A compact high-pressure oil pump drive component and a high-pressure oil pump

Abstract

This invention relates to a compact high-pressure oil pump drive component and a high-pressure oil pump. The pump body assembly provides support for the camshaft assembly via an interference-fitted bushing. The camshaft assembly includes a double thrust bushing and a slider assembly. An eccentric circle drives the slider to reciprocate, achieving the plunger's oil supply function. A sleeve is nested within the guide rod guide section, and its reciprocating motion is achieved through the elastic action of a limiting spring. The guide rod guide surface is coated and has lubrication spiral grooves to reduce friction loss and extend service life. The flange assembly has an internal bushing, and the lubrication oil circulation system is optimized through an oil cavity, eccentric groove, and connecting hole to ensure continuous lubrication of moving parts. The inner bore of the thrust bushing is interference-fitted with the camshaft support journal, and the shoulder surface is evenly distributed with oil grooves to form a dynamic lubrication film, limiting the camshaft axial movement to ≤0.5mm. The slider assembly has an internal bushing, which, together with the axial force of the plunger and sleeve, restricts slider rotation, improving motion stability.

Description

Technical Field

[0001] This invention belongs to the field of marine engine technology, and in particular to a compact high-pressure oil pump drive component and a high-pressure oil pump. Background Technology

[0002] As a core component of the internal combustion engine fuel system, the performance of the high-pressure fuel pump directly affects the engine's fuel supply efficiency, emission control, and operational reliability. Traditional high-pressure fuel pumps mostly adopt a split structure design, using multiple independent components such as camshafts, guide piston assemblies, and plunger pairs to achieve the fuel supply function, but this design has significant drawbacks.

[0003] First, the existing structure is complex. The camshaft-driven guide piston assembly transmits driving force, resulting in a heavy moving mass and a large plunger spring, leading to a bulky overall high-pressure oil pump with low space utilization, making it difficult to adapt to the needs of compact engines. Second, the lubrication system design is inadequate. Key friction pairs, such as the cam and roller surfaces, lack forced lubrication, making them prone to increased wear due to dry friction and shortening their service life. Furthermore, the complex camshaft axial movement restriction structure also contributes to the large overall size and weight of the high-pressure oil pump.

[0004] To address the aforementioned issues, existing technologies attempt to improve the design through structural optimization, but a systematic solution for optimizing the compact arrangement of drive components is still lacking. Therefore, there is an urgent need for an integrated, multi-dimensional lubrication high-pressure oil pump drive component to overcome traditional technological bottlenecks and meet the stringent requirements of modern engines for high-precision oil supply and long-life operation. Summary of the Invention

[0005] This invention relates to a compact high-pressure oil pump drive component and a high-pressure oil pump, aiming to solve the problems of complex structure, low lubrication efficiency, and high friction loss in traditional high-pressure oil pumps. Through integrated design, dynamic lubrication system, and wear-resistant coating technology, it significantly improves fuel supply efficiency and reliability, making it suitable for the precise fuel supply requirements of diesel engines to common rail high-pressure fuel systems.

[0006] The technical solution of this application is as follows:

[0007] This application provides a compact high-pressure oil pump drive component, including:

[0008] Pump body, the pump body having an internal cavity;

[0009] A camshaft, rotatably supported within the inner cavity of the pump body, the camshaft having at least one eccentric cam portion;

[0010] A slider assembly is sleeved outside the eccentric cam portion and slides in cooperation with the eccentric cam portion to convert the axial rotational motion of the camshaft into the vertical reciprocating motion of the slider assembly.

[0011] A pump cover assembly, which is fixedly mounted on the pump body;

[0012] A plunger is slidably disposed vertically within the pump cover assembly, and one end of the plunger abuts against the slider assembly;

[0013] An elastic element is disposed between the pump cover assembly and the plunger, for providing a restoring force to the plunger and keeping the plunger in contact with the slider assembly;

[0014] Driven by the eccentric cam, the slider assembly overcomes the elastic force of the elastic element to perform the vertical reciprocating motion, and oil is supplied through the plunger.

[0015] Preferably, the slider assembly includes a slider having a first plane and a second plane disposed opposite to each other, the first plane abutting against the end of the plunger, and the second plane being used for sliding engagement with an external guide.

[0016] Driven by the eccentric cam, the slider assembly performs the vertical reciprocating motion. The force exerted by the plunger on the first plane and the force exerted by the external guide on the second plane are combined to limit the flipping of the slider assembly during the reciprocating motion.

[0017] Preferably, the slider is provided with a bushing mounting hole and a guide groove;

[0018] The slider assembly also includes a bushing with a guide protrusion on its outer circumference. The bushing is interference-fitted into the bushing mounting seat hole, and the guide protrusion cooperates with the guide groove. The bushing slides with the eccentric cam portion.

[0019] Preferably, the pump further includes a guide rod assembly, which is fixedly mounted on the pump body and slides in cooperation with the second plane to guide the vertical reciprocating motion of the slider assembly and to cooperatively restrict the flipping of the slider assembly.

[0020] Preferably, the guide rod assembly includes a guide rod, a sleeve, and a resilient reset element;

[0021] The guide rod is fixedly mounted on the pump body, and the outer guide surface of the guide rod is provided with a wear-resistant coating and a lubrication spiral groove.

[0022] The sleeve is fitted onto the guide rod and slides in cooperation with the guide rod. One end of the sleeve is provided with a working plane, which slides in cooperation with the second plane. The surface of the working plane is provided with a wear-resistant coating. The other end of the sleeve is provided with a spring abutment surface.

[0023] The sleeve is provided with a straight groove, which connects the inner hole of the sleeve with the external space, and the edge of the working plane is provided with an oil guiding slope.

