CN111810410B - Multistage centrifugal pump with axial force balancing device - Google Patents
Multistage centrifugal pump with axial force balancing device Download PDFInfo
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- CN111810410B CN111810410B CN202010647752.2A CN202010647752A CN111810410B CN 111810410 B CN111810410 B CN 111810410B CN 202010647752 A CN202010647752 A CN 202010647752A CN 111810410 B CN111810410 B CN 111810410B
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- 230000001105 regulatory effect Effects 0.000 claims abstract description 102
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- 230000008859 change Effects 0.000 claims description 14
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- 238000005259 measurement Methods 0.000 claims description 5
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 claims description 5
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0088—Testing machines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/02—Selection of particular materials
- F04D29/026—Selection of particular materials especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
- F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a multistage centrifugal pump with a novel axial force balancing device, which comprises a conical body, a conical sleeve, an electric pressure regulating valve, a strain type force sensor, an eddy current displacement sensor and a PLC, wherein the conical body and the conical sleeve are hydraulic balance elements of axial force; the electric pressure regulating valve, the strain type force transducer, the eddy current displacement transducer and the pressure regulating tube are measuring and controlling elements of axial force; the high-pressure cavity and the pressure regulating cavity are isolated by the conical body and the conical sleeve, and the low-pressure cavity and the pressure regulating cavity are connected by the pressure regulating pipe. The novel axial force balancing device balances axial force in a two-stage adjusting mode, the hydraulic balance of the conical body and the conical sleeve is primary balance, and the regulation and control of the electric pressure regulating valve, the electric vortex displacement sensor, the strain type force sensor and the PLC is secondary balance. The invention can completely balance the axial force, is safe and reliable, has abrasion resistance and long service life, has no residual axial force, and can reliably work under rated working conditions and non-rated working conditions.
Description
Technical Field
The invention relates to the field of water pumps, in particular to a multistage centrifugal pump with a novel axial force balancing device.
Background
The multistage pump can generate higher pressure than the single-stage pump, so that the multistage pump is widely applied to industries such as electric power, chemical engineering, steel, mine and the like.
Due to its working principle, the pump rotor generates a large axial force. The pressure distribution of the suction side and the other side of the impeller is different, the suction inlet is a low pressure area, the corresponding area of the other side is a high pressure area, and a pressure difference is generated, so that each stage of impeller is subjected to an acting force opposite to the liquid suction direction, and the resultant force of all impellers is the axial force of the multistage pump. Too much axial force can have a great effect on the bearings of the pump, which greatly shorten the life of the bearings due to increased load, increased temperature, and severe wear. Since the axial force of the multistage pump is large, measures are taken to balance the axial force. There are two ways for the multistage pump to balance the axial force: a balancing drum balancing method and a balancing disk balancing method. However, the prior art balancing drum balancing method and balancing disk balancing method have a number of drawbacks: the balance disc balance method and the balance drum balance method require that the axial force of the pump under the rated working condition is calculated at the beginning of the design of the pump, which is calculated mainly by an empirical method, the result is often inaccurate, and the axial force of the pump under the non-rated working condition can not be obtained; the balance drum balancing method cannot completely balance the axial force in principle, and meanwhile, the balance drum is easy to wear, so that the balance effect is further reduced, and the service life of the bearing is seriously influenced by larger residual axial force; the balance disc balance method is particularly sensitive to the working clearance, so that great axial impact can be generated during startup or shutdown, and in addition, the balance effect of the balance disc is drastically reduced after the balance disc is worn in an abrasive medium; the balance disc balance method and the balance drum balance method in the prior art have unsatisfactory performances under the non-rated working condition.
