JP2002147896A - Motor flow control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor flow control valve which can control the flow rate surely even if the pressure increases by constituting throttle valve sections I and II comprising a valve seat and a valve element at the upper and lower sections of a tubular case such that the throttle valve sections are not opened due to increase of refrigerant pressure. SOLUTION: The motor flow control valve comprises an upper valve seat 32 and a lower valve seat 33 provided, respectively, at the upper end part and lower end part of a tubular case 31, and an upper valve element 35 and a lower valve element 36 provided, respectively, at the upper part and lower part of a tubular rotor 34 to touch the rotate or separate therefrom and to rotate integrally therewith. The upper valve element 35 and the upper valve seat 32 constitute a throttle valve section I9a, the lower valve element 36 and the lower valve seat 33 constitute a throttle valve section II9b and when the upstream side throttle valve section I9a is opened, flow control can be effected at the downstream side throttle valve section II9b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in an electric flow control valve for controlling the refrigerant flow rate of a heat pump type refrigeration cycle and controlling the capacity of the refrigeration cycle. The throttle valve does not open due to the increase in pressure, and reliable control can be performed even when the pressure increases, and the flow rate can be controlled until it is fully closed.
The present invention relates to a motor-operated flow control valve that consumes a small amount of power without changing the opening of the valve even when the power supply to the driving unit is stopped.

[0002]

2. Description of the Related Art Conventionally, various types of motorized flow control valves which are controlled by a microcomputer by combining a stepping motor and a valve integrated with a valve shaft have been devised. FIG.
Is a structure of a conventional control valve filed by the applicant of the present invention in Japanese Patent Application No. 11-184691, and the structure thereof will be described below. The conventional control valve includes a closed case 1 and a shaft 2
, A rotor 3, a valve seat 4, a compression coil spring 5, and a fixed coil 6.

The sealed case 1 is formed in an inverted bottomed cylindrical body having a lower opening, and a stopper 1b is provided on the upper inner surface of the sealed case 1 in a concave shape, and a bearing is provided at an upper central portion. A part 1a is provided.

[0004] The shaft 2 has an upper shaft 2a formed in an upper portion thereof, which is fitted into a bearing portion 1a of a case, a step 2b supporting a rotor 3 and a detent 2c for synchronizing rotation with a step 2b in an intermediate portion, and a lower portion formed in a lower portion. A valve body 2d for controlling the flow rate in contact with the valve seat 4 is formed.
A lower shaft 2e is formed on the lower surface of the. The shaft 2 is formed by resin molding. After the rotor is fitted to the shaft 2, the upper and lower ends of the shaft 2 are respectively connected to the bearing 1a of the case and the shaft hole 4a of the valve seat.
A compression coil spring 5 for pressing the rotor 3 and the valve body 2d downward is fitted into the upper shaft 2a of the shaft 2 and the valve port 4b in less than one rotation of the shaft 2. Can be controlled from the fully closed stage.

[0005] As described above, the rotor 3 is
The inner peripheral surface of the rotor 3 is provided with an internal detent 3a whose rotation is synchronized, and the upper outer peripheral edge of the rotor 3 is provided with a stopper of a closed case. An engagement piece 3b corresponding to 1b is provided.

The compression coil spring 5 is connected to the upper shaft 2 of the shaft 2.
a, and presses the shaft 2 downward through the rotor 3 so that the bottom surface of the valve body 2d is pressed against the valve seat 2 in a gas-tight manner.

A disc-shaped valve seat 4 is hermetically fixed to an opening at the lower end of the closed case 1. The valve seat 4 is provided with a shaft hole 4a at the center thereof.
The valve port 4b communicating with the first passage 4c and the second passage 4
A communication hole 4e communicating with d is provided.

As shown in FIG. 15, the shape of the valve body 2d is such that the valve opening 4e has a radius sufficient to cover the entire surface of the valve opening 4b.
Is formed to have a cam plate shape changed to a radius sufficient to open the cam plate.

The fixed coil 6 is fixed to the outer periphery of the closed case 1. The excitation of the fixed coil 6 causes the shaft to rotate with the rotation of the rotor,
The opening degree of the valve port 9 can be controlled with less than one rotation of the valve body 2d at the lower end.

