Hydraulic pump system

Abstract

To solve the problem found by the present inventors that, in a hydraulic pump system of a conventional work vehicle such as a carrot harvesting vehicle or a combine harvester, power selection between mechanical power by an engine and electric power by a motor is not always smoothly performed.SOLUTION: In a hydraulic pump system, a one-way clutch inner member 51 is connected to a main-hydraulic-pump drive shaft member 31 of a main hydraulic pump 30; a one-way clutch outer member 52 is connected to a sub-hydraulic-pump drive shaft member 41 of a sub-hydraulic-pump 40; an engine rotary shaft member 11 of an engine 10 is connected to the main-hydraulic-pump drive shaft member 31 or the one-way clutch inner member 51; and a motor rotary shaft member 21 of a motor 20 is connected to the one-way clutch outer member 52 or the sub-hydraulic-pump drive shaft member 41.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a hydraulic pump system for a work vehicle, such as a carrot harvesting vehicle or a combine harvester. [Background technology]

[0002] 2. Description of the Related Art A known hybrid electric vehicle is equipped with an engine, a generator driven by the engine, and a driving battery, and runs by driving a motor with electricity generated by the generator and electricity stored in the battery. The hybrid electric vehicle has a driving transmission that changes the speed of the motor rotation and transmits it to the drive wheels, a generator transmission that changes the speed of the engine rotation and transmits it to the generator, a single hydraulic pump that supplies lubricating oil to the driving transmission and the generator transmission, and a drive source selection mechanism that selects either the engine or the motor as the drive source for the hydraulic pump (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 7-315059 Summary of the Invention [Problem to be solved by the invention]

[0004] Meanwhile, the present inventor believes that, taking into consideration the various needs of work vehicle users, the trend of implementing convenient functions one after another in work vehicles such as carrot harvesting vehicles or combine harvesters will continue to accelerate.

[0005] However, the present inventors have noticed that hydraulic pump systems in conventional work vehicles are not necessarily easy to use when utilizing convenient functions.

[0006] More specifically, the inventors have realized that in the hydraulic pump systems of conventional work vehicles such as carrot harvesting vehicles or combine harvesters, power selection between mechanical power from an engine and electric power from a motor is not always smooth.

[0007] The present invention has been made in consideration of the above-mentioned problems in the conventional technology, and has an object to provide a hydraulic pump system that can improve usability. [Means for solving the problem]

[0008] The first aspect of the present invention is a hydraulic pump system in which engine rotational power generated by an engine and motor rotational power generated by a motor are input as driving forces, It is equipped with a main hydraulic pump, a sub hydraulic pump and a one-way clutch mechanism. the one-way clutch mechanism includes a one-way clutch inner member and a one-way clutch outer member, the one-way clutch inner member is connected to a main hydraulic pump drive shaft member of the main hydraulic pump, the one-way clutch outer member is connected to a sub-hydraulic pump drive shaft member of the sub-hydraulic pump, an engine rotating shaft member of the engine is connected to the main hydraulic pump drive shaft member or the one-way clutch inner member, The hydraulic pump system is characterized in that a motor rotating shaft member of the motor is connected to the one-way clutch outer member or the sub-hydraulic pump drive shaft member.

[0009] In a second aspect of the present invention, the engine rotating shaft member is connected to the main hydraulic pump drive shaft member, In the hydraulic pump system of the first invention, the motor rotating shaft member is connected to the one-way clutch outer member.

[0010] The third aspect of the present invention is a hydraulic pump having a main hydraulic pump drive shaft member, The hydraulic pump system according to the first aspect of the present invention is characterized in that the motor rotating shaft member is connected to the sub-hydraulic pump drive shaft member.

[0011] A fourth aspect of the present invention is the hydraulic pump system according to the second aspect of the present invention, characterized in that the one-way clutch inner member is a rotating shaft member arranged in parallel with the motor rotating shaft member.

[0012] A fifth aspect of the present invention is the hydraulic pump system according to the fourth aspect of the present invention, characterized in that the motor is driven when the hydraulic pressure of the main hydraulic pump and the sub hydraulic pump cannot be obtained by only the engine rotational power.

[0013] In a sixth aspect of the present invention, when the shaft rotation speed of the sub-hydraulic pump drive shaft member cannot be obtained by the engine rotation power alone, the motor is driven, A hydraulic pump system according to a fifth aspect of the present invention, characterized in that when the shaft rotation speed of the sub-hydraulic pump drive shaft member is obtained only by the engine rotational power, the motor is not driven and generates power.

