JP4629258B2 - Solenoid control valve - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an electromagnetic control valve, and more particularly to an electromagnetic control valve used as an electromagnetic proportional expansion valve for a refrigeration cycle apparatus, an electromagnetic proportional flow valve for a fuel cell system, or the like.
[0002]
[Prior art]
As electromagnetic control valves for proportional flow control, there are electromagnetic proportional expansion valves used in refrigeration squill devices such as air conditioners, and electromagnetic proportional flow valves for fuel gas flow control used in fuel cell systems. As an electromagnetic control valve of a kind, the one shown in Japanese Utility Model Publication No. 7-18939 is known.
[0003]
An electromagnetic control valve for proportional flow rate control includes a valve housing that defines a valve port, an inlet / outlet port, and the like, a valve body that is provided in the valve housing and opens and closes the valve port, a plunger, a suction element, a coil portion, and the like. An electromagnetic solenoid device that opens and closes the valve body, and biasing means such as a spring that biases the valve body in a direction that opposes the valve driving force by the electromagnetic solenoid device. The opening position of the valve element with respect to the valve port is determined by the balance relationship with the valve biasing force by the biasing means, and the flow rate can be proportionally controlled according to the coil current of the electromagnetic solenoid device.
[0004]
[Problems to be solved by the invention]
In order to perform proportional flow rate control with high accuracy by coil current control using the electromagnetic control valve as described above, the following is necessary.
(1) The valve body does not rattle and moves in the direction of separation and connection while maintaining concentricity with respect to the valve port.
(2) Friction resistance during movement of the valve body is small, and the hysteresis of the valve position with respect to the coil current of the electromagnetic solenoid device is small.
[0005]
However, in the conventional electromagnetic control valve, with regard to (1), the valve body is formed at one end of the valve stem and the other end extends to the plunger side of the electromagnetic solenoid device, and the guide of the valve stem is more than the valve seat. Since it can be performed only on the plunger side of the electromagnetic solenoid device, it is difficult to ensure that the valve body moves in the connecting / disconnecting direction while maintaining concentricity with respect to the valve port. This is improved to some extent by reducing the gap between the outer peripheral surface of the valve stem and the inner peripheral surface of the guide portion, but on the other hand, the frictional resistance during movement of the valve body increases and the hysteresis of the valve position is reduced. By increasing the size, it becomes difficult to perform proportional flow rate control with high accuracy.
[0006]
Regarding (2), the frictional resistance during movement of the valve body is reduced by shortening the dimension of the guide portion in the axial direction of the valve stem or by widening the gap between the outer peripheral surface of the valve stem and the inner peripheral surface of the guide portion. However, however, the degree of guarantee that the valve body moves in the contact / separation direction while maintaining concentricity with respect to the valve port is lowered, and it becomes difficult to perform proportional flow rate control with high accuracy.
[0007]
The present invention has been made to solve the above-described problems, and guarantees that the valve body moves in the separation / contact direction while maintaining concentricity with respect to the valve port; An object of the present invention is to provide a high-performance electromagnetic control valve capable of performing proportional flow rate control with high accuracy while achieving both low frictional resistance and low valve position hysteresis.
[0008]
[Means for Solving the Problems]
To achieve the above object, an electromagnetic control valve according to the present invention includes a valve housing that defines a first inlet / outlet port, a second inlet / outlet port, a valve chamber, a valve port, and a spring accommodating chamber, An electromagnetic solenoid device that includes a valve body that opens and closes the valve port, a plunger, a suction element, and a coil portion , and that opens and closes the valve body on one side of the valve body, and the valve body An electromagnetic control valve including spring means for energizing the valve body in a direction opposed to a valve driving force by the electromagnetic solenoid device and accommodated in the spring accommodating chamber on the other side of the first inlet / outlet port Is communicated directly with the valve chamber, the second inlet / outlet port communicates with the valve chamber via the valve port, and the valve chamber is connected to the valve chamber by a flexible diaphragm seal member hermetically connected to the valve body. The spring accommodating chamber is airtight It is, the suction element and the ball member which is movable supported on the central axis line direction fitted to the inner peripheral surface of the locking screw in the center axis and in the spring accommodating chamber of the valve port is disposed, A ball receiving member is fixed to a distal end portion of the valve body that penetrates the diaphragm seal member and is located in the spring accommodating chamber, and the ball member is automatically centripetally connected to the spring means on the opposite side of the valve body. In addition, the ball member is automatically centripetically connected to the valve body via the ball receiving member .
