JP4907231B2 - Energy regenerative power unit - Google Patents

Description

  The present invention relates to a power machine that is a construction machine such as a power shovel and can regenerate energy.

As a power device for a construction machine, for example, there is a power shovel. As a circuit configuration used for this power shovel, the one shown in Patent Document 1 is generally used. The main structure and operation of this power shovel will be described below.
As shown in FIG. 4, in this power shovel, the first pump P1 and the second pump P2 are linked to an engine that is a drive source, and hydraulic oil is discharged from both the pumps P1 and P2 by the rotation of the engine. I am doing so.

The first pump P1 is connected to the left travel valve 2 via the first pump passage 1 and the first tandem passage 1a. In the first tandem passage 1a, the turning valve 3 and the arm I speed valve are connected. 4. Boom II speed valve 5 and spare valve 6 are connected. However, the first parallel passage 7 is connected to the first pump passage 1, and the valves 3 to 6 are connected in parallel via the first parallel passage 7.
The second pump P2 is connected to the second pump passage 8 and the second tandem passage 8a, and the second tandem passage 8a includes a right travel valve 9, a bucket valve 10, and a boom I speed valve 11. The valve for arm II speed 12 is connected. However, the second pump passage 8 is connected to the second parallel passage 13, and the bucket valve 10 and the boom I speed valve 11 are connected in parallel to the second parallel passage 13.
The left travel valve 2 and the right travel valve 9 are valves that control the travel system actuator, and the other valves are valves that control the work machine system actuator.

A distribution passage 14 is connected to the second pump passage 8, and the distribution passage 14 is led to the left travel valve 2. A switching valve 15 is provided in the distribution passage 14 so as to communicate or block the second pump P2 and the left travel valve 2.
In the figure, reference numeral 16 is a main relief switching valve, 17 to 19 are relief valves, and 20 is a pilot pump. The pilot pump 20 discharges pilot pressure for switching each valve, the switching valve 15 and the switching valve 16, and the maximum pressure of the pilot line is set by the relief valve 19.
The relief valve 17 has a higher set pressure than the relief valve 18. Therefore, when the switching valve 16 is at the illustrated communication position, the set pressure of the relief valve 18 is the maximum pressure of the circuit, and when the switching valve 16 is at the shut-off position on the left side of the drawing, the set pressure of the relief valve 17 is set. Is the maximum pressure of the circuit.

  Reference symbol A in the figure denotes a boom actuator which is an example of an actuator for a work implement system. The boom actuator A accommodates a piston in a cylinder, and the piston partitions the cylinder into a rod side chamber A1 and a piston side chamber A2. A piston is fixed to the piston so as to protrude toward the rod side chamber A1, and a boom load is applied to the rod. A connecting passage 21 is connected to the rod side chamber A1, and a connecting passage 22 is connected to the piston side chamber A2. Although not shown, the connection passages 21 and 22 are connected to the first parallel passage 7 and the second parallel passage 13 when the boom II speed valve 5 and the boom I speed valve 11 are switched to one side. When the valves 5 and 11 are switched to the other side, they communicate with the tank.

Next, the operation of this power shovel will be described.
When operating the actuator of the work machine system with the excavator stopped, the first pump P1 is rotated and any one of the turning valve 3, the arm I speed valve 4, and the boom II speed valve 5 is turned on. Switch. Now, assuming that the arm I speed valve 4 is switched to control the arm actuator, the hydraulic oil discharged from the first pump P1 passes through the first parallel passage 7 and the arm I speed valve 4 for the arm. While being guided to the actuator, the arm actuator can be operated by the hydraulic oil. At this time, when the arm I speed valve 4 is switched, the first pump passage 1 is shut off, and the first pump P1 and the left travel valve 2 are shut off.

In the above state, the second pump P2 is rotated and the bucket valve 10 is switched while keeping the switching valve 15 in the illustrated cutoff position. Then, the hydraulic oil discharged from the second pump P2 is guided to a bucket actuator (not shown) via the second pump passage 8, the second parallel passage 13, and the bucket valve 10, and the bucket oil is used by the hydraulic oil. Can be activated.
If the arm I speed valve 4 and the arm II speed valve 12 are switched in a state where the hydraulic oil is discharged from the first and second pumps P1 and P2, the arm actuator can be controlled at the second speed. .
Thus, by rotating the first and second pumps P1 and P2 and switching the valve for controlling the actuator of the work implement system, the arm and boom can be controlled at the second speed, or the boom, arm and bucket can be controlled. Can be controlled at the same time.

