JP2018059439A - Hydraulic pressure supply device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve response delay of a hydraulic actuation device while suppressing occurrence of a malfunction of the hydraulic actuation device caused by air accumulated in an oil passage.SOLUTION: A hydraulic pressure supply device 2 includes: an oil passage 61 (first oil passage) to which oil (hydraulic fluid) is always supplied during operation of an engine 1; an oil passage 65 (second oil passage) which communicates with a valve stop mechanism 25b (hydraulic actuation device), and to which the oil is supplied by opening of a first direction changeover valve 56 (control valve) when a specific condition is satisfied; and a communication passage 66 (connection oil passage) causing the oil passage 61 and the oil passage 65 to communicate with each other and having an orifice unit 30A which allows the oil in the oil passage 61 to be introduced into the oil passage 65 while reducing a pressure thereof in closing of the first direction changeover valve in the halfway thereof. The orifice unit 30A has an air vent Ab for releasing air to the outside.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a hydraulic pressure supply device that supplies hydraulic oil to a hydraulic operation device such as a valve stop mechanism.

  As a pivot mechanism for a rocker arm (swing arm), a hydraulically operated lash adjuster that automatically adjusts a valve clearance to zero by hydraulic pressure has been applied. In recent years, as disclosed in Patent Document 1, a lash adjuster with a valve stop mechanism is applied as a lash adjust for some cylinders, and the suction is performed for some of the cylinders under certain conditions during engine operation. An engine is known in which the fuel consumption performance is improved by stopping the operation of the exhaust valve (implementing the reduced cylinder operation). The lash adjuster with a valve stop mechanism is a lash adjuster that can be switched between a state that allows operation of the intake and exhaust valves and a state that stops operation of the intake and exhaust valves, and supplies hydraulic oil to the valve stop mechanism. By doing so, it is configured to switch to a state in which the operation of the intake and exhaust valves is stopped.

  In the engine as described above, an adjuster oil passage that supplies hydraulic oil to a lash adjuster (including a lash adjuster with a valve stop mechanism) of each cylinder, and a valve that supplies hydraulic oil to the valve stop mechanism of the lash adjuster with a valve stop mechanism A stop oil passage is provided, and during operation of the engine, hydraulic oil is always supplied to the adjuster oil passage, while hydraulic oil is supplied to the valve stop oil passage only during reduced-cylinder operation. ing.

  However, in this case, if the valve stop oil passage is provided independently, the hydraulic oil in the valve stop oil passage is reduced due to oil return during all cylinder operation of the engine, and the next time the valve stop mechanism is operated. Response delay may occur. Therefore, in Patent Document 1, the adjuster oil passage and the valve stop oil passage are connected via a communication oil passage provided with an orifice (throttle) in the middle, and during the entire cylinder operation of the engine, the adjuster oil passage to the valve stop oil passage. The hydraulic oil is gradually allowed to flow in while reducing the pressure. According to this configuration, the valve stop mechanism can be kept stopped while the valve stop oil passage is filled with the hydraulic oil during all cylinder operation of the engine, so that it is possible to suppress the response delay as described above. .

Japanese Patent Application Laid-Open No. 2015-124752

  However, in the above configuration where the adjuster oil passage and the valve stop oil passage are connected via the communication oil passage provided with the orifice, the air accumulated in the adjuster oil passage is introduced into the valve stop oil passage through the orifice, and the valve stop It is possible that the mechanism malfunctions. In other words, since air has a lower viscosity than hydraulic oil, it cannot be depressurized even if an orifice is present, so that air is introduced into the valve stop oil passage so that the pressure in the valve stop oil passage can be reduced. However, it is conceivable that the valve stop mechanism malfunctions when it reaches the pressure at which the valve stop mechanism operates. In particular, if the engine has been stopped for a long period of time, the adjuster oil passage will also be in a state where a large amount of air has accumulated due to the return of oil, so there is a high possibility that the valve stop mechanism will malfunction when the engine is started. It is done. Therefore, it is required to improve this point.

  The present invention has been made in view of the above circumstances, and in a hydraulic supply device that supplies hydraulic oil to a hydraulic operation device such as a valve stop mechanism, the hydraulic operation device malfunctions due to air accumulated in the oil passage. It is an object of the present invention to provide a technique capable of improving the response delay of the hydraulic actuator while suppressing this.

  In order to solve the above problems, the present invention provides a hydraulic supply device for a multi-cylinder engine having a hydraulic operation device that operates under a specific condition while the engine is operating, and the hydraulic oil is constantly supplied during the operation of the engine. A first oil passage that communicates with the hydraulic actuator, a second oil passage that is supplied with hydraulic oil by opening a control valve when the specific condition is satisfied, and the first oil passage And the second oil passage, and the hydraulic oil in the first oil passage is introduced into the second oil passage while reducing the pressure when the control valve is closed. And a connecting oil passage provided with an orifice unit in the middle of the orifice unit, the orifice unit having an air vent for allowing air to escape to the outside.

  According to this hydraulic pressure supply device, the hydraulic oil in the first oil passage is introduced into the second oil passage through the connection oil passage (orifice unit) while reducing the hydraulic pressure under other conditions than the specific conditions. Therefore, the hydraulic actuator can be kept in a stopped state while filling the second oil passage with the hydraulic oil, and the hydraulic pressure can be quickly applied to the hydraulic actuator when the specific condition is satisfied. Even if air has accumulated in the first passage due to a long-term stop of the engine, when hydraulic oil is supplied to the first passage by starting the engine, the air is accordingly removed from the air vent portion of the orifice unit. Since the air escapes to the outside, the introduction of the air into the second passage is suppressed. Therefore, according to this hydraulic pressure supply device, it is possible to improve the response delay of the hydraulic actuator while suppressing the malfunction of the hydraulic actuator due to the air accumulated in the first oil passage.

  In the above hydraulic pressure supply device, a valve stop mechanism that stops at least one of an intake valve and an exhaust valve of some cylinders among a plurality of cylinders may be considered as the hydraulic operation device.

  According to this configuration, it is possible to improve the response delay of the valve stop mechanism and to prevent the valve stop mechanism from malfunctioning due to the air accumulated in the first passage being introduced into the second passage while the engine is stopped. It becomes.

  As a more specific configuration, the engine includes a hydraulically operated lash adjuster corresponding to the intake valves and exhaust valves of all the cylinders, and the valve stop mechanism includes the lashes of some cylinders. In the case of being incorporated in an adjuster, the first oil passage supplies hydraulic oil to the lash adjuster and extends in the cylinder row direction, and the second oil passage includes the first oil passage. The connecting oil passage extends in the up-down direction through the first oil passage at a position below the passage, and the connection oil passage extends in the up-down direction to the first oil passage and the second oil passage. The orifice unit is disposed in the connecting oil passage in a state straddling the first oil passage and the second oil passage, and includes the air vent portion at an upper portion thereof.

