An isolated fluid pressure conversion device with a hydraulic bladder linked to a piston

Abstract

The present invention discloses a fluid pressure conversion device, which includes a cylinder block (1), a piston (2) and a hydraulic bladder (3). The hydraulic bladder (3) is a tubular flexible bladder that can withstand pressure and tension and expand and contract. It is installed inside the cylinder block (1), and the bladder nozzles (32) at both ends are embedded in the mounting holes in the center of the piston (2) and the cylinder head (12) and are tightly connected. The bladder body (31) divides the space inside the cylinder barrel (11) into two parts, namely a bladder inner cavity (4) and a bladder outer cavity (5), which respectively accommodate two different fluids, and each is provided with a channel for the fluid medium to enter and exit. During operation, by actively changing the pressure or volume of the fluid in one of the cavities, through the combined action of the expansion and contraction of the bladder body (31) and the sliding of the piston (2), the pressure or volume of the fluid in the other cavity can be correspondingly changed, and the pressure change in the bladder inner cavity (4) is larger than that in the bladder outer cavity (5), while the volume change is smaller. This device can be used for supercharging transmission, material pumping, pipeline pressure regulation, etc.

Description

Technical Field

[0001] The present invention relates to the technical fields of hydraulics, pneumatics, and variable displacement fluid pumps, and particularly to an isolated fluid pressure conversion device with linkage between a hydraulic bladder and a piston. Background Art

[0002] In many industrial scenarios involving fluid pressure transmission or fluid material transportation, technologies and equipment for driving one fluid with another fluid carrying pressure energy have been widely applied. More typical applications include:

[0003] 1. Boosting transmission, such as gas-liquid boosting cylinders in hydraulic machinery, hydraulic hydro-expanding machines for rock excavation or internal pressure forming processing, etc.;

[0004] 2. Pumping and lifting, such as using water pressure to pump oil or discharging mud from underground to the ground in the oil and mining industries;

[0005] 3. Pressure filtration and penetration, such as using seawater pressure to pressurize filtered water for reverse osmosis to remove salts in seawater desalination;

[0006] 4. Energy storage compensation, such as bladder-type and piston-type accumulators and pressure compensators with compressed air;

[0007] 5. Compression phase change, such as the compression preparation of LNG and liquid CO2, pressure-exchange refrigeration compressors, etc.

[0008] These devices are essentially fluid pressure conversion devices, and there is a process of unidirectional or mutual transfer of pressure energy between different fluids during operation. Users usually expect the device to provide a larger conversion pressure difference, have less energy loss, and ensure strict isolation between the pressure medium and the material fluid without mutual contamination. In the prior art, there are usually two ways to achieve isolated fluid pressure conversion. One is to use piston groups with different diameters. Its advantage is that it can achieve a higher boosting multiple and output pressure. For example, there are many manufacturers at home and abroad providing gas-liquid boosting cylinders with an output of up to several hundred megapascals. However, the multi-piston structure increases the inertia of the moving parts and the friction with the cylinder wall, resulting in problems such as slow response and increased energy consumption. Moreover, the sliding gap between the piston and the cylinder barrel makes it difficult to avoid medium mixing. The other is to use flexible parts such as membranes and bladders, such as diaphragm pumps, bellows pumps, and bladder accumulators. The advantage is that it can achieve strict isolation between different media. However, the conventional flexible parts have relatively low pressure-bearing and crack-resistant strengths and are difficult to adapt to higher internal and external pressure differences. Such devices with a working pressure above ten megapascals are extremely rare at present.

[0009] In the domestic patent document CN 110566533 A, the present inventor has disclosed a tubular hydraulic bladder and a pressure generating device. In the "tubular hydraulic bladder" provided in this technical solution, the bladder wall is an elastic synthetic rubber sandwiching a reinforcing layer, and the reinforcing layer is obliquely cross-woven and densely woven with high-strength and high-modulus fiber bundles such as para-aramid and ultra-high molecular weight polyethylene. This enables the bladder to have comprehensive advantages far beyond those of ordinary membrane bladders and hydraulic hoses in terms of two originally contradictory properties of pressure bearing and expansion and contraction.

