WO2016179929A1

WO2016179929A1 - Spiral flow constant pressure pump

Info

Publication number: WO2016179929A1
Application number: PCT/CN2015/088551
Authority: WO
Inventors: 李世煌; 刘宗安
Original assignee: 山东昊安金科新材料股份有限公司
Priority date: 2015-05-13
Filing date: 2015-08-31
Publication date: 2016-11-17
Also published as: CN104895842A

Abstract

Disclosed is a spiral flow constant pressure pump, comprising a pump rear cover (1), a pump body (2), an impeller (3), a bearing body (4) and a pump shaft (5). The impeller (3) comprises a rear covering plate (301) having one side thereof provided with back blades (305), and the other side thereof provided with long blades (303) and short blades (304) which are evenly arranged in an intersected manner, wherein the long blades (303) and the short blades (304) curve in the same direction. The long blades (303) and the short blades (304) respectively form a respective gyration centre. The inner opening diameter of the common gyration centre of the short blades (304) is greater than that of the common gyration centre of the long blades (303). The spiral flow constant pressure pump is used for liquid transmission, and has a constant liquid output pressure and a stable flow, and the friction caused by the pressure from a mechanical seal is small.

Description

Spiral flow constant pressure pump

Technical field

[0001] The present invention relates to a constant pressure pump, and more particularly to a spiral flow constant pressure pump.

Background technique

[0002] The Chinese invention patent with the authorization number CN101294580B discloses a spiral flow constant pressure pump including a pump body, a pump casing, a pump shaft, an impeller and a motor, and the design is for a high viscosity high concentration liquid. In the case where the flow stability is high, the adaptability is poor, and the slurry pressure is small, the flow rate is not stable, the vibration of the body is large, and the service life is short. Due to the high concentration of the liquid in the industrial heavy pulp pump, the large particles have high requirements on the wear resistance and corrosion resistance of the pump body, and the higher performance requirements are imposed on the pump high lift, large flow and constant pressure.

[0003] Some existing fire-fighting pumps are used to increase the outlet pressure, and the lifting stroke is completed by a multi-stage centrifugal combination, and the axial force and the radial force cannot be balanced, the vibration is large and the noise is large, the mechanical seal is worn and the sealing performance is poor. Easy to leak, easy to relieve pressure, can only rely on frequency control device or gear speed increase box to increase the speed to increase the pressure, and the pressure is unstable, large volume, high failure rate. As the pressure increases, the flow rate decreases, and the flow-lift curve is flat and unstable. The existing foreign fire pump two-stage centrifugal pump has a combined head of only 300m and a flow rate of 90m3/h. It belongs to the medium and low-pressure fire pump and can not meet the needs of today's fire emergency rescue. As China's urbanization process accelerates, buildings become more and more dense and taller, and the fire situation becomes more and more complicated. The high-level fire protection technology can't keep up with the rising speed of high-rise buildings. High-rise fire protection has become a problem that plagues urban fire safety. The problem is that there is a need for a high pressure and constant pressure, large flow and stability, small size, light weight, low clogging failure, no frequency conversion device or gear speed increase box, low cost, convenient operation, suitable for various fire conditions. Medium and high pressure fire pumps that meet the requirements of various working environments.

technical problem

[0004] The present invention is to solve the problem that the existing spiral flow constant pressure pump has short friction life, poor adaptability to high-concentration and high-viscosity heavy slurry liquid, small discharge pressure is not constant, flow rate is small, and vibration is large and large. Technical problems such as overheating of the bearing body and large temperature difference between the two ends, providing a long friction, good adaptability to heavy slurry liquids such as high concentration and high viscosity, large and constant outlet pressure, and large flow rate Stable and effective A spiral flow constant pressure pump that balances axial and radial forces, small vibrations, and low failure rates.

Problem solution

Technical solution

[0005] The present invention provides a spiral flow constant pressure pump, which is provided with a pump back cover, a pump body, an impeller, a bearing body and a pump shaft. The pump back cover is disposed on the rear side of the pump body and is fixedly connected with the pump body. The back cover and the pump body together form a pump chamber; the pump shaft extends into the pump chamber, the impeller is arranged at the front end of the pump shaft of the pump chamber; a chamber is arranged between the pump back cover and the pump shaft, and a mechanical seal is arranged in the chamber; Connected to the pump body, the pump shaft is supported on the bearing body by double-rolling bearings at both ends; the impeller is provided with a rear cover plate, the rear cover plate is provided with two sides, one side is provided with a back blade, and the other side is uniformly distributed. The blade and the short blade, the long blade and the short blade are cross-distributed, and the long blade and the short blade are both provided with the same direction of bending, and the long blade and the short blade are collectively formed around the respective rotation center, and the diameter of the inner diameter of the common rotation center of the short blade It is larger than the inner diameter of the center of rotation of the common long blades.

