The present disclosure relates to a hydraulic unit.
A known hydraulic unit includes a motor that drives a hydraulic pump and an air-cooling cooler that cools a hydraulic oil. The motor and the air-cooling cooler are cooled by means of an air flow generated by a fan (see, for example, JP 2008-8252 A.
A hydraulic unit according to a first aspect of the present disclosure includes an oil tank, a hydraulic pump, a first return pipe, and a first heat exchanger. The oil tank stores a hydraulic oil. The hydraulic pump supplies the hydraulic oil in the oil tank to an actuator. The first return pipe returns the hydraulic oil from a flow path between a discharge port of the hydraulic pump and the actuator to the oil tank. The first heat exchanger causes a coolant to exchange heat with the hydraulic oil returning to the oil tank through the first return pipe.
Embodiments will be described below. In the drawings, the same reference numerals represent the same or corresponding parts. In addition, the dimensions on the drawings, such as lengths, widths, thicknesses, and depths, are appropriately changed from actual scales for clarity and simplification of the drawings, and do not represent actual relative dimensions. In the drawings, a left-right direction is defined as an X-axis direction, a front-rear direction is defined as a Y-axis direction, and an up-down direction is defined as a Z-axis direction.
As illustrated in
In
As illustrated in
The controller 60 includes a device (an element, a part, or a component) 61 of an inverter circuit (not illustrated) and a heat sink 62 thermally coupled to the device 61, the device 61 driving the motor 40. A pipe L5 into which the cooling water flows from a pipe L4 is in thermal contact with the heat sink 62. The pipe L5 and the heat sink 62 constitute a second heat exchanger 80. The controller 60 includes a central processing unit (CPU), a memory, and an input/output circuit. The device 61 is a power semiconductor such as an insulated gate bipolar transistor (IGBT).
The cooling water from the second heat exchanger 80 flows into a pipe L6 that is in thermal contact with the housing 40a of the motor 40. The pipe L6 and the housing 40a of the motor 40 constitute the third heat exchanger 90.
In the first heat exchanger 70, the hydraulic oil from the hydraulic pump 30 flows into a flow path between an outer peripheral surface of an inner pipe 70a and an inner peripheral surface of an outer pipe 70b through the pipe L1. The hydraulic oil returns from the flow path to the oil tank 10 through the pipe L2.
The cooling water supplied from an external supply source flows into the inner pipe 70a of the first heat exchanger 70 through the pipe L3. The cooling water from the inner pipe 70a flows out through the pipe L4. Alternatively, the cooling water may flow between the outer peripheral surface of the inner pipe 70a and the inner peripheral surface of the outer pipe 70b of the first heat exchanger 70.
Next, the cooling water from the pipe L4 flows into the pipe L5 of the second heat exchanger 80 to cause the second heat exchanger 80 to cool the heat sink 62 of the controller 60. Accordingly, the device 61 thermally coupled to the heat sink 62 is cooled.
Next, the cooling water from the second heat exchanger 80 flows into the pipe L6 of the third heat exchanger 90 to cause the third heat exchanger 90 to cool the motor 40. Then, the cooling water from the third heat exchanger 90 is discharged to the outside through the electromagnetic valve V1 and the drain pipe L7.
The cooling water given herein is an example of a coolant, and in this embodiment, industrial water is used. As the coolant, for example, cooling water supplied from a cooling water circulation device or the like may be used.
As illustrated in
Alternatively, as illustrated in
As illustrated in
The hydraulic unit 1 has the pump port P connected to the main machine through a pipe (not illustrated). Although not illustrated, the hydraulic unit 1 has a tank ports T1 and T2 connected to the main machine through pipes. The hydraulic pump 30 sucks the hydraulic oil in the oil tank 10 through the suction strainer 32 and the suction pipe 31, and discharges the hydraulic oil from the discharge port 30a.
The hydraulic oil is returned to the oil tank 10 through the relief valve 50 and the drain hose L10. The hydraulic oil is returned from a flow path between the discharge port 30a of the hydraulic pump 30 and the actuator to the oil tank 10 through a throttle 51 and the pipes L1 and L2. The pipes L1 and L2 are examples of the first return pipe.
In the present embodiment, the hydraulic oil is returned to the oil tank 10 through the relief valve 50 and the drain hose L10, or alternatively, the outlet of the relief valve 50 may be connected to the inlet of the hydraulic pump 30 through a pipe.
The controller 60 controls the number of rotations of the motor 40 and opens and closes the electromagnetic valve V1 on the basis of a pressure command signal or a flow rate command signal from the main machine, a pressure signal from the pressure sensor PS1, or the like. In the present embodiment, the hydraulic pump 30 of a fixed displacement type is used, or alternatively, a hydraulic pump of a variable displacement type may be used.