Disclosure of Invention
In order to solve the problems, the invention provides a multistage centrifugal pump with a novel axial force balancing device, which can well solve the defects of easy abrasion, axial impact, large residual axial force and the like existing in the axial force balancing method in the prior art; meanwhile, the invention provides a design method of the novel axial force balancing device, which solves the problems that the design in the prior art is inaccurate and excessively depends on personal experience.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
The multistage centrifugal pump with the novel axial force balancing device comprises a conical body, a conical sleeve, an electric pressure regulating valve, a strain type force transducer, an electric vortex displacement sensor and a PLC, wherein the conical body and the conical sleeve are hydraulic balancing elements of axial force; the electric pressure regulating valve, the strain type force transducer, the eddy current displacement transducer and the pressure regulating tube are measurement and control elements of axial force; the conical body is provided with a conical outer surface, the conical sleeve is provided with a conical inner surface, the cone angles of the conical outer surface and the conical inner surface are equal, and a certain running clearance is kept between the conical outer surface and the conical inner surface; the conical body is connected with the pump shaft through a key, the conical sleeve is fixed on the right side of the high-pressure cavity of the outlet section, the conical body is arranged in the conical inner hole of the conical sleeve and is coaxially arranged with the conical sleeve, and the conical body and the conical sleeve isolate the high-pressure cavity from the pressure regulating cavity; the electric pressure regulating valve is arranged in the middle of the pressure regulating pipe, and the pressure regulating pipe connects the low pressure cavity with the pressure regulating cavity; the strain type force transducer is arranged between the end face of the first bearing gland and the end face of the outer ring of the rolling bearing and is used for transmitting an electric signal of the axial thrust of the rolling bearing; the electric vortex displacement sensor is fixed on the fourth bearing gland through threads and is used for detecting axial displacement of the pump shaft, and a certain gap is kept between the end face of the electric vortex displacement sensor and the right end face of the pump shaft; when the left end face of the outer ring of the rolling bearing is tightly attached to the strain force transducer, a gap of 0.5-0.6 mm is kept between the right end face of the outer ring of the rolling bearing and the end face of the second bearing cover, the gap between the end face of the eddy current displacement transducer and the right end face of the pump shaft is 0.2mm larger than the gap, the gap between the conical body of the conical body and the conical surface of the conical sleeve is 0.05-0.1 mm, and the left end face and the right end face of the outer ring of the cylindrical roller bearing are respectively just contacted with the right end face of the third bearing cover and the left end face of the fourth bearing cover; the rotary parts of the pump shaft, the conical body, the plurality of impellers, the first shaft sleeve, the second shaft sleeve, the two pairs of round nuts, the rolling bearings and the cylindrical roller bearings form a rotor part, and when the rotor part generates axial displacement, other rotary parts except the rolling bearings and the cylindrical roller bearings do not contact the surfaces of any static parts; the strain type force transducer converts axial thrust of the rotor component into analog quantity and transmits the analog quantity to an analog quantity input port of the PLC through a first signal wire, and the eddy current displacement transducer converts displacement of the pump shaft into analog quantity and transmits the analog quantity to the analog quantity input port of the PLC through a second signal wire; the PLC converts the opening change quantity required by the electric pressure regulating valve into pulse quantity through calculation according to the input analog quantity, and transmits the pulse quantity to a servo motor controller of the electric pressure regulating valve through a third signal line so as to drive a servo motor to regulate the opening of the electric pressure regulating valve.
As a further improvement of the invention, the cone angles of the cone surfaces of the cone body and the cone sleeve are 30-45 degrees, the cone angles of the cone body and the cone sleeve are equal, and the dimensional tolerance and the form tolerance of the cone surfaces are higher than grade 6; the conical surfaces of the conical body and the conical sleeve are coated with wear-resistant tungsten carbide materials so as to improve the wear resistance of the surfaces; the conical surfaces of the conical body and the conical sleeve are respectively provided with a plurality of annular grooves with the width of 1mm and the depth of 1mm, and the two groups of annular grooves are arranged in a staggered manner; under certain working conditions, the conical body and the conical sleeve can form a pair of friction pairs.
As a further improvement of the invention, the eddy current displacement sensor is fixed on the fourth bearing gland through threads, and the gap between the end face of the eddy current displacement sensor and the end face of the pump shaft can be adjusted; the range of the eddy current displacement sensor is 0-1 mm.
As a further improvement of the invention, the control signal of the electric pressure regulating valve is pulse quantity sent by the PLC, the opening change quantity of the electric pressure regulating valve is in direct proportion to the total number of pulses, the opening change speed of the electric pressure regulating valve is in direct proportion to the number of pulses in unit time, and the electric pressure regulating valve is in linear pressure regulation; the PLC includes a pulse output.
As a further improvement of the invention, the invention also comprises a front bearing bracket, a suction section, a plurality of radial guide vanes, a plurality of middle sections, an outlet section, a rear cover and a rear bearing bracket which are arranged in sequence from left to right; the middle section and the radial guide vane are respectively cast, respectively rough machined, welded together and finally finish machined; the suction section comprises an annular low-pressure cavity communicated with the inlet, and the outlet section comprises an annular high-pressure cavity communicated with the outlet; the outlet section, the rear cover, the second shaft sleeve, the conical body and the conical sleeve enclose a pressure regulating cavity, and the pressure regulating cavity is communicated with the low pressure cavity through a pressure regulating pipe and an electric pressure regulating valve; the pressure regulating cavity is communicated with the high pressure cavity through an operation gap.
As a further improvement of the invention, the maximum pipeline pressure loss of the pressure regulating pipe is not more than 1% of the pressure difference between the high pressure cavity and the low pressure cavity.
