Double-flow-distribution plunger booster pump and energy recovery integrated device

Abstract

The invention belongs to the technical field of energy recovery equipment, and provides a double-flow-distribution plunger booster pump and energy recovery integrated device which comprises an isobaric energy exchanger and a plunger booster pump which are fixedly connected, and the plunger booster pump comprises a shell, a flow distribution plate, a swash plate, a plunger assembly and a plunger cylinder assembly. The plunger type cylinder assembly is rotatably installed on the inner side of the shell, the valve plate and the swash plate are located on the upper side and the lower side of the plunger type cylinder assembly respectively, and the plunger type cylinder assembly is movably installed on the inner side of a plunger type cylinder. The plunger assembly comprises a plunger and a sliding shoe, a spherical structure at the lower end of the plunger is rotatably mounted on the inner side of the sliding shoe, and runners which are communicated with each other penetrate through the interiors of the plunger and the sliding shoe; the valve plate is provided with a high-pressure valve window, and the swash plate is provided with a low-pressure valve window. The constant-pressure type energy recovery device is combined with the swash plate and valve plate double-flow-distribution type plunger booster pump, efficiency is high, flow is large, the service life is long, static pressure supporting is adopted, rigidity is larger, operation is more stable, and flow fluctuation is smaller.

Description

Technical Field

[0001] The present invention belongs to the technical field of energy recovery devices, and particularly relates to an integrated device of a double-flow-plunger booster pump and energy recovery, which can efficiently recover the pressure energy in high-pressure fluid and transfer it to low-pressure fluid, and is widely used in industrial fields such as seawater desalination, chemical processes, carbon dioxide refrigeration, energy recovery, and other industrial fields that require high-pressure fluid treatment. Background Art

[0002] In many industrial processes, the discharge of high-pressure fluid is often accompanied by a large amount of energy waste. For example, in a reverse osmosis seawater desalination system, a high-pressure pump pressurizes seawater and desalinates it through a reverse osmosis membrane, while the concentrated brine is discharged at high pressure as a by-product. In this process, more than 50% of the input energy will be lost with the discharge of the concentrated brine. If this part of the energy can be effectively recovered, it can not only significantly reduce the energy consumption of the system, but also reduce the operating cost, which helps to improve the economy and sustainability of the industrial process.

[0003] Currently, the existing energy recovery devices on the market mainly include the following types:

[0004] (1) Turbine-type energy recovery device:

[0005] The turbine-type device converts the pressure energy of high-pressure fluid into mechanical energy and then drives the high-pressure pump through a coupling. However, the energy recovery efficiency of this device is usually low (about 60% - 80%), and it has a complex structure and high maintenance cost.

[0006] (2) Isobaric pressure exchanger:

[0007] The pressure exchanger is one of the most widely used energy recovery devices at present. It realizes energy recovery by directly exchanging the pressure between high-pressure fluid and low-pressure fluid. Although its energy recovery efficiency is relatively high (up to more than 90%), the existing pressure exchangers generally have the following problems:

[0008] Fluid mixing problem: Cross-contamination may occur between high-pressure fluid and low-pressure fluid, especially in working conditions that require strict fluid separation, and this problem is particularly prominent.

[0009] Unstable operation: In working conditions with large flow fluctuations or pressure changes, the existing devices are difficult to maintain a stable operating state.

[0010] Limited application range: For fluids with high viscosity or containing solid particles, the adaptability of the existing devices is poor.

