Fluid pump with piston type wheel blades

Abstract

The utility model discloses a fluid pump with a piston type wheel blade, which comprises a shell and a rotating wheel, and the rotating wheel comprises a rotor and a wheel blade. The rotor is installed in the centrifugal pressurizing cavity in an internally tangent mode, so that when the rotor rotates, the wheel blades are periodically extruded by the inner wall of the centrifugal pressurizing cavity to periodically stretch out and retract in the blade grooves. According to the fluid pump disclosed by the utility model, through the special design of the wheel blades and the rotor, the wheel blades can be periodically extruded by the inner wall of the centrifugal booster cavity in the process of rotating along with the rotor so as to periodically stretch out and retract in the blade grooves; and through the piston type movement of the wheel blades, fluid pumping pressurization is guaranteed, meanwhile, fluid backflow can be effectively avoided or even eradicated, then the fluid pumping efficiency is remarkably improved, and the total energy consumption of fluid pumping is greatly reduced. In addition, the fluid pump has the advantages of being simple in overall structure, low in energy consumption, stable in fluid pumping, small in surge, easy and convenient to operate, low in cost input and the like.

Description

Technical Field

[0001] This invention relates to a fluid pump, specifically a fluid pump with piston-type impellers, belonging to the field of dynamic mechanical equipment technology. Background Technology

[0002] A pump is a machine that transports or pressurizes fluids. It transfers the mechanical energy of a prime mover or other external energy to the fluid, increasing the fluid's energy. Pumps are mainly used to transport fluids such as gas (or steam), water, oil, acids and alkalis, emulsions, suspensions, and liquid metals. They can also transport mixtures of liquid and gas, as well as mixtures containing suspended solids. Pumps are generally classified according to their working principle into positive displacement pumps, impeller pumps, jet pumps, and other types of pumps.

[0003] In the chemical and petroleum industries, raw materials, semi-finished products, and finished products are mostly liquids. Transforming raw materials into semi-finished and finished products requires complex processes, and pumps play a crucial role in these processes by transporting liquids and providing the pressure and flow for chemical reactions. Furthermore, pumps are used in many plants to regulate temperature. In agricultural production, pumps are the primary irrigation and drainage machinery. my country's rural areas are vast, and rural areas require a large number of pumps annually; generally, agricultural pumps account for more than half of the total pump production. Pumps are also the most widely used equipment in the mining and metallurgical industries. Mines require pumps for drainage, and pumps are needed for water supply during mineral processing, smelting, and rolling processes. In the power sector, nuclear power plants require main nuclear pumps, secondary pumps, and tertiary pumps; thermal power plants require a large number of boiler feed pumps, condensate pumps, oil and gas mixing pumps, circulating water pumps, and ash pumps. In national defense, pumps are needed for adjusting aircraft flaps, rudders, and landing gear; rotating warship and tank turrets; and for the buoyancy and snorkeling of submarines. In short, pumps are needed everywhere, from airplanes, rockets, tanks, and submarines to drilling, mining, trains, ships, and even in daily life. Pumps are an indispensable product in the general machinery industry.

[0004] A centrifugal pump is a pump that uses the centrifugal force generated by the rotation of an impeller to transport fluids. The impeller is the core component of a centrifugal pump; it rotates at high speed and delivers high output. The blades on the impeller play a major role, and the inner and outer surfaces of the impeller must be smooth to reduce frictional losses in the water flow. In current technology, centrifugal pumps are generally vane pumps. They rely on the interaction between the rotating blades and the fluid during rotation, where the blades transfer mechanical energy to the fluid, increasing the fluid's pressure energy and achieving the purpose of fluid transport. However, because there is a certain distance between the blades in a vane pump, forming a condensation area with a certain volume, and there is generally a certain distance between the outer end of the blade and the inner wall of the pump casing, the existence of this condensation area and edge gap means that during the high-speed rotation of the impeller, some of the fluid that has been sent downstream will flow back to the upstream area through this condensation area and edge gap. This leads to unavoidable system losses in the actual pumped fluid volume, resulting in low pumping efficiency, severely affecting the effective head of the pumped fluid, and increasing pumping energy consumption. To address this issue, researchers have continuously explored improvement solutions. By optimizing blade design, reducing the containment area and edge clearance, and using new materials to improve impeller surface smoothness, they strive to increase pumping efficiency while reducing energy consumption, ensuring more efficient and stable fluid transport. However, existing centrifugal pumps still face some insurmountable bottlenecks, such as difficulty in achieving breakthroughs in pumping efficiency, persistently high energy consumption, high maintenance costs, and limited applicability. Innovative technologies are urgently needed to achieve superior performance. Summary of the Invention

[0005] In view of the problems of low pumping efficiency, relatively low pump head, and high pumping energy consumption caused by fluid backflow in existing impeller centrifugal pumps, this invention provides a fluid pump with piston impellers. By using piston impellers in conjunction with a gradually changing flow channel, the pump can centrifugally pressurize and pump out the fluid while avoiding fluid backflow, which greatly improves the fluid pumping efficiency, significantly increases the pump head, and significantly reduces the fluid pumping energy consumption, providing new technical guidance for efficient fluid pumping.