[0014] A seventh aspect of the present invention is the hydraulic pump system according to the sixth aspect of the present invention, characterized in that when the motor is not driven and the power generation is being performed, in the event that the shaft rotation speed of the sub-hydraulic pump drive shaft member can no longer be obtained by the engine rotational power alone, the magnetic field of the motor is cut off and the power generation is terminated, and then the motor is driven.

[0015] The eighth invention of the present invention is the hydraulic pump system of the seventh invention of the present invention, characterized in that when the motor is not driven and the power generation is being performed, when charging of the battery by the power generation is completed, the magnetic field of the motor is cut and the power generation is terminated. Effect of the Invention

[0016] According to the first aspect of the present invention, it is possible to improve usability.

[0017] According to the second aspect of the present invention, in addition to the effect of the first aspect of the present invention, it is possible to simplify the configuration.

[0018] According to the third aspect of the present invention, in addition to the effect of the first aspect of the present invention, it is possible to simplify the configuration.

[0019] According to the fourth aspect of the present invention, in addition to the effects of the first aspect of the present invention, it is possible to improve convenience.

[0020] According to the fifth aspect of the present invention, in addition to the effect of the fourth aspect of the present invention, it is possible to reduce the burden on the worker.

[0021] According to the sixth aspect of the present invention, in addition to the effect of the fifth aspect of the present invention, it is possible to improve reliability.

[0022] According to the seventh aspect of the present invention, in addition to the effects of the sixth aspect of the present invention, it is possible to improve practicality.

[0023] According to the eighth aspect of the present invention, in addition to the effects of the seventh aspect of the present invention, it is possible to further improve practicality. [Brief description of the drawings]

[0024] [Figure 1] FIG. 1A is a schematic plan view of a hydraulic pump system according to an embodiment of the present invention; FIG. 1B is a schematic front view of a hydraulic pump system according to an embodiment of the present invention; and FIG. 1C is a schematic rear view of a hydraulic pump system according to an embodiment of the present invention. [Diagram 2] (a) A schematic plan view of a hydraulic pump system according to a first modified embodiment of the present invention, (b) a schematic front view of the hydraulic pump system according to the first modified embodiment of the present invention, and (c) a schematic rear view of the hydraulic pump system according to the first modified embodiment of the present invention. [Diagram 3](a) A schematic plan view of a hydraulic pump system according to a second modified embodiment of the present invention, (b) a schematic front view of the hydraulic pump system according to the second modified embodiment of the present invention, and (c) a schematic rear view of the hydraulic pump system according to the second modified embodiment of the present invention. [Figure 4] (a) A schematic plan view of a hydraulic pump system according to a third modified embodiment of the present invention, (b) a schematic front view of a hydraulic pump system according to a third modified embodiment of the present invention, and (c) a schematic rear view of a hydraulic pump system according to the third modified embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0025] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS With reference to the drawings, an embodiment of the present invention will be described in detail.

[0026] The same applies below, but some components may not be shown in the drawings, or may be shown in a perspective or simplified manner.

[0027] While describing the operation of the hydraulic pump system according to the embodiment of the present invention, a hydraulic pump system operation control method according to an invention related to the present invention, which is realized by a control unit and the like, will also be described.

[0028] Such a hydraulic pump system is a hydraulic pump system in which engine rotational power generated by the engine 10 and motor rotational power generated by the motor 20 are input as driving forces, and is a specific example of a hydraulic pump system of the present invention having a main hydraulic pump 30, a sub-hydraulic pump 40, and a one-way clutch mechanism 50.

[0029] (1) First, with reference to FIGS. 1(a) to 1(c), the configuration and operation of a hydraulic pump system according to an embodiment of the present invention will be specifically described.

[0030] Here, Figure 1(a) is a schematic plan view of a hydraulic pump system according to an embodiment of the present invention, Figure 1(b) is a schematic front view of the hydraulic pump system according to the embodiment of the present invention, and Figure 1(c) is a schematic rear view of the hydraulic pump system according to the embodiment of the present invention.

[0031] The hydraulic pump system according to the embodiment of the present invention is realized as a hydraulic supply system for a dual power system by dividing a tandem type hydraulic pump device, for example.

[0032] The one-way clutch mechanism 50 has a one-way clutch inner member 51 and a one-way clutch outer member 52, and the one-way clutch inner member 51 is connected to the main hydraulic pump drive shaft member 31 of the main hydraulic pump 30, and the one-way clutch outer member 52 is connected to the sub-hydraulic pump drive shaft member 41 of the sub-hydraulic pump 40.