Since how the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 are connected has been described with reference to
In
With the hydraulic unit 1 configured as described above, when the hydraulic oil is returned from a flow path between the discharge port 30a of the hydraulic pump 30 and the actuator to the oil tank 10 through the pipes L1 and L2 (first return pipe), the first heat exchanger 70 causes the coolant to exchange heat with the hydraulic oil returning to the oil tank 10 through the pipes L1 and L2. Therefore, it is possible to increase performance of cooling the hydraulic oil even under an environment where the ambient temperature is high.
The first heat exchanger 70 of double-pipe structure includes the inner pipe 70awith a multi-lobed cross section and the outer pipe 70b accommodating the inner pipe 70a. Thus, the use of the first heat exchanger 70 allows an increase in the performance of cooling the hydraulic oil in the first heat exchanger 70 that can be downsized.
The second heat exchanger 80 causes the coolant to exchange heat with the device 61 that drives the motor 40, so that it is possible to increase performance of cooling the device 61 as compared with air cooling.
The third heat exchanger 90 causes the coolant to exchange heat with the motor 40 that drives the hydraulic pump 30, so that it is possible to increase performance of cooling the motor 40 as compared with air cooling.
The first heat exchanger 70 can cool the hydraulic oil, and the second and third heat exchangers 80 and 90 can cool the device 61 and the motor 40. It is further possible to simplify, by connecting the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 in series, a piping configuration for the coolant. It is further possible to cause the electromagnetic valve V1 (flow rate control valve) to simultaneously regulate the flow rate of the coolant supplied to the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90. The first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 are connected in series in the order of the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90.
The first heat exchanger 70 first cools the hydraulic oil to increase the temperature of the coolant so that the second and third heat exchangers 80 and 90 have temperatures at which the device 61 and the motor 40 are prevented from suffering from water condensation. Closing the electromagnetic valve V1 (flow rate control valve) prevents the cooling water from flowing to the second and third heat exchangers 80 and 90, so that it is possible to prevent the device 61 and the motor 40 from suffering from water condensation due to excessive cooling.
The hydraulic unit 1 includes a first temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10, a second temperature sensor (not illustrated) that detects the temperature of the device 61, and a third temperature sensor (not illustrated) that detects the temperature of the motor 40. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 by controlling to open and close the electromagnetic valve V1 in accordance with the temperature of the hydraulic oil detected by the first temperature sensor, the temperature of the device 61 detected by the second temperature sensor, and the temperature of the motor 40 detected by the third temperature sensor. Here, the electromagnetic valve V1 is controlled on the basis of pulse width modulation (PWM) control. Alternatively, the third temperature sensor may detect the temperature of the housing 40a of the motor 40, the temperature of a coil, or the like.
The above-described hydraulic unit 1 can realize liquid cooling of the hydraulic oil, the device 61 of the controller 60, and the motor 40 while suppressing the occurrence of water condensation with a size equivalent to the size of a known air-cooled hydraulic unit.
In this embodiment, the flow rate of the coolant supplied to the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 is regulated by the electromagnetic valve V1, or alternatively, a flow rate control valve capable of controlling the opening degree continuously or in multiple levels may be used instead of the electromagnetic valve V1. In this case, the opening degree of the flow rate control valve is controlled in accordance with the temperature of the hydraulic oil, the temperature of the device 61, and the temperature of the motor 40.
Alternatively, as illustrated in
In
Alternatively, as illustrated in
In the hydraulic unit 1 according to the first embodiment illustrated in
The cooling water supplied from the external supply source flows into the first heat exchanger 70 through the electromagnetic valve V11 and a pipe L13, and flows out from the first heat exchanger 70 through a pipe L14.
The cooling water supplied from the external supply source flows into the second heat exchanger 80 through a pipe L17, and flows out from the second heat exchanger 80 through a pipe L18 and the electromagnetic valve V12.
The cooling water supplied from the external supply source flows into the third heat exchanger 90 through a pipe L15, and flows out from the third heat exchanger 90 through a pipe L16 and the electromagnetic valve V13.
The hydraulic unit 2 according to the second embodiment has the same effect as the hydraulic unit 1 of the first embodiment has. The electromagnetic valve V11 can regulate the flow rate of the coolant supplied to the first heat exchanger 70, the electromagnetic valve V12 can regulate the flow rate of the coolant supplied to the second heat exchanger 80, and the electromagnetic valve V13 can regulate the flow rate of the coolant supplied to the third heat exchanger 90.
