Patent Description:
The present invention relates to construction machineries, in particular to a pressure-compensation controlled hydraulic pump, a rotation speed control system for a heat dissipation device of a construction machinery, and a construction machinery.

During the operation of a large-size construction machinery, some of the pressure energy in the hydraulic system is converted into heat energy, consequently the oil temperature in the hydraulic system is increased. To maintain the temperature of the hydraulic oil within a reasonable range, a heat dissipation device has to be utilized to dissipate the heat from the hydraulic oil. Large-size construction machineries, such as excavators and loaders, etc., usually employ a separate heat dissipation control system, which is to say, the input shaft of a cooling fan is not connected to the output shaft of the engine; instead, the cooling fan is driven by a hydraulic motor separately to rotate. <FIG> shows the heat dissipation control system of an excavator in the technology currently available, in which a cooling pump <NUM> is connected to the output shaft of an engine <NUM>, the hydraulic oil outputted from the cooling pump <NUM> enters a fan motor <NUM> to drive the fan motor <NUM> to rotate, thereby drives a fan <NUM> to rotate via the fan motor <NUM>. A temperature sensor <NUM> detects the temperature of the hydraulic oil and feeds the temperature back to a controller <NUM>, which determines a desired rotation speed of the fan <NUM> through corresponding operations and outputs certain current to an electric proportional overflow valve <NUM> at the same time, controls the pressure at the oil inlet of the fan motor <NUM> by adjusting the pressure of the electric proportional overflow valve <NUM>, thereby controls the rotation speed of the fan. However, in the working process of a construction machinery, the rotation speed of the engine <NUM> varies with the load, and the speed variation of the engine <NUM> leads to the variation of the rotation speed of the cooling pump <NUM>, consequently leads to the variation of the output flow rate of the cooling pump <NUM>; the fluctuations of the output flow rate of the cooling pump <NUM> result in fluctuations of the rotation speed of the fan motor <NUM>, thereby result in fluctuations of the rotation speed of the fan <NUM>. As a result, the rotation speed of the fan <NUM> cannot be stabilized at a demand value, resulting in an adverse effect on the heat dissipation effect of the hydraulic system on one hand and high noise of the fan <NUM> on the other hand.

In view of the above problems, it is desirable to design a pressure-compensation controlled hydraulic pump.

Document <CIT> discloses that a restriction mechanism <NUM> capable of varying its opening area is provided in the connection circuit for a variable displacement hydraulic pump <NUM> driven by a vehicle-mounted engine <NUM> and a fixed displacement hydraulic motor <NUM> for driving a cooling fan <NUM>. When the flow rate in the restriction mechanism <NUM> gets larger than a predetermined flow rate as well as the differential pressure, P1 -P2 , between the self-discharging pressure P1 and the load pressure P2 gets larger than a predetermined pressure, a control valve <NUM> is switched over to its second position to reduce the displacement of the hydraulic pump <NUM> by a variable displacement piston <NUM> and thus to allow only the predetermined flow rate into the restriction mechanism <NUM>. When the flow rate in the restriction mechanism <NUM> becomes, however, smaller than the predetermined flow rate as well as the differential pressure, P1 -P2 , becomes smaller than the predetermine pressure, the control valve <NUM> is switched over to its first position to increase the displacement of the hydraulic pump <NUM>.

A pressure-compensation controlled hydraulic pump is know from <CIT>.

The technical problem to be solved in a first aspect of the present invention is to provide pressure-compensation controlled hydraulic pump, which can stabilize the output flow rate of a hydraulic pump at a demand value.

The technical problem to be solved in a second aspect of the present invention is to provide a rotation speed control system for a heat dissipation device of a construction machinery, which can stabilize the rotation speed of a cooling fan at a demand value.

The technical problem to be solved in a third aspect of the present invention is to provide a construction machinery, which has a hydraulic system that achieves a good heat dissipation effect and a heat dissipation device that generates lower noise.

The solution to the technical problem is according to the claims.