[0033] Since power can be smoothly selected between mechanical power from the engine 10 or the like and electric power from the motor 20 or the like, usability is improved.

[0034] Power for power steering or gear shifting by HST (Hydro Static Transmission) is supplied by a main hydraulic pump 30, which is a large-capacity hydraulic pump directly connected to the engine 10, and power for the lifting conveyor device of a carrot harvesting vehicle or the auger device of a combine harvester is supplied by a sub-hydraulic pump 40, which is a small-capacity hydraulic pump.

[0035] The engine rotating shaft member 11 of the engine 10 is connected to the main hydraulic pump drive shaft member 31 or the one-way clutch inner member 51, and the motor rotating shaft member 21 of the motor 20 is connected to the one-way clutch outer member 52 or the sub-hydraulic pump drive shaft member 41.

[0036] In an embodiment of the present invention (see Figures 1(a) to 1(c)), the engine rotating shaft member 11 is connected to a main hydraulic pump drive shaft member 31, and the motor rotating shaft member 21 is connected to a one-way clutch outer member 52.

[0037] The engine rotating shaft member 11 may be connected to a one-way clutch inner member 51 .

[0038] A one-way clutch mechanism 50, for which a cam clutch mechanism is typically used, is inserted between the main hydraulic pump 30 and the sub-hydraulic pump 40. When the engine 10 is running, both the main hydraulic pump 30 and the sub-hydraulic pump 40 can be driven by engine rotational power generated by the engine 10, and even when the engine 10 is not running, the sub-hydraulic pump 40 can be driven by motor rotational power generated by the motor 20.

[0039] When not only the engine 10 but also the motor 20 is driven, if the axial rotation speed of the motor rotating shaft member 21 does not exceed the axial rotation speed of the engine rotating shaft member 11, the one-way clutch outer member 52 does not mesh with the one-way clutch inner member 51 and the sub-hydraulic pump drive shaft member 41 is driven at the axial rotation speed of the engine rotating shaft member 11, but if the axial rotation speed of the motor rotating shaft member 21 exceeds the axial rotation speed of the engine rotating shaft member 11, the one-way clutch outer member 52 meshes with the one-way clutch inner member 51 and the sub-hydraulic pump drive shaft member 41 is driven at the axial rotation speed of the motor rotating shaft member 21.

[0040] When the required shaft rotation speed of the sub-hydraulic pump drive shaft member 41 exceeds the shaft rotation speed of the engine rotating shaft member 11, the motor 20 is driven and the sub-hydraulic pump drive shaft member 41 is driven at the shaft rotation speed of the motor rotating shaft member 21, so that the sub-hydraulic pump 40 is driven in response to lever operation of a first operating lever 104 and a second operating lever 105 via a motor speed controller 110. A first cylinder member 106 operated by opening and closing a first valve member 108 in response to lever operation of the first operating lever 104, etc., and a second cylinder member 107 operated by opening and closing a second valve member 109 in response to lever operation of the second operating lever 105, etc., are connected to the hydraulic circuit of the sub-hydraulic pump 40 together with an oil tank 103.

[0041] Since a so-called run-up effect is obtained with the axial rotation of the engine rotating shaft member 11 due to the engine rotational power, a large rotational torque of the motor 20 is not required to start the motor, and the axial rotation speed of the sub-hydraulic pump drive shaft member 41 quickly increases to exceed the axial rotation speed of the engine rotating shaft member 11 as the motor 20 is driven.

[0042] Even if the lever operation by the first operating lever 104 and the second operating lever 105 is terminated after the motor 20 has been driven, the driving of the motor 20 is not immediately terminated but is maintained, so that when the lever operation is performed again, a shortage of the oil flow rate supplied by the sub hydraulic pump 40 is unlikely to occur.

[0043] When the engine 10 is stopped or the required shaft rotation speed of the sub-hydraulic pump drive shaft member 41 is not achieved, a mode is implemented that realizes a standby state in which the rotation speed of the motor 20 is automatically increased when any lever operation is performed using the first operating lever 104 and the second operating lever 105.

[0044] Visualization units such as LED (Light Emitting Diode) lamps are provided on the lever heads of the first operating lever 104 and the second operating lever 105, and such standby states are indicated by a lit lamp or the like, and non-standby states are indicated by a flashing lamp or the like.

