An impeller for a mechanical supercharger

Abstract

This application relates to an impeller for a supercharger, comprising: a disc, shaped like a frustum; several first blades, circumferentially spaced on the sidewall of the disc; a hub connected to the larger diameter end of the disc; and a pulley disposed on the hub. The chord length of the first blades is inclined towards the rotation direction of the hub, and the length direction of the first blades is arc-shaped from the root to the tip of the impeller, with the curvature direction opposite to the rotation direction of the hub. The leading edge sweep angle of the first blades is 42°–48°, and the trailing edge sweep angle is 16°–20°. The chord length of the first blades gradually decreases from the root to the tip of the disc, and the thickness gradually decreases along the length direction of the first blades and from the root to the tip. The first blades manufactured with the above design can provide a larger compressed air supply, so that even with a reduced volume of the disc and the first blades, sufficient compressed air can still be supplied to the engine cylinders.

Description

TECHNICAL FIELD

[0001] The application relates to the technical field of mechanical superchargers, in particular to a mechanical supercharger impeller. BACKGROUND

[0002] The motorcycle mechanical supercharger is used to compress air outside and input the compressed air into the cylinder of the engine through rotation of the impeller, so as to increase the gas density in the cylinder of the motorcycle engine, and then make the fuel tank of the motorcycle deliver more fuel into the cylinder of the engine for combustion, thereby greatly enhancing the power output of the engine.

[0003] The power source of the mechanical supercharger on the motorcycle is generally the crankshaft of the engine, so the mechanical supercharger usually needs to be installed at the air inlet of the engine cylinder. Due to the overall structural design of the motorcycle, the available space at the air inlet of the engine cylinder is relatively small, and the traditional mechanical supercharger usually has a relatively large size in order to ensure the air compression amount. The diameter of the impeller of the commonly seen mechanical supercharger, such as the mechanical supercharger of Kawasaki H2, reaches 69mm, and the weight of only one impeller reaches 45g. Therefore, in order to install the mechanical supercharger, the volume of the fuel tank needs to be reduced when designing the motorcycle structure. Obviously, in the case of reducing the volume of the fuel tank of the motorcycle, the overall endurance of the motorcycle will be reduced, which is not conducive to commercial competition. Meanwhile, the larger impeller consumes more energy when being driven, which further reduces the endurance of the motorcycle.

[0004] The specific conditions of the traditional mechanical supercharger impeller can be referred to the following four patents: “2014800616558”, “2014800619541”, “2014800798895” and “2014800282913”. (The above four patents are only for illustration, and the above technical problems can be understood by understanding more prior art)

[0005] Therefore, there is an urgent need for a motorcycle mechanical supercharger with smaller volume but unchanged or even stronger air intake capacity. The size of the mechanical supercharger is determined by the size of the impeller, so it is necessary to design an impeller with smaller size but the same or even higher air intake capacity than the large-size impeller. SUMMARY

[0006] In order to solve the problem that the traditional mechanical supercharger has a large volume, so the fuel tank must be reduced to adapt, thereby reducing the overall endurance of the motorcycle, the application provides a mechanical supercharger impeller.

[0007] The mechanical supercharger impeller provided by the application adopts the following technical scheme:

[0008] The impeller of a mechanical supercharger comprises: a wheel disc in the shape of a circular truncated cone; a plurality of first blades arranged on the side wall of the wheel disc in a circumferential direction along the axis of the wheel disc; a hub coaxially connected to the end of the wheel disc with a larger diameter; and a belt pulley arranged on the hub for transmitting the power of a motorcycle engine through a belt.

[0009] The chord line of the first blade is inclined towards the rotation direction of the hub, the length direction of the first blade is arranged in an arc shape from the root to the top of the impeller, and the bending direction is opposite to the rotation direction of the hub, the leading edge angle of the first blade is designed to be 42-48°, the trailing edge angle of the first blade is 16-20°, the chord length of the first blade gradually decreases from the root to the top of the wheel disc, the thickness of the first blade gradually decreases from the root to the top of the wheel disc along the length direction of the first blade, and the thickness of the first blade gradually decreases from the root to the tip.