  According to this configuration, the hydraulic oil is introduced into the second oil passage while flowing downward from the first oil passage through the connecting oil passage (orifice unit), so that the air in the first oil passage is at the position of the orifice unit. Escape upwards. Therefore, according to the above configuration in which the air vent is provided in the upper part of the orifice unit, it is possible to release air to the outside satisfactorily.

  In the above hydraulic pressure supply device, the orifice unit includes a unit main body and a fixing member that fixes the unit main body in a state where the unit main body is pressed from the upper side into the connecting oil passage, and the air vent portion is the fixed body. An air vent passage comprising a gap formed between a member and the unit main body and a first air vent hole formed in the fixing member is provided.

  According to this configuration, it is possible to favorably escape the air in the first oil passage to the outside while maintaining the general structure of the orifice unit including the unit main body and the fixing member.

  In this case, it is preferable that the air bleed portion includes a second air bleed hole that is formed in the ceiling wall portion of the unit main body and joins the air that has entered the unit main body into the first air bleed hole. It is.

  According to this configuration, the air introduced into the unit body together with the hydraulic oil can be released to the outside, so that the introduction of air into the second passage can be more reliably suppressed.

  As a more specific configuration, in the hydraulic pressure supply device, when one end side in the cylinder row direction of the engine is defined as the front and the other end side is defined as the rear, the valve stop mechanism is located at the front end in the cylinder row direction. An intake side first valve stop mechanism for stopping the intake valve of the front end cylinder, an exhaust side first valve stop mechanism for stopping the exhaust valve of the front end cylinder, and an intake valve of the rear end cylinder located at the rear end in the cylinder row direction And an exhaust side second valve stop mechanism for stopping the exhaust valve of the rear end cylinder, and the first oil passage is connected to a lash adjuster of each intake valve of all cylinders. An intake side first oil passage for supplying hydraulic oil, and an exhaust side first oil passage for supplying hydraulic oil to the lash adjusters of the exhaust valves of all cylinders, wherein the second oil passage is the intake side first oil passage. An intake-side front end second oil passage for supplying hydraulic oil to the valve stop mechanism, and the exhaust-side first valve stop The exhaust side front end second oil passage for supplying hydraulic oil to the mechanism, the intake side rear end second oil passage for supplying hydraulic oil to the intake side second valve stop mechanism, and the exhaust side second valve stop mechanism are operated. An exhaust-side rear end second oil passage for supplying oil, and the connection oil passage communicates the intake-side first oil passage and the intake-side front end second oil passage; An intake side connecting the exhaust side first oil passage and the exhaust side front end second oil passage, and the intake side first oil passage and the intake side rear end second oil passage. A second connection oil passage, and an exhaust side second connection oil passage connecting the exhaust side first oil passage and the exhaust side rear end second oil passage, and the orifice unit is provided in each of the connection oil passages. Is provided.

  In this configuration, when the specific condition is satisfied, the valve stop mechanism corresponding to the intake valve and the exhaust valve of each of the front end cylinder and the rear end cylinder is operated, whereby the operation of the intake valve and the exhaust valve is stopped. . In this configuration, the air at the positions of the first and second connection oil paths, that is, at two positions along the intake side first oil path and at two positions along the exhaust side first oil path. Since the air is removed, it is difficult for the air accumulated in each first oil passage to lose its escape and be introduced into each second oil passage, and the air in each first oil passage is more reliably externally provided. It is possible to escape. Therefore, the malfunction of each valve stop mechanism is further suppressed to a high degree.

  In this case, each of the front end second oil passages causes the hydraulic oil to flow from the front end side toward the rear end side by opening the control valve, and each of the rear end second oil passages opens the control valve. The hydraulic oil flows from the rear end side toward the front end side by the valve operation, and each of the first connection oil passages is located at a position immediately downstream of each of the first valve stop mechanisms in the flow direction of the hydraulic oil. It is preferable that each of the second connection oil passages is provided at a position immediately downstream of each of the second valve stop mechanisms in the flow direction of the hydraulic oil.

  According to this configuration, since the distance from each first passage to the position of each valve stop mechanism in each second passage is as short as possible, each second oil passage is more reliably arranged at the position of each valve stop mechanism. It can be filled with hydraulic oil. Therefore, it is advantageous in improving the responsiveness of each valve stop mechanism.

  As described above, according to the present invention, in the hydraulic pressure supply device that supplies the hydraulic pressure to the hydraulic pressure operating device such as the valve stop mechanism, the malfunction of the hydraulic pressure operating device due to the air accumulated in the oil passage is suppressed. The response delay of the hydraulic actuator can be improved.

1 is a cross-sectional view of a multi-cylinder engine to which a hydraulic pressure supply device according to an embodiment of the present invention is applied. It is sectional drawing which shows the structure and action | operation of a valve stop mechanism. It is a hydraulic circuit diagram which shows schematic structure of a hydraulic pressure supply apparatus. It is sectional drawing of the cylinder head (intake side) of the said multi-cylinder engine. It is sectional drawing of the orifice unit integrated in the cylinder head. It is principal part sectional drawing of the orifice unit explaining the flow of air.

  Hereinafter, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

<Overall engine configuration>
FIG. 1 shows a multi-cylinder engine 1 (hereinafter simply referred to as an engine 1) to which a hydraulic pressure supply device of the present invention is applied. The engine 1 is a vehicle engine such as an automobile. The engine 1 is an in-line four-cylinder gasoline engine in which first to fourth cylinders # 1 to # 4 (shown in FIG. 4) are arranged in a line in a direction perpendicular to the plane of FIG.

  In this example, the cylinder row direction of the engine 1 is the front-rear direction of the engine, the direction perpendicular to the engine is the engine width direction, and the first cylinder # 1, the second cylinder # are sequentially arranged from the cylinder located on the front end side of the engine 1. 2, the third cylinder # 3 and the fourth cylinder # 4 shall be referred to. In this example, the first cylinder # 1 and the fourth cylinder # 4 correspond to the “front end cylinder” and the “rear end cylinder” of the present invention, respectively.

  The engine 1 includes a cam cover 3, a cylinder head 4, a cylinder block 5, a crankcase (not shown), and an oil pan (not shown) that are connected vertically. Four cylinder bores 7 are formed in the cylinder block 5, and pistons 8 are slidably accommodated in the respective cylinder bores 7. A combustion chamber 11 is formed for each cylinder by the piston 8, the cylinder bore 7 and the cylinder head 4. Yes. The piston 8 of each cylinder is connected via a connecting rod 10 to a crankshaft 9 that is rotatably supported by the crankcase.

