Efficient double-suction pump

Abstract

The efficient double-suction pump comprises a lower pump body, an upper pump body, an impeller arranged between the lower pump body and the upper pump body and sealing devices arranged on the two sides of an impeller suction inlet of the impeller, and each sealing device comprises a movable ring, a static ring and a guide sleeve; the moving ring is mounted on a front cover plate of the impeller; the static ring can move in the axis direction of the guide sleeve, and one end of the static ring makes contact with the movable ring. The end, away from the impeller, of the static ring is a free end, and the end, making contact with the movable ring, of the static ring is a friction end. The radial outer side of the guide sleeve and the corresponding parts of the lower pump body and the upper pump body form a static ring cavity for accommodating the static ring; and the radial inner side of the guide sleeve forms a channel through which a medium flows to the suction inlet of the impeller. According to the efficient double-suction pump, internal leakage of media can be remarkably reduced, the sealing effect is better, the service life of the sealing structure is longer, and maintenance is more convenient.

Description

Technical Field

[0001] The invention belongs to the field of centrifugal pump manufacturing, and in particular relates to a high-efficiency double-suction pump. Background Art

[0002] Centrifugal pumps are the most common fluid conveying equipment. When working, the impeller rotates to suck the medium from the suction port, and the blades work on the medium, thereby accelerating the medium and sending it into the pressure chamber. Double-suction pumps are equivalent to two centrifugal impellers set back to back, so the axial force of the impellers when working is almost completely offset, and the force conditions of the bearings and main shaft are very good, so they are widely used.

[0003] When a centrifugal pump is working, the water pressure in the pressure chamber is higher than the pressure at the suction port, so the medium in the pressure chamber will leak to the suction port through the gap between the impeller and the pump body. This situation is called internal leakage, and internal leakage will cause the working efficiency of the pump to decrease. In order to improve efficiency, many double-suction pumps are designed with sealing rings to reduce internal leakage. Since there is a clearance fit between the sealing ring and the impeller, the size of the clearance will be limited by many aspects such as machining accuracy and mechanical operation accuracy, which also makes internal leakage an important factor limiting the improvement of the working efficiency of centrifugal pumps.

[0004] In order to solve this problem, the invention patent with the authorized patent number CN114738311 B discloses "a leak-free centrifugal pump", the utility model patent with the authorized patent number CN2150371Y discloses "a pump suction ring sealing structure", and the invention patent application with the application publication number CN116696784 A discloses "a ship-used mud and sand pump with an inlet sealing ring". The above three patents / patent applications all disclose that a structure similar to a mechanical seal friction pair is set at the position of the sealing ring of the impeller, and the sealing ring is compressed by elastic parts such as springs, and the medium is blocked from leaking from the high-pressure area of ​​the pressure chamber to the low-pressure area at the suction port through the friction pair. The above structure can theoretically solve the internal leakage problem of the vane pump, but in the actual operation process, the size of the spring force is difficult to control, and the life of the friction pair is greatly affected by the spring force. When the spring force is large, the life of the friction pair will be greatly shortened; when the spring force is small, the medium pressure is enough to push open the friction pair, which will cause the sealing effect to fail to meet expectations. Secondly, the spring force changes continuously with the continuous wear of the friction pair, which results in a significant change in friction force and sealing effect when the friction pair is worn to a certain extent, which easily leads to seal failure due to wear. At the same time, due to the short life of the friction pair, the friction pair needs to be replaced regularly for maintenance. The above scheme has a complex structure and requires the pump body to be disassembled before replacement and maintenance, which is extremely inconvenient. Therefore, the above technical scheme has not been promoted in industrial applications because the above problems are difficult to solve. Summary of the invention

[0005] In order to overcome the deficiencies in the prior art, the present invention provides a high-efficiency double-suction pump, which can significantly reduce internal leakage of the medium, has a better sealing effect, a longer service life of the sealing structure, and is more convenient to maintain.

