Efficient double-suction pump

Abstract

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

Description

TECHNICAL FIELD

[0001] The utility model belongs to centrifugal pump manufacturing field, concretely relates to a high -efficient double -suction pump. BACKGROUND

[0002] Centrifugal pump is the most common fluid conveying equipment, when working, the impeller rotates and absorbs medium from the suction inlet, the blade does work to the medium, thereby accelerating and sending the medium into the pressure chamber. Double-suction pump is equivalent to two centrifugal impellers arranged back-to-back, so the axial force of the impeller during work is almost completely offset, and the stress condition of the bearing and main shaft is very good, so it is widely used.

[0003] When the centrifugal pump works, the water pressure in the pressure chamber is higher than the pressure at the suction inlet, so the medium in the pressure chamber will leak to the suction inlet through the gap between the impeller and the pump body, which is called internal leakage. Internal leakage can reduce the working efficiency of the pump. In order to improve the efficiency, many double-suction pumps are designed with sealing rings to reduce internal leakage. Since the sealing ring and the impeller are gap-fitted, the gap size is limited by machining accuracy, mechanical operation accuracy and other factors, which also leads to internal leakage becoming an important factor limiting the improvement of the working efficiency of the centrifugal pump.

[0004] 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 structure", and the invention patent application with the application publication number CN116696784 A discloses "a mud 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 presses the sealing ring by the spring and blocks the leakage of the medium from the high-pressure area of the pressure chamber to the low-pressure area of the suction inlet by the friction pair. The above structure can indeed solve the internal leakage problem of the blade pump in theory, but in actual operation, the size of the spring force is difficult to control, and the service life of the friction pair is greatly affected by the spring force. When the spring force is large, the service 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 lead to the sealing effect not meeting the expectation. Secondly, the spring force changes constantly with the continuous wear of the friction pair, which leads to a great change in the friction force and the sealing effect when the friction pair is worn to a certain extent, so that the sealing failure is likely to occur due to wear. At the same time, due to the short service life of the friction pair, it needs to be replaced and maintained regularly, and the structure of the above scheme is complex and needs to be disassembled for replacement and maintenance, which is very inconvenient. Therefore, the above technical solutions have not been popularized due to the above problems in industrial application. UTILITY MODEL CONTENT

[0005] The utility model discloses in order to overcome the deficiency that present technique exists, provide a kind of efficient double-suction pump, the efficient double-suction pump can significantly reduce medium leakage, and sealing effect is better, the service life of sealing structure is longer, and it is more convenient to maintain.

[0006] The technical scheme for solving the above technical problems of the utility model is:

[0007] An efficient double-suction pump, including lower pump body, upper pump body, be set in the impeller between the lower pump body and the upper pump body and be set in the impeller suction inlet both sides of the sealing device of the impeller, wherein, the sealing device includes dynamic ring, static ring and guide sleeve;The dynamic ring is installed on the front cover plate of the impeller;The static ring can be moved along the axis direction of the guide sleeve and make its one end and the dynamic ring contact;The one end of the static ring away from the impeller is free end, and the one end of the static ring and the dynamic ring contact is friction end;The radial outer side of the guide sleeve and the corresponding parts of the lower pump body, the upper pump body form the static ring cavity for accommodating the static ring;The radial inner side of the guide sleeve constitutes the passage of medium flow to the impeller suction inlet.

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

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

[0010] More preferably, the upper pump body and the lower pump body are provided with an axial protrusion on the axial outer side of the positioning flange of the guide sleeve.

[0011] More preferably, the cooperation gap between the guide sleeve and the static ring is smaller than the cooperation gap between the static ring and the lower pump body and the static ring and the upper pump body.

[0012] More preferably, a channel or pipeline is connected to the lower pump body or the upper pump body, one end of the channel or pipeline communicates with the high-pressure area of the water chamber or the pump outlet, and the other end communicates with the static ring cavity;The water outlet of the channel or pipeline communicating with the static ring cavity is provided at the end of the static ring cavity away from the impeller.

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

[0014] More preferably, a water hole extending in the axial direction of the static ring is provided on the static ring, the water hole penetrates the friction end of the static ring from the free end of the static ring;A water groove communicating with the water hole is provided at the friction end of the static ring, and the water groove is annular.

[0015] More 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 pin is arranged in parallel with the axis of the static ring cavity; the static ring is provided with a key groove matched with the pin.

