JP2001066020A - Electromagnetic flow rate control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electromagnetic flow control valve applicable to air conditioning systems having different optimal flow rate of refrigerant without modifying basic specifications concerning to the flow rate characteristics. SOLUTION: The electromagnetic flow control valve 1 for use as a pressure reducing means in a car air conditioning system can regulate the flow rate in three stages depending on the lift of a plunger 11. A flow rate regulating member 3 is fixed to the outlet port 6a of a valve body 2. The flow rate regulating member 3 is made of aluminum similarly to the body 2 into cylindrical shape having a round hole (refrigerant passage 3a) in the center and press fitted in an output port 6a. A plurality of kinds of flow rate regulating member 3 having a refrigerant passage 3a of different inside diameter are prepared previously and an optimal one is selected depending on the size of an evaporator used in the air conditioning system.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to an electromagnetic flow control valve used as a pressure reducing means in a refrigeration cycle.

[0002]

2. Description of the Related Art As a prior art, for example, Japanese Patent Application Laid-Open No. 11-1
An electromagnetic flow control valve disclosed in Japanese Patent No. 25472 is known. This electromagnetic flow control valve is used as pressure reducing means for reducing the pressure of the refrigerant supplied to the rear evaporator of the vehicle air conditioner, and is supplied to the rear evaporator by changing the value of the current flowing through the solenoid. The refrigerant flow rate can be controlled stepwise.

[0003]

However, when the size of the evaporator used in each air conditioning system is different, the optimal flow rate of the refrigerant supplied to the evaporator differs according to the size of the evaporator. In an air conditioning system using a large evaporator and an air conditioning system using a small evaporator, it is difficult to use electromagnetic flow control valves having the same specifications. That is, when an electromagnetic flow control valve used for an air conditioning system having a large evaporator is applied to an air conditioning system having a small evaporator, the flow rate of the refrigerant supplied to the evaporator becomes too large.

For this reason, when the size of the evaporator is different (when the optimum refrigerant flow rate supplied to the evaporator is different),
It is necessary to use an electromagnetic flow control valve corresponding to each air conditioning system. In this case, it is necessary to change the maximum flow rate of the electromagnetic flow control valve.However, the lift amount of the valve body and the orifice diameter, etc. built into the electromagnetic flow control valve, which is originally small in size, are determined by each air conditioning system. The setting corresponding to (1) has a problem that the cost is drastically increased because extremely high processing accuracy is required and strict component management is required. The present invention has been made based on the above circumstances, and an object of the present invention is to provide an electromagnetic flow control valve capable of responding to each air conditioning system having a different optimum refrigerant flow rate without changing basic specifications relating to flow characteristics. To provide.

[0005]

According to a first aspect of the present invention, there is provided a flow rate adjusting member which is attached to an outflow passage through which a depressurized refrigerant flows out through an orifice and has a refrigerant passage communicating with the outflow passage. ing. In this case, since the flow rate of the refrigerant can be adjusted according to the passage diameter of the flow adjustment member, for an air conditioning system having a different evaporator size, the electromagnetic flow control valve can be selected by selecting a flow adjustment member having an optimum passage diameter. It is possible to cope with the optimal refrigerant flow rate of each air conditioning system without changing the basic specifications relating to the flow rate characteristics of the air conditioner.

The orifice has at least a first orifice and a second orifice, and the first orifice and the second orifice are opened in a stepwise manner to step the refrigerant flow rate. Can be adjusted. When using the electromagnetic flow control valve as a pressure reducing means of the refrigeration cycle,
It is necessary to be able to adjust the refrigerant flow rate according to the cooling load. Therefore, at least the first orifice and the second orifice are configured to be able to be opened stepwise, and by selecting an appropriate flow rate adjusting member for an air conditioning system having a different evaporator size, It is possible to correspond to many air conditioning systems.

