CN108121838B - Impeller edge line matching method and device - Google Patents
Impeller edge line matching method and device Download PDFInfo
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Abstract
The invention relates to a matching method and a device for an edge line of a turbine, wherein the matching method for the edge line of the turbine comprises the following steps: obtaining an on-way velocity distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-obtained velocity model; determining a total circumferential offset distance for the fluid to flow from the upstream guide vane trailing edge to the downstream guide vane leading edge according to the on-way velocity profile; and obtaining the optimal time sequence position of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane according to the total circumferential offset distance. The impeller edge line matching method can simply and quickly find the optimal timing sequence position of the impeller, avoids the process of numerical software simulation calculation, can save calculation time and calculation resources, and improves design efficiency.
Description
Technical Field
The invention relates to the technical field of impeller design, in particular to a method and a device for matching an edge line of an impeller.
Background
The aerodynamic design of the turbine generally pursues high aerodynamic performance, and the limitation of the steady design is increasingly revealed along with the development of the design method. The internal flow field of the turbine is highly unsteady in nature, and the pneumatic benefit of fully exploiting the unsteady effects is a new breakthrough. The isentropic efficiency of the turbine can be further improved by utilizing the unsteady effect of the flow field by arranging the timing position of the turbine.
Different timing positions have different effects on the turbine isentropic efficiency, and an optimal timing position exists. In order to find the optimal time sequence position, the optimal time sequence position of the turbine can be obtained by carrying out unsteady numerical simulation on different time sequence positions of the turbine; the optimal timing position of the turbine can also be calculated by a semi-numerical simulation semi-empirical formula. The first method described above will encounter the following problems in finding the optimal timing position: firstly, the problem of blade reduction may be involved in the current unsteady calculation, and the process is complicated; secondly, the requirement of the non-constant calculation of a plurality of examples on computer resources is high; and thirdly, the repeated iteration of numerical simulation easily causes long calculation period. The second method described above is much less time and resource consuming than the first method, but still inevitably consumes computational resources using numerical simulations.
Disclosure of Invention
The invention aims to provide a method and a device for matching an edge line of a turbine, which can quickly and effectively obtain the optimal time sequence position of the turbine so as to match the edge line of the turbine.
To achieve the above object, a first aspect of the present invention provides a turbine edge line matching method, comprising:
obtaining an on-way velocity distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-obtained velocity model;
determining a total circumferential offset distance for the fluid to flow from the upstream vane trailing edge to the downstream vane leading edge from the on-way velocity profile;
and obtaining the optimal time sequence position of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane according to the circumferential total offset distance.
Further, the step of obtaining the on-way velocity distribution of the fluid when flowing through the bucket channel by the pre-learned velocity model specifically includes:
taking at least three positions axially within the bucket channel, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions;
and obtaining a relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions so as to obtain the axial speed value of any position in the bucket channel.
Further, the middle position of the bucket channel is located at the convex back of the suction surface of the bucket, and the step of obtaining the relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions comprises the following steps:
and setting the on-way velocity distribution of the inlet of the movable blade channel and the convex back of the suction surface of the movable blade and the on-way velocity of the convex back of the suction surface of the movable blade and the outlet of the movable blade channel as a linear relation.
Further, the step of determining a total circumferential offset distance for the fluid to flow from the upstream vane trailing edge to the downstream vane leading edge from the on-way velocity profile comprises:
determining a first time for fluid to pass through a bucket channel and a second time for fluid to pass through the bucket channel outlet and a downstream vane axial spacing from the on-way velocity profile;
determining the total circumferential offset distance from the first time and the second time.
Further, the step of determining a first time for fluid to pass through the bucket channel from the on-way velocity profile comprises:
taking at least three positions axially within the bucket channel, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions;
and determining the first time according to the axial velocity value of the fluid corresponding to the at least three positions, the axial chord length of the bucket, and the axial distance from the middle point of the at least one bucket channel to the inlet of the bucket channel.
Further, the step of determining a second time for the fluid to pass through the bucket channel from the on-way velocity profile comprises:
taking at least two positions axially between the bucket channel outlet and the downstream guide vane leading edge, the at least two positions including the bucket channel outlet and the downstream guide vane leading edge;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions;
and determining the second time according to the axial speed values of the fluid corresponding to the at least two positions and the axial distance between the outlet of the bucket channel and the downstream guide vane.
Further, the pre-acquisition speed model corresponding to each position is obtained through the following steps:
obtaining the Mach number corresponding to a certain position according to the flow area, the total pressure, the total temperature and the physical flow of the movable blade at the position in the axial direction;
and obtaining the axial velocity value of the fluid passing through the position according to the Mach number, the flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position.
Further, the corresponding mach number and axial velocity values at the suction surface convex back of the bucket are also related to the number of the bucket blades and the thickness of the bucket at the suction surface convex back of the bucket.
