Horizontal mid-surface-free working medium self-recovery organic working medium turbine

Abstract

The application discloses a kind of self-recovery organic working medium turbines without horizontal middle surface working medium, including no horizontal middle surface cylinder, whole circle baffle group, rotating part;Rotating part is decomposed into three parts along the axial direction;Whole circle baffle group is decomposed into a plurality of interval settings whole circle baffle along the axial direction;Whole circle baffle and the three parts are alternately assembled in no horizontal middle surface cylinder with vertical installation mode, and the three parts are connected into a whole after alternately assembling;Rotating part is provided with sealing arm and sealing shoulder to form balance chamber, and adopts balance pipe to set chamber pressure;Rotating part is connected mechanical seal at the shaft extension of no horizontal middle surface cylinder;Mechanical seal uses cold isolating liquid to flush dynamic ring friction pair and simultaneously uses cold isolating liquid to spray gas-liquid mixing chamber to realize cooling, and the isolating liquid of mechanical seal leaks into balance chamber by centrifugal booster ring on rotating part and is separated and recovered in gas-liquid header.The application effectively realizes the zero leakage and self-recovery of organic working medium.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of turbine structure, and particularly relates to a self-recovery organic working medium turbine without horizontal middle surface. BACKGROUND

[0002] The organic Rankine cycle (ORC) power generation technology is mainly applied to binary geothermal power generation, low-temperature waste heat power generation and small and medium-sized gas turbine combined cycle distributed energy. The basic process flow of the organic Rankine cycle (ORC) power generation system is shown in FIG. 1. The heat of geothermal brine, low-pressure steam, waste flue gas and the like is used to transfer heat to an evaporator to evaporate liquid organic working medium (such as freon or isopentane) supplied by a working medium pump into a gaseous state, and the working medium is used to drive a turbine expander to work and drive a generator to generate electricity. The exhausted gas after power generation is discharged into a condenser to condense into a liquid state, and the whole power cycle is completed. The mechanical seal is located at the shaft end of the turbine expander. In order to ensure that the mechanical seal has zero leakage to the outside, the separated and filtered working medium is also discharged into the condenser. Figure 1

[0003] The organic working medium turbine is the core equipment of the organic Rankine cycle (ORC) power generation system, adopts alkanes such as isopentane and n-pentane as working medium, and is flammable and explosive, so it is not allowed to leak to the outside. The mechanical seal is widely used as the shaft end seal of the organic working medium turbine. The sealing design of the cylinder body and the working medium recovery of the shaft end seal are key technical problems for ensuring that the organic working medium turbine has zero leakage to the outside.

[0004] The conventional steam turbine has a horizontal middle surface and a vertical middle surface, and a cross joint exists between the horizontal middle surface and the vertical middle surface, as shown in FIG. 2. Since the perfect contact at the cross joint cannot be ensured, leakage cannot be avoided. When water vapor is used as the working medium, the leakage to the outside will not cause the risk of explosion and environmental pollution, but it is not allowed for flammable and explosive or toxic organic working medium. Figure 2

[0005] The mechanical seal of the organic working medium turbine is a whole circle rather than an upper and lower half structure, and can only be connected to the cylinder through a vertical flange. If the cylinder structure with a horizontal middle surface is used, a cross joint will be formed between the vertical installation flange face of the mechanical seal and the horizontal middle surface of the cylinder, which will cause the leakage of the organic working medium to the outside. Therefore, the cylinder structure with a horizontal middle surface cannot be used for the organic working medium turbine. In addition, since the sealed medium pressure of the exhaust side mechanical seal is the exhaust pressure, which is equal to the pressure of the lowest point (the condenser) of the organic Rankine cycle (ORC) power generation system, the pressure difference cannot be used as a power source to realize the automatic separation and recovery of the working medium.

[0006] In order to solve the above technical problems, a cylinder without a horizontal middle surface is first used to avoid the cross joint between the vertical installation flange face of the mechanical seal and the horizontal middle surface of the cylinder. However, the assembly of the rotating part and the stator part caused by the absence of the horizontal middle surface becomes a technical difficulty. ​​

[0007] Secondly, due to the difficulty in installing the thrust balance components such as the balanced piston in the cylinder without horizontal middle surface, the thrust balance of the rotating component also becomes a technical difficulty.

