阅读说明：本技术 具有飞轮机构的施工机器 (Construction machine with flywheel mechanism ) 是由 蔡文 徐源俊 井光辉 黄绵剑 于 2019-06-13 设计创作，主要内容包括：本发明提供了一种电动液压施工机器的传动系。传动系包括具有电动机的驱动系统和连接至所述系统的飞轮机构。所述驱动系统还包括第一输出元件和液压泵,第一输出元件从电动机突出,液压泵设置于第一输出元件从其突出的电动机的一侧。(The invention provides a transmission system of an electro-hydraulic construction machine. The drive train includes a drive system having an electric motor and a flywheel mechanism connected to the system. The drive system further includes a first output member protruding from the electric motor, and a hydraulic pump provided on a side of the electric motor from which the first output member protrudes.)

1. A drive train (10) of an electro-hydraulic construction machine (1), the drive train (10) comprising:

drive system with an electric motor (11), the drive system comprising:

a first output element protruding from the motor (11), an

A hydraulic pump (14), the hydraulic pump (14) being provided on a side of the electric motor (11) from which the first output element protrudes; and

a freewheel mechanism (12, 12 ', 12 "), the freewheel mechanism (12, 12', 12") being connected to the system.

2. The drive train (10) according to claim 1, wherein the flywheel mechanism comprises an electric motor side flywheel (12), the electric motor side flywheel (12) being connected to a side of the electric motor (11) opposite to a side where a hydraulic pump (14) is located.

3. The power train (10) according to claim 1 or 2, wherein the flywheel mechanism comprises an interposed flywheel (12 '), the interposed flywheel (12') being arranged between the electric motor (11) and the hydraulic pump (14).

4. The drive train (10) according to claim 3, wherein a first output element of the electric motor (11) is connected to the interposing flywheel (12') in a rotationally fixed manner.

5. The drive train (10) according to any one of claims 1 to 4, wherein the flywheel mechanism comprises a hydraulic pump side flywheel (12 "), the hydraulic pump side flywheel (12") being connected to a side of the hydraulic pump (14) opposite to a side on which the electric motor (11) is located.

6. The drive train (10) according to any one of claims 1 to 5, further comprising a flexible coupling (13) between the electric motor (11) and the hydraulic pump (14).

7. The drive train (10) according to claim 6, wherein the flexible coupling (13) is connected to the hydraulic pump (14) via splines.

8. Drive train (10) according to claim 6 or 7, wherein the flexible coupling (13) is a torsionally elastic coupling.

9. The driveline (10) of any one of the preceding claims, wherein the freewheel mechanism (12, 12 ', 12 ") is configured to compensate for fluctuations in rotational speed of the driveline (10) based on inertia of the freewheel mechanism (12, 12', 12") in response to fluctuations in hydraulic pump load of the hydraulic pump (14).

10. An electro-hydraulic construction machine (1) comprising:

the drive train (10) according to one of the preceding claims,

a hydraulic system (50, 52, 54) connected to the hydraulic pump (14), and

a controller connected to the electric motor (11),

wherein the controller is configured to control operation of the electric motor (11) based on a hydraulic load required by the hydraulic system (50, 52, 54).

Technical Field

The present invention relates to a power train of an electro-hydraulic construction machine and an electro-hydraulic construction machine including the same.

Background

Construction machines, such as excavators, are widely used on the market, for example, for earth moving and material conveying. Such excavators typically include a boom, a dipper arm, a bucket, and a cab on a rotating platform that is supported by a chassis having tracks or wheels. Excavators are known to utilize hydraulic power from a hydraulic pump to actuate various elements of the excavator, particularly to move a boom, a dipper arm, and a bucket. During the working cycle of an excavator, the load of the hydraulic pump varies greatly over a long period of time, for example when the bucket of the excavator is full or not; and greatly changes in a short period of time, for example, due to vibration or other external forces acting on the excavator.

At present, also due to the more intense demands made on the exhaust emissions of vehicles in the field of construction machines, research and development work has been aimed at providing construction machines with an electric drive train. Heretofore, an electric motor of, for example, an electro-hydraulic excavator directly drives a hydraulic pump. The variation in load of the hydraulic pump causes the motor rotation speed to fluctuate and generates a dynamic load. Therefore, the motor rotation speed greatly fluctuates, which causes the hydraulic pump speed to fluctuate, affects the output flow rate of the hydraulic pump, and causes poor performance in the operation and control of the construction machine. In addition, the durability of the parts of the drive train connecting the motor and the hydraulic pump is reduced due to the large angular acceleration of the dynamic load. Furthermore, to overcome the peak short-term load of the hydraulic pump, in the known construction machine, a large net power must be provided to the electric motor, resulting in high cost and requiring a large installation space.

