Cylinder head assembly, engine and vehicle

Abstract

This utility model provides a cylinder head assembly, an engine, and a vehicle. The cylinder head assembly includes a cylinder head and a first bearing housing, which together form a lubrication passage. The first bearing housing includes a first base, and the cylinder head includes a first support plate opposite to the first base. The lubrication passage includes a distribution oil passage formed between the first base and the first support plate. The distribution oil passage replaces the transverse oil passages formed within the cylinder head in the prior art, thus eliminating the need for drilling in the cylinder head to obtain the transverse oil passages. The wall thickness of the drilling area on the cylinder head, which was originally intended for the transverse oil passages, is no longer limited by the minimum wall thickness requirement of the transverse oil passages. Therefore, the wall thickness of the machining area on the cylinder head, which was originally intended for the transverse oil passages, can be reduced along the length of the cylinder head, thereby reducing the length of the cylinder head and enabling the miniaturization of the engine equipped with the cylinder head assembly.

Description

Technical Field

[0001] This utility model relates to the field of transportation technology, and in particular to a cylinder head assembly, an engine, and a vehicle. Background Technology

[0002] Engine downsizing is an important design concept, aiming to make engines easier to place in the engine compartment by reducing their size. One of the keys to engine downsizing is reducing the length of the cylinder head. However, due to the need to balance structural strength, durability, and proper lubrication, existing engine lubrication systems cannot achieve the goal of reducing cylinder head size through traditional methods such as thinning the oil passage walls or adjusting the oil passage position. Utility Model Content

[0003] In view of this, the present invention provides a cylinder head assembly, an engine and a vehicle, the present invention being designed to reduce the length of the cylinder head in order to achieve engine miniaturization.

[0004] The cylinder head assembly of this utility model includes a cylinder head and a first bearing housing. The cylinder head and the first bearing housing form a lubrication oil passage. The first bearing housing includes a first base. The cylinder head includes a first support plate disposed opposite to the first base. The lubrication oil passage includes a distribution oil passage formed between the first base and the first support plate.

[0005] The beneficial effects of the cylinder head assembly of this utility model are:

[0006] The oil distribution passage replaces the lateral oil passages opened in the cylinder head in the existing technology. Therefore, it is not necessary to drill holes in the cylinder head to obtain the lateral oil passage. The wall thickness of the part of the cylinder head that was originally used as the lateral oil passage is no longer limited by the minimum wall thickness of the lateral oil passage. As a result, the wall thickness of the part of the cylinder head that was originally used as the lateral oil passage can be reduced along the length of the cylinder head. The length of the cylinder head can thus be reduced, thereby enabling the engine equipped with the cylinder head assembly to be miniaturized.

[0007] In some embodiments, the first base includes a first base surface disposed toward the first support, the first base surface having an oil guide groove recessed therein, the oil guide groove forming the oil supply channel.

[0008] With this configuration, the oil supply passage is transferred from the cylinder head to the first bearing housing. Compared to the transverse oil passage in the prior art, the oil supply passage is raised significantly, so there is no need to perform subtractive processing on the cylinder head. The wall thickness of the cylinder head can be further reduced, and the length dimension of the cylinder head can be further reduced. Compared to subtractive processing on the cylinder head, machining the oil guide groove on the first bearing housing is simpler, requires simpler tooling, shortens the machining time, and reduces the difficulty.

[0009] In some embodiments, the first base surface and the first bearing platform are fitted together to form a surface seal.

[0010] With this configuration, the sealing gasket between the cylinder head and the first bearing housing is eliminated, and the opening of the oil guide groove is directly closed by the first bearing platform, thus forming an oil distribution passage.

[0011] In some embodiments, the first base surface and the first support are in planar contact.

[0012] With this configuration, the side of the first base surface that is in contact with the first bearing platform is easy to process, and the two are evenly bonded together, resulting in a good planar sealing effect.

[0013] In some embodiments, the oil guide groove is a cast groove recessed on the first base surface, and the first base is also recessed with a weight reduction groove. The wall thickness of the oil guide groove on the side away from the weight reduction groove is equal to the wall thickness of the weight reduction groove on the side away from the oil guide groove, and is equal to the wall thickness between the oil guide groove and the weight reduction groove.

[0014] This design reduces the weight of the first bearing housing, which is beneficial for the lightweighting of the cylinder head assembly and engine. The oil guide groove has a uniform wall thickness, which avoids uneven shrinkage in different parts of the oil guide groove due to uneven wall thickness, and can ensure the shape and dimensional accuracy of the oil guide groove.

[0015] In some embodiments, the lubrication circuit further includes an oil supply passage opened in the cylinder head, and the first support has an oil inlet hole to connect the oil supply passage and the distribution passage. The distribution passage includes an inlet section and a distribution section. The inlet section is inclined relative to the distribution section and extends in a direction away from the outer side of the first base to connect the oil inlet hole.

[0016] With this configuration, the oil inlet connects the oil supply passage and the distribution passage. After the lubricating oil leaves the first bearing from the oil inlet, it can flow directly into the distribution passage. The appropriate position of the oil inlet ensures that the wall thickness of the oil supply passage is appropriate, preventing the oil supply passage from getting too close to the outer side of the cylinder head and reducing the wall thickness of the oil supply passage.

[0017] In some embodiments, the dispensing section includes a first clearance section, and the first support also has a fastening countersunk hole. The orthographic projection of the first clearance section on the first support is located outside the fastening countersunk hole, and the guiding section extends relative to the first clearance section in a direction away from the outside of the first support.

[0018] With this design, the first clearance section bypasses the fastening countersunk hole, thus ensuring that lubricating oil does not enter the fastening countersunk hole and preventing oil leakage from the cylinder head or cylinder block.

[0019] In some embodiments, the lubrication circuit further includes a turbocharger oil passage opened in the cylinder head, and the cylinder head further includes a turbocharger mounting portion located inside the first support. One end of the turbocharger oil passage is connected to the oil supply passage, and the other end passes through the turbocharger mounting portion.

[0020] With this configuration, the oil outlet formed by the turbocharger oil passage passing through the turbocharger mounting section is closer to the turbocharger, shortening the distance between the oil outlet and the turbocharger oil intake. Therefore, a shorter oil supply line can be used to connect the oil outlet and the turbocharger oil intake. The shortened oil supply line can improve the engine vibration amplitude, optimize the mode of the turbocharger and the oil supply line, and improve the engine's NVH performance.

[0021] In some embodiments, the cylinder head further includes a fastening platform forming the bottom of the fastening countersunk hole, the outer periphery of which is tangent to the inner wall of the fastening countersunk hole.

[0022] This configuration allows the first support to shift inwards to a greater extent along the length of the cylinder head, thus enabling a greater reduction in the size of the first base along the length of the cylinder head. This results in a significant reduction in the length of the cylinder head, which is beneficial for the miniaturization of the cylinder head assembly and the engine.