[0011] Currently, the isobaric energy recovery device is integrated with the booster pump device. The combination of isobaric energy recovery and vane pump is common. However, the vane pump requires the combination of rotor eccentricity and vane centrifugal force to boost the fluid pressure to 2 - 3 barg. Its volumetric efficiency is low, only 65 - 75%, and its service life is short. In the case of vane pump failure, it will affect the service life of the isobaric energy recovery device. Another common type is the hydraulic motor type energy recovery device, which extends from both ends of the motor shaft. A pump is installed at one end and a motor is installed at the other end. The torque provided by the motor can reduce the power of the motor to achieve energy-saving effects, but the overall efficiency is only 70 - 75%. Another type is the structure where the motor and the pump share a swash plate, plungers, and a valve plate. The main problem is that the structure design is complex, the motor efficiency is only 70 - 75%, and the flow rate cannot be increased, so it can only be used with small flow rates. There is also the turbine type energy recovery, whose main feature is that the efficiency is only 65 - 70%.

[0012] (3) Plunger type energy recovery device:

[0013] The plunger type device realizes the transfer of pressure energy through mechanical reciprocating motion, with high energy recovery efficiency and good adaptability. However, this type of device generally has disadvantages such as complex structure, large volume, and difficult maintenance.

[0014] In summary, the existing energy recovery technologies still have many deficiencies in terms of efficiency, stability, applicability, and maintainability, which limit their wide application in the industrial field. Therefore, developing an energy recovery device with high efficiency, stability, compact structure, and strong adaptability has become a research hotspot in the current technical field. Summary of the Invention

[0015] The purpose of the present invention is to overcome the existing defects and provide an integrated device of a double-valve-plate plunger booster pump and energy recovery. By optimizing the structure design and fluid control method, it realizes efficient and stable energy recovery and has broad industrial application prospects.

[0016] To solve the above technical problems, the present invention provides the following technical solutions:

[0017] An integrated device of a double-valve-plate plunger booster pump and energy recovery includes an isobaric energy exchanger and a plunger booster pump. The plunger booster pump is fixedly installed on the upper end of the isobaric energy exchanger. A high-pressure fluid outlet and a low-pressure fluid inlet are provided on the side of the plunger booster pump, and a high-pressure fluid inlet and a low-pressure fluid outlet are provided at the lower end of the isobaric energy exchanger;

[0018] The plunger type supercharger pump includes a housing, a distribution disk, a swash plate, a plunger assembly and a plunger cylinder assembly. The plunger cylinder assembly is rotatably installed inside the housing. The distribution disk and the swash plate are respectively located on the upper and lower sides of the plunger cylinder assembly. The plunger cylinder assembly includes a plunger cylinder and a plunger sleeve. A plurality of annularly and equally spaced plunger sleeves are arranged inside the plunger cylinder. A plunger assembly is movably installed in each plunger sleeve;

[0019] The plunger assembly includes a plunger and a slipper. The spherical structure at the lower end of the plunger is rotatably installed inside the slipper. The lower end face of the slipper slides against the upper surface of the swash plate. A mutually communicating flow passage runs through the plunger and the slipper;

[0020] The distribution disk is provided with a high-pressure distribution window, and the swash plate is provided with a low-pressure distribution window. The high-pressure distribution window and the low-pressure distribution window are distributed oppositely.

[0021] Furthermore, a first damping groove communicating with the high-pressure distribution window is formed on the surface of the distribution disk, and a second damping groove communicating with the low-pressure distribution window is formed on the surface of the swash plate.

[0022] Furthermore, a wear-resistant layer is arranged at the contact position between the inner side of the slipper and the plunger. The materials of the slipper and the wear-resistant layer are respectively stainless steel and PEEK material, or stainless steel and ceramic material, or ceramic and PEEK material.

[0023] Furthermore, a valve plate is installed at the upper end of the plunger cylinder assembly. The valve plate is located between the plunger cylinder assembly and the distribution disk. The valve plate is provided with a plurality of through holes corresponding to the flow passages of the plunger cylinder assembly. A positioning and guiding member is connected to the lower end of the through hole, and a sealing assembly is sleeved outside the positioning and guiding member.

[0024] Furthermore, a through hole is formed in the middle of the plunger cylinder. A small shaft and a large shaft are respectively fixedly installed at the upper and lower ends of the through hole. The small shaft penetrates through the upper end cover of the plunger type supercharger pump, and the large shaft is connected to the central rotating shaft of the isobaric energy exchanger through a coupling.

