JP2017106647A - Thermostatic expansion valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a thermostatic expansion valve capable of suppressing vibration and noise due to resonance.SOLUTION: A thermostatic expansion valve 50 includes: a valve body 54 in which a cylindrical valve chamber 58 and an orifice 59 provided at one end side in the cylinder axial direction of the valve chamber are formed; a valve body 61 for opening/closing the orifice; a coil spring 63 for energizing the valve body in a valve closing direction; and a first energization force adjustment member 64 and a second energization force adjustment member 84 selectively and detachably mounted on an opening 58a formed on the other end side in the cylinder axial direction of the valve chamber. The volume of a space inside the valve chamber when the first energization force adjustment member is mounted and the volume of the space inside the valve chamber when the second energization force adjustment member is mounted are different from each other.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a temperature type expansion valve that adjusts the flow rate of a refrigerant based on the temperature of the refrigerant.

  Patent Document 1 describes an expansion valve integrated with a solenoid valve. This solenoid valve-integrated expansion valve has a valve body, a valve body, a power element, and a solenoid valve. The valve body is formed with a valve chamber, an orifice communicating with the valve chamber, an inlet passage for introducing high-pressure refrigerant into the valve chamber, and an outlet passage for leading the refrigerant decompressed by the orifice to the outside. The two spaces located at both ends in the sliding direction of the valve body in the valve chamber communicate with each other through a pressure equalizing passage. In this configuration, when the solenoid valve is opened, the refrigerant flowing into the space on one end side of the valve body in the valve chamber can be released to the space on the other end side of the valve body through the pressure equalizing passage. Thereby, since the impact pressure applied to the valve body is relieved, the occurrence of defects can be avoided.

JP 2012-52693 A

  In general, in an expansion valve, not only a problem due to an impact pressure applied to a valve body when a solenoid valve is opened, but also vibration and noise due to resonance may occur. In the solenoid valve-integrated expansion valve described in Patent Document 1, the impact pressure when the solenoid valve is opened can be relieved, but no measures have been taken to avoid resonance.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a temperature-type expansion valve that can suppress vibration and noise due to resonance.

  The temperature type expansion valve according to the present invention is provided in an inlet passage through which refrigerant flows from the outside, a cylindrical valve chamber communicating with the inlet passage, and one end side in the cylinder axial direction of the valve chamber. An orifice that depressurizes the refrigerant that has flowed in; an outlet passage that allows the refrigerant depressurized by the orifice to flow outside; a valve body that is provided in the valve chamber and opens and closes the orifice; and A coil spring provided in the valve chamber for biasing the valve body in the valve closing direction, a power element for driving the valve body, and an opening formed on the other end side in the cylinder axial direction of the valve chamber. And a first urging force adjusting member and a second urging force adjusting member for closing the other end in the cylinder axis direction of the valve chamber and adjusting the urging force of the coil spring. The first urging force adjusting member is attached. The volume of the valve chamber space when the, the volume of the valve chamber space when the second biasing force adjusting member is mounted are different from each other.

  Further, the temperature type expansion valve according to the present invention is provided at an inlet passage through which refrigerant flows from the outside, a cylindrical valve chamber communicating with the inlet passage, and one end side in the cylinder axial direction of the valve chamber, A valve body formed with an orifice for depressurizing the refrigerant that has flowed into the chamber, and an outlet passage through which the refrigerant depressurized by the orifice flows out, and is attached to the valve chamber alternatively and detachably, A first valve body and a second valve body for opening and closing an orifice; a coil spring provided in the valve chamber for biasing the first valve body or the second valve body in a valve closing direction; A power element that drives the first valve body or the second valve body, and an opening formed on the other end side in the cylinder axis direction of the valve chamber are detachably attached, and the cylinder axis direction and the like of the valve chamber Biasing that closes the end and adjusts the biasing force of the coil spring An adjustment member, and a volume of the space in the valve chamber when the first valve body is attached and a volume of the space in the valve chamber when the second valve body is attached. They are different from each other.

  According to the present invention, since the volume of the space in the valve chamber can be easily changed, vibration and noise due to resonance can be suppressed.

It is a refrigerant circuit diagram which shows the whole structure of the refrigerating-cycle apparatus provided with the temperature type expansion valve 50 which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the structure of the temperature type expansion valve 50 which concerns on Embodiment 1 of this invention. It is a figure which expands and shows the A section of FIG. It is a figure which expands and shows the A section of FIG. It is sectional drawing which shows the structure of the temperature type expansion valve 50 which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
A temperature type expansion valve according to Embodiment 1 of the present invention will be described. FIG. 1 is a refrigerant circuit diagram showing an overall configuration of a refrigeration cycle apparatus including a temperature type expansion valve 50 according to the present embodiment. In the present embodiment, a refrigerator is illustrated as the refrigeration cycle apparatus. In the following drawings including FIG. 1, the relative dimensional relationship and shape of each component may be different from the actual one.

