Fluid pump with piston type wheel blades

Abstract

A fluid pump with a piston vane includes a housing and a runner including a rotor and vanes. 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, 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 pressurizing cavity in the process of rotating along with the rotor to periodically stretch out and retract in the blade grooves, and through the piston type movement of the wheel blades, it is guaranteed that fluid is pumped and pressurized; and backflow of the fluid can be effectively avoided or even eradicated, so that the pumping efficiency of the fluid is remarkably improved, and the total pumping energy consumption of the fluid 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] The present invention relates to a fluid pump, and more particularly to a fluid pump with piston-type vanes, belonging to the technical field of kinetic machinery and equipment. Background Art

[0002] A pump is a machine that transports fluids or increases the pressure of fluids. It transfers the mechanical energy of a prime mover or other external energy to the fluid, increasing the energy of the fluid. Pumps are mainly used to transport gases (or vapors), water, oil, acid-base solutions, emulsions, suspension liquids, and liquid metals, etc., and can also transport liquid-gas mixtures and mixed fluids containing suspended solids, etc. Pumps can generally be classified into positive displacement pumps, impeller pumps, jet pumps, and other types of pumps according to the working principle.

[0003] In the production of the chemical and petroleum industries, most raw materials, semi-finished products, and finished products are liquids. To convert raw materials into semi-finished and finished products, complex technological processes are required. Pumps play a role in transporting liquids and providing pressure and flow for chemical reactions in these processes. In addition, pumps are also used to regulate temperature in many devices. In agricultural production, pumps are the main irrigation and drainage machinery. Every year, a large number of pumps are needed in rural areas. Generally speaking, agricultural pumps account for more than half of the total pump output. In the mining and metallurgical industries, pumps are also the most used equipment. Mines need pumps to drain water, and in the processes of ore dressing, smelting, and rolling, pumps are needed to supply water, etc. In the power sector, nuclear power plants require nuclear main pumps, secondary pumps, and tertiary pumps, and thermal power plants need a large number of boiler feed pumps, condensate pumps, oil-gas mixed transportation pumps, circulating water pumps, and ash pumps, etc. In national defense construction, the adjustment of aircraft flaps, rudders, and landing gears, the rotation of warship and tank turrets, and the sinking and floating of submarines all require pumps. In short, whether it is an airplane, a rocket, a tank, a submarine, or drilling, mining, trains, ships, or daily life, pumps are needed everywhere. Pumps are indispensable products 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 part of the centrifugal pump. It rotates at a high speed and has a large output. The blades on the impeller play a major role. The inner and outer surfaces of the impeller are required to be smooth to reduce the frictional loss of the water flow. In the prior art, centrifugal pumps are generally vane pumps. Mainly relying on the rotating blades during rotation, due to the interaction between the blades and the fluid, the blades transfer mechanical energy to the fluid, increasing the pressure energy of the fluid to achieve the purpose of transporting the fluid. However, due to the certain spacing between the blades of the vane pump, a containing area with a certain volume is formed, and there is generally a certain distance between the outer ends of the blades and the inner wall of the pump casing, that is, an edge gap. The existence of the containing area and the edge gap causes some of the fluid that has been sent to the downstream to flow back to the upstream area through the containing area and the edge gap during the high-speed rotation of the impeller. As a result, there is an inevitable system loss in the actual pumping volume of the fluid, which in turn leads to a relatively low pumping efficiency of the fluid, seriously affecting the effective head of the pumped fluid and increasing the pumping energy consumption, etc. In response to this problem, researchers have continuously explored improvement solutions, such as optimizing the blade design, reducing the containing area and the edge gap, and using new materials to improve the smoothness of the impeller surface, aiming to improve the pumping efficiency while reducing energy consumption and ensuring more efficient and stable fluid transportation. However, the centrifugal pumps in the prior art still have some bottlenecks that are difficult to overcome, such as the difficulty in breaking through the pumping efficiency, the high energy consumption remaining high, the high maintenance cost, and the limited application range, etc. Innovative technologies are urgently needed to achieve better performance. Summary of the Invention

[0005] In view of the problems in the prior art, such as the relatively low fluid pumping efficiency, the relatively low head of the pumped fluid, and the relatively high pumping energy consumption caused by the fluid backflow in the existing vane centrifugal pumps, the present invention provides a fluid pump with piston-type vanes. Through the cooperation of the piston-type vanes and the gradually changing flow channel, while centrifugally boosting and pumping the fluid, the backflow of the fluid can be avoided, greatly improving the fluid pumping efficiency, significantly increasing the head of the pumped fluid, and significantly reducing the fluid pumping energy consumption, providing new technical guidance for the efficient pumping of fluids.

[0006] To achieve the above technical objectives, the technical solutions adopted by the present invention are specifically described as follows:

[0007] A fluid pump with piston-type blades, the fluid pump comprising a housing and a runner. An internally opened fluid inlet chamber, a centrifugal pressurization chamber, and a fluid discharge chamber that are connected in series in sequence are provided inside the housing. The runner is installed in the centrifugal pressurization chamber and includes a rotor and blades. The rotor is of a cylindrical structure and has blade grooves opened on its side wall. The blades are installed in the blade grooves. The rotor is installed in the centrifugal pressurization chamber in an inscribed manner, such that when the rotor rotates, the blades are periodically extruded by the inner wall of the centrifugal pressurization chamber and perform periodic extending and retracting movements in the blade grooves.

