Multi-purpose valve

FIELD: mechanics.

SUBSTANCE: invention related to hydraulic hardware and is designed to smoothly adjust working fluid for rate. The multi-purpose valve shutoff-and-governor element cylindrical guide part diameter is smaller than that of the element cylindrical sealing collar. The diameter of the aforesaid element upper stem located in the valve pot is smaller than that of the lower stem located on the valve outlet. The said diameters in the entire range of pressures in the valve outlet channel satisfy the terms of the specified set of inequalities.

EFFECT: higher reliability hermetic valve orifice size closing under abnormal conditions and higher accuracy in working fluid flow rate control over the entire valve orifice size variation range.

2 cl, 2 dwg

 

The invention relates to the field of hydraulic equipment, namely, pressure shut-off and control valves, i.e. valves, designed for modulating control of fluid flow in the area between the power source of high pressure and the hydraulic motor from zero (at full overlap of the bore of the valve) to the corresponding maximum (when the opening of the bore of the valve at maximum), and can be used, in particular, in the hydraulic control of the forging and stamping presses.

Known shut-off and regulating valve, comprising a housing with a flanged inlet and outlet channels in the bore which holds the saddle with the sealing chamfer and the Central cylindrical sealing band having a diameter not larger inner diameter of the sealing chamfer seat and orifice and placed shut-off and control element coaxially with the guide cylindrical portion, a collar with stop chamfered, second cylindrical sealing band and shank associated with two diametrically spaced rods, the ends of which are through sealed openings facing in opposite directions beyond the valve body, the valve body is sealed with a lid located in relation to shut-off and control ele is into side, opposite the valve seat, and shut-off and control element is installed with the education side of his collar inputs connected to connecting the input channel of the valve, to form between the surfaces of the shank shut-off and control element and the Central aperture of the saddle channel connected with connecting the output channel of the valve, and to form between the surfaces of the shut-off and control element and cover nallathanni cavity [1].

In the specified shut-off and control valve nadupana cavity through the throttle holes are connected with connecting input channel, and shut-off and control element provided with an axial hole and a cavity discharge seat, discharge valve, a shutter which is placed in the cavity of the discharge and is rigidly connected with the rod positioned in the axial hole shut-off and control element and provided with a longitudinal undercut ledge and forming a stop shut-off and control element from the side opposite to the seat of the discharge valve while the cavity is in communication with the discharge nallathanni cavity and through the seat of the discharge valve and the longitudinal undercut - output channel. The shank shut-off and control element provided with a tapered and aimed for the top of the cone in the direction of the output channel, and directing cilindrica the Kai part shut-off and control element has a diameter not less than the greatest diameter of the tapered shank, equal to the diameter of the cylindrical sealing band.

In this design the top (located at the side of nallathanni cavity) and the bottom (located at the side of the outlet channel of the valve rods are connected with shut-off and control element can move relative to it in the axial direction by a gap equal to the move shutter discharge valve and the shut-off and control element, and have the same diameters.

In the absence of a control signal for opening the considered valve shut-off and control element of the resultant force of the pressure fluid is pressed against the saddle. Since this force can be significant to prevent the destruction of the sealing chamfer seat and stop chamfer shut-off and control element (due to the large contact stresses) the surface area of contact must have a value not less than the certain limit. The limit values specified area for at least determines the complexity lapping sealing chamfer seat and stop chamfer shut-off and control element to a state that ensures the tightness of the specified pairs.

To reduce the effort which is required of the steering actuator shut-off and control valve, provided discharge to the of apan (the output link of the steering actuator is connected with one of the rods, rigidly connected with the gate of the discharge valve).

The presence of the unloading valve, placed in the inner cavity shut-off and control element that complicates the design of the known shut-off and control valve and reduces the reliability of its operation due to possible leaks additional pair valve: gate-saddle-relief valve.

The presence of two valve pairs in the considered structures (both of which require lapping) complicates the manufacture of the valve and repair work in process operation.

In the operation of this valve (especially in the contaminated working fluid) may blur (increase in diameter) throttle openings through which nadupana cavity are connected with connecting input channel. Due to the opening of the bore dump valve to the stop protrusion its shutter in shut-off and control element of the pressure loss on the throttle opening ceteris paribus be less pressure in nallathanni cavity above, and the force required for lifting valves of an element relative to its seat, more that predetermines the necessity of overstating the required effort of the steering actuator at the stage of its manufacture (with the corresponding increase in the dimensions and masses of the drive).

