CN113028071B - Design method of pilot balance cage type regulating valve - Google Patents

Design method of pilot balance cage type regulating valve Download PDF

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CN113028071B
CN113028071B CN202010731389.2A CN202010731389A CN113028071B CN 113028071 B CN113028071 B CN 113028071B CN 202010731389 A CN202010731389 A CN 202010731389A CN 113028071 B CN113028071 B CN 113028071B
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valve
small
force
valve core
pressure
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CN113028071A (en
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廖卿
丁远茂
宋虬
陈雷
余成达
余朝中
杨世岐
陈晓宇
张朝
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Zhejiang Linuo Flow Control Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/024—Devices for relieving the pressure on the sealing faces for lift valves using an auxiliary valve on the main valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
    • G06F17/10—Complex mathematical operations

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Abstract

The invention relates to the field of industrial valve design and discloses a design method of a pilot balance cage type regulating valve, wherein the pilot balance cage type regulating valve comprises a valve body, a valve seat, a large valve core, a small valve core, a valve cage, a spring, a pressing plate, a valve rod, an upper valve cover and a sealing ring; the maximum thrust of the small valve core, the minimum thrust required by the small valve core, the maximum lifting force required by the large valve core, the maximum sealing force required by the large valve core and the dynamic thrust of the large valve core are controlled by the control system; by changing the diameter d1 value of the small valve seat, the sealing force of the small valve core, the lifting force of the large valve core, the sealing force of the large valve core and the dynamic thrust of the large valve core tend to approach by comparison, and a valve seat design structure with the minimum thrust of an actuator is obtained; the regulating valve can be widely applied to the working conditions of high temperature, high pressure and large caliber, can ensure that the leakage grade of the regulating valve reaches V grade or VI grade, and realizes the process requirement of tight regulation and shutoff.

Description

Design method of pilot balance cage type regulating valve
Technical Field
The invention relates to the field of industrial valve design, in particular to a design method of a pilot balance cage type regulating valve.
Background
The pilot-operated cage type regulating valve is an improved pressure balance type regulating valve, and compared with a common cage type regulating valve, the pilot-operated cage type regulating valve is provided with an independent pressure balance type pilot valve core, and can realize small opening degree regulation. The valve has good sealing effect and strong cutting-off capability, is suitable for controlling various high-temperature high-pressure fluids, and can be used as an emptying cut-off valve.
At present, the high-temperature, high-pressure-difference, large-caliber and tight shutoff working conditions are more and more widely applied in industries such as petroleum, petrifaction, power plants, pharmacy, new energy, coal chemical industry, fine chemical industry and the like. Aiming at the harsh requirements that the nominal diameter is DN 80-DN 1200, the pressure grade is CL 150-CL 2500, the leakage grade requires V grade or VI grade, even zero leakage and the like. Although the unbalanced single-seat regulating valve is not limited by high temperature, unbalanced force generated by high pressure difference and sealing force required by a valve seat are overcome, although the unbalanced force of the balanced cage type regulating valve is small and the caliber can be also overlarge, the problem of sealing under the high-temperature working condition is difficult to solve. The pilot balance cage type regulating valve is a control valve which meets the above harsh working conditions and has the highest cost performance. But the structure is complex, the constraint by the working condition is strong, the size design universality of the big valve core and the small valve core is poor, and the wide use of the pilot balance cage type regulating valve is limited. Therefore, a calculation design method for the internal part of the pilot balance cage type adjusting valve is needed, and the design size of the internal part is universal.
Disclosure of Invention
Aiming at the defect of poor universality of size design of a pilot balance cage type regulating valve in the prior art, the invention provides a calculation design method of internal parts of the pilot balance cage type regulating valve, so that the sizes are universal.
