Hydraulic drive apparatus

Abstract

A hydraulic drive apparatus includes: an electric motor; a variable displacement pump driven by the electric motor, the pump including a pair of pump ports whose delivery side and suction side are switched with each other in accordance with a rotation direction of the electric motor; a hydraulic actuator connected to the pair of pump ports by a first supply/discharge line and a second supply/discharge line; and a control device that controls the electric motor based on an actuator position command value for the hydraulic actuator. The pump is configured such that a volume of the pump decreases in accordance with increase in a pressure difference between the first supply/discharge line and the second supply/discharge line.

Claims

1. A hydraulic drive apparatus comprising: an electric motor; a variable displacement pump driven by the electric motor, the pump including a pair of pump ports whose delivery side and suction side are switched with each other in accordance with a rotation direction of the electric motor; a hydraulic actuator connected to the pair of pump ports by a first supply/discharge line and a second supply/discharge line; and a control device that controls the electric motor based on an actuator position command value for the hydraulic actuator, wherein: the pump incudes: a rotary shaft; a cylinder block that rotates together with the rotary shaft, the cylinder block being provided with a plurality of cylinder bores formed therein; a plurality of pistons inserted in the plurality of cylinder bores, respectively; a port plate in which the pair of pump ports is formed; a swash plate that defines a stroke of each of the plurality of pistons; and a spring that presses the swash plate, each of the pair of pump ports has such a shape that when each pump port is divided at a center of the rotary shaft into a portion on a spring-present side where the spring is present and a portion on a spring-absent side where the spring is absent, a length of the portion on the spring-absent side is greater than a length of the portion on the spring-present side, and the pump is configured to generate, in accordance with a pressure difference between the pair of pump ports, a moment at which the pistons tilt the swash plate.

2. The hydraulic drive apparatus according to claim 1, wherein the hydraulic actuator is a hydraulic cylinder that changes a joint angle between a pair of members that are swingably coupled to each other.

3. The hydraulic drive apparatus according to claim 2, wherein the actuator position command value is a joint angle command value for the joint angle between the pair of members, the hydraulic drive apparatus further comprises a position sensor that detects a joint angle actual value of the joint angle between the pair of members, and the control device performs position feedback control by using the joint angle command value and a detection value of the joint angle actual value detected by the position sensor.

4. The hydraulic drive apparatus according to claim 2, further comprising a position sensor that detects a motor angle actual value that is a rotation angle of the electric motor, wherein the control device: determines a speed reduction ratio that corresponds to a tilting angle of the pump; calculates a motor angle command value for the electric motor by using the actuator position command value and the speed reduction ratio; and performs position feedback control by using the motor angle command value and the motor angle actual value detected by the position sensor.

5. The hydraulic drive apparatus according to claim 1, further comprising a position sensor that detects a motor angle actual value that is a rotation angle of the electric motor, wherein the control device: determines a speed reduction ratio that corresponds to a tilting angle of the pump; calculates a motor angle command value for the electric motor by using the actuator position command value and the speed reduction ratio; and performs position feedback control by using the motor angle command value and the motor angle actual value detected by the position sensor.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 shows a schematic configuration of a hydraulic drive apparatus according to one embodiment of the present invention.

(2) FIG. 2 shows a schematic configuration of a mechanical unit of the hydraulic drive apparatus shown in FIG. 1.

(3) FIG. 3 is a sectional view of a pump.

(4) FIG. 4 is a sectional view taken along line IV-IV of FIG. 3.

(5) FIG. 5A is a block diagram showing the internal configuration of a control device of the present embodiment, and FIG. 5B is a block diagram showing the internal configuration of the control device according to a variation.

(6) FIG. 6A shows a relationship between a cylinder speed and cylinder thrust in a case where the tilting angle of the pump is small, and FIG. 6B shows a relationship between the cylinder speed and cylinder thrust in a case where the tilting angle of the pump is great.

DESCRIPTION OF EMBODIMENTS

(7) FIG. 1 shows a hydraulic drive apparatus 1 according to one embodiment of the present invention. The hydraulic drive apparatus 1 includes a mechanical unit 2 and a control device 5.

(8) As shown in FIG. 2, the mechanical unit 2 is formed by integrating an electric motor 21, a pump 3, and a hydraulic actuator 22 together. Also, a small-volume reservoir chamber, which serves as a tank 29 (see FIG. 1), is formed on the mechanical unit 2.