[0006] To achieve the above-mentioned technical objectives, the technical solution adopted by the present invention is specifically as follows:

[0007] A fluid pump with piston-type impellers includes a housing and a rotor. The housing has a fluid inlet chamber, a centrifugal pressurization chamber, and a fluid discharge chamber connected in series. The rotor, mounted within the centrifugal pressurization chamber, includes a rotor and impeller blades. The rotor is cylindrical and has blade grooves on its sidewalls. The blades are mounted within these blade grooves. The rotor is tangentially mounted within the centrifugal pressurization chamber, causing the blades to periodically extend and retract within the blade grooves due to periodic compression from the inner wall of the chamber during rotation.

[0008] Preferably, the centrifugal pressurization chamber is a variable-diameter circular chamber, with its inner diameter being largest in the direction from the fluid discharge chamber to the fluid inlet chamber and smallest perpendicular to the direction from the fluid discharge chamber to the fluid inlet chamber. The rotor is eccentrically mounted within the centrifugal pressurization chamber. Along the direction of rotor rotation, the outer wall of the rotor is internally tangent to the inner wall of the centrifugal pressurization chamber in the section from the fluid discharge chamber to the fluid inlet chamber. At other locations within the centrifugal pressurization chamber, a gap exists between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber, forming a flow channel that communicates with both the fluid inlet chamber and the fluid discharge chamber.

[0009] Preferably, the arc length of the sidewall that contacts the inner wall of the centrifugal booster chamber is no greater than 0.4 times the circumference of the entire outer wall of the rotor, more preferably no greater than 0.2 times the circumference of the entire outer wall of the rotor, and more preferably no greater than 0.1 times the circumference of the entire outer wall of the rotor.

[0010] Preferably, along the circumferential direction of rotor rotation: from the point where the outer wall of the rotor contacts the inner wall of the centrifugal pressurization chamber to the fluid discharge chamber, the gap between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber is a uniform gap with the same radial width and / or a gradually widening gap with a gradually increasing radial width. The radial width of the uniform gap and / or the gradually widening gap is not greater than the height of the protruding portion of the blade after it has fully extended from the blade slot; preferably, the radial width of the uniform gap and / or the gradually widening gap is 0.7 to 1 times the height of the protruding portion of the blade after it has fully extended from the blade slot.

[0011] Preferably, along the circumferential direction of rotor rotation, the gap between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber, from the fluid discharge chamber to the contact point between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber, is a gradually narrowing gap with a gradually decreasing radial width. The maximum radial width of the narrowing gap is not less than the height of the blade extension after it has fully extended from the blade slot, and preferably, its maximum radial width is 1 to 1.3 times the height of the blade extension after it has fully extended from the blade slot. It should be noted that the minimum radial width of the narrowing gap must be less than the height of the blade extension after it has fully extended from the blade slot (generally 0.01 to 0.1 times the height of the blade extension after it has fully extended from the blade slot).

[0012] Preferably, a through hole or through groove connected to the fluid discharge chamber is also provided on the inner wall of the centrifugal pressurization chamber corresponding to the gradually narrowing gap.

[0013] Preferably, in the circumferential direction along the rotor rotation: the blade is an arc-shaped block structure with gradually increasing thickness, and the thinner end of the blade has a shaft hole, and a pre-tightening elastic element is installed in the shaft hole. Under the action of the pre-tightening elastic element, the thicker end of the blade is ejected out of the blade groove.

[0014] Preferably, the outer surface of the impeller is an arc-shaped surface that matches the rotor surface. The preloaded elastic element is a preloaded torsion spring.

[0015] Preferably, the thinner end of the impeller is an arc-shaped end face, and an arc-shaped limiting protrusion is provided on this arc-shaped end face. An arc-shaped limiting groove corresponding to the arc-shaped limiting protrusion is provided within the impeller groove, and the arc length of the arc-shaped limiting groove is greater than the arc length of the arc-shaped limiting protrusion. When the impeller rotates and extends and retracts around the shaft hole as the center of rotation, the arc-shaped limiting protrusion slides back and forth within the arc-shaped limiting groove.

[0016] Preferably, an upper drainage groove is provided on the inner side of the impeller, and the upper drainage groove extends to the upper edge of the thinner end face after penetrating the inner side of the impeller.

[0017] Preferably, a lower discharge groove is formed from top to bottom on the circumferential sidewall of the end of the blade groove corresponding to the thicker end of the blade, and the bottom end of the lower discharge groove extends downward and passes through the bottom surface of the blade groove and its other circumferential sidewall in sequence.

[0018] Preferably, a first rolling mechanism is embedded at the junction of the end face of the thicker end of the blade and its upper surface.

[0019] Preferably, a second rolling mechanism is embedded on both sides of the impeller axial direction.

[0020] Preferably, the first rolling mechanism and the second rolling mechanism are each independently rollers or balls.

[0021] Preferably, multiple blades are provided on the side wall of the rotor, and the multiple blades are evenly distributed along the circumference of the rotor. The thicker end of the blade is a slope, and the inclination angle of the slope is such that after the blade twists and extends out of the blade slot to the maximum angle, the plane containing the slope passes through the axis of the rotor.

[0022] Preferably, a drive motor is also installed on the axial outer side of the housing. The drive shaft of the drive motor passes through the housing and is connected to the shaft hole opened at the center of the rotor shaft. The drive motor drives the rotor to rotate in the centrifugal pressurization chamber.

[0023] Preferably, a grid is also provided at the fluid inlet of the fluid inlet cavity.