  As shown in FIG. 1, the refrigeration cycle apparatus includes a refrigerant circuit 10 that circulates refrigerant. In the refrigerant circuit 10, a compressor 11, a condenser 12, a liquid reservoir 13, a supercooler 14, a solenoid valve 15, a temperature expansion valve 50, an evaporator 16 and an accumulator 17 are sequentially connected in an annular manner through a refrigerant pipe. It has a configuration. The refrigeration cycle apparatus has a heat source unit 18. The heat source device 18 accommodates a compressor 11, a condenser 12, a liquid reservoir 13, a supercooler 14 and an accumulator 17, and a blower 19 that blows air to the condenser 12 and the supercooler 14. The heat source device 18 and the electromagnetic valve 15 are connected via a liquid pipe 20 that is a part of the refrigerant pipe. The evaporator 16 and the heat source unit 18 are connected via a gas pipe 21 that is a part of the refrigerant pipe.

  The compressor 11 is a fluid machine that compresses sucked low-pressure gas refrigerant and discharges it as high-pressure gas refrigerant. The condenser 12 is a heat exchanger that condenses the high-pressure gas refrigerant by heat exchange with the air blown by the blower 19. The liquid reservoir 13 is a container that gas-liquid separates the refrigerant flowing out of the condenser 12 and stores excess liquid refrigerant. The supercooler 14 is a heat exchanger that supercools the liquid refrigerant by exchanging heat with the air blown by the blower 19. In this example, the condenser 12 and the subcooler 14 are integrated, but the condenser 12 and the subcooler 14 may be separated from each other.

  The solenoid valve 15 is controlled by a control unit (not shown) so as to be opened when the compressor 11 is operated and closed when the compressor 11 is stopped. When the compressor 11 is repeatedly operated and stopped, if the liquid refrigerant accumulates on the upstream side of the compressor 11 while the compressor 11 is stopped, the compressor 11 is damaged due to the suction of the liquid refrigerant when the compressor 11 is restarted. There is a risk. In order to prevent such damage to the compressor 11, an electromagnetic valve 15 is provided on the upstream side of the temperature type expansion valve 50. For example, when controlling the temperature of the refrigeration cycle apparatus, when the temperature to be controlled reaches a set temperature, the control unit stops the compressor 11 and controls the electromagnetic valve 15 to be closed. On the other hand, when the temperature to be controlled becomes higher than the set temperature, the control unit operates the compressor 11 and controls the electromagnetic valve 15 to the open state.

  Further, when a plurality of evaporators 16 and the temperature type expansion valves 50 are provided in parallel, in order to control the refrigerant supply to each of the plurality of evaporators 16, upstream of the plurality of temperature type expansion valves 50. A solenoid valve 15 may be provided for each.

  The temperature type expansion valve 50 decompresses the liquid refrigerant supercooled by the supercooler 14 to form a low-pressure two-phase refrigerant. The opening degree of the temperature type expansion valve 50 is adjusted based on the degree of superheat of the refrigerant flowing out of the evaporator 16. A temperature sensitive cylinder 51 attached to the outlet pipe of the evaporator 16 is connected to the temperature type expansion valve 50 via a capillary tube 52. Further, a pressure equalizing pipe 53 communicating with the outlet pipe of the evaporator 16 is connected to the temperature type expansion valve 50. Details of the structure of the temperature type expansion valve 50 will be described later.

  The evaporator 16 is a heat exchanger that evaporates a low-pressure two-phase refrigerant by exchanging heat with an external fluid. The accumulator 17 is a container that gas-liquid separates the refrigerant flowing out of the evaporator 16 and supplies only the gas refrigerant to the compressor 11.

  In the refrigerant circuit 10, the liquid reservoir 13 can be omitted. In addition, an injection circuit for injecting high-pressure liquid refrigerant into the compressor 11 may be added to the refrigerant circuit 10.

  FIG. 2 is a cross-sectional view showing a configuration of the temperature type expansion valve 50 according to the present embodiment. As shown in FIG. 2, the temperature type expansion valve 50 includes a valve body 54. The valve body 54 has an inlet pipe 55 through which high-pressure liquid refrigerant flows from the condenser 12 side (that is, the solenoid valve 15 side) of the refrigerant circuit 10, and the reduced-pressure low-pressure two-phase refrigerant is the evaporator of the refrigerant circuit 10. An outlet pipe 56 that flows out to the 16 side is connected. A power element 70 for driving a valve body 61 (described later) is provided on the upper portion of the valve body 54. A pipe 71 for introducing a temperature sensitive gas is connected to the upper portion of the power element 70 through a capillary tube 52. The temperature-sensitive gas transmits the temperature of the refrigerant flowing out of the evaporator 16 to the power element 70. Further, a pressure equalizing tube 53 is connected to the power element 70.

