Wear-resistant impurity pump and pump body thereof

Abstract

The utility model discloses a wear-resisting impurity pump and a pump body thereof, the wear-resisting impurity pump comprises the pump body, an impeller and a sealing device arranged between the pump body and the impeller, and the sealing device comprises a moving ring, a static ring and a guide sleeve; a static ring cavity for accommodating the static ring is formed between the radial outer side of the guide sleeve and the pump body; a medium enters an impeller suction inlet of the impeller through the radial inner side of the guide sleeve, the end, away from the impeller, of the static ring is a free end, and the end, capable of making contact with the movable ring, of the static ring is a friction end. The static ring can move in the axis direction of the guide sleeve. And the static ring cavity is communicated with a flushing water inlet. The abrasion-resistant impurity pump can prevent or reduce internal leakage of media, and is better in sealing performance and abrasion resistance, low in cost and easy to maintain.

Description

TECHNICAL FIELD

[0001] The utility model belongs to the field of wear-resistant impurity pump manufacturing, and particularly relates to a wear-resistant impurity pump and a pump body thereof. BACKGROUND

[0002] Vane pumps are the most common fluid conveying equipment; when the conveyed liquid contains solid particles, that is, the medium is a liquid-solid two-phase flow, such a vane pump is often referred to as an impurity pump. Impurity pumps are sometimes also referred to as slurry pumps, sewage pumps, sand pumps, etc. according to different use scenarios. Since solid particles can cause great wear to the impeller, pump body and other flow parts of the pump, the flow parts of the impurity pump are generally made of materials that are resistant to wear, such as wear-resistant alloy, wear-resistant rubber, ceramic, etc. For clean water pumps, in order to improve the efficiency of the pump, a sealing ring is generally designed to reduce internal leakage, but for impurity pumps, since solid particles can quickly wear out and fail the sealing ring, a sealing ring is generally not designed, but a vice blade is designed to reduce internal leakage. However, whether it is a sealing ring or a vice blade, internal leakage of the impurity pump is unavoidable. For impurity pumps, internal leakage not only leads to a decrease in the working efficiency of the pump, but more importantly, it leads to accelerated wear of the flow parts, because when the particles in the medium leak from the high-pressure area in the pump body to the suction inlet direction through the gap between the impeller front cover plate and the pump body, the scouring speed of the medium on the outer surface of the impeller front cover plate and the surface of the corresponding pump body part is much higher than that on other parts such as flow parts, which also leads to a much higher wear rate of the surface of this part than that of other parts.

[0003] In order to solve this problem, the invention patent with the authorization patent number CN114738311 B discloses "a leakage-free centrifugal pump", the utility model patent with the authorization patent number CN2150371 Y discloses "pump suction inlet ring sealing device", and the invention patent application with the application publication number CN116696784 A discloses "a mud and sand pump for ships with an inlet sealing ring", the above three patents / patent applications all disclose a structure similar to a mechanical seal friction pair at the position of the sealing ring of the impeller, which is pressed tightly by an elastic member such as a spring, and the medium in the high-pressure area of the water chamber is blocked from leaking to the low-pressure area of the suction inlet by the friction pair. This structure can indeed solve the leakage problem in theory, but in actual operation, the service life of the friction pair will be very short under the influence of the medium containing a large number of particles, so it is difficult to promote in actual industrial applications.

[0004] Therefore, in order to improve the service life of the impeller ring part, the invention patent application with the application number of CN116696784A discloses "a mud pump with an inlet sealing ring for use on a ship", which proposes a technical solution of opening a flushing hole at the ring part to flush the ring part with external clean water through the flushing hole. However, this technical solution cannot reduce the leakage flow of the high-pressure area of the pressure chamber to the suction port, and the wear condition of the outer surface of the front cover plate of the impeller and the flow surface of the pump body corresponding thereto is not significantly improved, so the effect of prolonging the service life of the flow member is very limited.