[0024] In this invention, the rotor is installed in a tangential manner within the centrifugal pressurization chamber, such that the radial distance between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber varies in the circumferential direction. The specific variation pattern needs to match the periodic extension and retraction requirements of the blades in the blade slots. Generally, when the rotor is rotating, the outer end of the rotating blades is always in contact with the inner wall of the centrifugal pressurization chamber. Since this radial distance is gradually changing, the rotating blades are periodically squeezed by the inner wall of the centrifugal pressurization chamber and thus perform periodic extension and retraction movements in the blade slots. It should be noted that the fluid pump of the present invention has the function of pressurizing and pushing fluid. Therefore, in the region from the fluid inlet of the centrifugal pressurizing chamber to its fluid outlet, the impeller is in an extended state, that is, the radial spacing in this region is relatively large (generally not less than the sum of the rotor radius and the impeller extension height), so as to form a flow channel for the fluid to pass through. In contrast, in the region from the fluid outlet of the centrifugal pressurizing chamber to its fluid inlet, the impeller is in a partially or completely retracted state, that is, the radial spacing in this region is relatively small (generally not greater than the sum of the rotor radius and the impeller extension height), thereby effectively preventing fluid backflow.

[0025] In this invention, the centrifugal pressurization chamber is designed as a variable-diameter circular chamber. Specifically, when the rotor is installed tangentially within the centrifugal pressurization chamber, the outer wall of the rotor perpendicular to the fluid flow direction contacts the inner wall of the centrifugal pressurization chamber. The remaining outer walls have gaps with the inner wall of the centrifugal pressurization chamber, forming a flow channel connecting the fluid inlet chamber and the fluid outlet chamber. It should be noted that the portion of the rotor's outer wall that contacts the inner wall of the centrifugal pressurization chamber can be a point or a section of sidewall with a certain arc length (generally, the arc length of this section of sidewall is no greater than 0.1 to 0.4 times the circumference of the entire outer wall of the rotor), serving the purpose of preventing backflow of fluid that has already reached the fluid outlet of the centrifugal pressurization chamber. Furthermore, it should be noted that the flow channel mainly refers to the fluid passage formed by the reserved gap between the fluid inlet and the fluid outlet of the centrifugal booster chamber in the circumferential direction of rotor rotation. The radial spacing of this fluid passage is preferably always equal to the sum of the rotor radius and the blade extension height, so that when the blade rotates with the rotor to this area, the blade can be completely ejected from the blade slot and its outer end can slide and rotate against the inner wall of the centrifugal booster chamber. This maximizes the pushing effect of the blade on the fluid while preventing fluid backflow at the blade end. Further, the reserved gap between the fluid outlet of the centrifugal booster chamber and its contact area with the rotor's outer wall is designed with a gradually decreasing radial spacing to facilitate the gradual compression and retraction of the blade into the blade slot; similarly, the reserved gap between the contact area between the centrifugal booster chamber and the rotor's outer wall and its fluid inlet is designed with a gradually increasing radial spacing to facilitate the gradual release of the blade from the blade slot. In other words, along the circumferential direction of rotor rotation, the gap between the outer wall of the rotor and the inner wall of the centrifugal booster chamber mainly consists of three sections: the impeller booster pushing section (i.e., the main flow channel section) with a constant radial spacing, the impeller retraction section with a gradually decreasing radial spacing, and the impeller ejection section with a gradually increasing radial spacing. Through the design of these three varying gaps in conjunction with the piston-type impeller, the goal of efficient, high-quality, and low-energy-consumption pumping of fluid is achieved.

[0026] In this invention, the impeller is an arc-shaped block structure with a thickness that gradually increases along the circumferential direction of fluid flow. That is, the outer surface of the impeller is an arc-shaped surface. The design of the arc-shaped impeller allows its outer surface to fit with the outer wall of the rotor after the impeller is completely retracted into the blade slot. Thus, during rotation, it can better contact the inner wall of the centrifugal booster chamber without affecting its rotation and sliding.

[0027] In this invention, a shaft hole is provided at the thinner end of the impeller, and a pre-tensioned elastic element is installed in the shaft hole. Under the action of the pre-tensioned elastic element (preferably a pre-tensioned torsion spring), when the impeller is not subjected to external force, the thicker end is ejected out of the blade slot, thereby realizing the process of pushing and pressurizing the fluid. When the impeller is subjected to the squeezing force of the inner wall of the centrifugal pressurization chamber, it will be pressed back into the blade slot as a whole. That is, through the combined action of the pre-tensioned elastic element and the inner wall of the centrifugal pressurization chamber, the impeller periodically performs a piston-like action within the blade slot.

[0028] In this invention, an outwardly protruding arc-shaped limiting protrusion is provided on the inner side of the thinner end face of the impeller, and an arc-shaped limiting groove is provided in the corresponding blade groove below it. The arc length of the arc-shaped limiting groove is greater than the arc length of the arc-shaped limiting protrusion. As the impeller rotates and extends and retracts with the shaft hole as the rotation center, the arc-shaped limiting protrusion slides back and forth in the arc-shaped limiting groove, thereby limiting the maximum rotation angle of the impeller. This ensures that the maximum rotation angle of each impeller uniformly distributed in the rotor circumference is consistent, thereby improving the stability of fluid pushing. At the same time, it can also prevent the impeller from being over-rotated due to the reaction force of the fluid when pushing the fluid, thus avoiding damage to the pre-tightening elastic element.

