瑞典专利SE0950557A1 Hydraulic system, energy production plant and use of a hydraulic system

专利PDF首页>>瑞典专利

专利附录

专利说明

权利要求

类似技术

同族专利

引用文献

法律状态

优先权

专利摘要:

公开号:SE0950557A1
申请号:SE0950557
申请日:2009-07-14
公开日:2011-01-15
发明作者:Haakan Ingvast
申请人:Exencotech Ab；
IPC主号:

专利说明:

2 shows at least one further device for transmitting hydraulic energy to said at least one hydraulic motor.
Said at least one further device may be at least one ﬂ fate accumulator for accumulating ﬂ uidum when a de fate from said at least one hydraulic pressure generator is greater than an intended ﬂ fate to said at least one hydraulic motor and for delivering ﬂ uidum when ﬂ the fate of said hydraulic pressure means is at least one. than the intended ﬂ fate of the at least one hydraulic motor. Said at least one further device may be at least one further hydraulic pressure generator in hydraulic connection with said at least one hydraulic motor for transferring hydraulic energy to said at least one hydraulic motor. The at least one further device may be - at least one ﬂ fate accumulator for accumulating ﬂ uidum when a ﬂ fate from said at least one hydraulic pressure generator is greater than an intended ﬂ fate to said at least one hydraulic motor and for delivering ﬂ uidum when ﬂ a greater degree of said hydraulic pressure generators less than the intended till fate of said at least one hydraulic motor as well as - at least one further hydraulic pressure generator in hydraulic connection with said at least one hydraulic motor for transferring hydraulic energy to said at least one hydraulic motor. At least a pair of the hydraulic pressure generators may comprise a first hydraulic pressure generator and a second hydraulic pressure generator mutually hydraulically connected in parallel. The first and second pressure generators may be arranged to operate in cycles so that the first hydraulic pressure generator delivers an output while the second hydraulic pressure generator has an output while the first hydraulic pressure generator has an output while the second hydraulic pressure generator delivers an output . The first and second hydraulic pressure generators may be arranged to operate with a mutual phase difference of approximately 180 degrees. At least one of said at least one hydraulic pressure generators may be in hydraulic connection with said at least one hydraulic motor in a closed cycle. At least one of said at least one hydraulic pressure generator and / or at least one of said at least one further pressure generator may be in hydraulic connection with said at least one hydraulic motor in a closed cycle. At least one of said at least one hydraulic motor may have a variable displacement. The displacement may be variable in accordance with variations in a pressure of a ﬂ uidum, which ﬂ uidum transmits hydraulic energy to the at least one of said at least one hydraulic motor.
The displacement can be arranged to increase when the pressure increases while the displacement is arranged to decrease when the pressure decreases.
The displacement may be variable in accordance with variations in a ﬂ fate of a ﬂ uidum, which ﬂ uidum transmits hydraulic energy to the at least one of said at least one hydraulic motor. The displacement can be arranged to increase when the fate increases while the displacement is arranged to decrease when the fate decreases. At least one control system for controlling at least one of said at least one hydraulic motor. Said at least one control system is arranged to control a displacement of said at least one of said at least one hydraulic motor.
The hydraulic system may include at least one pressure transducer for transforming a hydraulic pressure into the hydraulic system. At least one of said at least one pressure transducer may be hydraulically connected between on the one hand said at least one hydraulic pressure generator and on the other hand said at least one hydraulic motor. The at least one pressure transducer may be arranged to lower the hydraulic pressure in the hydraulic system from a higher pressure in a flow from said at least one hydraulic pressure generator to a lower pressure in the flow to said at least one hydraulic motor. At least one of said at least one hydraulic pressure generators may be a pump. At least one of said at least one hydraulic pressure generators and / or at least one of said at least one additional hydraulic pressure generators may be a pump. The pump can be linear with pressure strokes for ﬂ uidum delivery and return strokes for ﬂ uidum suction. At least one of said at least one hydraulic pressure generators may have at least one path for ﬂuidum ﬂ fate, which path comprises at least one mechanical part which is resilient for extra powerful conversion of an internal energy 4 of a ﬂ uidum within the path to electrical energy. At least one of said at least one hydraulic pressure generators and / or at least one of said at least one additional hydraulic pressure generators may have at least one path for ﬂ uidum ﬂ destiny, which path comprises at least one mechanical part which is resilient for extra powerful conversion of an internal energy of a ﬂ uidum path to electrical energy. Said at least one mechanical part may be at least one membrane. Said at least one mechanical part may be at least one volume with at