Method of and system for controlling hydraulic power system

• US 4,606,313 A
• Filed: 06/09/1982
• Issued: 08/19/1986
• Est. Priority Date: 10/09/1980
• Status: Expired due to Term

• Current Assignee: Hitachi Construction Machinery Company Limited (Hitachi, Ltd.)
• Original Assignee: Hitachi Construction Machinery Company Limited (Hitachi, Ltd.)
• Inventors: Watanabe, Hiroshi, Nakajima, Kichio, Honma, Kazuo, Aoyagi, Yukio, Izumi, Eiki
• Primary Examiner(s): Miller, Carl Stuart
• Application Number:
  US06/387,884
• Time in Patent Office: 1,532 Days
• Field of Search: 123/387, 123/385, 123/386, 123/357-359, 414/699
• US Class Current: 123/386
• CPC Class Codes: B60W 10/06 including control of combustion engines
• CPC Class Codes: B60W 10/103 of fluid type
• CPC Class Codes: B60W 2710/0644 Engine speed
• CPC Class Codes: B60W 30/1882 characterised by the working point of the engine, e.g. by using engine output chart
• CPC Class Codes: E02F 9/2235 including an electronic controller
• CPC Class Codes: E02F 9/2246 Control of prime movers, e.g. depending on the hydraulic load of work tools
• CPC Class Codes: E02F 9/2296 Systems with a variable displacement pump
• CPC Class Codes: F02D 2200/0602 Fuel pressure
• CPC Class Codes: F02D 2250/18 Control of the engine output torque
• CPC Class Codes: F02D 2250/31 Control of the fuel pressure
• CPC Class Codes: F02D 29/04 peculiar to engines driving pumps
• CPC Class Codes: F02D 41/38 of the high pressure type
• CPC Class Codes: F16H 61/42 involving adjustment of a pump or motor with adjustable output or capacity F16H61/46 takes precedence
• CPC Class Codes: F16H 61/465 for achieving a target input speed

Abstract

A method of and system for controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combustion engine. An engine speed deviation is obtained from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed thereof. Then a fuel injection target value in predetermined functional relation to the engine speed deviation, is obtained based on at least the engine speed deviation, and a fuel injection rate of the fuel injection pump is controlled based on the fuel injection target value. At the same time, a displacement volume target value of the hydraulic pump is determined based on at least the engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that as the engine speed deviation increases an input torque of the hydraulic pump decreases, and the displacement volume of the hydraulic pump is controlled based on the displacement volume target value.

Claims

1. A method of controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combustion engine, the method comprising the steps of:

(a) obtaining an engine speed deviation from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed of the engine;

(b) obtaining a fuel injection target value based on at least said engine speed deviation, said fuel injection target value being in predetermined functional relationship to said deviation;

(c) controlling a fuel injection rate of said fuel injection pump based on said fuel injection target value;

(d) determining, at the same time, a displacement volume target value of said hydraulic pump based on at least said engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that an input torque of said hydraulic pump decreases as the engine speed deviation increases;

(e) controlling the displacement volume of the hydraulic pump based on the displacement volume target value; and

wherein in step (b), said fuel injection target value is in a functional relationship to said engine speed deviation in such a manner that the target value increases substantially linearly until the deviation reaches a predetermined value and has a substantially constant maximum value after the deviation has reached the predetermined value.

2. A method of controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combustion engine, the method comprising the steps of:

(a) obtaining an engine speed deviation from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed of the engine;

(b) obtaining a fuel injection target value based on at least said engine speed deviation, said fuel injection target value being in a predetermined functional relationship to said deviation;

(c) controlling a fuel injection rate of said fuel injection pump based on said fuel injection target value;

(d) determining, at the same time, a displacement volume target value of said hydraulic pump based on at least said engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that an input torque of the hydraulic pump decreases as the engine speed deviation increases;

(e) controlling the displacement volume of the hydraulic pump based on the displacement volume target value; and

wherein step (b) comprises;

(i) judging whether said target speed is in an idling range, an intermediate speed range, or a high speed range;

(ii) obtaining said fuel injection target value from said engine speed deviation based on a first function set beforehand when the target speed is in the idling speed range;

(iii) obtaining said fuel injection target value from said engine speed deviation based on a second function set beforehand when the target speed is in the intermediate speed range; and

(iv) obtaining said fuel injection target value from the engine based on a present third function when the target speed is in the high speed range.

