Some standard content:
UDC621.838.4=006.72
National Standard of the People's Republic of China
GB/T 3858—93
Hydrodynamic drive terminology
Hydrodynamic drive terminology1993-12-28 Issued
Implementation on 1994-10-01
Issued by the State Bureau of Technical Supervision
National Standard of the People's Republic of China
Hydrodynamic drive terminologyMain content and applicable scope
GB/T3858—93
385883
This standard specifies the terms for driven components, driven machine components and their average parameters, performance parameters, operating conditions and characteristics.
This standard is suitable for the research, teaching, design, application and use of force reduction transmission. 2.1 Hydraulic transmissionThe minimum diameter is indicated by "\", as shown in Figure 2. 6.8-1.3 Outer ring hell
The outer inductive surface of the impeller, as shown in Figure 2,
6.8-1.4 Inner ring ws
The inner surface of the impeller flow channel, as shown in Figure 2,
6.8.1.5ti intervel chuntiel The space formed by the two adjacent blades and the inner and outer rings, 6.B-2 Auxiliary chamber auxiliary chamber is used to adjust the space filled with liquid peptide in the workpiece cavity in the magnetic coupling. 6.8.2.T Front auxiliary chamber lorward auxiliary chamber is located in the center of the pump wheel and turbine, 6.8.2.2 Backward auxiliary chamber chamber is located on the outside of the gear.
6.B.2.3 Side auxiliary chamber is located on the outside of the gear.
6-8.2-4 Auxiliary chamber for discharging working fluid, 6.9 Design streamline center line flow path The streamline that divides the flow path into two equal parts in the axial flow path of the working chamber, 6.1 Center streamline center flow path The line connecting the centers of the inscribed circles of the axial flow path of the working chamber, 6.11 Front pressure of blade When the blade is under shearing condition, the side of the blade that bears the higher average pressure, 6.12 Back of blade var:uim aide nf BladeWhen calculating the working condition, the blade is subjected to the surface with the relatively high average pressure. 6.13 Blade inlet edgeThe edge of the blade that reduces the flow into the impeller.
6.14 Blade exit edgeof bladeThe edge of the blade that reduces the flow out of the impeller,
6.75 Blade inlet radiusof bladeThe distance from the intersection of the inlet edge of the impeller blade and the design flow path to the axis, expressed as "". 6. Blade exit radiusThe distance from the intersection of the outlet edge of the impeller blade and the design flow path to the axis, expressed as "". 6.17 Blade profilecentre Jineof blade profileThe center line of the blade shape along the flow direction. 6.18 Blade centre surface of bladeThe surface formed by the nodal lines of the same blade.
619 Flow widthwidthofflawpath
The width of the blade perpendicular to the flow path on the circulation circle, expressed as "\". 620Leaf lengthleng1hnflade
The length of the leaf is denoted by "".
The thickness of the leaf is denoted by ". GB/T3B58—93
The length of the leaf perpendicular to the stem and pointing upward is denoted by ". 6-22
Blade bladeangle
The angle between the blade flow line and the direction of the circular velocity, denoted by "3". Blade entrancebladeangle
The blade angle at the blade entrance
6-24 Blade exit angle exitlradeanrlThe blade rise angle at the blade exit,
6.25 Blade wrap angle reifblah
The angle between the two axial planes at the intersection of the streamline and the blade entrance and exit edges. 6.26 Microflowgle
The angle between the velocity and the direction of the circular velocity, denoted by "". 6.27 Attack angle nrtacknglz
The difference between the flow angle and the blade angle. The microflow angle is the positive angle of attack of the blade, and vice versa, it is the negative angle of attack, denoted by "". 6-28 Flow plate
Plate added between the impeller and turbine in the hydraulic coupling to control the dynamic state of the flow reduction, 6.29 Scoopcube
A guide pipe used to adjust the working energy in the speed-controlled fluid coupling, 6.30 Flow through
In the flow, the flow is cut off and perpendicular to it. Performance integers
7.1 External parameters
Dynamic parameters, motion state (work, force, speed) of the pulley and the guide wheel in the torque transmission and the parameters derived from them (efficiency, torque ratio, variable frame coefficient, etc.)