(9) In the present embodiment, the hydraulic actuator 22 is a single-rod hydraulic cylinder that changes a joint angle between a pair of members 71 and 72, which are swingably coupled to each other. For example, each of the members 71 and 72 is a robotic arm. Alternatively, the hydraulic actuator 22 may be a double-rod hydraulic cylinder. Further alternatively, the hydraulic actuator 22 may be a hydraulic motor.

(10) The mechanical unit 2 is provided with a hydraulic circuit that includes the pump 3 and the hydraulic actuator 22. A hydraulic liquid that flows through the hydraulic circuit is typically oil, but may be a different liquid such as water.

(11) The pump 3 includes a rotary shaft 31, which is coupled to the output shaft of the electric motor 21. That is, the pump 3 is driven by the electric motor 21. It should be noted that the rotary shaft 31 of the pump 3 may be directly coupled to the output shaft of the electric motor 21, or may be indirectly coupled to the output shaft of the electric motor 21 via, for example, a reduction gear.

(12) The pump 3 includes a pair of pump ports 3a and 3b. The delivery side and the suction side of the pump ports 3a and 3b are switched with each other in accordance with the rotation direction of the electric motor 21. For example, when the electric motor 21 rotates in one direction, the pump port 3a acts as a suction port, and the pump port 3b acts as a delivery port. When the electric motor 21 rotates in the reverse direction, the pump port 3b acts as a suction port, and the pump port 3a acts as a delivery port.

(13) The pump ports 3a and 3b of the pump 3 are connected to the hydraulic actuator 22 by a first supply/discharge line 23 and a second supply/discharge line 24. In the present embodiment, since the hydraulic actuator 22 is a single-rod hydraulic cylinder, the amount of hydraulic liquid supplied to the hydraulic actuator 22 and the amount of hydraulic liquid discharged from the hydraulic actuator 22 vary from each other. Accordingly, the first supply/discharge line 23 on the rod side of the hydraulic cylinder is connected to the tank 29 by a first adjustment line 25 provided with a check valve 26, and the second supply/discharge line 24 on the head side of the hydraulic cylinder is connected to the tank 29 by a second adjustment line 27 provided with a pilot check valve 28.

(14) Each of the check valve 26 and the pilot check valve 28 allows a flow led from the tank 29 to pass through, but blocks the reverse flow. The pressure of the first supply/discharge line 23 is led through a pilot line 28a to the pilot check valve 28 provided on the second adjustment line 27. The pilot check valve 28 stops exerting the reverse flow blocking function when the pressure of the first supply/discharge line 23 has become higher than a setting pressure.

(15) It should be noted that in a case where the hydraulic actuator 22 is a double-rod hydraulic cylinder or a hydraulic motor, the second adjustment line 27 may be provided with a simple check valve instead of the pilot check valve 28.

(16) The pump 3 is a variable displacement pump. The pump 3 is configured such that the volume of the pump 3 (displacement volume per rotation) decreases in accordance with increase in a pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24.

(17) In the present embodiment, the pump 3 is a swash plate pump. The tilting angle of the pump 3 is automatically changed in accordance with the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24.

(18) Specifically, as shown in FIG. 3, the pump 3 includes a port block 44 and a casing 45, which support the aforementioned rotary shaft 31 via a bearing in a rotatable manner. Components such as a port plate 43, a cylinder block 32, and a swash plate 35 are accommodated in a space surrounded by the port block 44 and the casing 45.

(19) The cylinder block 32 rotates together with the rotary shaft 31. A plurality of cylinder bores 41 are formed in the cylinder block 32. A plurality of pistons 33 are inserted in the plurality of cylinder bores 41, respectively. In the cylinder block 32, communication passages 42 are further formed at the bottom of the respective cylinder bores 41.

(20) The swash plate 35 defines the stroke of each of the pistons 33. To be more specific, a plurality of shoes 34 are each fitted to the head portion of a corresponding one of the pistons 33. These shoes 34 slide on the swash plate 35 in accordance with the rotation of the cylinder block 32. An angle formed by a sliding surface of the swash plate 35 on the shoe 34 side and a plane orthogonal to the rotary shaft 31 is the tilting angle of the pump 3.

(21) In the present embodiment, a spring 37 is disposed at the side of the cylinder block 32. The spring 37 is interposed between the swash plate 35 and the port block 44, and presses the swash plate 35 in the axial direction of the rotary shaft 31 via a pressing plate 36.

