JP2003065634A - Expansion valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a vibratory foreign sound of a valve element without additionally providing parts anew. SOLUTION: First and second hole sections 40a, 40b are formed such that the direction A of a central line of the second hole section 40a is inclined with respect to the direction B of a central axis of the first hole section 40b. Hereby, the direction of the sliding of a second valve rod 46 is not parallel to that of the first valve rod 49 but intersects the same, so that when the second valve rod 46 slides following the sliding of the first valve rod 49, the second valve rod 46 is pushed against a part of a body case 40 forming the second hole section 40a. Hereby, friction between the second valve rod 46 and the body case 40 is increased without increasing the number of part items of the expansion valve, whereby slide resistance of the second valve rod 46 is increased to reduce a vibratory foreign sound of the valve body 43.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an expansion valve for decompressing a high-pressure side liquid refrigerant into a low-temperature low-pressure gas-liquid two-phase refrigerant in a refrigerating cycle in an automobile air conditioner or the like, and particularly to a vibration abnormal noise of a valve body Improvement for reducing

[0002]

2. Description of the Related Art This type of expansion valve changes the valve opening to maintain the superheat degree of the refrigerant at the evaporator outlet at a predetermined value in response to fluctuations in the heat load of the evaporator, and the cycle refrigerant flow rate is changed. Is being adjusted. The displacement of the diaphragm due to the degree of heating of the refrigerant at the outlet of the evaporator is transmitted to the valve body by the valve rod that slides while being guided by the case body of the expansion valve.

In the above expansion valve, when the sliding resistance of the valve rod is small, the valve element and the valve rod follow a momentary pressure fluctuation caused by a change in the valve opening degree, and slightly vibrate, resulting in an abnormal noise. It is known to occur.

Therefore, in the expansion valve disclosed in Japanese Patent Laid-Open No. 8-145505, a spring means such as a coil spring is newly added and arranged around the valve rod, and this spring means causes the diameter of the valve rod relative to the valve rod. I try to apply force from the direction. This increases the sliding resistance of the valve rod and prevents abnormal noise due to slight vibration of the valve body.

[0005]

However, according to the noise prevention structure of the above publication, spring means must be newly added and arranged around the valve rod, which results in an increase in cost due to an increase in the number of parts. Was becoming.

In view of the above points, it is an object of the present invention to reduce vibration noise of a valve body without adding new parts.

[0007]

In order to achieve the above object, the present invention provides, in the invention as set forth in claim 1, a thermal reaction which is displaced in accordance with the heating degree of the gas refrigerant on the outlet side of the evaporator (5). The means (52), the first valve rod (49) that slides with the displacement of the heat responsive means (52), and the second valve rod (that slides with the sliding of the first valve rod (49) ( 46) and the second valve stem (46) are displaced along with the sliding movement of the second valve rod (46) to reduce the pressure of the liquid refrigerant on the high pressure side of the cycle.
5) the valve body (43) for adjusting the opening of the first valve rod (4)
9) a first hole portion (40b) for slidably guiding, and a second hole portion (40b)
Second hole (40a) for slidably guiding the valve rod (46)
In the expansion valve including the case member (40) having the first hole (4), the central axis (A) of the second hole (40a) is the first hole (4).
It is characterized in that the first and second hole portions (40a, 40b) are formed so as to be inclined with respect to the central axis (B) of 0b).

As a result, the sliding direction of the second valve rod (46) does not become parallel to the sliding direction of the first valve rod (49) but intersects with it, so that the first valve rod ( When the second valve rod (46) slides with the sliding of the valve member (49), the second valve rod (46) causes the second hole (40) of the case member (40) to move.
It will be pressed against the part forming a). Therefore, the frictional force between the second valve rod (46) and the case member (40) is increased without increasing the number of components of the expansion valve,
It is possible to increase the sliding resistance of the second valve rod (46),
It is possible to reduce vibration abnormal noise of the valve body (43).

According to the second aspect of the present invention, the end face (4) of the first valve rod (49) which comes into contact with the second valve rod (46).
9d) is formed substantially perpendicular to the central axis (B) of the first valve rod (49) and is in contact with the end face (49d) of the first valve rod (49). It is characterized in that (46d) is formed substantially perpendicular to the central axis (A) of the second valve rod (46).

