Читать книгу Hydraulic Fluid Power - Andrea Vacca - Страница 17

A possible representation of the hydraulic system is given by the figures below.

Alternative representation:

Remarks:

 The schematic in the top figure follows a left‐to‐right direction of representation. Starting from the prime mover positioned to the left, the schematic ends with the hydraulic function, or the actuator, at the right side of the schematic. As an alternative, the representation from bottom (prime mover) to top (actuator) is provided in the bottom figure.

Either of these two options for representing a hydraulic system is acceptable, and it usually increases the readability and facilitates a quick understanding of the functioning of the system.

 The schematic must represent the operation of the system during rest condition. In other words, the connections of the supply pump and those of the actuator must be aligned to the central (or neutral position) of the directional control valve (DCV). These connections are indicated with the letters P (connection to the supply pump), T (connection to tank), A, and B (actuator workports). This central (or neutral position) corresponds to the configuration of the system when the DCV is not actuated. In position 1 (parallel arrow), the hydraulic motor rotates in one direction (i.e. clockwise). In position 2 (crossed arrows), the hydraulic motor rotates in the opposite direction (i.e. counterclockwise).

 Most of the component details defined in the problem statement are useful information for the analysis of the system, and therefore they are reported in the schematic as suggested by ISO 1219. The construction type of the pump (axial piston pump) and of the motor (gear motor) is not provided because it is not essential for a basic study of the system. This additional information, such as the component manufacturer and the component code, and other information, can be reported in a separated table.

 The size of the component is not reflected in the size used for the corresponding symbol. For the case of this problem, the size of the circle used to represent the pump is the same of the one used to represent the hydraulic motor, even if the pump has a larger displacement.

 One pressure relief valve is used to protect the system against overpressurization. This relief valve is placed at the pump outlet, thus preventing the pump to supply fluid at a pressure higher than p*. A sophisticated control of the pump displacement might integrate this feature (this will be seen in Part 3). However, since it is unknown if the pump has a pressure limiting device integrated into its design, a relief valve is included in the figure above.

 The problem statement does not specify the neutral position of the DCV, although it specifies that in neutral the fan speed should be null.

As it will be seen later (Chapter 8), DCV can easily implement different options for the rest position. For this problem, the designer could choose among the options below.

In the hydraulic schematic shown above, the selected neutral position is (c). In this position all ports P, T, A, B are connected to tank. This allows the pump to divert the flow to the tank (which is the path of minimum effort for the fluid), thus maintaining the outlet port P at a minimum pressure. The motor ports are also connected to tank; therefore the fan will not rotate since no flow energy is provided to the hydraulic motor. Position (b) would be another reasonable solution, although it would require a pump able to adjust its instantaneous displacement to zero in rest conditions. Otherwise, in rest conditions, the pump would supply flow to the relief valve RV, thus at the maximum allowable pressure, requesting high energy to the CE. Position (a) and (d) would block the motor ports; this would cause excessive pressure at the motor workports when the fan is brought to a sudden stop through the DCV. Such positions would require additional relief valves to handle these transients.