At the small opening of the bore between the shut-off chamfer shut-off and control element and the sealing chamfer his seat (after the stop ledge shutter discharge valve shut-off and control element), when it is not opened or opened by a small amount the flow area between the cylindrical sealing belts shut-off and control element and seat, the pressure in the space between shut-off and control element and the saddle on the site, limited to the specified cylindrical sealing bands and the entrance to the gap between the locking chamfer shut-off and control element and the sealing chamfer seat, rises to a value equal to or close to the pressure in the inlet valve. In this regard, if the diameter of the guide cylinder part shutoff element more (which is one of the two possible interpretations of the concept of "not less than") the largest diameter of the tapered shank, which is equal to the diameter of the cylindrical sealing band shut-off and control element, hydraulic pressing shut-off and control element to the projection gate of the discharge valve cannot be guaranteed and under the influence of changing the balance of power fluid pressure may unmanaged displacement of the shut-off and control element from its seat, reducing Russ is coordination between the movement of the shutter discharge valve and shut-off and control element. This entails a reduction of the cross-section area of the discharge valve and the pressure increase in nallathanni cavity, which leads, in turn, to the movement of the shut-off and control element in the opposite direction and so on.

Thus, at small discoveries orifice valve is not possible the emergence of a longitudinal vibration shut-off and control element, accompanied by uncontrollable changes of the cross-section area of the valve and accordingly the flow rate of the working fluid through it blows shut-off and control element on the ledge of the shutter and stop chamfer relief valve, as a result of increased noise and wear of the valve, which reduces the reliability of the valve.

Installation is rigidly connected with the gate of the discharge valve rod with axial clearance relative to the shut-off and control element (equal during the shutter discharge valve and the shut-off and control element), first, creates conditions for uncontrollable movements (oscillations) of the specified element relative to the rod, secondly, leads to loss of time per sample a specified gap and to move the shut-off and control element relative to its seat with a delay relative to the beginning of the regulation, which reduces the performance of the valve when it is open is I.

When the outdoor pipe bore valve and low pressure drop in its input and output channels, the resulting pressure force exerted by the working fluid to the gate of the discharge valve stems and valves item considered for shut-off and control valve (due to the fact that the guide cylindrical portion of the shut-off and control element has a diameter not less than the greatest diameter of the tapered shank, and the diameters of the upper and lower rods of the same) may have a value that is not sufficient to overcome the friction in the moving pairs and moving gate discharge valve and thus shut-off and control element in the position at which the flow area of the valve is closed. Therefore, when the violation of the corresponding shaft with the output level control valve actuator or refusal of the specified drive the gate of the discharge valve and shut-off and control element can remain in the position in which the flow area of the valve is open, which is not allowed for security reasons, because it is accompanied by the movement of the output link of the hydraulic drive motor and driven them working equipment and can lead to an emergency situation. The specified circumstance (lack of reliability closing the bore in abnormal when the areas) is the main disadvantage of the known shut-off and control valve.

One way to ensure reliable closure of the orifice of the valve in emergency situations is the application in its design, the spring force preload which acts in the direction of closing the orifice of the valve and sufficient to implement the specified operation. However, the introduction of the valve, this spring complicates its design.

When performing shank valves element with a tapered side surfaces of the law changes in the area of AndR··CLbore of the working window, open the shut-off and control element after it ascends relative to the saddle on the amount of overlap cylindrical sealing belts, further displacement x relative to the saddle (if we neglect the size of the radial gap between the cylindrical sealing belts, valves of an element and its seat) has the form:

Androl=π(Dn-0,5x·sin2αx·sinα,

where Dn- diameter cylindrical sealing band;

α half - angle at the apex of the conical lateral surface of the shank.

Since the value of 0,5x·sin2α quite small compared with the diameter of Dn(especially for small values of x), then the law is close to linear. When linear as is the law of change of the cross-section area of the valve from moving to its locking and regulating element, as is known, the relative error in the regulation of fluid flow at a fixed error installing shut-off and control element in the desired position and other conditions being equal, is very much dependant on the value of x and theoretically increases the hyperbolic dependence with decreasing x (see: Guido ON Hydraulics with proportional electric control: a Training manual. - 2nd ed., revised and enlarged extra - Chelyabinsk: publishing house of the South Ural state University, 2000. - P.27-28).

Thus, the existing shut-off and control valve is characterized by low accuracy of flow control in the region of small discoveries shut-off and control element bore, which is a significant drawback.

The closest to the technical nature of the claimed object is passed as a prototype shut-off and regulating valve, comprising a housing with a flanged inlet and outlet channels in the bore which holds the saddle with the sealing chamfer and the Central cylindrical sealing band having a diameter not larger inner diameter of the sealing chamfer seat and orifice and placed shut-off and control element coaxially with the guide cylindrical portion, a collar with stop chamfered, second cylindrical sealing band and the tail is not far away, associated with two diametrically spaced rods, the ends of which are through sealed openings facing in opposite directions beyond the valve body, the valve body is sealed with a lid located relative to the shut-off and control element from the side opposite to the valve seat, and shut-off and control element is installed with the education side of his collar inputs connected to connecting the input channel of the valve, to form between the surfaces of the shank shut-off and control element and the Central aperture of the saddle channel connected with connecting the output channel of the valve, and to form between the surfaces of the shut-off and control element and cover nallathanni cavity provided with connecting the output channel [2, 4, 5]. The specified upper valve (located at the side of nallathanni cavity) and the bottom (located at the side of the outlet channel of the valve stems (the output link of the steering actuator is connected with one of these rods are fixed in the axial direction relative to the shut-off and control element and have the same diameters, and the effective areas of the surfaces involved in the transfer of force from fluid shut-off and control element, matter, providing full is whether almost full discharge shut-off and control element against the force of the hydrostatic pressure of the liquid.