[0006] Preferably, the pump back cover is provided with a self-cooling passage in the high pressure zone and a self-cooling passage in the low pressure zone, both of which communicate with the chamber and also communicate with the pump chamber. The self-cooling channel is inclined at an angle of 71° in the high-pressure zone, and the self-cooling channel is inclined at an angle of 64° in the low-pressure zone.

Preferably, the pump back cover is provided with a high pressure zone outer cooling channel and a low pressure zone outer cooling channel, both of which communicate with the chamber. The cooling channel outside the high pressure zone has an inclination angle of 15° or 90°, and the outer cooling channel of the low pressure zone has an inclination angle of 15° or 90°.

[0008] Preferably, the pump body is composed of a front end portion of the pump body having a radius R, a rear end portion of the pump body, and a middle portion of the pump body having a radius R1, and a radius R of the front end portion of the pump body is larger than a radius R1 of the middle portion of the pump body.

[0009] Preferably, the long blade and the short blade are perpendicularly intersected with the rear cover plate, and the common internal rotation angle of the long blade is 8°~12° or 55°.

[0010] Preferably, the front end of the long blade and the short blade are free edges, and the rear end is bent, and the angle of bending is inwardly inclined from the free side by 2° to 6°.

[0011] Preferably, the long blade and the short blade form an inlet angle of 20° to 40°.

[0012] Preferably, the long blade and the short blade are respectively bent at an angle of 20° to 40 in the direction of the tangential direction along the outer edge of the rear cover. .

[0013] Preferably, the root blade and the short blade are bent at a root outlet angle of 100° to 130°.

[0014] Preferably, both the long blade and the short blade intersect perpendicularly with the rear cover plate, and the common blade has a center angle of rotation The degree is 10°; the front end of the long blade and the short blade is a free edge, the rear end is a bend, and the angle of the bend is 4° inclined inward than the free edge; the entrance angle formed by the long blade and the short blade is 30°; The blade and the short blade are bent at an angle of 30° in the direction of the tangential direction along the outer edge of the rear cover, respectively; the root outlet angle of the long blade and the short blade is 110° after bending.

Advantageous effects of the invention

Beneficial effect

[0015] Compared with the prior art, the present invention has the following advantages and quality effects:

[0016] (1) The three parts of the inner wall of the pump rotate along the center of the pump body to form a smooth pump inner wall, which guides the impeller to increase the space, increases the amount of suction liquid, and reduces the flow of the liquid to the blade and the rear cover. The friction is provided; the invention is equipped with a mechanical seal and has an internal cooling passage from the high pressure zone to the low pressure zone, the cooling passage of the high pressure zone is inclined at an angle of 71°, and the cooling passage of the low pressure zone is inclined by 64°, and is mechanically sealed by its own hydraulic pressure. Cooling the same pressure, or using an external cooling channel from the high pressure zone to the low pressure zone, the cooling channel of the high pressure zone is inclined at 15° or 90°, and the cooling channel of the low pressure zone is inclined by 15° or 90°. The mechanical seal is cooled to equalize the equilibrium pressure. Both of the above cooling methods can reduce the friction caused by the pressure of the mechanical seal and ensure the mechanical seal is durable.

[0017] (2) precise setting of each angle, the rotary liquid flow formed in the pump chamber is squeezed and raised multiple times in the space between the long and short blades, so that the pressure at the liquid outlet is higher, and the viscosity is high, and the concentration is high. The heavy pulp liquid has better adaptability and is suitable for all pumps with a head of 0~500m.

[0018] (3) The uniform back blade is integrally formed with the rear end cover at the rear side of the rear end cover. When the pressure in the pump chamber is too high, the liquid flow enters the space of the back blade to form another longitudinal flow in the direction of the pump back cover. Balance the pump body pressure to keep the pressure in the pump chamber constant, so that the flow rate remains stable and the work is smoother.

[0019] (4) The bearing body adopts double-bearing structure with double bearings at both ends, and the bearing is supported on the bearing body through the double-rolling bearing at both ends, effectively balancing the axial force and the radial force, and balancing the axial force to make the spiral flow constant pressure pump The work is more stable, and the balanced radial force can avoid excessive heat generation in the spiral flow constant pressure pump bearing body, achieve the balance of rotation, low failure rate, and improve liquid transmission efficiency.

