CN203076287U - Large pipeline hydraulic flushing system - Google Patents
Large pipeline hydraulic flushing system Download PDFInfo
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- CN203076287U CN203076287U CN 201320061427 CN201320061427U CN203076287U CN 203076287 U CN203076287 U CN 203076287U CN 201320061427 CN201320061427 CN 201320061427 CN 201320061427 U CN201320061427 U CN 201320061427U CN 203076287 U CN203076287 U CN 203076287U
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- compensator
- butterfly valve
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Abstract
The utility model discloses a large pipeline hydraulic flushing system which comprises components including an oil tank, a liquidometer and the like, wherein the liquidometer is located on the front surface of the oil tank, electric heaters and oil drainage ball valves are located on the side surface of the oil tank, an air filter, a temperature relay and the liquidometer are all located on the top surface of the oil tank, on end of a screw pump is connected with a first pipeline, a motor is connected with the other end of the screw pump, a first butterfly valve, a first compensator, a second compensator, a check valve, a second butterfly valve and a third compensator are located on the first pipeline in sequence, a fourth butterfly valve and a pressure meter switch are both located on a second pipeline, the pressure meter is connected with a pressure meter, a fourth compensator, a third butterfly valve and a sampling ball valve are all located on a third pipeline, oil return filters and fifth butterfly valves are located on a fourth pipeline, the first pipeline is connected with the oil tank and the second pipeline, the second pipeline is connected with the third pipeline, and the third pipeline is connected with the fourth pipeline. According to the large pipeline hydraulic flushing system, turbulent flow can be achieved pressure by improving differences of two ends of the pipelines, and the phenomenon of valve blocking is prevented.
Description
Technical field
The utility model relates to a kind of rinse-system, particularly relates to a kind of big hydraulic pressure of pipe line rinse-system.
Background technology
In the design of a cover scouring stage, be roughly L(such as field condition and be cleaned pipeline length)=the 180m(straight tube, put aside the pressure loss of shunting and bend pipe), D(is cleaned pipeline diameter)=150mm, ρ (clean and use Media density)=900 kg/m3, the flushing oil temperature is about 50 ℃, uses VG46 hydraulic oil (viscosity is about 30 mm 2/s).The selection flow is that the screw pump group of 1200L/min is washed pipeline, because the screw pump rated pressure is lower, is 15bar so overflow valve limits pressure.Developing result is undesirable always in actual use, when system works again after having washed, card valve phenomenon often occurs.
The utility model content
Technical problem to be solved in the utility model provides a kind of big hydraulic pressure of pipe line rinse-system, and its pressure reduction that improves the pipeline two ends could be realized turbulent flow, prevents card valve phenomenon.
The utility model solves above-mentioned technical problem by following technical proposals: a kind of big hydraulic pressure of pipe line rinse-system, it is characterized in that, described big hydraulic pressure of pipe line rinse-system comprises fuel tank, liquid level gauge, empty filter, electric heater, first butterfly valve, first compensator, screw pump, motor, second compensator, the 3rd compensator, the 4th compensator, check (non-return) valve, second butterfly valve, the 3rd butterfly valve, the 4th butterfly valve, return filter, temperature relay, liquid level relay, the ball valve of draining the oil, Sampling ball valve, pressure meter switch, Pressure gauge, the 5th butterfly valve, first pipeline, second pipeline, the 3rd pipeline, the 4th pipeline, liquid level gauge is positioned at the front of fuel tank, electric heater, the ball valve of draining the oil all is positioned at the side of fuel tank, empty filter, temperature relay, liquid level relay all is positioned at the end face of fuel tank, one end of screw pump is connected with first pipeline, motor is connected with the other end of screw pump, first butterfly valve, first compensator, second compensator, check (non-return) valve, second butterfly valve, the 3rd compensator is positioned on first pipeline successively, the 4th butterfly valve, pressure meter switch all is positioned on second pipeline, pressure meter switch is connected with Pressure gauge, the 4th compensator, the 3rd butterfly valve, Sampling ball valve all is positioned on the 3rd pipeline, return filter, the 5th butterfly valve is positioned on the 4th pipeline, first pipeline and fuel tank, second pipeline connects, second pipeline is connected with the 3rd pipeline, and the 3rd pipeline is connected with the 4th pipeline.
Preferably, described big hydraulic pressure of pipe line rinse-system also comprises first welded flange and second welded flange, and first welded flange is connected with first pipeline, and second welded flange is connected with the 3rd pipeline.
Preferably, described big hydraulic pressure of pipe line rinse-system also comprises spacer flanger, and spacer flanger is positioned on the 3rd pipeline.