Due to almost complete discharge valves of the valve element is known from the forces of hydrostatic fluid pressure required to ensure a hermetic separation of the input and output cavities of the valve contact stresses in the contact zone of the sealing chamfer seat and stop chamfer shut-off and control element are created through the control valve actuator. When the violation of the corresponding stem valves element with the output element of the control valve actuator or refusal of the specified drive contact stresses in the contact zone of the sealing chamfer seat and stop chamfer shut-off and control element are reduced and the tightness of the valve is broken.

When the outdoor pipe bore of the valve resultant force of the pressure exerted by the working fluid in its shut-off and control element (due to the almost complete discharge shut-off and control element of the considered valve against the force of the hydrostatic pressure of the liquid)can have a value that is not sufficient to overcome the friction in the moving pairs and move shut-off and control element in a position in which the flow area of the valve is closed (moreover, this force can act in the direction of opening of the orifice valve). Poet of the mu when the violation of the corresponding shaft with the output level control valve actuator or refusal of the specified drive shut-off and control element may remain in position, wherein the flow area of the valve is open, which is not allowed for security reasons, because it is accompanied by the movement of the output link of the hydraulic drive motor and driven them working equipment and can lead to an emergency situation. The specified circumstance (lack of reliability seal bore in emergency situations) is the main disadvantage of the known shut-off and control valve.

The Central bore hole of the seat of this valve on the area between the sealing chamfer and the Central cylindrical sealing band has a conical surface with the apex of the cone directed toward the output channel). Adjustable flow section of the valve is formed between the said conical surface of the valve seat and the lower edge response cylindrical sealing band performed on the shank shut-off and control element from the output channel of the valve. However, the law changes in the area of Androlbore of the working window, open the shut-off and control element after it ascends relative to the saddle on the amount of overlap cylindrical sealing belts, further displacement x relative to the saddle is close to linear. At the same linear law of variation of the cross-section area of the valve is t move its shut-off and control element, as noted above, the relative error in the regulation of fluid flow at a fixed error installing shut-off and control element in the desired position and other conditions being equal, is very much dependant on the value of x and theoretically increases the hyperbolic dependence with decreasing H.

Therefore this shut-off control valve is characterized by low accuracy of flow control in the region of small discoveries shut-off and control element bore, which is a significant drawback.

In addition, since the maximum area of the orifice of the valve is determined by the area of the ring, the larger (outer) diameter of which is equal to the diameter of the Central cylindrical sealing seat belt, and the smaller (inner) diameter equal to the diameter of the lower stem shut-off and control element, the execution of the Central bore hole of the saddle on the area between the sealing chamfer and the Central cylindrical sealing band with a conical surface with the apex of the cone directed toward the output channel) ceteris paribus entails the necessity of increasing the diameter of the seat and the transverse dimensions of the valve as a whole, which is irrational.

The technical problem to be solved and the acquisition, is the creation of a shutoff valve, which is characterized by high reliability hermetic closing its bore in emergency situations (for example, when the disruption of the stem shut-off and control element with the output element of the control valve actuator), through appropriate selection of the ratio of the geometric dimensions of shut-off and control element (from the condition of ensuring validity of the resulting force of fluid pressure at shut-off and control element in the direction of its seat).

Another technical task of the invention is to provide a shutoff valve, high precision control of fluid flow in the entire range of variation of the cross-section area of the valve, due to the special profile of the lateral surface of the shank shut-off and control element (of the conditions for obtaining equal percentage control characteristic of the valve).