Some embodiments of the present disclosure will be detailed below with reference to the accompanying drawings. It should be understood that the embodiments described herein are only provided to describe and explain the present disclosure, but are not intended to constitute any limitation to the present disclosure.

In the present disclosure, it should be noted that the terms "connect" and "arrange" shall be interpreted in their general meanings, for example, a connection may be a fixed connection, a detachable connection, or an integral connection; may be a direct connection or an indirect connection via an intermediate medium, or internal communication between two elements or interaction between two elements, unless otherwise specified and defined explicitly. Those having ordinary skills in the art may interpret the specific meanings of the terms in the present disclosure in their context.

The terms "first", "second" and "third" are only for a descriptive purpose, but shall not be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. Therefore, features defined by "first", "second" or "third" may expressly or impliedly include one or more features.

<FIG> shows a basic flow chart of the rotation speed control method for a heat dissipation device of a construction machinery provided in the present disclosure. Specifically, the oil temperature of hydraulic oil in a hydraulic system where the heat dissipation device is located is acquired first, a corresponding first pressure value is obtained according to the oil temperature of the hydraulic oil, and a corresponding second pressure value is generated according to a load pressure generated by the heat dissipation device; the first pressure value is compared with the second pressure value; and the displacement of a hydraulic pump for driving the heat dissipation device in the hydraulic system is adjusted according to a result of the comparison, so that the output flow rate of the hydraulic pump is stabilized within a preset flow rate range when the rotation speed of the hydraulic pump varies, thereby the rotation speed of the heat dissipation device is stabilized within a preset rotation speed range. Owing to the fact that the displacement of a hydraulic pump multiplied by the rotation speed of the hydraulic pump is equal to the flow rate of the hydraulic pump multiplied by time, the control method can adjust the displacement of the hydraulic pump in real time when the rotation speed of the hydraulic pump varies, so that the output flow rate of the hydraulic pump is essentially stabilized at a demand value, thereby the rotation speed of a heat dissipation device driven by the hydraulic pump is stabilized at a demand value, and the operation of the heat dissipation device is more stable.

Preferably, the displacement control mechanism of the hydraulic system comprises an electric proportional pressure compensator, a corresponding current value is obtained according to the oil temperature of the hydraulic oil, and a current value is inputted into the electric proportional pressure compensator to control an opening pressure of the electric proportional pressure compensator, wherein the opening pressure is a first pressure value.

Specifically, a pressure comparison module of the hydraulic system comprises a servo cylinder <NUM> for controlling the displacement and a hydraulic control reversing valve <NUM> for controlling the servo cylinder <NUM> to extend and retract, and the first pressure value and the second pressure value act on hydraulic control ports at the two ends of the hydraulic control reversing valve <NUM> respectively; the valve spool of the hydraulic control reversing valve <NUM> can move to the smaller one of the first pressure value and the second pressure value, thereby the first pressure value is compared with the second pressure value. The displacement of the hydraulic pump is controlled to increase when the rotation speed of the hydraulic pump is decreased and the first pressure value is greater than the second pressure value, and the displacement of the hydraulic pump is controlled to decrease when the rotation speed of the hydraulic pump is increased and the first pressure value is smaller than the second pressure value.