[0008] Finally, in order to avoid the leakage of the working medium, the working pressure of the isolation liquid of the double-end-face isolation type mechanical seal is higher than that of the sealed medium, the isolation liquid leaks and mixes with the organic working medium, and the mixture needs to be prevented from entering the power generation system to affect the safety and operating efficiency of the unit, so the separation and recovery of the organic working medium and the isolation liquid become a technical difficulty that must be solved. SUMMARY

[0009] The present application aims at the deficiencies of the prior art, and provides a working medium self-recovery organic working medium turbine without horizontal middle surface, which adopts a cylinder without horizontal middle surface and a segmented joint rotating component, effectively avoids the external leakage at the cross joint between the vertical mounting flange surface of the mechanical seal and the horizontal middle surface of the cylinder, constructs a balance chamber, effectively realizes the thrust balance of the rotating component, adopts a centrifugal booster ring to pressurize the organic working medium to the gas-liquid mixing chamber to prevent the isolation liquid from entering the balance chamber, adopts cold isolation liquid flushing to reduce the temperature of the dynamic and static ring friction pair of the mechanical seal, and simultaneously adopts cold isolation liquid spraying to reduce the temperature of the gas-liquid mixing chamber, thereby effectively realizing the cooling of the mechanical seal, and adopts a gas-liquid header to separate and recover the working medium, thereby effectively realizing the self-recovery function of the organic working medium.

[0010] The technical purpose of the present application is realized by the following technical scheme:

[0011] A working medium self-recovery organic working medium turbine without horizontal middle surface comprises a cylinder without horizontal middle surface, a whole-circle partition group, a rotating component, a balance pipe, a mechanical seal, a centrifugal booster ring and a gas-liquid header. The rotating component is divided into a front main shaft provided with a first-stage impeller, an impeller group and a rear main shaft provided with a last-stage impeller along the axial direction. The whole-circle partition group is divided into a plurality of whole-circle partitions arranged at intervals along the axial direction. The whole-circle partitions and the three parts of the rotating component are alternately assembled in the cylinder without horizontal middle surface in a vertical mounting manner, and the three parts are connected into a whole after being alternately assembled. The rotating component is provided with a sealing arm and a sealing shoulder to form a balance chamber, and the balance pipe is used to set the chamber pressure. The rotating component is connected with the double-end-face isolation type mechanical seal at the shaft extension of the cylinder without horizontal middle surface. The mechanical seal uses cold isolation liquid to flush the dynamic and static ring friction pair and simultaneously uses cold isolation liquid to spray the gas-liquid mixing chamber to realize cooling. The leakage of the isolation liquid of the mechanical seal to the balance chamber is isolated by the centrifugal booster ring on the rotating component and separated and recovered in the gas-liquid header.

[0012] Further, the whole-circle partitions and the cylinder without horizontal middle surface are connected by bolts. The parts of the rotating component are positioned by end face teeth and connected into a whole by a pull rod and a nut assembly.

[0013] Furthermore, the balance pipe connects the balance chamber to a chamber after an intermediate stage of the impeller assembly; the axial leakage of the balance chamber is isolated by a mechanical seal; sealing shoulders are provided between the impellers of the rotating component and filled with sealing rings to achieve sealing between the first-stage impeller and the last-stage impeller; the first-stage impeller and the last-stage impeller are respectively provided with sealing arms, and the organic working fluid after the first-stage full-circle baffle leaks into the balance chamber through the sealing arm of the first-stage impeller and then leaks into the exhaust through the sealing arm of the last-stage impeller; each impeller of the rotating component is provided with a balance hole of appropriate size to limit the flow rate of the organic working fluid, so as to make the pressure in all parts of the balance chamber tend to be uniform.

[0014] Furthermore, the mechanical seal is a double-end-face isolation type, and uses turbine oil with a pressure 0.2 MPa to 0.3 MPa higher than that of the organic working fluid in the balance chamber as the isolation fluid to prevent the organic working fluid from leaking outward along the mechanical seal; a centrifugal pressurizing ring is provided on the rotating component to prevent the isolation fluid from entering the balance chamber; a gas-liquid mixing chamber is provided between the mechanical seal and the centrifugal pressurizing ring; the centrifugal pressurizing ring pressurizes the organic working fluid to the gas-liquid mixing chamber to prevent the isolation fluid from entering the balance chamber; the cooling Z-shaped ring and the mechanical seal housing form an annular chamber, and the cooling Z-shaped ring has several cooling nozzles arranged in the circumferential direction. The cold isolation fluid is injected into the gas-liquid mixing chamber through the cooling pipe and the cooling nozzles of the cooling Z-shaped ring. The temperature of the gas-liquid mixing chamber is limited to below 80°C by controlling the opening of the cooling regulating valve by a temperature measuring element provided in the gas-liquid mixing chamber; at the same time, the friction pair of the moving and stationary rings is flushed by introducing cold isolation fluid into the flushing pipe to remove frictional heat.

