High performance gasoline filter

Abstract

The application relates to the technical field of gasoline filters, in particular to a high-performance gasoline filter. The high-performance gasoline filter comprises an upper shell and a lower shell which are connected with each other, a turbine shell and a valve pipe which are fixed on the lower shell, a turbine driving unit arranged in the turbine shell, a turbine shaft driven to rotate by gasoline flow and connected with the turbine driving unit in a transmission mode, an oil guide pipe communicated with the turbine shell, a valve disc fixed on the top of the lower shell, a flow equalizing cylinder fixed on the valve disc, an oil equalizing cavity communicated with the oil guide pipe and arranged between the flow equalizing cylinder and the upper shell, oil injection holes communicated with the oil equalizing cavity and uniformly distributed on the flow equalizing cylinder, and a support fixed on the turbine shell and slidably connected with an X-direction sliding frame. The high-performance gasoline filter has the beneficial effects that the oil equalizing cavity is formed between the flow equalizing cylinder and the upper shell, the oil injection holes which are uniformly distributed on the side wall of the flow equalizing cylinder and whose axes are perpendicular to the filter core are matched, gasoline is uniformly injected to the whole outer circumferential surface of the filter core in a radial direction, and the traditional oil inlet mode of being concentrated in a local part is changed.

Description

Technical Field

[0001] This invention relates to the field of gasoline filter technology, specifically high-performance gasoline filters. Background Technology

[0002] The fuel filter is a key component of the automotive engine's fuel supply system. Its main function is to filter out water, impurities, and gum from the gasoline to protect precision components such as fuel injectors and fuel pumps, ensuring the engine's normal operation. Existing technologies have disclosed various fuel filter structures. For example, patent document CN104564459A discloses a fuel filter that uses a plastic shell and end caps connected by friction welding, and employs a direct assembly method between the filter element and the shell. This aims to solve the problems of complex manufacturing processes, high costs, and the need for glue to bond the filter element in traditional metal-shell filters. This technical solution has achieved significant progress in simplifying the manufacturing process and reducing costs. However, in the long-term use and research process, existing fuel filters still have the following technical problems: Most existing filter elements are static single-point oil inlet structures. As usage time increases, intercepted impurities quickly accumulate locally on the filter element surface, causing local blockages. This leads to a sharp decrease in effective filtration area and increased oil circuit resistance, forcing users to replace the filter element frequently, increasing operating costs and inconvenience. To achieve self-cleaning, some solutions use high-frequency or strong vibration and impact to remove impurities from the filter element surface. However, gasoline filter elements are mostly made of paper or non-woven fabric and other fibrous materials with limited structural strength. High-frequency and strong mechanical vibration can easily cause micro-cracks, fatigue fractures, or even delamination in the filter paper fibers. While achieving cleaning, this severely damages the structural integrity and filtration accuracy of the filter element itself. Based on this, the present invention provides a high-performance gasoline filter to solve the problems mentioned in the background art. Summary of the Invention

[0003] This invention addresses the technical problems existing in the prior art by providing a high-performance gasoline filter. This solves the problem that most existing filter elements have a static single-point oil inlet structure. As the usage time increases, the intercepted impurities will quickly accumulate locally on the surface of the filter element, forming a local blockage phenomenon, which leads to a sharp decrease in the effective filtration area and an increase in oil circuit resistance.

[0004] The technical solution of this invention to solve the above-mentioned technical problems is as follows: a high-performance gasoline filter, comprising an upper housing and a lower housing connected to each other, and further comprising: The turbine housing and valve tube are both fixed on the lower housing. The turbine housing contains a turbine drive unit, which is connected to a turbine shaft driven to rotate by the flow of gasoline. The turbine housing is connected to an oil guide pipe. The distribution plate is fixedly mounted on the top of the lower housing. A flow equalization cylinder is fixedly mounted on the distribution plate. An oil equalization chamber communicating with the oil guide pipe is provided between the flow equalization cylinder and the upper housing. Oil injection holes communicating with the oil equalization chamber are evenly distributed on the flow equalization cylinder. A bracket is fixedly mounted on the turbine housing. An X-axis slide is slidably connected to the bracket, and a Z-axis slide is slidably connected to the X-axis slide. Reciprocating springs are installed between the X-axis slide and the bracket, and between the Z-axis slide and the X-axis slide. A first wheel shaft is rotatably connected to the bracket, and a second wheel shaft is rotatably connected to the X-axis slide. Both the first and second wheel shafts are connected to the turbine shaft via a linkage module. The first wheel shaft is equipped with a first reciprocating unit that drives the X-axis slide to reciprocate along the X-axis direction, and the second wheel shaft is equipped with a second reciprocating unit that drives the Z-axis slide to reciprocate along the Z-axis direction. An intermittent shaft and a gear shaft are rotatably connected to the Z-axis slide. A half-tooth bevel gear is fixedly mounted on the gear shaft, and a full-tooth bevel gear that meshes with the half-tooth bevel gear is mounted on the intermittent shaft. A transmission slot is provided at the top of the intermittent shaft. The filter element is installed inside the upper housing and inserted into the transmission slot. Corrugated sealing discs are rotatably connected to the top of the filter element and the Z-axis slide. The corrugated sealing discs on the filter element are fixedly connected to the upper housing, and the corrugated sealing discs on the Z-axis slide are fixedly connected to the distribution plate. The top of the upper housing is equipped with a clean oil drain pipe. A valve mechanism is configured to connect the valve tube to the drive slot and the interior of the filter element when the filter element is clogged.

