Self-driven energy recovery device with an internally hydraulically self-compensating split-type hydrostatic rotor

Abstract

The present invention belongs to the technical field of energy recovery devices, and provides a self-driven energy recovery device with an internally hydraulically automatically compensated split static pressure rotor. An exchanger is installed inside a housing. The rotor cylinder of the exchanger is rotatably sleeved outside a static and dynamic shaft. Two distribution end covers are respectively fixedly installed at the upper and lower ends of the static and dynamic shaft. The rotor cylinder is divided into two upper and lower single-body rotor cylinders, and the two single-body rotor cylinders are connected by a connector. A first static pressure pool and damping grooves are formed on the outer end face of the single-body rotor cylinder, and a stepped structure is arranged at the opening position of the axial flow channel on the outer end face of the single-body rotor cylinder; the connector includes a connecting step and guide plates connected to both ends of the connecting step; thin-wall orifice channels communicating with the static and dynamic shaft are formed on the inner wall of the flow channel of the distribution end cover. By adopting a combination of double rotor cylinders, the present invention can achieve automatic compensation of the clearance under the conditions of pressure change or wear, improve the efficiency and service life, and enhance the reliability of the product.

Description

Technical Field

[0001] The present invention belongs to the technical field of energy recovery equipment, and particularly relates to a self-driven energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor, 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 then 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 industrial processes.

[0003] At present, 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 the structure is complex and the maintenance cost is high.

[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 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 operation state.

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

[0011] Traditional isobaric exchangers often integrate the flow distribution structure with the water inlet and outlet in order to ensure strength, which often results in high manufacturing costs. After wear, the entire water inlet and outlet need to be replaced, resulting in high costs.

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

[0013] The plunger type device realizes the transfer of pressure energy through mechanical reciprocating motion, and has 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 a self-driven energy recovery device with an internally hydraulically automatically compensated split static pressure rotor.

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

[0017] A self-driven energy recovery device with an internally hydraulically automatically compensated split static pressure rotor includes a housing. The upper and lower ends of the housing are respectively installed with an upper end cover and a lower end cover. The upper end cover is provided with a low-pressure fluid inlet and a high-pressure fluid outlet, and the lower end cover is provided with a low-pressure fluid outlet and a high-pressure fluid inlet. An exchanger is installed inside the housing;

[0018] The exchanger includes a first distribution end cover, a dynamic and static shaft, a rotor cylinder, and a second distribution end cover. The rotor cylinder is rotatably sleeved outside the dynamic and static shaft. A number of axially distributed annular flow channels are provided inside the rotor cylinder, and the cross-section of the axially distributed flow channels is a fan-shaped or circular structure. The first distribution end cover and the second distribution end cover are respectively fixedly installed at the upper and lower ends of the dynamic and static shaft, and the first distribution end cover, the dynamic and static shaft, and the second distribution end cover are sequentially connected through fastening bolts in the middle;

[0019] The rotor cylinder is divided into two single rotor cylinders up and down. The corresponding axially distributed flow channels between the two single rotor cylinders are connected through a connector. The two single rotor cylinders can perform relative displacement in the axial direction. A first static pressure pool and a damping groove are provided at the position of the middle through hole on the outer end face of the single rotor cylinder, and a stepped structure is provided at the opening position of the axially distributed flow channel on the outer end face of the single rotor cylinder;

[0020] The connector includes a connection step and guide plates connected to both ends of the connection step. An installation stepped groove matching the connection step is provided at the opening position of the axially distributed flow channel where the single rotor cylinder is connected to the connector;

[0021] The inner walls of the flow channels of the first flow distribution end cover and the second flow distribution end cover are provided with thin-wall small-hole flow channels communicating with the static and dynamic pressure shafts.