Positive progressive effect of the present utility model is: the big hydraulic pressure of pipe line rinse-system of the utility model improves system pressure, the flow of screw pump output is the pipeline by needing to clean all, so just can reach turbulent condition, the VG46 hydraulic oil of turbulent condition can be cleared up more completely attached to the impurity above the pipeline, just can avoid causing card valve phenomenon because of pipeline pollutes when normal pipeline normally uses.
Description of drawings
Fig. 1 is the structural representation of the big hydraulic pressure of pipe line rinse-system of the utility model.
The specific embodiment
Provide the utility model preferred embodiment below in conjunction with accompanying drawing, to describe the technical solution of the utility model in detail.
As shown in Figure 1, the big hydraulic pressure of pipe line rinse-system of the utility model comprises fuel tank 1, liquid level gauge 2, empty filter 3, electric heater 4, first butterfly valve 5, first compensator 6, screw pump 7, motor 8, second compensator 91, the 3rd compensator 92, the 4th compensator 93, check (non-return) valve 10, second butterfly valve 111, the 3rd butterfly valve 112, the 4th butterfly valve 113, return filter 12, temperature relay 13, liquid level relay 14, the ball valve 15 of draining the oil, Sampling ball valve 16, pressure meter switch 17, Pressure gauge 18, the 5th butterfly valve 19, first pipeline 201, second pipeline 202, the 3rd pipeline 203, the 4th pipeline 204, liquid level gauge 2 is positioned at the front of fuel tank 1, electric heater 4, the ball valve 15 of draining the oil all is positioned at the side of fuel tank 1, empty filter 3, temperature relay 13, liquid level relay 14 all is positioned at the end face of fuel tank 1, one end of screw pump 7 is connected with first pipeline 201, motor 8 is connected with the other end of screw pump 7, first butterfly valve 5, first compensator 6, second compensator 91, check (non-return) valve 10, second butterfly valve 111, the 3rd compensator 92 is positioned on first pipeline 201 successively, the 4th butterfly valve 113, pressure meter switch 17 all is positioned on second pipeline 202, pressure meter switch 17 is connected with Pressure gauge 18, the 4th compensator 93, the 3rd butterfly valve 112, Sampling ball valve 16 all is positioned on the 3rd pipeline 203, return filter 12, the 5th butterfly valve 19 is positioned on the 4th pipeline 204, first pipeline 201 and fuel tank 1, second pipeline 202 connects, second pipeline 202 is connected with the 3rd pipeline 203, and the 3rd pipeline 203 is connected with the 4th pipeline 204.
The big hydraulic pressure of pipe line rinse-system of the utility model can also comprise that first welded flange 221 and second welded flange, 222, the first welded flanges 221 are connected with first pipeline 201, and second welded flange 222 is connected with the 3rd pipeline 203.The big hydraulic pressure of pipe line rinse-system of the utility model can also comprise spacer flanger 21, and spacer flanger 21 is positioned on the 3rd pipeline 203.
The operation principle of the big hydraulic pressure of pipe line rinse-system of the utility model is as follows: the big hydraulic pressure of pipe line rinse-system of the utility model improves system pressure, the flow of screw pump output is the pipeline by needing to clean all, so just can reach turbulent condition, when VG46 hydraulic oil flow velocity reached the critical point of thunder Lip river number of fluid turbulence in the pipeline, the fluid in the pipeline was in turbulent condition.Unordered flowing done in mutual blending between the micelle of turbulent condition fluid, irregular fluctuation takes place in mechanics parameters such as its flow velocity, pressure in time and space, the transmission of momentum, heat and the quality that causes owing to this random motion in the turbulent flow is high more a lot of than laminar flow, the frictional force of also increased severely fluid and pipeline.Impurity in the frictional force increase detergent line more completely of fluid and pipeline just can be avoided causing card valve phenomenon because of pipeline pollutes when normal pipeline normally uses.