[0025] Furthermore, a magnetic coupling is installed on the upper side of the upper end cover of the plunger type supercharger pump. The pump shaft side of the magnetic coupling is installed at the upper end of the small shaft of the plunger cylinder assembly.

[0026] Furthermore, the magnetic coupling includes a sealing cover. The sealing cover is located in the middle of the motor side and the pump shaft side of the magnetic coupling.

[0027] Furthermore, the small shaft and the large shaft are respectively installed in cooperation with the upper end cover and the swash plate through hydrostatic bearings. Hydrostatic pools and load equalizing grooves are respectively formed on the inner and outer sides of the hydrostatic bearings, and damping holes are formed in the load equalizing grooves.

[0028] Further, a high-pressure water outlet for the outflow of the raw water after energy exchange is provided on the top cover of the isobaric energy exchanger, and the high-pressure water outlet is aligned with the low-pressure distribution window of the swash plate.

[0029] Further, a rotor assembly is installed inside the isobaric energy exchanger. The rotor assembly includes a valve plate assembly, a rotor cylinder, and a central rotating shaft. The rotor cylinder is rotatably installed outside the central rotating shaft. A valve plate assembly is installed at each of the upper and lower ends of the rotor cylinder. A hydraulic compensation device is installed between the valve plate assembly at the upper end of the rotor cylinder and the rotor cylinder.

[0030] The hydraulic compensation device includes an annular thrust plate and a plurality of compensation springs. The plurality of compensation springs are annularly and equidistantly distributed on the lower side of the thrust plate.

[0031] Further, a plurality of fastening screws are connected through between the isobaric energy exchanger and the plunger type booster pump.

[0032] Combined with the above technical solutions, the beneficial effects of the present invention compared with the prior art are as follows:

[0033] The present invention combines an isobaric energy recovery device with a swash plate and a double-port flow distribution plunger booster pump. The efficiency of the plunger booster pump is as high as 95%, with a large flow rate, high reliability, long service life, static pressure support, greater stiffness, more stable operation, and smaller flow fluctuations. By adopting the method of low-pressure flow distribution of the high-pressure raw water after exchange by the swash plate, the low-pressure inlet water enters the plunger through the swash plate and the center of the plunger, perfectly completing the low-pressure flow distribution, greatly reducing the tipping force of the plunger cylinder. At the same time, the pressure boosting range of this booster is larger and can meet the requirements within the range of 2 - 60 barg, greatly expanding the application scenarios. The high-pressure flow distribution adopts a single high-pressure groove flow distribution form. Overall, the tipping moment is smaller, and the low pressure can generate a large torque to balance the high-pressure torque, with higher operation reliability. Description of the Drawings

[0034] The drawings are used to provide a further understanding of the present invention, and constitute a part of the specification. Together with the embodiments of the present invention, they are used to explain the present invention and do not constitute a limitation to the present invention. In the drawings:

[0035] Figure 1 is a schematic structural diagram of a double-port flow distribution plunger booster pump and an energy recovery integrated device provided by an embodiment of the present invention;

[0036] Figure 2 is a sectional view of a double-port flow distribution plunger booster pump and an energy recovery integrated device provided by an embodiment of the present invention;

[0037] Figure 3 is a schematic structural diagram of a flow distribution plate provided by an embodiment of the present invention;

[0038] Figure 4 It is a schematic structural diagram of a swash plate provided by an embodiment of the present invention;

[0039] Figure 5 It is a schematic structural diagram of a plunger assembly provided by an embodiment of the present invention;

[0040] Figure 6 It is a schematic structural diagram of a plunger cylinder assembly provided by an embodiment of the present invention;

[0041] Figure 7 It is a schematic structural diagram of a valve plate provided by an embodiment of the present invention;