[0006] The technical solution of the present invention to solve the above technical problems is:

[0007] A high-efficiency double-suction pump comprises a lower pump body, an upper pump body, an impeller arranged between the lower pump body and the upper pump body, and a sealing device arranged on both sides of the impeller suction port of the impeller, wherein the sealing device comprises a dynamic ring, a static ring and a guide sleeve; the dynamic ring is mounted on the front cover plate of the impeller; the static ring can move along the axial direction of the guide sleeve and make one end of it contact with the dynamic ring; the end of the static ring away from the impeller is a free end, and the end of the static ring in contact with the dynamic ring is a friction end; the radial outer side of the guide sleeve and the corresponding parts of the lower pump body and the upper pump body constitute a static ring cavity for accommodating the static ring; the radial inner side of the guide sleeve constitutes a channel for the medium to flow to the impeller suction port.

[0008] More preferably, the guide sleeve is provided with a radially protruding positioning flange on a side away from the impeller, and both the lower pump body and the upper pump body are provided with positioning stops for cooperating with the positioning flange.

[0009] More preferably, the guide sleeve extends outward from the impeller suction port to the spiral water suction chamber.

[0010] More preferably, the upper pump body and the lower pump body are provided with axial protrusions on the axial outside of the positioning flange of the guide sleeve.

[0011] More preferably, the fitting clearance between the guide sleeve and the stationary ring is smaller than the fitting clearance between the stationary ring and the lower pump body and the fitting clearance between the stationary ring and the upper pump body.

[0012] More preferably, a channel or a pipe is connected to the lower pump body or the upper pump body, one end of the channel or the pipe is connected to the high-pressure area of ​​the water pressure chamber or the pump outlet, and the other end is connected to the static ring cavity; the water outlet of the channel or the pipe connected to the static ring cavity is arranged at an end of the static ring cavity away from the impeller.

[0013] More preferably, a seal is provided between the guide sleeve and the static ring.

[0014] More preferably, the stationary ring is provided with a water hole extending along its axial direction, and the water hole penetrates the friction end of the stationary ring from the free end of the stationary ring; a water groove connected to the water hole is provided at the friction end of the stationary ring, and the water groove is annular.

[0015] More preferably, the sealing device also includes an anti-rotation structure for preventing relative rotation between the guide sleeve and the stationary ring; the anti-rotation structure includes a pin arranged on the guide sleeve; the axial direction of the pin is parallel to the axial direction of the stationary ring cavity; and a keyway cooperating with the pin is arranged on the stationary ring.

[0016] More preferably, the sealing device further comprises an elastic member for driving the stationary ring to move toward the dynamic ring, one end of the elastic member acts on the stationary ring, and the other end acts on the guide sleeve.

[0017] More preferably, the axial thickness of the stationary ring is 2-8 times the axial thickness of the dynamic ring, and the hardness of the stationary ring is less than the hardness of the dynamic ring.

[0018] More preferably, the high-pressure medium injected into the static ring cavity can push the static ring to move in the direction of the dynamic ring, and make the friction end of the static ring contact with the dynamic ring.

[0019] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0020] The high-efficiency double-suction pump of the present invention can utilize the limited axial space at its suction port so that the stationary ring can have a larger length; the guide sleeve can be used to ensure that the friction surface of the stationary ring and the friction surface of the dynamic ring have higher coaxiality and parallelism, which is beneficial to reducing the leakage and wear of the friction pair composed of the stationary ring and the dynamic ring; at the same time, when the stationary ring is worn, the stationary ring can move along the axial direction of the guide sleeve to compensate for the wear; in addition, the longer stationary ring length is not only beneficial to extending the service life of the stationary ring, but also to extending the maintenance cycle; the radial inner side of the guide sleeve constitutes a channel for the medium to flow to the impeller suction port, so that the diameter of the stationary ring can be reduced as much as possible while meeting the cavitation performance, thereby reducing the linear speed of the friction pair and reducing its wear. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a cross-sectional view of a first specific embodiment of the high-efficiency double-suction pump of the present invention.

[0022] Figure 2 for Figure 1 Partial cross-sectional view at point A.

[0023] Figure 3 It is a cross-sectional view of a second specific embodiment of the high-efficiency double-suction pump of the present invention.

[0024] Figure 4 for Figure 3 Partial view at B.

[0025] Figure 5 It is a three-dimensional cross-sectional view of the static ring.

[0026] Figure 6 It is a cross-sectional view of a third specific embodiment of the high-efficiency double-suction pump of the present invention.

[0027] Figure 7 for Figure 6 Partial view at point C in the middle.

[0028] Figure 8 It is a cross-sectional view of a fourth specific embodiment of the high-efficiency double-suction pump of the present invention.