[0005] In addition, the invention patent application with the application number of CN116066373A discloses "a zero-leakage easy-to-maintain high-efficiency slurry pump", which proposes a scheme of setting four pairs of friction pairs. After injecting high-pressure clean water into the friction pairs, two high-pressure clean water chambers are formed in front and back of the friction pairs to flush and cool the four pairs of friction pairs, thereby reducing the wear of the flow member. The above-mentioned scheme can indeed reduce the wear of the flow member in theory, but the structure of the slurry pump of the scheme is complex, the manufacturing cost is high, and the service life of the friction pairs is difficult to guarantee. This leads to a high maintenance frequency, and the entire pump body needs to be disassembled when the friction pairs are replaced, so the maintenance workload is large, and thus the promotion difficulty is large. Practical new type content

[0006] The utility model discloses in order to overcome the insufficient of prior art, provide a wear-resistant impurity pump, wear-resistant impurity pump can prevent or reduce the leakage in medium, and the sealing property and wear resistance are better, and the cost is lower, and easy maintenance.

[0007] The second object of the utility model is to provide a pump body for the wear-resistant impurity pump.

[0008] The technical scheme of the utility model for solving above-mentioned technical problem is:

[0009] A wear-resistant impurity pump, including pump body, impeller and the sealing device that sets up between the pump body with the impeller, wherein, the sealing device includes dynamic ring, static ring and guide sleeve, the static ring cavity for accommodating the static ring is formed between the radial outer side of the guide sleeve and the pump body, medium passes through the radial inner side of the guide sleeve and enters the impeller suction port of the impeller, the end of the static ring away from the impeller is free end, and the end of the static ring that can contact with the dynamic ring is friction end, the static ring can move along the axis direction of the guide sleeve, the static ring cavity is communicated with flushing water inlet.

[0010] Preferably, the guide sleeve is installed on the pump body, and the guide sleeve can be installed into the pump body along the suction direction of the impeller, and the static ring can be installed into the pump body along the suction direction of the impeller.

[0011] Preferably, the guide sleeve extends from the outer end surface of the pump body to the suction inlet of the impeller; a positioning flange is arranged on the guide sleeve, the positioning flange being arranged at the end of the guide sleeve away from the impeller; the pump body is provided with a positioning stop at a position corresponding to the positioning flange; the positioning stop and the pump body are coaxially arranged; the outer diameter of the positioning flange is greater than the outer diameter of the static ring.

[0012] Preferably, the flushing water inlet is arranged at the end of the static ring cavity away from the impeller and close to the positioning flange.

[0013] Preferably, a first fit clearance exists between the guide sleeve and the static ring, and a second fit clearance exists between the static ring and the pump body; the size of the first fit clearance is smaller than the size of the second fit clearance.

[0014] Preferably, a sealing member is arranged between the guide sleeve and the static ring, and the sealing member is a sealing ring.

[0015] Preferably, the sealing device further comprises an anti-rotation structure for preventing relative rotation between the guide sleeve and the static ring; the anti-rotation structure comprises a pin arranged on the guide sleeve; the axis direction of the pin is parallel to the axis direction of the static ring cavity; the static ring is provided with a key groove matched with the pin.

[0016] Preferably, the sealing device further comprises an elastic member for driving the static ring to move towards the dynamic ring, one end of the elastic member acting on the static ring and the other end of the elastic member acting on the guide sleeve; when the guide sleeve is removed, the elastic member is taken out from the pump body in the direction opposite to the suction direction of the impeller.

[0017] Preferably, the axial length of the static ring is 3-20 times the axial length of the dynamic ring, and the hardness of the static ring is smaller than the hardness of the dynamic ring.

[0018] Preferably, an inlet flange is arranged on the end of the pump body outside the suction inlet, the outer end surface of the guide sleeve is flush with the end surface of the inlet flange; the flushing water inlet is close to the inlet flange, and the axis direction of the flushing water inlet is perpendicular to the axis direction of the pump body.