Further, the step of determining the total circumferential offset distance as a function of the first time and the second time comprises:
determining a first circumferential offset distance of the fluid according to the axial distance between the tail edge of the upstream guide vane and the inlet of the bucket channel and the geometric angle of the outlet of the upstream guide vane, wherein the first circumferential offset distance is the circumferential offset distance of the fluid from the tail edge of the upstream guide vane to the inlet of the bucket channel;
determining a second circumferential offset distance of the fluid as a function of the bucket primitive stage radial radius, the turbine speed, and the first time, wherein the second circumferential offset distance is a circumferential offset distance of the fluid from the bucket channel inlet to the bucket channel outlet;
determining a third circumferential offset distance of the fluid according to the bucket primitive stage radial radius, the turbine speed, the bucket outlet geometric angle, the axial spacing of the bucket channel outlet from the downstream guide vane leading edge, and the second time, wherein the third circumferential offset distance is the circumferential offset distance from the fluid at the bucket channel outlet to the downstream guide vane leading edge;
taking the sum of the first, second and third circumferential offset distances as the total circumferential offset distance.
Further, the step of obtaining an optimal timing position of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane according to the total circumferential offset distance comprises:
and determining the circumferential relative position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge as an optimal time sequence position according to the circumferential total offset distance, the downstream guide vane elementary stage radial radius and the number of the downstream guide vane blades.
To achieve the above object, a second aspect of the present invention provides a turbine edge line determining apparatus comprising:
the speed acquisition module is used for acquiring the on-way speed distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-acquired speed model;
a total offset acquisition module for determining a circumferential total offset distance for a fluid to flow from a trailing edge of an upstream guide vane to a leading edge of a downstream guide vane according to the on-way velocity profile;
and the optimal time sequence acquisition module is used for obtaining the optimal time sequence position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge according to the circumferential total offset distance.
Further, the speed acquisition module includes a typical position and speed calculation unit,
the speed calculation unit is used for taking at least three positions in the bucket channel along the axial direction, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet and at least one bucket channel middle position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; and obtaining a relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions so as to obtain the axial speed value of any position in the bucket channel.
Further, the speed acquisition module further comprises a along-the-way speed model obtaining unit,
the on-the-way speed model obtaining unit is used for setting on-the-way speed distribution of the inlet of the movable blade channel and the convex back of the suction surface of the movable blade and on-the-way speed of the convex back of the suction surface of the movable blade and the outlet of the movable blade channel to be in a linear relation.
Further, the total offset obtaining module comprises a time obtaining unit and a total offset obtaining unit, wherein,
the time obtaining unit is used for determining a first time when the fluid passes through the bucket channel and a second time when the fluid passes through the outlet of the bucket channel and is axially spaced from the downstream guide vane according to the on-way velocity distribution;
the total offset obtaining unit is used for determining the circumferential total offset distance according to the first time and the second time.
Further, the time acquisition unit comprises a first time acquisition subunit, wherein:
the first time obtaining subunit is configured to take at least three positions in the bucket channel along an axial direction, where the at least three positions include a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; and determining the first time according to the axial velocity values of the fluid corresponding to the at least three positions, the axial chord length of the movable blade, and the axial distance from the middle point of the at least one movable blade channel to the inlet of the movable blade channel.
Further, the time acquisition unit comprises a second time acquisition subunit, wherein:
the second time acquisition subunit is configured to take at least two positions in an axial direction between the bucket channel outlet and the downstream guide vane leading edge, the at least two positions including the bucket channel outlet and the downstream guide vane leading edge; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions; and determining the second time according to the axial speed values of the fluid corresponding to the at least two positions and the axial distance between the outlet of the bucket channel and the downstream guide vane.
Further, the speed obtaining module is used for obtaining a Mach number corresponding to a certain position according to the flow area, the total pressure, the total temperature and the physical flow of the movable blade at the position along the axial direction; and then obtaining the axial velocity value of the fluid passing through the position according to the Mach number, the through flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position so as to obtain the pre-obtained velocity model.
Further, the corresponding mach number and axial velocity values at the suction surface convex back of the bucket are also related to the number of the bucket blades and the thickness of the bucket at the suction surface convex back of the bucket.
Further, the total offset obtaining unit includes a first offset obtaining subunit, a second offset obtaining subunit, a third offset obtaining subunit, and a total offset obtaining subunit, where:
the first offset obtaining subunit is used for determining a first circumferential offset distance of the fluid according to the axial distance between the upstream guide vane trailing edge and the inlet of the bucket channel and the geometric angle of the upstream guide vane outlet, wherein the first circumferential offset distance is the circumferential offset distance of the fluid from the upstream guide vane trailing edge to the inlet of the bucket channel;
the second offset obtaining subunit is configured to determine a second circumferential offset distance of the fluid according to the bucket primitive stage radial radius, the turbine speed, and the first time, wherein the second circumferential offset distance is a circumferential offset distance of the fluid from the inlet of the bucket channel to the outlet of the bucket channel;
the third offset obtaining subunit is configured to determine a third circumferential offset distance of the fluid according to the bucket primitive radial radius, the turbine rotation speed, the bucket outlet geometric angle, the axial distance between the bucket channel outlet and the downstream guide vane leading edge, and the second time, where the third circumferential offset distance is a circumferential offset distance from the fluid driven blade channel outlet to the downstream guide vane leading edge;
the total offset acquisition subunit is configured to use a sum of the first circumferential offset distance, the second circumferential offset distance, and the third circumferential offset distance as the circumferential total offset distance.
Further, the optimal timing acquisition module is used for determining the circumferential relative position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge as the optimal timing position according to the circumferential total offset distance, the downstream guide vane primitive stage radial radius and the number of the downstream guide vane blades.