[0015] Furthermore, the gas-liquid mixing chamber and the gas-liquid header are connected by a connecting pipe; one end of the connecting pipe is connected to the gas-liquid recovery port of the mechanical seal housing, and the other end is connected to the hydrocyclone separator; the top of the gas-liquid header is connected to the balance chamber by a working fluid recovery pipe, and the bottom of the hydrocyclone separator is connected to a drain pipe and equipped with a liquid level regulating valve; the gas-liquid header is equipped with a liquid level gauge; the isolation fluid leaking from the mechanical seal, the cooling isolation fluid, and the gaseous organic working fluid pressurized by the centrifugal booster ring are mixed in the gas-liquid mixing chamber and then enter the hydrocyclone separator in the gas-liquid header through the gas-liquid recovery port for separation. The separated organic working fluid is recovered by the working fluid recovery pipe into the balance chamber under the action of pressure difference, and the separated isolation fluid accumulates at the bottom of the gas-liquid header and the liquid level of the gas-liquid header is controlled by the liquid level regulating valve to realize the recovery of the isolation fluid.

[0016] Compared with the prior art, the beneficial effects of the present invention are:

[0017] 1. This invention employs a cylinder without a horizontal split surface and rotating components with segmented joints, which effectively avoids external leakage caused by the cross joint between the vertical mounting flange surface of the mechanical seal and the horizontal split surface of the cylinder while realizing the assembly function, thus achieving the requirement of zero external leakage of alkane-based combustible organic working fluids.

[0018] 2. This invention employs a balance pipe to connect the balance chamber to a chamber after an intermediate stage of the impeller assembly; axial leakage from the balance chamber is isolated by a mechanical seal; sealing shoulders are provided between the impellers of the rotating components and filled with sealing rings to achieve sealing between the first-stage and last-stage impellers; the first-stage and last-stage impellers are each equipped with sealing arms, and the organic working fluid after the first-stage baffle leaks into the balance chamber through the first-stage impeller sealing arm and then leaks into the exhaust chamber through the last-stage impeller sealing arm; balancing holes of appropriate size are provided on each impeller of the rotating components to limit the flow rate of the organic working fluid, so as to achieve uniform pressure throughout the balance chamber. By adopting this technical measure, the mechanical seals on both sides of the balance chamber and the impeller disc portion of the thrust are self-balanced, and the thrust of the only blade portion on the rotating components is balanced by the thrust bearing, effectively achieving thrust balance of the rotating components.

[0019] 3. This invention employs a centrifugal pressurizing ring to pressurize the organic working fluid into the gas-liquid mixing chamber to prevent the isolation fluid from entering the balance chamber. The cold isolation fluid is injected into the gas-liquid mixing chamber through cooling pipes and cooling nozzles of the cooling Z-shaped ring. The temperature of the gas-liquid mixing chamber is limited to below 80°C by controlling the opening of the cooling regulating valve through a temperature sensing element installed in the gas-liquid mixing chamber. At the same time, the friction pair of the moving and stationary rings is flushed by introducing cold isolation fluid into the flushing pipe to remove frictional heat, thereby effectively cooling the mechanical seal.

[0020] 4. This invention employs a gas-liquid manifold for the separation and recovery of the working fluid. The isolation liquid and the gaseous organic working fluid, pressurized by a centrifugal booster ring, are separated in a hydrocyclone separator within the gas-liquid manifold. Under the action of pressure difference, the organic working fluid is self-recovered and enters the equilibrium chamber. The isolation liquid accumulates at the bottom of the gas-liquid manifold, and the liquid level in the gas-liquid manifold is controlled by a liquid level regulating valve to achieve the recovery of the isolation liquid, thereby effectively realizing the self-recovery function of the organic working fluid. Attached Figure Description

[0021] Figure 1 It is the existing Organic Rankine Cycle (ORC) power generation process;

[0022] Figure 2 This is a schematic diagram of the cross joint between the horizontal and vertical split surfaces of a conventional steam turbine.

[0023] Figure 3 This is a schematic diagram of the structure of the present invention;

[0024] Figure 4 yes Figure 3Detailed connection diagram of the central balance pipe;

[0025] Figure 5 These are schematic diagrams of (a) pressure distribution with a balanced chamber and (b) pressure distribution without a balanced chamber;

[0026] Figure 6 This is a schematic diagram of mechanical seal cooling and working fluid separation and recovery;

[0027] Figure 7 yes Figure 3 A schematic diagram of the mechanical seal and gas-liquid mixing chamber in which a cold insulating fluid is introduced;

[0028] Figure 8 This is a schematic diagram of the structure of the gas-liquid mixing chamber and the balance chamber in conjunction with the gas-liquid header;

[0029] Reference numerals: 1—rotating component, 1a—front main shaft, 1a1—first stage impeller, 1b—rear main shaft, 1b1—last stage impeller, 1c—impeller assembly, 1c1—second stage impeller, 1c2—third stage impeller, 1d—tie rod and nut assembly, 1e—sealing arm, 1e1—first stage impeller sealing arm, 1e2—last stage impeller sealing arm, 1f—sealing shoulder, 1g—end face teeth, 1h—centrifugal booster ring, 1j—thrust disc, 1k—balance hole;

