Efficient vane pump and application thereof

Abstract

The invention discloses an efficient vane pump and application thereof, and the efficient vane pump comprises a pump body, an impeller and a sealing device arranged between the pump body and the impeller; the sealing device comprises a movable ring, a static ring and a guide sleeve, the guide sleeve is installed on the pump body, and a static ring cavity used for containing the static ring is formed between the radial outer side of the guide sleeve and the pump body; the static ring is arranged in the static ring cavity and can move in the axis direction of the static ring cavity, 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 moving ring is installed on a front cover plate of the impeller or on the suction inlet side of the impeller. According to the efficient vane 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 vane pump manufacturing, and in particular relates to a high-efficiency vane pump and application thereof. Background Art

[0002] Vane pumps include centrifugal pumps, diagonal flow pumps and axial flow pumps. They are the most common fluid conveying equipment. When the vane pump is 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 of the pump body, converting the kinetic energy obtained by the machine into the potential energy of the medium. The structure of the turbine is almost exactly the same as that of the vane pump. The only difference is the usage scenario, that is, it is used to convert the potential energy of the medium into kinetic energy to drive other mechanical equipment. In some usage scenarios, such as pumped storage power stations, the same hydraulic machinery is used as a turbine when generating electricity and as a vane pump when pumping water. When the vane pump is working, since the pressure in the pressure chamber is higher than the pressure at the suction port, 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 vane pump to decrease. In order to improve efficiency, many existing vane pumps are designed with sealing rings to reduce internal leakage. Since there is a clearance fit between the sealing ring and the pump body, the size of the clearance is limited by many factors such as machining accuracy and mechanical operation accuracy, which also causes internal leakage to become an important factor limiting efficiency improvement.

[0003] 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 device", 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. This 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 very 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

[0004] In order to overcome the deficiencies in the prior art, the present invention provides a high-efficiency vane 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.

[0005] The second object of the present invention is to provide an application of a high-efficiency vane pump in the field of hydropower generation.

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

[0007] A high-efficiency vane pump comprises a pump body, an impeller and a sealing device arranged between the pump body and the impeller, wherein the sealing device comprises a dynamic ring, a static ring and a guide sleeve; the dynamic ring is installed on the front cover plate of the impeller or on the suction port side of the blade; 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 in contact with the dynamic ring is a friction end; the radial outer side of the guide sleeve and the corresponding part of the pump body constitute a static ring cavity for accommodating the static ring; the medium flows to the impeller suction port through the radial inner side of the guide sleeve; the axial thickness of the guide sleeve is greater than the axial thickness of the static ring.

[0008] Preferably, the guide sleeve can be installed in the pump body along the suction direction of the impeller, and the stationary ring can be installed in the pump body along the suction direction of the impeller.

[0009] Preferably, a positioning flange is provided on the guide sleeve; the positioning flange is arranged at the end thereof away from the impeller; the guide sleeve extends from the outer end of the suction port of the pump body to the suction port of the impeller; the pump body is provided with a positioning stop at a position corresponding to the positioning flange; the positioning stop is coaxially arranged with the pump body, and the positioning stop is arranged at the end of the pump body away from the impeller.

[0010] Preferably, there is a first fitting gap between the guide sleeve and the stationary ring, and there is a second fitting gap between the stationary ring and the pump body; and the size of the first fitting gap is smaller than the size of the second fitting gap.

[0011] Preferably, the pump body is provided with a channel or connected with a pipe, one end of the pipe or channel is connected to the high-pressure area of ​​the water pressure chamber or the outlet pipe of the pump body, and the other end is connected to the static ring cavity; the high-pressure water in the static ring cavity can push the static ring to move along the guide sleeve toward the dynamic ring, and make the friction end of the static ring contact with the dynamic ring.

[0012] Preferably, a seal is provided between the guide sleeve and the static ring.

[0013] Preferably, the stationary ring is provided with a plurality of water holes extending from the free end to the friction end, and a water guide groove communicating with the water holes is provided at the friction end, and the water guide groove is annular.

[0014] Preferably, an anti-rotation structure is provided to prevent 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 provided on the stationary ring.