[0019] Preferably, the static ring is provided with a plurality of water holes extending from the free end of the static ring to the friction end of the static ring and a water guide groove arranged at the friction end of the static ring and communicating with the water holes, wherein the water guide groove is annular; the outer side of the friction end of the static ring is provided with a plurality of water injection holes.

[0020] A pump body for the pump resistant to wear impurities.

[0021] Compared with the prior art, the utility model has the following advantages and beneficial effects:

[0022] 1、 The utility model discloses a sealing device of wear-resistant impurity pump, the guide sleeve of which is not only the channel of medium inflow impeller suction inlet, but also can keep the coaxial degree and flatness of static ring and dynamic ring, so that the axial length of static ring can be prolonged to obtain longer compensation length without increasing the axial size of impurity pump, thereby improving the coaxial degree and flatness of static ring and dynamic ring, and further reducing the wear of friction pair formed between static ring and dynamic ring.

[0023] 2、 The utility model discloses a wear-resistant impurity pump, when working, flushing water can flow from the gap between static ring cavity and static ring to the friction pair composed of static ring and dynamic ring, and the water pressure pushes static ring to move axially to the direction of dynamic ring, so that dynamic ring and static ring contact to block the channel of high-pressure zone medium leakage to low-pressure zone, thereby reducing the leakage amount to the inlet bottom pressure zone; since the pressure of flushing water can be higher than the pressure of friction pair and suction inlet, flushing water will penetrate into the surface of friction pair and lubricate and cool it. Compared with the prior art, the contact force and sealing effect between static ring and dynamic ring will not change obviously due to the surface wear of friction pair and the length change of static ring, and the medium entering the friction pair is mainly high-pressure clean water, which carries less solid particles, so that the service life of the friction pair can be greatly improved.

[0024] 3、 The utility model discloses a wear-resistant impurity pump, when working, under the condition that the water amount and pressure of flushing water are appropriate, the injection amount of flushing water can be greater than the leakage amount between friction pairs, at this time, the medium in the high-pressure zone of pump body will not leak to the direction of suction inlet, part of flushing water will flow from the friction pair to the high-pressure zone of pump body, and solid particles in the medium are difficult to enter the gap between impeller front cover plate and pump body due to the centrifugal action of impeller rotation, which greatly reduces the wear of the outer surface of impeller front cover plate and the corresponding pump body part, thereby improving the service life of impurity pump.

[0025] 4、 Even if the water amount of flushing water is less than the leakage amount between friction pairs, the leakage amount of high-pressure zone of pump body to suction inlet can still be reduced, thereby reducing the flow rate or concentration of leakage and improving the service life of wear-resistant impurity pump.

[0026] 5. Compared with the existing technology where the friction pair requires disassembling the pump body to replace vulnerable parts such as the stationary ring during maintenance, the present invention allows vulnerable parts such as the guide sleeve and stationary ring to be installed into the pump body along the direction of the impeller inlet, and can also be removed from the pump body in the opposite direction. In this way, vulnerable parts such as the stationary ring and guide sleeve can be replaced without disassembling the pump body, which can greatly reduce the workload of maintenance. Attached Figure Description

[0027] Figure 1 This is a cross-sectional view of the first specific embodiment of the wear-resistant impurity pump of this utility model.

[0028] Figure 2 for Figure 1 A partial view at point A.

[0029] Figure 3 This is a cross-sectional view of the second specific embodiment of the wear-resistant impurity pump of this utility model.

[0030] Figure 4 for Figure 3 A partial view at point B.

[0031] Figure 5 This is a cross-sectional view of the stationary ring.

[0032] Figure 6 This is a cross-sectional view of the third specific embodiment of the wear-resistant impurity pump of this utility model.

[0033] Figure 7 for Figure 6 A partial view at point C.

[0034] Figure 8 This is a three-dimensional sectional view of the stationary ring.

