Impeller and centrifugal booster pump

Abstract

The utility model provides an impeller and a centrifugal booster pump, the impeller comprises a cover plate, and the cover plate is provided with an oil inlet; the bottom plate and the cover plate are correspondingly arranged at an interval to form a cylindrical structure; the blades are connected between the cover plate and the bottom plate, and the adjacent blades are arranged at intervals to form an oil outlet; the radial extension lines of the projections of the blades on the bottom plate meet the exponential function y = aebx, a ranges from 1.35 to 1.95, and b ranges from 0.13 to 0.16. The centrifugal booster pump comprises a pump body, a main shaft, a rear cover and an impeller, the rear cover is fixed at the axial rear end of the pump body to form an axial through structure, the rear cover is provided with an oil suction port, a volute chamber is arranged in the pump body, the pump body is provided with an oil discharge port corresponding to the volute chamber, the impeller is arranged in the volute chamber, the main shaft is axially arranged in the pump body, and the main shaft is in transmission connection with the impeller. On the basis of ensuring the quality of hydraulic oil, the pressurizing effect and the oil conveying efficiency are improved, so that the oil suction requirement of the hydraulic pump is met, and the hydraulic pump has the characteristics of simple structure and low cost.

Description

Technical Field

[0001] The utility model relates to the technical field of oil pumps, in particular to an impeller and a centrifugal booster pump. Background Art

[0002] Currently, booster pumps commonly used are water pumps and gear pumps. Water pumps are simple pump bodies designed for water-based media. Their impellers are thin, and the gap between the upper and lower covers is very small. When the impeller rotates at high speed, it generates shear flows with shear rates reaching tens of thousands per second. Using this water pump as a hydraulic oil booster pump, prolonged high-shear operation can lead to gradual performance deterioration and significantly shortened service life. This is because hydraulic oil has a viscosity 40-50 times that of water. When used as a hydraulic oil booster pump, the hydraulic oil is forced to undergo high-speed shearing motion, causing it to "tear" and deteriorate. This, in turn, creates bubbles within the hydraulic oil, a phenomenon known as shear cavitation. This creates a large amount of free air within the hydraulic oil, disrupting its continuity. This, in turn, significantly reduces the effective output flow of the water pump under high-speed shear conditions, resulting in very low oil delivery efficiency and difficulty meeting the hydraulic pump's suction requirements.

[0003] A gear pump is a positive displacement pump. When used as a booster pump in a hydraulic pump, its displacement must be greater than the hydraulic pump's to meet the pump's oil suction needs, resulting in high costs. Furthermore, damage to the gear pump can not only prevent the hydraulic pump from absorbing oil but also cause it to inhale air and be damaged, posing a high safety risk to the hydraulic pump.

[0004] Based on this, there is an urgent need to provide a booster pump to solve the problems of hydraulic oil deterioration, low efficiency and low cost. Utility Model Content

[0005] In order to overcome at least one of the defects described in the above-mentioned prior art, the utility model provides an impeller and a centrifugal booster pump, which improves the boosting effect and oil delivery efficiency while ensuring the quality of the hydraulic oil, thereby meeting the oil suction requirements of the hydraulic pump, and has the characteristics of simple structure and low cost.

[0006] The first aspect of the present invention provides an impeller, comprising:

[0007] A cover plate, wherein an oil inlet is provided on the cover plate;

[0008] The bottom plate and the cover plate are spaced and arranged correspondingly to form a cylindrical structure;

[0009] A plurality of blades are connected between the cover plate and the bottom plate, and adjacent blades are spaced apart to form an oil outlet;

[0010] The radial extension line of the blade's projection on the base plate satisfies the exponential function y = ae bx The changing law of a is 1.35-1.95, and the value of b is 0.13-0.16.

[0011] As an optional embodiment, in the first aspect of the present invention, the blade includes a first surface and a second surface arranged circumferentially spaced apart, the first surface and the second surface both extend radially, and the projections of the first surface and the second surface on the base plate both satisfy the exponential function y=ae bx The changing law of a is 1.35-1.95, and the value of b is 0.13-0.16.

[0012] As an optional embodiment, in the first aspect of the present invention, the distance between the corresponding positions of the first surface and the second surface is the thickness d of the blade, the diameter of the circular structure formed by several blades is the diameter D of the impeller, and the ratio of D / d satisfies (5-10):1.