To solve the technical problem in the known shut-off and regulating valve, comprising a housing with a flanged inlet and outlet channels in the bore which holds the saddle with the sealing chamfer and the Central cylindrical sealing band having a diameter not larger inner diameter of the sealing chamfer seat, and held the th hole and placed valves element with a coaxial cylindrical guide part, the collar with stop chamfered, second cylindrical sealing band and shank associated with two diametrically spaced rods, the ends of which are through sealed openings facing in opposite directions beyond the valve body, the valve body is sealed with a lid located relative to the shut-off and control element from the side opposite to the valve seat, and shut-off and control element is installed with the education side of his collar inputs connected to connecting the input channel of the valve, to form between the surfaces of the shank shut-off and control element and the Central aperture of the saddle channel connected with connecting the output channel of the valve, and to form between the surfaces of the shut-off and control element and cover nallathanni cavity provided with connecting the output channel according to the invention the diameter of the guide cylinder part shutoff element is made smaller than the diameter of its cylindrical sealing band and the diameter of the upper rod shut-off and control element located on the side nallathanni cavity is made smaller than the diameter of the lower shaft located on the side of the outlet channel of the valve, and these diameters throughout the possible range of the value is of the pressure in the output channel of the valve satisfy the following system of inequalities:

where Dnthe diameter of the guide cylinder part shut-off and control element;

dK.DK.respectively the outer and inner diameters of the contact surface of the locking chamfer shut-off and control element and the sealing chamfer saddle;

dSNdW.the diameters respectively of the lower and upper rods, valves item;

DPS- diameter cylindrical sealing band shut-off and control element;

PPete- constant pressure (pressure supply) in the input channel of the valve;

p is the pressure at the outlet of the valve (0≤R≤pPete);

σminthat σmax- minimum values, respectively (conditions ensure tightness) and maximum (condition factor) allowable stresses on the contact surface of the stop chamfer shut-off and control element and the sealing bevel seat (σmin>pPete);

R - force, which must be attached to the shut-off and control element for moving it in the direction of the saddle to contact with him from a position in which the flow area of the valve is open.

According to the invention the lateral surface of the shank shut-off and control element of profilio is based on the following equation, establishes a connection between the current required by the value of the diameter Dzshank and z coordinate measured along the axis of the shank from the plane of its junction with the cylindrical sealing flanges, valves item:

where DPSthe diameter of the Central cylindrical sealing band saddle;

Dz- the current net value of the diameter of the shank;

the z - coordinate is measured along the axis of the shank from the plane of its junction with the cylindrical sealing band shut-off and control element;

A0- the initial value of the cross-section area between the shank shut-off and control element and the Central cylindrical sealing seat belt, is equal to the square ring, the outer diameter of which is equal to the diameter of the sealing seat belt, and the inner diameter of the cylindrical sealing band shut-off and control element;

δ - permissible relative error of regulating the flow of working fluid;

Δ - maximum absolute value of the error set shut-off and control element of the valve in the desired position.

The implementation of the guide diameter of the cylindrical part shutoff element is less than the diameter of its cylindrical sealing band, and dia is tra upper stem shut-off and control element, located by nallathanni cavity is less than the diameter of the lower shaft located on the side of the outlet channel of the valve, determines at any value of pressure at the outlet valve from the range from zero to the value of the pressure in the inlet valve (pressure supply) action of the resultant force of the hydrostatic pressure of the working fluid shut-off and control element in the direction of the seat shut-off and control element, i.e. in the direction of closing its bore, and thereby creates the prerequisites for closing the bore of the valve and providing a hermetic separation of the input and output channels in emergency situations (for example, when the disruption of the stem shut-off and control element with the output element of the control valve actuator).

The last position confirmed by the following the following calculations.

When closed, the pipe bore valve (with contact locking chamfer shut-off and control element and the sealing chamfer seat) the resultant force RPristhe hydrostatic pressure of the working fluid shut-off and control element, clamping it to the saddle, obviously, equal to:

Since according to the present invention Dn<DPSand, by default, DPS<DThe .In <DK.then obviously we have the inequality: Dn<DK.and the magnitude of the force PPriswhen p=0

is strictly positive.

According to expression (4) value of PPrislinearly dependent on the magnitude of the pressure p with the constant of proportionality In:

When=0 the value of PPrisnot actually depends on the pressure p and any value remains constant and equal to RPris.

When V>0, the value of PPriswith increasing values of the pressure p from zero to Pnumincreases in comparison with the value of PPrisand thus, obviously, is always positive.

If<0, the value of PPriswith increasing values of the pressure p from zero to pnumreduced compared with a value of PPris.

However, since R=Rnumin accordance with the expression (4) value of PPriswhen any value takes a value of Pprized:

and according to the invention DW.<DSNeven if<0 and R=RPetethe value of PPrisremains significantly positive, which was to be proved.

In the absence of contact between the locking chamfer shut-off and control element and the sealing chamfer seat in the first AP is the situation (if we neglect, in particular, the additional impact force from fluid shut-off and control element associated with the change quantity of the fluid by passing it through the open shut-off and control element of the flow area) power Pclosedexerted by the fluid shut-off and control element and directed to the side of his saddle, can be represented as follows:

Since in accordance with the invention Dn<DNCthe magnitude of the force Pclosedwhen p=0

is strictly positive.

According to expression (8) value of Pclosedlinearly depends on the pressure p, with the proportionality With:

Since DPS<DK.then obviously With>and, in particular, when V=0 the value of C is necessarily positive.