As a result, the portion of the second valve rod end surface (46d) that contacts the first valve rod end surface (49d) is a portion off the central axis of the second valve rod (46). When the valve rod (46) slides, a rotation moment is always generated in the second valve rod (46), and the second valve rod (46) is fixed to the case member (4).
0). Therefore, the frictional force between the second valve rod (46) and the case member (40) can be further increased.

By the way, in the conventional expansion valve in which the sliding direction of the second valve rod (46) is parallel to the sliding direction of the first valve rod (49), the second valve rod end surface (46d) is When the contact portion is to be a portion deviated from the central axis of the second valve rod (46), the first valve rod end surface (49d) is tapered with respect to the central axis (B) of the first valve rod (49). The second valve rod end surface (46d) must be machined or tapered to the central axis (A) of the second valve rod (46), and both end surfaces (46d, 49d) must be machined. Is a hassle.

On the other hand, in the present invention, the second valve rod (46)
Since the sliding direction of the first valve rod (49) intersects the sliding direction of the first valve rod (49),
9) is formed substantially perpendicular to the central axis (B), and the second valve rod end surface (46d) is formed substantially perpendicular to the central axis (A) of the second valve rod (46), and then the second The contact portion of the valve rod end surface (46d) with the first valve rod end surface (49d) is connected to the second valve rod (46).
It is possible to form a portion off the central axis of the above, and therefore the above-mentioned tapered processing can be eliminated.

Further, in the third aspect of the invention, the thermal response means (52) is displaced according to the heating degree of the gas refrigerant on the outlet side of the evaporator (5) and the displacement of the thermal response means (52). The sliding member (49b) that has a function of limiting the sliding range, a valve rod (46) that slides with the sliding of the sliding member (49b), and a valve rod ( Four
The sliding member (49b) and the valve body (43) for adjusting the opening degree of the throttle passage hole (45) for decompressing and expanding the liquid refrigerant on the cycle high pressure side by sliding along with the sliding of (6) slide. Expansion valve provided with a case member (40, 54) having a third hole (40c) movably guiding and a second hole (40a) slidably guiding the second valve rod (46) In, the second and third hole portions (40a, 40c) are arranged so that the central axis (A) of the second hole portion (40a) is inclined with respect to the central axis (B) of the third hole portion (40c). It is characterized by being formed.

As a result, the sliding direction of the valve rod (46) is
Not parallel to the sliding direction of the sliding member (49b),
Since they are in the intersecting direction, when the valve rod (46) slides as the sliding member (49b) slides, the valve rod (46)
Will be pressed against the portion of the case member (40) forming the second hole (40a). Therefore, the frictional force between the valve stem (46) and the case member (40) is increased without increasing the number of parts of the expansion valve, and the valve stem (46) is increased.
It is possible to increase the sliding resistance of the valve body (43) and reduce the abnormal vibration noise of the valve body (43).

In the invention according to claim 4, the end surface (49) of the sliding member (49b) which comes into contact with the valve rod (46).
g) is formed substantially perpendicular to the central axis (B) of the sliding member (49b), and the end surface (46d) of the valve rod (46) that contacts the end surface (49g) of the sliding member (49b) is , Valve stem (4
It is characterized in that it is formed substantially perpendicular to the central axis (A) of 6).

As a result, the portion of the valve rod end face (46d) that contacts the sliding member end face (49g) is the valve rod (46).
Since it is a portion deviated from the central axis of the valve rod (46), a rotational moment is always generated in the valve rod (46) when the valve rod (46) slides, and the valve rod (46) is pressed against the case member (40). Therefore, the frictional force between the valve rod (46) and the case member (40) can be further increased.

Further, in the present invention, since the sliding direction of the valve rod (46) intersects the sliding direction of the sliding member (49b), the sliding member end face (49g) is connected to the sliding member (49b). ) Is formed substantially perpendicular to the central axis (B) of
d) is formed substantially perpendicular to the central axis (A) of the valve rod (46), and the sliding member end surface (49) of the valve rod end surface (46d) is formed.
g) The contact portion with the valve stem (46) can be off the central axis of the valve stem (46), and thus both end faces (46d, 49g)
It is possible to eliminate the need for taper processing.