Although not shown, the cross-sectional shape of the valve portion is formed in a spiral shape, and the flow rate characteristic of this electric control valve is changed by changing the cross-sectional shape of the valve portion as shown in FIG. The flow rate can be controlled when the rotation angle of the valve body 2d is in the range of 0 ° to about 270 °. That is, 1 of the valve
Since the opening of the valve port is controlled from the fully closed stage at less than the rotation, the opening of the valve port can be controlled from the fully closed stage.

FIG. 17 shows the structure of a conventional motor-operated flow control valve disclosed in Japanese Patent Application Laid-Open No. Hei 8-31822. The structure will be described below. The electric control valve shown in FIG. 17 includes a valve section V and a stepping motor section M.
It consists of. The valve portion V includes a valve body 11, a shaft portion 13, and a rotor 19 including a permanent magnet 21 and a spacer 22. The valve body 11 has a primary port 1
1a and a secondary port 11b are formed, and a fluid such as a refrigerant flows in or out of the primary port 11a and the secondary port 11b.
Further, the valve body 11 also has a function of guiding the shaft portion 13,
A guide portion 11g for the shaft portion 13 is provided in the vertical direction.

A valve portion 13a is formed at the lower end of the shaft portion 13. The cross-sectional shape of the valve portion 13a is constant in the axial direction. Further, a space above the primary port 11a of the valve main body 11 and in which the valve portion 13a of the shaft portion 13 is housed constitutes a valve chamber 20, and a lower portion of the valve chamber 20 communicates with the primary port 11a. The chamber 20 and the secondary port 11b communicate with each other via the valve port 11c.

The shaft portion 13 and the rotor 19 are integrated to form a rotor portion 30, and the integrated rotor portion 30 is mounted on the upper end surface 11 d of the valve body 11. Here, 11 is a permanent magnet, and 12 is a spacer.

A step 11e is formed at the center of the outer periphery of the valve body 11, and a lower lid 15 is fixed on the step 11e by brazing. Further, the closed case 16 of the stepping motor section M is fixed on the lower lid 15. A stator 18 having a built-in coil 17 is provided on the outer periphery of the case 16.
Is provided, and a rotor portion 30 in which the shaft portion 13 and the rotor 19 are integrated is rotatably provided on the valve body 11 in the case 16. In addition, a step 22 a is formed below the rotor 19, and the step 22 a functions as a stopper integrated with the rotor 19. On the other hand, lower lid 1
5 is provided with a projection 15a.
It functions as a stopper on the main body side provided integrally with 5.

In the above configuration, when the coil 17 of the stator 18 is energized, the permanent magnet 21 rotates and the permanent magnet 2
The shaft 13 also rotates in accordance with the rotation of the shaft 1. When the shaft portion 13 rotates, the angle of the valve portion 13a with respect to the valve port portion 1c changes according to the rotation angle of the shaft portion 13, and the valve port portion 1c and
The gap formed between the valve port portion 1c and the opposing peripheral surface of the valve portion 3a is changed by the rotation of the rotor 19 according to the cross-sectional shape of the valve portion 13a perpendicular to the axis of the shaft portion 13. Therefore, the flow rate of a fluid such as a refrigerant can be controlled.

[0016]

However, in the former control valve shown in FIG. 14, the valve body is pressed against the valve seat by a compression coil spring, so that the valve body and the valve seat are brought into close contact with each other, and a throttle valve mechanism is provided. Depending on the difference in the flow direction of the refrigerant due to the switching between cooling and heating in the heat pump refrigeration cycle, when the pressure of the refrigerant becomes high, the valve body separates from the valve seat due to insufficient urging force of the compression coil spring. There is a problem that the valve opens in contact. Also, in order to control the valve stably without opening even under high pressure conditions, the urging force of the compression coil spring must be sufficiently large, which is the friction when the valve element slides in rotation. In order to rotate and slide against a large frictional force, the fixed coil and the rotor must be increased in size, increasing the cost, requiring a large electric input, and contravening energy saving. Was.