[0035] Figure 9 This is a cross-sectional view of the fourth specific embodiment of the wear-resistant impurity pump of this utility model.

[0036] Figure 10 for Figure 9 A partial view at point D.

[0037] Figure 11 This is a cross-sectional view of the fifth specific embodiment of the wear-resistant impurity pump of this utility model.

[0038] Figure 12 for Figure 11 A partial view at point E.

[0039] Figure 13 This is a cross-sectional view of the sixth specific embodiment of the wear-resistant impurity pump of this utility model.

[0040] Figure 14 for Figure 13A local view at F.

[0041] In the figure: 1-pump body, 101-rear pump body, 102-front pump body, 2-impeller, 3-flushing water inlet, 4-moving ring, 5-stationary ring, 51-water inlet hole, 52, water guide groove, 53, water jet hole, 6-guide sleeve, 61-positioning flange, 7-stationary ring cavity, 8-pintle, 9-seal ring, 10-spring, 11-inlet flange. DETAILED DESCRIPTION

[0042] The utility model will be described in further detail below in combination with examples and drawings, but the implementation of the utility model is not limited to this.

[0043] Example 1

[0044] As shown in Figure 1 and Figure 2 , the wear-resistant impurity pump of the embodiment comprises a pump body 1, an impeller 2 arranged in the pump body 1, and a sealing device arranged between the pump body 1 and the impeller 2, wherein the sealing device comprises a moving ring 4, a stationary ring 5, and a guide sleeve 6; the moving ring 4 is installed on the front cover plate of the impeller 2, a stationary ring cavity 7 for accommodating the stationary ring 5 is formed between the radial outer side of the guide sleeve 6 and the pump body 1; the medium flows to the suction inlet of the impeller 2 through the radial inner side of the guide sleeve 6; the stationary ring 5 can move along the axial direction of the guide sleeve 6 and make one end thereof contact the moving ring 4; the end of the stationary ring 5 close to the moving ring 4 is a friction end, and the end of the stationary ring 5 away from the moving ring 4 is a free end; the stationary ring cavity 7 is communicated with a flushing water inlet 3, and the flushing water inlet 3 is arranged at one end of the stationary ring cavity 7 away from the impeller 2 and close to the positioning flange 61; the water pressure of the medium entering the stationary ring cavity 7 can push the stationary ring 5 to move axially in the stationary ring cavity 7, so as to make the friction end of the stationary ring 5 contact the moving ring 4.

[0045] As shown in Figure 1 and Figure 2 , the guide sleeve 6 is provided with a positioning flange 61 arranged at one end of the guide sleeve 6 away from the impeller 2. By arranging the positioning flange 61, the axes of the guide sleeve 6 and the pump body 1 can be coaxial during installation, so as to ensure that the axis of the stationary ring 5 is concentric with the axis of the impeller 2, thereby reducing the wear of the stationary ring 5 and the moving ring 4 caused by different axes, and at the same time, the stationary ring cavity 7 can obtain a larger axial length to accommodate a longer stationary ring 5 as much as possible.

[0046] As shown in Figure 1 and Figure 2As shown, the guide sleeve 6 extends from the outer end face of the pump body 1 to the suction port of the impeller 2. The medium enters the suction port of the impeller 2 from the radially inner side of the guide sleeve 6. The guide sleeve 6 is made of wear-resistant alloy, which not only provides a longer service life but also prevents the medium from eroding the stationary ring 5, thus improving the service life of the stationary ring 5. The pump body 1 is provided with a positioning stop at a position corresponding to the positioning flange 501; the outer diameter of the positioning flange 61 is larger than the outer diameter of the stationary ring 5.