4. A control method as claimed in claim 2, wherein said first function and said second function are such that the fuel injection target value increases substantially linearly until the engine speed deviation reaches a first predetermined value and increases at a lower rate after it has reached the first predetermined value, the rate of increase being greater with the first function than with the second function, and wherein said third function is such that the fuel injection target value increases substantially linearly until the engine speed deviation reaches a second predetermined value and has a substantially constant maximum value after it has reached the second predetermined value.

5. A control method as claimed in claim 2, wherein said step (b) further comprises:

(v) obtaining an allowable maximum fuel injection rate from said engine speed deviation based on preset compensation characteristic function set beforehand; and

(vi) comparing the fuel injection target value obtained in step (ii), (iii) or (iv) with the allowable maximum fuel injection rate obtained in step (v) and selecting the allowable maximum fuel injection rate as a final fuel injection target value when the fuel injection target value is greater than the allowable maximum fuel injection rate.

3. A method of controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combustion engine, the method comprising the steps of:

(a) obtaining an engine speed deviation from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed of the engine;

(b) obtaining a fuel injection target value based on at least said engine speed deviation, said fuel injection target value being in predetermined functional relationship to said deviation;

(c) controlling a fuel injection rate of said fuel injection pump based on said fuel injection target value;

(d) determining, at the same time, a displacement volume target value of said hydraulic pump based on at least said engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that an input torque of the hydraulic pump decreases as the engine speed deviation increases;

(e) controlling the displacement volume of the hydraulic pump based on the displacement volume target value; and

wherein step (d) comprises;

(i) calculating the displacement volume target value from said engine speed deviation and said actual discharge pressure of the hydraulic pump based on a preset functional relationship in such a manner that as the engine speed deviation increases the product of the actual discharge pressure of the hydraulc pump and the displacement volume target value thereof decreases.

8. A control method as claimed in claim 3, wherein said displacement volume target value is in hyperbolic functional relation to the actual discharge pressure.

9. A control method as claimed in claim 3, wherein step (d) further comprises:

(ii) comparing said displacement volume target value with an allowable maximum displacement volume calculated from the actual displacement volume alone of the hydraulic pump and selecting the allowable maximum displacement volume as a final displacement volume when the displacement volume target value is greater than the allowable maximum displacement volume.

10. A control method as claimed in claim 3, wherein step (d) further comprises:

(ii) comparing the displacement volume target value, an externally manipulated variable of the displacement volume of the hydraulic pump and the allowable maximum displacement volume of the hydraulic pump calculated from the actual discharge pressure thereof alone with one another and selecting a smaller one of the externally manipulated variable and the allowable maximum displacement volume as a final displacement volume target value when the previous displacement volume target value is greater than the externally manipulated variable and/or the allowable maximum displacement volume.

6. A system for controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combustion engine, the system comprising:

(a) means for obtaining an engine speed deviation from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed of the engine;

(b) means for obtaining a fuel injection target value based on at least said engine speed deviation, said fuel injection target value being in predetermined functional relation to said deviation;

(c) means for controlling a fuel injection rate of said fuel injection pump based on said fuel injection target value;

(d) means for determining, at the same time, a displacement volume target value of said hydraulic pump based on at least said engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that the input torque of the hydraulic pump decreases as the engine speed deviation increases; and

(e) means for controlling the displacement volume of the hydraulic pump based on the displacement volume target value.

21. A control system as claimed in claim 6, wherein said fuel injection target value of said means (b) is set in functional relation to the engine speed deviation in such a manner that the target value increases substantially linearly until the deviation reaches a predetermined value and has a substantially constant maximum value after the deviation has reached the predetermined value.

22. A control system as claimed in claim 21, wherein said means (d) comprises:

(i) means for calculating said displacement volume target value from the engine speed deviation and the actual discharge pressure of the hydraulic pump based on a preset functional relation in such a manner that as the engine speed deviation increases the product of the actual discharge pressure of the hydraulic pump and the displacement volume target value thereof decreases.

23. A control system as claimed in claim 22, wherein said displacement volume target value of said means (i) is set at a hyperbolic functional relation to the actual discharge pressure.

