressure supply port and an exhaust valve side hydraulic pressure supply port, respectively. In the oil passage, the intake valve side hydraulic pressure supply port, the exhaust valve side hydraulic pressure supply port and a connecting portion 53 of the #3 main oil passage 51 and the respective branch oil passages 50, 52 are arranged on a line. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an oil passage of a variable valve mechanism.

2. Description of the Related Art Conventionally, a valve deactivation mechanism engine that incorporates a valve deactivation mechanism that is a variable valve mechanism in a valve lifter and deactivates the valve by applying hydraulic pressure is known. In such a valve deactivation mechanism engine, a main oil passage for supplying hydraulic oil from a hydraulic pressure source is usually formed in order to apply hydraulic pressure, and the hydraulic pressure is supplied from this main oil passage to the valve deactivation mechanism. (See Patent Document 1).
Japanese Patent Laid-Open No. 10-184327

  When the main oil passage can be disposed in the vicinity of the lifter hole simply by stopping the intake valve and the exhaust valve independently as in the above-described prior art, the main oil passage to the valve lifter is processed by processing from the lifter hole side of the cylinder head. Although an oil passage for hydraulic oil can be formed, a main oil passage for supplying hydraulic oil from the hydraulic power source must be provided for exhaust valve suspension and intake valve suspension, and the arrangement space is limited. There is a problem that it is difficult to arrange in the network. Therefore, there is a demand for an optimal oil passage shape that can switch the operation / pause of the valve pause mechanism at a time by oil passages that branch from the main oil passage to the exhaust valve and the intake valve.

  Accordingly, an object of the present invention is to provide an oil passage for a variable valve mechanism that can minimize the arrangement space and reduce the number of processing steps.

In order to achieve the above object, the invention described in claim 1 is characterized in that suction / exhaust is provided in a lifter hole (for example, lifter hole 47 in the embodiment) formed in a cylinder head (for example, the cylinder head 2 in the embodiment). A valve lifter (for example, the valve lifter 20 in the embodiment) provided between the valve (for example, the intake / exhaust valve IV, EV in the embodiment) and the intake / exhaust cam (for example, the valve operating cam 18IV, 18EV in the embodiment) slides. A valve suspension mechanism (for example, the valve suspension mechanism 21 in the embodiment) that is held movably and is operated by hydraulic pressure of hydraulic oil supplied from the cylinder head side into the valve lifter and switches between the operation and the suspension of the intake and exhaust valves. ) And a hydraulic pressure supply passage for supplying hydraulic oil from a hydraulic pressure source to the valve suspension mechanism. A supply passage is connected to a main oil passage (for example, # 3 main oil passage 51 in the embodiment) connected downstream of the hydraulic power source, and is branchedly connected to the main oil passage and supplies hydraulic pressure to the inner peripheral surface of the lifter hole. Branch oil passages (for example, the intake valve side branch oil passage 50 and the exhaust valve side branch oil passage 52 in the embodiment) that open as ports (for example, the intake valve side hydraulic supply port 50a and the exhaust valve side hydraulic supply port 52a in the embodiment). In the oil passage of the variable valve mechanism, the branch oil passage is a connection portion between the hydraulic supply port of the lifter hole on the exhaust valve side, the hydraulic supply port of the lifter hole on the intake valve side, and the main oil passage (For example, the connection portion 53 in the embodiment) is linearly connected and formed.
With this configuration, it is possible to form a branch oil passage for supplying hydraulic oil to the valve stop mechanism on the intake valve side / exhaust valve side by a single process. Further, only one main oil passage is sufficient.

According to a second aspect of the present invention, a part of a cylinder head that forms the lifter hole is formed separately as a lifter hole plate (for example, the lifter hole plate 2b in the embodiment), and the branch oil passage is formed. A drilling hole (for example, the processing hole 54 in the embodiment) is a side surface of the lifter hole plate, and a contact surface with the cylinder head (for example, the head body 2a in the embodiment) (for example, in the embodiment). The contact surface 55) is formed.
With this configuration, the machining hole formed in the contact surface of the lifter hole plate with the cylinder head is closed by the cylinder head.

According to a third aspect of the present invention, an annular oil groove (for example, the annular oil groove 48 in the embodiment) is formed in the lifter hole, and a machining hole formed when the branch oil passage is formed is formed in the annular oil groove. It is characterized by being drilled at a site other than the groove.
With such a configuration, since the hydraulic pressure does not act on the machining hole formed in a portion other than the oil groove unlike the oil groove, it is not necessary to close the machining hole.

According to a fourth aspect of the present invention, an engine having the cylinder head has a plurality of cylinders (for example, # 1, # 2, # 3, and # 4 cylinders in the embodiment), and the number of operating cylinders is increased. It is a multi-cylinder engine capable of cylinder deactivation that can be switched to a plurality of stages.
With this configuration, when the number of cylinders is to be controlled in several stages, the hydraulic pressure supply passage for supplying hydraulic oil to each cylinder is complicated, but a plurality of main oil passages are arranged in the cylinder head. It becomes possible to arrange in.