[0029] Fig. 9 for Figure 8 Partial view at point D in the middle.

[0030] Fig.10 It is a cross-sectional view of a fifth specific embodiment of the high-efficiency double-suction pump of the present invention.

[0031] Fig.11 for Fig.10 Partial view at E.

[0032] In the figure: 1-upper pump body, 2-lower pump body, 3-impeller, 4-high-pressure water pipe, 5-guide sleeve, 501-positioning flange, 6-static ring cavity, 7-static ring, 701 water hole, 702-water tank, 8-moving ring, 9-pin, 10-water inlet, 11-spring, 12-dark water channel, 13-axial protrusion, 14, sealing ring. DETAILED DESCRIPTION

[0033] The present invention is further described in detail below in conjunction with embodiments and drawings, but the embodiments of the present invention are not limited thereto.

[0034] Example 1

[0035] like Figure 1-Figure 2 As shown, the high-efficiency double-suction pump of the present invention comprises a lower pump body 2, an upper pump body 1, an impeller 3 and a sealing device arranged on both sides of the impeller suction port of the impeller 3, wherein the sealing device comprises a dynamic ring 8, a static ring 7 and a guide sleeve 5; the dynamic ring 8 is mounted on the front cover plate of the impeller 3; the static ring 7 can move along the axial direction of the guide sleeve 5 and make one end of it contact with the dynamic ring 8; the end of the static ring 7 away from the impeller 3 is a free end, and the end that can contact with the dynamic ring 8 is a friction end; the radial outer side of the guide sleeve 5 and the corresponding parts of the lower pump body 2 and the upper pump body 1 constitute a static ring cavity 6 for accommodating the static ring 7; the radial inner side of the guide sleeve 5 is a channel for the medium to flow to the impeller suction port.

[0036] like Figure 1-Figure 2As shown, the guide sleeve 5 is provided with a radially protruding positioning flange 501 on the side away from the impeller 3; the lower pump body 2 and the upper pump body 1 are provided with positioning stoppers that match the positioning flange 501; by setting the positioning flange 5 and the positioning stoppers, the coaxiality between the guide sleeve 5 and the upper pump body 1 and the lower pump body 2 can be ensured, and since the axial dimension of the positioning flange 501 can be designed to be smaller, the static ring 7 can obtain a longer axial length.

[0037] like Figure 1-Figure 2 As shown, the guide sleeve 5 extends outward from the impeller suction port of the impeller 3 to the spiral water suction chamber, and the upper pump body 1 and the lower pump body 2 are provided with axial protrusions 13 on the axial outside of the positioning flange 501 of the guide sleeve 5; in this way, the guide sleeve 5 can be made as long as possible in the axial direction without affecting the cavitation performance of the pump or having a small impact on the cavitation performance, so that the stationary ring 7 has a longer axial length, so as to promote the coaxiality and parallelism of the stationary ring 7 relative to the dynamic ring 8 to be higher, thereby promoting less leakage of the friction pair, and further extending the service life of the stationary ring 7.

[0038] Since the pressure difference between the static ring cavity 6 and the medium outside the friction pair is small, the high-pressure medium entering the static ring cavity 6 flows to the radial outside of the friction pair, which has almost no effect on the working efficiency of the pump; while there is a higher pressure difference between the static ring cavity 6 and the radial inside of the friction pair, and the leakage has a great influence on the working efficiency of the pump, so the fitting clearance between the guide sleeve 5 and the static ring 7 needs to be designed to be smaller, 0.2-0.3mm, to minimize the leakage between the two; and the fitting clearance between the static ring 7 and the lower pump body 2 and the upper pump body 1 is 3-4mm, which is significantly larger than the former, so that the manufacturing cost can be reduced, thereby reducing the probability of the static ring 7 being stuck.

[0039] like Figure 1-Figure 2 As shown, a high-pressure water pipe 4 is connected to the upper pump body 1, one end of the high-pressure water pipe 4 is connected to the high-pressure area of ​​the water pressure chamber, and the other end is connected to the static ring cavity 6; wherein, a water inlet 10 of the pipe connected to the static ring cavity 6 is arranged in the static ring cavity 6 at one end away from the impeller 3, so that the static ring 7 can have a longer axial length and obtain a longer service life.