[0009]
According to this configuration, since the valve chamber and the spring accommodating chamber are hermetically separated by the diaphragm seal member, there is no flow (leakage flow rate) between the inlet / outlet ports other than the valve port portion. In addition, since the valve body is arranged on the central axis of the suction element and valve port by the automatic centripetal connection with the valve body by the ball member, the valve body can be opened and closed smoothly without contacting the suction element and the valve housing. In addition, the concentricity of the valve body with respect to the valve port is maintained, and the flow rate measurement accuracy in the valve port with respect to the valve port opening degree is guaranteed.
[0011]
According to this configuration, due to the automatic centripetal connection with the spring means by the ball member on the opposite side to the valve body, the direction of action of the spring force of the spring means on the valve body coincides with the axial direction of the valve body. Even if the orientation is inclined, the spring force of the spring means is prevented from acting as an eccentric load on the valve body, the concentricity of the valve body with respect to the valve port is maintained, and the flow rate at the valve port relative to the valve port opening is maintained. The weighing accuracy is further guaranteed.
[0012]
Further, in the electromagnetic control valve according to the present invention, the spring accommodating chamber communicates with the second inlet / outlet port through a pressure equalizing passage, and the effective pressure receiving diameter of the diaphragm seal member is equal to the effective pressure receiving diameter of the valve body. It is equal to the inner diameter of the valve port to be defined.
[0013]
According to this configuration, since the spring accommodating chamber communicates with the second inlet / outlet port through the pressure equalizing passage, the pressure on the second inlet / outlet port side is introduced into the spring accommodating chamber, Since the effective pressure receiving diameter of the diaphragm seal member is equal to the inner diameter of the valve port that defines the effective pressure receiving diameter of the valve body, the pressure on the first inlet / outlet port side and the pressure on the second inlet / outlet port side are the same. The force generated at the valve port side portion of the valve body and the force generated at the diaphragm seal member side hermetically connected to the valve body are canceled by each other, so that the first time when the valve body is opened and closed The flow rate can be controlled with high accuracy without being affected by the differential pressure between the pressure on the inlet / outlet port side and the pressure on the second inlet / outlet port side.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 shows an embodiment of an electromagnetic control valve according to the present invention.
[0015]
The electromagnetic control valve has a valve housing 11. The valve housing 11 includes an inlet port (first inlet / outlet port) 12, an outlet port (second inlet / outlet port) 13, a valve chamber 14, a valve port 15, an upper pressure equalizing chamber 16, a spring accommodating chamber (lower lower equalizing port). A pressure chamber 17 is formed. The valve port 15 is located between the valve chamber 14 and the upper pressure equalizing chamber 16, and a ring-shaped valve seat member 19 is fixed to the valve housing 11 along with a washer 18 on the valve chamber 14 side of the valve port 15.
[0016]
The inlet port 12 communicates directly with the valve chamber 14 through the passage 20 as the primary side, and the outlet port 13 communicates with the valve chamber 14 through the passage 21, the upper pressure equalization chamber 16, and the valve port 15 as the secondary side. Communicate.
[0017]
A valve body 23 is disposed in the valve chamber 14. The valve body 23 sets the opening degree of the valve port 15 according to the positional relationship with the valve seat member 19, decreases the opening degree of the valve port 15 by moving upward as seen in FIG. 1, and moves downward. The opening degree of the valve port 15 is increased.