In order to solve the technical problem, the invention is solved by the following technical scheme:
a design method of a pilot balance cage type regulating valve comprises a valve body, a valve seat, a large valve core, a small valve core, a valve cage, a spring, a pressure plate, a valve rod, an upper valve cover and a sealing ring, and comprises the following steps:
A. calculating the relationship between the height of the flow channel and the stroke of the small valve core according to the structure of the small valve seat;
B. b, calculating the opening cross section area and the annular gap area of the small valve seat according to the data obtained in the step A, and further calculating the flow of the small valve seat and the annular gap flow of the large valve core to enable the outflow flow of the small valve seat to be not less than the inflow flow of the annular gap of the large valve core;
C. calculating the sealing force required by the small valve core, and obtaining the relation between the sealing force required by the small valve core and the diameter of the small valve seat according to the actual sealing coefficient, wherein the maximum thrust of the small valve core is obtained; obtaining the maximum thrust of the small valve core; the relation between the minimum thrust required by the small valve core and the diameter of the small valve seat is obtained without considering part of pretightening force caused by the working pressure before the valve;
D. calculating the maximum lifting force required by the large valve core according to the diameter of the large valve seat, the diameter of the valve cage, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
E. calculating to obtain the maximum sealing force required by the large valve core according to the diameter of the large valve seat, the sealing coefficient, the pressure before the valve and the pressure after the valve;
F. calculating to obtain the dynamic thrust of the large valve core according to the diameter of the large valve seat, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
G. by varying the diameter d of the small valve seat 1 And comparing the data obtained according to the formulas of the steps C, D, E and F to ensure that the sealing force of the small valve core, the lifting force of the large valve core, the sealing force of the large valve core and the dynamic thrust of the large valve core tend to approach each other, so as to obtain the valve seat design structure with the minimum thrust of the actuator.
Preferably, the design method of the pilot balance cage type regulating valve comprises the following steps:
A. measuring and calculating the relationship between the small valve core stroke and the flow passage height,
Figure GDA0003820505600000021
B. calculating the flow of the small valve seat and the annular gap flow of the large valve core, and obtaining H by the step A 1 ，
Figure GDA0003820505600000031
Figure GDA0003820505600000032
Figure GDA0003820505600000033
Figure GDA0003820505600000034
Figure GDA0003820505600000035
Figure GDA0003820505600000036
Figure GDA0003820505600000037
The outflow flow of the small valve seat is more than or equal to the inflow flow of the annular gap of the large valve core, so as to meet the requirement
Figure GDA0003820505600000038
Then
Figure GDA0003820505600000039
C. Calculating the minimum thrust F of the small valve core IZK And sealing force, i.e. maximum thrust force F 1M
Calculating the formula:
Figure GDA00038205056000000310
Figure GDA00038205056000000311
F 1M ＝d 1 K M
D. the maximum lift force required for the large spool is calculated,
Figure GDA00038205056000000312
Figure GDA00038205056000000313
Figure GDA00038205056000000314
Figure GDA0003820505600000041
E. the maximum sealing force required by the large valve core is calculated,
Figure GDA0003820505600000042
Figure GDA0003820505600000043
Figure GDA0003820505600000044
F. calculating the dynamic thrust of the large valve core,
Figure GDA0003820505600000045
Figure GDA0003820505600000046
Figure GDA0003820505600000047
Figure GDA0003820505600000048
G. by varying the diameter d of the small valve seat 1 Value of so that F 1M ，F T ，F DM ，F DD The thrust of the actuator is close to the minimum, and the aim of minimizing the thrust of the actuator is fulfilled, and the calculation is carried out according to the following formula:
F 1M ＝200d 1
Figure GDA0003820505600000049
Figure GDA00038205056000000410
Figure GDA0003820505600000051
wherein the meaning and units of the parameters are,
in the step A:
H 0 -small valve element stroke, mm;
H 1 -small spool flow channel height, mm;
d 0 the diameter of the upper cover of the small valve core is mm;