The orifice has at least a first orifice and a second orifice having different inner diameters, and selectively opens and closes the first and the second orifices. The refrigerant flow rate can be adjusted stepwise. Similarly to the case of the second aspect, when the electromagnetic flow control valve is used as the pressure reducing means of the refrigeration cycle, it is necessary to adjust the flow rate of the refrigerant according to the cooling load. Therefore, by configuring such that at least the first orifice and the second orifice having different inner diameters can be selectively opened and closed, and by selecting an appropriate flow rate adjusting member for an air conditioning system having different evaporator sizes, It is possible to support more air conditioning systems.

(Means of Claim 4) The flow regulating member can be easily fixed to the main body of the electromagnetic flow control valve by, for example, press fitting into the outflow passage.

[0009]

Next, an embodiment of the present invention will be described with reference to the drawings. (First Embodiment) FIG. 1 is a sectional view of an electromagnetic flow control valve 1. The electromagnetic flow control valve 1 of the present embodiment is used for a vehicle air conditioner that can independently control the temperature of a front side and a rear side of a vehicle, and is particularly used as a pressure reducing means of a rear side air conditioning system.

As shown in FIG. 1, the electromagnetic flow control valve 1 includes a valve body 2 made of, for example, aluminum die-casting. The valve body 2 is provided with a flow rate adjusting member 3, an electromagnetic actuator 4, and the like. I have. The valve body 2
An inflow passage 5 through which a refrigerant sent from a receiver (not shown) flows, an outflow passage 6 through which depressurized refrigerant flows out, a communication chamber 7 communicating the inflow passage 5 with the outflow passage 6, and the like are formed. A valve seat 8 is provided at the end. Also,
At an upstream end of the inflow passage 5 and a downstream end of the outflow passage 6, an inlet port 5 to which a refrigerant pipe (not shown) is connected, respectively.
a and an outlet port 6a.

The flow rate adjusting member 3 is made of, for example, the same aluminum as the valve body 2, and is provided in a substantially cylindrical shape having a central portion through which a round hole (hereinafter, referred to as a refrigerant passage 3a) penetrates.
As shown in (1), it is fixed to the outlet port 6a by press fitting. A plurality of types of the flow rate adjusting members 3 having different inner diameters of the refrigerant passages 3a are prepared in advance, and an optimal flow rate adjusting member 3 is selected according to the size (heat absorption capacity) of an evaporator (not shown) used in the air conditioning system. Is selected. The flow rate adjusting member 3 may be fixed by screwing, punching (partial caulking), or the like, instead of press fitting. The material of the flow rate adjusting member 3 may be a metal other than aluminum or a resin.

The electromagnetic actuator 4 includes a coil 9, a stator 10, a plunger 11, a stopper member 12, first to
The valve body 2 includes third springs 13 to 15 and the like.
It is attached to the upper part of. The coil 9 is sandwiched between two plates 16 and 17 forming a part of a magnetic circuit,
The energization is controlled by an ECU (electronic control device) that controls the operation of the air conditioning system. Note that an ECU (not shown) controls the blower air volume of the rear air conditioning system in three stages (Lo, Mi, Hi), and determines a current value (applied voltage) applied to the coil 9 in accordance with the blower air volume. It can be switched to three stages (IL, IM, IH). The stator 10 constitutes a part of a magnetic circuit together with the two plates 16 and 17, is arranged on the inner periphery of the coil 9, and is fixed to one of the plates 16 by screws 18 or the like.

The plunger 11 is made of a ferromagnetic material such as iron, and its upper side is slidably inserted into the inner periphery of the coil 9.
The lower part enters the communication chamber 7 of the valve body 2. The plunger 11 has a circular hole 19 for disposing the stopper member 12, a valve storage hole 20 for storing a valve element to be described later, and a plurality of lateral holes 21 communicating with the valve storage hole 20. Have been. The circular hole 19 is formed in a circular cross section downward from the upper end surface of the plunger 11 facing the stator 10.