[0008] Preferably, the centrifugal pressurization chamber is a variable-diameter circular chamber. In the direction from the fluid discharge chamber to the fluid inlet chamber, the inner diameter of the centrifugal pressurization chamber is the largest, and in the direction perpendicular to the direction from the fluid discharge chamber to the fluid inlet chamber, the inner diameter of the centrifugal pressurization chamber is the smallest. The rotor is installed in the centrifugal pressurization chamber in an eccentric manner. Along the rotation direction of the rotor, the outer wall of the rotor is inscribed with the inner wall of the centrifugal pressurization chamber in the section from the fluid discharge chamber to the fluid inlet chamber. At other positions of the centrifugal pressurization chamber, a gap is left between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber to form a flow channel, and the flow channel is respectively connected to the fluid inlet chamber and the fluid discharge chamber.

[0009] Preferably, the arc length of the part of the side wall of the rotor in contact with the inner wall of the centrifugal pressurization chamber is not greater than 0.4 times the entire outer wall circumference of the rotor, preferably not greater than 0.2 times the entire outer wall circumference of the rotor, and more preferably not greater than 0.1 times the entire outer wall circumference of the rotor.

[0010] Preferably, in the circumferential direction along the rotation of the rotor: between the contact position of the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber and the fluid discharge chamber, the gap between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber is an equal-width gap with the same radial width and / or a gradually expanding gap with a gradually increasing radial width. The radial widths of the equal-width gap and / or the gradually expanding gap are not greater than the height of the protruding part after the blade completely protrudes from the blade groove. Preferably, the radial widths of the equal-width gap and / or the gradually expanding gap are 0.7 to 1 times the height of the protruding part after the blade completely protrudes from the blade groove.

[0011] Preferably, in the circumferential direction along the rotation of the rotor: between the fluid discharge chamber and the contact position of the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber, the gap between the outer wall of the rotor and the inner wall of the centrifugal pressurization chamber is a gradually shrinking gap with a gradually decreasing radial width. The maximum radial width of the gradually shrinking gap is not less than the height of the protruding part after the blade completely protrudes from the blade groove. Preferably, its maximum radial width is 1 to 1.3 times the height of the protruding part after the blade completely protrudes from the blade groove. It should be noted that the minimum radial width of the gradually shrinking gap must be less than the height of the protruding part after the blade completely protrudes from the blade groove (generally 0.01 to 0.1 times the height of the protruding part after the blade completely protrudes from the blade groove).

[0012] Preferably, a through hole or a through groove communicating with the fluid discharge cavity is further formed in the inner wall of the centrifugal supercharging cavity corresponding to the tapered gap.

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

[0014] Preferably, the outer surface of the blade is an arc surface that fits the surface of the rotor. The pre-tightening elastic member is a pre-tightening torsion spring.

[0015] Preferably, the thinner end of the blade is an arc-shaped end face, and an arc-shaped limiting protrusion is provided on the arc-shaped end face. An arc-shaped limiting groove corresponding to the arc-shaped limiting protrusion is provided in the blade 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 blade 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.

[0016] Preferably, an upper drainage groove is formed on the inner side surface of the blade, and the upper drainage groove continues to extend to the upper edge of the end face of its thinner end after passing through the inner side surface of the blade.

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

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

[0019] Preferably, second rolling mechanisms are embedded on both side surfaces in the axial direction of the blade.

[0020] Preferably, the first rolling mechanism and the second rolling mechanism are each independently a roller or a ball.

[0021] Preferably, a plurality of blades are provided on the side wall of the rotor, and the plurality of blades are evenly distributed along the circumferential direction of the rotor. The thicker end of the blade is an inclined surface, and the inclination angle of the inclined surface is such that the plane of the inclined surface passes through the axis of the rotor after the blade is twisted and extended from the blade groove to the maximum angle.

[0022] Preferably, a driving motor is further installed on the outer side in the axial direction of the housing. The driving shaft of the driving motor passes through the housing and is connected to a shaft hole formed at the axis of the rotor, and the rotor is driven to rotate self in the centrifugal supercharging cavity by the driving motor.

[0023] Preferably, a grille is also provided at the fluid inlet of the fluid inlet chamber.