Fuel tank storage work is with hydraulic oil and arrange Hydraulic Elements, and have the cooling hydraulic oil effect, consider the integral body circulation of hydraulic oil, allow the foam of oil return overflow, the cooling of contamination precipitation and hydraulic oil, cleaning station fuel tank designed size should be flow system flow 8-10 doubly; Liquid level gauge can the field observation fuel tank in the liquid level of residual hydraulic pressure oil; Empty filter prevents that dust in air or other dust from entering fuel tank and polluting hydraulic oil, is to filter hydraulic oil in oiling simultaneously; Heater heating hydraulic oil makes it reach the required oil temperature of system works, and when screw pump was worked at big flow, the hydraulic pressure oil viscosity had very big influence to oil suction and pump running resistance, and the required power of pump running is strengthened, and may cause motor overload.And be the oil temperature with the hydraulic oil of medium to the influential most critical factor of viscosity, so it is very important to allow oily temperature reach the oily temperature that the pump running sets); The built-in pressure regulator valve of screw pump, but the pressure of initialization system; It is the protection screw pump that check (non-return) valve mainly acts on, and can produce impact in system works and when shutting down.If this impact is directly got back in the screw pump, will make screw pump counter-rotating (screw pump does not have the rotating function), at this moment will produce injury even damage screw pump screw pump, check (non-return) valve can cut off this impact, make impact only be confined in the pipeline that (native system is inactivity output executive component at work, can not produce reaction force, so in the system safety valve can be set); The 4th butterfly valve and Sampling ball valve are normally off when running well in system, and the 4th butterfly valve is opened in system act as off-load, and the hydraulic oil in simultaneously can the circulating filtration fuel tank improves the cleannes of hydraulic oil; Sampling ball valve is the hydraulic oil sample after the detergent line of ball valve extraction from then in cleaning process, checks the cleannes of hydraulic oil, and then judges the effect that pipeline cleans; The 5th butterfly valve and return filter are dual-purpose one to be equipped with, return filter has the obstruction warning function, the more impurity of starting stage oil return that cleans at pipeline causes that easily return filter stops up, the 5th butterfly valve can cut off being connected of T chamber and return filter, can realize not shutting down cleaning or renew cartridge more; First compensator and second compensator are avoided the influence of motor oscillating to pump oil inlet and outlet line seal and weld, and the 3rd compensator, the 4th compensator can be avoided system and be cleaned different vibration frequencies between the part to the influence of line seal and weld; Temperature relay has two alarm points, can control low temperature and connect heater and high temperature alarm; Liquid level warning hangs down in liquid level relay realization system, prevents that liquid level from crossing low screw pump and inhaling empty.Heater, liquid level gauge can increase safeguard procedures, prevent transportation, install and work in this element of damage, because of return line long, very inconvenient when pipeline is handled, so increase spacer flanger.The height of fuel tank is one meter eight, and for conveniently installing and overhauling the element that is installed in panel, the fuel tank sidewall is provided with staircase.The effect of first butterfly valve is the oil sources that cuts off fuel tank when plant maintenance; prevent that hydraulic oil from flowing out from inlet port when preventing to be lower than the annex of inlet port because of dismounting electric-motor pump group and other; motor be screw pump the driving power source; pressure meter switch protection Pressure gauge; the operating pressure of Pressure gauge display system reality, first welded flange, second welded flange all are the oil inlet and outlets that connects tested pipeline.
The mentality of designing of prior art is such, and flushing of pipeline must improve the flow velocity of hydraulic oil, makes it reach turbulent condition (the smooth metal pipe is 10000〉Re〉4000).Formula (1) according to Reynolds number (Re):
Re=VD/ν …………………………………………………………（1）
The formula of flow velocity is as shown in the formula (2):
V=4Q/πD2…………………………………………………………（2）
Each alphabetical implication in its Chinese style (1) and the formula (2) is as follows: V is flow velocity (m/s), and Q is flow (m3/s), and D is bore (m), and ν is viscosity coefficient (m2/s).Think that flow has determined flow velocity, as long as therefore have enough flows, flow velocity also can guarantee, heel pressure is irrelevant.Like this design is wrong in fact, has ignored that the pressure loss can cause flushing unclean to the influence of flow in the key factor pipeline, from now on use has been stayed very big hidden danger, even can cause the paralysis of whole hydraulic system, and consequence is hardly imaginable.Utilize some formula to explain relation between flow velocity, flow and the pressure reduction three in detail with regard to this problem below.
According to formula (3):
ΔP=λ
………………………………………………………（3）
Wherein: λ is the on-way resistance coefficient, it is a constant behind definite pipeline and Reynolds coefficient, the L(m in formula), ρ (kg/m3), D(m) definite, can significantly find out, decided by flow velocity V along the stroke pressure loss this moment, and flow velocity greatly then crushing is big.In our practice, meet the demands at the hydraulic oil source flow, when if the setting pressure of hydraulic oil source does not reach the pressure of linear loss, ducted flow velocity will diminish, may just not reach the turbulent needed flow that produces in the pipeline, unnecessary part will flow back to fuel tank by overflow valve.For mounted pipeline, guarantee that flow velocity reaches requirement, then must guarantee effect at the pressure of pipeline greater than losing in the pipeline along stroke pressure.
