Efficient vane pump

Abstract

The utility model discloses an efficient vane pump which 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] This utility model belongs to the field of vane pump manufacturing, and specifically relates to a high-efficiency vane pump. Background Technology

[0002] Centrifugal pumps, including centrifugal pumps, mixed-flow pumps, and axial-flow pumps, are the most common fluid transport equipment. When a centrifugal pump operates, the rotating impeller draws the medium in from the suction inlet. The blades do work on the medium, accelerating it and sending it into the plenum chamber of the pump body, converting the mechanical kinetic energy into the potential energy of the medium. The structure of a water turbine is almost identical to that of a centrifugal pump; the only difference is its application—it converts the potential energy of the medium into kinetic energy to drive other mechanical equipment. In some applications, such as pumped-storage power stations, the same hydraulic machinery is used as a turbine for power generation and as a centrifugal pump for pumping. When a centrifugal pump is operating, because the pressure in the plenum chamber is higher than the pressure at the suction inlet, the medium in the plenum chamber will leak to the suction inlet through the gap between the impeller and the pump body. This situation is called internal leakage, and internal leakage leads to a decrease in the efficiency of the centrifugal pump. To improve efficiency, many existing centrifugal pumps are designed with sealing rings to reduce internal leakage. Since the sealing ring and the pump body are in clearance fit, the size of the clearance is limited by many factors such as machining accuracy and mechanical operation accuracy, which makes internal leakage an important factor limiting efficiency improvement.

[0003] To address this issue, three patents / patent applications have been proposed: Patent CN114738311 B discloses a "leak-free centrifugal pump"; Patent CN2150371Y discloses a "pump inlet ring sealing device"; and Patent CN116696784 A discloses a "shipboard mud and sand pump with an inlet sealing ring." All three patents / patent applications describe a structure similar to a mechanical seal friction pair at the impeller's sealing ring location. This involves using an elastic element like a spring to press the sealing ring, thus preventing leakage of the medium from the high-pressure area of ​​the pressure chamber to the low-pressure area at the inlet. While this structure theoretically solves the internal leakage problem of centrifugal pumps, in actual operation, the spring force is difficult to control, and the lifespan of the friction pair is greatly affected by the spring force. Specifically, a large spring force significantly shortens the lifespan of the friction pair; conversely, a small spring force allows the medium pressure to force open the friction pair, resulting in a suboptimal sealing effect. Secondly, the spring force changes continuously with the wear of the friction pair. This leads to significant changes in friction and sealing effect when the friction pair experiences a certain level of wear, making it prone to seal failure due to wear. Furthermore, the short lifespan of the friction pair necessitates periodic replacement for maintenance. The aforementioned solutions are structurally complex and require disassembly of the pump body for replacement and maintenance, which is inconvenient. Therefore, the above-mentioned technical solutions have failed to gain widespread adoption in industrial applications due to these unresolved problems. Utility Model Content

[0004] In order to overcome the shortcomings of the existing technology, this utility model provides a high-efficiency vane pump. The high-efficiency vane pump can significantly reduce internal leakage of the medium, and has a better sealing effect, a longer service life of the sealing structure, and is more convenient to maintain.

[0005] The technical solution of this utility model to solve the above-mentioned technical problems is:

[0006] A high-efficiency vane pump includes a pump body, an impeller, and a sealing device disposed between the pump body and the impeller. The sealing device includes a rotating ring, a stationary ring, and a guide sleeve. The rotating ring is mounted on the front cover plate of the impeller or on the suction side of the vane. The stationary ring is movable along the axial direction of the guide sleeve, with one end contacting the rotating ring. The end of the stationary ring away from the impeller is a free end, and the end in contact with the rotating ring is a friction end. The radially outer side of the guide sleeve and the corresponding portion of the pump body form a stationary ring cavity to accommodate the stationary ring. The medium flows radially inner to the impeller suction port via the guide sleeve.

[0007] Preferably, the guide sleeve can be installed into the pump body along the suction direction of the impeller, and the stationary ring can be installed into the pump body along the suction direction of the impeller.

[0008] Preferably, the guide sleeve is provided with a positioning flange; the positioning flange is located at the end away from the impeller; the guide sleeve extends from the outer end of the pump body's suction port to the impeller's suction port; 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 located at the end of the pump body away from the impeller.

[0009] Preferably, there is a first fitting clearance between the guide sleeve and the stationary ring, and a second fitting clearance between the stationary ring and the pump body; the size of the first fitting clearance is smaller than the size of the second fitting clearance.