As a further improvement of the invention, the outer ring of the rolling bearing is in loose transition fit with the inner hole of the front bearing frame, and the tolerance level of the size of the inner hole of the front bearing frame is H8, so that the rolling bearing can freely slide along the axial direction under the action of axial force.
As a further improvement of the invention, the strain type force sensor is provided with 2 pieces, the strain type force sensor is symmetrically arranged on the upper and lower sides of the rotation axis, and the numerical value of the axial thrust measured by the 2 pieces of strain type force sensor is taken as final data by a PLC (programmable logic controller).
The invention also provides a design method of the novel axial force balancing device, which comprises the following steps:
(1) Determining initial parameters:
knowing the flow rate Q and the stroke H, taking the total pressure of the low pressure chamber as 0,
The static pressure P1 of the low pressure chamber is: p1=0-0.5ρv12= -0.5ρv12
The static pressure P2 of the high pressure chamber is: p2=pgh-0.5 pgv 22
Taking the static pressure P3=0.1ρgH of the pressure regulating cavity (which can be realized by adjusting the opening degree of the electric pressure regulating valve)
Wherein V1 and V2 are average flow rates of the low-pressure cavity and the high-pressure cavity respectively, and ρ is the medium density.
(2) Determining the axial force: and 3D models (not comprising a conical body and a conical sleeve) of the multistage centrifugal pump are established by using SOLIWORKS software, related boundary conditions are set by taking P1, P2, P3, rho and the like as basic parameters, and the hydraulic axial force Fz of the pump rotor is obtained by using CFX flow field analysis software.
(3) Size of the predetermined cone:
Taking the small diameter of the conical body:
Taking the cone angle of a conical body: y=30° to 45 °
Taking the effective thickness of the cone: l=0.4d 3
The cone has a large diameter: d 4＝d3 +2tg (0.5Y) L
Taking the running clearance between the conical body and the conical sleeve: d=0.1 to 0.2mm
The cone angle and the effective thickness of the conical sleeve are the same as those of the conical body, so that the large diameter and the small diameter of the conical sleeve can be calculated
Other dimensions of the cone and the cone sleeve are determined by structural design
(4) And (3) according to the size determined in the step (3), a 3D model (comprising a conical body and a conical sleeve) of the multistage centrifugal pump is established by using SOLIWORKS software, relevant boundary conditions are set by taking P1, P2, P3, rho and the like as basic parameters, and the residual hydraulic axial force Fz1 of the pump rotor is obtained by using CFX flow field analysis software.
(5) Judging whether Fz1 meets the condition of the expected residual hydraulic axial force value: if Fz1 is less than the expected value, then a condition is satisfied, indicating that the design is complete; if Fz1 is greater than or equal to the expected value, the dimensions of the relevant cone and cone sleeve need to be adjusted according to the actual performance, a 3D model of the multistage centrifugal pump (comprising the cone and cone sleeve) is re-established, and CFX is used again for analysis until Fz1 meets the conditions.
Compared with the prior art, the invention has the beneficial effects that:
1. The axial force can be completely balanced, and the safety and reliability are realized: the axial force can be automatically balanced through the change of the clearance between the conical body and the conical sleeve and the change of the opening degree of the electric pressure regulating valve, and no residual axial force exists.
2. The device can reliably work under rated working conditions and non-rated working conditions: because the hydraulic balance of the conical body and the conical sleeve and the automatic control and adjustment of the electric pressure regulating valve, the electric vortex displacement sensor and the strain force transducer are adopted, the working range of the balancing device is wide, and the balancing device can reliably work under rated working conditions and non-rated working conditions.
3. Wear-resisting, life-span is high: because the conical surfaces of the conical body and the conical sleeve are both coated with wear-resistant tungsten carbide and are provided with a plurality of annular grooves, fine particles can be flushed into the annular grooves, and the conical surfaces of the conical body and the conical sleeve are prevented from being worn.
4. The design method of the balancing device is aided by computer simulation, has high design precision, is simple and practical, and overcomes the defects that the traditional technology excessively depends on personal experience and the result is inaccurate.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate and together with the embodiments of the invention and do not constitute a limitation to the invention, and in which:
Fig. 1 is a front cross-sectional view of the present invention.
Fig. 2 is a top view of the present invention.
Fig. 3 is a partial enlarged view of a portion a of fig. 1.
Fig. 4 is a partial enlarged view of a portion B of fig. 1.
Fig. 5 is a schematic diagram of the design of the cone and cone sleeve.