When C=0 the value of Pclosednot actually depends on the pressure p and any value remains constant and equal to RSacr.

When C>0, the value of Pclosedwith increasing values of the pressure p from zero to PPeteincreases in comparison with the value of PSacrand thus, obviously, is always positive.

If<0, the value of Pclosedwith Uwe is Iconium values of pressure p from zero to P numreduced compared with a value of PSacr.

However, since R=Rnumin accordance with the expression (8) value of Pclosedwhen any value takes a value of Psacred:

and according to the invention DW.<DSNthen even if C<0 and R=Rnumthe value of Pclosedremains significantly positive, as indicated above.

The implementation of the diameters of the guide cylindrical part, the cylindrical sealing band, the upper and lower rods shut-off and control element in such a way that these diameters in addition to the fact that they satisfy the previously formulated relations, and even in the entire possible range of values of the pressure in the output channel of the valve satisfy the system of inequalities (1), (2), even in case of failure of the control valve actuator provides: first, when a closed pipe bore valve creation on the contact surface of the stop chamfer shut-off and control element and the sealing chamfer seat voltages sufficient to ensure a hermetic separation of the input and output channels of the valve and at the same time not exceeding the value of voltages allowed by the condition of strength of the contacting surfaces [see inequality (1)]; secondly, when the outdoor pipe bore is lapena effect on the shut-off and control element from the side of the working fluid efforts higher than the corresponding resistance and sufficient to move the valves in the direction of the seat to contact with him [see inequality (2)].

Thus, the implementation of the present invention ensures high reliability hermetic closure bore shutoff valve in emergency situations (for example, when the disruption of the stem shut-off and control element with the output element of the control valve actuator).

It should be noted that when assigning the value of the maximum allowable stress σmaxon the contact surface of the stop chamfer shut-off and control element and the sealing chamfer saddle should be taken into account the fact that with proper control valve actuator when he closed pipe bore valve provides additional force, clamping shut-off and control element to the saddle (that is, the value of σmaxmust be accordingly low in comparison to the maximum possible value of the contact stresses for the materials used details).

Because when you increase the pressure p at the outlet of the valve from zero to a value of pnumthe increase in contact stresses σ between a stop chamfer shut-off and control element and the sealing chamfer seat:

not make sense [because with increasing pressure p pressure difference (pnum- R) to the sealing area decreases], it is expedient when designing shut-off and control valve in a first approximation, assume the conditions of the following [more "hard" compared to inequality (1)] ratios:

On the basis of expressions (12), (13) and (14), we obtain the following formula for determining the required values of the diameter Dnthe guide cylindrical section shut-off and control element:

[diameters of DK.and DK.in the first approximation is chosen using the following equation (22) based on the information about the required diameters, valves and valve].

Excluding the value of Dnfrom (13) using the formula (15), we arrive at the following expression that establishes the relationship between the diameters Of2SNand DW.

Since DSN>DW.it is advisable to communicate with the output level control valve actuator to use the lower stem shut-off and control element. This rod is power and its diameter DSNmust have oblitarate requirements arising from conditions of strength and longitudinal stability of the stem. On the other hand, the diameter DW.upper stem shut-off and control element cannot be negative, and when using the top of the stem to control the current position of the shut-off and control element cannot be smaller than a certain size, usually appointed from design considerations. These additional terms, together with the expression (16) give the possibility to calculate the specific needs of the values of the diameters DSNand DW..

When performing the relations (13), which yields the equality:=0 [see expression (6)], automatically inequality:

which corresponds to the inequality: From>0 [see equation (10)].

In the present case, as noted above, the magnitude of the force Pclosedacting from the side of the fluid shut-off and control element in the direction of his saddle, with increasing values of the pressure p from zero to pnumincreases, and therefore, if inequality (2) at R=0, then it runs across the entire range of values of pressure p from zero to pnum. In this regard, to ensure closure of the bore of the valve under the action of the working fluid instead of following inequality (2) is quite inequality:

you want

or taking into account expressions (15)

Because the default is to run the inequality DP.Z.<DkVon the basis of his and inequality (20) we get the following inequality:

from which define the required ratio between the diameters DK.and DK.at the initial stage of selection:

The resulting calculation of the values of the diameters are subject to rounding and adjusting (including range of normal values of the diameters of the movable sealing cylindrical pairs nomenclatures used seals etc) and, ultimately, in the entire possible range of values of the pressure in the output channel of the valve must satisfy the system of inequalities (1) and (2).

The execution profile of the lateral surface of the shank shut-off and control element on the basis of equation (3) provides precise control of fluid flow through the valve throughout the range of change of the area of its orifice.