[0015] Preferably, an elastic member is provided to drive 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; when the guide sleeve is removed, the elastic member can be removed from the pump body along the opposite direction of the impeller suction.

[0016] Preferably, the axial thickness of the stationary ring is 2-20 times the axial thickness of the dynamic ring, and the hardness of the former is smaller than that of the latter.

[0017] Preferably, an inlet flange is provided at the outer end of the suction port of the pump body, and the outer end surface of the guide sleeve is flush with the end surface of the inlet flange.

[0018] Preferably, an inlet flange is provided at the outer end of the suction port of the pump body; the static ring cavity is connected to a water inlet, and the water inlet is connected to the high-pressure area of ​​the water pressure chamber or the water outlet pipe; the water inlet is close to the inlet flange, away from the impeller suction port, and perpendicular to the axis of the pump body.

[0019] The invention discloses an application of a high-efficiency vane pump in the field of hydroelectric power generation, wherein the high-efficiency vane pump is used as a water turbine.

[0020] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0021] 1. The stationary ring in the high-efficiency vane pump of the present invention can move along the axial direction of the stationary ring cavity and make one end of it contact with the dynamic ring; so that as long as the processing accuracy is controlled, it can be ensured that there is a high coaxiality between the stationary ring and the dynamic ring, and the friction pair formed by the stationary ring and the dynamic ring has a high degree of fit; when the friction pair is worn, the stationary ring can move along the axial direction of the guide sleeve to compensate for the wear, so that the sealing effect will not be reduced due to wear.

[0022] 2. Since the guide sleeve and the stationary ring in the sealing device of the present invention can be easily set with a longer axial dimension, the stationary ring can have a longer compensation length, thereby enabling the sealing device of the present invention to obtain a longer service life.

[0023] 3. The radial inner side of the guide sleeve in the high-efficiency vane pump of the present invention is a channel for the medium to flow toward the impeller suction port, which enables the guide sleeve to achieve a guiding function while, under the premise of satisfying the cavitation performance, minimizing the radial dimension of the stationary ring, thereby facilitating reducing the friction linear velocity of the stationary ring relative to the dynamic ring, thereby increasing the life of the friction pair. At the same time, the guide sleeve can prevent the stationary ring made of a softer material from being washed by the medium flowing in along the impeller suction direction, and obtain a longer life.

[0024] 4. When the guide sleeve and the static ring can be installed into the pump body along the suction direction of the impeller, the static ring or the guide sleeve can be replaced without dismantling the pump body, thereby greatly reducing the maintenance workload. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 It is a cross-sectional view of a first specific embodiment of a high-efficiency vane pump of the present invention.

[0026] Figure 2 It is a cross-sectional view of the pump body and guide sleeve.

[0027] Figure 3 for Figure 1 Partial view at A.

[0028] Figure 4It is a cross-sectional view of a second specific embodiment of the high-efficiency vane pump of the present invention.

[0029] Figure 5 for Figure 4 Partial view at B.

[0030] Figure 6 It is a three-dimensional cross-sectional view of the static ring.

[0031] Figure 7 It is a cross-sectional view of a third specific embodiment of the high-efficiency vane pump of the present invention.

[0032] Figure 8 for Figure 7 Partial view at point C in the middle.

[0033] Fig. 9 It is a cross-sectional view of a fourth specific embodiment of the high-efficiency vane pump of the present invention.

[0034] Fig.10 for Fig. 9 Partial view at point D in the middle.

[0035] Fig.11 It is a cross-sectional view of a fifth specific embodiment of the high-efficiency vane pump of the present invention.

[0036] Fig.12 for Fig.11 Partial view at point E in the middle.

[0037] Fig.13 It is a cross-sectional view of a sixth specific embodiment of the high-efficiency vane pump of the present invention.

[0038] Fig.14 for Fig.13 Partial view at point F in the middle.

[0039] Fig.15 It is a schematic diagram of the positions of the first fitting clearance, the second fitting clearance and the impeller suction port.

