scholarly journals Pressure Drop Equations for a Partially Penetrating Vertical Well in a Circular Cylinder Drainage Volume

2009 ◽  
Vol 2009 ◽  
pp. 1-33
Author(s):  
Jalal Farhan Owayed ◽  
Jing Lu

Taking a partially penetrating vertical well as a uniform line sink in three-dimensional space, by developing necessary mathematical analysis, this paper presents unsteady-state pressure drop equations for an off-center partially penetrating vertical well in a circular cylinder drainage volume with constant pressure at outer boundary. First, the point sink solution to the diffusivity equation is derived, then using superposition principle, pressure drop equations for a uniform line sink model are obtained. This paper also gives an equation to calculate pseudoskin factor due to partial penetration. The proposed equations provide fast analytical tools to evaluate the performance of a vertical well which is located arbitrarily in a circular cylinder drainage volume. It is concluded that the well off-center distance has significant effect on well pressure drop behavior, but it does not have any effect on pseudoskin factor due to partial penetration. Because the outer boundary is at constant pressure, when producing time is sufficiently long, steady-state is definitely reached. When well producing length is equal to payzone thickness, the pressure drop equations for a fully penetrating well are obtained.

2009 ◽  
Vol 2009 ◽  
pp. 1-34 ◽  
Author(s):  
Jing Lu ◽  
Tao Zhu ◽  
Djebbar Tiab ◽  
Jalal Owayed

Taking a partially penetrating vertical well as a uniform line sink in three-dimensional space, by developing necessary mathematical analysis, this paper presents steady state productivity formulas for an off-center partially penetrating vertical well in a circular cylinder drainage volume with constant pressure at outer boundary. This paper also gives formulas for calculating the pseudo-skin factor due to partial penetration. If top and bottom reservoir boundaries are impermeable, the radius of the cylindrical system and off-center distance appears in the productivity formulas. If the reservoir has a gas cap or bottom water, the effects of the radius and off-center distance on productivity can be ignored. It is concluded that, for a partially penetrating vertical well, different productivity equations should be used under different reservoir boundary conditions.


2021 ◽  
Author(s):  
A V Ogbamikhumi ◽  
E S Adewole

Abstract Dimensionless pressure gradients and dimensionless pressure derivatives characteristics are studied for horizontal and vertical wells completed within a pair of no-flow boundaries inclined at a general angle ‘θ’. Infinite-acting flow solution of each well is utilized. Image distances as a result of the inclinations are considered. The superposition principle is further utilized to calculate total pressure drop due to flow from both object and image wells. Characteristic dimensionless flow pressure gradients and pressure derivatives for the wells are finally determined. The number of images formed due to the inclination and dimensionless well design affect the dimensionless pressure gradients and their derivatives. For n images, shortly after very early time for each inclination, dimensionless pressure gradients of 1.151(N+1)/LD for the horizontal well and 1.151(N+1) for vertical well are observed. Dimensionless pressure derivative of (N+1)/2LD are observed for central and off-centered horizontal well locations, and (N+1)/2 for vertical well are observed. Central well locations do not affect horizontal well productivity for all the inclinations. The magnitudes of dimensionless pressure drop and dimensionless pressure derivatives are maximum at the farthest image distances, and are unaffected by well stand-off for the horizontal well.


1985 ◽  
Vol 25 (01) ◽  
pp. 113-120 ◽  
Author(s):  
Leif Larsen

Abstract General and simple algorithms are presented to determine the coordinates of sufficient numbers of image wells to compute pressure distributions and Matthews-Brons-Hazebroek (MBH) functions for rectangles of any shape, triangles with internal angles (30,60,90), (45,45,90), (60,60,60), and (30,30,120) degrees, rhombi with acute angle 60 degrees, and hexagons. A simple extension to compute their slopes also is included. The well must be located at the center of the hexagon, on the short diagonal of the rhombus, and on the corresponding height of the last triangle. For the other shapes there are no restrictions on well location. Any combination of no-flow and constant-pressure outer boundaries can be handled for pressure distributions in rectangles and (45,45,90) degrees triangles, but only special cases are possible for the other shapes. Introduction Matthews, Brons, and Hazebrock introduced the special function (p* -P)/(70.6qBu/kh) to determine the average pressure, P, from the Horner false pressure, p*, for closed homogeneous reservoirs of certain basic shapes. The reservoirs were assumed filled with a fluid of small and constant compressibility, and each was produced at a constant surface rate, q, from a single fully penetrating well with zero skin and no wellbore storage. With these conditions, it follows from results of Ramey and Cobb that the MBH function (1) can be expressed in the form (2) where (3) is dimensionless time based on the drainage area and (4) is dimensionless wellbore pressure drop. Note that the dimensionless time based on the wellbore radius is given by tD=AtDA/r2w The drainage shapes considered in this paper are similar to those in Ref. 1 in the sense that each can be generated by adding a regular infinite pattern of image wells to the actual well in an unbounded homogeneous reservoir, with all wells starting to produce or inject at time zero. If each well is a producer, then a closed drainage area is generated, while at least part of the outer boundary will remain at constant pressure otherwise. If qi denotes the rate of the ith well (negative for injecting wells) and q = q1>0 is the rate of the actual well, then (5) It is assumed here that the response of each well is given by the line-source solution, and that, and (xi, yi) is the location of the ith image well for i>2. In most cases considered in this paper, =. The dimensionless pressure drop, PD, at an arbitrary observation point ( ) within the drainage area, but outside the wellbore, is given by (6) (7) for the closed area drained by the well at the origin, with the infinite sum negligible for producing times in the infinite-acting period. To determine the linear and semilogarithmic slopes of PwD and PDMBH, note that (8) SpEJ P. 113^


