JP2966597B2 - Two-way solenoid valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solenoid valve for controlling a refrigerant in a heat pump type air conditioner, and more particularly to a two-way solenoid valve which operates in the same manner when the direction of refrigerant flow is reversed in a cooling / heating air conditioner.

[0002]

2. Description of the Related Art Conventionally, air conditioners having a heat pump type refrigeration circuit are widely used as air conditioners for cooling and heating.
A so-called multi-type air conditioner, which distributes refrigerant from a plurality of compression devices to a plurality of chambers and performs cooling and heating individually, is increasing. In such a multi-type air conditioner, a three-pipe type apparatus as shown in FIG. 4 in which an indoor unit and an outdoor unit are connected by three pipes in order to simultaneously perform cooling and heating for each room in parallel. Is used.

In this apparatus, a set of solenoid valves a and b for switching between cooling and heating is provided for each indoor unit I.
At the time of cooling, the electromagnetic valve a communicating with the discharge gas line A is closed and the electromagnetic valve b communicating with the suction gas line B is opened, thereby introducing the liquid refrigerant from the liquid line C into the indoor heat exchanger E and sending it to the suction gas line B. In addition, at the time of heating, the solenoid valve a communicating with the discharge gas line A is opened and the solenoid valve b communicating with the suction gas line B is closed to introduce the hot gas refrigerant from the suction gas line B into the indoor heat exchanger E so as to be in a liquid state. The refrigerant is sent to the liquid line C. Here, O is an outdoor unit, and M is a compressor.

[0004] However, in this system, there is a problem that the length of the piping becomes long and the equipment cost increases, and it is not easy to balance the thermal efficiency when the liquid refrigerant obtained in the heating indoor unit is used in the cooling indoor unit. Therefore, the flow dividing unit R is provided between the indoor unit I and the outdoor unit O, and the distance between the outdoor unit O and the flow dividing unit R and between the flow dividing unit R and each indoor unit I are all two. An apparatus as shown in FIG. 5 connected by book pipes has been proposed. In this device, the piping between the outdoor unit O and the diversion unit R is switched between high pressure and low pressure by a four-way valve D provided in the outdoor unit O. One of the pipes between the two is a liquid refrigerant, but the other is converted into a high-pressure gas and a low-pressure gas. Therefore, even if the flow direction is reversed, the solenoid valve provided in the branch unit R has a large flow rate. It is required that the valve be a two-way solenoid valve capable of controlling the fluid.

Conventional two-way solenoid valves usable in such a case are disclosed, for example, in JP-A-49-30917 (FIG. 6) and JP-A-49-5716. (FIG. 7). However, in these valves, the flow rate of the controlled fluid cannot be large, and when the controlled fluid flows in the opposite direction, the valve body pressed against the valve seat β by the valve closing spring α. Since γ is configured to be pushed open by the pressure of the controlled fluid, at least 0.15 to γ is required between the primary pressure and the secondary pressure.
Without the differential pressure of 0.2 kgf / cm ^2, the valve would not open fully, and this pressure loss was a constraint on improving the energy efficiency of the air conditioner. If the valve closing spring is weakened to reduce the pressure loss, the operation of the valve becomes unstable, especially when the flow rate is small, and there is a problem that abnormal noise is generated. Was said to have a limit.

[0006]

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to reduce the pressure loss of the controlled fluid by making it impossible to increase the flow rate of the controlled fluid in the above-described conventional two-way solenoid valve. Two-way electromagnetic that can stably control the flow of a large amount of fluid by exactly the same operation with almost no pressure loss regardless of whether the flow direction of the fluid is normal or reverse. It is intended to provide a valve.

[0007]

SUMMARY OF THE INVENTION The object of the present invention is as follows.
A main valve seat having a second fluid passage having a smaller diameter than the valve chamber is provided at the bottom of the cylindrical valve chamber communicating with the first fluid passage, and the valve chamber is divided into a back pressure chamber and a main flow passage. A first check valve which slidably fits a piston-shaped main valve body in the valve chamber and allows a flow from the main flow path into the back pressure chamber in the main valve body. A second leak passage provided with a second check valve for permitting the leak flow path and the second fluid passage to flow into the back pressure chamber; and a third leak passage allowing the flow from the back pressure chamber to the main flow path. A back pressure release passage provided with a check valve and a fourth check valve permitting outflow from the back pressure chamber to the second fluid passage; and a back pressure chamber side opening of the back pressure release passage. An electromagnetically actuated sub-valve that can open and close a sub-valve seat formed in the portion is provided coaxially with the main valve body, and a main valve spring that biases the main valve body in a direction away from the main valve seat is provided. Both sides characterized by It can be achieved by an electromagnetic valve.