[0024] In the present invention, the rotor is installed in the centrifugal supercharging chamber in an inscribed manner, so that the radial distance between the outer wall of the rotor and the inner wall of the centrifugal supercharging chamber varies in the circumferential direction. The specific variation law needs to meet the requirements of the periodic extension and retraction of the blade in the blade groove. Generally, when the rotor rotates, the outer end of the blade following the rotation always contacts the inner wall of the centrifugal supercharging chamber. Since this radial distance is gradually changing, the rotating blade will be periodically squeezed by the inner wall of the centrifugal supercharging chamber and perform periodic extension and retraction movements in the blade groove. It should be noted that the fluid pump of the present invention has the function of supercharging and pushing the fluid. Therefore, in the region from the fluid inlet to the fluid outlet of the centrifugal supercharging chamber, the blade is in the extended state, that is, the above-mentioned radial distance is relatively large in this region (generally not less than the sum of the rotor radius and the blade extension height), so as to form a flow channel for the fluid to pass through; while in the region from the fluid outlet to the fluid inlet of the centrifugal supercharging chamber, the blade is in a partially or fully retracted state, that is, the above-mentioned radial distance is relatively small in this region (generally not greater than the sum of the rotor radius and the blade extension height), thereby effectively preventing the backflow of the fluid.

[0025] In the present invention, the centrifugal supercharging chamber is designed as a variable-diameter circular chamber, specifically: when the rotor is installed in the centrifugal supercharging chamber in an inscribed manner, the outer wall on one side of the rotor perpendicular to the fluid flow direction contacts the inner wall of the centrifugal supercharging chamber, and a gap is left between the remaining outer walls and the inner wall of the centrifugal supercharging chamber to form a flow channel connecting the fluid inlet chamber and the fluid discharge chamber. It should be noted that the part where the outer wall of the rotor contacts the inner wall of the centrifugal supercharging chamber can be a point or a side wall with a certain arc length (generally, the arc length of this part of the side wall is not greater than 0.1 to 0.4 times the entire outer wall circumference of the rotor), as long as it can prevent the fluid that has flowed to the fluid outlet of the centrifugal supercharging chamber from flowing back. In addition, it should also be noted that the said flow channel mainly refers to the fluid channel formed by the reserved gap between the fluid inlet and the fluid outlet of the centrifugal supercharging chamber in the circumferential direction of the rotor rotation. The radial distance of this section of the fluid channel is preferably always equal to the sum of the rotor radius and the protruding height of the blade, so that when the blade rotates with the rotor to this section of the area, the blade can completely pop out of the blade groove and the outer end of the blade abuts against the inner wall of the centrifugal supercharging chamber and rotates and slides, which can maximize the pushing effect of the blade on the fluid and avoid the phenomenon of fluid backflow at the end of the blade. Further, the reserved gap between the fluid outlet of the centrifugal supercharging chamber and the area where it contacts the outer wall of the rotor is designed with a gradually decreasing radial distance, so as to gradually compress and recover the blade into the blade groove; similarly, the reserved gap between the area where the centrifugal supercharging chamber contacts the outer wall of the rotor and its fluid inlet is designed with a gradually increasing radial distance, so as to gradually release the blade from the blade groove. That is to say, along the circumferential direction of the rotor rotation, the gap reserved between the outer wall of the rotor and the inner wall of the centrifugal supercharging chamber mainly includes three sections: the blade supercharging and pushing section (i.e., the main flow channel section) with a constant radial distance, the blade retraction section with a gradually decreasing radial distance, and the blade ejection section with a gradually increasing radial distance. Through the cooperation of the reserved gaps with three distance changes and the design of the piston-type blades, the purpose of high-efficiency, high-quality and low-energy-consumption pumping of the fluid is achieved.

[0026] In the present invention, the blade is an arc-shaped block structure with a thickness gradually increasing along the circumferential direction of the fluid flow, that is, the outer surface of the blade is an arc surface. The design of the arc-shaped blade can make the outer surface of the blade fit with the outer wall surface of the rotor after the blade is completely recovered into the blade groove, and then it can better contact the inner wall of the centrifugal supercharging chamber tightly during the rotation process without affecting its rotation and sliding.

[0027] In the present invention, a shaft hole is provided at one end of the vane with a relatively thin thickness, and a pre-tightening elastic member is installed in the shaft hole. Under the action of the pre-tightening elastic member (preferably a pre-tightening torsion spring), when the vane is not subjected to an external force, the end with a relatively thick thickness is ejected out of the vane groove to realize the process of pushing and pressurizing the fluid. When the vane is subjected to the extrusion force from the inner wall of the centrifugal pressurizing chamber, it will be pressed back into the vane groove as a whole. That is, through the combined action of the pre-tightening elastic member and the inner wall of the centrifugal pressurizing chamber, the vane performs a periodic piston-like action in the vane groove.

[0028] In the present invention, an outwardly protruding arc-shaped limiting protrusion is provided on the inner side of the end face of the vane at the end with a relatively thin thickness, and an arc-shaped limiting groove is provided in the corresponding vane groove below it. Moreover, the arc length of the arc-shaped limiting groove is greater than the arc length of the arc-shaped limiting protrusion. Thus, when the vane 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 vane, ensuring that the maximum rotation angles of the vanes evenly distributed in the circumferential direction of the rotor are consistent, improving the stability of fluid pushing, and at the same time avoiding the situation where the vane is damaged due to excessive rotation under the reaction force of the fluid when pushing the fluid and damaging the pre-tightening elastic member.