In the figure: 1. the device comprises a first bearing gland, 2, a strain force transducer, 3, a rolling bearing, 4, a second bearing gland, 5, a suction section, 6, a pressure regulating tube, 7, an electric pressure regulating valve, 8, an outlet section, 9, a rear cover, 10, a third bearing gland, 11, a cylindrical roller bearing, 12, a fourth bearing gland, 13, an electric vortex displacement sensor, 14, a conical body, 15, a conical sleeve, 16, a middle section, 17, a radial guide vane, 18, an impeller, 19, a pump shaft, 20, a first shaft sleeve, 21, a round nut, 22, a second shaft sleeve, 23, a front bearing bracket, 24, a rear bearing bracket, 25, a key, 26, a first signal wire, 27, a second signal wire, 28, a third signal wire, 29, a PLC,100, a low pressure cavity, 200, a pressure regulating cavity, 300, a high pressure cavity, 400, an operating clearance, 500, an outlet, 600, an inlet, 700, a conical outer surface, 800 and a conical inner surface.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front", "rear", "both ends", "one end", "the other end", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific direction, be configured and operated in a specific direction, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "provided," "connected," and the like are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
As shown in fig. 1 to 5, the present invention provides a multistage centrifugal pump with a novel axial force balancing device, which comprises a conical body 14, a conical sleeve 15, an electric pressure regulating valve 7, a strain force sensor 2, an eddy current displacement sensor 13 and a PLC29, wherein the conical body 14 and the conical sleeve 15 are hydraulic balance elements of axial force, and the electric pressure regulating valve 7, the strain force sensor 2, the eddy current displacement sensor 13 and a pressure regulating pipe 6 are measurement and control elements of axial force. Cone 14 has a conical outer surface 700 and cone sleeve 15 has a conical inner surface 800 with equal cone angles, with a running clearance 400 maintained between the two surfaces. The cone 14 is connected to the pump shaft 19 by means of a key 25, the cone sleeve 15 is fixed to the right side of the high pressure chamber 300 of the outlet section 8, the cone 14 is arranged in the conical inner bore of the cone sleeve 15 and coaxially arranged with the cone sleeve 15, the cone 14 and the cone sleeve 15 isolate the high pressure chamber 300 from the pressure regulating chamber 200. The electric pressure regulating valve 7 is arranged in the middle of the pressure regulating pipe 6, and the pressure regulating pipe 6 connects the low pressure cavity 100 with the pressure regulating cavity 200. The electric pressure regulating valve 7 functions to change the flow resistance by adjusting the opening degree, thereby adjusting the pressure of the pressure regulating chamber 200. The strain force transducer 2 is arranged between the end face of the first bearing gland 1 and the end face of the outer ring of the rolling bearing 3, and is used for transmitting an electric signal of the axial thrust of the rolling bearing 3. The electric vortex displacement sensor 13 is fixed on the fourth bearing gland 12 through threads and is coaxial with the pump shaft 19, and is used for detecting axial displacement of the pump shaft 19, and a certain gap d2 is kept between the end face of the electric vortex displacement sensor 13 and the right end face of the pump shaft 19. When the left end face of the outer ring of the rolling bearing 3 is tightly attached to the strain force sensor 2, a gap d1 between the right end face of the outer ring of the rolling bearing 3 and the end face of the second bearing cover 4 is kept at 0.5-0.6 mm, a gap d2 between the end face of the eddy current displacement sensor 13 and the right end face of the pump shaft 19 is 0.2mm larger than the gap d1, a gap d between the conical body 14 and the conical surface of the conical sleeve 15 is 0.05-0.1 mm, and the left end face and the right end face of the outer ring of the cylindrical roller bearing 11 are just contacted with the right end face of the third bearing cover 10 and the left end face of the fourth bearing cover 12 respectively. The rotating parts of the pump shaft 19, the cone 14, the plurality of impellers 18, the first sleeve 20, the second sleeve 22, the two pairs of round nuts 21, the rolling bearing 3 and the cylindrical roller bearing 11 constitute a rotor part, and when the rotor part is axially displaced, the rotating parts except the rolling bearing 3 and the cylindrical roller bearing 11 do not contact the surfaces of any static parts. The strain gauge sensor 2 converts the axial thrust of the rotor component into an analog quantity which is transmitted to an analog quantity input port of the PLC29 through the first signal line 26, and the eddy current displacement sensor 13 converts the displacement of the pump shaft 19 into an analog quantity which is transmitted to another analog quantity input port of the PLC29 through the second signal line 27. The PLC29 calculates from the input analog quantity, converts the opening change amount required for the electric pressure regulating valve 7 into a pulse quantity, and transmits the pulse quantity to the servo motor controller of the electric pressure regulating valve 7 through the third signal line 28, so as to drive the servo motor to regulate the opening of the electric pressure regulating valve 7.