[0040] In the figure: 1-pump body, 101-rear pump body, 102-front pump body, 2-high-pressure water pipe, 3-impeller, 4-static ring cavity, 5-guide sleeve, 501-positioning flange, 6-static ring, 601-water hole, 602-water guide groove, 7-moving ring, 8-spring, 9-pin, 10-blind water channel, 11-inlet flange, 12-water inlet, 13-sealing ring, 14-first fitting gap, 15-second fitting gap, 16-impeller suction port. DETAILED DESCRIPTION

[0041] 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.

[0042] Example 1

[0043] like Figure 1-Figure 3 , Fig.15 As shown, the high-efficiency vane pump of the present invention comprises a pump body 1, an impeller 3 and a sealing device arranged between the pump body 1 and the impeller 3; the sealing device comprises a dynamic ring 7, a static ring 6 and a guide sleeve 5; wherein the guide sleeve 5 is mounted on the pump body 1, and a static ring cavity 4 for accommodating the static ring 6 is formed between the radial outer side of the guide sleeve 5 and the pump body 1; the static ring 6 is arranged in the static ring cavity 4, and can move along the axial direction of the static ring cavity 4 and make one end of it contact with the dynamic ring 7; the end of the static ring 6 away from the impeller 3 is a free end, and the end of the static ring 6 in contact with the dynamic ring 7 is a friction end; the dynamic ring 7 is mounted on the front cover plate of the impeller 3. The axial thickness of the guide sleeve 5 is greater than the axial thickness of the static ring 6.

[0044] In this embodiment, the guide sleeve 5 can be installed in the pump body 1 along the suction direction of the impeller 3, and the static ring 6 can also be installed in the pump body 1 along the suction direction of the impeller 3, that is, the guide sleeve 5 and the static ring 6 can be installed from Figure 1 The left side of the impeller 3 is installed into the pump body 1 to the right along the suction direction of the impeller 3, and can certainly be removed in the opposite direction. In this way, the easily damaged static ring 6 and guide sleeve 5 can be replaced without removing the pump body 1, thereby greatly reducing the maintenance workload.

[0045] like Figure 1-Figure 3 , Fig.15 As shown, a positioning flange 501 is provided on the guide sleeve 5, and the positioning flange 501 is arranged at the end away from the impeller 3; the guide sleeve 5 extends from the outer end of the suction port of the pump body 1 to the impeller suction port 16, so that the longest axial length of the guide sleeve 5 can be obtained without increasing the axial size of the pump body 1, thereby increasing the axial length of the static ring cavity 4 and the static ring 6 to extend the life of the static ring 6; the pump body 1 is provided with a positioning stop at a position corresponding to the positioning flange 501; the positioning stop is arranged at one end of the pump body 1 away from the impeller 3, and is coaxially arranged with the pump body 1.

[0046] like Figure 1-Figure 3 , Fig.15 As shown, there is a first fitting gap 14 between the guide sleeve 5 and the stationary ring 6 , and a second fitting gap 15 between the stationary ring 6 and the pump body 1 ; the size of the first fitting gap 14 is smaller than the size of the second fitting gap 15 .

[0047] In this embodiment, the first fitting gap 14 is 0.6 mm, and the second fitting gap 15 is 2 mm. The former is smaller than the latter. This design can reduce the leakage of the former and reduce the processing accuracy and processing cost of the latter.

[0048] In this embodiment, the material of the impeller 3 is carbon steel; the material of the stationary ring 6 is HDPE, and the axial thickness is 44mm; the material of the dynamic ring 7 is tungsten carbide alloy, and the axial thickness is 11mm; the axial thickness of the stationary ring 6 is 4 times the axial thickness of the dynamic ring 7, and the hardness of the stationary ring 6 is less than the hardness of the dynamic ring 7, so the wear rate of the dynamic ring 7 is much smaller, and its service life can also reach and be close to that of the impeller 3, so it does not need to be replaced separately. Although the hardness of the stationary ring 6 is lower and the cost is also lower, the wear resistance of the stationary ring 6 is better, and because the axial thickness of the stationary ring 6 is larger, the service life of the stationary ring 6 can still be greatly improved compared with the prior art.