In the latter type of electric control valve shown in FIG. 17, a method for controlling the flow rate is such that a gap formed between a valve port portion and a peripheral surface of the opposed valve portion is perpendicular to an axis of the valve portion. Since the valve opening is controlled by a complicated cross-sectional shape, the valve port cannot be fully closed, and as shown in FIG. 18, the minimum flow rate does not become zero and a considerable amount of refrigerant always flows. That is, in order to fully close the valve port and the valve portion, it is necessary to closely contact the axis and the direction perpendicular to the axis.
Due to the surface, it is very difficult to make close contact with the structure. This causes a problem in the multi air conditioner that the refrigerant flows to the stop unit and the refrigerant noise or the refrigerant is insufficient. Further, a room air conditioner requires a very small flow rate during dehumidification, but if it is too large, there is a problem that optimal dehumidification cannot be performed.

In addition, the flow direction of the fluid flows perpendicular to the axis of the valve portion, and the fluid flows along the gap, whereby a force for rotating the shaft portion is generated by the fluid and the magnetic force of the permanent magnet causes Since only the holding torque causes the shaft to rotate, it was necessary to always energize the coil after stopping at the optimum position during control so that the rotor would not rotate. At that time, there was also a problem that an electric input was required, which was against energy saving.

[0019]

SUMMARY OF THE INVENTION The present invention is directed to an upstream throttle valve portion and a downstream throttle valve portion capable of obtaining different flow characteristics comprising a valve seat and a valve body, respectively, at an upper portion and a lower portion of a cylindrical case. An upper valve body and a lower valve body that can rotate integrally with the rotor within a predetermined range are provided at the upper and lower parts of the rotor, and the one valve body is a refrigerant valve. When the pressure comes into contact with the valve seat of the throttle valve portion, the throttle valve portion on the upstream side of the refrigerant is fully opened regardless of the position of the drive means by providing the other valve body so as to be separated from the valve seat downstream. Only the throttle valve portion functions as a throttle valve, and the two throttle valve mechanisms are automatically used depending on the flow direction of the refrigerant. In any case, the throttle valve portion on the downstream side is increased by the increase in the refrigerant pressure. It does not open and the pressure rises It is an object to provide an electric flow control valve can be reliably controlled.

In other words, the electric flow control valve according to the first aspect of the present invention rotates integrally with the rotor 34 by the fixed coil 38 disposed on the outer periphery of the non-magnetic cylindrical case 31 and the rotor 34 disposed inside. The upper valve body 35 and the lower valve body 36 are reversibly operated by a driving means such as a stepping motor, and the opening degree of one of the two throttle valve portions is controlled by the rotation of the valve body. An electric flow control valve for adjusting the refrigerant flow rate of the refrigeration cycle and controlling the capacity of the refrigeration cycle, comprising an upper valve seat 32 and a lower valve seat 33 at an upper end and a lower end of the cylindrical case 31, respectively. And an upper valve body 35 and a lower valve body 36 which are rotatable integrally with the end of the rotor at the upper and lower portions of the cylindrical rotor 34 so as to be integrally rotatable. With the seat 32 A downstream throttle valve portion 41 is formed, and a downstream throttle valve portion 42 is formed by the lower valve body 36 and the lower valve seat 33. The difference in the flow direction of the refrigerant due to switching between cooling and heating of the heat pump refrigeration cycle. When the upper valve body 35 of the upstream throttle valve portion 41 is separated from the upper valve seat 32 and the lower valve body 36 of the downstream throttle valve portion 42 contacts the lower valve seat 33, the upstream throttle valve is closed. The part is fully opened irrespective of the position of the driving means, only the downstream throttle valve part functions as a throttle valve, and two throttle valve mechanisms are automatically used depending on the flow direction of the refrigerant. Also in this case, the throttle valve portion does not open due to an increase in the refrigerant pressure, and reliable control can be performed even when the pressure increases.

The motor-operated flow control valve according to claim 2 is
The throttle control grooves 35d and 36d formed on the upper valve body 35 and the lower valve body 36 have different shapes of the grooves, respectively, and have different flow characteristics depending on the flow direction of the refrigerant. Claim 1.

The electric flow control valve according to claim 3 is
A piston ring 44 is provided on the outer peripheral surface of the upper valve body 35 and the lower valve body 36, and a gap is formed between the inner peripheral surface of the cylindrical case 31 and the outer peripheral surfaces of the upper valve body 35, the lower valve body 36, and the rotor 34. The refrigerant is prevented from flowing through the first and second embodiments.

