GB2454683A - Accumulator and motor fluid drive - Google Patents

Accumulator and motor fluid drive Download PDF

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Publication number
GB2454683A
GB2454683A GB0722347A GB0722347A GB2454683A GB 2454683 A GB2454683 A GB 2454683A GB 0722347 A GB0722347 A GB 0722347A GB 0722347 A GB0722347 A GB 0722347A GB 2454683 A GB2454683 A GB 2454683A
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United Kingdom
Prior art keywords
hydraulic
fluid
accumulator
fluid flow
flow
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Granted
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GB0722347A
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GB2454683B (en
GB0722347D0 (en
Inventor
Grahame James Knowles
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Siemens AG
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Siemens AG
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Priority to GB0722347A priority Critical patent/GB2454683B/en
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Publication of GB2454683A publication Critical patent/GB2454683A/en
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Publication of GB2454683B publication Critical patent/GB2454683B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/20—Lubricating arrangements using lubrication pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/022—Installations or systems with accumulators used as an emergency power source, e.g. in case of pump failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N29/00—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A hydraulic circuit comprises a hydraulic accumulator 19 providing a first fluid flow 3, e.g. oil, at a first flow rate and high pressure through a pressure regulator 23 for driving a hydraulic motor 1 having a first capacity. A hydraulic pump 7 having a second capacity greater than the first capacity is driven through a coupling 17 by the hydraulic motor to produce a second fluid flow at a second flow rate higher than the first flow rate. Enables the high pressure, low flow accumulator to act as an energy store and provide a low pressure high flow emergency oil supply from a reservoir 15 to gas turbine bearings. The accumulator may be of compressed gas 25, piston and cylinder type. An accumulator gas and oil charging circuit is provided which introduces the relatively viscous oil between the gas and any gas charging valves to reduce leakage.