[0013] As an optional embodiment, in the first aspect of the present utility model, the ends of the first surface and the second surface close to the impeller axis are connected by a transition surface, and the transition surface is an arc surface.

[0014] As an optional embodiment, in the first aspect of the present utility model, the number of blades is 6-9, and the blades are distributed at equal intervals in the circumferential direction.

[0015] A second aspect of the present invention provides a centrifugal booster pump, comprising: a pump body, a main shaft, a rear cover and the above-mentioned impeller, the rear cover being fixed to the axial rear end of the pump body to form an axially through structure, the rear cover being provided with an oil suction port, a vortex chamber being provided in the pump body, an oil discharge port being provided in the pump body corresponding to the vortex chamber, the impeller being provided in the vortex chamber, the main shaft being axially provided in the pump body, and the main shaft being transmission-connected to the impeller.

[0016] As an optional embodiment, in the second aspect of the present invention, the axis of the base plate of the impeller protrudes outwardly away from the cover plate axis to form a connecting portion, the main shaft passes through the connecting portion, and the connecting portion and the main shaft are transmission-connected via a matching spline structure.

[0017] As an optional embodiment, in the second aspect of the present utility model, the cover plate protrudes axially outward away from the base plate to form a boss, the boss is arranged on the radial outer periphery of the oil inlet, and a second oil seal is provided between the outer periphery of the boss and the inner wall of the pump body, and a first oil seal is provided between the side wall of the main shaft and the inner wall of the front end of the pump body.

[0018] As an optional embodiment, in the second aspect of the present utility model, a first retaining ring is provided between the front end of the first oil seal and the pump body, a third retaining ring is provided between the rear end of the second oil seal and the pump body, and a second retaining ring is provided at the end where the impeller is connected to the main shaft.

[0019] As an optional embodiment, in the second aspect of the present utility model, the main shaft passes through the impeller, the front end interference sleeve of the main shaft is provided with a first bearing, the rear end interference sleeve of the main shaft is provided with a second bearing supported by the bearing seat, and the oil suction port is connected to the impeller through the bearing seat.

[0020] As an optional embodiment, in the second aspect of the present utility model, the front end of the main shaft is used to connect to the output shaft of the motor, and the main shaft and the output shaft of the motor are connected via a flat key transmission.

[0021] As an optional implementation, in the second aspect of the present utility model, an O-ring is provided between the rear cover and the pump body, and the rear cover and the pump body are fixedly connected by bolts.

[0022] The impeller and centrifugal booster pump provided by the utility model have the following beneficial effects:

[0023] The radial extension line of the projection of the impeller blade on the base plate satisfies the exponential function y = ae bx The values ​​of a and b are 1.35-1.95 and 0.13-0.16, respectively, so that the blades extend radially inward in an arc shape from the circumferential edge of the impeller, and the spacing between adjacent blades near the circumferential edge is greater than the spacing near the impeller's axis. In this manner, when the impeller is used in a centrifugal booster pump, after the pump draws oil, the high-speed rotation of the impeller drives the blades to rotate synchronously. This centrifugal force causes the hydraulic oil to be flung from the center of the impeller toward the circumferential edge, where it flows out of the oil discharge port at a higher pressure for the hydraulic pump to absorb. Simultaneously, a certain vacuum is created at the center of the impeller due to the flung hydraulic oil, facilitating the hydraulic oil's entry into the centrifugal booster pump through the oil suction port due to the pressure differential and into the impeller through the oil inlet. This reciprocating impeller rotation continuously draws and discharges hydraulic oil, improving the centrifugal booster pump's boosting effect and oil delivery efficiency while maintaining the hydraulic oil's quality, meeting the pump's suction requirements. Furthermore, the pump has the advantages of a simple structure and low cost. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 Schematic diagram of the structure of the impeller of Example 1;

[0025] Figure 2 This is a front view of the impeller of Example 1;

[0026] Figure 3 is a top view of the impeller of Example 1;

[0027] Figure 4 is an exponential function graph of the radial extension line of the blade of Example 1;

[0028] Figure 5 Schematic diagram of the structure of the centrifugal booster pump of Example 2;

[0029] Figure 6 An axial cross-sectional view of the centrifugal booster pump of Example 2;

[0030] Figure 7 This is a schematic structural diagram of the pump body of Example 2;

[0031] Figure 8 This is a cross-sectional view of the vortex chamber of the pump body of Example 2.