The hydraulic unit 2 includes a first temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10, a second temperature sensor (not illustrated) that detects the temperature of the device 61, and a third temperature sensor (not illustrated) that detects the temperature of the motor 40. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 by controlling to open and close the electromagnetic valve V11, V12, and V13 in accordance with the temperature of the hydraulic oil detected by the first temperature sensor, the temperature of the device 61 detected by the second temperature sensor, and the temperature of the motor 40 detected by the third temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valve V11 (first flow rate control valve) to regulate the flow rate of the coolant flowing through the first heat exchanger 70, so as to make a temperature To of the hydraulic oil higher than or equal to a predetermined first hydraulic oil temperature To1 and lower than or equal to a predetermined second hydraulic oil temperature To2 (>To1). The controller 60 can keep the device 61 at an appropriate temperature by controlling the electromagnetic valve V12 (second flow rate control valve) to regulate the flow rate of the coolant flowing through the second heat exchanger 80, so as to make a temperature Td of the device 61 higher than or equal to a predetermined first device temperature Td1 and lower than or equal to a predetermined second device temperature Td2 (>Td1). The controller 60 can keep the motor 40 at an appropriate temperature by controlling the electromagnetic valve V13 (third flow rate control valve) to regulate the flow rate of the coolant flowing through the third heat exchanger 90, so as to make a temperature Tm of the motor 40 higher than or equal to a predetermined first motor temperature Tm1 and lower than or equal to a predetermined second motor temperature Tm2 (>Tm1). Setting the device 61 at the predetermined second device temperature Td2 makes it possible to suppress heat-induced deterioration.
Setting the motor 40 at the predetermined second motor temperature Tm2 makes it possible to suppress heat-induced deterioration.
Here, the first device temperature Td1 is a temperature at which the device 61 is prevented from suffering from water condensation, and the first motor temperature Tm1 is a temperature at which the motor 40 is prevented from suffering from water condensation.
The above-described hydraulic unit 2 according to the second embodiment has the same effect as the hydraulic unit 1 of the first embodiment has.
As illustrated in
The hydraulic unit 3 includes a flow path switching valve V2 that switches whether the discharge port 30Aa of the hydraulic pump 30A is connected to a pipe close the discharge port 30Ba of the hydraulic pump 30B or the discharge port 30Aa of the hydraulic pump 30A is connected to a pipe L1B. A check valve 53 that regulates the flow of the hydraulic oil toward the hydraulic pump 30B is provided between the discharge port 30Ba of the hydraulic pump 30B and the pump port P. A throttle 54 is connected in parallel to the check valve 53.
The flow path switching valve V2 switches whether to cause the hydraulic pump 30B to solely control the pressure and flow rate at the pump port P or to cause both the hydraulic pump 30A and the hydraulic pump 30B to control the pressure and flow rate at the pump port P.
The pump port P of the hydraulic unit 3 is connected to the main machine through a pipe (not illustrated). The tank ports T1 and T2 of the hydraulic unit 3 is connected to the main machine through pipes (not illustrated). The hydraulic pump 30A sucks the hydraulic oil in the oil tank 10 through the suction strainer 32 and the suction pipe 31, and discharges the hydraulic oil from the discharge port 30Aa. The hydraulic pump 30B sucks the hydraulic oil in the oil tank 10 through the suction strainer 32 and the suction pipe 31, and discharges the hydraulic oil from the discharge port 30Ba. The suction pipe 31 branches off at its upper side to connect to the respective inlet ports of the hydraulic pumps 30A and 30B.
The hydraulic oil is returned from a flow path between the discharge port 30Aa of the hydraulic pump 30A and the actuator to the oil tank 10 through the relief valve 50A, the pipe L1B, a heat exchanger 70B, and a pipe L2B. The hydraulic oil is returned from a flow path between the discharge port 30Ba of the hydraulic pump 30B and the actuator to the oil tank 10 through the relief valve 50B, the pipe L1B, the heat exchanger 70B, and the pipe L2B. The hydraulic oil is returned from a flow path between the discharge port 30Ba of the hydraulic pump 30B and the actuator to the oil tank 10 through a throttle 52, a pipe L1A, a heat exchanger 70A, and a pipe L2A. The pipes L1A, L1B, L2A, and L2B are examples of the first return pipe. The heat exchangers 70A and 70B are examples of the first heat exchanger.
The cooling water supplied from the external supply source flows into the heat exchanger 70A through an electromagnetic valve V21A and a pipe L11A, and flows out from the heat exchanger 70A through a pipe L12A. The cooling water supplied from the external supply source flows into the heat exchanger 70B through an electromagnetic valve V21B and a pipe L11B, and flows out from the heat exchanger 70B through a pipe L12B.
The cooling water supplied from the external supply source flows into the second heat exchanger 80 through an electromagnetic valve V22 and a pipe L21, and flows out from the second heat exchanger 80 through a pipe L22.
The cooling water supplied from the external supply source flows into the third heat exchanger 90 through an electromagnetic valve V23 and a pipe L31, and flows out from the third heat exchanger 90 through a pipe L32.
The controller 60 controls the number of rotations of the motor 40 and opens and closes the electromagnetic valve V21A, V21B, V22, or V23 on the basis of the pressure command signal or the flow rate command signal from the main machine, the pressure signal from the pressure sensor PS1, or the like. In the present embodiment, the hydraulic pumps 30A and 30B of a fixed displacement type is used, or alternatively, a hydraulic pump of a variable displacement type may be used.