Based on the technical scheme, the impeller edge line matching method can utilize the unsteady effect of a flow field in the impeller, and based on a fluid migration mechanism and mathematical derivation, obtain the on-way velocity distribution of fluid flowing from the upstream guide vane to the downstream guide vane through a pre-obtained velocity model so as to obtain the optimal time sequence position of the front edge of the downstream guide vane relative to the tail edge of the upstream guide vane, thereby improving the isentropic efficiency of the impeller by utilizing the time sequence effect. The impeller edge line matching method can simply and quickly find the optimal time sequence position of the impeller, avoids the process of numerical software simulation calculation, can save calculation time and calculation resources, and improves design efficiency.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:
FIG. 1 is a schematic representation of an engineering model used in one embodiment of the turbine edge line matching process of the present invention;
FIG. 2 is a schematic illustration of the axial velocity distribution of a fluid within a bucket channel in an embodiment of the present invention method of vane edge line matching;
FIG. 3 is a schematic flow chart diagram of one embodiment of the turbine edge line matching method of the present invention;
FIG. 4 is a schematic flow chart of another embodiment of the inventive method of matching the edge line of a turbine;
FIG. 5 is a schematic flow chart of yet another embodiment of the turbine edge line matching method of the present invention;
FIG. 6 is a schematic diagram of the composition of one embodiment of the impeller edge line matching device of the present invention;
FIG. 7 is a schematic diagram of the composition of another embodiment of the impeller edge line matching device of the present invention;
fig. 8 is a schematic view showing the composition of a total deviation acquisition module in the edge line matching apparatus of the turbine of the present invention.
Detailed Description
The present invention is described in detail below. In the following paragraphs, different aspects of the embodiments are defined in more detail. Aspects so defined may be combined with any other aspect or aspects unless clearly indicated to the contrary. In particular, any feature considered to be preferred or advantageous may be combined with one or more other features considered to be preferred or advantageous.
The terms "first", "second", and the like in the present invention are merely for convenience of description to distinguish different constituent elements having the same name, and do not denote a sequential or primary-secondary relationship.
In the description of the present invention, it is to be understood that the terms "front", "rear", "circumferential", "axial" and "radial" etc. indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience in describing the present invention, and do not indicate or imply that the device referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be taken as limiting the scope of the present invention.
Through research, the inventor finds that the isentropic efficiency of the turbine can be further improved by utilizing the unsteady effect of a flow field by arranging the time sequence position of the turbine, and the essence of utilizing the time sequence effect is to enable low-energy fluid to flow close to the surface of the blade as much as possible so as to improve the isentropic efficiency of the turbine. The time sequence effect, namely the turbine isentropic efficiency, changes along with the change of the circumferential relative position of the adjacent relative static blade row. The low energy fluid includes wake, secondary flow, leakage flow, etc.
Different timing positions have different effects on the turbine isentropic efficiency, and an optimal timing position exists. The invention aims to obtain the circumferential offset distance of fluid in the flowing process between an upstream guide vane and a downstream guide vane through an engineering model so as to find the optimal time sequence position, and particularly, the optimal time sequence position can be obtained through a migration mechanism and formula derivation of the fluid, and different embodiments are given below for explanation.
The following embodiments are based on the schematic engineering model shown in fig. 1, and are cut along the same height position of each blade on the turbine and expanded along the axial direction of the turbine, i.e. the engineering model shown in fig. 1 is formed. The left row of blades is called an upstream guide vane, the middle row of blades is called a bucket, the space between adjacent buckets is a bucket channel, and the right row of blades is called a downstream guide vane. The guide vanes and the movable vanes are arranged in an axially penetrating manner along the turbine, and when the turbine works, the guide vanes are kept static, and the movable vanes rotate.
Preferably, the fluid is a wake, the optimal timing position is obtained based on a wake migration mechanism, when the airflow flows out along the trailing edge of the upstream guide vane, a wake group is formed and flows to the inlet point a of the movable vane channel (just cut by the blade) through the axial distance between the upstream guide vane and the movable vane, after the movable vane rotates for a plurality of circles due to the high rotating speed of the movable vane, the wake group reaches the outlet point B of the movable vane channel and generates a certain offset in the circumferential direction relative to the inlet point a, finally the wake group flows from the outlet point B of the movable vane channel to the leading edge point C of the downstream guide vane, the dotted line in fig. 1 is a migration track of the wake, the hollow and the oval and the circle with the shading represent the wake group, but do not represent the actual shape of the wake group.
In order to be able to increase the isentropic efficiency of the turbine, the fluid, e.g. the wake, should be made to flow as close as possible to the blade surface, i.e. to the leading edge C of the downstream guide vane. Thus, the optimal time sequence position can be obtained according to the preset target reaching position of the fluid and the geometric relation of the blades.
FIG. 3 is a schematic flow chart diagram of one embodiment of a method of matching a vane edge line, comprising the steps of:
101, obtaining on-way velocity distribution of fluid flowing from an upstream guide vane to a downstream guide vane through a pre-obtained velocity model;
102, determining a circumferential total offset distance S of a fluid flowing from a tail edge of an upstream guide vane to a front edge of a downstream guide vane according to an on-way speed distribution;
and 103, obtaining the optimal time sequence position of the front edge of the downstream guide vane relative to the tail edge of the upstream guide vane according to the circumferential total offset distance S.