least one phase change material (PCM). Said at least one mechanical part may be at least one membrane together with at least one volume with at least one phase change material (PCM). The membrane may be located between the phase change material (PCM) and the id uidet. At least one of said at least one hydraulic pressure generators may comprise at least one volume with at least one phase change material (PCM). At least one of said at least one pressure generators and / or at least one of said at least one additional hydraulic pressure generators may comprise at least one volume with at least one phase change material (PCM). At least one non-return valve may be hydraulically connected before and / or after at least one of said at least one hydraulic pressure generator in the hydraulic system. At least one non-return valve may be hydraulically connected before and / or after at least one of said at least one hydraulic pressure generators and / or before and / or after at least one of said at least one further hydraulic pressure generators in the hydraulic system. At least one valve may be hydraulically connected between said at least one fate accumulator and the rest of the hydraulic system. At least one of said at least one electric generator may be of an asynchronous type. At least one of said at least one electric generator may be of a synchronous type.
The invention further comprises an energy production plant for generating electrical energy and comprises a hydraulic system according to any one of the claims.
The invention further comprises the use of a hydraulic system according to any one of the claims for the operation of at least one electric generator for generating electrical energy. A rotational speed of a rotary shaft of at least one of said at least one electric generator can be kept substantially constant.
Brief Description of the Drawings Fig. 1 shows a schematic view of a lake-based power plant system 10 according to the present invention; Fig. 2 shows a schematic view of a power system or means 22 according to the present invention; Fig. 3 shows a schematic view of the surface platform 20 with the reservoir 26; Fig. 4 shows a schematic view of the water carrier 28 in a first state; Fig. 5 shows a schematic view of the water carrier 28 in a second condition; Fig. 6 schematically shows a configuration with two groups of energy cells 12 included in a power system 22; Fig. 7 schematically shows a configuration with six groups of energy cells 12 connected in series and included in a power system 22; Fig. 8 is a block diagram of a first embodiment of a hydraulic system 38 according to the present invention; Fig. 9 is a block diagram of a second embodiment of a hydraulic system 38 according to the present invention; Fig. 10 is a block diagram of a first embodiment of a pressure transducer 40 according to the present invention; and Fig. 11 is a block diagram of a second embodiment of a pressure transducer 40 according to the present invention.
Detailed description of the preferred embodiments is given. 1 shows a schematic view of a sea-based power plant system 10 according to the present invention. The sea-based power plant system 10 is drivable to generate energy, and comprises essentially a water supply system 18, a surface platform 20 and a power plant or system 22. In the general case, the water supply system 18 m comprises a number of pipe means 241, 24m, where m is an integer and m 2 1. For simplicity, is shown in ﬁ g. 1, only two pipe members 241 and 242. A third pipe member is further indicated by a dashed line. The two pipe members 241 and 242 are connected to a reservoir 26 forming part of the platform 20. 6 As further shown in ﬁ g. 1, each tubing member 241 and 242 includes a conveyor 281 and 282 operable to transport water having a first temperature, T1, from an end portion 301 and 302 of the tubing members 241 and 242 to the reservoir 26. In other words, cold water is transported from the depths of the sea to the reservoir 26 by means of the conveyors 281 and 282. The power plant 22 further comprises a heating machine system 32 (compare ﬁ g. 2) comprising n number 12.1 (compare ﬁ g. 6 and 7), where n is an integer, and n 2 1.
The energy cells 121, energy cells 121,. 12.1 may be linked in a sequence.
The heating machine system 32 further comprises a heat source 14 connected to the first energy cell 121 and a cooling sink 16 connected to the last energy cell 12,1.
The heat source 14 receives water with a second temperature, T2, via a first feed pipe 34 (compare Fig. 3) from the vicinity of the surface of the water. The temperature T2 corresponds to the temperature of the sea surface. The cooling sink 16 receives water with the first temperature, T1, from the reservoir 26 via a second feed pipe 36 (compare ﬁ g. 3). For the offshore power plant system 10 to work, the following condition must be met T2> T1. In a most preferred embodiment, T2 - T1 is 2 ° C. Each energy cell 121; ...; 12.1 is drivable to generate a pressurized fluid when a phase change material (PCM) is included in each energy cell 121; 12.1 changes from solid phase to ﬂ surface phase. The power plant 22 further comprises a hydraulic system 38 (compare ﬁ g. 2) connected to the heating machine system 32, and which is drivable to generate a constant rotational speed.