[0010] Through the above technical solution, the first blade designed and manufactured in the above manner can provide a larger supply of compressed air, so that after the volume of the wheel disc and the first blade is reduced, sufficient compressed air can still be supplied to the engine cylinder, and thus the volume of the mechanical supercharger using the above designed impeller can be reduced. The reduced mechanical supercharger not only leaves out the reduced space, but also can be installed in a smaller space that the traditional mechanical supercharger cannot be installed in, so that more space inside the motorcycle can be left out for expanding the fuel tank, thereby increasing the overall endurance and enhancing the market competitiveness of the motorcycle installed with the mechanical supercharger.

[0011] Optionally, the end of the wheel disc with a smaller diameter is coaxially provided with a wind breaking head, and the end of the wind breaking head away from the wheel disc is in the shape of a cone.

[0012] Optionally, a second blade is arranged between the two first blades, the chord line of the second blade is inclined towards the rotation direction of the hub, the length direction of the second blade is arranged in an arc shape from the root to the top of the impeller, and the bending direction is opposite to the rotation direction of the hub, the leading edge angle of the second blade is greater than the leading edge angle of the first blade by 14-16°, and the trailing edge angle of the second blade is less than the trailing edge angle of the first blade by 9-11°.

[0013] Optionally, the part of the wheel disc close to its axis is defined as the root, the part of the wheel disc far from its axis is defined as the top, the thickness of the second blade gradually decreases along its length direction and the root-to-top direction of the wheel disc, the thickness of the second blade gradually decreases along its root-to-tip direction, the chord length of the second blade gradually decreases along its length direction and the root-to-top direction of the wheel disc, the thickness of the second blade is smaller than the thickness of the first blade at the part of equal length proportion, the thickness difference is 0.5-1.0mm, the thickness of the second blade is smaller than the thickness of the first blade at the part of equal chord length proportion, the thickness difference is 0.5-1.0mm, and the length of the second blade is 62%-72% of the length of the first blade.

[0014] Optionally, the trailing edge surface of the second blade and the trailing edge surface of the first blade are smoothly transitioned with the top side wall of the wheel disc.

[0015] Optionally, the chord length of the leading edge of the first blade is greater than the chord length of the leading edge of the second blade, and the chord length of the trailing edge of the first blade is smaller than the chord length of the trailing edge of the second blade.

[0016] Optionally, the pulley is slidingly mounted on the hub, the hub is provided with a shaft shoulder for axially positioning the pulley, the inner wall of the pulley is provided with a plurality of first positioning grooves spaced apart circumferentially around its axis, the first positioning grooves are parallel to the pulley axis, one end of the first positioning grooves penetrates one side of the pulley, the side wall of the hub is provided with a plurality of second positioning grooves spaced apart circumferentially around its axis, the second positioning grooves are parallel to the hub axis, the first positioning grooves and the second positioning grooves correspond one by one, the diameter of the hub segment provided with the second positioning grooves is greater than the diameter of the rest of the hub, one end of the second positioning grooves penetrates the stepped surface at the junction of the large-diameter segment and the small-diameter segment of the hub, the second positioning grooves are embedded with positioning blocks, one end of the positioning blocks protrudes from the second positioning grooves, the first positioning grooves are defined as the upper side, and the second positioning grooves are defined as the lower side, the bottom wall of the positioning block is convex, the positioning block is transitionally fitted with the first positioning grooves and the second positioning grooves, the hub is provided with a pushing member, and the pushing member is used to push the upper side of the positioning block into the first positioning grooves.

[0017] Optionally, one end of the positioning block protruding from the second positioning groove is provided with a first inclined surface, the first inclined surface is inclined downward along the length direction of the second positioning groove, the pushing member includes a pressing ring threadedly mounted on the hub, the pressing ring is arranged at the smaller-diameter segment of the hub, an inner ring of one end of the pressing ring towards the pulley is provided with a second inclined surface, when the positioning block is embedded in the second positioning groove, the inclination of the first inclined surface and the second inclined surface is different, when the pressing ring is tightened, the first inclined surface and the second inclined surface are in close contact, and at this time the upper side of the positioning block is embedded in the first positioning groove.

[0018] Optionally, the third slope is arranged on the lower side of the end of the positioning block extending out of the second positioning groove, the top ring is coaxially arranged on the end of the abutting ring away from the belt pulley, the fourth slope is arranged on the outer edge of the end of the top ring away from the abutting ring, and the pressing ring is coaxially arranged on the side of the abutting ring provided with the top ring, and the diameter of the pressing ring is greater than that of the top ring. When the positioning block is separated from the first positioning groove and is embedded in the second positioning groove, the end of the abutting ring provided with the top ring is directed towards the belt pulley and is then tightened, at this time, the third slope and the fourth slope are in abutment, and the pressing ring extends into the space formed by the first positioning groove and the second positioning groove, and the inner edge of the pressing ring abuts against the top wall of the positioning block.

