CN107701241B - Nozzle flow regulator for turbine expander - Google Patents
Nozzle flow regulator for turbine expander Download PDFInfo
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- CN107701241B CN107701241B CN201711096876.0A CN201711096876A CN107701241B CN 107701241 B CN107701241 B CN 107701241B CN 201711096876 A CN201711096876 A CN 201711096876A CN 107701241 B CN107701241 B CN 107701241B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
- F01D9/045—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector for radial flow machines or engines
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
- Supercharger (AREA)
Abstract
The utility model provides a turboexpander's nozzle flow adjusting device, turboexpander includes expansion end ring flange and nozzle apron, and nozzle apron is fixed with the insulating disc of expansion end ring flange one side, and nozzle flow adjusting device includes moving, quiet ring, nozzle, pressure disk and moving ring drive adjusting device, and the moving ring is established at the insulating disc intracavity, and quiet ring is established in the moving ring, and the nozzle is connected between moving, quiet ring, and the pressure disk is established on the nozzle apron, and moving ring drive adjusting device is established on the insulating disc, characteristics: the surface of the movable ring facing the side of the pressure plate is lower than the surface of the stationary ring facing the side of the pressure plate; the nozzle movable ring adjusting connecting pin shaft and the nozzle stationary ring hinging pin shaft are retracted to the surface of the nozzle facing one side of the pressure plate; the two sides of the inner wall of the movable ring are respectively provided with a movable ring arc chamfer, the two sides of the outer wall of the stationary ring are respectively provided with a stationary ring arc chamfer, and the area between the movable ring arc chamfers and the stationary ring arc chamfers is formed into a movable stationary ring anti-blocking cavity. The nozzle is protected, and the rotation resistance of the movable ring is reduced; the friction resistance of the nozzle is reduced; the phenomenon of blocking of the moving and static rings is avoided.
Description
Technical Field
The application belongs to the technical field of low-temperature equipment, and particularly relates to a nozzle flow regulating device of a turbine expander.
Background
As known in the art, the expansion machines can be divided into two types, one type is a piston expansion machine and the other type is the turbine expansion machine. Compared with a piston expander, the turbine expander has the characteristics of large flow, small volume, high efficiency, long operation period and the like, and is widely applied to various low-temperature equipment.
Further, as is known in the art, turboexpanders are machines that transfer energy, also known as external work, from the change in velocity energy as the gas expands, typically through a main shaft coupled to an impeller, to mating devices or equipment that absorb energy, such as generators, blowers, pumps, superchargers, oil brakes, and the like.
Technical information about turboexpanders is not lacking in the published chinese patent literature, and "a gas bearing turboexpander" is cited as an example of CN2388351Y (micro turboexpander), CN2185339Y (gas suspension ceramic low temperature turboexpander), CN200955408Y (turboexpander), CN201367920Y (turboexpander), CN201190583Y (a compound turboexpander), CN201326419Y (turboexpander), and CN202039906U, and the like.
When the turbo expander works, dry compressed air enters from a working volute through a nozzle and pushes a working wheel blade, so that a working wheel (also called an impeller) moves, a working wheel shaft (also called a pull rod shaft) rotates at a high speed, the working wheel shaft is connected with a main shaft (also called an output transition shaft), so that the main shaft is driven by the working wheel shaft, a main shaft pinion on the main shaft drives an output shaft through an output shaft big gear arranged on the output shaft, and the output shaft drives a generator, a blower, a water pump, a booster or an oil brake and the like connected with the output shaft.
As known in the art, the current common starting mode of the expander is to set a pressurizing end at the inlet, drive the expander to rotate by using an air guide mode, start the expander when the pressurizing end is boosted to a rated required value, and then rapidly start the nozzle to make the expander rapidly and stably pass the critical rotation speed. If the air guide is too fast, namely in an overpressure starting state, the pressure of the inlet of the pressurizing end of the expander is higher, so that the pressure difference of the pressurizing end of the expander is too large and the air flow speed is too fast, and parts of the expander are damaged; on the contrary, if the air guide is too slow, namely in the under-voltage starting state, the inertia of the rotor of the expander is too large, so that the expander cannot normally operate.