[0029] In the present invention, the end of the vane with a relatively thick thickness is a slope that slopes downward from top to bottom towards the end with a relatively thin thickness. The inclination angle of this slope is such that after the vane twists and extends from the vane groove to the maximum angle, the plane where this slope is located passes through the axis of the rotor. That is, when the vane rotates its end with a relatively thick thickness out of the vane groove to the maximum angle under the action of the pre-tightening elastic member, the end face of the end of the vane with a relatively thick thickness is always perpendicular to the surface of the rotor (the rotation angle is accurately ensured by the arc-shaped limiting protrusion and the arc-shaped limiting groove). Thus, when the vane rotates with the rotor, the end face that directly pushes the fluid can always apply the maximum possible thrust to the fluid.

[0030] In the present invention, an upper drainage groove that is integrally connected is provided on the inner side surface of the vane and on the end face of the end with a relatively thin thickness, and / or a lower drainage groove with the same extending direction as the upper drainage groove is provided on the two side walls and the bottom of the vane groove. One end of the upper drainage groove and the lower drainage groove is connected to the fluid source side. When the vane is recovered into the vane groove under the pressure from the inside of the centrifugal pressurizing chamber, the fluid located in the vane groove is compressed and flows out through the upper drainage groove and the lower drainage groove and finally enters 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 a through groove communicating with the fluid discharge chamber is also provided on the inner wall of the centrifugal pressurizing chamber corresponding to the tapered gap.

[0031] In the present invention, a first rolling mechanism is embedded at the junction of the end face and the outer surface at the thicker end of the blade. Through the first rolling mechanism, a sliding contact is achieved between the outer end of the blade and the inner wall of the centrifugal supercharging chamber, reducing the frictional force therebetween, which is beneficial to reducing the frictional loss between the two and improving the rotation efficiency of the runner. It should be noted that, if necessary, an auxiliary rolling mechanism can also be provided on the outer surface of the blade to further reduce the frictional resistance between the blade and the inner wall of the centrifugal supercharging chamber.

[0032] In the present invention, second rolling mechanisms are embedded on both side surfaces in the axial direction of the blade. Through the second rolling mechanisms, the frictional resistance between the side wall of the blade and the side wall of the groove during the ejection and recovery processes of the blade is reduced, ensuring the smooth ejection and recovery of the blade.

[0033] In the present invention, the fluid inlet diameter of the fluid inlet chamber is 1 - 1000 cm, preferably 5 - 500 cm, more preferably 10 - 300 cm. The fluid outlet diameter of the fluid discharge chamber is 1 - 1000 cm, preferably 5 - 500 cm, more preferably 10 - 300 cm. The radius of the centrifugal supercharging chamber is 5 - 500 cm, preferably 10 - 300 cm, more preferably 12 - 100 cm. The radius of the runner is 1 - 300 cm, preferably 5 - 200 cm, more preferably 10 - 100 cm.

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

[0035] 1: Through the special design of the blades and the rotor of the fluid pump of the present invention, the blades can be periodically extruded by the inner wall of the centrifugal supercharging chamber during the rotation with the rotor, and perform periodic extension and recovery movements in the blade grooves. And through this piston-like movement of the blades, while ensuring the pumping and supercharging of the fluid, it can effectively avoid or even eliminate the backflow of the fluid, thereby significantly improving the pumping efficiency of the fluid and greatly reducing the total pumping energy consumption 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 surging, simple operation, and low cost investment, providing new technical guidance for the efficient pumping of fluids. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] Figure 1 is the axial structure schematic diagram of the fluid pump of the present invention.

[0038] Figure 2 is the axial sectional view schematic diagram of the fluid pump of the present invention.

[0039] Figure 3 is the structure schematic diagram of the runner of the present invention.

[0040] Figure 4 This is a schematic structural view of the impeller of the present invention.

[0041] Figure 5 This is a top half-sectional schematic view of the fluid pump of the present invention.

[0042] Reference numerals: 1: housing; 101: fluid inlet chamber; 102: centrifugal supercharging chamber; 103: fluid discharge chamber; 104: flow channel; 2: runner; 201: rotor; 202: impeller; 203: blade groove; 204: shaft hole; 205: pre-tightening elastic member; 206: arc-shaped limit projection; 207: arc-shaped limit groove; 208: upper drainage groove; 209: lower drainage groove; 210: first rolling mechanism; 211: second rolling mechanism; 3: drive motor. Detailed implementation manners

[0043] The technical solutions of the present invention will be illustrated by way of examples below. The scope of protection claimed by the present invention includes but is not limited to the following embodiments.

[0044] A fluid pump with piston-type impellers, the fluid pump comprising a housing 1 and a runner 2. A fluid inlet chamber 101, a centrifugal supercharging chamber 102 and a fluid discharge chamber 103 are sequentially connected in series and opened inside the housing 1. The runner 2 is installed in the centrifugal supercharging chamber 102 and comprises a rotor 201 and impellers 202. The rotor 201 is of a cylindrical structure, and blade grooves 203 are opened on its side wall. The impellers 202 are installed in the blade grooves 203. The rotor 201 is installed in the centrifugal supercharging chamber 102 in an inscribed manner, such that when the rotor 201 rotates, the impellers 202 are periodically extruded by the inner wall of the centrifugal supercharging chamber 102 and perform periodic extending and retracting movements in the blade grooves 203.