[0019] Optionally, the upper end surface of the end of the positioning block extending out of the second positioning groove is provided with a friction layer, the end of the abutting ring provided with the first slope is coaxially provided with the lock ring, the inner wall of the lock ring is circumferentially spaced apart about the axis to form a plurality of installation grooves, the friction plate is slidably arranged in the installation groove, the side of the friction plate directed towards the direction of the slot of the installation groove is in abutment with the side of the positioning block provided with the friction layer, the side of the friction plate in abutment with the positioning block is also provided with a friction layer, and a plurality of fixing bolts are threadedly arranged on the outer side wall of the lock ring. When the abutting ring is tightened, the lock ring abuts against the shaft shoulder, at this time, the fixing bolts are tightened, and the fixing bolts can push the friction plate to abut against the friction layer of the positioning block.

[0020] In summary, the first blade designed and manufactured according to the application can provide a larger supply amount of compressed air, the second blade can assist in air supply, and thus, after the volume of the wheel disc and the first blade and the second blade is reduced, sufficient compressed air can still be supplied to the engine cylinder, the volume of the mechanical supercharger adopting the above-mentioned design of the blade wheel can be reduced, the reduced mechanical supercharger not only leaves out the reduced space, but also can be installed in a smaller space that cannot be installed by a traditional mechanical supercharger, and thus, more space inside the motorcycle can be left out to expand the fuel tank, and thus, the overall endurance is increased, and the market competitiveness of the motorcycle provided with the mechanical supercharger is enhanced.

[0021] When the belt pulley is worn, the fixing bolts are loosened, the abutting ring is loosened, the positioning block is separated from the first positioning groove by abutting the third slope and the fourth slope after the abutting ring is tightened in the reverse direction, and then the belt pulley can be easily removed from the wheel hub for replacement. BRIEF DESCRIPTION OF DRAWINGS

[0022] FIG. 1 is a perspective structural schematic view of the application.

[0023] FIG. 2 is another perspective structural schematic view of the application.

[0024] FIG. 3 is a front view of one side of the wind-breaking head of the application.

[0025] Fig. 4 is a cross-sectional schematic view of the present application.

[0026] Fig. 5 is an enlarged schematic view of section A in Fig. 4.

[0027] Fig. 6 is an enlarged schematic view of section B in Fig. 5.

[0028] Fig. 7 is a pressure ratio test diagram of a conventional design and a pressure ratio test diagram of the present application.

[0029] Those skilled in the art will appreciate that the elements in the figures are illustrated for simplicity and clarity and have not necessarily been drawn to scale. For example, the dimensions and / or relative positioning of some of the elements in the figures can be exaggerated relative to other elements to help to improve understanding of the present application.

[0030] Reference signs: 1, wheel disc; 11, wheel hub; 111, second positioning groove; 12, belt pulley; 121, first positioning groove; 13, wind breaking head; 14, root; 15, top; 2, first blade; 21, leading edge; 22, trailing edge; 3, second blade; 4, positioning block; 41, first inclined surface; 42, third inclined surface; 5, abutting ring; 51, second inclined surface; 52, top ring; 521, fourth inclined surface; 53, pressing ring; 54, force adding hole; 6, friction layer; 7, anti-loosening ring; 71, mounting groove; 72, friction plate; 73, fixing bolt. DETAILED DESCRIPTION

[0031] The present application is further described in detail below with reference to Figs. 1-7.

[0032] The embodiment of the present application discloses a mechanical supercharger impeller, referring to Figs. 1 and 2, comprising a wheel disc, a plurality of first blades and a plurality of second blades, a wheel hub coaxially and integrally arranged at a larger diameter end of the wheel disc, and a belt pulley coaxially and slidingly mounted on the wheel hub.

[0033] Referring to Figs. 1 and 3, the first blades and the second blades are both circumferentially and integrally arranged on the side wall of the wheel disc along the wheel disc axis, and the first blades and the second blades are alternately arranged.