Incidentally, the reference numerals in parentheses of the above-mentioned respective means are examples showing the correspondence with the concrete means described in the embodiments described later.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION (First Embodiment) An embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 shows an embodiment in which the expansion valve of the present invention is applied to a refrigeration cycle of an automobile air conditioner.
Is a compressor arranged in an engine room of an automobile, and the compressor 1 is driven by an automobile engine (not shown) to compress and discharge a refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is cooled and condensed in the condenser 2 in the engine room. The condensed high-pressure gas-liquid two-phase refrigerant is separated into gas and liquid in the liquid receiver 3, and the liquid refrigerant accumulates in the liquid receiver 3.

Reference numeral 4 denotes a temperature type expansion valve which constitutes a decompression means of the refrigeration cycle, and is a superheat degree of the refrigerant at the outlet of the evaporator 5 (refrigerant temperature at the outlet of the evaporator 5) provided in the cooling unit of the automobile air conditioner. ) Is adjusted so that the valve opening degree is adjusted to a predetermined value set in advance to adjust the refrigerant flow rate. The expansion valve 4 and the evaporator 5 are usually installed in the passenger compartment of an automobile.

Next, the specific structure of the expansion valve 4 will be described in detail. Reference numeral 40 denotes a main body case (case member) of the expansion valve 4, which is made of metal such as aluminum and is formed into a substantially rectangular parallelepiped shape extending in the vertical direction of FIG. ing. A refrigerant inlet 41 into which the liquid refrigerant from the liquid receiver 3 of the refrigeration cycle flows is opened on the lower right side of the main body case 40.

The refrigerant inlet 41 communicates with a valve body accommodating chamber 42 formed in the lower central portion of the main body case 40. Inside the chamber 42, a spherical valve body 43 of the expansion valve 4 and this valve are accommodated. Support member 44 to which body 43 is fixed by spot welding or the like
Is housed. Reference numeral 45 denotes a throttle passage (passage hole) that decompresses the high-pressure liquid refrigerant from the refrigerant inlet 41 into a low-temperature low-pressure gas-liquid two-phase refrigerant, and the opening degree of the throttle passage 45 is adjusted by the valve body 43. ing. Further, a conical valve seat surface 45a is formed in a portion of the throttle passage 45 facing the spherical valve body 43.

Reference numeral 46 denotes a stepped cylindrical second valve rod, and the small-diameter shaft portion 46a on the lower side penetrates the throttle passage 45, and the second valve rod 4
The lower end surface 46b of 6 is formed in a plane perpendicular to the central axis of the second valve rod 46 and is in contact with the spherical valve body 43.
On the other hand, the large-diameter shaft portion 46c on the upper side of the second valve rod 46 is inserted into the second hole portion 40a formed in the main body case 40, and the second hole portion 40a moves the second valve rod 46 up and down. The guide is slidable in any direction. Then, the upper end surface 4 of the second valve rod 46
6d is in contact with a lower end surface 49d of a first valve rod 49 described later.

Here, FIG. 2 is a partially enlarged sectional view of FIG. 1, and the alternate long and short dash line indicated by reference character A in FIG. 2 indicates the central axis of the second hole 40a and the alternate long and short dash line indicated by reference sign B is indicated. The central axis of the throttle passage 45 is shown. The central axis A of the second hole 40a is formed so as to be inclined with respect to the central axis B of the throttle passage 45. In addition, the lower end surface 46 of the second valve rod 46
b and the upper end surface 46d are formed in a plane perpendicular to the central axis A of the second valve rod 46.

Reference numeral 47 denotes a refrigerant outflow passage through which the low-temperature low-pressure gas-liquid two-phase refrigerant that has been depressurized through the throttle passage 45 flows, and is formed at a substantially middle portion of the main body case 40 in the vertical direction.
The refrigerant outflow passage 47 is connected to the refrigerant inlet portion of the evaporator 5.

Reference numeral 48 denotes an evaporator outlet side passage through which the gas refrigerant evaporated in the evaporator 5 flows, and in this embodiment, it is formed so as to penetrate in the left-right direction in a cylindrical shape in the upper portion of the main body case 40. The inlet end of the evaporator outlet passage 48 (see FIG.
Is connected to the refrigerant outlet part of the evaporator 5, and the outlet end (right end in FIG. 1) is connected to the suction port of the compressor 1.