Further, a main valve seat having a second fluid passage having a smaller diameter than the valve chamber is provided at the bottom of the cylindrical valve chamber communicating with the first fluid passage. A first reverse valve that slidably fits a piston-shaped main valve body into the valve chamber so as to be divided into a main flow passage and a main flow passage. A first leak passage provided with a stop valve and a second leak passage provided with a second check valve permitting inflow from the second fluid passage into the back pressure chamber; (2) An electromagnetically actuated plunger provided with a valve opening member capable of simultaneously opening the check valve, and a main valve spring for urging the main valve body away from the main valve seat is provided. This can also be achieved by a directional solenoid valve.

[0009]

In the bidirectional solenoid valve of the present invention, when the valve is closed, the primary pressure of the controlled fluid is applied to the back pressure chamber, so that the main valve body is pressed against the main valve seat. The fluid pressure in the back pressure chamber is released to the low pressure side through the flow path provided in the main valve body, and there is no difference between the primary pressure and the secondary pressure of the controlled fluid due to the action of the main valve spring at this time. The main valve is also fully opened. Therefore, a large amount of fluid can be circulated with almost no pressure loss.

[0010]

【Example】

(First Embodiment) A first embodiment of a two-way solenoid valve according to the present invention will be described with reference to FIG. In FIG. 1, 1 is a valve body,
A main valve seat 1b is provided at the bottom of the cylindrical valve chamber 1a communicating with the first fluid passage 2a, and the second fluid passage 2b is open here. A piston-shaped main valve body 3 is slidably fitted in the valve chamber 1a, and divides the valve chamber 1a into a back pressure chamber 1c and a main flow path 1d. Here, since the diameter of the main valve seat 1b is smaller than the diameter of the valve chamber 1a, even when the main valve body 3 is seated on the main valve seat 1b, the pressure in the main flow path 1d remains on the bottom surface of the main valve body 3. This is the case.

The main valve body 3 is provided with a compound check valve having a ball-shaped check valve body 3a, a first check valve seat 3b and a second check valve seat 3e. Although the fluid in the main flow path 1d can flow into the back pressure chamber 1c through the first leakage flow path 3c by the valve body 3a and the first check valve seat 3b, on the contrary, the back pressure chamber 1c
A first check valve that cannot flow out from the main flow path 1d to the main flow path 1d, and the fluid in the second fluid passage 2b is formed by the check valve body 3a and the second check valve seat 3e. (2) A second check valve that can flow into the back pressure chamber 1c through the leak passage 3f but cannot flow out from the back pressure chamber 1c toward the second fluid passage 2b. ing.

Further, the main valve body 3 is provided with a back pressure release flow passage 3g extending from the back pressure chamber 1c to the main flow passage 1d and the second fluid passage 2b. Fluid in the back pressure release flow passage 3g is provided. Main channel 1
d to the main flow path 1d
The third check valve 3h, which cannot flow into the back pressure release flow path 3g, and the fluid in the back pressure release flow path 3g can flow out toward the second fluid passage 2b.
Conversely, fourth check valves 3i which cannot flow from the second fluid passage 2b toward the back pressure release passage 3g are provided. A sub-valve seat 3j is formed at the back pressure chamber side opening of the back pressure release passage 3g. Reference numeral 3k is a packing for sealing between the inner wall of the valve chamber 1a and the outer wall of the main valve body 3 so as not to leak fluid.

Reference numeral 4 denotes a plunger which is electromagnetically operated by an electromagnetic coil 5. A sub-valve 4 a capable of opening and closing the sub-valve seat 3 j is provided at the tip of the plunger 4 so as to be coaxial with the main valve 3. Reference numeral 6 denotes a main valve spring that biases the main valve body 3 in a direction away from the main valve seat 1b.
This is a plunger spring biased toward j.

When fluid is supplied from the first fluid passage 2a in this valve, if the electromagnetic coil 5 is not energized, the sub-valve 4a closes the sub-valve seat 3j and at the same time the main valve 3
Also contact the main valve seat 1b. Then, the fluid in the main flow path 1d flows into the back pressure chamber 1c from the first leakage flow path 3c via the first check valve seat 3b, and at this time, the check valve body 3a is pressed against the second check valve seat 3e. Therefore, the fluid cannot flow out to the second fluid passage 2b. Therefore, the pressure in the back pressure chamber 1c becomes equal to the pressure in the main flow path 1d , and the first fluid passage 2
The main valve body 3 is pressed against the main valve seat 1b by a force obtained by multiplying the pressure difference between the pressure difference a and the second fluid passage 2b by the area of the main valve seat 1b. However, the plunger spring 7 than the force of the main valve spring 6 at this time
Must be configured to have a large force.