[0034] Referring to Figs. 1 and 3, the wheel disc is in the shape of a circular truncated cone, and a wind breaking head is coaxially and integrally arranged at a smaller diameter end of the wheel disc, and the end of the wind breaking head is in the shape of a cone. Air first passes through the wind breaking head before entering the range of the wheel disc, and is uniformly scattered into the range of the wheel disc after being uniformly broken by the conical wind breaking head. When the subsequent wheel disc pressurizes the air through the first blades and the second blades thereon, the load borne by each part of the blades is relatively uniform, thereby making the actual service life of each blade similar. Since the wheel disc, the first blades and the second blades are integrally cast, the actual service life of the impeller is improved.

[0035] Referring to FIG. 1 and FIG. 3, the tip portion of the blade at the air inlet end of the impeller is referred to as the leading edge of the blade, and the tip portion at the other end is referred to as the trailing edge of the blade. The part of the disc close to its axis is defined as the root, and the part of the disc away from its axis is defined as the top.

[0036] Referring to FIG. 1 and FIG. 3, the chord line of the first blade is inclined toward the rotation direction of the hub, the length direction of the first blade is arranged in an arc shape along the root-to-top direction of the impeller, and the bending direction is opposite to the rotation direction of the hub, the leading edge angle of the first blade is designed to be 42°-48°, the trailing edge angle of the first blade is 16°-20°, the chord length of the first blade gradually decreases along the leading edge-to-trailing edge direction of the first blade, the thickness of the first blade gradually decreases along the leading edge-to-trailing edge direction of the first blade, and the thickness of the first blade gradually decreases along the root-to-tip direction.

[0037] Referring to FIG. 1 and FIG. 3, the first blade and the second blade are arranged in an interlaced manner, the chord line of the second blade is inclined toward the rotation direction of the hub, the length direction of the second blade is arranged in an arc shape along the root-to-top direction of the impeller, and the bending direction is opposite to the rotation direction of the hub, the leading edge angle of the second blade is greater than the leading edge angle of the first blade by 14-16°, and the trailing edge angle of the second blade is less than the trailing edge angle of the first blade by 9-11°.

[0038] Referring to FIG. 1 and FIG. 3, the thickness of the second blade gradually decreases along the leading edge-to-trailing edge direction of the second blade, the thickness of the second blade gradually decreases along the root-to-tip direction of the second blade, the chord length of the second blade gradually decreases along the leading edge-to-trailing edge direction of the second blade, the thickness of the second blade is less than the thickness of the first blade at the equal length proportion position, the thickness difference is 0.5-1.0㎜, the thickness of the second blade is less than the thickness of the first blade at the equal chord length proportion position, the thickness difference is 0.5-1.0㎜, and the length of the second blade is 62%-72% of the length of the first blade.

[0039] Through the design of the first blade and the second blade described above, the supercharging capacity of the impeller can be higher than that of the traditional impeller under the same size, and thus, in the design of the impeller of the present application, the maximum diameter of the disc can be designed to be 61㎜, compared with the traditional design in which the maximum diameter of the disc needs to be designed to be 69㎜ to meet the air supply demand of the engine cylinder.

[0040] The first blade root thickness along the length direction is designed to gradually decrease from 1.5-1.6mm to 1.45-1.35mm, the first blade tip thickness along the length direction is designed to gradually decrease from 0.85-0.95mm to 0.65-0.75mm, the second blade root thickness along the length direction is designed to gradually decrease from 1.15-1.25mm to 0.95-1.05mm, and the second blade tip thickness along the length direction is designed to gradually decrease from 0.85-0.95mm to 0.65-0.75mm.

[0041] Referring to FIG. 1 and FIG. 3, the chord length of the first blade is designed to gradually decrease from 18.5-19.5mm to 6.5-7.5mm, the centerline length of the first blade is designed to be 37-40mm, and the end surface of the first blade root part of the trailing edge is smoothly connected with the side wall of the wheel disc. The chord length of the second blade is designed to gradually decrease from 14-15mm to 7-8mm, the centerline length of the second blade is designed to be 23-29mm, and the end surface of the second blade root part of the trailing edge is smoothly connected with the side wall of the wheel disc.

[0042] The centerline length of the first blade and the second blade is adjusted according to the thickness of the wheel disc, and the thickness of the wheel disc needs to be adjusted according to the size of the actual mechanical supercharger. The above adjustment method is the same as the prior art. Under the condition that the chord length design, thickness design, leading edge sweep angle design, and trailing edge sweep angle design of the first blade and the second blade remain unchanged, the supercharging capacity remains the same.