Description

-1 -2454683 A hydraulic circuit This invention relates to a hydraulic circuit.
A direct current system is known that supplies oil to the bearings of a gas turbine engine in the event of failure of other arrangements for the supply of the oil. Jirect current batteries power an electric motor that drives an oil pump. A battery charger is provided to top up the batteries. Such a system has the disadvantage that the direct current batteries are very large, heavy, and need a specially ventilated store room as they produce nitric acid fumes. Further, the batteries require regular topping up with distilled water.
Such systems are also expensive.
According to the present invention there is provided a hydraulic circuit comprising: a hydraulic accumulator for providing a first fluid flow travelling at a first flow rate; a hydraulic motor having a first capacity, the hydraulic motor being driven by the first fluid flow; and a hydraulic pump having a second capacity greater than the first capacity, the hydraulic pump being driven by the hydraulic motor, the hydraulic pump producing a second fluid flow travelling at a second flow rate higher than the first flow rate.
In a hydraulic circuit according to the preceding paragraph, it is preferable that the hydraulic motor has a fluid input line and a fluid output line and the first fluid flow is carried by the fluid input line, that the hydraulic pump has a fluid input line and a fluid output line and the second fluid flow is carried by the fluid output line, and that the hydraulic motor drives the hydraulic pump by means of a mechanical coupling.
In a hydraulic circuit according to either of the preceding two paragraphs, it is preferable that the hydraulic accumulator is a compressed gas hydraulic accumulator.
In a hydraulic circuit according to the preceding paragraph, it is preferable that a charging circuit is provided for charging the compressed gas hydraulic accumulator, the charging circuit being adapted to charge the accumulator so that the compressed gas of the accumulator is held between volumes of hydraulic fluid.
In a hydraulic circuit according to the preceding paragraph, it is preferable that the compressed gas hydraulic accumulator comprises a hydraulic cylinder containing a piston movable in either direction along the hydraulic cylinder by pressure applied to either side of the piston, and, when the compressed gas hydraulic accumulator is charged, hydraulic fluid is present in the hydraulic cylinder on one side of the piston and compressed gas is present in the hydraulic cylinder on the other side of the piston.
In a hydraulic circuit according to any one of the preceding five paragraphs, it is preferable that a hydraulic pressure intensifier is connected across the hydraulic motor to increase the speed of the hydraulic motor.
In a hydraulic circuit according to the preceding paragraph, it is preferable that the hydraulic pressure intensifier (i) receives a fluid flow from the hydraulic motor, and (ii) provides a fluid flow that is added to the first fluid flow to drive the hydraulic motor.
In a hydraulic circuit according to any one of the preceding seven paragraphs, it is preferable that the first fluid flow is a flow of oil, the second fluid flow is a flow of oil, and the second fluid flow travels to the bearings of a gas turbine engine.
The invention will now be described, by way of example, with reference to the accompanying drawings, in which: Fig 1 shows a hydraulic circuit for transforming a first fluid flow travelling at a first flow rate to a second fluid flow travelling at a second flow rate higher than the first flow rate; Fig 2 shows a piston type hydraulic accumulator, and, in the output line of the accumulator, a fluid control valve; Fig 3 shows a piston type hydraulic accumulator together with a hydraulic circuit for charging the accumulator; and Fig 4 shows a hydraulic motor of the hydraulic circuit of Fig 1, and, connected across the motor, a hydraulic pressure intensifier for increasing the speed of the motor.
The circuit of Fig 1 comprises a hydraulic motor 1 having a fluid input line 3 and a fluid output line 5, a hydraulic pump 7 having a fluid input line 9 and a fluid output line 11, a reservoir 13 to which leads fluid output line 5, a reservoir 15 from which leads fluid input line 9, and a mechanical coupling 17 by which hydraulic motor 1 drives hydraulic pump 7.
Let the capacity of hydraulic motor 1 be X' cc, i.e. X cc of fluid supplied via input line 3 gives rise to one complete revolution of motor 1. Let the capacity of hydraulic pump 7 be Y' cc, i.e. one complete revolution of pump 7 gives rise to the pumping via output line 11 of Y cc of fluid. Thus, if the flow rate of the fluid supplied on input line 3 to motor 1 is A' litres/mm, then the flow rate of the fluid supplied on output line 11 of pump 7 will be (Y/X) times A. It can therefore be seen that by making the capacity of hydraulic pump 7 greater than the capacity of hydraulic motor 1, the flow rate on input line 3 can be increased, the increased flow rate being supplied on output line 11.
Take the example X is 1cc, Y is 100cc, and A is 0.4 litres/mm, this provides an output flow rate of (100/1) times 0.4 equals 40 litres/mm. The increase in flow rate is at the expense of pressure. The product of pressure and volume at the input must equal the product of pressure and volume at the output. [f a duration of 1 mm is taken, and the pressure in input line 3 is 200 bar, then 200 times 0.4 must equal the pressure in output line 11 times 40. This gives the pressure in output line 11 as 2 bar.