[0047] like Figure 1 and Figure 2 As shown, the guide sleeve 6 can be installed into the pump body 1 along the suction direction of the impeller 2 (i.e., the guide sleeve 6 can be installed into the pump body 1 from right to left), and the stationary ring 5 can be installed into the pump body 1 along the suction direction of the impeller 2 (i.e., the stationary ring 5 can be installed into the pump body 1 from right to left). In this way, the easily damaged stationary ring 5 and guide sleeve 6 can be replaced without removing the pump body 1, thereby greatly reducing the amount of maintenance work.

[0048] like Figure 1 and Figure 2 As shown, the flushing water inlet 3 is located at one end of the stationary ring cavity 7, away from the impeller 2 and close to the positioning flange 61. This allows the stationary ring 5 to have a larger axial length and thus a longer service life.

[0049] In addition, the pressure of the flushing water is about 30% higher than the outlet pressure of the wear-resistant impurity pump in this embodiment. The flushing water is generally industrial clean water. When the wear-resistant impurity pump in this embodiment is working, the flushing water enters the stationary ring cavity 7 from the flushing water inlet 3. The stationary ring 5 moves towards the moving ring 4 and contacts it under the water pressure in the stationary ring cavity 7, thereby preventing the high-pressure medium in the pressure chamber from leaking into the suction chamber.

[0050] In addition, the flushing water in the stationary ring chamber 7 enters the outer side of the friction pair formed by the friction end face of the stationary ring 5 and the moving ring 4 from the first fitting gap of 3-4 mm between the stationary ring 5 and the pump body 1. Part of the flushing water permeates from the high-pressure area on the outside of the friction pair to the low-pressure area on the inside of the friction pair, thereby cooling and lubricating the friction pair and improving its lifespan. Another part of the flushing water flows from the outside of the friction pair along the gap between the front cover plate of the impeller 2 and the pump body 1 to the high-pressure area of ​​the pressure chamber, thereby preventing solid particles in the high-pressure area of ​​the pressure chamber from entering the gap between the front cover plate of the impeller 2 and the pump body 1, thus reducing wear between them. The first fitting gap between the stationary ring 5 and the guide sleeve 6 is 0.5-0.8 mm, which is smaller than the second fitting gap between the stationary ring 5 and the pump body 1. This allows most of the flushing water to enter the high-pressure area of ​​the pressure chamber, thereby reducing the amount entering the suction port and thus reducing the consumption of flushing water.

[0051] As shown in Figure 1 and Figure 2 , the material of the static ring 5 is bronze, and the material of the dynamic ring 4 is tungsten carbide hard alloy. Since the hardness of the dynamic ring 4 is much greater than that of the static ring 5, the wear rate of the dynamic ring 4 is much smaller than that of the static ring 5. After the static ring 5 is worn, it moves axially towards the dynamic ring 4 under the action of the flushing water pressure to compensate for the wear, thereby ensuring the contact of the friction pair, so that the sealing effect is almost not affected by wear. Since the static ring 5 can be designed to have a longer axial length, a longer service life can be obtained. Generally, the axial length of the static ring 5 can be 3-30 times the axial length of the dynamic ring 4. When it is less than 3 times, the service life of the static ring 5 is too short. When it is greater than 30 times, the axial length of the pump body 1 is too large, thereby making the manufacturing cost of the wear-resistant impurities pump in this embodiment too high.

[0052] In this embodiment, the axial length of the static ring 5 is 400 mm, and the axial length of the dynamic ring 4 is 22 mm, which is 18.2 times the former.

[0053] As shown in Figure 1 and Figure 2 , the end of the suction side of the pump body 1 is provided with an inlet flange 11, and the outer end surface of the guide sleeve 6 is flush with the end surface of the inlet flange 11. The guide sleeve 6 extends from the outside of the pump body 1 to the suction inlet of the impeller 2 in the suction direction of the impeller 2. In this way, the guide sleeve 6 can be fastened by the flange on the suction pipe matched with the inlet flange 11, so that the guide sleeve 6 obtains the maximum axial length, that is, the cost is saved, and the maintenance and assembly are facilitated.