[0029] In this invention, the thicker end of the blade is an inclined plane that slopes downwards towards the thinner end. The inclination angle of this inclined plane is such that after the blade twists and extends out of the blade slot to its maximum angle, the plane containing this inclined plane passes through the axis of the rotor. That is, when the blade rotates and ejects its thicker end out of the blade slot to its maximum angle under the action of the pre-tightened elastic element, the end face of the thicker end of the blade is always perpendicular to the surface of the rotor (its rotation angle is precisely ensured by the arc-shaped limiting protrusion and the arc-shaped limiting groove). Thus, when the blade rotates with the rotor, the end face that directly pushes the fluid can always apply the largest possible thrust to the fluid.

[0030] In this invention, an integrally connected upper discharge groove is formed on the inner surface of the impeller and the thinner end face, and / or a lower discharge groove is formed on the two side walls and the bottom of the blade groove, extending in the same direction as the upper discharge groove. One end of both the upper and lower discharge grooves is connected to the fluid source side. When the impeller is retracted into the blade groove due to pressure from inside the centrifugal pressurization chamber, the fluid in the blade groove is compressed and flows out through the upper and lower discharge grooves, eventually entering the fluid discharge chamber. It should be noted that, in order to ensure that this part of the fluid can enter the fluid discharge chamber, a through hole or through groove connected to the fluid discharge chamber is also formed on the inner wall of the centrifugal pressurization chamber corresponding to the tapering gap.

[0031] In this invention, a first rolling mechanism is embedded at the junction of the thicker end face of the impeller and its outer surface. This first rolling mechanism enables sliding contact between the outer end of the impeller and the inner wall of the centrifugal booster chamber, reducing friction between them and thus minimizing frictional losses and improving the rotational efficiency of the impeller. It should be noted that, if necessary, an auxiliary rolling mechanism can also be provided on the outer surface of the impeller to further reduce the frictional resistance between the impeller and the inner wall of the centrifugal booster chamber.

[0032] In this invention, a second rolling mechanism is embedded on both sides of the blade along the axial direction. The second rolling mechanism reduces the frictional resistance between the side wall of the blade and the side wall of the groove during the ejection and retraction process, thus ensuring the smooth ejection and retraction of the blade.

[0033] In this invention, the fluid inlet diameter of the fluid inlet chamber is 1-1000 cm, preferably 5-500 cm, and more preferably 10-300 cm. The fluid outlet diameter of the fluid outlet chamber is 1-1000 cm, preferably 5-500 cm, and more preferably 10-300 cm. The radius of the centrifugal booster chamber is 5-500 cm, preferably 10-300 cm, and more preferably 12-100 cm. The radius of the impeller is 1-300 cm, preferably 5-200 cm, and more preferably 10-100 cm.

[0034] Compared with the prior art, the beneficial technical effects of the present invention are as follows:

[0035] 1. The fluid pump of the present invention, through the special design of the impeller and rotor, enables the impeller to be periodically squeezed by the inner wall of the centrifugal pressurization chamber during the rotation of the rotor, and to periodically extend and retract in the impeller groove. In addition, through this piston-like movement of the impeller, while ensuring the pumping and pressurization of the fluid, it can also effectively avoid or even eliminate the backflow of the fluid, thereby significantly improving the pumping efficiency of the fluid and greatly reducing the total energy consumption of the pumping of the fluid.

[0036] 2. The fluid pump of the present invention has the advantages of simple overall structure, low energy consumption, stable fluid pumping, small surge, easy operation and low cost, providing new technical guidance for efficient fluid pumping. Attached Figure Description

[0037] Figure 1 This is a schematic diagram of the axial structure of the fluid pump described in this invention.

[0038] Figure 2 This is an axial cross-sectional schematic diagram of the fluid pump described in this invention.

[0039] Figure 3 This is a schematic diagram of the structure of the rotary wheel described in this invention.

[0040] Figure 4 This is a schematic diagram of the structure of the impeller described in this invention.

[0041] Figure 5 This is a top half-sectional view of the fluid pump described in this invention.

[0042] Reference numerals: 1: Housing; 101: Fluid inlet chamber; 102: Centrifugal pressurization chamber; 103: Fluid outlet chamber; 104: Flow channel; 2: Wheel; 201: Rotor; 202: Blade; 203: Blade groove; 204: Shaft hole; 205: Pre-tightening elastic element; 206: Arc-shaped limiting protrusion; 207: Arc-shaped limiting groove; 208: Upper discharge groove; 209: Lower discharge groove; 210: First rolling mechanism; 211: Second rolling mechanism; 3: Drive motor. Detailed Implementation

[0043] The technical solution of the present invention will be illustrated below with examples. The scope of protection sought by the present invention includes, but is not limited to, the following embodiments.

[0044] A fluid pump with piston-type impellers includes a housing 1 and a rotor 2. The housing 1 has a fluid inlet chamber 101, a centrifugal booster chamber 102, and a fluid outlet chamber 103 connected in series inside. The rotor 2 is installed within the centrifugal booster chamber 102 and includes a rotor 201 and impellers 202. The rotor 201 has a cylindrical structure and impeller grooves 203 formed on its sidewall. The impellers 202 are installed within the impeller grooves 203. The rotor 201 is tangentially installed within the centrifugal booster chamber 102, so that when the rotor 201 rotates, the impellers 202 are periodically compressed by the inner wall of the centrifugal booster chamber 102, causing them to periodically extend and retract within the impeller grooves 203.