  The valve body 54 is formed with an inlet passage 57 through which refrigerant flows from the outside via an inlet pipe 55 and a valve chamber 58 communicating with the inlet passage 57. The valve chamber 58 has a cylindrical shape having a cylinder axis in the vertical direction. The valve chamber 58 has an opening 58a on the lower end side in the cylinder axis direction. In the valve main body 54, an orifice 59 is formed on the upper end side in the cylinder axis direction of the valve chamber 58 to depressurize the refrigerant flowing into the valve chamber 58. The valve body 54 is formed with an outlet passage 60 through which the refrigerant decompressed by the orifice 59 flows out. An outlet pipe 56 is connected to the outlet passage 60. An insertion hole 72 extending in the vertical direction is formed above the outlet passage 60. The lower end of the insertion hole 72 communicates with the outlet passage 60, and the upper end communicates with the lower pressure chamber 73 of the power element 70.

  A valve body 61 that opens and closes the orifice 59 is inserted in an upper part of the valve chamber 58 so as to be slidable in the vertical direction. The valve body 61 can be attached and detached through the opening 58a. A conical tapered surface 61 a is formed at the upper end of the valve body 61. When the tapered surface 61a of the valve body 61 contacts the orifice 59, the orifice 59 is closed, and when the tapered surface 61a is separated from the orifice 59, the orifice 59 is opened.

  A lower end portion of the valve body 61 is supported by a support member 62. The support member 62 is biased upward by a coil spring 63 that is a compression spring. That is, the valve body 61 is urged in the valve closing direction by the coil spring 63 via the support member 62. The coil spring 63 is provided in the valve chamber 58 so that the spiral axis of the coil spring 63 is coaxial with the cylinder axis of the valve chamber 58. The coil spring 63 can be attached and detached through the opening 58a. The lower end of the coil spring 63 is supported by an urging force adjusting member 64 or an urging force adjusting member 84 described later.

  Either the urging force adjusting member 64 or the urging force adjusting member 84 is attached to the opening 58 a of the valve chamber 58. The urging force adjusting member 64 and the urging force adjusting member 84 are both components of the temperature type expansion valve 50, and are alternatively and detachably attached to the opening 58a. In the configuration shown in FIG. 2, the urging force adjusting member 64 is attached to the opening 58a, and the urging force adjusting member 84 is removed from the opening 58a. In FIG. 2, a white double arrow between the urging force adjusting member 64 and the urging force adjusting member 84 indicates that the urging force adjusting member 64 and the urging force adjusting member 84 are alternatively attached.

  The urging force adjusting member 64 includes a bottom portion 64a that supports the lower end portion of the coil spring 63, and a cylindrical portion 64b that protrudes from the bottom portion 64a coaxially with the coil spring 63 along the outer periphery of the coil spring 63. It has a shape. The biasing force adjusting member 64 is detachably attached to the opening 58a of the valve chamber 58 via the screw portion 64c, and closes the lower end side of the valve chamber 58. A slit 64d is formed in the lower surface of the bottom portion 64a of the urging force adjusting member 64. The biasing force adjusting member 64 can adjust the biasing force to the valve body 61 by changing the amount of compression of the coil spring 63 by inserting a tool such as a screwdriver into the slit 64d and rotating it. A seal groove 64e that accommodates an annular seal member 65 for preventing the refrigerant in the valve chamber 58 from leaking to the outside is formed in the outer peripheral portion of the cylindrical portion 64b of the urging force adjusting member 64.

  Similar to the urging force adjusting member 64, the urging force adjusting member 84 includes a bottom portion 84 a that supports the lower end portion of the coil spring 63, and a cylindrical portion that protrudes from the bottom portion 84 a coaxially with the coil spring 63 along the outer periphery of the coil spring 63. 84b, and has a bottomed cylindrical shape. The biasing force adjusting member 84 is detachably attached to the opening 58a of the valve chamber 58 via the screw portion 84c, and closes the lower end side of the valve chamber 58. A slit 84d is formed on the bottom surface of the bottom 84a of the urging force adjusting member 84. The urging force adjusting member 84 can adjust the urging force to the valve body 61 by changing the amount of compression of the coil spring 63 by inserting a tool such as a screwdriver into the slit 84d and rotating it. A sealing groove 84e for accommodating an annular sealing member 65 for preventing the refrigerant in the valve chamber 58 from leaking to the outside is formed in the outer peripheral portion of the cylindrical portion 84b of the urging force adjusting member 84.