[0045] When both the first operating lever 104 and the second operating lever 105 are operated simultaneously to request an increase in the oil flow rate supplied to the large sub-hydraulic pump 40, the rotation speed of the motor 20 is automatically increased, for example, from 2000 [rpm] to 2800 [rpm].

[0046] After the rotation speed of motor 20 has been increased with a margin in this manner, even when lever operation using first operating lever 104 and second operating lever 105 is terminated and single-lever operation using only first operating lever 104 is being performed, the high rotation speed of motor 20, such as 2800 rpm, is maintained for a while.

[0047] In the high flow mode in which the rotation speed of the motor 20 is automatically increased and maintained for a while, if a single lever operation is performed for a predetermined period of time, the rotation speed of the motor 20 is automatically reduced, for example, from 2800 rpm to 2000 rpm, to a constant flow mode, and the drive of the motor 20 is also terminated upon termination of the single lever operation.

[0048] The one-way clutch inner member 51 is a rotating shaft member arranged in parallel with the motor rotating shaft member 21 .

[0049] The main hydraulic pump drive shaft member 31 penetrates the body case of the main hydraulic pump 30, and the engine rotational power from the engine rotating shaft member 11 is input to the one-way clutch inner member 51 via the main hydraulic pump drive shaft member 31 without significant loss.

[0050] The engine rotating shaft member 11, the main hydraulic pump drive shaft member 31, the one-way clutch inner member 51 and the sub-hydraulic pump drive shaft member 41 are aligned in a straight line, achieving a parts layout that does not generate wasted space.

[0051] The motor rotational power generated by the motor 20 is input to the one-way clutch outer member 52 via a gear or a sprocket, and is then transmitted to the sub-hydraulic pump drive shaft member 41.

[0052] By not arranging the motor rotating shaft member 21 coaxially with other rotating shaft members such as the one-way clutch inner member 51, a layout is realized in which the length of the hydraulic pump system as the overall unit length is kept small.

[0053] The motor rotating shaft member 21 is connected to the one-way clutch outer member 52 via a reduction gear device, and by reducing the rotational speed of the motor 20, which is generally a drive unit with a high rotational speed and low rotational torque, and increasing the rotational torque, it is possible to use an inexpensive motor in which unnecessary reduction functions are omitted as the motor 20 to drive the sub-hydraulic pump 40 of engine-driven specifications, which often requires a relatively large rotational torque.

[0054] At least the motor 20, the one-way clutch mechanism 50 and the sub-hydraulic pump 40 are integrally configured, so that specifications as a so-called retrofit unit can often be easily realized.

[0055] The one-way clutch outer member 52 is connected to the sub-hydraulic pump drive shaft member 41, and by adopting a so-called rigid connection to connect the motor 20 to the sub-hydraulic pump 40, a unit frame can be constructed without any additional frame members.

[0056] By connecting the motor rotating shaft member 21 to the one-way clutch outer member 52 via a multi-stage gear or chain, etc., a layout is realized in which the outer diameter of the gear or sprocket for inputting the motor rotational power to the one-way clutch outer member 52 is kept from becoming large.

[0057] When the hydraulic pressure of the main hydraulic pump 30 and the sub hydraulic pump 40 cannot be obtained by the engine rotational power alone, the motor 20 is driven.

[0058] The input and output of the main hydraulic pump 30 and the sub hydraulic pump 40 are independent of each other, and even if the sub hydraulic pump 40 stops due to a problem, for example, there is almost no adverse effect on the oil flow rate supplied by the main hydraulic pump 30.

[0059] By changing the rotation speed of the motor 20 according to the lever tilt angle of an actuator operating lever such as the first operating lever 104 or the second operating lever 105, the oil supply flow rate of the sub hydraulic pump 40 can be continuously changed.

[0060] By using continuous control such as PWM (Pulse Width Modulation) control or inverter control, the rotation speed of the motor 20 can be continuously changed within a motor rotation speed range from a minimum motor rotation speed to a maximum motor rotation speed according to a practical rotation speed of the engine 10.

[0061] For example, in the case where the rotational speed of the engine 10 is a relatively low rotational speed of 1000 [rpm] and a relatively high rotational speed of 2000 [rpm] is required to drive the sub-hydraulic pump 40, when the motor rotational power is input from the motor rotating shaft member 21 to the one-way clutch outer member 52 to obtain the required shaft rotational speed of the sub-hydraulic pump drive shaft member 41, the shaft rotational speed of the one-way clutch outer member 52 quickly exceeds around 1000 [rpm], and the clutch is smoothly and continuously switched on and off, such as when a cam clutch is engaged and disengaged, so that there is little adverse effect on the clutch life of the one-way clutch mechanism 50.