[0010] Preferably, the pump body is provided with a channel or connected to a pipe, one end of the pipe or channel is connected to the high-pressure zone of the pump body's pressure chamber or the outlet pipe, and the other end is connected to the stationary ring cavity; the high-pressure water in the stationary ring cavity can push the stationary ring to move along the guide sleeve toward the moving ring, and make the friction end of the stationary ring contact the moving ring.

[0011] Preferably, a seal is provided between the guide sleeve and the stationary ring.

[0012] 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, wherein the water guide groove is annular.

[0013] 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 disposed on the guide sleeve; the axial direction of the pin is parallel to the axial direction of the stationary ring cavity; and the stationary ring is provided with a keyway that mates with the pin.

[0014] Preferably, an elastic element is provided to drive the stationary ring to move toward the rotating ring; one end of the elastic element acts on the stationary ring, and the other end acts on the guide sleeve; when the guide sleeve is removed, the elastic element can be removed from the pump body in the opposite direction of impeller suction.

[0015] Preferably, the axial length of the stationary ring is 2-20 times the axial length of the rotating ring, and the hardness of the former is less than that of the latter.

[0016] Preferably, an inlet flange is provided at the outer end of the pump body's suction port, and the outer end face of the guide sleeve is flush with the end face of the inlet flange.

[0017] Preferably, an inlet flange is provided at the outer end of the pump body's suction port; the stationary ring cavity is connected to a water inlet, which is connected to the high-pressure zone of the 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.

[0018] An application of a high-efficiency vane pump in the field of hydropower generation, wherein the high-efficiency vane pump is used as a water turbine.

[0019] Compared with the prior art, this utility model has the following advantages and beneficial effects:

[0020] 1. In the high-efficiency vane pump of this utility model, the stationary ring can move along the axial direction of the stationary ring cavity and make one end of it contact the rotating ring; thus, as long as the machining accuracy is controlled, a high degree of coaxiality between the stationary ring and the rotating ring can be guaranteed, and a high degree of fit can be achieved between the friction pair formed between the stationary ring and the rotating ring; when the friction pair wears, 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.

[0021] 2. Because the guide sleeve and stationary ring in the sealing device of this utility model are easy to set with a longer axial dimension, the stationary ring can have a longer compensation length, thereby enabling the sealing device of this utility model to obtain a longer service life.

[0022] 3. In the high-efficiency vane pump of this utility model, the radial inner side of the guide sleeve is the channel for the medium to flow to the impeller inlet. This allows the guide sleeve to perform its guiding function while minimizing the radial dimension of the stationary ring under the premise of satisfying cavitation performance. This helps to reduce the frictional linear velocity of the stationary ring relative to the rotating ring, thereby improving the life of the friction pair. At the same time, the guide sleeve can prevent the softer stationary ring from being eroded by the medium flowing in along the impeller inlet direction and obtain a longer life.

[0023] 4. When the guide sleeve and the stationary ring can be installed into the pump body along the suction direction of the impeller, the stationary ring or guide sleeve can be replaced without removing the pump body, thereby greatly reducing the workload of maintenance. Attached Figure Description

[0024] Figure 1 This is a cross-sectional view of the first specific embodiment of the high-efficiency vane pump of this utility model.

[0025] Figure 2 This is a sectional view of the pump body and guide sleeve.

[0026] Figure 3 for Figure 1 A partial view at point A.

[0027] Figure 4This is a cross-sectional view of the second specific embodiment of the high-efficiency vane pump of this utility model.

[0028] Figure 5 for Figure 4 A partial view at point B.

[0029] Figure 6 This is a three-dimensional sectional view of the stationary ring.

[0030] Figure 7 This is a cross-sectional view of the third specific embodiment of the high-efficiency vane pump of this utility model.

[0031] Figure 8 for Figure 7 A partial view at point C.

[0032] Figure 9 This is a cross-sectional view of the fourth specific embodiment of the high-efficiency vane pump of this utility model.

[0033] Figure 10 for Figure 9 A partial view at point D in the middle.

[0034] Figure 11 This is a cross-sectional view of the fifth specific embodiment of the high-efficiency vane pump of this utility model.

[0035] Figure 12 for Figure 11 A partial view of point E in the middle.

[0036] Figure 13 This is a cross-sectional view of the sixth specific embodiment of the high-efficiency vane pump of this utility model.

[0037] Figure 14 for Figure 13 A partial view at point F in the middle.

