JP2017219167A - Composite valve and refrigeration cycle device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a composite valve that can configure a simple piping system and change a refrigerant flow rate in a multistep manner depending on ambient temperature while reducing assembly cost, component cost and the like, in a refrigeration cycle device such as an air conditioner, and to provide a refrigeration cycle device including the same.SOLUTION: In a composite valve, a main valve body 10 where a stationary throttle valve 17 and a plurality of differential pressure valves 20A, 20B each having different valve opening pressure is provided in parallel is disposed in an airtight manner in a passage member 7 constituting part of a refrigerant passage.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a composite valve that can change the flow rate stepwise according to the differential pressure before and after the valve (inlet side and outlet side), and in particular, in a refrigeration cycle apparatus dedicated to cooling or a refrigeration cycle apparatus for both cooling and heating. The present invention relates to a composite valve suitable for changing a refrigerant flow rate stepwise and a refrigeration cycle apparatus including the same.

  A conventional general air conditioner for cooling is usually provided with a compressor, an outdoor heat exchanger (condenser), an indoor heat exchanger (evaporator), and a capillary tube as a fixed throttle, and a pipe (pipe) between each device. ), Etc., and during operation, high-temperature and high-pressure refrigerant is led from the compressor to the outdoor heat exchanger, where it is condensed by exchanging heat with outdoor air. The high-pressure refrigerant is decompressed by this capillary tube, and the decompressed low-pressure refrigerant is introduced into the indoor heat exchanger, where it heats (cools) the room air and evaporates. The low-temperature and low-pressure refrigerant is returned from the indoor heat exchanger to the suction side of the compressor.

  Such a cooling-only air conditioner has the advantage that it is simpler in structure and can be provided at a lower price than a cooling / heating air-conditioning air conditioner. In other words, there is a desire to change the refrigerant flow rate from the high pressure side (outdoor heat exchanger) toward the low pressure side (indoor heat exchanger) as the outside air temperature increases.

  In this case, in order not to impair the advantages of the cooling-only air conditioner with a simple configuration and low price, it is not required to change the refrigerant flow rate linearly according to the outside air temperature. It is considered that it is only necessary to change in a stepwise manner (about 3 steps).

  In order to meet this demand, as a conventional technique, focusing on the fact that the outside air temperature and the pressure on the high pressure side have a correlation (the outside air temperature rise ≈ the high pressure side pressure rise), for example, the bypass passage is bypassed to bypass the capillary tube. It is proposed to install a differential pressure valve that opens when the differential pressure across the valve (inlet side and outlet side) exceeds a predetermined pressure, in other words, to provide a differential pressure valve in parallel with the capillary tube. ing.

JP-A-61-237981

  By providing a differential pressure valve in parallel with the capillary tube as described above, when the differential pressure is equal to or lower than a predetermined pressure, that is, when the outside air temperature is relatively low, the refrigerant flows only through the capillary tube, and the differential pressure is less than the predetermined pressure. When the temperature is high, that is, when the outside air temperature is relatively high, the differential pressure valve is opened and the refrigerant is allowed to flow through the differential pressure valve in addition to the capillary tube. Therefore, the refrigerant flow rate can be changed in two stages according to the outside air temperature.

  However, in such a conventional technique, the refrigerant flow rate can be changed only in two stages, and it is required to separately provide a bypass passage that bypasses the capillary tube, and a differential pressure valve is provided in the bypass passage. Since it is necessary to incorporate it, the piping system becomes complicated, and the assembly cost, parts cost, etc. increase.

  In the above prior art, in order to change the refrigerant flow rate in multiple stages (for example, 3 stages or more) according to the outside air temperature, two or more bypass passages bypassing the capillary tube are provided, and the valve opening pressure is set in each bypass passage. Therefore, there is a problem that the piping system becomes more complicated, and the assembly cost and parts cost increase further.

  Note that Patent Document 1 describes a cooling-only air conditioner (local cooling unit) in which a differential pressure valve is provided in parallel with a capillary tube. However, the differential pressure valve in this local cooling unit has excessive pressure on the high pressure side. When the pressure becomes high, it functions as a relief valve that releases the pressure on the high pressure side to the low pressure side, and is not for changing the refrigerant flow rate according to the outside air temperature.

  The cooling-only air conditioner has been described above. However, for a cooling / heating air conditioner capable of switching between the cooling operation and the heating operation, when the refrigerant flow rate is changed in multiple stages according to the outside air temperature, the same cost as described above is used. It is inevitable that problems related to the above will occur.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to simply configure the piping system in an refrigeration cycle apparatus such as an air conditioner, while keeping assembly costs and component costs low, and the like. It is an object of the present invention to provide a composite valve capable of changing the refrigerant flow rate in multiple stages according to the temperature and a refrigeration cycle apparatus including the same.