[0040] In this embodiment, the material of the stationary ring 7 is HDPE, and its axial thickness is 42 mm; the material of the dynamic ring 8 is tungsten carbide alloy, and its axial thickness is 8 mm; therefore, the former is 5.2 times that of the latter; since the hardness of the former is much smaller than that of the latter, the dynamic ring 8 can obtain a very long service life, and its service life can be close to the service life of the impeller 3; although the stationary ring 7 has a lower hardness, due to its longer axial length, the stationary ring 7 and the guide sleeve 5 can be replaced when only the upper pump body 1 is disassembled, which reduces the maintenance workload and reduces the maintenance cost.

[0041] In general, the axial thickness of the stationary ring 7 is preferably 2-8 times the axial thickness of the dynamic ring 8; if the axial thickness of the stationary ring 7 is too large, the cavitation performance of the pump will be reduced; otherwise, the service life of the stationary ring 7 will be short and the maintenance frequency will be high.

[0042] like Figure 1-Figure 2 As shown, the working principle of the high-efficiency double-suction pump of this embodiment is:

[0043] When the high-efficiency double-suction pump of the present embodiment is in operation, a high-pressure zone is formed in the pressure water chamber, and the high-pressure water in the high-pressure zone of the pressure water chamber of the upper pump body 1 enters the static ring cavity 6 through the high-pressure water pipe 4 and the water inlet 10, and acts on the free end of the static ring 7, thereby pushing the static ring 7 to move toward the conveying dynamic ring 8 along the axial direction of the guide sleeve 5; after the static ring 7 and the dynamic ring 8 are in contact, the channel for the medium to leak from the high-pressure zone to the low-pressure zone at the suction port can be blocked, thereby achieving sealing; in this process, since the outer pressure of the contact surface between the static ring 7 and the dynamic ring 8 is high and the inner pressure is low, and relative rotational motion occurs between the static ring 7 and the dynamic ring 8, the medium will leak from the outer side to the inner side of the contact surface between the static ring 7 and the dynamic ring 8, thereby cooling and lubricating the friction surface between the static ring 7 and the dynamic ring 8, thereby making the high-efficiency double-suction pump of the present embodiment have higher efficiency, and at the same time, the static ring 7 and the dynamic ring 8 also have a longer service life.

[0044] Example 2

[0045] This embodiment is substantially the same as Embodiment 1, and the main differences are as follows:

[0046] like Figure 3-Figure 4As shown, the stationary ring 7 is provided with 20 water holes 701 for connecting the friction end and the free end of the stationary ring 7, and the water holes 701 extend along the axial direction of the stationary ring 7; the friction end of the stationary ring 7 is provided with a water trough 702 connected with the water holes 701; by providing a plurality of water holes 701 connecting the friction end and the free end of the stationary ring 7 on the stationary ring 7, high-pressure medium can be injected into the friction surface between the moving ring 8 and the stationary ring 7 through the water holes 701, thereby forming a structure similar to a hydrostatic thrust bearing, which greatly improves the lubrication condition at the friction surface, and further improves the life of the friction pair.

[0047] like Figure 3-Figure 4 As shown, a water tank 702 connected to the water hole 701 is provided on the friction end of the stationary ring 7. The water tank 702 can further improve the lubrication condition of the friction pair, thereby increasing the service life of the friction pair.

[0048] In this embodiment, the material of the stationary ring 7 is tin bronze.

[0049] like Figure 3-Figure 4 As shown, the working principle of the high-efficiency double-suction pump of this embodiment is:

[0050] When the high-efficiency double-suction pump of this embodiment is working, the high-pressure medium from the high-pressure area of ​​the pressure water chamber enters the static ring cavity 6 through the high-pressure water pipe 4 and the water inlet 10, and enters the water tank 702 through the water hole 701 in the static ring 7. Since the water pressure at the static ring cavity 6 is higher than the water pressure at the friction pair, the water pressure will push the static ring 7 and the dynamic ring 8 to contact to achieve sealing; when the friction end of the static ring 7 and the dynamic ring 8 are in contact, the water pressure at the water tank 702 increases, and reversely pushes the static ring 7 away from the dynamic ring 8, so that the high-pressure medium leaks to the suction port, which in turn causes the water pressure at the water tank 702 to decrease, so that the water pressure at the static ring cavity 6 is higher than the water pressure at the friction pair, and this pressure will again push the static ring 7 and the dynamic ring 8 to contact to achieve sealing; this is equivalent to causing the static ring 7 to dynamically float under the action of the water pressure at its two ends, so that the leakage of the friction pair can be kept appropriate while meeting the cooling and lubrication requirements of the friction pair.