With the hydraulic unit configured as described above, when the hydraulic oil is returned from a flow path between the discharge ports 30Aa and 30Ba of the hydraulic pumps 30A and 30B and the actuator to the oil tank 10 through the pipes L1A, L1B, L2A, and L2B (first return pipes), the heat exchangers 70A and 70B (first heat exchanger) cause the coolant to exchange heat with the hydraulic oil returning to the oil tank 10 through the pipes L1A, L1B, L2A, and L2B. Thus, it is possible to increase the performance of cooling the hydraulic oil even under an environment where the ambient temperature is high. Since the heat exchangers 70A and 70B (first heat exchanger) of double-pipe configuration have no joint and thus have high strength as compared with the oil cooler of the known air-cooled hydraulic unit, the heat exchanger 70B can cool the hydraulic oil flowing through the pipe L1B, which is a flow path in which surge pressure is generated.
It is possible to increase the heat exchange efficiency of the heat exchangers 70A and 70B (first heat exchanger) and further increase the performance of cooling the hydraulic oil by using, for the heat exchangers 70A and 70B, a double pipe increasing the inner pipe 70a with a multi-lobed cross section and the outer pipe 70b accommodating the inner pipe 70a illustrated in
The second heat exchanger 80 causes the coolant to exchange heat with the device 61 that drives the motor 40, so that it is possible to increase the performance of cooling the device 61 as compared with air cooling.
The third heat exchanger 90 causes the coolant to exchange heat with the motor 40 that drives the hydraulic pumps 30A and 30B, so that it is possible to increase the performance of cooling the motor 40 as compared with air cooling.
The hydraulic unit 3 according to the third embodiment can cause the electromagnetic valve V21A (first flow rate control valve) to regulate the flow rate of the coolant supplied to the heat exchanger 70A, cause the electromagnetic valve V21B (first flow rate control valve) to regulate the flow rate of the coolant supplied to the heat exchanger 70B, cause the electromagnetic valve V22 (second flow rate control valve) to regulate the flow rate of the coolant supplied to the second heat exchanger 80, and cause the electromagnetic valve V23 (third flow rate control valve) to regulate the flow rate of the coolant supplied to the third heat exchanger 90.
The hydraulic unit 3 includes a first temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10, a second temperature sensor (not illustrated) that detects the temperature of the device 61, and a third temperature sensor (not illustrated) that detects the temperature of the motor 40. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70, the second heat exchanger 80, and the third heat exchanger 90 by controlling to open and close the electromagnetic valves V21A, V21B, V22, and V23 in accordance with the temperature of the hydraulic oil detected by the first temperature sensor, the temperature of the device 61 detected by the second temperature sensor, and the temperature of the motor 40 detected by the third temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valves V21A and V21B (first flow rate control valve) to regulate the flow rate of the coolant flowing through the first heat exchangers 70A and 70B, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1). The controller 60 can keep the device 61 at an appropriate temperature by controlling the electromagnetic valve V22 to regulate the flow rate of the coolant flowing through the second heat exchanger 80, so as to make the temperature Td of the device 61 higher than or equal to the predetermined first device temperature Td1 and lower than or equal to the predetermined second device temperature Td2 (>Td1). The controller 60 can keep the motor 40 at an appropriate temperature by controlling the electromagnetic valve V22 to regulate the flow rate of the coolant flowing through the third heat exchanger 90, so as to make the temperature Tm of the motor 40 higher than or equal to the predetermined first motor temperature Tm1 and lower than or equal to the predetermined second motor temperature Tm2 (>Tm1).
Here, the first device temperature Td1 is a temperature at which the device 61 is prevented from suffering from water condensation, and the first motor temperature Tm1 is a temperature at which the motor 40 is prevented from suffering from water condensation.
In this embodiment, the flow rate of the coolant supplied to each of the heat exchangers 70A and 70B, the second heat exchanger 80, and the third heat exchanger 90 is regulated by controlling to open and close the electromagnetic valves V21A, V21B, V22, and V23, or alternatively, a flow rate control valve capable of controlling the opening degree continuously or in a multiple levels may be used instead of the electromagnetic valves V21A, V21B, V22, and V23.
In the third embodiment, the two heat exchangers 70A and 70B are used as the first heat exchanger, or alternatively, as illustrated in
In
As illustrated in
The hydraulic unit 4 includes a first temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70 by controlling to open and close the electromagnetic valve V1 in accordance with the temperature of the hydraulic oil detected by the first temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valve V1 to regulate the flow rate of the coolant flowing through the first heat exchanger 70, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1).
In the hydraulic unit 4 configured as described above, both the motor 40 and the device 61 of the controller 60 (control unit) are cooled by the air supplied from the fan F, so that it is possible to make the configuration simple as compared with a case where a heat exchanger for cooling is provided in the motor 40 or the device 61 of the controller 60. Alternatively, either one of the motor 40 and the device 61 of the controller 60 (control unit) may be cooled by the air supplied from the fan F, and the other of the motor 40 and the device 61 of the controller 60 (control unit) may be cooled by liquid in a manner similar to the first to third embodiments.