[0020] (5) The invention also has the advantages of small vibration and small volume.

Brief description of the drawing

DRAWINGS 1 is a schematic structural view of Embodiment 1 of the present invention;

2 is a schematic structural view of a pump back cover according to Embodiment 1 of the present invention;

3 is a schematic structural view of a pump body of the present invention;

Figure 4 is a left side elevational view of the impeller of the present invention;

5 is a schematic structural view of an impeller of the present invention;

Figure 6 is a right side view of the impeller of the present invention;

Figure 7 is a schematic view showing the assembly of the bearing body of the present invention;

8 is a schematic structural view of Embodiment 2 of the present invention;

9 is a schematic structural view of a pump cover according to Embodiment 2 of the present invention.

[0030] The symbol in the figure illustrates:

[0031] 1. Pump back cover; 2. Pump body; 3. Impeller; 4. Bearing body; 5. Pump shaft; 6. Bearing; 7. Bearing end cover; 8. Seal ring; 101. Mechanical seal; Self-cooling channel in high pressure zone; 103. Self-cooling channel in low pressure zone; 104. Outer cooling channel in high pressure zone; 105. Outer cooling channel in low pressure zone; 201. Front end part of pump body; 202. Rear end part of pump body; Middle part; 204. Inlet port; 205. Outlet port; 301. Rear cover; 302. Bend; 303. Long blade; 304. Short blade; 305. Back blade.

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1

As shown in FIG. 1, the present invention is provided with a pump back cover 1, a pump body 2, an impeller 3, a bearing body 4, and a pump shaft 5. The pump rear cover 1 is disposed on the rear side of the pump body 2 and is fixedly coupled to the pump body 2, which together with the pump body 2 surrounds the pump chamber. The front end of the pump shaft 5 extends into the pump chamber, and the impeller 3 is screwed to the front end of the pump shaft 5 in the pump chamber by a reverse nut. A chamber is arranged between the pump back cover 1 and the pump shaft 5, and a mechanical seal is arranged in the chamber; the bearing body 4 is connected to the pump body 2 through a nut, and the rear end of the pump shaft 5 is supported on the bearing body 4 by double-rolling bearings at both ends. . The front end of the pump body 2 is provided with a horizontal liquid inlet 204, and the right side is provided with a vertical liquid outlet 205.

[0034] As shown in FIG. 2, 101 is a mechanical seal. The pump back cover 1 is provided with a self-cooling passage 102 in the high pressure region and a self-cooling passage 103 in the low pressure region, both of which communicate with the chamber in which the mechanical seal 101 is located, and also communicate with the pump chamber. The inclination angle of the self-cooling passage in the high pressure zone is 71°, and the inclination angle of the self-cooling passage in the low pressure zone is 64°. The spiral flow constant pressure pump of the present embodiment operates to cool the mechanical seal 101 by its own water pressure. Thus, the friction caused by the mechanical seal 101 is reduced, and the mechanical seal 101 is durable.

As shown in FIG. 3, the pump body front end portion 201 is not a conventional single arc inner wall but a multi-arc inner wall. The inner wall of the pump body 2 is composed of a pump body front end portion 201 (a circular arc portion having a radius R), a pump body rear end portion 202 (straight side portion), and a pump body center portion 203 having a radius R1 at the intersection thereof. The center of the body 2 rotates to form a smooth pump inner wall, which acts to guide the impeller 3 to increase the space and reduce the friction of the impeller 3. The radius R of the front end portion 201 of the pump body is larger than the radius R1 of the central portion 203 of the pump body.

[0036] As shown in FIG. 4, FIG. 5 and FIG. 6, the impeller 3 is provided with a rear cover plate 301, and one side of the rear cover plate 301 is provided with seven long blades 303 and seven short blades 304, long blades uniformly distributed. The 303 and the short blades 304 are distributed across each other, and the long blades 303 and the short blades 304 are each provided with a bend 302 in the same direction. The other side of the rear cover 301 is provided with 13 back blades 30 5 , and the height of the long blades 303 and the short blades 304 is higher than the height of the back blades 305. The number of long blades 303, short blades 304 and back blades 305 can be adjusted according to the actual number required.