[0054] As shown in Figure 1 and Figure 2 , the flushing water inlet 3 is close to the inlet flange 11 and away from the suction inlet of the impeller 2. The axial direction of the flushing water inlet 3 is perpendicular to the axial direction of the pump body 1, which is also to make the static ring 5 have a longer axial length.

[0055] Embodiment 2

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

[0057] As shown in Figure 1 , the static ring 5 is provided with 20 water holes 51 extending along the axial direction and penetrating the free end and the friction end of the static ring 5. In this way, flushing water can be injected into the friction surface between the dynamic ring 4 and the static ring 5 through the water holes 51, forming a structure similar to a static pressure thrust bearing, so that the lubrication condition of the friction surface is greatly improved, thereby further improving the service life of the friction pair.

[0058] In addition, a water guide groove 52 communicating with the water hole 51 is provided on the friction end face of the stationary ring 5, which can further improve the lubrication of the friction pair and thus improve the service life of the friction pair.

[0059] In addition, an anti-rotation structure is provided between the guide sleeve 6 and the stationary ring 5 to prevent relative rotation between them. The anti-rotation structure includes a pin 8 disposed on the guide sleeve 6; the axis of the pin 8 is parallel to the axis of the stationary ring cavity 7; and the stationary ring 5 has a keyway that mates with the pin 8. By providing the anti-rotation structure, rotation of the stationary ring 5 can be prevented from causing wear on the stationary ring 5 or the stationary ring cavity 7, thereby improving the lifespan of the guide sleeve 6 and the stationary ring 5.

[0060] Example 3

[0061] The main differences between this embodiment and Embodiment 2 are as follows:

[0062] like Figure 2 As shown, a sealing ring 9 is provided between the stationary ring 5 and the guide sleeve 6, which can reduce the flow rate of flushing water leaking to the suction port, thereby improving the efficiency of the wear-resistant impurity pump in this embodiment, and also reducing the consumption of flushing water. In addition, this is equivalent to adding a damping mechanism, thereby reducing the vibration amplitude of the stationary ring 5 and improving the life of the friction pair.

[0063] In addition, 20 spray holes 53 connected to the water inlet 51 are provided on the end face of the stationary ring 5 near its friction end. This can increase the leakage to the high-pressure area of ​​the pressure chamber, thereby reducing the amount of solid particles in the gap between the front cover plate of the impeller 2 and the pump body 1, and further improving the service life of the impeller 2 and the pump body 1.

[0064] Example 4

[0065] The main differences between this embodiment and Embodiment 2 are as follows:

[0066] like Figures 3-5 and Figures 6-8 As shown, the end face area of ​​the friction end of the stationary ring 5 (including the area of ​​the water hole 51, the water guide groove 52, and the water spray hole 53) is larger than the end face area of ​​the free end of the stationary ring 5 (including the area of ​​the water hole 51). This arrangement provides the following advantages:

[0067] For high-lift pump, because the pressure of its water pressure chamber is quite different from that of its suction port, the water pressure difference between the free end and the friction end of the static ring 5 is also quite large, which may cause the pressure between the friction surface of the static ring 5 and the dynamic ring 4 to be too large and thus shorten the service life of the friction pair; if the area of the friction end of the static ring 5 is larger than that of its free end, the resultant force of the pressure of the flushing water acting on the free end and the friction end of the static ring 5 after superposition will be reduced, which can reduce the unit area pressure between the friction pair and thus improve the service life of the friction pair.

[0068] Embodiment 5

[0069] The differences between this embodiment and Embodiment 4 are mainly as follows:

[0070] As shown in Figs. 1 and 2, the static ring 5 is arranged in the static ring cavity 7 of the pump body 1, and the free end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the dynamic ring 4, and the friction end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the guide sleeve 6. Figure 9 and Figure 10 As shown in Figs. 1 and 2, the static ring 5 is arranged in the static ring cavity 7 of the pump body 1, and the free end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the dynamic ring 4, and the friction end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the guide sleeve 6.