  The urging force adjusting member 84 has a protruding portion 84 f that protrudes from the bottom portion 84 a along the inner periphery of the coil spring 63. The protruding portion 84 f has a cylindrical shape that is coaxial with the coil spring 63. The protrusion 84 f has an outer diameter smaller than the inner diameter of the coil spring 63 and an axial length shorter than the axial length of the compressed coil spring 63. The protruding portion 84f of the urging force adjusting member 84 does not affect the basic operation of the temperature type expansion valve 50, for example, and has only a function of adjusting the volume of the space in the valve chamber 58. By disposing the protruding portion 84f on the inner peripheral side of the coil spring 63, contact interference with the movable portion (for example, the coil spring 63, the support member 62, or the valve body 61) in the valve chamber 58 and fretting wear are prevented. Can do.

  On the other hand, the urging force adjusting member 64 does not have such a protruding portion. That is, the support surface 64f that supports the coil spring 63 at the bottom portion 64a of the urging force adjusting member 64 is formed substantially flat. Although the urging force adjusting member 64 of this example does not have a protruding portion, the urging force adjusting member 64 may have a protruding portion having a smaller volume than the protruding portion 84f of the urging force adjusting member 84. Good.

  A bottomed cylindrical cap 66 is provided below the biasing force adjusting member 64 attached to the opening 58a. The cap 66 is detachably attached to the bottom of the valve main body 54 via a screw portion 66a.

  3 and 4 are enlarged views of a portion A in FIG. FIG. 3 shows a portion A of the thermal expansion valve 50 in which the biasing force adjusting member 64 is attached to the opening 58a, and FIG. 4 shows a thermal expansion in which the biasing force adjusting member 84 is attached to the opening 58a. Part A of the valve 50 is shown. In FIGS. 3 and 4, dot hatching is given to the space in the valve chamber 58. As shown in FIGS. 3 and 4, the volume of the space in the valve chamber 58 (see FIG. 4) when the urging force adjusting member 84 is attached to the opening 58a is such that the urging force adjusting member 64 is in the opening 58a. It becomes smaller than the volume of the space in the valve chamber 58 when attached (see FIG. 3). More precisely, the volume of the space in the valve chamber 58 when the biasing force adjusting member 84 is attached to the opening 58a and the compression amount of the coil spring 63 is adjusted to a predetermined value by the biasing force adjusting member 84 is as follows. The biasing force adjusting member 64 is attached to the opening 58a, and the volume of the space in the valve chamber 58 when the compression amount of the coil spring 63 is adjusted to the same value as the predetermined value by the biasing force adjusting member 64 becomes smaller. . The difference between the volume of the space in the valve chamber 58 when the biasing force adjusting member 84 is attached and the volume of the space in the valve chamber 58 when the biasing force adjusting member 64 is attached is, for example, the biasing force adjustment This is equal to the volume of the protruding portion 84 f of the member 84.

  Returning to FIG. 2, an operating rod 74 formed of stainless steel or the like is slidably inserted into the insertion hole 72. The lower end portion of the operating rod 74 is in contact with the valve body 61, and the upper end portion is in contact with the stopper 75 of the power element 70.

  The power element 70 includes an upper lid 76, a lower lid 77, and a diaphragm 78 that is sandwiched between the upper lid 76 and the lower lid 77. An upper pressure chamber 79 is formed between the upper lid 76 and the diaphragm 78. The upper pressure chamber 79 and the capillary tube 52 and the temperature sensing cylinder 51 connected thereto are filled with a temperature sensitive gas. As the temperature sensitive gas, for example, the same type of gas as the refrigerant in the refrigerant circuit 10 is used. The temperature of the refrigerant flowing out of the evaporator 16 is transmitted to the upper pressure chamber 79 by the temperature sensitive gas. Thereby, the inside of the upper pressure chamber 79 becomes a pressure corresponding to the temperature of the refrigerant flowing out of the evaporator 16.

  A lower pressure chamber 73 is formed between the diaphragm 78 and the lower lid 77. The lower pressure chamber 73 communicates with the outlet piping of the evaporator 16 via the pressure equalizing pipe 53. Thereby, the inside of the lower pressure chamber 73 becomes the same pressure as the pressure of the refrigerant flowing out of the evaporator 16.

  The diaphragm 78 is displaced in the vertical direction according to the pressure difference between the internal pressure in the upper pressure chamber 79 and the internal pressure in the lower pressure chamber 73. When the superheat degree of the refrigerant increases and the pressure difference increases, the diaphragm 78 is displaced downward. As a result, the operating rod 74 is pushed down via the stopper 75, so that the valve body 61 moves in the valve opening direction against the urging force of the coil spring 63. On the other hand, when the degree of superheat of the refrigerant decreases and the pressure difference decreases, the diaphragm 78 is displaced upward. As a result, the force to push down the operating rod 74 is weakened, so that the valve body 61 moves in the valve closing direction by the biasing force of the coil spring 63. Therefore, the amount of the refrigerant passing through the orifice 59 is adjusted so that the degree of superheat of the refrigerant at the outlet of the evaporator 16 becomes a predetermined value.