[0045] Preferably, the centrifugal supercharging chamber 102 is a variable-diameter circular chamber. In the direction from the fluid discharge chamber 103 to the fluid inlet chamber 101, the inner diameter of the centrifugal supercharging chamber 102 is the largest, and in the direction perpendicular to the direction from the fluid discharge chamber 103 to the fluid inlet chamber 101, the inner diameter of the centrifugal supercharging chamber 102 is the smallest; the rotor 201 is installed in the centrifugal supercharging chamber 102 in an eccentric manner. Along the rotation direction of the rotor 201, the outer wall of the rotor 201 is inscribed with the inner wall of the centrifugal supercharging chamber 102 in the section from the fluid discharge chamber 103 to the fluid inlet chamber 101. At other positions of the centrifugal supercharging chamber 102, a gap is left between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 to form a flow channel 104, and the flow channel 104 is respectively communicated with the fluid inlet chamber 101 and the fluid discharge chamber 103.

[0046] Preferably, the arc length of the side wall of the part where the rotor 201 contacts the inner wall of the centrifugal supercharging chamber 102 is not greater than 0.4 times the entire outer wall circumference of the rotor 201, preferably not greater than 0.2 times the entire outer wall circumference of the rotor 201, and more preferably not greater than 0.1 times the entire outer wall circumference of the rotor 201.

[0047] Preferably, in the circumferential direction along the rotation of the rotor 201: between the contact point of the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 and the fluid discharge chamber 103, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 is an equal-width gap with the same radial width and / or a gradually expanding gap with a gradually increasing radial width. The radial width of the equal-width gap and / or the gradually expanding gap is not greater than the height of the protruding part after the blade 202 completely protrudes from the blade groove 203. Preferably, the radial width of the equal-width gap and / or the gradually expanding gap is 0.7 - 1 times the height of the protruding part after the blade 202 completely protrudes from the blade groove 203.

[0048] Preferably, in the circumferential direction along the rotation of the rotor 201: between the fluid discharge chamber 103 and the contact point of the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 is a gradually shrinking gap with a gradually decreasing radial width. The maximum radial width of the gradually shrinking gap is not less than the height of the protruding part after the blade 202 completely protrudes from the blade groove 203. Preferably, its maximum radial width is 1 - 1.3 times the height of the protruding part after the blade 202 completely protrudes from the blade groove 203.

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

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

[0051] Preferably, the outer surface of the blade 202 is an arc-shaped surface that fits the surface of the rotor 201. The pre-tightening elastic member 205 is a pre-tightening torsion spring.

[0052] Preferably, the thinner end of the blade 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 blade 202 rotates out 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.

[0053] Preferably, an upper drainage groove 208 is formed on the inner side surface of the blade 202, and the upper drainage groove 208 continues to extend to the upper edge of the end face of its thinner end after passing through the inner side surface of the blade 202.

[0054] Preferably, a lower drainage groove 209 is formed on the circumferential side wall of the blade groove 203 corresponding to the thicker end of the blade 202 from top to bottom, and the bottom end of the lower drainage groove 209 extends downward and completely passes through the bottom surface of the blade groove 203 and its other circumferential side wall in sequence.

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

[0056] Preferably, second rolling mechanisms 211 are embedded on both side surfaces of the blade 202 in the axial direction.

[0057] Preferably, the first rolling mechanism 210 and the second rolling mechanisms 211 are each independently a roller or a ball.

[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 circumferential direction 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 the plane where the inclined surface is located passes through the axis of the rotor 201 after the blade 202 twists out of the blade groove 203 to the maximum angle.

[0059] Preferably, a driving motor 3 is further installed on the outer side in the axial direction of the housing 1. The driving shaft of the driving motor 3 passes through the housing 1 and is connected to the shaft hole formed at the axis of the rotor 201, and the rotor 201 is driven to rotate self in the centrifugal supercharging cavity 102 by the driving motor 3.

[0060] Preferably, a grille is further provided at the fluid inlet of the fluid inlet cavity 101.

[0061] Embodiment 1

[0062] As Figures 1-5As shown in the figure, a fluid pump with piston-type blades, the fluid pump includes a housing 1 and a runner 2. An inlet fluid chamber 101, a centrifugal pressurization chamber 102, and an outlet fluid chamber 103 that are connected in series in sequence are provided inside the housing 1. The runner 2 is installed in the centrifugal pressurization chamber 102, and it includes a rotor 201 and blades 202. The rotor 201 is of a cylindrical structure, and blade grooves 203 are provided on its side wall. The blades 202 are installed in the blade grooves 203. The rotor 201 is installed in the centrifugal pressurization chamber 102 in an inscribed manner, such that when the rotor 201 rotates, the blades 202 are periodically extruded by the inner wall of the centrifugal pressurization chamber 102 and perform periodic extending and retracting movements in the blade grooves 203.

