阅读说明：本技术 一种高效有机工质膨胀机 (High-efficiency organic working medium expander ) 是由 郭擎 何嘉琪 邓浩 文鑫 于 2019-11-15 设计创作，主要内容包括：本发明公开了一种高效有机工质膨胀机,包括进气壳、排气壳和固定有涡轮的主轴,进气壳内设有喷嘴环座,喷嘴环座一侧与进气壳内壁围合成进气流道,喷嘴环座另一侧与排气壳外壳内壁、内壳外壁围合成排气流道,喷嘴环座上设有喷嘴环,喷嘴环和涡轮形成涡轮级流道,涡轮级流道输入端与进气流道连通,输出端与排气流道连通,进气壳上固定有轴承座,主轴一端通过第一轴承支撑,主轴另一端通过第二轴承支撑,进气流道采用对称式等环量,进气流道截面两侧对称布置,进气流道截面由进气法兰至进气法兰远端逐步减小,排气壳内壳直径D小于涡轮底径D1,使经过涡轮级流道的气体进入排气流道后不转向,沿排气壳法兰轴向排气。(The invention discloses a high-efficiency organic working medium expander, which comprises an air inlet shell, an air outlet shell and a main shaft fixed with a turbine, wherein a nozzle ring seat is arranged in the air inlet shell, one side of the nozzle ring seat and the inner wall of the air inlet shell enclose to form an air inlet flow passage, the other side of the nozzle ring seat and the inner wall of the air outlet shell and the outer wall of the inner shell enclose to form an air outlet flow passage, a nozzle ring is arranged on the nozzle ring seat, the nozzle ring and the turbine form a turbine stage flow passage, the input end of the turbine stage flow passage is communicated with the air inlet flow passage, the output end of the turbine stage flow passage is communicated with the air outlet flow passage, a bearing seat is fixed on the air inlet shell, one end of the main shaft is supported by a first bearing, the other end of the main shaft is supported by a second bearing, the air inlet flow passage adopts symmetrical equal annular flow, the two sides of the cross section of the, and exhausting gas along the axial direction of the exhaust shell flange.)

1. The utility model provides a high-efficient organic working medium expander, includes the air inlet shell, fixed mounting is in the air outlet shell on the air inlet shell and is fixed with the main shaft of turbine, its characterized in that: the exhaust shell is provided with an inner shell and an outer shell, a nozzle ring seat is arranged in the air inlet shell, one side of the nozzle ring seat and the inner wall of the air inlet shell enclose a gas inlet channel, the other side of the nozzle ring seat and the inner wall of the outer shell of the exhaust shell and the outer wall of the inner shell enclose a gas exhaust channel, a nozzle ring is arranged on the nozzle ring seat, the nozzle ring and a turbine form a turbine stage channel, the input end of the turbine stage channel is communicated with the gas inlet channel, the output end of the turbine stage channel is communicated with the gas exhaust channel, a bearing seat is fixed on the air inlet shell, one end of a main shaft is supported through a first bearing installed on the bearing seat, the other end of the main shaft is supported through a second bearing installed on the inner shell of the exhaust shell, the gas inlet channel adopts a symmetrical equal-ring flow channel, the sections of the gas inlet channel are symmetrically arranged along the left side, the gas passing through the turbine stage flow passage is directly exhausted along the axial direction of the exhaust shell flange without turning after entering the exhaust flow passage.

2. A high efficiency organic working medium expander as claimed in claim 1, wherein: the cross-sectional area of the air inlet flange at the maximum position of the cross section of the air inlet flow channel is S, the cross-sectional area of the far end of the air inlet flange at the minimum position is S1, and the cross-sectional area S1 at the minimum position is 0.15-0.2S.

3. A high efficiency organic working medium expander as claimed in claim 1 or 2, wherein: and a first mechanical seal and a second mechanical seal are arranged between the two ends of the turbine and the first bearing and between the two ends of the turbine and the second bearing respectively and are used for axially sealing the organic working medium.

4. A high efficiency organic working medium expander as claimed in claim 1, wherein: the turbine stage runner is a full-cycle air inlet type runner.

5. A high efficiency organic working medium expander as claimed in claim 1, wherein: the second bearing diameter is smaller than the first bearing diameter for reducing an exhaust case inner shell diameter D1.

6. A high efficiency organic working medium expander as claimed in claim 1, wherein: the inner shell of the exhaust shell is supported on the outer shell through a reinforcing rib.

7. A high efficiency organic working medium expander as claimed in claim 1, wherein: the turbine is an axial flow turbine.

Technical Field

The invention belongs to the technical field of expanders, and relates to a high-efficiency organic working medium expander.