Reference numeral 49 denotes a first valve rod which is disposed through the evaporator outlet passage 48 and is formed in a columnar shape with a metal having good heat conduction such as aluminum. ) 52 and the function of transmitting the displacement to the second valve rod 46 and the function of sensing the temperature of the superheated gas refrigerant evaporated in the evaporator 5.

The specific form of the first valve rod 49 will be described. A small-diameter shaft portion 49a penetrating the evaporator outlet passage 48 and an end portion of the small-diameter shaft portion 49a are connected to a diaphragm 52 to be described later. It is composed of a diaphragm stopper portion (sliding member) 49b which abuts. The diaphragm stopper portion 49b is integrally formed in a disk-like shape whose outer diameter is enlarged from the upper end portion side (end portion on the diaphragm 52 side) of the first valve rod 49.

The first case formed on the body case 40
The small diameter shaft portion 49a of the first valve rod 49 is inserted into the hole portion 40b, and the first hole portion 40a guides the first valve rod 49 slidably in the vertical direction.

The second hole 40a and the first hole 40
The diameter of b is formed to correspond to the outer diameter of the second valve rod 46 and the outer diameter of the small-diameter shaft portion 49a.
The a and 40b are formed in a continuous stepped shape. The central axis of the first hole 40b and the central axis B of the throttle passage 45 are formed to be coaxial. Therefore, the central axis A of the second hole 40a is also inclined with respect to the central axis B of the first hole 40b. The lower end surface 49d of the small-diameter shaft portion 49a of the first valve rod 49 is formed in a plane perpendicular to the central axis B of the first valve rod 49.

A ring-shaped groove portion 49c is formed on the outer periphery of the portion of the small-diameter shaft portion 49a of the first valve rod 49 which is inserted into the first hole portion 40b, and this groove portion 49c is formed. In addition, there is an elastically deformable first seal member (O ring in the present embodiment) 51 that seals between the small diameter shaft portion 49a of the first valve rod 49 and the first hole portion 40b. It is arranged and held in a state of being compressed in the direction and elastically deformed. As a result, the first valve rod 49 has the first hole portion 4
It is fitted to 0b in an airtight and slidable manner.

Further, a diaphragm stopper portion 49b formed at the upper end portion of the first valve rod 49 is inserted into the third hole portion 40c formed in the body case 40, and the third hole portion 40c has a first hole portion 40c. The valve rod 49 is guided slidably in the vertical direction. The central axis of the third hole 40c is the same as that of the first hole 40b.
Of course, it is formed coaxially with the central axis B of the.

The diaphragm stopper portion 49b
Is in contact with a diaphragm 52 disposed on the outermost side of the uppermost part of the main body case 40. Therefore, when the diaphragm 52 is displaced in the vertical direction, the first
The valve body 43 is also displaced via the valve rod 49 and the second valve rod 46.

When the first valve rod 49 slides downward by a predetermined amount, the diaphragm stopper portion 49b comes into contact with a case member 54, which will be described later, to limit the downward sliding, while the first valve rod 49 The amount of upward sliding of the diaphragm is limited because the diaphragm stopper portion 49b is in contact with the diaphragm 52. Thus, the diaphragm stopper portion 49b has a function of limiting the sliding range of the first valve rod 49.

The portion of the small-diameter shaft portion 49a above the groove portion 49c (diaphragm stopper portion 49b side) and the diaphragm stopper portion 49b are referred to as a temperature sensing portion (temperature sensing means) 49f, and this temperature sensing portion 49f. Is for conducting the heat of the superheated gas refrigerant to the diaphragm 52 and sensing the temperature of the superheated gas refrigerant.

A heat transfer delay member 64 is mounted on the surface of the temperature sensing portion 49f by press-fitting fixation or the like in order to suppress hunting in valve operation. The heat transfer delay member 64 is
The first valve rod 49 is formed of a material (for example, resin) having a thermal conductivity sufficiently lower than that of aluminum.