[0023] In some embodiments, the first bearing housing is further provided with a fastening through hole through which a bearing housing fastener passes. The cylinder head is connected to the first bearing housing via the bearing housing fastener. The lubrication circuit also includes a pressure relief oil passage communicating with the fastening through hole.

[0024] With this configuration, the pressure relief oil passage can serve as a channel for lubricating oil to flow out from the fastening through hole. The lubricating oil in the fastening through hole can be discharged in a timely manner through the pressure relief oil passage, preventing the lubricating oil from accumulating in the fastening through hole and eventually leaking out from the top opening of the fastening through hole.

[0025] In some embodiments, the pressure relief passage includes a first pressure relief groove recessed in the first base, the first pressure relief groove penetrating the side of the first bearing housing, and the supply passage further includes a second clearance section that bypasses the bearing housing fastener and is spaced apart from the first pressure relief groove.

[0026] With this configuration, the lubricating oil in the fastening through hole can be discharged in time through the first pressure relief groove and flow into the timing cover or cylinder body. The second clearance section and the first pressure relief groove are mutually isolated, which can prevent the lubricating oil from entering the fastening through hole directly from the distribution oil passage through the first pressure relief groove, and ensure that a certain oil pressure is maintained in the distribution oil passage so that the distribution oil passage can effectively supply and distribute the lubricating oil.

[0027] In some embodiments, the first pressure relief groove passes through the inner side of the first bearing housing, and the second clearance section passes between the bearing housing fastener and the outer side of the first bearing housing.

[0028] With this configuration, the lubricating oil in the fastening hole can be discharged in time through the first pressure relief groove and flow into the cylinder body, realizing the recycling of waste lubricating oil.

[0029] In some embodiments, the first bearing housing includes a first upper bearing housing and a first lower bearing housing having the first base, and the pressure relief oil passage further includes a second pressure relief groove and / or a third pressure relief groove, wherein the second pressure relief groove is located at the bottom of the first upper bearing housing and the third pressure relief groove is located at the top of the first lower bearing housing.

[0030] With this configuration, both the second and third pressure relief grooves form pressure relief oil channels, increasing the number of pressure relief oil channels based on the first pressure relief groove. This makes it easier and more thorough for the lubricating oil accumulated in the fastening through hole to be discharged outwards, further reducing the risk of oil leakage from the top opening of the fastening through hole.

[0031] In some embodiments, the lubrication passage further includes a journal channel formed in the first base, the journal channel connecting the oil supply passage to the bearing bore of the first bearing housing.

[0032] With this configuration, a portion of the lubricating oil in the distribution oil passage is distributed to the journal for lubricating and cooling the camshaft through the journal channel. Compared to the transverse oil passage in the cylinder head in the prior art, the distribution oil passage is closer to the bearing hole of the first bearing housing. Therefore, the journal channel connecting the distribution oil passage is shorter than the journal channel connecting the transverse oil passage in the prior art. Obviously, the oil intake path of the camshaft journal is shorter, and the lubricating oil can enter the bearing hole from the distribution oil passage through the journal channel more quickly.

[0033] In some embodiments, the lubrication circuit further includes a tappet oil passage opened in the cylinder head and a flow-limiting oil passage connecting the tappet oil passage and the distribution oil passage.

[0034] With this configuration, a portion of the lubricating oil in the distribution oil passage is distributed to the hydraulic tappet for lubrication through the flow-limiting oil passage and the tappet oil passage. The flow-limiting oil passage has a flow-limiting function, which allows the amount of lubricating oil entering the tappet oil passage to be precisely controlled, avoiding excessive lubricating oil. The flow-limiting oil passage can replace devices such as throttle valves, reducing the number of parts and assembly steps in the cylinder head assembly.

[0035] In some embodiments, the first bearing housing is further provided with a valve insertion hole for installing an oil control valve, and the lubrication circuit further includes a insertion hole oil passage provided in the first bearing housing, the insertion hole oil passage connecting the distribution oil passage and the valve insertion hole.

[0036] With this configuration, a portion of the lubricating oil in the distribution oil passage is distributed to the oil control valve in the valve port through the port oil passage. The oil control valve is part of the variable valve timing system. Compared to the port oil passage which connects to the transverse oil passage located in the cylinder head, the port oil passage connected to the distribution oil passage is shorter. This shortens the oil intake path of the oil control valve, allowing the lubricating oil to enter the oil control valve more quickly and improving the response speed of the variable valve timing system.

[0037] In some embodiments, the oil supply passage includes an oil collecting cavity, the insertion oil passage extends through the first base to connect the oil collecting cavity, and the flow-limiting oil passage extends through the first support to connect the oil collecting cavity.

[0038] With this design, the oil collecting chamber has the function of buffering and accumulating lubricating oil. When the amount of lubricating oil accumulated in the oil collecting chamber reaches a certain level and the oil pressure in the oil collecting chamber reaches a certain pressure value, the lubricating oil in the oil collecting chamber enters the insertion oil passage and the flow-limiting oil passage in two parts. This can ensure the flow rate of lubricating oil in the insertion oil passage and the flow-limiting oil passage, and realize the continuous and uninterrupted supply of lubricating oil to the oil control valve and hydraulic tappet.

[0039] In some embodiments, the first bearing housing is further provided with a fastening through hole through which a bearing housing fastener passes. The cylinder head is connected to the first bearing housing via the bearing housing fastener. The lubrication circuit also includes a pressure relief oil passage connecting the valve insertion hole and the fastening through hole.

[0040] With this design, the lubricating oil accumulated in the fastening orifice will not be wasted after flowing out through the pressure relief oil passage. Instead, it can enter the valve port and be used by the oil control valve, which improves the utilization rate of the lubricating oil and helps the oil control valve to work smoothly under conditions such as rapid vehicle acceleration.

[0041] The engine of this utility model includes a cylinder block, a camshaft, and a cylinder head assembly. The cylinder head is fixedly connected to the cylinder block, and the camshaft is rotatably mounted on the bearing housing.

[0042] The beneficial effects of the engine of this utility model are:

[0043] The wall thickness of the cylinder head can be reduced at the location where the transverse oil passages were originally drilled, thus reducing the length of the cylinder head. As a result, the length of the engine with the cylinder head assembly can be reduced, achieving engine miniaturization.

[0044] The vehicle of this utility model includes an engine. Attached Figure Description

[0045] Figure 1 This is a schematic diagram of the structural composition of a cylinder head assembly according to one embodiment of the present invention.

[0046] Figure 2 This is a schematic diagram of the lubrication oil circuit of a cylinder head assembly according to one embodiment of the present invention;

[0047] Figure 3 An exploded view of a cylinder head assembly according to one embodiment of the present invention;

[0048] Figure 4 This is a partial top view of a cylinder head assembly according to one embodiment of the present invention.

