A 50mw class heat pump energy storage system matching -60 ℃ exhaust low temperature turbine

Abstract

A 50MW level heat pump energy storage system matching - 60 DEG C exhaust low temperature turbine belongs to the field of steam turbine design, in order to solve the problem that the low temperature turbine in the existing 50MW level heat pump energy storage system has poor flow efficiency and insufficient thermal performance in work, the application comprises a cylinder body, a rotor is inserted in the cylinder body, both ends of the rotor extend to the outside of the cylinder body, and both ends of the rotor are inserted into corresponding No. Bearing box or No. Bearing box, a No. Baffle sleeve and a No. Baffle sleeve are symmetrically installed on the inner wall of the cylinder body, and the No. Baffle sleeve and the No. Baffle sleeve are coaxially arranged with the rotor, two blade groups are symmetrically arranged in the cylinder body by double split flow mode, a plurality of moving blades in each blade group are installed on the rotor, a plurality of static blades in each blade group are installed on the No. Baffle sleeve or the No. Baffle sleeve, and the application is mainly used as a low temperature turbine matched in the 50MW level heat pump energy storage system matching.

Description

Technical Field

[0001] This utility model belongs to the field of steam turbine design, specifically relating to a -60℃ exhaust low-temperature turbine for a 50MW-class heat pump energy storage system. Background Technology

[0002] The novel heat pump energy storage system achieves energy exchange through molten salt thermal storage devices and water cooling devices, achieving a high round-trip efficiency for the energy storage and power generation system. Compared to traditional battery energy storage systems, it can store energy in larger capacities, has higher energy storage efficiency, and eliminates concerns about battery life. Low-temperature air turbines are core equipment for energy transition and cutting-edge technology, possessing irreplaceable value in fields such as heat pump energy storage, hydrogen energy, and superconductivity. As a crucial component of heat pump energy storage systems, the design and development level of low-temperature air turbines is also a significant factor limiting the development of heat pump energy storage.

[0003] Existing cryogenic turbines mostly adopt a tapered cross-section volute design. By adjusting the pressure and velocity field distribution within the inlet chamber, pressure loss is reduced and the uniformity of the outlet flow field is improved, thereby increasing unit efficiency. However, in the operation of 50MW-class heat pump energy storage systems, it has been found that traditional cryogenic turbines suffer from poor flow efficiency and insufficient thermal performance when operating in a -60℃ environment due to unreasonable arrangement of dynamic and static blades and gas seal structure design. This directly affects the energy storage efficiency of the heat pump energy storage system. Therefore, developing a cryogenic air turbine with a reasonable structural design and high stage and cycle efficiency is of great significance for promoting the rapid industrialization and large-scale application of heat pump energy storage. Utility Model Content

[0004] This invention aims to address the problem of poor flow efficiency and insufficient thermal performance of existing low-temperature turbines in 50MW heat pump energy storage systems when operating in a -60℃ working environment, and provides a -60℃ exhaust low-temperature turbine for 50MW heat pump energy storage systems.

[0005] A 50MW-class heat pump energy storage system is equipped with a -60℃ exhaust cryogenic turbine. The cryogenic turbine includes a cylinder body, in which a rotor is inserted. Both ends of the rotor extend outside the cylinder body and are respectively inserted into a first or second bearing housing. A first and second partition sleeve are symmetrically installed on the inner wall of the cylinder body, and both partition sleeves are coaxially aligned with the rotor. Two blade groups are symmetrically arranged in the cylinder body using a dual-flow splitting method. Multiple moving blades in each blade group... All blades are mounted on the rotor. In each blade group, multiple stationary blades are mounted on either the No. 1 septum or the No. 2 septum. The arrangement spacing between the No. 1 septum and the No. 2 septum is 124 mm. The minimum arrangement spacing between the inner wall of the No. 1 septum and the outer wall of the rotor is 99.5 mm. The minimum arrangement spacing between the inner wall of the No. 2 septum and the outer wall of the rotor is 99.5 mm. The arrangement spacing between the end of the No. 1 septum and the end of the cylinder body is 220 mm. The arrangement spacing between the end of the No. 2 septum and the end of the cylinder body is 220 mm.

[0006] Furthermore, the cylinder body is positioned between the first bearing housing and the second bearing housing, and the cylinder body is supported on the first bearing housing and the second bearing housing by multiple cat claws;

[0007] Furthermore, a centering beam is provided at both the front and rear ends of the cylinder body. One end of the centering beam is fixedly connected to the cylinder body by bolts and positioning pins, and the other end of the centering beam is fixedly connected to the first bearing box or the second bearing box by bolts and positioning pins.