[0032] The meanings of the reference numerals are as follows:

[0033] 1. Pump body; 101. Vortex chamber; 102. Oil discharge port; 2. Main shaft; 3. Flat key; 4. First retaining ring; 5. First oil seal; 6. First bearing; 7. Second retaining ring; 8. Impeller; 81. Cover plate; 811. Oil inlet; 82. Bottom plate; 83. Blade; 831. First surface; 832. Second surface; 833. Transition surface; 84. Oil outlet; 85. Connecting part; 851. Spline structure; 86. Boss; 9. Second oil seal; 10. Third retaining ring; 11. Rear cover; 111. Oil suction port; 12. Bolt; 13. O-ring; 14. Bearing seat; 15. Second bearing. DETAILED DESCRIPTION

[0034] For better understanding and implementation, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention.

[0035] In the description of the present invention, it should be noted that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they cannot be understood as limitations on the present invention.

[0036] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art in the art of the present invention. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention.

[0037] Example 1

[0038] See Figure 1-4This embodiment provides an impeller comprising: a cover plate 81, a base plate 82, and a plurality of blades 83. The cover plate 81 is provided with an oil inlet 811. The base plate 82 and the cover plate 81 are spaced apart and arranged correspondingly to form a cylindrical structure. The plurality of blades 83 are connected between the cover plate 81 and the base plate 82. Adjacent blades 83 are spaced apart to form an oil outlet 84. The radial extension line of the projection of the blades 83 on the base plate 82 satisfies the exponential function y = ae. bx The changing law of a is 1.35-1.95, and the value of b is 0.13-0.16.

[0039] The cover plate 81 and base plate 82 are two opposing, matching circular plates. They are positioned so that the cover plate 81, base plate 82, and the area between them form a cylindrical structure, facilitating rotation of the impeller 8 about its axis. Opposite ends of a plurality of blades 83 are connected to the cover plate 81 and base plate 82, respectively. Blades 83 are spaced apart and extend radially from the circumferential edge of the impeller 8 toward its axis, forming a chamber at its center.

[0040] On this basis, the radial extension line of the projection of the blade 83 of the impeller 8 on the bottom plate 82 satisfies the exponential function y=ae bx The change pattern of a is 1.35-1.95, and the value of b is 0.13-0.16, so that the blades 83 extend radially inward in an arc shape from the circumferential edge of the impeller 8, and the spacing between adjacent blades 83 near the circumferential edge of the impeller 8 is greater than the spacing near the axis of the impeller 8, that is, the thickness of the blades 83 gradually decreases from the circumferential edge to the inside. In this way, when the impeller 8 rotates, it drives the blades 83 to rotate synchronously, thereby using centrifugal force to cause the hydraulic oil to be thrown from the center of the impeller 8 to the circumferential edge, so that the hydraulic oil flows out from the oil outlet 84. At the same time, a certain vacuum is formed in the central chamber of the impeller 8 due to the hydraulic oil being thrown out, which facilitates the hydraulic oil to enter the impeller 8 through the oil inlet 811 due to the pressure difference. In this reciprocating manner, the impeller 8 rotates continuously, so that the hydraulic oil is continuously sucked in and discharged, thereby improving the boosting effect and oil delivery efficiency while ensuring the quality of the hydraulic oil.

[0041] See Figure 3 and Figure 4 The blade 83 includes a first surface 831 and a second surface 832 spaced circumferentially. The first surface 831 and the second surface 832 both extend radially, and the projections of the first surface 831 and the second surface 832 on the bottom plate 82 both satisfy the exponential function y=ae bxThe changing rule of a is 1.35-1.95, and the value of b is 0.13-0.16. In this way, the first surface 831 and the second surface 832 are spaced apart and both extend radially inward in an arc shape from the circumferential edge of the impeller 8, and according to the changing rule of the exponential function curve, the spacing between the first surface 831 and the second surface 832 gradually decreases from the axial edge inward, that is, the thickness of the blade 83 gradually decreases from the circumferential edge inward, which is conducive to the formation of a vortex in the central chamber of the impeller 8 when several blades 83 rotate, which is convenient for using centrifugal force to discharge the hydraulic oil, and can also form a certain vacuum in the central chamber of the impeller 8 when discharging the hydraulic oil, so as to use the pressure difference to suck in the hydraulic oil. In this way, the impeller 8 can continuously inhale and discharge hydraulic oil, achieving the purpose of efficient pressurization and oil transportation.

