GB/T 15468-2020 (GB/T15468-2020, GBT 15468-2020, GBT15468-2020) & related versions
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GB/T 15468-2020
GB
NATIONAL STANDARD OF THE
PEOPLE’S REPUBLIC OF CHINA
ICS 27.140
K 55
Replacing GB/T 15468-2006
Fundamental technical requirements for hydraulic
turbines
ISSUED ON: JUNE 02, 2020
IMPLEMENTED ON: DECEMBER 01, 2020
Issued by: State Administration for Market Regulation;
Standardization Administration of PRC.
Table of Contents
Foreword ... 3
Introduction ... 5
1 Scope ... 6
2 Normative references ... 6
3 Terms and definitions ... 8
4 Technical requirements ... 30
5 Performance guarantee ... 44
6 Basic functions of turbine control system ... 48
7 Scope of supply and spare parts ... 49
8 Data and drawings ... 51
9 Factory inspection and testing ... 53
10 Nameplate, packaging, transportation and storage ... 58
11 Installation, operation, maintenance, acceptance test ... 60
Appendix A (Normative) The efficiency correction formula of the reaction turbine
... 62
Appendix B (Normative) The efficiency correction formula of impulse turbine 64
Appendix C (Normative) Recommended evaluation area for peak-to-peak value
of relative vibration displacement of main shaft ... 67
Appendix D (Informative) Instruments for basic configuration of hydraulic
turbine ... 68
Appendix E (Informative) Spare parts list of hydraulic turbine ... 69
Fundamental technical requirements for hydraulic
turbines
1 Scope
This standard specifies the performance guarantee, technical requirements,
scope of supply, inspection and test items for the design and manufacture of
hydraulic turbine products; proposes the requirements to be followed, for its
packaging, transportation, storage, installation, operation, maintenance.
This standard applies to hydraulic turbine products, that meet one of the
following conditions:
a) The rated power is 10 MW and above;
b) For Francis and impulse turbines, the nominal diameter of the runner is
1.0 m and above;
c) For Kaplan, Deriaz and bulb turbine, the nominal diameter of the runner is
3.0 m and above.
2 Normative references
The following documents are essential to the application of this document. For
the dated documents, only the versions with the dates indicated are applicable
to this document; for the undated documents, only the latest version (including
all the amendments) is applicable to this standard.
GB/T 191 Packaging - Pictorial marking for handling of goods (GB/T 191-
2008, ISO 780:1997, MOD)
GB/T 2900.45 Electrotechnical terminology - Hydroelectric powerplant
machinery (GB/T 2900.45-2006, IEC/TR 61364:1999, MOD)
GB/T 3323.1 Non-destructive testing of welds - Radiographic testing - Part
1: X-and gamma-ray techniques with film
GB/T 8564 Specification for installation of hydraulic turbine generator Unit
GB/T 9239.1 Mechanical vibration - Balance quality requirements for rotors
in a constant (rigid) state - Part 1: Specification and verification of balance
tolerances (GB/T 9239.1-2006, ISO 1940-1: 2003, IDT)
GB/T 9797 Metallic coatings - Electroplated coatings of nickel plus chromium
and of copper plus nickel plus chromium (GB/T 9797-2005, ISO 1456:2003,
IDT)
GB/T 10969 Specification for water passage components of hydraulic
turbines, storage pumps and pump-turbines
GB 11120 Lubricating oils for turbines
GB/T 11345 Non-destructive testing of welds - Ultrasonic testing -
Techniques, testing levels, and assessment
GB/T 11805 General specifications of automatic control components
(devices) and their related system for hydroturbine-generating sets
GB/T 15469.1 Hydraulic turbines storage pumps and pump-turbines
cavitation pitting evaluation - Part 1: cavitation pitting evaluation in reaction
turbines (GB/T 15469.1-2008, IEC 60609-1: 2004, MOD)
GB/T 15613 (all parts) Model acceptance tests of hydraulic turbines storage
pumps and pump-turbine
GB/T 17189 Code for field measurement of vibrations and pulsation in
hydraulic machines (turbines, storage pumps and pump-turbines) (GB/T
17189-2017, IEC 60994:1991, MOD)
GB/T 19184 Cavitation pitting evaluation in Pelton turbines (GB/T 19184-
2003, IEC 60609-2:1997, MOD)
GB/T 20043 Field acceptance test to determine the hydraulic performance
of hydraulic turbine, storage pumps and pump-turbines (GB/T 20043-2005,
IEC 60041:1991, MOD)
GB/T 28546 Specification for package, transportation and storage of large
and medium hydraulic units
GB/T 32584 Evaluation of mechanical vibration for machine sets in hydraulic
power plants and pump-storage plants
DL/T 443 Guide for factory inspection of hydraulic turbine generator unit and
its auxiliary equipment
DL/T 507 Testing regulations for hydroelectric generating set start-up
DL/T 710 Code of operation for hydraulic turbines
allowable runaway time.