[0016] More 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 acts on the static ring, and the other end acts on the guide sleeve.

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

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

[0019] Compared with the prior art, the high-efficiency double-suction pump has the following advantages and beneficial effects:

[0020] The high-efficiency double-suction pump can utilize the limited axial space at the suction inlet to make the static ring have a larger length; the guide sleeve can make the friction surface of the static ring and the friction surface of the dynamic ring have higher coaxiality and parallelism, which is conducive to reducing the leakage and wear of the friction pair composed of the static ring and the dynamic ring; at the same time, when the static ring is worn, the static ring can move along the axis of the guide sleeve to compensate for the wear; in addition, the longer length of the static ring is not only conducive to prolonging the service life of the static ring, but also conducive to prolonging the maintenance cycle; the radial inner side of the guide sleeve constitutes a channel for the medium flowing to the impeller suction inlet, so that the diameter of the static ring can be reduced as much as possible under the premise of meeting the cavitation performance, thereby reducing the linear speed of the friction pair and reducing the wear. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 is a sectional view of the first specific embodiment of the high-efficiency double-suction pump of the utility model.

[0022] Figure 2 is Figure 1 is a partial sectional view at A.

[0023] Figure 3 is a sectional view of the second specific embodiment of the high-efficiency double-suction pump of the utility model.

[0024] Figure 4 is Figure 3 is a partial view at B.

[0025] Figure 5 is a sectional view of the static ring.

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

[0027] Figure 7 is Figure 6 a partial view at C.

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

[0029] Figure 9 is Figure 8 a partial view at D.

[0030] Figure 10 is a sectional view of a fifth embodiment of the high-efficiency double-suction pump of the present application.

[0031] Figure 11 is Figure 10 a partial view at E.

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

[0033] The present application will be further described in conjunction with the embodiments and the accompanying drawings, but the embodiments of the present application are not limited thereto.

[0034] Example 1

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

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

[0037] As shown in the drawings, Figures 1-2 The guide sleeve 5 extends outward from the impeller suction inlet of the impeller 3 to the spiral water suction chamber, and the upper pump body 1 and the lower pump body 2 are provided with an axial protrusion 13 on the axial outside of the positioning flange 501 of the guide sleeve 5; in this way, the guide sleeve 5 can obtain a longer axial dimension without affecting the cavitation performance of the pump or with a smaller influence on the cavitation performance, so that the static ring 7 has a longer axial length, and the coaxiality and parallelism of the static ring 7 relative to the dynamic ring 8 are higher, so that the leakage of the friction pair is smaller, and the service life of the static ring 7 is longer.

[0038] Since the pressure difference between the static ring cavity 6 and the medium outside the friction pair is small, the high-pressure medium entering the static ring cavity 6 flows to the radial outside of the friction pair, which hardly affects the working efficiency of the pump; while the static ring cavity 6 and the radial inside of the friction pair have a higher pressure difference, and the leakage has a great influence on the working efficiency of the pump, so the matching gap between the guide sleeve 5 and the static ring 7 needs to be designed to be smaller, i.e. 0.2-0.3mm, so as to reduce the leakage between them as much as possible; the matching gap between the static ring 7 and the lower pump body 2 and the upper pump body 1 is 3-4mm, which is obviously larger than the former, so that the manufacturing cost can be reduced, and the probability of the static ring 7 being stuck can be reduced.

[0039] As shown in the drawings, Figures 1-2 The upper pump body 1 is connected with a high-pressure water pipe 4, one end of the high-pressure water pipe 4 communicates with the high-pressure area of the water chamber, and the other end communicates with the static ring cavity 6; wherein the water inlet 10 of the pipeline communicating with the static ring cavity 6 is arranged at the end of the static ring cavity 6 away from the impeller 3, so that the static ring 7 has a longer axial length and a longer service life.