[0024] The elastic reset element is sleeved on the guide rod and located between the guide rod and the spring contact surface, and is used to provide a reset force to the sleeve and limit the range of motion of the sleeve.

[0025] Preferably, thrust bushings are provided at both ends of the camshaft, and the thrust bushings are interference-fitted onto the support journal of the camshaft;

[0026] One of the thrust bushings is slidably fitted with a first support bushing provided in the pump body to provide axial positioning and rotational support for the camshaft.

[0027] Preferably, the camshaft has a lubrication channel inside, the lubrication channel having an oil inlet and at least one oil outlet;

[0028] The oil inlet is located at the end of the camshaft;

[0029] The oil outlet is provided corresponding to the outer surface of the eccentric cam and the outer surface of the support journal, and is used to guide the lubricating oil to the corresponding sliding mating surface.

[0030] Preferably, when the camshaft has two or more eccentric cam portions, a limiting shaft section is provided on the camshaft. The limiting shaft section is located between two adjacent eccentric cam portions and is used to cooperate with the end face of the slider assembly to limit the axial displacement of the slider assembly.

[0031] Preferably, the pump also includes a flange assembly disposed on the pump body, the flange assembly comprising a flange and a second support bushing;

[0032] The flange is provided with a bushing mounting hole, and the second support bushing is interference-fitted into the bushing mounting hole for sliding cooperation with another thrust bushing on the camshaft to provide support for the camshaft.

[0033] The flange has a lubricating oil chamber inside, which is connected to the inner cavity of the pump body. The lubricating oil chamber is used to install the oil pump.

[0034] The lubricating oil cavity is provided with an eccentric groove and an oil outlet, and the eccentric groove connects the lubricating oil cavity and the oil outlet;

[0035] The flange is also provided with a connecting hole, which connects the lubricating oil chamber with the inner cavity of the pump body;

[0036] A sealing ring groove is provided at the contact surface between the flange and the pump body.

[0037] This application also provides a high-pressure oil pump, including the aforementioned compact high-pressure oil pump drive component.

[0038] The beneficial effects of this application are as follows:

[0039] Through integrated structural design, the slider assembly is directly fitted onto the outside of the eccentric cam section of the camshaft, replacing the independent guide piston and its precision pump body guide hole in the traditional cam-guide piston-plunger structure, significantly reducing the overall volume and achieving a compact layout. By having the first plane on the slider assembly abut against the plunger and the second plane slide against the guide rod assembly, the synergistic effect of the plunger force and the guide force effectively limits the flipping of the slider assembly during reciprocating motion without an independent guide structure, improving motion stability. By setting a lubrication channel inside the camshaft to precisely deliver lubricating oil to the sliding mating surfaces of the eccentric cam section and the slider assembly, the thrust bushing and the support bushing, and the support bushing, and by forming a dynamic lubrication film in the axial clearance through the lubrication oil groove on the end face of the thrust bushing, the wear of key friction pairs is significantly reduced while limiting axial movement. This solves the problems of insufficient lubrication and high friction loss in traditional structures, meeting the stringent requirements of modern engines for high-precision oil supply and long service life of high-pressure oil pumps. Attached Figure Description

[0040] Figure 1 A schematic diagram of the structure of a compact high-pressure oil pump drive component;

[0041] Figure 2 This is a schematic diagram of the slider assembly.

[0042] Figure 3 This is a schematic diagram of the guide rod assembly.

[0043] Figure 4 A schematic diagram of the structure of the thrust bushing, slider assembly, and camshaft assembly;

[0044] Figure 5 A schematic diagram of the structure of the thrust bushing, slider assembly, and camshaft assembly;

[0045] Figure 6 This is a structural schematic diagram of the flange assembly;

[0046] Figure 7 This is a schematic diagram of the pump body.

[0047] Explanation of reference numerals in the attached figures:

[0048] 1-Pump body; 101-Inner cavity; 102-Sealing ring groove at the mating surface of the pump body and pump cover assembly; 103-Oil outlet;

[0049] 2-Camshaft; 21-Eccentric cam section; 22-Support journal; 23-Lubrication channel; 231-Oil inlet; 232-Oil outlet; 24-Rectangular connection port; 25-Limiting shaft section; 26-Camshaft end sealing ring groove;

[0050] 3-Slider assembly; 31-Slider; 311-First plane; 312-Second plane; 313-Bushing mounting hole; 314-Guide groove; 32-Bushing; 321-Guide protrusion; 322-Oil groove;

[0051] 4-Pump cover assembly;

[0052] 5-Plunger;

[0053] 6-Elastic element;

[0054] 7-Guide rod assembly; 71-Guide rod; 711-Lubrication spiral groove; 712-Spring positioning ring groove; 713-Sealing ring groove between guide rod and pump body; 72-Sleeve; 721-Working plane; 722-Spring abutment surface; 723-Straight groove; 724-Oil guide slope; 73-Elastic reset element;

[0055] 8-Thrust sleeve; 81-End face; 82-Lubricating oil groove; 83-Oil hole;

[0056] 9-First support bushing;

[0057] 10-Flange assembly; 1001-Flange; 10011-Bushing mounting hole; 10012-Lubricating oil cavity; 10013-Eccentric groove; 10014-Oil outlet; 10015-Connecting hole; 10016-Sealing ring groove on the contact surface between the flange and the pump body; 1002-Second support bushing;

[0058] 11-Oil pump. Detailed Implementation

[0059] Reference Figures 1-7 This application provides a compact high-pressure oil pump drive component, including:

[0060] Pump body 1, the pump body 1 has an inner cavity 101;

[0061] Camshaft 2 is rotatably supported in the inner cavity 101 of pump body 1, and camshaft 2 has at least one eccentric cam portion 21.