4.2.1.8 For the Francis and impulse turbines, the runners should be made of
stainless steel. For the Kaplan and bulb turbines, the blades should be made of
stainless steel. Other cavitation-prone parts of the turbine should be made of
anti-cavitation materials OR take necessary protective measures. If the
cavitation-prone parts are surfacing stainless steel, the thickness of the
stainless steel layer, after processing, shall not be less than 5 mm.
4.2.1.9 Lifting facilities should be provided on the top of the turbine chamber.
4.2.1.10 When performing shafting calculation, the mass imbalance of the
runner is calculated according to the grade G6.3 in GB/T 9239.1.
4.2.1.11 The runner shall be subjected to a static balance test. The mass
imbalance of the runner, after static balance, shall meet the requirements of
grade G6.3 in GB/T 9239.1.
4.2.1.12 The maximum temperature of the babbitt bearing bush of the thin oil-
lubricated guide bearing of the hydraulic turbine, under various operating
conditions, shall not exceed 70 °C. The maximum temperature of the radial
thrust bearing bush of the horizontal-shaft turbine shall not exceed 70 °C. The
maximum temperature of the oil does not exceed 60 °C.
4.2.1.13 The hydraulic moment of the guide vane of the reaction turbine should
have a self-closing trend, from near the full opening to near the no-load opening.
The water guide mechanism shall be equipped with reliable protection devices
(such as shear pins, friction pairs, limit blocks, etc.), to prevent damage to the
guide vane and the expansion of the accident. The design of the limit block shall
have sufficient rigidity; it should provide a buffer pad. For the protection device
combined with the friction device and the shear pin, the breaking force of the
shear pin should not be less than 1.5 times the force on the shear pin, which is
applied by the servomotor at rated operating force. It should provide hydraulic
and manual locking devices, in the fully closed position; it should provide
manual locking devices, in the fully open position.
4.2.1.14 There should be a difference in hardness, between the movable
wearing ring and the corresponding fixed wearing ring.
4.2.1.15 The arrangement of top cover drainage equipment of the hydraulic
turbine should be one in-use and one standby; if necessary, it may be one in-
use and two standby. If the top cover of the vertical-shaft turbine has the
conditions of gravity drainage, it shall provide a sufficiently large gravity
drainage channel.
4.2.1.16 For the reaction turbine, the design of the metal volute and seat ring
shall be such, that they can bear the design pressure alone (the maximum
momentary pressure in the volute). In the seat ring design, which adopts the
concrete volute, it shall consider the concrete weight and other vertical load,
which are supported by the seat ring. For the impulse turbine, the design of
water distribution loop shall be such, that it bears the design pressure alone
(the maximum momentary pressure in the distribution loop).
4.2.1.17 Exhaust and supplemental air devices shall be provided, on the top of
the volute of the horizontal-shaft turbine.