  The cylinder head 4 is provided with an intake port 12 and an exhaust port 13 that open to the combustion chamber 11, and an intake valve 14 and an exhaust valve 15 that open and close the intake port 12 and the exhaust port 13, respectively. Equipped.

  The intake valve 14 and the exhaust valve 15 are urged in the direction of closing the ports 12 and 13 (upward in FIG. 1) by return springs 16 and 17, respectively, and are provided on the outer periphery of the camshafts 18 and 19. Each port 12 and 13 is configured to be opened when pressed by the cam portions 18a and 19a. Specifically, as the camshafts 18 and 19 rotate, the cam portions 18a and 19a press the cam followers 20a and 21a provided at the substantially central portions of the swing arms 20 and 21, so that the swing arms 20 and 21 are The top of the pivot mechanism of HLA (24) and 25, which will be described later, provided on one end side is swung, and the other end of the swing arms 20, 21 is subjected to the urging force of the return springs 16, 17 along with this swinging. The intake valve 14 and the exhaust valve 15 are pressed down against it. As a result, the ports 12 and 13 are opened.

  Among the first to fourth cylinders # 1 to # 4 of the engine 1, the central second, third cylinders # 2 and # 3 are hydraulic lash adjusters (as pivot mechanisms for the swing arms 20 and 21). (Hydraulic Lash Adjuster) 24 is provided (see FIG. 4). The hydraulic lash adjuster 24 (hereinafter referred to as HLA 24) automatically adjusts the valve clearance to zero by hydraulic pressure.

  On the other hand, among the first to fourth cylinders # 1 to # 4, the first and fourth cylinders # 1 and # 4 located at both ends in the cylinder row direction are hydraulic lashes as the pivot mechanism of the swing arms 20 and 21. A hydraulic lash adjuster 25 with a valve stop mechanism in which the valve stop mechanism is incorporated in the adjuster (hereinafter referred to as an HLA 25 with a valve stop mechanism, or simply referred to as HLA 25) is provided. The HLA 25 with a valve stop mechanism automatically adjusts the valve clearance to zero like the HLA 24, but in addition to this function, the intake valve 14 and the exhaust valve 15 are allowed to operate. It has a function of switching to a stopped state. As a result, the engine 1 is operated in such a way that all cylinders are operated (open / close operation) to operate the intake and exhaust valves 14 and 15 of all cylinders, and the first and fourth cylinders # 1 and # 1 among all cylinders. The operation of the intake / exhaust valves 14 and 15 of 4 is stopped (open / close operation is stopped), and the operation is switched to the reduced cylinder operation in which only the intake and exhaust valves 14 and 15 of the second and third cylinders # 2 and # 3 are operated. It is possible.

  In the cylinder head 4, mounting holes 26, 27 into which the lower end portions of the HLA 25 with a valve stop mechanism are inserted and mounted in the intake side and exhaust side portions corresponding to the first and fourth cylinders # 1 and # 4. Is provided. In addition, the mounting holes 26 and 27 into which the lower end portion of the HLA 24 is inserted and mounted in the portions on the intake side and the exhaust side corresponding to the second and third cylinders # 2 and # 3 in the cylinder head 4 are the same. Is provided. The two oil passages 61, 62 extend in the cylinder row direction over the first to fourth cylinders # 1, # 4 and communicate with the mounting holes 26, 27 of the HLA 24, 25 on the intake side and the exhaust side, respectively. The two oil passages 65 extend in the cylinder row direction at positions corresponding to the first and fourth cylinders # 1 and # 4 and communicate with the mounting holes 26 and 27 of the HLA 25 with a valve stop mechanism on the intake side and the exhaust side, respectively. (75) and 67 (77) are formed in the cylinder head 4.

  Of these oil passages 61, 62, 65 (75), 67 (77), the oil passages 61, 62 are the pivot mechanism main bodies 25a described later for the HLA 24 mounted in the mounting holes 26, 27 and the HLA 25 with a valve stop mechanism. The pivot mechanism body 25a of the HLA 24 and the HLA 25 with a valve stop mechanism automatically adjusts the valve clearance to zero by its hydraulic pressure (operating pressure). On the other hand, the oil passages 65 (75) and 67 (77) supply oil to a later-described valve stop mechanism 25b (shown in FIG. 2) of the HLA 25 with a valve stop mechanism mounted in the mounting holes 26 and 27. is there. This point will be described in detail later.

  The cam cover 3 is provided with shower nozzles 28 and 29. The cam portions 18a and 19a of the camshafts 18 and 19 located below the shower nozzles 28 and 29 and the swing arms 20 and 21 and the cam follower are provided. Oil (lubricating oil) is dripped at the contact portions with 20a and 21a.

<Configuration of HLA 25 with valve stop mechanism>
Next, the valve stop mechanism 25b of the HLA 25 with a valve stop mechanism will be described with reference to FIG. As described above, the valve stop mechanism 25b switches the intake valve 14 and the exhaust valve 15 between a state in which the operation is permitted and a state in which the operation is stopped, thereby changing the operation state of the engine 1 from the all-cylinder operation state to the reduced cylinder operation. It switches to the operating state. In other words, when the engine 1 is controlled to operate all cylinders, the valve stop mechanism 25b is stopped, and thereby the intake and exhaust valves 14 and 15 of all cylinders including the first and fourth cylinders # 1 and # 4 are stopped. When the opening / closing operation is performed while the engine 1 is controlled to reduce cylinder operation, the valve stop mechanism 25b is operated by hydraulic pressure, and thereby, intake and exhaust of the first and fourth cylinders # 1 and # 4 among all the cylinders. The opening / closing operation of the valves 14 and 15 is stopped.

  In this example, the valve stop mechanism 25b is incorporated in the HLA 25 with a valve stop mechanism as described above. That is, the HLA 25 with a valve stop mechanism includes a pivot mechanism body 25a and a valve stop mechanism 25b. The pivot mechanism body 25a has substantially the same configuration as the HLA 24 that automatically adjusts the valve clearance to zero by hydraulic pressure.

  As shown in FIG. 2A, the valve stop mechanism 25b is provided opposite to the bottomed outer cylinder 251 in which the pivot mechanism main body 25a is slidably accommodated in the axial direction and the peripheral side wall of the outer cylinder 251. A pair of lock pins 252 provided to be able to enter and exit each of the two through holes 251a, a lock spring 253 for urging the pair of lock pins 252 radially outward, an inner bottom portion of the outer cylinder 251 and the pivot mechanism body 25a. And a lost motion spring 254 that biases the pivot mechanism main body 25a upward.