[0045] Preferably, the centrifugal booster chamber 102 is a variable-diameter circular chamber. The inner diameter of the centrifugal booster chamber 102 is largest in the direction from the fluid discharge chamber 103 to the fluid inlet chamber 101, and smallest in the direction perpendicular to the fluid discharge chamber 103 to the fluid inlet chamber 101. The rotor 201 is eccentrically mounted within the centrifugal booster chamber 102. Along the rotation direction of the rotor 201, the outer wall of the rotor 201 is internally tangent to the inner wall of the centrifugal booster chamber 102 in the section from the fluid discharge chamber 103 to the fluid inlet chamber 101. At other locations within the centrifugal booster chamber 102, a gap is left between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102, forming a flow channel 104. This flow channel 104 communicates with both the fluid inlet chamber 101 and the fluid discharge chamber 103.

[0046] Preferably, the arc length of the part of the sidewall of the rotor 201 that contacts the inner wall of the centrifugal booster chamber 102 is no greater than 0.4 times the circumference of the entire outer wall of the rotor 201, more preferably no greater than 0.2 times the circumference of the entire outer wall of the rotor 201, and more preferably no greater than 0.1 times the circumference of the entire outer wall of the rotor 201.

[0047] Preferably, along the circumferential direction of rotor 201 rotation: from the point where the outer wall of rotor 201 contacts the inner wall of centrifugal booster chamber 102 to the fluid discharge chamber 103, the gap between the outer wall of rotor 201 and the inner wall of centrifugal booster chamber 102 is a uniform gap with the same radial width and / or a gradually expanding gap with a gradually increasing radial width. The radial width of the uniform gap and / or the gradually expanding gap is not greater than the height of the portion of the blade 202 extending fully from the blade slot 203. Preferably, the radial width of the uniform gap and / or the gradually expanding gap is 0.7 to 1 times the height of the portion of the blade 202 extending fully from the blade slot 203.

[0048] Preferably, in the circumferential direction along which the rotor 201 rotates: between the fluid discharge chamber 103 and the contact point between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102 is a gradually narrowing gap with a gradually decreasing radial width. The maximum radial width of the gradually narrowing gap is not less than the height of the part of the blade 202 that has fully extended out of the blade slot 203. Preferably, its maximum radial width is 1 to 1.3 times the height of the part of the blade 202 that has fully extended out of the blade slot 203.

[0049] Preferably, a through hole or through groove communicating with the fluid discharge chamber 103 is also provided on the inner wall of the centrifugal pressurization chamber 102 corresponding to the gradually narrowing gap.

[0050] Preferably, in the circumferential direction along the rotation of the rotor 201: the blade 202 is an arc-shaped block structure with gradually increasing thickness. The thinner end of the blade 202 is provided with a shaft hole 204, and a pre-tightening elastic element 205 is installed in the shaft hole 204. Under the action of the pre-tightening elastic element 205, the thicker end of the blade 202 is ejected out of the blade groove 203.

[0051] Preferably, the outer surface of the impeller 202 is an arc-shaped surface that matches the surface of the rotor 201. The preloaded elastic element 205 is a preloaded torsion spring.

[0052] Preferably, the thinner end of the impeller 202 has an arc-shaped end face, and an arc-shaped limiting protrusion 206 is provided on this arc-shaped end face. An arc-shaped limiting groove 207 corresponding to the arc-shaped limiting protrusion 206 is provided in the blade groove 203, and the arc length of the arc-shaped limiting groove 207 is greater than the arc length of the arc-shaped limiting protrusion 206. When the impeller 202 rotates and extends and retracts around the shaft hole 204 as the rotation center, the arc-shaped limiting protrusion 206 slides back and forth within the arc-shaped limiting groove 207.

[0053] Preferably, an upper drainage groove 208 is provided on the inner side of the impeller 202, and the upper drainage groove 208 extends to the upper edge of the thinner end face after penetrating the inner side of the impeller 202.

[0054] Preferably, a lower discharge groove 209 is provided on the circumferential sidewall of the blade groove 203 at the end of the blade 202 that is thicker, from top to bottom, and the bottom end of the lower discharge groove 209 extends downward and passes through the bottom surface of the blade groove 203 and its other circumferential sidewall in sequence.

[0055] Preferably, a first rolling mechanism 210 is embedded at the junction of the end face of the thicker end of the blade 202 and its upper surface.

[0056] Preferably, a second rolling mechanism 211 is embedded on both sides of the impeller 202 along the axial direction.

[0057] Preferably, the first rolling mechanism 210 and the second rolling mechanism 211 are each independently rollers or balls.

[0058] Preferably, a plurality of blades 202 are provided on the side wall of the rotor 201, and the plurality of blades 202 are evenly distributed along the circumference of the rotor 201. The thicker end of the blade 202 is a slope, and the inclination angle of the slope is such that after the blade 202 twists and extends out of the blade slot 203 to the maximum angle, the plane on which the slope is located passes through the axis of the rotor 201.

[0059] Preferably, a drive motor 3 is also installed on the axial outer side of the housing 1. The drive shaft of the drive motor 3 passes through the housing 1 and is connected to the shaft hole opened at the center of the rotor 201. The drive motor 3 drives the rotor 201 to rotate in the centrifugal pressurization chamber 102.