These three steps are performed in sequence. In step 101, the on-way velocity profile of the fluid flowing from the upstream guide vane to the downstream guide vane may be velocity values at a plurality of typical positions, or may be a velocity profile function or model in the whole flowing process. The pre-acquired velocity model is based on the fluid migration mechanism and mathematical derivation, and is obtained by the relationship between the velocity of the fluid flowing through each position and physical parameters and geometrical parameters. In step 103, the optimal timing position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge is a circumferential offset distance of the downstream guide vane leading edge relative to the upstream guide vane trailing edge, so that the arrangement position of the downstream guide vane in the circumferential direction can be obtained, and a basis is provided for designing the downstream guide vane position.
According to the embodiment, by utilizing the unsteady effect of a flow field in the turbine, under the condition of avoiding numerical simulation, the on-way velocity distribution of fluid flowing from the upstream guide vane to the downstream guide vane is obtained through a pre-obtained velocity model so as to obtain the optimal time sequence position of the front edge of the downstream guide vane relative to the tail edge of the upstream guide vane, so that the unsteady flow phase of each section of the vane is adjusted, and finally the space positions of the front edge of the downstream guide vane and the tail edge of the upstream guide vane are adjusted. This is equivalent to providing a fast and efficient engineering model of the turbine edge line non-constant matching to take advantage of the timing effect to improve turbine isentropic efficiency. The impeller edge line matching method can simply and quickly find the optimal timing sequence position of the impeller, avoids the process of numerical software simulation calculation, can save calculation time and calculation resources, and improves design efficiency.
Further, as shown in the flowchart of fig. 4, step 101 specifically includes:
step 201, taking at least three positions in a bucket channel along an axial direction, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet and at least one bucket channel middle position;
step 203, obtaining a relation model between the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions so as to obtain an axial speed value of any position in the bucket channel. Wherein the axial velocity versus position model of the fluid is a function of the axial velocity of the fluid at each position during the flow process with respect to the axial position of the bucket passage, with reference to the graph shown in FIG. 2. Steps 201 and 203 are performed sequentially.
Specifically, the pre-capture speed model corresponding to each position in step 202 can be obtained through the following steps: firstly, obtaining the Mach number corresponding to each position according to the through flow area, the total pressure, the total temperature and the physical flow of the movable blades at each position; and then obtaining the axial velocity value of the fluid passing through the position according to the Mach number, the flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position. Wherein the flow area at each location is the annular area formed between the inner wall of the casing and the outer wall of the hub in the cross-section at that location. Similarly, the determination of the pre-capture velocity model is also applicable to the fluid passing from the outlet of the vane passage to the leading edge of the downstream vane.
In a preferred design, the middle position of the bucket channel is located at the convex back of the suction surface of the bucket, and step 203 specifically includes:
the on-way velocity distribution of the inlet of the movable vane channel and the convex back of the suction surface of the movable vane and the on-way velocity of the convex back of the suction surface of the movable vane and the outlet of the movable vane channel are set to be in a linear relation.
In particular, the corresponding mach number and axial velocity values at the suction surface convex back of the bucket are also related to the number of bucket blades, the blade thickness at the suction surface convex back of the bucket.
Three discrete points in the curve shown in fig. 2 correspond to the inlet of the moving blade channel, the convex back of the suction surface of the moving blade and the outlet of the moving blade channel from left to right respectively, the axial speed of the fluid reaches the maximum when the fluid reaches the convex back of the suction surface of the moving blade, and in order to simplify the model, the speed change is set to be linear change according to the change trend of the fluid speed. Of course, if a more accurate model is desired, more typical positions may be taken axially within the bucket channel, such as five points, etc.
In the following, a specific calculation method is given by taking the middle position of the moving blade channel as the convex back position of the suction surface of the moving blade as an example. Suppose the axial velocity at the inlet of the bucket passage is VZ1Axial velocity V at the outlet of the rotor blade channelZ2Axial velocity V at the convex back of the suction surface of the rotor bladeZm。
1、VZ1The calculation method comprises the following steps: firstly, calculating the Mach number Ma at the inlet of a movable blade channel according to a formula (1)1Then, the axial velocity V is calculated according to the formula (2)Z1：
Wherein, Pt1For total pressure at the inlet of the rotor blade, Tt1For total inlet temperature of the moving blades, Ma1Mach number, R, at the inlet of the rotor bladeS1Is the radius of the bucket inlet casing, RH1K is constant for the bucket inlet hub radius, typically 0.04042 for air.
Wherein W is the physical flow of the movable blade, R is the gas constant, and R is the adiabatic index.
2、VZ2The calculation method comprises the following steps: firstly, calculating the Mach number Ma at the inlet of a movable blade channel according to a formula (3)2Then, the axial velocity V is calculated according to the formula (4)Z2：
Wherein, Pt2For total pressure at the outlet of the rotor blade, Tt2Is the total temperature of the outlet of the movable vane, Ma2Mach number, R, at the outlet of the rotor bladeS2Radius of the bucket outlet casing, RH2Is the bucket exit hub radius.