[0062] When the shaft rotation speed of the sub-hydraulic pump drive shaft member 41 cannot be obtained only from the engine rotational power, the motor 20 is driven, and when the shaft rotation speed of the sub-hydraulic pump drive shaft member 41 can be obtained only from the engine rotational power, the motor 20 is not driven and generates electricity.

[0063] The engine rotational power generated by the engine 10 is not only used to drive the main hydraulic pump 30 and the sub hydraulic pump 40, but is also used to cause the motor 20 to function as a generator through its driven rotation.

[0064] In the case where the required shaft rotation speed of the sub-hydraulic pump drive shaft member 41 does not exceed the shaft rotation speed of the engine rotating shaft member 11, the driving of the motor 20 which is generating electricity is prohibited by electronic control or the like.

[0065] When the motor 20 is not driven and generating power, if the shaft rotation speed of the sub-hydraulic pump drive shaft member 41 can no longer be obtained by the engine rotational power alone, the magnetic field of the motor 20 is cut and power generation is terminated, and then the motor 20 is driven.

[0066] For example, even when the engine 10 is in an idling state and the shaft rotation speed of the engine rotating shaft member 11 is insufficient, in cases where a relatively large oil supply flow rate is required from the sub-hydraulic pump 40, the motor 20 is additionally driven to replenish the sub-hydraulic pump drive shaft member 41 as necessary.

[0067] When the required shaft rotation speed of the sub-hydraulic pump drive shaft member 41 exceeds the shaft rotation speed of the engine rotating shaft member 11 and switching is performed from the generator power generation mode to the motor drive mode, after the magnetic field of the motor 20 is temporarily cut off, power generation is terminated and the sub-hydraulic pump 40 is driven together with the driving of the motor 20.

[0068] Whether or not sufficient engine rotational power is being generated by the engine 10 can be determined from the direction of rotation of the generator rotor of the motor 20 in the generator power generation mode or the direction of the current generated by power generation.

[0069] When the motor 20 is not driven but generating power, and charging of the battery 60 through power generation is completed, the magnetic field of the motor 20 is cut off and power generation is terminated.

[0070] When the motor 20 is functioning as a generator and the battery 60 reaches a fully charged state, charging cutoff is performed through power generation control, thereby reducing the excess load associated with the power generation of the motor 20 and driving the main hydraulic pump 30 and the sub hydraulic pump 40 efficiently.

[0071] When the remaining capacity of the battery 60 is insufficient, an alarm sound or the like is issued and driving of the motor 20 is prohibited.

[0072] The motor 20 is positioned so as not to interfere with the oil suction port and the oil discharge port of the sub hydraulic pump 40 .

[0073] In specifications where the sub-hydraulic pump 40 is not driven by the electric power of the motor 20, the motor 20 is removed together with units such as the one-way clutch mechanism 50, and possible configurations include a configuration in which the sub-hydraulic pump 40 is directly connected to the main hydraulic pump 30, or a configuration in which the sub-hydraulic pump 40 is also removed and the main hydraulic pump 30 is used alone as a large-capacity, stand-alone mechanically driven pump.

[0074] Even in a specification in which the sub-hydraulic pump 40 is installed together with the main hydraulic pump 30, a main / sub-hydraulic pump unconnected configuration in which power transmission between the main hydraulic pump 30 and the one-way clutch mechanism 50 is cut off may be considered.

[0075] When the idling of the engine 10 is stopped, a mode is implemented in which the motor 20 is automatically started so that the sub hydraulic pump 40 can be smoothly driven by only the electric power of the motor 20.

[0076] When the sub-hydraulic pump 40 is driven only by the electric power of the motor 20, even after the lever operation using the first operating lever 104 and the second operating lever 105 is terminated, the rotation speed of the motor 20 is maintained for a while, such as the standby rotation speed of 2000 rpm, and after a predetermined time has elapsed, the rotation speed of the motor 20 is gradually reduced to 500 rpm via 1500 rpm and 1000 rpm. This makes it less likely that uneven rotational torque will occur in the motor 20 when the motor 20 is restarted, for example.

[0077] By providing sufficient play at the point where the one-way clutch inner member 51 is connected to the main hydraulic pump drive shaft member 31, it is possible to suppress the occurrence of oil leakage from the main hydraulic pump 30 due to misalignment of the shaft core.