[0005] Based on the above technical solution, the present invention can be further improved as follows.

[0006] Preferably, the turbine drive unit includes an oil inlet pipe fixed on the lower housing, the oil inlet pipe being connected to the turbine housing, turbine blades being arrayed on the turbine shaft at positions corresponding to the inner side of the turbine housing, the turbine shaft being coaxially arranged with the valve pipe, and the turbine shaft being rotatably sleeved on the outer periphery of the valve pipe via bearings.

[0007] Preferably, the linkage module includes a drive shaft and a rotating shaft rotatably connected to the bracket. A first synchronous drive belt is connected between the drive shaft and the rotating shaft. Both the drive shaft and the turbine shaft are equipped with linkage bevel gears, which mesh orthogonally. A synchronous groove with an open tail end and slidably connected to the rotating shaft is provided on the second wheel shaft. The cross-section of the synchronous groove and the rotating shaft are both regular hexagonal. A second synchronous drive belt is connected to the second wheel shaft. The second synchronous drive belt is connected to the gear shaft. A tensioning unit is provided on the Z-axis slide to keep the second synchronous drive belt taut.

[0008] Preferably, the tensioning unit includes a tensioning slider slidably connected to a Z-axis slide, a tensioning spring is mounted on the side of the tensioning slider, the other end of the tensioning spring is fixedly connected to the Z-axis slide, a tensioning guide wheel is rotatably connected to the tensioning slider, and the tensioning guide wheel is driven by a second synchronous transmission belt.

[0009] Preferably, both the first reciprocating unit and the second reciprocating unit include a reciprocating guide wheel and two cams. The outer contours of the two cams alternately abut against the reciprocating guide wheel, and the pushing strokes of the two cams on the reciprocating guide wheel are different. The reciprocating guide wheel in the first reciprocating unit is rotatably connected to the X-axis slide, and the two cams on it are symmetrically installed on the outer periphery of the first wheel shaft. The reciprocating guide wheel in the second reciprocating unit is rotatably connected to the Z-axis slide, and the two cams on it are symmetrically installed on the outer periphery of the second wheel shaft.

[0010] Preferably, the bottom end of the filter element is fixedly connected to a sealing tube that is connected to the transmission slot. The cross-section of the sealing tube and the transmission slot is a regular hexagon. The outer periphery of the sealing tube and the distribution plate and the bottom end of the flow equalization cylinder are all fixedly fitted with sealing rings. The axis of the oil injection hole is perpendicular to the axis of the filter element.

[0011] Preferably, the valve mechanism includes a bypass valve module fixed to the bottom of the valve tube, a corrugated metal section is provided at the top of the valve tube, a flow channel with openings at both ends is provided in the intermittent shaft, the flow channel at the bottom of the intermittent shaft is rotatably connected to the corrugated metal section, the flow channel at the top of the intermittent shaft is connected to the sealing tube through a transmission slot, a clean oil outlet is provided at the top of the filter element and is connected to the clean oil drain pipe, and a one-way oil outlet valve is installed in the clean oil drain pipe.

[0012] Preferably, the flow equalization cylinder is a hollow cylindrical structure with an open top. The flow equalization cylinder, the upper shell, and the lower shell are all made of 304 stainless steel. A drain valve communicating with the oil equalization chamber is installed on the side of the upper shell.

[0013] Preferably, the reciprocating direction of the Z-axis carriage is parallel to the axis of the filter element.

[0014] The beneficial effects of this invention are: 1. This invention forms an oil equalization chamber between the flow equalization cylinder and the upper shell. Combined with fuel injection holes evenly distributed on the sidewall of the flow equalization cylinder and perpendicular to the filter element's axis, gasoline is radially and uniformly sprayed onto the entire outer circumference of the filter element, changing the traditional mode of concentrated fuel intake. Simultaneously, the gasoline flow drives the turbine shaft to rotate, which, via a linkage module, synchronously drives the first and second wheel shafts. Through two cams with different strokes in the first and second reciprocating units, these cams alternately abut against the reciprocating guide wheels. With the help of reciprocating springs, this drives the X-axis slide and Z-axis slide to perform alternating variable-stroke reciprocating motions in directions perpendicular to and parallel to the filter element's axis, respectively. Then... The intermittent meshing transmission of the half-tooth bevel gear and the full-tooth bevel gear causes the intermittent shaft to drive the filter element to perform intermittent rotational motion, ultimately realizing the composite motion of the filter element in three-dimensional space, including reciprocating motion with the vertical axis, reciprocating motion with the parallel axis, and intermittent rotation. The synergistic effect of the above multi-dimensional motions ensures that every outer surface of the filter element can pass through the flushing area of ​​the oil injection hole in sequence. Impurities are continuously and evenly stripped and settled to the bottom of the oil equalization chamber, effectively avoiding local clogging, significantly improving the effective filtration area utilization rate of the filter element, extending the filter element replacement cycle, and solving the problem of frequent replacement due to the filter element being stationary in the prior art.