[0049] Figure 5 for Figure 3 An exploded view of the first bearing housing of the cylinder head assembly shown.

[0050] Figure 6 This is a partial structural cross-sectional view of a cylinder head assembly according to one embodiment of the present invention.

[0051] Explanation of reference numerals in the attached figures:

[0052] 100. Cylinder head assembly; 10. Cylinder head; 11. First bearing plate; 110. Fastening countersunk hole; 121. Fastening platform; 122. First row of cylinder head bolt holes; 123. Second row of cylinder head bolt holes; 124. Third row of cylinder head bolt holes; 125. Fourth row of cylinder head bolt holes; 126. Fifth row of cylinder head bolt holes; 13. Oil inlet; 14. Turbocharger mounting section; 151. First bearing housing fastening hole; 152. Second bearing housing fastening hole; 153. Third bearing housing fastening hole; 16. Second bearing plate; 20. First bearing housing; 201. Bearing hole; 21. First upper bearing housing; 22. First lower bearing housing; 23. First base; 24. Oil guide groove; 25. Weight reduction groove; 261. First pressure relief groove; 271. First fastening through hole; 272. Second fastening through hole; 2 73. Third fastening through hole; 274. Fourth fastening through hole; 275. Fifth fastening through hole; 276. Sixth fastening through hole; 200. Lubricating oil passage; 210. Oil supply passage; 220. Turbocharger oil passage; 230. Distribution passage; 231. Inlet section; 232. First clearance section; 233. Oil collection chamber; 234. Second clearance section; 240. Journal passage; 250. Tappet oil passage; 260. Flow limiting oil passage; 270. Valve insertion hole; 280. Insertion hole oil passage; 290. Pressure control oil passage; 300. Camshaft; 410. Oil control valve; 420. Bearing housing fastener; 421. First bearing housing bolt; 422. Second bearing housing bolt; 423. Third bearing housing bolt; 430. Locating pin; 440. Timing gear train; 450. Sealing component. Detailed Implementation

[0053] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0054] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0055] This utility model provides a cylinder head assembly 100, an engine, and a vehicle having the engine. The cylinder head assembly 100 includes a cylinder head 10 and a bearing housing. The engine includes the cylinder head assembly 100, a cylinder block, and a camshaft 300. The cylinder head 10 is fixedly connected to the cylinder block. The bearing housing has a bearing hole 201 for the camshaft 300 journal to extend into. The camshaft 300 is rotatably mounted in the bearing housing and can rotate relative to the cylinder head assembly 100 and the cylinder block. (See reference...) Figure 1 and Figure 3 In some embodiments, the engine also includes a timing gear train 440 mounted on the camshaft 300 and an oil control valve 410 mounted on the bearing housing. The timing gear train 440 is used to connect the timing chain. The timing gear train 440, the timing chain, and the oil control valve 410 are key components of the engine's variable valve timing mechanism. The cylinder head 10 and the bearing housing are initially positioned before connection by a locating pin 430 and are fixedly connected by bearing housing fasteners 420.

[0056] The bearing housing includes a first bearing housing 20 and a second bearing housing (not shown in the figure). The first bearing housing 20 and the second bearing housing are arranged side by side and spaced apart along the length direction of the cylinder head 10. The length direction of the cylinder head 10 is also the axial direction of the camshaft 300 and the axial direction of the engine crankshaft. Figure 1 The diagram illustrates a cylinder head assembly 100 according to one embodiment of the present invention. The length direction of the cylinder head 10 is parallel to the X-axis direction of the spatial rectangular coordinate system in the diagram. The cylinder block, cylinder head 10, and bearing housing are arranged sequentially along the height direction of the cylinder head 10. The height direction of the cylinder head 10 is parallel to the Z-axis direction of the spatial rectangular coordinate system in the diagram, and the X-axis direction is parallel to the width direction of the cylinder head 10. Figures 1-6In the medium-space rectangular coordinate system, the X-axis direction always represents the length direction of the cylinder head 10, the Y-axis direction always represents the width direction of the cylinder head 10, and the Z-axis direction always represents the height direction of the cylinder head 10.

[0057] Figure 1 The cylinder head assembly 100 shown is suitable for an engine equipped with two camshafts 300, which are spaced apart along the width of the cylinder head 10. The first bearing housing 20 and the second bearing housing each have two bearing holes 201, through which the two bearing holes 201 on each bearing housing are respectively passed.

[0058] The cylinder head 10 and the first bearing housing 20 together form a lubrication passage 200. The first bearing housing 20 includes a first base 23, and the cylinder head 10 includes a first support 11 disposed opposite to the first base 23. The first support 11 serves as the bearing surface of the first base 23 and supports the first bearing housing 20 and the camshaft 300. The lubrication passage 200 includes an oil supply passage 210 and a distribution passage 230 that are interconnected. The oil supply passage 210 is connected to the engine's oil pump, and the distribution passage 230 is formed between the first base 23 and the first support 11. In some embodiments, an oil guide groove 24 is recessed in the first base surface of the first base 23 facing the first support 11, and an oil supply passage 230 is formed by the oil guide groove 24. The oil guide groove 24 has an oil groove opening facing the first support 11. When the first base 23 is supported on the first support 11, the oil groove opening of the oil guide 24 is closed by the first support 11, thereby forming the oil supply passage 230. Lubricating oil first flows into the oil supply passage 210, and then flows into the oil guide groove 24.

[0059] Optionally, the first base surface and the first bearing platform 11 are in direct contact, and no sealing gasket or other sealing material is required between them; a surface seal is formed after they are bonded together. Figure 1 and Figure 3 As shown, the first base surface is entirely located in the same plane and forms a planar fit with the first bearing seat 11. With this configuration, the oil supply passage 230 is equivalent to completely transferring the existing transverse oil passage from the cylinder head 10 to the first bearing seat 20. Therefore, it is not necessary to perform subtractive processing on the cylinder head 10. The wall thickness of the drilling part on the cylinder head 10 that originally served as the transverse oil passage is reduced. Compared with processing the cylinder head 10, processing the oil guide groove 24 on the first base 23 is simpler, the positioning tooling required for processing is simplified, the processing time is shortened, and the difficulty is reduced. The accuracy of the oil guide groove 24 is easier to ensure. The fit between the first base surface and the first bearing seat 11 in the same plane can improve the uniformity of the fit and the sealing effect.