  The pair of lock pins 252 are spaced apart from each other and inserted into the through-holes 251a with their tips protruding from the inside of the outer cylinder 251, and an approach position protruding from the through-holes 251a to the inside of the outer cylinder 251. Can be displaced. When the pair of lock pins 252 are arranged at the separated positions by the urging force of the lock spring 253 with the pivot mechanism main body 25a protruding upward from the outer cylinder 251, as shown in FIG. 2A, the pivot mechanism The vertical movement of the main body 25a is restricted (referred to as the pivot mechanism main body 25a being locked). On the other hand, as shown in FIG. 2B, the hydraulic pressure (indicated by the black arrow in the figure) supplied through the oil passages 65 (75) and 67 (77) resists the elastic force of the lock spring 253. When the pair of lock pins 252 are arranged at the approach position, as shown in FIG. 2C, the pair of lock pins 252 can move up and down in the outer cylinder 251 together with the pivot mechanism body 25a ( This is referred to as the unlocked state of the pivot mechanism body 25a).

  That is, in the locked state of the pivot mechanism main body 25a shown in FIG. 2A, the top of the pivot mechanism main body 25a protruding from the outer cylinder 251 serves as a pivot for swinging the swing arms 20 and 21. Therefore, when the cam portions 18a and 19a press the cam followers 20a and 21a by the rotation of the cam shafts 18 and 19, the intake and exhaust valves 14 and 15 are pressed against the urging force of the return springs 16 and 17, and the ports 12, 13 opens. Therefore, the entire cylinder operation of the engine 1 can be performed by setting the valve stop mechanism 25b to the locked state for the first and fourth cylinders # 1 and # 4.

  On the other hand, in the unlocked state of the pivot mechanism main body 25a shown in FIG. 2B, the pivot mechanism main body 25a can move in the vertical direction (axial direction) in the outer cylinder 251, thereby stopping the opening / closing operation of the intake and exhaust valves 14, 15. Is done. That is, the urging force of the lost motion spring 254 is set to be smaller than the urging force of the return springs 16 and 17 that urge the intake and exhaust valves 14 and 15, and in the unlocked state of the pivot mechanism body 25a, the cam follower When the cam portions 18a and 19a are pushed down by the cam portions 18a and 19a, the top portions of the intake and exhaust valves 14 and 15 serve as fulcrums of the swing arms 20 and 21, and the pivot mechanism main body resists the urging force of the lost motion spring 254. 25a will be pressed. Therefore, the intake / exhaust valves 14 and 15 are not displaced, and the ports 12 and 13 are kept closed. Therefore, the cylinder stop operation of the engine 1 can be performed when the valve stop mechanism 25b is unlocked for the first and fourth cylinders # 1 and # 4.

<Configuration of hydraulic pressure supply device 2>
Next, the hydraulic pressure supply device 2 for supplying oil to each part of the engine 1 will be described in detail with reference to FIG.

  The hydraulic pressure supply device 2 includes an oil pump (not shown) that is driven by rotation of the crankshaft 9, and oil that has been boosted by the oil pump as oil for the hydraulic operating device of the engine 1, the lubricated portion, and the cooled portion. And an oil supply path 50 that leads to the supply unit.

  The oil supply passage 50 includes pipes, passages formed in the cam cover 3, the cylinder head 4, and the cylinder block 5. FIG. 1 shows an oil passage provided mainly in the cylinder head 4 in the oil supply passage 50.

  The oil supply passage 50 includes a first communication path 52 extending to the cylinder head 4 via a main gallery (not shown) in the cylinder head 4 and a front end portion (end portion on the first cylinder side) in the cylinder head 4 on the intake side. And a second communication passage 53 extending in the engine width direction from the exhaust side to the exhaust side, and a plurality of oil passages described later extending from the second communication passage 53. The main gallery is an oil passage through which oil is constantly supplied while the engine 1 is being driven.

  The cylinder head 4 includes an oil passage 61 that branches from the second communication passage 53 at a branch point 53c and extends in a cylinder row direction at a predetermined position on the intake side (first oil passage (intake-side first oil passage of the present invention)). And an oil passage 62 (a first oil passage (exhaust side first oil passage) of the present invention) that branches from the second communication passage 53 at a branch point 53a and extends in a cylinder row direction at a predetermined position on the exhaust side. Corresponding). These oil passages 61 and 62 are provided in parallel to each other.

  The oil passage 61 on the intake side includes an oil supply portion 54 (see a white triangle (Δ) in FIG. 3) for cam journal lubrication of the camshaft 18 on the intake side, and the HLA 24 (black triangle (see FIG. 3)). )) And an HLA 25 with a valve stop mechanism (see the white oval in FIG. 3). The cylinder head 4 is further provided with an oil passage 63 that branches from the branch point 61a of the oil passage 61 and extends in the cylinder row direction. The oil passage 63 supplies lubricating oil to the swing arm 20 on the intake side. 28. Oil is always supplied to the oil passages 61 and 63 while the engine 1 is driven.

  Similarly, the oil passage 62 on the exhaust side includes an oil supply portion 55 (see a white triangle (Δ) in FIG. 3) for lubricating the cam journal of the camshaft 18 on the exhaust side, and the above-described oil passage 62. It is connected to HLA 24 (see black triangle (三角) in FIG. 3) and HLA 25 with a valve stop mechanism (see white oval in FIG. 3). The cylinder head 4 is provided with an oil passage 64 that branches off from a branch point 62a of the oil passage 62 and extends in the cylinder row direction. The oil passage 64 supplies the lubricating oil to the exhaust-side swing arm 20 with a shower nozzle 29. It is connected to the. Oil is constantly supplied to these oil passages 62 and 64 while the engine 1 is driven.

  The cylinder head 4 extends in the cylinder row direction along the oil passage 61 at a position on the front side (right side in FIG. 3) and the intake side, and the valve on the intake valve 14 side of the first cylinder # 1. Corresponding to the oil passage 65 (the second oil passage (the intake-side front end second oil passage) of the present invention) connected to the valve stop mechanism 25b (corresponding to the intake-side first valve stop mechanism of the present invention) of the HLA 25 with a stop mechanism. When this is done, the oil passage 65 branches to the exhaust side and extends in the cylinder row direction. The valve stop mechanism 25b of the HLA 25 with the valve stop mechanism on the exhaust valve 15 side of the first cylinder # 1 (the exhaust side of the present invention) An oil passage 67 (corresponding to the second oil passage (exhaust side front end second oil passage) of the present invention) connected to the one-valve stop mechanism is provided. The oil passage 65 is connected to an oil passage 70 branched from the second communication passage 53 at a branch point 53b via a first direction switching valve 56 (corresponding to a control valve of the present invention). By the switching control of the direction switching valve 56, oil is supplied to and stopped from each valve stop mechanism 25b of the first cylinder # 1.

