JPS63303276A - Valve mechanism - Google Patents

Abstract

PURPOSE:To supply the high pressure oil without increasing the dimension of an electromagnetic actuator by setting the force of the electromagnetic actuator larger than the difference between the pressure acting onto the spool rands each having a large diameter and the pressure acting onto the spool rands each having a small diameter from a pressure source. CONSTITUTION:The oil supplied from a pressure source 13 provides each propulsion force in the opposite direction onto the spool rands 21f and 22f each having a large diameter and the spool rands 21g and 22g each having a small diameter, and since the propulsion force which each of the spool rands 21f and 22f each having a large diameter is larger, the spools 21e and 2e receives the propulsion force in the direction for opening the discharge ports 21b and 22b. An electromagnetic actuator provides the force in the direction for closing the discharge ports 21b and 22b, onto the spools 21e and 22e, and the force of the actuator is larger than the difference between the propulsion force which the spool rands 21f and 22f each having a large diameter obtain and the propulsion force which the spool rands 21g and 22g each having a small diameter obtain.

Description

[Detailed description of the invention] [Industrial application field]

The present invention relates to a valve mechanism, and particularly to an improvement in a valve mechanism in which the direction of oil discharge is switched by an electromagnetic actuator.

[Conventional technology]

For example, Japanese Patent Application Laid-open No. 59-1888 and Japanese Patent Application Laid-open No. 61-2985 can be cited as the prior art that is the eleventh aspect of the present invention. Referring to FIG. 4, 7 valve machines (14
Explain the structural effects of. First of all, it consists of a swinging uphill as a whole,
The operating pin I is rotatably supported in the case 3 by the central flange 2 of the operating pin I, which is made of a single piece of ferromagnetic material with a small amount of ferromagnetic material. Both ζ・：;
Part i↓ protrudes from L case 3. Also 1 operation e y
]+= +: 21 il 45) is wrapped, 21 il 4
-◇:1. ; is OR-connected to ground :) along with each other -Qμ;C
51-OR connection and connected to the one-tabar oscillator 6 1i. Two faces! When the current in the positive direction is supplied from the pulse oscillator 6 (hereinafter, the output of the pulse oscillator 6 is simply expressed as positive), the left end of the output pin 1 becomes N. so that the right end becomes the S pole.When a negative current is supplied from the pulse oscillator 6 (below, the output of the pulse oscillator 6 is indicated as negative in Ip), the left end of the "operating pin" They are wound so that the S pole is the N pole and the right end is the N pole. Also, permanent magnets 7 and 8910 are provided inside the case 3, and the S poles of the permanent magnets 7 and 9 and the N pole of the permanent magnet 810 are towards the actuating pin 1. Therefore, the pulse oscillator 6
When the output of the pulse oscillator 6 becomes positive, the operating pin 1 rotates clockwise, and when the output of the pulse oscillator 6 becomes f+, the operating pin 1 rotates counterclockwise. Once the operating pin 1 rotates in several directions, the permanent magnet 7
10 (or 8/9) and maintains that state until the current j■power direction is reversed. Next, 11 and 12 indicate valves, 13 indicates correct reading,
Valve 1 is supplied with oil from a normal reading 13 through a pressure path 14, and oil is supplied to valve 2 12 from a normal reading 13 through a pressure path 15. In addition, the 2-valve 11 (+2) is equipped with Borche, Ki IIa (1
2a) is provided, with a ball tier. When the pin 11a (1, 2a) is pushed down with the pin 16 (17), the discharge port 11b (+2b) and the train 11 (.
12a) is released from pin 16 (17), the pressure tX13
Hydraulic pressure Q applied through pressure 1 path 14 (+5) from
When F is pressed, the hole checker 1la (12a) is pushed down by -1, and the pressure path 14 (+5) and the discharge port 11t) (12b) are brought into communication. Therefore, when the output polarity of the pulse oscillator 6 becomes positive and the operating pin 1 rotates clockwise, the oil supplied from the correct reading 13! When the output polarity of the pulse oscillator 6 becomes negative and the operating pin l rotates in the counterclockwise direction, the oil supplied from the positive reading 13 becomes under pressure. Path 15 - is discharged from outlet +2b via valve 12.