[0042] Figure 8 It is a schematic structural diagram of a hydrostatic bearing provided by an embodiment of the present invention;

[0043] Figure 9 It is a schematic structural diagram of an isobaric energy exchanger provided by an embodiment of the present invention;

[0044] Figure 10 It is a schematic structural diagram of a rotor assembly provided by an embodiment of the present invention;

[0045] Figure 11 It is a schematic structural diagram of a hydraulic compensation device provided by an embodiment of the present invention;

[0046] Figure 12 It is a schematic diagram of the flow direction principle of fluid from the high-pressure fluid inlet to the low-pressure fluid outlet provided by an embodiment of the present invention;

[0047] Figure 13 It is a schematic diagram of the flow direction principle of fluid from the low-pressure fluid inlet to the high-pressure fluid outlet provided by an embodiment of the present invention;

[0048] Figure 14 It is a schematic diagram of the layout principle of the valve plate and the swash plate provided by an embodiment of the present invention.

[0049] In the figure: 1. Motor side of the magnetic coupling; 2. Sealing cover; 3. Pump shaft side of the magnetic coupling; 4. Distribution plate; 5. Swash plate; 6. Plunger assembly; 7. Isobaric energy exchanger; 8. Coupling; 9. Plunger cylinder assembly; 10. Hydrostatic bearing; 11. Valve plate; 12. Plunger type booster pump; 13. Upper end cover; 14. Lower end cover; 15. Low-pressure fluid inlet; 16. High-pressure fluid outlet; 17. Low-pressure fluid outlet; 18. High-pressure fluid inlet; 19. Tightening screw; 4.1 First damping groove; 4.2 High-pressure distribution window; 5.1 Second damping groove; 5.2 Low-pressure distribution window; 6.1 Plunger; 6.2 Wear-resistant layer; 6.3 Slipper; 6.4 Hydrostatic groove; 6.5 Plunger end; 9.1 Large shaft; 9.2 Small shaft; 9.3 Plunger cylinder; 9.4 Plunger sleeve; 11.1 Through hole; 11.2 Positioning and guiding part; 10.1 Hydrostatic pool; 10.2 Load equalizing groove; 10.3 Damping hole; 7.1 High-pressure water outlet; 7.2 Valve plate assembly; 7.3 Rotor cylinder; 7.4 Central rotating shaft; 7.5 Hydraulic compensation device; 7.5.1 Thrust disc; 7.5.2 Compensation spring. Detailed implementation mode

[0050] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are only used to illustrate and explain the present invention, and are not used to limit the present invention.

[0051] As Figure 1 shown, it is an embodiment of the integrated device of a double-distribution plunger booster pump and energy recovery provided by the present invention, including an isobaric energy exchanger 7 and a plunger type booster pump 12. The plunger type booster pump 12 is fixedly installed on the upper end of the isobaric energy exchanger 7, and a plurality of tightening screws 19 are connected through between the isobaric energy exchanger 7 and the plunger type booster pump 12. Upper end covers 13 and lower end covers 14 are respectively installed at the upper and lower ends of the plunger type booster pump 12, a high-pressure fluid outlet 16 and a low-pressure fluid inlet 15 are respectively opened on the sides of the upper end cover 13 and the lower end cover 14, and a high-pressure fluid inlet 18 and a low-pressure fluid outlet 17 are opened at the lower end of the isobaric energy exchanger 7.

[0052] As Figure 2 shown, the plunger type booster pump 12 in the embodiment of the present invention includes a housing, a distribution plate 4, a swash plate 5, a plunger assembly 6 and a plunger cylinder assembly 9. The plunger cylinder assembly 9 is rotatably installed inside the housing. The distribution plate 4 and the swash plate 5 are respectively located on the upper and lower sides of the plunger cylinder assembly 9. The plunger cylinder assembly 9 includes a plunger cylinder 9.3 and a plunger sleeve 9.4. A plurality of annularly and equally spaced plunger sleeves 9.4 are arranged inside the plunger cylinder 9.3, and a plunger assembly 6 is movably installed in each plunger sleeve 9.4. The number of the plunger assemblies 6 is generally 5-11.