  In order to achieve the above object, a first aspect of the composite valve according to the present invention is characterized in that a plurality of differential pressure valves having different valve opening pressures are provided in parallel in a single passage member.

  A second aspect of the composite valve according to the present invention includes a passage member and a main valve main body disposed in the passage member, and the main valve main body includes a plurality of different fixed throttle holes and different valve opening pressures. A differential pressure valve is provided in parallel.

  A third aspect of the composite valve according to the present invention includes a passage member and a pair of main valve bodies disposed opposite to each other in the passage member, and each of the pair of main valve bodies has a valve opening pressure. A plurality of different differential pressure valves and through valve ports are provided in parallel, and a differential pressure drive type is provided between the pair of main valve bodies to selectively open and close the through valve ports in the pair of main valve bodies. The check valve body is movably disposed.

  On the other hand, the refrigeration cycle apparatus for cooling only according to the present invention is characterized in that the composite valve of the first aspect or the second aspect is interposed in a refrigerant passage connecting the outdoor heat exchanger and the indoor heat exchanger. .

  The cooling / heating refrigeration cycle apparatus according to the present invention is characterized in that the composite valve of the third aspect is interposed in a refrigerant passage connecting the outdoor heat exchanger and the indoor heat exchanger.

  In the composite valve according to the first aspect of the present invention, since a plurality of differential pressure valves having different valve opening pressures are provided in parallel in a single passage member, the flow rate of refrigerant passing through the composite valve is set to 2 by the differential pressure valve. The number of differential pressure valves can be changed stepwise according to the number of differential pressure valves, for example, two stages in the case of three and three stages in the case of three.

  Here, as described above, since the outside air temperature and the pressure on the high pressure side are correlated, the composite valve of the first aspect is, for example, a refrigerant passage connecting an outdoor heat exchanger and an indoor heat exchanger in a cooling-only air conditioner. In addition, by interposing in place of the capillary tube, it becomes possible to change the refrigerant flow rate stepwise according to the outside air temperature.

  In this way, the composite valve of the first aspect is used in, for example, a cooling air conditioner instead of a capillary tube, thereby providing a bypass passage that bypasses the capillary tube as in the prior art and incorporating a differential pressure valve in the bypass passage. Compared with measures, especially when the refrigerant flow rate is changed in multiple stages (for example, three stages or more) according to the outside air temperature, the piping system can be simply configured, and the assembly cost, parts cost, etc. are effective. Can be suppressed.

  In the composite valve according to the second aspect of the present invention, the main valve body disposed in the passage member is provided with a fixed throttle hole and a plurality of differential pressure valves having different valve opening pressures in parallel. In addition to obtaining substantially the same effect as the composite valve, the number of differential pressure valves can be reduced by one from the composite valve of the first mode (for example, if the refrigerant flow rate is to be changed in three stages, In addition, since a plurality of differential pressure valves are provided in a common main valve body, each differential pressure valve does not require a case portion that forms an inlet, an outlet, a valve chamber, or the like. For this reason, compared with the composite valve of the first aspect, the number of parts can be reduced, and assembly costs, parts costs, and the like can be further suppressed.

  The composite valve according to the third aspect of the present invention includes a pair of main valve bodies in which a plurality of differential pressure valves and through valve ports having different valve opening pressures are provided in parallel, and the through valves in the pair of main valve bodies. Since the mouth is selectively opened and closed by a check valve body movably disposed between the pair of main valve bodies, the composite valve of the third aspect corresponds to both flows, that is, It can be interposed in the refrigerant passage whose flow direction is switched, and in any case of the flow direction, the refrigerant flow rate can be changed in a stepwise manner as in the composite valve of the first aspect and the second aspect.

  Therefore, the composite valve of the third aspect can be interposed in the refrigerant passage connecting the outdoor heat exchanger and the indoor heat exchanger, for example, in a cooling / heating air conditioner, instead of the expansion valve corresponding to both flows. In this case, the refrigerant flow rate can be changed stepwise according to the outside air temperature during cooling operation, and the refrigerant flow rate can be changed stepwise according to the differential pressure before and after the valve (inlet and outlet) also during heating operation. Can save energy and so on.