According to a preferred embodiment of the sea-based power plant system, the pipe means 241, 24.1 ﬁ are axed to each other. This means that the construction will be stable and able to withstand sea waves.
According to an alternative, the conveyor 281 may be in the form of an electric or hydraulic pump member 281 located in the end portion 301 of the tubular member 241.
According to another alternative, the conveyor 281 may be in the form of an electric or hydraulic propeller member 281 also located in the end portion 301 of the pipe member 241.
According to a third alternative, the conveyor 281 may be in the form of a PCM-based water carrier 281 which uses temperature differentials for autonomous propulsion in the pipe member 241. For a more detailed description of the water carrier 28, compare Figs. 4 and 5 and the corresponding description. 7 It is pointed out that in the same sea-based power plant system 10, a combination of two or three of the different examples of conveyor 28 may coexist. In order to increase the efficiency of the lake-based power plant system, the reservoir 26 is thermally isolated from the surrounding water.
According to a preferred embodiment, the level of the water inside the reservoir 26 should be lower than or equal to the level of the water outside the ﬂ surface platform 20. This ratio is shown in ﬁ g. 1, where the water level in the reservoir 26 is lower than the water level in the sea, i.e., outside the ﬂ-floating platform 20.
According to another embodiment of the sea-based power plant system 10, the hydraulic system 38 comprises a pressure transducer 40 (compare ﬁ g. 10 and 11), and a hydraulic motor 42 connected to the pressure transducer 40. l ﬁ g. 2 shows a schematic view of the power system or plant 22 according to the present invention. The heating machine system 32 comprises or is connected to a heat source 14, and a cooling sink 16. As further shown in ﬁ g. 2, the power plant 22 further includes a hydraulic system 38 connected to the heating machine system 32, and drivable to produce a constant rotational speed.
The power plant 22 further includes an electric generator means 44 connected to the hydraulic system 38, and more precisely to the hydraulic motor 42. The electric generator means 44 is drivable to generate electricity with a specific frequency and amplitude. As also shown in ﬁ g. 2, the power plant 22 further includes a controllable control system 46 for controlling process performance based on real-time measurements of time, fate, temperature, and pressure.
According to a preferred embodiment of the sea-based power plant system, the energy cells 121, 12.1 are drivable between a first phase and a second phase, wherein, during the first phase, every second energy cell produces pressurized fluid and every other energy cell cools down, and vice versa during the second phase. l ﬁ g. 3 shows a schematic view of the surface platform 20 included in the sea-based power plant system 10 according to the present invention.
As shown in ﬁ g. 3, the surface platform 20 comprises a reservoir 26 intended for storing water. l ﬁ g. 3 also shows a first supply pipe 34 for supplying hot water from the surface of the sea to the heat source 14 (compare fig. 2). In addition, a second feed pipe 36 is shown for feeding water from the reservoir 26 to the cooling sink 16 (compare ﬁ g. 2). It is pointed out that the water in the reservoir 26, which has been transported 8 from the depths of the sea, has a temperature which is lower than the temperature of the surface water. As also shown in ﬁ g. 3, there is also a water flushing pipe 110 for flushing out spi | water from the sea-based power plant system 10. l ﬁ g. 4 shows a schematic view of the PCM-based water carrier 28 in a first state, and in ﬁ g. 5 is a schematic view of the water carrier 28 in a second condition. As shown in both ﬁ g. 4 and 5, the water carrier 28 includes a high pressure vessel 282, high pressure gas 284, ambient water 286, a gas passage 288, water inlet / outlet 290, a main piston 292, phase change material (PCM), 29 noses 294, a slave piston 296 and an ib exile membrane 298. The main and slave pistons 292 and 296 are connected via a rod to a gas equalization channel 288.
The operation of the water carrier 28 will now be described with reference to first Fig. 4 and then to ﬁ g. 5. The first state shown in ﬁ g. 4 is when it ﬂ surface. Cold water from the bottom is cooled by PCM, which freezes and shrinks.
The pistons 292 and 296 are forced down by the gas 284. As the slave piston 296 moves, it pushes the water out of the vessel 282, thus making the vessel 282 lighter. The vessel 282 ﬂ thus surfaces up to the water surface.
The second condition shown in ﬁ g. 5 is when it drops. Hot water from the surface heats up the PCM, which melts and expands. The main piston 292 is forced up by the PCM. The slave piston 296 is forced up by the connecting rod. The gas 284 is compressed and acts as a spring. As the slave piston 296 moves, it leaves room for ambient water to fill the membrane 298 thus making the vessel 282 heavier, due to the fact that water has a higher density than PCM. The vessel 282 sinks to the bottom. Since the gas chambers 284 are connected, the gas pressure on both pistons 292 and 296 thus increases the capercaillie force.