On the other hand, when the actuator of the work machine system is controlled during traveling of the power shovel, in other words, when the traveling system and the work machine system are simultaneously controlled, the switching valve 15 is switched to the communication position on the left side in the drawing. When the second pump P2 is rotated and the left travel valve 2 and the right travel valve 9 are switched, the hydraulic oil discharged from the second pump P2 causes the second pump passage 8 and the right travel valve 9 to be switched. To the right traveling actuator via the distribution passage 14 and the left traveling valve 2. Thus, since the hydraulic oil discharged from the second pump P2 is guided to both actuators of the traveling system, the power shovel can travel.
In this state, if the first pump P1 is rotated and any one of the turning valve 3, the arm I speed valve 4, and the boom II speed valve 5 is switched, the operation is performed by the hydraulic oil discharged from the first pump P1. Mechanical actuators can be activated.

When the excavator is driven without operating the work machine system actuator, the first and second pumps P1 and P2 are rotated while the switching valve 15 is kept at the cut-off position shown in the drawing. The travel valve 2 and the right travel valve 9 are switched. Then, the hydraulic oil discharged from the first pump P1 is guided to the left travel actuator, and the hydraulic oil discharged from the second pump P2 is guided to the right travel actuator, so that the power shovel can travel.
Hydraulic Pneumatic Handbook (Edited by Japan Society of Hydraulic and Pneumatics) Hydraulic Excavator Application Examples P638 and 639

In the power shovel, the hydraulic oil discharged from the first pump P1 is guided to the left travel actuator, and the hydraulic oil discharged from the second pump P2 is guided to the right travel actuator so that the power shovel travels. ing.
However, in construction sites that use power shovels, mud and bumps are scattered, and the road surface condition is often very poor. When a power shovel runs on such mud or uneven ground, the crawler may be trapped in mud or uneven and may not be able to escape from there.

Therefore, the maximum discharge capacity of both pumps P1 and P2 can be increased so that a large operating force can be applied to the traveling system actuator, and even when the crawler gets stuck in mud or uneven, it can easily come out from there. To be able to.
However, if the maximum discharge capacity of both pumps P1 and P2 is increased so that the vehicle can run even in poor road surface conditions, the load of the drive source is reduced when working with a light load or when traveling on a flat road surface. It becomes bigger than necessary. For this reason, there has been a problem that the energy efficiency during normal work is very poor.

  An object of the present invention is to provide a power device for a construction machine with high energy efficiency.

The present invention provides a power for a construction machine including an actuator for a work machine system, a travel system actuator, and a first pump and a second pump that selectively supply hydraulic oil to the work machine system or the travel system actuator. Assume equipment.
Based on the above configuration, the first invention is a variable capacity regenerative motor that is connected to a return path when inertial energy or potential energy is applied to an actuator of a work machine system, and this regenerative motor is integrated with the regenerative motor. A variable displacement auxiliary pump that combines hydraulic oil with one or both of the first pump and the second pump, a generator motor that rotates integrally with the regenerative motor and the auxiliary pump, It has a feature in that it includes a power storage unit that stores power generated by the electric motor.

  The second invention is provided with a controller for controlling the tilt angle of the regenerative motor, the tilt angle of the auxiliary pump, and the rotation of the generator motor, and this controller converts the inertial energy and potential energy acting on the actuator of the work machine system into electrical energy. When converting, the auxiliary pump is controlled to minimize the tilt angle, and when the hydraulic oil discharged from the auxiliary pump is merged with the hydraulic oil discharged from the first and second pumps, the generator motor is rotated and the auxiliary oil is rotated. It is characterized in that the tilt angle of the pump is increased and the tilt angle of the regenerative motor is controlled to the minimum.

According to a third aspect of the present invention, a confluence control mechanism is provided in the connection process between the auxiliary pump and the first and second pumps, and the first pump passage or the second pump connected from the auxiliary pump to the first pump by the confluence control mechanism. It is characterized in that the hydraulic oil supplied to either one or both of the second pump passages connected to is controlled.

According to the first invention, the hydraulic oil discharged from the auxiliary pump can be merged as necessary, so that the capacities of the first and second pumps can be reduced. Therefore, the load of the drive source can be reduced and the energy efficiency can be increased.
Further, since the auxiliary pump can be rotated by inertial energy or potential energy acting on the actuator of the work machine system, energy efficiency can be increased even when auxiliary force is applied by the auxiliary pump.

