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渣漿泵在交匯管路上工作的裝置特性
在石油生產(chǎn)中，礦區(qū)中各轉(zhuǎn)油站的原油匯集后輸往油庫(kù)的管路屬于交匯管路。
交匯管路與兩泵并聯(lián)不同，設(shè)兩泵分別從A、B兩油罐吸入油品,并經(jīng)過兩條相當(dāng)長(zhǎng)的管路1、2把油品送到匯合點(diǎn)O,然后經(jīng)一條管路3把油品送到儲(chǔ)油處C點(diǎn)，如圖1-49所示。這種管路系統(tǒng)的特點(diǎn)是:在整個(gè)系統(tǒng)工作時(shí),盡管兩臺(tái)泵性能不同,管1和管2的阻力、靜揚(yáng)程也不同,但油品從泵I和泵II輸送到O點(diǎn)后的剩余能頭必須相等。
(1) 圖解法。
交匯管路的工作狀況可以用性能曲線圖來分析。首先作出泵 I的性能曲線(H-Q)l和管路1的特性(h-Q)(包括泵I的吸入管和排出的總管路特性) .從泵I性能曲線的縱坐標(biāo)上減去同流量下管1的管路特生的縱坐標(biāo),即得出在不同流量下泵I輸送油品到O點(diǎn)的剩余揚(yáng)程曲線l。它表示從泵1給出的能頭中減去管1的阻力損失等能頭后還剩余的能頭，此剩余能頭是用來克服管3的阻力損失及將油品輸送到C處所需克服的位高能頭。按同樣的方法，可以作出泵lI輸送油品至0點(diǎn)后的剩余揚(yáng)程曲線lI。曲線I、lI就相當(dāng)于裝在0點(diǎn)處另兩泵的性能曲線。把曲線I和Il并聯(lián)相加,得并聯(lián)剩余揚(yáng)程曲線lll,它表示0點(diǎn)處油品在不同流量下的能頭大小。
作管3的管路特性與曲線lII相交于M點(diǎn),則M點(diǎn)為工作點(diǎn)，該點(diǎn)對(duì)應(yīng)的流量Qm就是管3中的流量Q3,必等于管1和管2中的流量和。M點(diǎn)的能頭為管1和管2匯合后的剩余能頭，也就是用來克服管3中阻力和位高差所需要的能頭。
為確定泵I和泵lI的工作點(diǎn)，過M點(diǎn)作水平線與曲線1和Il相交于點(diǎn)1和2.過點(diǎn)I和點(diǎn)2作垂線,分別交泵1性能曲線于M點(diǎn)，交菜口性能曲線于M,點(diǎn)。M點(diǎn)對(duì)應(yīng)的流量Q就是管1中的流量，M2點(diǎn)對(duì)應(yīng)的流量:就是管2中的流量。M點(diǎn)的縱坐標(biāo)即泵l的工作揚(yáng)程，M2點(diǎn)的縱坐標(biāo)即泵II的工作揚(yáng)程。
由此可見，只要掌握能量供應(yīng)和能量消耗的關(guān)系，就能在任何復(fù)雜工況下確定每臺(tái)泵的工作流量和工作揚(yáng)程，即工作點(diǎn)。
(2)解析法。
分別由兩臺(tái)渣漿泵實(shí)測(cè)或泵特性曲線上取點(diǎn)得到幾組揚(yáng)程、流量數(shù)據(jù)，用最小二乘法回歸得到泵的特性方程分別為:
泵l的特性方程 H1=a1-b1Q1
泵ll的特性方程 H2=a2-b2Q2
系數(shù)a1、b1、a2、b2可由式(1-69)計(jì)算得到。
管路1的特性方程為： h1=（z-z1）+k1Q1
管路2的特性方程為： h2=（z-z2）+k2Q2
管路3的特性方程為： h3=（z-z3）+k3Q3
Device characteristics of slurry pump working on the intersection pipeline
In oil production, the pipelines that the crude oil from each oil transfer station in the mining area is collected and then transported to the oil depot belong to the intersection pipelines.
Different from the parallel connection of two pumps, two pumps are set to draw oil from oil tanks a and B respectively, and then send the oil to the confluence point O through two rather long pipelines 1 and 2, and then send the oil to the oil storage point C through one pipeline 3, as shown in Figure 1-49. The characteristics of this pipeline system are as follows: during the operation of the whole system, although the performance of the two pumps is different, the resistance and static head of pipe 1 and pipe 2 are also different, the residual energy head after the oil is transported from pump I and pump II to point O must be equal.
(1) Graphic method.
The working condition of the intersection pipeline can be analyzed by performance curve. Firstly, the performance curve (H-Q) l of pump I and the characteristics (H-Q) of pipeline 1 (including the characteristics of suction pipe and discharge pipe of pump I) are made. The vertical coordinates of the special pipeline of pipeline 1 under the same flow are subtracted from the vertical coordinates of the performance curve of pump I, and the residual lift curve l of the oil delivered by pump I to o point under different flow is obtained. It represents the remaining energy head after subtracting the resistance loss and other energy heads of tube 1 from the energy head given by pump 1. The remaining energy head is used to overcome the resistance loss of tube 3 and the potential energy head to be overcome when delivering oil to place C. According to the same method, the remaining lift curve (LI) after the pump Li delivers the oil to the zero point can be made. Curve I and Li are equivalent to the performance curve of the other two pumps installed at point 0. By adding curve I and IL in parallel, the curve LLL of the remaining head in parallel is obtained, which represents the energy head size of the oil at point 0 under different flow rates.
If the pipeline characteristic of work pipe 3 intersects with the curve LII at point m, then point m is the work point, and the corresponding flow QM at this point is the flow Q3 in pipe 3, which must be equal to the flow sum of pipe 1 and pipe 2. The energy head at point m is the residual energy head after the combination of tube 1 and tube 2, which is the energy head needed to overcome the resistance and height difference in tube 3.
In order to determine the working points of pump I and pump Li, the horizontal line passing through point m intersects with curve 1 and IL at points 1 and 2. The vertical line passing through point I and point 2 intersects with pump 1 performance curve at point m, and the performance curve passing through point m, respectively. The flow Q corresponding to point m is the flow in tube 1, and the flow corresponding to point M2 is the flow in tube 2. The ordinate of point m is the working head of pump L, and the ordinate of point M2 is the working head of pump II.
Thus, as long as we master the relationship between energy supply and energy consumption, we can determine the working flow and head of each pump under any complex working condition, that is, the working point.
(2) Analytical method.
Several groups of head and flow data are obtained from the actual measurement of two slurry pumps or the points on the pump characteristic curve. The characteristic equations of the pumps are obtained by least square regression
Characteristic equation of pump l H1 = a1-b1q1
Characteristic equation of pump ll h2 = a2-b2q2
The coefficients A1, B1, A2 and B2 can be calculated by formula (1-69).
The characteristic equation of pipeline 1 is: H1 = (z-z1) + k1q1
The characteristic equation of pipeline 2 is: h2 = (z-z2) + k2q2
The characteristic equation of pipeline 3 is: H3 = (z-z3) + k3q3