The surface platform 20 may also be constructed of concrete, steel, composites or other materials suitable for offshore use for a long time. The surface platform 20 can also accommodate other machines, for example for the production of hydrogen gas. The floating platform 20 will allow ships to dock and helicopters to land.
It is also pointed out that the conveyor 28 must be ib visibly mounted to allow service and repair at the service level.
I ﬁ g. Fig. 6 schematically shows a configuration with two groups of energy cells 12 included in a power system or plant 22. As schematically shown in Fig. 6, the energy cells 121-124 are connected, and operate in parallel, and the energy cells 128-128 are connected, and operate in parallel. . I ﬁ g. 6 also shows the heat source 14 connected to the energy cells, and the cooling sink 16 connected to the energy cells. In addition, i ﬁ g. 6 also shows the hydraulic system 38 connected to the heating machine system 32 (not shown in ﬁ g. 6) comprising the energy cells 121-128. In the first part of the cycle (Phase 1; P1), the heat source 14 heats the energy cells 121-124, while the cooling sink 16 cools the energy cells 125-128. In the second part of the cycle (Phase 2; P2), the heat source 14 heats the energy cells 125-128, while the cooling sink 16 cools the energy cells 121-124. The temperature difference between the heat source 14 and the cooling sink 16 is adapted to the selected PCM characteristics.
It must normally be at least 20 ° C in order to obtain an acceptable efficiency and power output.
I ﬁ g. 7 schematically show a configuration with six groups of energy cells included in a power system 22. Groups A 1.1, A 2.1 and A 3.1 are connected in series and groups B 1.1, B 2.1 and B 3.1 are also connected in series, in order to reuse heat and increase efficiency. Also shown in ﬁ g. 7, the heat source 14 is connected to the energy cells 12, and the cooling sink 16 is also connected to the energy cells 12. In addition, in ﬁ g. 7 also shows the hydraulic system 38 connected to the heating machine system 32 (not shown in ﬁ g. 7) comprising all the energy cells 12. In the first part of the cycle (Phase 1; P1), the heat source 14 heats the energy cells 12 in the group A 1.1, meaning that PCM in these energy cells melt. Excess heat from the energy cells in group A 2.1 is used to heat the energy cells in group A 3.1. This means that the PCM in the energy cells 12 in A 2.1 freezes and the PCM in the energy cells 12 in A 3.1 melts. Excess heat from the energy cells in group B 1.1 is used to heat the energy cells in group B 2.1. This means that PCM in the energy cells in B 1.1 freezes and PCM in the energy cells in B 2.1 melts. The cooling sink 16 cools the PCM in the energy cells 12 in B 3.1.
In the second part of the cycle (Phase 2; P2), the heat source 14 heats the energy cells 12 in group B 1.1, meaning that the PCM in these energy cells melts. Excess heat from the energy cells in B 2.1 is used to heat the energy cells in B 3.1. This means that PCM in the energy cells in B 2.1 freezes and PCM in the energy cells in B 3.1 melts. Excess heat from the energy cells in group A 1.1 is used to heat the energy cells in group A 2.1. This means that the PCM in the energy cells 12 in A 1.1 freezes and the PCM in the energy cells 12 in A 2.1 melts. The cooling sink 16 cools the energy cells 12 in group A 3.1, meaning that the PCM in the energy cells 12 in A 3.1 freezes.
According to a preferred embodiment of the power system 22, the energy cells 121-12 "are connected in a sequence, and the heat source 14 is connected to the first energy cell 121, and the cooling sink 16 is connected to the last energy cell 12n.
During the first phase, every second energy cell 121, 123, 125, produces pressurized fluid, and every other energy cell 122 124, 12, .. cools down, and vice versa during the second phase. Reuse can be performed in one or more steps. Each step requires a temperature difference between the heat source 14 and the cooling sink 16 of approximately ° C. For example, if we have a heat source 14 at 80 ° C and a cooling sink 16 at ° C, we can reuse heat in two steps, ie, 2 x 3 groups with energy cells 12 (as in ﬁ g. 7).
According to a further embodiment, the pressure transducer 40 is drivable to reduce the pressure in the pressurized fluid from the energy cells 121-12n.
In addition, the hydraulic motor 42 in the power system 22 is drivable to generate the constant rotational speed during variable torque.
I ﬁ g. 8 is a block diagram of a first embodiment of a hydraulic system 38 in accordance with the present invention. The embodiment shown in fig. 8 includes a hydraulic motor 42 for operating an electric generator to generate electrical energy. In addition, the hydraulic system 38 also includes a first hydraulic pressure generator 21A and a second hydraulic pressure generator 21B, both in hydraulic connection to the hydraulic motor 42. It is noted that each of the hydraulic pressure generators 21A and 21B corresponds to and is equal to the heating machine system. 