[0060] Optionally, the oil guide groove 24 is a cast groove recessed on the first base surface. Based on this, refer to... Figure 4The first base 23 is also recessed with a weight reduction groove 25 adjacent to the oil guide groove 24. The weight reduction groove 25 is also a cast groove. The wall thickness of the oil guide groove 24 on the side away from the weight reduction groove 25 is equal to or approximately equal to the wall thickness of the weight reduction groove 25 on the side away from the oil guide groove 24, and is also equal to the wall thickness between the oil guide groove 24 and the weight reduction groove 25. This design reduces the weight of the first bearing housing 20, which is beneficial for the lightweighting of the cylinder head assembly 100 and the engine. The oil guide groove 24 has a uniform wall thickness, which avoids casting defects such as internal shrinkage and porosity caused by excessive differences in wall thickness at different parts of the oil guide groove 24 and the weight reduction groove 25. This ensures the shape and dimensional accuracy of the oil guide groove 24. In addition, the first base 23 presents a grid-like rib structure by recessing the oil guide groove 24 and the weight reduction groove 25. These grid-like rib structures form the groove walls of the oil guide groove 24 and the weight reduction groove 25 and separate the oil guide groove 24 and the weight reduction groove 25. Therefore, the oil guide groove 24 and the weight reduction groove 25 improve the modality of the first bearing housing 20, which helps to improve the NVH performance of the cylinder head assembly 100 and the engine.

[0061] The oil distribution passage 230 has the same function as the transverse oil passages opened in the cylinder head 10 or bearing housing in the prior art, namely, to obtain lubricating oil and guide and distribute lubricating oil.

[0062] In some implementations, see Figures 2-4 The lubrication passage 200 also includes a journal channel 240 formed in the first base 23. The journal channel 240 connects the oil supply passage 230 with the bearing hole 201 of the first bearing housing 20. With this configuration, at least a portion of the lubricating oil in the oil supply passage 230 is supplied to the bearing hole 201 through the journal channel 240, thereby lubricating and cooling the journal of the camshaft 300. The oil supply passage 230 is closer to the bearing hole 201 of the first bearing housing 20 than the transverse oil passage formed in the cylinder head 10 in the prior art. Therefore, the journal channel 240 used to connect the oil supply passage 230 in this embodiment is shorter than the journal channel 240 used to connect the transverse oil passage in the prior art. Obviously, the oil intake path of the camshaft 300 journal in this embodiment is shorter than the oil intake path of the camshaft 300 journal in the prior art. The lubricating oil can enter the bearing hole 201 of the first bearing housing 200 from the oil supply passage 230 through the journal channel 240 more quickly.

[0063] In other implementations, such as Figures 2-4As shown, the lubrication circuit 200 also includes a tappet oil passage 250 and a flow-limiting oil passage 260 opened in the cylinder head 10. The distribution oil passage 230 and the tappet oil passage 250 are connected through the flow-limiting oil passage 260. With this configuration, at least a portion of the lubricating oil in the distribution oil passage 230 passes through the flow-limiting oil passage 260 and the tappet oil passage 250 to lubricate the hydraulic tappet. The flow-limiting oil passage 260 precisely controls the amount of lubricating oil entering the tappet oil passage 250. Therefore, the flow-limiting oil passage 260 has a flow-limiting function and can replace devices such as throttle valves, reducing the number of parts and assembly steps of the cylinder head assembly 100.

[0064] In some other implementations, such as Figures 2-4 As shown, the first bearing housing 20 also has a valve insertion hole 270 for installing the oil control valve 410. The oil control valve 410, also known as the OCV module, is part of the variable valve timing system. The lubrication circuit 200 also includes an insertion oil passage 280 and a pressure control oil passage 290 opened in the first bearing housing 20. One end of the insertion oil passage 280 is connected to the valve insertion hole 270, and the other end passes through the first base 23 to connect to the distribution oil passage 230. The pressure control oil passage 290 is connected to the bearing hole 201. With this configuration, at least a portion of the lubricating oil in the distribution oil passage 230 is distributed to the oil control valve 410 through the port oil passage 280. The oil control valve 410 can send a portion of the lubricating oil into the bearing hole 201 through the pressure control oil passage 290, thereby improving the lubrication effect on the camshaft 300 journal. Because the distribution oil passage 230 is closer to the valve port 270 than the transverse oil passage opened in the cylinder head 10 in the prior art, the port oil passage 280 connected to the distribution oil passage 230 in this embodiment is shorter than the port oil passage 280 connected to the transverse oil passage in the prior art. This shortens the oil intake path of the oil control valve 410, allowing the lubricating oil to enter the oil control valve 410 more quickly, improving the response speed of the variable valve timing system, and enabling the vehicle to perform better under conditions such as rapid acceleration.

[0065] It is understood that in other embodiments, the lubrication oil passage 200 includes the aforementioned journal channel 240, flow-limiting oil passage 260, and tappet oil passage 250; or the lubrication oil passage 200 includes the aforementioned journal channel 240 and socket oil passage 280; or the lubrication oil passage 200 includes the aforementioned socket oil passage 280, flow-limiting oil passage 260, and tappet oil passage 250; or the lubrication oil passage 200 includes the aforementioned journal channel 240, flow-limiting oil passage 260, tappet oil passage 250, and socket oil passage 280. The journal channel 240, flow-limiting oil passage 260, tappet oil passage 250, and socket oil passage 280 provide three different destinations for the lubricating oil in the oil passage 230.

[0066] Taking the transverse oil passage within the cylinder head 10 in the prior art as an example, the transverse oil passage is formed inside the side wall of the cylinder head 10 by drilling. Therefore, the transverse oil passage is a cylindrical straight oil passage, and its extension direction is the width direction of the cylinder head 10. In addition, the cylinder head 10 also has multiple sets of cylinder head bolt holes, typically five sets. (See reference...) Figure 5 Multiple sets of cylinder head bolt holes are arranged along the length of the cylinder head 10. Each set of cylinder head bolt holes includes one or more cylinder head bolt holes arranged along the width of the cylinder head 10. The cylinder head bolt holes are for the cylinder head fastening bolts to pass through. The cylinder block and the cylinder head 10 are connected by the cylinder head fastening bolts. The extension direction of the cylinder head bolt holes is the height direction of the cylinder head 10.

[0067] Among the multiple sets of cylinder head bolt holes, the row of cylinder head bolt holes closest to the transverse oil passage is the first row of cylinder head bolt holes 122. The axis of the transverse oil passage and the axis of the first row of cylinder head bolt holes 122 intersect in opposite planes. A certain distance must be maintained between the axis of the transverse oil passage and the axis of the first row of cylinder head bolt holes 122; otherwise, the transverse oil passage and the first row of cylinder head bolt holes 122 will be too close, resulting in an insufficient wall thickness of the transverse oil passage. An insufficient wall thickness of the transverse oil passage will cause weak areas on the sidewall of the transverse oil passage, which are prone to fatigue, dark cracks, or even cracking. Since the current technology for processing transverse oil passages is a slender hole drilling process, the drilling center is prone to shift during the drilling process. The distance between the axis of the transverse oil passage and the axis of the first row of cylinder head bolt holes 122 needs to be increased based on the theoretical distance to leave a safe machining allowance. The safe machining allowance prevents the transverse oil passage from thinning due to the offset of the drilling center line during drilling. Therefore, in order to ensure the minimum wall thickness of the transverse oil passage, the existing technology requires a large gap between the axis of the transverse oil passage and the axis of the first row of cylinder head bolt holes 122. However, the drawback of this design is that the wall thickness of the drilling part on the cylinder head 10 that serves as the transverse oil passage is large, the length of the cylinder head 10 is large, the dimensions of the cylinder head assembly 100 and the engine in the length direction of the cylinder head 10 are large, and the engine is difficult to install in the engine compartment. This drawback is particularly obvious for transversely mounted engines.