[0015] 2. This invention transmits power to the first and second wheel shafts through a linkage module. By utilizing the alternating contact between two cams with different strokes and reciprocating guide wheels, a low-amplitude, low-frequency variable-stroke reciprocating motion is generated. Combined with the gentle intermittent rotation, this creates a gentle shearing and vibration force on the filter element, rather than the traditional high-frequency strong impact. This low-speed, low-amplitude, variable-stroke composite motion can effectively remove impurities attached to the surface of the filter element and deep blockages in the pores. At the same time, due to the small motion amplitude, low frequency, and gentle impact force, fatigue damage, crack propagation, and structural delamination of the filter paper fibers are completely avoided, ensuring the structural integrity and filtration accuracy of the filter element during long-term use. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of the high-performance gasoline filter of the present invention; Figure 2 For the present invention Figure 1 A schematic diagram of the cross-sectional structure; Figure 3 For the present invention Figure 2 A magnified schematic diagram of the partial structure at point A in the middle; Figure 4 This is a schematic diagram of the distribution plate and flow equalization cylinder of the present invention; Figure 5 This is a schematic diagram of the filter element of the present invention; Figure 6 This is a schematic diagram of the structure of the corrugated sealing disc and transmission slot of the present invention; Figure 7 For the present invention Figure 6 A magnified view of the structure at point B in the middle; Figure 8 This is a schematic diagram of the Z-axis carriage and support structure of the present invention; Figure 9 This is a schematic diagram of the structure of the rotating shaft and cam of the present invention; Figure 10 This is a schematic diagram of the structure of the second wheel shaft and the reciprocating guide wheel of the present invention; Figure 11 This is a schematic diagram of the structure of the toothed shaft and the half-tooth bevel gear of the present invention.

[0017] The attached diagram lists the components represented by each number as follows: 1. Upper housing; 2. Lower housing; 3. Turbine housing; 4. Valve pipe; 5. Bracket; 6. Filter element; 7. Corrugated sealing disc; 101. Clean oil drain pipe; 102. Drain valve; 201. Flow distribution plate; 202. Flow equalization cylinder; 203. Oil equalization chamber; 204. Injection hole; 301. Turbine shaft; 302. Oil inlet pipe; 303. Turbine blades; 304. Oil guide pipe; 401. Bypass valve module; 402. Corrugated metal section; 5 01. X-axis slide; 502. Z-axis slide; 503. Reciprocating spring; 504. First wheel axle; 505. Second wheel axle; 506. Intermittent shaft; 507. Gear shaft; 508. Half-tooth bevel gear; 509. Transmission slot; 510. Transmission shaft; 511. Rotating shaft; 512. Tensioning slider; 513. Tensioning spring; 514. Tensioning guide wheel; 515. Reciprocating guide wheel; 516. Cam; 601. Sealing tube. Detailed Implementation

