CN109312970B - Expansion valve and refrigeration cycle device provided with same - Google Patents
Expansion valve and refrigeration cycle device provided with same Download PDFInfo
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- CN109312970B CN109312970B CN201680085852.2A CN201680085852A CN109312970B CN 109312970 B CN109312970 B CN 109312970B CN 201680085852 A CN201680085852 A CN 201680085852A CN 109312970 B CN109312970 B CN 109312970B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
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Abstract
The expansion valve (10) has a valve body (12) provided with a valve chamber (14). A communication hole (26) and an orifice (22) that communicate with the valve chamber (14) are formed in the valve body (12). A first pipe and a second pipe (32) are connected to the valve body (12). The first pipe is connected to the communication hole (26). The second pipe (32) communicates with the orifice (22). In an expansion valve (10), when a needle (16) reciprocates between the lowest point and the uppermost point, a through hole (18) penetrating the needle (16) is formed in an opposing portion (FN) which is constantly opposed to the inner peripheral surface of an orifice (22) and which is located between a position (PN3) and a position (PN2) in the needle (16).
Description
Technical Field
The present invention relates to an expansion valve and a refrigeration cycle apparatus including the expansion valve, and also relates to an expansion valve having a valve needle and an orifice and a refrigeration cycle apparatus including the expansion valve.
Background
As a refrigeration cycle apparatus, there is an air conditioner including a refrigerant circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected in this order.
An expansion valve of a refrigeration cycle apparatus (air conditioner) has a function of decompressing a high-pressure liquid refrigerant condensed in a condenser to a state where the refrigerant is easily evaporated in an evaporator and adjusting a flow rate of the refrigerant. The expansion valve includes an orifice and a valve needle, and the valve needle is inserted through the orifice. The pressure and flow rate of the refrigerant are adjusted by changing the position of the valve needle relative to the orifice.
It is known that sound (refrigerant sound) is generated when the refrigerant flows through a gap between the orifice and the needle. For example, in an indoor air conditioner, a sound having a frequency of about 5 to 10kHz is generated as a refrigerant sound. Conventionally, various measures have been taken to suppress this refrigerant noise (for example, patent documents 1 and 2).
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. H07-91778
Patent document 2: japanese patent laid-open No. 2000-346495
Disclosure of Invention
Problems to be solved by the invention
As described above, in the refrigeration cycle apparatus, various measures have been taken to generate a refrigerant sound due to the refrigerant flowing to the expansion valve during operation. The present invention has been made as part of the measures against the refrigerant noise, and an object thereof is to provide an expansion valve in which the refrigerant noise is suppressed, and another object thereof is to provide a refrigeration cycle device including such an expansion valve.
Means for solving the problems
An expansion valve of the present invention has a valve body and a valve needle. The valve body includes a valve chamber and an orifice communicating with the valve chamber. The valve needle is inserted through the orifice and reciprocates between a lowermost first position and an uppermost second position. When the needle reciprocates between the first position and the second position, a through hole penetrating a portion of the needle is formed in a portion of the needle facing the inner peripheral surface of the orifice.
Another expansion valve of the present invention includes a valve main body and a valve needle. The valve body includes a valve chamber and an orifice communicating with the valve chamber. The valve needle is inserted through the orifice and reciprocates between a lowermost first position and an uppermost second position. When the needle reciprocates between the first position and the second position, a groove is formed along the circumferential surface portion in at least one of the outer circumferential surface portion of the needle facing the inner circumferential surface of the orifice and the inner circumferential surface portion of the orifice facing the outer circumferential surface of the needle.
The refrigeration cycle apparatus of the present invention includes the expansion valve.
Effects of the invention
According to one expansion valve of the present invention, refrigerant noise can be reduced by suppressing self-excited vibration of the valve needle.
According to another expansion valve of the present invention, refrigerant sound can be reduced by suppressing self-excited vibration of the valve needle.
According to the refrigeration cycle apparatus of the present invention, the refrigerant noise of the refrigerant flowing through the expansion valve can be reduced.
Drawings
Fig. 1 is a diagram showing a refrigeration circuit of a refrigeration cycle apparatus including an expansion valve according to embodiment 1.
Fig. 2 is a partial sectional view including a part of a side of an expansion valve used in the refrigeration cycle device in this embodiment.
Fig. 3 is a first partial sectional view including a part of the side surface for explaining the operation of the expansion valve in this embodiment.