According to the fifth aspect of the present invention, a valve lifter provided between the intake / exhaust valve and the intake / exhaust cam is slidably held in a lifter hole formed in the cylinder head, and the cylinder head is accommodated in the valve lifter. A hydraulic pressure supply passage for supplying hydraulic oil from a hydraulic source to the valve pause mechanism is provided. A variable valve that includes a main oil passage connected downstream of the hydraulic power source, and a branch oil passage that is branched and connected to the main oil passage and opens as an oil pressure supply port on the inner peripheral surface of the lifter hole. In the oil passage of the mechanism, a part of the cylinder head that forms the lifter hole is formed separately as a lifter hole plate to form the branch oil passage An outer surface of the processing hole of the lifter hole plate that is bored in that, characterized by being formed on the contact surface between the cylinder head.
With this configuration, there is no need to separately provide a member for closing the processing hole that is closed by contacting the cylinder head.

The invention described in claim 6 is provided with a hole filling member (for example, steel balls 67 and 77 in the embodiment) that is inserted into the processing hole from the outside of the lifter hole plate and holds the processing hole in an oil-tight manner. Features.
With this configuration, the hole filling member is sandwiched between the cylinder head and the lifter hole plate.

According to a seventh aspect of the present invention, a valve lifter provided between a suction / exhaust valve and a suction / exhaust cam is slidably held in a lifter hole formed in the cylinder head, and the cylinder head is accommodated in the valve lifter. A hydraulic pressure supply passage for supplying hydraulic oil from a hydraulic source to the valve pause mechanism is provided. A main oil passage (for example, # 4 main oil passage 71 in the embodiment) connected downstream of the hydraulic power source, a branching connection to the main oil passage, and a hydraulic pressure supply port (for example, the inner peripheral surface of the lifter hole) The branch oil passage (for example, the intake valve side in the embodiment) that opens as the intake valve side hydraulic supply port 70a and the exhaust valve side hydraulic supply port 72a in the embodiment. In the oil passage of the variable valve mechanism constituted by the manifold oil passage 70 and the exhaust valve side branch oil passage 72), the branch oil passage is provided between the hydraulic supply port of the exhaust valve side lifter hole and the intake valve side lifter hole. An opening is formed with the hydraulic supply port, and the hydraulic supply port of the lifter hole on the exhaust valve side and the hydraulic supply port of the lifter hole on the intake valve side are located at a position higher than the arrangement position of the main passage. And
With this configuration, even when hydraulic oil is not supplied, the exhaust valve side lifter hole hydraulic pressure supply port and the intake valve side lifter hole hydraulic pressure supply port are located higher than the main oil passage. The hydraulic oil does not flow out, and the hydraulic oil can be held in the hydraulic pressure supply passage.

According to the first aspect of the present invention, a branch oil passage for supplying hydraulic oil to the valve stop mechanism on the intake valve side / exhaust valve side can be formed by a single process, so that the processing man-hour can be reduced. . In addition, since only one main oil passage is required, the arrangement space can be minimized.
According to the second aspect of the present invention, since the machining hole formed in the contact surface of the lifter hole plate with the cylinder head is closed by the cylinder head, a member for closing the machining hole is not required. There is an effect that the number of parts can be reduced.
According to the invention described in claim 3, since the hydraulic pressure does not act on the machining hole formed in a portion other than the oil groove unlike the oil groove, it is not necessary to close the machining hole. No need for members. Therefore, there is an effect that the number of parts can be reduced.
According to the invention described in claim 4, when the number of cylinders is to be controlled in several stages, the hydraulic pressure supply passages for supplying hydraulic oil to each cylinder are complicated, but a plurality of main oil passages are provided. Can be arranged in the cylinder head, so that it is possible to realize complicated control of the number of cylinders with a compact engine.
According to the fifth aspect of the present invention, since it is not necessary to separately provide a member for closing the processing hole that is in contact with the cylinder head and closed, there is an effect that the number of parts can be reduced.
According to the invention described in claim 6, since the hole-filling member is sandwiched between the cylinder head and the lifter hole plate, there is an effect that the hole-filling member is reliably prevented from coming off.
According to the seventh aspect of the present invention, even if hydraulic oil is not supplied, the hydraulic pressure supply port of the lifter hole on the exhaust valve side and the hydraulic pressure of the lifter hole on the intake valve side that are higher than the main oil passage. Since the hydraulic oil does not flow out from the supply port and the hydraulic oil can be held in the hydraulic pressure supply passage, there is an effect that it is possible to maintain responsiveness when driving again.

Next, 1st Embodiment of this invention is described based on drawing.
As shown in FIGS. 1 to 3, the engine E is, for example, a water-cooled in-line four-cylinder engine of a motorcycle. A cylinder head 2 is fixed to the upper surface of the cylinder block 1, and a head cover 3 is bolted to the upper surface of the cylinder head 2. It is attached by B2.
A cam chain case C is formed on the side of the engine E, and # 1 cylinder, # 2 cylinder, # 3 cylinder, and # 4 cylinder are arranged along the vehicle width direction from the cam chain case C side. One intake valve IV and two exhaust valves EV are provided. The # 1 and # 2 cylinders are normal cylinders that are always in operation. Both the # 3 and # 4 cylinders can be deactivated (cylinder deactivation) with all the intake valves IV and exhaust valves EV closed. Cylinder.
Here, in the following description, the intake valve IV and the exhaust valve EV which are a pair of engine valves on the cam chain case C side adjacent to each other in the longitudinal direction of the vehicle body in the # 3 cylinder will be described as an example. A pair of intake / exhaust valves, intake valve IV and exhaust valve EV, and each intake valve IV and exhaust valve EV of the # 4 cylinder are the same as those of the # 3 cylinder, so description thereof will be omitted.

