Self-driven energy recovery device with internal hydraulic automatic compensation split type static pressure rotor

Abstract

The invention belongs to the technical field of energy recovery equipment, and provides a self-driven energy recovery device with an internal hydraulic automatic compensation split type static pressure rotor, an exchanger is mounted in a shell, a rotor cylinder of the exchanger is rotatably sleeved on the outer side of a dynamic and static pressure shaft, and two flow distribution end covers are fixedly mounted at the upper end and the lower end of the dynamic and static pressure shaft respectively; the rotor cylinder is divided into an upper single rotor cylinder and a lower single rotor cylinder, the two single rotor cylinders are connected through a connector, a first static pressure pool and a damping groove are formed in the outer end face of each single rotor cylinder, and a stepped structure is arranged at the opening position of an axial flow channel in the outer end face of each single rotor cylinder. The connector comprises a connecting step and guide plates connected to the two ends of the connecting step. The inner wall of the flow channel of the flow distribution end cover is provided with a thin-wall small hole flow channel communicated with the dynamic and static pressure shaft. By adopting the combination of the double rotor cylinders, the automatic compensation of the clearance can be realized under the condition of pressure change or abrasion, the efficiency is improved, the service life is prolonged, and the reliability of a product is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of energy recovery devices, and particularly relates to a self-driven energy recovery device with an internal hydraulic automatic compensation split static pressure rotor, which can efficiently recover the pressure energy in high-pressure fluids and transfer it to low-pressure fluids, 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 fluids 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 economic efficiency and sustainability of industrial processes.

[0003] Currently, the energy recovery devices existing on the market mainly include the following types: (1) Turbine-type energy recovery devices: Turbine-type devices convert the pressure energy of high-pressure fluids into mechanical energy and then drive high-pressure pumps through couplings. However, the energy recovery efficiency of this type of device is usually low (about 60% - 80%), and it has a complex structure and high maintenance costs.

[0004] (2) Isobaric pressure exchangers: Pressure exchangers are one of the most widely used energy recovery devices at present. They achieve energy recovery by directly exchanging pressure between high-pressure fluids and low-pressure fluids. Although their energy recovery efficiency is relatively high (up to more than 90%), the existing pressure exchangers generally have the following problems: Fluid mixing problem: Cross-contamination may occur between high-pressure fluids and low-pressure fluids, especially in working conditions that require strict fluid separation, and this problem is particularly prominent.

[0005] Unstable operation: In working conditions with large flow fluctuations or pressure changes, the existing devices are difficult to maintain a stable operating state.

[0006] Limited application range: The existing devices have poor adaptability to high-viscosity or solid-particle-containing fluids.

[0007] Traditional isobaric exchangers often integrate the flow distribution structure with the water inlet and outlet 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.

[0008] (3) Plunger-type energy recovery devices: The plunger 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.

[0009] 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

[0010] 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-type hydrostatic rotor.

[0011] To solve the above technical problems, the present invention provides the following technical solutions: A self-driven energy recovery device with an internally hydraulically automatically compensated split-type hydrostatic 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; The exchanger includes a first distribution end cover, a static and dynamic shaft, a rotor cylinder, and a second distribution end cover. The rotor cylinder is rotatably sleeved outside the static and dynamic shaft. A number of axially distributed annular and equally spaced axial flow channels are provided inside the rotor cylinder. The cross-section of the axial 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 static and dynamic shaft. The first distribution end cover, the static and dynamic shaft, and the second 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 corresponding axial 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 hydrostatic 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 axial 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 axial flow channel where the single rotor cylinder is connected to the connector; Thin-walled small hole flow channels communicating with the static and dynamic shaft are provided on the inner walls of the flow channels of the first distribution end cover and the second distribution end cover.

[0012] Furthermore, first positioning holes are formed on one side of the first and second flow distribution end caps opposite to the dynamic and static pressure shafts. 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 formed at both ends of the dynamic and static pressure shafts. A positioning pin is inserted through the connection position of each group of connected first and second positioning holes, and a thin-wall damping hole is formed in the middle of the positioning pin.