d 3 -the diameter of the lower end of the small valve element, mm;
d 1 small valve seat diameter, mm;
in the step B:
D 1 sealing ring diameter, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 -pressure after valve, MPaA
D 3 -diameter of bore of large spool, mm P 3 Big spool bore pressure, MPaA
d 1 Small valve seat diameter, mm Q 1 -a small valveSeat flow rate, m 3 /h
ζ 1 Small valve seat flow resistance factor Q 2 Annular gap flow, m 3 /h
ζ 2 Annular gap flow resistance coefficient ρ Medium Density, kg/m 3
A 1 Small valve seat opening cross section, mm 2 A 2 Annular gap area, mm 2
In the step C:
P 1 pre-valve pressure, MPaA
F 21 Small spool valve front media imbalance force, nP 2 Pressure after valve, MPaA
F 22 Small spool valve back media imbalance force, nk M Sealing coefficient
F 1M Sealing force required for a small valve cartridge, NK M =25, leakage class IV
F 1ZG -actuator closing force, nk M =80, leakage class V
F 1ZK Actuator opening force, NK M =170, leakage class VI
In the step D:
d-diameter of large valve seat, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 Pressure after valve, MPaA
F T -large spool lift force, np 3 Valve pocket pressure, MPaA
F 1 Force applied by the valve chamber medium to the big spool sealing ring, N
F 2 Force of the pre-valve medium on the big spool sealing ring, N
F 3 Force of the post-valve medium on the valve seat of the big valve core, N
F 4 Application of pre-valve media toForce at valve seat of big valve core, N
In the step E:
d-diameter of large valve seat, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 Pressure after valve, MPaA
F J -big spool medium force, nf DM Large spool sealing force, N
F 01 The force applied by the valve chamber medium to the big spool sealing ring, nk M Sealing coefficient
F 02 Force of pre-valve medium applied to big spool seal ring, nk M =25, leakage class IV
F 03 Force of the medium behind the valve on the valve seat of the big poppet, N K M =80, leakage class V
F 04 Force of pre-valve medium applied to big-spool valve seat, N K M =170, leakage class VI
In the step F:
D 2 cage diameter, mm P 1 Pre-valve pressure, MPaA
F DD Dynamic thrust of big spool, nP 2 -pressure after valve, MPaA
F 11 The force applied by the valve chamber medium to the big spool sealing ring, N
P 3 Valve pocket pressure, MPaA
F 12 Force of the pre-valve medium on the big spool sealing ring, N
F 13 Force of the post-valve medium on the valve seat of the big valve core, N
Step G:
d 1 small valve seat diameter, mm
d-diameter of valve seat, mm
H 0 Small valve core stroke, mm
F 1M Small valve core sealing force, N
P 1 Pre-valve pressure, MPaA
P 2 -pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
A 1 Small valve-element flow cross-section in mm 2 A 2 Large valve core annular area, mm 2
F T -large spool lift force, N
F DM Large spool sealing force, N
Preferably, also according to d 1 、d、H 0 P is calculated from the design values and the following data 3 The value of (c):
CL150 P 1 ＝1.3、P 2 ＝0.4
CL300 P 1 ＝3.3、P 2 ＝0.8
CL600 P 1 ＝7.3、P 2 ＝1.5
CL900 P 1 ＝10.3、P 2 ＝2.4
CL1500 P 1 ＝16.3、P 2 ＝3.8
CL2500 P 1 ＝27.3、P 2 ＝5.5
preferably, the valve is of the structure
And (3) obtaining a small valve core stroke: d 0 ＝d 1 +2
Figure GDA0003820505600000081
Preferably, in step C
Selecting P in consideration of actual conditions 2 ＝0，K M ＝200
To obtain
Figure GDA0003820505600000082
Preferably, the tight shut-off sealing force required by the small valve element is 200d without taking into account the partial pretension due to the pre-valve operating pressure 1 It is considered that the small valve core sealing force is always larger than the small valve core lifting forceLarge, therefore small valve spools require a minimum thrust of
F 1M ＝d 1 K M ＝200d 1 。
Preferably, in step D, the step of,
according to valve structural design data, D 2 ＝d+2
The lifting force of the large valve core is obtained through simplification:
Figure GDA0003820505600000083
due to the adoption of the technical scheme, the invention has the remarkable technical effects that:
the structure of the invention can realize the sealing under high temperature working condition, the general size design of the big valve core and the small valve core makes the pilot balance cage type regulating valve usable, compared with the regulating valve, in the same opening range, because the change degree of the flow area formed between the valve holes is gentle, the regulating precision is higher, the invention can be widely applied to the working conditions under high temperature, high pressure and large caliber, can ensure the leakage grade of the regulating valve to reach V grade or VI grade, and realizes the technical requirement of tight regulation and shutoff.