[0062] The slider assembly 3 is sleeved on the outside of the eccentric cam portion 21 and slides in cooperation with the eccentric cam portion 21, and is used to convert the axial rotational motion of the camshaft 2 into the vertical reciprocating motion of the slider assembly 3.

[0063] Pump cover assembly 4 is fixedly mounted on pump body 1;

[0064] The plunger 5 is slidably disposed in the pump cover assembly 4 along the vertical direction, and one end of the plunger 5 abuts against the slider assembly 3;

[0065] The elastic element 6 is disposed between the pump cover assembly 4 and the plunger 5, and is used to provide a restoring force to the plunger 5 and keep the plunger 5 in contact with the slider assembly 3.

[0066] Driven by the eccentric cam 21, the slider assembly 3 overcomes the elastic force of the elastic element 6 to perform vertical reciprocating motion and achieves oil supply through the plunger 5.

[0067] The working process of camshaft 2 during rotation is as follows:

[0068] During the lifting phase of the eccentric cam section 21, its outer contour pushes the slider assembly 3 upward. The slider assembly 3 overcomes the elastic force of the elastic element 6 and the hydraulic pressure transmitted by the plunger 5 to push the plunger 5 upward, thus realizing the oil supply stroke. During the lowering phase of the eccentric cam section 21, its outer contour pushes the slider assembly 3 downward. The elastic force of the elastic element 6 pushes the plunger 5 downward, and keeps the plunger 5 in contact with the slider assembly 3 at all times.

[0069] Traditional cam-guide piston-plunger type high-pressure oil pumps employ a three-stage transmission structure. The guide piston, as an independent intermediate transmission component, requires precise guide holes and installation space within the pump body, resulting in a large pump body and complex structure. The contact between the cam and the guide piston is point or line contact, with high contact stress and lateral force, which easily leads to uneven wear of the guide piston. At the same time, the friction pair requires high lubrication conditions. In addition, the large number of moving parts and the large overall moment of inertia limit the response speed and maximum speed of the high-pressure oil pump, making it difficult to meet the requirements of modern engines for compact space and high-reliability oil supply.

[0070] To address the aforementioned deficiencies, this application proposes the following solutions:

[0071] This application adopts a fitting structure in which the slider assembly 3 is sleeved on the outside of the eccentric cam part 21, replacing the traditional independent guide piston. The slider assembly 3 is directly sleeved on the eccentric cam part 21 and arranged coaxially with the eccentric cam part 21. There is no need to set an independent guide hole and installation space in the pump body 1, thereby greatly reducing the overall volume of the pump body 1 and realizing a compact layout.

[0072] Meanwhile, through the direct drive relationship between the plunger 5 and the slider assembly 3, although it is still a three-stage transmission in terms of stages, the slider assembly 3 is directly mounted on the eccentric cam 21, eliminating the guide piston and its guide structure, making the power transmission more direct, reducing the number of moving parts, and lowering the overall motion inertia.

[0073] Reference Figure 2The slider assembly 3 includes a slider 31, which has a first plane 311 and a second plane 312 disposed opposite to each other. The first plane 311 abuts against the end of the plunger 5, and the second plane 312 is used for sliding engagement with an external guide. Driven by the eccentric cam 21, the slider assembly 3 performs a vertical reciprocating motion. Through the combined action of the force exerted by the plunger 5 on the first plane 311 and the force exerted by the external guide on the second plane 312, the flipping of the slider assembly 3 during the reciprocating motion is restricted, ensuring the stability of the slider assembly 3's movement.

[0074] During the reciprocating motion of the slider assembly 3 driven by the eccentric cam 21, the slider is subjected to forces from multiple directions, posing a risk of overturning. By setting the first plane 311 and the second plane 312 as parallel planes arranged opposite each other, this problem can be solved using the principle of mechanical equilibrium: the first plane 311 is subjected to a downward force from the plunger 5, while the second plane 312 is subjected to an upward force from the external guide. Since the first plane 311 and the second plane 312 are parallel and opposite, the two forces are in opposite directions and their lines of action are nearly coincident, forming a torque balance that effectively counteracts the overturning torque.

[0075] Reference Figure 2 The slider 31 is provided with a bushing mounting seat hole 313 and a guide groove 314; the slider assembly 3 also includes a bushing 32, the outer circle of which is provided with a guide protrusion 321. The bushing 32 is interference-fitted into the bushing mounting seat hole 313, and the guide protrusion 321 cooperates with the guide groove 314. The bushing 32 is slidably fitted with the eccentric cam part 21. The bushing 32 achieves a rigid connection with the slider 31 through the interference fit and guide fit, ensuring that there is no fretting clearance between the bushing 32 and the bushing mounting seat hole 313, eliminating wear and impact caused by relative movement; the cooperation between the guide protrusion 321 and the guide groove 314 achieves circumferential positioning, enabling the bushing 32 to reliably transmit the driving force applied by the eccentric cam part 21 to the entire slider. The bushing 32 is provided with an oil groove 322 for storing lubricating oil.

[0076] Reference Figure 1 The embodiments of this application also include a guide rod assembly 7, which is fixedly mounted on the pump body 1. The guide rod assembly 7 is slidably engaged with the second plane 312 to guide the vertical reciprocating motion of the slider assembly 3 and to cooperate in restricting the flipping of the slider assembly 3.