[0042] The distance between corresponding positions on the first surface 831 and the second surface 832 is the thickness d of the blades 83. The diameter of the circular structure formed by the blades 83 is the diameter D of the impeller 8. The ratio D / d is 5-10:1. Preferably, the ratio D / d is 7:1. This ensures smooth intake and discharge of hydraulic oil while maintaining the centrifugal force and pressure differential generated by the rotation of the blades 83, thereby increasing the effective output flow of the hydraulic oil and achieving efficient oil delivery.

[0043] The number of blades 83 is 6-9, and the blades 83 are evenly spaced around the circumference. In this way, the blades 83 are arranged in the impeller 8, and the spacing between adjacent blades 83 can effectively balance the centrifugal force, pressure difference, and oil discharge, thereby achieving efficient pressure boosting and efficient oil delivery.

[0044] Furthermore, the ends of the first surface 831 and the second surface 832 near the axis of the impeller 8 are connected by a transition surface 833, which is a circular arc surface. The circular arc surface 833 prevents the hydraulic oil from being sheared at high speed when the blades 83 rotate at high speed, thereby preventing the hydraulic oil from being "stretched" and deteriorating, thereby ensuring the effective output flow of the hydraulic oil and improving oil delivery efficiency.

[0045] In addition, see Figure 1-3 The axis of the base plate 82 of the impeller 8 projects axially outward away from the cover plate 81 to form a connecting portion 85, which is used for transmission connection with the pump shaft. Specifically, the connecting portion 85 is sleeved on the pump shaft, and the connecting portion 85 and the pump shaft are respectively provided with a matching spline structure 851. The spline structure 851 realizes transmission between the pump shaft and the impeller 8. When the motor drives the pump shaft to rotate, the impeller 8 is driven to rotate synchronously, thereby achieving the suction and discharge of hydraulic oil.

[0046] Cover plate 81 axially protrudes outward away from base plate 82 to form boss 86, which is located radially outward of oil inlet 811. Boss 86 serves as a flow guide, facilitating flow of hydraulic oil along boss 86 through oil inlet 811 into the central chamber of impeller 8, thereby improving the smoothness of hydraulic oil intake.

[0047] Example 2

[0048] See Figure 5-8 This embodiment provides a centrifugal booster pump, including: a pump body 1, a main shaft 2, a rear cover 11 and the impeller 8 of Example 1. The rear cover 11 is fixed to the axial rear end of the pump body 1 to form an axially through structure. The rear cover 11 is provided with an oil suction port 111, a vortex chamber 101 is provided in the pump body 1, and an oil discharge port 102 is provided in the pump body 1 corresponding to the vortex chamber 101. The impeller 8 is arranged in the vortex chamber 101, the main shaft 2 is axially arranged in the pump body 1, and the main shaft 2 is transmission-connected to the impeller 8.

[0049] Vortex chamber 101 is located within pump body 1 and communicates with oil discharge port 102, with the center of vortex chamber 101 coinciding with the axis of pump body 1. Vortex chamber 101 is a volute-shaped structure, with the flow channel within vortex chamber 101 gradually increasing in area as it approaches oil discharge port 102. This reduces the velocity of the high-speed hydraulic oil ejected by impeller 8, converting some of its kinetic energy into static pressure energy before it is discharged through oil discharge port 102. Impeller 8 is located within vortex chamber 101, and main shaft 2 axially extends through impeller 8 for a driving connection therewith.