[0038] Figure 15 This is a schematic diagram showing the positions of the first fitting clearance, the second fitting clearance, and the impeller inlet.

[0039] In the diagram: 1-Pump body, 101-Rear pump body, 102-Front pump body, 2-High-pressure water pipe, 3-Impeller, 4-Stationary ring cavity, 5-Guide sleeve, 501-Positioning flange, 6-Stationary ring, 601-Water hole, 602-Water guide groove, 7-Dynamic ring, 8-Spring, 9-Pin, 10-Hidden water channel, 11-Inlet flange, 12-Water inlet, 13-Sealing ring, 14-First fitting clearance, 15-Second fitting clearance, 16-Impeller suction port. Detailed Implementation

[0040] The present invention will be further described in detail below with reference to the embodiments and accompanying drawings, but the implementation of the present invention is not limited thereto.

[0041] Example 1

[0042] like Figures 1-3 , Figure 15 As shown, the high-efficiency vane pump of this utility model includes a pump body 1, an impeller 3, and a sealing device disposed between the pump body 1 and the impeller 3; the sealing device includes a moving ring 7, a stationary ring 6, and a guide sleeve 5; wherein, the guide sleeve 5 is mounted on the pump body 1, and the radial outer side of the guide sleeve 5 and the pump body 1 form a stationary ring cavity 4 for accommodating the stationary ring 6; the stationary ring 6 is disposed in the stationary ring cavity 4 and can move along the axial direction of the stationary ring cavity 4 so that one end of it contacts the moving ring 7; the end of the stationary ring 6 away from the impeller 3 is a free end, and the end of the stationary ring 6 in contact with the moving ring 7 is a friction end; the moving ring 7 is mounted on the front cover plate of the impeller 3.

[0043] In this embodiment, the guide sleeve 5 can be installed into the pump body 1 along the suction direction of the impeller 3, and the stationary ring 6 can also be installed into the pump body 1 along the suction direction of the impeller 3, that is, the guide sleeve 5 and the stationary ring 6 can be installed from... Figure 1 The impeller 3 is inserted into the pump body 1 from the left side along the suction direction of the impeller 3. Of course, it can also be removed in the opposite direction. This way, the easily damaged stationary ring 6 and guide sleeve 5 can be replaced without removing the pump body 1, thereby greatly reducing the amount of maintenance work.

[0044] like Figures 1-3 , Figure 15 As shown, a positioning flange 501 is provided on the guide sleeve 5, and the positioning flange 501 is located 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 suction port 16 of the impeller, so that the longest axial length of the guide sleeve 5 can be obtained without increasing the axial dimension of the pump body 1, thereby increasing the axial length of the stationary ring cavity 4 and the stationary ring 6, and extending the service life of the stationary ring 6; the pump body 1 is provided with a positioning stop at the position corresponding to the positioning flange 501; the positioning stop is located at the end of the pump body 1 away from the impeller 3, and is coaxially arranged with the pump body 1.

[0045] like Figures 1-3 , Figure 15 As shown, there is a first fitting gap 14 between the guide sleeve 5 and the stationary ring 6, and there is 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.

[0046] 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.

[0047] In this embodiment, the impeller 3 is made of carbon steel; the stationary ring 6 is made of HDPE with an axial length of 44 mm; the rotating ring 7 is made of tungsten carbide alloy with an axial length of 11 mm. The axial length of the stationary ring 6 is four times that of the rotating ring 7, and the hardness of the stationary ring 6 is less than that of the rotating ring 7. Therefore, the wear rate of the rotating ring 7 is much lower, and its service life can be close to that of the impeller 3, so it does not need to be replaced separately. Although the stationary ring 6 has lower hardness and lower cost, it has better wear resistance, and due to its larger axial length, its service life can still be significantly improved compared to the prior art.

[0048] like Figures 1-3 , Figure 15 As shown, an inlet flange 11 is provided on the outer end of the suction port of the pump body 1. The outer end face of the guide sleeve 5 is flush with the end face of the inlet flange 11. In this way, the positioning flange 501 of the guide sleeve 5 does not need to be equipped with fastening bolts. 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 this utility model and reducing its manufacturing cost.

[0049] like Figures 1-3 , Figure 15 As shown, the high-pressure zone of the pressure chamber of the pump body 1 is connected to the inlet 12 of the stationary ring cavity 4 through a high-pressure water pipe 2; the inlet 12 is located 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 stationary ring cavity 4 can be increased without increasing the axial dimension of the pump body 1, thereby increasing the axial length of the stationary ring 6 and improving its service life.

