GB2118241A - A hydraulic or pneumatic power supply system for a motor- vehicle including an ic engine - Google Patents
A hydraulic or pneumatic power supply system for a motor- vehicle including an ic engine Download PDFInfo
- Publication number
- GB2118241A GB2118241A GB08203846A GB8203846A GB2118241A GB 2118241 A GB2118241 A GB 2118241A GB 08203846 A GB08203846 A GB 08203846A GB 8203846 A GB8203846 A GB 8203846A GB 2118241 A GB2118241 A GB 2118241A
- Authority
- GB
- United Kingdom
- Prior art keywords
- hydraulic
- carrier member
- feedback control
- piston
- pneumatic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/04—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving pumps
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A feedback control 4 is connected in the fluid supply line between a pump and a road digger. The feedback control 4 is arranged to act mechanically on a carburettor or fuel rack to alter the fuel intake to the engine and control its speed in response to the pressure of fluid in the supply line. Fluid supplied to inlet 7 acts on the member 11 to move the piston 10 connected to the carburettor or rack until the member 11 engages the member 8a. At a higher pressure the piston 10 moves relative to the member 11 against the bias of the spring 17. <IMAGE>
Description
SPECIFICATION
A hydraulic or pneumatic power supply system and a motor-vehicle including such a system
This invention relates to a hydraulic or pneumatic power supply system, to a motor-vehicle including such a system, and more particularly but not exclusively to such a system for supplying hydraulic power to a hydraulic device which operates under a variable load, such as a piston-action road breaker or digger.
It is well known to power such road breakers by a hydraulic or pneumatic power supply system which includes an internal combustion engine of a motor vehicle as a power source.
It is also known for the power source to power one or more road breakers or other hydraulic devices or equipment including, for example, a generator. Usually, the speed of the engine, and therefore the power output to the hydraulic device or devices is pre-set. The power output to the device or devices may be altered by manually varying the speed of the engine, but, where the load on the device or devices varies considerably, there is still a tendency for power to be wasted so that the system is more inefficient than it need be.
It is an object of the present invention to alleviate this disadvantage.
According to the present invention there is provided a hydraulic or pneumatic power supply system for supplying hydraulic or pneumatic power to a hydraulically or pneumatically powered device, comprising a hydraulic or pneumatic pump connected, or connectable, to a power source of the system, for example, an internal combustion engine, the pump being adapted to supply hydraulic or pneumatic power from the power source to the device, a hydraulic or pneumatic feedback control responsive to a variation in pressure of hydraulic or pneumatic power supplied to the device by the pump, said feedback control being arranged, in use, to regulate the power supplied to the pump from the power source in response to said variation.
Further according to the present invention there is provided a motor vehicle including a system as described in the immediately preceding paragraph, and in which the power source is an internal combustion engine of the vehicle.
By the present invention the power output supplied by the power source to the hydraulic or pneumatic device may be regulated automatically, so that more power is supplied to the device as and when required thereby resulting in a more efficient operation of the power source.
Preferably, the power source comprises a speed controllable prime mover (an internal combustion engine being an example of such) and the feedback control is capable of regulating the power supplied to the pump by influencing the speed of the prime mover. Where the prime mover is a petrol engine the feedback control, preferably, is mechanically cooperable with the carburettor to regulate the supply of fuel to the engine. Where the prime mover is a diesel engine the feedback control is, preferably, mechanically co-operable with the fuel rack of the engine. The feedback control may be provided with a mechanical actuator, to act on the carburettor or fuel rack.
Additionally the feedback control may be connected into the system so that the actuator is in contact with the pressurizable medium powering the device.
In one embodiment of the present invention, the feedback control, preferably, operates in two modes, the first of the modes being suitable to allow low power to be supplied to said device when the device is operating in a substantially no-load condition and the second of the two modes being suitable to allow higher power to be supplied to said device under a varying load condition. In this instance, when the prime mover is an internal combustion engine and the device a road digger, as soon as the digger is switched into the hydraulic circuit under a no-load condition the speed of the engine may be raised by a fast tick-over during the first mode, the second mode of operation being when the digger is operating under a varying load condition (i.e. digging or breaking the road surface).