Next, when the electromagnetic coil 5 is energized, the sub-valve 4a
Is separated from the sub-valve seat 3j, and the fluid in the back pressure chamber 1c flows toward the second fluid passage 2b through the back pressure release passage 3g and the fourth check valve 3i. Is closer to the pressure in the second fluid passage 2b, the force obtained by multiplying the pressure difference between the back pressure chamber 1c and the main flow path 1d by the area difference between the main valve body 3 and the main valve seat 1b, and the urging force of the main valve spring 6. As a result, the main valve body 3 separates from the main valve seat 1b. Then, the main valve element 3 is fully opened by the combined force of the force obtained by multiplying the differential pressure between the back pressure chamber 1c and the main flow path 1d by the sectional area of the main valve element 3 and the urging force of the main valve spring 6. At this time, even if the differential pressure between the back pressure chamber 1c and the main flow path 1d becomes almost zero, the main valve body 3 maintains a stable fully open state due to the urging force of the main valve spring 6.

Conversely, when fluid is supplied from the second fluid passage 2b and the electromagnetic coil 5 is in a non-energized state, the sub-valve 4a closes the sub-valve seat 3j and the main valve Since the body 3 is also in contact with the main valve seat 1b, the second fluid passage 2b
The fluid inside flows into the back pressure chamber 1c from the second leak passage 3f via the second check valve seat 3e. At this time, the check valve body 3a
The fluid is pressed against the check valve seat 3b, and the fluid flows into the main flow path 1d.
Can not be leaked to Therefore, the pressure in the back pressure chamber 1c becomes equal to the pressure in the second fluid passage 2b, and the pressure difference between the second fluid passage 2b and the first fluid passage 2a is reduced by the area of the main valve body 3 and the main valve seat 1b. The main valve body 3 is pressed against the main valve seat 1b by the force multiplied by the difference.

Next, when the electromagnetic coil 5 is energized, the sub-valve 4a
Is separated from the sub-valve seat 3j, and the fluid in the back pressure chamber 1c flows out toward the main flow path 1d via the back pressure release passage 3g and the third check valve 3h. The main valve body 3 approaches the pressure in the passage 1d, and is formed by the combined force of the force obtained by multiplying the differential pressure between the back pressure chamber 1c and the second fluid passage 2b by the sectional area of the main valve seat 1b and the urging force of the main valve spring 6. Will be fully opened. At this time, even if the differential pressure between the back pressure chamber 1c and the main flow path 1d becomes almost zero, the main valve body 3 maintains a stable fully open state due to the urging force of the main valve spring 6.

(Second Embodiment) FIGS. 2A and 2B are longitudinal sectional views of a two-way solenoid valve according to a second embodiment of the present invention.
(B) of the figure is a longitudinal sectional view of the main valve body portion cut in a direction perpendicular to the section of (a). In FIG.
Reference numeral 11 denotes a valve body, and a main valve seat 11b is provided at the bottom of a cylindrical valve chamber 11a communicating with the first fluid passage 12a, and the second fluid passage 12b is open here. This is the same as the embodiment. The first embodiment is different from the first embodiment in that a piston-shaped main valve body 13 is slidably fitted in the valve chamber 11a, and the valve chamber 11a is divided into a back pressure chamber 11c and a main flow path 11d. The same is true.

The main valve body 13 is provided with a first leak passage 13b provided with a first check valve 13a and a second leak passage 13d provided with a second check valve 13c. The fluid in the passage 11d can flow into the back pressure chamber 11c via the first leak passage 13b, but on the contrary, the main passage 11
d is not allowed to flow out, and the fluid in the second fluid passage 12b is
Although it is possible to flow into the back pressure chamber 11c via 3d, it is configured such that it cannot flow out from the back pressure chamber 11c toward the second fluid passage 12b.

The main valve body 13 has the same structure as the first embodiment.
A back pressure release flow path 13e is provided from the back pressure chamber 11c to the main flow path 11d and the second fluid passage 12b, and the fluid in the back pressure release flow path 13e can flow toward the main flow path 11d. Conversely, the third check valve 13f, which cannot flow from the main flow path 11b to the back pressure release flow path 13e, and the fluid in the back pressure release flow path 13e flows out to the second fluid path 12b. Can be done, but on the contrary
Fourth check valves 13g, which cannot flow from the fluid passage 12b toward the back pressure release passage 13e, are provided. Further, a sub-valve seat 13h is formed at the back pressure chamber side opening of the back pressure release passage 13e, similarly to the first embodiment. Reference numeral 13i denotes a packing for sealing between the inner wall of the valve chamber 11a and the outer wall of the main valve body 13 so as not to leak fluid.