24. A control system as claimed in claim 6, wherein said means (d) comprises:

(i) means for obtaining a control pressure command value based on said engine speed deviation, said control pressure command value being in predetermined functional relation to the deviation;

(ii) means for converting said control pressure command value into a hydraulic control pressure; and

(iii) means for introducing said control pressure and said actual discharge pressure of the hydraulic pump to hydraulic servo means for adjusting the displacement volume of the hydraulic pump thereby to determine said displacement volume target value.

25. A control system as claimed in claim 24, wherein said control pressure command value of said means (i) is in functional relation to said engine speed deviation in such a manner that the command value has a substantially constant minimum value until the engine speed deviation reaches a first predetermined value and increases substantially linearly until the deviation reaches a second predetermined value, and then has a substantially constant maximum value after the deviation has reached the second predetermined value.

26. A control system as claimed in claim 24, wherein said control pressure command value of said means (i) is in functional relation to said engine speed deviation in such a manner that the command value has a substantially constant maximum value until the engine speed deviation reaches a first predetermined value and decreases substantially linearly until the deviation reaches a second predetermined value, and then has a substantially constant minimum value after the deviation has reached the second predetermined value.

27. A control system as claimed in claim 6 wherein said hydraulic power system comprises a plurality of variable displacement hydraulic pumps, such control system further comprising:

(f) means for deciding the types of hydraulic actuators driven by at least two of said hydraulic pumps; and

(g) means for determining said displacement volume target values with respect to said two hydraulic pumps in such a manner that the distribution ratio of the output torque of the internal combustion engine to said two hydraulic pumps has a predetermined value in conformity with the decided types of the hydraulic actuators.

28. A control system as claimed in claim 6, wherein said means (d) comprises:

(i) means for calculating the discharge pressure target value from the engine speed deviation and the actual displacement volume of the hydraulic pump based on a preset functional relation in such a manner that as the engine speed deviation increases the product of the actual displacement volume of the hydraulic pump and the discharge pressure target value of the hydraulic pump increases;

(ii) means for obtaining the difference between the discharge pressure target value and the actual discharge pressure;

(iii) means for calculating a displacement volume increment of the hydraulic pump from said pressure difference based on a preset functional relation in such a manner that as the pressure difference increases the displacement volume increment of the hydraulic pump increases; and

(iv) means for obtaining a new displacement volume target value by adding to or subtracting from the previous displacement volume target value said displacement volume increment.

29. A control system as claimed in claim 28, wherein the discharge pressure target value of said means (i) is set at a hyperbolic functional relation to the actual displacement volume.

30. A control system as claimed in claim 28, wherein the discharge pressure target value of said means (i) is set at a hyperbolic functional relation to the actual displacement volume and smaller than an allowable maximum discharge pressure set by the rated pressure of the equipment.

31. A control system as claimed in claim 28, wherein the displacement volume increment of said means (iii) is set at a functional relation to said pressure difference in such a manner that the increment increases substantially linearly until the pressure difference reaches a predetermined value and has a substantially constant maximum value after the pressure difference has reached the predetermined value.

7. A method of controlling a hydraulic power system comprising an internal combustion engine receiving a supply of fuel from a fuel injection pump, and at least one variable displacement hydraulic pump driven by the internal combusion engine, the method comprising the steps of:

(a) obtaining an engine speed deviation from the difference between a target speed set by an accelerator operation of the internal combustion engine and an output speed of the engine;

(b) obtaining a fuel injection target value based on at least said engine speed deviation, said fuel injection target value being in a predetermined functional relationship to said deviation;

(c) controlling a fuel injection rate of said fuel injection pump based on said fuel injection target value;

(d) determining, at the same time, a displacement volume target value of said hydraulic pump based on at least said engine speed deviation and an actual discharge pressure of the hydraulic pump in such a manner that an input torque of the hydraulic pump decreases as the engine speed deviation increases;

(e) controlling the displacement volume of the hydraulic pump based on the displacement volume target value; and

wherein in step (b), said fuel injection target value is in the functional relationship to said engine speed deviation in such a manner that the target value increases until the deviation reaches a predetermined value and the increase in the target value is restricted thereafter, and in step (d), the decrease in the input torque of the hydraulic pump is initiated when the deviation at least approximately reaches said predetermined value at least when said target speed is in a high speed range.