  As shown in FIGS. 1 and 4, the oil passage 65 on the intake side is provided close to the lower side of the oil passage 61 and in parallel with the oil passage 65. These oil passages 61 and 65 are located between the first cylinder # 1 and the second cylinder # 2, and are connected to the communication passage 66 (the communication oil passage (the intake-side first connection oil passage of the present invention) provided with the orifice unit 30A. ) Corresponding to each other). The same applies to the oil passage 67 on the exhaust side, and the oil passage 67 is provided close to the lower side of the oil passage 62 and in parallel with the oil passage 62. The first cylinder # 1 and the second cylinder It is connected to the oil passage 62 through a communication passage 68 (corresponding to a communication oil passage (exhaust side first connection oil passage) of the present invention) provided with the orifice unit 30B at a position between the cylinder # 2. .

  Further, the cylinder head 4 extends in the cylinder row direction along the oil passage 61 at the rear side (left side in FIG. 3) and the intake side, and is located on the intake valve 14 side of the fourth cylinder # 4. The oil passage 75 (the second oil passage of the present invention (the intake side rear end second oil passage) of the present invention is connected to the valve stop mechanism 25b of the HLA 25 with the valve stop mechanism (corresponding to the intake side second valve stop mechanism of the present invention). )) And the valve stop mechanism 25b of the HLA 25 with the valve stop mechanism on the exhaust valve 15 side of the fourth cylinder # 4 (in the present invention). An oil passage 77 (corresponding to the second oil passage (exhaust side rear end second oil passage) of the present invention) connected to the exhaust side second valve stop mechanism) is provided. The oil passage 75 is connected to the oil passage 72 via a second direction switching valve 57 (corresponding to the control valve of the present invention). By the switching control of the second direction switching valve 57, the fourth cylinder # The oil is supplied to and stopped from each of the four valve stop mechanisms 25b. The oil passage 72 is formed to branch from a branch point 53d on the second communication passage 53 and extend in the cylinder row direction, and further extend in the engine width direction at a position near the rear end of the cylinder head 4.

  As shown in FIGS. 1 and 4, the oil passage 75 on the intake side is provided close to the lower side of the oil passage 61 and in parallel with the oil passage 61. These oil passages 61 and 75 are located between the third cylinder # 3 and the fourth cylinder # 4, and are connected to the communication passage 76 (the communication oil passage (the intake-side second connection oil passage of the present invention) provided with the orifice unit 31A. ) Corresponding to each other). The same applies to the oil passage 77 on the exhaust side, and the oil passage 77 is provided in close proximity to the lower side of the oil passage 62 and in parallel with the oil passage 62. It is connected to the oil passage 62 through a communication passage 78 (corresponding to the communication oil passage (exhaust side second connection oil passage) of the present invention) provided with the orifice unit 31B at a position between the cylinder # 4. .

  The end of the oil passage 62 on the rear side of the fourth cylinder # 4 is an oil supply portion 59 for supplying lubricating oil to a bearing of a vacuum pump (not shown), and lubricating oil to the journal of the fuel pump. Are connected to oil supply portions 58 for supplying the oil.

  The lubricating and cooling oil supplied to the lubricated and cooled parts by the shower nozzles 28, 29, etc., after cooling and lubrication are dropped into the oil pan and recirculated by the oil pump. Is done.

<Configuration of Orifice Unit 30A (30B, 31A, 31B)>
FIG. 5 is a cross-sectional view of the orifice unit incorporated in the cylinder head 4. More specifically, FIG. 5 is a diagram showing the connection between the oil passages 61 and 65 at a position between the first cylinder # 1 and the second cylinder # 2. 4 is a sectional view of an orifice unit 30A provided in a passage 66. FIG.

  As shown in the figure, the communication passage 66 is a hole that penetrates the oil passage 61 in the vertical direction from the position of the oil passage 65 and opens to the upper surface of the cylinder head. The orifice unit 30A is connected to the oil passages 61, 65. It is fixed to the cylinder head 4 in a state of being inserted into the communication path 66 (hole) so as to straddle. Specifically, the orifice unit 30A includes a substantially cylindrical unit main body 31 extending in the vertical direction and a blind plug 32 (corresponding to the fixing member of the present invention), and the unit main body 31 is inserted into the communication path 66. The orifice body 30 </ b> A is fixed to the cylinder head 4 by screwing the blind plug 32 into the opening portion of the communication path 66 while the unit body 31 is pressed from above by the blind plug 32.

  The unit main body 31 includes a substantially cylindrical orifice holder 36 that includes a ceiling wall portion 37 and a peripheral wall portion 38 and that extends in the vertical direction, and an orifice 42 that is disposed inside and held by the orifice holder 36. .

  A cylindrical protrusion 44 protruding outward in the radial direction is provided in the middle part of the peripheral wall 38 of the orifice holder 36 in the vertical direction. The projecting portion 44 is in contact with the inner peripheral surface of the communication passage 66 at a position between the oil passage 61 and the oil passage 65, so that the unit body 31 is in a posture along the center line of the communication passage 66. It is supported. A space between the outer peripheral surface of the protruding portion 44 and the inner peripheral surface of the communication path 66 is oil-tightly sealed by a seal member 44a.

  A plurality of slit-shaped openings 38a extending in the vertical direction are provided at equal intervals in the circumferential direction on the portion of the peripheral wall portion 38 of the orifice holder 36 above the projecting portion 44, that is, on the oil passage 61 side. A cylindrical mesh filter 40 is disposed inside the peripheral wall portion 38 along the inner peripheral surface of the peripheral wall portion 38 so as to close the openings 38a.

  The orifice 42 is a cylindrical body having a small-diameter passage 42a extending straight in the vertical direction, and the peripheral wall 38 and the peripheral wall 38 are connected to the inside of the peripheral wall 38 via an annular support member 46 made of a metal material. Is held with a predetermined gap between them. The total length of the orifice 42 and the inner diameter of the small-diameter passage 42a are dimensions that allow the oil in the oil passage 61 to be introduced into the oil passage 65 while sufficiently reducing the pressure (hydraulic pressure) during operation of all cylinders of the engine 1. Are set to dimensions that can be introduced into the oil passage 65 while being reduced to a pressure lower than the operating pressure of the valve stop mechanism 25b of the HLA 25 with the valve stop mechanism. That is, during the all cylinder operation of the engine 1, as shown in FIG. 6 (solid arrow), part of the oil in the oil passage 61 is introduced into the inside of the unit body 31 through the opening 38a and the mesh filter 40, and the orifice 42 is After flowing from the upper end toward the lower end, the oil is introduced into the oil passage 65 from the lower end of the orifice holder 36 (orifice unit 30A). At this time, the oil is introduced into the oil passage 65 while being reduced in pressure by passing through the narrow passage 42 a of the orifice 42.