Drawings
FIG. 1 is a schematic diagram of a pilot balance cage type regulating valve according to the present invention;
FIG. 2 is a schematic view of the calculation of the cross-sectional flow area of the small valve element according to the present invention;
FIG. 3 is an enlarged view of a portion of Y in FIG. 2;
FIG. 4 is a schematic diagram of the calculation of the thrust required by the small valve spool of the present invention, which is in the closed state of the small valve spool;
FIG. 5 is a graph showing the comparative trend of the sealing force and the thrust force of the small valve core of the present invention;
FIG. 6 is a schematic diagram of the calculation of the lifting force of the large spool according to the present invention, which is the small spool open state;
FIG. 7 is a schematic view of the large valve core sealing force calculation of the present invention, which is the valve closed state;
fig. 8 is a schematic diagram of calculating the dynamic thrust of the large valve element according to the present invention, which is in an open state of the large valve element.
The valve comprises 11 parts of a small valve core, 12 parts of a large valve core, 13 parts of a valve cage, 14 parts of a valve seat, 15 parts of a valve body, 16 parts of a spring and 111 parts of a small valve seat.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples.
Example 1
A design method of a pilot balance cage type regulating valve comprises a valve body 15, a valve seat 14, a large valve core 12, a small valve core 11, a valve cage 13, a spring 16, a pressure plate, a valve rod, an upper valve cover and a sealing ring, and is characterized by comprising the following steps:
A. calculating the relationship between the height of the flow channel and the stroke of the small valve core according to the structure of the small valve seat 111;
B. calculating the opening cross section area and the annular gap area of the small valve seat 111 according to the data obtained in the step A, and further calculating the flow of the small valve seat 111 and the annular gap flow of the large valve core to ensure that the outflow flow of the small valve seat 111 is not less than the inflow flow of the annular gap of the large valve core;
C. calculating the sealing force required by the small valve core, and obtaining the relation between the sealing force required by the small valve core and the diameter of the small valve seat 111 according to the actual sealing coefficient to obtain the maximum thrust of the small valve core; the relation between the minimum thrust required by the small valve core and the diameter of the small valve seat 111 is obtained without considering part of pretightening force caused by the working pressure before the valve;
D. calculating the maximum lifting force required by the large valve core according to the diameter of the large valve seat, the diameter of the valve cage, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
E. calculating to obtain the maximum sealing force required by the large valve core according to the diameter of the large valve seat, the sealing coefficient, the pressure before the valve and the pressure after the valve;
F. calculating to obtain the dynamic thrust of the large valve core according to the diameter of the large valve seat, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
G. by varying the diameter d of the small valve seat 111 1 And C, comparing the data obtained according to the formulas of the step C, the step D, the step E and the step F to ensure that the sealing force of the small valve core, the lifting force of the large valve core, the sealing force of the large valve core and the dynamic thrust of the large valve core tend to be close to each other to obtainTo a valve seat design configuration that minimizes actuator thrust.