Fig. 4 is a second partial sectional view including a part of the side surface for explaining the operation of the expansion valve in this embodiment.
Fig. 5 is a partially enlarged perspective view showing the structure of the valve needle in the expansion valve according to this embodiment.
Fig. 6 is a partially enlarged perspective view for explaining the flow of the refrigerant in the throttle portion of the expansion valve in this embodiment.
Fig. 7 is a partial plan view for explaining vibration of the valve needle in the expansion valve according to this embodiment.
Fig. 8 is a partially enlarged cross-sectional view including a part of the side for explaining the operation and effect of the expansion valve in this embodiment.
Fig. 9 is a partially enlarged perspective view showing a valve needle of an expansion valve according to a first modification of the embodiment.
Figure 10 is a top view of the valve needle of figure 9 as viewed axially in this embodiment.
Fig. 11 is a partially enlarged perspective view showing a valve needle of an expansion valve according to a second modification of this embodiment.
Fig. 12 is a partially enlarged perspective view showing the structure of a valve needle in an expansion valve according to embodiment 2.
Fig. 13 is a partially enlarged sectional view including a part of the side for explaining the operation effect of the expansion valve in this embodiment.
Fig. 14 is a partially enlarged perspective view showing a valve needle of an expansion valve according to a first modification of the embodiment.
Fig. 15 is a partially enlarged perspective view showing a valve needle of an expansion valve according to a second modification of this embodiment.
Fig. 16 is a partially enlarged perspective view including a partial cross section showing the structure of an orifice in an expansion valve according to embodiment 3.
Fig. 17 is a partially enlarged perspective view including a partial cross section for explaining the operation and effect of the expansion valve in this embodiment.
Fig. 18 is a partially enlarged perspective view including a partial cross section of an orifice of an expansion valve according to a modification of this embodiment.
Detailed Description
An expansion valve and a refrigeration cycle apparatus including the expansion valve according to embodiment 1 will be described. First, an air conditioner as a refrigeration cycle device will be described.
As shown in fig. 1, in the air-conditioning apparatus 2 (refrigeration cycle apparatus 1), a refrigerant circuit is formed, and the compressor 4, the condenser 6, the expansion valve 10, and the evaporator 8 are connected in this order. The refrigerant compressed by the compressor 4 becomes a high-temperature and high-pressure gas refrigerant and is discharged from the compressor 4. The discharged high-temperature high-pressure gas refrigerant is sent to the condenser 6. In the condenser 6, heat exchange is performed between the refrigerant flowing in and the air sent into the condenser 6. By the heat exchange, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant (single phase).
The high-pressure liquid refrigerant sent from the condenser 6 passes through the expansion valve 10 to become a two-phase refrigerant of a low-pressure gas refrigerant and a liquid refrigerant. The two-phase refrigerant flows into the evaporator 8. In the evaporator 8, heat is exchanged between the two-phase refrigerant flowing into the evaporator 8 and the air fed into the evaporator 8. The liquid refrigerant is evaporated by the heat exchange to become a low-pressure gas refrigerant (single phase).
The low-pressure gas refrigerant sent from the evaporator 8 flows into the compressor 4, and is compressed into a high-temperature high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant is discharged from the compressor 4 again and sent to the condenser 6. Hereinafter, this cycle is repeated.
Next, the expansion valve 10 used in the air-conditioning apparatus 2 will be described. The expansion valve 10 has a function of decompressing the high-pressure liquid refrigerant condensed by the condenser 6 to a state in which the refrigerant is easily evaporated by the evaporator 8, and adjusting the flow rate of the refrigerant.
As shown in fig. 2, the expansion valve 10 has a valve main body 12. The valve body 12 is provided with a valve chamber 14. The valve main body 12 is formed with a communication hole 26 and an orifice 22 that communicate with the valve chamber 14, respectively. A first pipe 30 and a second pipe 32 are connected to the valve main body 12. The first pipe 30 communicates with the communication hole 26. The second pipe 32 communicates with the orifice 22.
A needle 16 is inserted through the orifice 22. The throttle 11 is composed of an orifice 22 and a needle 16. The dimension of the gap of the throttle portion 11 is changed by reciprocating the needle 16 in the axial direction (refer to an arrow). Fig. 3 shows a state where the throttle unit 11 is fully closed. This state is a state in which the needle 16 is located at the lowermost point (first position). In this state, the needle 16 contacts the end of the orifice 22, and the flow path of the throttle section 11 is closed.