Background

The organic working medium expander is a rotary power machine which converts the energy of the organic working medium into mechanical work and is mainly used for low-temperature heat recovery. The existing steam turbine uses steam as a working medium, the medium has a high boiling point and is liquid at normal temperature, low-temperature waste heat within 150 ℃ cannot be efficiently recovered, the existing organic working medium expander usually adopts a design method of the steam turbine, so that the air flow loss is large, the economical efficiency is poor, the purpose of fully utilizing the waste heat cannot be achieved, and the heat recovery efficiency is influenced. Therefore, how to manufacture the organic working medium expander with small air flow loss, improved waste heat utilization rate, ensured rotor stability and integral air tightness becomes the most needed problem at present.

Disclosure of Invention

The invention aims to overcome the defects of the prior art and provide a high-efficiency organic working medium expansion machine which can reduce the air flow loss and improve the waste heat utilization rate and the air tightness of the whole structure.

The purpose of the invention is realized as follows:

a high-efficiency organic working medium expander comprises an air inlet shell, an air outlet shell fixedly arranged on the air inlet shell and a main shaft fixed with a turbine, wherein the air outlet shell is provided with an inner shell and an outer shell, a nozzle ring seat is arranged in the air inlet shell, one side of the nozzle ring seat and the inner wall of the air inlet shell enclose a synthetic air inlet flow channel, the other side of the nozzle ring seat, the inner wall of the air outlet shell and the outer wall of the inner shell enclose a synthetic air outlet flow channel, a nozzle ring is arranged on the nozzle ring seat, the nozzle ring and the turbine form a turbine stage flow channel, the input end of the turbine stage flow channel is communicated with the air inlet flow channel, the output end of the turbine stage flow channel is communicated with the air outlet flow channel, a bearing seat is fixed on the air inlet shell, one end of the main shaft is supported by a first bearing arranged on the bearing seat, the other end of the, the cross section of the air inlet flow channel is gradually reduced from the air inlet flange to the far end of the air inlet flange, and the diameter D of the inner shell of the exhaust shell is smaller than the diameter D1 of the bottom of the turbine, so that the gas passing through the turbine stage flow channel does not turn after entering the exhaust flow channel and is directly exhausted along the axial direction of the flange of the exhaust shell.

Furthermore, the cross-sectional area of the air inlet flange at the maximum cross section of the air inlet flow channel is S, the cross-sectional area of the far end of the air inlet flange at the minimum cross section is S1, and the cross-sectional area S1 at the minimum cross section is 0.15-0.2S. The cross section of the air inlet flow channel is gradually reduced, so that when an organic medium flows in the air inlet flow channel, the air flow is uniform, the acceleration and deceleration process is reduced, and the air inlet loss is reduced.

Furthermore, a first mechanical seal and a second mechanical seal are arranged between the two ends of the turbine and the first bearing and between the two ends of the turbine and the second bearing respectively and are used for axially sealing the organic working medium.

Further, the turbine stage runner is a full-circle air inlet type runner. The gas flow can be uniformly distributed along the circumference of the nozzle ring and the turbine without additional separation loss and secondary flow loss.

Further, the second bearing diameter is smaller than the first bearing diameter for reducing the exhaust case inner shell diameter D1. The axial flow of the gas in the exhaust runner is facilitated.

Furthermore, the inner shell of the exhaust shell is supported on the outer shell through a reinforcing rib.

Further, the turbine is an axial flow turbine.

Due to the adoption of the technical scheme, the invention has the following beneficial effects:

1. the air inlet flow channel in the air inlet shell adopts a symmetrical equal-annular-flow design, the cross section of the air inlet flow channel is symmetrically arranged along the left side and the right side, the cross section of the air inlet flow channel is gradually reduced from the air inlet flange to the far end of the air inlet flange, and the cross section area of the far end of the air inlet flange is only 0.15-0.2 of that of the air inlet flange, so that when an organic medium flows in the air inlet flow channel, the air flow is uniform, the acceleration and deceleration process is reduced, and the air inlet loss is reduced.

2. The gas flow enters the turbine stage flow channel from the gas inlet flow channel, after the work is done in the turbine, the gas does not turn to enter the exhaust flow channel of the exhaust shell, and because the diameter D of the inner shell of the exhaust shell is smaller than the bottom diameter D1 of the turbine, when the gas in the exhaust flow channel passes through the outlet flange of the exhaust shell, the gas does not turn, the gas is uniformly exhausted along the axial direction of the flange of the exhaust shell, and the exhaust loss is reduced.

3. The turbine stage runner adopts a full-circumference air inlet type runner, so that air flow can be uniformly distributed along the nozzle ring and the circumference of the turbine for air inlet, and no additional separation loss or secondary flow loss exists.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a schematic view of the direction of gas flow in the present invention;

FIG. 3 is a cross-sectional view of an inlet conduit from an inlet flange to the distal end of the inlet flange in accordance with the present invention.