[0022] Furthermore, on the side of the first flow distribution end cover and the second flow distribution end cover opposite to the static and dynamic pressure shafts, first positioning holes are provided. The inner ends of the first positioning holes communicate with the thin-wall small-hole flow channels. Second positioning holes axially aligned with the first positioning holes are respectively provided at both ends of the static and dynamic pressure shafts. A positioning pin is inserted through the connection position of each group of connected first positioning holes and second positioning holes, and a thin-wall damping hole is provided in the middle of the positioning pin.

[0023] Furthermore, a plurality of zigzag grooves are circumferentially and equidistantly distributed on the outer surface of the static and dynamic pressure shafts. Second static pressure pools are provided at both ends of the static and dynamic pressure shafts, and a stepped shaft is provided at the outer ends of the second static pressure pools.

[0024] Furthermore, a longitudinal flow dividing plate or a cross-shaped flow dividing plate is fixed in the middle of the connector.

[0025] Furthermore, an end face inclined groove is provided at the edge position of the outer end face of the single rotor cylinder.

[0026] Furthermore, two positioning support rings are fixed outside the fastening bolts, and positioning grooves cooperating with the positioning support rings are provided at the connection positions of the upper end cover, the lower end cover and the static and dynamic pressure shafts.

[0027] Furthermore, both the fastening bolts and the positioning support rings are made of super duplex stainless steel or nickel-based alloy.

[0028] Furthermore, hydraulic drive slopes are provided at the flow distribution ports of the first flow distribution end cover and the second flow distribution end cover. Two balance and anti-friction grooves are provided on the end faces of the first flow distribution end cover and the second flow distribution end cover opposite to the static and dynamic pressure shafts. Low-pressure balance static pressure bags are provided on the outer end faces of the first flow distribution end cover and the second flow distribution end cover.

[0029] Furthermore, a balance groove sealing O-ring is installed in the low-pressure balance static pressure bag, and a static seal O-ring is installed outside the first flow distribution end cover and the second flow distribution end cover.

[0030] Furthermore, through holes are provided on the outer side surface of the housing, and the through holes are used as convective exchange ports or rotational speed sensor access ports.

[0031] Combined with the above technical solutions, the beneficial effects of the present invention compared with the prior art are as follows:

[0032] In the present invention, a pair of balanced forces is formed by the pressure from the first static pressure pool on the end face of the rotor cylinder towards the center and the thrust formed by the cross-sectional difference of the internal flow passage. Since the two single rotor cylinders can perform relative displacement in the axial direction, the gap between the end face of the rotor cylinder and the distribution end cover can be kept constant, realizing automatic compensation under the conditions of pressure change or wear, and achieving the function of adapting to the gap between the rotor cylinder and the distribution end cover.

[0033] In the present invention, by adopting a variable cross-section design for the cross-section of the internal flow passage of the rotor cylinder, it is possible to better reduce the turbulence and the residence time of the fluid, better form a hydraulic interface barrier between the high-pressure concentrated water and seawater, and reduce the proportion of dead volume in the flow passage. The cross-section of the internal flow passage of the rotor cylinder becomes larger from small at the high-pressure fluid inlet. Since the viscosity and density of the high-pressure fluid are large here, the pressure loss can be reduced. The cross-section of the internal flow passage of the rotor cylinder becomes smaller from large at the high-pressure fluid outlet, forming a small back pressure, which can reduce turbulence and noise, thereby achieving a lower mixing degree.

[0034] In the present invention, through the first static pressure pool and the thin-wall small-hole flow passage, the turbulence during the high-low pressure exchange can be reduced, the noise can be lowered, and the mixing degree can be reduced.

[0035] In the present invention, by using a connector to assemble and connect the rotor cylinders, since the cross-sectional area of the internal flow passage of the connector is smaller than that of the internal flow passage of the rotor cylinder, the internal flow passage of the connector has certain damping characteristics, which can better form a hydraulic interface barrier, reduce the mixing degree, and the presence of the connector can well cope with thermal expansion.