[Problems to be solved by the invention]

The valve mechanism with the structure shown in 1-1 changes the oil discharge direction depending on the direction of the output current of the pulse oscillator 6, and can be used as a direction switching valve by itself, as well as a larger valve (Byron) valve. By using it as 7, high precision direction cutting Ie! However, there is room for improvement as described below. Immediately, the valve mechanism with the -4-2 structure is the ball checker 11.
A (12a) is designed to slowly sow the pressure path 14 (15), so the C1 operating pin 1 must have a torque greater than the thrust that the m source 13 applies to the ball check Ila (12a). . Therefore, when using high-pressure oil, the torque of the actuating pin 1 must be increased accordingly. This makes high-speed operation difficult to fit.Also,
In order to achieve high-speed operation, it is necessary to downsize the swing motor A, and if the torque of the operating pin 1 decreases accordingly, it becomes difficult to use high-pressure oil. Furthermore, there is also the problem that the hydraulic sole is not completely corrected due to the vibration of the ball checker l1a (12a) itself.

[Means to solve the problem]

The present invention was made in view of these problems, and
The first purpose is to provide a valve mechanism that can supply high-pressure oil without increasing the size of the electromagnetic actuator that includes a single pin. On the other hand, electromagnetic Acuji 1 without lowering the correct reading,
:I: Valve machine 11 that made it possible to downsize the Ichiyo
4 to 1, and its second purpose is to provide a side valve with a higher hydraulic sole.
. -1- In order to achieve the above purpose, the valve mechanism of the present invention has the following means. A rotor having at least two operating points is an actuator.
A spool having a large-diameter spool land and a small-diameter spool land is placed in a sleeve extending from the inlet [] to the old outlet. A pressure in the opposite direction to the pressure applied to the small diameter spool run F4 is applied to the small diameter spool land at the inlet inlet (iii).
The valve has two valves. A common normal reading is connected to the inlet of each of these two valves. Further, each operating point of the electronic actuator applies a force in the closing direction to the large diameter spool land of each valve. Further, the force of the electronic actuator is adjusted so as to be larger than the difference between the pressure applied to the large diameter spool land during the normal reading and the pressure applied from the pressure source 111j to the small diameter spool land. 5. If desired, make the large diameter spool land saw 1 to Bopeno I shape.