Further, the electric flow control valve according to claim 4 is
The upper valve body 35 and the lower valve body 36 are connected to the upper valve seat 32.
And the lower valve seat 33 is loosely fitted to the shaft 37 supported by the shaft holes 32a, 33a of the lower valve seat 33.

Further, the electric flow control valve according to claim 5 is
A plurality of valve seats including the periphery of the valve ports 32b and 33b are provided at sliding positions on the sliding surfaces of the upper valve seat 32 and the lower valve seat 33 and opposite to the valve ports 32b and 33b around the shaft 37. Disc-shaped contact surface 32 projected from the surface
c is provided integrally with each of the valve seats, and communication holes 3 are formed in the wall surfaces of the upper valve body 35 and the lower valve body 36, respectively.
Claims 1, 2, 3, and 4 are provided with 5 g and 36 g.

The electric flow control valve according to claim 6 is
A valve cap 43 made of a highly slippery resin such as a fluororesin material is provided around the valve ports 32b and 33b provided in the upper valve seat 32 and the lower valve seat 33. Claim 1, Claim 2, Claim 3, Claim 4 and Claim 5.

Further, in the electric flow control valve according to claim 7, a compression coil spring 45 is disposed between the upper valve body 35 and the lower valve body 36. , Claim 3, claim 4, and claim 4, claim 5, and claim 6.

[0027]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to the drawings. 1 is a longitudinal sectional view of the electric expansion valve of the present invention, FIG. 2 is a sectional view taken along line AA of FIG. 1, and FIG.
BB sectional view, FIG. 4 is a CC sectional view of FIG. 1, FIG. 5 is a fully opened state of the DD sectional view of FIG. 1, FIG. 6 is an intermediate state of the DD sectional view of FIG. 7 shows a fully closed state of the DD sectional view of FIG. 1, and FIG. 8 shows a longitudinal sectional view when the flow direction of the electric expansion valve of the present invention is reversed.

The electric flow control valve according to the present invention has a cylindrical case 31.
The upper valve seat 32 and the lower valve seat 33 airtightly fixed to both ends of the cylindrical case 31 and the cylindrical rotor 3
4 and an upper valve body 35 and a lower valve body 36 which rotate by engaging with the rotor, a shaft 37 and a fixed coil 38.

The cylindrical case 31 has a cylindrical shape with both ends made of non-magnetic metal.

The upper valve seat 32 and the lower valve seat 33 are disk-shaped, and have shaft holes 32a, 3
3a is provided, and valve ports 32b and 33b are respectively provided at positions slightly away from the center. Also,
In order to stabilize the rotation of the valve element, as shown in FIG.
0, the upper valve seat 32 and the lower valve seat 33
And the valve port 32b around the shaft 37.
At a position opposite to 33b, a disc-shaped contact surface 32c protruding from the valve seat surface at a plurality of positions including around the valve ports 32b and 33b may be provided integrally with each valve seat. The inflow / outflow pipes 39a and 39b are hermetically fixed to the valve ports 32b and 33b of the valve seat.

The upper valve seat 32 and the lower valve seat 33 are air-tightly fixed to both ends of the cylindrical case 31, and stoppers 40 are fixed to the lower valve seat 33. However, it goes without saying that the stopper 40 may be provided on the upper valve seat 32 instead of the lower valve seat 33.

A piston ring 44 is provided on the outer peripheral surface of the upper valve body 35 and the lower valve body 36. The piston ring 44 allows the inner peripheral surface of the cylindrical case 31 to be in contact with the upper valve body 35. The refrigerant can be prevented from flowing into the gap between the lower valve body 36 and the outer peripheral surface of the rotor 34. That is, as shown in FIG.
a → the valve port 32b of the upper valve seat 32 → the communication hole 35b of the upper valve body 35 → the interior of the rotor 34 → the communication hole 36 of the lower valve body 36
b → When flowing from the valve port 33b of the lower valve seat 33 to the inflow / outflow pipe 39b, the refrigerant can be prevented from flowing outside the rotor 34, and the refrigerant contains magnetic foreign matter or the like. In addition, a highly reliable electric flow control valve can be provided without foreign matter accumulating on the outer peripheral portion of the rotor and hindering rotation.