[0036] In the case of the failure and wear of the dynamic and static shaft pressure lubrication, the housing can play the role of a new dynamic and static pressure bearing to ensure the normal operation of the energy recovery device. The static pressure is formed between the tiny leakage generated by the gap between the connector and the single rotor cylinder and the inner wall of the housing. In the case of the failure of the dynamic and static shaft pressure caused by system water shortage, the failure of the thin-wall damping hole, etc., the housing itself can continue to support the rotation of the rotor as a bearing, improving the reliability of the whole product. The present invention adopts the form of a double-rotor cylinder combination, which can compensate for the manufacturing error and wear compensation in the length direction, can realize the automatic compensation of the gap, ensure a constant gap value, ensure that the pressure conversion efficiency operates persistently at an efficient value greater than 98%, improve the efficiency and service life, avoid deep hole machining, and at the same time avoid the situation with extremely high length tolerance requirements, greatly reducing the processing and use costs, and improving the reliability of the product at the same time. The dynamic and static shaft pressure can enable the product to work in the pressure range of 5 - 120 barg, with the noise lower than 78 decibels and the mixing degree lower than 1.5%. By adopting a modular design, the cost can be lower, the maintenance can be simpler, and there can be more categories, and it can be randomly combined to be suitable for different working conditions (it can be used for the recovery of hydraulic residual pressure and also for the recovery of gas residual pressure). Description of the Drawings

[0037] The accompanying 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 accompanying drawings:

[0038] Figure 1 is a schematic structural diagram of a self-driving energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor provided by an embodiment of the present invention;

[0039] Figure 2 is a sectional view of a self-driving energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor provided by an embodiment of the present invention;

[0040] Figure 3 is a schematic structural diagram of an exchanger provided by an embodiment of the present invention;

[0041] Figure 4 is the present invention Figure 3 a partial enlarged schematic view of position A therein;

[0042] Figure 5 is a schematic structural diagram of a rotor cylinder provided by an embodiment of the present invention;

[0043] Figure 6 is a schematic structural diagram of a single rotor cylinder provided by an embodiment of the present invention, wherein (a) and (b) are schematic structural diagrams of the single rotor cylinder from different perspectives respectively;

[0044] Figure 7 is a schematic structural diagram of a connector provided by an embodiment of the present invention;

[0045] Figure 8 is a schematic structural diagram of two different forms of connectors provided by an embodiment of the present invention;

[0046] Figure 9 is a schematic structural diagram of a static and dynamic pressure shaft provided by an embodiment of the present invention;

[0047] Figure 10 is a schematic structural diagram of a positioning pin provided by an embodiment of the present invention;

[0048] Figure 11 is a schematic structural diagram of a fastening bolt provided by an embodiment of the present invention;

[0049] Figure 12 is a schematic structural diagram of a first flow distribution end cover provided by an embodiment of the present invention, wherein (a) and (b) are schematic structural diagrams of the first flow distribution end cover from different perspectives respectively;

[0050] Figure 13 is a schematic structural diagram of a housing provided by an embodiment of the present invention.

[0051] In the figure: 1. Low-pressure fluid inlet; 2. High-pressure fluid outlet; 3. Low-pressure fluid outlet; 4. High-pressure fluid inlet; 5. Upper end cover; 6. Exchanger; 7. Lower end cover; 8. Shell; 9. Through hole; 6.1. Fastening nut; 6.2. First flow distribution end cover; 6.3. Positioning support ring; 6.4. Fastening bolt; 6.5. Dynamic and static pressure shaft; 6.6. Rotor cylinder; 6.7. Second flow distribution end cover; 6.8. Positioning pin; 6.9. Balance groove sealing O-ring; 6.10. Static sealing O-ring; 6.11. Thin-walled small hole flow channel; 6.2.1. Hydraulic drive ramp; 6.2.2. First balance anti-friction groove; 6.2.3. Second balance anti-friction groove; 6.2.4. First positioning hole; 6.2.5. Low-pressure balance static pressure pocket; 6.5.1. Zigzag groove pattern; 6.5.2. Second static pressure pool; 6.5.3. Step shaft; 6.5.4. Second positioning hole; 6.6.1. Single rotor cylinder; 6.6.2. Connector; 6.6.1.1. End face inclined groove; 6.6.1.2. First static pressure pool; 6.6.1.3. Damping groove; 6.6.1.4. Step structure; 6.6.1.5. Installation step groove; 6.6.2.1. Guide plate; 6.6.2.2. Connection step; 6.8.1. Thin-walled damping hole; 6.8.2. Positioning pin surface. Detailed implementation manners

[0052] 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.