According to the second invention, when the inertial energy or the potential energy is converted into electric energy, the controller controls the auxiliary pump to minimize the tilt angle, so the auxiliary pump does not become a load. Therefore, inertial energy and potential energy can be efficiently converted into electric energy.
Further, when the auxiliary pump is rotated by the generator motor, the controller controls the regenerative motor to minimize the tilt angle, so that the regenerative motor does not become a load. Therefore, the auxiliary force can be efficiently applied by the auxiliary pump.

  According to the third aspect of the invention, since the hydraulic fluid supplied from the auxiliary pump to the travel system or work machine system actuator is controlled by the merging control mechanism, the road surface condition and the load acting on the work machine system actuator are affected. Accordingly, optimal control is possible.

A first embodiment of the present invention will be described with reference to FIG.
In the first embodiment, as in the conventional circuit configuration, the working machine actuator, the traveling actuator, and the working oil or the traveling actuator are selectively supplied with hydraulic oil. 1. Assume a power device for a construction machine including a second pump. And this 1st Embodiment has the characteristics in the point which connected the confluence | merging control mechanism and the regeneration mechanism in the conventional circuit structure. Therefore, the conventional circuit configuration is denoted by the same reference numeral, and here, the configuration and operation of the merging control mechanism and the regeneration mechanism will be mainly described.

  FIG. 1 shows a circuit configuration of a power shovel that is one of the power units. In this power shovel, a variable displacement auxiliary pump P3 that rotates integrally with the generator motor M is connected to the passage 23 and joined together. The passage 23 is branched into a first joining passage 25 and a second joining passage 26 by a control valve 24. The first junction passage 25 is connected to the first pump passage 1 and the second junction passage 26 is connected to the second pump passage 8.

  The merging control valve 24 is a valve that can be switched to three positions, and communicates the passage 23 with the first merging passage 25 and the second merging passage 26 at the center position. Further, when the merging control valve 24 is switched to the upper position in the drawing, the passage 23 and the first merging passage 25 are communicated, and the passage 23 and the second merging passage 26 are blocked and switched to the lower position in the drawing. The passage 23 and the second joining passage 26 are communicated with each other, and the passage 23 and the first joining passage 25 are blocked.

  The merging control valve 24 is switched by the pilot pressure acting on both ends. The controller C controls the pilot pressure. That is, the controller C is electrically connected to each operation lever 27, controls the pilot electromagnetic valves 28 and 29 based on the operation signal of each operation lever 27, and controls the pilot pressure acting on the merging control valve 24. Control. In the first embodiment, the merge control valve 24 and the pilot solenoid valves 28 and 29 constitute the merge control mechanism of the present invention.

  On the other hand, the regenerative motor M1 is connected to the connection passage 22 connected to the piston side chamber A2 of the boom actuator A via the return flow path 30. The regenerative motor M1 is of a variable displacement type and rotates integrally with the auxiliary pump P3 and the generator motor M. Note that a two-position switching valve 31 is provided in the return flow path 30 to shut off the piston side chamber A2 and the regenerative motor M1 in a normal state. However, the two-position switching valve 31 is switched to a position where the piston side chamber A2 and the regenerative motor M1 communicate with each other by applying a pilot pressure controlled by the pilot solenoid valve 32.

The generator motor M generates power by the rotation of the regenerative motor M1, and the electric energy generated by the generator motor M is stored in the power storage unit U via the power converter G having functions of an inverter, a converter, and the like. . When the generator motor M is driven, the generator motor M is driven by the electric energy stored in the power storage unit U.
The controller C controls the rotation speed of the generator motor M and the inclination angles of the first pump P1, the second pump P2, the auxiliary pump P3, and the regenerative motor M1 based on the operation signals input from the operation levers 27. At the same time, the pilot solenoid valves 28, 29 and 32 are controlled. The two-position switching valve 31, the pilot electromagnetic valve 32, the generator motor M, the regenerative motor M1, the auxiliary pump P3, the power converter G, and the power storage unit U constitute a regenerative mechanism.