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

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

[0042] As shown in Figures 1-2 The working principle of the high-efficiency double-suction pump of this embodiment is as follows:

[0043] When the high-efficiency double-suction pump of this embodiment is running, the water pressure chamber forms a high-pressure area, and the high-pressure water in the high-pressure area of the water pressure chamber of the upper pump body 1 enters the static ring cavity 6 through the high-pressure water pipe 4 and the water inlet 10, and acts on the free end of the static ring 7, thereby pushing the static ring 7 to move along the axis direction of the guide sleeve 5 to the dynamic ring 8; after the static ring 7 and the dynamic ring 8 contact, the channel for leaking the medium from the high-pressure area to the low-pressure area at the suction inlet is blocked, thereby achieving sealing; in this process, since the outside of the contact surface between the static ring 7 and the dynamic ring 8 has a high pressure and the inside has a low pressure, and at the same time, the static ring 7 and the dynamic ring 8 will have relative rotational motion, therefore, the medium will seep from the outside to the inside of the contact surface between the static ring 7 and the dynamic ring 8, thereby cooling and lubricating the friction surface between the static ring 7 and the dynamic ring 8, and further making the high-efficiency double-suction pump of this embodiment have a higher efficiency, and at the same time, the static ring 7 and the dynamic ring 8 also obtain a longer service life.

[0044] Embodiment 2

[0045] This embodiment is basically the same as Embodiment 1, and the main difference is as follows:

[0046] As shown in Figures 3-4As shown, the static ring 7 is provided with 20 water holes 701 for connecting the friction end and the free end of the static ring 7, the water holes 701 extend along the axial direction of the static ring 7; the friction end of the static ring 7 is provided with a water groove 702 connected with the water holes 701; by providing several water holes 701 on the static ring 7 for connecting the friction end and the free end, the high-pressure medium can be injected through the water holes 701 at the friction surface between the dynamic ring 8 and the static ring 7, thereby forming a structure similar to a static pressure thrust bearing, so that the lubrication condition at the friction surface is greatly improved, and the service life of the friction pair can be further improved.

[0047] As shown in the figure, the static ring 7 is provided with a water groove 702 connected with the water hole 701 on the friction end of the static ring 7, which can further improve the lubrication condition of the friction pair, thereby improving the service life of the friction pair. Figures 3-4

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

[0049] As shown in the figure, the working principle of the high-efficiency double-suction pump of the present embodiment is: Figures 3-4

[0050] In the working process of the high-efficiency double-suction pump of the present embodiment, the high-pressure medium from the high-pressure area of the water chamber enters the static ring cavity 6 through the high-pressure water pipe 4 and the water inlet 10, and then enters the water groove 702 through the water hole 701 in the static ring 7. Since the water pressure at the static ring cavity 6 is higher than that at the friction pair, the water pressure will push the static ring 7 and the dynamic ring 8 to contact to achieve sealing. When the friction end of the static ring 7 contacts the dynamic ring 8, the water pressure at the water groove 702 increases, which pushes the static ring 7 away from the dynamic ring 8, so that the high-pressure medium leaks to the suction port, which in turn causes the water pressure at the water groove 702 to decrease, so that the water pressure at the static ring cavity 6 is higher than that at the friction pair, and the pressure will again push the static ring 7 and the dynamic ring 8 to contact to achieve sealing. This is equivalent to promoting the dynamic floating of the static ring 7 under the action of the water pressure at both ends, so that the leakage of the friction pair can be kept appropriate, and the cooling and lubrication requirements of the friction pair can be met at the same time.

[0051] Embodiment 3

[0052] This embodiment is basically the same as embodiment 2, the main difference is:

[0053] As shown in the figure, the working principle of the high-efficiency double-suction pump of the present embodiment is: Figure 6 and Figure 7 ​​As shown in the figure, the guide sleeve 5 and the static ring 7 are provided with an anti-rotation structure for preventing relative rotation between the guide sleeve 5 and the static ring 7; the anti-rotation structure comprises a pin 9 provided on the guide sleeve 5; the axis direction of the pin 9 is parallel to the axis direction of the static ring cavity 6; the static ring 7 is provided with a key groove matched with the pin 9. By providing the anti-rotation structure, the static ring 7 can be prevented from rotating around the axis direction of the impeller 3 to wear the static ring 7 and the guide sleeve 5.

[0054] As shown in the figure, Figure 6 and Figure 7 As shown in the figure, the guide sleeve 5 and the static ring 7 are provided with a sealing ring 14, which is installed on the guide sleeve 5; by the above-mentioned arrangement, the leakage flow of the high-pressure medium from the cooperation gap between the guide sleeve 5 and the static ring 7 to the suction port can be reduced, thereby improving the working efficiency of the double-suction pump of the embodiment; in addition, since the sealing ring 14 has resistance to the axial movement of the static ring 7, the sealing ring 14 is equivalent to a damping mechanism, which can reduce the vibration amplitude of the static ring 7, thereby reducing the leakage amount, so as to prolong the service life of the friction pair.

