They identified a maximum in correspondence with the stagnation region, because in this area the boundary layer thickness is at minimum. A secondary peak may be present at a certain distance; several numerical and experimental studies have focused on this phenomenon [5; 6; 7; 8; 9]. The laminar boundary layer (in the stagnation point) becomes turbulent after a transition region, which leads to an improvement in the mass transfer in the normal direction to the wall. Furthermore, in the wall jet region, the flow bend accelerates the stream causing a heat exchange increase. Heat exchange intensity decreases because the cross-sectional flow area in the jet region increases. Experiments performed by [PERSON] [10] found that the turbulence development in the free jet influences the local trend of heat exchange and the Nusselt number in the stagnation region. For shaped nozzles at a high distance from the wall (H/D > 5) or for jets from a long pipe, the Nusselt trend has a peak just on the jet axis. For shaped nozzles placed close to the wall, with low inlet turbulence (Tu \(\sim\) 1%), the maximum Nusselt value is reached in the range 0.4 < r/D < 0.6, while a local minimum (95% of the peak value) is located at r = 0. Numerical simulations performed by [PERSON] and [PERSON] [11] show that mass and heat transfer in the deceleration zone is dominated by large-scale eddies, in contrast to the wall jet phenomena, where the shear stresses are dominant. Figure 1: Flow regions of a jet impingement [1]. Most of the literature studies conducted on the jet impingement phenomenon concern single circular jets, while less effort of research is devoted to the slot jet configuration, as in Figure 2. Slot jet configuration consists of a long slot having a width B, which creates a long and thin jet, with a two-dimensional velocity profile. From a theoretical point of view, a single round jet concentrates the heat exchange in the impingement area, while a slot jet configuration guarantees a more uniform exchange. Theoretical and experimental researches on such an impingement configuration have been found and can be mentioned following a time evolution. [PERSON] et al. (2012) and [PERSON] et al. (2013) measured the Nusselt distribution by varying the main influence parameters. [PERSON] (1974) studied the aspect ratio influence on outflow problems from rectangular flared outflow jets. [PERSON] et al. (2015); [PERSON] et al. (2016); [PERSON] and [PERSON] (2017) developed a mathematical model for calculating the heat release in turbulent impinging premixed flames by comparing different eddy viscosity turbulence models and including the thermal radiation. [PERSON] and [PERSON] (2017) carried out experiments on rectangular jets, flared by 45\({}^{\circ}\) at the outlet, in order to investigate the flow structure and the heat exchange, by varying the nozzle-wall distance and the Reynolds number. [PERSON] and [PERSON] (2019) experimentally investigated the flow field of a confined turbulent slot air jet impinging normally on a moving flat surface. Experiments were conducted for a nozzle-to-plate spacing of eight slot nozzle widths, at three jet Reynolds numbers (Re = 5300, 8000, and 1.06 \(\times\) 10\({}^{4}\)) and four surface-to-jet velocity ratios of 0, 0.25, 0.5, and 1. It appeared that the flow field patterns at a given surface-to-jet velocity ratio are independent of the jet Reynolds number in the range of 5300-1.06 \(\times\) 10\({}^{4}\). A slight modification of the flow field was observed for a surface-to-jet velocity ratio of 0.25 whereas at higher ratios of 0.5 and 1, the flow field was significantly affected. [PERSON] and [PERSON] (2017) investigated numerically the heat transfer due to a confined turbulent slot-jet impinging on a hot moving plate for a range of the jet exit Reynolds number, plate velocity, and jet to plate distance, using the standard k-\(\varepsilon\) turbulence model with enhanced wall treatment to calculate the eddy viscosity. [PERSON] et al.