32 described earlier in this specification. The first and second hydraulic pressure generators 21A, 21B are both drivable to transfer hydraulic energy to the hydraulic motor 42. As shown in ﬁ g. 8, the first and second hydraulic pressure generators 21A, 21B are mutually hydraulically connected in parallel. The first and second hydraulic pressure generators 21A, 21B are arranged to operate in cycles so that the first hydraulic pressure generator 21A delivers an output while the second hydraulic pressure generator 21B has an input, while the first hydraulic pressure generator 21A has an input at the same time as the second hydraulic pressure generator 21 B delivers an output. The first and second hydraulic pressure generators 21A, 21B are arranged to operate with a mutual phase difference of approximately 180 degrees. The hydraulic system 38 further comprises a number of check valves 1, 2 and 8. The flow to the hydraulic pressure generators 21A, 21B has a base pressure and passes the control valve 1. The flow passes the check valve 2. The flow passing the point x in the block diagram comes either from the first hydraulic pressure generator 21A or from the second hydraulic pressure generator 21 B. In addition, the hydraulic system 38 also includes a pressure transducer 40 connected between the hydraulic pressure generators 21A and 21B and the hydraulic motor 42. The pressure transducer 40 is drivable to lower the hydraulic pressure from a higher pressure in a ﬂ uidum to a lower pressure in the ﬂ uidet. This will ensure a high reliability in operation and a long service life of the hydraulic motor 42.
In order to protect the hydraulic motor 42 from an excessive pressure, the hydraulic system 38 further comprises a pressure reducing valve 9 which bypasses a gap next to the hydraulic motor 42 at an excessive working pressure. In order to protect the hydraulic motor 42 against cavitation, there is a non-return valve 8 in the hydraulic system 38. The non-return valve 8 is drivable to prevent the pressure in front of the hydraulic motor 42 from being lower than the base pressure.
Cavitation can occur if the ﬂ fate of the pressure transducer 40 is temporarily too low or if the displacement is too high in relation to the ﬂ fate.
The hydraulic motor 42 may be, for example, an asynchronous machine with four poles or a synchronous machine with four poles, both of which provide a constant rotational speed at a constant power frequency. After the hydraulic motor 42, a small part of the pass passes to a base unit 6 via a pressure reducing valve 5 which regulates the base pressure.
As also shown in ﬁ g. 8, the hydraulic system 38 also includes a fate accumulator 7 operable to stabilize the base fate of the system 38.
In addition, it may be justified to have a fate accumulator 7 in the hydraulic system 38 if the flow to and from the hydraulic pressure generators 21A, 21 is much higher or if the return flow from the base unit is too low.
It is pointed out that it is possible to have more than one hydraulic motor 42 in the hydraulic system 38 (not shown in any gear). If your hydraulic motors 42 are connected for the operation of the generator, at least one of the hydraulic motors 42 shall have a variable displacement. 12 When the hydraulic pressure generator 21A has completed half of its cycle, i.e., when it has reached 180 degrees, energy is still stored in the ﬂ uidet.
Now the pressure will decrease during the following process and when the pressure has decreased to p1, the displacement of the hydraulic motor 42 will also start to decrease. The hydraulic motor 42 will still have the same rotational speed but the torque delivered to the generator will decrease in relation to the reduction of the displacement and the pressure. The energy delivered to the generator will decrease faster and faster. Most of the energy stored in the ﬂ uidet will be transferred to the generator during this phase.
The output of output from the hydraulic pressure generators 21A, 21B starts with a certain delay due to the fact that the pressure must be increased before a flow is possible. As long as the pressure from the hydraulic pressure generator 21A is higher than the pressure from the hydraulic pressure generator 21B, the non-return valve 1 will be closed. The flow of ﬂ uidum at point x in the block diagram shown in ﬁ g. 8 comes in principle from the hydraulic pressure generator 21A from the point when the duty cycle (360 degrees) of the hydraulic pressure generator 21A has passed a number of degrees until it has passed more than half of its cycle. For the rest of the time, the ﬂ fate will of course come from the hydraulic pressure generator 21 B. Assuming that the hydraulic pressure generator 21A is started at phase zero, and if the delay corresponds to 40 degrees of the cycle, then the vid fate at point x will come from the hydraulic pressure generator 21A below 40-220 degrees, from the hydraulic pressure generator 21B below 220-400 degrees and from the hydraulic pressure generator 21A below 400-580 degrees. i ﬁ g. 9 is a block diagram of a second embodiment of a hydraulic system 38 in accordance with the present invention. In this embodiment, there is only one hydraulic pressure generator 21A, and consequently only one check valve each of 1 and 2, as shown in. G. 9. Another difference between the embodiments shown in ﬁ g. 8 and 9 is that in this second embodiment there is also a fate accumulator 1000 and a valve 11. The other similar elements which occur in both embodiments have been provided with the same reference numerals and will not be described in detail again.