A hydraulic circuit as shown in Fig 1 may be used in reserve equipment for the supply of oil to the bearings of a gas turbine engine, the reserve equipment only being used in the event that other arrangements for the supply of the oil fail.
A typical requirement for such equipment would be that it be capable of supplying oil at a flow rate of 40 litres/mm, at a pressure of 2 bar, for a duration of 3 hours. In this case the total volume of oil supplied is 40 litres/mm times 180 mins equals 7200 litres. This oil could be supplied by output line 11 of hydraulic pump 7. Pressure multiplied by volume at input line 3 of hydraulic motor 1 must equal pressure multiplied by volume at output line 11. Thus, taking the earlier example, 200 bar times volume at input line 3 equals 2 bar times 7200 litres. This gives the volume of oil required to be supplied on input line 3 as 72 litres.
A piston type hydraulic accumulator could suitably store 72 litres of oil at a pressure of 200 bar. Fig 2 shows a piston type hydraulic accumulator 19, and, in the output line 21 of accumulator 19, a flow control valve 23. The accumulator 19 contains a volume of gas 25 and 72 litres of oil 27. The gas 25 is in a compressed state such that the oil 27 is held at a pressure of 200 bar. Output line 21 would be connected to input line 3 of hydraulic motor 1. In the event that the reserve equipment for the supply of oil is required, flow control valve 23 would be opened to allow the oil 27 to pass via output line 21 to input line 3.
The accumulator 19 is required to store oil under pressure for a long period of time. Oil leakage during this time may occur resulting in a drop in pressure. Accordingly, to maintain pressure it may be required periodically to top up or charge the accumulator.
The hydraulic scheme shown in Fig 3 is intended to replace accumulator 19 in Fig 2. Thus, the hydraulic scheme of Fig 3 provides the required pressurised oil supply to flow control valve 23 in Fig 2. The hydraulic scheme of Fig 3 comprises a piston type hydraulic accumulator 31 and a hydraulic circuit for charging the accumulator. The hydraulic circuit comprises a high pressure oil supply 33, first and second solenoid operated, spring biased, two position, directional control valves 35, 37, solenoid operated check valves 39, 41, 43, 45, 47, pressure transducer 49, restrictor 51, fixed check valve 53, first and second oil tanks 55, 57, and pressurjsed air supply 65. Accumulator 31 comprises first and second hydraulic cylinders 59, 61, each of which contains a piston 63 that may be moved in either direction along its cylinder by pressure applied to either side of the piston.
Charging of the accumulator 31 with oil so that the oil is stored at high pressure occurs as follows. It is to be understood that initially all solenoids are de-energised.
In order to discharge air the following steps are taken.
Valves 41, 45 and 47 are opened to permit flow in both directions, and valves 35 and 37 are switched to setting Fill accumulator 31', i.e. the setting they are shown having in Fig 3. Oil from supply 33 travels via valves 35, 37 and 39 to the right hand chambers of cylinders 59, 61, moving pistons 63 to the left, forcing air to leave the left hand chambers of cylinders 59, 61 via valves 41, 45 and 47. In addition, a small amount of the oil leaving valve 39 travels via restrictor 51, and valves 53, 45 and 47, to tank 57. When the pistons 63 reach the left hand ends of cylinders 59, 61, a sudden pressure rise is seen by pressure transducer 49. In response to this, valves 41, 45 and 47 are closed and valve is switched to setting Direct to tank 55', i.e. the other setting to the one it is shown having in Fig 3.
In order to charge with air the following steps are taken.
Valves 39 and 43 are opened. Air from supply 65 travels via valves 43, 45 and 41 to the left hand chambers of cylinders 59, 61, moving pistons 63 to the right, forcing oil to leave the right hand chambers of cylinders 59, 61 and travel via valves 39, 37 and 35 to tank 55. The pressure seen by pressure transducer 49 will drop to zero when the pistons 63 reach the right hand ends of cylinders 59, 61. Tn response to this, valves 39 and 43 are closed.
In order to pressurise with oil the following steps are taken. Valve 35 is switched to setting Fill accumulator 31'.
Oil from supply 33 travels via valves 35, 37 and 39 to the right hand chambers of cylinders 59, 61, moving pistons 63 to the left, compressing the air in the left hand chambers of cylinders 59, 61. It is to be noted here that the air is trapped in the left hand chambers because valve 41 is closed.
In addition, a small amount of the oil leaving valve 39 travels via restrictor 51, via valves 53, 41, and along the hydraulic circuit lines 67 that lead to the left hand chambers. This forces into the left hand chambers the air present in (i) hydraulic circuit line 71 between circuit junction 75 and valve 41, and (ii) circuit lines 67. The passage of oil via restrictor 51, valves 53, 41, and circuit lines 67 takes place because valves 53, 41 always pass flow travelling from restrictor 51, and valve 45 always stops such flow unless it is open which it is not. When pressure transducer 49 sees the pressure to which it is required to charge accumulator 31 with oil, say a pressure of 200 bar as in the earlier example, valve 35 is switched to setting Direct to tank 55' and valve 37 is switched to setting Direct to flow control valve 23', i.e. the other setting to the one it is shown having in Fig 3. Thus, accumulator 31, charged with oil to a pressure of 200 bar, is now available as an oil supply to flow control valve 23.