In an embodiment of the present invention, as shown in <FIG>, the pressure-compensation controlled hydraulic pump comprises an electric proportional pressure compensator <NUM>, a hydraulic pump <NUM>, a hydraulic control reversing valve <NUM>, and a servo cylinder <NUM> for adjusting the displacement of the hydraulic pump <NUM>. The electric proportional pressure compensator <NUM> is electrically connected to a controller <NUM>, so as to adjust an opening pressure of the electric proportional pressure compensator <NUM> via the controller <NUM>. As shown in <FIG>, usually the electric proportional pressure compensator <NUM> employs an inversely proportional control mode, i.e., the opening pressure can be decreased by increasing the current. The oil outlet of the hydraulic pump is connected to an internal output oil path <NUM>, the oil inlet of the hydraulic pump is connected to an internal input oil path <NUM>, a power drive device <NUM> is connected to the hydraulic pump <NUM> to supply power to the hydraulic pump <NUM>; thus, variations of the rotation speed of the power drive device <NUM> lead to variations of the rotation speed of the hydraulic pump <NUM> and further affect the output flow rate of the hydraulic pump <NUM>; the hydraulic pump <NUM> can drive an connected actuator element via a hydraulic circuit, and fluctuations of the output flow rate of the hydraulic pump <NUM> lead to fluctuations of the rotation speed of the actuator element. A first hydraulic control port <NUM> of the hydraulic control reversing valve <NUM> is connected to an internal oil drain path <NUM> via the electric proportional pressure compensator <NUM>, and the first hydraulic control port <NUM> is connected to an internal output oil path <NUM> via an hydraulic control oil inlet path <NUM> provided with a first throttle valve <NUM>, wherein the first throttle valve <NUM> attains pressure and flow rate regulation effects, so that the pressure at the first hydraulic control port <NUM> of the hydraulic control reversing valve <NUM> is smaller than the pressure at a second hydraulic control port <NUM>, the second hydraulic control port <NUM> of the hydraulic control reversing valve <NUM> is connected to the internal output oil path <NUM>, and the hydraulic control reversing valve <NUM> is preferably a two-position three-way directional control valve. A piston chamber of the servo cylinder <NUM> is connected to the internal output oil path <NUM> and the internal oil drain path <NUM> respectively via the hydraulic control reversing valve <NUM>, a pressure difference between an opening pressure of the electric proportional pressure compensator <NUM> and the pressure at the oil outlet of the hydraulic pump acts on a valve spool of the hydraulic control reversing valve <NUM> via the first hydraulic control port <NUM> and the second hydraulic control port <NUM> to drive the hydraulic control reversing valve <NUM> to perform reversing, thereby selectively enables the piston chamber of the servo cylinder <NUM> to be in communication with the internal output oil path <NUM> or the internal oil drain path <NUM>; the oil input into the piston chamber of the servo cylinder <NUM> or oil output from the piston chamber of the servo cylinder <NUM> makes a push rod of the servo cylinder <NUM> extend or retract, thereby adjusts the displacement of the hydraulic pump <NUM> by adjusting the inclination angle of a swash plate of the hydraulic pump <NUM>.

The working principle of the pressure-compensation controlled hydraulic pump in the above embodiment of the present invention is described below.

When the rotation speed of the power drive device <NUM> is increased and causes an increased rotation speed of the hydraulic pump <NUM>, as shown in <FIG>, the rotation speed of the actuator element is increased thereby the torque of the actuator element is increased, the load pressure generated by the actuator element is fed back to the oil outlet of the hydraulic pump, so that the pressure at the second hydraulic control port <NUM> is greater than the pressure at the first hydraulic control port <NUM>, and the electric proportional pressure compensator <NUM> reaches an opening pressure, the hydraulic oil in the internal output oil path <NUM> enters the valve via the second hydraulic control port <NUM> of the hydraulic control reversing valve <NUM>, and the hydraulic oil flows out of the first hydraulic control port <NUM>, passes through the electric proportional pressure compensator <NUM> to the internal oil drain path <NUM>, the valve spool moves and makes the piston chamber of the servo cylinder <NUM> in communication with the internal output oil path <NUM>, the oil flows into the piston chamber, and the displacement of the hydraulic pump is decreased; as the displacement of the hydraulic pump <NUM> is decreased gradually, the output flow rate of the hydraulic pump <NUM> is decreased, thereby the load pressure of the actuator element fed back to the oil outlet of the hydraulic pump is decreased; at that point, the pressure at the second hydraulic control port <NUM> is lower than the pressure at the first hydraulic control port <NUM>, the electric proportional pressure compensator <NUM> is closed because the pressure is lower than the opening pressure, the hydraulic oil in the hydraulic control oil inlet path <NUM> enters the valve via the first hydraulic control port <NUM>, and is drained via the second hydraulic control port <NUM>, the valve spool moves and makes the piston chamber of the servo cylinder <NUM> in communication with the internal oil drain path <NUM>, the oil is drained from the piston chamber, and the displacement of the hydraulic pump <NUM> is increased; thus, the opening pressure of the electric proportional pressure compensator <NUM> and the pressure at the oil outlet of the hydraulic pump are always kept in a dynamic balance state, thereby the output flow rate of the hydraulic pump <NUM> is maintained essentially at the demand value. To increase or decrease the output flow rate of the hydraulic pump <NUM>, the opening pressure of the electric proportional pressure compensator <NUM> may be increased or decreased.