[0077] Reference Figure 3The guide rod assembly 7 includes a guide rod 71, a sleeve 72, and an elastic reset member 73. The guide rod 71 is fixedly mounted on the pump body 1, and its outer guide surface is provided with a wear-resistant coating and a lubrication spiral groove 711. The sleeve 72 is fitted onto the guide rod 71 and slides in engagement with it. One end of the sleeve 72 has a working plane 721 that slides in engagement with a second plane 312. The surface of the working plane 721 is provided with a wear-resistant coating, and the other end of the sleeve 72 has a spring abutment surface 722. The sleeve 72 has a straight groove 723 that connects its inner hole to the external space, and the edge of the working plane 721 has an oil-guiding inclined surface 724. The elastic reset member 73 is fitted onto the guide rod 71 and located between the guide rod 71 and the spring abutment surface 722, providing a reset force to the sleeve 72 and limiting its range of motion.

[0078] The guide rod 71 adopts a slender cylindrical structure, with one end fixedly installed in the lower mounting hole of the pump body 1 via a threaded connection. The outer guide surface of the guide rod 71 is precision ground to ensure the fitting accuracy between it and the inner hole of the sleeve 72. The wear-resistant coating on the outer guide surface is a chromium or nickel plating layer to enhance surface hardness and wear resistance. The lubrication spiral groove 711 extends spirally along the axial direction of the guide rod 71. When the sleeve 72 slides back and forth along the guide rod 71, the lubrication spiral groove 711 stores lubricating oil, forming a continuous oil film on the sliding contact surface, and guides the lubricating oil to be evenly distributed throughout the contact surface, avoiding dry friction caused by local lack of oil.

[0079] The guide rod 71 is also equipped with a spring positioning structure for fixing one end of the elastic reset member 73. Specifically, the tail of the guide rod 71 is provided with a spring positioning ring groove 712. The lower end of the elastic reset member 73 is embedded in the spring positioning ring groove 712 of the guide rod 71, and its upper end acts on the spring abutment surface 722 of the sleeve 72. The elastic force limits the stroke range of the sleeve 72 and provides a reset force when the slider assembly 3 returns. A sealing ring groove 713 is provided between the guide rod 71 and the mounting surface of the pump body 1. An O-ring is embedded in the sealing ring groove 713 to prevent lubricating oil from leaking from the mounting hole.

[0080] The sleeve 72 is made of high-carbon steel and hardened. Its inner hole is precisely fitted with the guide outer circle of the guide rod 71, enabling the sleeve 72 to slide smoothly along the guide rod 71. The surface of the working plane 721 is coated with a ceramic coating or a chrome-plated coating to withstand the friction and wear caused by high-frequency reciprocating contact. The oil guiding slope 724 is located at the outer and inner edges of the working plane 721 and is inclined at a small angle. When the slider assembly 3 slides relative to the sleeve 72, the lubricating oil is actively squeezed and distributed between the contact surfaces of the working plane 721 and the second plane 312 under the guidance of the oil guiding slope 724, forming a wedge-shaped oil film, which effectively reduces the frictional resistance during start-up and movement.

[0081] The straight groove 723 on the side wall of the sleeve 72 extends radially. On the one hand, it serves as a lubricating oil channel, introducing external lubricating oil into the sliding contact surface between the inner hole and the guide rod 71. On the other hand, it plays a role in venting and depressurizing, preventing the sleeve 72 from generating resistance due to the compression of the lubricating oil in the inner hole during high-speed reciprocating motion, thus ensuring smooth movement.

[0082] When the camshaft 2 rotates to drive the slider assembly 3 to perform vertical reciprocating motion, the second plane 312 of the slider assembly 3 contacts the working plane 721 of the sleeve 72 and applies force. When the slider assembly 3 moves upward, the elastic force of the elastic reset member 73 pushes the sleeve 72 to slide upward along the guide rod 71; when the slider assembly 3 moves downward, it compresses the elastic reset member 73, so that the working plane 721 of the sleeve 72 always remains in contact with the second plane 312 of the slider assembly 3.

[0083] Reference Figure 1 The camshaft 2 is provided with thrust bushings 8 at both ends. The thrust bushings 8 are interference-fitted to the support journal 22 of the camshaft 2. One of the thrust bushings 8 is slidably fitted with the first support bushing 9 provided in the pump body 1, and the other thrust bushing 8 is slidably fitted with the second support bushing 1002 installed in the flange 1001, which is used to provide axial positioning and rotational support for the camshaft 2.

[0084] The thrust sleeve 8 is an annular sleeve structure. Its inner hole is fixedly connected to the support journal 22 of the camshaft 2 by an interference fit, ensuring that the thrust sleeve 8 and the camshaft 2 form a rigid whole with no relative movement between them. When the camshaft 2 rotates, it drives the thrust sleeve 8 to rotate synchronously. The outer circle of one of the thrust sleeves 8 forms a sliding fit with the inner hole of the first support bushing 9 provided in the pump body 1. The first support bushing 9 is interference-fitted into the bushing mounting seat hole of the pump body 1, providing stable rotational support for the camshaft 2.

[0085] The end face 81 of the thrust sleeve 8 forms an axial fit with the adjacent component. When the camshaft 2 is subjected to axial force, the end face 81 of the thrust sleeve 8 contacts the end face of the adjacent component, restricting the axial movement of the camshaft 2 and providing it with precise axial positioning. Through the fit between the shoulder surface of the thrust sleeve 8 and the pump body 1 and the flange end face, the axial movement of the camshaft 2 can be controlled within a small range.