[0049] like Figure 1-Figure 3 , Fig.15 As shown, an inlet flange 11 is provided on the end portion of the outer side of the suction port of the pump body 1, and the outer end face of the guide sleeve 5 is flush with the end face of the inlet flange 11, so that the positioning flange 501 of the guide sleeve 5 does not need to be provided with fastening bolts, so that the positioning flange 501 can be pressed by the flange of the external suction pipe, thereby simplifying the structure of the high-efficiency vane pump of the present invention and reducing its manufacturing cost.

[0050] like Figure 1-Figure 3 , Fig.15 As shown, the high-pressure area of ​​the water pressure chamber of the pump body 1 is connected to the water inlet 12 of the static ring cavity 4 through the high-pressure water pipe 2; the water inlet 12 is arranged on the side of the pump body 1 close to the inlet flange 11 and away from the impeller suction port 16; in this way, the axial length of the static ring cavity 4 can be increased without increasing the axial size of the pump body 1, thereby increasing the axial length of the static ring 6 and improving its service life.

[0051] like Figure 1-Figure 3 , Fig.15 As shown, the working principle of the high-efficiency vane pump of this embodiment is:

[0052] When the high-efficiency vane pump in this embodiment is running, high pressure is formed in the water pressure chamber of the pump body 1, and the high-pressure water at the water outlet of the pump body 1 enters the static ring cavity 4 through the high-pressure water pipe 2 and the water inlet 12, and acts on the free end of the static ring 6, thereby pushing the static ring 6 to move axially in the direction of the dynamic ring 7; when the static ring 6 and the dynamic ring 7 are in contact, the channel for high-pressure water to leak from the high-pressure area to the low-pressure area at the impeller suction port 16 can be blocked, thereby achieving sealing, thereby improving efficiency; in this process, since the outer pressure of the contact surface between the static ring 6 and the dynamic ring 7 is high and the inner pressure is low, and at the same time, relative rotational motion occurs between the static ring 6 and the dynamic ring 7, the high-pressure water will leak from the outer side to the inner side of the contact surface between the static ring 6 and the dynamic ring 7, thereby cooling and lubricating the friction surface between the static ring 6 and the dynamic ring 7.

[0053] In addition, in order to improve the life of the friction pair formed between the stationary ring 6 and the dynamic ring 7, the dynamic ring 7 in this embodiment is made of tungsten carbide hard alloy, and its surface is polished, while the stationary ring 6 is made of HDPE polymer material; since the hardness of the dynamic ring 7 is much higher than that of the stationary ring 6, the wear rate of the dynamic ring 7 is much lower than that of the stationary ring 6; generally, the axial length of the stationary ring 6 can be 2-20 times the axial length of the dynamic ring 7. When it is less than 2 times, the life of the stationary ring 6 is too short, and the guiding effect of the guide sleeve 5 on the stationary ring 6 is not good, so that the parallelism and coaxiality accuracy of the stationary ring 6 relative to the dynamic ring 7 are low; and when it is greater than 20 times, the axial length of the pump body 1 is too large, which will increase the axial length of the pump body 1 and the manufacturing cost is too high; in this embodiment, the axial thickness of the stationary ring 6 is 44 mm, and the axial thickness of the dynamic ring 7 is 11 mm, that is, the former is 4 times the latter.

[0054] In addition, since the stationary ring 6 has a longer axial length, after the stationary ring 6 is worn, the water pressure of the medium entering the high-pressure water inlet will push the stationary ring 6 to automatically compensate. Even if the stationary ring 6 is worn, it will hardly cause a decrease in the sealing effect. Compared with the spring force compensation in the prior art, the automatic compensation method adopted in the present invention has a more stable pressure and a better sealing effect, thereby greatly improving the life of the friction pair.

[0055] Example 2

[0056] The main differences between this embodiment and embodiment 1 are:

[0057] like Figure 4-Figure 6 As shown, the impeller 3 is an open impeller, and its material is 304 stainless steel; the dynamic ring 7 is arranged on the suction side of the blades of the impeller 3, and the dynamic ring 7 is directly processed on the blank of the impeller 3.