[Effect] The yuzu supplied from the correct reading gives thrust in opposite directions to the large diameter spool land and the small diameter spool land, but since the thrust obtained by the large diameter spool land is larger, the spool as a whole Receives HD force in the direction of opening the outlet. Then, the electromagnetic actuator applies a force to the spool in the direction of closing the discharge port, and the actuator's force is larger than the difference between the thrust obtained by the large diameter spool land and the thrust obtained by the small diameter spool land, so the two The one of the valves receiving the force of the electromagnetic actuator is shielded. The force required for an electromagnetic actuator is equal to the difference between the thrust force obtained by a large-diameter spool land and the 111 force obtained by a small-diameter spool land. The correct reading pressure can be increased every time. [Embodiment] An embodiment of the present invention will be explained in detail below with reference to the drawings. Fig. 1 shows a valve mechanism according to an embodiment of the present invention as a flow control valve. It is a vertical cross-sectional view showing an example of use as a pi-a7l-valve, and the same elements as in FIG. 4 are denoted by the same reference numerals as in FIG. In Fig. 1, valves 21 and 22 (J valves) are shown. Fig. 2 is an enlarged vertical cross-sectional view of the valve 21. Since the valves 21 and 22 are configured in a left-right symmetrical shape, In Figure 2, the elements of the valve 22 are indicated by symbols in parentheses.The valve 2I is connected to the pressure #13 via the pressure path 14; T-Bo I
・Insert 21(1) and spool 2 into sleeve 21d.
1 (! is arranged. The spool 21e is the large diameter spool land 2 ], f and the small diameter spool land F 21
g, the large diameter spool run F' 21 f and the small diameter spool land 21g have a spool opening y l" 21 h
are connected. In addition, the inlet 2]a is the spool run l
-' 21 It opens at the part h. In addition, the large-diameter spool run l''21f connects the discharge port 21b and the T-bow (・2
1c or between the discharge port 21b and the sleeve 21. d, and its seat portion is formed into a poppet shape. Furthermore. The upper surface of the large-diameter spool land 21f has a swinging morph △ (
A pin 16 driven by a pin 16 (see FIG. 1) is in abutment. Now, the effective oil pressure of the large diameter spool run l” 21 f.
-The area of action is 81. Small diameter spool run F 21g
The effective hydraulic action area of 32. When the hydraulic pressure applied from pressure a13 is P, large diameter spool run I"
A +11 force in the 1-direction of Sl x P is applied to 21 f, and a downward thrust of s2 xp is applied to 2 small diameter spool run F'
A total thrust of 7 (S, -3,)P in the -1- direction is applied to 1e. In this embodiment, the spool 2Ie is rotated by the swing motor A against the hydraulic pressure.
The swing moke A is adjusted to have a torque of (S, -3,)P less than I-. Now, FIG. 1 shows an example in which the valve mechanism having the above structure is used as a pilot valve to control all the flow rate control valves 31. Between the primary side port 32 and the secondary side port 33 of the flow control valve 31, oil passages 34a and 34b are provided in parallel. - The valve seat 35a between the next side port 32 and the oil passage 34a is a poppet 36
The valve seat 3 is opened and closed by a and is located between the negative side port 32 and the oil whisker 34b.
5b is opened and closed by a poppet 36b. Further, a valve seat 37a between the oil passage 34a and the secondary side port 33 is opened and closed by a poppet 38a. A valve seat 37b between the oil passage 34b and the secondary port 33 is opened and closed by a poppet 38b. Then, 1 poppet 36a and poppet 36b are connected by lot 39, and 2 poppets 38a and 38b are connected.
are connected by rod 40, so 1 Bopeno l-36
a and Bopeno 1 to 36b operate in conjunction. Poppet 38a and poppet 38b operate in conjunction. Further, a valve 21 is connected to a chamber 41 for moving the popeso 36a forward in the closing direction, and an orifice 43 is connected to a chamber 42 for moving the 2 cylinder 38b forward in the closing direction.
Valve 21 is connected via. Furthermore, a chamber 44 for advancing the poppet 36b in the closing direction is provided.
The valve 22 is connected to the chamber 45 through an orifice 46 for advancing the poppet 38a in the closing direction. Next, the operation of this embodiment will be explained with reference to the above matters and the Quim Jar 1 shown in FIG. In addition, in Figure 3,
(a) shows the pulse signal generated by the pulse oscillator 6; (b)
) indicates the time T for oil to pass through the oil passage 34b, and (C) indicates the time 'F for oil to pass through the oil passage 34a. First, assume that the polarity of the pulse generated by the pulse oscillator 6 in the initial state is negative as shown in FIG. 3 (a+). In the embodiment shown in FIG. 1, when the output of the pulse oscillator 6 is negative, the operating pin The left end of 1 is the S pole and the right end is the N pole.Therefore, the 1 operating pin 1 rotates counterclockwise around the shaft 2; They are each attracted to the permanent magnets 3. Therefore, in this initial state, as shown in FIG. Because it pushes down
In the valve 21, the space between the inlet 21a and the outlet 21b is covered by a spool land 21f. -Since the horn and pin 17 are opened, is the pressure at the valve 22? The spool 22e is lifted by the pilot pressure applied from the ffX13 through the oil passage 15, and the +1A inlet 22a and the discharge port 22b are brought into communication. Therefore, every time pyropressure is applied from the valve 22 to the chambers 44 and 45 of the 5 flow control valve 31, the 2 oil passage 342 is connected to the oil passage 34b by the boveno l-38a.
are each shielded by bobetsu l-36b, - next side entrance 3
If oil does not leak from 2 to the secondary side port 33. In this state, when the polarity of the pulse generated by the pulse oscillator 6 is reversed and becomes positive, the polarity of the actuating pin 1 is also reversed and 2
The left end becomes the north pole, 2 and the right end becomes the south pole, and a clockwise rotational force, ie, a rotational force in the direction of pushing down the pin 17, is generated in the operating pin 1. Now, an upward thrust of (s, -32)P is applied to the spoo )'v 22e from the source 13, and the swing motor A has a torque of at least (St 32 )P or more. 2 When a clockwise rotational force is generated on the operating pin 1, the pin 17 pushes down the spool 22e against the pilot pressure applied through the oil passage 15. 22a and discharge port 22
The space between b is shielded by the spool run F' 22 f. On the other hand, due to the clockwise rotation of the swing motor A, the 2 pins】6