A sub-valve 14a, which can open and close the sub-valve seat 13h, is provided at the tip of the plunger 14 which is electromagnetically actuated by the electromagnetic coil 15, and separates the main valve 13 from the main valve seat 11b. The main valve spring 16 and the plunger spring 17 for urging the sub-valve element 14a toward the sub-valve seat 13h are provided similarly to the first embodiment.

This valve is characterized in that a first leak passage 13b having a first check valve 13a and a second leak passage 13d having a second check valve 13c are provided independently. First
Although different from the first embodiment, the other configuration is almost the same as that of the first embodiment, and the operation status is the same as that of the first embodiment.

(Third Embodiment) FIG. 3 is a longitudinal sectional view of a two-way solenoid valve according to a third embodiment of the present invention. In FIG.
Is a valve body, a main valve seat 21b is provided at the bottom of a cylindrical valve chamber 21a communicating with the first fluid passage 22a, and the second fluid passage 22b is open here. Same as the example. Also, a piston-shaped main valve body 23 is slidably fitted in the valve chamber 21a, and the valve chamber 21a is divided into a back pressure chamber 21c and a main flow path 21d.
This is the same as the embodiment.

The main valve body 23 is provided with a first leak passage 23b provided with a first check valve 23a and a second leak passage 23d provided with a second check valve 23c. Although the fluid in the passage 21d can flow into the back pressure chamber 21c through the first leak passage 23b, the fluid from the back pressure chamber 21c
d is not allowed to flow out, and the fluid in the second fluid passage 22b is
Although it is possible to flow into the back pressure chamber 21c via 3d, it is configured such that it cannot flow out from the back pressure chamber 21c toward the second fluid passage 22b.

A plunger 24 electromagnetically operated by an electromagnetic coil 25 is provided so as to be coaxial with the main valve body 23. A first check valve 23a is provided at the tip of the plunger 24.
And a locking step 23 formed at the rear end of the second check valve 23c
e and 23f are provided so that the first check valve 23a and the second check valve 23c are both opened when the plunger 24 is attracted to the electromagnetic coil 25. ing. Here, 23g is a throttle valve provided in the second leak passage 23d to limit the flow rate flowing into the back pressure chamber 21c, but does not limit the flow rate in the reverse direction.
Reference numeral 26 denotes a main valve spring that urges the main valve body 23 in a direction away from the main valve seat 21b, and reference numeral 27 denotes a plunger spring that urges the valve opening member 24a toward the main valve body 23.

In this valve, when the electromagnetic coil 25 is in a non-energized state, the valve opening member 24a is disengaged from the locking steps 23e and 23f, and the first check valve 23a and the second Each of the stop valves 23c is in a normal operation state.
Therefore, when the fluid is supplied from the first fluid passage 22a, the fluid in the main flow passage 21d flows from the first leak passage 23b to the first
It flows into the back pressure chamber 21c through the check valve 23a , but cannot flow out of the back pressure chamber 21c to the second fluid passage 22b. Therefore, as in the case of the first embodiment, the pressure in the back pressure chamber 21c becomes equal to the pressure in the main flow path 21b, and
The main valve element 3 is pressed against the main valve seat 1b by a force obtained by multiplying the pressure difference between the second fluid passage 22b and the area of the main valve seat 1b.

Next, when the electromagnetic coil 25 is energized, the valve opening member 24a engages with the locking steps 23e and 23f to pull up the first check valve 23a and the second check valve 23c. 23a and 23c are both open, the pressure in the back pressure chamber 21c approaches the pressure in the second fluid passage 22b, and the main valve body 23 separates from the main valve seat 21b as in the first embodiment. become. Then back pressure chamber 2
The combined force of the force obtained by multiplying the differential pressure between 1c and the main flow path 21d by the sectional area of the main valve body 23 and the urging force of the main valve spring 26 causes the main valve body 23 to be fully opened, and the urging force of the main valve spring 26 Therefore, the main valve body 23 maintains a stable fully open state in the same manner as in the first embodiment.

On the contrary, when the fluid is supplied from the second fluid passage 22b, the fluid flows into the back pressure chamber 21c from the second fluid passage 22b. When the electromagnetic coil 25 is energized, the fluid in the back pressure chamber 21 c is
d, the pressure in the back pressure chamber 21c is
d, the back pressure chamber 21c and the second fluid passage 22
The main valve body 23 is opened by the resultant force of the force obtained by multiplying the pressure difference between the pressure difference b and the sectional area of the main valve seat 21b and the urging force of the main valve spring 26. Thus, the main valve body 23 maintains a stable fully open state due to the urging force of the main valve spring 26.