Reference numerals

In the drawing, 1 is a bearing seat, 2 is an air inlet shell, 3 is a nozzle ring seat, 4 is a nozzle ring, 5 is a turbine, 6 is a second mechanical seal, 7 is a second bearing, 8 is an exhaust shell, 9 is a main shaft, 10 is a first mechanical seal, 11 is a first bearing, 12 is an air inlet channel, 13 is a turbine stage channel, 14 is an exhaust channel, 21 is an air inlet flange, 22 is an air inlet flange far end, 81 is an exhaust shell inner shell, and 82 is an exhaust shell outer shell

Detailed Description

Embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

The direction of the arrow in the figure indicates the direction of the airflow passage, and the direction of the airflow passage is along the radial direction for air intake and axial direction exhaust, and the direction of the airflow passage is along the direction behind the direction of the exhaust of the expander and along the direction in front of the direction opposite to the exhaust.

Referring to fig. 1-3, a high-efficiency organic working medium expander comprises an air inlet casing 2, an air outlet casing 8 fixedly mounted on the air inlet casing 2, and a main shaft 9 fixed with an axial flow turbine 5, wherein the air outlet casing 8 is provided with an inner casing 81 and an outer casing 82, the inner casing 81 is supported on the outer casing 82 through reinforcing ribs, a nozzle ring seat 3 is arranged in the air inlet casing 2, one side of the nozzle ring seat 3 and the inner wall of the air inlet casing 2 enclose an air inlet flow channel 12, the other side of the nozzle ring seat 3 and the inner wall of the air outlet casing 82 and the outer wall of the inner casing 81 enclose an air outlet flow channel 14, a nozzle ring 4 is arranged on the nozzle ring seat 3, the nozzle ring 4 and the turbine 5 form a turbine stage flow channel 13, the input end of the turbine stage flow channel 13 is communicated with the air inlet flow channel 12, the output end of the turbine stage flow channel 13 is communicated with the air outlet flow channel, the other end of the main shaft 9 is supported by a second bearing 7 mounted on an exhaust casing inner shell 81, the intake runner 12 adopts a symmetrical equal-annular-flow runner, the cross section of the intake runner is symmetrically arranged along the left side and the right side, the cross section of the intake runner is gradually reduced from an intake flange 21 to a far end 22 of the intake flange, and the diameter D of the exhaust casing inner shell 81 is smaller than the bottom diameter D1 of the turbine, so that the gas passing through the turbine stage runner 13 does not turn after entering the exhaust runner 14, and is directly exhausted along the axial direction of the exhaust casing flange.

In this embodiment, as shown in fig. 3, 6 positions on the intake runner are selected to explain a process of changing the cross section of the intake runner, the cross-sectional area of the intake flange at the maximum cross section of the intake runner is S, and the cross-sectional area of the distal end of the intake flange at the minimum cross section is S1, and it can be seen from the figure that the cross-sectional area of the intake runner is gradually changed from S to S1, and gradually decreased until the cross-sectional area S1 at the minimum cross section is 0.15-0.2S, and the cross-sectional area of the intake runner is gradually decreased, so that when an organic medium flows in the intake runner, uniform flow of airflow can be realized through the change of the ratio of the flow passage areas, and airflow loss in the acceleration and deceleration process is reduced.

As shown in fig. 1, a first mechanical seal 10 and a second mechanical seal 6 are further disposed between two ends of the axial flow turbine 5 and the first bearing 11 and the second bearing 7 respectively, so as to axially seal the organic working medium.

The turbine stage runner 13 in this embodiment adopts a full-cycle intake type runner, and according to the flow characteristics of the gas, the full-cycle intake type runner can uniformly distribute the gas flow along the nozzle ring and the turbine circumference to intake without additional separation loss and secondary flow loss.

To reduce the diameter D1 of the exhaust casing inner casing 81, in the present embodiment, the diameter of the second bearing 7 is designed to be smaller than the diameter of the first bearing 11, which facilitates the axial flow of the gas in the exhaust flow passage.

When the invention works, organic working medium airflow radially enters from the air inlet shell, sequentially passes through the air inlet flow passage of the air inlet shell, the nozzle ring, the turbine and the exhaust flow passage of the exhaust shell, and finally axially flows out of the exhaust shell.

The expansion machine can reduce the air flow loss, improve the waste heat utilization rate and ensure the stability of the rotor and the air tightness of the whole structure.

Finally, it is noted that the above-mentioned preferred embodiments illustrate rather than limit the invention, and that, although the invention has been described in detail with reference to the above-mentioned preferred embodiments, it will be understood by those skilled in the art that various changes in form and detail may be made therein without departing from the scope of the invention as defined by the appended claims.