The novel axial force balancing device balances axial force in a two-stage adjusting mode, the hydraulic balance of the conical body 14 and the conical sleeve 15 is primary balance, and the regulation and control of the electric pressure regulating valve 7, the electric vortex displacement sensor 13, the strain type force transducer 2 and the PLC29 are secondary balance.
As shown in fig. 1 and 5, the taper angles of the tapered surfaces of the tapered body 14 and the tapered sleeve 15 are 30 ° to 45 °, and the taper angles are equal, the dimensional tolerance and the form tolerance of the tapered surfaces are higher than 6 levels, the tapered surfaces of the tapered body 14 and the tapered sleeve 15 are both coated with wear-resistant tungsten carbide materials to improve the wear resistance of the surfaces, and the roughness values of the surfaces are not more than ra0.1, so that the tapered body 14 and the tapered sleeve 15 can form a pair of high-precision friction pairs. The conical surfaces of the conical body 14 and the conical sleeve 15 are provided with a plurality of annular grooves with the width of 1mm and the depth of 1mm, and the two groups of annular grooves are arranged in a staggered manner, so that the advantage is that tiny particles in a medium can be flushed into the annular grooves to avoid abrasion of the friction pair surface, the flow resistance of the running clearance 400 can be increased, and the sensitivity of the novel axial force balancing device to the axial displacement of a rotor part is finally reduced.
As shown in fig. 1, 2 and 4, the eddy current displacement sensor 13 is fixed to the fourth bearing cover 12 by screw threads, and the gap between the end face of the eddy current displacement sensor and the end face of the pump shaft 19 can be adjusted, so that the measurement data can fall in a high-precision range. The range of the eddy current displacement sensor 13 is 0-1 mm, the measurement requirement is completely met, and the eddy current displacement sensor transmits an analog current signal of 4-20 mA.
As shown in fig. 2, the control signal of the electric pressure regulating valve 7 is the pulse amount sent by the PLC29, the opening change amount of the electric pressure regulating valve 7 is proportional to the total number of pulses, the opening change speed of the electric pressure regulating valve 7 is proportional to the number of pulses per unit time, and the electric pressure regulating valve 7 is a linear pressure regulation. The PLC29 comprises a pulse output port for sending pulse quantity to control the rotating speed and the rotating angle of the servo motor of the electric pressure regulating valve 7, and an encoder arranged on the servo motor transmits the actual rotating angle to an analog quantity input port of the PLC29 in a 4-20 mA current signal for the PLC29 to carry out closed-loop control so as to achieve the purpose of precisely controlling the rotating angle of the servo motor. The opening change amount of the electric pressure regulating valve 7 is proportional to the rotation angle of the servo motor, and the opening change speed of the electric pressure regulating valve 7 is proportional to the rotation speed of the servo motor. In addition, the PLC29 further includes a plurality of digital input ports, digital output ports, analog input ports, and analog output ports to meet control requirements.
As shown in fig. 1 and 2, the present embodiment further includes a front bearing frame 23, a suction section 5, a plurality of radial guide vanes 17, a plurality of middle sections 16, an outlet section 8, a rear cover 9, and a rear bearing frame 24, which are arranged in this order from left to right. The middle section 16 and the radial guide vane 17 are respectively cast and respectively rough machined, then welded together and finally finish machined, so that the middle section 16 and the radial guide vane 17 can be integrated, and the integral precision and rigidity of the equipment can be improved. The suction section 5 comprises an annular low pressure chamber 100 communicating with the inlet 600 and the outlet section 8 comprises an annular high pressure chamber 300 communicating with the outlet 500. The outlet section 8, the rear cover 9, the second sleeve 22, the cone 14 and the cone sleeve 15 enclose a pressure regulating cavity 200, and the pressure regulating cavity 200 is communicated with the low pressure cavity 100 through the pressure regulating pipe 6 and the electric pressure regulating valve 7. The pressure regulating chamber 200 communicates with the high pressure chamber 300 through the running clearance 400.
The maximum line pressure loss of the pressure regulating pipe 6 is not more than 1% of the pressure difference between the high pressure chamber 300 and the low pressure chamber 100, so that the electric pressure regulating valve 7 has a larger regulating range.
As shown in fig. 1 and 3, the outer ring of the rolling bearing 3 is in loose transition fit with the inner hole of the front bearing frame 23, and the tolerance level of the size of the inner hole of the front bearing frame 23 is H8, so that the rolling bearing 3 can freely slide along the axial direction in the inner hole of the front bearing frame 23 under the action of axial force.
The strain force sensor 2 has 2 pieces, which are symmetrically arranged up and down on the rotation axis, and the value of the axial thrust force measured by the 2 pieces of strain force sensor 2 is taken as final data by the PLC 29. The strain force transducer 2 transmits 4-20 mA analog current signals.