  As shown in FIG. 2, in the cylinder head 2, a combustion chamber 5 is formed above the piston 4 in the cylinder block 1, and an intake valve opening 6 a and an exhaust valve opening 7 b formed in the combustion chamber 5 each have an intake air. The lower end openings of the port 6 and the exhaust port 7 are configured. The intake valve opening 6a is opened and closed by an intake valve IV, the exhaust valve opening 7a is opened and closed by an exhaust valve EV, and the intake valve IV and the exhaust valve EV are arranged so that the angle between them is small and each engine valve rises. Here, both the intake valve IV and the exhaust valve EV are engine valves that can be closed. Hereinafter, the intake valve IV side will be mainly described, and the exhaust valve EV side is the same as that of the intake valve IV side.

The intake valve IV is configured such that the base end of the valve stem 9 is integrally connected to a valve body portion 8 that can close the corresponding intake valve opening 6a. The exhaust valve EV closes the corresponding exhaust valve opening 7a. The base end of the valve stem 11 is integrally connected to the obtained valve body portion 10.
The valve stems 9 and 11 of the intake valve IV and the exhaust valve EV are slidably fitted to the guide cylinders 12 and 12 provided in the cylinder head 2, respectively.

A retainer 14 is fixed to a portion of the valve stem 9 of the intake valve IV that protrudes upward from the guide cylinder 12, and a coil-shaped valve spring 15 provided between the retainer 14 and the cylinder head 2 causes the intake valve IV is biased in a direction to close the intake valve opening 6a.
Further, the exhaust valve EV is urged in a direction to close the exhaust valve opening 7 a by a coiled valve spring 17 provided between the retainer 16 fixed to the valve stem 11 of the exhaust valve EV and the cylinder head 2. Yes.

  The intake valve IV and the exhaust valve EV are driven by the valve gear 13. This valve operating device 13 has cam shafts 19IV and 19EV provided with valve operating cams 18IV and 18EV (intake cams and exhaust cams), and further has a bottomed cylindrical shape that slides following the valve operating cams 18IV and 18EV. The valve lifters 20 and 20 are provided.

  The camshafts 19IV and 19EV have an axis that is orthogonal to the axial extension of the valve stem 9 in the intake valve IV and the exhaust valve EV, and the camshaft holder 34 that is coupled to the cylinder head 2 by a bolt B3. , 34 are rotatably supported. The valve lifters 20 and 20 are slidably fitted and held on the cylinder head 2 in the same direction as the axis of the valve stems 9 and 11 of the intake valve IV and the exhaust valve EV, and the outer surfaces of the closed ends of the valve lifters 20 and 20 are valve-operated. The cams 18IV and 18EV are in sliding contact.

  As shown in FIG. 3 by taking the intake side as an example, between the valve stems 9 and 11 of the intake valve IV and the exhaust valve EV and the valve lifters 20 and 20, the valve lifters 20 and 20 to the intake valve IV and the exhaust valve EV. It is possible to switch the action / non-action of the pressing force in the valve opening direction, and in a specific operating range of the engine E, for example, a low load range such as a low speed operating range, Valve pause mechanisms 21 and 21 are provided for bringing the intake valve IV and the exhaust valve EV into a pause state regardless of the sliding operation.

  As shown in FIGS. 3 to 5 by taking the intake valve IV side as an example, the valve pause mechanism 21 includes a hydraulic chamber 23 between a pin holder 22 slidably fitted to the valve lifter 20 and the inner surface of the valve lifter 20. And a slide pin 24 that is slidably fitted to the pin holder 22 and a spring force that urges the slide pin 24 in a direction that reduces the volume of the hydraulic chamber 23 to exert a force between the slide pin 24 and the pin holder 22. A return spring 25 is provided, and a stopper pin 26 is provided between the pin holder 22 and the slide pin 24 to prevent rotation of the slide pin 24 around the axis.

  The pin holder 22 includes a ring portion 22a that is slidably fitted into the valve lifter 20, and an annular groove 27 is provided on the outer periphery of the ring portion 22a. In addition, a bridging portion 22b that connects between the inner circumferences of the ring portion 22a is integrally formed along one diameter line of the ring portion 22a, and the inner circumference of the ring portion 22a and the side surfaces of the bridging portion 22b are reduced in weight. Meat is cut for illustration. Such a pin holder 22 is formed by lost wax casting or forging of iron or aluminum alloy, or is formed of synthetic resin, and the outer peripheral surface of the pin holder 22 made of metal, that is, the outer peripheral surface of the ring portion 22a, and the inner periphery of the valve lifter 20 The surface is carburized.

The bridging portion 22b is provided with a sliding hole 28 having an axis in the longitudinal direction, that is, in a direction orthogonal to the axis of the valve lifter 20. The sliding hole 28 has a bottomed shape with one end opened to the annular groove 27 and the other end closed. In addition, an insertion hole 29 that communicates with the sliding hole 28 is provided in the lower center portion of the bridging portion 22b. An extension hole 30 that communicates with the sliding hole 28 is provided coaxially with the insertion hole 29 in the center upper portion of the bridging portion 22b. A cylindrical accommodation tube portion 31 is integrally provided on the bridging portion 22 b around the extension hole 30 so as to be coaxial with the axis of the extension hole 30. Furthermore, a mounting hole 32 that communicates with the sliding hole 28 is provided in the upper part of the bridging portion 22 b from the portion corresponding to one end (open end) of the sliding hole 28 to the extension hole 30.
Similarly, as shown in FIG. 3, a mounting hole 33 that communicates with the sliding hole 28 is provided at a lower portion of the bridging portion 22 b from a portion corresponding to one end of the sliding hole 28 to the insertion hole 29. Yes. The mounting hole 33 is provided coaxially with the mounting hole 32, and the stopper pin 26 is mounted thereon.