The outer peripheral edge of the diaphragm (heat responsive means) 52 is sandwiched between and supported by the upper and lower case members 53 and 54. The case members 53 and 54 are made of a metal material such as stainless steel (SUS304) and are integrally joined by welding, brazing or the like. Lower case member 5
4 is fixed to the uppermost part of the main body case 40 by screwing, and this screwing and fixing part is airtight by a second seal member (O ring in this embodiment) 55. And
The space inside the case members 53 and 54 is partitioned by the diaphragm 52 into an upper chamber 56 and a lower chamber 57.

A capillary tube 56a for filling a refrigerant is joined to the upper chamber 56. This tube 56a
The upper chamber 56 is a sealed space because the tip of is closed. The inside of the upper chamber 56 is filled with a gas refrigerant of the same type as the circulating refrigerant in the refrigeration cycle, and the pressure of the enclosed gas changes according to the temperature conducted by the temperature sensing portion 49f of the first valve rod 49. To do.

Therefore, the diaphragm 52 is highly elastic,
In addition, it is preferable that it is formed of a tough material that has good thermal conductivity and is made of a metal such as stainless steel (SUS304).

On the other hand, the lower chamber 57 passes through a space around the diaphragm stopper portion 49b of the first valve rod 49, a pressure introducing space 58 and an annular communication passage 59 formed in the lower part of the space, and then the evaporator outlet. The refrigerant pressure in the evaporator outlet side passage 48 communicates with the lower passage 57.
Will be introduced in. That is, the pressure in the lower chamber 57 becomes substantially the same as the pressure in the passage 48.

Reference numeral 60 denotes a screw hole portion opened to the outside of the lower surface of the main body case 40, and the adjustment plug 61 is provided in the screw hole portion 60.
Are fixed with screws. This adjustment plug 61 has a third seal member (O-ring in the present embodiment) 6 on its outer peripheral portion.
2 is attached, and thereby, the gap with the screw hole portion 60 is hermetically sealed.

Further, in the present embodiment, the elastic member 63 that elastically deforms with the displacement of the valve body 43 is provided, and the direction of the elastic force that the valve body 43 receives from the elastic member 63 is the second valve rod 46. Is inclined with respect to the central axis A direction. Specifically, as shown in FIG. 1, a coil spring 63 is provided as an elastic member, and one end of the coil spring 63 is provided by the spring guide portion 61 a of the adjustment plug 61 to the throttle passage 45.
Is positioned and supported so as to be coaxial with the central axis B, and the other end is supported by the spring guide portion 44 a of the support member 44.
Therefore, by adjusting the tightening position of the adjustment plug 61,
The mounting load of the coil spring 63 can be adjusted.

Next, the operation of the above configuration will be described.

When the compressor 1 operates in the refrigeration cycle of FIG. 1 and the refrigerant circulates in the cycle, the first valve rod 49 and the metal diaphragm 52 are added to the gas filled in the upper chamber 56 of the diaphragm 52. The temperature of the superheated gas refrigerant at the outlet of the evaporator in the passage 48 is conducted via the via. As a result, the pressure in the upper chamber 56 becomes a pressure corresponding to the temperature of the overheated gas refrigerant in the passage 48, while the pressure in the lower chamber 57 of the diaphragm 52 becomes the refrigerant pressure in the passage 48. Therefore, both rooms 5
The valve body 43 is displaced by the balance between the pressure difference in the valves 6 and 57 and the mounting load of the spring 63 that presses the valve body 43 upward.

As described above, when the temperature of the superheated gas refrigerant in the passage 48 is lowered, the pressure in the upper chamber 56 is lowered, and the valve body 43 is displaced to the valve seat surface 45a side (upper side in FIG. 1) to restrict the throttle passage 45.
And the refrigerant flow rate decreases.

On the other hand, when the temperature of the superheated gas refrigerant in the passage 48 rises, the pressure in the upper chamber 56 rises, and the valve body 43 is displaced in the direction away from the valve seat surface 45a (downward in FIG. 1) to move the throttle passage 45. The opening degree increases and the refrigerant flow rate increases. Due to such automatic adjustment of the refrigerant flow rate, the superheat degree of the gas refrigerant at the outlet of the evaporator 5 is maintained at a predetermined value.