Fuel ◽  
1991 ◽  
Vol 70 (11) ◽  
pp. 1303-1307 ◽  
Author(s):  
M.Kirk Green ◽  
E.Eddy Isaacs ◽  
John M. Smid

2021 ◽  
Vol 11 (2) ◽  
pp. 171-177
Author(s):  
Evgeny A. KRESTIN ◽  
Grigoriy V. SEREBRYAKOV

Non-contact seals with fl at slott ed gaps of drives of electric power systems used in switchgears of hydraulic units, as well as in pumps and hydraulic motors have been investigated. Calculation of seals based on average clearance results in an underestimation or overestimation of the leakage rate compared to the operational values. The regularity of the distribution of pressure and fl ow rate in the gap of a fl at conical slot is determined, and formulas for the fl ow rate (leakage) and friction forces acting on the walls of the conical slot are found. To solve the problem, the approximate Navier-Stokes and fl ow continuity equations are used. Several special cases of the fl ow of the working fl uid in diff erent gaps are considered: a plane-parallel gap with an oscillating wall and at a constant pressure gradient and a conical gap at diff erent ratios of the pressure drop and the frictional action of the moving channel wall. When the wall oscillates in a conical gap and constant pressure, the presence of an extremum is characteristic. In this case, an excess pressure appeared in the slott ed gap, creating a supporting force, and the pressure value became high enough. When the lower wall of the conical slot moves in the direction of the increasing gap, the pressure inside the slott ed channel, under certain conditions, can reach a complete vacuum, the value of which is limited by the bulk strength of the liquid and the pressure of saturated vapor at a given temperature. When the pressure drop and oscillations of the wall of the conical gap are additive, then at a suffi ciently high velocity of the wall movement, the pressure inside the slot can even increase and exceed the value of the supplied pressure.


Author(s):  
Duqiang Wu ◽  
Richard Burton ◽  
Greg Schoenau ◽  
Doug Bitner

A pressure compensated valve (PC valve) is a type of flow control device that is a combination of a control orifice and a compensator (often called a hydrostat). The compensator orifice modulates its opening to maintain a constant pressure drop across the control orifice. In other words, the PC valve is so designed that the flow rate through the valve is governed only by the opening of the control orifice and is independent of the total pressure drop across the valve. Because of the high non-linearities associated with this type of valve, it is impossible, in practice, to design such a valve where the flow rate is completely unaffected by the pressure drop across the valve. In this paper, the effect of the non-linerities on the performance of the PC valve is investigated. First, a generic non-liner model of a PC valve is developed. Using this model, all possible operating conditions can be determined. Then a linearized model is developed and used to analyze the dynamic behavior of the PC valve. The model can then be used to optimize the design and operation of the valve for specific applications.


2015 ◽  
Vol 138 (1) ◽  
Author(s):  
Xidong Zhang ◽  
Hulin Huang ◽  
Yin Zhang ◽  
Hongyan Wang

The predictions of flow structure, vortex shedding, and drag force around a circular cylinder are promoted by both academic interest and a wide range of practical situations. To control the flow around a circular cylinder, a magnetic obstacle is set upstream of the circular cylinder in this study for active controlling the separated flow behind bluff obstacle. Moreover, the changing of position, size, and intensity of magnetic obstacle is easy. The governing parameters are the magnetic obstacle width (d/D = 0.0333, 0.1, and 0.333) selected on cylinder diameter, D, and position (L/D) ranging from 2 to 11.667 at fixed Reynolds number Rel (based on the half-height of the duct) of 300 and the relative magnetic effect given by the Hartmann number Ha of 52. Results are presented in terms of instantaneous contours of vorticity, streamlines, drag coefficient, Strouhal number, pressure drop penalty, and local and average Nusselt numbers for various magnetic obstacle widths and positions. The computed results show that there are two flow patterns, one with vortex shedding from the magnetic obstacle and one without vortex shedding. The optimum conditions for drag reduction are L/D = 2 and d/D = 0.0333–0.333, and under these conditions, the pressure drop penalty is acceptable. However, the maximum value of the mean Nusselt number of the downstream cylinder is about 93% of that for a single cylinder.


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