[0013] Furthermore, a plurality of zigzag grooves are circumferentially and equidistantly distributed on the outer surface of the dynamic and static pressure shafts. Second static pressure pools are formed at both ends of the dynamic and static pressure shafts, and a stepped shaft is formed at the outer end of the second static pressure pool.

[0014] Furthermore, a longitudinal flow dividing plate or a cross-shaped flow dividing plate is fixed in the middle of the connector.

[0015] Furthermore, an end face inclined groove is formed at the edge position of the outer end face of the single-rotor cylinder.

[0016] Furthermore, two positioning support rings are fixed outside the fastening bolts, and positioning grooves matched with the positioning support rings are formed at the connection positions of the upper end cover, the lower end cover and the dynamic and static pressure shafts.

[0017] Furthermore, both the fastening bolts and the positioning support rings are made of super duplex stainless steel or nickel-based alloy.

[0018] Furthermore, hydraulic driving slopes are formed at the flow distribution ports of the first and second flow distribution end caps. Two balance anti-friction grooves are formed on the end faces of the first and second flow distribution end caps opposite to the dynamic and static pressure shafts, and a low-pressure balance static pressure pocket is formed on the outer end faces of the first and second flow distribution end caps.

[0019] Furthermore, a balance groove sealing O-ring is installed in the low-pressure balance static pressure pocket, and a static seal O-ring is installed outside the first and second flow distribution end caps.

[0020] Furthermore, a through hole is formed on the outer side face of the housing, and the through hole is used as a convection exchange port or a rotational speed sensor access port.

[0021] Combined with the above technical solutions, the beneficial effects of the present invention compared with the prior art are as follows: In the present invention, a pair of balanced forces are formed by the pressure from the first static pressure pool at the end face of the rotor cylinder towards the center and the thrust formed by the cross-sectional difference of the internal flow channels. 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 flow distribution end cap can be kept constant, and automatic compensation can be realized under the conditions of pressure change or wear, realizing the function of self-adapting the gap between the rotor cylinder and the flow distribution end cap.

[0022] By adopting a variable cross-section design for the flow channel in the rotor cylinder, the present invention can better reduce 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 channel. The cross-section of the flow channel in the rotor cylinder gradually increases from small to large at the high-pressure fluid inlet. Since the high-pressure fluid has a high viscosity and density here, the pressure loss can be reduced. The cross-section of the flow channel in the rotor cylinder gradually decreases from large to small at the high-pressure fluid outlet, forming a small backpressure, which can reduce turbulence and noise, thereby achieving a lower mixing degree.

[0023] Through the first static pressure pool and the thin-wall small-hole flow channel, the present invention can reduce turbulence during the high-low pressure exchange, reduce noise, and reduce the mixing degree.

[0024] The present invention assembles and connects the rotor cylinders by using a connector. Since the cross-section of the internal flow channel of the connector is smaller than that of the internal flow channel of the rotor cylinder, the internal flow channel of the connector has a certain damping characteristic, which can better form a hydraulic interface barrier, reduce the mixing degree, and the presence of the connector can well cope with thermal expansion.

[0025] In the case of lubrication failure and wear of the dynamic and static shaft sleeves, 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 sleeves caused by system water shortage, the failure of the thin-wall damping holes, etc., the housing itself can continue to support the rotation of the rotor as a bearing, improving the reliability of the entire product. The present invention adopts the form of a double-rotor cylinder combination, which can compensate for manufacturing errors and wear compensation in the length direction, can achieve 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 of extremely high length tolerance requirements, greatly reducing the processing and use costs, while improving the reliability of the product. The dynamic and static shaft sleeves can enable the product to work in the pressure range of 5 - 120 barg, with a noise lower than 78 decibels and a 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 arbitrarily 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