11. A control method as claimed in claim 7, wherein step (d) comprises:

(i) obtaining a control pressure command value based on said engine speed deviation, said control pressure command value being in predetermined functional relation to the deviation;

(ii) converting said control pressure command value to a hydraulic control pressure; and

(iii) introducing said control pressure and said actual discharge pressure of the hydraulic pump to hydraulic servo means for adjusting the displacement volume of the hydraulic pump thereby to determine said displacement volume target value.

12. A control method as claimed in claim 11, wherein in step (i), said control pressure command value is in functional relation to said engine speed deviation in such a manner that the command value has a substantially constant minimum value until the engine speed deviation reaches a first predetermined value and increases substantially linearly until the deviation reaches a second predetermined value, and then has a substantially constant maximum value after the deviation has reached the second predetermined value.

13. A control method as claimed in claim 11, wherein in step (i), said control pressure command value is in functional relation to said engine speed deviation in such a manner that the command value has a substantially constant maximum value until the engine speed deviation reaches a first predetermined value and decreases substantially linearly until the deviation reaches a second predetermined value, and then has a substantially constant minimum value after the deviation has reached the second predetermined value.

14. A control method as claimed in claim 7 wherein said hydraulic drive system comprises a plurality of variable displacement hydraulic pumps, such method further comprising the steps of:

(f) deciding the types of hydraulic actuators driven by at least two of said hydraulic pumps; and

(g) performing steps (d) and (e) with respect to said two hydraulic pumps in such a manner that the distribution ratio of the output torque of the internal combustion engine to said two hydraulic pumps has a predetermined value in conformity with the decided types of the hydraulic actuators.

15. A control method as claimed in claim 14, wherein the step (d) performed in step (g) comprises calculating the displacement volume target values of the respective hydraulic pumps from the engine speed deviation and actual discharge pressures of the two hydraulic pumps based on preset predetermined functional relations for the hydraulic actuators in such a manner that as the deviation increases the products of the actual discharge pressures of the hydraulic pumps and the displacement volume target values decrease.

16. A control method as claimed in claim 14, wherein step (f) comprises actuating electric switches in conjunction with actuation of said hydraulic actuators, and the step (d) performed in step (g) comprises:

(i) obtaining a control pressure command value based on said engine speed deviation, said control pressure command value being in predetermined functional relation to the deviation,

(ii) obtaining at least two corrected control pressure command values having said distribution ratio from said control pressure target value by actuating said electric switches;

(iii) converting said two corrected control pressure command values into hydraulic control pressures;

(iv) introducing an actual discharge pressure of each said hydraulic pump to one end of a servo valve for adjusting the displacement volume of the associated hydraulic pump, said servo valve being connected to said hydraulic pump in such a manner that the position represents the displacement volume of the hydraulic pump, said servo valve having a spring mounted at the other end thereof; and

(v) introducing the control pressures into the other ends of said servo valves to adjust the biasing forces of the respective springs thereby to determine the positions of the servo valves by balancing the discharge pressures and the biasing forces of the springs.

17. A control method as claimed in claim 7, wherein step (d) comprises:

(i) calculating the discharge pressure target value from the engine speed deviation and the actual displacement volume of the hydraulic pump based on a functional relation set beforehand in such a manner that as the engine speed deviation increases the product of the actual displacement volume of the hydraulic pump and the discharge pressure target value of the hydraulic pump increases;

(ii) obtaining the difference between the discharge pressure target value and the actual discharge pressure;

(iii) calculating a displacement volume increment of the hydraulic pump from said pressure difference based on a preset functional relation in such a manner that as the pressure difference increases the displacement volume increment increases; and

(iv) obtaining a new displacement volume target value by adding to or subtracting from the previous displacement volume target value said displacement volume increment.

18. A control method as claimed in claim 17, wherein the discharge pressure target value of step (i) is in hyperbolic functional relation to said actual displacement volume.

19. A control method as claimed in claim 17, wherein the discharge pressure target value of step (i) is in hyperbolic functional relation to the actual displacement volume and smaller than an allowable maximum discharge pressure set by the rated pressure of the equipment.

20. A control method as claimed in claim 17, wherein the displacement volume increment of step (iii) is in functional relation to said pressure difference in such a manner that the increment increases substantially linearly until the pressure difference reaches a predetermined value and has a substantially constant maximum value after the pressure difference has reached the predetermined value.