[0030] 2—Stator component, 2a—Cylinder without horizontal center split surface, 2b—Full ring baffle assembly, 2b1—First stage full ring baffle, 2b2—Second stage full ring baffle, 2b3—Third stage full ring baffle, 2b4—Last stage full ring baffle, 2c—Balance tube, 2d—Support bearing, 2e—Thrust bearing;

[0031] 3—Mechanical seal; 3a—Dynamic ring; 3b—Static ring; 3c—Temperature sensing element; 3d—Flushing pipe; 3d1—Flushing regulating valve; 3e—Cooling pipe; 3e1—Cooling regulating valve; 3f—Cooling Z-ring; 3g—Cooling nozzle; 3h—Mechanical seal housing; 3j—Annular chamber; 3k—Mechanical seal isolation fluid flushing chamber; 3m—Gas-liquid recovery hole;

[0032] 4—Gas-liquid header, 4a—Swirl separator, 4b—Level gauge, 4c—Working fluid recovery pipe, 4d—Drain pipe, 4d1—Level regulating valve, 4e—Connecting pipe;

[0033] 5—Balance chamber;

[0034] 6—Gas-liquid mixing chamber.

[0035] A—Inlet oil port, B—Return oil port, C—Separator fluid recovery port. Detailed Implementation

[0036] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0037] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0038] It should be noted that similar reference numerals and letters in the following figures indicate similar items; therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures. Furthermore, the terms "first," "second," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0039] It should be noted that, without loss of generality, the accompanying drawings only show a schematic diagram of a 4-stage flow structure. Depending on different inlet and outlet parameters, a 5-stage or more flow structure can be selected. It should not be construed as this embodiment being used only for a 4-stage flow structure. All other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0040] It should be noted that this paper uses a double subscript method to express thermodynamic parameters, which is a common method in the field of turbine technology for expressing internal thermodynamic parameters of a flow path. The symbol T represents temperature, and the symbol P represents pressure. The first subscript indicates the thermodynamic stage; a first-stage baffle and a first-stage impeller constitute a thermodynamic stage. The second subscript indicates the specific location of the thermodynamic parameter within the stage (0 for before stage, 1 for between stages, 2 for after stage). For example: T11 represents the interstage temperature of the first stage, T21 represents the interstage temperature of the second stage; P11 represents the interstage pressure of the first stage, P12 represents the afterstage pressure of the first stage; P21 represents the interstage pressure of the second stage, and P22 represents the afterstage pressure of the second stage. The external thermodynamic parameters of the flow path are: Pin and Tin are the turbine inlet pressure and temperature, determined by the evaporator; Pout and Tout are the turbine exhaust pressure and temperature, determined by the condenser.

[0041] like Figures 3 to 8As shown, a self-recovering organic working fluid turbine without a horizontal split surface includes a cylinder 2a without a horizontal split surface, a full-circle baffle assembly 2b, a rotating component 1, a balance pipe 2c, a mechanical seal 3, a centrifugal booster ring 1h, and a gas-liquid header 4. The rotating component 1 is axially divided into three parts: a front main shaft 1a with a first-stage impeller 1a1, an impeller assembly 1c, and a rear main shaft 1b with a final-stage impeller 1b1. The full-circle baffle assembly 2b is axially divided into multiple spaced full-circle baffles. The three parts of the rotating component 1 are connected into a whole after alternating assembly. The rotating component 1 is equipped with a sealing arm 1e and a sealing... Shoulder 1f forms a balance chamber 5, and a balance pipe 2c is used to set the chamber pressure. The rotating component 1 is connected to a double-end-face isolation mechanical seal 3 at the shaft extension of the cylinder 2a without a horizontal split surface. The mechanical seal 3 flushes the dynamic and static ring friction pairs by introducing cold isolation liquid through the flushing pipe 3d to remove frictional heat, and at the same time, cold isolation liquid is sprayed to reduce the temperature of the gas-liquid mixing chamber 6. The leakage of the isolation liquid in the gas-liquid mixing chamber 6 to the balance chamber 5 is isolated by the centrifugal pressure ring 1h on the rotating component 1 and gas-liquid separation is carried out in the gas-liquid header 4, effectively achieving zero leakage and self-recovery of the organic working fluid. By using the cylinder 2a without a horizontal split surface and the segmented rotating component 1, the assembly function is realized while effectively avoiding external leakage caused by the cross joint between the vertical mounting flange face of the mechanical seal and the horizontal split surface of the cylinder, thus achieving the requirement of zero external leakage of alkane-based combustible organic working fluids.