is opened, so in the valve 21, the spool 21e is lifted by the oil added from the source 13 through the oil path 14, and the spool 21e is lifted up between the inlet port 2a and the outlet port 2b. is conductive. Then, pilot pressure is applied to the chamber 41 by conducting between the /R inlet 2+a and the discharge port 21b, and after a time difference T set as the diameter of the orifice 43 has elapsed, pilot pressure is applied to the chamber 42. First, by applying pilot pressure to the chamber 41, the valve seat 35a is closed and the valve seat 35b is opened. Since the valve seat 37b is open until the time T set by the orifice 43 has elapsed, the oil is supplied from the primary side port 32 to the secondary side 33 via the oil passage 34b within the time T shown in FIG. 3+b+. Oil flows. When the time T set by this orifice 43 has elapsed, the pyron pressure applied to the chamber 42 closes the valve seat 37'b. The passage of oil through the oil passage 34b is completed. Soshi゛ζ,
Thereafter, until the polarity of the pulses generated by the pulse oscillator 6 is reversed, the poppet 36a and the poppet 36a are used. 138b closes valve seat 35a and valve seat 37b, respectively, while poppet 36b and boveno I-38a continue to open valve seat 35b and valve seat 37a, respectively. Next, in this way, the pyro, I.
When pressure is applied, the pulse oscillator 6 generates a pulse, and when the polarity of the pulse is reversed again and becomes negative, the left end of the 1 actuation pin 1 becomes the S pole, and the right end becomes the N pole, and the left end of the 1 actuation pin 1 becomes the N pole. The right end is attracted to the permanent magnet 8 and the permanent magnet 9, respectively. And 1 pin 1G resists pilot pressure and spool 2
1e is pushed down, so in the valve 21, the inlet 2
The space between 1a and the discharge port 21 is cut off, and the 5th chamber 41 and the 5th chamber 42
Pyro 7+ pressure can no longer be applied to. At the same time, the spool land 22f of the valve 22 is released from the pin 17. The spool 22e is pushed down by pilot pressure, and oil flows from the inlet 22a to the outlet 22b. Therefore, the pilot pressure is applied to the chamber 44, and after the time difference T set as the diameter of the orifice 46 has elapsed, the pilot pressure is applied to the chamber 45. By applying pilot pressure to the chamber 44, the valve seat 35
b is closed, and the valve seat 35a is opened. The valve seat 37a remains open until the time T set by the orifice 46 has elapsed. Oil flows from the primary side port 32 to the secondary side port 33 via the oil path 34a during the time T shown in FIG. 3 tc+. When the time T711 set by the orifice 46 has elapsed, pilot pressure is applied to the chamber 45 and the valve seat 37a closes, so that the passage of oil through the oil passage 34a is completed. Thereafter, until the polarity of the noggle generated by the pulse oscillator 6 is reversed, the poppet 36b and the bopeno) 38
a closes the valve seat 35b and the valve seat 37a, respectively, and
Bobeno l□ 362 and poppet 38b are each valve seat 35
Opening a and valve seat 37b! The voice takes over. In this way, in this embodiment, when the polarity of the pulse generated by the pulse oscillator 6 is reversed from negative to positive, the oil remains in the oil for a short period of time T set by the orifice 43, as shown in FIG. 3(b). When oil passes through the path 34b and the polarity of the pulse generated by the pulse oscillator 6 is reversed from positive to negative, it continues until the minute time T set by the orifice 46 elapses as shown in FIG. Every time the polarity of the pulse is reversed, such as when oil passes through the oil passage 34a, a minute time T is generated.
Only oil passes through. From the primary side port 32 to the secondary side port 3 per pulse
3 is determined in proportion to the length of the minute time T during which the oil passage 34a or the oil passage 34b is open, and this minute time T is determined by the diameters of the orifice 43 and the orifice 46. Therefore. In this embodiment, by determining the diameters of the orifice 43 and the orifice 46, if the minute time difference T mentioned above is determined in advance, the amount of oil flowing from the -outlet side port 32 to the secondary side port 33 per one pulse can be determined. will be uniformly determined. and -next side port 32 per unit time (for example, 1 second)
Since the flow rate of oil flowing from to the secondary side port 33 is the meteor per pulse multiplied by the number of pulses per intermediate time (for example, 1 second), the frequency of the pulses generated by the 5-pulse oscillator 6 must be controlled. For example, the number of meteors per unit time can be precisely controlled. In the above description, the swing motor A is used as an example of an electromagnetic actuator, and the two operating pins 1 are swung around the shaft 2.
By moving pins 16 and 17 around, pie l:
Although an example was shown in which the voltage was switched between I 'y and
It may also be possible to allow it to fall. In addition, 5 above shows an example in which the oil passages 34a and 34b are provided in parallel so that oil is discharged both when the polarity of the pulse is reversed from positive to negative and when the polarity of the pulse is reversed from negative to positive. Even if the number of beats of one oil passage 34a to b is omitted, it is possible to control the flow rate based on the pulse frequency. In this case, oil will be discharged at either the timing when the polarity of the pulse is reversed from positive to fl or from negative to positive. In addition, in section -1-, the time difference T from when the pilot pressure is applied to the chamber 41 or the chamber 44 until the pyro-I pressure is applied to the chamber 42 or the chamber 45 is expressed as the time difference T between the orifice 43 and the orifice 4.
Although the example was shown in which the settings were made based on the diameter of chamber 4,
After pilot pressure is applied to chamber 1 or chamber 44, pyro is applied to chamber 42 or chamber 45. Any method can be used as long as it can accurately set the time difference T until the voltage is applied. For example, a choke may be used instead of an orifice. Furthermore, in the case of the above embodiment, ideal control characteristics can be obtained not only by adjusting the frequency of the pulse oscillator, but also by adjusting its output voltage, and by adjusting the diameter of the orifice. can be easily understood. Further, in the above, an example was shown in which the valve mechanism of the present invention is used as a picono valve of a flow rate control valve that digitally opens and closes, but the valve mechanism of the present invention is capable of high-speed operation. It goes without saying that it can be used as a single directional switching valve, and it also enables high-speed operation when used as a picono one-valve of a two-pilot switching type directional switching valve.