  Note that an air vent portion Ab for releasing the air in the oil passage 61 and the air contained in the oil to the outside is provided at the upper portion of the orifice unit 30A. The air vent portion Ab has the following configuration.

  The ceiling wall portion 37 of the orifice holder 36 is provided with an air vent hole 37c (corresponding to the second air vent hole of the present invention) having a circular opening at the center thereof, which is indicated by a one-dot chain line in FIG. As shown in FIG. 4, the air that has entered the unit main body 31 together with the oil can escape to the outside of the unit main body 31 through the air vent hole 37c.

  A mesh filter 39 is provided inside the air vent hole 37c. The mesh filter 39 has, for example, a mesh equivalent to the mesh filter 40 provided on the peripheral wall portion 38.

  On the other hand, in the blind plug 32, the air that has escaped from the unit body 31 to the outside through the air vent hole 37c is further defined as a closed space (hereinafter simply referred to as the outside of the cylinder head 4) formed between the cylinder head 4 and the cam cover 3. ) Is provided with an air vent hole 34 for escape. The air vent hole 34 communicates a concave section 34 a having a circular cross section formed in the lower surface 32 a of the blind plug 32, and a space in the concave section 34 a and a space in the tool hole 33 formed in the upper surface of the blind plug 32. It is composed of a narrow passage 34b. That is, as shown by a one-dot chain line in FIG. 6, the air that has escaped from the unit body 31 through the air vent hole 37 c is released from the tool hole 33 to the outside of the cylinder head 4 through the air vent hole 34 of the blind plug 32. It has become so.

  The upper surface 37a of the orifice holder 36 (ceiling wall portion 37) has a truncated cone shape as shown in FIG. A plurality of radial ribs 37b protruding upward from the upper surface 37a and abutting against the lower surface 32a of the blind plug 32 are provided at a plurality of positions in the circumferential direction of the upper surface 37a, and the lower surface of the blind plug 32 is provided by these ribs 37b. A gap S is formed between 32a and the upper surface 37a of the unit body 31 (blind plug 32). With this configuration, the air in the oil passage 61 can be guided to the air vent hole 34 of the blind plug 32 without passing through the inside of the unit body 31 as indicated by the broken line arrow in FIG. Yes.

  The diameter R1 of the concave portion 34a of the blind plug 32 is appropriately larger than the diameter R2 of the smallest diameter portion (uppermost end surface) of the frustoconical upper surface 37a of the orifice holder 36. A tapered surface 35 substantially parallel to the inclined surface portion 37a is formed. The unit main body 31 is disposed in the communication path 66 so that the gap S is located above the uppermost part of the oil passage 61.

  As described above, the air vent portion Ab includes the gap S formed between the lower surface 32a of the blind plug 32 and the upper surface 37a of the unit body 31 (orifice holder 36) and the air vent hole 34 formed in the blind plug 32. And an air vent hole 37c that is formed in the ceiling wall portion 37 of the unit main body 31 and joins the air introduced into the unit main body 31 to the air vent hole 34. Yes.

  Although the configuration of the orifice unit 30A has been described above, the other orifice units 30B, 31A, and 31B have the same configuration as the orifice unit 30A.

<Operation effect of hydraulic pressure supply device 2>
In the hydraulic pressure supply device 2, during the operation of the engine 1, the oil stored in the oil pan is pumped up by the operation of the oil pump and introduced into the second communication passage 53 through the first communication passage 52. It is introduced into each oil passage 61, 62, 70, 72 from the communication passage 53.

  By introducing the oil into the oil passages 61 and 62 in this way, the oil is supplied to the intake side and exhaust side HLA 24 and 25 (for the HLA 25, the pivot mechanism body 25a), and the intake valve 14 and the exhaust gas are supplied. The valve clearance of the valve 15 is automatically adjusted to zero.

  During the all-cylinder operation of the engine 1, the first directional switching valve 56 and the second directional control valve 56 are configured so that the oil passage 65 (67) is cut off from the oil passage 70 and the oil passage 75 (77) is cut off from the oil passage 72. The direction switching valve 57 is controlled (the valve is controlled in a state opposite to the state shown in FIG. 3). As a result, the oil supply to the valve stop mechanism 25b of each HLA 25 on the intake side and the exhaust side is stopped, and the valve stop mechanism 25b is stopped. That is, the pivot mechanism main body 25a is kept in the locked state (the state shown in FIG. 2A), whereby the intake valve 14 and the exhaust valve 15 are operated as the camshafts 18 and 19 rotate.

  On the other hand, during the reduced-cylinder operation of the engine 1, that is, when the first and fourth cylinders # 1 and # 4 are stopped, the oil passage 65 (67) and the oil passage 70 communicate with each other and the oil passage 75 (77 ) And the oil passage 72 are in communication with each other, the first direction switching valve 56 and the second direction switching valve 57 are controlled (the valves are controlled to the state shown in FIG. 3). As a result, oil is supplied to the valve stop mechanisms 25b of the intake side and exhaust side HLA 25, and the valve stop mechanism 25b is activated. That is, the pivot mechanism main body 25a is brought into the unlocked state (the state shown in FIG. 2B), whereby the operations of the intake valve 14 and the exhaust valve 15 are stopped.

  By the way, when the engine 1 is operated for all cylinders for a long period of time, the oil in the oil passages 65 and 67 and the oil passages 75 and 77 flows into the drain oil passage through the gap between the HLA 25 and the mounting holes 26 and 27. Due to the return, the oil in the oil passages 65 and 67 and the oil passages 75 and 77 decreases, and thereafter, when the engine 1 shifts from the all-cylinder operation to the reduced-cylinder operation, a response delay may occur in the valve stop mechanism 25b. Conceivable.

  However, in this hydraulic pressure supply device 2, the oil passages 65, 75 on the intake side are connected to the oil passage 61 via communication passages 66, 76 provided with orifice units 30 A, 31 A, and the exhaust side oil passages 65, 75 are also connected to the exhaust side. Similarly, the oil passages 67 and 77 are connected to the oil passage 62 via communication passages 68 and 78 having orifice units 30B and 31B. Therefore, during the entire cylinder operation of the engine 1, the oil in the oil passage 61 on the intake side is gradually introduced into the oil passages 65 and 75 while being depressurized through the orifice units 30A and 31A. The valve stop mechanism 25b is kept in a stopped state while 75 is filled with oil. Similarly, in the exhaust-side passages 67 and 77, the valve stop mechanism 25b is kept stopped while the oil passages 67 and 77 are filled with oil. Therefore, when the engine 1 is shifted from the all-cylinder operation to the reduced-cylinder operation, the operation pressure is quickly applied to each valve stop mechanism 25b in accordance with the switching of each direction switching valve 56, 57. As a result, the valve stop mechanism 25b Will operate promptly. Therefore, according to this hydraulic pressure supply device 2, it is possible to smoothly perform the transition from the all-cylinder operation to the reduced-cylinder operation of the engine 1 without a response delay of the valve stop mechanism 25b.