[0053] As Figure 1 and Figure 2 shown, an embodiment of the self-driving energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor provided by the present invention includes a shell 8, an upper end cover 5, a lower end cover 7 and an exchanger 6. The upper end cover 5 and the lower end cover 7 are respectively installed at the upper and lower ends of the shell 8, the exchanger 6 is installed inside the shell 8, the upper end cover 5 is provided with a low-pressure fluid inlet 1 and a high-pressure fluid outlet 2, and the lower end cover 7 is provided with a low-pressure fluid outlet 3 and a high-pressure fluid inlet 4.

[0054] As Figure 3 and Figure 4 shown, the exchanger 6 in the embodiment of the present invention includes a first flow distribution end cover 6.2, a dynamic and static pressure shaft 6.5, a rotor cylinder 6.6 and a second flow distribution end cover 6.7. The rotor cylinder 6.6 is rotatably sleeved outside the dynamic and static pressure shaft 6.5. A plurality of axially distributed annular equidistant axial flow channels are provided inside the rotor cylinder 6.6. The cross-section of the axial flow channel is a fan-shaped or circular structure. The first flow distribution end cover 6.2 and the second flow distribution end cover 6.7 are respectively fixedly installed at the upper and lower ends of the dynamic and static pressure shaft 6.5. Thin-walled small hole flow channels 6.11 communicating with the dynamic and static pressure shaft 6.5 are respectively provided on the inner walls of the flow channels of the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7.

[0055] The first flow distribution end cover 6.2, the dynamic and static shaft presses 6.5, and the second flow distribution end cover 6.7 are sequentially penetrated and connected through the fastening bolts 6.4 in the middle. Fastening nuts 6.1 are respectively installed at both ends of the fastening bolts 6.4, and counterbores for cooperating with the fastening nuts 6.1 are respectively provided on the outer end faces of the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7.

[0056] As Figure 5 shown, the rotor cylinder 6.6 in the embodiment of the present invention is divided into two single - body rotor cylinders 6.6.1 up and down. The axial flow channels corresponding to the two single - body rotor cylinders 6.6.1 are connected through a connector 6.6.2, and the two single - body rotor cylinders 6.6.1 can perform relative displacement in the axial direction.

[0057] Specifically, the exchanger 6 provided in the embodiment of the present invention has a certain compensation ability and reliable safety. By designing the rotor cylinder 6.6 into two single - body rotor cylinders 6.6.1, the manufacturing error and wear can be compensated through the non - equilibrium state of force, and the energy recovery device can work in the high - efficiency range greater than 98% for a long time. The appearance of this structure completely changes the current mainstream rotor manufacturing method. The traditional rotor manufacturing has extremely high length precision requirements and completely relies on the final closed loop to control the tolerance. This combined structure of the present invention completely eliminates the need to consider the tolerance in the length direction, greatly reducing the manufacturing cost.

[0058] Since the rotor cylinder 6.6 of the present invention is composed of two single - body rotor cylinders 6.6.1 connected through a connector 6.6.2, the difficulty of internal long - hole machining is reduced. At the same time, this structure has a certain displacement in the axial direction, which can compensate for the manufacturing error and wear in the axial direction. The normal axial movement gap between the two single - body rotor cylinders 6.6.1 can be 0.05mm, 0.06mm, 0.07mm, 0.08mm, 0.09mm, 0.10mm, 0.11mm, 0.12mm, 0.13mm, 0.14mm, 0.15mm, etc.