[0058] like Figure 4-Figure 6 As shown, 20 water holes 601 for connecting the friction end and the free end of the static ring 6 are arranged in the static ring 6; the water holes 601 extend along the axial direction of the static ring cavity 4; a water guide groove 602 connected to the water hole 601 is arranged on the friction end of the static ring 6; the water guide groove 602 is annular; by arranging a plurality of water holes 601 for connecting the friction end and the free end of the static ring 6, high-pressure water can be injected into the friction surface between the moving ring 7 and the static ring 6 through the water holes 601 to form a structure similar to a static thrust bearing, thereby greatly improving the lubrication condition at the friction surface, and further improving the life of the friction pair; in addition, a water guide groove 602 connected to the water hole 601 is also arranged on the friction end of the static ring 6, and the water guide groove 602 can further improve the lubrication condition of the friction pair, thereby improving the life of the friction pair.

[0059] In this embodiment, the material of the stationary ring 6 is polytetrafluoroethylene.

[0060] like Figure 4-Figure 6 As shown, the working principle of the high-efficiency vane pump of this embodiment is:

[0061] When the high-efficiency vane pump of this embodiment is working, high-pressure water enters the water guide groove 602 from the static ring cavity 4 through the water hole 601. Since the water pressure at the static ring cavity 4 is higher than the pressure at the friction pair, the pressure will push the static ring 6 and the dynamic ring 7 to contact to achieve sealing; when the friction end of the static ring 6 is in contact with the dynamic ring 7, the pressure at the water guide groove 602 increases, pushing the static ring 6 away from the dynamic ring 7 in the opposite direction, so that the high-pressure water leaks to the suction port of the pump body 1, which in turn causes the water pressure at the water guide groove 602 to decrease, so that the pressure at the static ring cavity 4 is higher than the pressure at the friction pair, and the pressure will again push the static ring 6 and the dynamic ring 7 to contact to achieve sealing; this is equivalent to causing the static ring 6 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.

[0062] Example 3

[0063] The main differences between this embodiment and embodiment 1 are:

[0064] like Figure 7-Figure 8As shown, a seal is provided between the guide sleeve 5 and the stationary ring 6, and the seal is a seal ring 13, and the seal ring 13 is installed on the guide sleeve 5; through the above arrangement, the flow rate of high-pressure water leaking from the gap between the guide sleeve 5 and the stationary ring 6 to the suction port can be reduced, thereby improving the working efficiency of the high-efficiency vane pump in this embodiment; in addition, since the seal ring 13 has resistance to the axial movement of the stationary ring 6, the seal ring 13 is equivalent to a damping mechanism, which can reduce the vibration amplitude of the stationary ring 6, thereby reducing the leakage amount, thereby extending the life of the friction pair.

[0065] In addition, the end surface area of ​​the friction end of the static ring 6 (including the area of ​​the water hole 601 and the water guide groove 602) is larger than the end surface area of ​​the free end of the static ring 6 (including the area of ​​the water hole 601); the reason is that: due to the large pressure difference between the pressure chamber and the suction port of the high-lift pump, the water pressure difference acting on the free end of the static ring 6 and the friction end of the static ring 6 will also be large, which may cause the pressure between the friction surface of the static ring 6 and the dynamic ring 7 to be too large, resulting in a shortened life of the friction pair. Therefore, the end surface area of ​​the friction end of the static ring 6 is set to be larger than the end surface area of ​​its free end, so that the combined force of the pressure of the high-pressure water acting on the friction end surface and the free end surface of the static ring 6 will be reduced, thereby reducing the unit area pressure between the friction pairs and thereby increasing the life of the friction pairs.

[0066] In this embodiment, the static ring 6 is made of HDPE; the guide sleeve 5 is made of wear-resistant alloy. The guide sleeve 5 extends from the outer end of the suction port of the pump body 1 to the impeller suction port 16, which can protect the static ring 6 made of a softer material from being eroded and worn by the medium flowing into the impeller suction port 16.