[0050] like Figures 1-3 , Figure 15 As shown, the working principle of the high-efficiency vane pump in this embodiment is as follows:

[0051] During operation of the high-efficiency vane pump in this embodiment, the pressure chamber in the pump body 1 generates high pressure. The high-pressure water at the outlet of the pump body 1 enters the stationary ring cavity 4 through the high-pressure water pipe 2 and the inlet 12, and acts on the free end of the stationary ring 6, thereby pushing the stationary ring 6 to move axially towards the moving ring 7. When the stationary ring 6 and the moving ring 7 come into 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 a seal and improving efficiency. During this process, since the pressure on the outer side of the contact surface between the stationary ring 6 and the moving ring 7 is high and the pressure on the inner side is low, and the stationary ring 6 and the moving ring 7 will rotate relative to each other, the high-pressure water will leak from the outer side of the contact surface between the stationary ring 6 and the moving ring 7 to the inner side, thereby cooling and lubricating the friction surface between the stationary ring 6 and the moving ring 7.

[0052] Furthermore, to improve the lifespan of the friction pair formed between the stationary ring 6 and the rotating ring 7, the rotating ring 7 in this embodiment is made of tungsten carbide hard alloy with a polished surface, while the stationary ring 6 is made of HDPE polymer material. Since the hardness of the rotating ring 7 is much higher than that of the stationary ring 6, the wear rate of the rotating 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 rotating ring 7. When it is less than 2 times, the lifespan of the stationary ring 6 is too short, and the guiding effect of the guide sleeve 5 on the stationary ring 6 is poor, resulting in low parallelism and coaxiality accuracy between the stationary ring 6 and the rotating ring 7. When it is greater than 20 times, the axial length of the pump body 1 is too large, which leads to an increase in the axial length of the pump body 1 and excessively high manufacturing costs. In this embodiment, the axial length of the stationary ring 6 is 44 mm, and the axial length of the rotating ring 7 is 11 mm, meaning the former is 4 times the latter.

[0053] Furthermore, since the stationary ring 6 has a relatively long axial length, after the stationary ring 6 wears, the water pressure of the medium entering the high-pressure water inlet will drive the stationary ring 6 to perform automatic compensation. Even if the stationary ring 6 wears, it will hardly cause a decrease in the sealing effect. Compared with the spring force compensation of the prior art, the automatic compensation method adopted by this utility model has more stable pressure and better sealing effect, thereby greatly improving the life of the friction pair.

[0054] Example 2

[0055] The main differences between this embodiment and Embodiment 1 are as follows:

[0056] like Figures 4-6 As shown, the impeller 3 is an open impeller made of 304 stainless steel; the moving ring 7 is located on the suction side of the blades of the impeller 3, and the moving ring 7 is directly machined from the blank of the impeller 3.

[0057] like Figures 4-6 As shown, the stationary ring 6 has 20 water holes 601 for connecting the friction end and the free end of the stationary ring 6; the water holes 601 extend along the axial direction of the stationary ring cavity 4; the friction end of the stationary ring 6 has a water guide groove 602 communicating with the water holes 601; the water guide groove 602 is annular; by setting a number of water holes 601 on the stationary ring 6 to connect its friction end and the free end, high-pressure water can be injected into the friction surface between the moving ring 7 and the stationary ring 6 through the water holes 601 to form a structure similar to a hydrostatic thrust bearing, thereby greatly improving the lubrication condition at the friction surface and further increasing the life of the friction pair; in addition, the friction end of the stationary ring 6 also has a water guide groove 602 communicating with the water holes 601, which can further improve the lubrication condition of the friction pair and thus increase the life of the friction pair.

[0058] In this embodiment, the stationary ring 6 is made of polytetrafluoroethylene.

[0059] like Figures 4-6 As shown, the working principle of the high-efficiency vane pump in this embodiment is as follows:

[0060] In this embodiment, when the high-efficiency vane pump is working, high-pressure water enters the guide groove 602 from the stationary ring cavity 4 through the water hole 601. Since the water pressure at the stationary ring cavity 4 is higher than the pressure at the friction pair, this pressure will push the stationary ring 6 and the rotating ring 7 into contact to achieve a seal. When the friction end of the stationary ring 6 contacts the rotating ring 7, the pressure at the guide groove 602 increases, pushing the stationary ring 6 away from the rotating ring 7 in the opposite direction, thereby causing high-pressure water to leak to the suction port of the pump body 1. This, in turn, causes the water pressure at the guide groove 602 to decrease, making the pressure at the stationary ring cavity 4 higher than the pressure at the friction pair. This pressure will then push the stationary ring 6 and the rotating ring 7 into contact again to achieve a seal. This is equivalent to causing the stationary ring 6 to dynamically float under the action of the water pressure at both ends, thereby maintaining an appropriate leakage of the friction pair while meeting the cooling and lubrication requirements of the friction pair.