[0059] As Figure 6 shown, an end - face inclined groove 6.6.1.1 is provided at the edge position of the outer end face of the single - body rotor cylinder 6.6.1 in the embodiment of the present invention. As Figure 6 shown in (a) of Figure 6 it, a first static pressure pool 6.6.1.2 and a damping groove 6.6.1.3 are provided at the position of the middle through - hole on the outer end face of the single - body rotor cylinder 6.6.1. As

[0060] In the rotor cylinder 6.6 of the present invention, by adopting the design of end face inclined grooves 6.6.1.1 on the end face, the problem of eccentric wear caused by end face force or insufficient lubrication is greatly reduced, the pumping effect on the surface is improved, the stiffness of the end face fluid is increased, and wear is reduced.

[0061] By adopting the double-damping structure design of the first static pressure pool 6.6.1.2 and the damping groove 6.6.1.3, the risk of end face cavitation and wear is greatly reduced, the pressure drop is more uniform, and the inner hole adopts a tiny stepped structure 6.6.1.4. The stepped structure 6.6.1.4 enables a certain tension to be generated axially between the two single rotor cylinders 6.6.1, pushing themselves towards the distribution end cover at the outer end. At the same time, due to the existence of the first static pressure pool 6.6.1.2 and the damping groove 6.6.1.3, a certain reaction force will be generated, pushing the two single rotor cylinders 6.6.1 towards the center. The thrust and the reaction force form a pair of balanced forces, realizing a constant gap between the end face of the rotor cylinder 6.6 and the distribution end cover, and achieving automatic compensation under the conditions of pressure change or wear.

[0062] As Figure 7 shown, the connector 6.6.2 in the embodiment of the present invention includes a connection step 6.6.2.2 and a guide plate 6.6.2.1. One guide plate 6.6.2.1 is integrally connected to each end of the connection step 6.6.2.2, and the connection step 6.6.2.2 is assembled in cooperation with the installation stepped groove 6.6.1.5 of the single rotor cylinder 6.6.1.

[0063] The connector 6.6.2 in the embodiment of the present invention is an innovative design of an isobaric exchanger. It can adopt a polymer-reinforced plastic to ensure a certain elasticity, toughness and self-lubricity under the condition of ensuring sufficient strength, and ensure the relative sliding between the rotor cylinder and itself.

[0064] Due to the existence of the connector 6.6.2, the cross-sectional area of the internal flow channel of the connector 6.6.2 is smaller than that of the internal flow channel of the rotor cylinder 6.6, so that the internal flow channel of the connector 6.6.2 has a certain damping characteristic, which is equivalent to forming a damping hole in the middle of the rotor cylinder 6.6, which can form a certain back pressure, reduce the turbulence of the fluid, and reduce the mixing degree, and the mixing degree can be controlled below 2%.

[0065] As Figure 8 shown, a longitudinal flow dividing plate or a cross-shaped flow dividing plate can be added in the middle of the connector 6.6.2 in the embodiment of the present invention. Through the action of the flow dividing plate, the effect of reducing the mixed flow can be improved without causing too much influence on the fluid pressure.

[0066] As Figure 9As shown, on the outer surface of the static and dynamic pressure shaft 6.5 in the embodiment of the present invention, a plurality of zigzag grooves 6.5.1 are circumferentially and equidistantly distributed. Second static pressure pools 6.5.2 are provided at both ends of the static and dynamic pressure shaft 6.5, and stepped shafts 6.5.3 are provided at the outer ends of the second static pressure pools 6.5.2.