As described above, according to the structure of this embodiment, the central axis direction A of the second hole 40a is inclined with respect to the central axis direction B of the first hole 40b. The 1st and 2nd hole parts 40a and 40b are formed. As a result, the sliding direction of the second valve rod 46 intersects with the sliding direction of the first valve rod 49, so that the second valve rod 46 moves along with the sliding of the first valve rod 49. When sliding, the second
The valve rod 46 will be pressed against the portion of the body case 40 that forms the second hole 40a.

Further, since the central axis direction A of the second hole 40a is inclined with respect to the central axis direction B of the coil spring 63, the sliding direction of the second valve rod 46 is such that the coil spring 63 is the valve body. When the second valve rod 46 slides as the valve body 43 is pushed upward by the coil spring 63, the second valve 43 is pushed. The rod 46 is pressed against the portion of the main body case 40 that forms the second hole 40a.

As described above, the frictional force between the second valve rod 46 and the main body case 40 can be increased and the sliding resistance of the second valve rod 46 can be increased without increasing the number of parts of the expansion valve. It is possible to reduce abnormal vibration noise of the valve body 43.

Further, according to the structure of this embodiment, the sliding direction of the second valve rod 46 is a direction intersecting the sliding direction of the first valve rod 49, and Lower end surface 4 of 49
9d is formed substantially perpendicular to the central axis B of the first valve rod 49, and the upper end surface 46d of the second valve rod 46 is formed substantially perpendicular to the central axis A of the second valve rod 46. Thereby, the lower end surface 49 of the first valve rod 49 among the upper end surfaces 46d of the second valve rod 49
Since the portion that comes into contact with d is a portion that is off the central axis of the second valve rod 46, a rotational moment is always generated in the second valve rod 46 when the second valve rod 46 slides, and the second valve The rod 46 is pressed against the case member 40. Therefore, the frictional force between the second valve rod 46 and the main body case 40 can be further increased.

(Second Embodiment) In the first embodiment,
Although the first valve rod 49 is composed of the small diameter shaft portion 49a and the diaphragm stopper portion 49b, in the present embodiment,
As shown in FIG. 3, the small diameter shaft portion 49a is eliminated and the second valve rod 4
6 to the diaphragm stopper 49b, and
The extending portion 46e of the valve rod 46 has the same function as the small diameter shaft portion 49a.

Then, as shown in FIG. 3, the second hole 40
The central axis A of a is formed so as to be inclined with respect to the central axis B of the third hole 40c, and this central axis B is coaxial with the central axis of the throttle passage 45 as in the first embodiment. Is formed. In addition, the upper end surface 46d of the second valve rod 46
Is formed in a plane perpendicular to the central axis A, and the lower end surface 49g of the diaphragm stopper portion 49b is formed in a plane perpendicular to the central axis B of the third hole 40c.

In the first embodiment, the O-ring 5
Although the groove portion 49c for arranging 1 is formed on the first valve rod 49 side, in the present embodiment, the groove portion 49c is eliminated and the extending portion 46e of the second valve rod 46 is formed in the first hole portion 40b. The O-ring 51 is disposed between the main body case 40 and
e does not slide on the first hole 40b.
Further, by fixing the C-shaped snap ring 65 and the like to the extending portion 46e of the second valve rod 46, the O-ring 51 is prevented from slipping out of the first hole portion 40b into the evaporator outlet side passage 48.

As described above, according to this embodiment, the sliding direction of the second valve rod 46 intersects the sliding direction of the diaphragm stopper portion 49b, so that the diaphragm stopper portion 49b can be slid. Along with this, when the second valve rod 46 slides, the second valve rod 46 is pressed against the main body case 40. Therefore, the frictional force between the second valve rod 46 and the main body case 40 can be increased and the sliding resistance of the second valve rod 46 can be increased without increasing the number of components of the expansion valve, and the valve body 43 Vibration noise can be reduced.

In addition to the sliding direction of the second valve rod 46 intersecting with the sliding direction of the diaphragm stopper portion 49b, the lower end surface 49g of the diaphragm stopper portion 49b with respect to the central axis B. Is formed almost vertically, the second
The upper end surface 46d of the valve rod 46 is formed substantially perpendicular to the central axis A. As a result, a portion of the upper end surface 46d of the second valve rod, which comes into contact with the lower end surface 49g of the diaphragm stopper portion 49b, is a portion off the central axis of the second valve rod 46, so that the second valve rod 46 slides. When moving, the second valve rod 46
A rotation moment is always generated in the second valve rod 46, and the second valve rod 46 is pressed against the case member 40. Therefore, the frictional force between the second valve rod 46 and the main body case 40 can be further increased.