In order for the relative error in the regulation of fluid flow, due to the setting error is shut-off and control element in the desired position, at a fixed absolute led the maximum rank value Δ this error and other equal conditions did not exceed modulo some beforehand set a valid value δneed to link space AndRbore of the working window, open the shut-off and control element, with its displacement y in the direction of the open flow area of the valve relative to the position at which the edge of the cylindrical sealing seat belt, near to the sealing chamfer last, is located in the plane of the junction of the shank and a cylindrical sealing band shut-off and control element, had the appearance (see: Guido ON Hydraulics with proportional electric control: a Training manual. - 2nd ed., revised and enlarged extra - Chelyabinsk: publishing house of the South Ural state University, 2000. - P.29):

For this valve determines from the point of view of its regulating characteristics of the flow area, open shut-off and regulating element is a lateral surface of a truncated cone formed by the normals to the side of the profiled surface of the shank shut-off and control element, drawn from the edge points of the cylindrical sealing seat belt, near to the sealing chamfer last.

For each value of displacement y these normals intersect the lateral profiled p is the surface of the shank shut-off and control element at a distance z from the plane of the junction of the shank with a cylindrical sealing band shut-off and control element, where the diameter of the shank has a value of Dz.

Based on the above fair the following relations:

(here βz- the angle complementary to the value of 180° the angle of the tangent to the lateral profiled surface of the shank at a point at a distance z from the plane of the junction of the shank with a cylindrical sealing band shut-off and control element and lying, respectively, on the circle with diameter Dzrelative to the axis of the shank in the direction of reference (z).

Equating the left-hand part of expression (23) and (24) subject to the relations (25), (26) and taking into account the fact that

cosβz=(1+tgβz)l/2,

get the

The last equation (27)that establishes a connection between the current required by the value of the diameter Dzshank and z coordinate measured along the axis of the shank from the plane of its junction with the cylindrical sealing flanges, valves item is identical to equation (3).

And since equation (27) is obtained based on the ratio in (23), the identity of equations (27) and (3) proves the above position that when running Pro the I-side surface of the shank shut-off and control element on the basis of equation (3) is high (with a relative error, not exceeding a predetermined allowable value δ) precision control of fluid flow through the valve throughout the range of change of the area of its orifice.

The invention is illustrated by drawings, where figure 1 shows a structural diagram of a shut-off and control valve, figure 2 - calculation scheme for determining the cross-section area of the valve.

Shut-off and control valve (figure 1) includes a housing 1 with connecting the input 2 and output 3 channels. In the bore of the stationary housing 1 is installed coaxially with the seat 4 with the sealing chamfer 5 and the Central cylindrical sealing band 6, which has a diameter not larger inner diameter of the sealing chamfer 5 seat 4, and a through hole 7 and the guide sleeve 8 with holes 9 from input channel 2. In the guide sleeve 8 posted by shut-off and control element 10 coaxially with the guide cylindrical portion 11, the collar 12 with a stop chamfer 13, second cylindrical sealing band 14 and the shaft 15, is made with two diametrically spaced upper 16 and lower 17 stocks. Upon contact of the stop chamfer 13 shut-off and control element 10 and the sealing chamfer 5 seat 4 response cylindrical sealing band 14 shut-off and control element 10 formed with a Central cylindrical upl is taosim belt 6 seat 4 spool couple with a guaranteed radial clearance and a positive overlap. The housing 1 is sealed by a cover 18 that is located relative to the shut-off and control element 10 on the side opposite the valve seat 4. Shut-off and control element 10 is installed with the education side of his collar 12 of the input cavity 19, which is connected through holes 9 made in the guide sleeve 8, with connecting input channel 2 valve, with the formation between the side surface 20 of the shank 15 shut-off and control element 10 and the surface of the Central bore hole 7 seat 4 channel 21 connected to the connecting output channel 3 of the valve, and to form between the surfaces of the shut-off and control element 10 and the cover 18 nallathanni cavity 22, communicated through hole 23 made in shut-off and control element 10, with connecting weekends channel 3.

The ends of the upper rod 16 located on the side nallathanni cavity 22, and the lower rod 17 located on the side output of channel 3 of the valve, through the appropriate sealed the holes drilled in the lid 18 and the housing 1, is beyond the housing 1 of the valve into the atmosphere.

The contact surface of the guide cylinder part 11 shut-off and control element 10 and the guide sleeve 8 is sealed by a seal 24 to prevent partecke working fluid through the radial force is the resultant gap between the parts 10 and 8 from the input cavity 19 of the valve in its nadupanou cavity 22.

The diameter Dnthe guide cylindrical part 11 shut-off and control element 10 is made smaller than the diameter DPSits cylindrical sealing band 14, and the diameter DW.the upper rod 16 shut-off and control element 10 is made smaller than the diameter DSNthe bottom of the shaft 17, and these diameters throughout the possible range of values of the pressure at the outlet 3 of the valve satisfy the system of inequalities (1) and (2).