  By the way, in general, in the installation work of the refrigerator, there are many choices of component parts, and installation restrictions greatly differ for each case. For example, the hole diameter, capacity, or size of the temperature type expansion valve 50 or the electromagnetic valve 15 may be changed locally. Further, in order to adjust the superheat degree of the outlet of the evaporator 16 by adjusting the load of the temperature type expansion valve 50 at the site, the urging force of the coil spring 63 is adjusted by the urging force adjusting member 64 or the urging force adjusting member 84, In some cases, the coil spring 63 may be replaced with another coil spring having a different spring constant.

  As one of the factors of vibration and noise generated in the refrigerant circuit 10, Helmholtz in the space in the refrigerant pipe between the temperature type expansion valve 50 and the valve (in this example, the electromagnetic valve 15) provided upstream thereof. Resonance is considered. In a general model of Helmholtz resonance, the fluid in the space is a gas, but the fluid in the space between the electromagnetic valve 15 and the temperature expansion valve 50 is a liquid. Moreover, although the solenoid valve 15 and the temperature type expansion valve 50 are throttles provided at both ends of the space, the ends of the space are not completely closed. Therefore, this space is not a completely closed space but a pseudo closed space. However, even in a pseudo closed space, there is a strong correlation between the volume of the space and the natural frequency of the space. For this reason, the space between the throttle part of the electromagnetic valve 15 and the orifice 59 of the temperature type expansion valve 50 can be considered as a Helmholtz resonator.

  As a vibration applied to the Helmholtz resonator, there is a natural vibration of the coil spring 63 of the temperature type expansion valve 50. When the natural frequency of the space as the Helmholtz resonator and the natural frequency of the coil spring 63 are the same or approximate, pressure pulsation and pipe vibration are generated due to resonance, resulting in damage to pipes or devices and noise.

  An EEV (electronic expansion valve) used in an air conditioner or the like allows flow in both forward and reverse directions. For this reason, a spring having a relatively large spring constant is used for EEV. On the other hand, the temperature type expansion valve does not allow the flow in the reverse direction, and operates by the balance between the pressure of the temperature sensitive gas and the spring load. For this reason, a spring having a relatively small spring constant is used for the temperature type expansion valve. The natural frequency of the spring used for the temperature type expansion valve is approximately in the range of 100 Hz to 1 kHz.

  In a refrigerator, the connection of the electromagnetic valve 15 or the like is often left to an equipment supplier. For this reason, it is difficult for the manufacturer to adjust in advance the natural frequency of the Helmholtz resonator that depends on the volume of the space. Further, in the case of an electromagnetic valve integrated expansion valve in which the electromagnetic valve 15 and the temperature type expansion valve 50 are integrated, the specification can be set so that the manufacturer avoids resonance in advance. However, especially in the case of a refrigerator, since the application range is large and it is often used in a range outside the manufacturer's assumption, there is a possibility that resonance cannot be avoided in practice.

  Whether or not resonance occurs is not known unless the refrigeration cycle apparatus is actually operated. If resonance occurs as a result of the actual operation of the refrigeration cycle apparatus, the resonance may be avoided by replacing the temperature type expansion valve 50 with another type of temperature type expansion valve. However, in this case, operations such as refrigerant recovery and brazing are newly required.

  Further, there is a possibility that resonance can be avoided by adjusting the biasing force of the coil spring 63 or replacing the coil spring 63 with another coil spring having a different spring constant. However, since adjustment and replacement of the coil spring 63 are originally performed mainly for load adjustment of the refrigeration cycle apparatus, load adjustment and resonance avoidance may not be compatible.

  In the present embodiment, the volume of the space in the valve chamber 58 can be changed between when the urging force adjusting member 64 is attached and when the urging force adjusting member 84 is attached. Therefore, the natural frequency of the Helmholtz resonator can be changed by changing the urging force adjusting member 64 and the urging force adjusting member 84. Therefore, it is not necessary to add work such as refrigerant recovery and brazing, and resonance can be easily avoided.

  For example, when the refrigeration cycle apparatus is installed using the temperature type expansion valve 50 to which the urging force adjusting member 64 is attached, it is assumed that vibration and noise due to resonance occur as a result of actually operating the refrigeration cycle apparatus. In this case, the urging force adjusting member 64 is replaced with the urging force adjusting member 84. Thereby, since the volume of the space in the valve chamber 58 can be reduced, the natural frequency of the Helmholtz resonator can be increased. On the other hand, the coil spring 63 is used as it is, and the compression amount of the coil spring 63 is adjusted to the same level as the original compression amount by the urging force adjusting member 84, so that the natural frequency of the coil spring 63 does not change. Therefore, since the difference between the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be increased, resonance can be avoided.