Next, the operation of the first embodiment will be described.
In a state where a load is applied to the boom actuator A, the following operation is performed when the load acting on the boom actuator A is lowered to convert inertial energy or potential energy into electric energy.
That is, the boom operation lever 27 is operated to the lower side so that the connection passage 21 and the first parallel passage 7 and the second parallel passage 13 communicate with each other, and the boom II speed valve 5 and the boom I speed valve 11 are operated. Switch.
Then, the controller C that has received the operation signal from the operation lever 27 controls the first pump P1 or the second pump P2, the auxiliary pump P3, the regenerative motor M1, and the pilot electromagnetic valve 32.

  Then, the hydraulic oil is discharged from the first pump P1 or the second pump P2, the hydraulic oil is supplied to the rod side chamber A1, the inclination angle of the regenerative motor M1 is set to a predetermined angle, and the inclination angle of the auxiliary pump P3 is set to zero. Control. At this time, since the two-position switching valve 31 is switched to the communication position by the pilot pressure introduced from the pilot solenoid valve 32, the return oil from the piston side chamber A2 is connected to the connection passage 22 as a return side passage → The flow path 30 is guided to the regenerative motor M1 through the two-position switching valve 31.

Then, the regenerative motor M1 is rotated by the return oil from the piston side chamber A2, and the auxiliary pump P3 and the generator motor M are rotated along with the rotation of the regenerative motor M1. As described above, when the regenerative motor M1 rotates, the generator motor M generates power, and the power storage unit U stores the electric energy generated by the generator motor M.
However, since the tilt angle of the auxiliary pump P3 is controlled to zero by the controller C, the auxiliary pump P3 rotates idly without discharging oil. Therefore, when the inertial energy and the potential energy acting on the boom actuator A are converted into electric energy, the auxiliary pump P3 can efficiently generate power without being a load.

On the other hand, when the hydraulic oil discharged from the auxiliary pump P3 is merged with the hydraulic oil discharged from the first pump P1 or the second pump P2, the auxiliary force is applied to the actuator of the traveling system or the work machine system. Based on the operation signal of the operation lever 27, the controller C performs the following control.
In other words, the tilt angle of the first and second pumps P1 and P2 is controlled to supply hydraulic oil to the traveling system or working machine system actuator, and the generator motor M is driven by the electrical energy stored in the power storage unit U. Further, at this time, the regenerative motor M1 is controlled to make the tilt angle zero, and the auxiliary pump P3 is controlled to change the tilt angle according to the operation amount of each operation lever 27.

Then, the auxiliary pump P3 rotates with the rotation of the generator motor M, and hydraulic oil corresponding to the inclination angle is discharged to the passage 23. At this time, since the regenerative motor M1 has an inclination angle of zero, the regenerative motor M1 does not become a load with respect to the rotation of the generator motor M and the auxiliary pump P3, and the auxiliary force can be efficiently applied. it can.
The merging control mechanism guides the hydraulic oil discharged from the auxiliary pump P3 as described above to the traveling system actuator or to the working machine system actuator.

  For example, it is assumed that the hydraulic oil discharged from the first pump P1 is guided to the left traveling actuator, and the hydraulic oil discharged from the second pump P2 is guided to the right traveling actuator, and the power shovel is traveling. When the power shovel is run at a high speed from this state, the hydraulic oil may be discharged from the auxiliary pump P3 as described above. Since the merging control valve 24 holds the center position by springs provided at both ends, the hydraulic oil discharged from the auxiliary pump P3 is equally distributed to the first merging passage 25 and the second merging passage 26, The auxiliary force of the auxiliary pump P3 can be guided to both travel actuators.

  Further, when the traveling system and the work machine system are simultaneously controlled, in the case where the assisting force is applied to the traveling system actuator, the controller C drives the generator motor M and regenerates in the same manner as described above. The tilt angle of the motor M1 and the auxiliary pump P3 is controlled, and at the same time, the pilot solenoid valve 29 is controlled. Then, the merge control valve 24 is switched to the lower position in the figure by the pilot pressure controlled by the pilot solenoid valve 29. Therefore, the hydraulic oil discharged from the auxiliary pump P3 merges with the hydraulic oil discharged from the second pump P2 in the second pump passage 8 via the second merging passage 26, and gives auxiliary force to the travel system actuator. can do.