The side surface 20 of the shank 15 shut-off and control element 10 profiled on the basis of equation (3), establishes a connection between the current required by the value of the diameter Dzthe shank 15 and the z coordinate measured along the axis of the shank 15 from the plane of its junction with the cylindrical sealing band 14 shut-off and control element 10 (figure 2).

The lower shaft 17 shut-off and control element 10 is a control (power) and connected (preferably without a clearance in the axial direction) with an output level control valve actuator, for example, with the rod of the hydraulic cylinder management (in the drawings, the control actuator and the output link is not shown).

The upper rod 16 shut-off and control element 10 is measuring and is connected with a movable part of the displacement sensor (in the drawings, the displacement transducer and its movable element not shown).

Shut-reg which regulates the valve operates as follows.

When closed, the pipe bore valve (with contact locking chamfer 13 shut-off and control element 10 and the sealing chamfer 5 seat 4) the working fluid acts on the shut-off and control element 10 with the resulting force RPris[see the expression (4)], pointing towards the saddle 4.

The specified force at any value of pressure p at the outlet 3 of the valve from the range from zero to the value of the pressure in the inlet 2 of the valve (pressure supply pnumeven in case of failure of the control valve actuator enables the creation on the contact surface of the stop chamfer 13 shut-off and control element 10 and the sealing chamfer 5 seat 4 voltage, sufficient to provide a hermetic separation of the input 2 and output 3 channel valve [see inequality (1)]. At the same time (due to the limitation of the maximum values of the stresses caused by forces PPriseven when creating a control valve actuator further efforts, clamping shut-off and control element 10 to the seat 4, the magnitude of the stresses on the contact surface of the stop chamfers 13 and the sealing chamfer 5 does not exceed the value of voltages allowed by the condition of strength of the contacting surfaces.

The displacement of the shut-off and control element 10 relative to the seat 4 under the influence at rawsumer valve actuator (in the drawings, the control valve actuator not shown) by an amount less overlapping cylindrical sealing belts 14 and 6 respectively shutoff element 10 and the seat 4, the pressure in the space between the shut-off and control element 10 and the seat 4 at the site, limited to the specified cylindrical sealing belts 14 and 6 and the entrance to the gap between the locking chamfer 13 shut-off and control element 10 and the sealing chamfer 5 seat 4, rises to a value equal to or close to the pressure pPetein the input channel of the valve (because the gap between the cylindrical sealing belts 14 and 6 has a large hydraulic resistance). Thus the resultant force exerted by the working fluid, at shut-off and control element 10 decreases from the values of RPrisdefined by the formula (4), to a value of Pcloseddefined by the formula (8), but for any value of the pressure p at the outlet 3 of the valve from the range from zero to the value of the pressure in the inlet 2 of the valve (pressure supply pPeteremains directed toward the seat 4 (i.e. in the direction of closing the bore of the valve) and of sufficient magnitude to overcome the respective forces of resistance and move the valves in the direction of the seat to contact with him [see inequality (2)].

Reduction of the resulting force is the hydrostatic pressure of the working fluid shut-off and control element 10 after the formation of the gate chamfer 13 shut-off and control element 10 from the sealing chamfer 5 seat 4 facilitates the subsequent shift valves element 10 in the direction of opening of the orifice valve and ceteris paribus helps reduce the time required for opening the orifice.

The displacement of the shut-off and control element 10 relative to the seat 4 under the action of the control valve actuator (in the drawings, the control valve actuator not shown) by an amount equal to or greater overlap cylindrical sealing belts 14 and 6 respectively shutoff element 10 and the seat 4, opens the flow area of the valve, which is a side surface of a truncated cone formed by the normals to the side of the profiled surface 20 of the shank 15 shut-off and control element 10, drawn from the edge points of the cylindrical sealing band 6 of the seat 4, closest to the sealing chamfer last 5 (see figure 2). Since the side surface 20 of the shank 15 profiled on the basis of equation (3), in the entire range of variation of the cross-section area of the proposed shut-off and control valve is provided relative error flow control does not exceed a predetermined permissible value of 8.

Thanks to a specified profile of the side surface 20 of the shank 15 is provided a seamless extension of the channel 21 formed by the specified surface and the surface is through the Central bore hole 7 of the saddle 4, in the direction to the outlet channel 3, thereby reducing the likelihood when the valve cavitation tear type, leading to the most intense cavitation wear of the elements of the valve (see: Bocharov Y.A., Denisyuk A.K. Improving the flowing part of the valve distributors for hydraulic die forging hammers / Forging and stamping production. - 1974. No. 5. - P.31-33).

Since the beginning of the open flow area of the valve shut-off chamfer 13 shut-off and control element 10 is shifted with respect to the sealing chamfer 5 seat 4 by a distance equal to the amount of overlap of the cylindrical sealing belts 14 and 6, the area of the channel formed by the chamfers 13 and 5, after the opening of the bore of the valve greatly exceeds the area specified orifice. Thanks chamfers 13 and 5 are obviously outside the zone of cavitation processes, possible flow area of the valve during its operation, and is not subjected to cavitation wear, thereby increasing their durability.