[0018] The principles and features of the present invention are described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0019] The present invention provides the following preferred embodiments. like Figure 1-11 As shown, a high-performance gasoline filter includes an upper housing 1 and a lower housing 2 that are connected to each other; In a preferred embodiment, both the lower housing 2 and the upper housing 1 are provided with threaded connection holes, and a locking element is provided in the threaded connection holes. A sealing gasket is provided at the connection between the upper housing 1 and the lower housing 2. Also includes: Turbine housing 3 and valve pipe 4 are both fixedly mounted on lower housing 2. Turbine housing 3 is equipped with a turbine drive unit. The turbine drive unit is connected to a turbine shaft 301 that is driven to rotate by the flow of gasoline. A guide pipe 304 is connected to turbine housing 3. In a preferred embodiment, the turbine shaft 301 is a hollow tubular structure with openings at both ends; The turbine drive unit includes an oil inlet pipe 302 fixed on the lower housing 2. The oil inlet pipe 302 is connected to the turbine housing 3 and is arranged along the tangential direction of the turbine housing 3. The oil inlet port of the oil inlet pipe 302 is connected to the oil outlet port of the automobile oil pump. Turbine blades 303 are arranged on the turbine shaft 301 at positions corresponding to the inner side of the turbine housing 3. The turbine shaft 301 is coaxially arranged with the valve pipe 4. The turbine shaft 301 is rotatably sleeved on the outer periphery of the valve pipe 4 through bearings. In operation, gasoline enters the tangentially arranged fuel inlet pipe 302 from the car fuel pump, impacts the turbine blades 303 inside the turbine housing 3 at high speed, and drives the turbine shaft 301 to rotate coaxially around the valve pipe 4. The above structure enables oil-driven, non-electrical operation, simplifies the overall filter structure, and reduces manufacturing costs and the risk of electrical component failure. The turbine blade 303 adopts a high torque optimized design: its helix angle is set to 45°-60°, the number of blades is 8-12, and they are evenly distributed along the circumference of the turbine shaft 301; This design can still enable the turbine shaft 301 to achieve a stable rotation of 5-20 r / min under idling conditions with a gasoline flow rate of only 1.5-3.5 L / h and a pressure of 80-120 kPa. The turbine shaft 301 and valve pipe 4 are arranged in a coaxial nested manner, making full use of the internal radial space of the filter, making the overall structure more compact and suitable for the narrow installation environment of the car engine compartment. The tangential oil inlet design maximizes the use of the impact kinetic energy of gasoline, significantly improves the output torque of the turbine shaft 301, and ensures that the subsequent self-cleaning mechanism can operate stably under different oil pressure conditions. The distribution plate 201 is fixedly mounted on the top of the lower housing 2. A flow equalization cylinder 202 is fixedly mounted on the distribution plate 201. An oil equalization chamber 203 communicating with the oil guide pipe 304 is provided between the flow equalization cylinder 202 and the upper housing 1. Oil injection holes 204 communicating with the oil equalization chamber 203 are evenly distributed on the flow equalization cylinder 202. The flow equalization cylinder 202 is a hollow cylindrical structure with an open top. The flow equalization cylinder 202, the upper shell 1 and the lower shell 2 are all made of 304 stainless steel. The side of the upper shell 1 is equipped with a drain valve 102 that communicates with the oil equalization chamber 203. The axis of the oil injection hole 204 is perpendicular to the axis of the flow equalization cylinder 202. The diameter of the oil injection holes 204 evenly distributed on the flow equalizer 202 is 2mm, and the hole spacing is 8mm. In operation, the gasoline delivered by the oil guide pipe 304 first fills the oil equalization chamber 203, forming an annular pressure-stabilizing oil chamber between the flow equalization cylinder 202 and the upper housing 1. Then, it is evenly sprayed radially onto the entire outer circumference of the filter element 6 through the oil injection holes 204 evenly distributed on the side wall of the flow equalization cylinder 202, whose axis is perpendicular to the filter element 6. The above structural design solves the problems of concentrated oil intake, insufficient utilization of filter element 6 filtration area, and rapid local clogging in traditional filters. The radial vertical oil inlet method allows gasoline to evenly flush the outer surface of the filter element 6, which, combined with the movement of the filter element 6, greatly improves the impurity flushing and self-cleaning effect. 304 stainless steel has excellent resistance to gasoline corrosion and impact, preventing metal rust from contaminating gasoline and extending the overall service life of the filter. The hollow structure with an opening at the top of the flow equalization cylinder 202 provides ample space for the reciprocating motion of the filter element 6 in the X and Z directions, while not affecting the uniform distribution of the oil. The bracket 5 is fixedly mounted on the turbine housing 3. An X-axis slide 501 is slidably connected to the bracket 5. A Z-axis slide 502 is slidably connected to the X-axis slide 501. Reciprocating springs 503 are installed between the X-axis slide 501 and the bracket 5, and between the Z-axis slide 502 and the X-axis slide 501. A first wheel axle 504 is rotatably connected to the bracket 5. A second wheel axle 505 is rotatably connected to the X-axis slide 501. Both the first wheel axle 504 and the second wheel axle 505 are connected to the turbine shaft 301 through a linkage module. An X-axis guide rail is fixedly mounted on the bracket 5 along the X-axis direction, and the X-axis slide 501 is slidably connected to the X-axis guide rail through the first slider. The X-axis slide 501 is fixedly provided with a Z-axis guide rail along the Z-axis direction, and the Z-axis slide 502 is slidably connected to the Z-axis guide rail through a second slider. In a preferred embodiment, the linkage module includes a drive shaft 510 and a rotating shaft 511 rotatably connected to the bracket 5. A first synchronous drive belt is connected between the drive shaft 510 and the rotating shaft 511. Both the drive shaft 510 and the turbine shaft 301 are equipped with linkage bevel gears, which mesh orthogonally. A synchronous groove with an open tail end and slidably connected to the rotating shaft 511 is provided on the second wheel shaft 505. The cross-sections of the synchronous groove and the rotating shaft 511 are both regular hexagonal. A second synchronous drive belt is connected to the second wheel shaft 505. The second synchronous drive belt is connected to the gear shaft 507. A tensioning unit is provided on the Z-axis slide 502 to keep the second synchronous drive belt taut. The tensioning unit includes a tensioning slider 512 slidably connected to the Z-axis slide 502. A tensioning spring 513 is installed on the side of the tensioning slider 512. The other end of the tensioning spring 513 is fixedly connected to the Z-axis slide 502. A tensioning guide wheel 514 is rotatably connected to the tensioning slider 512. The tensioning guide wheel 514 is connected to the second synchronous transmission belt. In operation, the rotational power of the turbine shaft 301 is transmitted to the transmission shaft 510 through the orthogonally meshing linkage bevel gears, and then drives the rotating shaft 511 to rotate via the first synchronous transmission belt. The rotating shaft 511 drives the second wheel shaft 505 to rotate synchronously through the synchronous groove with a regular hexagonal cross section, and allows the second wheel shaft 505 to slide axially with the X-direction slide 501 and the Z-direction slide 502; The second wheel shaft 505 drives the gear shaft 507 to rotate via the second synchronous transmission belt. The tension spring 513 constantly pushes the tension slider 512 to drive the tension guide wheel 514 to press the second synchronous transmission belt, maintaining the tension of the transmission belt during the full-stroke reciprocating motion of the Z-axis slide 502.