[0068] This invention replaces the transverse oil passages in the cylinder head 10 of the prior art with oil passages 230. Therefore, it is not necessary to drill long and narrow holes in the cylinder head 10 to obtain transverse oil passages. The wall thickness of the drilled part on the cylinder head 10 that originally served as a transverse oil passage is no longer limited by the minimum wall thickness of the transverse oil passage. As a result, the wall thickness of the drilled part on the cylinder head 10 that originally served as a transverse oil passage can be reduced along the length of the cylinder head 10. The length of the cylinder head 10 can thus be reduced, ultimately reducing the size of the cylinder head assembly 100 and the engine mounted on the cylinder head assembly 100 in the length direction of the cylinder head 10. This achieves miniaturization of the cylinder head assembly 100 and the engine, making it easier to install the engine in a compact engine compartment and avoiding interference with other components in the engine compartment.

[0069] The first bearing housing 20 also has a fastening through hole, and the first bearing platform 11 has a bearing housing fastening hole. The cylinder head 10 is connected to the first bearing housing 20 by a bearing housing fastener 420. The bearing housing fastener 420 passes through the fastening through hole, extends out of the first base surface of the first bearing housing 20, and then extends into the bearing housing fastening hole. See reference. Figure 1 , Figures 3-5 , Figure 5 The diagram illustrates the first bearing platform 11 from a top-down view. The first bearing housing 20 includes a first upper bearing housing 21 and a first lower bearing housing 22. A pressure control oil passage 290 is formed in the first upper bearing housing 21, and a first base 23 is formed in the first lower bearing housing 22. The bearing hole 201 is formed by the first upper bearing housing 21 and the first lower bearing housing 22. The fastening through holes include a first fastening through hole 271, a third fastening through hole 273, and a fifth fastening through hole 275 formed in the first upper bearing housing 21, and a second fastening through hole 272, a fourth fastening through hole 274, and a sixth fastening through hole 276 formed in the first lower bearing housing 22. The bearing housing fastener 420 includes a first bearing housing bolt 421, a second bearing housing bolt 422, and a third bearing housing bolt 423. The bearing housing fastening hole includes a first... The bearing housing has a fastening hole 151, a second bearing housing fastening hole 152, and a third bearing housing fastening hole 153. The first bearing housing bolt 421 passes through the first fastening through hole 271 and the second fastening through hole 272 and then extends into the first bearing housing fastening hole 151. The second bearing housing bolt 422 passes through the third fastening through hole 273 and the fourth fastening through hole 274 and then extends into the second bearing housing fastening hole 152. The third bearing housing bolt 423 passes through the fifth fastening through hole 275 and the sixth fastening through hole 276 and then extends into the third bearing housing fastening hole 153. One of the bearing holes 201 of the first bearing housing 20 is located between the first bearing housing bolt 421 and the second bearing housing bolt 422, and the other bearing hole 201 is located between the second bearing housing bolt 422 and the third bearing housing bolt 423.

[0070] See Figures 3-4 , Figure 6When the oil guide groove 24 recessed in the first base surface forms the oil distribution channel 230, compared with the cross-sectional shape of the transverse oil channel in the prior art, the cross-sectional shape of the oil distribution channel 230 can have more forms. The cross-sectional shape of the oil distribution channel 230 includes, but is not limited to, arc-shaped, rectangular, trapezoidal, and triangular. The cross-sectional shape and area of ​​the oil distribution channel 230 can be different at different positions on the oil distribution channel 230. In contrast, for transverse oil channels obtained by drilling, the cross-sectional shape of the oil channel can only be circular, and the cross-sectional area of ​​the oil channel is always unique. In addition, the oil guide groove 24 can be curved. The extension groove allows the oil supply passage 230 to be a non-linear oil passage with a curved section. In contrast, for transverse oil passages obtained by drilling, the extension direction of the oil passage can only be straight. The reasonably designed non-linear oil supply passage 230 can flexibly avoid the bearing housing fastener 420 and the bearing housing fastening hole, ensuring that there is sufficient distance between the oil supply passage 230 and the bearing housing fastener 420, and between the oil supply passage 230 and the bearing housing fastening hole. This reduces the amount of lubricating oil entering the fastening through hole and the bearing housing fastening hole, and improves the problem of lubricating oil seeping out of the fastening through hole.

[0071] Figure 6 The oil supply channel 230 shown has a rectangular cross-sectional shape. It can be understood that for two oil supply channels 230 with equal cross-sectional areas and circular and square cross-sectional shapes respectively, the side length of the square cross-section is smaller than the diameter of the circular cross-section. Therefore, using a square cross-section for the oil supply channel 230 makes it easier to thin the first base 23. The dimensions of the first base 23 along the X-axis and along the Z-axis are easier to reduce, and correspondingly, it is easier to reduce the dimension of the first support 11 along the X-axis. Of course, the cross-sectional shape of the oil supply channel 230 is not limited to a square. To further reduce the dimensions of the first base 23 and the first support 11 along the X-axis, the cross-sectional shape of the oil supply channel 230 can also be rectangular. The side length a along the X-axis in the rectangular cross-section can be smaller than the side length b along the Z-axis. The smaller the side length a, the smaller the dimensions of the first base 23 and the first support 11 along the X-axis.

[0072] See Figures 1-3 The oil supply passage 210 is located in the cylinder head 10. One end of the oil supply passage 210 passes through the side of the cylinder head 10 closest to the cylinder block. Lubricating oil, driven by the oil pump, first flows into the cylinder block and then into the oil supply passage 210. The other end of the oil supply passage 210 passes through the side of the first support 11 facing the first base surface, forming an oil inlet hole 13. The oil inlet hole 13 connects to the opening of the oil guide groove 24. The oil supply passage 210 and the distribution oil passage 230 are directly connected. After leaving the oil supply passage 210, the lubricating oil enters the distribution oil passage 230 through the oil inlet hole 13. Optionally, the oil supply passage 210 extends along the height direction of the cylinder head 10. Figures 2-3The Z-axis direction indicates the height direction of the cylinder head 10.