  A disc-shaped shim 35 is fitted into the receiving cylinder portion 31 of the pin holder 22, and the end of the extension hole 30 is closed. A protrusion 36 provided at the central portion of the inner surface of the closed end of the valve lifter 20 is in contact with the shim 35. The stem end 9a of the valve stem 9 of the intake valve IV is inserted through the insertion hole 29 below the pin holder 22. A slide pin 24 is slidably fitted in the slide hole 28. A hydraulic chamber 23 communicating with the annular groove 27 is formed between one end of the slide pin 24 and the inner surface of the valve lifter 20, and a spring formed between the other end of the slide pin 24 and the closed end of the slide hole 28. A return spring 25 is accommodated in the chamber 37. When the pin holder 22 is made of synthetic resin, only the sliding contact portion with the slide pin 24 may be made of metal.

  As shown also in FIG. 5, an accommodation hole 38 is provided in the axially intermediate portion of the slide pin 24. The accommodation hole 38 is coaxially connected to the insertion hole 29 and the extension hole 30 and has a diameter capable of accommodating the stem end 9 a of the valve stem 9. Furthermore, the end of the accommodation hole 38 on the side of the insertion hole 29 is opened to a flat contact surface 39 formed on the lower outer surface of the slide pin 24 so as to face the insertion hole 29. Here, the contact surface 39 is formed relatively long along the axial direction of the slide pin 24, and the accommodation hole 38 is opened at a portion of the contact surface 39 on the spring chamber 37 side. A slit 40 that opens to the hydraulic chamber 23 side is provided on one end side of the slide pin 24.

  The slide pin 24 is provided with a communication hole 41 that allows the spring chamber 37 to communicate with the accommodation hole 38, and prevents the spring chamber 37 from being pressurized or depressurized when the slide pin 24 moves in the axial direction. Furthermore, the pin holder 22 is provided with a communication hole 42 that allows the space between the pin holder 22 and the valve lifter 20 to communicate with the spring chamber 37, thereby preventing the pressure in the space from changing due to temperature. An opening 27 b is formed in the wall portion 27 a of the annular groove 27 that forms the spring chamber 37. The diameter of the opening 27b is set smaller than the diameter of the return spring 25.

  Further, a coil spring 43 is provided between the pin holder 22 and the cylinder head 2 to urge the pin holder 22 in a direction in which a shim 35 attached to the pin holder 22 abuts against the protrusion 36 of the valve lifter 20. Yes. The coil spring 43 is attached so as to surround the valve stem 9 at a position where the outer periphery of the coil spring 43 avoids contact with the inner surface of the valve lifter 20, and the end of the coil spring 43 is connected to the bridging portion 22 b of the pin holder 22. A pair of protrusions 44 and 45 that are positioned in a direction orthogonal to the axis 9 are integrally projected.

  Both protrusions 44, 45 are integrally projected on the pin holder 22 with a protrusion amount equal to or less than the wire diameter of the coil spring 43, and are formed in an arc shape centering on the axis of the valve stem 9. Further, one of the protrusions 44 and 45 is formed with a step portion 46 for contacting the end portion of the stopper pin 26 and preventing the stopper pin 26 from moving to the intake valve IV side. Yes.

  The cylinder head 2 is provided with a lifter hole 47 into which the valve lifter 20 is fitted to slidably support the valve lifter 20. An annular oil groove 48 surrounding the valve lifter 20 is provided on the inner surface of the lifter hole 47. The annular oil groove 48 is connected to an intake valve side branch oil passage 50 (an intake valve side branch oil passage, a hydraulic pressure supply passage), which will be described later, formed in the cylinder head 2 so that hydraulic oil is supplied. ing. The valve lifter 20 is provided with a communication hole 100 and a release hole 101 that allow the annular oil groove 48 to communicate with the annular groove 27 of the pin holder 22.

  The communication hole 100 is provided at a position where the annular oil groove 48 and the annular groove 27 communicate with each other regardless of sliding in the lifter hole 47 of the valve lifter 20. When the valve lifter 20 moves to the uppermost position, the release hole 101 allows the annular oil groove 48 to pass through the valve lifter 20 below the pin holder 22, but as the valve lifter 20 moves downward from the uppermost position, The valve lifter 20 is provided at a position where communication with the oil groove 48 is cut off, and hydraulic oil is ejected from the release hole 101 into the valve lifter 20 as lubricating oil.

  The hydraulic oil supplied from the intake valve side branch oil passage 50 to the annular groove 27 of the pin holder 22 through the communication hole 100 and the release hole 101 is supplied from one end of the sliding hole 28 to the hydraulic chamber 23. The slide pin 24 is axially arranged so that the hydraulic pressure acting on one end side of the slide pin 24 by the hydraulic pressure of the hydraulic chamber 23 and the spring force acting on the other end side of the slide pin 24 by the return spring 25 are balanced. To slide. When the hydraulic pressure in the hydraulic chamber 23 is low, the stem end 9a of the valve stem 9 inserted through the insertion hole 29 moves to the left side of FIG. 3 so as to be accommodated in the accommodation hole 38 and the extension hole 30. When the hydraulic pressure in the hydraulic chamber 23 is high, the receiving hole 38 is shifted from the axis of the insertion hole 29 and the extension hole 30 so that the stem end 9a of the valve stem 9 contacts the contact surface 39 of the slide pin 24. Move to the right side of FIG.