In the hydraulic unit 4 of the fourth embodiment, the hydraulic oil is returned to the oil tank 10 through the relief valve 50 and the drain hose L10, or alternatively, as illustrated in
This causes the hydraulic oil from the relief valve 50, the hydraulic oil from the throttle 51, and the hydraulic oil from the tank ports T1 and T2 to merge with each other and be cooled by the first heat exchanger 70. The pipe L8 is an example of the first return pipe, and the pipes L41 and L42 are examples of a second return pipe.
When the hydraulic oil discharged from the actuator is returned to the oil tank 10 through the pipes L41 and L42 (second return pipe), the first heat exchanger 70 causes the coolant to exchange heat with the hydraulic oil returning to the oil tank 10 through the pipes L41 and L42. This causes the first heat exchanger 70 to cool not only the hydraulic oil returning from a flow path between the discharge port 30a of the hydraulic pump 30 and the actuator to the oil tank 10 through the relief valve 50 but also the hydraulic oil discharged from the actuator, so that it is possible to further increase the performance of cooling the hydraulic oil.
In the hydraulic unit 4 according to the fourth embodiment, the hydraulic oil is guided from the drain port DR1 to the oil tank 10 through the pipe L43, and the hydraulic oil is guided from the drain port DR2 to the oil tank 10 through the pipe L44, or alternatively, as illustrated in
This causes the first heat exchanger 70 to cool the hydraulic oil from the throttle 51 and cool the hydraulic oil from the drain ports DR1 and DR2. The pipes L1 and L2 are examples of the first return pipe, and the pipes L43 and L 44 are examples of the second return pipe.
As illustrated in
The hydraulic unit 5 includes a temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70 by controlling to open and close the electromagnetic valve V1 in accordance with the temperature of the hydraulic oil detected by the temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valve V1 to regulate the flow rate of the coolant flowing through the first heat exchanger 70, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1). For example, it is desirable that the hydraulic oil cooled by the first heat exchanger 70 be kept at about 40° C., which makes it possible to cool the motor 40 and the device 61 of the controller 60 to the extent that the motor 40 and the device 61 are prevented from suffering from water condensation due to excessive cooling.
As illustrated in
The controller 60 includes the device 61 of an inverter circuit (not illustrated) that drives the motor 40 and the heat sink 62 thermally coupled to the device 61. The pipe L2a into which the cooled hydraulic oil from the first heat exchanger 70 flows is in thermal contact with the heat sink 62. The pipe L2a and the heat sink 62 constitute the second heat exchanger 180.
The hydraulic oil from the second heat exchanger 180 flows into the pipe L2bthat is in thermal contact with the housing 40a of the motor 40. The pipe L2b and the housing 40a of the motor 40 constitute the third heat exchanger 190.
The hydraulic oil from the hydraulic pump 30 flows into a flow path between the outer peripheral surface of the inner pipe 70a (illustrated in
The cooling water supplied from the external supply source flows into the inner pipe 70a of the first heat exchanger 70 through the pipe L3, and the cooling water from the inner pipe 70a flows out through the pipe L4. Alternatively, the cooling water may flow between the outer peripheral surface of the inner pipe 70a of the first heat exchanger 70 and the inner peripheral surface of the outer pipe 70b of the first heat exchanger 70. Next, the cooling water from the first heat exchanger 70 is discharged to the outside through the electromagnetic valve V1 and the drain pipe L7.
The hydraulic unit 5 according to the fifth embodiment has the same effect as the hydraulic unit 1 of the first embodiment has.
The second heat exchanger 180 can cool the device 61 of the controller 60 with the hydraulic oil flowing through the first return pipes (L2a, L2b, and L2c) downstream of the first heat exchanger 70 so as to prevent device 61 from suffering from water condensation due to excessive cooling.
The third heat exchanger 190 can cool the motor 40 with the hydraulic oil flowing through the first return pipes (L2a, L2b, and L2c) downstream of the first heat exchanger 70 so as to prevent the motor 40 from suffering from water condensation due to excessive cooling.
In the fifth embodiment, the hydraulic oil from the drain ports DR1 and DR2 is guided to the first heat exchanger 70 for cooling, or alternatively, the hydraulic oil from the drain ports DR1 and DR2 may be directly returned to the oil tank 10 through the pipes L43 and L44.
As illustrated in
The drain port DR3 is connected to one end of a pipe L45, the hydraulic oil inlet of the fourth heat exchanger 200 is connected to the other end of the pipe L45, the drain port DR4 is connected to one end of a pipe L46, and the pipe L45 is connected to the other end of the pipe L46. The hydraulic oil outlet of the fourth heat exchanger 200 is connected to one end of a pipe L47, and the pipe L1 is connected to the other end of the pipe L47.