[0078] (2) Next, the configuration and operation of the hydraulic pump system according to the first modified example of the embodiment of the present invention will be described in more detail with reference mainly to FIGS. 2(a) to 2(c).

[0079] Here, Figure 2(a) is a schematic plan view of a hydraulic pump system according to a first modified embodiment of the present invention, Figure 2(b) is a schematic front view of the hydraulic pump system according to the first modified embodiment of the present invention, and Figure 2(c) is a schematic rear view of the hydraulic pump system according to the first modified embodiment of the present invention.

[0080] In a first modified embodiment of the present invention (see Figures 2(a) to 2(c)), the engine rotating shaft member 11 is connected to a main hydraulic pump drive shaft member 31, and the motor rotating shaft member 21 is connected to a sub-hydraulic pump drive shaft member 41.

[0081] The engine rotating shaft member 11 may be connected to a one-way clutch inner member 51 .

[0082] A one-way clutch mechanism 50 is inserted between the main hydraulic pump 30 and the sub-hydraulic pump 40, and a simple configuration is realized that does not require complex driving force transmission members such as an Oldham coupling.

[0083] The body case of the sub hydraulic pump 40 is securely attached to the body case of the main hydraulic pump 30 by so-called bolt-on fastening, and by inserting the one-way clutch mechanism 50 into the internal space between these two body cases, the one-way clutch mechanism 50 is not exposed to the external space, and the one-way clutch mechanism 50 can be protected from external disturbance factors that affect the clutch operation.

[0084] Although the sub-hydraulic pump 40 is mechanically integrated with the main hydraulic pump 30, there is no flow of hydraulic oil between the main hydraulic pump 30 and the sub-hydraulic pump 40, and therefore the discharge capacities of the main hydraulic pump 30 and the sub-hydraulic pump 40 do not affect each other.

[0085] As shown in Figures 3(a) to 3(c), for example, by eliminating the main hydraulic pump partition 113 and the sub-hydraulic pump partition 114, the number of oil supply ports can be reduced and the one-way clutch mechanism 50 can be lubricated with the hydraulic oil of the main hydraulic pump 30 and the sub-hydraulic pump 40, and the one-way clutch mechanism 50 can be used without relying on so-called dry use.

[0086] Here, Figure 3(a) is a schematic plan view of a hydraulic pump system according to a second modified embodiment of the present invention, Figure 3(b) is a schematic front view of the hydraulic pump system according to the second modified embodiment of the present invention, and Figure 3(c) is a schematic rear view of the hydraulic pump system according to the second modified embodiment of the present invention.

[0087] The central shaft end of the one-way clutch outer member 52 functions as a part of the gear pump shaft connected to the sub-hydraulic pump drive shaft member 41.

[0088] An end of the central shaft of the one-way clutch outer member 52 described above protrudes in a direction away from the one-way clutch inner member 51 as a shaft member for driving the sub-hydraulic pump 40 .

[0089] The reduction gear between the motor 20 and the one-way clutch mechanism 50 is not inserted between the main hydraulic pump 30 and the sub-hydraulic pump 40, but is provided by utilizing a drive case 111 attached to the back surface of the sub-hydraulic pump 40.

[0090] The motor 20 is attached to the outer side surface of the housing of the drive case 111, which simplifies the configuration.

[0091] By utilizing the pump mounting flange 112 provided on the side where the engine rotational power is input, the motor 20, the main hydraulic pump 30, the sub-hydraulic pump 40, the one-way clutch mechanism 50, and the drive case 111 are mounted in a stacked manner without the need for additional mounting stay members for mounting the sub-hydraulic pump 40 and the one-way clutch mechanism 50.

[0092] The main hydraulic pump 30 and the sub hydraulic pump 40 are each provided with a sealing member to prevent oil leakage, but the body case of the main hydraulic pump 30 firmly presses against the sealing member of the sub hydraulic pump 40, and the body case of the sub hydraulic pump 40 firmly presses against the sealing member of the main hydraulic pump 30, so oil leakage caused by high hydraulic pressure hardly occurs.

[0093] The main hydraulic pump drive shaft member 31 is arranged so as to partially penetrate the one-way clutch inner member 51 and the one-way clutch outer member 52, which are sometimes called the cam clutch A part and the cam clutch B part, respectively, so that misalignment of the axis of the one-way clutch mechanism 50 is unlikely to occur.

[0094] The outer end of the one-way clutch inner member 51 functions as the main hydraulic pump drive shaft member 31, and the outer end of the one-way clutch outer member 52 functions as the sub-hydraulic pump drive shaft member 41, so-called shaft member skewering specification can be adopted.