As shown in ﬁ g. 9, the output from the pressure transducer 40 is connected to the output accumulator 1000 via the valve 11, and to the hydraulic motor 42 which in turn drives an electric generator. The flow accumulator 1000 has a relatively high charge pressure and the pressure is assumed to increase to the maximum operating pressure when it has reached the maximum charge. The flow accumulator 1000 is operable to accumulate när uidum when a de fate from the hydraulic pressure generator 21A is greater than an intended ﬂ fate to the hydraulic motor 42, and to deliver id uidum when the ﬂ fate of the hydraulic pressure generator 21A is less than the intended ﬂ fate of the hydraulic motor 42. .
The valve 11 is either open or closed, which is controlled either hydraulically or electrically.
It is pointed out that there are mainly three different pressure levels in the hydraulic system 38: a base pressure p1 which prevails downstream in relation to the hydraulic motor 42 and the non-return valve 1, and also between the non-return valves 1, 2 when there is an inlet to the hydraulic pressure generator 21A; an actuating high pressure p2 which prevails between the non-return valves 1, 2 at discharge and between the non-return valve 2 and the pressure transducer 40; an ﬂ actuating operating pressure p3 between the pressure transducer 40 and the hydraulic motor 42.
According to one embodiment of the hydraulic system 38, at least one of the hydraulic pressure generators 21A, 21B is a pump. The pump can also be linear with a pressure stroke for ﬂ uidum delivery and a return stroke for ﬂ uidum suction.
I ﬁ g. 10 is a block diagram of a first embodiment of a pressure transducer 40 in accordance with the present invention. The pressure transducer 40 is operable to transform a pressure of one fluid from one pressure level Pin to another pressure level Put. This embodiment shown in ﬁ g. 10 comprises a pair of hydraulic rotating machines A, B which are mutually mechanically connected in such a way that the first machine A can drive the second machine B.
Machines A, B are mounted in a substantially closed space, and each of the machines A, B is in hydraulic connection with the closed space. As also shown in Fig. 10, each of the machines A, B is provided with a hydraulic inlet (Pin) and a hydraulic outlet (Put). It is pointed out that the embodiment shown in ﬁ g. 10 is used to reduce the pressure of the id uidet. This means that each of the machines A, B is hydraulically connected to the closed space via the hydraulic outlet (Put). If, on the other hand, the pressure transducer 40 is to be used to increase the pressure of the (uid, (not shown in the ur gures), each of the machines A, B is in hydraulic connection with the closed space via the hydraulic inlet. In the embodiment shown in ﬁ g. 10, the 14 closed space is in hydraulic connection with a pressure source with the pressure level Pin, the hydraulic rotary machine A is in hydraulic connection with a pressure source with the pressure level Pin and the hydraulic rotary machine B is in hydraulic connection with a pressure source with a pressure level 0 bar. If the machines A, B have the same size, and the normal maximum pressure is 200 bar, then the embodiment will be shown in ﬁ g. 10 to give the figures 400 bar for Pin and 200 bar for Pin.
According to an embodiment of the pressure transducer 40, the mutually mechanically connected machines A, B are connected via at least one shaft coupling.
According to one embodiment of the pressure transducer 40, all the machines A, B have open connections with the drainage connections and the closed space in such a way that pressure balancing prevails. This ensures that the pressure inside and the pressure outside the closed room are equal.
I ﬁ g. 11 shows a block diagram of a second embodiment of a pressure transducer 40 according to the present invention. In this embodiment of the pressure transducer 40 there are two closed spaces, each comprising two hydraulic rotary machines A, B. The hydraulic rotary machines A, B are mutually mechanically connected in such a way that for each pair of machines A, B and for each closed room, the first machine A can run the second machine B. As shown in ﬁ g. 11, the pressure transducer 40 is provided with a hydraulic inlet (Pin) and a hydraulic outlet (Pin). In addition, machine A in the left pair of machines is hydraulically connected to the second, right space, while machine B in the right pair of machines is hydraulically connected to the first, left space. It is pointed out that the embodiment shown in ﬁ g. 11 is used to reduce the pressure of the ﬂ uidet. Using the same pressure levels as in fig. 10, comes in the case shown in ﬁ g. 11, i.e., if two pressure transducers 40 according to ﬁ g. 10 are connected in accordance with ﬁ g. 11, to give the figures 600 bar for Pin and 200 bar for Pni.
The same applies to the case where three pressure transducers 40 according to ﬁ g. 10 are connected in series (not shown), i.e., it will give the digits 800 bar for Pin and 200 bar for Piii.
The invention is not limited to the described embodiments. It will be apparent to those skilled in the art that many different embodiments are possible within the scope of the following claims.