3、VZmThe calculation method comprises the following steps: first according to equations (5) and (6)) Respectively calculating the relative total temperature T of the convex back of the suction surface of the movable bladetwmAnd relative total pressure PtwmThen, Mach number Ma is calculated according to formula (7)wmThen, the velocity V is calculated according to the formula (8)Zm：
Wherein, in the formulae (5) to (8), R1Is the radial radius of the rotor blade element stage, n is the rotor blade rotation speed, alpha2For the bucket inlet geometry angle, σ1Restoring a coefficient, R, for the total pressure from the inlet of the bucket passage to somewhere in the passagesmIs the radius, R, of the casing at a location in the bucket passageHmIs the radius of the hub somewhere in the channel of the moving blade, N1Delta is the leading edge L of the detached bucket in the bucket passage for the number of the blademThe blade thickness at the distance.
Fig. 5 shows a flowchart of a specific implementation manner of step 102, where step 102 specifically includes:
Step 302, according to the first time t1And a second time t2A circumferential total offset distance S is determined.
Wherein a first time t for a fluid to pass through a bucket channel is determined from an in-path velocity profile in step 3011Comprises the following steps:
step 201, taking at least three positions in a bucket channel along an axial direction, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet and at least one bucket channel middle position;
step 301A, according to the axial speed values of the fluid and the axial chord length L of the movable blade corresponding to at least three positions2Axial distance L from intermediate point of at least one bucket channel to inlet of bucket channelmDetermining a first time t1. Step 301A is not shown in the figure, and step 201 and 301A are executed sequentially.
V obtained from the above formulaZ1、VZmAnd VZ2First time t1Can be obtained by the following formula (9):
wherein a second time t for the fluid to pass through the bucket channel is determined from the in-path velocity profile in step 3012Includes 301B-301D (not shown in the figure), 301B-301D are performed sequentially. Determining a first time t1And a second time t2The sequence of the steps can be changed.
301B, taking at least two positions along the axial direction between the outlet of the movable blade channel and the front edge of the downstream guide vane, wherein the at least two positions comprise the outlet of the movable blade channel and the front edge of the downstream guide vane;
step 301C, obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions;
step 301D, according to the axial speed values of the fluid corresponding to at least two positions and the axial distance D between the outlet of the bucket channel and the downstream guide vane2Determining a second time t2。
In particular, assume that the axial velocity at the bucket channel exit is VZ2Under, isAxial velocity V at the leading edge of the guide vaneZ3. Wherein, VZ3The calculation method comprises the following steps: firstly, calculating the Mach number Ma at the leading edge of the downstream guide vane according to the formula (10)3Then, the axial velocity V is calculated according to the formula (11)Z3：
Wherein M isa3Mach number, R, at the leading edge of the downstream guide vaneS3Is the downstream vane leading edge casing radius, RH3Radius of the leading edge hub of the downstream vane, σ2And recovering coefficients for the total pressure from the outlet of the rotor blade to the inlet of the downstream guide vane.
Thus, according to equation (12), the second time t2The calculation method comprises the following steps:
further, step 302 is based on the first time t1And a second time t2Determining the circumferential total offset distance S specifically includes steps 302A-302D (not shown in the figures), wherein the execution sequence between steps 302A-302C is not limited, and 302D needs to be executed after steps 302A-302C. The method comprises the following steps:
step 302A, according to an axial distance D between the tail edge of the upstream guide vane and the inlet of the bucket channel1Upstream guide vane outlet geometry angle alpha1Determining a first circumferential offset distance S of the fluid1；
Wherein the first circumferential offset distance S1For the circumferential offset distance of the fluid from the trailing edge of the upstream guide vane to the inlet of the bucket passage, S1Can be obtained by the following equation (13):
S1＝D1×tanα1 (13)
step 302B, according toBucket element stage radial radius R1A turbine speed n and a first time t1Determining a second circumferential offset distance S of the fluid2；
Wherein the second circumferential offset distance S2For the circumferential offset distance, S, of the fluid from the blade channel inlet to the blade channel outlet2This can be obtained by the following equation (14):
step 302C, radial radius R according to the moving blade element level1The rotating speed n of the turbine, the geometric angle beta of the outlet of the movable blade, and the axial distance S between the outlet of the passage of the movable blade and the front edge of the downstream guide blade2And a second time t2Determining a third circumferential offset distance S of the fluid3；
Wherein the third circumferential offset distance S3For the circumferential offset distance, S, of the flow from the outlet of the vane passage to the leading edge of the downstream vane3Can be obtained by the following equation (15):
step 302D, offsetting the first circumferential direction by a distance S1A second circumferential offset distance S2And a third circumferential offset distance S3As the total circumferential offset distance S, i.e. S ═ S1+S2+S3。
On the basis of the foregoing embodiments, step 103 specifically includes: according to the circumferential total offset distance S and the downstream guide vane elementary-grade radial radius R2And number N of downstream guide vane blades2And determining the circumferential relative position delta L of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane as the optimal time sequence position. Δ L can be obtained by the following formula (16), where K is an integer:
in addition, the invention also provides a turbine edge line matching device which can be based on the turbine edge line matching method. The various embodiments of the impeller edge line matching method set forth above may be implemented by an impeller edge line matching device. Since the steps are explained in detail in the method section, only a brief description of the apparatus section is provided, and reference may be made to the description of the method section.