[0086] Reference Figure 5The thrust sleeve 8 has circumferentially distributed lubricating oil grooves 82 on its end face 81. These lubricating oil grooves 82 penetrate the end face 81, forming multiple radial or arc-shaped oil channels. Lubricating oil is delivered to the sliding mating surface through the oil holes 83 on the thrust sleeve 8, and some lubricating oil is guided into the lubricating oil grooves 82 on the end face 81. When the camshaft 2 rotates, the thrust sleeve 8 rotates synchronously with the camshaft 2, and the lubricating oil forms a load-bearing oil film between the thrust sleeve 8 and the sliding mating surfaces of the first support bushing 9 and the second support bushing 1002, achieving rotational support and lubrication. At the same time, the lubricating oil entering the lubricating oil grooves 82 on the end face 81 forms a dynamic lubricating film between the end face 81 and the end faces of adjacent components. On the one hand, this reduces end face friction loss, and on the other hand, it forms an oil film support between the two end faces, helping to limit the axial movement of the camshaft 2 to ≤0.5mm.

[0087] Reference Figure 4 and Figure 5 The camshaft 2 has a lubrication channel 23 inside, which has an oil inlet 231 and at least one oil outlet 232. The oil inlet 231 is located at the end of the camshaft 2. The oil outlet 232 is located on the outer surface of the eccentric cam portion 21 and the outer surface of the support journal 22, and is used to guide the lubricating oil to the corresponding sliding mating surfaces. The end face of the camshaft 2 has a rectangular connection port 24 for connecting to the oil pump drive shaft to achieve synchronous rotation drive.

[0088] The lubrication channel 23 extends along the axial direction of the camshaft 2 and is formed by center drilling or casting, serving as the main channel for lubricating oil delivery. The oil inlet 231 is located at the end of the camshaft 2 and connects to the external lubrication system. A sealing ring groove 26 is provided around the oil inlet 231, and a sealing ring is embedded within the groove to prevent lubricating oil leakage from the end of the camshaft 2. When the camshaft 2 rotates, lubricating oil from the external lubrication system continuously enters the lubrication channel 23 through the oil inlet 231, providing a stable oil source for the entire lubrication system.

[0089] Reference Figure 4 The lubrication channel 23 has multiple oil outlets 232 along its axis. These oil outlets 232 are radial holes that extend from the lubrication channel 23 to the outer surface of the camshaft 2. The positions of the oil outlets 232 are precisely designed to correspond to the key friction pairs requiring lubrication, including oil outlets corresponding to the outer surface of the eccentric cam portion 21 and oil outlets corresponding to the outer surface of the support journal 22. For a camshaft 2 with multiple eccentric cam portions 21 and multiple support journals 22, the lubrication channel 23 is correspondingly provided with multiple oil outlets 232, each aligned with each eccentric cam portion 21 and each support journal 22.

[0090] An oil outlet 232 corresponding to the eccentric cam portion 21 is provided within the contour area of ​​the eccentric cam portion 21. When the camshaft 2 rotates, lubricating oil flows out from the oil outlet 232 and is directly delivered to the outer surface of the eccentric cam portion 21. Since the slider assembly 3 is sleeved on the outside of the eccentric cam portion 21 and slides with it, a continuous lubricating film is formed between the eccentric cam portion 21 and the bushing inner hole of the slider assembly 3. To ensure uniform lubrication, multiple oil outlets 232 corresponding to the eccentric cam portion 21 can be provided, distributed circumferentially or spaced axially, to ensure that the entire sliding contact surface is adequately lubricated. After the lubricating oil is delivered to the outer surface of the eccentric cam portion 21, with the rotation of the camshaft 2 and the relative sliding of the slider assembly 3, the lubricating oil is carried into the sliding fit gap between the eccentric cam portion 21 and the bushing inner hole. Some of the lubricating oil enters the oil groove 322 on the bushing inner hole for storage, and is continuously carried out during the sliding process to replenish the contact surface, forming a continuous and stable lubricating film on the sliding fit surface.

[0091] An oil outlet 232, corresponding to the support journal 22, is located within the area of ​​the support journal 22. Lubricating oil flows out from this outlet 232 and is delivered to the outer surface of the support journal 22. Since a thrust sleeve 8 is interference-fitted onto the support journal 22, and the thrust sleeve 8 slides with the first support bushing 9 and the second support bushing 1002 within the pump body 1, the lubricating oil, after being delivered to the outer surface of the support journal 22 through the oil outlet 232, is guided from the inner bore side of the thrust sleeve 8 to its outer circular surface through the oil hole 83 provided on the thrust sleeve 8. A bearing oil film is formed between the sliding mating surfaces of the thrust sleeve 8 and the first support bushing 9 and the second support bushing 1002, providing rotational support and lubrication for the camshaft 2. Simultaneously, some lubricating oil is introduced into the gap between the end face 81 of the thrust sleeve 8 and the end face of adjacent components through the lubricating oil groove 82 provided on the end face 81 of the thrust sleeve 8, forming a dynamic lubricating film at the end face contact area.

[0092] Reference Figure 1 , Figure 4 and Figure 5 When the camshaft 2 has two or more eccentric cam portions 21, a limiting shaft section 25 is provided on the camshaft 2. The limiting shaft section 25 is located between two adjacent eccentric cam portions 21 and is used to cooperate with the end face of the slider assembly 3 to limit the axial displacement of the slider assembly 3.

[0093] When two or more eccentric cam portions 21 are provided on the camshaft 2, the eccentric cam portions 21 are arranged at intervals along the axial direction of the camshaft 2. Between two adjacent eccentric cam portions 21, a limiting shaft section 25 is provided on the camshaft 2. The limiting shaft section 25 is a section of the outer circular surface on the camshaft 2, and its axial position is precisely located in the midpoint region of the two eccentric cam portions 21. Each eccentric cam portion 21 is fitted with a corresponding slider assembly 3, and in the axial direction of the camshaft 2, the opposite inner end faces of two adjacent slider assemblies 3 are arranged opposite to the two side end faces of the limiting shaft section 25.