[0043] Referring to FIG. 4 and FIG. 5, the diameter of one end of the hub connected with the wheel disc is larger than the diameter of the remaining part, the pulley is slidingly installed at the end of the hub with a larger diameter, and the hub is connected with the wheel disc. The side wall of the end of the hub with a larger diameter is circumferentially spaced apart around the axis and is provided with a plurality of second positioning grooves, the length direction of the second positioning grooves is parallel to the axis of the hub, and one end of the second positioning grooves penetrates the stepped surface at the boundary between the end of the hub with a larger diameter and the end of the hub with a smaller diameter.

[0044] Referring to FIG. 4 and FIG. 5, a plurality of first positioning grooves are circumferentially spaced apart on the inner wall of the pulley, the number of the first positioning grooves is the same as the number of the second positioning grooves, the length direction of the first positioning grooves is parallel to the axis of the pulley, and one end of the first positioning grooves penetrates one side of the pulley.

[0045] The widths of the first positioning grooves and the second positioning grooves are the same, and when the pulley is slidingly installed on the hub, the pulley can be rotated to correspond to the first positioning grooves and the second positioning grooves one by one.

[0046] Referring to Figures 4 and 5, one side of the second positioning groove is defined as the lower side, and one side of the first positioning groove is defined as the upper side. A positioning block is fitted into the second positioning groove, and the positioning block can be completely embedded into the second positioning groove in the vertical direction. One end of the positioning block extends out of the second positioning groove, and a first inclined surface is provided on the upper side of the end of the positioning block extending out of the second positioning groove. The inclined surface slopes downward along the length direction of the second positioning groove, and a third inclined surface is provided on the lower side of the end of the positioning block extending out of the second positioning groove. The third inclined surface slopes upward along the length direction of the second positioning groove.

[0047] Referring to Figures 4 and 5, the hub is provided with a pusher, which includes a clamping ring threaded onto the smaller diameter section of the hub. The inner edge of the inner ring end of the clamping ring facing the pulley is provided with a second inclined surface. When the positioning block is fully embedded in the second positioning groove in the vertical direction, the inclination of the first inclined surface of the positioning block is different from the inclination of the second inclined surface, and one end of the positioning block abuts against the end of the second positioning groove.

[0048] Referring to Figures 4 and 5, the clamping block can be screwed and rotated until its end is in contact with and abuts the pulley. When the clamping block is tightened and in contact with the pulley, the first inclined surface and the second inclined surface are in contact. The end of the positioning block rotates under the cooperation between the first inclined surface and the second inclined surface until it is fitted into the first positioning groove. The rotational freedom of the pulley is limited by the cooperation between the positioning block, the second positioning groove and the first positioning groove. At the same time, the support of the positioning block makes the pulley and the hub form a transitional fit, thereby making the pulley and the hub more stable. When the pulley transmits power through the belt, it is not easy for relative slippage and relative rotation to occur between the pulley and the hub. Moreover, it is not easy for mutual vibration between the pulley and the hub to cause noise or even damage to the pulley and the hub.

[0049] Referring to Figures 4 and 5, the end of the clamping ring opposite to the pulley is coaxially and integrally provided with a top ring. The outer edge of the end of the top ring opposite to the clamping ring is provided with a fourth inclined surface. The side of the clamping ring with the top ring is also coaxially provided with a pressure ring. The diameter of the pressure ring is larger than that of the top ring. When the positioning block is separated from the first positioning groove and fitted into the second positioning groove, the end of the clamping ring with the top ring is turned toward the pulley and then tightened. At this time, the third and fourth inclined surfaces are in contact, and the pressure ring extends into the space where the first and second positioning grooves are joined. The inner edge of the pressure ring abuts against the top wall of the positioning block.

[0050] Referring to Figures 4 and 5, when it is necessary to disassemble the pulley, the positioning block must first be removed. During disassembly, the retaining ring is first loosened and removed, and then the retaining ring is threaded onto the hub. Then the retaining ring is tightened, and the top ring and pressure ring of the retaining ring push the positioning block to rotate, so that the positioning block is rotated and pressed back into the second positioning groove, thereby removing the fixation between the pulley and the hub. Then the retaining ring is loosened again and removed, and the pulley can be easily slid off the hub for replacement.