[0020] The first axle 504 is provided with a first reciprocating unit that drives the X-axis slide 501 to reciprocate along the X-axis direction, and the second axle 505 is provided with a second reciprocating unit that drives the Z-axis slide 502 to reciprocate along the Z-axis direction. Both the first reciprocating unit and the second reciprocating unit include a reciprocating guide wheel 515 and two cams 516. The outer contours of the two cams 516 alternately abut against the reciprocating guide wheel 515, and the pushing strokes of the two cams 516 on the reciprocating guide wheel 515 are different. The reciprocating guide wheel 515 in the first reciprocating unit is rotatably connected to the X-direction slide 501, and the two cams 516 in the first reciprocating unit are symmetrically installed on the outer periphery of the first wheel shaft 504. The reciprocating guide wheel 515 in the second reciprocating unit is rotatably connected to the Z-axis slide 502, and the two cams 516 in the second reciprocating unit are symmetrically installed on the outer periphery of the second wheel shaft 505. Under normal driving conditions of 40-100km / h, the fuel pump output pressure is 250-300kPa and the fuel flow is 60-80L / h. The gasoline flow drives the turbine shaft 301 to rotate stably at a low speed of 5-180r / min. The power is synchronously transmitted to the first wheel shaft 504 and the second wheel shaft 505 through the linkage module. When the first wheel shaft 504 rotates, the two cams 516 with different strokes alternately abut against the reciprocating guide wheel 515 on the X-direction slide 501. Together with the reciprocating spring 503 between the X-direction slide 501 and the bracket 5, the X-direction slide 501 is driven to make alternating variable stroke reciprocating motions of 5mm and 8mm in a direction perpendicular to the axis of the filter element 6. Similarly, when the second wheel shaft 505 rotates, the two cams 516 with different strokes alternately abut against the reciprocating guide wheel 515 on the Z-axis slide 502, and cooperate with the reciprocating spring 503 between the Z-axis slide 502 and the X-axis slide 501 to drive the Z-axis slide 502 to make alternating variable stroke reciprocating motions of 3mm and 6mm along the axis of the filter element 6. This low-speed, smooth transmission, combined with dual-axis variable stroke composite motion, generates low-amplitude, low-frequency, non-uniform, gentle vibration. This effectively avoids the fatigue, breakage, and delamination problems caused by traditional high-frequency, strong vibrations in filter paper fibers. The gradient vibration force can gently peel off impurities inside and outside the filter element 6, achieving efficient self-cleaning while protecting the filter paper structure to the greatest extent. This ensures that the filtration load of the filter element 6 is evenly distributed, significantly reducing local overload clogging, and significantly slowing down the aging and hardening rate of the filter paper. It effectively reduces the wear of the filter element 6 and extends its service life. Furthermore, the pure mechanical cam 516 drives the operation smoothly without impact.

[0021] An intermittent shaft 506 and a gear shaft 507 are rotatably connected to the Z-axis slide 502. A half-tooth bevel gear 508 is fixedly mounted on the gear shaft 507, and a full-tooth bevel gear that meshes with the half-tooth bevel gear 508 is mounted on the intermittent shaft 506. In a preferred embodiment, the incomplete bevel gear has an 18-tooth half-tooth structure, and the fully toothed bevel gear meshing with it has a 36-tooth structure, so that when the incomplete bevel gear rotates one revolution, the filter element 6 rotates 0.5 revolutions synchronously. A transmission slot 509 is provided on the top of the intermittent shaft 506; The filter element 6 is installed inside the upper housing 1 and is inserted into the transmission slot 509. The reciprocating direction of the Z-axis slide 502 is parallel to the axis of the filter element 6, and the reciprocating direction of the X-axis slide 501 is perpendicular to the axis of the filter element 6. In a preferred embodiment, the filter element 6 has a diameter of 70 mm, a height of 120 mm, a filtration accuracy of 5 μm, and an effective filtration area of ​​0.25 m². The filter element 6 is a pleated paper filter element 6. When replacing filter element 6, it should be replaced as a whole with the upper housing 1. The filter element 6 has a filtration pore size of 5μm to ensure effective interception of tiny impurities in gasoline. The bottom end of the filter element 6 is fixedly connected to a sealing tube 601 that is connected to the transmission slot 509. The cross-section of the sealing tube 601 and the transmission slot 509 is a regular hexagon. The outer periphery of the sealing tube 601 and the distribution plate 201 and the bottom end of the flow equalization cylinder 202 are all fixedly fitted with sealing rings. A corrugated sealing disc 7 is rotatably connected to the top of the filter element 6 and the Z-direction slide 502. The corrugated sealing disc 7 on the filter element 6 is fixedly connected to the upper housing 1. The corrugated sealing disc 7 on the Z-direction slide 502 is fixedly connected to the distribution plate 201. The top of the upper housing 1 is provided with a clean oil drain pipe 101. The top of the filter element 6 is provided with an oil outlet that is connected to the oil drain pipe 101, and a one-way oil outlet valve is installed inside the oil drain pipe 101. The oil outlet of the oil drain pipe 101 is located above the corrugated sealing disc 7 on the top of the filter element 6; The corrugated sealing disc 7 is integrally molded from oil-resistant fluororubber or hydrogenated nitrile rubber. Its corrugated structure provides axial and radial deformation compensation capabilities, ensuring that the filter element 6 maintains a reliable seal during the three-dimensional composite motion. In operation, the gear shaft 507 drives the 18-tooth half-tooth bevel gear 508 to rotate. The half-tooth bevel gear 508 intermittently meshes with the 36-tooth full-tooth bevel gear, driving the intermittent shaft 506 to perform intermittent rotational motion. For every 1 revolution of the half-tooth bevel gear 508, the intermittent shaft 506 rotates 0.5 revolutions. The intermittent shaft 506 drives the sealing tube 601 to rotate synchronously through the regular hexagonal transmission slot 509, thereby driving the filter element 6 to perform intermittent rotational motion; Meanwhile, the reciprocating motion of the X-axis slide 501 and the Z-axis slide 502 is transmitted to the filter element 6 through the transmission slot 509, so that the filter element 6 simultaneously generates a three-dimensional composite motion of intermittent rotation, X-axis reciprocating vibration and Z-axis reciprocating vibration. The corrugated sealing discs 7 at both ends of the filter element 6 ensure sealing during rotation and reciprocating motion, while allowing the filter element 6 to generate a certain axial and radial displacement. The filter element 6 is intermittently rotated by the meshing of the semi-tooth bevel gear 508, so that the entire outer circumference of the filter element 6 passes through the flushing area of ​​the oil injection hole 204 in sequence, achieving full circumference self-cleaning without dead angles. The three-dimensional composite motion generates multi-directional shearing and vibration forces in the filter element 6, which can simultaneously remove the attached impurities on the surface of the filter element 6 and the deep-seated clogging impurities inside the pores, thus extending the replacement cycle of the traditional paper filter element 6. The regular hexagonal snap-fit ​​transmission structure has a large transmission torque, no slippage, and facilitates quick disassembly and replacement of filter element 6. The corrugated sealing disc 7 has excellent axial and radial compensation capabilities, maintaining a reliable seal throughout the three-dimensional composite motion of the filter element 6, thus eliminating the risk of unfiltered gasoline directly entering the clean oil side. A valve mechanism is configured to connect the valve tube 4 to the drive slot 509 and the interior of the filter element 6 when the filter element 6 is clogged.