Disclosure of Invention

In view of the above-discussed inherent drawbacks of known electro-hydraulic construction machines, it is an object of the present invention to provide a drive train of a construction machine having improved controllability of the entire machine, improved durability of the drive train, and a small-sized motor with reduced weight and size, and a construction machine including the same.

This object is achieved by a drive train of an electrohydraulic construction machine. The drive train includes a drive system having an electric motor, and a flywheel mechanism connected to the system. The drive system further includes a first output member protruding from the electric motor, and a hydraulic pump provided on a side of the electric motor from which the first output member protrudes.

In the sense of the present invention, an electric motor is an electric motor configured to convert electric energy into mechanical energy. The electric motor may be powered by a Direct Current (DC) source (e.g., a battery) or by an Alternating Current (AC) source (e.g., a power grid) or by a generator. The generator may be mechanically equivalent to the electric motor, but operates in the opposite direction, and thus accepts mechanical energy (such as fluid flowing back from the hydraulic pump) and converts the mechanical energy into electrical energy.

The motor may be brushed or brushless. The motor may be of various phases (single, two or three phase) and may be air-cooled or liquid-cooled. Furthermore, the electric motor may in turn be used as a generator to recover energy, for example during a rest period of the construction machine. Thus, the electric motor may also be connected to a battery, preferably a lithium ion battery, may be configured to be charged by the electric motor and/or via an external power port, and may be discharged to power the construction machine, preferably the electric motor.

The hydraulic pump according to the present invention is a mechanical power source configured to convert mechanical power (i.e., torque supplied to the hydraulic pump via a drive train) into hydraulic energy (hydrostatic energy). When the hydraulic pump operates, it creates a vacuum at the pump inlet that forces liquid (preferably oil) from the reservoir into the inlet line of the pump and through mechanical action delivers the liquid to the pump outlet and forces it into the hydraulic system. The hydraulic pump may be a gear pump, a rotary vane pump, a screw pump, a damped axial pump, an in-line axial piston pump, a radial piston pump, or a peristaltic pump.

The flywheel mechanism includes an electric motor-side flywheel connected to a side of the electric motor opposite to a side where the hydraulic pump is located. In other words, the motor-side flywheel is connected to the output side of the motor. Thus, the motor-side flywheel is the outermost part of the drive train. Thus, the motor-side flywheel is easy to install, replace and maintain while the construction machine is in production and/or during its field operation.

The flywheel mechanism may include an interposed flywheel disposed between the electric motor and the hydraulic pump. Preferably, the first output element of the electric motor is connected to the interposed flywheel in a rotationally fixed manner.

The flywheel mechanism may include a hydraulic pump-side flywheel connected to a side of the hydraulic pump opposite to the side on which the electric motor is located. In other words, the hydraulic pump side flywheel is connected to the output side of the hydraulic pump. Therefore, the hydraulic pump side flywheel is the outermost part of the power train. Thus, the hydraulic pump-side flywheel is easy to install, replace and maintain while the construction machine is in production and/or during its field operation.

The drive train may further comprise a flexible coupling between the first flywheel and the hydraulic pump. The flexible coupling may be a clutch for coupling or decoupling the hydraulic pump from the drive train. The flexible coupling may also be an adapter so that the motor and flywheel can be provided in existing construction machines in the form of a retrofit solution.

The flexible coupling may be connected to the hydraulic pump via splines. Spline means a connection via ridges and/or teeth on the drive shaft that engage and transfer torque to grooves in the counterpart, maintaining angular correspondence between them. Different splines may be used, such as parallel spline, involute spline, convex spline, triangular spline, helical spline or spherical spline. In a parallel key spline, the sides of equally spaced grooves are parallel in both directions (radial and axial). In the involute spline, the side portions of the equally spaced grooves are involute, like involute gears. The curve increases strength by reducing stress concentrations. In a male spline, the sides of the equally spaced grooves are involute, but the male teeth are modified to allow for misalignment. In the triangular spline, the side portions of the equally spaced grooves form a V-shape. In a helical spline, equally spaced grooves form a helix around the shaft. The sides may be parallel or involute. This may minimize stress concentrations at the static joint under high load conditions, or allow rotational and linear motion between the parts. In a spherical spline, the teeth of the outer part are realized with ball bearings to allow free linear motion even under high torque conditions.