  Here, the rotation of the slide pin 24 around the axis is prevented by the stopper pin 26. The stopper pin 26 passes through the slit 40 of the slide pin 24. That is, the stopper pin 26 is attached to the pin holder 22 through the slide pin 24 while allowing the slide pin 24 to move in the axial direction, and the stopper pin 26 contacts the inner end blocking portion of the slit 40. The contact end of the slide pin 24 toward the hydraulic chamber 23 is also regulated by the contact.

Similar to the above-described # 3 cylinder, the # 4 cylinder also includes a valve deactivation mechanism 21 so that the # 3 cylinder and the # 4 cylinder can be deactivated independently.
Accordingly, since the # 3 cylinder and # 4 cylinder are provided with the valve deactivation mechanism 21 for all engine valves, the valve deactivation mechanism 21 functions as a cylinder deactivation mechanism, and the cylinder deactivation in which all the engine valves are deactivated is performed. It can be carried out. In addition, the # 1 cylinder and the # 2 cylinder are always operated cylinders because the valve deactivation mechanism 21 is not provided.

  Here, as shown in FIG. 2, the cylinder head 2 slides on a valve body lifter 20 and a head body 2 a (cylinder head) having an intake port 6 and an exhaust port 7 in the # 3 and # 4 cylinders. The lifter hole plate 2b (cylinder head) is provided with a lifter hole 47 that is freely supported. That is, the lifter hole plate 2b is formed separately and is fixed to the head body 2a by the bolt B1.

  A cam chain (not shown) for driving the camshafts 19IV, 19EV of the intake side and exhaust side valve gears 13 is housed in the cam chain case C shown in FIG. The hydraulic oil supplied from a hydraulic source (not shown) is supplied to the # 3 and # 4 cylinders on the side wall of the cylinder head 2 on the opposite side of the cam chain case C, that is, the side wall of the lifter hole plate 2b. Ports P1 and P2 are formed, and hydraulic control valves V1 and V2 are connected to the respective ports.

  As shown in FIG. 6, the connection port P1 includes a # 3 main oil passage 51 (main oil passage) that terminates at a portion reaching the arrangement position of the intake and exhaust valves IV and EV on the cam chain case C side of the # 3 cylinder. , A hydraulic pressure supply passage) is formed toward the cam chain case C side. Specifically, the # 3 main oil passage 51 is located at a height position of the annular oil groove 48 of the lifter holes 47 in the lifter hole plate 2b and closer to the exhaust valve opening 7a at the center in the front-rear direction of the cylinder head 2. It is formed along the longitudinal direction of the cylinder head 2.

  The # 3 main oil passage 51 is branchedly connected to an intake valve side branch oil passage 50 and an exhaust valve side branch oil passage 52 (exhaust valve side branch oil passage, hydraulic pressure supply passage). The intake valve side branch oil passage 50 is a passage that opens as an intake valve side hydraulic pressure supply port 50a from the connecting portion 53 to the # 3 main oil passage 51 to the annular oil groove 48 of the lifter hole 47 of the intake valve, and is an exhaust valve side branch. The oil passage 52 is a passage that opens as an exhaust valve side hydraulic pressure supply port 52a from the connecting portion 53 to the # 3 main oil passage 51 to an annular oil groove 48 formed in the lifter hole 47 of the exhaust valve EV. The intake valve side branch oil passage 50 and the exhaust valve side branch oil passage 52 linearly connect the connecting portion 53 to the # 3 main oil passage 51, the intake valve side hydraulic supply port 50a, and the exhaust valve side hydraulic supply port 52a. It is formed at a position where it is tied.

On the extended line of the exhaust valve side branch oil passage 52, a processing hole 54 is formed which is formed when the intake valve side branch oil passage 50 and the exhaust valve side branch oil passage 52 are formed on the exhaust valve EV side. The processing hole 54 is a side surface of the lifter hole plate 2b and opens as a side surface opening 54a on the contact surface 55 with the head body 2a, and also opens as a lifter hole opening 54b on the inner peripheral surface of the lifter hole 47 on the exhaust valve EV side. Therefore, it is disengaged from the annular oil groove 48 and is disposed on the upper side.
A shoulder 56 is formed in the head body 2a at a position where the side opening 54a of the processing hole 54 of the lifter hole plate 2b is closed, and the processing hole 54 is closed in a state where the lifter hole plate 2b is tightened with the bolt B1. It has come to be. A steel ball 57 (shown by a chain line) that maintains oil tightness may be press-fitted in the vicinity of the side opening 54a of the processed hole 54.

  Here, the intake valve side branch oil passage 50 and the exhaust valve side branch oil passage having the same configuration with the # 3 main oil passage 51 in common are also used for the intake and exhaust valves IV and EV on the # 4 cylinder side of the # 3 cylinder. 52 is formed.