[0022] The valve mechanism includes a bypass valve module 401 fixedly mounted at the bottom of the valve tube 4. A corrugated metal section 402 is provided at the top of the valve tube 4. A flow channel with openings at both ends is provided inside the intermittent shaft 506. The flow channel at the bottom of the intermittent shaft 506 is rotatably connected to the corrugated metal section 402. The flow channel at the top of the intermittent shaft 506 is connected to the sealing tube 601 through the transmission slot 509.

[0023] Specifically, the bypass valve module 401 includes a valve seat with a main flow port, an axially sliding conical valve core, and an elastic element that provides preload. Under normal conditions, the valve core blocks the valve seat. When the filter element 6 is blocked and the pressure difference exceeds the threshold, the valve core opens, allowing unfiltered gasoline to enter the filter element 6 through the valve pipe 4, the corrugated metal section 402, and the intermittent shaft 506. In operation, under normal working conditions, gasoline is filtered through the oil equalization chamber 203, the injection hole 204, and the filter element 6, and then enters the clean oil drain pipe 101 from the clean oil drain port at the top of the filter element 6, and is delivered to the engine through the one-way oil outlet valve. When filter element 6 becomes abnormally clogged due to extreme working conditions (such as not being replaced for a long time or extremely poor fuel quality), causing the pressure on the oil inlet side to exceed the preset safety threshold, the bypass valve module 401 automatically opens to form a temporary bypass oil circuit, directly introducing unfiltered gasoline into the interior of filter element 6 and supplying it to the engine, so as to prevent the engine from stalling due to fuel shortage and realize the engine protection function. Under normal use conditions, filter element 6 will not become clogged. The bypass valve module 401 is designed as a safety redundancy for extreme situations, rather than a regular working mode. Its existence is to protect the engine in case of accidents. Furthermore, the bypass valve module 401 has a universal configuration structure in the gasoline filter settings, which will not be elaborated here; The corrugated metal section 402 allows the intermittent shaft 506 to reciprocate in the X and Z directions while maintaining the rotational seal and oil circuit connection between the valve pipe 4 and the intermittent shaft 506.

[0024] The specific steps for using this invention are as follows: This filter is suitable for intake manifold injection passenger cars with a displacement of 1.5L-3.0L, with an idle flow rate of 1.5-3.5L / h and a pressure of 80-120kPa, and a medium-to-high speed flow rate of 20-80L / h. The above parameter range is the design input boundary of the turbo drive unit of this invention. It should be noted in advance that under extreme idling conditions with a flow rate of less than 1.5L / h, the turbine shaft 301 may stop intermittently. However, at this time, the impurity deposition rate is extremely low, and the filter element 6 can still maintain an effective filtration area utilization rate through the radial uniform oil injection structure, without local rapid clogging. In the preparation stage, filter element 6 is inserted into the transmission slot 509 at the top of intermittent shaft 506 through the bottom hexagonal sealing tube 601, so that the corrugated sealing plate 7 at the top of filter element 6 is fixed to upper housing 1 and the corrugated sealing plate 7 on Z-axis slide 502 is fixed to distribution plate 201, thus completing the sealing and transmission connection at both ends of filter element 6. The oil inlet pipe 302 of lower housing 2 and the oil inlet port of bypass valve module 401 are connected to the oil outlet of automobile oil pump, and the clean oil drain pipe 101 of upper housing 1 is connected to engine oil inlet. The drain valve 102 on the side of upper housing 1 is closed, and the bypass valve module 401 is confirmed to be in the normally closed state. Each reciprocating spring 503 is reset to the initial position, and the tension spring 513 of tensioning unit pushes tension guide wheel 514 to press the second synchronous transmission belt, ensuring that the transmission system is in the ready-to-work state. During the working phase, after the car is started, the gasoline output by the fuel pump enters the turbine housing 3 tangentially and impacts the turbine blades 303 on the turbine shaft 301 at high speed, causing the turbine shaft 301 to rotate at low speed around the coaxial valve pipe 4. The gasoline in the turbine housing 3 enters the oil equalization chamber 203 through the oil guide pipe 304 to form an annular pressure stabilizing oil chamber, and then is radially and evenly sprayed onto the entire outer circumference of the filter element 6 through the fuel injection holes 204 evenly distributed on the side wall of the flow equalization cylinder 202 with the axis perpendicular to the filter element 6. Simultaneously, the rotational power of the turbine shaft 301 is transmitted to the transmission shaft 510 via orthogonally meshing bevel gears, and then drives the rotating shaft 511 to rotate via the first synchronous transmission belt. The rotating shaft 511 drives the second wheel shaft 505 to rotate synchronously via a regular hexagonal synchronous groove, allowing it to slide with the X-axis slide 501. After the power is synchronously transmitted to the first wheel shaft 504, the first wheel shaft 504 drives the X-axis slide 501 to perform alternating vertical axis reciprocating motion of the filter element 6 by two cams 516 with different strokes in the first reciprocating unit in conjunction with the reciprocating spring 503. The second wheel shaft 505 drives the Z-axis slide 502 to move the filter element through two cams 516 with different strokes in the second reciprocating unit in conjunction with the reciprocating spring 503. The filter element 6 performs alternating parallel axis reciprocating motions of 3mm and 6mm. At the same time, the second wheel shaft 505 drives the gear shaft 507 to rotate via the second synchronous transmission belt. The 18-tooth half-tooth bevel gear 508 on the gear shaft 507 intermittently meshes with the 36-tooth full-tooth bevel gear, driving the intermittent shaft 506 to drive the filter element 6 to perform half-turn intermittent rotation. Ultimately, the filter element 6 simultaneously generates a three-dimensional composite motion of intermittent rotation, X-axis reciprocating vibration, and Z-axis reciprocating vibration. The multi-directional shearing force and low-amplitude, low-frequency non-uniform vibration force gently peel off the impurities attached to the surface of the filter element 6 and the deep-seated blockage impurities in the pores. The impurities settle to the bottom of the oil equalization chamber 203. The filtered clean oil enters the clean oil drain pipe 101 from the clean oil drain port at the top of the filter element 6 and is delivered to the engine through the one-way oil outlet valve. When the filter element 6 is severely clogged, causing the pressure on the oil inlet side to exceed the opening pressure of the bypass valve, the bypass valve module 401 automatically opens. Unfiltered gasoline enters the filter element 6 through the valve pipe 4, the corrugated metal section 402, the inner flow channel of the intermittent shaft 506, the transmission slot 509, and the sealing pipe 601 in sequence, and then supplies oil through the clean oil drain pipe 101 to ensure the normal operation of the engine. After the vehicle is turned off and then started, the oil pump stops supplying oil, and the turbine shaft 301 and all transmission components gradually stop operating. The filter element 6 returns to its initial position, and the one-way oil outlet valve in the clean oil drain pipe 101 closes to prevent fuel backflow. During routine maintenance, the drain valve 102 is opened periodically to drain the impurities deposited at the bottom of the oil equalization chamber 203. When the filter element 6 reaches the end of its service life, the locking parts of the upper and lower housings 2 are removed, and the filter element 6, together with the upper housing 1 and the top corrugated sealing disc 7, are replaced as a whole. After resealing and reassembling the upper housing 1 and the lower housing 2, the device can be restored to normal use.