  In the case where the traveling system and the work machine system are simultaneously controlled, when the auxiliary force is applied to the actuator of the work machine system, the controller C drives the generator motor M as described above, The tilt angle of the regenerative motor M1 and the auxiliary pump P3 is controlled, and at the same time, the pilot solenoid valve 28 is controlled. Then, the confluence control valve 24 is switched to the upper position in the figure by the pilot pressure controlled by the pilot solenoid valve 28. Therefore, the hydraulic oil discharged from the auxiliary pump P3 merges with the hydraulic oil discharged from the first pump P1 in the first pump passage 1 via the first merging passage 25, and gives auxiliary force to the actuator of the work machine system. Can be granted.

In the above description, the driving force is applied from the auxiliary pump P3 by driving the generator motor M. However, according to the first embodiment, the inertia energy acting on the actuator of the work machine system, The auxiliary force can be directly applied from the auxiliary pump P3 by the potential energy.
For example, when the hydraulic oil discharged from the first pump P1 is guided to the rod side chamber A1, the boom actuator A is operated, and the hydraulic oil discharged from the second pump P2 is used to operate both travel system actuators. The controller C may control as follows.

That is, the controller C controls the tilt angles of the pilot solenoid valves 29 and 32 and the auxiliary pump P3. Then, the regenerative motor M1 is rotated by the return oil from the piston side chamber A2, and the auxiliary pump P3 is rotated along with the rotation of the regenerative motor M1. Since the auxiliary pump P3 is controlled by the controller C at an inclination angle corresponding to the operation amount of each operation lever 27, the auxiliary pump P3 rotates to discharge hydraulic oil to the passage 23.
At this time, since the controller C controls the pilot electromagnetic valve 29, the merging control valve 24 is switched to the lower position in the figure, and the passage 23 and the second merging passage 26 communicate with each other. Therefore, the hydraulic oil discharged from the auxiliary pump P3 can merge with the hydraulic oil discharged from the second pump P2, and an auxiliary force can be applied to both the traveling actuators.

According to the first embodiment, since the hydraulic oil discharged from the auxiliary pump P3 can be merged as necessary, it is not necessary to increase the capacities of the first and second pumps P1 and P2 more than necessary. Therefore, the load of the drive source can be reduced and the energy efficiency can be increased.
Moreover, since the auxiliary pump P3 can be rotated by inertial energy or potential energy acting on the actuator of the work machine system, energy efficiency can be improved even when an auxiliary force is applied by the auxiliary pump P3.
Furthermore, since the merging control mechanism is controlled to control the hydraulic fluid supplied from the auxiliary pump P3 to the traveling system or working machine system actuator, depending on the road surface condition and the load acting on the working machine system actuator Optimum control is possible.

In the first embodiment, the inertia energy or potential energy acting on the boom actuator is converted into electric energy. However, the actuator is a work machine system actuator, and the inertia energy or potential energy acts on it. Any actuator may be used as long as it is present. Therefore, the actuator of the work machine system is not limited to the cylinder but may use a motor.
In the first embodiment, the discharge amount can be varied by controlling the tilt angles of the first and second pumps, but a constant discharge pump may be used.
Further, the merging control valve may control the switching amount in proportion to the operation amount of each operation lever, or may be switched on and off.
Moreover, in 1st Embodiment, although the circuit structure of the power shovel was demonstrated, this invention is not limited to a power shovel, In the power plant which guides hydraulic oil to the actuator of a running system and a working machine system with two pumps Can be widely used.

A second embodiment of the present invention will be described with reference to FIG.
In the second embodiment, only the configuration of the merging control mechanism in the first embodiment is different, and the other circuit configuration, the method for converting electric energy, and the method for driving the auxiliary pump are the same as those in the first embodiment. It is.
Therefore, the same circuit configuration as that of the first embodiment is denoted by the same reference numeral, and here, the configuration and operation of the merging control mechanism that is different from the first embodiment will be mainly described.

As shown in FIG. 2, the passage 23 connected to the auxiliary pump P3 is branched into the first joining passage 25 and the second joining passage 26 by the joining control valve 33 constituting the joining control mechanism of the present invention, and the first The merge passage 25 is connected to the first pump passage 1, and the second merge passage 26 is connected to the second pump passage 8.
The merging control valve 33 is a valve that can be switched to three positions, and holds the center position by the spring force of springs provided at both ends. At this center position, the merging control valve 33 causes the passage 23 to communicate with the first merging passage 25 and the second merging passage 26, and equally distributes the hydraulic oil discharged from the auxiliary pump P3 to the merging passages 25, 26.