[0063] Example 2

[0064] Repeat Example 1, except that the centrifugal pressurization chamber 102 is a variable-diameter circular chamber. In the direction from the outlet fluid chamber 103 to the inlet fluid chamber 101, the inner diameter of the centrifugal pressurization chamber 102 is the largest, and in the direction perpendicular to the direction from the outlet fluid chamber 103 to the inlet fluid chamber 101, the inner diameter of the centrifugal pressurization chamber 102 is the smallest; the rotor 201 is installed in the centrifugal pressurization chamber 102 in an eccentric manner. Along the rotation direction of the rotor 201, the outer wall of the rotor 201 is in inscribed contact with the inner wall of the centrifugal pressurization chamber 102 in the section from the outlet fluid chamber 103 to the inlet fluid chamber 101. At other positions of the centrifugal pressurization chamber 102, a gap is left between the outer wall of the rotor 201 and the inner wall of the centrifugal pressurization chamber 102 to form a flow channel 104, and the flow channel 104 is respectively connected to the inlet fluid chamber 101 and the outlet fluid chamber 103.

[0065] Example 3

[0066] Repeat Example 2, except that the arc length of the part of the side wall of the rotor 201 in contact with the inner wall of the centrifugal pressurization chamber 102 is 0.15 times the entire outer wall circumference of the rotor 201.

[0067] Example 4

[0068] Repeat Example 2, except that the arc length of the part of the side wall of the rotor 201 in contact with the inner wall of the centrifugal pressurization chamber 102 is 0.05 times the entire outer wall circumference of the rotor 201.

[0069] Example 5

[0070] Repeat Example 4, except that in the circumferential direction along the rotation of the rotor 201: between the contact point of the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 and the fluid inlet chamber 101, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 is a tapered gap with a gradually increasing radial width; between the fluid inlet chamber 101 and the fluid discharge chamber 103, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 is an equal-width gap with an equal radial width. The maximum radial width of the tapered gap is consistent with the radial width of the equal-width gap, both being 1 times the height of the protruding part after the blade 202 completely protrudes from the blade groove 203.

[0071] Example 6

[0072] Repeat Example 5, except that in the circumferential direction along the rotation of the rotor 201: between the fluid discharge chamber 103 and the contact point of the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102, the gap between the outer wall of the rotor 201 and the inner wall of the centrifugal supercharging chamber 102 is a tapered gap with a gradually decreasing radial width. The maximum radial width of the tapered gap is 1.1 times the height of the protruding part after the blade 202 completely protrudes from the blade groove 203. The minimum radial width of the tapered gap is 0.03 times the height of the protruding part after the blade 202 completely protrudes from the blade groove 203.

[0073] Example 7

[0074] Repeat Example 6, except that a through hole communicating with the fluid discharge chamber 103 is further opened on the inner wall of the centrifugal supercharging chamber 102 corresponding to the tapered gap.

[0075] Example 8

[0076] Repeat Example 7, except that in the circumferential direction along the rotation of the rotor 201: the blade 202 is an arc-shaped block structure with a gradually increasing thickness. A shaft hole 204 is opened at the thinner end of the blade 202, and a pre-tightening elastic member 205 is installed in the shaft hole 204. Under the action of the pre-tightening elastic member 205, the thicker end of the blade 202 is ejected out of the blade groove 203.

[0077] Example 9

[0078] Repeat Example 8, except that the outer surface of the blade 202 is an arc surface that fits the surface of the rotor 201. The pre-tightening elastic member 205 is a pre-tightening torsion spring.

[0079] Example 10

[0080] Repeat Example 9, except that the thinner end of the vane 202 has 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 vane 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 vane 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.

[0081] Example 11

[0082] Repeat Example 10, except that an upper drainage groove 208 is provided on the inner side surface of the vane 202, and the upper drainage groove 208 continues to extend to the upper edge of the end face of its thinner end after passing through the inner side surface of the vane 202.

[0083] Example 12

[0084] Repeat Example 2, except that a lower drainage groove 209 is provided on the circumferential side wall of the vane groove 203 corresponding to the thicker end of the vane 202 from top to bottom, and the bottom end of the lower drainage groove 209 extends downward and completely passes through the bottom surface of the vane groove 203 and its other circumferential side wall in sequence.

[0085] Example 13

[0086] Repeat Example 12, except that a first rolling mechanism 210 is embedded at the junction of the end face and the upper surface of the thicker end of the vane 202.

[0087] Example 14

[0088] Repeat Example 13, except that second rolling mechanisms 211 are embedded on both side surfaces of the vane 202 in the axial direction.

[0089] Example 15

[0090] Repeat Example 14, except that the first rolling mechanism 210 is an axial roller; the second rolling mechanism 211 is a ball series-connected by a cage in the radial direction.

[0091] Example 16

[0092] Repeat Example 15, except that a plurality of vanes 202 are provided on the side wall of the rotor 201, and the plurality of vanes 202 are evenly distributed along the circumferential direction of the rotor 201. The thicker end of the vane 202 is an inclined surface, and the inclination angle of the inclined surface is such that the plane where the inclined surface is located passes through the axis of the rotor 201 after the vane 202 twists and extends from the vane groove 203 to the maximum angle.