[0025] The turbine drive unit of the present invention does not rely on high flow and high pressure conditions to operate; By optimizing the helix angle and number of blades of turbine blade 303, it can still generate a starting torque sufficient to overcome the static friction of the transmission system and the initial preload of reciprocating spring 503 under idling conditions with a flow rate of only 1.5-3.5L / h and a pressure of 80-120kPa. Meanwhile, the movement of the filter element 6 driven by the X-axis slide 501, Z-axis slide 502 and intermittent shaft 506 is a light-load movement with low inertia and low load. The overall driving force requirement is extremely small. In the idling state, the turbine shaft 301 can rotate stably at a speed of 5-20 r / min, driving the filter element 6 to achieve slow and small-amplitude compound movement. Although the amplitude and frequency of this movement are lower than those in the driving condition, it can still effectively suppress the initial adhesion and local accumulation of impurities on the surface of the filter element 6 compared to the traditional static filter element 6, and avoid accelerated clogging due to long-term idling operation. It should also be noted that even if the turbine blades 303 do not rotate at all or only start occasionally (such as rotating for a few seconds every 1-2 minutes), this solution is still superior to traditional filters. First, the oil injection holes 204 evenly distributed on the side wall of the flow equalization cylinder 202 achieve radial uniform injection. In static mode, the effective filtration area utilization rate of the filter element is improved, and the local clogging time is extended. Second, the low-frequency vibration generated by occasional startup is sufficient to reduce the adhesion of already attached impurities. Combined with the instantaneous shear force, it destroys the impurity accumulation layer, achieving short-term movement and long-term clogging removal. The impurity deposition rate is extremely low at idle speed, and the cleaning needs are automatically matched, so there is no risk of failure.

[0026] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A high-performance gasoline filter, comprising an upper housing (1) and a lower housing (2) connected to each other, characterized in that, Also includes: The turbine housing (3) and valve pipe (4) are both fixed on the lower housing (2). The turbine housing (3) is equipped with a turbine drive unit. The turbine drive unit is connected to a turbine shaft (301) that is driven to rotate by the flow of gasoline. The turbine housing (3) is connected to an oil guide pipe (304). The distribution plate (201) is fixedly mounted on the top of the lower housing (2). A flow equalization cylinder (202) is fixedly mounted on the distribution plate (201). An oil equalization chamber (203) communicating with the oil guide pipe (304) is provided between the flow equalization cylinder (202) and the upper housing (1). Oil injection holes (204) communicating with the oil equalization chamber (203) are evenly distributed on the flow equalization cylinder (202). A bracket (5) is fixedly mounted on a turbine housing (3). An X-axis slide (501) is slidably connected to the bracket (5), and a Z-axis slide (502) is slidably connected to the X-axis slide (501). Reciprocating springs (503) are installed between the X-axis slide (501) and the bracket (5), and between the Z-axis slide (502) and the X-axis slide (501). A first wheel axle (504) is rotatably connected to the bracket (5), and a second wheel axle (505) is rotatably connected to the X-axis slide (501). Both the first wheel axle (504) and the second wheel axle (505) are connected to the turbine shaft (301) via a linkage module. The transmission connection is as follows: the first wheel shaft (504) is provided with a first reciprocating unit that drives the X-axis slide (501) to reciprocate along the X-axis direction; the second wheel shaft (505) is provided with a second reciprocating unit that drives the Z-axis slide (502) to reciprocate along the Z-axis direction; the Z-axis slide (502) is rotatably connected with an intermittent shaft (506) and a gear shaft (507); a half-tooth bevel gear (508) is fixedly mounted on the gear shaft (507); a full-tooth bevel gear that meshes with the half-tooth bevel gear (508) is installed on the intermittent shaft (506); and a transmission slot (509) is opened on the top of the intermittent shaft (506). The filter element (6) is installed inside the upper housing (1) and is inserted into the transmission slot (509). The top of the filter element (6) and the Z-direction slide (502) are rotatably connected to the corrugated sealing disc (7). The corrugated sealing disc (7) on the filter element (6) is fixedly connected to the upper housing (1). The corrugated sealing disc (7) on the Z-direction slide (502) is fixedly connected to the distribution plate (201). The top of the upper housing (1) is provided with a clean oil drain pipe (101). A valve mechanism is configured to connect the valve tube (4) to the drive slot (509) and the interior of the filter element (6) when the filter element (6) is clogged.