On the other hand, fig. 4 shows a state where the throttle unit 11 is fully opened. This state is a state in which the valve needle 16 is located at the uppermost point (second position). In this state, the clearance between the needle 16 and the orifice 22 is maximized. The widest flow path is formed as the flow path of the throttle section 11. In the expansion valve 10, the valve needle 16 is slid between the lowermost point and the uppermost point, and the width (flow passage area) of the flow passage of the throttle portion 11 is changed, thereby adjusting the pressure and flow rate of the refrigerant.
In the expansion valve 10 according to embodiment 1, in the needle 16 that reciprocates (slides) between the lowermost point and the uppermost point, a through hole is formed in a portion (facing portion) of the needle 16 that faces the inner peripheral surface of the orifice 22.
First, as shown in fig. 3, in the fully closed state of the throttle portion, the portion of the needle 16 located between the position PN1 and the position PN2 faces the inner peripheral surface of the orifice 22. On the other hand, as shown in fig. 4, in the fully opened throttle position, the portion of the needle 16 located between the position PN3 and the position PN4 faces the inner peripheral surface of the orifice 22.
Then, when the needle 16 reciprocates between the lowermost point and the uppermost point, a portion (facing portion FN) of the needle 16 located between the position PN3 and the position PN2 always faces the inner peripheral surface of the orifice 22. As shown in fig. 5, the expansion valve 10 has a through hole 18 formed in the facing portion FN thereof to pass through the needle 16. Here, the through hole 18 is formed to pass through the center axis AC of the needle 16, for example.
In the expansion valve 10, the through-hole 18 is formed in the needle 16, which contributes to reducing the refrigerant noise. This will be explained. First, the refrigerant sound will be explained.
The source of the sound of the refrigerant sound is the valve needle of the expansion valve. There is a vibration source that applies vibration to the sound source. The excitation source includes self-excited vibration and liquid column resonance. The needle has a natural frequency, and when the natural frequency resonates with the excitation source, a refrigerant sound is generated.
The self-excited vibration is a vibration caused by the air gap of the expansion valve. As described above, in the expansion valve 10, the valve needle 16 is slid between the lowermost point and the uppermost point, and the width (flow passage area) of the flow passage of the throttle portion 11 is changed, thereby adjusting the pressure and flow rate of the refrigerant. Therefore, a clearance is provided for the needle that reciprocates.
Since the gap is provided, the central axis of the needle may be inclined with respect to the central axis of the orifice. When the valve needle is tilted, the clearance between the valve needle and the orifice results in a relatively wide portion and a narrow portion in the circumferential direction. The refrigerant flowing in the portion where the gap is wide has a lower velocity than the refrigerant flowing in the portion where the gap is narrow. Therefore, a static pressure of the refrigerant flowing through the gap between the needle and the orifice varies in the circumferential direction, with the result that the needle vibrates (self-excited vibration).
On the other hand, liquid column resonance is generated in a state where the refrigerant flowing through the expansion valve is a liquid refrigerant. The liquid column resonance is generated from the relationship between the vibration frequency determined by the arrangement of the piping connected to the expansion valve and the natural vibration frequency of the expansion valve, the vibration frequency being obtained from the wavelength of the refrigerant and the sound velocity of the liquid refrigerant.
The vibration frequency of the liquid refrigerant is not the same within the expansion valve. Therefore, when the vibration frequency of the liquid refrigerant becomes a value close to the natural vibration frequency, resonance occurs, and the needle vibrates. Further, even when one of the vibration frequency and the natural frequency of the liquid refrigerant has a frequency that is a multiple of the other vibration frequency, resonance is caused and the needle vibrates.
In particular, the expansion valve 10 according to embodiment 1 can suppress self-excited vibration as an excitation source and self-excited vibration in liquid column resonance. This is explained in further detail.
As described above, the clearance between the needle and the orifice is generated at a relatively wide portion and a narrow portion in the circumferential direction. When the refrigerant flows through the gap, the portion with the wide gap and the portion with the narrow gap are more susceptible to the influence of viscosity than the portion with the wide gap. Therefore, as shown in fig. 6, the speed of the refrigerant flowing through the narrow gap NA is lower than the speed of the refrigerant flowing through the wide gap WA (see arrows). Thus, the static pressure generated by the refrigerant flowing through the narrow gap NA is higher than the static pressure of the refrigerant flowing through the wide gap WA.