[0042] In this embodiment, as Figure 3 As shown, the stator component 2 includes a cylinder 2a without a horizontal split surface, a full-circle baffle group 2b, a balance tube 2c, etc. The full-circle baffle group 2b is decomposed axially into four spaced full-circle baffles, specifically the first-stage full-circle baffle 2b1, the second-stage full-circle baffle 2b2, the third-stage full-circle baffle 2b3, and the last-stage full-circle baffle 2b4. The rotating component 1 is decomposed axially into three parts: a front main shaft 1a with a first-stage impeller 1a1, an impeller group 1c, and a rear main shaft 1b with a last-stage impeller 1b1; wherein, the impeller of the rotating component 1 includes a first-stage impeller 1a1, a second-stage impeller 1c1 of the impeller group 1c, a third-stage impeller 1c2 of the impeller group 1c, and a last-stage impeller 1b1 arranged axially.

[0043] The cylinder body of the cylinder 2a without a horizontal split surface is a cylindrical cylinder body. When assembling the rotating part 1 and the full-circle partition group 2b, the cylindrical cylinder body is rotated 90 degrees and the first full-circle partition 2b1 of the full-circle partition group 2b is installed first, so that the first full-circle partition 2b1 is fixed inside the cylinder 2a without a horizontal split surface. Then the front main shaft 1a is installed, so that the first impeller 1a1 on the front main shaft 1a is adjacent to the first full-circle partition 2b1 at intervals. Then the second full-circle partition 2b2, the second impeller 1c1, the third full-circle partition 2b3, the third impeller 1c2, the last full-circle partition 2b4 and the rear main shaft 1b are installed alternately in sequence.

[0044] In practical implementation, the entire ring partition is bolted to the cylinder 2a without a horizontal split surface; the various parts of the rotating component 1 are positioned by end face teeth 1g and connected as a whole by a tie rod and nut assembly 1d. In practical implementation, the first-stage entire ring partition 2b1, the second-stage entire ring partition 2b2, the third-stage entire ring partition 2b3, and the last-stage entire ring partition 2b4 of the entire ring partition 2b are bolted to the cylinder 2a without a horizontal split surface. The first-stage impeller 1a1 and the second-stage impeller 1c1 of the front main shaft 1a, the second-stage impeller 1c1 and the third-stage impeller 1c2 of the front main shaft 1a, and the third-stage impeller 1c2 and the last-stage impeller 1b1 of the rear main shaft 1b are respectively provided with end face teeth 1g for positioning.

[0045] like Figure 3 As shown, the first-stage impeller 1a1 of the front main shaft 1a, the impeller group 1c, and the last-stage impeller 1b1 of the rear main shaft 1b are respectively provided with tie rod holes. The various parts of the rotating component 1 are connected as a whole by tie rod and nut assembly 1d after being positioned by end face teeth 1g.

[0046] The combination of the above methods enables the assembly of the entire ring partition group 2b and the rotating component 1 in the cylinder 2a without a horizontal split surface. Since there is no intersection between the vertical flange and the horizontal flange, leakage at the cross joint connection between the vertical mounting flange face of the mechanical seal and the horizontal split surface of the cylinder is effectively avoided.

[0047] Furthermore, such as Figure 3 As shown, the rotating component 1 is radially supported and positioned by the support bearing 2d of the stator component 2; the rotating component 1 is equipped with a thrust disk 1j and is axially positioned by a thrust bearing 2e. In a specific implementation, the stator component 2 also includes two support bearings 2d, and the front main shaft 1a and rear main shaft 1b of the rotating component 1 are respectively provided with journals that cooperate with the support bearings 2d; the rotating component 1 is radially supported and positioned by the support bearings 2d. The thrust disk 1j is mounted on the front main shaft 1a of the rotating component 1, and correspondingly, the cylinder 2a without a horizontal split surface is equipped with a thrust bearing 2e that cooperates with the thrust disk 1j.

[0048] Furthermore, such as Figure 3 and Figure 4As shown, the balance pipe 2c connects the balance chamber 5 to a chamber after an intermediate stage of the impeller assembly 1c. In this embodiment, a balance chamber 5 is constructed to achieve thrust balance of the rotating component 1. The balance pipe 2c connects the balance chamber 5 to a chamber after the second-stage impeller 1c1 of the impeller assembly 1c. The pressure Pbc in the balance chamber 5 is equal to the pressure P22 in the chamber connected by the balance pipe 2c. The axial leakage of the organic working medium in the balance chamber 5 is isolated by the mechanical seal 3. A sealing shoulder 1f is provided between the impellers of the rotating component 1 and filled with a sealing ring to achieve sealing between the first-stage impeller 1a1 and the last-stage impeller 1b1. The first-stage impeller 1a1 and the last-stage impeller 1b1 are respectively provided with sealing arms 1e. The organic working medium (pressure P11) after the first-stage full-circle baffle 2b1 leaks into the balance chamber through the first-stage impeller sealing arm 1e1 and then leaks into the exhaust gas (pressure Pout) through the last-stage impeller sealing arm 1e2. A balance hole 1k of appropriate size is provided on each impeller of the rotating component 1 to limit the flow rate of the organic working medium so as to make the pressure in the balance chamber 5 tend to be consistent. Thus, the mechanical seal 3 on both sides of the balance chamber 5 and the impeller disk part thrust are self-balanced. The thrust of the only blade part on the rotating component 1 (the thrust generated by the reaction degree of the moving blade) is balanced by the thrust bearing, which effectively realizes the balance of the thrust of the rotating component 1.