[0053] AsFigure 3 and Figure 4 As shown in Figure 4 , the distribution plate 4 in the embodiment of the present invention is provided with a high-pressure distribution window 4.2, and the swash plate 5 is provided with a low-pressure distribution window 5.2. The high-pressure distribution window 4.2 and the low-pressure distribution window 5.2 are distributed oppositely. The surface of the distribution plate 4 is provided with a first damping groove 4.1 communicated with the high-pressure distribution window 4.2, and the surface of the swash plate 5 is provided with a second damping groove 5.1 communicated with the low-pressure distribution window 5.2.

[0054] The distribution plate 4 of the present invention is different from the traditional double-waist configuration (high and low pressure waist-shaped grooves). There is no low-pressure distribution groove, only the high-pressure distribution window 4.2. The advantage of this is that there can be a greater hydraulic pressure on the low-pressure side to balance the overturning force of the plunger cylinder. This makes the booster operate more smoothly, with less wear and longer life. In order to reduce the friction on the low-pressure side, the end face of the distribution plate 4 can be subjected to a process treatment to reduce friction. By providing damping grooves on the distribution plate and the swash plate, the noise and vibration can be better reduced.

[0055] In a conventional plunger pump, the swash plate only forms a volume difference for the plunger assembly in the plunger cylinder, so that the plunger moves up and down along the inner wall of the plunger cylinder (ensuring that the plunger has a definite stroke), and the suction and discharge of fluid are completed through a conventional double-waist distribution plate.

[0056] The swash plate 5 of the present invention not only plays the role of providing the up and down movement of the plunger and providing the stroke. At the same time, it itself also has a low-pressure distribution window 5.2, which can boost the raw water with the pressure exchanged by the isobaric energy recovery to the pressure required by the membrane system. It can be made of stainless steel or ceramic materials.

[0057] As Figure 5 shown, the plunger assembly 6 in the embodiment of the present invention includes a plunger 6.1 and a slipper 6.3. The spherical structure at the lower end of the plunger 6.1 is rotatably installed inside the slipper 6.3, and the lower end face of the slipper 6.3 slides against the upper surface of the swash plate 5; a wear-resistant layer 6.2 is provided at the contact position between the inside of the slipper 6.3 and the plunger 6.1. The materials of the slipper 6.3 and the wear-resistant layer 6.2 are respectively stainless steel and PEEK materials, or stainless steel and ceramic materials, or ceramic and PEEK materials.

[0058] The end of the slipper of a conventional axial water hydraulic plunger pump is not water inlet. Generally, there are only damping holes with diameters of 0.8mm, 1.0mm, 1.2mm, 1.5mm, 1.8mm, 2.0mm, 2.5mm, 3.0mm or 3.2mm to adaptively adjust the static pressure in the static pressure groove.

[0059] Since the device provided by the embodiment of the present invention is used for boosting, the fluid pressure before boosting is already relatively high, and usually only needs to be increased by between 2 - 6 barg. The incoming water to be boosted already has sufficient supporting force for the slipper 6.3, which is balanced with the pressure of the plunger end 6.5 on the slipper 6.3. Therefore, the conditions of the plunger 6.1 and the incoming water at the root of the slipper 6.3 can be fully adopted to realize the flow distribution by using the swash plate 5.

[0060] As Figure 2 and Figure 6 As shown, a through hole is provided in the middle of the plunger cylinder 9.3. A small shaft 9.2 and a large shaft 9.1 are respectively fixedly installed at the upper and lower ends of the through hole. The small shaft 9.2 passes through the upper end cover of the plunger type booster pump 12, and the large shaft 9.1 is connected to the central rotating shaft of the isobaric energy exchanger 7 through a coupling 8.