[0094] The axial length of the limiting shaft segment 25 is precisely designed to match the axial distance between two adjacent slider assemblies 3. Under normal operating conditions, a small gap is maintained between the end face of the slider assembly 3 and the end face of the limiting shaft segment 25 to avoid motion interference. When the camshaft 2 is subjected to axial force, causing the slider assembly 3 to tend to move axially, the end face of the slider assembly 3 will contact the corresponding end face of the limiting shaft segment 25, thereby preventing the slider assembly 3 from continuing to move axially.

[0095] By cooperating with the end face of the slider assembly 3, the axial movement range of each slider assembly 3 is precisely limited to the area between adjacent limit shaft sections 25, ensuring that the slider assembly 3 always remains in the designed working position, avoiding problems such as interference with adjacent parts or deviation from the correct mating position caused by axial movement, and ensuring the motion accuracy and reliability of the entire drive component.

[0096] The outer cylindrical surface of the limiting shaft section 25 can be hardened to improve wear resistance and withstand the contact load that may be generated on the end face of the slider assembly 3. At the same time, the end face of the limiting shaft section 25 can also be provided with a lubricating oil groove or an oil hole connected to the lubrication channel, so as to guide the lubricating oil to the potential contact area between the limiting shaft section 25 and the end face of the slider assembly 3, thereby reducing frictional loss during end face contact.

[0097] Reference Figure 1 and Figure 6This application embodiment also includes a flange assembly 10, which is disposed on the pump body 1. The flange assembly 10 includes a flange 1001 and a second support bushing 1002. The flange 1001 is provided with a bushing mounting hole 10011, and the second support bushing 1002 is interference-fitted into the bushing mounting hole 10011 for sliding engagement with the camshaft 2 and providing support for the camshaft 2. A lubricating oil chamber 10012 is provided inside the flange 1001, which is connected to the inner cavity 101 of the pump body 1. The lubricating oil chamber 10012 is used to install the oil pump 11. The lubricating oil chamber 10012 is provided with an eccentric groove 10013 and an oil outlet 10014, with the eccentric groove 10013 connecting the lubricating oil chamber 10012 and the oil outlet 10014. The flange 1001 is also provided with a connecting hole 10015, which connects the lubricating oil chamber 10012 and the inner cavity 101 of the pump body 1. A sealing ring groove 10016 is provided at the contact surface between the flange 1001 and the pump body 1.

[0098] The flange assembly 10 is located at one end of the pump body 1 and is installed in the flange mounting hole of the pump body 1. It is fixed and locked to the pump body 1 by multiple connecting screws to form a rigid connection. As an extension of the pump body 1, the flange assembly 10 not only provides support for the camshaft 2, but also integrates lubrication and oil pump mounting functions.

[0099] The bushing mounting hole 10011 is a precision-machined round hole that penetrates or extends along the axial direction of the flange 1001. The second support bushing 1002 is fitted into the bushing mounting hole 10011 with an interference fit, forming a fixed connection. The inner hole of the second support bushing 1002 forms a sliding fit with the outer circle of the support journal of the camshaft 2 or the thrust sleeve 8, providing rotational support for the end of the camshaft 2. The second support bushing 1002 is made of wear-resistant material and its replaceable design facilitates maintenance.

[0100] The lubricating oil chamber 10012 is a hollow structure inside the flange 1001, which is connected to the inner cavity 101 of the pump body 1. It is used to store lubricating oil and also serves as the mounting base for the oil pump 11. The oil pump 11 is installed in the lubricating oil chamber 10012, and its drive shaft is connected to the rectangular connection port 24 at the end of the camshaft 2. It is driven by the camshaft 2 to rotate synchronously and realize the oil delivery function.

[0101] The eccentric groove 10013 is a circumferentially oriented groove located off-center from the axis of the flange 1001. One end of the groove is connected to the lubricating oil chamber 10012, and the other end is connected to the oil outlet 10014. When the camshaft 2 drives the oil pump 11 to rotate, the lubricating oil in the lubricating oil chamber 10012 flows circumferentially under centrifugal force, accumulates in the eccentric groove 10013, and is guided towards the oil outlet 10014, thereby delivering the lubricating oil from the flange lubricating oil chamber 10012 to the lubricating oil chamber of the pump body 1.

[0102] The oil outlet 10014 is an oil hole that penetrates the wall of the flange 1001. One end is connected to the eccentric groove 10013, and the other end is connected to the lubricating oil chamber of the pump body 1. The lubricating oil guided by the eccentric groove 10013 flows out of the flange lubricating oil chamber 10012 through the oil outlet 10014 and enters the lubricating oil chamber of the pump body 1, realizing the recycling of lubricating oil.

[0103] The connecting hole 10015 is a through hole that penetrates the wall of the flange 1001 and directly connects the flange lubricating oil chamber 10012 with the inner cavity 101 of the pump body 1. It is used to balance the pressure between the two cavities, avoid resistance caused by changes in internal pressure of the lubricating oil chamber 10012 or air retention, ensure that the lubricating oil can flow smoothly, and can also serve as an auxiliary return oil channel.

[0104] The sealing groove 10016 is an annular groove circumferentially formed along the end face of the flange 1001, and an O-ring is embedded therein. When the flange assembly 10 is tightened onto the pump body 1 by connecting screws, the O-ring is pressed between the contact surfaces of the flange 1001 and the pump body 1, forming a reliable seal and preventing the lubricating oil inside the lubricating oil chamber of the pump body 1 from leaking to the external environment from the joint surface between the two.

[0105] A sealing ring groove is also provided between the oil pump 11 and the mounting surface of the flange 1001, and a sealing ring is embedded in the sealing ring groove to prevent lubricating oil from leaking from the mounting point of the oil pump 11.