[0049] In this embodiment, the rotating component 1 includes a sealing arm 1e and a sealing shoulder 1f. Specifically, the sealing arm 1e and the sealing shoulder 1f are clearance-fitted with the air seal inside the cylinder 2a without a horizontal split surface. The sealing arm 1e includes a first-stage impeller sealing arm 1e1 and a last-stage impeller sealing arm 1e2 respectively disposed on the first-stage impeller 1a1 of the front main shaft 1a and the last-stage impeller 1b1 of the rear main shaft 1b. The sealing shoulder 1f includes a first sealing shoulder and a second sealing shoulder respectively disposed on opposite sides of the first-stage impeller 1a1 and the second-stage impeller 1c1; a third sealing shoulder and a fourth sealing shoulder respectively disposed on opposite sides of the second-stage impeller 1c1 and the third-stage impeller 1c2; and a fifth sealing shoulder and a sixth sealing shoulder respectively disposed on opposite sides of the third-stage impeller 1c2 and the last-stage impeller 1b1 of the rear main shaft 1b. The first and second sealing shoulders abut against each other, the third and fourth sealing shoulders abut against each other, and the fifth and sixth sealing shoulders abut against each other. By setting the sealing arm 1e and the sealing shoulder 1f, a balanced chamber 5 is constructed between the horizontally split cylinder 2a, the rotating component 1, and the mechanical seal 3.

[0050] In this embodiment, the first sealing shoulder, the fourth sealing shoulder, and the fifth sealing shoulder are each provided with a sealing groove, and a sealing ring is filled in the sealing groove to achieve sealing between the first stage and the last stage impeller.

[0051] like Figure 3 and Figure 4As shown, each impeller of the rotating component 1 is provided with a balance hole 1k in the axial direction to limit the flow rate of the organic working fluid. This allows the pressure in all parts of the balance chamber 5 to become more uniform, thereby achieving self-balancing of the thrust of the mechanical seal 3 on both sides of the balance chamber 5 and the impeller disk portion. By uniformizing the pressure on both sides of the impeller disk through the balance hole 1k of the impeller disk portion, the thrust formed by the pressure difference on both sides of the impeller disk is eliminated, significantly reducing the total axial thrust value.

[0052] In this embodiment, as Figure 4 As shown, the first-stage impeller 1a1, the second-stage impeller 1c1, the third-stage impeller 1c2, and the last-stage impeller 1b1 of the rotating component 1 are respectively provided with coaxial balance holes 1k in the axial direction, which can make the pressure in all parts of the balance chamber 5 tend to be consistent.

[0053] like Figure 5 As shown in Figure (a), the design with the balancing chamber 5 eliminates the thrust caused by the pressure difference on both sides of the wheel because the pressure is the same on both sides, thus effectively achieving the balance of the thrust of the rotating components. Otherwise, as... Figure 5 As shown in Figure (b), the design without a balance chamber 5 results in a pressure difference on both sides of the impeller. Due to the large impeller diameter, a huge axial thrust will be generated, making it difficult to balance the thrust of the rotating components.

[0054] Furthermore, such as Figures 3 to 4 As shown, to isolate the external leakage of the organic working fluid, the rotating component 1 is connected to the mechanical seal 3 at the shaft extension of the cylinder 2a without horizontal split surface. The main functional components of the mechanical seal 3 are the rotating ring 3a connected to the rotating component 1 and the stationary ring 3b connected to the stator component 2. The mechanical seal 3 is a double-end face type and uses turbine oil with a pressure 0.2 MPa to 0.3 MPa higher than that of the organic working fluid in the balance chamber as the isolation fluid to prevent the organic working fluid from leaking outward along the mechanical seal 3. To prevent the isolation fluid from entering the balance chamber 5, a centrifugal booster ring 1h is provided on the rotating component 1. A gas-liquid mixing chamber 6 is provided between the mechanical seal 3 and the centrifugal booster ring 1h. The centrifugal booster ring 1h pressurizes the organic working fluid to the gas-liquid mixing chamber 6 to prevent the isolation fluid from entering the balance chamber.

[0055] Furthermore, the temperature of the heat source organic working fluid is between 100℃ and 300℃. The organic working fluid (temperature T11) after passing through the first-stage full-circle baffle 2b1 and leaking into the balance chamber 5 after being throttled by the first-stage impeller sealing arm 1e1, has a temperature of Tbc. See also Figure 4 Since the temperature remains basically constant during the throttling process, we have Tbc≈T11, 100℃≤Tbc≤300℃. If no cooling measures are taken for the gaseous organic working fluid in the balance chamber 5, the mechanical seal 3 will overheat and fail under high temperature conditions.