Example 2
A design method of a pilot balance cage type regulating valve comprises a valve body 15, a valve seat 14, a large valve core 12, a small valve core 11, a valve cage 13, a spring 16, a pressure plate, a valve rod, an upper valve cover and a sealing ring, and is characterized by comprising the following steps:
A. calculating the stroke and the height of the flow passage of the small valve core 11, and referring to fig. 2: small valve core 11 stroke and flow passage
Description of the symbols:
H 0 stroke of small valve element, mm H 1 Height of small valve core flow passage, mm
d 0 Diameter of upper cover of small valve core, mm d 3 Diameter of the lower end of the small valve element, mm
d 1 Small valve seat diameter, mm
Calculating the formula:
Figure GDA0003820505600000101
Figure GDA0003820505600000102
CE＝0.5tan50°
CB＝CE+AD AB＝H 0 -0.5-AD
Figure GDA0003820505600000103
and (3) simplifying calculation:
according to the structural design of the valve: d is a radical of 0 ＝d 1 +2
Obtaining the stroke of the small valve core 11:
Figure GDA0003820505600000111
B. 111 flow of small valve seat and 12 rings of large valve coreShape flow calculation D 1 Sealing ring diameter, mm
D 2 Cage diameter, mm
D 3 Diameter of the large valve core bore, mm
d 1 Small valve seat diameter, mm
ζ 1 Small valve seat flow resistance coefficient
ζ 2 -annular gap flow resistance coefficient
A 1 Small valve seat opening cross section, mm 2
P 1 Pre-valve pressure, MPaA
P 2 Pressure after valve, MPaA
P 3 Big spool bore pressure, MPaA
Q 1 Small valve seat flow, m 3 /h
Q 2 Annular gap flow, m 3 /h
Rho-medium density, kg/m 3 A 2 Annular gap area, mm 2
Calculating the formula:
Figure GDA0003820505600000112
Figure GDA0003820505600000113
Figure GDA0003820505600000114
Figure GDA0003820505600000115
Figure GDA0003820505600000116
calculating the flow according to the formula:
Figure GDA0003820505600000121
Figure GDA0003820505600000122
and (3) simplifying calculation:
according to the structural design of the valve:
d-diameter of valve seat
D 2 ＝d+2
D 1 ＝D 2 -0.5＝d+1.5
Obtaining:
Figure GDA0003820505600000123
ζ 2 ＝1.499
according to the following steps:
Figure GDA0003820505600000124
(range: 0.4 to 0.18)
Obtaining: ζ represents a unit 1 ＝0.455
Constraint conditions are as follows: the outflow rate of the small valve seat 111 is larger than or equal to the inflow rate of the annular gap of the large valve core 12, that is, the medium flowing into the valve cavity is rapidly discharged to the valve, so that the pressure in the valve cavity is not increased cumulatively. Only in this way can it be guaranteed that the pressure P3 in front of the valve approaches the pressure P2 behind the valve as much as possible, and thus that the force lifting the large spool 12 is at a small value.
Outflow rate Q 1 Not less than inflow Q 2
Figure GDA0003820505600000125
Figure GDA0003820505600000126
C. Minimum thrust and maximum thrust of the small valve spool 11 are calculated:
d 1 small valve seat diameter, mm
F 21 Small spool valve front media imbalance force, N
F 22 Small spool valve post-media imbalance force, N
F 1M Sealing force required for a small valve cartridge, N
F 1ZG -actuator closing force, N
F 1ZK -actuator opening force, N
P 1 Pre-valve pressure, MPaA
P 2 Pressure after valve, MPaA
K M Sealing coefficient
K M =25, IV of leakage etc
K M =80, leakage class V
K M =170, leakage class VI
The flow direction of the valve is upward-in-downward-out, partial valve front pressure is used for sealing the small valve core 11, and as the tight shutoff sealing force required by the small valve core 11 is fixed, the required actuator thrust is smaller as the valve front working pressure is increased. Calculating the formula:
Figure GDA0003820505600000131
Figure GDA0003820505600000132
according to fig. 5, it can be seen that the sealing force of the small valve core 11 is always larger than the lifting force of the small valve core 11, so the maximum thrust required by the small valve core 11 is the small valve core sealing force:
F 1M ＝d 1 K M ＝200d 1