The pipe L45 and the drain port DR2 are connected through a check valve 56. The check valve 56 restricts the flow of the hydraulic oil from the drain port DR2 toward the pipe L45, and opens when the pressure applied to the pipe L45 becomes higher than or equal to a predetermined pressure to allow the hydraulic oil to flow from the pipe L45 toward the drain port DR2.
The hydraulic unit 6 includes a temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70 by controlling to open and close the electromagnetic valve V1 in accordance with the temperature of the hydraulic oil detected by the temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valve V1 to regulate the flow rate of the coolant flowing through the first heat exchanger 70, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1). For example, it is desirable that the hydraulic oil cooled by the first heat exchanger 70 be kept at about 40° C., which makes it possible to cool the motor 40 and the device 61 of the controller 60 to the extent that the motor 40 and the device 61 are prevented from suffering from water condensation due to excessive cooling.
As illustrated in
The controller 60 includes the device 61 of an inverter circuit (not illustrated) that drives the motor 40 and the heat sink 62 thermally coupled to the device 61. The pipe L2a into which the cooled hydraulic oil from the first heat exchanger 70 flows is in thermal contact with the heat sink 62. The pipe L2a and the heat sink 62 constitute the second heat exchanger 180.
The hydraulic oil from the second heat exchanger 180 flows into the pipe L2b that is in thermal contact with the housing 40a of the motor 40. The pipe L2b and the housing 40a of the motor 40 constitute the third heat exchanger 190.
The fourth heat exchanger 200 cools the hydraulic oil by causing the hydraulic oil returning to the oil tank 10 through the pipes L45, L46, and L47 and the cooling water to exchange heat with each other. The pipes L45, L46, and L47 are examples of the second return pipe.
The hydraulic oil from the hydraulic pump 30 flows into a flow path between the outer peripheral surface of the inner pipe 70a (illustrated in
The cooling water supplied from the external supply source flows into the inner pipe 70a of the first heat exchanger 70 through the pipe L3, and the cooling water from the inner pipe 70a flows into the fourth heat exchanger 200 through the pipe L4. Then, the cooling water from the fourth heat exchanger 200 is discharged to the outside through the pipe L5, the electromagnetic valve V1, and the drain pipe L7.
The above-described hydraulic unit 6 according to the sixth embodiment has the same effect as the hydraulic unit 5 of the fifth embodiment has.
In the sixth embodiment, the hydraulic oil from the drain ports DR3 and DR4 is returned to the oil tank 10 through the fourth heat exchanger 200 and the first heat exchanger 70, or alternatively, the hydraulic oil from the drain ports DR3 and DR4 may be directly returned to the oil tank 10 through the fourth heat exchanger 200. This case also allows an increase in the performance of cooling the hydraulic oil.
In the sixth embodiment, the hydraulic oil cooled by the first heat exchanger 70 is returned to the oil tank 10 through the second and third heat exchangers 180 and 190, or alternatively, the hydraulic oil cooled by the first heat exchanger 70 may be directly returned to the oil tank 10 without passing through the second and third heat exchangers 180 and 190, and cooling air may be supplied from the fan to both the motor 40 and the heat sink 62 of the controller 60 (control unit) as in the fourth embodiment.
As illustrated in
The pipe L46 has one end connected to the drain port DR4 and has the other end connected to the hydraulic oil inlet of the fourth heat exchanger 200. The hydraulic oil is guided from the hydraulic oil outlet of the fourth heat exchanger 200 into the oil tank 10 through the pipe L47.
The hydraulic unit 7 includes a temperature sensor (not illustrated) that detects the temperature of the hydraulic oil in the oil tank 10. The controller 60 can optimize the flow rate of the coolant flowing through the first heat exchanger 70 by controlling to open and close the electromagnetic valve V1 in accordance with the temperature of the hydraulic oil detected by the temperature sensor.
Specifically, the controller 60 can keep the hydraulic oil at an appropriate temperature by controlling the electromagnetic valve V1 to regulate the flow rate of the coolant flowing through the first heat exchanger 70, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1). For example, it is desirable that the hydraulic oil cooled by the first heat exchanger 70 be kept at about 40° C., which makes it possible to cool the motor 40 and the device 61 of the controller 60 to the extent that the motor 40 and the device 61 are prevented from suffering from water condensation due to excessive cooling.
The hydraulic oil from the hydraulic pump 30 flows into a flow path between the outer peripheral surface of the inner pipe 70a (illustrated in
The cooling water supplied from the external supply source flows into the inner pipe 70a of the first heat exchanger 70 through the pipe L3, and the cooling water from the inner pipe 70a flows into the fourth heat exchanger 200 through the pipe L4. Then, the cooling water from the fourth heat exchanger 200 is discharged to the outside through the pipe L5, the electromagnetic valve V1, and the drain pipe L7.
The above-described hydraulic unit 7 according to the seventh embodiment has the same effect as the hydraulic unit 6 of the sixth embodiment has.
Although specific embodiments of the present disclosure have been described, the present disclosure is not limited to the first to seventh embodiments, and various modifications can be made within the scope of the present disclosure. For example, an appropriate combination of the contents described in the first to seventh embodiments may be regarded as an embodiment of the present disclosure.