[0056] To solve the above technical problems, see [link to relevant documentation]. Figures 6 to 8By setting up a gas-liquid mixing chamber 6, the mechanical seal 3 is isolated from the balance chamber 5. First, by spraying a cooling isolation fluid and mixing it with the working gas from the balance chamber 5, the temperature of the gas-liquid mixing chamber 6 is reduced, thereby achieving the purpose of reducing the operating environment temperature of the mechanical seal 3. Second, a flushing isolation fluid is used to reduce the operating temperature of the friction surface of the mechanical seal sealing pair. Finally, the working gas from the balance chamber 5, the cooling isolation fluid from the sealing oil tank, and the isolation fluid leaking from the working side of the mechanical seal 3 are mixed in the gas-liquid mixing chamber 6 and then enter the gas-liquid manifold. The working gas separated in the gas-liquid manifold 4 returns to the balance chamber 5, and the separated isolation fluid returns to the sealing oil tank.

[0057] like Figure 7 As shown, the cold isolation liquid enters the annular chamber 3j formed by the cooling Z-shaped ring 3f and the mechanical seal housing 3h through the cooling pipe 3e. The cooling Z-shaped ring 3f has several cooling nozzles 3g arranged in the circumferential direction. The cold isolation liquid in the annular chamber 3j is injected into the gas-liquid mixing chamber 6 through the cooling nozzles 3g. The temperature of the gas-liquid mixing chamber 6 is limited to below 80°C by controlling the opening of the cooling regulating valve 3e1 by the temperature measuring element 3c set in the gas-liquid mixing chamber 6.

[0058] Furthermore, to prevent the cooling oil injected through the cooling nozzles 3g of the Z-shaped ring 3f from directly contacting the rotating component 1 and causing poor expansion and bending of the rotating component 1, the centrifugal booster ring 1h has a long hub section within the gas-liquid mixing chamber 6. This method avoids the influence of the uneven temperature field during the mixing process of the cold isolation fluid and the hot organic working fluid on the expansion of the rotating component. Furthermore, the cold isolation fluid enters the mechanical seal isolation fluid flushing chamber 3k through the flushing pipe 3d to flush the friction pair of the moving and stationary rings and remove frictional heat. The combination of these methods effectively achieves cooling of the mechanical seal.

[0059] In this embodiment, as Figure 7 As shown, the mechanical seal housing 3h is provided with a cold isolation fluid inlet for connecting the cooling pipe 3e and the flushing pipe 3d, corresponding to the annular chamber 3j and the mechanical seal isolation fluid flushing chamber 3k; the mechanical seal housing 3h is also provided with an isolation fluid outlet corresponding to the mechanical seal isolation fluid flushing chamber 3k. The liquid outlet ends of the cooling pipe 3e and the flushing pipe 3d are respectively connected to the annular chamber 3j and the mechanical seal isolation fluid flushing chamber 3k; the liquid inlet ends of the cooling pipe 3e and the flushing pipe 3d are connected to the oil supply port A of the sealing oil tank; the isolation fluid outlet of the mechanical seal isolation fluid flushing chamber 3k is connected to the oil return port B of the sealing oil tank; the cooling pipe 3e and the flushing pipe 3d are respectively provided with a cooling regulating valve 3e1 and a flushing regulating valve 3d1.

[0060] like Figure 8As shown, the gas-liquid mixing chamber 6 and the gas-liquid manifold 4 are connected by a connecting pipe 4e; one end of the connecting pipe 4e is connected to the gas-liquid recovery hole 3m of the mechanical seal housing 3h, and the other end is connected to the hydrocyclone separator 4a; the top of the gas-liquid manifold 4 is connected to the balance chamber 5 by a working fluid recovery pipe 4c, the bottom of the hydrocyclone separator 4a is connected to the drain pipe 4d, and a liquid level regulating valve 4d1 is provided; the gas-liquid manifold 4 is equipped with a liquid level gauge 4b; the isolation fluid leaking from the mechanical seal 3, the cooling isolation fluid, and the gaseous organic working fluid pressurized by the centrifugal pressurizing ring 1h are mixed in the gas-liquid mixture. After mixing in chamber 6, the mixture enters the hydrocyclone separator 4a in gas-liquid header 4 through gas-liquid recovery hole 3m for separation. Due to the pressurization effect of centrifugal pressurizing ring 1h, the pressure in gas-liquid mixing chamber 6 is higher than that in equilibrium chamber 5. Under the action of pressure difference, the separated organic working fluid is recovered by working fluid recovery pipe 4c and enters equilibrium chamber 5. The separated isolation liquid accumulates at the bottom of gas-liquid header 4 and the liquid level in gas-liquid header 4 is controlled by liquid level regulating valve 4d1 to realize the recovery of isolation liquid, thereby effectively realizing the self-recovery function of organic working fluid and the recovery function of isolation liquid.