[0008] Furthermore, the blade height of the last moving blade in each blade group is 161.5 mm;

[0009] Furthermore, a main air valve is provided on each side of the cylinder body, and each main air valve is connected to the cylinder body through an air guide pipe;

[0010] Furthermore, the moving blades in each blade group are all reaction blades, and each moving blade is installed on the rotor using a pre-twisted assembly method;

[0011] Furthermore, the stationary blades in each blade group are reaction blades, and each stationary blade is installed on the first or second diaphragm sleeve using a pre-twisted assembly method:

[0012] Furthermore, end air seals are provided between both ends of the cylinder body and the rotor;

[0013] Furthermore, a first blade tip seal is provided between the first and second diaphragm sleeves and each moving blade; a second blade tip seal is provided between the rotor and each stationary blade.

[0014] Furthermore, the cylinder block is a single-layer cylinder block.

[0015] The beneficial effects of this application compared to the prior art are:

[0016] 1. This application proposes a 50MW-class heat pump energy storage system equipped with a -60℃ exhaust cryogenic turbine, wherein the dynamic and static blade groups adopt a double-flow symmetrical arrangement structure with a total of 2×5 stages, designed through optimization of flow structure and improvement of intake pattern. Through iterative optimization during the design process, this unit possesses excellent thermodynamic performance and flow efficiency, high product reliability, flexible start-up and shutdown, safe and reliable operation, and convenient maintenance.

[0017] 2. The present application proposes a 50MW-class heat pump energy storage system with a -60℃ exhaust low-temperature turbine. The flow blades of the low-temperature turbine adopt a small enthalpy drop, reaction type, post-load, and pre-twist design, and are formed by full three-dimensional bending and twisting. The aerodynamic matching within and between stages is good, the airflow is uniform, and it has good aerodynamic performance.

[0018] 3. The 50MW-class heat pump energy storage system proposed in this application is equipped with a -60℃ exhaust cryogenic turbine. The strength of the flowing stationary blades of the cryogenic turbine is qualified, with a high safety margin; the vibration frequency of the moving blades is qualified, with good vibration resistance characteristics; the strength and airtightness of the stationary components such as the cryogenic turbine partition sleeve, outer cylinder, and end gas seal are all qualified, meeting the safety design requirements. Attached Figure Description

[0019] Figure 1 This is a longitudinal sectional view of the cryogenic turbine described in this application;

[0020] Figure 2 This is a front view schematic diagram of the cryogenic turbine described in this application;

[0021] Figure 3 This is a top view of the cryogenic turbine described in this application;

[0022] Figure 4 This is a schematic cross-sectional view of the cylinder block in the cryogenic turbine described in this application;

[0023] Figure 5 This is a schematic cross-sectional view of the diaphragm sleeve of the cryogenic turbine described in this application;

[0024] Figure 6 This is a schematic diagram of the fit between the moving and stationary blade assemblies in the low-temperature turbine described in this application;

[0025] Figure 7 This is a schematic diagram of the structure of the end gas seal of the cryogenic turbine described in this application.

[0026] In the diagram, 1 is the No. 1 bearing housing, 2 is the cylinder body, 3 is the No. 1 partition sleeve, 4 is the No. 2 partition sleeve, 5 is the rotor, 6 is the No. 2 bearing housing, 7 is the moving blade, 8 is the stationary blade, and 9 is the end air seal. DETAILED DESCRIPTION OF EMBODIMENTS

[0027] Specific Embodiment 1: In combination with Figures 1 to 7 this embodiment is described. The present embodiment provides a -60℃ exhaust low-temperature turbine matched with a 50MW-grade heat pump energy storage system. The low-temperature turbine comprises a cylinder block 2, a rotor 5 is inserted into the cylinder block 2, both ends of the rotor 5 extend to the outside of the cylinder block 2, and both ends of the rotor 5 are respectively inserted into the corresponding No.1 bearing box 1 or No.2 bearing box 6. A No.1 diaphragm sleeve 3 and a No.2 diaphragm sleeve 4 are symmetrically installed on the inner wall of the cylinder block 2, both the No.1 diaphragm sleeve 3 and the No.2 diaphragm sleeve 4 are coaxially arranged with the rotor 5, two blade groups are symmetrically arranged in the cylinder block 2 in a double splitting flow mode, a plurality of moving blades 7 in each blade group are all installed on the rotor 5, and a plurality of stationary blades 8 in each blade group are all installed on the No.1 diaphragm sleeve 3 or the No.2 diaphragm sleeve 4;

[0028] End seals 9 are arranged between both ends of the cylinder block 2 and the rotor 5;

[0029] A No.1 blade tip seal is arranged between the No.1 diaphragm sleeve 3, the No.2 diaphragm sleeve 4 and each moving blade 7; a No.2 blade tip seal is arranged between the rotor 5 and each stationary blade 8.