[0067] At the beginning of startup, since static pressure cannot be established and the gap between the static and dynamic pressure shaft 6.5 and the inner wall of the central hole of the rotor cylinder 6.6 is too small, they can be regarded as two parallel cylindrical surfaces, and no pressure (dynamic pressure support or lubrication) will be generated in the gap. In the present invention, appropriate zigzag grooves 6.5.1 are provided on the static and dynamic pressure shaft 6.5. When the fluid flows through the grooves, it is like passing through a series of stepped bearings, and because the flow direction is not directly facing the direction of the stepped shaft 6.5.3, a lateral pumping effect is also generated. Both situations result in an increase in the pressure in the lubricating liquid (formation of dynamic pressure characteristics). Before the static pressure is fully established, good lubricating support characteristics of dynamic pressure are formed, so this product can work at a very low pressure, which is the main reason for low-pressure energy exchange. Through the perfect cooperation of the zigzag grooves 6.5.1, the second static pressure pools 6.5.2, and the stepped shafts 6.5.3, the energy recovery device can be used well within the pressure range of 5 - 120 barg.

[0068] The fitting clearance between the static and dynamic pressure shaft 6.5 and the inner wall of the central hole of the rotor cylinder 6.6 can be 0.01 mm, 0.02 mm, 0.03 mm, 0.04 mm, 0.05 mm, 0.06 mm, 0.07 mm, 0.08 mm, 0.09 mm, 0.10 mm, 0.11 mm, 0.12 mm, 0.13 mm, 0.14 mm, 0.15 mm, 0.16 mm, 0.17 mm, 0.18 mm, 0.19 mm, 0.20 mm, etc.

[0069] As Figure 3 、 Figure 9 、 Figure 10 and Figure 12 As shown, on the sides of the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7 in the embodiment of the present invention opposite to the static and dynamic pressure shaft 6.5, first positioning holes are provided. The inner ends of the first positioning holes are communicated with the thin-wall small hole flow channels 6.11. Second positioning holes 6.5.4 are respectively provided at both ends of the static and dynamic pressure shaft 6.5, and the second positioning holes 6.5.4 at both ends are respectively aligned with the first positioning holes of the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7. A positioning pin 6.8 is inserted through the connection position of each group of connected first positioning holes and second positioning holes 6.5.4, and a thin-wall damping hole 6.8.1 is provided in the middle of the positioning pin 6.8.

[0070] In the embodiment of the present invention, the positioning pin 6.8 and the thin-walled damping hole 6.8.1 are integrally designed. The design of the thin-walled damping hole 6.8.1 avoids the influence of temperature on damping, and at the same time can reliably provide the rotor cylinder with the stiffness of strain.

[0071] As Figure 11 shown, two positioning support rings 6.3 are fixed on the outside of the fastening bolt 6.4 in the embodiment of the present invention. Positioning grooves matching with the positioning support rings 6.3 are provided at the connection positions of the upper end cover 5, the lower end cover 7 and the static and dynamic pressure shafts 6.5.

[0072] Preferably, both the fastening bolt 6.4 and the positioning support ring 6.3 are made of super duplex stainless steel or nickel-based alloy.

[0073] As Figure 12 shown, a hydraulic drive ramp 6.2.1 is provided at the flow distribution port of the first flow distribution end cover 6.2 in the embodiment of the present invention. A first balance anti-friction groove 6.2.2 and a second balance anti-friction groove 6.2.3 are provided on the opposite end faces of the first flow distribution end cover 6.2 and the static and dynamic pressure shafts 6.5. A low-pressure balance static pressure pocket 6.2.5 is provided on the outer end face of the first flow distribution end cover 6.2. The low-pressure balance static pressure pocket 6.2.5 is a fully sealed balance static pressure pocket structure formed by placing an O-ring inside the groove. Similarly, the structure of the second flow distribution end cover 6.7 is the same as the above structure of the first flow distribution end cover 6.2.

[0074] For the flow distribution port, in order to reduce wear and balance force, a number of innovative designs are made, and various anti-friction and balance grooves are opened from multiple angles. The slope of the hydraulic drive ramp can be 8°, 10°, 13°, 15°, 19°, 23°, 25°, 27°, 30°, 31°, 32°, 33°, 34°, 35°, etc.