[0010] Through product actual measurement and practical inspection, we have proved that this tubular hydraulic bladder has the following advantages: First, it has high pressure bearing capacity. The bladder can reliably seal and bear pressure for water, oil, and gas, and the minimum burst pressure in the free state can reach more than 70 MPa. Second, it has high tensile strength. The bladder itself and its connection with the two end bladder nozzles can withstand tensile forces of several tons or even dozens of tons (varying with models). Third, it has a high expansion and contraction ratio. When comparing the two states of the same bladder when it expands to the thickest and shortest and when it stretches to the thinnest and longest, the diameter change is greater than 3 times, the length change is greater than 1.6 times, and the bladder volume change is greater than 5 times. In addition, it also has some common advantages of general flexible devices, such as light weight, low cost, and good durability. In summary, the emergence of this new type of technology product provides a feasible new idea for the technical improvement of the isolated fluid pressure conversion device. Summary of the Invention

[0011] The purpose of the present invention is to provide a fluid pressure conversion device to solve the problems in the prior art such as incomplete medium isolation, large energy loss, and heavy equipment when realizing the pressure conversion of two fluid media. This device is applicable to both the boosting transmission device of hydraulic and pneumatic mechanical equipment and the material pumping or pressure regulating equipment in high-pressure fluid conveying pipelines, such as superchargers, booster pumps, compressors, or accumulators.

[0012] To achieve the above purpose, the present invention provides the following solutions:

[0013] The present invention provides an isolated fluid pressure conversion device with the linkage of a hydraulic bladder and a piston, and its structure mainly includes a cylinder block, a piston, and a hydraulic bladder. Among them, the cylinder block is a rigid housing, including a cylinder barrel and a cylinder head installed at its end; the piston is an armless piston with a diameter adapted to the cylinder barrel, and is installed in the cylinder barrel in a sliding manner. Axially through mounting holes are provided at the centers of the cylinder head and the piston body; the hydraulic bladder is composed of a bladder body and a bladder nozzle. The bladder body is a tubular soft bladder that can bear pressure and tension. Its inner and outer layers are elastic synthetic rubber impermeable layers, and the middle layer is a reinforcing layer obliquely cross-woven and wound with synthetic fiber bundles or fine steel wires. Its diameter and length can expand, contract, and stretch within a certain range with the change of the internal and external pressure difference and the forces at both ends; the bladder nozzle is a metal connecting piece installed at the end of the bladder body, used to lock and seal the bladder opening and assemble and connect with other components.

[0014] The hydraulic bladder is arranged between the inner cylinder head and the piston in the cylinder barrel. The bladder nozzles at both ends of the hydraulic bladder are respectively embedded in the mounting holes at the centers of the cylinder head and the piston, forming a firm and sealed connection. The bladder body separates the cylindrical space between the piston and the cylinder head in the cylinder barrel into two chambers, namely the inner bladder chamber and the outer bladder chamber, which are respectively used to accommodate two media, i.e., the first fluid and the second fluid. During operation, as long as the pressure or volume of the fluid in any one of the chambers is actively changed, the two fluids will interact with each other through the combined actions of the expansion and contraction of the bladder body and the sliding of the piston, causing the pressure or volume of the fluid in the other chamber to change passively accordingly. Moreover, the change in the pressure of the fluid in the inner bladder chamber is greater than the change in the pressure of the fluid in the outer bladder chamber, and the change in the volume of the outer bladder chamber is greater than the change in the volume of the inner bladder chamber.