[0061] The plunger cylinder 9.3 adopts a through - shaft design. The advantage is that the shaft is small and the cylinder can be made relatively large, and a pump device with a larger flow rate can be designed. At the same time, a double - shaft design is adopted with two support points. And due to the relatively high inlet pressure, a hydrostatic support method can be used to support the two shafts, and its stiffness can be made larger, so that the plunger pump can reach flow rates of 21 m³ / h, 40 m³ / h, 70 m³ / h, 70 m³ / h. It can be made of stainless steel plus PEEK, or stainless steel plus ceramic, or ceramic plus PEEK materials.

[0062] Preferably, a magnetic coupling is installed on the upper side of the upper end cover 13 of the plunger type booster pump 12 in the embodiment of the present invention. The pump shaft side of the magnetic coupling is installed at the upper end of the small shaft 9.2 of the plunger cylinder assembly 9. The magnetic coupling includes a sealing cover 2, and the sealing cover 2 is located between the motor side 1 of the magnetic coupling and the pump shaft side 3 of the magnetic coupling.

[0063] By adopting the design of the magnetic coupling in the present invention, the sealing performance is better and the reliability is higher. Since the entire chamber is filled with high - pressure raw water whose pressure has been exchanged, a more reliable magnetic coupling is selected, and the structure of the unreliable high - pressure shaft seal is abandoned.

[0064] As Figure 2 and Figure 7 As shown, a valve plate 11 is installed at the upper end of the plunger cylinder assembly 9 in the embodiment of the present invention. The valve plate 11 is located between the plunger cylinder assembly 9 and the flow distribution plate 4. The valve plate 11 is provided with a plurality of through holes 11.1 corresponding to the flow channels of the plunger cylinder assembly 9. The lower end of the through hole 11.1 is connected with a positioning and guiding member 11.2, and a sealing assembly is sleeved outside the positioning and guiding member 11.2.

[0065] The valve plate 11 is used to compensate for manufacturing errors. At the same time, the internal cavity pressure of the plunger cylinder assembly 9 will push the valve plate tightly against the flow distribution plate to reduce leakage. It can be made of stainless steel or ceramic plus stainless steel materials.

[0066] As Figure 2 and Figure 8 shown, in the embodiment of the present invention, the small shaft 9.2 and the large shaft 9.1 are respectively installed in cooperation with the upper end cover 13 and the swash plate 5 through the hydrostatic bearings 10. The inner and outer sides of the hydrostatic bearing 10 are respectively provided with a hydrostatic pool 10.1 and a load equalizing groove 10.2, and damping holes 10.3 are provided in the load equalizing groove 10.2.

[0067] Due to the relatively high pressure inside the booster pump, the hydrostatic support method is used to support the two shafts, and its stiffness can be made larger, the operation is stable, there is no wear, and the size of the plunger cylinder can be made larger and the flow rate can be larger for the same shaft diameter. Materials can be PEEK or ceramics.

[0068] The installation clearances between the small shaft 9.2, the large shaft 9.1 and the hydrostatic bearing 10 can be 0.01 mm, 0.02 mm, 0.03 mm, 0.04 mm, 0.05 mm, 0.06 mm or 0.07 mm.

[0069] As Figure 2 and Figure 9 shown, a high-pressure water outlet 7.1 for the outflow of the raw water after energy exchange is provided on the top cover of the isobaric energy exchanger 7, and the high-pressure water outlet 7.1 is aligned with the low-pressure distribution window 5.2 of the swash plate 5.

[0070] When the present invention is in use, the energy recovery device will perform at least 1 energy exchange during one rotation. Normally designed to be 1 - 3 times, the pressure of the high-pressure fluid inlet 18 will be transmitted to the low-pressure fluid inlet 15, the fluid at the low-pressure fluid inlet 15 will be transformed into the fluid at the high-pressure fluid outlet 16, and the fluid at the high-pressure fluid inlet 18 that has been exchanged will be discharged as the low-pressure fluid at the low-pressure fluid outlet 17.