[0018]
A valve rod 24 is integrally provided on one side (upper side) of the valve body 23. The valve stem 24 also serves as a plunger rod of an electromagnetic solenoid device 51 to be described later, and is disposed on the central axis of the guide hole 53 formed in the suction element 52 fixed to the valve housing 11. A gap is maintained so that the guide hole 53 of the child 52 and the valve stem 24 do not contact each other. Due to this gap, the pressure in the plunger chamber 58 and the outlet port 13 is equalized.
[0019]
The spring accommodating chamber 17 is formed at the end (lower end) of the valve housing 11 and is closed by a fixed spring retainer 25 screwed to the valve housing 11. The pressure passage 33 communicates with the outlet port 13 and communicates with the lower surface side of the diaphragm seal member 28 through the gap between the fixing screw member 27 and the ball member 32.
[0020]
Between the valve chamber 14 and the spring accommodating chamber 17, a flexible diaphragm seal whose outer edge side is hermetically connected to the valve housing 11 by a ring member 26 and a fixing screw member 27 that regulate the fully open position of the valve body 23. A member 28 is provided. A distal end portion 23 </ b> A of the valve body 23 is airtightly connected to the center portion of the diaphragm seal member 28 in a form that penetrates the diaphragm seal member 28. With this structure, the valve chamber 14 and the spring accommodating chamber 17 are completely hermetically separated.
[0021]
The area of the diaphragm seal member 28 where the differential pressure between the valve chamber 14 side and the spring accommodating chamber 17 side acts is determined by the effective pressure receiving diameter φDf of the diaphragm seal member 28, and the area between the valve chamber 14 side and the spring accommodating chamber 17 side is determined. The area of the valve port 15 side portion of the valve body 23 on which the differential pressure acts is determined by the inner diameter (effective pressure receiving diameter of the valve body 23) φD of the valve port 15, and the effective pressure receiving diameter φDf of the diaphragm seal member 28 and the valve port 15 The inner diameter φD is set to an equal dimension.
[0022]
A ball receiving member 29 is fixed to the distal end portion 23 </ b> A of the valve body 23 that passes through the diaphragm seal member 28 and is located in the spring accommodating chamber 17. A movable spring retainer 30 is disposed in the spring accommodating chamber 17, and a compression coil spring 31 is provided between the movable spring retainer 30 and the fixed spring retainer 25.
[0023]
The upper surface portion of the movable spring retainer 30 is a spherical seat portion 30A, and a ball member (steel ball) 32 is disposed between the spherical seat portion 30A and the ball receiving member 29 on the valve body 23 side. . The ball member 32 is fitted to the inner peripheral surface 27A of the fixed screw member 27 on the central axis of the suction element 52 and the valve port 15, and is movably supported by the fixed screw member 27. On the other hand, the ball member 32 is attached to the spherical seat portion 30A. On the other hand, it abuts on the ball receiving member 29 in a spherical articulated manner, and an automatic centripetal connection structure is formed between the valve element 23 and the movable spring retainer 30.
[0024]
An electromagnetic solenoid device 51 is attached to the end (upper end) of the valve housing 11. The electromagnetic solenoid device 51 includes a suction element 52 screwed to the valve housing 11, a bottom plate 54 fixed to the suction element 52, an outer rod 55 attached to the bottom plate 54, and a plunger case fixed to the suction element 52. 56 and a magnetic guide member 57 fitted and attached to the upper end portion of the outer casing 55, and a plunger chamber 58 is defined in the plunger case 56.
[0025]
The electromagnetic solenoid device 51 includes a plunger 59 that is inserted into the plunger case 56 so as to be movable in the axial direction, and a coil portion 60 that is provided in the outer casing 55. Is plated with a highly lubricating resin such as a fluororesin, and the frictional resistance of the sliding portion with the inner peripheral surface of the plunger case 56 is reduced. A fitting hole 59A is formed at the center of the plunger 59, and the upper end portion of the valve rod 24 is fitted into the fitting hole 59A so that both are fixedly connected. A pressure equalizing hole 59B for equalizing the space above the plunger 59 and the space below the plunger 59 in the plunger case 56 is provided at a slightly displaced position.