The two modes are provided to suit the power requirements under the two conditions, and the feedback control may be such as to restrain a sudden violent surge or fluctation in power when the device is switched into or out of the circuit.
The system may include one or more hydraulic or pneumatically powered devices, or be adapted for connection to more than one such device.
The feedback control is, preferably, adjustable to achieve different hydraulic or pneumatic response characteristics to suit the particular power source and hydraulic or pneumatic device or devices.
Where two modes of operation are provided as aforesaid and the feedback control has a mechanical actuator as aforesaid, the feedback control is, preferably, an elongate housing and the actuator is in the form of a piston axially slidable in the housing, a first carrier member being provided to move axially with said piston in said first mode which is stationary in said second mode, said piston continuing to move axially in said second mode relative to said carrier member, said carrier member moving in said first mode against spring biassing means.There may also be provided a second carrier member spring biassed away from the first carrier member, the second carrier member being connected to said piston and movable therewith in the first and second modes, the second carrier member being engageable with the stationary first member to limit the axial movement of the piston rod at the end of said second mode of operation.
According to a second aspect of the present invention there is provided a feedback control for use as part of a hydraulic or pneumatic power supply system for supplying hydraulic or pneumatic power to a hydraulically or pneumatically powered device, the control having two modes of operation, the first of the two modes being suitable to allow low power to be supplied to a hydraulic or pneumatic device of the system when the device is operating in a substantially no-load condition and the second of the two modes being suitable to allow higher power to be supplied to the device under a varying load condition, the control having an elongate housing and a mechanical actuator in the form of a piston axially slidable in the housing, a first carrier member being provided to move axially with said first piston in said first mode which is stationary in said second mode, said piston continuing to move axially in said second mode relative to said carrier member, said carrier member moving in said first mode against spring biassing means.
An embodiment of a motor vehicle including a hydraulic power supply system in accordance with the present invention will now be described, by way of example only, with reference to the accompanying drawings in which:
Figure 1 shows a much-simplified diagrammatic view of the motor vehicle and system;
Figure 2 shows a cross-sectional view of a feedback control of the system; and
Figure 3 shows a hydraulic circuit of the system.
Fig. 1 shows a motor vehicle body 1 housing a power source in the form of a prime mover 2 for powering a hydraulic pump 3.
The prime mover 2 is a petrol-driven internal combustion engine, and a hydraulic feedback control 4 is mounted on a carburettor 5 of the engine. The feedback control 4 is connected in the hydraulic fluid supply line between the pump 3 and a hydraulically powered device 6, in this instance a road digger 6. In this embodiment the feedback control 4, pump 3 and device 6 are individual elements linked together by a hydraulic supply line but in other embodiments two or more of these individual elements may be integrated into one element.
The pump 3 is connected to engine 2 and digger 6 in a manner known per se, and, additionally, the feedback control 4 is arranged to act mechanically on the carburettor 5 to alter the fuel intake to the engine and thereby control the speed of the engine in response to the pressure of the hydraulic fluid in the supply line.
The control 4 is shown in detail in Fig. 2, hydraulic fluid being fed into the control through connector portion 7. The control 4 has an elongate housing 8 closed at its righthand end in Fig. 2 by an end cap 9, and connector 7 is located laterally of the housing (at the top of Fig. 2). A mechanical actuator or piston 10 is arranged co-axially in housing 8 and extends outwardly from the left-hand end of the housing. The amount by which the piston 10 extends from the housing 8 is made to vary according to the pressure of the hydraulic fluid within the housing in a manner explained below, and the piston 10 is arranged to act directly on the carburettor to vary the fuel intake to the engine 2. The piston 10 extends through a gland 8a, which closes off the left-hand end of the housing 8, and through a first carrier member 11 slidable in the housing along the axis of piston 10.As shown, carrier member 11 is sealed to housing 8 by a ring seal 1 2. The diameter of piston 10 is stepped so that carrier member 11 engages an annular abutment or rim 10a at its left-hand end. Piston 10 is also sealed to carrier member 11 by ring seal 13, and extends through a second carrier member 14.