[0029]

Since the two-way solenoid valve of the present invention is a pilot-type solenoid valve having the above-described configuration, the two-way solenoid valve has a structure in which the primary side and the secondary side are asymmetric, and the flow direction of the fluid is large. Operates in exactly the same manner even if the rotation is reversed, the fluid control characteristics are symmetrical, and there is a feature that almost no pressure loss occurs regardless of the flow direction of the fluid. In addition, except for the structure of the main valve body, other parts used in a normal solenoid valve can be diverted almost as they are, which is advantageous for mass production and economical.

[Brief description of the drawings]

FIG. 1 is a structural view showing a longitudinal section of a first embodiment of a bidirectional solenoid valve of the present invention.

FIG. 2 is a structural view showing a longitudinal section of a second embodiment of the bidirectional solenoid valve of the present invention.

FIG. 3 is a structural view showing a longitudinal section of a third embodiment of the bidirectional solenoid valve of the present invention.

FIG. 4 is a three-pipe refrigeration circuit diagram in a simultaneous cooling / heating type air conditioning system.

FIG. 5 is a two-pipe refrigeration circuit diagram in a simultaneous cooling / heating type air conditioning system.

FIG. 6 is a structural view showing a longitudinal section of an example of a conventional bidirectional solenoid valve.

FIG. 7 is a structural view showing a longitudinal section of another example of the bidirectional solenoid valve of the prior art.

[Explanation of symbols]

 1, 11, 21 Valve body 1a, 11a, 21a Valve chamber 1b, 11b, 21b Main valve seat 1c, 11c, 21c Back pressure chamber 1d, 11d, 21d Main flow path 2a, 12a, 22a First fluid path 2b, 12b, 22b Second fluid passage 3, 13, 23 Main valve body 3a Check valve body 3b First check valve seat 3c First leak passage 3e Second check valve seat 3f Second leak passage 3g Back pressure release passage 3h Third check valve 3i Fourth check valve 3j Secondary valve seat 3k Packing 13a First check valve 13b First leak passage 13c Second check valve 13d Second leak passage 13e Back pressure release passage 13f Third check Valve 13g Fourth check valve 13h Secondary valve seat 13i Packing 23a First check valve 23b First leak passage 23c Second check valve 23d Second leak passage 23e, 23f Locking step 23g Throttle valve 4, 14, 24 Plunger 4 , 14a Sub-valve 24a Valve-opening member 5, 15, 25 Electromagnetic coil 6, 16, 26 Main valve spring 7, 17, 27 Plunger spring α Valve closing spring β Valve seat γ Valve A Discharge gas line B Intake gas line C Liquid line D Four-way valve E Indoor heat exchanger I Indoor unit M Compressor O Outdoor unit R Distribution unit a, b Solenoid valve

Claims (2)

(57) [Claims] A main valve seat having a second fluid passage having a smaller diameter than the valve chamber is provided at a bottom of a cylindrical valve chamber communicating with the first fluid passage, and the valve chamber is connected to a back pressure chamber and a main flow chamber. A first piston-shaped main valve body is slidably fitted in the valve chamber so as to be divided into a passage and a first passage for allowing the main valve body to flow into the back pressure chamber from the main flow path.
A first leakage flow path provided with a check valve, a second leakage flow path provided with a second check valve permitting flow from the second fluid passage into the back pressure chamber, and a main flow path from the back pressure chamber A third check valve for allowing outflow to the second fluid passage, and a back pressure release flow path including a fourth check valve for allowing outflow from the back pressure chamber to the second fluid passage. An electromagnetically operated sub-valve that can open and close the sub-valve seat formed at the back pressure chamber side opening of the flow path is provided coaxially with the main valve body,
And a main valve spring for urging the main valve body away from the main valve seat. 2. A main valve seat having a second fluid passage having a smaller diameter than the valve chamber is provided at the bottom of a cylindrical valve chamber communicating with the first fluid passage. A first piston-shaped main valve body is slidably fitted in the valve chamber so as to be divided into a passage and a first passage for allowing the main valve body to flow into the back pressure chamber from the main flow path.
A first leak passage provided with a check valve and a second leak passage provided with a second check valve permitting inflow from the second fluid passage into the back pressure chamber; An electromagnetically actuated plunger having a valve opening member capable of simultaneously opening the second check valve is provided, and a main valve spring for biasing the main valve body in a direction away from the main valve seat is provided. Two-way solenoid valve.