Further, when the pressure of the first merging passage 25 becomes higher than the pressure of the second merging passage 26, the merging control valve 33 is switched to the upper position in the figure, and the communication opening degree between the passage 23 and the second merging passage 26 is increased. Since the throttle pump is gradually throttled, the discharge flow rate of the auxiliary pump P3 does not flow much toward the second merging passage 26, which is the low pressure side. On the other hand, when the pressure of the second merging passage 26 becomes higher than the pressure of the first merging passage 25, the merging control valve 33 is switched to the lower position in the figure, and the communication opening degree between the passage 23 and the first merging passage 25 is increased. Is gradually reduced, so that the discharge flow rate of the auxiliary pump P3 does not flow much toward the first merging passage 25 which is the low pressure side.
The merging control valve 33 guides pilot pressure from the first merging passage 25 side to one end (upper side in the figure) of the valve, and pilot pressure from the second merging passage 26 side to the other end (lower side in the figure). Is leading.
Therefore, when the pressure on the first merging passage 25 side becomes higher than the pressure on the second merging passage 26 side, the merging control valve 33 is switched to the upper position in the figure by the pilot pressure, and conversely on the second merging passage 26 side. When the pressure becomes higher than the pressure on the first merging passage 25 side, the merging control valve 33 is switched to the lower position in the figure by the pilot pressure.

The merging control valve 33 having the above configuration performs the following control when hydraulic oil is discharged from the auxiliary pump P3.
For example, the hydraulic pump is discharged from the auxiliary pump P3 while the left excavator is running while the left pump actuator is operated by the first pump P1 and the right pump actuator is operated by the second pump P2. Assume that an auxiliary force is applied to both travel actuators.

At this time, since the merging control valve 33 holds the center position by springs provided at both ends, the hydraulic oil discharged from the auxiliary pump P3 is fed by the merging control valve 33 to the first merging passage 25 and the second merging passage 26. Equally distributed. Therefore, the hydraulic oil discharged from the first pump P1 and the auxiliary pump P3 merges in the first pump passage 1 and is guided to the left travel actuator, and the hydraulic oil discharged from the second pump P2 and the auxiliary pump P3 is They merge in the second pump passage 8 and are guided to the right traveling actuator.
Thus, a large operating force can be applied to the travel system actuator by joining the hydraulic oil discharged from the auxiliary pump P3 to the hydraulic oil discharged from the first and second pumps P1, P2. Therefore, the excavator can be run at a high speed as necessary, and even when the crawler gets stuck in the mud, it can be easily escaped from there.

  In the case where the hydraulic oil discharged from the auxiliary pump P3 is joined and traveling, for example, it is assumed that the left crawler gets stuck in mud. Then, the pressure of the left traveling actuator becomes higher than the pressure of the right traveling actuator, and the pressures of the first pump passage 1 and the first joining passage 25 are the pressures of the second pump passage 8 and the second joining passage 26. Higher than. When the pressure of the first joining passage 25 becomes higher than the pressure of the second joining passage 26, the joining control valve 33 is gradually switched to the upper position in the figure by the pilot pressure.

  When the merging control valve 33 is switched to the upper position in the figure, the communication opening degree toward the second merging passage 26 is gradually reduced, and the communication opening degree toward the first merging passage 25 is gradually increased. Therefore, more hydraulic oil discharged from the auxiliary pump P3 is guided to the first merging passage 25 side, and more hydraulic oil is guided to the higher pressure actuator among the traveling system actuators, that is, the left traveling actuator. be able to. In this way, the hydraulic oil that is guided to the lower pressure actuator of the traveling system actuator is throttled, so that a large flow rate does not flow to the lower pressure side, and the power shovel does not bend reliably. You can travel.

In addition, in this 2nd Embodiment, although the case where the power shovel was drive | working was demonstrated, the case where the actuator of a working machine system is controlled, or the case where the traveling system and the work machine system are controlled simultaneously Alternatively, the hydraulic oil discharged from the auxiliary pump P3 may be merged.
For example, when the traveling system and the work machine system are simultaneously controlled, if the hydraulic oil discharged from the auxiliary pump P3 is merged, even during simultaneous control, high-load work or high-speed traveling is performed. Can be.
It is natural that the merging control valve 33 performs the same control even when the auxiliary pump P3 is rotated by the generator motor M or when the auxiliary pump P3 is rotated along with the rotation of the regenerative motor M1. .