thus, the small spool 11 requires no consideration for part of the preload force due to the pre-valve operating pressureThe tight shut-off sealing force of (c) is considered as 200d 1. Selecting P in consideration of actual conditions 2 ＝0，K M Minimum thrust required for 200 small spool 11:
Figure GDA0003820505600000141
D. maximum lift force required for the large spool 12 is calculated:
d-diameter of large valve seat, mm
D 2 Cage diameter, mm
F T -large spool lift force, N
P 1 Pre-valve pressure, MPaA
P 2 Pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
F 1 The force applied by the valve chamber medium to the big spool sealing ring, N
F 2 Force of the pre-valve medium on the big spool sealing ring, N
F 3 Force of the post-valve medium on the valve seat of the big valve core, N
F 4 Force of the pre-valve medium on the valve seat of the big valve core, N
Calculating the formula:
Figure GDA0003820505600000142
Figure GDA0003820505600000143
Figure GDA0003820505600000144
and (3) simplifying calculation:
according to valve structural design data, D 2 ＝d+2
The simplification yields the large spool 12 lift:
Figure GDA0003820505600000151
d-diameter of large valve seat, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 -pressure after valve, MPaA
F J Large spool medium force, N F DM Large spool sealing force, N
F 01 Force applied by the valve cavity medium to the big spool sealing ring, nk M Sealing coefficient
F 02 Force of the pre-valve medium on the big spool sealing ring, N K M =25, leakage class IV
F 03 Force of the post-valve medium on the valve seat of the big valve core, N K M =80, leakage class V
F 04 Force of pre-valve medium applied to big-spool valve seat, N K M =170, leakage class VI
E. Calculation of the maximum sealing force required for the large spool 12:
calculating the formula:
Figure GDA0003820505600000152
Figure GDA0003820505600000153
Figure GDA0003820505600000154
Figure GDA0003820505600000155
Figure GDA0003820505600000156
Figure GDA0003820505600000161
Figure GDA0003820505600000162
F. calculating the dynamic thrust of the big valve core 12:
D 2 cage diameter, mm
F DD -big spool dynamic thrust, NF 11 Force applied by the valve chamber medium to the big spool sealing ring, N
P 1 Pre-valve pressure, MPaA
P 2 -pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
F 12 Force of the pre-valve medium on the big spool sealing ring, N
F 13 Force of the post-valve medium on the valve seat of the big valve core, N
Calculating the formula:
Figure GDA0003820505600000163
Figure GDA0003820505600000164
Figure GDA0003820505600000165
Figure GDA0003820505600000166
Figure GDA0003820505600000171
G. according to d 1 、d、H 0 P3 was calculated from the design values and the following data:
d 1 small valve seat diameter, mm
d-diameter of valve seat, mm
H 0 Small valve core stroke, mm
F DD Dynamic thrust of big spool, N F 1M Small valve core sealing force, N
P 1 Pre-valve pressure, MPaA
P 2 Pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
A 1 Small valve-element flow cross-section in mm 2 A 2 Large valve core annular area, mm 2
F T -large spool lift force, N
F DM Large spool sealing force, N
F DD Dynamic thrust of big spool, N
K M Sealing coefficient
K M =25, IV leakage etc
K M =80, leakage class V
K M VI of 170, leakage, etc
CL150 P 1 ＝1.3、P 2 ＝0.4
CL300 P 1 ＝3.3、P 2 ＝0.8
CL600 P 1 ＝7.3、P 2 ＝1.5
CL900 P 1 ＝10.3、P 2 ＝2.4
CL1500 P 1 ＝16.3、P 2 ＝3.8
CL2500 P 1 ＝27.3、P 2 ＝5.5
Figure GDA0003820505600000181
A 2 ＝0.785d+1.3737
Figure GDA0003820505600000182
And calculated according to the following formula: f 1M ，F T ，F DM ，F DD
F 1M ＝200d 1
Figure GDA0003820505600000183
Figure GDA0003820505600000184
Figure GDA0003820505600000185
By varying the diameter d of the small valve seat 111 1 Value of so that F 1M ，F T ，F DM ，F DD And the thrust tends to be close to the maximum, so that the aim of minimizing the thrust of the actuator is fulfilled.
In summary, the above-mentioned embodiments are only preferred embodiments of the present invention, and all equivalent changes and modifications made in the claims of the present invention should be covered by the claims of the present invention.