[0061] like Figure 8 As shown, in actual use, one end of the drain pipe 4d is connected to the hydrocyclone separator 4a, and the other end is connected to the isolation fluid recovery port C of the sealing oil tank.

[0062] The technical solutions provided by the embodiments of the present invention have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of the embodiments of the present invention. The descriptions of the embodiments above are only for helping to understand the principles of the embodiments of the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the embodiments of the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A self-recovering organic working fluid turbine without horizontal splitting surface, characterized in that: It includes a cylinder without a horizontal split surface, a full-circle baffle assembly, a rotating component, a balance pipe, a mechanical seal, a centrifugal booster ring, and a gas-liquid manifold; the rotating component is axially divided into three parts: a front main shaft with a first-stage impeller, an impeller assembly, and a rear main shaft with a last-stage impeller; the full-circle baffle assembly is axially divided into multiple spaced full-circle baffles. The three parts of the full-circle partition and the rotating component are alternately assembled in a vertical installation manner in the cylinder without a horizontal center split surface, and the three parts are connected into a whole after the alternating assembly. The rotating component is equipped with sealing arms and sealing shoulders to form a balance chamber, and a balance pipe is used to set the chamber pressure. The balance pipe connects the balance chamber to a chamber after an intermediate stage of the impeller assembly. The axial leakage of the balance chamber to the outside is isolated by a mechanical seal. Sealing shoulders are provided between the impellers of the rotating component and filled with sealing rings to achieve sealing between the first-stage impeller and the last-stage impeller. The first-stage impeller and the last-stage impeller are respectively equipped with sealing arms. The organic working fluid after the first-stage full-circle baffle leaks into the balance chamber through the sealing arm of the first-stage impeller and then leaks into the exhaust through the sealing arm of the last-stage impeller. The rotating component has balance holes of appropriate size on each impeller to limit the flow rate of the organic working fluid, so as to make the pressure in the balance chamber tend to be uniform. The rotating component is connected to a double-end-face isolation mechanical seal at the shaft extension of the cylinder without a horizontal split surface; the mechanical seal uses cold isolation liquid to flush the dynamic and static ring friction pair and simultaneously uses cold isolation liquid to spray the gas-liquid mixing chamber for cooling; the leakage of the isolation liquid of the mechanical seal into the balance chamber is isolated by the centrifugal booster ring on the rotating component and separated and recovered in the gas-liquid header; The gas-liquid mixing chamber and the gas-liquid header are connected by a connecting pipe; one end of the connecting pipe is connected to the gas-liquid recovery port of the mechanical seal housing, and the other end is connected to the hydrocyclone separator; the top of the gas-liquid header is connected to the balance chamber by a working fluid recovery pipe, and the bottom of the hydrocyclone separator is connected to a drain pipe and is equipped with a liquid level regulating valve; the gas-liquid header is equipped with a liquid level gauge; the isolation fluid leaking from the mechanical seal, the cooling isolation fluid, and the gaseous organic working fluid pressurized by the centrifugal pressurizing ring are mixed in the gas-liquid mixing chamber and then enter the hydrocyclone separator in the gas-liquid header through the gas-liquid recovery port for separation. The separated organic working fluid is recovered by the working fluid recovery pipe into the balance chamber under the action of pressure difference. The separated isolation fluid accumulates at the bottom of the gas-liquid header and the liquid level of the gas-liquid header is controlled by the liquid level regulating valve to realize the recovery of the isolation fluid.

2. The self-recovering organic working fluid turbine without horizontal splitting surface as described in claim 1, characterized in that: The mechanical seal is a double-end isolation type, and uses turbine oil with a pressure 0.2 MPa to 0.3 MPa higher than that of the organic working fluid in the balance chamber as the isolation fluid to prevent the organic working fluid from leaking outward along the mechanical seal. A centrifugal pressurizing ring is provided on the rotating component to prevent the isolation fluid from entering the balance chamber. A gas-liquid mixing chamber is provided between the mechanical seal and the centrifugal pressurizing ring. The centrifugal pressurizing ring pressurizes the organic working fluid to the gas-liquid mixing chamber to prevent the isolation fluid from entering the balance chamber. The cooling Z-shaped ring and the mechanical seal housing form an annular chamber. The cooling Z-shaped ring has several cooling nozzles arranged in the circumferential direction. The cold isolation fluid is injected into the gas-liquid mixing chamber through the cooling pipe and the cooling nozzles of the cooling Z-shaped ring. The temperature of the gas-liquid mixing chamber is limited to below 80°C by controlling the opening of the cooling regulating valve by a temperature measuring element provided in the gas-liquid mixing chamber. At the same time, the friction pair of the moving and stationary rings is flushed by introducing cold isolation fluid into the flushing pipe to remove frictional heat.

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