From the above description, in combination with common general knowledge: the turboexpander has a nozzle flow regulator, wherein the moving ring and the stationary ring are key components of the structural system of the nozzle flow regulator. The nozzle flow rate adjusting device of the turbine expander in the prior art can meet the adjusting requirement of the nozzle flow rate, but has the following defects: firstly, because the surface of the moving ring arranged outside the stationary ring towards one side of the nozzle is flush with the surface of the stationary ring arranged on one side of the stationary ring towards the nozzle, and a plurality of nozzles are connected to the moving ring in an adjustable mode at intervals around the circumferential direction of the moving ring and are also connected with the stationary ring, specifically, one end of the nozzle towards the moving ring is connected with the moving ring in an adjustable mode, and one end of the nozzle towards the stationary ring is hinged with the stationary ring, when the moving ring rotates, the surface of the nozzle and the surface of the moving ring can generate severe friction, so that the nozzle is easy to damage, the nozzle is increased, the rotating resistance of the moving ring is increased, and the energy consumption for driving the moving ring to rotate is not beneficial; secondly, as the tail end of the nozzle static ring hinge pin shaft which is used for hinging the nozzle and the static ring extends out of one side surface of the nozzle back to the static ring, and as the tail end of the nozzle dynamic ring adjusting connecting pin shaft which is used for adjusting and connecting the nozzle and the dynamic ring extends out of one side surface of the nozzle back to the dynamic ring, the friction resistance between the nozzle and a pressure plate (also called as a supporting plate) is large in the process of changing the flow rate when the dynamic ring rotates to drive the nozzle to perform angle adjustment, the energy consumption of the power for driving the dynamic ring to rotate is also not facilitated, and the motion stability of the nozzle in the adjusting process is also affected; third, because the cross-section shape of moving ring, quiet ring is the rectangle, specifically, the quiet ring is towards one side surface of moving ring and the moving ring towards one side surface of quiet ring each other contact or call whole cooperation, however, moving, quiet ring is limited on the expansion end flange through the aforesaid pressure disk, therefore when the expansion end flange appears the deformation condition, easily lead actuation, quiet ring each other card and die, do not have to realize the adjustment to the nozzle.
In view of the foregoing, improvements are necessary, and for this purpose the inventors have devised advantageous designs that result in the solutions described below, and that have proven to be viable by computer simulation deduction tests with security measures.
Disclosure of Invention
The application aims to provide a nozzle flow regulating device of a turbine expander, which is beneficial to avoiding friction between a nozzle and the surface of a movable ring to protect the nozzle, reducing the rotation resistance of the movable ring to save the electric energy consumption of a power device for driving the movable ring to move, being beneficial to obviously reducing the friction resistance between the nozzle and a pressure plate to ensure the movement stability of the nozzle in the regulating process, and being convenient to prevent the movable ring and a static ring from being blocked when an expansion end flange is deformed to ensure the required regulation of the nozzle.
The object of the application is achieved by a nozzle flow control device for a turboexpander, comprising an expansion end flange and a nozzle cover plate, an insulating disk being fastened to the expansion end flange on the side facing the nozzle cover plate, an insulating disk chamber being formed in the central region of the insulating disk on the side facing the nozzle cover plate, the nozzle cover plate being fastened to the insulating disk, the nozzle flow control device comprising a moving disk, a stationary ring, nozzles, a pressure disk and a moving ring drive control device, the moving disk being arranged in the insulating disk chamber, the stationary ring being fastened in a concentric circle with the moving disk and the stationary ring outer wall of the stationary ring being in contact with the inner wall of the moving ring, the nozzles being arranged in a plurality of nozzles being fastened between the moving ring and the stationary ring in a spaced-apart manner on the side facing the insulating disk, the moving disk being fastened to the moving ring via the insulating disk and the moving ring drive control device being in a sequential manner to the moving disk and the moving ring drive control device being fastened to the moving disk via the moving disk and the moving disk drive control device, the moving disk being fastened to the moving disk in a spaced-apart manner on the moving ring in a pin-apart manner on the side facing the moving ring and being fastened to the moving ring in a pin-apart manner around the moving ring, the moving disk being fastened to the moving ring being fastened to the moving disk, characterized in that the surface of the side of the movable ring facing the pressure plate is lower than the surface of the side of the stationary ring facing the pressure plate; the nozzle movable ring adjusting connecting pin shaft and the nozzle stationary ring hinging pin shaft are retracted to the surface of one side of the nozzle facing the pressure plate; two sides of the inner wall of the moving ring are respectively provided with a moving ring arc chamfer, two sides of the outer wall of the stationary ring are respectively provided with a stationary ring arc chamfer, and the area between the moving ring arc chamfer and the stationary ring arc chamfer is formed into a moving stationary ring anti-blocking cavity.