[0075] As Figure 3 and Figure 12 shown, a balance groove seal O-ring 6.9 is installed in the low-pressure balance static pressure pocket 6.2.5 in the embodiment of the present invention. Static seal O-rings 6.10 are installed on the outside of the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7.

[0076] As Figure 1 and Figure 13 shown, a through hole 9 is provided on the outer side surface of the housing 8 in the embodiment of the present invention. The through hole 9 is used as a convection exchange port or a rotational speed sensor access port.

[0077] Because the two single rotor cylinders 6.6.1 of the rotor cylinder 6.6 are connected by the connector 6.6.2, there will be a certain amount of leakage. Under normal circumstances, the through hole 9 is required as a convection exchange port to discharge the fluid, or install a speed sensor. The inside of the shell can be specially surface treated. In the case of lubrication failure and wear of the dynamic and static pressure shaft 6.5, the inner wall of the shell can form a static pressure support bearing with the outer circle of the rotor cylinder 6.6. The static pressure provider is the trace amount of high-pressure water leaked after the two single rotor cylinders 6.6.1 are separated. The gap between the connector 6.6.2 and the single rotor cylinder 6.6.1 is the high-pressure water supply damping. When the embodiment of the present invention is in use, the exchanger of the energy recovery device will exchange energy at least once per rotation, and the normal design is 1-3 times. The number of times can be controlled by selecting the number of distribution port groups of the first distribution end cover 6.2 and the second distribution end cover 6.7.

[0078] When the exchanger 6 is exchanging energy, the high-pressure fluid entering the high-pressure fluid inlet 4 drives the rotor cylinder 6.6 to rotate around the dynamic and static pressure axis 6.5. The pressure of the high-pressure fluid inlet 4 is transmitted to the low-pressure fluid inlet 1, and the fluid of the low-pressure fluid inlet 1 is converted into the fluid of the high-pressure fluid outlet 2. The exchanged fluid of the high-pressure fluid inlet 4 is converted into the low-pressure fluid of the low-pressure fluid outlet 3 and discharged.

[0079] By providing a stepped structure 6.6.1.4 at the opening position of the rotor cylinder 6.6, the internal flow channel of the rotor cylinder 6.6 becomes a variable cross-section form. As the flow channel opening becomes smaller, the fluid in the flow channel will generate thrusts toward both ends. At the same time, since the outer end surface of the rotor cylinder 6.6 is provided with a first static pressure pool 6.6.1.2 and a damping groove 6.6.1.3, a reaction force that pushes the two single rotor cylinders 6.6.1 toward the center is generated. The thrust and the reaction force form a pair of balancing forces. Since the two single rotor cylinders 6.6.1 can be relatively displaced in the axial direction, a constant gap can be achieved between the end surface of the rotor cylinder 6.6 and the distribution end cover, and automatic compensation can be achieved in the case of pressure changes or wear.

[0080] In the description of the present invention, unless otherwise specified, "plurality" means two or more than two; the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail", etc. are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", "third", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0081] Finally, it should be noted that the above are only preferred embodiments of the present invention and are not intended 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 for some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A self-driven energy recovery device with an internally hydraulically self-compensating split hydrostatic rotor, comprising a housing, an upper end cover and a lower end cover are respectively installed at the upper and lower ends of the housing, a low-pressure fluid inlet and a high-pressure fluid outlet are provided on the upper end cover, and a low-pressure fluid outlet and a high-pressure fluid inlet are provided on the lower end cover, characterized in that, An exchanger is installed inside the housing; The exchanger includes a first flow distribution end cover, a static and dynamic shaft, a rotor cylinder, and a second flow distribution end cover. The rotor cylinder is rotatably sleeved outside the static and dynamic shaft. A number of axially distributed annular flow channels are provided inside the rotor cylinder at equal intervals. The first flow distribution end cover and the second flow distribution end cover are respectively fixedly installed at the upper and lower ends of the static and dynamic shaft. The first flow distribution end cover, the static and dynamic shaft, and the second flow distribution end cover are sequentially connected through fastening bolts in the middle; The rotor cylinder is divided into two single rotor cylinders up and down. The axially distributed flow channels corresponding to the two single rotor cylinders are connected through a connector. The two single rotor cylinders can perform relative displacement in the axial direction. A first static pressure pool and a damping groove are provided at the position of the middle through hole on the outer end face of the single rotor cylinder. A stepped structure is provided at the opening position of the axially distributed flow channel on the outer end face of the single rotor cylinder; The connector includes a connection step and guide plates connected to both ends of the connection step. An installation stepped groove matching the connection step is provided at the opening position of the axially distributed flow channel where the single rotor cylinder is connected to the connector; Thin-walled orifice flow channels communicating with the static and dynamic shaft are respectively provided on the inner walls of the flow channels of the first flow distribution end cover and the second flow distribution end cover.