[0071] As Figure 2 , Figure 10 and Figure 11 shown, a rotor assembly is installed inside the isobaric energy exchanger in the embodiment of the present invention. The rotor assembly includes a valve plate assembly 7.2, a rotor cylinder 7.3 and a central rotating shaft 7.4. The rotor cylinder 7.3 is rotatably installed outside the central rotating shaft 7.4. A valve plate assembly 7.2 is installed at each of the upper and lower ends of the rotor cylinder 7.3, and a hydraulic compensation device 7.5 is installed between the valve plate assembly 7.2 at the upper end of the rotor cylinder 7.3 and the rotor cylinder 7.3; the hydraulic compensation device 7.5 includes an annular thrust plate 7.5.1 and a plurality of compensation springs 7.5.2, and the plurality of compensation springs 7.5.2 are annularly and equidistantly distributed on the lower side of the thrust plate 7.5.1.

[0072] As Figure 12 and Figure 13As shown, the arrow direction represents the flow direction routes of the fluid from the high-pressure fluid inlet 18 to the low-pressure fluid outlet 17, and from the low-pressure fluid inlet 15 to the high-pressure fluid outlet 16. The low-pressure fluid entering from the low-pressure fluid inlet 15 exchanges energy with the high-pressure fluid entering from the high-pressure fluid inlet 18 in the isobaric energy exchanger 7, and then is pressurized by the plunger type booster pump 12. The plunger cylinder assembly 9 drives the plunger assembly 6 to rotate on the upper surface of the swash plate 5. As Figure 14 shown, the arrow direction indicates the rotation direction of the plunger assembly 6. Point A on the upper surface of the swash plate 5 is the bottom dead center, and point B is the top dead center. When the plunger assembly 6 rotates to the bottom dead center A, the area between the low-pressure porting window of the swash plate and the high-pressure porting window of the porting plate forms a pre-unloading area. When the plunger assembly rotates to the top dead center B, the area between the low-pressure porting window of the swash plate and the high-pressure porting window of the porting plate forms a pre-pressurizing area.

[0073] The space between the upper end of the plunger 6.1 and the upper end face of the plunger cylinder is the volume chamber. When the plunger 6.1 and the slipper 6.3 move upward along the swash plate 5 towards the top dead center, the volume of the chamber becomes larger, and water is sucked into the chamber through the swash plate porting groove and the root port of the plunger slipper. When the plunger and the slipper move downward along the swash plate towards the bottom dead center, the volume of the chamber becomes smaller, and the solution in the chamber is discharged through the high-pressure porting window 4.2 of the porting plate.

[0074] Since the plunger cylinder 9.3 is rotating, the plunger rotates with it. After the plunger passes through the top dead center B, the water intake ends, the slipper disengages from the low-pressure porting window 5.2 of the swash plate, and enters the pre-pressurizing area. After passing through the pre-pressurizing area, the plunger and the slipper move upward along the swash plate and are pressed out through the high-pressure porting window 4.2 of the porting plate.

[0075] In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more; the orientation or positional relationships indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, 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, and therefore should not be construed as a limitation of the present invention. In addition, the terms "first", "second", "third", etc. are only used for descriptive purposes and cannot be construed as indicating or implying relative importance.