[0060] Preferably, a grid is also provided at the fluid inlet of the fluid inlet cavity 101. Example 1

[0061] like Figure 1-5As shown, a fluid pump with piston-type impellers includes a housing 1 and a rotor 2. The housing 1 has a fluid inlet chamber 101, a centrifugal booster chamber 102, and a fluid outlet chamber 103 connected in series inside. The rotor 2 is installed within the centrifugal booster chamber 102 and includes a rotor 201 and impellers 202. The rotor 201 has a cylindrical structure and impeller grooves 203 formed on its side wall. The impellers 202 are installed within the impeller grooves 203. The rotor 201 is tangentially installed within the centrifugal booster chamber 102, so that when the rotor 201 rotates, the impellers 202 are periodically compressed by the inner wall of the centrifugal booster chamber 102, causing them to periodically extend and retract within the impeller grooves 203. Example 2

[0062] The embodiment 1 is repeated, except that the centrifugal booster chamber 102 is a variable-diameter circular chamber. The inner diameter of the centrifugal booster chamber 102 is largest in the direction from the fluid discharge chamber 103 to the fluid inlet chamber 101, and smallest in the direction perpendicular to the fluid discharge chamber 103 to the fluid inlet chamber 101. The rotor 201 is eccentrically mounted within the centrifugal booster chamber 102. Along the rotation direction of the rotor 201, the outer wall of the rotor 201 is internally tangent to the inner wall of the centrifugal booster chamber 102 in the section from the fluid discharge chamber 103 to the fluid inlet chamber 101. At other locations within the centrifugal booster chamber 102, a gap is left between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102, forming a flow channel 104. This flow channel 104 communicates with both the fluid inlet chamber 101 and the fluid discharge chamber 103. Example 3

[0063] Repeat Example 2, except that the arc length of the part of the sidewall of the rotor 201 that contacts the inner wall of the centrifugal booster chamber 102 is 0.15 times the circumference of the entire outer wall of the rotor 201. Example 4

[0064] Repeat Example 3, except that the arc length of the part of the sidewall of the rotor 201 that contacts the inner wall of the centrifugal booster chamber 102 is 0.05 times the circumference of the entire outer wall of the rotor 201. Example 5

[0065] Repeat Example 4, except that in the circumferential direction of the rotor 201 rotation: from the contact point between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102 to the fluid inlet chamber 101, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102 is a gradually widening gap with a gradually increasing radial width; from the fluid inlet chamber 101 to the fluid outlet chamber 103, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102 is a uniformly wide gap with equal radial width. The maximum radial width of the gradually widening gap is consistent with the radial width of the uniformly wide gap, both being 1 times the height of the extended portion of the blade 202 after it has fully extended from the blade slot 203. Example 6

[0066] Repeat Example 5, except that in the circumferential direction of rotor 201 rotation: the gap between the fluid discharge chamber 103 and the contact point between the outer wall of rotor 201 and the inner wall of centrifugal booster chamber 102 is a gradually decreasing radial gap, wherein the maximum radial width of the gradually decreasing gap is 1.1 times the height of the protruding portion of blade 202 after it has fully extended from blade slot 203, and the minimum radial width of the gradually decreasing gap is 0.03 times the height of the protruding portion of blade 202 after it has fully extended from blade slot 203. Example 7

[0067] The embodiment 6 is repeated, except that a through hole connected to the fluid discharge chamber 103 is also provided on the inner wall of the centrifugal pressurization chamber 102 corresponding to the gradually narrowing gap. Example 8

[0068] Repeat Example 7, except that in the circumferential direction of the rotor 201: the blade 202 is an arc-shaped block structure with gradually increasing thickness. The thinner end of the blade 202 has a shaft hole 204, and a pre-tightening elastic element 205 is installed in the shaft hole 204. Under the action of the pre-tightening elastic element 205, the thicker end of the blade 202 is ejected out of the blade groove 203. Example 9

[0069] Example 8 is repeated, except that the outer surface of the impeller 202 is an arc-shaped surface that matches the surface of the rotor 201. The preloaded elastic element 205 is a preloaded torsion spring. Example 10

[0070] The embodiment 9 is repeated, except that the thinner end of the impeller 202 has an arc-shaped end face, and an arc-shaped limiting protrusion 206 is provided on this arc-shaped end face. An arc-shaped limiting groove 207 corresponding to the arc-shaped limiting protrusion 206 is provided in the blade groove 203, and the arc length of the arc-shaped limiting groove 207 is greater than the arc length of the arc-shaped limiting protrusion 206. When the impeller 202 rotates and extends and retracts around the shaft hole 204 as the rotation center, the arc-shaped limiting protrusion 206 slides back and forth within the arc-shaped limiting groove 207. Example 11

[0071] The embodiment 10 is repeated, except that an upper drainage groove 208 is provided on the inner side of the impeller 202, and the upper drainage groove 208 extends to the upper edge of the thinner end face after penetrating the inner side of the impeller 202. Example 12

[0072] Repeat embodiment 2, except that a lower discharge groove 209 is provided from top to bottom on the circumferential sidewall of the blade groove 203 corresponding to the thicker end of the blade 202, and the bottom end of the lower discharge groove 209 extends downward and passes through the bottom surface of the blade groove 203 and its other circumferential sidewall in sequence. Example 13

[0073] The embodiment 12 is repeated, except that a first rolling mechanism 210 is embedded at the junction of the end face of the thicker end of the blade 202 and its upper surface. Example 14

[0074] The embodiment 13 is repeated, except that a second rolling mechanism 211 is embedded on both sides of the impeller 202 in the axial direction. Example 15

[0075] Example 14 is repeated, except that the first rolling mechanism 210 is an axial roller; and the second rolling mechanism 211 is a ball bearing connected in series radially through a cage. Example 16

[0076] The embodiment 15 is repeated, except that multiple blades 202 are provided on the side wall of the rotor 201, and the multiple blades 202 are evenly distributed along the circumference of the rotor 201. The thicker end of the blade 202 is a slope, and the inclination angle of the slope is such that after the blade 202 twists and extends out of the blade slot 203 to the maximum angle, the plane of the slope passes through the axis of the rotor 201. Example 17

[0077] The embodiment 16 is repeated, except that a drive motor 3 is also installed on the axial outer side of the housing 1. The drive shaft of the drive motor 3 passes through the housing 1 and is connected to the shaft hole opened at the center of the rotor 201. The drive motor 3 drives the rotor 201 to rotate in the centrifugal pressurization chamber 102. Example 18

[0078] The same embodiment 17 is repeated, except that a grid is also provided at the fluid inlet of the fluid inlet cavity 101.