[0106] Reference Figure 1 The pump body 1, serving as the mounting base for the entire drive component, is made of high-strength cast iron or aluminum alloy. The inner cavity 101 of the pump body 1 houses the aforementioned camshaft 2, slider assembly 3, pump cover assembly 4, plunger 5, and elastic element 6.

[0107] In the inner cavity 101 of the pump body 1, the lubricating oil chamber of the pump body 1 is connected to the outside through the oil outlet 103. The oil outlet 103 can control the internal liquid level of the lubricating oil chamber. In order to keep the first plane 311 always immersed, the position of the oil outlet 103 needs to be higher than the position of the first plane 311.

[0108] A sealing ring groove 102 is provided at the mating surface of the pump body 1 and the pump cover assembly 4. An O-ring is embedded in the sealing ring groove 102 to prevent the lubricating oil in the inner cavity 101 from leaking from the mating surface.

[0109] A sealing groove 10016 is provided at the mating surface between flange 1001 and pump body 1. An O-ring is embedded in the sealing groove 10016 to ensure the sealing reliability of the mating surface.

[0110] When the camshaft 2 rotates, lubricating oil from the external lubrication system continuously enters the lubrication channel 23 through the oil inlet 231 at the end of the camshaft 2. Under the combined action of centrifugal force and oil pressure, the lubricating oil flows along the lubrication channel 23 and is precisely delivered to the various parts requiring lubrication through the oil outlets 232.

[0111] For the support journal 22, after the lubricating oil flows out from the oil outlet 232, it is delivered to the outer surface of the support journal 22, and then guided to the outer circular surface of the thrust sleeve 8 through the oil hole 83 on the thrust sleeve 8, forming a load-bearing oil film between the sliding mating surfaces of the thrust sleeve 8 and the first support bushing 9 and the second support bushing 1002. At the same time, some lubricating oil is introduced into the gap between the end face 81 of the thrust sleeve 8 and the end face of the adjacent component through the lubricating oil groove 82 on the end face 81 of the thrust sleeve 8, forming a dynamic lubricating film at the end face contact area.

[0112] For the eccentric cam section 21, after the lubricating oil flows out from the oil outlet 232, it is directly delivered to the outer surface of the eccentric cam section 21. As the camshaft 2 rotates and the slider assembly 3 slides relative to each other, the lubricating oil is carried into the sliding fit gap between the eccentric cam section 21 and the inner hole of the bushing. Some of the lubricating oil enters the oil groove 322 on the inner hole of the bushing for storage and is continuously carried out during the sliding process, forming a continuous and stable lubricating film on the sliding fit surface.

[0113] For the guide rod assembly 7, the lubrication spiral groove 711 on the guide rod 71 stores and guides the lubricating oil to be evenly distributed, the straight groove 723 on the sleeve 72 ensures smooth lubrication, and the oil guiding slope 724 on the working plane 721 forms a wedge-shaped oil film between the working plane 721 and the second plane 312.

[0114] Meanwhile, the lubricating oil stored in the lubricating oil chamber 10012 of the flange assembly 10 is transported to the lubricating oil chamber of the pump body 1 through the eccentric groove 10013 and the oil outlet 10014. The connecting hole 10015 balances the pressure of the two chambers to ensure smooth circulation of lubricating oil.

[0115] The entire lubrication system ensures that all key friction pairs receive adequate lubrication under high-speed and heavy-load conditions through multi-point precise oil supply and multi-level sealing protection, while effectively preventing lubricant leakage, significantly reducing friction loss, and extending the service life of components.

[0116] This application achieves the following technical effects through the aforementioned integrated structural design and multi-dimensional lubrication system:

[0117] First, by using the fitting structure of the slider assembly 3 fitted onto the eccentric cam part 21, the traditional independent guide piston is replaced, which greatly reduces the overall volume of the pump body 1 and achieves a compact layout.

[0118] Second, by utilizing the synergistic effect of the force of the plunger 5 and the force of the guide rod assembly 7 on the first plane 311 and the second plane 312 that are relatively set on the slider assembly 3, the reciprocating motion and flipping of the slider assembly 3 are effectively restricted without an independent guide structure, thereby improving motion stability.

[0119] Third, by setting a lubrication channel 23 inside the camshaft 2, lubricating oil is accurately delivered to the sliding mating surfaces of the eccentric cam part 21 and the slider assembly 3, the thrust bushing 8 and the first support bushing 9, and the second support bushing 1002. A dynamic lubrication film is formed in the axial clearance through the lubrication groove 82 on the end face of the thrust bushing 8, which significantly reduces the wear of key friction pairs while restricting axial movement.

[0120] Fourth, by setting multiple sealing structures, including the sealing ring groove at the joint surface of the pump body 1 and each component, the sealing ring groove at the end of the camshaft 2, and the sealing ring groove of the flange assembly 10, a complete sealing protection system is formed to effectively prevent lubricating oil leakage.

[0121] Fifth, by integrating the lubricating oil chamber 10012, eccentric groove 10013, and connecting hole 10015 into the flange assembly 10, the circulation and pressure balance of the lubricating oil are realized, simplifying the layout of external pipelines.

[0122] In summary, this application solves the problems of complex structure, large size, insufficient lubrication, and high friction loss of traditional high-pressure oil pumps, and meets the stringent requirements of modern engines for high-precision oil supply, compact layout, and long service life of high-pressure oil pumps.