(Other Embodiments) In the first and second embodiments described above, the capillary tube 56a is used for charging the upper chamber 56 with the refrigerant, and the temperature sensing section 4 serving as the temperature sensing means is used.
The present invention is applied to a box type expansion valve in which 9f is built in the main body case 40, while the first valve rod 49 and the second valve
When integrally formed with the valve rod 46, a temperature sensitive tube for sensing the refrigerant temperature at the outlet of the evaporator is provided instead of the temperature sensitive section 49f, and the temperature sensitive tube is connected to the upper chamber 56 as a capillary tube. The present invention may be applied to a well-known joint connection type expansion valve using 56a.

[Brief description of drawings]

FIG. 1 is a refrigeration cycle diagram including a cross-sectional structure of an expansion valve according to a first embodiment of the present invention.

FIG. 2 is a partially enlarged sectional view of FIG.

FIG. 3 is a refrigeration cycle diagram including a sectional structure of an expansion valve according to a second embodiment of the present invention.

FIG. 4 is a partially enlarged sectional view of FIG.

[Explanation of symbols]

40 ... Main body case, 40a ... 2nd hole part, 40b ... 1st hole part, 43 ... Valve body, 46 ... 2nd valve rod, 49 ... 1st valve rod, A
... central axis of the second hole portion, B ... central axis of the first hole portion.

Claims (4)

[Claims] 1. A thermal responsive means (52) which is displaced according to the heating degree of the gas refrigerant on the outlet side of the evaporator (5), and a first valve rod which slides with the displacement of said thermal responsive means (52). (49) and a second valve slides with the first valve rod (49).
A valve body that adjusts the opening degree of a throttle passage hole (45) for decompressing and expanding the liquid refrigerant on the cycle high pressure side by displacing the valve rod (46) and the second valve rod (46) along with sliding. (43), a first hole (40b) for slidably guiding the first valve rod (49), and a second hole (40a) for slidably guiding the second valve rod (46). ) And a case member (40) having
In the expansion valve including, the first and second axes are arranged so that the central axis (A) of the second hole (40a) is inclined with respect to the central axis (B) of the first hole (40b). An expansion valve having holes (40a, 40b) formed therein. 2. An end surface (49d) of the first valve rod (49) that comes into contact with the second valve rod (46) is formed substantially with respect to a central axis (B) of the first valve rod (49). The end face (46d) of the second valve rod (46), which is formed vertically and is in contact with the end face (49d) of the first valve rod (49), has the central axis (A) of the second valve rod (46). The expansion valve according to claim 1, wherein the expansion valve is formed substantially perpendicular to the. 3. A thermal responsive means (52) that is displaced according to the heating degree of the gas refrigerant on the outlet side of the evaporator (5), and is slid along with the displacement of the thermal responsive means (52). A sliding member (49b) having a function of limiting the range of motion, a valve rod (46) sliding with the sliding of the sliding member (49b), and a sliding movement of the valve rod (46). The sliding member (49b) is slidably guided by the valve member (43) for adjusting the opening degree of the throttle passage hole (45) for decompressing and expanding the liquid refrigerant on the high pressure side of the cycle by being displaced together. A case member (40) having a third hole (40c) and a second hole (40a) slidably guiding the second valve rod (46).
54) with the second and the second holes (40a) such that the central axis (A) of the second hole (40a) is inclined with respect to the central axis (B) of the third hole (40c). An expansion valve having a third hole (40a, 40c) formed therein. 4. An end surface (49g) of the sliding member (49b) that comes into contact with the valve rod (46) is formed substantially perpendicular to a central axis (B) of the sliding member (49b). The end surface (46d) of the valve rod (46) contacting the end surface (49g) of the sliding member (49b) is connected to the valve rod (46).
The expansion valve according to claim 3, wherein the expansion valve is formed substantially perpendicular to a central axis (A) of the.