[0079] In use, external fluid (such as water) enters the centrifugal booster chamber 102 after initial filtration through the screen and via the fluid inlet chamber 101. An external motor drives the rotor 201 and impeller 202 to rotate synchronously, thereby... Figure 2 For reference, the rotor 201 and the impeller 202 rotate clockwise synchronously. A gradually widening gap (i.e., flow channel 104) with a gradually increasing radial width is formed between the left side wall of the rotor 201 and the inner wall of the centrifugal booster chamber 102. During the clockwise rotation of the impeller 202, the impeller 202 is gradually ejected from the blade groove 203 under the action of the pre-tightened elastic element 205, so that the outer end of the impeller 202 is always in contact with the left inner wall of the centrifugal booster chamber 102 until the impeller 202 is completely ejected from the blade groove 203. During this process, the impeller 202 pushes the fluid in the flow channel 104 forward and finally enters the fluid discharge chamber 103 for discharge. As the impeller 202 rotates past the fluid inlet of the fluid discharge chamber 103 and enters the tapering gap located on the right side of the rotor 201, with further rotation, the impeller 202 first contacts the right inner wall of the centrifugal booster chamber 102, and is then gradually pressed back into the blade groove 203 by the right inner wall of the centrifugal booster chamber 102. During this process, the outer end of the impeller 202 contacts the right inner wall of the centrifugal booster chamber 102, and the fluid carried by inertia will move along with the impeller 202. The fluid gradually retracts and is squeezed, and is pushed back to the side of the fluid discharge chamber 103 through the upper discharge groove 208 and the lower discharge groove 209, thereby preventing fluid backflow. When the impeller 202 rotates to the fluid outlet of the fluid inlet chamber 101 again, the impeller 202 will no longer be squeezed by the inner wall of the centrifugal booster chamber 102 and will start to pop out from the blade groove 203 again, thereby boosting and pushing the fluid from the fluid inlet chamber 101 for a new round. This cycle is repeated to achieve efficient pumping of fluid.

[0080] Application Example 1

[0081] The fluid pump described in Example 17 was used to pump water from a pool (2m in length, width, and height). The inlet and outlet pipes were both 8cm in diameter, the impeller radius was 50cm, the impeller blades extended 5cm from their slots, and there were 12 impeller blades. The drive motor had a power of 20kW. The pumping began with the maximum head of the pumped water at approximately 221m, the outlet velocity at approximately 40.41m / s, and the overall efficiency of 89%.

[0082] Comparative tests conducted under similar conditions on the NK / NKE series pumps manufactured by Grundfos showed that their maximum head was approximately 165 m, outlet velocity was approximately 29.2 m / s, and overall efficiency was approximately 77%. In contrast, the fluid pump of Embodiment 17 of this invention shows improvements in all performance indicators, demonstrating superior design and higher efficiency. By optimizing the impeller structure and drive mechanism, the fluid pump of this invention not only significantly surpasses traditional pump types in head and velocity but also exhibits superior energy efficiency, providing an efficient solution for fluid transportation. Further tests showed that after 24 hours of continuous operation, the temperature rise of the fluid pump of this invention was only 5°C, and the noise was controlled below 60 dB, demonstrating excellent stability and low noise characteristics. In the comparative test, the temperature rise of the GRUNDFOS pump reached 12°C, and the noise was around 75 dB, further demonstrating the reliability and environmental friendliness of the fluid pump of this invention during long-term operation and verifying its comprehensive advantages in practical applications. In addition, the fluid pump of this invention maintains high efficiency under complex working conditions, is highly adaptable, and is suitable for various fluid environments. Its innovative structure effectively reduces energy consumption and improves pump efficiency, contributing to energy conservation and emission reduction.

Claims

1. A fluid pump having a piston-type vane, characterized by: The fluid pump includes a housing (1) and a rotor (2); the housing (1) has a fluid inlet chamber (101), a centrifugal booster chamber (102) and a fluid outlet chamber (103) connected in series inside; the rotor (2) is installed in the centrifugal booster chamber (102) and includes a rotor (201) and impellers (202); the rotor (201) is a cylindrical structure and has impeller grooves (203) on its side wall; the impellers (202) are installed in the impeller grooves (203); the rotor (201) is installed in the centrifugal booster chamber (102) in an incisional manner, so that when the rotor (201) rotates, the impellers (202) are periodically squeezed by the inner wall of the centrifugal booster chamber (102) and periodically extend and retract in the impeller grooves (203).