[0015] Working principle: For the convenience of description, hereinafter, fluid A and fluid B are respectively used to represent the first fluid in the inner bladder chamber and the second fluid in the outer bladder chamber. When the bladder body and the piston in the cylinder are temporarily in a static equilibrium state, the pressure P of fluid A A is greater than the pressure P of fluid B B , because the fluid B in the outer bladder chamber obeys Pascal's law. In addition to directly transmitting its pressure to fluid A through the flexible bladder wall it surrounds, it also acts on the inner wall of the cylinder barrel and the inner end face of the piston at the same pressure, pushing the piston to slide in the direction away from the piston and stretching the bladder body. The oblique spiral structure of the reinforcing layer fibers in the bladder body will convert the axial tensile force into a radial tightening force, further compressing the fluid A in the bladder and generating an additional increased pressure difference P C , that is, P A = P B + P C = P B(1 + k), where k is always a positive value, and its magnitude is proportional to the area of the annular end face on the inner side of the piston and is positively correlated with the stretching elongation of the bladder. Dynamically, there are two reciprocal ways of pressure exchange between the two fluids: Way 1, when fluid B is actively injected into the outer cavity of the bladder from outside the cylinder, its pressure acts on the outer wall of the bladder and the annular inner side of the piston simultaneously, pushing the piston to slide away from the cylinder head side. The bladder increases in length and decreases in diameter due to the circumferential extrusion of fluid B and the tensile force of the piston, the volume of the inner cavity of the bladder decreases, the pressure of fluid A increases, and it is output through the bladder nozzle. This process is a pressure-increasing process in which a low-pressure large-displacement fluid drives a high-pressure small-displacement fluid. Way 2, when fluid A is actively injected into the inner cavity of the bladder from outside the bladder nozzle, the bladder expands and deforms accordingly, that is, it expands and thickens and shortens in length, pulling the piston to slide towards the cylinder head side. The space in the outer cavity of the bladder is compressed by the bladder and the piston together, reducing the volume, and the fluid B in the outer cavity of the bladder is discharged outside the cylinder. It can be seen that this process is a pumping process in which a high-pressure small-displacement drives a low-pressure large-displacement. In short, when used in the forward direction, the large flow rate in the outer cavity of the bladder drives the small flow rate in the inner cavity of the bladder to increase the pressure; conversely, when used in the reverse direction, the high pressure in the inner cavity of the bladder drives the low pressure in the outer cavity of the bladder to increase the flow rate, which is obviously consistent with the law of conservation of energy. In practical applications, the device is connected to an external pipeline system, and under the control of a corresponding switching valve, the above two processes can work continuously in a cyclic and alternating manner.

[0016] Preferably, the cylinder head can be installed at the end of the cylinder barrel either by means of flange bolts or by screwing in, and the sealing effect can be achieved either by adding a sealing gasket or by precision machining fit.

[0017] Preferably, the locking and sealing method for the bladder nozzle to be embedded and connected in the cylinder head or piston mounting hole is any one or two of the three methods of stepped hole fit, tapered hole fit or internal threaded hole fit.

[0018] Preferably, according to actual application needs, the channel for fluid A to enter and exit the inner cavity of the bladder can be arranged on one of the bladder nozzles in the cylinder head or piston mounting hole, or the dedicated channels for injecting and outputting fluid A can be respectively arranged on the bladder nozzles at both ends of the bladder.

[0019] Preferably, at least one channel for fluid B to enter and exit is provided in the cylinder barrel or cylinder head of the outer cavity of the bladder, or according to actual application needs, the injection port and output port of fluid B can be separately arranged on the cylinder barrel or cylinder head.

[0020] Preferably, threads are provided in the mounting holes at the centers of the cylinder head and the piston for installing valve parts, connecting parts or sealing parts.

[0021] Preferably, among the two fluids where pressure conversion occurs, the driving medium with an actively changing pressure is any one of water, pressure fluid, or compressed gas, and the driven fluid is any one of gaseous, liquid, solid-liquid mixed slurry, or gas-liquid phase change state.

[0022] Furthermore, a cylinder head can be installed at each end of the cylinder barrel. The piston is placed between them, dividing the interior of the cylinder into left and right cylinder chambers. Each cylinder chamber has its own port on the cylinder body for fluid B to enter and exit. A hydraulic bladder is installed between the left and right sides of the piston and the two cylinder heads respectively, forming an extended structure with two hydraulic bladders. Working principle: Under the control of an external reversing valve, when fluid B is pressurized and injected into the outer cavity on the left side, it compresses the piston to slide to the right. The left bladder is stretched and thinned, and the contained fluid A is pressurized and discharged through the nozzle at the left end. At the same time, the right bladder shortens and thickens, and its inner cavity volume expands. Fluid A flows in through the nozzle at the right cylinder head, and the fluid B in the outer cavity on the right side flows back to the outside of the cylinder. In this way, it works alternately left and right. The two bladders push and pull each other through the middle piston, stretching and contracting to assist each other. It can not only achieve double-acting continuous pressurization but also make full use of the remaining pressure energy and save power consumption.