In one embodiment of the turbine edge line matching apparatus of the present invention, as shown in fig. 6, the apparatus includes a speed obtaining module 10, a total deviation obtaining module 20, and an optimal timing obtaining module 30, the total deviation obtaining module 20 is connected to the speed obtaining module 10, and the optimal timing obtaining module 30 is connected to the total deviation obtaining module 20. Wherein:
the speed acquisition module 10 is used for acquiring an on-way speed distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-acquired speed model;
a total offset acquisition module 20 for determining a circumferential total offset distance S for the fluid to flow from the upstream guide vane trailing edge to the downstream guide vane leading edge according to the on-way velocity profile;
and the optimal time sequence acquisition module 30 is used for obtaining the optimal time sequence position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge according to the circumferential total offset distance S.
The impeller edge line matching device of the embodiment can simply and quickly find the optimal time sequence position of the impeller, avoids the process of numerical software simulation calculation, can save calculation time and calculation resources, and improves design efficiency.
In this embodiment, the speed obtaining module 10 comprises a typical position and speed calculating unit, configured to take at least three positions in the bucket channel along the axial direction, where the at least three positions comprise the bucket channel inlet, the bucket channel outlet, and at least one bucket channel intermediate position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; and obtaining a relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to at least three positions so as to obtain the axial speed value of any position in the bucket channel.
Further, the speed obtaining module 10 further includes an on-way speed model obtaining unit, where the on-way speed model obtaining unit is configured to set an on-way speed distribution at the inlet of the bucket channel and the suction surface convex back of the bucket, and an on-way speed at the suction surface convex back of the bucket and the outlet of the bucket channel to be in a linear relationship.
Preferably, the speed obtaining module 10 is configured to obtain a mach number corresponding to each position according to a flow area, a total pressure, a total temperature, and a physical flow rate of the movable blade at the position; and then obtaining an axial velocity value of the fluid passing through the position according to the Mach number, the through flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position so as to obtain a pre-obtained velocity model. Moreover, the corresponding mach number and axial velocity values at the suction surface convex back of the bucket are also related to the number of bucket blades, the blade thickness at the suction surface convex back of the bucket.
In another embodiment of the turbine edge line matching apparatus of the present invention, as shown in fig. 7, the total deviation acquiring module 20 includes a time acquiring unit 21 and a total deviation acquiring unit 22 connected to each other, the time acquiring unit 21 is connected to the speed acquiring module 10, and the optimal timing acquiring module 30 is connected to the total deviation acquiring unit 22. Wherein:
the time obtaining unit 21 is used for determining a first time t of the fluid passing through the bucket channel according to the on-way velocity distribution1And a second time t at which the fluid passes through the blade passage outlet and the downstream guide vane axial spacing2；
The total offset obtaining unit 22 is used for obtaining a total offset according to the first time t1And a second time t2A circumferential total offset distance S is determined.
Specifically, referring to fig. 8, the time obtaining unit 21 includes a first time obtaining subunit 211, where the first time obtaining subunit is configured to take at least three positions in the bucket channel along the axial direction, where the at least three positions include a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; and determining first time according to the axial velocity values of the fluid corresponding to the at least three positions, the axial chord length of the movable blade and the axial distance from the middle point of the at least one movable blade channel to the inlet of the movable blade channel.
Further, the time obtaining unit 21 further comprises a second time obtaining subunit 212, the second time obtaining subunit 212 is configured to, when at least two positions are taken between the bucket channel outlet and the downstream guide vane leading edge along the axial direction, the at least two positions include the bucket channel outlet and the downstream guide vane leading edge; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions; and determining a second time according to the axial speed values of the fluid corresponding to the at least two positions and the axial distance between the outlet of the bucket channel and the downstream guide vane.
Still referring to fig. 8, the total offset obtaining unit 22 includes a first offset obtaining sub-unit 221, a second offset obtaining sub-unit 222, a third offset obtaining sub-unit 223, and a total offset obtaining sub-unit 224, the second offset obtaining sub-unit 222 is connected to the first time obtaining sub-unit 211, the third offset obtaining sub-unit 223 is connected to the second time obtaining sub-unit 212, and the three offset obtaining sub-units are connected to the total offset obtaining sub-unit 224. Wherein:
the first offset capture subunit 221 is for obtaining an axial separation D according to the upstream guide vane trailing edge and the bucket channel inlet1Upstream guide vane outlet geometry angle alpha1Determining a first circumferential offset distance S of the fluid1Wherein the first circumferential offset distance S1A circumferential offset distance for the fluid to reach the inlet of the bucket channel from the trailing edge of the upstream guide vane;
the second offset obtaining subunit 222 is configured to obtain the radial radius R according to the bucket primitive stage1A turbine speed n and a first time t1Determining a second circumferential offset distance S of the fluid2Wherein the second circumferential offset distance S2A circumferential offset distance for the fluid from the bucket channel inlet to the bucket channel outlet;
the third offset obtaining subunit 223 is configured to obtain the radial radius R according to the bucket primitive stage1The rotating speed n of the turbine, the geometric angle beta of the outlet of the movable blade, and the axial distance S between the outlet of the passage of the movable blade and the front edge of the downstream guide blade2And 1Two times t2Determining a third circumferential offset distance S of the fluid3Wherein the third circumferential offset distance S3The circumferential offset distance for the fluid from the vane passage outlet to the leading edge of the downstream vane;
the total offset obtaining subunit 224 is configured to offset the first circumferential offset by the distance S1A second circumferential offset distance S2And a third circumferential offset distance S3As the total circumferential offset distance S.