Once the above procedure for charging accumulator 31 is completed: (1) all solenoids are in a de-energised state; (ii) air is present in the left hand chambers of cylinders 59, 61; and (iii) oil is present in the right hand chambers of cylinders 59, 61, in the hydraulic circuit lines 69 between the right hand chambers and valve 39, in the hydraulic circuit line 71 from circuit junction 73 to circuit junction 75, in the hydraulic circuit line 71 from circuit junction 75 to valve 41, and in hydraulic circuit lines 67.
The oil and air pressures are equal, and it is to be noted that the air is trapped between volumes of oil: on one side of the air is the oil in the right hand cambers of cylinders 59, 61, on the other side of the air is the oil in the hydraulic circuit lines 67. This trapping of the air by oil is beneficial as it prevents air leakage, and the only sealing required is against leakage of oil which has a much higher viscosity than air and hence is much easier to seal.
Leak tight check valves 39 and 41 provide the required sealing against leakage of oil. If leakage of oil occurs over time, as sensed by pressure transducer 49, then accumulator 31 can be topped up by repeating the pressurising with oil stage of the charging procedure, or by repeating the full charging procedure.
In the event that the reserve equipment for the supply of oil is required, the solenoid of valve 39 is energised to open valve 39 to allow accumulator 31 to discharge oil via valves 39 and 37 to flow control valve 23.
Fig 4 shows the hydraulic motor 1 of Fig 1, and, connected across the motor 1, a hydraulic pressure intensifier for increasing the speed of the motor. The hydraulic pressure intensifier comprises a piston and cylinder arrangement 81, a directional control valve 83, check valves 85, 87, and an oil tank 89. Piston and cylinder arrangement 81 comprises a single cylinder 91 containing a single piston 93. Piston 93 may be moved in either direction along cylinder 91 by pressure applied to the heads 95, 97 of the piston at either end of the piston. The heads 95, 97 have large and small areas respectively, and consequently single cylinder 91 comprises first and second sub-cylinders of correspondingly large and small cross sectional area. In Fig 4 the fluid output line 5 of hydraulic motor 1 leads to directional control valve 83 and check valve 85. This is a change to Fig 1 where fluid output line 5 leads to reservoir 13. Fig 4 omits to show the mechanical coupling 17 of Fig 1 by which hydraulic motor 1 drives the hydraulic pump 7 of Fig 1.
When single piston 93 is being driven to the left in Fig 4 the speed of hydraulic motor 1 is increased. This will now be explained. Let the speed of fluid flow on fluid input line 3 prior to junction 99 be qs'. Let the speed of fluid flow on fluid input line 3 following junction 99 be qm'. Let the speed of fluid flow on the line 101 to junction 99 be qa'.
Now, qm equals qs plus qa. qa will now be determined. The setting of directional control valve 83 is as shown in Fig 4.
Fluid travelling at speed qm will leave motor 1 on fluid output line 5 to reach junction 103. For reasons that will be given below, the fluid will not then travel via check valve 85, but will travel via valve 83 to the right hand chamber of piston and cylinder arrangement 81. This drives to the left piston 93, forcing fluid to leave the left hand chamber 107 of arrangement 81 on line 101. If the ratio of the area of piston head 95 to the area of piston head 97 is R' then the speed qa of fluid flow on line 101 will be qmIR. Thus, qm equals qs plus qm/R. To take the example that R equals 1.5, then qm equals three times qs, i.e. the speed of hydraulic motor 1 is three times what it would be if the hydraulic pressure intensifier were not present. it is stated earlier in this paragraph that fluid reaching junction 103 will not -10 -then travel via valve 85 but will travel via valve 83. This is because valve 85 is connected to the high pressure side of piston and cylinder arrangement 81 and valve 83 to the low pressure side.
Increasing the speed of hydraulic motor 1 may well be useful: (i) the efficiency of the motor may be greater at higher speed; and (ii) it may be required to reduce the capacity of hydraulic pump 7, see Fig 1. Regarding reducing the capacity of the pump, in the example of the previous paragraph where qm equals three times qs, the pump's capacity can be reduced to a third without reducing the speed of fluid flow on fluid output line 11 of the pump.
Once piston head 97 has reached the left hand end of left hand chamber 107, valve 83 is switched to the other setting to that shown in Fig 4. In this setting fluid reaching junction 103 travels via valve 85 to left hand chamber 107, driving piston 93 to the right, forcing fluid from right hand chamber 105 via valve 83 to tank 89. Once piston head 95 reaches the right hand end of right hand chamber 105, valve 83 is switched back to the setting shown in Fig 4, and piston 93 is driven to the left again.