2. The fluid pump of claim 1, wherein: The centrifugal booster chamber (102) is a variable-diameter circular chamber. The inner diameter of the centrifugal booster chamber (102) is the largest in the direction from the fluid discharge chamber (103) to the fluid inlet chamber (101), and the inner diameter of the centrifugal booster chamber (102) is the smallest in the direction perpendicular to the direction from the fluid discharge chamber (103) to the fluid inlet chamber (101). The rotor (201) is installed eccentrically in the centrifugal booster chamber (102). Along the rotation direction of the rotor (201), the outer wall of the rotor (201) is internally tangent to the inner wall of the centrifugal booster chamber (102) from the fluid discharge chamber (103) to the fluid inlet chamber (101). A gap is left between the outer wall of the rotor (201) and the inner wall of the centrifugal booster chamber (102) to form a flow channel (104), which is connected to the fluid inlet chamber (101) and the fluid discharge chamber (103) respectively.

3. The fluid pump of claim 2, wherein: The arc length of the part of the sidewall of the rotor (201) that contacts the inner wall of the centrifugal booster chamber (102) is no greater than 0.4 times the circumference of the entire outer wall of the rotor (201).

4. The fluid pump of claim 3, wherein: The arc length of the part of the sidewall of the rotor (201) that contacts the inner wall of the centrifugal booster chamber (102) is no greater than 0.2 times the circumference of the entire outer wall of the rotor (201).

5. The fluid pump of claim 4, wherein: The arc length of the part of the sidewall of the rotor (201) that contacts the inner wall of the centrifugal booster chamber (102) is no greater than 0.1 times the circumference of the entire outer wall of the rotor (201).

6. The fluid pump of claim 3, wherein: Along the circumferential direction of the rotor (201) rotation: from the point where the outer wall of the rotor (201) contacts the inner wall of the centrifugal booster chamber (102) to the fluid discharge chamber (103), the gap between the outer wall of the rotor (201) and the inner wall of the centrifugal booster chamber (102) is a uniform gap with the same radial width and / or a gradually expanding gap with a gradually increasing radial width; the radial width of the uniform gap and / or the gradually expanding gap is not greater than the height of the protruding part of the blade (202) after it has fully extended from the blade slot (203); and / or Along the circumferential direction of the rotor (201) rotation: between the fluid discharge chamber (103) and the contact point between the outer wall of the rotor (201) and the inner wall of the centrifugal booster chamber (102), the gap between the outer wall of the rotor (201) and the inner wall of the centrifugal booster chamber (102) is a gradually narrowing gap with a gradually decreasing radial width. The maximum radial width of the gradually narrowing gap is not less than the height of the part of the blade (202) after it has fully extended out of the blade slot (203).

7. The fluid pump of claim 6, wherein: On the inner wall of the centrifugal pressurization chamber (102) corresponding to the gradually narrowing gap, there is also a through hole or through groove that communicates with the fluid discharge chamber (103).

8. The fluid pump of claim 2, wherein: In the circumferential direction along the rotor (201): the blade (202) is an arc-shaped block structure with gradually increasing thickness. The thinner end of the blade (202) is provided with a shaft hole (204), and a pre-tightening elastic element (205) is installed in the shaft hole (204). Under the action of the pre-tightening elastic element (205), the thicker end of the blade (202) is ejected outside the blade groove (203).

9. The fluid pump of claim 8, wherein: The outer surface of the impeller (202) is an arc-shaped surface that fits the surface of the rotor (201); the pre-tightened elastic element (205) is a pre-tightened torsion spring.

10. The fluid pump of claim 8, wherein: The thinner end of the impeller (202) is an arc-shaped end face, and an arc-shaped limiting protrusion (206) is provided on the arc-shaped end face; an arc-shaped limiting groove (207) corresponding to the arc-shaped limiting protrusion (206) is provided in the blade groove (203), and the arc length of the arc-shaped limiting groove (207) is greater than the arc length of the arc-shaped limiting protrusion (206); when the impeller (202) rotates and extends and retracts with the shaft hole (204) as the rotation center, the arc-shaped limiting protrusion (206) slides back and forth in the arc-shaped limiting groove (207).

11. The fluid pump of claim 8, wherein: An upper discharge groove (208) is provided on the inner surface of the impeller (202), and the upper discharge groove (208) extends from the inner surface of the impeller (202) to the upper edge of the thinner end face; and / or A lower discharge groove (209) is provided on the circumferential sidewall of the blade groove (203) at the end of the blade (202) that is thicker, from top to bottom. The bottom end of the lower discharge groove (209) extends downward and passes through the bottom surface of the blade groove (203) and its other circumferential sidewall in sequence.

12. The fluid pump of claim 8, wherein: A first rolling mechanism (210) is embedded at the junction of the end face of the thicker end of the impeller (202) and its upper surface; and / or A second rolling mechanism (211) is embedded on both sides of the impeller (202) along the axial direction.

13. The fluid pump of claim 12, wherein: The first rolling mechanism (210) and the second rolling mechanism (211) are each independently rollers or balls.

14. The fluid pump of claim 8, wherein: Multiple blades (202) are provided on the side wall of the rotor (201), and the multiple blades (202) are evenly distributed along the circumference of the rotor (201); the thicker end of the blade (202) is an inclined surface, and the inclination angle of the inclined surface is such that after the blade (202) twists and extends out of the blade slot (203) to the maximum angle, the plane on which the inclined surface is located passes through the axis of the rotor (201).

15. The fluid pump of any one of claims 1-14, wherein: A driving motor (3) is also installed on the axial outer side of the shell (1), the driving shaft of the driving motor (3) passes through the shell (1) and is connected with the shaft hole opened at the shaft center of the rotor (201), the rotor (201) is driven to rotate in the centrifugal supercharging cavity (102) by the driving motor (3); and / or A grid is also arranged at the fluid inlet of the fluid inflow cavity (101).

Images