The flexible coupling may also be a torsionally elastic coupling. The torsionally resilient coupling may be a flexible jaw coupling (jawcoupling), a flexible jaw coupling (close coupling) or a flexible pin-type coupling. The flexible jaw coupling is a positive twist flexible coupling that also allows for radial, axial, and angular displacement between the driving part and the driven part. The flexible jaw coupling is fail safe. The flexible jaw coupling comprises two coupling halves with concave jaws positioned opposite each other and circumferentially offset, preferably by half the separation distance. An involute elastomeric body having a convex profile is disposed in the space between the jaws. The involute elastomer serves as an internal damping member that protects the drive motor (here, the electric motor) from dynamic overload. The progressive raised tooth feature also reduces vibration energy and limits vibration amplitude. In contrast to other flexible couplings, the elastomeric teeth of the involute elastomers are not subjected to bending stresses, but are only subjected to pressure, resulting in lower wear and higher load capacity of the teeth. The flexible jaw coupling is a positive lock torsion flexible coupling that allows radial, axial, and angular displacement between the driving and driven parts. Which is a fail-safe coupling. Torque is transmitted by a flexible bumper designed to fit into the bumper feature and is distributed generally symmetrically around the circumference of the flexible pawl coupling. The jaw rings or jaws of the jaw piece operate in the space between the buffers. The buffer is subjected to a compressive force. Thus, low wear and high load capacity may be provided. The damping characteristics of the flexible jaw coupling protect the drive motor (here the motor) from dynamic overload. The flexible pin shaft type connecting piece is a positive locking torsion elastic flexible shaft connecting piece with a rubber elastic transmission element. The flexpin-type coupling is fail-safe and pluggable.

The flywheel mechanism described above may be configured to compensate for fluctuations in rotational speed of the driveline based on inertia of the flywheel mechanism in response to fluctuations in hydraulic pump load of the hydraulic pump. A fluctuation is a random short-term change of the system from its target state, i.e. the difference between the target state and the actual state of the system. The flywheel is a mechanical device preferably having a circular cross-section. The flywheel stores rotational energy. The flywheel is thus prevented from varying and rotating at a speed by its moment of inertia. The amount of energy stored by the flywheel is approximately proportional to the square of its rotational speed. In other words, the flywheel, as for example added between the electric motor and the hydraulic pump, stores and releases energy to compensate for fluctuations in the load of the hydraulic pump. Therefore, the flywheel mechanism including at least one of the motor-side flywheel, the interposing flywheel, and the hydraulic pump-side flywheel can stabilize the rotational speed of the electric motor, can reduce fluctuation of the angular speed thereof and instantaneous angular acceleration of the electric motor, which can reduce the rate of change of the output flow rate of the hydraulic pump and can improve the control performance of the entire construction machine. In addition, reducing the dynamic loads caused by non-uniform rotation protects the motors and couplings used in the drive train and other parts and improves the durability of these parts. Furthermore, overcoming a short overload period by providing a flywheel results in a motor having a smaller size compared to a direct connection of the motor to the hydraulic pump. Furthermore, it is not necessary to provide a complex control system to measure fluctuations in the hydraulic pump load and adapt the rotational speed of the electric motor substantially in real time. Therefore, not only development costs can be reduced, but also the weight and size of the motor can be reduced.

Further, according to the present invention, there is provided an electro-hydraulic construction machine including the above-described power train, a hydraulic system connected to the hydraulic pump, and a controller connected to the motor. The controller is configured to control operation of the electric motor based on a hydraulic load required by the hydraulic system. The construction machine may be a forklift, wheel loader, excavator (crawler or wheel excavator), road roller, backhoe loader, crane, skid steer loader or mining truck. The hydraulic system may include hydraulic cylinders for moving a bucket mounted to the work machine, and/or other hydraulic actuators for rotating a platform of the work machine relative to its chassis, for example. The controller may be, for example, an SPS controller. The controller may include an interface coupled with an operator input interface for an operator of the work machine to input control data. The controller may also be configured to determine a pressure required by the hydraulic system based on control data input via the operator's input interface and received by the controller's input interface. The connection between the operator's input interface and the input interface of the controller may be wired and/or wireless. The hydraulic load required by the hydraulic system corresponds to the hydraulic pump load of the hydraulic pump and depends on the load condition of the load to be carried/moved by the construction machine.

Drawings

FIG. 1 illustrates an electro-hydraulic excavator including a drive train in accordance with the present disclosure;

FIG. 2 is a perspective view of a drive train according to a first embodiment;

FIG. 3 is a top view of the drive train shown in FIG. 2;

fig. 4 is a view schematically showing a power train according to a second embodiment;

fig. 5 is a view schematically showing a power train according to a third embodiment.