[0061] Example 3

[0062] The main differences between this embodiment and Embodiment 1 are as follows:

[0063] like Figures 7-8As shown, a sealing element, namely a sealing ring 13, is provided between the guide sleeve 5 and the stationary ring 6. The sealing 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 sealing ring 13 provides resistance to the axial movement of the stationary ring 6, the sealing ring 13 is equivalent to a damping mechanism, which can reduce the vibration amplitude of the stationary ring 6, thereby reducing the leakage and extending the life of the friction pair.

[0064] Furthermore, the end face area of ​​the friction end of the stationary ring 6 (including the area of ​​the water hole 601 and the water guide groove 602) is larger than the end face area of ​​the free end of the stationary ring 6 (including the area of ​​the water hole 601). This is because, in high-lift pumps, the pressure difference between the pressure chamber and the suction port is large, resulting in a larger water pressure difference acting on the free end and the friction end of the stationary ring 6. This could lead to excessive pressure between the friction surfaces of the stationary ring 6 and the moving ring 7, shortening the lifespan of the friction pair. Therefore, by setting the end face area of ​​the friction end of the stationary ring 6 to be larger than that of its free end, the combined force of the pressure exerted by the high-pressure water on the friction end and free end of the stationary ring 6 is reduced. This reduces the pressure per unit area between the friction pairs, thereby increasing their lifespan.

[0065] In this embodiment, the stationary 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 relatively soft stationary ring 6 from the scouring and wear of the medium flowing into the impeller suction port 16.

[0066] Example 4

[0067] The main differences between this embodiment and Embodiment 2 are as follows:

[0068] like Figure 9 and Figure 10 As shown, an anti-rotation structure is provided between the guide sleeve 5 and the stationary ring 6 to prevent 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; the stationary ring 6 is provided with a keyway that mates with the pin 9; by providing the anti-rotation structure, the stationary ring 6 can be prevented from rotating around the axis of the impeller 3, thus preventing wear on the stationary ring 6 and the guide sleeve 5.

[0069] In this embodiment, the impeller 3 is made of wear-resistant alloy; the moving ring 7 and the impeller 3 are made of the same material and are manufactured as a single piece; this can reduce manufacturing costs. At this time, the axial length of the moving ring 7 is the same as the axial length of the impeller front cover plate corresponding to the stationary ring 6.

[0070] In this embodiment, the axial length of the stationary ring 6 is 44 mm, and the axial length of the moving ring 7 is 21 mm, the former being 2.1 times the latter.

[0071] In addition, an elastic element, consisting of six springs 8, is provided between the free end of the stationary ring 6 and the pump body 1. One end of each 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 springs 8 can be removed from the pump body 1 in the opposite direction to the suction direction of the impeller 3 (i.e., Figure 9 (The pump body 1 can be removed from right to left) instead of first removing the pump body 1, which helps reduce the amount of maintenance work.

[0072] Furthermore, by setting the spring 8, the following effects can be achieved:

[0073] When high-pressure water is injected into the friction end of the stationary ring 6 through the water inlet 601, the water pressure at the friction end of the stationary ring 6 is fluctuating. When the high-pressure water pushes the stationary ring 6 to move axially towards the moving ring 7, it will cause the water inlet 601 or the water guide groove 602 at the friction end of the stationary ring 6 to 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 towards the moving ring 7. The forces between the friction end and the free end of the stationary ring 6 will reach equilibrium at a certain position. However, since both the stationary ring 6 and the water have inertia, the stationary ring 6 cannot be stably at the equilibrium point, but will 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, several elastic elements are provided 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 improving the life of the friction pair and reducing the consumption of high-pressure water.

[0074] In this embodiment, since the sealing force of the friction pair does not rely entirely on the elastic force of the spring 8, the elastic force linearity of the spring 8 can be designed differently from that of springs in the prior art, which can be more conducive to improving the life of the friction pair.