Next, the # 4 cylinder will be described with reference to FIGS. The # 4 cylinder is provided with two intake valves IV and two exhaust valves EV that can be stopped as in the case of the # 3 cylinder. However, the arrangement of the intake and exhaust valves IV and EV on the cam chain case C side is provided. A description will be given by taking a part as an example.
As shown in FIG. 1, a # 4 main oil passage 61 is formed in the connection port P2 toward the cam chain case C side. Specifically, the # 4 main oil passage 61 is formed along the longitudinal direction of the cylinder head 2 in the lifter hole plate 2b, near the intake valve opening 6a at the center in the front-rear direction of the cylinder head 2, It terminates at a portion that reaches the arrangement position of the intake and exhaust valves IV and EV on the 4-cylinder cam chain case C side. The # 4 main oil passage 61 is formed at a position higher than the # 3 main oil passage 51 (see FIG. 6).

An intake valve side branch oil passage 60 and an exhaust valve side branch oil passage 62 are branchedly connected to the # 4 main oil passage 61. The intake valve side branch oil passage 60 is formed obliquely downward from the connecting portion 63 with the # 4 main oil passage 61 toward the annular oil groove 48 of the lifter hole 47 of the intake valve IV and opens as an intake valve side hydraulic supply port 60a. The exhaust valve-side branch oil passage 62 is formed obliquely downward from the connecting portion 63 with the # 4 main oil passage 61 toward the annular oil groove 48 formed in the lifter hole 47 of the exhaust valve EV. The passage opens as the hydraulic pressure supply port 62a.
The intake valve side branch oil passage 60 is linearly formed from the connecting portion 63 of the # 4 main oil passage 61 to the intake valve side hydraulic supply port 60a, and the exhaust valve side branch oil passage 62 is # 4 main. It is formed linearly from the connecting portion 63 of the oil passage 61 to the exhaust valve side hydraulic pressure supply port 62a.

On the extended line of the exhaust valve side branch oil passage 62, a processing hole 64 is formed which is formed when the exhaust valve side branch oil passage 62 is formed on the exhaust valve EV side. The processing hole 64 is opened as a side opening 64a on the side surface of the lifter hole plate 2b and is opened as an annular oil groove opening 64b on the inner peripheral surface of the annular oil groove 48 on the exhaust valve EV side.
In the vicinity of the side opening 64a of the processing hole 64 of the lifter hole plate 2b, a steel ball 67 (hole filling member) that closes the processing hole 64 and maintains oil tightness is press-fitted.
Here, the intake valve side branch oil passage 60 and the exhaust valve having the same configuration as the # 4 main oil passage 61 are common to the intake and exhaust valves IV and EV on the opposite side to the # 4 cylinder cam chain case C. A side branch oil passage 62 is formed.

According to the above embodiment, for the # 3 cylinder shown in FIG. 6, the machining hole 54, the exhaust valve side branch oil passage 52, and the intake valve side branch oil passage 50 are once provided from the side surface of the lifter hole plate 2b on the exhaust valve EV side. Therefore, the exhaust valve side branch oil passage 52 and the intake valve side branch oil passage 50 can be simplified and the number of processing steps can be reduced.
Further, since the side opening 54a formed on the contact surface 55 of the lifter hole plate 2b is closed by the shoulder 56 of the head main body 2a, a special member for closing the machining hole 54 is not necessary and the number of parts is reduced. Can be reduced. Thereby, the interruption | blocking with an outer side is ensured, and the oil leak inside can be suppressed to the minimum. That is, when the side lift 54a is opened when the valve lifter 20 is lowered, it is possible to prevent oil from escaping from here.
The processing hole 54 is formed as a lifter hole opening 54b on the inner peripheral surface other than the annular oil groove 48 in the lifter hole 47 on the exhaust valve EV side. Therefore, the lifter hole opening 54b has an annular oil groove 48 as shown in FIG. Hydraulic pressure does not act, and in this respect as well, no special member is required to close the machining hole 54, and the number of parts can be reduced.

On the other hand, in the # 4 cylinder shown in FIG. 7, a steel ball 67 that closes the processing hole 64 and maintains oil tightness is press-fitted in the vicinity of the side opening 64a of the processing hole 64 of the lifter hole plate 2b. The steel ball 67 is sandwiched between the head main body 2a and the lifter hole plate 2b, and the steel ball 67 is reliably prevented from coming off.
Further, as shown in FIG. 1, in order to supply hydraulic oil to the valve deactivation mechanism 21 of the intake / exhaust valves IV and EV of the # 3 cylinder or # 4 cylinder, the # 3 main oil passage 51 and the # 4 main oil passage 61 are provided. However, the arrangement space for the # 3 main oil passage 51 and the # 4 main oil passage 61 can be minimized.

  Here, if the hydraulic control valves V1 and V2 are operated and the # 3 cylinder and the # 4 cylinder are deactivated, the engine E in which only the # 1 cylinder and the # 2 cylinder are operated, and any of the hydraulic control valves V1 and V2 is selected. If the # 3 cylinder or # 4 cylinder is deactivated by operating the engine, the engine E is operated in which the # 1 cylinder, the # 2 cylinder and the # 3 cylinder or the # 1 cylinder, the # 2 cylinder and the # 4 cylinder are operated. If the cylinder and the # 4 cylinder are operated, the engine E is operated with four cylinders. As described above, the # 3 main oil passage 51 and the # 4 main oil passage 61 can be arranged in the head body 2a while the multi-cylinder engine capable of stopping the cylinder can be switched in a plurality of stages. Therefore, complicated cylinder number control can be realized with a compact engine.