Detailed Description

Fig. 1 is a side view of an electric hydraulic excavator 1 according to an embodiment of the present disclosure. Excavator 1 includes a platform 2 (also referred to as a top frame), platform 2 being rotatably coupled to an undercarriage 3 having tracks 5. The boom 4 is hingedly mounted at the hinge portion 24 of the platform 2 (i.e., at a first end of the boom 4), and an operator cab 40 is provided on the platform 2. A dipper arm 6 (also referred to as a stick or stick) is hingedly coupled to the boom 4. The bucket 7 is hingedly coupled to the dipper arm 6. The boom 4 is movable by means of a first hydraulic cylinder 50, the first hydraulic cylinder 50 being supported on the platform 2 and being coupled to the boom 4; the dipper 6 is movable by means of a second hydraulic cylinder 52, the second hydraulic cylinder 52 being supported on the boom 4 and connected to the dipper 6; the bucket 7 is movable by means of a third hydraulic cylinder 54, the third hydraulic cylinder 54 being supported on the bucket arm 6 and being coupled to the bucket 7. It should be noted that although fig. 1 shows only one first hydraulic cylinder 50, it is possible to use two hydraulic cylinders 50, one on each side of the boom 4. In the illustrated configuration, the hydraulic cylinder 50 exerts an urging force on the boom 4 for moving it.

Inside the platform 2, a drive train 10 (not shown in fig. 1) is provided in the engine compartment 8 for generating power for moving the excavator 1 and for actuating the hydraulic cylinders 50, 52, 54.

The drive train 10 will now be described in detail with reference to fig. 2 and 3.

The drive train 10 includes an electric motor 11, an interposed flywheel 12', a flexible coupling 13, a hydraulic pump 14, a mounting 15, a bracket 16, a cushion 17 and a drive shaft 18.

The electric motor 11 is connected to the flexible coupling 13 via a drive shaft 18. The drive shaft 18 and the flexible coupling 13 are flanged. The flexible coupling 13 is connected to the hydraulic pump 14 via splines. The interposed flywheel 12' is mounted on the drive shaft 18 between the electric motor 11 and the flexible coupling 13. The hydraulic pump 14 is connected to hydraulic actuators of the excavator, i.e., for example, hydraulic cylinders 50, 52, 54 of the boom 4.

In the mounted state of the drive train, the electric motor 11 is connected and fixed to the mounting 15 via the bracket 16, the mounting 15 being located below the electric motor 11. Four cushioning pads 17 are provided at each corner of the mounting member 15. Each of the cushioning pads 17 is arranged partly above the mounting 15 and partly below the mounting 15, wherein a middle portion of each of the cushioning pads 17 passes through a respective through hole of the mounting 15, such that the portion of the cushioning pad 17 arranged above the mounting 15 is connected to the portion of the cushioning pad 17 arranged below the mounting 15. Cushion 17 comprises an elastomeric material and thus reduces (i.e., compensates for) the vibrations generated by drive train 10.

Fig. 4 is a view schematically showing a power train 10 according to a second embodiment.

The configuration of the power train 10 according to the second embodiment is the same as that of the power train 10 according to the first embodiment. The principle of action of the power train 10 according to the second embodiment is the same as that of the power train 10 according to the first embodiment. However, the relative arrangement of the individual components forming the power train 10 according to the second embodiment differs from the relative arrangement of the power train 10 according to the first embodiment. Therefore, only the differences between the two embodiments will be described below.

According to the second embodiment, the flywheel mechanism includes the motor-side flywheel 12, and the motor-side flywheel 12 is connected to the electric motor 11 on the side of the electric motor 11 opposite to the side of the electric motor 11 where the hydraulic pump 14 is provided.

Fig. 5 is a view schematically showing a power train 10 according to a third embodiment.

The configuration of the power train 10 according to the third embodiment is the same as the configuration of the power train 10 according to the first and second embodiments. The principle of action of the power train 10 according to the third embodiment is the same as that of the power train 10 according to the first and second embodiments. However, the relative arrangement of the individual components forming the power train 10 according to the third embodiment differs from the relative arrangement of the power train 10 according to the first and second embodiments. Therefore, only the differences between the two embodiments will be described below.

According to the third embodiment, the flywheel mechanism includes the hydraulic pump-side flywheel 12 ", and the hydraulic pump-side flywheel 12" is connected to the hydraulic pump 14 on the side of the hydraulic pump 14, which is opposite to the side of the hydraulic pump 14 in which the electric motor 11 is provided.

Combinations of the above described embodiments are also possible for the sake of completeness. That is, the flywheel mechanism may include an electric motor-side flywheel 12, an interposing flywheel, and/or a hydraulic pump-side flywheel 12 ″.

Reference numerals

1 excavator

2 platform

24 hinge part

3 Chassis

4 cantilever

40 operator's cab

6 bucket arm

7 bucket

8 Engine compartment

10 drive train

11 electric motor

12. 12 ', 12' flywheel

13 Flexible coupling

14 hydraulic pump

15 mounting part

16 support

17 buffer cushion

18 drive shaft

50 first hydraulic cylinder

52 second hydraulic cylinder

54 third hydraulic cylinder.