  Moreover, according to the hydraulic pressure supply device 2, the air vent portion Ab is provided above the orifice units 30A, 30B, 31A, and 31B, so that even when the engine has been stopped for a long time, the valve is stopped. The occurrence of malfunction in the mechanism 25b is effectively suppressed. That is, when the engine has been stopped for a long period of time, the oil in the oil passages 61 and 62 is reduced due to the return of oil, and air is accumulated. When the engine 1 is started in this state, for example, air accumulated in the intake-side oil passage 61 is pushed by the oil and introduced into the intake-side oil passages 65 and 75 through the orifice units 30A and 31A. At this time, since the viscosity of air is lower than that of oil, it is considered that the valve stop mechanism 25b malfunctions as a result of air being introduced into the oil passages 65 and 75 through the orifice units 30A and 31A without being decompressed. Similarly, in the exhaust-side passages 67 and 77, the air accumulated in the exhaust-side oil passage 62 is pushed by the oil and introduced into the oil passages 67 and 77 through the orifice units 30B and 31B. It is conceivable that 25b malfunctions.

  However, according to the hydraulic pressure supply device 2 in which the air vents Ab are provided in the orifice units 30A, 30B, 31A, 31B, when oil is supplied to the oil passages 61, 62 as the engine 1 starts. The air accumulated in the oil passages 61 and 62 is pushed by the oil and escapes to the outside of the cylinder head 4 through the air vents Ab of the orifice units 30A, 30B, 31A and 31B. Specifically, as indicated by a broken line arrow in FIG. 6, the cylinder head 4 passes through the clearance S between the upper surface 37 a of the unit body 31 (orifice holder 36) and the lower surface 32 a of the blind plug 32 and the air vent hole 34 of the blind plug 32. Will escape to the outside. Therefore, according to this hydraulic pressure supply device 2, it is possible to effectively suppress the malfunction of the valve stop mechanism 25b caused by the air accumulated in the oil passages 61 and 62.

  In particular, the unit main bodies 31 of the orifice units 30A, 30B, 31A, 31B are arranged in the communication passage 66 so that the gap S is located above the uppermost part of the oil passages 61, 62. , 62 can efficiently escape to the outside. In other words, the air in the oil passages 61 and 62 moves mainly along the ceiling side wall surface of the oil passages 61 and 62 with the supply of oil. Thus, the air is smoothly introduced into the air vent hole 34 of the blind plug 32. In this case, the upper surface 37a of the unit main body 31 (orifice holder 36) that forms the gap S is formed in a truncated cone shape, so that air is smoothly introduced into the air vent hole 34 along the slope of the upper surface 37a. (See the broken line arrow in FIG. 6). Therefore, according to the hydraulic pressure supply device 2, the air accumulated in the oil passages 61 and 62 can be released to the outside of the cylinder head 4 while being efficiently guided to the air vent hole 34.

  Further, the unit main body 31 (orifice holder 36) of the orifice units 30A, 30B, 31A, 31B has an air vent hole 37c in the ceiling wall portion 37, and the air introduced into the unit main body 31 together with the oil is supplied. It is possible to escape above the unit main body 31 through the air vent hole 37c. Therefore, according to this hydraulic pressure supply device 2, the introduction of air into the oil passages 65, 67, 75, 77 can be suppressed to a higher level, and the malfunction of the valve stop mechanism 25b can be further increased. There is an advantage that it can be suppressed.

  Further, in the hydraulic pressure supply device 2, as described above, since the air vents Ab are provided in each of the four orifice units 30A, 30B, 31A, and 31B, the air accumulated in the oil passages 61 and 62 is more reliably collected. There is an advantage that it can escape to the outside. For example, in FIG. 4, (1) an intermediate portion of the oil passage 61 in the engine longitudinal direction (intermediate portion of the orifice units 30A and 31A), (2) a rear end portion of the oil passage 61 (rear side of the orifice unit 31A), (3) It is also conceivable to provide an air vent at any position in the front end of the oil passage 61 (the front side of the orifice unit 30A). However, when an air vent is provided in the middle of the oil passage 61, the oil is supplied to the oil passage 61 as the engine 1 starts, and when this oil exceeds the position of the air vent, Air behind the position loses its place and is introduced into the oil passage 75 through the orifice unit 31A. Further, when an air vent is provided at the rear end portion of the oil passage 61, for example, when the vehicle is stopped in a state where the engine 1 is rearwardly lowered, residual oil in the oil passage 61 is removed from the oil passage 61. When the oil is supplied to the oil passage 61 as the engine 1 is started, the lost air is introduced into the oil passages 65 and 75 through the orifice units 30A and 31A. Will be. Further, when an air vent is provided at the front end of the oil passage 61, when the oil is supplied to the oil passage 61 as the engine 1 is started, the oil is positioned at a relatively early timing. Therefore, a large amount of residual air loses its place and is introduced into the oil passages 65 and 75 through the orifice units 30A and 31A. Therefore, even if the air vent is provided at any of the positions (1) to (3), it may be difficult to suppress the intrusion of air into the oil passages 65 and 75. This also applies to the oil passage 62 on the exhaust side.

  However, according to the configuration of the hydraulic pressure supply device 2 in which the air bleeding portion Ab is provided in each of the orifice units 30A, 30B, 31A, 31B, the air bleeding portion is located at any one of the positions (1) to (3). In comparison with the case where the air is provided, it is difficult for the air in the oil passages 61 and 62 to lose its place. Therefore, according to the hydraulic pressure supply device 2, the air accumulated in the oil passages 61 and 62 is more reliably collected. It is possible to escape to the outside of the cylinder head 4.

<Other configurations>
The above-described hydraulic pressure supply device 2 is an example of a preferred embodiment of the hydraulic pressure supply device according to the present invention, and the specific configuration thereof can be appropriately changed without departing from the gist of the present invention.

  For example, in the above-described embodiment, this configuration is used as a configuration for suppressing malfunction of the valve stop mechanism 25b caused by air intrusion into the oil passages 65, 67, 75, and 77 for supplying oil to the valve stop mechanism 25b. Although the invention is applied, of course, the present invention may be applied as a configuration for suppressing a malfunction of a hydraulic actuator other than the valve stop mechanism 25b.

  In addition, the specific configuration of the air vent is not limited to that described above, and any configuration that allows air to escape from the top of each orifice unit 30A, 30B, 31A, 31B may be used.