The valve accommodating hole 20 is formed in a stepped hollow shape having a circular section in the upward direction from the lower end surface of the plunger 11 and having a smaller inner diameter at a predetermined depth from the lower end surface. Here, the one having the larger inner diameter is the large-diameter hole portion 20a,
The smaller inner diameter is called the small diameter hole 20b. In the center of the upper end surface of the small-diameter hole portion 20b, a valve portion 22 that protrudes downward in a conical shape is provided. Furthermore, the small diameter hole 2
A first washer 23 formed in a ring shape is fixed to a step surface between the large diameter hole 20a and the large diameter hole 20a.
A second washer 24, which is also formed in a ring shape, is fixed to the lower end surface of the second member. The horizontal hole 21 is formed in the small-diameter hole portion 20.
b (the deepest part of the valve housing hole 20) with the plunger 11
And penetrates the small-diameter hole portion 20b and the outside of the plunger 11.

The stopper member 12 regulates the amount of lift of the plunger 11 when the current supplied to the coil 9 is at the IL level, and is disposed between the stator 10 and the circular hole 19 of the plunger 11. The stator 10 and the plunger 11 are held by a stopper retainer 50 fastened to the plunger 11 and the second spring 14. However, when the coil 9 is de-energized (the state shown in FIG. 1), the stopper member 12 has a predetermined gap (referred to as a first lift amount) between the upper end surface of the stopper member 12 and the lower end surface of the stator 10. ) Is held in a secured state.

The first spring 13 is interposed between the stator 10 and the stopper member 12 and urges the plunger 11 downward in the figure with respect to the stator 10 via a stopper retainer 50. The second spring 14 is disposed in the circular hole 19 of the plunger 11, is interposed between the bottom surface of the circular hole 19 and the stopper member 12, and stores the spring force therebetween. The third spring 15 regulates the lift of the plunger 11 when the current supplied to the coil 9 is at the IM level, and is disposed in the circular hole 19 of the plunger 11 along with the second spring 14. ing. However, the total length of the third spring 15 (the length in the vertical direction in FIG. 1) is such that the circular hole 1
9 is set to be shorter than the distance between the bottom surface of the stopper member 9 and the lower end surface of the stopper member 12, and the difference (referred to as a second lift amount) is larger than the first lift amount.

The valve body accommodated in the valve accommodating hole 20 of the plunger 11 has a first valve body 25 slidably disposed on the inner periphery of the small-diameter hole portion 20b and the inner wall of the large-diameter hole portion 20a. And a second valve element 26 slidably disposed. First valve body 25
Is provided in a cylindrical shape through which a circular hole (referred to as a first passage 25a) penetrates a central portion, and has a plurality of outer peripheral surfaces along a penetrating direction of the first passage 25a as shown in FIG. Is provided. The first passage 25a is
The upper end opening surface is opened and closed by the valve portion 22 of the plunger 11, and is closed by the valve portion 22 when the coil 9 is not energized. Further, when the coil 9 is not energized, the distance between the first washer 23 fixed to the plunger 11 and the step surface of the first valve body 25 provided with the slit portion 25b is equal to the above-mentioned first distance. It is set substantially equal to the lift amount. Therefore, when the plunger 11 is lifted by the first lift amount, the first washer 23 comes into contact with the step surface of the first valve body 25 (see FIG. 3).

The second valve body 26 is provided in the shape of a ring having a round hole (referred to as a second passage 26a) in the center, and the valve seat portion 8 of the valve body 2 and the first valve body 25 are provided. And placed between. The inner diameter of the second passage 26a is slightly smaller than that of the outflow passage 6 of the valve body 2, and the first passage 25a
Has an inner diameter slightly smaller than that of the second passage 26a. When the plunger 11 is lifted by the second lift amount and the first valve body 25 is lifted upward by the first washer 23, the second valve body 26
5 between the large-diameter hole 20a and the second passage 2
6a communicates directly (see FIG. 4).