In a specific embodiment of the application, a limit block accommodating cavity is formed in the heat insulation disc cavity of the heat insulation disc, a limit block is fixed in the limit block accommodating cavity, a limit block penetrating groove is formed in the outer wall of the moving ring, and the limit block penetrates into the limit block penetrating groove.
In another specific embodiment of the present application, an eccentric disc cavity and a pull rod groove are formed on one side of the heat insulation disc facing the nozzle cover plate, an eccentric disc shaft hole is formed at the bottom of the cavity of the eccentric disc cavity, the pull rod groove is communicated with the eccentric disc cavity, the moving ring driving adjusting device connected with the moving ring is matched with the eccentric disc cavity and the pull rod groove at the same time, and the moving ring driving adjusting device is connected with the power mechanism in a transmission way after extending to one side of the expansion end flange plate facing away from the nozzle cover plate through the eccentric disc shaft hole.
In another specific embodiment of the present application, a pull rod connecting pin hole is formed on the moving ring, the moving ring driving adjustment device includes an eccentric disc shaft and a pull rod, an eccentric disc is formed at one end of the eccentric disc shaft facing the moving ring, the eccentric disc shaft extends to the power mechanism after reaching the side of the expansion end flange opposite to the nozzle cover plate at the position corresponding to the eccentric disc shaft hole, the eccentric disc is matched with the eccentric disc cavity, the pull rod is matched with the pull rod groove, one end of the pull rod facing the eccentric disc is connected with the pull rod pin hole formed on the eccentric disc through a pull rod pin shaft, a pull rod moving ring connecting pin shaft is fixed at one end of the pull rod facing the moving ring, and the pull rod moving ring connecting pin shaft is connected with the moving ring at the position corresponding to the pull rod connecting pin hole.
In still another specific embodiment of the present application, a nozzle adjusting groove is formed at an end of the nozzle facing the moving ring, a nozzle hinge hole is formed at an end of the nozzle facing the stationary ring, the nozzle moving ring adjusting connection pin shaft extends into the nozzle adjusting groove, and the nozzle stationary ring hinge pin shaft is hinged with the nozzle hinge hole.
In still another specific embodiment of the present application, the shape of the limiting block is a convex shape of a chinese character.
In a further specific embodiment of the present application, the nozzle-adjusting groove has an elliptical shape.
In a further specific embodiment of the application, a pressure plate cavity is formed on the side of the nozzle cover plate facing the expansion end flange plate, the pressure plate is arranged in the pressure plate cavity, and the pressure plate contacts with the nozzle on the side surface facing the nozzle.
In a further specific embodiment of the application, spring holes are formed in the bottom wall of the pressure plate chamber and are spaced apart around the circumference of the bottom wall of the pressure plate chamber at positions corresponding to the pressure plate, springs are arranged in the spring holes, and are in contact with one side of the pressure plate facing the pressure plate chamber, wherein pressure plate guide pins are fixed on the nozzle cover plate and at positions corresponding to between every two adjacent springs, pressure plate guide pin holes are formed on the pressure plate and at positions corresponding to the pressure plate guide pins, and the pressure plate guide pins are matched with the pressure plate guide pin holes.
In a further specific embodiment of the application, a nozzle cover plate holder is formed on the outer wall of the nozzle cover plate and at intervals around the circumferential direction of the nozzle cover plate, holder screws are arranged on the nozzle cover plate holder, and holder screw holes are arranged in the heat-insulating disk cavity at intervals around the circumferential direction of the heat-insulating disk cavity and at positions corresponding to the holder screws, and the holder screws are fixed with the holder screw holes.