Therefore, the needle 16 is urged from the side where the gap is narrow to the side where the gap is wide. By applying a force to the needle 16, the gap is gradually increased in the narrow portion, and the gap is gradually decreased in the wide portion. As a result, as shown in fig. 7, the needle 16 is biased to the right, and passes from the state shown in the left of fig. 7 through the state shown in the center, and then to the state shown in the right.
When the state shown in the right drawing of fig. 7 is reached, the force is applied to the left from the narrow side toward the wide side, opposite to the former direction, and the state shown in the right drawing of fig. 7 passes through the state shown in the center drawing, and the state shown in the left drawing is reached. Thereafter, by repeating this operation, the needle self-vibrates. In fig. 7, although one-dimensional vibration is shown in order to avoid complication of the drawing, actual vibration is two-dimensional vibration.
In this case, the wide gap region is spatially connected to the narrow gap region. Therefore, if the pressure (static pressure) at the narrow gap portion is higher than the pressure (static pressure) at the wide gap portion, the pressure should be released from the narrow gap portion to the wide gap portion.
However, since the refrigerant passes through a minute gap between the needle and the orifice, the refrigerant flows at a high speed. Therefore, the refrigerant passes through the gap before the pressure is released from the narrow portion to the wide portion, and thus the pressure (static pressure) at the narrow portion and the pressure (static pressure) at the wide portion are maintained. That is, the operation of the needle is repeated.
In such a situation, if liquid column resonance occurs, self-excited vibration may be amplified. When the vibration frequency of the self-excited vibration approaches a value of the natural vibration frequency of the expansion valve, resonance occurs, and refrigerant sound is generated. For example, in an indoor air conditioner, a refrigerant sound having a frequency of about 5 to 10kHz is generated.
As shown in fig. 5, in the expansion valve 10 according to embodiment 1, when the needle 16 reciprocates between the lowermost point and the uppermost point, a through hole 18 penetrating the needle 16 is formed in a portion (facing portion FN) of the needle 16 that always faces the inner peripheral surface of the orifice 22. The through hole 18 is formed substantially perpendicular to the flow of the refrigerant flowing through the throttle portion 11.
As a result, as shown in fig. 8, the pressure (static pressure) can be released from a portion where the gap with high static pressure is narrow to a portion where the gap with low static pressure is wide without being affected by the flow of the refrigerant. As a result, self-excited vibration as an excitation source and self-excited vibration in liquid column resonance can be suppressed, and refrigerant sound can be reduced.
Refrigeration cycle apparatuses are used in various environments in various countries around the world. Selection of the specification (natural frequency) of the expansion valve in accordance with the environment and the like becomes a factor of cost increase. For example, in the low outside air cooling operation, the liquid refrigerant may be present on both the inlet side and the outlet side of the expansion valve. In this case, it is necessary to consider not only the inlet side of the expansion valve but also the liquid column resonance on the outlet side. Further, cavitation of the refrigerant flowing through the throttle portion tends to further generate refrigerant noise.
In the expansion valve 10 according to embodiment 1, the through-hole 18 is formed only in the needle 16, and the refrigerant noise can be suppressed in the expansion valve 10, whereby a refrigeration cycle device with a reduced cost can be provided. In addition, by suppressing the refrigerant sound, a comfortable environment can be provided. In an actual air conditioning apparatus (refrigeration cycle apparatus), although the directions of the refrigerant flowing through the expansion valve are opposite to each other in the heating operation and the cooling operation, the refrigerant noise can be reduced for a flow in any direction.
Further, as a valve needle of an expansion valve, there is a valve needle using a porous body (for example, patent document 2). The porous body is formed with a plurality of pores. Therefore, a part of the small hole may have the same function as the through hole. The porous body is manufactured to have a predetermined specification (average pore diameter, porosity, pore pitch, or the like).
However, in the valve needle using the porous body, the fine pores are formed randomly in the valve needle, not in the specific position. Therefore, even if the position of the needle with respect to the orifice is the same, the amount of the refrigerant flowing through the fine hole varies. That is, the flow rate of the refrigerant differs among the expansion valves.
In the porous body, the fine holes extending in the longitudinal direction (axial direction of the valve needle) are connected to the fine holes penetrating in the lateral direction (direction orthogonal to the axial direction of the valve needle). Therefore, the flow of the refrigerant to be flowed in the transverse direction is obstructed by the refrigerant to be flowed in the longitudinal direction, and the static pressure is difficult to be released.