A hydraulic unit according to a first aspect of the present disclosure includes:
According to the present disclosure, when the hydraulic oil is returned from the flow path between the discharge port of the hydraulic pump and the actuator to the oil tank through the first return pipe, the first heat exchanger causes the hydraulic oil returning to the oil tank through the first return pipe and the coolant to exchange heat with each other, so that it is possible to increase performance of cooling the hydraulic oil even under an environment where an ambient temperature is high.
A hydraulic unit according to a second aspect of the present disclosure is based on the hydraulic unit according to the first aspect and further includes a relief valve connected to the discharge port of the hydraulic pump, in which the first return pipe includes a pipe through which the hydraulic oil is returned to the oil tank through the relief valve.
According to the present disclosure, when the hydraulic oil is returned from the flow path between the discharge port of the hydraulic pump and the actuator to the oil tank through the relief valve, the first heat exchanger causes the hydraulic oil returning to the oil tank through the first return pipe and the coolant to exchange heat with each other, so that it is possible to further increase the performance of cooling the hydraulic oil.
A hydraulic unit according to a third aspect of the present disclosure is based on the hydraulic unit according to the first aspect or the second aspect and further includes a second return pipe through which the hydraulic oil discharged from the actuator is returned to the oil tank, in which the first heat exchanger causes the hydraulic oil returning to the oil tank through the first return pipe and the coolant to exchange heat with each other, and causes the hydraulic oil returning to the oil tank through the second return pipe and the coolant to exchange heat with each other.
According to the present disclosure, the first heat exchanger cools not only the hydraulic oil returning from the flow path between the discharge port of the hydraulic pump and the actuator to the oil tank through the relief valve but also the hydraulic oil discharged from the actuator, so that it is possible to further increase the performance of cooling the hydraulic oil.
A hydraulic unit according to a fourth aspect of the present disclosure is based on the hydraulic unit according to any one of the first aspect to the third aspect, in which the first heat exchanger includes a double pipe having an inner pipe with a multi-lobed cross section and an outer pipe accommodating the inner pipe.
According to the present disclosure, the use of the first heat exchanger of double-pipe structure having the inner pipe with a multi-lobed cross section and the outer pipe accommodating the inner pipe allows an increase in the performance of cooling the hydraulic oil in the first heat exchanger that can be downsized.
A hydraulic unit according to a fifth aspect of the present disclosure is based on the hydraulic unit according to any one of the first aspect to the fourth aspect and further includes:
According to the present disclosure, the second heat exchanger causes the device that drives the motor and the coolant to exchange heat with each other, so that it is possible to increase performance of cooling the device as compared with air cooling.
A hydraulic unit according to a sixth aspect of the present disclosure is based on the hydraulic unit according to any one of the first aspect to the fourth aspect and further includes:
According to the present disclosure, the third heat exchanger causes the motor that drives the hydraulic pump and the coolant to exchange heat with each other, so that it is possible to increase performance of cooling the motor as compared with air cooling.
A hydraulic unit according to a seventh aspect of the present disclosure is based on the hydraulic unit according to any one of the first aspect to the fourth aspect and further includes:
According to the present disclosure, the first heat exchanger can cool the hydraulic oil, and the second and third heat exchangers can cool the device and the motor. It is further possible to simplify, by connecting the first heat exchanger, the second heat exchanger, and the third heat exchanger in series, a piping configuration for the coolant. It is further possible to cause the flow rate control valve to simultaneously regulate the flow rate of the coolant supplied to the first heat exchanger, the second heat exchanger, and the third heat exchanger. For example, it is possible to optimize the flow rate of the coolant flowing through the first heat exchanger, the second heat exchanger, and the third heat exchanger in accordance with the temperature of the hydraulic oil, the temperature of the device, and the temperature of the motor.
A hydraulic unit according to an eighth aspect of the present disclosure is based on the hydraulic unit according to the seventh aspect, in which the control unit controls an opening degree of the flow rate control valve so as to make a temperature Td of the device of the control unit higher than or equal to a predetermined first device temperature Td1 and lower than or equal to a predetermined second device temperature Td2 (>Td1).
According to the present disclosure, the control unit can keep the device at an appropriate temperature by controlling the opening degree of the flow rate control valve to regulate the flow rate of the coolant flowing through the second heat exchanger, so as to make the temperature Td of the device higher than or equal to the predetermined first device temperature Td1 and lower than or equal to the predetermined second device temperature Td2 (>Td1).