According to one of the technical effects provided by the technical scheme, as the surface of the movable ring facing the pressure plate is designed to be lower than the surface of the stationary ring facing the pressure plate, the thickness of the movable ring is thinner than that of the stationary ring, so that friction between the nozzle and the surface of the movable ring can be avoided when the movable ring drives the nozzle, the nozzle can be protected, the rotation resistance of the movable ring can be reduced, and the power consumption of a power mechanism for driving the movable ring to drive the movable ring to work can be reduced, so that energy conservation is realized; secondly, the nozzle movable ring adjusting connecting pin shaft and the nozzle static ring hinging pin shaft are designed to retract on the surface of one side of the nozzle facing the pressure plate, so that the friction resistance of the nozzle during adjustment can be obviously reduced, and the motion stability of the nozzle during adjustment can be ensured; and the two sides of the inner wall of the moving ring are respectively provided with a moving ring arc chamfer, and the two sides of the outer wall of the static ring are respectively provided with a static ring arc chamfer, and the area between the moving ring arc chamfer and the static ring arc chamfer is formed into a moving ring anti-blocking cavity, so that the phenomenon that the moving ring and the static ring are blocked possibly can be effectively avoided when the expansion end flange plate deforms.
Drawings
Fig. 1 is a structural diagram of an embodiment of the present application.
Fig. 2 is a detailed structural view of the connection of the nozzle of fig. 1 with the moving ring and the stationary ring.
Fig. 3 is a schematic view of a circular arc chamfer of a moving ring and a circular arc chamfer of a stationary ring respectively formed on the moving and stationary rings shown in fig. 1 and 2.
Fig. 4 is a schematic diagram of an application of the present application.
Fig. 5 is a cross-sectional view of fig. 4.
Detailed Description
In order to make the technical spirit and advantages of the present application more clearly understood, the applicant will now make a detailed description by way of example, but the description of the examples is not intended to limit the scope of the application, and any equivalent transformation made merely in form, not essentially, according to the inventive concept should be regarded as the scope of the technical solution of the present application.
In the following description, any reference to the directional or azimuthal sense of up, down, left, right, front and rear is not to be construed as a specific limitation on the solution provided by the present application, since the directional or azimuthal sense is defined with respect to the illustrated position.
Referring to fig. 1 and 3, there are shown an expansion end flange 1 and a nozzle cover plate 2 of a structural system of a turboexpander, a heat insulating plate 3 is fixed to a side of the expansion end flange 1 facing the nozzle cover plate 2 by heat insulating plate fixing screws 34, a heat insulating plate cavity 31 is formed in a central region of a side (i.e., right side) of the heat insulating plate 3 facing the nozzle cover plate 2, and the nozzle cover plate 2 is fixed to the heat insulating plate 3.
The moving ring 4, the stationary ring 5, the nozzles 6, the pressure plate 7 and the moving ring driving adjustment device 8 showing the structural system of the nozzle flow adjustment device of the present application, the moving ring 4 is disposed in the aforesaid insulating disk cavity 31, the stationary ring 5 is fixed with the aforesaid moving ring 4 by the stationary ring fixing screw 54 in the moving ring 4 in a state of forming concentric circles with the moving ring 4, and the stationary ring outer wall 51 of the stationary ring 5 is in contact with the moving ring inner wall 41 of the moving ring 4, the plurality of nozzles 6 are connected between the moving ring 4 and the stationary ring 5 in a state of spacing on the side corresponding to the pressure plate 7 facing the aforesaid insulating disk 3, i.e. the right side corresponding to the pressure plate 7, the pressure plate 7 is disposed on the aforesaid nozzle cover plate 2, the moving ring driving adjustment device 8 is disposed on the aforesaid insulating disk 3, the moving ring driving adjustment device 8 is connected with the aforesaid moving ring 4, and the moving ring driving adjustment device 8 is also in turn via the insulating disk 3 and the expansion end flange 1 to be in driving connection with the power mechanism. Wherein, on the side of the aforementioned moving ring 4 facing the aforementioned pressure plate 7 and around the circumferential direction of the moving ring 4 at a position corresponding to the aforementioned nozzle 6, nozzle moving ring adjustment connection pins 42 are fixed, and on the side of the aforementioned stationary ring 5 facing the pressure plate 7 and around the circumferential direction of the stationary ring 5 also at a position corresponding to the nozzle 6, nozzle stationary ring hinge pins 52 are fixed, nozzle 6 is movably sleeved on the nozzle moving ring adjustment connection pins 42 toward one end of the moving ring 4, and one end of the nozzle 6 facing the stationary ring 5 is hinged with the nozzle stationary ring hinge pins 52.