[0051] Example 3

[0052] This embodiment is substantially the same as Embodiment 2, and the main differences are:

[0053] like Figure 6 and Figure 7As shown, an anti-rotation structure for preventing relative rotation between the guide sleeve 5 and the stationary ring 7 is provided between the guide sleeve 5 and the stationary ring 7; the anti-rotation structure includes a pin 9 provided on the guide sleeve 5; the axial direction of the pin 9 is parallel to the axial direction of the stationary ring cavity 6; and a keyway for cooperating with the pin 9 is provided on the stationary ring 7. By providing the anti-rotation structure, the stationary ring 7 can be prevented from rotating around the axial direction of the impeller 3 to wear the stationary ring 7 and the guide sleeve 5.

[0054] like Figure 6 and Figure 7 As shown, a sealing ring 14 is provided between the guide sleeve 5 and the stationary ring 7, and the sealing ring 14 is installed on the guide sleeve 5; through the above arrangement, the flow rate of the high-pressure medium leaking from the fitting gap between the guide sleeve 5 and the stationary ring 7 to the suction port can be reduced, thereby improving the working efficiency of the double-suction pump of this embodiment; in addition, since the sealing ring 14 has resistance to the axial movement of the stationary ring 7, the sealing ring 14 is equivalent to a damping mechanism, which can reduce the vibration amplitude of the stationary ring 7, thereby reducing the leakage amount, thereby extending the life of the friction pair.

[0055] Example 4

[0056] This embodiment is substantially the same as Embodiment 2, and the main differences are:

[0057] like Figure 8 and Fig. 9 As shown, the impeller 3 is made of wear-resistant alloy, and the dynamic ring 8 and the impeller 3 are made of the same material and are manufactured in one piece, which can reduce the manufacturing cost; at this time, the axial thickness of the dynamic ring 8 is the thickness of the front cover plate of the impeller 3 corresponding to the static ring 7.

[0058] In this embodiment, the axial thickness of the stationary ring 7 is 98 mm, and the axial thickness of the dynamic ring 8 is 46 mm, and the former is 2.13 times the latter.

[0059] In addition, an elastic member is provided between the free end face of the stationary ring 7 and the guide sleeve 5, and the elastic force of the elastic member causes the friction end face of the stationary ring 7 to press against the dynamic ring 8, wherein the elastic member is a spring 11. By providing the spring 11, the following effects can be achieved:

[0060] When the high-pressure medium is injected into the friction end of the stationary ring 7 through the water hole 701 on the stationary ring 7, the water pressure at the friction end of the stationary ring 7 is in a fluctuating state. When the high-pressure medium pushes the stationary ring 7 to move axially in the direction of the moving ring 8, the water hole 701 or the water groove 702 at the friction end of the stationary ring 7 will be blocked, and the pressure of the high-pressure medium at the friction end of the stationary ring 7 will naturally rise, thereby preventing the stationary ring 7 from moving in the direction of the moving ring 8. The forces in the two directions will reach equilibrium at a certain position, but because both the stationary ring 7 and the high-pressure medium have inertia, the stationary ring 7 cannot be stably at the equilibrium point, but vibrates near the equilibrium point. If the vibration amplitude is large, it may accelerate the wear of the friction pair, thereby increasing the consumption of the high-pressure medium; therefore, a number of elastic parts are arranged on the free end side of the stationary ring 7, which is equivalent to adding a damping mechanism, thereby reducing the vibration amplitude of the stationary ring 7, thereby increasing the life of the friction pair, thereby reducing the consumption of the high-pressure medium.

[0061] In addition, in this embodiment, a sealing ring 14 is provided between the stationary ring 7 and the stationary ring cavity 6 or between the stationary ring 7 and the guide sleeve 5, which can also achieve a similar effect.

[0062] Different from the prior art, the friction pair in this embodiment does not rely entirely on spring force to achieve friction pair sealing, so the linearity of the spring force can be different from that of the prior art design, so that the sealing force of the friction pair will not change significantly due to the friction of the friction pair.