4.2.1.18 The hydraulic turbine shall be provided with a manhole. The manhole,
on the volute, should not be less than ϕ600 mm. The high head turbine volute
should use an inward opening manhole. The size of the manhole, on the tail
water tube, should not be less than ϕ600 mm or 600 mm × 600 mm. When a
square manhole is used, it shall prevent the four corners from stress
concentration and cracking. At the lower side of the manhole, it shall be
equipped with a water inspection valve. Reinforcement shall be carried out at
the manhole. The location, quantity, size of the manholes shall be as negotiated,
between the supplier and the buyer.
4.2.1.19 A light-weight maintenance platform that is easy to disassemble AND
has sufficient load-bearing capacity, shall be installed in the tail water tube of
the vertical-shaft reaction turbine.
4.2.1.20 When phase-modulated operation is required, it shall provide a phase
modulation pressurized water inlet and exhaust device AND a cooling device to
reduce the temperature of the small clearance of the runner.
4.2.1.21 For the parts of the hydraulic turbine and its auxiliary equipment, that
need to be subjected to pressure test, except for the parts that need to be
welded on the site, all need to be pressure tested in the factory, according to
the test pressure; the pressure of the pressure test should not be less than 1.3
times the design pressure; the pressure test time shall continue to stabilize for
30 minutes. The pressure-bearing parts shall not produce abnormal
phenomena, such as harmful deformation and leakage.
4.2.1.22 The metal volute of the reaction turbine and the water distribution pipe
of the impulse turbine, may be subjected to a pressure test, according to the
requirements of the contract.
4.2.2 Working stress and safety factor
4.2.2.1 Safety performance analysis shall be carried out in the structural design
of hydraulic turbines. In the design of parts subject to alternating stress,
vibration or impact, it shall leave sufficient safety margins. Under all expected
conditions, it shall have sufficient rigidity and strength.
4.2.2.2 The working stress of the components can be analyzed and calculated
of the runner blade shall not exceed 2/5 of the material's yield strength. For the
impulse runner, when it is operating normally, under the expected maximum
load conditions, the maximum stress at each part of the runner, which is
analyzed and calculated by the classical formula, shall not exceed 1/18 of the
material's yield strength. The maximum stress at each part of the runner, which
is calculated by the finite element method, shall not exceed 1/9 of the yield
strength of the material; meanwhile it shall carry out verification for the fatigue
strength.
4.2.2.10 The maximum composite stress Smax of the main shaft is defined as:
Smax = (S2 + 3T2) 1/2; its value shall not exceed 1/4 of the yield strength of the
material. In the formula, S is the sum of axial stress and bending stress, which
are caused by hydraulic load and static load; T is the torsional shear stress, at
the maximum power of the hydraulic turbine. It shall calculate AND take into
account the maximum composite stress Smax, according to the above formula;
the maximum stress, after the occurrence of stress concentration, shall not
exceed 2/5 of the yield strength of the material. At the same time, the torsional
shear stress of the main shaft of the turbine, at maximum power, shall not
exceed 1/6 of the yield strength of the material. The main shaft of the horizontal-
shaft turbine shall be subjected to verification of fatigue strength.
4.2.3 Material and manufacturing requirements
4.2.3.1 The castings and forgings of the main structural components of the
turbine shall comply with CCH-70-4 and JB/T 1270, OR the corresponding
standards as stipulated in the contract. For important castings and forgings, the
acceptance shall be carried out, under the participation of the representatives
of the buyer. The treatment of defects, which are deemed to be major defects,
in the above standards, shall be approved by the buyer.
4.2.3.2 Only the welding personnel, who have passed the examination and hold
the certificate, can perform the welding work of the main components. The main
stressed welds of the main components shall be subjected to 100% non-
destructive testing. The weld inspection shall comply with the requirements of
GB/T 3323.1, GB/T 11345, NB/T 47013.2, NB/T 47013.3, NB/T 47013.4, NB/T
47013.5, NB/T 47013.10, OR the corresponding standards as stipulated in the
contract.