Claims (7)

  1. -1]. -Claims: 1. A hydraulic circuit comprising: a hydraulic accumulator for providing a first fluid flow travelling at a first flow rate; a hydraulic motor having a first capacity, the hydraulic motor being driven by the first fluid flow; and a hydraulic pump having a second capacity greater than the first capacity, the hydraulic pump being driven by the hydraulic motor, the hydraulic pump producing a second fluid flow travelling at a second flow rate higher than the first flow rate.
  2. 2. A hydraulic circuit according to claim 1 wherein the hydraulic motor has a fluid input line and a fluid output line and the first fluid flow is carried by the fluid input line, wherein the hydraulic pump has a fluid input line and a fluid output line and the second fluid flow is carried by the fluid output line, and wherein the hydraulic motor drives the hydraulic pump by means of a mechanical coupling.
  3. 3. A hydraulic circuit according to claim 1 or claim 2 wherein the hydraulic accumulator is a compressed gas hydraulic accumulator.
  4. 4. A hydraulic circuit according to claim 3 wherein a charging circuit is provided for charging the compressed gas hydraulic accumulator, the charging circuit being adapted to charge the accumulator so that the compressed gas of the accumulator is held between volumes of hydraulic fluid.
  5. 5. A hydraulic circuit according to claim 4 wherein the compressed gas hydraulic accumulator comprises a hydraulic cylinder containing a piston movable in either direction -12 -along the hydraulic cylinder by pressure applied to either side of the piston, and, when the compressed gas hydraulic accumulator is charged, hydraulic fluid is present in the hydraulic cylinder on one side of the piston and compressed gas is present in the hydraulic cylinder on the other side of the piston.
  6. 6. A hydraulic circuit according to any one of the 00 preceding claims wherein a hydraulic pressure intensifier is connected across the hydraulic motor to increase the speed of the hydraulic motor.
    L.C')
  7. 7. A hydraulic circuit according to claim 6 wherein the hydraulic pressure intensifier (i) receives a fluid flow from the hydraulic motor, and (ii) provides a fluid flow that is added to the first fluid flow to drive the hydraulic motor.
    6. A hydraulic circuit according to any one of the preceding claims wherein a hydraulic pressure intensifier is connected across the hydraulic motor to increase the speed of the hydraulic motor.
    7. A hydraulic circuit according to claim 6 wherein the hydraulic pressure intensifier (i) receives a fluid flow from the hydraulic motor, and (ii) provides a fluid flow that is added to the first fluid flow to drive the hydraulic motor.
    8. A hydraulic circuit according to any one of the preceding claims wherein the first fluid flow is a flow of oil, the second fluid flow is a flow of oil, and the second fluid flow travels to the bearings of a gas turbine engine.
    Amendments to the claims have been filed as follows: Claims: 1. A hydraulic circuit comprising: a hydraulic accumulator for providing a first fluid flow travelling at a first flow rate of a first number of litres per minute; a hydraulic motor having a first capacity, the hydraulic motor being driven by the first fluid flow; and a hydraulic pump having a second capacity greater than the first capacity, the hydraulic pump being driven by the hydraulic motor, the hydraulic pump producing a second fluid flow travelling at a second flow raze of a second number of litres per minute higher than the first flow rate, wherein the first fluid flow CO is a flow of oil, the second fluid flow is a flow of oil, and the second fluid flow travels to the bearings of a gas turbine engine.
    IC) 2. A hydraulic circuit according to claim 1 wherein the hydraulic motor has a fluid input line and a fluid output line and the first fluid flow is carried by the fluid input line, wherein the hydraulic pump has a fluid input line and a fluid output line and the secord fluid flow is carried by the fluid output line, and wherein the hydraulic motor drives the hydraulic pump by means of a mechanical coupling.
    3. A hydraulic circuit according to claim 1 or claim 2 wherein the hydraulic accumulator is a compressed gas hydraulic accumulator.
    4. A hydraulic circuit according to claim 3 wherein a charging circuit is provided for charging the compressed gas hydraulic accumulator, the charging circuit being adapted to charge the accumulator so that the compressed gas of the accumulator is held between volumes of hydraulic fluid.
    -fLI-- 5. A hydraulic circuit according to claii 4 wherein the compressed gas hydraulic accumulator comprises a hydraulic cylinder containing a piston movable in either direction along the hydraulic cylinder by pressure applied to either side of the piston, and, when the compressed gas hydraulic accumulator is charged, hydraulic fluid is present in the hydraulic cylinder on one side of the piston and compressed gas is present in the hydraulic cylinder on the other side of the piston.
GB0722347A 2007-11-14 2007-11-14 A hydraulic circuit Expired - Fee Related GB2454683B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB0722347A GB2454683B (en) 2007-11-14 2007-11-14 A hydraulic circuit