[0050] In this way, the rotation of the main shaft 2 drives the impeller 8 and the blades 83 to rotate synchronously, causing the centrifugal booster pump to absorb oil. The hydraulic oil enters the central chamber of the impeller 8 through the oil suction port 111 and the oil inlet 811 in turn, so that the centrifugal force can be used to cause the hydraulic oil to be thrown from the center of the impeller 8 to the circumferential edge, so that the hydraulic oil flows out from the oil outlet 84 into the vortex chamber 101, and flows out through the oil discharge port 102 at a higher pressure for the hydraulic pump to absorb oil. At the same time, the central chamber of the impeller 8 forms a certain vacuum due to the hydraulic oil being thrown out, so that the hydraulic oil can enter the impeller 8 through the oil suction port 111 and the oil inlet 811 in turn due to the pressure difference. In this way, the impeller 8 rotates continuously, so that the hydraulic oil is continuously sucked in and discharged, thereby improving the boosting effect and oil delivery efficiency of the centrifugal booster pump while ensuring the quality of the hydraulic oil, so as to meet the oil suction requirements of the hydraulic pump, and has the characteristics of simple structure and low cost.

[0051] The axis of the base plate 82 of the impeller 8 projects outwardly from the cover plate 81 to form a connecting portion 85. The main shaft 2 passes through the connecting portion 85, and the connecting portion 85 and the main shaft 2 are connected by a matching spline structure 851. The connecting portion 85 is sleeved on the main shaft 2, and the connecting portion 85 and the main shaft 2 are respectively provided with matching spline structures 851. The spline structure 851 realizes the transmission connection between the main shaft 2 and the impeller 8. When the motor drives the main shaft 2 to rotate, the impeller 8 is driven to rotate synchronously, thereby realizing the suction and discharge of hydraulic oil.

[0052] The cover plate 81 protrudes axially outward away from the base plate 82 to form a boss 86, which is arranged on the radial outer periphery of the oil inlet 811, and a second oil seal 9 is provided between the outer periphery of the boss 86 and the inner wall of the pump body 1, and a first oil seal 5 is provided between the side wall of the main shaft 2 and the inner wall of the front end of the pump body 1.

[0053] Boss 86 serves as a flow guide, facilitating the flow of hydraulic oil along boss 86 through oil inlet 811 into the central chamber of impeller 8, thereby improving the smoothness of hydraulic oil intake. The first oil seal 5 prevents hydraulic oil from leaking from the front end of main shaft 2 along the connection between main shaft 2 and connecting portion 85. The second oil seal 9 prevents hydraulic oil from flowing back into oil intake port 111 after being ejected from impeller 8. Thus, the first and second oil seals 5, 9 work together to prevent hydraulic oil from leaking forward and backward, ensuring that the hydraulic oil is discharged along the designated route through oil discharge port 102 to the hydraulic pump, thereby improving the solvent efficiency of the centrifugal booster pump.

[0054] Furthermore, a first retaining ring 4 is provided between the front end of the first oil seal 5 and the pump body 1, a third retaining ring 10 is provided between the rear end of the second oil seal 9 and the pump body 1, and a second retaining ring 7 is provided at the end where the impeller 8 is transmission-connected to the main shaft 2.

[0055] The first retaining ring 4 is used to axially secure the first oil seal 5, thereby ensuring the sealing performance of the first oil seal 5. The third retaining ring 10 is used to axially secure the second oil seal 9, thereby ensuring the sealing performance of the second oil seal 9. The second retaining rings 7 are provided at both ends of the connecting portion 85, thereby ensuring the reliability of the transmission connection between the main shaft 2 and the connecting portion 85 while further preventing hydraulic oil from leaking toward the front end of the main shaft 2.

[0056] The main shaft 2 passes through the impeller 8. A first bearing 6 is provided through an interference fit at the front end of the main shaft 2. A second bearing 15 supported by a bearing seat 14 is provided through an interference fit at the rear end of the main shaft 2. An oil suction port 111 communicates with the impeller 8 through the bearing seat 14. The combination of the main shaft 2, the first bearing 6, and the second bearing 15 facilitates smooth rotation of the main shaft 2, thereby improving the rotational efficiency of the impeller 8 and enabling efficient oil delivery.

[0057] The front end of the main shaft 2 is connected to the output shaft of the motor, and the main shaft 2 and the output shaft of the motor are connected by a flat key 3. The motor is used to drive the main shaft 2 to rotate. The provision of flat key 3 helps to improve the reliability of the rotational connection between the motor and the main shaft 2, thereby increasing the service life of the centrifugal booster pump.