[0063] Example 5

[0064] This embodiment is substantially the same as Embodiment 1, and the main differences are as follows:

[0065] like Fig.10 and Fig.11 As shown, the high-efficiency double-suction pump of this embodiment is not provided with an external high-pressure water pipe, but is provided with a dark water channel 12 connecting the high-pressure area of ​​the water pressure chamber and the static ring cavity 6; when the high-efficiency double-suction pump of this embodiment is working, the high-pressure water in the high-pressure area of ​​the water pressure chamber enters the static ring cavity 6 through the dark water channel 12, and since the water pressure at the free end of the static ring 7 is higher than the water pressure at the friction end, the static ring 7 moves toward the direction of the impeller 3 under the action of the water pressure, so that its friction end contacts the dynamic ring 8 on the impeller 3, and sealing is achieved.

[0066] Finally, in the above five embodiments, the high-pressure medium / medium in the water inlet, high-pressure water pipe 4, water hole 701, dark water channel 12, water tank 702 and other components can be water, oil, alcohol and other liquid media.

[0067] The above is a preferred embodiment of the present invention, but the embodiment of the present invention is not limited to the above content. Any other changes, modifications, substitutions, combinations, and simplifications that do not deviate from the spirit and principles of the present invention should be equivalent replacement methods and are included in the protection scope of the present invention.

Claims

1. A high-efficiency double-suction pump, characterized in that: It comprises a lower pump body, an upper pump body, an impeller arranged between the lower pump body and the upper pump body, and a sealing device arranged on both sides of the impeller suction port of the impeller, wherein the sealing device comprises a dynamic ring, a static ring and a guide sleeve; the dynamic ring is mounted on the front cover plate of the impeller; the static ring can move along the axial direction of the guide sleeve and make one end of it contact with the dynamic ring; the end of the static ring away from the impeller is a free end, and the end of the static ring in contact with the dynamic ring is a friction end; the radial outer side of the guide sleeve and the corresponding parts of the lower pump body and the upper pump body constitute a static ring cavity for accommodating the static ring; the radial inner side of the guide sleeve constitutes a channel for the medium to flow to the impeller suction port.

2. The high-efficiency double-suction pump according to claim 1, characterized in that: The guide sleeve is provided with a radially protruding positioning flange on a side away from the impeller, and the lower pump body and the upper pump body are both provided with positioning stops for matching with the positioning flange.

3. The high-efficiency double-suction pump according to claim 2, characterized in that: The upper pump body and the lower pump body are provided with axial protrusions on the axial outer side of the positioning flange of the guide sleeve.

4. The high-efficiency double-suction pump according to claim 1, characterized in that: The guide sleeve extends outward from the impeller suction port to the spiral water suction chamber.

5. The high-efficiency double-suction pump according to claim 1, characterized in that: The fitting clearance between the guide sleeve and the stationary ring is smaller than the fitting clearance between the stationary ring and the lower pump body and the fitting clearance between the stationary ring and the upper pump body.

6. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: A channel or a pipe is connected to the lower pump body or the upper pump body, one end of the channel or the pipe is connected to the high-pressure area of ​​the water pressure chamber or the pump outlet, and the other end is connected to the static ring cavity; the water outlet of the channel or the pipe connected to the static ring cavity is arranged at one end of the static ring cavity away from the impeller.

7. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: A sealing member is arranged between the guide sleeve and the static ring.

8. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: The sealing device also includes an anti-rotation structure for preventing relative rotation between the guide sleeve and the stationary ring; the anti-rotation structure includes a pin arranged on the guide sleeve; the axial direction of the pin is parallel to the axial direction of the stationary ring cavity; and a keyway cooperating with the pin is arranged on the stationary ring.

9. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: The sealing device further comprises an elastic member for driving the stationary ring to move toward the dynamic ring, one end of the elastic member acts on the stationary ring, and the other end of the elastic member acts on the guide sleeve.

10. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: The axial thickness of the stationary ring is 2-8 times the axial thickness of the dynamic ring, and the hardness of the stationary ring is less than that of the dynamic ring.

11. The high-efficiency double-suction pump according to any one of claims 1 to 3, characterized in that: The high-pressure medium injected into the static ring cavity can push the static ring to move in the direction of the dynamic ring, and make the friction end of the static ring contact with the dynamic ring.

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