Thus, when the rotation speed of the power drive device <NUM> varies, the servo cylinder <NUM> can adjust the displacement of the hydraulic pump <NUM>, so that the output flow rate of the hydraulic pump <NUM> is essentially stabilized at the demand value, thereby the rotation speed of the actuator element driven by the hydraulic pump is stabilized at the demand value, and the operation of the actuator element is more stable; moreover, by controlling the opening pressure of the electric proportional pressure compensator <NUM> via the controller <NUM>, the demand value of the output flow rate of the hydraulic pump <NUM> can be adjusted conveniently; the valve spool of the hydraulic control reversing valve <NUM> moves in small amplitudes continuously under the action of the opening pressure of the electric proportional pressure compensator <NUM> and the pressure at the oil outlet of the hydraulic pump to adjust the relative position in the valve body, so that oil flows into or out of the piston chamber of the servo cylinder <NUM>, thereby the output flow rate of the hydraulic pump <NUM> is adjusted accurately and sensitively. Specifically, the hydraulic pump <NUM> is a variable displacement plunger pump, the displacement of which can be adjusted more conveniently. The push rod of the servo cylinder <NUM> can adjust the displacement of the hydraulic pump <NUM> by adjusting the inclination angle of a swash plate of the variable displacement plunger pump.

Preferably, a second throttle valve <NUM> is provided in the connection oil path between the piston chamber of the servo cylinder <NUM> and the hydraulic control reversing valve <NUM>. The second throttle valve <NUM> can adjust the oil inflow rate and oil outflow rate of the piston chamber of the servo cylinder <NUM>; when the flow rate through the second throttle valve <NUM> is high, the response rate of the pressure-compensation controlled hydraulic pump is high, but the disturbances to the hydraulic oil and the impact on the pipeline in the system are high.

Preferably, a safety oil path <NUM> is connected between the piston chamber of the servo cylinder <NUM> and the internal oil drain path <NUM> and is provided with a third throttle valve <NUM>, one end of the safety oil path <NUM> is connected to the connection oil path between the piston chamber of the servo cylinder <NUM> and the hydraulic control reversing valve <NUM>, and the connection point is between the first throttle valve <NUM> and the second throttle valve <NUM>; the other end of the safety oil path <NUM> is connected to the internal oil drain path <NUM> at a position after the connection position of the oil outlet of the electric proportional pressure compensator <NUM>. The valve spool of the hydraulic control reversing valve <NUM> moves in small amplitudes continuously in the valve; when the valve spool is at a specific position, the hydraulic control reversing valve <NUM> is closed, making the piston chamber of the servo cylinder <NUM> a dead space, i.e., the oil path between the piston chamber and the hydraulic control reversing valve <NUM> becomes a rigid oil path. It should be noted that the first throttle valve, the second throttle valve and the third throttle valve may be replaced with damping holes.