4.2.3.3 The surface of the hydraulic turbine shall have an anti-rust coating.
Meanwhile, it shall specify:
a) Requirements for surface treatment;
b) Paint and other protection methods, as well as instructions for their use;
c) Requirements for use before shipment and at the construction site;
d) Number of coating courses;
e) The thickness and total thickness of each coating film;
f) Quality inspection and quality control requirements.
The decorative electroplating layer shall meet the requirements of GB/T 9797.
4.2.3.4 All fasteners, which are in contact with water, shall be made of rust-proof
or corrosion-resistant materials, OR it shall take corresponding measures.
4.2.3.5 For bearing bushes, which are made of babbitt alloy, 100% ultrasonic
inspection shall be carried out on the combination with the bush base; the
contact surface shall not be less than 95%; the single shelling area shall not be
more than 1%. The surface shall be free from unaccepted defects, when tested
by the penetration method.
4.3 Specific requirements for different types of turbines
4.3.1 Francis turbine
4.3.1.1 In order to ensure the safe, stable, efficient operation of the hydropower
station, as well as the life of the flow-through components such as runners, the
turbine should not be operated outside the guaranteed scope.
4.3.1.2 When the turbine is operating within the guaranteed range, the hydraulic
excitation frequency, as well as the natural frequency of the main flow-through
components, such as the runner, movable guide vane, top cover, bottom ring,
fixed guide vane, shall be staggered by at least 10%.
4.3.1.3 For the turbines of medium and high head, it may use the leaking water,
which is drawn from the upper wearing ring on the top cover, as a backup water
source for unit cooling.
4.3.1.4 For the structural design of high-head, high-speed turbines, it shall
consider reducing the possibility of lifting the turbine; there shall be measures
to prevent the lifting of the turbine.
4.3.1.5 The hydraulic turbine shall be equipped with a natural air supplement
device; OR it shall take other measures, to improve the stability of the unit.
4.3.1.6 The runner blades can be cast or molded; the blades should be
processed by CNC. The runners of the hydraulic turbine should adopt the
group-welding structure.
4.3.1.7 The pre-tightening force of the coupling bolts shall not be less than 3
times the maximum working load, under normal working conditions.
4.3.3.1 When the runner adopts a cantilever structure, it shall consider the
influence of the deflection of the main shaft.
4.3.3.2 The single-sided clearance, between the outer edge of the runner blade
and the runner chamber, should not be greater than 0.1% D1 and not less than
0.065% D1.
4.3.3.3 The runner chamber shall have sufficient rigidity, to prevent vibration
from exceeding the limit. During design, it shall consider the axial displacement
of the runner. The parts corresponding to the outer edges of the blades AND
other cavitation-prone parts of the runner chamber, should be made of stainless
steel or surfacing stainless steel. The natural frequency of the runner chamber
shall be at least 10% staggered from the overcurrent frequency of the runner
blades.
4.3.3.4 The radial guide bearing should be equipped with a high-pressure oil-
lubricated jacking device.
4.3.3.5 The operating mechanism of the runner blades shall be flexible. The
association device shall be accurate and reliable. During the seal test of the
runner blades, there shall be no oil leakage; no water is allowed to enter the oil
supply cavity of the runner body, through the runner seal. If the runner body is
filled with oil, the oil pressure shall be higher than the water pressure, which is
outside the runner body.
4.3.3.6 An expansion joint shall be provided, between the runner chamber and
the lining of the tail water tube.
4.3.3.7 It should not set a manhole on the runner chamber.
4.3.3.8 In order to prevent runaway, it shall provide a hammer to close the guide
vanes.
4.3.3.9 The split surface and joint surface of the inner and outer water
distribution ring, shall be equipped with sealing strips OR coated with sealant.
4.3.3.10 For the main shaft's coupling bolt, it shall consider working in water
AND bearing the influence of alternating stress. The pre-tightening force should
not be less than 3 times the maximum working load.
4.3.3.11 The dynamic response analysis shall be carried out for the whole unit,
to prevent resonance.