Further, in the case where the sliding surfaces of the upper valve seat 32 and the lower valve seat 33 described above are provided with disc-shaped contact surfaces 32c at a plurality of positions including the vicinity of the valve ports 32b and 33b. On the wall surfaces of the upper valve body 35 and the lower valve body 36, communication holes 35g and 36g are provided, respectively. The meaning of providing the communication holes 35g and 36g is as follows.
For example, in the case of the flow of the refrigerant shown in FIG. 1, when the communication hole 36b of the lower valve body 36 is in contact with the contact surface 32c, the flow of the refrigerant is restricted at the contact portion, and the lower valve body 36 A pressure difference is generated between the upper portion and the lower portion of the valve body 36, and the pressure difference is applied to the entire size of the lower valve body 36, so that the force pressing the valve body becomes large, and the valve body does not rotate smoothly. However, if there are the communication holes 35g and 36g, the pressure difference between the upper part and the lower part of the lower valve body 36 is balanced, the force for pressing the valve body becomes small, and the valve body can rotate smoothly.

The cylindrical rotor 34 is provided with notches 34a, 34b (see FIGS. 2 and 3) at its upper end and lower end, and the notches 34a, 34b are provided.
Is a protrusion 35 of an upper valve body 35 and a lower valve body 36, which will be described later.
c, 36c.

The upper valve body 35 and the lower valve body 36 have a cylindrical shape, and are provided with shaft holes 35a and 36a at the center thereof. 2 and 3, there are provided protrusions 35c, 36c corresponding to the notches 34a, 34b of the rotor, as shown in FIGS.

The upper valve body 35 and the lower valve body 36 are located at positions corresponding to the valve openings 32b and 33b of the upper and lower valve seats.
As shown in FIGS. 4, 5 and 11, grooves 35 d and 36 d whose cross-sectional areas gradually change with the rotation direction are provided, and communication holes 35 b are provided at positions 35 e and 36 e where the cross-sectional areas of the grooves become maximum. , 36b, as shown in FIG. 1, the refrigerant flows into and out of the pipe 39b → the valve port 33b of the lower valve seat 33 → the communication hole 36b of the lower valve body 36 → the inside of the rotor 34 → the upper valve body 35.
Of the upper valve seat 32 → the inflow / outflow pipe 39a.

As shown in FIG. 5, the lower valve body 36 is provided with a locking piece 36f corresponding to the stopper 40 of the lower valve seat described above. , The rotor 34, the upper valve body and the lower valve body regulate the rotation end position when they rotate.

In the present invention, the throttle valve portion 41 on the upstream side is constituted by the upper valve body 35 and the upper valve seat 32, and the lower valve body 36 and the lower valve seat are provided. The seat 33 constitutes a downstream throttle valve portion 42. In the throttle control unit, the upper valve body 35
And throttle control grooves 35d and 36 formed in the lower valve body 36
By making the shape of d different, the flow characteristics can be made different depending on the flow direction of the refrigerant.

The shaft 37 is connected to the rotor 34 and the upper valve body 35
And both ends of the shaft 37 are axially supported by the shaft holes 32a, 33a of the upper valve seat 32 and the lower valve seat 33, respectively. It penetrates the shaft holes 35a and 36a. The shaft 37 is not always necessary, and may be appropriately selected as needed.

FIG. 8 shows the motorized flow control valve of FIG.
It is a diagram showing a state when the flow direction of the refrigerant is reversed by switching the cooling and heating of the heat pump refrigeration cycle,
In this state, the rotor 34 and the upper valve body 35 are pressed against the upper valve seat 32 above, but it goes without saying that the same operation and effect as in the state of FIG.

In the above embodiment, the upper valve body 35
The lower valve body 36 is formed as a separate component from the rotor 34, but it is needless to say that the same operation and effect can be obtained by integrally forming them.

[0042]

FIG. 12 shows another embodiment of the electric flow control valve according to the present invention.
FIG. 5 is a partial vertical cross-sectional view showing a state where No. 5 is attached. In this embodiment, only differences from the embodiment shown in FIG. 1 will be described below.