Also in the second embodiment, as in the first embodiment, the hydraulic oil discharged from the auxiliary pump P3 can be merged as necessary, so that the capacity of the first and second pumps P1, P2 is more than necessary. There is no need to make it bigger. Therefore, the load of the drive source can be reduced and the energy efficiency can be increased.
Moreover, since the auxiliary pump P3 can be rotated by inertial energy or potential energy acting on the actuator of the work machine system, energy efficiency can be improved even when an auxiliary force is applied by the auxiliary pump P3.
However, in the first embodiment, the auxiliary pump P3 can be selectively joined to one or both of the first pump P1 and the second pump P2, but in this second embodiment, You cannot select a destination.

A third embodiment of the present invention will be described with reference to FIG.
In the third embodiment, only the configuration of the merging control mechanism in the second embodiment is different, and the other circuit configuration, the conversion method of electric energy, and the driving method of the auxiliary pump are the same as those in the second embodiment. It is.
Therefore, the same circuit configuration as that of the second embodiment is denoted by the same reference numeral, and here, the configuration and operation of the merging control mechanism that is different from the second embodiment will be mainly described.
As shown in FIG. 3, the passage 23 connected to the auxiliary pump P <b> 3 is branched and connected to the first joining passage 25 and the second joining passage 26, and the first joining passage 25 is connected to the first pump passage 1. The second junction passage 26 is connected to the second pump passage 8.

  A pair of pressure compensation valves 34 and 35 are provided in the first and second junction passages 25 and 26, which are the connection process between the first and second pumps P1 and P2 and the auxiliary pump P3. In addition, a high pressure selection valve 36 is connected to the first and second pump passages 25 and 26 and closer to the first and second pumps P1 and P2 than the pair of pressure compensation valves 34 and 35. The pair of pressure compensating valves 34 and 35 and the high pressure selection valve 36 constitute a merging control mechanism of the present invention. The merging control mechanism has the following configuration.

In other words, the high pressure selection valve 36 selects the higher pressure of the first merging passage 25 and the second merging passage 26 and guides the selected pressure to the pair of pressure compensating valves 34 and 35 as a pilot pressure. ing.
The pressure compensation valve 34 is the first merging passage 25 and balances with the pressure on the auxiliary pump P3 side (passage 23 side) and the pilot pressure guided from the high pressure selection valve 36. On the other hand, the pressure compensation valve 35 is the second merging passage 26 and balances with the pressure on the auxiliary pump P3 side (passage 23 side) and the pilot pressure introduced from the high pressure selection valve 36. In addition, since fixed throttles having the same area are provided on the upstream side of the pressure compensation valves 34 and 35, the hydraulic oil guided from the auxiliary pump P3 to the first merging passage 25 and the second merging passage from the auxiliary pump P3. The hydraulic fluid led to 26 is always equal.

The merging control mechanism configured as described above performs the following control when hydraulic oil is discharged from the auxiliary pump P3.
For example, the hydraulic pump is discharged from the auxiliary pump P3 while the left excavator is running while the left pump actuator is operated by the first pump P1 and the right pump actuator is operated by the second pump P2. Assume that an auxiliary force is applied to both travel actuators.

At this time, the pressures of both the traveling actuators are led as a pilot pressure to the pair of pressure compensating valves 34 and 35 via the high pressure selection valve 36. Therefore, the pressure compensation valves 34 and 35 are balanced by the pilot pressure and the discharge pressure of the auxiliary pump P3 to compensate for the pressures in the combined passages 25 and 26, and the hydraulic oil discharged from the auxiliary pump P3 is passed through the passage 23. To the first merging passage 25 and the second merging passage 26.
The hydraulic oil discharged from the first pump P1 and the auxiliary pump P3 merges in the first pump passage 1 and is guided to the left travel actuator, and the hydraulic oil discharged from the second pump P2 and the auxiliary pump P3 is They merge in the second pump passage 8 and are guided to the right traveling actuator.

  As described above, by combining the hydraulic oil discharged from the auxiliary pump P3 with the hydraulic oil discharged from the first and second pumps P1 and P2, a large operating force can be applied to the travel system actuator. Therefore, the excavator can be run at a high speed as necessary, and even when the crawler gets stuck in the mud, it can be easily escaped from there.

