Common use of Initial Design Clause in Contracts

Initial Design. The initial design of the SD-CPRT was derived with ADT’s TURBOdesign suite at prototype scale. Figure 1 shows the two runners 3D geometry. Note that Rotor1 has 8 runner blades and Rotor2 has 7 runner blades. Figure 1 : Geometry of Rotor 1 and Rotor 2 Table 1summarises the input data to TURBOdesign in order to generate the blade profiles depicted at Figure 1. A constant work coefficient is specified at the trailing and leading edges of the runners, and a constant thickness of 60 mm is used. As can been seen in Table 1, the design flow rate is 130 𝑚3/𝑠 in pump mode and the two runners rotate in opposite directions. The second runner rotates at 90 % of the speed of the first runner. Meanline Design Details Shaft Driven Flow rate [m3/s] 130 Rotor1 speed [rev/min] 50 Rotor2 speed [rev/min] 45 Hub Diameter [mm] 3502 Shroud Diameter [mm] 6064 Maximum rotor1 axial span [mm] 773 Maximum rotor2 axial span [mm] 1220 Minimum axial gap between rotors [mm] 200 Table 1 : Main parameters from TURBOdesign Pre 2.1 Performance, CFD a) Efficiency b) Head c) Power Figure 2 : Efficiency, head, and power as a function of volumetric flow rate in pump mode for the initial design of the SD-CRPT Figure 3shows the corresponding efficiency, flow rate, and power, in turbine mode displayed as a function of total-to-static head. The results indicate a relatively high efficiency over a head range of 8- 16 m but efficiency drops very rapidly below 8 m head. The volumetric flow rate and power depicted show that both the power and flow rate increase linearly with the increase of head. a) Efficiency b) Volumetric flow rate c) Power Figure 3 : Efficiency, volumetric flow rate, and power as a function of total-to-static head in turbine mode for the initial design of the SD-CRPT

Initial Design. The initial design of the SDRD-CPRT was derived with ADT’s TURBOdesign suite [1] at prototype scale. The software uses a 3D inverse design method [2], [3] and [4] to design the blade shape for a given distribution of blade loading (pressure jump across the blade). It can be used for axial, mixed flow or centrifugal configurations and can easily handle contra-rotating stages. Figure 1 shows the two runners 3D geometrygeometry of the initial contra-rotating stage designed by TURBOdesign Suite. Note that Rotor1 has 8 runner blades and Rotor2 has 7 runner blades. Figure 1 : Geometry of Rotor Initial RD-CRPT designed at Prototype scale Table 1 summarises the dimensions and Rotor 2 Table 1summarises design parameters used to create the input data to initial design of RD- CRPT by using TURBOdesign Suite. As in order to generate the blade profiles depicted at Figure 1. A constant work coefficient is specified at the trailing and leading edges case of the runners, and a constant thickness of 60 mm is used. As can been seen in Table 1, shaft driven design the design flow rate is 130 𝑚3/𝑠 in pump mode and the two runners rotate in opposite directions. The second runner rotates at 90 % otwo runners have f thsame rotational e speed of the first runn50 RPM and a constant thickness of 60 mm is used for both runnerser. Meanline Design Details ShafRim t Driven Flow rate [m3/s] 130 Rotor1 speed [rev/min] 50 Rotor2 speed [rev/min] 4-50 5 Hub Diameter [mm] 3501000 2 Shroud Diameter [mm] 6065939 4 Maximum rotor1 axial span [mm] 77983 3 Maximum rotor2 axial span [mm] 122875 0 Minimum axial gap between rotors [mm] 20245 Rotor1 blade count 8 Rotor2 blade count 7 0 Table 1 : Maidesign n parameters from TURBOdesign Pfor the RD-CRPT Stagere 2.1 Performance, CFD a) Efficiency b) Head c) Power Figure 2 : Efficiency, head, and powePerformance of initial design for CR-RDPT - Pump mode The results for turbine mode are shown in Figure 3. The results for turbine are shown r as a function of volumetric flow rate in pump mode for the initial design of the SD-CRPT Figure 3shows the corresponding efficiency, flow rate, and power, in turbine mode displayed as a function of total-Totalto-static head. The results indicatthat the machine has e a relatively higfairly constant h efficiency over a head range of 8around 90% between 9-- 16 head m buthe t efficiency drops very rapidly below 8 m he9 m, see Figure 3(a)ad. The volumetric flow rate and powepower, r depictein Figure 3 (b) and (c), d show that both the power and flow rate increase linearly with the increase of head. a) Efficiency b) Volumetric floFlow w rate c) Power Figure 3 : Efficiency, volumetric flow rate, and power as a functioPerformance n of total-to-static head in turbine mode for the initial design of the for CRSD-CRRDPT – Turbine mode‌PT