Next, a second embodiment will be described based on FIG. 8 with reference to FIG. In this embodiment, an explanation will be given by taking as an example the arrangement site of the intake and exhaust valves IV and EV on the cam chain case C side of the # 4 cylinder. In addition, the same code | symbol is attached | subjected about the same part as 1st Embodiment mentioned above, and description is abbreviate | omitted.
In the connection port P2, a # 4 main oil passage 71 (main oil passage, hydraulic pressure supply passage) is formed toward the cam chain case C side. Specifically, the # 4 main oil passage 71 is formed along the longitudinal direction of the cylinder head 2 in the lifter hole plate 2b, near the intake valve opening 6a at the center in the front-rear direction of the cylinder head 2, It terminates at a portion that reaches the arrangement position of the intake and exhaust valves IV and EV on the 4-cylinder cam chain case C side. The # 4 main oil passage 71 is formed at a position lower than the annular oil groove 48.

The # 4 main oil passage 71 is branched into an intake valve side branch oil passage 70 (intake valve side branch oil passage, hydraulic supply passage) and an exhaust valve side branch oil passage 72 (exhaust valve side branch oil passage, hydraulic supply passage). It is connected. The intake valve side branch oil passage 70 is formed obliquely upward from the connecting portion 73 with the # 4 main oil passage 71 toward the annular oil groove 48 of the lifter hole 47 of the intake valve IV and opens as an intake valve side hydraulic supply port 70a. The exhaust valve side branch oil passage 72 is formed obliquely upward from the connecting portion 73 with the # 4 main oil passage 71 toward the annular oil groove 48 formed in the lifter hole 47 of the exhaust valve EV. This is a passage that opens as a hydraulic pressure supply port 72a.
The intake valve side branch oil passage 70 is linearly formed from the connection portion 73 of the # 4 main oil passage 71 to the intake valve side hydraulic pressure supply port 70a, and the exhaust valve side branch oil passage 72 is # 4 main. It is formed linearly from the connecting portion 73 of the oil passage 71 to the exhaust valve side hydraulic pressure supply port 72a.

On the extended line of the exhaust valve side branch oil passage 72, a processing hole 74 is formed which is formed when the exhaust valve side branch oil passage 72 is formed on the exhaust valve EV side. The processing hole 74 opens as a side opening 74 a on the side surface of the lifter hole plate 2 b and opens as a lifter hole opening 74 b on the inner surface by the lifter hole 47 on the exhaust valve EV side, and is disposed above the annular oil groove 48. ing. In the vicinity of the side opening 74a of the processing hole 74 of the lifter hole plate 2b, a steel ball 77 (a hole filling member) that closes the processing hole 74 and maintains oil tightness is press-fitted. The intake / exhaust valves IV and EV on the side opposite to the cam chain case C side of the # 4 cylinder also have the same configuration as the intake valve side branch oil passage 70 and the exhaust valve side with the # 4 main oil passage 71 in common. A branch oil passage 72 is formed.
Here, if the # 3 cylinder does not interfere with the # 4 main oil passage 71 of the # 4 cylinder, it may be formed at a position contrasting with the # 4 main oil passage 71, or the # 3 main in the first embodiment. An arrangement structure such as the oil passage 51 or the # 4 main oil passage 61 may be employed.

  According to this embodiment, the # 4 main oil passage 71 has only to be formed in the # 4 cylinder as in the above-described embodiment, so that the arrangement space of the # 4 main oil passage 71 can be minimized. it can. In particular, in this embodiment, the intake valve side branch oil passage 70 and the exhaust valve side branch oil passage 72 branched from the connecting portion 73 of the # 4 main oil passage 71 are formed obliquely upward, and the # 4 main oil passage 71. In other words, the intake valve side hydraulic pressure supply port 70a and the exhaust valve side hydraulic pressure supply port 72a are formed at a position higher than the position where the connection portion 73 is disposed. For example, the engine E stops and hydraulic oil is supplied. Even if not, the hydraulic oil does not flow out from the intake valve side hydraulic supply port 70a and the exhaust valve side hydraulic supply port 72a that are higher than the # 4 main oil passage 71, and the hydraulic oil is branched into the intake valve side. It can be held in the oil passage 70 and the exhaust valve side branch oil passage 72. Therefore, the responsiveness when driving again can be maintained.

The present invention is not limited to the above embodiment. For example, in the # 3 cylinder of the first embodiment, the position of the # 3 main oil passage 51 may be on the intake valve IV side, You may set in the outer side position of the lifter hole 47 of the exhaust valve EV. This can also be applied to the # 4 main oil passage 61 of the first embodiment. Further, the # 4 main oil passage 61 of the first embodiment may be provided at any position with respect to the # 3 main oil passage 51 as long as it does not overlap with the # 3 main oil passage 51 in the vertical direction.
Further, the configurations of the # 4 main oil passage 61, the intake valve side branch oil passage 60 and the exhaust valve side branch oil passage 62 of the # 4 cylinder of the first embodiment may be applied to the # 3 cylinder with their directions reversed. Is possible. In each embodiment, the case where all the engine valves of one cylinder are deactivated has been described. However, the present invention may be applied to some engine valves, for example, the engine E in which a pair of intake / exhaust valves IV and EV are deactivated. Can do.