[0051] Referring to Figures 5 and 6, a friction layer is integrally provided on the upper end face of the end of the positioning block that extends out of the second fixing groove. An anti-loosening ring is integrally provided on the end of the tightening ring that has a first inclined surface. Two mounting grooves are circumferentially spaced around the inner wall of the anti-loosening ring. A friction plate is slidably provided in the mounting groove. The side of the friction plate facing the groove opening of the mounting groove is in contact with the friction layer of the positioning block.

[0052] Referring to Figures 5 and 6, the side of the friction plate that fits into the positioning block is also integrally provided with a friction layer. Several fixing bolts are threaded on the outer wall of the anti-loosening ring. When the anti-loosening ring is tightened, the anti-loosening ring fits into the shaft shoulder. At this time, tightening the fixing bolts can push the friction plate to fit into the friction layer of the positioning block.

[0053] The anti-loosening ring is prevented by the cooperation between the friction layer of the positioning block and the friction layer of the friction plate. When the anti-loosening ring needs to be loosened, the friction between the positioning block and the anti-loosening ring can be removed by loosening the fixing bolt, making it convenient to both disassemble and tighten the anti-loosening ring.

[0054] The tightening ring also has several force-applying holes on its side wall. These holes are spaced apart around the circumference of the tightening ring. By inserting the force-applying rod into the force-applying holes, the tightening ring can be tightened or loosened with relatively little effort.

[0055] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. An impeller for a mechanical supercharger, characterized in that, include: The roulette wheel (1) is shaped like a frustum. The first blade (2) is provided in several circumferentially spaced around the axis of the wheel (1) on the side wall of the wheel (1); The hub (11) is coaxially connected to the larger diameter end of the disc (1); A pulley (12) is provided on the hub (11) for transmitting power from the motorcycle engine via a belt; The chord length of the first blade (2) is inclined toward the rotation direction of the hub (11). The length direction of the first blade (2) is curved along the impeller from the root (14) to the top (15), and the curvature direction is opposite to the rotation direction of the hub (11). The sweep angle of the leading edge (21) of the first blade (2) is designed to be 42°-48°, and the sweep angle of the trailing edge (22) of the first blade (2) is 16°-20°. The chord length of the first blade (2) gradually decreases from the root (14) of the impeller (1) to the top (15) of the impeller (1). The thickness of the first blade (2) gradually decreases along the length direction of the first blade (2) from the root (14) of the impeller (1) to the top (15) of the impeller (1). The thickness of the first blade (2) gradually decreases along the blade root to the blade tip. The pulley (12) is slidably mounted on the hub (11). The hub (11) has a shoulder for axial positioning of the pulley (12). The inner wall of the pulley (12) is circumferentially spaced with several first positioning grooves (121) around its axis. The first positioning grooves (121) are parallel to the axis of the pulley (12), and one end of each first positioning groove (121) passes through one side of the pulley (12). The side wall of the hub (11) is circumferentially spaced with several second positioning grooves (111) around its axis. The second positioning grooves (111) are parallel to the axis of the hub (11). The first positioning grooves (121) and the second positioning grooves (111) correspond one-to-one. The section with the second positioning grooves (111)... The diameter of the hub (11) segment is larger than the diameter of the rest of the hub (11). One end of the second positioning groove (111) penetrates the stepped surface at the junction of the large diameter segment and the small diameter segment of the hub (11). The second positioning groove (111) is embedded with a positioning block (4). One end of the positioning block (4) extends out of the second positioning groove (111). The first positioning groove (121) is defined as the upper side, and the second positioning groove (111) is defined as the lower side. The bottom wall of the positioning block (4) is raised. The positioning block (4) is transitionally fitted with both the first positioning groove (121) and the second positioning groove (111). The hub (11) is provided with a pusher. The pusher is used to push the upper side of the positioning block (4) into the first positioning groove (121). The positioning block (4) has a first inclined surface (41) at one end extending out of the second positioning groove (111). The first inclined surface (41) is inclined downward along the length direction of the second positioning groove (111). The pushing member includes a clamping ring (5) threaded onto the hub (11). The clamping ring (5) is located in the smaller diameter section of the hub (11). The inner ring of the clamping ring (5) facing the pulley (12) has a second inclined surface (51). When the positioning block (4) is embedded in the second positioning groove (111), the inclination of the first inclined surface (41) and the second inclined surface (51) are different. When the clamping ring (5) is tightened, the first inclined surface (41) and the second inclined surface (51) fit together, and at this time the upper part of the positioning block (4) is embedded in the first positioning groove (121). The positioning block (4) has a third inclined surface (42) on the lower side of the end extending out of the second positioning groove (111). The end of the clamping ring (5) opposite to the pulley (12) has a top ring (52) coaxially provided. The outer edge of the end of the top ring (52) opposite to the clamping ring (5) has a fourth inclined surface (521). The side of the clamping ring (5) with the top ring (52) also has a pressure ring (53) coaxially provided. The diameter of the pressure ring (53) is larger than that of the top ring (52). When the positioning block (4) is separated from the first positioning groove (121) and fitted into the second positioning groove (111), the end of the pressing ring (5) with the top ring (52) is facing the pulley (12) and then tightened. At this time, the third inclined surface (42) and the fourth inclined surface (521) are in contact, and the pressure ring (53) extends into the space where the first positioning groove (121) and the second positioning groove (111) are joined. The inner edge of the pressure ring (53) presses against the top wall of the positioning block (4).