  Further, for example, when the refrigeration cycle apparatus is installed using the temperature type expansion valve 50 to which the urging force adjusting member 84 is attached, it is assumed that vibration and noise due to resonance occur as a result of actually operating the refrigeration cycle apparatus. In this case, the urging force adjusting member 84 is replaced with the urging force adjusting member 64. Thereby, since the volume of the space in the valve chamber 58 can be increased, the natural frequency of the Helmholtz resonator can be reduced. On the other hand, the coil spring 63 is used as it is, and the compression amount of the coil spring 63 is adjusted to the same level as the original compression amount by the biasing force adjusting member 64, so the natural frequency of the coil spring 63 does not change. Therefore, since the difference between the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be increased, resonance can be avoided.

  In this way, even when the refrigeration cycle apparatus is installed on site, resonance can be easily avoided when vibration and noise are generated due to resonance. Further, since the volume of the space in the valve chamber 58 can be adjusted independently of the adjustment of the compression amount of the coil spring 63, both load adjustment and resonance avoidance can be achieved.

  As described above, the thermal expansion valve 50 according to the present embodiment includes the inlet passage 57 through which refrigerant flows from the outside, the cylindrical valve chamber 58 communicating with the inlet passage 57, and the cylinder shaft of the valve chamber 58. A valve body 54 provided on one end side in the direction and formed with an orifice 59 for depressurizing the refrigerant flowing into the valve chamber 58 and an outlet passage 60 for allowing the refrigerant depressurized by the orifice 59 to flow to the outside; 58, a valve element 61 that opens and closes the orifice 59, a coil spring 63 that is provided in the valve chamber 58 and urges the valve element 61 in the valve closing direction, and a power element 70 that drives the valve element 61. The valve chamber 58 is selectively and detachably attached to an opening 58a formed on the other end side in the cylinder axis direction, closes the other end side in the cylinder axis direction of the valve chamber 58 and urges the coil spring 63. First biasing force adjusting member 64 to be adjusted And a second urging force adjusting member 84, the volume of the space in the valve chamber 58 when the first urging force adjusting member 64 is attached to the opening 58a, and the second urging force adjusting member 64 to the opening 58a. The volume of the space in the valve chamber 58 when the force adjusting member 84 is attached is different from each other.

  According to this configuration, the volume of the space in the valve chamber 58 can be changed between when the urging force adjusting member 64 is attached and when the urging force adjusting member 84 is attached. Therefore, vibration and noise due to resonance can be suppressed by changing the urging force adjusting member 64 and the urging force adjusting member 84.

  Further, in the temperature type expansion valve 50 according to the present embodiment, each of the first urging force adjusting member 64 and the second urging force adjusting member 84 has a bottom portion (for example, an urging force adjusting member) that supports the coil spring 63. 64 bottom 64a, urging force adjusting member 84 bottom 84a) and a cylindrical portion protruding from the bottom along the outer periphery of coil spring 63 (for example, urging force adjusting member 64 cylindrical portion 64b, urging force adjusting member 84 cylinder). The second urging force adjusting member 84 has a protruding portion 84f protruding from the bottom along the inner periphery of the coil spring 63, and the first urging force adjusting member 84b). No protrusion 64 protrudes from the bottom along the inner periphery of the coil spring 63 or protrudes from the bottom along the inner periphery of the coil spring 63 and has a smaller volume than the protrusion 84f. Even if you have There.

  According to this configuration, while preventing the contact interference with the movable part in the valve chamber 58 and fretting wear, the inside of the valve chamber 58 is different between when the biasing force adjusting member 64 is attached and when the biasing force adjusting member 84 is attached. The volume of the space can be changed.

Embodiment 2. FIG.
A temperature type expansion valve according to Embodiment 2 of the present invention will be described. FIG. 5 is a cross-sectional view showing a configuration of the temperature type expansion valve 50 according to the present embodiment. In addition, about the component which has the function and effect | action same as Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 5, the temperature type expansion valve 50 according to the present embodiment includes a valve body 61 and a valve body 81 that are selectively and detachably attached in the valve chamber 58. In the configuration shown in FIG. 5, the valve body 61 is attached in the valve chamber 58, and the valve body 81 is removed from the valve chamber 58. In FIG. 5, a white double arrow between the valve body 61 and the valve body 81 indicates that the valve body 61 and the valve body 81 are alternatively attached. Both the valve body 61 and the valve body 81 can be attached and detached via the opening 58 a of the valve chamber 58.

  For example, the valve body 61 and the valve body 81 have the same external dimensions. That is, the axial length (the vertical dimension in FIG. 5) and the entire outer diameter (the horizontal dimension in FIG. 5) of the valve body 61 and the valve body 81 are the same. Moreover, since the shape of the taper surfaces 61a and 81a in the valve body 61 and the valve body 81 is the same, the valve body 61 and the valve body 81 have the same valve opening characteristic (characteristic of the valve opening degree with respect to the lift amount). ing. Further, the valve body 61 and the valve body 81 are formed of the same material.