(22) The port plate 43 is fixed to the port block 44, and the cylinder block 32 slides on the port plate 43. As shown in FIG. 4, the aforementioned pump ports 3a and 3b are formed in the port plate 43. The communication passages 42 formed in the cylinder block 32 are, in one case, brought into communication with the pump ports 3a and 3b, and in another case, cut off from the pump ports 3a and 3b.

(23) The pump 3 is configured to generate, in accordance with a pressure difference between the pump ports 3a and 3b, a moment at which the pistons 33 tilt the swash plate 35. In the present embodiment, the pump ports 3a and 3b have such a shape that when each of the pump ports is divided at the center of the rotary shaft 31 into a portion on one side where the spring is present, i.e., a portion on the spring-present side, and a portion on the other side where the spring is absent, i.e., a portion on the spring-absent side, the length of the portion on the spring-absent side is greater than the length of the portion on the spring-present side. Hereinafter, for the sake of convenience of the description, the spring-present side relative to the center of the rotary shaft 31 is referred to as the upper side, and the spring-absent side relative to the center of the rotary shaft 31 is referred to as the lower side.

(24) Accordingly, regardless of which one of the pump ports 3a and 3b acts as a delivery port, at the delivery port, the force at which the pistons 33 press the lower portion of the swash plate 35 is greater than the force at which the pistons 33 press the upper portion of the swash plate 35. On the other hand, at the suction port, the force at which the pistons 33 press the lower portion of the swash plate 35 is less than the force at which the pistons 33 press the upper portion of the swash plate 35. Thus, in accordance with increase in delivery pressure, i.e., in accordance with increase in the pressure difference between the pump ports 3a and 3b, a moment at which the pistons 33 tilt the swash plate 35 against the urging force of the spring 37 in such a direction as to decrease the tilting angle of the pump 3 increases.

(25) The aforementioned control device 5 controls the electric motor 21 based on an actuator position command value for the hydraulic actuator 22. For example, the control device 5 is a computer including a CPU and memories such as a ROM and RAM. The CPU executes a program stored in the ROM. It should be noted that the control device 5 may be a single device, or may be divided up into a plurality of devices.

(26) Specifically, as shown in FIG. 5A, the control device 5 includes a motor angle converter 51, a position controller 52, a speed controller 53, an inverter 54, and a differentiator 55. The control device 5 receives the actuator position command value, which is inputted from another device that is not shown. In the present embodiment, the actuator position command value is a joint angle command value θc for the joint angle between the members 71 and 72.

(27) Further, in the present embodiment, the control device 5 is electrically connected to two encoders 61 and 62 (position sensors). As shown in FIG. 1, the encoder 61 is provided on the output shaft of the electric motor 21, and detects a motor angle actual value θmf, which is the rotation angle of the electric motor 21. As shown in FIG. 2, the encoder 62 is provided on a swing shaft that couples the members 71 and 72 together, and detects a joint angle actual value θf of the joint angle between the members 71 and 72.

(28) It should be noted that, instead of the encoder 62, for example, a stroke sensor provided on the hydraulic cylinder serving as the hydraulic actuator 22 can be used as a position sensor that detects the joint angle actual value θf.

(29) In the present embodiment, as shown in FIG. 5A, the control device 5 performs position feedback control by using: the joint angle command value θc; and the joint angle actual value θf between the members 71 and 72, which is detected by the encoder 62. The control device 5 also performs speed feedback control by using: a motor speed command value ωmc for the electric motor 21; and a derivative value (motor speed actual value) ωmf of the motor angle actual value θmf of the electric motor 21, which is detected by the encoder 61. Hereinafter, functions of the respective units of the control device 5 are described in detail.

(30) The motor angle converter 51 determines a speed reduction ratio R, which corresponds to the tilting angle of the pump 3 and depends on a link mechanism of, for example, the members 71 and 72. The motor angle converter 51 calculates a motor position deviation θme for the electric motor 21 by using the joint angle command value θc and the speed reduction ratio R.

(31) The speed reduction ratio R also depends on the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24. For example, the motor angle converter 51 calculates the speed reduction ratio R based on, for example, a detection value of a torque meter provided on the electric motor 21 or detection values of pressure meters provided on the first and second supply/discharge lines 23 and 24.

(32) Then, the motor angle converter 51 calculates the motor position deviation θme for the electric motor 21 by dividing a deviation between the joint angle actual value θf detected by the encoder 62 and the joint angle command value θc between the members 71 and 72 by the speed reduction ratio R.