It is a principal part top view of 1st, 2nd embodiment of this invention. It is sectional drawing which follows the AA line of FIG. FIG. 3 is an enlarged cross-sectional view showing the intake valve side of FIG. 2. It is the perspective view which looked at the pin holder from the upper part. It is a perspective view of a slide pin. It is sectional drawing of the site | part (# 3 cylinder) lifter hole plate in alignment with the AA of FIG. It is sectional drawing of the site | part (# 4 cylinder) lifter hole plate in alignment with the BB line of FIG. It is sectional drawing of the lifter hole plate corresponding to FIG. 7 of 2nd Embodiment.

Explanation of symbols

2 Cylinder head 2a Head body (cylinder head)
2b Lifter hole plate (cylinder head)
18IV Valve cam (intake cam)
18EV Valve cam (exhaust cam)
20 valve lifter 21 valve rest mechanism 47 lifter hole 48 annular oil groove 51 # 3 main oil passage (main oil passage, hydraulic pressure supply passage)
50, 70 Branch oil passage (intake valve side branch oil passage, hydraulic pressure supply passage)
50a, 70a Intake valve side hydraulic supply ports 52, 72 Branch oil passage (exhaust valve side branch oil passage, hydraulic supply passage)
52a, 72a Exhaust valve side hydraulic supply port 53 Connection portion 54 Processing hole 55 Contact surface 67 Steel ball (hole filling member)
71 # 4 main oil passage (main oil passage, hydraulic pressure supply passage)
77 Steel balls (filling holes)
IV Intake valve EV Exhaust valve

Claims (7)

  A valve lifter provided between a suction / exhaust valve and a suction / exhaust cam is slidably held in a lifter hole formed in the cylinder head, and hydraulic pressure of hydraulic oil supplied from the cylinder head side to the valve lifter Is provided with a valve stop mechanism that switches between operation and stop of the intake / exhaust valve, a hydraulic supply passage for supplying hydraulic oil from a hydraulic source to the valve stop mechanism, and the hydraulic supply passage is A variable valve mechanism comprising a main oil passage connected downstream of the hydraulic power source and a branch oil passage branchingly connected to the main oil passage and opening as an oil pressure supply port on the inner peripheral surface of the lifter hole In the oil passage, the branch oil passage includes a hydraulic supply port for the lifter hole on the exhaust valve side, a hydraulic supply port for the lifter hole on the intake valve side, and the main passage. Oil passage of the variable valve mechanism, characterized in that it is formed by connecting in a straight line and a connecting portion between the oil passage.   A part of the cylinder head that forms the lifter hole is formed separately as a lifter hole plate, and a machining hole formed when forming the branch oil passage is a side surface of the lifter hole plate, The oil passage of the variable valve mechanism according to claim 1, wherein the oil passage is formed on a contact surface of the variable valve mechanism.   2. The variable motion according to claim 1, wherein an annular oil groove is formed in the lifter hole, and a machining hole is formed in a portion other than the annular oil groove when the branch oil passage is formed. Oil passage of the valve mechanism.   The engine having the cylinder head is a multi-cylinder engine having a plurality of cylinders and capable of stopping a cylinder in which the number of operating cylinders can be switched to a plurality of stages. An oil passage of the variable valve mechanism described.   A valve lifter provided between a suction / exhaust valve and a suction / exhaust cam is slidably held in a lifter hole formed in the cylinder head, and hydraulic pressure of hydraulic oil supplied from the cylinder head side to the valve lifter Is provided, and a valve stop mechanism for switching the operation / pause of the intake / exhaust valves is provided, and a hydraulic supply passage for supplying hydraulic oil from the hydraulic source to the valve stop mechanism is connected downstream of the hydraulic source. In the oil passage of the variable valve mechanism, which is constituted by a main oil passage that is branched and connected to the main oil passage and opens as a hydraulic pressure supply port on the inner peripheral surface of the lifter hole, the lifter hole is A part of the cylinder head to be formed is formed separately as a lifter hole plate, and is drilled when the branch oil passage is formed. The Koana an outer surface of the lifter hole plate, the oil passage of the variable valve mechanism, characterized in that formed in the contact surface between the cylinder head.   6. The oil passage for a variable valve mechanism according to claim 5, further comprising a hole filling member inserted into the processing hole from the outside of the lifter hole plate and holding the processing hole in an oil-tight manner.   A valve lifter provided between a suction / exhaust valve and a suction / exhaust cam is slidably held in a lifter hole formed in the cylinder head, and hydraulic pressure of hydraulic oil supplied from the cylinder head side to the valve lifter Is provided, and a valve stop mechanism for switching the operation / pause of the intake / exhaust valves is provided, and a hydraulic supply passage for supplying hydraulic oil from the hydraulic source to the valve stop mechanism is connected downstream of the hydraulic source. In the oil passage of the variable valve mechanism, which is constituted by a main oil passage that is branched and connected to the main oil passage and opens as an oil pressure supply port on the inner peripheral surface of the lifter hole. The passage is formed by the hydraulic pressure supply port of the lifter hole on the exhaust valve side and the hydraulic pressure supply port of the lifter hole on the intake valve side, and the arrangement position of the main passage Remote a high position, the oil passage of the variable valve mechanism, wherein the hydraulic supply port Rifutahoru the exhaust valve side to the intake valve side of the hydraulic supply port Rifutahoru is located.

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