  The valve body 61 of this example has a solid structure with no cavity inside. On the other hand, the valve body 81 of this example has a hollow structure provided with a hollow portion 81b formed inside, and a communication portion 81c that communicates the hollow portion 81b with the outside (for example, the space in the valve chamber 58). Have. Thereby, the valve body 61 and the valve body 81 are different from each other in volume and mass. The cavity 81b has, for example, a spheroid shape. An open end 81 d of the communication portion 81 c is provided on the outer peripheral surface of the valve body 81. The open end 81d may be provided at another position of the valve body 81 excluding the tapered surface 81a.

  The volume of the space in the valve chamber 58 when the valve body 81 is attached is a fraction of the volume of the cavity 81b and the communication portion 81c than the volume of the space in the valve chamber 58 when the valve body 61 is attached. Only get bigger.

  For example, when the refrigeration cycle apparatus is installed using the temperature type expansion valve 50 to which the valve body 61 is attached, it is assumed that vibration and noise due to resonance occur as a result of actually operating the refrigeration cycle apparatus. In this case, the valve body 61 is replaced with the valve body 81. Thereby, since the volume of the space in the valve chamber 58 can be increased, the natural frequency of the Helmholtz resonator can be reduced. On the other hand, since the valve body 81 has a smaller mass than the valve body 61, the natural frequency of the coil spring 63 is increased. Therefore, since the difference between the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be increased, resonance can be avoided.

  Further, for example, when the refrigeration cycle apparatus is installed using the temperature type expansion valve 50 to which the valve body 81 is attached, it is assumed that vibration and noise due to resonance occur as a result of actually operating the refrigeration cycle apparatus. In this case, the valve body 81 is replaced with the valve body 61. Thereby, since the volume of the space in the valve chamber 58 can be reduced, the natural frequency of the Helmholtz resonator can be increased. On the other hand, since the valve body 61 has a larger mass than the valve body 81, the natural frequency of the coil spring 63 is reduced. Therefore, since the difference between the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be increased, resonance can be avoided.

  As described above, in the present embodiment, by replacing the valve body 61 and the valve body 81, the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be changed in opposite directions. it can. Therefore, according to the present embodiment, resonance can be avoided more reliably than in the first embodiment.

  As described above, the thermal expansion valve 50 according to the present embodiment includes the inlet passage 57 through which refrigerant flows from the outside, the cylindrical valve chamber 58 communicating with the inlet passage 57, and the cylinder shaft of the valve chamber 58. A valve body 54 provided on one end side in the direction and formed with an orifice 59 for depressurizing the refrigerant flowing into the valve chamber 58 and an outlet passage 60 for allowing the refrigerant depressurized by the orifice 59 to flow to the outside; A first valve body 61 and a second valve body, which are selectively and detachably attached to the valve chamber 58 through an opening 58a formed on the other end side in the cylinder axial direction of 58, and open and close the orifice 59. 81, a coil spring 63 provided in the valve chamber 58 and biasing the first valve body 61 or the second valve body 81 in the valve closing direction, and the first valve body 61 or the second valve body 81. Is detachably attached to the power element 70 for driving and the opening 58a. And an urging force adjusting member 64 that adjusts the urging force of the coil spring 63 and closes the other end of the valve chamber 58 in the cylinder axis direction, and the valve chamber 58 when the first valve body 61 is attached. The volume of the inner space and the volume of the space in the valve chamber 58 when the second valve body 81 is attached are different from each other.

  According to this configuration, the volume of the space in the valve chamber 58 can be changed between when the valve body 61 is attached and when the valve body 81 is attached. Therefore, vibration and noise due to resonance can be suppressed by replacing the valve body 61 and the valve body 81.

  Further, in the temperature type expansion valve 50 according to the present embodiment, the first valve body 61 and the second valve body 81 have the same outer dimensions, and the first valve body 61 is solid. The second valve body 81 has a hollow portion 81b formed inside, and a communication portion 81c that communicates the hollow portion 81b with the outside (for example, the space in the valve chamber 58). You may have.

  According to this configuration, by replacing the valve body 61 and the valve body 81, the natural frequency of the Helmholtz resonator and the natural frequency of the coil spring 63 can be changed in opposite directions. Therefore, vibration and noise due to resonance can be more reliably suppressed.

Other embodiments.
The present invention is not limited to the above embodiment, and various modifications can be made.
For example, the temperature type expansion valve 50 according to the first embodiment includes two types of biasing force adjusting members 64 and 84 in order to change the volume of the space in the valve chamber 58 in two stages. The invention is not limited to this. The temperature type expansion valve 50 may have three or more types of biasing force adjusting members in order to change the volume of the space in the valve chamber 58 in three or more stages.