As shown in fig. 1 to 5, the present invention further provides a design method of the novel axial force balancing device, which includes the following steps:
(1) Determining initial parameters:
knowing the flow rate Q and the stroke H, taking the total pressure of the low pressure chamber 100 as 0,
The static pressure P1 of the low pressure chamber 100 is: p1=0-0.5ρv12= -0.5ρv12
The static pressure P2 of the high pressure chamber 300 is: p2=pgh-0.5 pgv 22
Taking the static pressure p3=0.1ρgh of the pressure regulating chamber 200 (which can be achieved by adjusting the opening degree of the electric pressure regulating valve 7)
Where V1 and V2 are the average flow rates of the low pressure chamber 100 and the high pressure chamber 300, respectively, and ρ is the medium density.
(2) Determining the axial force: A3D model of the multistage centrifugal pump (excluding the cone 14 and the cone sleeve 15) is established by using SOLIWORKS software, related boundary conditions are set by taking P1, P2, P3, rho and the like as basic parameters, and the hydraulic axial force Fz of the pump rotor is obtained by CFX flow field analysis software.
(3) The dimensions of the predetermined cone 14:
Taking the small diameter of the conical body 14:
taking the cone angle of the conical body 14: y=30° to 45 °
Taking the effective thickness of cone 14: l=0.4d 3
The cone 14 has a large diameter: d 4＝d3 +2tg (0.5Y) L
Taking the size of the running clearance 400 between cone 14 and cone sleeve 15: d=0.1 to 0.2mm
The taper angle and the effective thickness of the taper sleeve 15 are the same as those of the taper sleeve 15, so that the large diameter and the small diameter of the taper sleeve 15 can be calculated
Other dimensions of cone 14 and cone sleeve 15 are determined by the structural design
(4) And (3) according to the size determined in the step (3), a 3D model (comprising a conical body 14 and a conical sleeve 15) of the multistage centrifugal pump is established by using SOLIWORKS software, relevant boundary conditions are set by taking P1, P2, P3, rho and the like as basic parameters, and the residual hydraulic axial force Fz1 of the pump rotor is obtained by using CFX flow field analysis software.
(5) Judging whether Fz1 meets the condition of the expected residual hydraulic axial force value: if Fz1 is less than the expected value, then a condition is satisfied, indicating that the design is complete; if Fz1 is greater than or equal to the expected value, the dimensions of the relevant cone 14 and cone sleeve 15 need to be adjusted according to the actual performance, a 3D model of the multistage centrifugal pump (comprising cone 14 and cone sleeve 15) is re-built, and analysis is performed again using CFX until Fz1 meets the conditions.
The working principle of the novel axial force balancing device (hereinafter referred to as balancing device) is as follows: as shown in fig. 1 to 5, the axial force generated by the rotor component during operation is to the left, so that the balancing force generated by the balancing device should be equal to the axial force, opposite in direction to the axial force, and directed to the right. The left and right sides of the cone 14 are respectively provided with a high pressure cavity 300 and a pressure regulating cavity 200, the pressure regulating pipe 6 introduces the low pressure of the low pressure cavity 100 into the pressure regulating cavity 200, the left and right sides of the cone 14 are respectively provided with the high pressure and the low pressure, and the high pressure and the low pressure acting on the left side and the right side of the cone 14 generate a rightward balance force. The rotor component may have a play of 0.5-0.6 mm in the axial direction for adjusting the size of the running clearance 400 between the cone 14 and the cone sleeve 15. The pressure of the pressure regulating chamber 200 will be slightly higher than that of the low pressure chamber 100 and lower than that of the high pressure chamber 300 due to the throttling and depressurizing function of the electric pressure regulating valve 7. If the balance force is greater than the axial force, the rotor member moves rightward, at which time the running clearance 400 increases, the flow resistance of the liquid flowing through the running clearance 400 decreases, the pressure of the pressure regulating chamber 200 increases, the pressure difference between the left and right sides of the cone 14 decreases, and the balance force decreases accordingly until it is balanced with the axial force; if the balancing force is smaller than the axial force, the rotor member moves to the left, at which time the running clearance 400 decreases, the flow resistance of the liquid flowing through the running clearance 400 increases, the pressure in the pressure regulating chamber 200 decreases, the pressure difference between the left and right sides of the cone 14 increases, and the balancing force increases until it balances with the axial force. The balance of axial force by cone 14 and cone sleeve 15 is continuously in dynamic adjustment, and the size of running clearance 400 is changed by the left-right movement of the rotor components, so as to achieve the purpose of balancing axial force, namely primary balance. If the eddy current displacement sensor 13 passes the detection gap d2, dynamic balancing cannot be achieved at all when the rotor component has reached the limit position to the right, indicating that the balancing force is too large to achieve new balancing. At this time, the PLC29 determines from the displacement signal from the eddy current displacement sensor 13 and then sends a signal for decreasing the opening degree to the electric pressure regulating valve 7. After the opening degree of the electric pressure regulating valve 7 is reduced, the pressure of the pressure regulating cavity 200 is increased, the