[0037] The seven long blades 303 and the rear cover 301 are perpendicularly intersected, and the angle a of the liquid in the center of the rotation center of the seven long blades 303 is 10°; the seven short blades 304 also intersect the rear cover 301 vertically. The inner diameter of the common rotary center of the seven short blades 304 is larger than the diameter of the inner diameter of the common rotary center of the seven long blades 303. The front end of the long blade 303 and the short blade 304 is a free side, the rear end is a bend 302, and the angle b of the bend 302 inclined inward from the free side is 4°; the entrance angle c formed by the long blade 303 and the short blade 304 is 30 The long blade 303 and the short blade 30 4 are bent at an angle d of 30° in the direction of the circular tangential direction along the circular tangential edge of the rear cover 301, respectively. After the long blade 303 and the short blade 304 are bent, the root exit angle e is 110°.

[0038] As shown in FIG. 7, the pump shaft 5 is integrally formed with the bearing body 4 through the double-bearing bearings 6 at both ends, the bearing end 4 is provided with bearing end caps 7 at both ends thereof, and the bearing end cap 7 is provided with a sealing ring 8 therein. The structure is double-supported and double-sealed structure, which can effectively balance the axial force and the radial force to ensure the smooth rotation of the pump shaft and the impeller, and improve the liquid transportation efficiency.

[0039] The working process of the spiral flow constant pressure pump of the present invention will be further described below.

[0040] The liquid enters from the liquid inlet 204. Since the present invention uses the evenly distributed long blades 303 and short blades 304 provided with the bend 302 at the rear end, the liquid pressure at the root of the impeller 3 is greater than the free edge pressure at the front end of the impeller 3. The liquid creates a longitudinal flow from the inside to the outside, further following the rotation of the blade to produce a swirling flow. Due to the uniform length of the blades, the pump room has a larger space. After pumping a large amount of liquid flow, two different pressure differences are formed in the space between the long blades 303 and the short blades 304, and the liquid flow is continuously squeezed. Pressurize multiple times to form a spiral The flow is finally discharged from the liquid outlet 205.

[0041] The evenly distributed back blade 305 is formed integrally with the rear end cover 301 at the rear side of the rear end cover 301. When the pressure in the pump chamber is too high, the liquid flows into the space between the 13 back blades 305 to form another direction. The longitudinal flow in the direction of the pump back cover 1 can balance the pressure in the pump chamber and bring the pressure to a constant pressure.

Embodiments of the invention

Embodiment 2

[0043] This embodiment is mostly the same as Embodiment 1, except that the angle a of the liquid inlet of the common center of the rotation of the seven long blades 303 is 8°; the front end of the long blade 303 and the short blade 304 is The free edge, the back end is a bend 302, the angle b of the bend 302 inclined inwardly from the free edge is 2°; the entrance angle c formed by the long blade 303 and the short blade 304 is 20°; the long blade 303 and the short blade 304 respectively The angle d of the circular tangent edge along the rear cover plate 301 is 20° in the direction of the reverse needle. The long blade 303 and the short blade 304 are bent after the root exit angle e is 100°

[0044] The pump back cover 1 of the embodiment is provided with a high pressure zone outer cooling channel 104 and a low pressure zone outer cooling channel 105, as shown in FIGS. 8 and 9, both of which are adjacent to the cavity between the pump back cover 1 and the pump shaft 5. The room is connected. The outer cooling passage 104 of the high pressure zone has an inclination angle of 15° or 90°, and the outer cooling passage 105 of the low pressure zone has an inclination angle of 15° or 90°. The spiral flow constant pressure pump of the present embodiment operates to cool the mechanical seal 101 by the external cooling water, thereby reducing the friction caused by the mechanical seal 101 and ensuring the durability of the mechanical seal 101.

Embodiment 3

[0046] This embodiment is mostly the same as Embodiment 1, except that the angle a of the liquid inlet of the common center of the rotation of the 7 long blades 303 is 12°; the front end of the long blade 303 and the short blade 304 is The free side, the back end is a bend 302, the angle b of the bend 302 inclined inwardly from the free side is 6°; the entrance angle c formed by the long blade 303 and the short blade 304 is 40°; the long blade 303 and the short blade 304 respectively The angle d of the circular tangent edge along the rear cover plate 301 is 40° in the direction of the counterclockwise direction. The long blade 303 and the short blade 304 are bent after the root exit angle e is 130°

Embodiment 4

[0048] This embodiment is mostly the same as Embodiment 1, except that the angle a of the liquid inlet of the common center of the rotation of the seven long blades 303 is 55°; the front end of the long blade 303 and the short blade 304 is Free side, back end For the bend 302, the angle b of the bend 302 inclined inwardly from the free edge is 4°; the inlet angle c formed by the long blade 303 and the short blade 304 is 30°; the long blade 303 and the short blade 304 are respectively along the rear cover 301 The circular tangent edge has a bending angle d of 30° in the direction of the counterclockwise direction. After the long blade 303 and the short blade 304 are bent, the root exit angle e is 110°

[0049] In the embodiments 1 to 3, the angle a of the water inlet of the common center of the rotation of the 7 long blades 303 is 8 to 12°, and other angles are theoretical calculations by the unconventional technicians. In practice, it is more suitable for the transmission of heavy pulp liquids, and in Example 4, a is 55°, which is also the most suitable for fire pumps obtained by unconventional technicians after many theoretical calculations and practices. Good choice.