7.?Internal parameters
Parameters (energy head, flow, flow rate, pressure) and energy loss in the torque transmission. 7.3 Parphcral velocity The velocity of a fluid particle relative to the impeller, represented by “\\”. 7.4
Relative velocity
The velocity of a fluid particle relative to the impeller, represented by “W\”. 7.5 Absolute velocity
When a fluid particle rotates with the impeller, the perimeter velocity of the impeller at which the point is located is represented by “”. 7.6 Absolute velocity
The velocity of a fluid particle relative to a fixed point, represented by \V\. 7.7 Axial velocity
The velocity of a fluid particle on the axial plane, represented by “V\”. 7.8 Circular velocity
The inverse component of the absolute velocity of the body mass in the direction of the closed tangent, expressed as "V". 7-9 Inverse circulation quantity
The velocity loss is the line integral of the projection of the velocity loss on a certain closed circumference line along the boundary. For an impeller, it is the product of the two velocity derivatives of the point on the design streamline and the length of the circumference where the point is located, expressed as ". 6
7.10 Circular flow quantityof fluid(lowGR/T3858--93
The amount of work done by a fluid flowing through a circulating flow passage in a unit time, expressed as \Q\, 7.11
Energy head: hpad
The energy of a working body in a unit time, expressed as efficiency. 7.11.1 Absolute energy head heand
The average amount of energy head after the working fluid passes through the impeller when the simulated value is not taken into account, indicated by "". 7.T1.2 Actual energy gain of the working fluid after passing through the impeller when the pressure is high, indicated by "". 7.12 Finite blade quick stop coefficient
The positive coefficient of the theoretical energy head of the impeller when the number of blades is finite, indicated by "", 7.13 Hydraulic effect
The coefficient of reducing the flow section due to the thickness of the blade, indicated by "". 7.14 Hydraulie losses
The energy loss caused by the viscosity of the working fluid, the shape of the flow channel and the flow state in the hydraulic circulation channel, indicated by ", \,
7.14.7 Narrowband hydraulic loss
The energy loss caused by the viscosity of the working fluid, the shape of the flow channel and the flow state in the hydraulic circulation channel, indicated by ", \,
7.14.7 Narrowband hydraulic loss
The energy loss caused by the viscosity of the working fluid, the shape of the flow channel and the flow state in the hydraulic circulation channel, indicated by ", \,
7.14.7 Narrowband hydraulic loss
lases The hydraulic loss between the working body and the flow channel and working surfaces and the internal hydraulic loss of the working body, denoted by "",. 7.14.2 Shock loss When the working fluid enters the blade flow channel, the relative velocity direction is not consistent with the blade inlet line direction, denoted by \\
7.74.3 Disk friction loss All force losses except impact loss, which includes the static loss along the way and various local resistance losses. 7.15 Mechanical loss The sum of the mechanical losses at the disc, seal and bearing is denoted by "\". 7.15.1 Disc friction joE6es Energy loss caused by all relative rotational surfaces and working efficiency of the flow, expressed as -V\. 7.15.2 Blowing loss oles
Energy loss caused by the rotating parts of the filter element and the air quality due to the wind, expressed as "". 7.16 Volumetric loss yolumetriclusses The volumetric loss caused by the downflow, expressed as "g-". 7.17 Cooptubelo99e3