Claims

1. A compact high-pressure oil pump drive component, characterized in that, include: Pump body (1), the pump body (1) having an inner cavity; A camshaft (2) is rotatably supported in the cavity of the pump body (1), and the camshaft (2) has at least one eccentric cam portion (21). The slider assembly (3) is sleeved outside the eccentric cam part (21) and slides in cooperation with the eccentric cam part (21) to convert the axial rotational motion of the camshaft (2) into the vertical reciprocating motion of the slider assembly (3). Pump cover assembly (4), which is fixedly mounted on the pump body (1); A plunger (5) is slidably disposed in the pump cover assembly (4) along the vertical direction, and one end of the plunger (5) abuts against the slider assembly (3); An elastic element (6) is disposed between the pump cover assembly (4) and the plunger (5) to provide a restoring force to the plunger (5) and to keep the plunger (5) in contact with the slider assembly (3); Driven by the eccentric cam (21), the slider assembly (3) overcomes the elastic force of the elastic element (6) to perform the vertical reciprocating motion and supplies oil through the plunger (5).

2. The compact high-pressure oil pump drive component according to claim 1, characterized in that, The slider assembly (3) includes a slider (31), which has a first plane (311) and a second plane (312) disposed opposite to each other. The first plane (311) abuts against the end of the plunger (5), and the second plane (312) is used to slide with an external guide. Driven by the eccentric cam (21), the slider assembly (3) performs the vertical reciprocating motion. The force exerted by the plunger (5) on the first plane (311) and the force exerted by the external guide on the second plane (312) are combined to limit the flipping of the slider assembly (3) during the reciprocating motion.

3. The compact high-pressure oil pump drive component according to claim 2, characterized in that, The slider (31) is provided with a bushing mounting seat hole (313) and a guide groove (314); The slider assembly (3) further includes a bushing (32), the outer circle of which is provided with a guide protrusion (321). The bushing (32) is interference-fitted into the bushing mounting seat hole (313), and the guide protrusion (321) cooperates with the guide groove (314). The bushing (32) is slidably engaged with the eccentric cam portion (21).

4. The compact high-pressure oil pump drive component according to claim 2 or 3, characterized in that, It also includes a guide rod assembly (7), which is fixedly mounted on the pump body (1). The guide rod assembly (7) slides in cooperation with the second plane (312) to guide the vertical reciprocating motion of the slider assembly (3) and to cooperate in restricting the flipping of the slider assembly (3).

5. The compact high-pressure oil pump drive component according to claim 4, characterized in that, The guide rod assembly (7) includes a guide rod (71), a sleeve (72), and an elastic reset member (73); The guide rod (71) is fixedly mounted on the pump body (1), and the outer guide surface of the guide rod (71) is provided with a wear-resistant coating and a lubrication spiral groove (711); The sleeve (72) is sleeved on the guide rod (71) and slides in cooperation with the guide rod (71). One end of the sleeve (72) is provided with a working plane (721), which slides in cooperation with the second plane (312). The surface of the working plane (721) is provided with a wear-resistant coating. The other end of the sleeve (72) is provided with a spring abutment surface (722). The sleeve (72) is provided with a straight groove (723), the straight groove (723) connects the inner hole of the sleeve (72) with the external space, and the edge of the working plane (721) is provided with an oil guiding slope (724); The elastic reset member (73) is sleeved on the guide rod (71) and located between the guide rod (71) and the spring contact surface (722), and is used to provide a reset force to the sleeve (72) and limit the range of motion of the sleeve (72).

6. The compact high-pressure oil pump drive component according to claim 1, characterized in that, The camshaft (2) is provided with thrust bushings (8) at both ends, and the thrust bushings (8) are interference-fitted onto the support journal (22) of the camshaft (2); One of the thrust bushings (8) is slidably fitted with a first support bushing (9) provided inside the pump body (1) to provide axial positioning and rotational support for the camshaft (2).

7. The compact high-pressure oil pump drive component according to claim 6, characterized in that, The camshaft (2) is provided with a lubrication channel (23) inside, the lubrication channel (23) having an oil inlet (231) and at least one oil outlet (232); The oil inlet (231) is located at the end of the camshaft (2); The oil outlet (232) is provided on the outer surface of the eccentric cam portion (21) and the outer surface of the support journal (22) to guide the lubricating oil to the corresponding sliding mating surface.

8. The compact high-pressure oil pump drive component according to claim 1, characterized in that, When the camshaft (2) has two or more eccentric cam portions (21), a limiting shaft section (25) is provided on the camshaft (2). The limiting shaft section (25) is located between two adjacent eccentric cam portions (21) and is used to cooperate with the end face of the slider assembly (3) to limit the axial displacement of the slider assembly (3).

9. The compact high-pressure oil pump drive component according to claim 6, characterized in that, It also includes a flange assembly (10) disposed on the pump body (1), the flange assembly (10) including a flange (1001) and a second support bushing (1002); The flange (1001) is provided with a bushing mounting hole (10011), and the second support bushing (1002) is interference-fitted into the bushing mounting hole (10011) for sliding cooperation with another thrust bearing (8) on the camshaft (2) to provide support for the camshaft (2); The flange (1001) is provided with a lubricating oil chamber (10012), which is connected to the inner cavity of the pump body (1). The lubricating oil chamber (10012) is used to install the oil pump (11). The lubricating oil cavity (10012) is provided with an eccentric groove (10013) and an oil outlet (10014), and the eccentric groove (10013) connects the lubricating oil cavity (10012) and the oil outlet (10014); The flange (1001) is also provided with a connecting hole (10015), which connects the lubricating oil chamber (10012) with the inner cavity of the pump body (1); A sealing ring groove (10016) is provided at the contact surface between the flange (1001) and the pump body (1).

10. A high-pressure oil pump, characterized in that, It includes a compact high-pressure oil pump drive component as described in any one of claims 1 to 9.

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