[0076] Finally, it should be noted that the above are only the preferred embodiments of the present invention and are not used to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions recorded in the foregoing embodiments, or perform equivalent replacements on some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A dual-distribution plunger booster pump and energy recovery integrated device, characterized in that: It includes an isobaric energy exchanger and a plunger-type booster pump, wherein the plunger-type booster pump is fixedly mounted on the upper end of the isobaric energy exchanger, a high-pressure fluid outlet and a low-pressure fluid inlet are provided on the side of the plunger-type booster pump, and a high-pressure fluid inlet and a low-pressure fluid outlet are provided on the lower end of the isobaric energy exchanger; The plunger-type booster pump comprises a housing, a valve plate, a swash plate, a plunger assembly and a plunger cylinder assembly, wherein the plunger cylinder assembly is rotatably mounted on the inner side of the housing, the valve plate and the swash plate are respectively located on the upper and lower sides of the plunger cylinder assembly, and the plunger cylinder assembly comprises a plunger cylinder and a plunger sleeve, wherein a plurality of annular equidistantly distributed plunger sleeves are arranged on the inner side of the plunger cylinder, and a plunger assembly is movably mounted in each plunger sleeve; The plunger assembly includes a plunger and a sliding shoe. The spherical structure at the lower end of the plunger can be rotatably mounted on the inner side of the sliding shoe. The lower end surface of the sliding shoe slides against the upper surface of the swash plate. The plunger and the sliding shoe are penetrated by mutually connected flow channels. The distribution plate is provided with a high-pressure distribution window, and the inclined plate is provided with a low-pressure distribution window, and the high-pressure distribution window and the low-pressure distribution window are relatively distributed.

2. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: A first damping groove communicating with the high-pressure flow distribution window is formed on the surface of the flow distribution plate, and a second damping groove communicating with the low-pressure flow distribution window is formed on the surface of the inclined plate.

3. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: A wear-resistant layer is provided at the contact position between the inner side of the sliding shoe and the plunger. The sliding shoe and the wear-resistant layer are made of stainless steel and PEEK material, or stainless steel and ceramic material, or ceramic and PEEK material respectively.

4. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: A valve plate is installed at the upper end of the plunger cylinder assembly, and the valve plate is located between the plunger cylinder assembly and the distribution plate. The valve plate is provided with a plurality of through holes corresponding to the flow channels of the plunger cylinder assembly, and a positioning guide is connected to the lower end of the through hole, and a sealing assembly is sleeved on the outer side of the positioning guide.

5. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: A through hole is provided in the middle of the plunger cylinder, and a small shaft and a large shaft are fixedly installed at the upper and lower ends of the through hole respectively. The small shaft passes through the upper end cover of the plunger booster pump, and the large shaft is connected to the central rotating shaft of the isobaric energy exchanger through a coupling.

6. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 5, characterized in that: The plunger-type booster pump is provided with a magnetic coupling on the upper side of the upper end cover, and the pump shaft side of the magnetic coupling is installed on the upper end of the small shaft of the plunger cylinder assembly.

7. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 6, characterized in that: The magnetic coupling comprises a sealing cover, and the sealing cover is located between the motor side of the magnetic coupling and the pump shaft side of the magnetic coupling.

8. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 5, characterized in that: The small shaft and the large shaft are respectively installed with the upper end cover and the swash plate through the hydrostatic bearings. The hydrostatic bearings are respectively provided with a hydrostatic pool and a load-balancing groove on the inner and outer sides. The load-balancing grooves are provided with damping holes.

9. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: The top cover of the isobaric energy exchanger is provided with a high-pressure water outlet for the raw water to flow out after energy exchange, and the high-pressure water outlet is aligned with the low-pressure distribution window of the inclined plate.

10. The dual-distribution plunger booster pump and energy recovery integrated device according to claim 1, characterized in that: The isobaric energy exchanger is internally installed with a rotor assembly, the rotor assembly comprising a valve plate assembly, a rotor cylinder and a central rotating shaft, the rotor cylinder is rotatably installed on the outside of the central rotating shaft, a valve plate assembly is respectively installed at the upper and lower ends of the rotor cylinder, and a hydraulic compensation device is installed between the valve plate assembly at the upper end of the rotor cylinder and the rotor cylinder; The hydraulic compensation device comprises an annular thrust plate and a plurality of compensation springs, wherein the plurality of compensation springs are distributed annularly and equidistantly on the lower side of the thrust plate.

Images