[0023] The present invention discloses the following technical effects:

[0024] The isolated fluid pressure conversion device with the hydraulic bladder linked to the piston provided by the present invention has at least one of the following advantages compared with such devices in the prior art:

[0025] 1. The hydraulic bladder can reliably isolate two fluid media with a large pressure difference, effectively avoiding the mixing and pollution between different media;

[0026] 2. The flexible linkage structure of the telescopic hydraulic bladder and a single piston can significantly reduce the energy consumption generated by friction and vibration and improve the energy conversion efficiency;

[0027] 3. The inner-soft and outer-hard sleeve structure enables the hydraulic bladder and the cylinder body to share the internal high-pressure load, which can greatly reduce the pressure-bearing burden of the cylinder body, facilitating the reduction of equipment weight and manufacturing cost;

[0028] 4. This device has good versatility and a large pressure adaptation range, is suitable for various fluids such as water, oil, and gas. A set of devices can be used reciprocally to respectively achieve two functions of boosting transmission and amplifying pumping flow;

[0029] 5. This device has a simple and compact structure, low manufacturing process difficulty, cost savings, and is convenient for assembly and maintenance.

[0030] In addition to the above-listed technical effects of the present invention, there are still other direct or indirect descriptions in the specification. Brief Description of the Drawings

[0031] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required in the embodiments. Obviously, the following drawings only depict a part of the embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0032] Figure 1 Structural schematic diagram of the fluid pressure exchange device of the present invention;

[0033] Figure 2 Schematic diagram of the connection mode of the capsule nozzle with the cylinder head and the piston in the fluid pressure exchange device of the present invention;

[0034] Figure 3 、 Figure 4 Schematic diagram of the working principle and process of the pressure boosting transmission of the fluid pressure exchange device of the present invention;

[0035] Figure 5 、 Figure 6 Schematic diagram of the working principle and process of the compression pumping of the fluid pressure exchange device of the present invention;

[0036] Figure 7 Schematic diagram of the double-capsule structure and application mode of the fluid pressure exchange device of the present invention.

[0037] Wherein, the cylinder block 1, the cylinder barrel 11, the cylinder head 12, the piston 2, the mounting hole 21, the blind plug seal 23, the hydraulic capsule 3, the capsule body 31, the capsule nozzle 32, the capsule nozzle through hole 33, the capsule inner cavity 4, the capsule outer cavity 5, the injection check valve 71, the output check valve 72, and the reversing valve 8. Detailed implementation manners

[0038] The following will more clearly and meticulously describe the technical solutions in the embodiments of the present invention in conjunction with the drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts belong to the scope of protection of the present invention.

[0039] Figure 1 Structural schematic diagram of an isolated fluid pressure conversion device with the linkage of a hydraulic capsule and a piston provided by the present invention, as Figure 1As shown in the figure, the device includes a cylinder block 1, a piston 2, and a hydraulic bladder 3. The cylinder block 1 is a rigid housing, which further includes a cylinder barrel 11 with a cylindrical chamber inside and a cylinder head 12 installed at its end. There is a longitudinally penetrating mounting hole at the center of the cylinder head 12; the piston 2 is a sealable sliding piston installed inside the cylinder barrel 11 with a diameter adapted thereto, and there is also an axially penetrating mounting hole 21 at its center; the hydraulic bladder 3 is composed of a flexible tubular bladder body 31 and bladder nozzles 32 at both ends thereof. The bladder body 31 is a tubular soft bladder that can withstand pressure and tension. Its inner and outer layers are high-elastic synthetic rubber impermeable layers, and the middle layer is a reinforcing layer formed by obliquely crossing and weaving fine steel wires or synthetic fiber bundles. Its diameter and length can expand, contract, and stretch within a certain range with the changes of the internal and external pressure differences and the forces at both ends. The bladder nozzle 32 is a metal part assembled at the end of the bladder body 31 for sealing, locking the bladder opening, and connecting with other components. There is a through hole 33 at its center. (Refer to the domestic patent document CN 110566533 A for a more detailed understanding of the technical details of the hydraulic bladder. The scope of reference of the "hydraulic bladder" described in the claims and the description of the present invention includes the "tubular hydraulic bladder" described in this document, but should not be understood as being limited to only this type.) The hydraulic bladder 3 is arranged between the cylinder head 12 and the piston 2 inside the cylinder barrel 11. The bladder nozzles 32 at both ends are respectively inserted into the mounting holes 21 at the center of the cylinder head 23 and the piston 3, and are sealed and locked with nuts. The bladder body 31 of the hydraulic bladder isolates the cylindrical space inside the cylinder barrel 11 into two pressure-bearing chambers, namely the inner bladder cavity 4 and the outer bladder cavity 5, which respectively accommodate two different fluids, fluid A and fluid B.