[0071] In addition, through the above arrangement, the following advantages are also achieved:

[0072] When the flushing water is injected into the friction end of the static ring 5 through the water inlet hole 51 of the static ring 5, the water pressure of the friction end of the static ring 5 is in a fluctuating state, and when the flushing water pushes the static ring 5 to move axially in the direction of the dynamic ring 4, the water inlet hole 51 or the water guide groove 52 of the friction end of the static ring 5 will be blocked, so that the pressure of the flushing water at the friction end of the static ring 5 will naturally rise, thereby preventing the static ring 5 from moving in the direction of the dynamic ring 4, and the forces in the two directions will balance at a certain position, but due to the inertia of the static ring 5 and the water, the static ring 5 cannot stably stay at the balance point, but vibrates around the balance point; if the vibration amplitude is large, the wear of the friction pair may be accelerated, thereby increasing the consumption of flushing water; by arranging a plurality of elastic members (springs 10) on the free end side of the static ring 5, it is equivalent to adding a damping mechanism, thereby reducing the vibration amplitude of the static ring 5 and thus improving the service life of the friction pair, thereby reducing the consumption of flushing water. In addition, a sealing ring 9 can also be arranged between the static ring 5 and the static ring cavity 7 or the guide sleeve 6, which can also have a similar effect; in this embodiment, since the sealing force of the friction pair is not entirely dependent on the elastic force of the spring 10, the linear elastic force of the spring 10 can be designed differently from that of the prior art, which can be more conducive to improving the service life of the friction pair.

[0073] As shown in Figs. 1 and 2, the static ring 5 is arranged in the static ring cavity 7 of the pump body 1, and the free end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the dynamic ring 4, and the friction end of the static ring 5 is arranged in the static ring cavity 7 and is in contact with the guide sleeve 6. Figure 11 and Figure 12As shown, the pump body 1 is composed of two parts: a front pump body 102 and a rear pump body 101. This allows for the replacement of different parts based on their wear condition during maintenance, thereby reducing maintenance costs.

[0074] Example 6

[0075] The main differences between this embodiment and Embodiment 5 are as follows:

[0076] like Figure 11 and Figure 12 Figure 13 Figure 14 As shown, the pump body 1 is also divided into a front pump body 102 and a rear pump body 101, but the division parts are different. However, different parts can be replaced according to the wear condition of the pump body 1 to reduce operating costs.

[0077] In addition, the impeller 2 in this embodiment is made of high-chromium wear-resistant alloy, and the moving ring 4 is directly machined from the blank of the impeller 2, which can reduce manufacturing costs; at this time, the axial thickness of the moving ring 4 is the same as the thickness of the front cover plate of the impeller 2 corresponding to the stationary ring 5.

[0078] In this embodiment, the axial length of the stationary ring 5 is 220mm, and the axial length of the moving ring 4 is 35mm, the former being 6.3 times that of the latter.

[0079] In this embodiment, the stationary ring 5 is made of two materials: the free end is made of aluminum alloy and the friction end is made of bronze. This structure can reduce the manufacturing cost and inertia of the stationary ring 5.

[0080] Example 7

[0081] In this embodiment, the pump body 1 is provided with a space to accommodate the impeller 2 and the guide sleeve 6, which can be combined with the guide sleeve 6 to form a stationary ring cavity 7 to accommodate the stationary ring 5. The guide sleeve 6 and the stationary ring 5 can be installed into the pump body 1 along the suction direction of the impeller 2. The positioning stop, which is coaxial with the axial direction of the pump body 1, can cooperate with the positioning flange 61 provided on the guide sleeve 6 to position the guide sleeve 6. The medium enters the suction port of the impeller 2 from the outside along the axial direction of the pump body 1 through the radial inner side of the guide sleeve 6.