The valve seat cap 43 is formed of a highly slippery resin such as a fluorine resin material. As shown in FIG. 13, the valve seat cap 43 is provided on the upper valve seat 32. Around the valve port 32b and the valve port 33b provided in the lower valve seat 33, the upper valve seat 32 and the lower valve seat 33 are fixed to the upper valve seat 32 and the lower valve seat 33 by spot welding or the like via a valve cap cap 46. This valve seat cap 43
Thus, the upper and lower valve bodies 35 and 36 can be rotated with a small torque.

A stopper 40 is provided on the valve seat cap retainer 46.

The compression coil spring 45 is connected to the upper valve body 35.
And the lower valve element 36, and the compression coil spring 45 is disposed between the upper valve element 35 and the lower valve element 36, so that the upper valve element 35 and the lower valve element 36 respectively Provided is an easy-to-operate electric flow control valve that is urged to press against the upper valve seat 32 and the lower valve seat 33 so that the valve body does not rotate even when the refrigerant is not flowing. can do.

Next, the operation of the electric flow control valve of the present invention shown in FIGS. 1 and 12 will be described. FIGS. 5 to 7 correspond to the cross section taken along line D-D in FIG. 1 and show how the electric flow control valve is fully opened (FIG. 5), intermediate (FIG. 6), fully closed (FIG. 7), and how the valve opening changes. Show. Each figure shows a positional relationship between the lower valve body 35 and the valve port 33b of the lower valve seat 33. The refrigerant flowing from the communication port 36b of the lower valve body 36 flows into the valve port 33b of the lower valve seat 33 through a groove 36d whose sectional area gradually changes with the rotation of the valve body. The flow rate is reduced by the size of the cross-sectional area of the groove 36d at a position where the flow rate is in contact with the valve port 33b of the lower valve seat 33. In other words, the refrigerant passage amount can be adjusted by the rotation position of the lower valve body 36 that rotates by the rotation of the rotor 34, and the capacity control of the refrigeration cycle can be performed.

In the electric flow control valve of the present invention constructed as described above, the upper valve body 35 of the upstream throttle valve portion 41 is moved upward by the difference in the flow direction of the refrigerant due to the switching of the cooling and heating of the heat pump refrigeration cycle. By separating from the surface of the seat 32, the upstream throttle valve portion 41 is fully opened irrespective of the position of the drive means, and only the downstream throttle valve portion 42 functions as a throttle valve. Two throttle valve mechanisms are selectively used, and in any flow direction, the throttle valve section does not open due to an increase in refrigerant pressure, and reliable control can be performed even when the pressure increases.

The lower valve element 36 on the downstream side of the throttle valve section 42 rotates while engaging with the rotor 34 and is pressed against a valve seat provided on a plane perpendicular to the rotation axis by the flow of refrigerant. Since the opening degree of the valve port can be controlled from the fully closed stage with less than one rotation of the lower valve body 36, as shown in the flow characteristic diagram of FIG.
The minimum flow can be zero.

Further, the lower valve body 36 on the downstream side is pressed against the lower valve seat 33 by the pressure difference due to the flow of the refrigerant, and a frictional force for holding the lower valve body 36 at that position acts. The force that does not rotate the rotor 34
The holding torque due to the magnetic force is integrated, and the valve body is prevented from rotating even if the energization to the coil is stopped after controlling the rotation position of the valve body and stopping it at the optimum position.

[0050]

As described above, according to the first aspect of the present invention, two throttle valve mechanisms are automatically used depending on the flow direction of the refrigerant, and the refrigerant pressure rises in any of the flow directions. Thus, the throttle valve does not open, and reliable control can be performed even when the pressure increases.

Of the valve elements provided at two locations, the valve element located on the downstream side is pressed against the valve seat surface provided at a plane perpendicular to the rotation axis by the flow of the refrigerant, and slides and rotates. By controlling the flow rate by adjusting the opening degree of the valve, the opening degree of the valve port can be controlled from the fully closed stage in less than one rotation of the valve body, and the minimum flow rate can be reduced to zero. And optimal control for room air conditioners.