On the other hand, the through hole 18 formed in the valve needle 16 of the expansion valve 10 according to embodiment 1 is intended to release pressure (static pressure) and is different from a flow path through which the refrigerant actively flows. Therefore, the through-holes 18 do not need to have an opening area as large as that of a porous body. Therefore, in the expansion valve 10 of embodiment 1 in which the through-hole 18 is formed in the valve needle 16, the refrigerant noise can be suppressed more reliably than in an expansion valve using a porous body.
(first modification)
In the expansion valve according to the first modification, a plurality of through holes are formed in the valve needle. As shown in fig. 9 and 10, in the needle 16, a through hole 18a and a through hole 18b penetrating the needle 16 are formed in an opposing portion FN that faces the inner peripheral surface of the orifice 22 (see fig. 3 and 4).
The through hole 18a and the through hole 18b are formed at positions different from each other in the position in the center axis AC direction (height direction position) of the needle 16. That is, here, the through-hole 18a (height H2) is formed at a position lower than the through-hole 18b (height H3). The through-holes 18a and 18b are formed to have different circumferential positions and to be substantially orthogonal in plan view. The through-holes 18a and 18b are formed so as to pass through the central axis AC.
By making the height H2 of the through-hole 18a different from the height H3 of the through-hole 18b, even when the position of the needle 16 with respect to the orifice changes, the pressure in the portion with a narrow gap can be efficiently released to the portion with a wide gap. Further, since the circumferential position of the through hole 18a is different from the circumferential position of the through hole 18b, the self-excited vibration of the needle, which becomes two-dimensional vibration, can be reliably suppressed.
(second modification)
In the above-described expansion valve, a through hole is formed in a plane parallel to a plane substantially orthogonal to the central axis AC of the needle. The through hole 18 formed in the needle 16 is not limited to such a configuration, and for example, as shown in fig. 11, the through hole 18 may be formed so as to be inclined so as to intersect the plane. That is, the through-hole 18 may be formed to connect the height H4 and the height H5. The pressure in the narrow gap portion can be released to the wide gap portion through the through hole 18. This can reduce the refrigerant noise.
In embodiment 1, an expansion valve in which a through hole is formed in a needle is described. Here, an expansion valve in which a groove is formed in the valve needle will be described.
As shown in fig. 12, in the needle 16, an annular groove 20 is formed along the outer peripheral surface of the needle 16 at a facing portion FN facing the inner peripheral surface of an orifice 22 (see fig. 3 and 4). The groove 20 is not a passage for actively sending out the refrigerant from the valve chamber 14, but is formed as a passage for releasing the static pressure of the refrigerant, similarly to the through hole 18. Since the other configurations are the same as the expansion valve shown in fig. 2, the same components are denoted by the same reference numerals, and descriptions thereof will not be repeated except where necessary.
In the expansion valve 10 described above, when the refrigerant flows through the gap between the needle 16 and the orifice 22, the flow is less likely to be affected in the groove 20. As a result, as shown in fig. 13, the pressure (static pressure) can be released along the annular groove from a narrow gap portion where the static pressure is high to a wide gap portion where the static pressure is low (see arrows). As a result, self-excited vibration is suppressed, and refrigerant noise can be reduced. The groove may be formed by cutting the valve pin. This can minimize an increase in manufacturing cost.
(first modification)
In the expansion valve according to the first modification, a plurality of grooves are formed in the valve needle. As shown in fig. 14, in the needle 16, annular grooves 20a and 20b are formed along the outer peripheral surface at an opposing portion FN of the needle 16 that opposes the inner peripheral surface of the orifice 22 (see fig. 3 and 4). The groove 20a and the groove 20b are formed at positions different from each other in the position (height direction position) in the center axis AC direction of the needle 16. That is, here, the groove 20a is formed at a position higher than the groove 20 b.
By making the height (position) of the groove 20a different from the height (position) of the groove 20b, even when the position of the needle 16 with respect to the orifice changes, the pressure in the portion with a narrow gap can be efficiently released to the portion with a wide gap. Further, since the grooves 20a and 20b are formed in an annular shape along the outer peripheral surface of the needle, the self-excited vibration of the needle, which is two-dimensional vibration, can be reliably suppressed.