[0030] The -60℃ exhaust low-temperature turbine matched with a 50MW-grade heat pump energy storage system provided in this embodiment uses air as the working medium, which has high safety factor, small environmental pollution, and huge economic and social benefits, and can save a large amount of resources. The design rotation speed of the turbine is 4690r / min, the air flow rate is 1512t / h, the exhaust pressure is 0.88MPa, the turbine inlet temperature is 35.17℃, and the inlet pressure is 3.298MPa. The blade groups are arranged in a double splitting flow mode, and the total number of stages is 2×5 stages. The rotor 5 adopts an integrally forged structure, the material is 30Cr2Ni4MoV, and the rotor material has excellent mechanical properties and can meet the use requirements at different temperatures. During operation, after compressed air enters the valve, it does work through the rotor 5, the diaphragm sleeves and the blade groups to generate mechanical energy. Both ends of the rotor 5 are respectively inserted into elliptical shell bearings in the No.1 bearing box 1 or the No.2 bearing box 6. The elliptical shell bearing is a sliding bearing with an elliptical working surface, and its side clearance is increased, usually twice the top clearance. This design increases the absolute eccentricity of the journal in the bearing shell, thereby improving the stability of the bearing. When the elliptical shell bearing is working, the rotation of the journal will form two oil films on the upper and lower sides, and the resultant force generated by the pressures of the two oil films balances the external load, which helps maintain the stable operation of the shaft;

[0031] The end air seal 9 between the rotor 5 and the cylinder body 2 includes multiple air seal components. Each air seal component is a conventional comb-tooth structure design. The air seal component is fixed on the inner ring surface at the end of the cylinder body 2. Wall-type air seal teeth that cooperate with the comb-tooth air seal components are machined on the outer circular surface of the rotor 5 to ensure the stability of the end air seal 9 during operation.

[0032] The first blade tip gas seal between the first partition sleeve 3 and the second partition sleeve 4 and each moving blade 7 is also a comb-tooth structure. The first blade tip gas seal is usually composed of 3 gas seal teeth. After the 3 gas seal teeth are installed in the gas seal groove on the inner wall of the corresponding partition sleeve, they are fixed by the slit. A wall-type gas seal tooth that mates with the first blade tip gas seal is machined at the end of the moving blade 7 to ensure the stability of the first blade tip gas seal operation.

[0033] The second blade tip gas seal between the rotor 5 and each stationary blade 8 is also a comb-tooth structure. The second blade tip gas seal is also composed of two gas seal teeth. After the two gas seal teeth are installed in the gas seal grooves of the corresponding stationary blades 8, they are fixed by the slit. Wall-type gas seal teeth that cooperate with the second blade tip gas seal are machined on the outer wall of the rotor 5 to ensure the stability of the second blade tip gas seal operation.

[0034] Specific Implementation Method Two: Combining Figures 1 to 7 This embodiment differs from specific embodiment one in that the cylinder body 2 is a single-layer cylinder body, positioned between bearing housing 1 and bearing housing 6, and supported on bearing housing 1 and bearing housing 6 by multiple cat-claw supports. A centering beam is also provided at both the front and rear ends of the cylinder body 2. One end of the centering beam is fixedly connected to the cylinder body 2 by bolts and locating pins, and the other end is fixedly connected to bearing housing 1 or bearing housing 6 by bolts and locating pins. Other components and connection methods are the same as in specific embodiment one.

[0035] Specific implementation method three: Combining Figures 1 to 7 This embodiment differs from specific embodiment two in that a main air valve is provided on each side of the cylinder body 2, and each main air valve is connected to the cylinder body 2 via an air guide pipe. Other components and connections are the same as in specific embodiment two.

[0036] Combining specific implementation methods two and three, the cylinder body 2 adopts a central air intake design. The main air enters the cylinder body 2 through the main air valve and the air guide pipe. The gas drives the moving blades 7 on the rotor 5 to rotate, realizing the conversion of kinetic energy into mechanical energy. The exhaust port is located at the lower part of the cylinder body 2. The gas that has done work enters the heat exchanger through the exhaust port. The main air valve itself is supported on the foundation by an elastic bracket. The cylinder is cast from carbon steel and is divided into upper and lower halves. The horizontal split surface adopts a bolt tightening structure. The upper and lower halves of the cylinder are tightened and sealed with double-ended bolts. The cylinder body 2 is supported by four "cat claws". These four "cat claws" are cast integrally with the lower half of the cylinder and are located on the upper part of the lower horizontal flange, thus making the support surface flush with the horizontal split surface. The "cat's paw" rests on the keys located on both sides of bearing housing 1 or bearing housing 6, and can slide freely on them. At the front and rear ends, the cylinder is connected to the adjacent bearing housing by centering beams, which are fixed to the cylinder and adjacent bearings by bolts and locating pins. These centering beams ensure the correct axial and lateral positioning of the cylinder relative to the bearing housing. Each "cat's paw" is connected to the bearing housing with double-ended bolts to prevent the cylinder from coming loose from the bearing housing. An appropriate gap is left between the nut and the "cat's paw" so that the cylinder "cat's paw" can expand and contract freely when the temperature changes. In this embodiment, the cylinder body 2 adopts a single-layer cylinder structure. The single-layer cylinder structure is simple, reduces the manufacturing workload of the unit, and can also meet the adaptability of the unit to load changes.