[0040] Figure 2 Described are three selectable embedded locking and sealing methods when the hydraulic bladder 3 in the present invention is connected to the cylinder head and the piston through the bladder nozzles 32, namely stepped hole fit, tapered hole fit, or internal thread hole fit.

[0041] Embodiment 1 Figure 3 、 Figure 4 Describes a connection method and a working process when the fluid pressure conversion device provided by the present invention is used for oil-water pressurization transmission. As Figure 3 、 4 shown, the hydraulic station is used as an external pressure source device. Its oil supply pipe and return pipe are connected to the port 14 on the cylinder body of the outer bladder cavity 5 through a hydraulic pipe via a reversing valve 8. The position switching of the reversing valve 8 can realize the alternation of the oil supply and oil return processes; the low-pressure water pump is an external pre-stage device for replenishing water to the inner bladder cavity 4, usually a servo pressurized pipeline pump. It is connected to the inner bladder cavity 4 through a low-pressure water pipe via an injection check valve 71 installed in the mounting hole outside the piston 2; the output check valve 72 is installed in the mounting hole outside the cylinder head 12, and its function is to prevent the output high-pressure water from flowing back into the bladder body. It is connected to a high-pressure water expander through a high-pressure pipe. Each working cycle includes two alternating processes: water replenishment and pressurization

[0042] The water replenishment process Figure 3 As shown, when the reversing valve 8 is switched to the oil return pipe conduction position, the oil supply pipe is cut off, the hydraulic station enters the standby state, the low-pressure water pump starts to supply water, and when the water pressure reaches the positive opening pressure of the injection check valve 71, water begins to be injected into the capsule cavity 4 through the low-pressure hose, and the water injection pressure acts on the inner wall of the capsule, forcing the capsule 31 to expand radially and become thicker, and the axial length to shrink, pulling the piston 2 to slide toward the cylinder head 12. Since the capsule cavity 5 is in a low-pressure oil return state directly connected to the hydraulic station oil tank pipeline at this time, the combined effect of the expansion of the capsule 31 and the compression of the piston 2 reduces the volume of the capsule cavity 5, which is equivalent to the water injection pressure promoting the accelerated discharge of hydraulic oil from the cylinder back to the oil tank. When the capsule is fully filled with water and the internal and external water pressures reach a low-pressure equilibrium state, the injection check valve 71 is closed, and the low-pressure water pump outlet pressure will rise to the set upper limit water pressure, automatically entering the standby state of suspending water supply, and the system enters the pressurization process.

[0043] The pressurization process is as follows Figure 4 As shown, when the reversing valve 8 is switched to the oil supply pipe conduction position, the oil return pipe is cut off, and the hydraulic station starts to inject hydraulic oil into the outer cavity 5 of the capsule. The hydraulic oil pressurizes the water filling the inner cavity 4 from all sides of the capsule body 31 through the capsule wall, and also pushes the piston 2 to slide away from the cylinder head 12. The capsule body 31 tends to be elongated and thinned by the huge tensile force of the piston 2, and the volume of the inner cavity 4 of the capsule is reduced, and the internal water pressure is further increased. Since the water injection passage is reversely blocked by the injection check valve 71, the high-pressure water can only be output from the output check valve through the high-pressure pipe to drive the water expansion machine to work. When the water in the inner cavity 4 of the capsule is emptied or the internal and external water pressures reach a balanced state under high pressure, the hydraulic station outlet oil pressure will rise to the set upper limit oil pressure, automatically enter the standby state of suspending oil supply, and the system will enter the water supply process. In the above process, the position switching of the reversing valve can be automatically controlled by the standby signal of the low-pressure water pump and the hydraulic station, and can also be manually controlled as needed.