Claims (6)

1. The design method of the pilot balance cage type regulating valve comprises a valve body, a valve seat, a large valve core, a small valve core, a valve cage, a spring, a pressing plate, a valve rod, an upper valve cover and a sealing ring, and is characterized by comprising the following steps of:
A. calculating the relationship between the height of the flow channel and the stroke of the small valve core according to the structure of the small valve seat;
B. b, calculating the opening cross section area and the annular gap area of the small valve seat according to the data obtained in the step A, and further calculating the flow of the small valve seat and the annular gap flow of the large valve core to enable the outflow flow of the small valve seat to be not less than the inflow flow of the annular gap of the large valve core;
C. calculating the sealing force required by the small valve core, and obtaining the relation between the sealing force required by the small valve core and the diameter of the small valve seat according to the actual sealing coefficient to obtain the maximum thrust of the small valve core; the relation between the minimum thrust required by the small valve core and the diameter of the small valve seat is obtained without considering part of pretightening force caused by the working pressure before the valve;
D. calculating the maximum lifting force required by the large valve core according to the diameter of the large valve seat, the diameter of the valve cage, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
E. calculating to obtain the maximum sealing force required by the large valve core according to the diameter of the large valve seat, the sealing coefficient, the pressure before the valve and the pressure after the valve;
F. calculating to obtain the dynamic thrust of the large valve core according to the diameter of the large valve seat, the pressure before the valve, the pressure after the valve and the pressure of the valve cavity;
G. by varying the diameter d of the small valve seat 1 Comparing the data obtained according to the formulas of the steps C, D, E and F to enable the sealing force of the small valve core, the lifting force of the large valve core, the sealing force of the large valve core and the dynamic thrust of the large valve core to approach to each other, and obtaining a valve seat design structure with the minimum thrust of the actuator;
the design method of the pilot balance cage type regulating valve comprises the following steps:
A. measuring and calculating the relationship between the small valve core stroke and the flow passage height,
Figure FDA0003832913860000011
B. calculating the flow of the small valve seat and the annular gap flow of the large valve core, and using the H obtained in the step A 1 ，
Figure FDA0003832913860000021
Figure FDA0003832913860000022
Figure FDA0003832913860000023
Figure FDA0003832913860000024
Figure FDA0003832913860000025
Figure FDA0003832913860000026
Figure FDA0003832913860000027
The outflow flow of the small valve seat is more than or equal to the inflow flow of the annular gap of the large valve core, so that the requirement of
Figure FDA0003832913860000028
Then the
Figure FDA0003832913860000029
C. Calculating the maximum thrust of the small valve core
Calculating the formula:
Figure FDA00038329138600000210
Figure FDA00038329138600000211
F 1M ＝d 1 K M
D. the maximum lift force required for the large spool is calculated,
Figure FDA00038329138600000212
Figure FDA00038329138600000213
Figure FDA00038329138600000214
Figure FDA0003832913860000031
E. the maximum sealing force required by the large valve core is calculated,
Figure FDA0003832913860000032
Figure FDA0003832913860000033
Figure FDA0003832913860000034
F. calculating the dynamic thrust of the big valve core,
Figure FDA0003832913860000035
Figure FDA0003832913860000036
Figure FDA0003832913860000037
Figure FDA0003832913860000038
G. by varying the diameter d of the small valve seat 1 Value of so that F 1M ，F T ，F DM ，F DD The thrust of the actuator is close to the minimum, and the aim of minimizing the thrust of the actuator is fulfilled, and the calculation is carried out according to the following formula:
F 1M ＝200d 1
Figure FDA0003832913860000039
Figure FDA00038329138600000310
Figure FDA0003832913860000041
wherein the meaning of a parameter and its unit are,