[0037] Specific implementation method four: Combination Figures 1 to 7 This embodiment differs from Specific Embodiment Three in that the moving blades 7 in each blade group are all reaction blades, and each moving blade 7 is pre-twisted and mounted on the rotor 5; the stationary blades 8 in each blade group are all reaction blades, and each stationary blade 8 is pre-twisted and mounted on the first diaphragm sleeve 3 or the second diaphragm sleeve 4; the blade height of the last-stage moving blade 7 in each blade group is 161.5 mm. Other components and connections are the same as in Specific Embodiment Three.

[0038] In this embodiment, both the moving blade 7 and the stationary blade 8 adopt a pre-twisted assembly design. The pre-twisted assembly of the stationary blade 8 and the moving blade 7 is assembled by pre-twisting after processing, without any welding parts. There is contact pre-tightening force between the blade shrouds and between the blade roots, which can maintain the stability of the interconnection and ensure the safe and stable operation of the unit. The pre-twisted assembly partition is very convenient to disassemble and assemble. If the blade is damaged, the specified blade can be replaced, making on-site installation and disassembly more convenient and quick, ensuring that the unit can be put into operation more quickly and increasing the operating hours of the unit.

[0039] The present invention has been disclosed above with reference to preferred embodiments, but it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed structure and technical content to create equivalent embodiments without departing from the scope of the present invention. However, any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the scope of the present invention.

Claims

1. A 50MW-class heat pump energy storage system equipped with a -60℃ exhaust low-temperature turbine, characterized in that: The low-temperature turbine includes a cylinder body (2), in which a rotor (5) is inserted. Both ends of the rotor (5) extend to the outside of the cylinder body (2), and both ends of the rotor (5) are respectively inserted into the corresponding first bearing housing (1) or second bearing housing (6). A first partition sleeve (3) and a second partition sleeve (4) are symmetrically installed on the inner wall of the cylinder body (2), and the first partition sleeve (3) and the second partition sleeve (4) are coaxially arranged with the rotor (5). Two blade groups are symmetrically arranged in the cylinder body (2) in a double-flow manner. Multiple moving blades (7) in each blade group are installed on the rotor (5), and multiple stationary blades (8) in each blade group are installed on the first partition sleeve (3) or the second partition sleeve (4).

2. The -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 1, characterized in that: The cylinder body (2) is located between the first bearing housing (1) and the second bearing housing (6), and the cylinder body (2) is supported on the first bearing housing (1) and the second bearing housing (6) by multiple cat claws.

3. The -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 2, characterized in that: The cylinder body (2) is provided with a centering beam at both ends. One end of the centering beam is fixedly connected to the cylinder body (2) by bolts and positioning pins, and the other end of the centering beam is fixedly connected to the first bearing box (1) or the second bearing box (6) by bolts and positioning pins.

4. The -60℃ exhaust low-temperature turbine of the 50 MW-level heat pump energy storage system complete set according to claim 3, characterized in that: The blade height of the last moving blade (7) in each blade group is 161.5 mm.

5. The -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 4, characterized in that: A main air valve is provided on each side of the cylinder body (2), and each main air valve is connected to the cylinder body (2) through an air guide pipe.

6. The -60℃ exhaust low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 5, characterized in that: The moving blades (7) in each blade group are all reaction blades, and each moving blade (7) is installed on the rotor (5) by pre-twisting assembly.

7. A -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 6, characterized in that: The stationary blades (8) in each blade group are reaction blades, and each stationary blade (8) is installed on the first diaphragm sleeve (3) or the second diaphragm sleeve (4) by pre-twisting assembly.

8. A -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 7, characterized in that: Both ends of the cylinder body (2) and the rotor (5) are provided with end air seals (9).

9. A -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 8, characterized in that: A first blade tip seal is provided between the first diaphragm sleeve (3) and the second diaphragm sleeve (4) and each moving blade (7); a second blade tip seal is provided between the rotor (5) and each stationary blade (8).

10. A -60℃ exhaust gas low-temperature turbine for a 50MW-class heat pump energy storage system according to claim 9, characterized in that: The cylinder block (2) is a single-layer cylinder block.

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