[0044] This embodiment is an application mode of using medium-pressure fluid to increase the pressure of another low-pressure fluid to high pressure. For example, the 31.5MPa pressure fluid provided by the hydraulic station can increase the pressure of low-pressure water not higher than 1.6MPa to high-pressure water above 70MPa, so as to drive mechanical equipment that performs water pressure work. A feature that needs special attention is that even if the water pressure in the capsule is increased to more than 70MPa, or even higher pressure, the capsule bears an internal and external pressure difference of about 40MPa, and the oil pressure directly acting on the inner wall of the cylinder body will never exceed 31.5MPa, which means that the cylinder body of this boosting device can be designed and manufactured according to the industrial standard of general hydraulic cylinders without the need to specially increase the pressure rating, which is obviously conducive to saving costs for users.

[0045] In practical applications, the pressurized medium may be mixed slurries such as paint and coatings in addition to water, and the driven actuator may be a grouting machine, a spraying machine, etc. in addition to a high-pressure water expansion machine.

[0046] Embodiment 2: Figure 5 , Figure 6 The present invention describes an assembly method and working process for gas compression pumping using the fluid pressure conversion device provided by the present invention. Figure 5 , Figure 6 As shown, the hydraulic station is an external power device, and its oil supply pipe and oil return pipe are connected to the common oil inlet and outlet ports opened on the cylinder head through a reversing valve 8 through a hydraulic pipe in the inner chamber 4 of the capsule, and a blind plug seal 23 is installed in the mounting hole outside the piston 2; the outer chamber 5 of the capsule is provided with two ports for injection and output on the cylinder barrel, and an injection check valve 71 and an output check valve 72 are installed respectively, and are connected to the external low-pressure gas source and high-pressure storage tank through pressure pipes. Each working cycle includes two alternating processes of inflation and compression:

[0047] The inflation process is as follows Figure 5 As shown, when the reversing valve 8 is switched to the oil return pipe conduction position, the oil supply pipe is cut off and the hydraulic station enters the standby state. Due to the opening of the oil return passage, the hydraulic oil pressure in the bag inner cavity 4 drops sharply. The bag body loses internal pressure and becomes thinner under the pressure of the expansion pressure of the gas in the bag outer cavity 5, relaxing the pulling force on the piston, so that the piston is pushed by the air pressure to slide away from the cylinder head 12, and the volume of the bag outer cavity 5 increases. When the internal air pressure drops to below the external air source pressure, the external gas pushes open the one-way valve and is injected into the bag outer cavity 5. The air pressure continues to push the piston to stretch the bag body to the longest and thinnest, accelerating most of the hydraulic oil to flow back to the hydraulic station tank. At this time, the volume of the bag outer cavity reaches the maximum and is filled with gas that has not been further compressed.

[0048] The compression process is as follows Figure 6 As shown, when the reversing valve 8 is switched to the oil supply pipe conduction position, the oil return pipe is cut off, and the hydraulic station starts to inject hydraulic oil into the capsule cavity 4. As the amount of oil in the capsule cavity 4 increases and the pressure rises, the oil pressure acts on the inner wall of the capsule, forcing the capsule 31 to expand radially and become thicker, and the axial length to shrink, pulling the piston 2 to slide toward the cylinder head 12 with a huge pulling force. The dual effects of the capsule expansion and the piston compression reduce the volume of the capsule cavity 5 by more than ten times, and the gas inside is compressed, and the density increases and the pressure rises, and is transported to the high-pressure storage tank through the output one-way valve. In the above process, the position switching of the reversing valve 8 and the start and stop of the hydraulic station can be controlled by installing sensors to detect the signals of the piston reaching the farthest and closest positions.

[0049] This embodiment is an application method for driving a large-flow low-pressure fluid compression pump by a small-flow high-pressure fluid. For example, it is driven by a pressure fluid of 31.5 MPa provided by a hydraulic station to further compress and boost compressed natural gas, liquefied petroleum gas or carbon dioxide gas not greater than 0.6 MPa to more than 8 MPa, so that it exceeds the liquefaction critical pressure for liquefaction, refrigeration or canned storage and transportation.