In normal operating conditions the valve position change its shut-off and control element 10 is in strict accordance with the position change of the output level control valve actuator (in the drawings, the control actuator and the output link n is shown), connected with the lower shaft 17 shut-off and control element 10.

If you have network problems between the lower shaft 17 and the output level control valve actuator and the offset of the specified element in the direction of reducing the cross-section area of the valve shut-off and control element 10 under the action from the side of the working fluid forces Pclosed[see expression (8), inequality (2)] is shifted in the direction of its seat 4 until it stops or until the stop rod 17 in the output link of the steering actuator (depending on what position moved this link).

During brake release output link of the steering actuator (for example, due to the disappearance of the power of this drive) shut-off and control element 10 under the action from the side of the working fluid forces Pclosed[see expression (8), inequality (2)] is shifted in the direction of its seat 4 all the way into him, moving with an output link of the steering actuator. As a result, the flow area shut-off valve is closed to prevent emergency situations associated with failure of the steering actuator.

Thus, the implementation of the invention provides increased reliability seal bore shutoff valve in emergency situations (for example, when the disruption of the stem is aporno-regulatory element with the output element of the control valve actuator) and precise control of fluid flow through him in the entire range of variation of the cross-section area of the valve.

Shut-off and control valve can be used in hydraulic control of the forging and stamping presses.

Literary sources

1. Control valve: USSR Author's certificate No. 1543170. MCI F16 47/02. Declared 31.03.1987. Published 15.02.1990.

2. Shutoff valve: RF Patent № 2103583. MCI F16 39/02. Declared 01.04.1996. Published 27.01.1998.

1. Shut-off and regulating valve, comprising a housing with a flanged inlet and outlet channels in the bore which holds the saddle with the sealing chamfer and the Central cylindrical sealing band having a diameter not larger than the inner diameter of the sealing chamfer seat and orifice and placed shut-off and control element coaxially with the guide cylindrical portion, a collar with stop chamfered, second cylindrical sealing band and shank associated with two diametrically spaced rods, the ends of which are through sealed openings facing in opposite directions beyond the valve body, the valve body is sealed with a lid located relative to the locking-regulatory element from the side opposite to the valve seat, and shut-off and control element is installed with the education side of his collar inputs connected to connecting the input is the anal valve, to form between the surfaces of the shank shut-off and control element and the Central bore hole of the saddle channel connected with connecting the output channel of the valve, and to form between the surfaces of the shut-off and control element and cover nallathanni cavity provided with connecting the output channel, characterized in that the diameter of the guide cylinder part shutoff element is made smaller than the diameter of its cylindrical sealing band and the diameter of the upper rod shut-off and control element located on the side nallathanni cavity is made smaller than the diameter of the lower shaft located on the side of the outlet channel of the valve, and these diameters throughout the possible range of values of pressure in the output channel of the valve satisfy the following system of inequalities:

where Dnthe diameter of the guide cylinder part shut-off and control element;

dK.DK.respectively the outer and inner diameters of the contact surface of the locking chamfer shut-off and control element and the sealing chamfer saddle;

DSNDW.the diameters respectively of the lower and upper rods locking and maintains the existing item;

DPS- diameter cylindrical sealing band shut-off and control element;

PPete- constant pressure (pressure supply) in the input channel of the valve;

p is the pressure at the outlet of the valve (0≤p≤pPete);

σminthat σmax- minimum values, respectively (conditions ensure tightness) and maximum (condition factor) allowable stresses on the contact surface of the stop bevel lock shield element and the sealing bevel seat (σmin>Pete);

R - force, which must be attached to the shut-off and control element for moving it in the direction of the saddle to contact with him from a position in which the flow area of the valve is open.

2. The valve according to claim 1, characterized in that the side surface of the shank shut-off and control element profiled on the basis of the following equation, which establishes the relationship between the current required by the value of the diameter Dzshank and z coordinate measured along the axis of the shank from the plane of its junction with the cylindrical sealing flanges, valves

where Dn.cthe diameter of the Central cylindrical sealing band saddle;

Dz- the current net value of the diameter of the shank;

the z - coordinate is measured along the axis of the shank from the plane of its junction with the cylindrical sealing band shut-off and control element;

And0- the initial value of the cross-section area between the shank shut-off and control element and the Central cylindrical sealing seat belt, is equal to the square ring, the outer diameter of which is equal to the diameter of the sealing seat belt, and the inner diameter of the cylindrical sealing band shut-off and control element;

σ - permissible relative error of regulating the flow of working fluid;

Δ - maximum absolute value of the error set shut-off and control element of the valve in the desired position.



 

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