When the coil 9 is not energized, the distance between the second washer 24 and the second valve body 26 is set to be substantially equal to the second lift amount. Therefore, the plunger 11
Is lifted by the second lift amount, the second washer 24
Abuts against the lower end surface of the second valve body 26 (see FIG. 4). Further, the plunger 11 is lifted by the second lift amount or more, and the second
When the second valve body 26 is lifted upward by the washer 24, the space between the valve seat portion 8 and the second valve body 26 is opened, and the communication chamber 7 and the outflow passage 6 are in direct communication (FIG. 5).

Next, the operation of this embodiment will be described with reference to FIGS. a) When the coil 9 is not energized, as shown in FIG.
The plunger 11 is pushed downward by the urging force of the spring 13, so that between the valve seat portion 8 and the second valve body 26 and between the second valve body 26 and the first valve body 25,
Each is in a closed state, and the upper end opening of the first passage 25 a is closed by the valve portion 22 of the plunger 11.

B) Thereafter, when the coil 9 is energized with the current value IL, the plunger 11 is attracted to the stator 10 while pressing and contracting the first spring 13, and lifted by the first lift amount. As a result, as shown in FIG. 3, when the valve portion 22 of the plunger 11 opens the upper end opening of the first passage 25a, the refrigerant flowing into the inflow passage 5 is moved into the inflow passage 5 → communication chamber 7 → lateral hole. 21 → small-diameter hole 20b → first passage 25a → second passage 26a → outflow passage 6 → refrigerant passage 3a of flow rate adjusting member 3 and supplied to the evaporator (this flow of the refrigerant Call it flow).

C) Subsequently, when the coil 9 is energized at the current value IM, the plunger 11 is further attracted to the stator 10 while pressing and contracting the second spring 14, and lifted by the second lift amount. As a result, as shown in FIG. 4, the first valve body 25 is lifted by the first washer 23, and the space between the first valve body 25 and the second valve body 26 is opened, so that the inflow passage is opened. In addition to the above-described first flow, the refrigerant that has flowed into the flow path 5 has an inflow passage 5 → a communication chamber 7 → a lateral hole 21 → a small diameter hole 20 b → a slit 25 b → a large diameter hole 20 a → a first valve body 25. Between the second valve body 26 and the second passage 26a →
Outflow passage 6 → flows sequentially through refrigerant passage 3a of flow rate adjusting member 3 and is supplied to the evaporator (this refrigerant flow is referred to as a second flow).

D) Subsequently, when the coil 9 is energized with the current value IH, the plunger 11 is further attracted to the stator 10 while compressing and compressing the third spring 15, and the upper end surface of the plunger 11 contacts the stator 10. Lift to the touching position. As a result, as shown in FIG. 5, the second valve body 26 is lifted by the second washer 24, and
The opening between the first valve body 26 and the second valve body 26 opens the inflow passage 5.
The liquid refrigerant that has flowed into the first and second flows, as well as the inflow passage 5 → the communication chamber 7 → the valve seat 8 and the second valve body 2
6 → Outflow passage 6 → Refrigerant passage 3 of flow regulating member 3
a in order and supplied to the evaporator.

(Effects of the First Embodiment) In the electromagnetic flow control valve 1 of the present embodiment, various flow regulating members 3 having different passage diameters can be selectively mounted on the outlet port 6a of the valve body 2. . Therefore, by attaching the flow rate adjusting member 3 having the optimal passage diameter to the air conditioning system having different evaporator sizes, each basic specification relating to the flow rate characteristics of the electromagnetic flow control valve 1 can be changed without changing It can correspond to the optimum refrigerant flow rate of the air conditioning system.

In particular, changing the basic specifications of the electromagnetic flow control valve 1, which is originally small in size, requires a very high machining accuracy and requires strict parts management, which results in significant cost reduction. As a result, the effect of adjusting the flow rate of the refrigerant corresponding to each air conditioning system only by attaching the flow rate adjusting member 3 as described above is extremely large. In addition, when the electromagnetic flow control valve 1 is used as a decompression unit of a refrigeration cycle, the flow rate adjusting member 3 is attached to the outlet side where the flow rate of the refrigerant is higher than the inlet side, so that compared to the case where it is attached to the inlet side, It is possible to obtain a larger flow rate adjusting effect.