【effect】

As explained above, according to the present invention, the difference between the thrust applied to the large-diameter spool land from the normal reading and the thrust applied to the small-diameter spool land from the normal reading causes the oil that acts on the spool as a whole to Because it becomes pressure. Even if the correct hydraulic pressure is increased, the overall hydraulic pressure acting on the spool will be minute. Therefore. When this spool is actuated by an electric actuator, only a small amount of force is required from the electromagnetic actuator. Therefore, the electric actuator can be made smaller and faster. On the other hand, if the size of the electromagnetic actuator is not changed, it is possible to use a normal reading having a larger hydraulic pressure.Also, in the case of the second invention, a large diameter spool land and a small diameter spool land are used. They are connected by a spool lot, and the small-diameter spool land acts as a guide for the large-diameter spool land, making stable opening and closing operations possible.Therefore, as mentioned above, high-speed operation synchronized with the pulse cycle is particularly required. However, in cases where the valve mechanism of the present invention is used as a piconometric valve for a flow rate control valve that requires complete digital opening and closing, the valve mechanism of the present invention is capable of high-speed operation and can handle high pressure. In this respect, it is truly optimal.

[BRIEF DESCRIPTION OF THE DRAWINGS] FIG. 1 is a longitudinal sectional view showing an example of a valve mechanism according to an embodiment of the present invention used as a pilot valve of a flow rate control valve, and FIG. 2 is a valve 2 in FIG. 1] FIG. 3 is a time chart showing the operating state of the flow control valve shown in FIG. 1. FIG. 4 is a longitudinal sectional view of the conventional valve mechanism that is the premise of the present invention. . A... Swing motor 2... Operating pin 6...
Oscillator 13... Pressure source 14, 15... Pressure path 16, 17 Pin 21, 22... Valve 2
1a 21b...Inflow port 21b/22b/Discharge port 2 ] c 22 c -T port 21d/22d...Sleeve 21e 22e...Spool

Claims (3)

[Claims] (1) An electromagnetic actuator having at least two operating points, a spool having a large diameter spool land and a small diameter spool land in a sleeve extending from an inflow port to a discharge port, and a spool having a large diameter spool land and a small diameter spool land; two valves slidably interposed so that when the land opens and closes, a pressure in a direction opposite to the pressure applied from the inflow port to the large diameter spool land is applied from the inflow port to the small diameter spool land; A common pressure source is connected to the inlet of each of the two valves, and each operating point of the electromagnetic actuator applies a force in the closing direction to the large diameter spool land of each of the valves. and the force of the electromagnetic actuator is greater than the difference between the thrust applied from the pressure source to the large diameter spool land and the thrust applied from the pressure source to the small diameter spool land. (2) In the valve mechanism according to claim 1, the electromagnetic actuator includes a swing motor configured to swing an operating pin having operating points at both ends thereof, the operating pin A valve mechanism characterized in that a force in a closing direction is applied to each of the large diameter spool lands at both ends of the valve mechanism. (3) The valve mechanism according to claim 1 or 2, wherein the seat portion of each of the large diameter spool lands is shaped like a poppet.