[0050] In practical applications, the driving fluid medium is not limited to hydraulic oil, and water or emulsion can also be used according to actual needs; the fluid to be boosted and transported is not limited to gas, and can also be liquid or viscous fluid materials, etc.

[0051] Embodiment Three Figure 7 describes a double hydraulic bladder expansion structure of the fluid pressure conversion device of the present invention, as Figure 7 shown. A cylinder head 12 is installed at each end of the cylinder barrel 11. The piston 2 is placed therebetween, dividing the inside of the cylinder body 1 into left and right cylinder chambers. The left and right cylinder chambers each have their own fluid inlet and outlet ports 14 on the cylinder body 1. Between the left and right sides of the piston 2 and the two cylinder heads 12, a hydraulic bladder 3 is installed respectively. The outlets of the bladder nozzles 32 of the left and right hydraulic bladders installed on the piston are blocked, and the bladder nozzles 32 are provided with injection and output common ports in the mounting holes of the cylinder heads 12.

[0052] Figure 7 It also describes a supporting method and working principle when applying this double hydraulic bladder expansion structure for oil-water boosting transmission. As Figure 7 shown, the oil supply pipe and the oil return pipe of the hydraulic station pass through a two-position four-way directional control valve 8, and then are respectively connected to the left and right two ports 14 on the cylinder body 1 through two hydraulic pipes. The switching of the directional control valve 8 between the two working positions can synchronously and alternately convert the outer chambers 5 of the bladders in the left and right cylinder chambers during the oil injection and oil return processes; the low-pressure water pump is also connected to the hydroexpander through two water supply pipes in series with two check valves 71 and 72 respectively. A high-pressure water pipe is branched out between the injection check valve 71 and the output check valve 72 on the left and right two paths and is respectively connected to the inlet and outlet ports of the inner chamber 4 of the bladder on the left and right cylinder heads 11. The four check valves divide the left and right two water paths into three sections. The low-pressure water supply pipe is before the injection check valve 71, the high-pressure water delivery pipe is after the output check valve 72, and the high-pressure pipe between the two valves is shared for water replenishment and water outlet of the inner chamber 4 of the bladder.

[0053] This device with a double hydraulic bladder structure can, through the switching of the reversing valve 8 between two working positions, synchronously and alternately convert the outer cavities 5 of the bladders in the left and right cylinder chambers between an oil injection process and an oil return process. That is, the pressurization and water replenishment are carried out simultaneously on the left and right sides of the piston 2 in opposite processes. Compared with the single bladder structure, the hydraulic station and the water supply pump no longer need to frequently standby and start. The system works in a double-acting continuous pressurization mode, and the efficiency can be doubled. In addition, the expansion and contraction of the bladder bodies 31 on the left and right sides of the piston 2 are also synchronous and in opposite phases, forming a push-pull effect with a consistent force direction on the left and right reciprocating sliding of the piston 2. The remaining pressure of water replenishment and oil return can be fully utilized, thus effectively improving the energy conversion efficiency.

[0054] Obviously, by combining the above-mentioned Embodiment 2 and Embodiment 3, those of ordinary skill in the art will naturally understand that the extended device with a double bladder structure can also be used reversely, that is, using the fluid A in the inner cavities 4 of the left and right bladders as the high-pressure drive to continuously compress and pump the low-pressure fluid B in the outer cavity of the bladder. Therefore, such an embodiment will not be described in detail in the form of pictures and texts.

[0055] In summary, a fluid pressure conversion device provided by the present invention innovatively adopts an inner-soft and outer-hard sleeve layer to share the pressure-bearing structure and a conversion mechanism of bladder plug linkage. It can not only strictly isolate the two media to avoid mixing and pollution, but also expand the pressure adaptation range, and is also conducive to reducing energy consumption and costs. It can be applied to the pressurization transmission of hydraulic and pneumatic machinery and the pumping and pressure regulation of fluid materials in pressure pipeline systems.

[0056] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "longitudinal", "transverse", "upper", "lower", "front", "rear", "left", "right", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present invention.

[0057] The above-described embodiments are only used to describe the preferred mode of the present invention, and do not limit the scope of the present invention. Without departing from the design spirit of the present invention, various deformations and improvements made by those of ordinary skill in the art to the technical solution of the present invention should fall within the protection scope determined by the claims of the present invention.