Further, the downstream valve body is pressed against the valve seat surface by the pressure difference caused by the flow of the refrigerant, so that the rotation of the valve body is controlled and stopped at an optimum position, and then the energization to the coil is stopped. Even when the valve body does not rotate, the power consumption can be reduced.

According to the second aspect of the present invention,
Groove 3 for throttle control formed in upper valve body 35 and lower valve body 36
By making the shapes of 5d and 36d different,
For example, the flow characteristic can be made different between the heating operation and the cooling operation, and fine-grained air conditioning control can be performed.

According to the third aspect of the present invention, since the piston rings 44 are disposed on the outer peripheral portions of the upper valve body 35 and the lower valve body 36, respectively, the refrigerant flows as shown in FIG. Inlet / outlet pipe 39a → valve port 32b of upper valve seat 32
→ Communication hole 35b of upper valve body 35 → Inside rotor 34 → Communication hole 36b of lower valve body 36 → Valve port 33b of lower valve seat 33
→ When flowing to the inflow / outflow pipe 39b, the refrigerant can be prevented from flowing outside the rotor 34, and even if the refrigerant contains a magnetic foreign substance or the like, the foreign substance accumulates on the outer periphery of the rotor. A highly reliable electric flow control valve can be provided without hindering rotation.

According to the fourth aspect of the present invention, since the upper valve body 35 and the lower valve body 36 are supported by the shaft 37, the rotation operation is stable and the electric flow control valve with high reliability is provided. can do.

According to the fifth aspect of the present invention, disc-shaped contact surfaces 32c are provided at a plurality of positions opposite to the valve ports 32b and 33b, and the upper valve body 35 and the lower valve body 36 Since the communication holes 35g and 36g are provided on the wall surface, the communication holes 36b of the lower valve body 36
The valve body can be smoothly rotated even in a state where the valve body is in contact with 2c.

According to the sixth aspect of the present invention, the valve seat cap 43 made of a highly lubricating resin such as a fluororesin material is fixed around the valve ports 32b and 33b.
The valve element can be rotated with a small torque, so that the driving means can be downsized and an inexpensive electric flow control valve can be provided.

Further, according to the invention described in claim 7,
By disposing the compression coil spring 45 between the upper valve body 35 and the lower valve body 36, the upper valve body 35 and the lower valve body 36 are pressed against the upper valve seat 32 and the lower valve seat 33, respectively. Therefore, it is possible to provide an easy-to-operate electric flow control valve in which the valve body does not rotate even when the refrigerant is not flowing.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG. 1;

FIG. 4 is a sectional view taken along line CC of FIG. 1;

FIG. 5 is a sectional view taken along the line DD of FIG. 1 (in a fully opened state).

FIG. 6 is a sectional view taken along line DD in FIG. 1 (an intermediate state).

FIG. 7 is a sectional view taken along the line DD in FIG. 1 (fully closed state).

FIG. 8 is a diagram when the flow direction of the refrigerant is reversed with respect to FIG.

FIG. 9 is a flow characteristic diagram of the electric flow control valve according to the present invention.

FIG. 10 is a perspective view of a lower valve seat according to the present invention.

FIG. 11 is a perspective view of a lower valve body of the present invention.

FIG. 12 is a longitudinal sectional view showing another embodiment of the present invention.

FIG. 13 is an exploded perspective view showing a state in which a valve seat cap 43 is attached to a valve opening.

FIG. 14 is a longitudinal sectional view of a conventional electric flow control valve.

FIG. 15 is a sectional view taken along line BB of FIG. 14;

FIG. 16 is a flow characteristic diagram of the electric flow control valve shown in FIG.

FIG. 17 is a longitudinal sectional view of another conventional electric flow control valve.

18 is a flow characteristic diagram of the electric flow control valve shown in FIG.