[0067] Example 4

[0068] The main differences between this embodiment and embodiment 2 are:

[0069] like Fig. 9 and Fig.10 As shown, an anti-rotation structure is provided between the guide sleeve 5 and the stationary ring 6 for preventing relative rotation between the guide sleeve 5 and the stationary ring 6; 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 4; a keyway cooperating with the pin 9 is provided on the stationary ring 6; by providing the anti-rotation structure, the stationary ring 6 can be prevented from rotating around the axis of the impeller 3, which may cause wear of the stationary ring 6 and the guide sleeve 5.

[0070] In this embodiment, the impeller 3 is made of wear-resistant alloy; the dynamic ring 7 and the impeller 3 are made of the same material and are integrally manufactured; this can reduce the manufacturing cost. At this time, the axial thickness of the dynamic ring 7 is the axial thickness of the impeller front cover corresponding to the static ring 6;

[0071] In this embodiment, the axial thickness of the stationary ring 6 is 44 mm, and the axial thickness of the dynamic ring 7 is 21 mm, and the former is 2.1 times of the latter.

[0072] In addition, an elastic member is provided between the free end of the stationary ring 6 and the pump body 1, and the elastic member is 6 springs 8; one end of the spring 8 acts on the stationary ring 6, and the other end acts on the guide sleeve 5. When the guide sleeve 5 is removed, the spring 8 can be removed from the pump body 1 in the opposite direction of the suction direction of the impeller 3 (i.e. Fig. 9 It can be removed from right to left in the process of maintenance without first removing the pump body 1, which helps to reduce the workload of maintenance.

[0073] In addition, by providing the spring 8, the following effects can be obtained:

[0074] When high-pressure water is injected into the friction end of the stationary ring 6 through the water inlet hole 601 on the stationary ring 6, the water pressure on the friction end surface of the stationary ring 6 is in a fluctuating state. When the high-pressure water pushes the stationary ring 6 to move axially in the direction of the moving ring 7, the water inlet hole 601 or the water guide groove 602 at the friction end of the stationary ring 6 will be blocked, and the pressure of the high-pressure water at the friction end of the stationary ring 6 will naturally rise, thereby preventing the stationary ring 6 from moving in the direction of the moving ring 7; the forces at the friction end and the free end of the stationary ring 6 will reach equilibrium at a certain position, but because both the stationary ring 6 and the water have inertia, this will cause the stationary ring 6 to not be stably at the equilibrium point, but to vibrate near the equilibrium point. If the vibration amplitude is large, it may accelerate the wear of the friction pair, thereby increasing the consumption of high-pressure water; therefore, a number of elastic parts are arranged on the free end side of the stationary ring 6, which is equivalent to adding a damping mechanism, which can reduce the vibration amplitude of the stationary ring 6, thereby increasing the life of the friction pair, and further reducing the consumption of high-pressure water.

[0075] In this embodiment, since the sealing force of the friction pair does not entirely rely on the elastic force of the spring 8, the elastic linearity of the spring 8 can be designed to be different from that of the spring in the prior art, which can be more conducive to improving the life of the friction pair.

[0076] In addition, in this embodiment, the pump body 1 is configured to be composed of two parts, namely, a rear pump body 101 and a front pump body 102 , so that different parts can be replaced according to the wear conditions of the parts to reduce the use cost.

[0077] Example 5

[0078] The main differences between this embodiment and embodiment 2 are:

[0079] like Fig.11 and Fig.12 As shown, the static ring 6 is composed of two materials, wherein the material at the friction end of the static ring 6 is bronze, and the material at the free end is aluminum alloy, which can reduce costs and inertia. In addition, the high-pressure water pipe 2 is not connected to the high-pressure area or the water outlet pipe of the water pressure chamber, but to a dedicated water source with more stable pressure.

[0080] Example 6

[0081] The main differences between this embodiment and embodiment 1 are:

[0082] like Fig.13 and Fig.14 As shown, the pump body 1 is not provided with an external high-pressure water pipe, but is provided with a dark water channel 10 connecting the high-pressure area of ​​the water pressure chamber and the static ring cavity 4; when the high-efficiency vane 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 4 through the dark water channel 10, and since the water pressure at the free end of the static ring 6 is higher than the water pressure at its friction end, the static ring 6 moves toward the direction of the dynamic ring 7 under the action of the water pressure, so that the friction end of the static ring 6 contacts the dynamic ring 7 to achieve sealing.