2. The impeller of a mechanical supercharger according to claim 1, characterized in that: The smaller diameter end of the wheel (1) is coaxially provided with a wind-breaking head (13), and the end of the wind-breaking head (13) away from the wheel (1) is conical.

3. The impeller of a mechanical supercharger according to claim 1, characterized in that: A second blade (3) is provided between the two first blades (2). The chord length of the second blade (3) is inclined toward the rotation direction of the hub (11). The length direction of the second blade (3) is curved along the root (14) to the top (15) of the impeller, and the curvature direction is opposite to the rotation direction of the hub (11). The sweep angle of the leading edge (21) of the second blade (3) is 14-16° greater than the sweep angle of the leading edge (21) of the first blade (2). The sweep angle of the trailing edge (22) of the second blade (3) is 9-11° less than the sweep angle of the trailing edge (22) of the first blade (2).

4. The impeller of a mechanical supercharger according to claim 3, characterized in that: The part of the wheel (1) near its axis is defined as the root (14), and the part of the wheel (1) away from its axis is defined as the top (15). The thickness of the second blade (3) gradually decreases along its length direction and from the root (14) to the top (15) of the wheel (1). The thickness of the second blade (3) gradually decreases along its leaf root to its leaf tip. The chord length of the second blade (3) gradually decreases along its length direction and from the root (14) to the top (15) of the wheel (1). At the part with equal length ratio, the thickness of the second blade (3) is less than the thickness of the first blade (2), with a thickness difference of 0.5-1.0 mm. At the part with equal chord length ratio, the thickness of the second blade (3) is less than the thickness of the first blade (2), with a thickness difference of 0.5-1.0 mm. The length of the second blade (3) is 62%-72% of the length of the first blade (2).

5. The impeller of a mechanical supercharger according to claim 3, characterized in that: The trailing edge (22) surfaces of the second blade (3) and the first blade (2) are smoothly transitioned to the top (15) sidewall of the wheel disk (1).

6. The impeller of a mechanical supercharger according to claim 3, characterized in that: The chord length of the leading edge (21) of the first blade (2) is greater than the chord length of the leading edge (21) of the second blade (3), and the chord length of the trailing edge (22) of the first blade (2) is less than the chord length of the trailing edge (22) of the second blade (3).

7. The impeller of a mechanical supercharger according to claim 1, characterized in that: The upper end of the positioning block (4) extending out of the second positioning groove (111) is provided with a friction layer (6). The end of the clamping ring (5) with a first inclined surface (41) is coaxially provided with an anti-loosening ring (7). The inner wall of the anti-loosening ring (7) is provided with several mounting grooves (71) spaced apart around its axis. A friction plate (72) is slidably provided in the mounting groove (71). The side of the friction plate (72) facing the groove opening of the mounting groove (71) is in contact with the side of the positioning block (4) with the friction layer (6). The side of the friction plate (72) in contact with the positioning block (4) is also provided with a friction layer (6). Several fixing bolts (73) are threaded on the outer wall of the anti-loosening ring (7). When the clamping ring (5) is tightened, the anti-loosening ring (7) abuts against the shaft shoulder. At this time, tightening the fixing bolts (73) can push the friction plate (72) to fit against the friction layer (6) of the positioning block (4).

Images