[0073] See Figures 1-2 , Figures 4-5 The first bearing platform 11 is also provided with a fastening countersunk hole 110, which can be obtained by countersinking. Therefore, the bottom countersinking plane of the fastening countersunk hole 110 forms a fastening platform 121 facing the first base surface. That is, a height difference is formed between the fastening platform 121 and the side of the first bearing platform 11 used to fit the first base surface. The first row of cylinder head bolt holes 122 are through holes opened in the fastening platform 121. After obtaining the fastening countersunk hole 110, drilling is performed on the bottom countersinking plane of the fastening countersunk hole 110 to obtain the first row of cylinder head bolt holes 122. When the cylinder head 10 and the cylinder block are connected by cylinder head fastening bolts, the head of the cylinder head fastening bolt abuts against the fastening platform 121. The fastening countersunk hole 110 provides operating space for the bolt gun. The bolt gun connected to the cylinder head fastening bolt extends into the fastening countersunk hole 110 and then drives the cylinder head fastening bolt to rotate. The oil guide groove 24 is a curved strip-shaped groove. Figure 5 The dashed line represents the orthographic projection of the oil guide groove 24 onto the first bearing platform 11. The oil supply passage 230 is a curved strip-shaped flow channel with a curved section. The curved section includes an inlet section 231 and a supply section. The supply section includes a first clearance section 232. The orthographic projection of the first clearance section 232 on the first bearing platform 11 is located outside the fastening countersunk hole 110. The outside of the fastening countersunk hole 110 refers to the side of the fastening countersunk hole 110 that is relatively far away from the other cylinder head bolt holes except for the first row of cylinder head bolt holes 122. The second row of cylinder head bolt holes 123, the third row of cylinder head bolt holes 124, the fourth row of cylinder head bolt holes 125, and the fifth row of cylinder head bolt holes 126 gradually move away from the first row of cylinder head bolt holes 122 along the length direction of the cylinder head 10. The inlet section 231 is inclined and bent relative to the first clearance section 232 and extends in a direction away from the outside of the first base 23 to connect to the oil inlet hole 13. The outside of the first base 23 is the side of the first base 23 that is relatively far away from the second bearing seat.

[0074] With this configuration, the position of the oil inlet hole 13 along the length of the cylinder head 10 is the same as the position of the oil supply passage 210 along the length of the cylinder head 10. The appropriate position of the oil supply passage 210 along the length of the cylinder head 10 ensures that its wall thickness is suitable, and the wall thickness S between the inner wall of the oil supply passage 210 and the outer wall of the cylinder head 10 is sufficient. Furthermore, the first clearance section 232 can bypass the fastening countersunk hole 110, ensuring that the lubricating oil flowing through the first clearance section 232 does not enter the fastening countersunk hole 110, thus preventing oil leakage in the cylinder head 10 or cylinder block. It is understandable that if the inlet section 231 and the first clearance section 232 were designed to be straight, extending along the width of the cylinder head 10, the oil supply passage 210 and the outer wall of the cylinder head 10 would be too close, resulting in a thinner wall thickness for the oil supply passage 210.

[0075] Optionally, such as Figure 5 As shown, the outer peripheral edge of the fastening platform 121 is tangent to the inner wall of the fastening countersunk hole 110, and the fastening platform 121 can be a circular platform. With this configuration, the first support 11 can be moved inward to a greater extent along the length direction of the cylinder head 10, which means that the first support 11 as a whole can be closer to the other cylinder head bolt holes except for the first row of cylinder head bolt holes 122. Therefore, the dimensions of the first base 23 and the first support 11 can be further reduced along the length direction of the cylinder head 10, thereby significantly reducing the length dimension of the cylinder head 10.

[0076] See Figures 1-2 In some embodiments, the lubrication circuit 200 further includes a turbocharger oil passage 220 opened in the cylinder head 10. The cylinder head 10 also includes a second support 16 and a turbocharger mounting portion 14 located inside the first support 11. The first support 11 and the second support 16 are arranged side by side and spaced apart along the length direction of the cylinder head 10. The second support 16 is used to support and install the second bearing seat. The inner side of the first support 11 is the side of the first support 11 that is relatively close to the second support 16. The turbocharger mounting portion 14 is used to install the turbocharger. The turbocharger oil passage 220 extends along the length direction of the cylinder head 10 and passes through the turbocharger mounting portion 14 to form an oil outlet. With this configuration, the oil outlet is closer to the turbocharger, shortening the distance between the oil outlet and the turbocharger's oil intake. Therefore, a shorter oil supply line can be used to connect the oil outlet and the turbocharger's oil intake. The shorter oil supply line can reduce the vibration amplitude of the engine, optimize the mode of the turbocharger and the oil supply line, and help improve the NVH performance of the engine and the vehicle.

[0077] Furthermore, the lubrication circuit 200 also includes a pressure relief oil passage connecting to the fastening through-hole. See details... Figures 3-4In some embodiments, the pressure relief oil passage includes a first pressure relief groove 261 recessed in the first base surface of the first base 23. The first pressure relief groove 261 can be a cast groove. The first pressure relief groove 261 extends through the side of the first bearing seat 20. The dispensing section of the dispensing oil passage 230 also includes a second clearance section 234, which bypasses the bearing seat fastener 420. The first pressure relief groove 261 and the second clearance section 234 are spaced apart and not connected to each other. With this configuration, the pressure relief oil passage can serve as a channel for lubricating oil to flow outward from the fastening through hole. Especially when the first base surface and the first bearing platform 11 are in direct contact, a small amount of lubricating oil is likely to enter the fastening through hole. The configuration of the pressure relief oil passage can allow the accumulated lubricating oil in the fastening through hole to be discharged in a timely manner, preventing the continuous accumulation of lubricating oil in the fastening through hole and thus preventing oil leakage. The lubricating oil entering the first pressure relief groove 261 can flow into the timing cover or cylinder body. Since the second clearance section 234 and the first pressure relief groove 261 are mutually blocked, the lubricating oil in the second clearance section 234 will not directly enter the fastening through hole, which helps to maintain the oil pressure and oil quantity inside the distribution oil passage 230, and ensures that the distribution oil passage 230 effectively supplies and distributes lubricating oil.

[0078] like Figure 5 As shown, one end of the first pressure relief groove 261 passes through the fourth fastening through hole 274, and the other end passes through the inner side of the first bearing housing 20. The inner side of the first bearing housing 20 is the side of the first bearing housing 20 that is relatively close to the second bearing housing. The second clearance section 234 passes between the second bearing housing bolt 422 and the outer side of the first bearing housing 20. The outer side of the first bearing housing 20 is the side of the first bearing housing 20 that is relatively far away from the second bearing housing. With this configuration, the lubricating oil accumulated in the fourth fastening through hole 274 can flow into the cylinder body through the first pressure relief groove 261. This lubricating oil can be used to lubricate the components inside the cylinder body, thus achieving recycling. If the first pressure relief groove 261 passes through the outer side of the first bearing housing 20, the lubricating oil accumulated in the fourth fastening through hole 274 will flow into the timing cover.