A lock nut 1 5 on the right-hand end of piston 10 is seated in a circular depression 1 4a at the right-hand end of carrier members 1 4. A first resilient means in the form of helicalcoiled compression spring 1 6 acts between, and surrounds part of, gland 8a and carrier member 11. The spring 1 6 is arranged coaxially with piston 10 in housing 8. A second resilient means in the form of helical-coiled compression spring 1 7 acts between, and surrounds part of carrier member 11 and carrier member 14. Spring 1 6 is aligned with spring 1 7 on axially opposing sides of carrier member 11.
The connector portion 7 is connected into the hydraulic power supply line to the road digger 6, and fluid may be fed into a chamber 1 8 defined by housing 8 which surrounds the right-hand end of piston 10. Fluid is fed into the chamber 1 8 via port 1 9 after passing through a ball valve 20 in the connector 7.
The ball valve 20 is a free-flow/flow-restricted valve and has a ball 21 urged outwardly from housing 8 by a compression spring 22. The ball 21 may be adjusted on its seat by grub screw 23 to adjust the amount of fluid permitted to flow through port 19.
The ball is capable of being displaced downwardly against resistance provided by spring 22, which spring returns the ball to its original position once the pressure is removed.
Fluid can, therefore, flow freely into chamber 1 8 from port 1 9 but is restricted from flowing out of the chamber via port 19. This helps to prevent a violent surge of power when the road digger 6 is switched on and off.
The axial movement of the piston 10 to the left is limited by adjuster means 24 which is partially located in chamber 1 8. The adjuster means 24 consists of an axially slidable carriage 25 surrounding carrier member 14, an annular, rotatable, stop adjuster 26 sealed to the housing 8 by a ring seal 27, and a guide bolt 28. The left-hand end of the carriage 25 acts as an adjustable stop for carrier member 14, and the carriage 25 is in screw-threaded engagement with the stop adjuster 26. The guide bolt 28 passes through the housing into an upper elongate slot in carriage 25 to limit rotational movement of the carriage 25 relative to the housing 8 during axial displacement towards or away from carrier member 11.
In operation, the feedback control 4 operates in essentially two modes. As soon as the digger 6 is switched on and is operating in a no-load condition it is desirable merely to raise the speed of engine 2 to a fast tick-over in which the control 4 operates in a first or low pressure mode. Hydraulic fluid flowing in the supply line to the digger enters connector 7 and displaces ball 21 from its seat against biassing provided by spring 22 to allow fluid into chamber 18 through port 19. The fluid acts on the carrier member 11 and urges the member 11 against biassing provided by spring 16, and thereby moves piston 1 0 (by engagement of rim 1 Oa with member 11) to the left in Fig. 2. Piston 10 extends from the housing and acts on the carburettor 6 directly, until the carrier member 11 engages the gland 8a and is stopped from any further axial movement to the left.The feedback control 4 then operates in a second or high pressure mode in which, as the pressure through inlet 1 9 increases, the piston 10 is further extended from the housing whilst the carrier member 11 remains stationary. The carrier member 14 moves to the left in both the first and second modes against biassing provided by spring 1 7 (by engagement of lock nut 1 5 with circular depression 14a).
As pressure increases in the second mode the piston 10 slides to the left through carrier member 11, further extending from the housing 8 to increase the speed of engine 2 progressively in accordance with the pressure variation, until carrier member 1 4 engages the stop on carrier member 11. In this position carrier member 14 extends beyond carriage 25. The final extent to which piston 10 can extend beyond housing 8 may be provided by carrier member 1 4 engaging carriage 25, depending on the setting of the adjuster means 24.
Adjuster means 24 may be used to vary the modes of operation to suit different devices and various springs may be used to suit the biassing required. Rotation of stop adjuster 26 forces carriage 25 to move axially, its rotational movement being prevented by guide bolt 28 engaging in the elongate slot in the carriage. Gland 8a may also be screwed in and out of housing 8 to adjust the spring force of spring 1 6.