[0083] Finally, in the above six embodiments, the water in the water inlet 12, high-pressure water pipe 2, water hole 601, hidden water channel 10, water guide groove 602 and other components is only for the convenience of description, rather than limiting the type of medium. The same effect can be achieved by replacing it with other liquid media such as oil and alcohol.

[0084] Since the structures of the turbine and the vane pump can be exactly the same, but the names are different due to different usage scenarios. Therefore, the high-efficiency vane pumps provided in the above six embodiments can all be used as turbines and improve the efficiency of turbines as long as the usage scenarios are changed. Therefore, the usage scenario of the high-efficiency vane pump of the present invention for turbines is also included in the protection scope of the present invention.

[0085] 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 vane pump, characterized in that: It comprises a pump body, an impeller and a sealing device arranged between the pump body and 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 or on the suction port side of the blade; 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 in contact with the dynamic ring is a friction end; the radial outer side of the guide sleeve and the corresponding part of the pump body constitute a static ring cavity for accommodating the static ring; the medium flows to the suction port of the impeller through the radial inner side of the guide sleeve; the axial thickness of the guide sleeve is greater than the axial thickness of the static ring.

2. The high-efficiency vane pump according to claim 1, characterized in that: The guide sleeve can be installed in the pump body along the suction direction of the impeller, and the stationary ring can be installed in the pump body along the suction direction of the impeller.

3. The high-efficiency vane pump according to claim 1, characterized in that: The guide sleeve is provided with a positioning flange; the positioning flange is arranged at the end thereof away from the impeller; the guide sleeve extends from the outer end of the suction port of the pump body to the suction port of the impeller; the pump body is provided with a positioning stop at a position corresponding to the positioning flange; the positioning stop is coaxially arranged with the pump body, and the positioning stop is arranged at the end of the pump body away from the impeller.

4. The high-efficiency vane pump according to claim 1, characterized in that: There is a first fitting gap between the guide sleeve and the stationary ring, and there is a second fitting gap between the stationary ring and the pump body; the size of the first fitting gap is smaller than the size of the second fitting gap.

5. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: The pump body is provided with a channel or connected with a pipe, one end of the pipe or channel is connected to the high-pressure area of ​​the water pressure chamber or the outlet pipe of the pump body, and the other end is connected to the static ring cavity; the high-pressure water in the static ring cavity can push the static ring to move along the guide sleeve toward the dynamic ring, and make the friction end of the static ring contact with the dynamic ring.

6. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: A sealing member is arranged between the guide sleeve and the static ring.

7. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: The stationary ring is provided with a plurality of water holes extending from the free end to the friction end, and the friction end is provided with a water guide groove communicating with the water holes, and the water guide groove is annular.

8. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: An anti-rotation structure is provided to prevent relative rotation between the guide sleeve and the stationary ring; the anti-rotation structure includes a pin provided 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 provided on the stationary ring.

9. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: An elastic member is provided to drive 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; when the guide sleeve is removed, the elastic member can be removed from the pump body along the opposite direction of the impeller suction.

10. The high-efficiency vane pump according to any one of claims 1 to 4, characterized in that: The axial thickness of the stationary ring is 2-20 times that of the dynamic ring, and the hardness of the former is smaller than that of the latter.

11. The vane pump according to any one of claims 1 to 4, characterized in that: An inlet flange is arranged at the outer end of the suction port of the pump body, and the outer end surface of the guide sleeve is flush with the end surface of the inlet flange.

12. The high-efficiency vane pump according to claim 5, characterized in that: An inlet flange is arranged at the outer end of the suction port of the pump body; a water inlet is connected to the static ring cavity, and the water inlet is connected to the high pressure area of ​​the water pressure chamber or the water outlet pipe; the water inlet is close to the inlet flange, away from the impeller suction port, and perpendicular to the axis of the pump body.

13. Use of the high-efficiency vane pump according to claim 1 in the field of hydropower generation.

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