[0075] In addition, in this embodiment, the pump body 1 is configured to be composed of two parts: a rear pump body 101 and a front pump body 102. This allows for the replacement of different parts according to their wear condition, thereby reducing the cost of use.

[0076] Example 5

[0077] The main differences between this embodiment and Embodiment 2 are as follows:

[0078] like Figure 11 and Figure 12 As shown, the stationary ring 6 is composed of two materials: bronze at the friction end and aluminum alloy at the free end. This reduces cost and inertia. Furthermore, the high-pressure water pipe 2 is not connected to the high-pressure zone of the pressure chamber or the outlet pipe, but rather to a dedicated water source with more stable pressure.

[0079] Example 6

[0080] The main differences between this embodiment and Embodiment 1 are as follows:

[0081] like Figure 13 and Figure 14 As shown, the pump body 1 does not have an external high-pressure water pipe, but instead has a hidden water channel 10 connecting the high-pressure zone of the pressure chamber and the stationary ring cavity 4. When the high-efficiency vane pump in this embodiment is working, the high-pressure water in the high-pressure zone of the pressure chamber enters the stationary ring cavity 4 through the hidden water channel 10. Since the water pressure at the free end of the stationary ring 6 is higher than the water pressure at its friction end, the stationary ring 6 moves towards the moving ring 7 under the action of water pressure, thereby making the friction end of the stationary ring 6 contact the moving ring 7 to achieve a seal.

[0082] Finally, in the above six embodiments, the water in the components such as the water inlet 12, high-pressure water pipe 2, water hole 601, underground water channel 10, and water guide trough 602 is only for ease of description and is not a limitation on the type of medium. Replacing it with other liquid media such as oil or alcohol can achieve the same effect.

[0083] Since the structures of water turbines and vane pumps can be completely identical, differing only in their application scenarios, the high-efficiency vane pumps provided in the above six embodiments can all be used as water turbines, improving their efficiency, simply by changing the application scenario. Therefore, the high-efficiency vane pump of this utility model, when used in water turbine applications, is also included within the scope of protection of this utility model.

[0084] The above are preferred embodiments of the present utility model, but the embodiments of the present utility model are not limited to the above content. Any changes, modifications, substitutions, combinations, or simplifications made without departing from the spirit and principle of the present utility model shall be considered equivalent substitutions and shall be included within the protection scope of the present utility model.

Claims

1. A high-efficiency vane pump, characterized in that, The pump includes a pump body, an impeller, and a sealing device disposed between the pump body and the impeller. The sealing device includes a rotating ring, a stationary ring, and a guide sleeve. The rotating ring is mounted on the front cover plate of the impeller or on the suction side of the blades. The stationary ring is movable along the axial direction of the guide sleeve, with one end contacting the rotating ring. The end of the stationary ring away from the impeller is a free end, and the end in contact with the rotating ring is a friction end. The radially outer side of the guide sleeve and the corresponding part of the pump body form a stationary ring cavity to accommodate the stationary ring. The medium flows to the impeller suction port through the radially inner side of the guide sleeve.

2. The high-efficiency vane pump according to claim 1, characterized in that, The guide sleeve can be installed into the pump body along the suction direction of the impeller, and the stationary ring can be installed into 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 located at the end away from the impeller; the guide sleeve extends from the outer end of the pump body's suction port to the impeller's suction port; 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 located 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 clearance between the guide sleeve and the stationary ring, and there is a second fitting clearance between the stationary ring and the pump body; the size of the first fitting clearance is smaller than the size of the second fitting clearance.

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

6. The high-efficiency vane pump according to any one of claims 1-4, characterized in that, A seal is provided between the guide sleeve and the stationary ring.

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

8. The high-efficiency vane pump according to any one of claims 1-4, 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 disposed on the guide sleeve; the axial direction of the pin is parallel to the axial direction of the stationary ring cavity; the stationary ring is provided with a keyway that mates with the pin.

9. The high-efficiency vane pump according to any one of claims 1-4, characterized in that, An elastic element is provided to drive the stationary ring to move toward the rotating ring; one end of the elastic element acts on the stationary ring, and the other end acts on the guide sleeve; when the guide sleeve is removed, the elastic element can be removed from the pump body in the opposite direction of impeller suction.

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

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

12. The high-efficiency vane pump according to claim 5, characterized in that, An inlet flange is provided at the outer end of the pump body's suction port; the stationary ring cavity is connected to a water inlet, which is connected to the high-pressure zone of the 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.

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