in the step A:
H 0 -small valve element stroke, mm;
H 1 -small spool flow channel height, mm;
d 0 the diameter of the upper cover of the small valve core is mm;
d 3 -the diameter of the lower end of the small valve element, mm;
d 1 -small valve seat diameter, mm;
in the step B:
D 1 sealing ring diameter, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 -pressure after valve, MPaA
D 3 Diameter of the large valve core bore, mm P 3 Big spool bore pressure, MPaA
d 1 Small valve seat diameter, mm Q 1 Small valve seat flow, m 3 /h
ζ 1 Small valve seat flow resistance factor Q 2 Annular gap flow, m 3 /h
ζ 2 -annular gap flow resistance coefficient ρ -Medium Density, kg/m 3
A 1 Small valve seat opening cross section, mm 2 A 2 Annular gap area, mm 2
In the step C:
P 1 pre-valve pressure, MPaA
F 21 Small spool valve front media imbalance force, nP 2 -pressure after valve, MPaA
F 22 Small spool valve post-media imbalance force, nk M Sealing coefficient
F 1M Sealing force required for a small valve cartridge, NK M =25, leakage class IV
F 1ZG Actuator closing force, NK M =80, leakage class V
F 1ZK Actuator opening force, NK M =170, leakage class VI
In the step D:
d-diameter of large valve seat, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 Pressure after valve, MPaA
F T Large spool lifting force, nP 3 Valve pocket pressure, MPaA
F 1 Force applied by the valve chamber medium to the big spool sealing ring, N
F 2 Force of pre-valve medium applied to big spool seal ring, N
F 3 Force of the post-valve medium on the valve seat of the big valve core, N
F 4 Force of pre-valve medium on the valve seat of the big poppet, N
In the step E:
d-diameter of large valve seat, mm P 1 Pre-valve pressure, MPaA
D 2 Cage diameter, mm P 2 Pressure after valve, MPaA
F J -big spool medium force, nf DM Large spool sealing force, N
F 01 Force applied by the valve cavity medium to the big spool sealing ring, nk M Sealing coefficient
F 02 Force of pre-valve medium applied to big spool seal ring, nk M =25, leakage class IV
F 03 Force of the post-valve medium on the valve seat of the big valve core, N K M =80, leakage class V
F 04 Force of the pre-valve medium on the valve seat of the big valve core, N K M VI of leakage =170, etc
In the step F:
D 2 cage diameter, mm
F DD Dynamic thrust of big spool, N
F 11 Force applied by the valve chamber medium to the big spool sealing ring, N
P 1 Pre-valve pressure, MPaA
P 2 -pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
F 12 Force of pre-valve medium applied to big spool seal ring, N
F 13 Force of the post-valve medium on the valve seat of the big valve core, N
Step G:
d 1 small valve seat diameter, mm
d-diameter of valve seat, mm
H 0 Small valve core stroke, mm
F 1M Small valve core sealing force, N
P 1 Pre-valve pressure, MPaA
P 2 Pressure after valve, MPaA
P 3 Valve pocket pressure, MPaA
A 1 Small valve-element flow cross-section in mm 2
A 2 Large valve core annular area, mm 2
F T Large spool lifting force, N
F DM -large spool sealing force, N.
2. The method as claimed in claim 1, further comprising designing the pilot balance cage valve according to d 1 、d、H 0 P was calculated from the design values and the following data 3 The value of (c):
Figure FDA0003832913860000071
3. the method as claimed in claim 1, wherein the valve has a structure d 0 ＝d 1 +2
And (3) obtaining a small valve core stroke:
Figure FDA0003832913860000072
4. the design method of a pilot balance cage type regulating valve according to claim 1, wherein in the step C, P is selected in consideration of actual working conditions 2 ＝0，K M ＝200
Obtaining the minimum thrust required by the small valve core
Figure FDA0003832913860000073
5. The method as claimed in claim 1, wherein the tight shut-off sealing force required by the small spool is considered as 200d1 regardless of the partial preload force due to the pre-valve operating pressure, the small spool sealing force is always larger than the lifting force of the small spool, and thus the maximum thrust force required by the small spool is F 1M ＝d 1 K M ＝200d 1 。
6. The design method of the pilot balance cage type regulating valve according to claim 1, wherein in the step D,
according to valve structural design data, D 2 ＝d+2
The lifting force of the large valve core is obtained through simplification:
Figure FDA0003832913860000074
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