(second modification)
In the expansion valve described above, the groove is formed parallel to a plane substantially orthogonal to the center axis AC of the needle, for example. The groove 20 formed in the outer peripheral surface of the needle 16 is not limited to such a configuration, and for example, as shown in fig. 15, the groove 20 may be formed so as to be inclined with respect to the plane. Such a groove 20 can also release the pressure at a narrow gap portion to a wide gap portion. This can reduce the refrigerant noise.
Embodiment 3
In embodiment 2, an expansion valve in which a groove is formed in a valve needle is described. Here, an expansion valve having a groove formed in an orifice will be described.
As described in embodiment 1, the valve needle of the expansion valve reciprocates (slides) between the lowermost point and the uppermost point with respect to the orifice. First, as shown in fig. 3, in the fully closed state of the throttle portion, a portion of the orifice 22 located between the position PO1 and the position PO2 faces the needle 16. On the other hand, as shown in fig. 4, in the throttle portion fully opened state, a portion of the orifice 22 located between the position PO1 and the position PO3 faces the needle 16.
Then, when the needle 16 reciprocates between the lowermost point and the uppermost point, a portion (facing portion FO) of the orifice 22 located between the position PO1 and the position PO3 always faces the outer peripheral surface of the needle 16. As shown in fig. 16, in the expansion valve 10, an annular groove 24 is formed along the inner peripheral surface in the facing portion FO of the orifice 22.
The groove 24 is formed not as a passage for actively sending out the refrigerant from the valve chamber 14 but as a passage for releasing the static pressure of the refrigerant, similarly to the through hole 18. Since the other configurations are the same as the expansion valve shown in fig. 2, the same components are denoted by the same reference numerals, and descriptions thereof will not be repeated except where necessary.
In the expansion valve 10 described above, when the refrigerant flows through the gap between the needle 16 and the orifice 22, the flow is less likely to be affected in the groove 24. As a result, as shown in fig. 17, the pressure (static pressure) can be released along the annular groove 24 from a narrow portion having a high static pressure gap to a wide portion having a low static pressure gap (see arrows). As a result, self-excited vibration is suppressed, and refrigerant noise can be reduced.
(modification example)
In the expansion valve of the first modification, a plurality of grooves are formed in the orifice. As shown in fig. 18, in the orifice 22, annular grooves 24a and 24b are formed along the inner peripheral surface of an opposing portion FO of the orifice 22 that faces the needle 16 (see fig. 3 and 4). The groove 24a and the groove 24b are formed at positions different in the axial direction (height direction position) of the orifice 22. That is, here, the groove 24a is formed at a position higher than the groove 24 b. Like the through hole 18, the grooves 24a and 24b are not formed as passages for actively sending out the refrigerant from the valve chamber 14, but formed as passages for releasing the static pressure of the refrigerant.
By making the height (position) of the groove 24a different from the height (position) of the groove 24b, even when the position of the needle 16 with respect to the orifice changes, the pressure in the portion with a narrow gap can be efficiently released to the portion with a wide gap. Further, since the grooves 24a and 24b are formed in a ring shape along the inner peripheral surface of the orifice 22, the self-excited vibration of the needle, which is two-dimensional vibration, can be reliably suppressed.
The groove formed in the inner circumferential surface of the orifice may be formed to be inclined with respect to a plane substantially perpendicular to the axis of the orifice (or the central axis AC of the needle) (not shown).
Further, the annular groove formed over the entire circumference of the inner circumferential surface of the orifice 22 is exemplified, but the groove may be formed along a part of the circumferential surface, such as a half circumference of the inner circumferential surface.
The structures (through-hole and groove) of the valve needle and the structures (groove) of the orifice of the expansion valve described in the embodiments may be combined in various ways as necessary.
The embodiments disclosed herein are illustrative, and are not limited thereto. The present invention is defined by the claims, not the scope of the above description, and is intended to include all modifications within the meaning and scope equivalent to the claims.
Industrial applicability
The present invention can be effectively used for an expansion valve in which a throttle portion is formed by a valve needle and an orifice.
Description of the reference numerals
1 a refrigeration cycle device; 2 an air conditioning device; 4, a compressor; 6, a condenser; 8, an evaporator; 10 an expansion valve; 11 a throttle section; 12 a valve body; 14 a valve chamber; 16 a valve needle; 18. 18a, 18b through holes; 20. 20a, 20b slots; 22 orifice holes; 24. 24a, 24b slots; 26 a communication hole; 30 a first piping; 32 a second pipe; PN1, PN2, PO1, PO2 positions; a WA wide region; a narrow NA site; FN, FO opposite fractions; an AC center axis.