Energy loss caused by the flow of the working wave tube and the flow of the guiding liquid, expressed as "N\, 7.18 Efficiency
The ratio of output to input power, expressed as \\\. 7.18.1 Filter efficiency liydranlie efficiency Efficiency only when hydraulic loss is considered, expressed as "". 7.18-2 Mechenieul efficiency Efficiency only when mechanical loss is considered, expressed as "". 7.19.3. Volur per efficiency efficiency only considers the efficiency when the load is lost, expressed in "". 7.4. maximum efficiency efficiency is the efficiency of the force reducing element after deducting all small losses, expressed in " and ". 7.19 Input torque inpur tozque
GB/T 385B—93
The torque absorbed by the force reducing element, expressed in -M\. 7.20 Output mlpm irr
The torque acting on the working machine by the force reducing element, expressed in ". 7.21
The distance absorbed by the worm wheelwwW.bzxz.Net
The distance absorbed by the worm wheel, expressed in 4f\. 7.22 Turbine torque
The torque on the wheel shaft acting on the negative rotation of the external gear, expressed in \M"\. .23, hydraulic torque of pump impeller is the torque of the impeller acting on the flow in the working chamber, expressed in M. F24 hydraulic torque of turbine is the force of the turbine acting on the flow in the working chamber, expressed in M-. 7.25 hydraulic torque of guide wheel is the force of the guide wheel acting on the flow in the working chamber, expressed in M. 7.26 starting torque starting torque is the instantaneous output torque when the impeller is pulled from the stop to the start of operation, expressed in M. 7.27 brake torque dam pedtorgue
At the seasonal speed condition, the output force range of the turbine from running to stationary moment is expressed by ",\, 7.28 Rated force range
The torque of the filter coupling at rated working time is expressed by ". 7.29 Nominal torque primctorque
When the pump wheel speed is 10or/nin, the torque absorbed by the system wheel at the highest efficiency condition, M
Where: M pump wheel nominal torque.N
Pump wheel speed r,min,
Mfm——system wheel speed tu is 1 CCOr/min when the high efficiency working condition is short, N-hl, 7.30 energy capacity
The ability of hydraulic components to transfer energy
The torque factor of impeller torque factor of impeller is -31
The chain force is an integer of the chain capacity, and its value is: Mg
The torque factor of impeller min*/m (or min/mr): Impeller force cage, Nm
Working filter density, kg/m| |tt||Gravity shear m/s\,
--Effective diameter of energy element.m.
7.32 Torque coefficient torqueBtio
8/T3858-93
Ratio of the output torque of the wave transformer to the manpower, M
Where K-
-Torque conversion system effect
-Extraction and auxiliary manpower distance, N·m,
7.33 Torque coefficient of the speed control system gtalltorquetio at zero speed condition, | |tt||7.34 Overload coefficient nverlaudratio
Ratio of the maximum torque of the force-reducing coupling to the rated torque, M
Where: Next one-by-one overload coefficient,
Mu\—-maximum torque, N·
M. Rated torque, Nn.
7.34.1 Starting overload coefficient 6tartingaverloudratio Ratio of the starting force of the force-reducing coupling to the rated torque. f
Where: Next one-by-one overload coefficient,
Mu\—-maximum torque, N·
M. Rated torque, Nn.
7.34.1 Starting overload coefficient 6tartingaverloudratio Ratio of the starting force of the force-reducing coupling to the rated torque. f
Where: Next one-by-one overload coefficient,
Mu\—-maximum torque, N·
M. Rated torque, Nn.
t||Ma Starting torque N·m.
M.—Rated power consumption, Nn.