[0093] Example 17

[0094] Repeat Example 16, except that a driving motor 3 is also installed on the outer side of the housing 1 in the axial direction. The driving shaft of the driving motor 3 passes through the housing 1 and is connected to the shaft hole opened at the center of the rotor 201, and the rotor 201 is driven by the driving motor 3 to rotate self - sufficiently in the centrifugal supercharging chamber 102.

[0095] Example 18

[0096] Repeat Example 17, except that a grille is also provided at the fluid inlet of the fluid inlet chamber 101.

[0097] During use, the external fluid (such as water) enters the centrifugal supercharging chamber 102 through the fluid inlet chamber 101 after preliminary filtration through the grille. The externally connected motor drives the rotor 201 and the blades 202 to rotate synchronously, so as to... Figure 2 For reference, the rotor 201 and the blades 202 rotate clockwise synchronously. A gradually expanding gap (i.e., the 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 supercharging chamber 102. During the clockwise rotation of the blades 202, the blades 202 gradually pop out of the blade grooves 203 under the action of the pre - tightening elastic member 205, so that the outer ends of the blades 202 always contact the left inner wall of the centrifugal supercharging chamber 102 until the blades 202 completely pop out of the blade grooves 203. During this process, the blades 202 push the fluid in the flow channel 104 forward and finally enter the fluid discharge chamber 103 for discharge. When the blades 202 rotate past the fluid inlet of the fluid discharge chamber 103 and enter the gradually shrinking gap on the right side of the rotor 201, as the blades 202 further rotate, the blades 202 first contact the right inner wall of the centrifugal supercharging chamber 102 and are further gradually pressed back into the blade grooves 203 by the right inner wall of the centrifugal supercharging chamber 102. During this process, the outer ends of the blades 202 contact the right inner wall of the centrifugal supercharging chamber 102, and the fluid brought over by inertia will be squeezed as the blades 202 gradually retract, and is pressed back to one side of the fluid discharge chamber 103 through the upper discharge groove 208 and the lower discharge groove 209, thus playing a role in preventing fluid backflow. When the blades 202 rotate to the fluid outlet of the fluid inlet chamber 101 again, the blades 202 will no longer be squeezed by the inner wall of the centrifugal supercharging chamber 102 and will start to pop out of the blade grooves 203 again, thereby performing a new round of pressurizing and pushing on the fluid from the fluid inlet chamber 101. By this cycle, efficient fluid pumping operation is achieved.

[0098] Application Example 1

[0099] The water in a pool (2m in length, width and height) was pumped out using the fluid pump described in Example 17. The diameters of the inlet pipe and the outlet pipe were both 8cm, the radius of the runner was 50cm, the height of the runner blades fully extended out of the blade grooves was 5cm, the number of runner blades was 12, and the power of the driving motor was 20Kw. The driving motor was started to pump out the water. Among them: the maximum head of the pumped water flow was about 221m, the outlet flow velocity was about 40.41m / s, and the total efficiency reached 89%.

[0100] A comparative test was carried out on the NK / NKE series pumps produced by GRUNDFOS under similar conditions. The results showed that the maximum head was about 165m, the outlet flow velocity was about 29.2m / s, and the total efficiency was about 77%. In contrast, the fluid pump of Example 17 of the present invention has improved in various performance indicators, reflecting a better design and higher efficiency. By optimizing the runner blade structure and the driving mechanism, the fluid pump of the present invention not only significantly exceeds the traditional pump types in terms of head and flow velocity, but also shows excellent advantages in the energy efficiency ratio, providing an efficient solution for the fluid transportation field. Further tests showed that after continuous operation for 24 hours, the temperature rise of the fluid pump of the present invention was only 5°C, and the noise was controlled within 60dB, showing excellent stability and low-noise characteristics. In the comparative test, the temperature rise of the GRUNDFOS pump reached 12°C, and the noise was about 75dB, further indicating the reliability and environmental friendliness of the fluid pump of the present invention during long-term operation, and verifying its comprehensive advantages in practical applications. In addition, the fluid pump of the present invention still operates efficiently under complex working conditions, has strong adaptability, and is suitable for a variety of 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 with a piston impeller, characterized in that: The fluid pump comprises a housing (1) and a rotor (2); the housing (1) is provided with a fluid inlet chamber (101), a centrifugal boost chamber (102) and a fluid outlet chamber (103) which are connected in series in sequence; the rotor (2) is installed in the centrifugal boost chamber (102) and comprises a rotor (201) and a blade (202); the rotor (201) is a cylindrical structure and has a blade groove (203) on its side wall; the blade (202) is installed in the blade groove (203); the rotor (201) is installed in the centrifugal boost chamber (102) in an inscribed manner, so that when the rotor (201) rotates, the blade (202) is periodically squeezed by the inner wall of the centrifugal boost chamber (102) and performs periodic extension and recovery movements in the blade groove (203).