[0026] The drawings are used to provide a further understanding of the present invention and constitute a part of the specification. They are used to explain the present invention together with the embodiments of the present invention and do not constitute a limitation to the present invention. In the drawings: Figure 1 It is a schematic structural diagram of a self-driven energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor provided by an embodiment of the present invention; Figure 2It is a sectional view of the self-driving energy recovery device with an internal hydraulic automatic compensation split-type hydrostatic rotor provided by an embodiment of the present invention; Figure 3 It is a schematic structural diagram of the exchanger provided by an embodiment of the present invention; Figure 4 It is the present invention Figure 3 A partial enlarged schematic diagram at position A in; Figure 5 It is a schematic structural diagram of the rotor cylinder provided by an embodiment of the present invention; Figure 6 It is a schematic structural diagram of a single rotor cylinder provided by an embodiment of the present invention, where (a) and (b) are schematic structural diagrams of the single rotor cylinder from different perspectives respectively; Figure 7 It is a schematic structural diagram of the connector provided by an embodiment of the present invention; Figure 8 It is a schematic structural diagram of two different forms of connectors provided by an embodiment of the present invention; Figure 9 It is a schematic structural diagram of the static and dynamic shaft presses provided by an embodiment of the present invention; Figure 10 It is a schematic structural diagram of the positioning pin provided by an embodiment of the present invention; Figure 11 It is a schematic structural diagram of the fastening bolt provided by an embodiment of the present invention; Figure 12 It is a schematic structural diagram of the first flow distribution end cover provided by an embodiment of the present invention, where (a) and (b) are schematic structural diagrams of the first flow distribution end cover from different perspectives respectively; Figure 13 It is a schematic structural diagram of the housing provided by an embodiment of the present invention.

[0027] 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-wall 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-wall damping hole; 6.8.2. Positioning pin face. Detailed implementation mode

[0028] The following is a description of the preferred embodiments of the present invention with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are only for the purpose of illustrating and explaining the present invention, and are not used to limit the present invention.

[0029] As Figure 1 and Figure 2 shown, it is an embodiment of a self-driving energy recovery device with an internal hydraulic automatic compensation split-type static pressure rotor provided by the present invention, including 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, and 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.

[0030] 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 flow channels are arranged inside the rotor cylinder 6.6 at equal intervals. The cross-section of the axially distributed flow channels 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-wall small hole flow channels 6.11 communicating with the dynamic and static pressure shaft 6.5 are respectively arranged 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.

[0031] 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.

[0032] As Figure 5 shown, the rotor cylinder 6.6 in the embodiment of the present invention is divided into two single-rotor cylinders 6.6.1 up and down. The axial flow channels corresponding to the two single-rotor cylinders 6.6.1 are connected through a connector 6.6.2, and the two single-rotor cylinders 6.6.1 can perform relative displacement in the axial direction.

[0033] 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-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. For the combined structure of the present invention, there is no need to consider the tolerance in the length direction at all, which greatly reduces the manufacturing cost.

[0034] Since the rotor cylinder 6.6 of the present invention is formed by connecting two single-rotor cylinders 6.6.1 through a connector 6.6.2, the difficulty of internal long-hole processing 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 clearance between the two single-rotor cylinders 6.6.1 can be 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, etc.

[0035] 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-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-rotor cylinder 6.6.1. As

[0036] In the rotor cylinder 6.6 of the present invention, by adopting the design of an end face inclined groove 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.

[0037] 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 a tiny stepped structure 6.6.1.4 is adopted for the inner hole. The stepped structure 6.6.1.4 enables a certain tension to be generated axially between the two single-body rotor cylinders 6.6.1, pushing themselves towards the direction of 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-body 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.

[0038] 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-body rotor cylinder 6.6.1.

[0039] 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. Under the condition of ensuring sufficient strength, it ensures a certain elasticity and toughness and its self-lubricity, ensuring the relative sliding between the rotor cylinder and itself.

[0040] 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, making the internal flow channel of the connector 6.6.2 have 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, reducing the turbulence of the fluid and lowering the mixing degree, and the mixing degree can be controlled below 2%.

[0041] As Figure 8 shown, a longitudinal flow splitter or a cross-shaped flow splitter 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 splitter, the effect of reducing the mixed flow can be improved without causing too much influence on the fluid pressure.

[0042] 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.

[0043] 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 generated, both of which cause the pressure in the lubricating liquid to increase (the formation of dynamic pressure characteristics). Before the static pressure is fully established, good lubrication support characteristics of dynamic pressure are formed, so the 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.

[0044] 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.

[0045] 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.

[0046] 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 can reliably provide the strain stiffness for the rotor cylinder.

[0047] As Figure 11 shown, two positioning support rings 6.3 are fixed outside 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 shaft 6.5.