权利要求:
Claims (35)
[1]
A hydraulic system (38) comprising at least one hydraulic motor (42) for operating at least one electric generator to generate electrical energy, the system (38) comprising at least one hydraulic pressure generator (21A) in hydraulic connection with said at least one hydraulic motor (42) for transmitting hydraulic energy to said at least one hydraulic motor (42), characterized by at least one further device (1000, 21 B) for transmitting hydraulic energy to said at least one hydraulic motor (42), said at least one further device (1000, 21B) is at least one ﬂ fate accumulator (1000) for accumulating ﬂ uidum when a ﬂ fate from said at least one hydraulic pressure generator (21A) is greater than an intended ﬂ fate for said at least one hydraulic motor (42) and for delivering ﬂ uidum when the från fate of said at least one hydraulic pressure generator (21A) is less than the intended ﬂ fate of said at least one hydraulic motor ( 42) and wherein at least one valve (11) is hydraulically connected between said at least one fate accumulator (1000) and the rest of the hydraulic system (38), which valve (11) is either open or closed and is either hydraulically or electrically controlled.
[2]
A hydraulic system (38) according to claim 1, comprising at least two further devices (1000, 21 B) for transmitting hydraulic energy to said at least one hydraulic motor (42), said at least two further devices (1000, 21 B) being said at least one fate accumulator (1000) as well as at least one further hydraulic pressure generator (21B) in hydraulic connection with said at least one hydraulic motor (42) for transferring hydraulic energy to said at least one hydraulic motor (42).
[3]
The hydraulic system (38) of claim 2, wherein at least one pair of the hydraulic pressure generators (21A, 21B) comprises a first hydraulic pressure generator (21A) and a second hydraulic pressure generator (21B) mutually hydraulically connected in parallel. 20 25 30 2
[4]
The hydraulic system (38) of claim 3, wherein the first and second hydraulic pressure generators (21A, 21B) are arranged to operate in cycles so that the first hydraulic pressure generator (21A) delivers a discharge while the second hydraulic pressure generator ( 21 B) has an input while the first hydraulic pressure generator (21A) has an input at the same time as the second hydraulic pressure generator (21 B) delivers an output.
[5]
The hydraulic system (38) of claim 4, wherein the first and second pressure generators (21A, 21B) are arranged to operate with a mutual phase difference of approximately 180 degrees.
[6]
The hydraulic system (38) of claim 1, wherein at least one of said at least one hydraulic pressure generator (21A) is in hydraulic communication with said at least one hydraulic motor (42) in a closed cycle.
[7]
The hydraulic system (38) of claim 2, wherein at least one of said at least one pressure generator (21A) and / or at least one of said at least one additional hydraulic pressure generator (21B) is in hydraulic communication with said at least one hydraulic motor (42). ) in a closed cycle.
[8]
The hydraulic system (38) of claim 1, wherein at least one of said at least one hydraulic motor (42) has a variable displacement.
[9]
A hydraulic system (38) according to claim 8, wherein the displacement is variable according to variations in a pressure of a ﬂ uidum, which ﬂ uidum transmits hydraulic energy to said at least one of said at least one hydraulic motor (42).
[10]
The hydraulic system (38) of claim 9, wherein the displacement is arranged to increase as the pressure increases while the displacement is arranged to decrease as the pressure decreases.
[11]
A hydraulic system (38) according to claim 8, wherein the displacement is variable according to variations in a ﬂ fate of a ﬂ uidum, which 3 ﬂ uidum transmits hydraulic energy to said at least one of said at least one hydraulic motor (42).
[12]
The hydraulic system (38) of claim 11, wherein the displacement is arranged to increase as the ﬂ fate increases while the displacement is arranged to decrease as the ﬂ fate decreases.
[13]
The hydraulic system (38) of claim 1, comprising at least one control system for controlling at least one of said at least one hydraulic motor (42).
[14]
The hydraulic system (38) of claim 13, wherein said at least one control system is arranged to control a displacement of said at least one of said at least one hydraulic motor (42).
[15]
The hydraulic system (38) of claim 1, comprising at least one pressure transducer (40) for transforming a hydraulic pressure into the hydraulic system (38).
[16]
A hydraulic system (38) according to claim 15, wherein at least one of said at least one pressure transducer (40) is hydraulically connected between on the one hand said at least one hydraulic pressure generator (21A) and on the other hand said at least one hydraulic motor (42).
[17]
A pressure transducer (40) is arranged to lower the hydraulic pressure in the Hydraulic system (38) according to claim 16, wherein at least one hydraulic system (38) from a higher pressure in a distance from said at least one hydraulic pressure generator (21A) to a lower pressure in the direction of said at least one hydraulic motor (42).
[18]
The hydraulic system (38) of claim 1, wherein at least one of said at least one hydraulic pressure generator (21A) is a pump. 20 25 30 4
[19]
The hydraulic system (38) of claim 2, wherein at least one of said at least one hydraulic pressure generator (21A) and / or at least one of said at least one additional pressure generator (21B) is a pump.
[20]
Hydraulic system (38) according to claim 18 or 19, wherein the pump is linear with pressure stroke for ﬂ uidum delivery and return stroke for ﬂ uidum suction.
[21]
The hydraulic system (38) of claim 1, wherein the at least one of said at least one hydraulic pressure generators (21A) has at least one path for ﬂuidum ﬂ fate, said path comprising at least one mechanical part which is för resilient for extra powerful conversion of an internal energy of a ﬂ uidum within the path to electrical energy.
[22]
The hydraulic system (38) of claim 2, wherein at least one of said at least one hydraulic pressure generator (21A) and / or at least one of said at least one additional hydraulic pressure generator (21B) has at least one föruidum ﬂ path, which path comprises at least a mechanical part that is resilient for extra powerful conversion of an internal energy of an ﬂ uidum within the web into electrical energy.
[23]
A hydraulic system (38) according to claim 21 or 22, wherein said at least one mechanical part is at least one diaphragm.
[24]
The hydraulic system (38) of claim 21 or 22, wherein said at least one mechanical member is at least one volume with at least one phase change material (PCM).
[25]
A hydraulic system (38) according to claim 21 or 22, wherein said at least one mechanical part is at least one diaphragm together with at least one volume of at least one phase change material (PCM).
[26]
The hydraulic system (38) of claim 25, wherein the diaphragm is located between the phase change material (PCM) and the id uidet. 10 20 25 30 5
[27]
The hydraulic system (38) of claim 1, wherein the at least one of said at least one hydraulic pressure generator (21A) comprises at least one volume of at least one phase change material (PCM).
[28]
The hydraulic system (38) of claim 2, wherein at least one of said at least one hydraulic pressure generator (21A) and / or at least one of said at least one additional hydraulic pressure generator (21B) comprises at least one volume of at least one phase change material (PCM) .
[29]
A hydraulic system (38) according to claim 1, wherein at least one non-return valve (1, 2) is hydraulically connected before and / or after at least one of said at least one hydraulic pressure generator (21A9 in the hydraulic system (38).
[30]
Hydraulic system (38) according to claim 2, wherein at least one non-return valve (1, 2) is hydraulically connected before and / or after at least one of said at least one hydraulic pressure generator (21A9 and / or before and / or after at least one of said at least one additional hydraulic pressure generator (21 B) in the hydraulic system (38).
[31]
The hydraulic system (38) of claim 1, wherein at least one of said at least one electric generator is of an asynchronous type.
[32]
The hydraulic system (38) of claim 1, wherein at least one of said at least one electric generator is of a synchronous type.
[33]
An energy production plant for generating electrical energy and comprising a hydraulic system (38) according to any one of the preceding claims.
[34]
Use of a hydraulic system (38) according to any one of the preceding claims for the operation of at least one electric generator for generating electrical energy. 6
[35]
Use according to claim 34, wherein a rotational speed of a rotary axis of at least one of said at least one electric generator is kept substantially constant.