As shown in <FIG>, based on the technical scheme of the above-mentioned pressure-compensation controlled hydraulic pump in the present invention, the present invention provides a rotation speed control system for a heat dissipation device of a construction machinery, which comprises a temperature sensor <NUM> for detecting the oil temperature of hydraulic oil, a fan motor <NUM> for driving a fan <NUM> to rotate, and a pressure-compensation controlled hydraulic pump, the hydraulic pump <NUM> of which is connected to a power drive device <NUM>, the power drive device <NUM> may be a common drive device, such as an engine or electric motor, etc., an internal input oil path <NUM> and an internal oil drain path <NUM> are connected to an oil tank <NUM>, a first working oil port A and a second working oil port B of the fan motor <NUM> are connected to a first working oil path <NUM> and a second working oil path <NUM> respectively, the first working oil path <NUM> and the second working oil path <NUM> are connected to a main oil inflow path <NUM> and a main oil return path <NUM> via a main reversing valve <NUM> to switch the fan motor <NUM> to rotate in a normal direction or a reversed direction, a controller <NUM> is electrically connected to the temperature sensor <NUM> to receive a signal from the temperature sensor <NUM> and controls an opening pressure of the electric proportional pressure compensator <NUM> according to the signal, thereby controls the displacement of the hydraulic pump <NUM> to adjust the rotation speed of the fan <NUM>.

The working principle of the rotation speed control system for a heat dissipation device of a construction machinery in the basic embodiments of the present invention is described below.

As shown in <FIG> and <FIG>, the pressure-compensation controlled hydraulic pump in the present invention is applied in a rotation speed control system for a heat dissipation device, the hydraulic pump drives the hydraulic oil to enter the main oil inflow path <NUM> and the second working oil path <NUM> sequentially, then flow back to the oil tank <NUM> through the first working oil path <NUM> and the main oil return path <NUM>, thereby an oil loop is formed to drive the fan motor <NUM> to rotate; when the fan motor <NUM> rotates in the normal direction, it can drive the fan <NUM> to rotate in the normal direction, thereby dissipate heat from the heat radiator; after the main reversing valve <NUM> performs reversing, the hydraulic pump <NUM> drives the hydraulic oil to enter the main oil inflow path <NUM> and the first working oil path <NUM> sequentially, then flows back to the oil tank <NUM> through the second working oil path <NUM> and the main oil return path <NUM>, thereby an oil loop is formed to drive the fan motor <NUM> to rotate in the reversed direction; when the fan motor <NUM> rotates in the reversed direction, it can drive the fan <NUM> to rotate in the reversed direction, thereby the dust on the heat radiator is blown off. When the rotation speed of the engine is increased so that the rotation speed of the hydraulic pump <NUM> is increased, the load pressure generated by the fan motor <NUM> is increased and fed back to the oil outlet of the hydraulic pump <NUM>, the opening pressure of the electric proportional pressure compensator <NUM> is lower than the pressure at the oil outlet of the hydraulic pump, and the displacement of the pressure-compensation controlled hydraulic pump is decreased adaptively; as the displacement of the hydraulic pump <NUM> is decreased gradually, the output flow rate of the hydraulic pump <NUM> is decreased, thereby the load pressure of the fan motor <NUM> fed back to the oil outlet of the hydraulic pump is decreased, the opening pressure of the electric proportional pressure compensator <NUM> is greater than the pressure at the oil outlet of the hydraulic pump, and the displacement of the pressure-compensation controlled hydraulic pump is increased adaptively. The temperature sensor sends the detected oil temperature to the controller <NUM>, which outputs corresponding current through operations to control the opening pressure of the electric proportional pressure compensator <NUM>, so as to increase or decrease the output flow rate of the hydraulic pump.

Thus, as shown in <FIG>, where C represents the rotation speed of the engine, D represents the rotation speed of a fan in the technology currently available, E represents the rotation speed of the fan in the present disclosure, F represents a target rotation speed of the fan. When the rotation speed of the engine varies, the displacement of the pressure-compensation controlled hydraulic pump can vary correspondingly, so that the output flow rate of the hydraulic pump <NUM> is essentially maintained at a demand value, thereby the rotation speed of the fan motor <NUM> is essentially maintained at a demand value; rotation speed E of the fan in the present disclosure is closers to the target rotation speed F of the fan, thereby a better heat dissipation effect can be attained, and the noise generated owing to the fluctuations of the rotation speed of the fan <NUM> can be avoided or effectively reduced.