[0026]
The electromagnetic control valve having the above-described configuration operates as follows. When the coil portion 60 of the electromagnetic solenoid device 51 is energized, a magnetic attractive force corresponding to the amount of current is generated, and the plunger 59 is attracted to the attractor 52 side by the magnetic attractive force. This suction force acts on the valve body 23 by the valve rod 24 that also serves as a plunger rod.
[0027]
As a result, the valve body 23 is determined in the vertical movement position (valve opening position) based on the equilibrium relationship between the suction force of the electromagnetic solenoid device 51 and the spring force of the compression coil spring 31, and the opening degree of the valve port 15 is determined accordingly. Is decided. The flow rate of the fluid flowing from the inlet port 12 to the outlet port 13 is quantitatively measured by the opening degree of the valve port 15.
[0028]
The spring accommodating chamber 17 communicates with the outlet port 13 through the pressure equalizing passage 33, and the pressure on the outlet port 13 side is introduced into the spring accommodating chamber 17 for pressure balance, but the valve chamber 14, the spring accommodating chamber 17, Is completely hermetically separated by the diaphragm seal member 28, the flow path of the inlet port 12 → the valve chamber 14 → the spring accommodating chamber 17 → the pressure equalizing passage 33 → the outlet port 13 is not established, and the valve chamber 14 There is no leakage flow rate between the spring housing chamber 17 and the spring housing chamber 17.
[0029]
When the effective diameter of the valve port 15 (effective pressure receiving diameter of the valve body 23) is φD and the effective pressure receiving diameter of the diaphragm seal member 28 is φDf, the valve body 23 includes a primary pressure P1 on the inlet port 12 side and an outlet port. the differential pressure [Delta] P between the secondary pressure P2 of 13 side, an upward force generated in the valve port 15 parts (πD ^2/4) ΔP and a downward force caused in the diaphragm seal member 28 side (πDf ^2/4) ΔP However, when φD = φDf, they are canceled each other, and control that is not affected by the differential pressure ΔP in the opening and closing of the valve body 23 becomes possible.
[0030]
The valve body 23 fixedly connected to the plunger 59 and automatically centripetically connected to the ball member 32 has the inner peripheral surface 56A of the plunger case 56 as an upper guide and the inner peripheral surface 27A of the fixing screw member 27 as a lower guide. It arrange | positions so that a movement on the center axis | shaft of the suction element 52 and the valve port 15 is possible. Accordingly, the valve body 23 can be opened and closed without contacting the suction element 52 and the valve housing 11, the concentricity of the valve body 23 with respect to the valve port 15 is maintained, and the arrangement posture of the compression coil spring 31 is maintained. Even if there is an inclination, it is avoided that the spring force of the compression coil spring 31 acts on the valve body 23 as an unbalanced load, the concentricity of the valve body 23 with respect to the valve seat member 19 is maintained, and the valve is opened and closed. Hysteresis does not occur with time, and the flow rate measurement accuracy at the valve port 15 with respect to the valve port opening is guaranteed.
[0031]
As a result, the electromagnetic control valve performs high-accuracy proportional flow control as an electromagnetic proportional flow valve, and is required for an electromagnetic proportional flow valve for fuel gas flow control used in a fuel cell system. High flow control accuracy can be guaranteed.
[0032]
【The invention's effect】
As understood from the above description, according to the electromagnetic control valve of the present invention, the valve chamber and the spring accommodating chamber are hermetically separated by the diaphragm seal member, so that the flow between the inlet / outlet ports other than the valve port portion. (Leakage flow rate) does not occur. In addition, since the valve body is arranged on the central axis of the suction element and valve port by the automatic centripetal connection with the valve body by the ball member, the valve body can be opened and closed smoothly without contacting the suction element and the valve housing. Since the concentricity of the valve body with respect to the valve port can be maintained and the flow rate measurement accuracy at the valve port with respect to the valve port opening degree is guaranteed, electromagnetics used in refrigeration squill devices such as air conditioners It is possible to guarantee a high degree of flow control accuracy as required by a proportional expansion valve or an electromagnetic proportional flow valve for fuel gas flow control used in a fuel cell system.