A hydraulic unit according to a ninth aspect of the present disclosure is based on any one of the first aspect to the fourth aspect and further includes:
According to the present disclosure, the first heat exchanger can increase the performance of cooling the hydraulic oil, and the second and third heat exchangers can increase the performance of cooling the device and the motor. Furthermore, the first flow rate control valve can regulate the flow rate of the coolant supplied to the first heat exchanger, the second flow rate control valve can regulate the flow rate of the coolant supplied to the second heat exchanger, and the third flow rate control valve can regulate the flow rate of the coolant supplied to the third heat exchanger. For example, it is possible to optimize the flow rate of the coolant flowing through each of the first heat exchanger, the second heat exchanger, and the third heat exchanger in accordance with the temperature of the hydraulic oil, the temperature of the device, and the temperature of the motor.
A hydraulic unit according to a tenth aspect of the present disclosure is based on the hydraulic unit according to the ninth aspect, in which the control unit controls an opening degree of the first flow rate control valve so as to make a temperature To of the hydraulic oil in the oil tank higher than or equal to a predetermined first hydraulic oil temperature To1 and lower than or equal to a predetermined second hydraulic oil temperature To2 (>To1), controls an opening degree of the second flow rate control valve so as to make a temperature Td of the device of the control unit higher than or equal to a predetermined first device temperature Td1 and lower than or equal to a predetermined second device temperature Td2 (>Td1), and controls an opening degree of the third flow rate control valve so as to make a temperature Tm of the motor higher than or equal to a predetermined first motor temperature Tm1 and lower than or equal to a predetermined second motor temperature Tm2 (>Tm1).
According to the present disclosure, the control unit can keep the hydraulic oil at an appropriate temperature by controlling the opening degree of the first flow rate control valve to regulate the flow rate of the coolant flowing through the first heat exchanger, so as to make the temperature To of the hydraulic oil higher than or equal to the predetermined first hydraulic oil temperature To1 and lower than or equal to the predetermined second hydraulic oil temperature To2 (>To1). The control unit can keep the device at an appropriate temperature by controlling the opening degree of the second flow rate control valve to regulate the flow rate of the coolant flowing through the second heat exchanger, so as to make the temperature Td of the device higher than or equal to the predetermined first device temperature Td1 and lower than or equal to the predetermined second device temperature Td2 (>Td1). The control unit can keep the motor at an appropriate temperature by controlling the opening degree of the third flow rate control valve to regulate the flow rate of the coolant flowing through the third heat exchanger, so as to make the temperature Tm of the motor higher than or equal to the predetermined first motor temperature Tm1 and lower than or equal to the predetermined second motor temperature Tm2 (>Tm1).
A hydraulic unit according to an eleventh aspect of the present disclosure is based on the hydraulic unit according to any one of the first aspect to the fourth aspect and further includes:
According to the present disclosure, at least one of the motor or the device of the control unit is cooled by the air supplied from the fan, so that it is possible to make the configuration simple as compared with a case where a heat exchanger for cooling is provided in the motor and the device of the control unit.
A hydraulic unit according to a twelfth aspect of the present disclosure is based on the hydraulic unit according to the first aspect or the second aspect and further includes:
According to the present disclosure, the second heat exchanger can cool the device of the control unit using the hydraulic oil flowing through the first return pipe downstream of the first heat exchanger, and can suppress the occurrence of water condensation due to excessive cooling.
A hydraulic unit according to a thirteenth aspect of the present disclosure is based on the hydraulic unit according to the first aspect or the second aspect and further includes:
According to the present disclosure, the third heat exchanger can cool the motor using the hydraulic oil flowing through the first return pipe downstream of the first heat exchanger, and can suppress the occurrence of water condensation due to excessive cooling.
A hydraulic unit according to a fourteenth aspect of the present disclosure is based on the hydraulic unit according to the first aspect, the second aspect, the twelfth aspect, or the thirteenth aspect and further includes:
According to the present disclosure, the fourth heat exchanger cools the hydraulic oil discharged from the actuator, and the first heat exchanger cools the hydraulic oil cooled by the fourth heat exchanger and the hydraulic oil returning from the flow path between the discharge port of the hydraulic pump and the actuator to the oil tank through the relief valve, so that it is possible to further increase the performance of cooling the hydraulic oil.
A hydraulic unit according to a fifteenth aspect of the present disclosure is based on the hydraulic unit according to the twelfth aspect or the thirteenth aspect and further includes a second return pipe through which the hydraulic oil discharged from the actuator is returned to the oil tank.
A hydraulic unit according to a fifteenth aspect of the present disclosure is based on the hydraulic unit according to the first aspect or the second aspect and further includes:
According to the present disclosure, the fourth heat exchanger cools the hydraulic oil discharged from the actuator, so that it is possible to further increase the performance of cooling the hydraulic oil.
Number | Date | Country | Kind |
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2021-145508 | Sep 2021 | JP | national |
This application is a Continuation of PCT International Application No. PCT/JP2022/027398, filed on Jul. 12, 2022, which claims priority under 35 U.S.C. § 119(a) to Patent Application No. 2021-145508, filed in Japan on Sep. 7, 2021, all of which are hereby expressly incorporated by reference into the present application.
Number | Date | Country | |
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Parent | PCT/JP2022/027398 | Jul 2022 | WO |
Child | 18596408 | US |