Claims

1. A fluid pressure conversion device, characterized in that Comprising: A cylinder block (1), a piston (2), and a hydraulic bladder (3); The cylinder block (1) is a rigid housing, including a cylinder barrel (11) and a cylinder head (12). The interior of the cylinder barrel (11) is a cylindrical chamber. The cylinder head (12) is installed at the end of the cylinder barrel (11). At the center of the cylinder head (12) body, there is a longitudinally penetrating mounting hole. The cylinder block (1) has at least one port (14) for the fluid medium to enter and exit; The diameter of the piston (2) is adapted to the cylinder barrel (11) and is slidably installed in the cylinder barrel (11). At the center of the piston (2) body, there is an axial mounting hole (21); The hydraulic bladder (3) includes a bladder body (31) and a bladder nozzle (32). The bladder body (31) is a pressure-resistant and tensile-resistant tubular soft bladder. There is an anti-leakage layer and a reinforcement layer in the bladder wall. Its diameter and length change with the internal and external pressure difference and the axial force at both ends, and it can radially expand and contract and axially contract and extend within a certain range. The bladder nozzle (32) is a connecting piece installed at the end of the bladder body (31) for locking, sealing the bladder opening, and assembling and connecting with other components; The hydraulic bladder (3) is arranged between the cylinder head (12) and the piston (2) in the cylinder barrel (11). The bladder nozzles (32) at both ends of the hydraulic bladder (3) are respectively embedded into the mounting holes at the centers of the cylinder head (12) and the piston (2) to form a firm and sealed connection. The bladder body (31) separates the cylindrical space between the piston (2) and the cylinder head (12) in the cylinder barrel (11) into two chambers, namely a bladder inner cavity (4) and a bladder outer cavity (5), which are respectively used to accommodate the first fluid and the second fluid; During operation, actively changing the pressure or volume of the fluid in either the bladder inner cavity (4) or the bladder outer cavity (5), the two fluids interact with each other through the combined action of the expansion and contraction of the bladder body (31) and the sliding of the piston (2), causing the pressure or volume of the fluid in the other cavity to change passively accordingly. Moreover, the change in the pressure of the fluid in the bladder inner cavity (4) is greater than the change in the pressure of the fluid in the bladder outer cavity (5), and the change in the volume of the bladder inner cavity (4) is greater than the change in the volume of the bladder outer cavity (5); A double-hydraulic-bladder expansion structure based on this fluid pressure conversion device includes two of the hydraulic bladders (3). The two hydraulic bladders (3) are respectively arranged on both sides of the piston (2). Cylinder heads (12) are installed at both ends of the cylinder barrel (11). The bladder nozzles (32) on the side of the hydraulic bladder (3) close to the piston (2) are blocked.

2. The fluid pressure conversion device according to claim 1, wherein The installation method of the cylinder head (12) at the end of the cylinder barrel (11) is any one or both of the flange bolt or screw-in methods, and the sealing method is any one or both of adding a sealing washer or precision machining fit.

3. The fluid pressure conversion device according to claim 1, characterized in that The locking and sealing method of the bladder nozzle (32) embedded and connected in the mounting holes of the cylinder head (12) and the piston (2) is any one or both of the stepped hole fit, taper hole fit, or internal thread hole fit methods.

4. The fluid pressure conversion device according to claim 1, wherein The bladder inner cavity (4) is provided with a channel for the first fluid to enter and exit through the bladder nozzle (32) at least on one of the cylinder head (12) and the piston (2).

5. The fluid pressure conversion device according to claim 1, wherein At least one port (14) for the second fluid in the outer cavity (5) to enter and exit is provided on the cylinder block (1).

6. The fluid pressure conversion device according to claim 1, wherein Threads are provided in the mounting holes at the centers of the cylinder head (12) and the piston (2) for mounting valve components, connecting components or sealing components.

7. The fluid pressure conversion device according to claim 1, wherein Among the two fluids for which pressure conversion occurs, the driving medium with an actively changing pressure is any one of water, pressure liquid or compressed gas, and the driven fluid is any one of gaseous state, liquid state, solid-liquid mixed slurry state or gas-liquid phase transformation state.

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