7.34.2 Dynamic overload coefficient lumpednverlaudratip The ratio of brush torque to rated torque,
In the formula,
Braking overload coefficient:
Brush torque.N·mF
M. Rated power year.Nm
7.35 Special speed ratio speedratio
The ratio of output shaft speed to input shaft speed, expressed as a number or 2. For the force reduction element: 1
For the force transmission device:
In the formula:
Worm gear, gear speed, r/min
CH/T 385B -93
The speed of extraction and input thrust (r/min), 7.36Phase conversion point
The intersection of the two phases of the hydraulic converter, 7.37
Slip rate
The ratio of the speed difference between the gear and turbine of the clutch to the speed of the gear, and its value is expressed in ">" x100%
7.38Rated speed
The speed specified by the product before leaving the factory is expressed in "". 7.39Filling volumefillingurmunint
The amount of working fluid filled into the cavity of the wave element, expressed in "". 7.40Filling and reducing fector
The percentage of the ratio of the sugar filling volume to the total volume, its value "" indicates the ratio of the guide opening BcooptubeEpan
The ratio of the actual stroke of the guide to the measured stroke. 7.2 Design ratio [urmlerari
The ratio of the maximum ripple value to the minimum selected value of the external characteristic curve of the hydraulic coupling, 7.43
Penetration number petmeablicynumber
It indicates the adaptability of the torque converter, usually evaluated by the following penetration numbers T, working, T
In our city:
Zero speed working wheel torque coefficient min*/m (or min/mr) Maximum pump wheel torque coefficient.min\/n (or mint/mr): Pump wheel torque coefficient under even working conditions +min/m (or min/mr*). 7. Axial foreon blade of impeller: The axial potential of the working fluid on the impeller and its associated surfaces, expressed as \F, \. 7.45 Compensation pressure charging Ppressure: The supply pressure of the compensation system at the inlet of the hydraulic element, expressed as \P. 7.46 Speed range: The ratio of the overall speed of the output shaft of the combined type of force reduction and the single minimum stable speed. 7.47: Geometric similarity: The situation where the dimensions of two components are equal and the corresponding angles are equal. 7.48 Kinematic phase: The kinematic phase gimiarity The situation where the speed ratio of hydraulic components is the same. 7.49 Dynamics inertia The situation where the geometrical similarity and kinematic similarity exist. 19 (9) Working conditions and characteristics B.1 Working conditions GR/T3858-93 The working conditions are represented by the speed ratio of hydraulic components, which is indicated by "". 1-1 Tarque condition is the working condition where the wheel is small and the combustion is quarterly, and the speed ratio is the same. 1.2 Zero speed condition The working condition where the speed ratio is equal is indicated by the subscript \O\. 1.2.1 Starting and sinking condition The working condition from static to running under zero working conditions. B.1.2.2 Dampedecndicicn The working condition when the turbine is transferred to a standstill. 3.3 Design condition
The working condition to be used in the design calculation is indicated by a superscript " or \. The maximum efficiency working condition is indicated by a " ". 1.4
The working condition when the efficiency is low is indicated by a " ". The working condition when the torque reducer and turbine torque are equal is indicated by a " ". 1.6 Working condition when the torque reducer is transferred to the turbine.
8-1. Easing dumping condition rulition The pump wheel rotates forward and the turbine wheel rotates reversely under the external load. BB overrunning condition
Under the external load, the turbine speed is high and the speed is M= the center speed. 1.&1 overtunning danped condition In the overtuning condition, the impeller is driven by the external load and the power is lost. 8.1&2 Backwardcandition In overtaking conditions, the case wheel reverses the power to the starting power machine, 8.2 Flow similanditio
In several cabinets, the speed ratio of the power element is equal to the working condition, R.3 No impact condition hocklextrancecoditinn filter flow into the specified angle of attack equal to the working condition.
.4 Steam cavitationcondition
The working condition where the steam grounding phenomenon occurs in the working chamber, B-5 Pertmeability
In the killing condition area, when the transformer pump wheel rotation remains unchanged, the performance of the load change causing the input torque change. 8.5.1 Positive permeability Pasitive permeabitity When the torque increases slightly, the input torque increases accordingly. 8.5-2 NIGATIVIRPERMEABILITY Performance of input torque decreasing when output torque increases 8.5.3 NIGATIVIRPERMEABILITY Performance of input torque not changing much when shaft output changes 8.5.4 Compliance
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