pressure difference between the high pressure cavity 300 and the pressure regulating cavity 200 is reduced, and the balance force is reduced, so that the rotor component is properly moved back leftwards until the balance force and the axial force reach new balance; if the eddy current displacement sensor 13 passes the detection gap d2, dynamic balancing cannot be achieved at all when the rotor component has reached the extreme position to the left (or the strain gauge sensor 2 detects thrust from the rolling bearing 3), indicating that the balancing force is too small to achieve new balancing. At this time, the PLC29 judges from the displacement signal (or the thrust signal of the rolling bearing 3 detected by the strain gauge sensor 2) transmitted from the eddy current displacement sensor 13, and then sends a signal for increasing the opening degree to the electric pressure regulating valve 7. After the electric pressure regulating valve 7 increases the opening degree, the pressure of the pressure regulating chamber 200 decreases, the pressure difference between the high pressure chamber 300 and the pressure regulating chamber 200 increases, and the balancing force increases, so that the rotor component moves back to the right properly until the balancing force and the axial force reach new balance, namely the secondary balance. In general, the axial force balance requirement can be met only by primary balance, and secondary balance can be used only after the balance device is used for a plurality of years or when the pump runs in a state of seriously deviating from the rated working condition.
Compared with the balance drum and the balance disc in the prior art for balancing axial force, the novel axial force balancing device has obvious advantages. On one hand, the balance drum cannot completely balance axial force due to the limitation of the working principle, and is easy to wear, so that the performance is seriously reduced; on the other hand, the balance disc is too sensitive to the gap, the impact is easy to occur in the working process, the balance performance is fast reduced after the disc surface is damaged, even the balance disc cannot work normally, and the balance disc is not ideal in the non-rated working condition of the pump. The novel axial force balancing device has two-stage balancing measures, can perform well under rated working conditions or non-rated working conditions, can automatically and completely balance axial force, has high reliability, and greatly prolongs the service life due to the adoption of the anti-wear material tungsten carbide and the anti-wear annular groove structure.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and not for limiting the same; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the invention.
Claims (8)
1. A multistage centrifugal pump having an axial force balancing device, characterized by: the device comprises a conical body, a conical sleeve, an electric pressure regulating valve, a strain type force transducer, an eddy current displacement sensor and a PLC, wherein the conical body and the conical sleeve are hydraulic balance elements of axial force; the electric pressure regulating valve, the strain type force transducer, the eddy current displacement transducer and the pressure regulating tube are measurement and control elements of axial force; the conical body is provided with a conical outer surface, the conical sleeve is provided with a conical inner surface, the cone angles of the conical outer surface and the conical inner surface are equal, and a certain running clearance is kept between the conical outer surface and the conical inner surface; the conical body is connected with the pump shaft through a key, the conical sleeve is fixed on one side of the high-pressure cavity of the outlet section, the conical body is arranged in the conical inner hole of the conical sleeve and is coaxially arranged with the conical sleeve, and the conical body and the conical sleeve isolate the high-pressure cavity from the pressure regulating cavity; the electric pressure regulating valve is arranged in the middle of the pressure regulating pipe, and the pressure regulating pipe connects the low pressure cavity with the pressure regulating cavity; the bearing comprises a first bearing gland, a front bearing frame, a suction section, a plurality of middle sections, an outlet section, a rear bearing frame and a fourth bearing gland, wherein the first bearing gland, the front bearing frame, the suction section, the middle sections, the outlet section, the rear bearing frame and the fourth bearing gland are sequentially arranged and connected from a driving end to a non-driving end, the front bearing frame is internally provided with and connected with a second bearing gland, the rear bearing frame is internally provided with and connected with a third bearing gland, and radial guide vanes are embedded in the middle sections; the inner hole of the front bearing frame is provided with a rolling bearing, and the inner hole of the rear bearing frame is provided with a cylindrical roller bearing; the strain type force transducer is arranged between the end face of the first bearing gland and the end face of the outer ring of the rolling bearing and is used for transmitting an electric signal of axial thrust of the rolling bearing; the electric vortex displacement sensor is fixed on the fourth bearing gland through threads and is used for detecting axial displacement of the pump shaft, and a certain gap is kept between the end face of the electric vortex displacement sensor and the right end face of the pump shaft; when the left end face of the outer ring of the rolling bearing is tightly attached to the strain force transducer, a gap of 0.5-0.6 mm is kept between the right end face of the outer ring of the rolling bearing and the end face of the second bearing cover, the gap