2. The high-performance gasoline filter according to claim 1, characterized in that, The turbine drive unit includes an oil inlet pipe (302) fixed on the lower housing (2), the oil inlet pipe (302) is connected to the turbine housing (3), and turbine blades (303) are mounted on the turbine shaft (301) at positions corresponding to the inner side of the turbine housing (3). The turbine shaft (301) is coaxially arranged with the valve pipe (4), and the turbine shaft (301) is rotatably sleeved on the outer periphery of the valve pipe (4) through bearings.

3. The high-performance gasoline filter according to claim 1, characterized in that, The linkage module includes a drive shaft (510) and a rotating shaft (511) rotatably connected to the bracket (5). A first synchronous drive belt is connected between the drive shaft (510) and the rotating shaft (511). Both the drive shaft (510) and the turbine shaft (301) are equipped with linkage bevel gears. The two linkage bevel gears mesh orthogonally. The second wheel shaft (505) has a synchronous groove with an open tail end and is slidably connected to the rotating shaft (511). The cross-section of the synchronous groove and the rotating shaft (511) are both regular hexagonal. A second synchronous drive belt is connected to the second wheel shaft (505). The second synchronous drive belt is connected to the gear shaft (507). The Z-axis slide (502) is provided with a tensioning unit to keep the second synchronous drive belt tensioned.

4. The high-performance gasoline filter according to claim 3, characterized in that, The tensioning unit includes a tensioning slider (512) slidably connected to a Z-axis slide (502). A tensioning spring (513) is mounted on the side of the tensioning slider (512). The other end of the tensioning spring (513) is fixedly connected to the Z-axis slide (502). A tensioning guide wheel (514) is rotatably connected to the tensioning slider (512). The tensioning guide wheel (514) is connected to the second synchronous transmission belt.

5. The high-performance gasoline filter according to claim 1, characterized in that, Both the first reciprocating unit and the second reciprocating unit include a reciprocating guide wheel (515) and two cams (516). The outer contours of the two cams (516) alternately abut against the reciprocating guide wheel (515), and the pushing strokes of the two cams (516) on the reciprocating guide wheel (515) are different. The reciprocating guide wheel (515) in the first reciprocating unit is rotatably connected to the X-axis slide (501), and the two cams (516) on it are symmetrically installed on the outer periphery of the first wheel shaft (504). The reciprocating guide wheel (515) in the second reciprocating unit is rotatably connected to the Z-axis slide (502), and the two cams (516) on it are symmetrically installed on the outer periphery of the second wheel shaft (505).

6. The high-performance gasoline filter according to claim 1, characterized in that, The bottom end of the filter element (6) is fixedly connected to a sealing tube (601) connected to the transmission slot (509). The cross-section of the sealing tube (601) and the transmission slot (509) is a regular hexagon. The outer periphery of the sealing tube (601) and the distribution plate (201) and the bottom end of the flow equalization cylinder (202) are all fixedly fitted with sealing rings. The axis of the oil injection hole (204) is perpendicular to the axis of the filter element (6).

7. The high-performance gasoline filter according to claim 1, characterized in that, The valve mechanism includes a bypass valve module (401) fixedly mounted at the bottom of the valve tube (4). A corrugated metal section (402) is provided at the top of the valve tube (4). A flow channel with openings at both ends is provided in the intermittent shaft (506). The flow channel at the bottom of the intermittent shaft (506) is rotatably connected to the corrugated metal section (402). The flow channel at the top of the intermittent shaft (506) is connected to the sealing tube (601) through the transmission slot (509). A clean oil outlet is provided at the top of the filter element (6) and is connected to the clean oil drain pipe (101). A one-way oil outlet valve is installed in the clean oil drain pipe (101).

8. The high-performance gasoline filter according to claim 1, characterized in that, The flow equalization cylinder (202) is a hollow cylindrical structure with an open top. The flow equalization cylinder (202), the upper shell (1) and the lower shell (2) are all made of 304 stainless steel. The side of the upper shell (1) is equipped with a drain valve (102) that communicates with the oil equalization chamber (203).

9. The high-performance gasoline filter according to claim 1, characterized in that, The reciprocating direction of the Z-axis carriage (502) is parallel to the axis of the filter element (6).

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