[0050] The above examples are preferred embodiments of the present invention in light of the above disclosure and teachings. Therefore, the present invention is not limited by the above-described embodiments, and any other changes, combinations, and modifications which are made without departing from the spirit and scope of the invention are equivalent to the alternatives and are included in the scope of the present invention. Inside

[0051]

Claims

Claim

A spiral flow constant pressure pump is provided with a pump back cover, a pump body, an impeller, a bearing body and a pump shaft, and the pump rear cover is disposed on a rear side of the pump body and is fixedly connected with the pump body. The pump back cover and the pump body together form a pump chamber; the pump shaft extends into the pump chamber, the impeller is disposed at a front end of the pump shaft of the pump chamber; the pump rear cover and the pump shaft a chamber is disposed between the chamber, and the chamber is provided with a mechanical seal; the bearing body is connected to the pump body, and the pump shaft is supported on the bearing body by double-rolling bearings at both ends; a rear cover plate, the rear cover plate is provided with two sides, and one side is provided with a back blade, wherein the other side of the rear cover plate is provided with uniformly distributed long blades and short blades, the long blades and the a short blade cross-distribution, wherein the long blade and the short blade are each provided with a bend in the same direction, and the long blade and the short blade both collectively form a respective center of rotation, and the short blade has a common center of rotation The port diameter is larger than the inner diameter of the center of rotation of the long blades.

A spiral flow constant pressure pump according to claim 1, wherein said pump back cover is provided with a self-cooling passage in a high pressure zone and a self-cooling passage in a low pressure zone, both of which communicate with said chamber

And communicating with the pump chamber; the inclination angle of the self-cooling passage in the high pressure region is 71°, and the inclination angle of the self-cooling passage in the low pressure region is 64°.

A spiral flow constant pressure pump according to claim 1, wherein said pump rear cover is provided with a high pressure zone outer cooling passage and a low pressure zone outer cooling passage, said high pressure zone outer cooling passage and said low pressure zone outer cooling passage. Both are in communication with the chamber; the outer cooling passage of the high pressure zone has an inclination angle of 15° or 90°, and the outer cooling passage of the low pressure zone has an inclination angle of 15° or 90°.

The spiral flow constant pressure pump according to claim 2 or 3, wherein the pump body is composed of a front end portion of a pump body having a radius R, a rear end portion of the pump body, and a middle portion of a pump body having a radius R1, the pump The radius R of the front end portion of the body is larger than the radius R1 of the middle portion of the pump body.

The spiral flow constant pressure pump according to claim 4, wherein the long blade and the short blade each intersect perpendicularly with the rear cover, and the angle of the inner opening of the common blade of the long blade is 8°. 12° or 55°.

The spiral flow constant pressure pump according to claim 5, wherein the front end of the long blade and the short blade are free edges, and the rear end is bent, and the bending is inclined inwardly than the free edge The oblique angle is 2°~6°.

[Claim 7] The spiral flow constant pressure pump according to claim 6, wherein the long blade and the short blade form an inlet angle of 20 to 40.

[Claim 8] The spiral flow constant pressure pump according to claim 7, wherein the long blade and the short blade are respectively bent at an angle of 20° in the direction of the tangential direction along the outer edge of the rear cover. ~40°

[Claim 9] The spiral flow constant pressure pump according to claim 8, wherein the long blade and the short blade are bent at a root outlet angle of 100 to 130.

[Claim 10] The spiral flow constant pressure pump according to claim 4, wherein the long blade and the short blade each intersect perpendicularly with the rear cover, and the long blade has a common center of rotation An angle of 10°; a front end of the long blade and the short blade is a free edge, and a rear end is a bend, and the bending is inclined at an angle of 4° inward than the free edge; The inlet angle of the short blade is 30°; the long blade and the short blade are respectively bent at an angle of 30° along the tangential direction of the outer edge of the rear cover; the long blade and the short blade The root exit angle is 110° after bending.