[Explanation of symbols] [Explanation of symbols]

31 cylindrical case, 32 upper valve seat, 33 lower valve seat, 32a, 33
a Shaft bore, 32b, 33b Valve port, 32
c, 33c contact surface, 34 rotor,
34a, 34b notch, 35 upper valve body,
36 Lower valve body, 35a, 36a Shaft hole, 35b, 36b Communication hole, 35c, 3
6c protrusion, 35d, 36d groove, 35
e, 36e Position where the cross-sectional area of the groove is maximum, 36f locking piece, 37 shaft, 38 fixed coil, 39a, 39b inflow / outflow pipe,
40 stopper, 41 upstream throttle valve part, 42 downstream throttle valve part. 43 Valve cap 44 Piston ring 45 Compression coil spring 46 Valve cap retainer

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (reference) // F25B 13/00 371 F25B 13/00 371 F term (reference) 3H053 AA02 AA03 BA04 CA02 DA01 3H057 AA13 BB06 BB09 CC01 DD22 FA03 FA04 FD13 HH07 HH18 3H062 AA07 AA13 AA15 BB26 BB28 BB30 CC02 DD03 EE07 FF39 HH04 HH09 3L092 AA02 AA11 BA23

Claims (7)

[Claims] A fixed coil (38) arranged on the outer periphery of a non-magnetic cylindrical case (31) and a rotor (3) arranged inside the fixed coil (38).
4), the upper valve body (35) and the lower valve body (36), which rotate integrally with the rotor (34), are reversibly operated by driving means such as a stepping motor. An electric flow control valve that controls the opening degree of one of the two throttle valve portions to adjust the amount of refrigerant passing through the heat pump type refrigeration cycle and control the capacity of the refrigeration cycle. An upper valve seat (32) and a lower valve seat (33) are respectively provided at the upper end and the lower end of 31), and the upper and lower parts of the cylindrical rotor (3) are separated from and integral with the end of the rotor. An upper valve body 35 and a lower valve body (36), which are rotatably movable, and the upper valve body 35 and the upper valve seat (32) constitute an upstream throttle valve portion (41);
The downstream throttle valve (42) is constituted by the lower valve body (36) and the lower valve seat (33). Part (41)
The upper valve body (35) separates from the upper valve seat (32) and the lower valve body (36) of the throttle valve portion (42) on the downstream side abuts on the lower valve seat (33), thereby increasing the upstream side. The throttle valve part is fully opened regardless of the position of the driving means, and only the downstream throttle valve part functions as a throttle valve. Also in the case of the direction, the throttle valve portion on the downstream side does not open due to the increase in the refrigerant pressure, and reliable control can be performed even when the pressure increases. 2. An upper valve body (35) and a lower valve body (3).
6) Aperture control grooves (35d) and (36d) to be formed
The electric flow control valve according to claim 1, wherein the shape of each groove is different, and the flow characteristics are different depending on the flow direction of the refrigerant. 3. The upper valve body (35) and the lower valve body (36).
A piston ring (44) is provided on the outer peripheral surface of the cylindrical case (31), the inner peripheral surface of the cylindrical case (31), the upper valve body (35), and the lower valve body (3).
The electric flow control valve according to claim 1 or 2, wherein a refrigerant is prevented from flowing into a gap between the outer peripheral surface of the rotor (6) and the outer peripheral surface of the rotor (34). 4. The upper valve body (35) and the lower valve body (36).
Are supported by shaft holes (32a) and (33a) of the upper valve seat (32) and the lower valve seat (33).
7. The method according to claim 1, wherein the second connector is loosely fitted to the first connector.
The electric flow control valve according to claim 2 or 3. 5. A valve port on a sliding surface of the upper valve seat (32) and the lower valve seat (33) and around the shaft 37.
The valve port (32b) is located at a position opposite to (32b) and (33b).
A disk-shaped contact surface (32c) protruding from the valve seat surface at a plurality of locations including the periphery of (33b) and provided integrally with each valve seat, and the upper valve body (35); And a communication hole (35 g) in the wall surface of the lower valve body (36), respectively.
The motorized flow control valve according to any one of claims 1, 2, 3, and 4, wherein (36g) is provided. 6. The valve ports (32b) and (33b) provided on the upper valve seat (32) and the lower valve seat (33).
A valve seat cap (43) made of a highly lubricating resin such as a fluororesin material is disposed around the periphery of the valve seat (1), (2), (3), (4) and (5). 3. The electric flow control valve according to claim 1. 7. The upper valve body (35) and the lower valve body (36).
An electric motor according to claim 1, wherein a compression coil spring (45) is disposed between the first and second motors (1), (2), (3), (4), (4), (5) and (6). Flow control valve.