The technical key points of the technical scheme provided by the application are as follows: the surface of the side of the movable ring 4 facing the pressure plate 7 is lower than the surface of the side of the stationary ring 5 facing the pressure plate 7, that is, the left side surface of the movable ring 4 is lower than the left side surface of the stationary ring 5, and the right side surfaces of the movable and stationary rings 4, 5 are flush with each other; the nozzle movable ring adjusting connecting pin 42 and the nozzle stationary ring hinge pin 52 are retracted on the surface of the nozzle 6 facing the platen 7, i.e., on the left surface of the nozzle 6; as shown in fig. 3, a circular arc chamfer 43 is formed on both sides of the inner wall 41 of the moving ring 4, a circular arc chamfer 53 is formed on both sides of the outer wall 51 of the stationary ring 5, and a region between the circular arc chamfer 43 and the circular arc chamfer 53 is formed as a moving-stationary ring anti-seize chamber 9. Because the expansion end flange plate 1 does not have deformation, the expansion end flange plate and the heat insulation plate 3 generate corresponding deformation when the expansion end flange plate is deformed, so that the heat insulation plate 3 is guided to actuate, the static rings 4 and 5 are mutually clamped (mutually clamped), and the deformation is retracted by the dynamic and static ring anti-clamping cavity 9 under the existence of the dynamic and static ring anti-clamping cavity 9, so that the moving ring 4 is ensured to move.
With continued reference to fig. 1, a stopper accommodating cavity 311 is formed in the heat insulating disc cavity 31 of the heat insulating disc 3, a stopper 3111 is fixed to the stopper accommodating cavity 311 by a pair of stopper screws 31111 at a position corresponding to a pair of stopper screw holes 3112 preset in the stopper accommodating cavity 311, a stopper penetrating groove 441 is formed in the outer wall 44 of the moving ring 4, and the stopper 3111 is penetrated into the stopper penetrating groove 441.
An eccentric disc cavity 32 and a pull rod groove 33 are arranged on one side of the heat insulation disc 3 facing the nozzle cover plate 2, namely, on the left side of the heat insulation disc 3, an eccentric disc shaft hole 321 is arranged at the bottom of the cavity of the eccentric disc cavity 32, the pull rod groove 33 is communicated with the eccentric disc cavity 32, the movable ring driving adjusting device 8 connected with the movable ring 4 is matched with the eccentric disc cavity 32 and the pull rod groove 33 at the same time, and the movable ring driving adjusting device 8 extends to one side of the expansion end flange plate 1 facing away from the nozzle cover plate 2 through the eccentric disc shaft hole 321 and is in transmission connection with the power mechanism.
With continued reference to fig. 1, a tie rod connecting pin shaft hole 45 is formed in the moving ring 4, the moving ring driving adjustment device 8 includes an eccentric disc shaft 81 and a tie rod 82, an eccentric disc 811 is formed at one end of the eccentric disc shaft 81 facing the moving ring 4, i.e., the left end of the eccentric disc shaft 81, and the end of the eccentric disc shaft 81 facing the heat insulation disc 3, i.e., the right end of the eccentric disc shaft 81, extends to the side of the expansion end flange 1 facing away from the nozzle cover plate 2, i.e., to the right side of the expansion end flange 1, and is connected to the power mechanism, and the eccentric disc 811 is engaged with the eccentric disc cavity 32, the tie rod 82 is engaged with the tie rod groove 33, the end of the tie rod 82 facing the eccentric disc 811 is connected to a tie rod pin shaft hole 8111 formed in the eccentric disc 811, and the end of the tie rod 82 facing the moving ring 4 is fixed with a tie rod moving ring connecting pin 822, which is connected to the moving ring 4 at a position corresponding to the connecting pin shaft hole 45.
Referring to fig. 2 in combination with fig. 1, a nozzle adjusting slot 61 is formed at an end of the nozzle 6 facing the moving ring 4, a nozzle hinge hole 62 is formed at an end of the nozzle 6 facing the stationary ring 5, the nozzle moving ring adjusting pin 42 is inserted into the nozzle adjusting slot 61, and the nozzle stationary ring hinge pin 52 is hinged with the nozzle hinge hole 62. As shown in fig. 1 and 2, the nozzles 6 are substantially 6-shaped, and the space between each two adjacent nozzles 6 is configured as a jet slot 63, specifically, the size of the space (also referred to as distance) between each two adjacent nozzles 6 toward one end of the stationary ring 5 determines the size of the nozzle flow rate.