[0058] In addition, an O-ring 13 is provided between the rear cover 11 and the pump body 1, and the rear cover 11 and the pump body 1 are fixedly connected by bolts 12. The rear cover 11 and the pump body 1 are firmly connected, and the O-ring 13 helps to improve the sealing of the connection between the rear cover 11 and the pump body 1 and prevent oil leakage.

[0059] The technical means disclosed in the present invention are not limited to those disclosed in the above-mentioned embodiments, but also include technical solutions composed of any combination of the above-mentioned technical features. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principles of the present invention, and such improvements and modifications are also considered to be within the scope of protection of the present invention.

Claims

1. An impeller, characterized in that: include: A cover plate, wherein an oil inlet is provided on the cover plate; A bottom plate, the bottom plate and the cover plate are spaced and arranged correspondingly to form a cylindrical structure; a plurality of blades, wherein the plurality of blades are connected between the cover plate and the bottom plate, and adjacent blades are spaced apart to form an oil outlet; The radial extension line of the projection of the blade on the base plate satisfies the exponential function y=ae bx The changing law of a is 1.35-1.95, and the value of b is 0.13-0.

16.

2. The impeller according to claim 1, characterized in that: The blade includes a first surface and a second surface spaced circumferentially, the first surface and the second surface both extend radially, and the projections of the first surface and the second surface on the base plate both satisfy the exponential function y=ae bx The changing law of a is 1.35-1.95, and the value of b is 0.13-0.

16.

3. The impeller according to claim 2, characterized in that: The distance between the corresponding positions of the first surface and the second surface is the thickness d of the blade, the diameter of the circular structure formed by the blades is the diameter D of the impeller, and the ratio of D / d satisfies (5-10):

1.

4. The impeller according to claim 2, characterized in that: The ends of the first surface and the second surface close to the impeller axis are connected by a transition surface, and the transition surface is an arc surface.

5. The impeller according to claim 1, characterized in that: The number of the blades is 6-9, and the blades are circumferentially distributed at equal intervals.

6. A centrifugal booster pump, characterized in that: include: A pump body, a main shaft, a rear cover and an impeller according to any one of claims 1 to 5, wherein the rear cover is fixed to the axial rear end of the pump body to form an axially through structure, the rear cover is provided with an oil suction port, a vortex chamber is provided in the pump body, an oil discharge port is provided in the pump body corresponding to the vortex chamber, the impeller is provided in the vortex chamber, the main shaft is axially provided in the pump body, and the main shaft is transmission-connected to the impeller.

7. The centrifugal booster pump according to claim 6, characterized in that: The axis of the bottom plate of the impeller is axially protruded outward away from the cover plate to form a connecting portion, the main shaft passes through the connecting portion, and the connecting portion and the main shaft are transmission-connected via a matching spline structure.

8. The centrifugal booster pump according to claim 6, characterized in that: The cover plate protrudes axially outward away from the base plate to form a boss, which is arranged at the radial outer periphery of the oil inlet, and a second oil seal is provided between the outer periphery of the boss and the inner wall of the pump body, and a first oil seal is provided between the side wall of the main shaft and the inner wall of the front end of the pump body.

9. The centrifugal booster pump according to claim 8, characterized in that: A first retaining ring is provided between the front end of the first oil seal and the pump body, a third retaining ring is provided between the rear end of the second oil seal and the pump body, and a second retaining ring is provided at the end where the impeller is connected to the main shaft for transmission.

10. The centrifugal booster pump according to claim 6, characterized in that: The main shaft passes through the impeller, the front interference sleeve of the main shaft is provided with a first bearing, the rear interference sleeve of the main shaft is provided with a second bearing supported by a bearing seat, and the oil suction port is connected to the impeller through the bearing seat.

11. The centrifugal booster pump according to claim 6, characterized in that: The front end of the main shaft is used to connect to the output shaft of the motor, and the main shaft and the output shaft of the motor are connected through a flat key transmission.

12. The centrifugal booster pump according to claim 6, characterized in that: An O-ring is provided between the rear cover and the pump body, and the rear cover and the pump body are fixedly connected by bolts.

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