On the basis of the above embodiment, the optimal timing acquisition module 30 is used for acquiring the radial radius R of the downstream guide vane primitive stage according to the circumferential total offset distance S2And number N of downstream guide vane blades2And determining the circumferential relative position delta L of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane as the optimal time sequence position.
The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to aid in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (14)
1. A method of matching a turbine edge line, comprising:
obtaining an on-way velocity distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-obtained velocity model;
determining a total circumferential offset distance for the fluid to flow from the upstream vane trailing edge to the downstream vane leading edge from the on-way velocity profile;
obtaining the optimal time sequence position of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane according to the circumferential total offset distance;
the step of obtaining the on-way velocity distribution of the fluid when flowing through the bucket channel by the pre-acquisition velocity model specifically comprises the following steps:
taking at least three positions axially within the bucket channel, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions;
obtaining a relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions so as to obtain the axial speed value of any position in the bucket channel;
the method comprises the following steps of obtaining a relation model of axial speed and position of fluid according to axial speed values corresponding to at least three positions, wherein the middle position of the bucket channel is positioned at the convex back of a suction surface of the bucket, and the step of obtaining the relation model of the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions comprises the following steps:
setting the on-way velocity distribution of the inlet of the movable blade channel and the convex back of the suction surface of the movable blade and the on-way velocity of the convex back of the suction surface of the movable blade and the outlet of the movable blade channel as a linear relation;
the pre-acquisition speed model corresponding to each position is obtained through the following steps:
obtaining the Mach number corresponding to a certain position according to the flow area, the total pressure, the total temperature and the physical flow of the movable blade at the position in the axial direction;
and obtaining the axial velocity value of the fluid passing through the position according to the Mach number, the flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position.
2. The impeller edge line matching method of claim 1, wherein said step of determining a total circumferential offset distance for fluid flow from an upstream vane trailing edge to a downstream vane leading edge from said on-way velocity profile comprises:
determining a first time for fluid to pass through a bucket channel and a second time for fluid to pass through the bucket channel outlet and a downstream vane axial spacing from the on-way velocity profile;
determining the total circumferential offset distance from the first time and the second time.
3. The method of claim 2, wherein the step of determining a first time for a fluid to pass through a bucket channel based on the on-way velocity profile comprises:
taking at least three positions axially within the bucket channel, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions;
and determining the first time according to the axial velocity value of the fluid corresponding to the at least three positions, the axial chord length of the bucket, and the axial distance from the middle point of the at least one bucket channel to the inlet of the bucket channel.
4. The method of claim 2, wherein the step of determining a second time for the fluid to pass through the bucket channel based on the on-way velocity profile comprises:
taking at least two positions axially between the bucket channel outlet and the downstream guide vane leading edge, the at least two positions including the bucket channel outlet and the downstream guide vane leading edge;
obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions;
and determining the second time according to the axial speed values of the fluid corresponding to the at least two positions and the axial distance between the outlet of the bucket channel and the downstream guide vane.
5. The method of claim 1, wherein the corresponding mach number and axial velocity values at the suction surface convex back of a bucket are further related to a number of bucket blades, a blade thickness at the suction surface convex back of the bucket.
6. The method of matching an impeller rim line of claim 2, wherein said step of determining said total circumferential offset distance as a function of said first time and said second time comprises:
determining a first circumferential offset distance of the fluid according to the axial distance between the tail edge of the upstream guide vane and the inlet of the bucket channel and the geometric angle of the outlet of the upstream guide vane, wherein the first circumferential offset distance is the circumferential offset distance of the fluid from the tail edge of the upstream guide vane to the inlet of the bucket channel;
determining a second circumferential offset distance of the fluid as a function of the bucket primitive stage radial radius, the turbine speed, and the first time, wherein the second circumferential offset distance is a circumferential offset distance of the fluid from the bucket channel inlet to the bucket channel outlet;
determining a third circumferential offset distance of the fluid according to the bucket primitive stage radial radius, the turbine speed, the bucket outlet geometric angle, the axial spacing of the bucket channel outlet from the downstream guide vane leading edge, and the second time, wherein the third circumferential offset distance is the circumferential offset distance from the fluid at the bucket channel outlet to the downstream guide vane leading edge;
taking the sum of the first, second and third circumferential offset distances as the total circumferential offset distance.
7. The turbine edge line matching method of any of claims 1 to 6, wherein said step of deriving an optimal timing position of a downstream vane leading edge relative to an upstream vane trailing edge from said total circumferential offset distance comprises:
and determining the circumferential relative position of the downstream guide vane leading edge relative to the upstream guide vane trailing edge as an optimal time sequence position according to the circumferential total offset distance, the downstream guide vane elementary stage radial radius and the number of the downstream guide vane blades.