4.3.4 Impulse turbine
4.3.4.1 It shall be possible to assemble, disassemble, replace the runner of the
impulse turbine, without disassembling the generator.
4.3.4.2 The runner shall be subjected to dynamic response analysis, to avoid
resonance.
4.3.4.3 The runner shall be safe and reliable; it shall be designed according to
fatigue strength; it shall be subject to flaw testing, according to CCH-70-4 or the
criteria as stipulated in the contract. During operation, it shall also check
whether the water bucket has cracks, on a regular basis. After being put into
operation, the initial inspection should be carried out within 500 hours of
operation.
4.3.4.4 The pre-tightening force of the coupling bolts should not be less than 3
times the maximum working load.
4.3.4.5 The abrasion-prone parts of the nozzle and the needle shall be made of
erosion-resistant and abrasion-resistant materials.
4.3.4.6 Each nozzle shall have a separate operating servomotor. Each nozzle
shall have a separate stroke indicator; the deflector shall have a position
indicator.
4.3.4.7 On the enclosure, it shall take necessary sound insulation or noise
reduction measures.
4.3.4.8 The water-stabilizing grid, in the pit of the impulse turbine, shall have
sufficient strength and rigidity. Meanwhile, it shall take anti-corrosion measures,
to facilitate the disassembly, assembly, maintenance of the turbine runner,
nozzles, etc.
4.3.4.9 For the multi-nozzle impulse turbine, the speed control system shall be
able to automatically turn on or cut off the number of nozzles running, according
to the system load and a predetermined procedure, to ensure stable and
efficient operation of the unit; the switching process shall be smooth. During the
whole process of nozzle switching and load increase and decrease, the turbine
shall be regulated normally; the vibration and swing of the unit shall be within
the allowable range. There shall be no interference, between the jets, when all
nozzles are working at the same time.
4.3.4.10 The discharge height of the impulse turbine shall meet the
requirements, that the safe and stable operation of the turbine and the efficiency
are not influenced. At the maximum tail water level, there shall be sufficient
ventilation height above the tail water surface. It shall be equipped with
necessary air supplement devices on the enclosure.
4.3.4.11 When the tail water level of the power station varies greatly, the
installation elevation of the impulse turbine is allowed to be lower than the
highest operating tail water level, during the flood season. However, there shall
be a compressed air system, to lower the water level in the enclosure.
......
| Standard ID | GB/T 15468-2020 (GB/T15468-2020) | | Description (Translated English) | Fundamental technical requirements for hydraulic turbines | | Sector / Industry | National Standard (Recommended) | | Classification of Chinese Standard | K55 | | Classification of International Standard | 27.140 | | Word Count Estimation | 46,463 | | Date of Issue | 2020-06-02 | | Date of Implementation | 2020-12-01 | | Drafting Organization | Harbin Electric Machinery Factory Co., Ltd., China Electric Power Construction Group Kunming Survey, Design and Research Co., Ltd., Dongfang Electric Group Dongfang Electric Machinery Co., Ltd., China Electric Power Construction Group East China Survey and Design Research Institute Co., Ltd. Electric Motor Research Institute, China Yangtze Power Co., Ltd., Three Gorges Electromechanical Engineering Technology Co., Ltd., China Three Gorges Group Co., Ltd., General Institute of Hydropower and Water Conservancy Planning and Design, China Power Construction Group Beijing Survey and Design Research Institute Co., Ltd., State Grid Liaoning Electric Power Co., Ltd. Company Electric Power Research Institute, State Grid Hunan Electric Power Company Electric Power Research Institute, Datang Yunnan Power Generation Co., Ltd., Chongqing Hydro Turbine Factory Co., Ltd., Yunnan Datang International Lixianjiang River Basin Hydropower Development Co., Ltd. | | Administrative Organization | National Hydraulic Turbine Standardization Technical Committee (SAC/TC 175) | | Proposing organization | China Electrical Equipment Industry Association | | Issuing agency(ies) | State Administration for Market Regulation, National Standardization Administration |
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