As shown in fig. 1, the shape of the limiting block 3111 is a convex shape of a chinese character; the nozzle adjustment groove 61 has an elliptical shape.
With continued reference to fig. 1, a platen chamber 21 is formed on the side of the nozzle cover plate 2 facing the expansion end flange 1, the platen 7 is disposed in the platen chamber 21, and a side surface of the platen 7 facing the nozzle 6 is in contact with the nozzle 6.
Spring holes 211 are formed in the platen chamber bottom wall of the platen chamber 21 at intervals around the circumferential direction of the platen chamber bottom wall at positions corresponding to the platen 7, springs 2111 are provided in the spring holes 211, the springs 2111 are in contact with the side of the platen 7 facing the platen chamber 21, wherein platen guide pins 23 are fixed to the nozzle cover plate 2 at positions corresponding to between every two adjacent springs 2111, platen guide pin holes 71 are formed in the platen 7 at positions corresponding to the platen guide pins 23, and the platen guide pins 23 are engaged with the platen guide pin holes 71. As can be seen, the platen 7 is provided in the platen chamber 21 in a floating manner, and a gap between the right side of the platen 7 and the nozzle cover plate 2 is configured as an air intake groove 72 (indicated in fig. 4).
As shown in fig. 1, the nozzle cover plate holders 22 are formed on the outer wall of the nozzle cover plate 2 at intervals around the circumferential direction of the nozzle cover plate 2, holder screws 221 are provided on the nozzle cover plate holders 22, holder screw holes 312 are provided in the heat insulating disk chamber 31 at intervals around the circumferential direction of the heat insulating disk chamber 31 at positions corresponding to the holder screws 221, and the holder screws 221 are fixed to the holder screw holes 312.
Also shown in FIG. 1 is an eccentric disc shaft seat 812 for rotatably supporting the eccentric disc shaft 81, the eccentric disc shaft seat 812 being fixed to the right side of the expansion end flange 1 with eccentric disc shaft seat screws 8121 at a position corresponding to the aforementioned eccentric disc shaft hole 321, and an eccentric disc shaft seat heat-insulating jacket 8122 being provided on the eccentric disc shaft seat 812 the aforementioned eccentric disc shaft 81 is rotatably supported on the eccentric disc shaft seat 812 at a position corresponding to the eccentric disc shaft hole 8123 of the eccentric disc shaft seat 812, and the right end of the eccentric disc shaft 81 extends to the right side of the eccentric disc shaft seat 812.
Referring to fig. 4 and 5 in conjunction with fig. 1, an impeller 10 and an impeller intake 101 belonging to the structural system of a turboexpander are shown in fig. 4 and 5. In fig. 5, there are shown a scroll 20 and an expander compression end 30 belonging to the structural system of a turbo expander, a turbo expander body 40 is provided between the aforementioned expansion end flange 1 and the expander compression end 30 as the structural system of the expansion end, the scroll 20 is fixed to the aforementioned expansion end flange 1, the scroll 20 has a high pressure gas inlet 201 and a low pressure gas outlet 202, and high pressure gas enters a high pressure gas chamber 203 of the scroll 20 from the high pressure gas inlet 201, passes through a gas outlet 2011 and a gas injection groove 63 between each two adjacent nozzles 6, and further enters a low pressure gas chamber 203 of the scroll 20 through an impeller gas flow groove of the impeller 10 and is led out from the low pressure gas outlet 202.
Since the function and principle of nozzle flow regulation is known in the art, applicant will only briefly describe the following. When the nozzle flow is to be regulated, the eccentric disc shaft 81 of the structural system of the power drive regulating device 8 is driven by the power mechanism which is repeatedly mentioned above, the eccentric disc 811 is driven by the eccentric disc shaft 81, and since the pull rod 82 is connected with the moving ring 4 through the pull rod moving ring connecting pin 822, the angle required by the rotating process of the moving ring 4 is driven by the pull rod moving ring connecting pin 822 of the pull rod 82, and the nozzle flow is regulated by the nozzle moving ring regulating connecting pin 42 on the moving ring 4 at the position corresponding to the nozzle regulating groove 61. The eccentric disc shaft 81 is driven to rotate in the forward and reverse directions by the forward and reverse rotation working state of the power mechanism, so that the moving ring 4 rotates in the forward and reverse directions, and the size of the nozzle flow is adjusted.