Fig. 3 shows a hydraulic circuit for transmitting hydraulic power to road digger 6 and also to a second device in the form of an auxiliary generator 29. A tank 30 supplies hydraulic fluid to two hydraulic pumps 31, 32, arranged in tandem. Pump 31 is arranged to feed hydraulic fluid to a hose reel assembly 33 attached to the digger 6 (not shown in
Fig. 3) and pump 32 is arranged to supply hydraulic power to generator 29. The feedback control 4 is shown connected in the hydraulic supply line between pump 31 and hose reel assembly 33 via shuttle valve 34; ball valve 20 is shown diagrammatically. As shown, hydraulic fluid is fed to the hose reel assembly 33 and then back along to the control 4 via shuttle valve 34 to control the speed of engine 2. The feedback control 4 may also, or alternatively, be switched into the hydraulic supply line between the generator 2 and pump 32 via shuttle valve 34. The control 4 as shown in the hydraulic circuit is particularly useful in saving power when the hydraulic device or devices are operating in conditions where the load varies considerably.
The remainder of the circuit should be selfexplanatory and, therefore, is not described in further detail.
Claims (13)
1. A hydraulic or pneumatic power supply system for supplying hydraulic or pneumatic power to a hydraulically or pneumatically powered device, comprising a hydraulic or pneumatic pump connected, or connectable, to a power source of the system, for example, an internal combustion engine, the pump being adapted to supply hydraulic or pneumatic power from the power source to the device, a hydraulic or pneumatic feedback control responsive to a variation in pressure of hydraulic or pneumatic power supplied to the device by the pump, said feedback control being arranged, in use, to regulate the power supplied to the pump from the power source in response to said variation.
2. A system as claimed in Claim 1 in which the power source comprises a speedcontrollable prime mover and the feedback control is capable of regulating said power supplied to the pump by influencing the speed of the prime mover.
3. A system as claimed in Claim 2 in which the feedback control has two modes of operation, the first of the two modes being suitable to allow low power to be supplied to said device when the device is operating in a substantially no-load condition and the second of the two modes being suitable to allow higher power to be supplied to the said device under a varying load condition.
4. A system as claimed in Claim 2 or
Claim 3 in which the feedback control has a mechanical actuator co-operable with the prime mover mechanically to vary the speed of the prime mover, said mechanical actuator being arranged, in use, to be in direct operative contact with hydraulic or pneumatic medium powering said device.
5. A system as claimed in Claim 4 in which the speed-controllable prime mover is a petrol driven internal combustion engine and the mechanical actuator is adapted to act on a carburettor of the engine, in use.
6. A system as claimed in Claim 4 in which the speed-controllable prime mover is a diesel engine and the mechanical actuator is adapted to act on a fuel rack of the engine, in use.
7. A system as claimed in any one of
Claims 4 to 6 when dependent on Claim 3 in which the feedback control comprises an elongate housing and the actuator is in the form of a piston axially slidable in the housing, a first carrier member being provided to move axially with said piston in said first mode which is stationary in said second mode, said piston continuing to move axially in said second mode relative to said carrier member, said carrier member moving in said first mode against spring biassing means.
8. A system as claimed in Claim 7 comprising a second carrier member spring biassed away from the first carrier member, the second carrier member being connected to said piston and movable therewith in the first and second modes, the second carrier member being engageable with the stationary first member to limit the axial movement of the piston rod at the end of said second mode of operation.
9. A system as claimed in any one of the preceding claims in which the feedback control is adjustable.
10. A system as claimed in Claim 9 when dependent from Claim 8 in which the feedback control is adjustable by adjuster means comprising a carriage surrounding the second carrier member which is co-operable with an adjuster stop means and with an axial guide means, for example, a guide bolt in an elongate slot in the second carrier member, so that on rotation of said adjuster stop means about the axis of the piston the carriage carrying a stop for the second carrier member moves axially.
11. A system as claimed in any one of the preceding claims comprising a hydraulic or pneumatic powered device or devices.
1 2. A system as claimed in Claim 1 in which the feedback control is substantially as herein described and illustrated with reference to Fig. 2 of the accompanying drawings.