[0033]
In addition, by the automatic centripetal connection with the spring means by the ball member on the opposite side of the valve body, the direction of the spring force of the spring means with respect to the valve body coincides with the axial direction of the valve body and the spring means is inclined to the arrangement posture. Even if there is, it is avoided that the spring force of the spring means acts on the valve body as an eccentric load, the concentricity of the valve body with respect to the valve port is maintained, and the flow rate measurement accuracy at the valve port with respect to the valve port opening is further improved. Higher flow rate as required by electromagnetic proportional expansion valves used in refrigeration squill devices such as air conditioners and electromagnetic proportional flow valves for fuel gas flow control used in fuel cell systems. Control accuracy can be further ensured.
[0034]
Further, since the spring accommodating chamber communicates with the second inlet / outlet port through the pressure equalizing passage, the pressure on the second inlet / outlet port side is introduced into the spring accommodating chamber, and then the diaphragm Since the effective pressure receiving diameter of the seal member is made equal to the inner diameter of the valve port defining the effective pressure receiving diameter of the valve body, the differential pressure between the pressure on the first inlet / outlet port side and the pressure on the second inlet / outlet port side Accordingly, the force generated at the valve port side portion of the valve body and the force generated at the side of the diaphragm seal member that is hermetically connected to the valve body are canceled each other, so that the first inlet / outlet port is opened when the valve body is opened and closed. The flow rate can be controlled with high accuracy without being affected by the differential pressure between the pressure on the side and the pressure on the second inlet / outlet port side.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing one embodiment of an electromagnetic control valve according to the present invention.
[Explanation of symbols]
11 Valve housing 12 Inlet port 13 Outlet port 14 Valve chamber 15 Valve port 16 Upper pressure equalizing chamber 17 Spring accommodating chamber 19 Valve seat member 23 Valve body 24 Valve rod 28 Diaphragm seal member 31 Compression coil spring 32 Ball member 33 Pressure equalizing passage 51 Electromagnetic solenoid device 52 Suction element 59 Plunger 60 Coil part

Claims (2)

A valve housing defining a first inlet / outlet port, a second inlet / outlet port, a valve chamber, a valve port and a spring accommodating chamber ; a valve body provided in the valve chamber for opening and closing the valve port; a plunger; child, comprising a coil portion, and an electromagnetic solenoid device for opening and closing the valve body there on one side of the valve body, is accommodated in the spring accommodating chamber at the other side of the valve body the solenoid device An electromagnetic control valve including spring means for urging the valve body in a direction opposite to the valve driving force by
The first inlet / outlet port communicates directly with the valve chamber, the second inlet / outlet port communicates with the valve chamber via the valve port;
The valve chamber and the spring accommodating chamber are hermetically separated by a flexible diaphragm seal member hermetically connected to the valve body,
A ball member which is fitted to an inner peripheral surface of a fixed screw member on a central axis of the suction element and the valve port and is movably supported in the direction of the central axis in the spring accommodating chamber is disposed, and the diaphragm seal member A ball receiving member is fixed to a tip portion of the valve body that penetrates the spring and is located in the spring accommodating chamber,
The ball member has an automatic centripetal connection with the spring means on the side opposite to the valve body, and the ball member has an automatic centripetal connection with the valve body via the ball receiving member. Control valve. The spring accommodating chamber communicates with the second inlet / outlet port through a pressure equalizing passage, and an effective pressure receiving diameter of the diaphragm seal member is equal to an inner diameter of the valve port that defines an effective pressure receiving diameter of the valve body. The electromagnetic control valve according to claim 1 .

Images