[0055] Embodiment 4

[0056] The embodiment is basically the same as embodiment 2, and the main difference is as follows:

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

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

[0059] In addition, the free end surface of the static ring 7 and the guide sleeve 5 are provided with an elastic member, and the elastic force of the elastic member urges the friction end surface of the static ring 7 to abut against the dynamic ring 8, wherein the elastic member is a spring 11. By providing the spring 11, the following effects can be achieved:

[0060] When the high-pressure medium is injected into the friction end of the stationary ring 7 through the water hole 701, the water pressure at the friction end of the stationary ring 7 is fluctuating. When the high-pressure medium pushes the stationary ring 7 to move axially towards the moving ring 8, it will cause the water hole 701 or water groove 702 at the friction end of the stationary ring 7 to be blocked. The pressure of the high-pressure medium at the friction end of the stationary ring 7 will naturally rise, thereby preventing the stationary ring 7 from moving towards the moving ring 8. The forces in the two directions will reach equilibrium at a certain position. However, since both the stationary ring 7 and the high-pressure medium have inertia, the stationary ring 7 cannot be stably positioned 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 the high-pressure medium. Therefore, several elastic elements are provided on the free end side of the stationary ring 7, which is equivalent to adding a damping mechanism, thereby reducing the vibration amplitude of the stationary ring 7, thus improving the life of the friction pair and reducing the consumption of the high-pressure medium.

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

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

[0063] Example 5

[0064] This embodiment is largely the same as Embodiment 1, with the main differences being:

[0065] like Figure 10 and Figure 11 As shown, the high-efficiency double-suction pump in this embodiment does not have an external high-pressure water pipe, but instead has a hidden water channel 12 connecting the high-pressure zone of the pressure chamber and the stationary ring cavity 6. When the high-efficiency double-suction pump in this embodiment is working, the high-pressure water in the high-pressure zone of the pressure chamber enters the stationary ring cavity 6 through the hidden water channel 12. Since the water pressure at the free end of the stationary ring 7 is higher than the water pressure at the friction end, the stationary ring 7 moves towards the impeller 3 under the action of water pressure, so that its friction end contacts the moving ring 8 on the impeller 3 and achieves a seal.

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

[0067] 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 high-efficiency double suction pump characterized in that, 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; the static ring can move along the axial direction of the guide sleeve and makes one end thereof contact with the dynamic ring; one end of the static ring away from the impeller is a free end, and the other end contacting with the dynamic ring is a friction end; the radial outer side of the guide sleeve and the corresponding parts of the lower pump body and the upper pump body constitute a static ring cavity for accommodating the static ring; the radial inner side of the guide sleeve constitutes a channel for the medium to flow to the suction inlet of the impeller.

2. The high-efficiency double suction pump of claim 1, wherein, The guide sleeve is provided with a radially protruding positioning flange on the side away from the impeller, and the lower pump body and the upper pump body are each provided with a positioning stop opening for cooperating with the positioning flange.

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

4. The high-efficiency double suction pump of claim 1, wherein, The guide sleeve extends outwardly from the suction inlet of the impeller to a spiral water suction chamber.

5. The high-efficiency double suction pump of claim 1, wherein, The cooperation gap between the guide sleeve and the static ring is smaller than the cooperation gaps between the static ring and the lower pump body and between the static ring and the upper pump body.

6. The high-efficiency double suction pump of any one of claims 1-3, wherein, The lower pump body or the upper pump body is connected with a channel or a pipeline, one end of the channel or the pipeline communicates with the high-pressure area of the water chamber or the pump outlet, and the other end communicates with the static ring cavity; the water outlet of the channel or the pipeline communicating with the static ring cavity is arranged at the end of the static ring cavity away from the impeller.

7. The high-efficiency double suction pump of any one of claims 1-3, wherein, A sealing element is arranged between the guide sleeve and the static ring.

8. The high-efficiency double suction pump of any one of claims 1-3, 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; the axial direction of the pin is parallel to the axial direction of the static ring cavity; the static ring is provided with a key groove cooperating with the pin.

9. The high-efficiency double suction pump of any one of claims 1-3, 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 acts on the guide sleeve.

10. The high-efficiency double suction pump of any one of claims 1-3, wherein, The axial length of the static ring is 2-8 times the axial length of the dynamic ring, and the hardness of the static ring is smaller than the hardness of the dynamic ring.

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

Images