  In the case where the hydraulic oil discharged from the auxiliary pump P3 is joined and traveling, for example, it is assumed that the left crawler gets stuck in mud. Then, the pressure of the left traveling actuator becomes higher than the pressure of the right traveling actuator, and the pressures of the first pump passage 1 and the first joining passage 25 are the pressures of the second pump passage 8 and the second joining passage 26. Higher than. When the pressure of the first merging passage 25 becomes higher than the pressure of the second merging passage 26, the high pressure selection valve 36 selects the pressure of the first merging passage 25, and the pressure of the first merging passage 25 is used as the pilot pressure. It leads to a pair of pressure compensation valves 34 and 35. Therefore, both pressure compensation valves 34 and 35 are both controlled by the pressure of the left travel actuator, and a fixed throttle having the same area is provided upstream of the pressure compensation valves 34 and 35. An equal amount of hydraulic fluid is guided to both merge passages 25 and 26.

  In this way, if the pair of pressure compensating valves 34 and 35 is controlled by the higher pressure of the traveling system actuators, even if a pressure difference occurs between both of the traveling system actuators, the lower pressure actuator is controlled. A lot of hydraulic oil does not flow. Therefore, the hydraulic oil that merges with the first pump P1 and the hydraulic oil that merges with the second pump P2 can always be made equal regardless of the pressure generated in the actuator of the traveling system, without being affected by the road surface condition. You can go straight ahead.

In addition, in this 3rd Embodiment, although the case where the power shovel was drive | working was demonstrated, the case where the actuator of a working machine system is controlled, or the case where the traveling system and the work machine system are controlled simultaneously Alternatively, the hydraulic oil discharged from the auxiliary pump P3 may be merged.
For example, when the traveling system and the work machine system are simultaneously controlled, if the hydraulic oil discharged from the auxiliary pump P3 is merged, even during simultaneous control, high-load work or high-speed traveling is performed. Can be.
It is natural that the merging control mechanism performs the same control whether the auxiliary pump P3 is rotated by the generator motor M or is rotated in accordance with the rotation of the regenerative motor M1.

Also in the third embodiment, the hydraulic oil discharged from the auxiliary pump P3 can be merged as necessary, as in the second embodiment, so that the capacity of the first and second pumps P1, P2 is more than necessary. There is no need to make it bigger. Therefore, the load of the drive source can be reduced and the energy efficiency can be increased.
Moreover, since the auxiliary pump P3 can be rotated by inertial energy or potential energy acting on the actuator of the work machine system, energy efficiency can be improved even when an auxiliary force is applied by the auxiliary pump P3.

It is a circuit diagram of a 1st embodiment. It is a circuit diagram of a 2nd embodiment. It is a circuit diagram of a 3rd embodiment. It is a circuit diagram used for the power unit of the conventional construction machine.

Explanation of symbols

24, 33 Junction control valves 28, 29 Pilot solenoid valve 30 Return flow path 34, 35 Pressure compensation valve 36 High pressure selection valve A Boom actuator C Controller G Power converter M Generator motor M1 Regenerative motor P1 First pump P2 Second pump P3 Auxiliary pump U Power storage unit

Claims (3)

  In a construction machine power device comprising: a work machine actuator; a travel system actuator; and a first pump and a second pump that selectively supply hydraulic oil to the work machine system or the travel system actuator. A variable capacity regenerative motor connected to a return path when inertial energy or potential energy is applied to an actuator of a work machine system, and the first pump or the second pump while rotating integrally with the regenerative motor A variable displacement auxiliary pump that joins hydraulic oil to one or both of the above, a regenerative motor and a generator motor that rotates together with the auxiliary pump, and a power storage unit that stores electric power generated by the generator motor. Regenerative power unit.   A controller for controlling the tilt angle of the regenerative motor, the tilt angle of the auxiliary pump, and the rotation of the generator motor is provided, and this controller converts the inertial energy and potential energy acting on the actuator of the work machine system into electric energy. In order to minimize the tilt angle by controlling the hydraulic oil discharged from the auxiliary pump, the generator motor is rotated and the tilt angle of the auxiliary pump is increased when the hydraulic fluid discharged from the first and second pumps is merged. The energy regenerative power unit according to claim 1, wherein the tilt angle of the regenerative motor is controlled to a minimum. In the connection process between the auxiliary pump and the first and second pumps, a confluence control mechanism is provided, and by this confluence control mechanism, the first pump passage connected from the auxiliary pump to the first pump or the second pump connected to the second pump. The energy regenerative power unit according to claim 1 or 2, wherein the hydraulic oil supplied to one or both of the pump passages is controlled.

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