2. The fluid pump according to claim 1, characterized in that: The centrifugal boost chamber (102) is a variable diameter circular chamber. In the direction from the fluid discharge chamber (103) to the fluid inlet chamber (101), the inner diameter of the centrifugal boost chamber (102) is the largest, and perpendicular to the direction from the fluid discharge chamber (103) to the fluid inlet chamber (101), the inner diameter of the centrifugal boost chamber (102) is the smallest; the rotor (201) is eccentrically mounted in the centrifugal boost chamber (102); along the direction of the rotor (201), the inner diameter of the centrifugal boost chamber (102) is the smallest. In the direction of rotation, the outer wall of the rotor (201) is inscribed with the inner wall of the centrifugal boost chamber (102) from the fluid discharge chamber (103) to the fluid inlet chamber (101); at other positions of the centrifugal boost chamber (102), a gap is left between the outer wall of the rotor (201) and the inner wall of the centrifugal boost chamber (102) to form a flow channel (104), and the flow channel (104) is respectively connected to the fluid inlet chamber (101) and the fluid discharge chamber (103).

3. The fluid pump according to claim 2, characterized in that: The arc length of the portion of the side wall of the rotor (201) that contacts the inner wall of the centrifugal boost chamber (102) is no greater than 0.4 times the circumference of the entire outer wall of the rotor (201), 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).

4. The fluid pump according to claim 3, characterized in that: In the circumferential direction of the rotation of the rotor (201): between the contact point between the outer wall of the rotor (201) and the inner wall of the centrifugal boost chamber (102) and the fluid discharge chamber (103), the gap between the outer wall of the rotor (201) and the inner wall of the centrifugal boost chamber (102) is an equal-width gap with the same radial width and / or a gradually expanding gap with a gradually increasing radial width; the radial width of the equal-width gap and / or the gradually expanding gap is not greater than the height of the protruding portion of the blade (202) after it is fully extended from the blade slot (203), and preferably, the radial width of the equal-width gap and / or the gradually expanding gap is 0.7 to 1 times the height of the protruding portion of the blade (202) after it is fully extended from the blade slot (203); and / or In the circumferential direction of the rotation of the rotor (201): 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 boost chamber (102), the gap between the outer wall of the rotor (201) and the inner wall of the centrifugal boost chamber (102) is a tapered gap with a gradually decreasing radial width, and the maximum radial width of the tapered gap is not less than the height of the protruding portion of the blade (202) after it is fully extended from the blade slot (203), and preferably, the maximum radial width is 1 to 1.3 times the height of the protruding portion of the blade (202) after it is fully extended from the blade slot (203); Preferably, a through hole or a through groove communicating with the fluid discharge chamber (103) is provided on the inner wall of the centrifugal boost chamber (102) corresponding to the tapered gap.

5. The fluid pump according to any one of claims 2 to 4, characterized in that: In the circumferential direction of the rotation of the rotor (201): the blade (202) is an arc-shaped block structure with gradually increasing thickness, an axial hole (204) is opened at the thinner end of the blade (202), and a pre-tightening elastic member (205) is installed in the axial hole (204), and under the action of the pre-tightening elastic member (205), the thicker end of the blade (202) is ejected out of the blade slot (203); Preferably, the outer surface of the blade (202) is an arc-shaped surface that fits the surface of the rotor (201); and the preloaded elastic member (205) is a preloaded torsion spring.

6. The fluid pump according to claim 5, characterized in that: The thinner end of the impeller blade (202) is an arc-shaped end face, and an arc-shaped limiting protrusion (206) is arranged on the arc-shaped end face; an arc-shaped limiting groove (207) corresponding to the arc-shaped limiting protrusion (206) is arranged in the impeller 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 blade (202) is rotated, extended and retracted 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).

7. The fluid pump according to claim 5 or 6, characterized in that: An upper drainage groove (208) is provided on the inner side surface of the blade (202), and the upper drainage groove (208) extends to the upper edge of the end surface of the thinner end of the blade (202) after penetrating the inner side surface of the blade (202); and / or A lower drainage groove (209) is provided from top to bottom on the circumferential side wall of the blade groove (203) corresponding to the thicker end of the blade (202), and the bottom end of the lower drainage groove (209) extends downward and completely passes through the bottom surface of the blade groove (203) and the other circumferential side wall thereof in sequence.

8. The fluid pump according to any one of claims 5 to 7, characterized in that: A first rolling mechanism (210) is embedded at the junction of the end surface of the thicker end of the blade (202) and its upper surface; and / or Second rolling mechanisms (211) are embedded on both axial side surfaces of the impeller blade (202); Preferably, the first rolling mechanism (210) and the second rolling mechanism (211) are each independently a roller or a ball.

9. The fluid pump according to any one of claims 5 to 8, characterized in that: A plurality of blades (202) are arranged on the side wall of the rotor (201), and the plurality of blades (202) are evenly distributed along the circumferential direction 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) is twisted and extended from the blade slot (203) to a maximum angle, the plane where the inclined surface is located passes through the axis of the rotor (201).

10. The fluid pump according to any one of claims 1 to 9, characterized in that: A drive motor (3) is also installed on the axially outer side of the housing (1); a drive shaft of the drive motor (3) passes through the housing (1) and is connected to an axial hole provided at the axis center of the rotor (201); the drive motor (3) drives the rotor (201) to rotate in the centrifugal boost chamber (102); and / or A grid is also provided at the fluid inlet of the fluid inlet chamber (101).

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