For fixed hydraulic system, pipeline length, internal diameter, hydraulic oil is all selected, and temperature also is metastable, by formula (1), (2), (3) as seen, the relation of pressure reduction and the proportional exponential form of flow velocity, in other words, the flow velocity speed only depends on pressure reduction.Formula (1), (2) are right-on in fact, and what just determine the flow size also is pressure reduction.We know have pressure reduction just to have flow, and not having pressure reduction is can not produce flow, could realize turbulent flow so finally still will improve the pressure reduction at pipeline two ends.The scouring stage design that we can utilize above these formula to calculate proves prior art is problematic.Suppose the turbulent flow (Re=4000) that reaches rinsing requirement, V=ν Re/D=0.8m/s then, plain tube curb journey resistance coefficient λ=0.3164 * Re-0.25=0.3164 * 4000-0.25=0.0398.Q=847L/min; Δ P=0.0398*
*
=29bar, from above calculating as can be seen, although the screw pump flow is very big, only need 847L/min just much of that but flushing reaches turbulent flow, and the minimum pressure reduction 29bar of actual needs does not also reach as yet, system's overflow valve has reached setting pressure 15bar and has opened, most of flow is all got back to fuel tank by overflow valve, therefore so the in fact main acting of flushing all has been converted into the heating of overflow valve, and the actual flow in the pipeline can not thoroughly clean because of not reaching turbulent condition.Consider the pressure loss of shunting and bend pipe, therefore the Δ P that needs is generally more than 40bar.Suggestion can be used the high-pressure oil pump flushing, and return filter must be installed the higher filter of filtering accuracy in the return line, if generally require system's cleannes below the NAS7 level, to realize by return filter, then filter core requires filtering accuracy at β 3 〉=100 usually, and have pressure reduction and report to the police, guarantee timely replacing, avoid stopping up.
Those skilled in the art can carry out various remodeling and change to the utility model.Therefore, the utility model has covered various remodeling and the change in the scope that falls into appending claims and equivalent thereof.
Claims (3)
1. one kind big hydraulic pressure of pipe line rinse-system, it is characterized in that, described big hydraulic pressure of pipe line rinse-system comprises fuel tank, liquid level gauge, empty filter, electric heater, first butterfly valve, first compensator, screw pump, motor, second compensator, the 3rd compensator, the 4th compensator, check (non-return) valve, second butterfly valve, the 3rd butterfly valve, the 4th butterfly valve, return filter, temperature relay, liquid level relay, the ball valve of draining the oil, Sampling ball valve, pressure meter switch, Pressure gauge, the 5th butterfly valve, first pipeline, second pipeline, the 3rd pipeline, the 4th pipeline, liquid level gauge is positioned at the front of fuel tank, electric heater, the ball valve of draining the oil all is positioned at the side of fuel tank, empty filter, temperature relay, liquid level relay all is positioned at the end face of fuel tank, one end of screw pump is connected with first pipeline, motor is connected with the other end of screw pump, first butterfly valve, first compensator, second compensator, check (non-return) valve, second butterfly valve, the 3rd compensator is positioned on first pipeline successively, the 4th butterfly valve, pressure meter switch all is positioned on second pipeline, pressure meter switch is connected with Pressure gauge, the 4th compensator, the 3rd butterfly valve, Sampling ball valve all is positioned on the 3rd pipeline, return filter, the 5th butterfly valve is positioned on the 4th pipeline, first pipeline and fuel tank, second pipeline connects, second pipeline is connected with the 3rd pipeline, and the 3rd pipeline is connected with the 4th pipeline.
2. big hydraulic pressure of pipe line rinse-system as claimed in claim 1 is characterized in that, described big hydraulic pressure of pipe line rinse-system also comprises first welded flange and second welded flange, and first welded flange is connected with first pipeline, and second welded flange is connected with the 3rd pipeline.
3. big hydraulic pressure of pipe line rinse-system as claimed in claim 1 is characterized in that, described big hydraulic pressure of pipe line rinse-system also comprises spacer flanger, and spacer flanger is positioned on the 3rd pipeline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320061427 CN203076287U (en) | 2013-02-04 | 2013-02-04 | Large pipeline hydraulic flushing system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320061427 CN203076287U (en) | 2013-02-04 | 2013-02-04 | Large pipeline hydraulic flushing system |
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| Publication Number | Publication Date |
|---|---|
| CN203076287U true CN203076287U (en) | 2013-07-24 |
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ID=48822170
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320061427 Expired - Fee Related CN203076287U (en) | 2013-02-04 | 2013-02-04 | Large pipeline hydraulic flushing system |
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| Country | Link |
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| CN (1) | CN203076287U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103056136A (en) * | 2013-02-04 | 2013-04-24 | 康百世朝田液压机电(中国)有限公司 | Large-pipeline hydraulic flushing system |
| CN104895873A (en) * | 2014-03-05 | 2015-09-09 | 中石化胜利油建工程有限公司 | Oil feeder for cleaning hydraulic oil and hydraulic pipeline |
-
2013
- 2013-02-04 CN CN 201320061427 patent/CN203076287U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103056136A (en) * | 2013-02-04 | 2013-04-24 | 康百世朝田液压机电(中国)有限公司 | Large-pipeline hydraulic flushing system |
| CN104895873A (en) * | 2014-03-05 | 2015-09-09 | 中石化胜利油建工程有限公司 | Oil feeder for cleaning hydraulic oil and hydraulic pipeline |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130724 Termination date: 20140204 |