13. A system as claimed in Claim 1 comprising a hydraulic circuit substantially as herein described and illustrated with reference to Figs. 1 and 3 of the accompanying drawings.
1 4. A motor vehicle including a system as claimed in any one of the preceding claims in which the power source is the internal combustion engine of the vehicle.
1 5. A feedback control for use as part of a hydraulic or pneumatic power supply system for supplying hydraulic or pneumatic power to a hydraulically or pneumatically powered device, the control having two modes of operation, the first of the two modes being suitable to allow low power to be supplied to a hydraulic or pneumatic device of the system when the device is operating in a substantially no-load condition and the second of the two modes being suitable to allow higher power to be supplied to the device under a varying load condition, the control having an elongate housing and a mechanical actuator in the form of a piston axially slidable in the housing, a first carrier member being provided to move axially with said first piston in said first mode which is stationary in said second mode, said piston continuing to move axially in said second mode relative to said carrier member, said carrier member moving in said first mode against spring biassing means.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08203846A GB2118241A (en) | 1982-02-10 | 1982-02-10 | A hydraulic or pneumatic power supply system for a motor- vehicle including an ic engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08203846A GB2118241A (en) | 1982-02-10 | 1982-02-10 | A hydraulic or pneumatic power supply system for a motor- vehicle including an ic engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB2118241A true GB2118241A (en) | 1983-10-26 |
Family
ID=10528225
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08203846A Withdrawn GB2118241A (en) | 1982-02-10 | 1982-02-10 | A hydraulic or pneumatic power supply system for a motor- vehicle including an ic engine |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2118241A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0249138A2 (en) * | 1986-06-11 | 1987-12-16 | Shimadzu Corporation | Acceleration modulator for a hydraulic driving system |
| WO2009112121A1 (en) * | 2008-03-12 | 2009-09-17 | Weber Hydraulik Gmbh | Controller and the use thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB732660A (en) * | 1950-10-19 | 1955-06-29 | City Tank Corp | Servo-motor control for the throttle valve or fuel feed of an internal combustion engine |
| GB1439193A (en) * | 1972-07-24 | 1976-06-09 | Sargent Industries | Noise reduction apparatus and method |
| GB1495822A (en) * | 1974-01-23 | 1977-12-21 | Akermans Verkstad Ab | Speed regulators for internal combustion engines particularly diesel engines in earth workers |
| GB2017599A (en) * | 1978-03-03 | 1979-10-10 | Nissan Motor | Motor Vehicle Equipped with Power Steering System |
| GB2072260A (en) * | 1980-02-14 | 1981-09-30 | Durham M E | Fuel control system for an earth-moving vehicle |
-
1982
- 1982-02-10 GB GB08203846A patent/GB2118241A/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB732660A (en) * | 1950-10-19 | 1955-06-29 | City Tank Corp | Servo-motor control for the throttle valve or fuel feed of an internal combustion engine |
| GB1439193A (en) * | 1972-07-24 | 1976-06-09 | Sargent Industries | Noise reduction apparatus and method |
| GB1495822A (en) * | 1974-01-23 | 1977-12-21 | Akermans Verkstad Ab | Speed regulators for internal combustion engines particularly diesel engines in earth workers |
| GB2017599A (en) * | 1978-03-03 | 1979-10-10 | Nissan Motor | Motor Vehicle Equipped with Power Steering System |
| GB2072260A (en) * | 1980-02-14 | 1981-09-30 | Durham M E | Fuel control system for an earth-moving vehicle |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0249138A2 (en) * | 1986-06-11 | 1987-12-16 | Shimadzu Corporation | Acceleration modulator for a hydraulic driving system |
| EP0249138A3 (en) * | 1986-06-11 | 1989-02-15 | Shimadzu Corporation | Acceleration modulator for a hydraulic driving system |
| WO2009112121A1 (en) * | 2008-03-12 | 2009-09-17 | Weber Hydraulik Gmbh | Controller and the use thereof |
| US8545188B2 (en) | 2008-03-12 | 2013-10-01 | Weber Hydraulik Gmbh | Controller and the use thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |