CN110206712B - Unloading device of reciprocating compressor air quantity adjusting system - Google Patents

Unloading device of reciprocating compressor air quantity adjusting system Download PDF

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CN110206712B
CN110206712B CN201910436626.XA CN201910436626A CN110206712B CN 110206712 B CN110206712 B CN 110206712B CN 201910436626 A CN201910436626 A CN 201910436626A CN 110206712 B CN110206712 B CN 110206712B
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unloader
force
representing
spring
valve
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CN110206712A (en
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周超
张进杰
江志农
王瑶
孙旭
祁桢
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Beijing University of Chemical Technology
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Beijing University of Chemical Technology
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

The invention relates to an unloader of a reciprocating compressor air volume adjusting system, aiming at the problems of the unloader in the aspects of impact, abrasion, noise and service life commonly existing in the application of the existing reciprocating compressor stepless air volume adjusting actuating mechanism, safety accidents such as sparks generated by impact are avoided by depending on impact parts and the optimization of an impact area, and the impact noise of the unloader is reduced; the anti-rotating body structure is adopted on the valve seat of the unloader, so that the conditions of abrasion and spark danger caused by friction between the press fork of the unloader and the valve seat are avoided, and the unloader can safely operate; the lower limit structure design of the unloader is optimized, and the defect that the service life of the valve plate is shortened due to the fact that the unloader depends on valve plate limit is avoided; according to the regulation requirement of the stepless air quantity regulation system of the reciprocating compressor, a mathematical calculation model of the return spring of the unloader is provided.

Description

Unloading device of reciprocating compressor air quantity adjusting system
Technical Field
The invention relates to an unloader of a reciprocating compressor air quantity adjusting system.
Background
The reciprocating compressor occupies an important position in the petrochemical industry in China, is quite wide in application, and is mainly used for gas treatment and transportation. In the production of the petrochemical industry, the reciprocating compressor often causes different required gas amounts due to the change of the process, so that the gas amount is regulated in order to meet the gas amount requirements under different working conditions, and the application of stepless gas amount regulation not only meets the gas amount requirements, but also has the advantages of energy conservation, stable pressure, convenience in operation and the like.
The working principle of adjusting the air displacement by jacking an air inlet valve is as follows: at the compression stage of the reciprocating compressor, a valve plate of the air inlet valve is forcibly jacked open by the actuating mechanism, and the air flows back to the air inlet pipeline, so that the purpose of adjusting the air quantity is achieved. The adjusting device for opening the air suction valve in the top is disclosed at home and abroad, the Helbi lattice at home is A patent CN03158561 applied at home, the patent US-A-5695325 at foreign country and the patent EP-A-0893605 are also adjusting devices for opening the air suction valve in the top, and the patent CN200610155395 applied at Zhejiang university at home and the patent CN201110117265 applied at the fertilizer combination communication research institute are also disclosed at home and abroad.
Aiming at the problems that the adjusting devices in the prior patents are provided with unloaders, the unloading devices are badly influenced in application, the structural design of the unloaders is unreasonable, impact or friction can occur, the temperature is too high, the risk of spark generation is caused, the valve plate is seriously impacted, and the design calculation of an unloading device reset spring is not provided, the invention provides a novel unloading device structure of a reciprocating compressor air quantity adjusting system, and the badly influence is skillfully solved.
Disclosure of Invention
1. The unloading device of the reciprocating compressor air quantity adjusting system is characterized in that:
1) the unloader consists of an air inlet valve, an unloader body and an anti-rotation part, wherein the air inlet valve structure comprises a valve seat (1), a lift limiter (2), an air inlet valve spring (3), a valve plate (4), a cylindrical pin A (5), a stud (6), a cylindrical pin B (7) and a cylindrical pin C (8); the main structure of the unloader comprises a pressure fork (9), a sliding sleeve (10), a buffer box (11), a buffer ring (12), a buffer box cover (13), a top plate (14), an elastic retainer ring (15), an unloader outer shell (16), a gland (17), an elastic washer (18), a threaded column (19), a return spring (20), a spacer bush (21) and a noise reduction washer (23); the main structure of the anti-rotation part comprises a bolt (22), an anti-rotation body (24) and an anti-rotation spacer bush (25);
2) the unloader main body structure is fixed on the upper surface of a valve seat (1) of an air inlet valve structure by a locking nut, an unloader spacer bush (21) is sleeved on a stud (6) of the air inlet valve, a sliding sleeve (10) is installed in a ring groove of the spacer bush (21), a buffer box (11) is positioned between a buffer box cover (13) and the spacer bush (21), a return spring (20) is installed between the buffer box cover (13) and a top plate (14), an elastic retainer ring (15) limits the axial movement of a gland (17), a press fork (9) is in interference connection with an unloader outer shell (16), a mandril (26) is arranged on the unloader top plate (14), and an anti-rotation body structure is fixed on the valve seat (1) of the air inlet valve structure by a bolt (22);
3) in the air suction working process of the compressor, the hydraulic pressure provided by the hydraulic driving mechanism acts on the ejector rod (26), the unloader overcomes the spring force, the friction force and the gas force to finish the action of pushing the valve plate (4) downwards, and the valve plate is kept static at the lower limit position; the hydraulic pressure provided by the hydraulic driving mechanism acts on the ejector rod (26) firstly, the hydraulic pressure is transmitted to the unloading device top plate (14) through the ejector rod (26), the hydraulic pressure overcomes spring force and friction force, and moves downwards along the guide assembly together with the unloading device outer shell (16) and the pressure fork (9), the unloading device outer shell (16) is separated from the buffer box (11), and the noise reduction gasket (23) moving to the valve seat (1) keeps static;
4) in the compression working process of the compressor, the motion state of the unloader is divided into two states, one is that the unloader keeps still under the action of hydraulic pressure P, and a pressure fork (9) jacks an air inlet valve plate (4) to ensure that an air suction valve is in an open state in the compression process of the compressor, so that part of air flows back to an air inlet pipeline through the air inlet valve, and the air quantity adjusting function is realized; the other is that the hydraulic pressure is reduced, the unloader overcomes the hydraulic pressure and the friction force under the action of a return spring (20) and the gas force, the top plate (14) drives the top plate (14) to drive the unloader outer shell (16) and the pressure fork (9) to move upwards along the guide assembly together, and the unloader withdraws to the upper limit;
further, the method is characterized in that the calculation model of the stiffness of the unloader return spring (20) is as follows:
Figure BDA0002070713920000021
wherein:
k: represents the stiffness of the return spring (20);
Fs1: representing the spring force of a return spring (20) when the displacement of the unloader is zero;
Fs2representing the spring force of the return spring (20) when the unloader displacement is L, L representing the maximum stroke of the unloader;
Fp1: representing the hydraulic pressure acted on the mandril (26) by a hydraulic driving mechanism in the ejection process of the unloader;
Fg2: representing the gas force of the gas in the suction valve chamber acting on the mandril (26);
m: representing the total mass of the unloader outer shell (16), the top plate (14), the pressure fork (9), the elastic retainer ring (15), the gland (17) and the ejector rod (26);
α, representing the installation angle of the unloader, wherein the angle is the included angle between the central line of the unloader and the vertical line of the ground;
g: represents the acceleration of gravity;
f: representing the friction force of the unloader and the driving mechanism;
t represents the action time required by the unloading device to move from a static state to a displacement L in the ejection process, and the value is taken within the range of 0.008s to 0.02s in consideration of the adjustment effect of the air quantity adjustment system;
the boundary conditions and constraint conditions calculated by the above formula are:
1) the boundary conditions are as follows:
(A)
Figure BDA0002070713920000031
representing that the speed at the initial moment is 0 in the ejection process of the unloader;
(B)x(t)t＝00; representing that the displacement at the initial moment is 0 in the ejection process of the unloader;
(C)x(t)t＝Tl, representing the displacement of the unloader is L when the time is T in the ejecting process of the unloader;
(D)F＝Fg1+Fs2+Fg2(ii) a Representing the boundary condition that the resultant force of the spring force of the return spring (20) and the gas force acting on the pressure fork (9) and the valve plate (4) needs to be met at the initial withdrawal moment of the unloader;
wherein:
x: representing the unloader displacement;
f: representing the initial withdrawal moment of the unloader, the resultant force of the spring force of the return spring (20) and the gas force acting on the pressure fork (9) and the valve plate (4);
Fg1: representing the resultant force of the gas acting on the upper surface and the lower surface of the suction valve plate (4);
2) the constraints are as follows:
(E)Fs1＞Fp2-Fg2+mgcosα+f
(F)Fs2＜Fp1-Fg2-f+mgcosα
(E) the formula shows that when the displacement of the unloader is zero, the spring force of the reset spring (20) needs to be larger than the resultant force of oil pressure, gas force, gravity and friction force acting on the ejector rod (26) in the withdrawing process, so that the unloader can be ensured to withdraw to the displacement zero point and keep still;
(F) the formula shows that the spring force of a return spring (20) when the displacement of the unloader is L needs to be smaller than the resultant force of oil pressure, gas force, gravity and friction force acting on a mandril (26) in the ejection process, so that the unloader can move to the displacement L and keep still;
when (F)p2-Fg2When + mgcos α + F) is negative, (F)p2-Fg2+ mgcos α + f) is set to 0;
Fp2: representing the hydraulic force acted on the mandril (26) by the hydraulic driving mechanism when the unloader withdraws.
Further, the method is characterized in that the calculation method of the spring force, the gas force and the hydraulic force in the formula comprises the following steps:
1) spring force
Figure BDA0002070713920000041
2) Force of gas
Figure BDA0002070713920000042
3) Hydraulic pressure
Figure BDA0002070713920000043
Wherein:
x1: represents the precompression of the return spring (20) when the unloader displacement is zero;
pcy: representative of compressor in-cylinder pressure;
ps: representing the gas pressure in the valve chamber of the suction valve;
Asv: representing the area of the upper surface or the lower surface of a valve plate (4) of the suction valve;
Al: represents the cross section area of the mandril (26);
p1: representing the oil pressure provided by the hydraulic driving mechanism when the unloader is ejected out;
p2: representing the oil pressure provided by the hydraulic drive mechanism when the unloader is withdrawn.
The model of the stiffness of the return spring of the unloader is characterized in that the stiffness k of the spring and the precompression x are obtained1Then, according to the mechanical design manual, other parameters of the spring are designed:
1) confirming the installation space of the diameter direction of the spring and giving the middle diameter D of the spring preliminarily2
2) Calculating the diameter of the section of the spring: determining the spring material, and finding out [ tau ] according to national standard]Calculation of spring section diameter
Figure BDA0002070713920000051
And
Figure BDA0002070713920000052
and (3) repeating the steps 1) and 2), repeatedly calculating, stopping the calculation when d' is not less than d, and taking the value as the section diameter of the spring.
3) Effective number of turns n of spring1
Figure BDA0002070713920000053
4) Actual stiffness of the spring: obtaining n 'after taking and shaping according to the effective number of turns obtained in the step 3)'1And calculating the actual stiffness k' of the spring.
Figure BDA0002070713920000054
5) Spring pitch p
Figure BDA0002070713920000055
6) Spring compression height Hb
Hb＝(n′1+2-0.5)d
The detailed parameter calculation of the unloader return spring is characterized in that the constraint conditions of the unloader return spring are as follows:
constraint conditions are as follows:
(1)Hb≤H0-x1-L
drawings
FIG. 1 is a schematic view of an unloader configuration;
FIG. 2 is an assembly view of the unloader with the pressure cap, valve cover, and drive mechanism;
FIG. 3 is an analytical graph of the load from the unloader return spring;
FIG. 4 is a graph of in-cylinder pressure at 20-100% load;
Detailed Description
The invention is further illustrated with reference to the figures and examples.
FIG. 1 is a schematic diagram of an unloader structure, wherein the unloader is composed of an air inlet valve, an unloader body and an anti-rotation part, and the air inlet valve structure comprises (1) a valve seat, (2) a lift limiter, (3) an air inlet valve spring, (4) a valve plate, (5) a cylindrical pin A, (6) a stud, (7) a cylindrical pin B and (8) a cylindrical pin C; the main structure of the unloader comprises (9) a pressure fork, (10) a sliding sleeve, (11) a buffer box, (12) a buffer ring, (13) a buffer box cover, (14) a top plate, (15) an elastic retainer ring, (16) an unloader outer shell, (17) a gland, (18) an elastic washer, (19) a threaded column, (20) a return spring, (21) a spacer sleeve and (23) a noise reduction washer; the main structure of the anti-rotation part comprises a bolt (22), an anti-rotation body (24) and an anti-rotation spacer sleeve (25); the unloader body is fixed on the valve seat (1) through a stud (6) and a nut of the air valve, the pressure fork (9) is fixed on the unloader outer shell (16) through interference fit, and the anti-rotating body part is fixed on the valve seat through a bolt (22).
FIG. 2 is an assembly diagram of the unloader, a pressure cover, a valve cover and a driving mechanism, wherein a push rod (26) is firstly installed in the unloader, then the unloader is installed in an air chamber of the reciprocating compressor, then the pressure cover is installed on an outer ring step of a valve seat of an air inlet valve (1), and finally the valve cover and the push rod driving mechanism are sequentially installed.
FIG. 3 is a force analysis diagram of the unloader return spring, wherein the (20) return spring can be divided into three states, namely an uncompressed state, a pre-compressed state and a maximum compressed state, a top plate (14) on the (20) return spring is taken as an analysis object, a hydraulic driving force P and a gravity mgcos α are applied downwards, and a gas pressure F is applied upwardsg2Spring force kx, friction force f, (20) the stroke of the return spring from the pre-compression state to the maximum compression state is L, and the required time is less than or equal to tmax。
Fig. 4 is a pressure diagram of a cylinder of a laboratory bench compressor, and in the backflow stage, even if the valve plate is in an open state, the pressure in the cylinder can still rise due to the reason that the piston compresses gas and the like, and when the backflow process is finished, the pressure difference between the upper surface and the lower surface of the valve plate reaches the maximum: p is a radical ofA-pB。
The spring adopted in the embodiment of the invention is a cylindrical compression spring, and the design process of the return spring of the unloader (20) mainly comprises the following steps:
(1) the unit parameters and the mechanical structure correlation coefficients of the stepless air quantity regulating system are determined, and are shown in table 1:
TABLE 1 air quantity regulating system size
Figure BDA0002070713920000061
Figure BDA0002070713920000071
TABLE 2 reciprocating compressor bench parameters and suction and discharge valve parameters
Figure BDA0002070713920000072
Figure BDA0002070713920000081
(2) According to the data in the first step, combining a spring stiffness calculation method to obtain the spring stiffness and the precompression amount;
(3) checking whether the spring stiffness and the pre-compression amount obtained in the second step meet the limiting conditions, and if so, designing a complete spring by combining actual parameters such as spring installation space and the like; if the constraint condition is not met, the unloading device withdrawal initial force needs to be adjusted, and the spring stiffness and the pre-compression amount are solved again until the requirement is met;
(4) and testing the spring test effect.
According to the dimensions of table 1, a spring design was performed:
1. system individual force calculation
1) Chamber pressure (intake pressure) force:
Figure BDA0002070713920000082
2) hydraulic drive pressure acting force:
Figure BDA0002070713920000083
Figure BDA0002070713920000084
3) weight of gravity:
mgcosα＝2×9.8×cos30°＝17N
4) the gas resultant force of the upper surface and the lower surface of the valve sheet in the backflow process is as follows:
Fg1＝(pA-pB)Asv＝(114237.64-100000)×0.0043＝61.2N
2. calculating spring rate range
Substituting the parameters and the system acting force results in the table 1 into the mathematical model to obtain:
Figure BDA0002070713920000085
Figure BDA0002070713920000091
the spring rate and the precompression can be obtained by simultaneous equations (1) and (2):
Figure BDA0002070713920000092
3. checking spring limit conditions
The spring rate and the pre-compression amount are substituted into equation (9) for verification as follows:
Figure BDA0002070713920000093
the condition is satisfied.
4. Design of springs
1) Spring installation space
According to the structural size of the unloader, the unloader comprises the following components: the spring installation space is 15-28 mm;
spring free height: 40.9+ 7.1-48 mm.
2) Spring section diameter calculation
The spring material is 65Mn steel wire, and the diameter of the spring section needs to be calculated
Figure BDA0002070713920000094
And
Figure BDA0002070713920000095
performing an iterative calculation wherein D2The diameter is determined to be 20mm according to the installation space, and when d ═ d, the sectional diameter of the spring is determined. And looking up a table and repeatedly calculating to obtain C-5, the section diameter of the spring is as follows:
Figure BDA0002070713920000096
3) the effective number of turns of the spring:
Figure BDA0002070713920000097
4) rounding the effective number of turns obtained according to 3) to 6 turns, the spring rate is:
Figure BDA0002070713920000101
5) spring pitch:
Figure BDA0002070713920000102
6) spring pressing and height:
Hb＝(n′1+2-0.5)d＝(6+2-0.5)×4＝30mm
the height of the spring when it reaches the maximum compression is: 48-7.1 is 40.9>30mm, so the requirement is met. Table 3 is a table of spring parameters used in the air quantity adjusting system.
TABLE 3 gas quantity regulating System used spring parameters
Figure BDA0002070713920000103
。

Claims (2)

1. An unloading device of a reciprocating compressor air quantity adjusting system,
1) the unloader consists of an air inlet valve, an unloader body and an anti-rotation part, wherein the air inlet valve structure comprises a valve seat (1), a lift limiter (2), an air inlet valve spring (3), a valve plate (4), a cylindrical pin A (5), a stud (6), a cylindrical pin B (7) and a cylindrical pin C (8); the main structure of the unloader comprises a pressure fork (9), a sliding sleeve (10), a buffer box (11), a buffer ring (12), a buffer box cover (13), a top plate (14), an elastic retainer ring (15), an unloader outer shell (16), a gland (17), an elastic washer (18), a threaded column (19), a return spring (20), a spacer bush (21) and a noise reduction washer (23); the main structure of the anti-rotation part comprises a bolt (22), an anti-rotation body (24) and an anti-rotation spacer bush (25);
2) the unloader main body structure is fixed on the upper surface of a valve seat (1) of an air inlet valve structure by a locking nut, an unloader spacer bush (21) is sleeved on a stud (6) of the air inlet valve, a sliding sleeve (10) is installed in a ring groove of the spacer bush (21), a buffer box (11) is positioned between a buffer box cover (13) and the spacer bush (21), a return spring (20) is installed between the buffer box cover (13) and a top plate (14), an elastic retainer ring (15) limits the axial movement of a gland (17), a press fork (9) is in interference connection with an unloader outer shell (16), a mandril (26) is arranged on the unloader top plate (14), and an anti-rotation body structure is fixed on the valve seat (1) of the air inlet valve structure by a bolt (22);
3) in the air suction working process of the compressor, the hydraulic pressure provided by the hydraulic driving mechanism acts on the ejector rod (26), the unloader overcomes the spring force, the friction force and the gas force to finish the action of pushing the valve plate (4) downwards, and the valve plate is kept static at the lower limit position; the hydraulic pressure provided by the hydraulic driving mechanism acts on the ejector rod (26) firstly, the hydraulic pressure is transmitted to the unloading device top plate (14) through the ejector rod (26), the hydraulic pressure overcomes spring force and friction force, and moves downwards along the guide assembly together with the unloading device outer shell (16) and the pressure fork (9), the unloading device outer shell (16) is separated from the buffer box (11), and the noise reduction gasket (23) moving to the valve seat (1) keeps static;
4) in the compression working process of the compressor, the motion state of the unloader is divided into two states, one is that the unloader keeps still under the action of hydraulic pressure P, and a pressure fork (9) jacks an air inlet valve plate (4) to ensure that an air suction valve is in an open state in the compression process of the compressor, so that part of air flows back to an air inlet pipeline through the air inlet valve, and the air quantity adjusting function is realized; the other is that the hydraulic pressure is reduced, the unloader overcomes the hydraulic pressure and the friction force under the action of a return spring (20) and the gas force, the top plate (14) drives the top plate (14) to drive the unloader outer shell (16) and the pressure fork (9) to move upwards along the guide assembly together, and the unloader withdraws to the upper limit;
the method is characterized in that a calculation model of the rigidity of the unloader return spring (20) is as follows:
Figure FDA0002481422130000021
wherein:
k: represents the stiffness of the return spring (20);
Fs1: representing the spring force of a return spring (20) when the displacement of the unloader is zero;
Fs2representing the spring force of the return spring (20) when the unloader displacement is L, L representing the maximum stroke of the unloader;
Fp1: representing the hydraulic pressure acted on the mandril (26) by a hydraulic driving mechanism in the ejection process of the unloader;
Fg2: representing the gas force of the gas in the suction valve chamber acting on the mandril (26);
m: representing the total mass of the unloader outer shell (16), the top plate (14), the pressure fork (9), the elastic retainer ring (15), the gland (17) and the ejector rod (26);
α, representing the installation angle of the unloader, wherein the angle is the included angle between the central line of the unloader and the vertical line of the ground;
g: represents the acceleration of gravity;
f: representing the friction force of the unloader and the driving mechanism;
t represents the action time required by the unloading device to move from a static state to a displacement L in the ejection process, and the value is taken within the range of 0.008s to 0.02s in consideration of the adjustment effect of the air quantity adjustment system;
the boundary conditions and constraint conditions calculated by the above formula are:
1) the boundary conditions are as follows:
(A)
Figure FDA0002481422130000022
representing that the speed at the initial moment is 0 in the ejection process of the unloader;
(B)x(t)|t＝00; representing that the displacement at the initial moment is 0 in the ejection process of the unloader;
(C)x(t)|t＝Tl, representing the displacement of the unloader is L when the time is T in the ejecting process of the unloader;
(D)F＝Fg1+Fs2+Fg2(ii) a Representing the boundary condition that the resultant force of the spring force of the return spring (20) and the gas force acting on the pressure fork (9) and the valve plate (4) needs to be met at the initial withdrawal moment of the unloader;
wherein:
x: representing the unloader displacement;
f: representing the initial withdrawal moment of the unloader, the resultant force of the spring force of the return spring (20) and the gas force acting on the pressure fork (9) and the valve plate (4);
Fg1: representing the resultant force of the gas acting on the upper surface and the lower surface of the suction valve plate (4);
2) the constraints are as follows:
(E)Fs1>Fp2-Fg2+mg cosα+f
(F)Fs2<Fp1-Fg2-f+mg cosα
(E) the formula shows that when the displacement of the unloader is zero, the spring force of the reset spring (20) needs to be larger than the resultant force of oil pressure, gas force, gravity and friction force acting on the ejector rod (26) in the withdrawing process, so that the unloader can be ensured to withdraw to the displacement zero point and keep still;
(F) the formula shows that the spring force of a return spring (20) when the displacement of the unloader is L needs to be smaller than the resultant force of oil pressure, gas force, gravity and friction force acting on a mandril (26) in the ejection process, so that the unloader can move to the displacement L and keep still;
when (F)p2-Fg2+ mg cos α + F) is negative, (Fp2-Fg2+ mg cos α + f) set to 0;
Fp2: representing the hydraulic force acted on the mandril (26) by the hydraulic driving mechanism when the unloader withdraws.
2. The method for applying the unloader of the reciprocating compressor air quantity regulating system as claimed in claim 1, wherein the calculation method of the spring force, the air force and the hydraulic force in the formula is as follows:
1) spring force
Figure FDA0002481422130000031
2) Force of gas
Figure FDA0002481422130000032
3) Hydraulic pressure
Figure FDA0002481422130000033
Wherein:
x1: represents the precompression of the return spring (20) when the unloader displacement is zero;
pcy: representative of compressor in-cylinder pressure;
ps: representing the gas pressure in the valve chamber of the suction valve;
Asv: representing the area of the upper surface or the lower surface of a valve plate (4) of the suction valve;
Al: represents the cross section area of the mandril (26);
p1: representing the oil pressure provided by the hydraulic driving mechanism when the unloader is ejected out;
p2: representing the oil pressure provided by the hydraulic drive mechanism when the unloader is withdrawn.
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CN110728044B (en) * 2019-09-30 2022-08-02 哈尔滨工程大学 Integrated calculation method for gas pressure state in piston ring groove

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