2. The self-driven energy recovery device with an internally hydraulically self-compensating split-type static pressure rotor according to claim 1, wherein, First positioning holes are respectively provided on the sides of the first flow distribution end cover and the second flow distribution end cover opposite to the static and dynamic shaft. The inner ends of the first positioning holes communicate with the thin-walled orifice flow channels. Second positioning holes axially aligned with the first positioning holes are respectively provided at both ends of the static and dynamic shaft. A positioning pin is inserted through the connection position of each group of connected first positioning holes and second positioning holes. A thin-walled damping hole is provided in the middle of the positioning pin.

3. The self-driven energy recovery device with a split-type hydrostatic rotor having internal hydraulic automatic compensation according to claim 1, characterized in that, A plurality of zigzag grooves are circumferentially and equidistantly distributed on the outer surface of the static and dynamic shaft. Second static pressure pools are provided at both ends of the static and dynamic shaft. A stepped shaft is provided at the outer end of the second static pressure pool.

4. The self-driven energy recovery device with an internally hydraulically self-compensating split-type static pressure rotor according to claim 1, wherein, A longitudinal flow dividing plate is fixed in the middle of the connector.

5. The self-driving energy recovery device with an internally hydraulically automatically compensated split hydrostatic rotor according to claim 1, characterized in that, End face inclined grooves are provided at the edge positions of the outer end faces of the single rotor cylinders.

6. The self-driven energy recovery device with a split hydrostatic rotor having internal hydraulic automatic compensation according to claim 1, characterized in that, Two positioning support rings are fixed outside the fastening bolts. Positioning grooves matching the positioning support rings are provided at the connection positions of the upper end cover, the lower end cover, and the static and dynamic shaft.

7. The self-driving energy recovery device with an internally hydraulically self-compensating split hydrostatic rotor according to claim 6, characterized in that, The fastening bolts and the positioning support rings are both made of super duplex stainless steel or nickel-based alloy.

8. The self-driven energy recovery device with a split-type hydrostatic rotor having internal hydraulic automatic compensation according to claim 1, characterized in that, Hydraulic drive slopes are provided at the flow distribution ports of the first flow distribution end cover and the second flow distribution end cover. Two balance anti-friction grooves are provided on the opposite end faces of the first flow distribution end cover and the second flow distribution end cover and the static and dynamic shaft. Low-pressure balance static pressure bags are provided on the outer end faces of the first flow distribution end cover and the second flow distribution end cover.

9. The self-driven energy recovery device with an internally hydraulically automatically compensated split-type hydrostatic rotor according to claim 8, characterized in that, Balance groove sealing O-rings are installed inside the low-pressure balance static pressure bags. Static sealing O-rings are installed outside the first flow distribution end cover and the second flow distribution end cover.

10. The self-driven energy recovery device with an internally hydraulically automatically compensated split hydrostatic rotor according to claim 1, characterized in that, A through hole is provided on the outer side of the housing. The through hole is used as a convection exchange port or a rotational speed sensor access port.

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