between the end face of the eddy current displacement transducer and the right end face of the pump shaft is 0.2mm larger than the gap, the gap between the conical body of the conical body and the conical surface of the conical sleeve is 0.05-0.1 mm, and the left end face and the right end face of the outer ring of the cylindrical roller bearing are respectively just contacted with the right end face of the third bearing cover and the left end face of the fourth bearing cover; the rotary parts of the pump shaft, the conical body, the plurality of impellers, the first shaft sleeve, the second shaft sleeve, the two pairs of round nuts, the rolling bearings and the cylindrical roller bearings form a rotor part, and when the rotor part generates axial displacement, other rotary parts except the rolling bearings and the cylindrical roller bearings do not contact the surfaces of any static parts; the strain type force transducer converts axial thrust of a rotor component into analog quantity and transmits the analog quantity to an analog quantity input port of the PLC through a first signal wire, and the eddy current displacement transducer converts displacement of a pump shaft into analog quantity and transmits the analog quantity to the analog quantity input port of the PLC through a second signal wire; the PLC converts the opening change quantity required by the electric pressure regulating valve into pulse quantity through calculation according to the input analog quantity, and transmits the pulse quantity to a servo motor controller of the electric pressure regulating valve through a third signal wire so as to drive a servo motor to regulate the opening of the electric pressure regulating valve.
2. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the cone angles of the cone surfaces of the cone body and the cone sleeve are 30-45 degrees, the cone angles of the cone body and the cone sleeve are equal, and the dimensional tolerance and the form tolerance of the cone surfaces are higher than level 6; the conical surfaces of the conical body and the conical sleeve are coated with wear-resistant tungsten carbide materials so as to improve the wear resistance of the surfaces; the conical surfaces of the conical body and the conical sleeve are respectively provided with a plurality of annular grooves with the width of 1mm and the depth of 1mm, and the two groups of annular grooves are arranged in a staggered manner; under certain working conditions, the conical body and the conical sleeve can form a pair of friction pairs.
3. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the eddy current displacement sensor is fixed on the fourth bearing gland through threads, and the gap between the end face of the eddy current displacement sensor and the end face of the pump shaft can be adjusted; the range of the eddy current displacement sensor is 0-1 mm.
4. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the control signal of the electric pressure regulating valve is pulse quantity sent by the PLC, the opening change quantity of the electric pressure regulating valve is in direct proportion to the total number of pulses, the opening change speed of the electric pressure regulating valve is in direct proportion to the number of pulses in unit time, and the electric pressure regulating valve is in linear pressure regulation; the PLC includes a pulse output.
5. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the device also comprises a front bearing frame, a suction section, a plurality of radial guide vanes, a plurality of middle sections, an outlet section, a rear cover and a rear bearing frame which are sequentially arranged from left to right; the middle section and the radial guide vane are respectively cast, respectively rough machined, welded together and finally finish machined; the suction section comprises an annular low-pressure cavity communicated with the inlet, and the outlet section comprises an annular high-pressure cavity communicated with the outlet; the outlet section, the rear cover, the second shaft sleeve, the conical body and the conical sleeve enclose a pressure regulating cavity, and the pressure regulating cavity is communicated with the low pressure cavity through a pressure regulating pipe and an electric pressure regulating valve; the pressure regulating cavity is communicated with the high pressure cavity through an operation gap.
6. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the maximum pipeline pressure loss of the pressure regulating pipe is not more than 1% of the pressure difference between the high-pressure cavity and the low-pressure cavity.
7. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the outer ring of the rolling bearing is in loose transition fit with the inner hole of the front bearing frame, and the tolerance level of the size of the inner hole of the front bearing frame is H8, so that the rolling bearing can slide along the axial direction freely under the action of axial force.
8. A multistage centrifugal pump with axial force balance according to claim 1, characterized in that: the strain type force sensor is provided with 2 pieces, the strain type force sensor is symmetrically arranged up and down on the rotation axis, and the numerical value of the axial thrust measured by the 2 pieces of strain type force sensor is taken as final data by the PLC.
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| CN212429197U (en) * | 2020-07-07 | 2021-01-29 | 长沙中联泵业股份有限公司 | Multistage centrifugal pump with novel axial force balancing device |
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| CA2126262A1 (en) * | 1994-06-20 | 1995-12-21 | Thomas William Ramsay | Shaft mounted and impeller mounted pumping sleeve and bushing |
| US6210103B1 (en) * | 1995-10-02 | 2001-04-03 | A. W. Chesterton Co. | Rotary seal and/or bearing |
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