(33) The position controller 52 calculates the motor speed command value ωmc for the electric motor 21 by multiplying the motor position deviation θme by a positional gain Kp. It should be noted that the control device 5 may calculate the motor speed command value ωmc by multiplying the deviation between the joint angle actual value θf detected by the encoder 62 and the joint angle command value θc between the members 71 and 72 by Kp/R without calculating the motor position deviation θme.

(34) The differentiator 55 calculates the motor speed actual value ωmf by performing differentiation on the motor angle actual value θmf detected by the encoder 61. The speed controller 53 calculates a current command value Imc for the electric motor 21 by multiplying a deviation between the motor speed command value ωmc and the motor speed actual valueωmf by a speed gain Kv. The inverter 54 supplies electric power to the electric motor 21 based on the current command value Imc.

(35) As described above, in the hydraulic drive apparatus 1 according to the present embodiment, the pump 3 is configured such that the volume of the pump 3 decreases in accordance with increase in the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24. Normally, the pressure of the supply/discharge line at the hydraulic oil supply side to the hydraulic actuator 22 is higher, and the pressure of the supply/discharge line at the hydraulic liquid discharge side from the hydraulic actuator 22 is lower. That is, the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24 being great means that necessary thrust for the hydraulic actuator 22, which is a hydraulic cylinder, is great. Also, the volume of the pump 3 being small means that the speed reduction ratio R is high. Therefore, according to the hydraulic drive apparatus 1 of the present embodiment, even when the rotational speed and the torque of the electric motor 21 are constant, the speed reduction ratio R is changeable in accordance with necessary thrust for the hydraulic actuator 22.

(36) For example, as shown in FIG. 6A, in a case where necessary thrust for the hydraulic actuator 22, which is a hydraulic cylinder, is great, the speed reduction ratio R can be made high since the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24 is great. On the other hand, as shown in FIG. 6B, in a case where necessary thrust for the hydraulic actuator 22 is small, the speed reduction ratio R can be made low since the pressure difference between the first supply/discharge line 23 and the second supply/discharge line 24 is small. It should be noted that a rectangular area that is formed by the cylinder thrust and the cylinder speed changes in accordance with a two-dot chain line shown in each of FIG. 6A and FIG. 6B.

(37) In the present embodiment, the hydraulic actuator 22 is a hydraulic cylinder that changes the joint angle between the members 71 and 72. Therefore, the hydraulic drive apparatus 1 can be used for a joint of, for example, a humanoid robot or an industrial robot.

(38) In the position feedback control performed by the control device 5, instead of the joint angle actual value θf between the members 71 and 72, which is detected by the encoder 62, the motor angle actual value θmf for the electric motor 21, which is detected by the encoder 61, may be used as shown in FIG. 5B. That is, the control device 5 may calculate a motor angle command value θmc by using the joint angle command value θc and the speed reduction ratio R, and perform the position feedback control by using the motor angle command value θmc and the motor angle actual value θmf. However, by performing the position feedback control by using the joint angle actual value θf between the members 71 and 72, which is detected by the encoder 62, as in the above-described embodiment, the movement position of the hydraulic actuator 22 can be controlled with high precision even if, for example, the speed reduction ratio R is not properly determined, or leakage of the hydraulic liquid from the hydraulic circuit occurs.

(39) (Variations)

(40) The present invention is not limited to the above-described embodiment. Various modifications can be made without departing from the spirit of the present invention.

(41) For example, it is not essential that the tilting angle of the pump 3 be changed automatically. Alternatively, the tilting angle of the pump 3 may be changed by an electric actuator.

(42) In the above-described embodiment, the pump 3 is a swash plate pump. However, as an alternative, the pump 3 may be a bent axis pump. Further alternatively, the pump 3 is not limited to a particular type of pump, so long as the pump 3 is a variable displacement pump. For example, the pump 3 may be a vane pump or a variable displacement gear pump. However, if the pump 3 is a swash plate pump as in the above-described embodiment, the mechanical unit 2, which is constituted by the electric motor 21, the pump 3, and the hydraulic actuator 22, can be made compact.

(43) The control device 5 may perform sensorless control based on control theory that uses, for example, an OBSERVER.

REFERENCE SIGNS List

(44) 1 hydraulic drive apparatus 21 electric motor 22 hydraulic actuator 23 first supply/discharge line 24 second supply/discharge line 3 pump 3a, 3b pump port 31 rotary shaft 32 cylinder block 33 piston 35 swash plate 37 spring 41 cylinder bore 43 port plate 44 port block 5 control device 61, 62 encoder (position sensor) 71, 72 member