(Second Embodiment) FIG. 6 shows an electromagnetic flow control valve 1
FIG. As shown in FIG. 6, the electromagnetic flow control valve 1 of the present embodiment includes a first actuator 29 that drives a first valve body 27 to open and close a first orifice 28 having a small inner diameter, By driving the valve body 30, the second
Actuator 32 for opening and closing the orifice 31
The flow control member 3 described in the first embodiment can be attached to the outflow passage downstream of the orifices 28, 31.

According to this configuration, by appropriately switching between the first actuator 29 and the second actuator 32, the flow rate can be adjusted in three stages according to the cooling load. That is, the second orifice 31 is closed,
By opening only the first orifice 28, the first refrigerant flow rate can flow. Next, by closing the first orifice 28 and opening only the second orifice 31, a second refrigerant flow rate larger than the first refrigerant flow rate can flow. Further, by opening both the first orifice 28 and the second orifice 31, a third refrigerant flow rate larger than the second refrigerant flow rate can flow (see FIG. 7).

Also, as in the first embodiment, the flow rate adjusting member 3 having the optimum passage diameter is selected and attached to an air conditioning system having different evaporator sizes, so that the flow rate of the electromagnetic type flow control valve 1 is increased. It is possible to cope with the optimum refrigerant flow rate of each air conditioning system without changing basic specifications relating to characteristics. Therefore, as shown in FIG. 7, in contrast to the flow rate characteristics (solid line) when the flow rate adjusting member 3 is not used, in the air conditioning systems A and B having a small evaporator size, the flow rate adjusting member 3 ( For example, by attaching passage diameters: φ0.8 and φ0.7)
The flow control range can be changed according to each air conditioning system.

[Brief description of the drawings]

FIG. 1 is a sectional view of an electromagnetic flow control valve (first embodiment).

FIG. 2 is a top view (a) and a cross-sectional view (b) of a first valve body.

FIG. 3 is a sectional view showing a state where a first passage is opened.

FIG. 4 is a sectional view showing a state where a first valve body is lifted.

FIG. 5 is a cross-sectional view showing a state where a first valve body and a second valve body are lifted.

FIG. 6 is a sectional view of an electromagnetic flow control valve (second embodiment).

FIG. 7 is a flow characteristic diagram of an electromagnetic flow control valve (second embodiment).

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Electromagnetic flow control valve 3 Flow rate adjusting member 3a Refrigerant passage 6 Outflow passage 25a First passage (first orifice) 26a Second passage (second orifice) 28 First orifice 31 Second orifice

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3H052 AA01 BA03 BA25 BA26 CA12 CD09 DA03 DA05 EA04 EA11 3H106 DA05 DA13 DA23 DB02 DB12 DB23 DB32 DC02 DC06 DC17 DD08 DD20 EE07 EE34 EE35 GB01 GB08 GB15 GC29 HH04 HH05 KK03 KK17 KK17 KK17

Claims (4)

[Claims] 1. An electromagnetic flow control valve which is provided upstream of an evaporator in a refrigerating cycle and has an orifice through which a refrigerant can pass, and which supplies a depressurized refrigerant through the orifice to the evaporator. An electromagnetic flow control valve, comprising: a flow control member attached to an outflow passage through which the depressurized refrigerant flows out through the orifice and having a refrigerant passage communicating with the outflow passage. 2. The method according to claim 1, wherein the orifice has at least a first orifice and a second orifice, and the flow rate of the refrigerant can be adjusted stepwise by opening the first orifice and the second orifice stepwise. The electromagnetic type flow control valve according to claim 1, wherein: 3. The orifice has at least a first orifice and a second orifice having different inner diameters, and selectively opens and closes the first and second orifices to step the refrigerant flow rate. 2. The electromagnetic flow control valve according to claim 1, wherein the valve is adjustable. 4. The flow rate adjusting member is fixed to the outflow passage by press fitting.
2. An electromagnetic flow control valve according to claim 1.