In summary, the technical scheme provided by the application overcomes the defects in the prior art, successfully completes the task of the application, and faithfully honors the technical effects carried by the applicant in the technical effect column above.
Claims (10)
1. A nozzle flow regulating device of a turboexpander, the turboexpander comprises an expansion end flange plate (1) and a nozzle cover plate (2), an insulating disc (3) is fixed on one side of the expansion end flange plate (1) facing the nozzle cover plate (2), an insulating disc cavity (31) is formed in the central area of one side of the insulating disc (3) facing the nozzle cover plate (2), the nozzle cover plate (2) is fixed with the insulating disc (3), the nozzle flow regulating device comprises a movable disc (4), a static ring (5), a nozzle (6), a pressure disc (7) and a movable disc drive regulating device (8), the movable disc (4) is arranged in the insulating disc cavity (31), the static ring (5) is fixed in the movable disc (4) in a state of forming concentric circles with the movable disc (4), the static ring outer wall (51) of the static ring (5) is contacted with the movable disc inner wall (41) of the movable disc (4), a plurality of the nozzles (6) are connected with the movable disc (3) at intervals on one side corresponding to the pressure disc (3) facing the movable disc, the movable disc (7) is arranged between the movable disc (3) and the movable disc (8), the movable ring drive adjusting device (8) is connected with the movable ring (4), and the movable ring drive adjusting device (8) is further connected with a power mechanism in a transmission way through the heat insulation disc (3) and the expansion end flange disc (1), wherein a nozzle movable ring adjusting connecting pin shaft (42) is fixed at intervals around the circumferential direction of the movable ring (4) at the position corresponding to the nozzle (6) on one side of the movable ring (4) facing the pressure disc (7), a nozzle stationary ring hinging pin shaft (52) is fixed at intervals around the circumferential direction of the stationary ring (5) at the position corresponding to the nozzle (6), one end of the nozzle (6) facing the movable ring (4) is movably sleeved on the nozzle movable ring adjusting connecting pin shaft (42), and one end of the nozzle (6) facing the stationary ring (5) is hinged with the nozzle stationary ring hinging pin shaft (52), and the surface of the side of the movable ring (4) facing the pressure disc (7) is lower than the surface of the side of the stationary ring (5) facing the pressure disc (7); the nozzle movable ring adjusting connecting pin shaft (42) and the nozzle static ring hinging pin shaft (52) are retracted into the surface of one side of the nozzle (6) facing the pressure plate (7); a movable ring circular arc chamfer (43) is formed on two sides of a movable ring inner wall (41) of the movable ring (4), a stationary ring circular arc chamfer (53) is formed on two sides of a stationary ring outer wall (51) of the stationary ring (5), and a region between the movable ring circular arc chamfer (43) and the stationary ring circular arc chamfer (53) is formed as a movable stationary ring anti-locking cavity (9).
2. The nozzle flow regulator of the turboexpander according to claim 1, characterized in that a stopper accommodating cavity (311) is formed in a heat insulating disc cavity (31) of the heat insulating disc (3), a stopper (3111) is fixed in the stopper accommodating cavity (311), a stopper penetrating groove (441) is formed in an outer wall (44) of the moving ring (4), and the stopper (3111) penetrates into the stopper penetrating groove (441).
3. The nozzle flow regulator of the turboexpander according to claim 1, characterized in that an eccentric disc cavity (32) and a pull rod groove (33) are formed on one side of the heat insulation disc (3) facing the nozzle cover plate (2), an eccentric disc shaft hole (321) is formed at the bottom of the eccentric disc cavity (32), the pull rod groove (33) is communicated with the eccentric disc cavity (32), the moving ring driving regulator (8) connected with the moving ring (4) is matched with the eccentric disc cavity (32) and the pull rod groove (33) at the same time, and the moving ring driving regulator (8) is connected with the power mechanism in a transmission way after being extended to one side of the expansion end flange plate (1) facing away from the nozzle cover plate (2) through the eccentric disc shaft hole (321).