Preferably, the oil tank <NUM> is a closed-type oil tank, to prevent impurities from mixed into the hydraulic oil and keep the hydraulic oil clean.

Preferably, a probe of the temperature sensor <NUM> is arranged at the bottom of the oil tank <NUM> to acquire the real-time oil temperature of the hydraulic oil. Of course, the probe of the temperature sensor <NUM> may be arranged at other positions as required according to the design.

An overflow valve <NUM> is provided between the main oil inflow path <NUM> and the main oil return path <NUM>, to control the pressure in the main oil inflow path <NUM> and control excessive oil to flow back to the oil tank <NUM>.

Preferably, the main reversing valve <NUM> is a solenoid directional control valve that is electrically connected to the controller <NUM>, and the controller <NUM> can control the main reversing valve <NUM> to perform reversing, so that the fan motor <NUM> is switched to rotate in the normal direction or reversed direction.

A check valve is connected in parallel between the two ends of the fan motor <NUM>, and can replenish oil to the second working oil port B of the fan motor <NUM> when the fan motor <NUM> rotates in the reversed direction. The fan motor <NUM> rotates in the normal direction in the normal state; when the fan motor <NUM> is switched to rotate in the reversed direction, the disturbances to the hydraulic oil in the system are higher, so as to prevent an excessive pressure at the second working oil port B of the fan motor <NUM>.

A construction machinery disclosed in the present invention comprises a heat radiator for cooling the hydraulic oil and the rotation speed control system for a heat dissipation device of a construction machinery according to any of the above technical schemes, wherein a fan motor <NUM> can drive the fan <NUM> to rotate to cool the heat radiator. Since the construction machinery disclosed in the present invention employs all technical schemes in the above embodiments, it at least has all beneficial effects brought by the technical schemes in the above embodiments.

While the present disclosure is described above in detail in some preferred embodiments with reference to the accompanying drawings, the present invention is not limited to those embodiments.

Claim 1:
A pressure-compensation controlled hydraulic pump, comprising a pressure control device, a hydraulic pump (<NUM>) and a displacement adjusting device, wherein the displacement adjusting device is adapted to compare a first pressure value generated by the pressure control device with a second pressure value at an oil outlet of the hydraulic pump, and to adjust the displacement of the hydraulic pump (<NUM>) according to a result of the comparison, so that the output flow rate of the hydraulic pump (<NUM>) is stabilized within a preset flow rate range when the rotation speed of the hydraulic pump (<NUM>) varies,
wherein the displacement adjusting device comprises a hydraulic control reversing valve (<NUM>) and a servo cylinder (<NUM>) for adjusting the displacement of the hydraulic pump (<NUM>), the oil outlet of the hydraulic pump is connected to an internal output oil path (<NUM>), an oil inlet of the hydraulic pump is connected to an internal input oil path (<NUM>), a first hydraulic control port (<NUM>) of the hydraulic control reversing valve (<NUM>) is connected to an internal oil drain path (<NUM>) via the pressure control device, a piston chamber of the servo cylinder (<NUM>) is connected to the internal output oil path (<NUM>) and the internal oil drain path (<NUM>) respectively via the hydraulic control reversing valve (<NUM>), a pressure difference between the pressure control device and an oil outlet pressure of the hydraulic pump acts on a valve spool of the hydraulic control reversing valve (<NUM>) via the first hydraulic control port (<NUM>) and a second hydraulic control port (<NUM>) of the hydraulic control reversing valve (<NUM>) to drive the hydraulic control reversing valve (<NUM>) to perform reversing, thereby selectively enables the piston chamber of the servo cylinder (<NUM>) to be in communication with the internal output oil path (<NUM>) or the internal oil drain path (<NUM>), and wherein the first hydraulic control port (<NUM>) is connected to the internal output oil path (<NUM>) through a hydraulic control oil inlet path (<NUM>) provided with a first throttle valve (<NUM>), and the second hydraulic control port (<NUM>) of the hydraulic control reversing valve (<NUM>) is connected to the internal output oil path (<NUM>).