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Application Number Priority Date Filing Date Title
GB0722347A GB2454683B (en) 2007-11-14 2007-11-14 A hydraulic circuit

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GB0722347D0 GB0722347D0 (en) 2007-12-27
GB2454683A true GB2454683A (en) 2009-05-20
GB2454683B GB2454683B (en) 2009-10-21

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMO20120305A1 (en) * 2012-12-13 2014-06-14 Carelli Nicola Ing METHOD OF PRODUCTION OF ROLLING MOTION ENERGY
IT202000012133A1 (en) 2020-05-27 2021-11-27 Nicola Carelli NEW SYSTEM FOR THE PRODUCTION OF ELECTRICITY AND CRYPTOCURRENCIES BY ROLLING MOTION

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2609065A (en) * 1950-08-22 1952-09-02 Gen Electric Means for scavenging engine bearings
US4026107A (en) * 1974-11-23 1977-05-31 Osrodek Badawczo-Rozwojowy Przemyslu Budowy Urzaszen Chemicznych "Cebea" Electrohydraulic press drive system
US4553391A (en) * 1982-11-30 1985-11-19 Mannesmann Rexroth Gmbh Control device for a hydraulic cylinder for maintaining the pulling force thereof constant

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2609065A (en) * 1950-08-22 1952-09-02 Gen Electric Means for scavenging engine bearings
US4026107A (en) * 1974-11-23 1977-05-31 Osrodek Badawczo-Rozwojowy Przemyslu Budowy Urzaszen Chemicznych "Cebea" Electrohydraulic press drive system
US4553391A (en) * 1982-11-30 1985-11-19 Mannesmann Rexroth Gmbh Control device for a hydraulic cylinder for maintaining the pulling force thereof constant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMO20120305A1 (en) * 2012-12-13 2014-06-14 Carelli Nicola Ing METHOD OF PRODUCTION OF ROLLING MOTION ENERGY
WO2014090400A1 (en) * 2012-12-13 2014-06-19 Gallelli Vincenzo Method for the production of energy from a rolling motion
US10683853B2 (en) 2012-12-13 2020-06-16 Vincenzo GALLELLI Method for the production of energy from a rolling motion
IT202000012133A1 (en) 2020-05-27 2021-11-27 Nicola Carelli NEW SYSTEM FOR THE PRODUCTION OF ELECTRICITY AND CRYPTOCURRENCIES BY ROLLING MOTION

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GB2454683B (en) 2009-10-21
GB0722347D0 (en) 2007-12-27

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Effective date: 20111114