4. A nozzle flow regulator of a turboexpander according to claim 3, characterized in that a tie rod connecting pin hole (45) is formed in the moving ring (4), the moving ring driving regulator (8) includes an eccentric disc shaft (81) and a tie rod (82), an eccentric disc (811) is formed at one end of the eccentric disc shaft (81) facing the moving ring (4), the end of the eccentric disc shaft (81) facing the insulating disc (3) is extended to the power mechanism after the expansion end flange (1) faces away from the nozzle cover plate (2) at a position corresponding to the position of the eccentric disc hole (321), the eccentric disc (811) is matched with the eccentric disc cavity (32), the tie rod (82) is matched with the tie rod groove (33), one end of the tie rod (82) facing the eccentric disc (811) is connected with the tie rod pin hole (8111) formed on the eccentric disc (811) through the tie rod pin shaft (821), and one end of the tie rod (82) facing the moving ring (4) is fixedly connected with the moving ring (4) at a position corresponding to the tie rod pin hole (822).
5. The nozzle flow regulator of the turboexpander according to claim 1, wherein a nozzle adjusting groove (61) is formed at an end of the nozzle (6) facing the moving ring (4), a nozzle hinge hole (62) is formed at an end of the nozzle (6) facing the stationary ring (5), the nozzle moving ring adjusting connecting pin (42) is inserted into the nozzle adjusting groove (61), and the nozzle stationary ring hinge pin (52) is hinged with the nozzle hinge hole (62).
6. The nozzle flow regulator of the turbo expander according to claim 2, wherein the stopper (3111) has a shape of a Chinese character's convex shape.
7. The nozzle flow regulator of the turboexpander according to claim 5, wherein the nozzle regulating groove (61) has an elliptical shape.
8. A nozzle flow regulator of a turboexpander according to claim 1, characterized in that a pressure plate chamber (21) is formed on the side of the nozzle cover plate (2) facing the expansion end flange (1), the pressure plate (7) is disposed in the pressure plate chamber (21), and a side surface of the pressure plate (7) facing the nozzle (6) is in contact with the nozzle (6).
9. The nozzle flow regulator of the turboexpander according to claim 8, characterized in that spring holes (211) are provided on a platen chamber bottom wall of the platen chamber (21) and at positions corresponding to the platen (7) in a spaced state around a circumferential direction of the platen chamber bottom wall, springs (2111) are provided in the spring holes (211), the springs (2111) are in contact with a side of the platen (7) facing the platen chamber (21), wherein platen guide pins (23) are fixed on the nozzle cover plate (2) and at positions corresponding to between each two adjacent springs (2111), platen guide pin holes (71) are provided on the platen (7) and at positions corresponding to the platen guide pins (23), and the platen guide pins (23) are fitted with the platen guide pin holes (71).
10. The nozzle flow rate adjustment device of a turboexpander according to claim 1, characterized in that a nozzle cover plate fixing seat (22) is formed on an outer wall of the nozzle cover plate (2) and around a circumferential direction of the nozzle cover plate (2) in a spaced state, a fixing seat screw (221) is provided on the nozzle cover plate fixing seat (22), a fixing seat screw hole (312) is provided in the heat insulation disc chamber (31) around the circumferential direction of the heat insulation disc chamber (31) and at a position corresponding to the fixing seat screw (221) in a spaced manner, and the fixing seat screw (221) is fixed with the fixing seat screw hole (312).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711096876.0A CN107701241B (en) | 2017-11-09 | 2017-11-09 | Nozzle flow regulator for turbine expander |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711096876.0A CN107701241B (en) | 2017-11-09 | 2017-11-09 | Nozzle flow regulator for turbine expander |
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| CN107701241A CN107701241A (en) | 2018-02-16 |
| CN107701241B true CN107701241B (en) | 2023-08-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711096876.0A Active CN107701241B (en) | 2017-11-09 | 2017-11-09 | Nozzle flow regulator for turbine expander |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN116291761B (en) * | 2023-03-18 | 2024-01-30 | 东台宏仁气体有限公司 | Nozzle structure of expander |
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| CN107701241A (en) | 2018-02-16 |
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