[0079] The reason why the first pressure relief groove 261 penetrates the fourth fastening through hole 274 is that the rigidity of the two ends of the first bearing housing 20 along the width direction of the cylinder head 10 is relatively high, while the rigidity of the middle part of the first bearing housing 20 along the width direction of the cylinder head 10 is relatively low. This results in a more serious accumulation of lubricating oil in the fourth fastening through hole 274, while the second fastening through hole 272 and the sixth fastening through hole 276 accumulate little or almost no lubricating oil. Of course, the first pressure relief groove 261 that penetrates the second fastening through hole 272 and the sixth fastening through hole 276 can also be recessed on the first base surface.

[0080] In other embodiments, the pressure relief passage further includes at least one of a second pressure relief groove and a third pressure relief groove. The second pressure relief groove is recessed at the bottom of the first upper bearing seat 21, and the third pressure relief groove is recessed at the top of the first lower bearing seat 22. One end of the second pressure relief groove passes through the third fastening through hole 273, and the other end passes through the inner or outer side of the first upper bearing seat 21. One end of the third pressure relief groove passes through the fourth fastening through hole 274, and the other end passes through the inner or outer side of the first lower bearing seat 22. When the first upper bearing seat 21 and the second lower bearing seat are closed to form the bearing hole 201, the bottom of the first upper bearing seat 21 and the top of the first lower bearing seat 22 are mated together. With this configuration, the lubricating oil accumulated in the third fastening through hole 273 and the fourth fastening through hole 274 can be discharged in a timely manner through the second pressure relief groove and the third pressure relief groove. In particular, when there is a lot of lubricating oil accumulated in the third fastening through hole 273 and the fourth fastening through hole 274, it is difficult to guarantee the oil discharge efficiency by relying solely on the first pressure relief groove 261 to discharge oil. At this time, the second pressure relief groove and the third pressure relief groove can improve the oil discharge efficiency.

[0081] Furthermore, in some embodiments not shown in the figures, the valve insertion hole 270 includes a first insertion hole in the first upper bearing seat 21 and a second insertion hole in the first lower bearing seat 22. When the bottom of the first upper bearing seat 21 and the top of the first lower bearing seat 22 are mated together, and the first upper bearing seat 21 and the second lower bearing seat together form a bearing hole 201, the first insertion hole and the second insertion hole are coaxially connected to form a cavity for the oil control valve 410 to be inserted. The second pressure relief groove can also penetrate the first insertion hole, and the third pressure relief groove can also penetrate the second insertion hole. With this configuration, the lubricating oil accumulated in the third fastening through hole 273 and the fourth fastening through hole 274 can enter the valve insertion hole 270 through the second pressure relief groove and the third pressure relief groove, thereby being obtained and utilized by the oil control valve 410, achieving efficient utilization of the lubricating oil.

[0082] In some embodiments, the oil supply passage 230 further includes an oil collecting chamber 233, which is formed by the expanded portion in the oil guide groove 24. If the oil supply passage 230 is cut by a plane parallel to the height and length directions of the cylinder head 10, the cross-section of the oil collecting chamber 233 obtained by the plane is larger than the cross-section formed by the plane cutting other sections of the oil supply passage 230. Figures 4-5As shown, the insertion oil passage 280 penetrates the first base surface of the first base 23, thus directly connecting to the oil collecting chamber 233. The flow-limiting oil passage 260 penetrates the side of the first support 11 that is in contact with the first base surface, thus directly connecting to the oil collecting chamber 233. With this configuration, the oil collecting chamber 233 has the function of buffering and accumulating lubricating oil. When a certain amount of lubricating oil accumulates in the oil collecting chamber 233, the oil pressure in the oil collecting chamber 233 can be maintained relatively stable. The lubricating oil in the oil collecting chamber 233 has two destinations: the first destination is through the insertion oil passage 280 into the valve insertion hole 270, where it is taken by the oil control valve 410; the second destination is through the flow-limiting oil passage 260 into the tappet oil passage 250, where it is taken by the hydraulic tappet. The buffer function of the oil collection chamber 233 allows the lubricating oil to be distributed simultaneously along the two directions mentioned above, so as to meet the oil demand of the oil control valve 410 and the hydraulic tappet at the same time; and the buffer function can ensure that the lubricating oil is supplied to the oil control valve 410 and the hydraulic tappet in sufficient quantity and without interruption. For example, when the vehicle accelerates rapidly, the instantaneous oil demand of the oil control valve 410 increases, and the lubricating oil buffered in the oil collection chamber 233 can replenish the oil control valve 410 in time.

[0083] See Figures 1-2 , Figures 4-5 There are two flow-limiting oil passages 260 and two tappet oil passages 250. There are two oil control valves 410 and two insertion oil passages 280. The distribution oil passage 230 includes two oil collection chambers 233. One flow-limiting oil passage 260 and one insertion oil passage 280 are connected to one oil collection chamber 233. The other flow-limiting oil passage 260 and the other insertion oil passage 280 are connected to the other oil collection chamber 233. The two oil collection chambers 233 are located at both ends of the second relief section 234. The shape of each oil collection chamber 233 projected onto the first support 11 is approximately triangular, semi-circular or semi-elliptical. The outline of the oil collection chamber 233 projected onto the first support 11 protrudes relative to the first relief part and the second relief part to the remaining cylinder head bolt holes except for the first row of cylinder head bolt holes 122. With this configuration, the oil passage 280 can be moved further inward along the length of the cylinder head 10. This inward movement of the oil passage 280 means that the oil passage 280 moves closer to the second bearing seat and the second bearing platform 16 along the length of the cylinder head 10 to reduce the size K. The positions of the valve port 270 and the oil control valve 410 can also be moved inward along the length of the cylinder head 10, making the cylinder head assembly 100 and the engine more compact. At the same time, more space can be left for wiring harness installation to install the wiring harness connected to the oil control valve 410.

[0084] Further, see Figure 1 and Figure 2The turbocharger oil passage 220 and the tappet oil passage 250 pass through the outer side of the cylinder head 10. To prevent the lubricating oil in the turbocharger oil passage 220 and the tappet oil passage 250 from flowing out of the outer side of the cylinder head 10, the cylinder head assembly 100 also includes a sealing element 450. The sealing element 450 can be a ball or a plug. The sealing element 450 can be a metal element. The opening on the outer side of the cylinder head 10 that is penetrated by the turbocharger oil passage 220 and the tappet oil passage 250 is sealed by the sealing element 450.