[0082] In addition, the pump body 1 is provided with a flushing water inlet 3 to communicate with the stationary ring cavity 7, and an inlet flange 11 is provided on the suction side end of the pump body 1; the outer end face of the guide sleeve 6 is flush with the end face of the inlet flange 11; the flushing water inlet 3 is close to the inlet flange 11, away from the impeller suction port, and its axial direction is perpendicular to the axial direction of the pump body 1.

[0083] The above is the preferred embodiment of the present application, but the embodiment of the present application is not limited by the above, any change, modification, replacement, combination, simplification made without departing from the spirit and principles of the present application should be an equivalent replacement method, and all are included in the protection scope of the present application.

Claims

1. A pump for abrasive slurries, characterized in that, The sealing device 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; a radial outer side of the guide sleeve and the pump body form a static ring cavity for accommodating the static ring; medium enters an impeller suction inlet of the impeller through a radial inner side of the guide sleeve; an end of the static ring away from the impeller is a free end, and an end of the static ring capable of contacting the dynamic ring is a friction end; the static ring is movable along an axial direction of the guide sleeve; the static ring cavity is connected to a flushing water inlet.

2. The wear particulate pump of claim 1, wherein, The guide sleeve is mounted on the pump body and is capable of being mounted into the pump body along a suction direction of the impeller; the static ring is capable of being mounted into the pump body along the suction direction of the impeller.

3. The wear particulate pump of claim 1, wherein, The guide sleeve extends from an outer side end surface of the pump body to a suction inlet of the impeller; the guide sleeve is provided with a positioning flange arranged at an end of the guide sleeve away from the impeller; the pump body is provided with a positioning stopper at a position corresponding to the positioning flange; the positioning stopper and the pump body are coaxially arranged; an outer diameter of the positioning flange is greater than an outer diameter of the static ring.

4. The wear particulate pump of claim 3, wherein, The flushing water inlet is arranged at an end of the static ring cavity away from the impeller and close to the positioning flange.

5. The wear particulate pump of claim 1, wherein, A first matching gap exists between the guide sleeve and the static ring, and a second matching gap exists between the static ring and the pump body; a size of the first matching gap is smaller than a size of the second matching gap.

6. The wear particulate pump of claim 1, wherein, A sealing element is arranged between the guide sleeve and the static ring, and the sealing element is a sealing ring.

7. The wear debris tolerant pump of any of claims 1-6, wherein, The sealing device further comprises an anti-rotation structure for preventing relative rotation between the guide sleeve and the static ring; the anti-rotation structure comprises a pin arranged on the guide sleeve; an axial direction of the pin is parallel to an axial direction of the static ring cavity; the static ring is provided with a key groove matched with the pin.

8. The wear debris tolerant pump of any of claims 1-6, wherein, The sealing device further comprises an elastic element for driving the static ring to move towards the dynamic ring; one end of the elastic element acts on the static ring, and the other end of the elastic element acts on the guide sleeve; when the guide sleeve is removed, the elastic element is taken out from the pump body in a direction opposite to the suction direction of the impeller.

9. The wear-debris tolerant pump of any of claims 1-6, wherein, An axial length of the static ring is 3-20 times an axial length of the dynamic ring, and a hardness of the static ring is smaller than a hardness of the dynamic ring.

10. The wear debris tolerant pump of any of claims 1-6, wherein, An inlet flange is arranged on an end of the pump body outside a suction inlet; an outer side end surface of the guide sleeve is flush with an end surface of the inlet flange; the flushing water inlet is close to the inlet flange, and an axial direction of the flushing water inlet is perpendicular to an axial direction of the pump body.

11. The wear debris tolerant pump of any of claims 1-6, wherein, The static ring is provided with a plurality of water holes extending from the free end of the static ring to the friction end of the static ring and a water guide groove arranged at the friction end of the static ring and communicated with the water holes, wherein the water guide groove is annular; an outer side of the friction end of the static ring is provided with a plurality of water injection holes.

12. A pump body for the wear-resistant impurity pump of claim 1.

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