  Further, the thermal expansion valve 50 according to the second embodiment has two types of valve bodies 61 and 81 in order to change the volume of the space in the valve chamber 58 in two stages. It is not limited to this. The temperature type expansion valve 50 may have three or more types of valve bodies in order to change the volume of the space in the valve chamber 58 in three or more stages.

  Moreover, in the said embodiment, although the solenoid valve 15 and the temperature type expansion valve 50 are provided separately, the solenoid valve integrated expansion valve with which the solenoid valve and the temperature type expansion valve were integrated may be used. .

  In addition, the above embodiments and modifications can be implemented in combination with each other.

  DESCRIPTION OF SYMBOLS 10 Refrigerant circuit, 11 Compressor, 12 Condenser, 13 Liquid reservoir, 14 Supercooler, 15 Solenoid valve, 16 Evaporator, 17 Accumulator, 18 Heat source machine, 19 Blower, 20 Liquid pipe, 21 Gas pipe, 50 Temperature type Expansion valve, 51 Temperature sensing tube, 52 Capillary tube, 53 Pressure equalizing tube, 54 Valve body, 55 Inlet piping, 56 Outlet piping, 57 Inlet passage, 58 Valve chamber, 58a Opening, 59 Orifice, 60 Outlet passage, 61 Valve body , 61a Tapered surface, 62 Support member, 63 Coil spring, 64 Energizing force adjustment member, 64a Bottom portion, 64b Cylindrical portion, 64c Screw portion, 64d Slit, 64e Seal groove, 64f Support surface, 65 Seal member, 66 Cap, 66a Screw Part, 70 power element, 71 piping, 72 insertion hole, 73 lower pressure chamber, 74 operating rod, 7 Stopper, 76 Upper lid, 77 Lower lid, 78 Diaphragm, 79 Upper pressure chamber, 81 Valve body, 81a Tapered surface, 81b Hollow portion, 81c Communication portion, 81d Open end, 84 Biasing force adjusting member, 84a Bottom portion, 84b Cylindrical portion, 84c Screw part, 84d Slit, 84e Seal groove, 84f Projection part.

Claims (4)

An inlet passage through which refrigerant flows in from the outside, a cylindrical valve chamber communicating with the inlet passage, an orifice provided in one end of the valve chamber in the cylinder axial direction, and depressurizing the refrigerant flowing into the valve chamber; An outlet passage through which the refrigerant decompressed by the orifice flows out to the outside, and a valve body formed with,
A valve body provided in the valve chamber for opening and closing the orifice;
A coil spring provided in the valve chamber and biasing the valve body in a valve closing direction;
A power element for driving the valve body;
It is alternatively and detachably attached to an opening formed on the other end side in the cylinder axis direction of the valve chamber, and closes the other end side in the cylinder axis direction of the valve chamber and adjusts the biasing force of the coil spring. A first urging force adjusting member and a second urging force adjusting member;
With
The volume of the space in the valve chamber when the first biasing force adjustment member is attached and the volume of the space in the valve chamber when the second biasing force adjustment member is attached are different from each other. Expansion valve. Each of the first urging force adjusting member and the second urging force adjusting member has a bottom portion that supports the coil spring, and a cylindrical portion that protrudes from the bottom portion along the outer periphery of the coil spring. And
One of the first urging force adjusting member or the second urging force adjusting member has a first protrusion protruding from the bottom along the inner periphery of the coil spring,
The other of the first urging force adjusting member or the second urging force adjusting member does not have a protruding portion protruding from the bottom along the inner periphery of the coil spring, or the inside of the coil spring. The temperature type expansion valve according to claim 1, further comprising a second projecting portion projecting from the bottom portion along a circumference and having a smaller volume than the first projecting portion. An inlet passage through which refrigerant flows in from the outside, a cylindrical valve chamber communicating with the inlet passage, an orifice provided in one end of the valve chamber in the cylinder axial direction, and depressurizing the refrigerant flowing into the valve chamber; An outlet passage through which the refrigerant depressurized by the orifice flows out, and a valve body formed;
A first valve body and a second valve body, which are selectively and detachably attached to the valve chamber, and open and close the orifice;
A coil spring provided in the valve chamber for biasing the first valve body or the second valve body in a valve closing direction;
A power element for driving the first valve body or the second valve body;
A biasing force adjusting member that is detachably attached to an opening formed on the other end side in the cylinder axis direction of the valve chamber, closes the other end side in the cylinder axis direction of the valve chamber, and adjusts the biasing force of the coil spring. When,
With
The volume of the space in the valve chamber when the first valve body is attached is different from the volume of the space in the valve chamber when the second valve body is attached. The first valve body and the second valve body have the same outer dimensions,
One of the first valve body or the second valve body has a solid structure,
The other of said 1st valve body or said 2nd valve body has a cavity part formed in the inside, and a communication part which makes the said cavity part and the exterior communicate. Temperature expansion valve.

Images