[0095] As shown in Figures 4(a) to 4(c), for example, by employing a fixed joint member instead of the one-way clutch mechanism 50 inserted between the main hydraulic pump 30 and the sub-hydraulic pump 40 and eliminating the motor 20, it is also possible to configure a tandem type hydraulic pump device in which the sub-hydraulic pump 40 is directly connected to the main hydraulic pump 30.

[0096] Here, Figure 4(a) is a schematic plan view of a hydraulic pump system according to a third modified embodiment of the present invention, Figure 4(b) is a schematic front view of the hydraulic pump system according to the third modified embodiment of the present invention, and Figure 4(c) is a schematic rear view of the hydraulic pump system according to the third modified embodiment of the present invention.

[0097] In addition to the normal operation mode involving so-called overrunning, in which the one-way clutch outer member 52 may not mesh with the one-way clutch inner member 51, a system can also be configured in which an emergency operation mode using the above-described tandem method in which the sub hydraulic pump 40 is directly connected to the main hydraulic pump 30 is selectively available in the event of a failure of the motor 20 or the one-way clutch mechanism 50.

[0098] One possible configuration is one in which the connection and disconnection of engine rotational power can be switched by utilizing the sliding of a key member or pin member that is slidably provided on the sub-hydraulic pump drive shaft member 41 itself, which is the gear drive shaft of the sub-hydraulic pump 40, or on an inner diameter shaft member inside the sub-hydraulic pump drive shaft member 41.

[0099] It is also possible to consider a configuration in which the one-way clutch mechanism 50 can be switched between a locked state and an unlocked state by using a clutch switching lever or the like provided on the outer periphery of the sub-hydraulic pump 40, thereby making it possible to select whether or not to use a mode in which the sub-hydraulic pump 40 is directly connected to the main hydraulic pump 30.

[0100] By adopting a tandem arrangement in which the motor 20 is mounted on the sub-hydraulic pump 40 rather than being arranged in series with the main hydraulic pump 30 and the sub-hydraulic pump 40, a layout is realized that keeps the overall length of the unit from becoming too large.

[0101] By filling the inside of the drive case 111 with hydraulic oil for the sub-hydraulic pump 40 and bringing the housing of the motor 20 into contact with the drive case 111, the motor 20, which tends to generate heat, can be cooled by the hydraulic oil for the sub-hydraulic pump 40.

[0102] The rotor portion of the motor 20 is sufficiently separated from the oil suction ports and oil discharge ports of the main hydraulic pump 30 and the sub-hydraulic pump 40, so that even if an oil leak occurs in the main hydraulic pump 30 or the sub-hydraulic pump 40, the motor 20 will hardly be exposed to the leaked oil.

[0103] When the main hydraulic pump 30 and the sub hydraulic pump 40 are driven by the engine rotational power generated by the engine 10 and the power generating rotor of the motor 20 is rotating, if the battery 60 is sufficiently charged, the engine load is reduced by cutting the generator magnetic field of the motor 20.

[0104] When the generator magnetic field of the motor 20 is cut, if the role of the motor 20 as a motor is requested by lever operation using the first operating lever 104 and the second operating lever 105, the role of the motor is given priority.

[0105] When the motor 20 is functioning as a generator, if the motor 20 is required to function as a motor, the generator magnetic field is temporarily cut to stop the current, and then the motor 20 is operated as a motor.

[0106] The multiple transmission gears provided inside the drive case 111 can be switched between drive gears and driven gears, and the shaft rotation speed of the sub-hydraulic pump drive shaft member 41 when the sub-hydraulic pump 40 is driven by utilizing the motor 20 can be changed, thereby adjusting the so-called assist ratio by changing the amount of oil discharged per unit rotation of the motor 20.

[0107] By protruding the sub-hydraulic pump driven shaft member 102 of the sub-hydraulic pump 40, which is arranged approximately coaxially with the main hydraulic pump driven shaft member 101 of the main hydraulic pump 30, toward the motor 20, the position of the gear shaft core on the motor 20 side is accurately adjusted, so that shaft core misalignment hardly occurs.

[0108] In addition, the program of the invention related to the present invention is a program for causing a computer to execute all or part of the steps (or processes, operations and actions, etc.) of the hydraulic pump system operation control method of the invention related to the present invention described above, and is a program that operates in cooperation with a computer.