8. A turbine edge line mating arrangement, comprising:
the speed acquisition module (10) is used for acquiring an on-way speed distribution of the fluid in the process of flowing from the upstream guide vane to the downstream guide vane through a pre-acquired speed model;
a total offset acquisition module (20) for determining a circumferential total offset distance for a fluid flowing from an upstream guide vane trailing edge to a downstream guide vane leading edge from the on-way velocity profile; and
the optimal time sequence acquisition module (30) is used for obtaining the optimal time sequence position of the leading edge of the downstream guide vane relative to the trailing edge of the upstream guide vane according to the circumferential total offset distance;
wherein the speed acquisition module (10) comprises:
a speed calculation unit for taking at least three positions in an axial direction within a bucket channel, wherein the at least three positions comprise a bucket channel inlet, a bucket channel outlet and at least one bucket channel intermediate position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; obtaining a relation model between the axial speed and the position of the fluid according to the axial speed values corresponding to the at least three positions so as to obtain the axial speed value of any position in the movable blade channel; and
an on-way velocity model obtaining unit, configured to set an on-way velocity distribution at the convex back of the suction surface of the bucket and the inlet of the bucket channel as well as an on-way velocity at the convex back of the suction surface of the bucket and the outlet of the bucket channel as a linear relationship;
the speed acquisition module (10) is used for obtaining a Mach number corresponding to a certain position according to the flow area, the total pressure, the total temperature and the physical flow of the movable blade at the position along the on-way axis; and then obtaining the axial velocity value of the fluid passing through the position according to the Mach number, the through flow area, the total pressure, the total temperature and the physical flow of the movable blade corresponding to the position so as to obtain the pre-obtained velocity model.
9. Impeller rim line matching device according to claim 8, characterized in that said total offset retrieval module (20) comprises a time retrieval unit (21) and a total offset retrieval unit (22), wherein,
the time acquisition unit (21) is used for determining a first time when the fluid passes through the bucket channel and a second time when the fluid passes through the outlet of the bucket channel and is axially spaced from the downstream guide vane according to the on-way speed distribution;
the total offset acquisition unit (22) is configured to determine the circumferential total offset distance from the first time and the second time.
10. The impeller rim line matching device according to claim 9, wherein said time acquisition unit (21) comprises a first time acquisition subunit (211), wherein:
the first time obtaining subunit is configured to take at least three positions in the bucket channel along an axial direction, where the at least three positions include a bucket channel inlet, a bucket channel outlet, and at least one bucket channel intermediate position; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least three positions; and determining the first time according to the axial velocity values of the fluid corresponding to the at least three positions, the axial chord length of the movable blade, and the axial distance from the middle point of the at least one movable blade channel to the inlet of the movable blade channel.
11. The impeller rim line matching device according to claim 9, wherein said time acquisition unit (21) comprises a second time acquisition subunit (212), wherein:
the second time acquisition subunit (212) is configured to take at least two positions in an axial direction between the bucket channel outlet and the downstream guide vane leading edge, the at least two positions comprising the bucket channel outlet and the downstream guide vane leading edge; obtaining axial speed values of the fluid flowing through corresponding positions according to the pre-obtained speed models corresponding to the at least two positions; and determining the second time according to the axial speed values of the fluid corresponding to the at least two positions and the axial distance between the outlet of the bucket channel and the downstream guide vane.
12. The turbine rim line mating arrangement of claim 8, wherein the corresponding mach number and axial velocity values at the suction surface lands of the buckets are further related to the number of bucket blades, the blade thickness at the suction surface lands of the buckets.
13. Impeller rim line matching device according to claim 9, characterized in that said total offset capturing unit (22) comprises a first offset capturing subunit (221), a second offset capturing subunit (222), a third offset capturing subunit (223) and a total offset capturing subunit (224), wherein:
the first offset obtaining subunit (221) is configured to determine a first circumferential offset distance of the fluid according to an axial spacing between the upstream guide vane trailing edge and the bucket channel inlet and an upstream guide vane outlet geometric angle, wherein the first circumferential offset distance is a circumferential offset distance of the fluid from the upstream guide vane trailing edge to the bucket channel inlet;
the second offset obtaining subunit (222) is configured to determine a second circumferential offset distance of the fluid from the bucket primitive stage radial radius, the turbine speed, and the first time, wherein the second circumferential offset distance is a circumferential offset distance of the fluid from the bucket channel inlet to the bucket channel outlet;
the third offset obtaining subunit (223) is configured to determine a third circumferential offset distance of the fluid according to the bucket primitive radial radius, the turbine speed, the bucket outlet geometric angle, the axial distance between the bucket channel outlet and the downstream guide vane leading edge, and the second time, wherein the third circumferential offset distance is the circumferential offset distance from the fluid at the outlet of the bucket channel to the downstream guide vane leading edge;
the total offset acquisition subunit (224) is configured to take a sum of the first circumferential offset distance, the second circumferential offset distance, and the third circumferential offset distance as the circumferential total offset distance.
14. The turbine edge line matching device according to any one of claims 8 to 13, wherein the optimal timing acquisition module (30) is configured to determine a circumferential relative position of a downstream guide vane leading edge with respect to an upstream guide vane trailing edge as an optimal timing position according to the circumferential total offset distance, a downstream guide vane elementary stage radial radius, and a downstream guide vane blade number.
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