类似技术:

公开号 | 公开日 | 专利标题

KR101493126B1|2015-02-12|Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression

US8495872B2|2013-07-30|Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas

RU2434159C1|2011-11-20|Conversion method of heat to hydraulic energy and device for its implementation

KR20070075321A|2007-07-18|Method for converting thermal energy into mechanical work

CN107810312B|2020-07-10|Energy storage device and energy storage method for storing energy

CN108708836A|2018-10-26|A kind of ocean profile sports equipment and its ocean thermal energy conversion device

KR20180102646A|2018-09-17|Changing CO2 cycles and resulting concussions of long-term unmanned underwater vehicles

EP2105610A1|2009-09-30|Method for converting thermal energy into mechanical work

US20180156185A1|2018-06-07|Device and method for converting and storing electrical energy in the form of compressed air

SE0950557A1|2011-01-15|Hydraulic system, energy production plant and use of a hydraulic system

US9169852B2|2015-10-27|Hydraulic pressure transducer and hydraulic system

SE0950558A1|2011-01-15|Hydraulic pressure transducer and hydraulic system

SE0950555A1|2011-01-15|A power system

US8919117B2|2014-12-30|Energy cell operable to generate a pressurized fluid via bladder means and a phase change material

SE0950556A1|2011-01-15|A sea-based power plant system

CN109764013B|2021-05-11|Hydraulic potential energy conversion device of self-synchronizing multistage hydraulic cylinder

WO2016134440A1|2016-09-01|Thermal εngiνε

US11081904B1|2021-08-03|Methods, systems and installations for the compression, expansion and/or storage of a gas

US20210071918A1|2021-03-11|System and method of pumped heat energy storage

WO2014020581A2|2014-02-06|Fluid displacement methods and resultant machines

WO2011090773A2|2011-07-28|Power conversion system

WO2017198725A1|2017-11-23|Hybrid multistage gas compression/expansion systems and methods

CN111868368A|2020-10-30|Floating head piston assembly

WO2013134001A1|2013-09-12|Power conversion system

RO125116B1|2011-08-30|Wind system for providing thermal and electric power

同族专利:

公开号 | 公开日

SE534697C2|2011-11-22|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

法律状态:

优先权:

申请号 | 申请日 | 专利标题

SE0950557A|SE534697C2|2009-07-14|2009-07-14|Hydraulic system, energy production plant and use of a hydraulic system|SE0950557A| SE534697C2|2009-07-14|2009-07-14|Hydraulic system, energy production plant and use of a hydraulic system|

US13/383,437| US9169852B2|2009-07-14|2010-07-12|Hydraulic pressure transducer and hydraulic system|

PCT/SE2010/050810| WO2011008158A1|2009-07-14|2010-07-12|Hydraulic pressure transducer and hydraulic system|

EP10800114.0A| EP2454488B1|2009-07-14|2010-07-12|Hydraulic pressure transducer and hydraulic system|

[返回顶部]