[0048] 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.

[0049] As Figure 12 shown, a hydraulic driving 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 shaft 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.

[0050] 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 driving ramp can be 8°, 10°, 13°, 15°, 19°, 23°, 25°, 27°, 30°, 31°, 32°, 33°, 34°, 35°, etc.

[0051] As Figure 3 and Figure 12 shown, a balance groove sealing 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 sealing O-rings 6.10 are installed outside the first flow distribution end cover 6.2 and the second flow distribution end cover 6.7.

[0052] As Figure 1 and Figure 13 shown, through holes 9 are provided on the outer side surface of the housing 8 in the embodiment of the present invention. The through holes 9 are used as convection exchange ports or rotational speed sensor access ports.

[0053] 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.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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 described in the foregoing embodiments or perform equivalent replacements for some of the technical features. Any modification, equivalent replacement, improvement, 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 internal hydraulic automatic compensation 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, 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, characterized in that: An exchanger is installed inside the shell; The exchanger includes a first flow distribution end cover, a dynamic and static pressure shaft, a rotor cylinder and a second flow distribution end cover, the rotor cylinder can be rotatably sleeved on the outside of the dynamic and static pressure shaft, a plurality of annular equidistantly distributed axial flow channels are opened on the inner side of the rotor cylinder, the first flow distribution end cover and the second flow distribution end cover are respectively fixedly mounted on the upper and lower ends of the dynamic and static pressure shaft, and the first flow distribution end cover, the dynamic and static pressure shaft and the second flow distribution end cover are sequentially connected through the middle fastening bolts; The rotor cylinder is divided into two upper and lower single rotor cylinders, the corresponding axial flow passages of the two single rotor cylinders are connected by a connector, and the two single rotor cylinders can be relatively displaced in the axial direction, a first static pressure pool and a damping groove are provided at the middle through hole position of the outer end surface of the single rotor cylinder, and a stepped structure is provided at the axial flow passage opening position of the outer end surface of the single rotor cylinder; The connector includes a connecting step and guide plates connected to both ends of the connecting step, and an installation step groove matching the connecting step is provided at the opening position of the axial flow passage where the single rotor cylinder is connected to the connector; The inner walls of the flow channels of the first distribution end cover and the second distribution end cover are respectively provided with thin-walled small hole flow channels connected with the dynamic and static pressure shafts.

2. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: The first distribution end cover and the second distribution end cover are both provided with a first positioning hole on the side opposite to the dynamic and static pressure shafts, the inner end of the first positioning hole is connected with a thin-walled small hole flow channel, and the two ends of the dynamic and static pressure shafts are respectively provided with second positioning holes axially aligned with the first positioning holes, and the connecting position of each group of connected first positioning holes and second positioning holes is penetrated by a positioning pin, and a thin-walled damping hole is provided in the middle of the positioning pin.

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

4. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: A longitudinal splitter plate or a cross-shaped splitter plate is fixed in the middle of the connector.

5. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: An end face inclined groove is provided at the edge of the outer end face of the single rotor cylinder.

6. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: Two positioning support rings are fixed on the outer side of the fastening bolts, and the connection positions of the upper end cover, the lower end cover and the dynamic and static pressure shafts are all provided with positioning grooves that cooperate with the positioning support rings.

7. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 6, characterized in that: The fastening bolts and the positioning support ring are both made of super duplex steel or nickel-based alloy.

8. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: The distribution ports of the first distribution end cover and the second distribution end cover are both provided with a hydraulically driven slope, the end faces of the first distribution end cover and the second distribution end cover opposite to the dynamic and static pressure shafts are provided with two balancing and anti-friction grooves, and the outer end faces of the first distribution end cover and the second distribution end cover are provided with a low-pressure balancing static pressure bag.

9. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 8, characterized in that: A balancing groove sealing O-ring is installed in the low-pressure balancing static pressure bag, and static sealing O-rings are installed on the outer sides of the first distribution end cover and the second distribution end cover.

10. The self-driven energy recovery device with internal hydraulic automatic compensation split hydrostatic rotor according to claim 1, characterized in that: A through hole is provided on the outer side of the shell, and the through hole is used as a convection exchange port or a rotation speed sensor access port.

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