[0085] In some other embodiments not shown in the figure, in addition to the oil guide groove 24 recessed on the first base surface, the first support 11 also has an oil guide groove 24 recessed on the side for supporting the first bearing seat 20. The oil guide groove 24 recessed on the first base surface can be a casting groove, and the oil guide groove 24 recessed on the first support 11 can be a milling groove. When the first base 23 is supported on the first support 11, the oil guide groove 24 recessed on the first base surface and the oil guide groove 24 recessed on the first support 11 together constitute the oil supply channel 230. With this configuration, the cross-sectional area of ​​the oil passage 230 is shared by two oil guide grooves 24, thus the cross-sectional area of ​​each of the two oil guide grooves 24 can be further reduced, which helps to further reduce the size of the first base 23 and the first support 11 in the length direction of the cylinder head 10, thereby further reducing the size of the cylinder head assembly 100 in the length direction of the cylinder head 10. It can be understood that when the oil consumption of the camshaft 300 journal, the oil control valve 410 and the hydraulic tappet increases, the oil passage 230 can also be formed by the two oil guide grooves 24 to increase the cross-sectional size of the oil passage 230, thereby increasing the flow rate of lubricating oil in the oil passage 230.

[0086] The technical features of the above-described embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0087] Those skilled in the art should recognize that the above embodiments are only used to illustrate the present utility model and are not intended to limit the present utility model. Any appropriate changes and variations made to the above embodiments within the scope of the essential spirit of the present utility model shall fall within the scope of protection claimed by the present utility model.

Claims

1. A cylinder head assembly comprising a cylinder head (10) and a first bearing housing (20), wherein the cylinder head (10) and the first bearing housing (20) form a lubrication passage (200), characterized in that, The first bearing housing (20) includes a first base (23), the cylinder head (10) includes a first support (11) disposed opposite to the first base (23), and the lubrication passage (200) includes a distribution oil passage (230) formed between the first base (23) and the first support (11).

2. The cylinder head assembly as described in claim 1, characterized in that, The first base (23) includes a first base surface disposed toward the first support (11), and the first base surface is recessed with an oil guide groove (24), the oil guide groove (24) forming the oil supply channel (230).

3. The cylinder head assembly as described in claim 2, characterized in that, The first base surface and the first bearing platform (11) are in contact with each other to form a surface seal.

4. The cylinder head assembly as described in claim 3, characterized in that, The first base surface and the first support (11) form a planar fit; and / or, the oil guide groove (24) is a cast groove recessed on the first base surface.

5. The cylinder head assembly as described in claim 1, characterized in that, The lubrication circuit (200) also includes an oil supply passage (210) opened in the cylinder head (10). The first support (11) is provided with an oil inlet hole (13) to connect the oil supply passage (210) and the distribution passage (230). The distribution passage (230) includes an inlet section (231) and a distribution section. The inlet section (231) is inclined relative to the distribution section and extends in a direction away from the outside of the first base (23) to connect the oil inlet hole (13).

6. The cylinder head assembly as described in claim 5, characterized in that, The dispensing section includes a first clearance section (232), and the first support (11) is also provided with a fastening countersunk hole (110). The orthographic projection of the first clearance section (232) on the first support (11) is located outside the fastening countersunk hole (110), and the guide section (231) is inclined relative to the first clearance section (232) in a direction away from the outside of the first base (23).

7. The cylinder head assembly as described in claim 6, characterized in that, The cylinder head (10) also includes a fastening platform (121) formed from the bottom of the fastening counterbore (110), the outer periphery of which is tangent to the inner wall of the fastening counterbore (110).

8. The cylinder head assembly as described in claim 5, characterized in that, The lubrication circuit (200) also includes a turbocharger oil passage (220) opened in the cylinder head (10). The cylinder head (10) also includes a turbocharger mounting part (14). One end of the turbocharger oil passage (220) is connected to the oil supply passage (210), and the other end passes through the turbocharger mounting part (14).

9. The cylinder head assembly as claimed in claim 1, characterized in that, The first bearing housing (20) is also provided with a fastening through hole, through which the bearing housing fastener (420) passes. The cylinder head (10) is connected to the first bearing housing (20) through the bearing housing fastener (420). The lubrication oil passage (200) also includes a pressure relief oil passage that connects to the fastening through hole.

10. The cylinder head assembly as claimed in claim 9, characterized in that, The pressure relief oil passage includes a first pressure relief groove (261) recessed in the first base (23), the first pressure relief groove (261) penetrating the side of the first bearing seat (20), and the supply oil passage (230) further includes a second clearance section (234) that bypasses the bearing seat fastener (420) and is separated from the first pressure relief groove (261).

11. The cylinder head assembly as claimed in claim 10, characterized in that, The first pressure relief groove (261) passes through the inner side of the first bearing housing (20), and the second clearance section (234) passes between the bearing housing fastener (420) and the outer side of the first bearing housing (20).

12. The cylinder head assembly as claimed in claim 9, characterized in that, The first bearing housing (20) includes a first upper bearing housing (21) and a first lower bearing housing (22) having the first base (23). The pressure relief oil passage also includes a second pressure relief groove and / or a third pressure relief groove. The second pressure relief groove is located at the bottom of the first upper bearing housing (21), and the third pressure relief groove is located at the top of the first lower bearing housing (22).

13. The cylinder head assembly according to any one of claims 1 to 12, characterized in that, The lubrication passage (200) further includes a journal channel (240) formed in the first base (23), the journal channel (240) connecting the oil supply passage (230) to the bearing hole (201) of the first bearing housing (20); and / or, The lubrication circuit (200) further includes a tappet oil passage (250) opened in the cylinder head (10), a flow-limiting oil passage (260) connecting the tappet oil passage (250) and the distribution oil passage (230); and / or, The first bearing housing (20) is also provided with a valve insertion hole (270) for installing an oil control valve (410). The lubrication oil circuit (200) also includes an insertion oil passage (280) opened in the first bearing housing (20). The insertion oil passage (280) connects the distribution oil passage (230) and the valve insertion hole (270).

14. The cylinder head assembly as claimed in claim 13, characterized in that, The oil supply channel (230) includes an oil collection chamber (233), the insertion oil channel (280) passes through the first base (23) to connect the oil collection chamber (233), and the flow limiting oil channel (260) passes through the first support (11) to connect the oil collection chamber (233).

15. The cylinder head assembly as claimed in claim 13, characterized in that, The first bearing housing (20) is also provided with a fastening through hole, through which the bearing housing fastener (420) passes. The cylinder head (10) is connected to the first bearing housing (20) through the bearing housing fastener (420). The lubrication oil circuit (200) also includes a pressure relief oil passage connecting the valve insertion hole (270) and the fastening through hole.

16. An engine, characterized in that, The assembly includes a cylinder block, a camshaft (300), and a cylinder head assembly as described in any one of claims 1 to 15, wherein the cylinder head (10) is fixedly connected to the cylinder block, and the camshaft (300) is rotatably mounted on the bearing housing.

17. A vehicle, characterized in that, Including the engine as described in claim 16.

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