  Further, in the hydraulic pressure supply device 2, the communication passages 66 and 68 including the orifice units 30 </ b> A and 30 </ b> B are in the oil flow direction of the oil passages 65 and 67 (the oil flow direction when the first direction switching valve 56 is opened). Is provided at a position immediately downstream of the valve stop mechanism 25b, that is, a position between the first cylinder # 1 and the second cylinder # 2, but may be provided at other positions. Similarly, the communication passages 76 and 78 including the orifice units 31A and 31B are connected to the valve stop mechanism 25b in the oil flow direction of the oil passages 75 and 77 (the oil flow direction when the second direction switching valve 57 is opened). Although it is provided at a position immediately downstream, that is, a position between the third cylinder # 3 and the fourth cylinder # 4, it may be provided other than this. However, when the communication passages 66, 68, 76, 78 are provided at the positions of the above embodiment, the distance from the oil passage 61 to the position of each valve stop mechanism 25 b of the oil passages 65, 75 and the oil passage 62. Since the distance from the oil passages 67 and 77 to the positions of the valve stop mechanisms 25b is as short as possible, the oil passages 65, 67, 75, and 77 are more reliably filled with oil at the positions of the valve stop mechanisms 25b. It becomes possible. Therefore, it is advantageous in improving the responsiveness of each valve stop mechanism 25b.

1 Multi-cylinder engine 2 Hydraulic supply device 24 Hydraulic lash adjuster 25 Hydraulic lash adjuster with valve stop mechanism 25a Pivot mechanism body 25b Valve stop mechanism (hydraulic actuator)
50 Oil supply passage 56 First direction switching valve (control valve)
57 Second direction switching valve (control valve)
61 oil passage (first oil passage / intake side first oil passage)
62 oil passage (first oil passage / exhaust side first oil passage)
65 oil passage (second oil passage / intake side front end second oil passage)
66 Communication path (connected oil passage / intake-side first connected oil passage)
67 Oil passage (second oil passage / exhaust side front end second oil passage)
68 Communication path (connected oil passage / exhaust side first connected oil passage)
75 oil passage (second oil passage / intake side rear end second oil passage)
76 Communication path (Linked oil passage / Intake side second connected oil passage)
77 Oil passage (second oil passage / exhaust side rear end second oil passage)
78 Communication path (Linked oil passage / Exhaust side second connected oil passage)

Claims (7)

A hydraulic supply device for a multi-cylinder engine having a hydraulic actuator that operates under specific conditions during engine operation,
A first oil passage to which hydraulic oil is constantly supplied during engine operation;
A second oil passage that communicates with the hydraulic actuator and is supplied with hydraulic oil by opening a control valve when the specific condition is satisfied;
An oil passage connecting the first oil passage and the second oil passage, and when the control valve is closed, the hydraulic oil in the first oil passage reduces the pressure of the second oil passage. A connecting oil passage provided with an orifice unit on the way to allow introduction into the passage,
The orifice supply unit is provided with an air vent for allowing air to escape to the outside. The hydraulic pressure supply device according to claim 1,
The hydraulic actuator is a valve supply mechanism that stops at least one of an intake valve and an exhaust valve of a part of a plurality of cylinders. The hydraulic pressure supply apparatus according to claim 2,
The engine includes hydraulically operated lash adjusters corresponding to the intake valves and exhaust valves of all the cylinders,
The valve stop mechanism is incorporated in the lash adjuster of some cylinders,
The first oil passage supplies hydraulic oil to the lash adjuster and extends in the cylinder row direction.
The second oil passage extends in the cylinder row direction at a position below the first oil passage,
The connecting oil passage communicates the first oil passage with the second oil passage by extending in the vertical direction through the first oil passage,
The orifice unit is disposed in the connecting oil passage in a state straddling the first oil passage and the second oil passage, and includes the air vent portion at an upper portion thereof. apparatus. In the hydraulic pressure supply device according to claim 3,
The orifice unit includes a unit main body, and a fixing member that fixes the unit main body in a state where the unit main body is pressed from above into the connection oil passage.
The air vent part includes a gap formed between the fixing member and the unit main body and an air vent passage formed by a first air vent hole formed in the fixing member. . The hydraulic pressure supply device according to claim 4,
The air bleed portion includes a second air bleed hole that is formed in a ceiling wall portion of the unit main body and joins air that has entered the unit main body into the first air bleed hole. Hydraulic supply device. The hydraulic pressure supply device according to any one of claims 3 to 5,
When one end side in the cylinder row direction of the engine is defined as front and the other end side is defined as rear,
The valve stop mechanism includes an intake side first valve stop mechanism for stopping an intake valve of a front end cylinder located at a front end in a cylinder row direction, an exhaust side first valve stop mechanism for stopping an exhaust valve of the front end cylinder, and a cylinder An intake side second valve stop mechanism for stopping the intake valve of the rear end cylinder located at the rear end in the column direction, and an exhaust side second valve stop mechanism for stopping the exhaust valve of the rear end cylinder;
The first oil passage includes an intake-side first oil passage that supplies hydraulic oil to the lash adjusters of the intake valves of all cylinders, and an exhaust-side first oil that supplies hydraulic oil to the lash adjusters of the exhaust valves of all cylinders. Including roads,
The second oil passage includes an intake-side front end second oil passage that supplies hydraulic oil to the intake-side first valve stop mechanism, and an exhaust-side front end second oil that supplies hydraulic oil to the exhaust-side first valve stop mechanism. An intake side rear end second oil passage for supplying hydraulic oil to the intake side second valve stop mechanism, and an exhaust side rear end second oil passage for supplying hydraulic oil to the exhaust side second valve stop mechanism; Including
The connection oil passage includes an intake side first connection oil passage connecting the intake side first oil passage and the intake side front end second oil passage, the exhaust side first oil passage and the exhaust side front end second oil passage, An exhaust side first connection oil passage that communicates with the intake side, an intake side second connection oil passage that communicates the intake side first oil passage and the intake side rear end second oil passage, and the exhaust side first oil passage and the exhaust. An exhaust side second connecting oil passage communicating with the side rear end second oil passage,
The hydraulic pressure supply device, wherein each of the connecting oil passages is provided with the orifice unit. The hydraulic pressure supply apparatus according to claim 6,
Each of the front end second oil passages flows from the front end side to the rear end side by opening the control valve, and each of the rear end second oil passages is opened by opening the control valve. The hydraulic oil flows from the rear end side toward the front end side,
Each of the first connection oil passages is provided at a position immediately downstream of each of the first valve stop mechanisms in the flow direction of the hydraulic oil, and each of the second connection oil passages is each of the first connection oil passages in the flow direction of the hydraulic oil. A hydraulic pressure supply device provided at a position immediately downstream of the two-valve stop mechanism.

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