[0109] In addition, the recording medium of the invention related to the present invention is a recording medium having recorded thereon a program for causing a computer to execute all or some of the operations of all or some of the steps (or processes, operations and actions, etc.) of the hydraulic pump system operation control method of the invention related to the present invention described above, and is a computer-readable recording medium in which the read program is used in cooperation with a computer.

[0110] In addition, the above-mentioned "some steps (or processes, operations, actions, etc.)" means one or some steps among the multiple steps.

[0111] In addition, the above-mentioned "operation of a step (or process, operation, action, etc.)" means the operation of all or a part of the above-mentioned steps.

[0112] Furthermore, one mode of use of the inventive program related to the present invention may be in the form of being transmitted through a transmission medium such as the Internet, light, radio waves, or sound waves, being read by a computer, and operating in cooperation with the computer.

[0113] Furthermore, the recording medium includes a ROM (Read Only Memory) and the like.

[0114] Furthermore, a computer is not limited to pure hardware such as a CPU (Central Processing Unit), and may also include firmware, an OS (Operating System), and even peripheral devices.

[0115] As described above, the configuration of the present invention may be realized in software or in hardware. [Industrial Applicability]

[0116] The hydraulic pump system of the present invention can improve usability and is useful for use in a hydraulic pump system of a work vehicle such as a carrot harvesting vehicle or a combine harvester. [Explanation of symbols]

[0117] 10 Engine 11 Engine rotating shaft member 20 Motor 21 Motor rotating shaft member 30 Main hydraulic pump 31 Main hydraulic pump drive shaft member 40 Sub hydraulic pump 41 Sub-hydraulic pump drive shaft member 50 One-way clutch mechanism 51 One-way clutch inner member 52 One-way clutch outer member 60 Battery 101 Main hydraulic pump driven shaft member 102 Sub-hydraulic pump driven shaft member 103 Oil Tank 104 First operating lever 105 Second operating lever 106 First cylinder member 107 Second cylinder member 108 First valve member 109 Second valve member 110 Motor Speed ​​Controller 111 Drive case 112 Pump mounting flange 113 Main hydraulic pump bulkhead 114 Sub hydraulic pump bulkhead

Claims

1. A hydraulic pump system in which engine rotational power generated by an engine and motor rotational power generated by a motor are input as driving forces, It is equipped with a main hydraulic pump, a sub hydraulic pump and a one-way clutch mechanism. the one-way clutch mechanism includes a one-way clutch inner member and a one-way clutch outer member, the one-way clutch inner member is connected to a main hydraulic pump drive shaft member of the main hydraulic pump, the one-way clutch outer member is connected to a sub-hydraulic pump drive shaft member of the sub-hydraulic pump, an engine rotating shaft member of the engine is connected to the main hydraulic pump drive shaft member or the one-way clutch inner member, A hydraulic pump system, characterized in that a motor rotating shaft member of the motor is connected to the one-way clutch outer member or the sub-hydraulic pump drive shaft member.

2. the engine rotating shaft member is connected to the main hydraulic pump drive shaft member, 2. The hydraulic pump system according to claim 1, wherein the motor rotating shaft member is connected to the one-way clutch outer member.

3. the engine rotating shaft member is connected to the main hydraulic pump drive shaft member, 2. The hydraulic pump system according to claim 1, wherein the motor rotating shaft member is connected to the sub-hydraulic pump driving shaft member.

4. 3. The hydraulic pump system according to claim 2, wherein the one-way clutch inner member is a rotating shaft member arranged in parallel with the motor rotating shaft member.

5. 5. The hydraulic pump system according to claim 4, wherein the motor is driven when the hydraulic pressure of the main hydraulic pump and the sub hydraulic pump cannot be obtained by the engine rotational power alone.

6. When the shaft rotation speed of the sub hydraulic pump drive shaft member cannot be obtained by the engine rotation power alone, the motor is driven, 6. The hydraulic pump system according to claim 5, wherein when the shaft rotation speed of the sub-hydraulic pump drive shaft member is obtained only by the engine rotational power, the motor is not driven and generates power.

7. 7. The hydraulic pump system according to claim 6, wherein when the motor is not driven and the power generation is being performed, in the case where the shaft rotation speed of the sub-hydraulic pump drive shaft member can no longer be obtained by the engine rotational power alone, the magnetic field of the motor is cut off to terminate the power generation, and then the motor is driven.

8. 8. The hydraulic pump system according to claim 7, wherein when the motor is not driven and the power generation is being performed, if charging of the battery by the power generation is completed, the magnetic field of the motor is cut off and the power generation is terminated.

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