Claims (7)
1. An expansion valve, comprising:
a valve body including a valve chamber and an orifice communicating with the valve chamber; and
a needle inserted through the orifice and reciprocating between a lowermost first position and an uppermost second position,
a through hole penetrating the portion of the needle facing the inner peripheral surface of the orifice is formed in the portion of the needle facing the inner peripheral surface of the orifice when the needle reciprocates between the first position and the second position,
the through hole penetrates a portion of the needle, which is located in a region including a central axis of the needle.
2. An expansion valve according to claim 1,
the through-holes are formed as a plurality of through-holes including a first through-hole and a second through-hole.
3. An expansion valve according to claim 2,
the first through-hole and the second through-hole are formed to intersect with each other.
4. An expansion valve according to claim 2,
the first through-hole and the second through-hole are formed so as to have different positions in the direction of the central axis of the needle.
5. An expansion valve, comprising:
a valve body including a valve chamber and an orifice communicating with the valve chamber; and
a needle inserted through the orifice and reciprocating between a lowermost first position and an uppermost second position,
a groove is formed along at least one of an outer peripheral surface portion of the needle facing an inner peripheral surface of the orifice and an inner peripheral surface portion of the orifice facing the outer peripheral surface of the needle when the needle reciprocates between the first position and the second position,
the groove is formed over a half of the circumference of the circumferential surface portion.
6. An expansion valve according to claim 5,
the groove is formed in plurality.
7. A refrigeration cycle apparatus, wherein,
an expansion valve according to any one of claims 1 to 6.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2016/068814 WO2017221402A1 (en) | 2016-06-24 | 2016-06-24 | Expansion valve and refrigeration cycle device with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109312970A CN109312970A (en) | 2019-02-05 |
| CN109312970B true CN109312970B (en) | 2021-06-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680085852.2A Active CN109312970B (en) | 2016-06-24 | 2016-06-24 | Expansion valve and refrigeration cycle device provided with same |
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| Country | Link |
|---|---|
| JP (1) | JP6639667B2 (en) |
| CN (1) | CN109312970B (en) |
| WO (1) | WO2017221402A1 (en) |
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| JP7134146B2 (en) * | 2019-07-26 | 2022-09-09 | 株式会社鷺宮製作所 | Expansion valve and refrigeration cycle system |
| CN113090811B (en) * | 2020-08-12 | 2022-06-28 | 深圳市亨瑞达制冷设备有限公司 | Industrial water-cooled water chiller without squeaking |
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| CN101107485A (en) * | 2005-02-28 | 2008-01-16 | 大金工业株式会社 | Expansion valve and refrigeration device |
| JP2009287769A (en) * | 2008-05-28 | 2009-12-10 | Korea Inst Of Mach & Materials | Low noise type electronic expansion valve with built-in disc bellows |
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| JPS5261541U (en) * | 1975-11-01 | 1977-05-06 | ||
| JPS5934073A (en) * | 1982-08-18 | 1984-02-24 | Yamatake Honeywell Co Ltd | Control valve |
| JP2005226846A (en) * | 2004-02-10 | 2005-08-25 | Daikin Ind Ltd | Expansion valve and refrigeration unit |
| JP4831808B2 (en) * | 2005-02-25 | 2011-12-07 | 三菱重工業株式会社 | Expansion valve and air conditioner |
| CN103890505B (en) * | 2011-09-26 | 2015-12-09 | 丹佛斯公司 | There is pressure balanced flow control valve |
| JP6109094B2 (en) * | 2014-01-31 | 2017-04-05 | 株式会社鷺宮製作所 | Control valve |
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2016
- 2016-06-24 WO PCT/JP2016/068814 patent/WO2017221402A1/en active Application Filing
- 2016-06-24 JP JP2018523252A patent/JP6639667B2/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101107485A (en) * | 2005-02-28 | 2008-01-16 | 大金工业株式会社 | Expansion valve and refrigeration device |
| JP2009287769A (en) * | 2008-05-28 | 2009-12-10 | Korea Inst Of Mach & Materials | Low noise type electronic expansion valve with built-in disc bellows |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6639667B2 (en) | 2020-02-05 |
| JPWO2017221402A1 (en) | 2019-01-31 |
| CN109312970A (en) | 2019-02-05 |
| WO2017221402A1 (en) | 2017-12-28 |
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