The 1st Example of the compound valve which concerns on this invention is shown, (A) is a longitudinal cross-sectional view, (B) is XX arrow sectional drawing of (A). (A) is an enlarged view of a differential pressure valve portion in the composite valve shown in FIG. 1 (A), (B) is a cross-sectional view taken along line JJ of (A), and (C) is a valve body of the differential pressure valve. (D) is a valve closing state, (E) is a valve opening state, respectively (B) U-U arrow sectional drawing. The graph which shows the relationship between the differential pressure | voltage before and behind a valve, and a refrigerant | coolant flow rate. The schematic block diagram which shows an example of the air conditioner only for cooling using the compound valve of 1st Example shown by FIG. (A), (B) is a figure where each is provided for description of the modification of the compound valve of 1st Example. Sectional drawing which shows the other examples of the differential pressure | voltage valve used with the compound valve of 1st Example. Fig. 2 shows a second embodiment of the composite valve according to the present invention, wherein (A) is a left-to-right flow, and (B) is a vertical cross-sectional view of the right-to-left flow (the main valve main body is a diagram). 8 (A) is a cross-sectional view taken along the line ZZ, and the check valve body portion is a cross-sectional view taken along the line ZZ 'in FIG. 8 (A). 7A is a right side view of the composite valve of the second embodiment shown in FIG. 7, FIG. 7B is a cross-sectional view taken along the line Y-Y in FIG. 7A, and FIG. (D) is a VV arrow sectional view of (B) at the time of the flow from left to right. The schematic block diagram which shows an example of the air conditioner for both the heating and cooling using the composite valve of 2nd Example shown by FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

  In each drawing, gaps formed between members, separation distances between members, etc. may be exaggerated for easy understanding of the invention and for convenience of drawing. is there. Further, in this specification, descriptions representing positions and directions such as up and down, left and right, and front and rear are given for the sake of convenience in accordance with the drawings in order to avoid complicated explanation, and the positions and directions in the actual use state. Does not necessarily mean

[First embodiment]
1A and 1B show a first embodiment of a composite valve according to the present invention, in which FIG. 1A is a longitudinal sectional view and FIG. 1B is a sectional view taken along line XX in FIG.

  As shown in FIG. 4, the composite valve 1 according to the present embodiment includes an outdoor heat exchanger 120 and an indoor heat in a cooling-only air conditioner 100 including a compressor 110, an outdoor heat exchanger 120, and an indoor heat exchanger 130. A passage member 7 constituting a part of the refrigerant passage 105 and a main valve disposed so as to hermetically partition the passage member 7 are interposed in a refrigerant passage 105 connecting the exchanger 130. A main body 10.

  The passage member 7 is made of, for example, a copper pipe having a predetermined length, and pipes constituting the refrigerant passage 105 are connected to both ends thereof.

  1, the main valve body 10 is made of, for example, brass and has a short cylindrical shape having an outer diameter substantially the same as the inner diameter of the passage member 7, and has a rectangular cross section at the center of the outer periphery. An annular groove 16 is formed. The main valve body 10 is assembled to the passage member 7 by caulking (for example, roll caulking) so as to squeeze a part of the outer periphery of the passage member 7 (caulking portion 9). A part is pushed into the annular groove 16 and the outer peripheral surface of the main valve body 10 and the inner peripheral surface of the passage member 7 are brought into close contact with each other.

  The main valve body 10 is provided with a fixed throttle hole 17 serving as a capillary tube used in a conventional air conditioner for conventional cooling at the center (on the center line O of the passage member 7). Two differential pressure valves 20 </ b> A and 20 </ b> B are provided in parallel to the fixed throttle hole 17 at an angular interval of 180 ° on a concentric circle on the side. In other words, the main throttle body 10 is provided with the fixed throttle hole 17 and the two differential pressure valves 20A and 20B in parallel. The fixed throttle hole 17 is formed as a stepped through hole whose inner diameter changes in two stages, but it goes without saying that it may be a through hole whose inner diameter does not change.

  The two differential pressure valves 20A and 20B differ only in their valve opening pressures (details will be described later) and have almost the same basic configuration. As shown in FIG. In order from the left side (high pressure side) to the valve body 10, a valve chamber (inlet) 21 and a valve chamber 23 into which a valve body 25 is slidably inserted, and a four-leaf or cross-shaped spring receiving member 27 are press-fitted and fastened. An annular mounting groove 24A that is mounted and fixed by caulking or the like is provided with a step. An outlet 22 having substantially the same diameter as the valve port 21 is provided at the center of the spring receiving member 27.

  The valve body 25 slidably inserted in the valve chamber 23 includes a conical portion 25a at the distal end (left end portion) and the cone, as can be understood by referring to FIGS. 2 (A) to (E). A cylindrical body 25b having four corners in a plan view arc-shaped inscribed portion 25c that is slidably inscribed in the valve chamber 23 and is continuously provided on the bottom side of the cylindrical portion 25a. A circular opening 25d for smoothly circulating the refrigerant is formed on two opposing surfaces of the four flat surfaces (flat surface portions other than the inscribed portion 25c). An arcuate flat surface portion 25e that is flush with the flat surface portion other than the inscribed portion 25c in the body portion 25b is formed on the bottom side of the conical portion 25a. Therefore, a flow passage is formed between portions (25a, 25b, 25e) of the valve body 25 other than the inscribed portion 25c and the inner peripheral surface of the valve chamber 23.

  In this example, an inscribed portion 25 c having a circular arc shape in plan view that is slidably inscribed in the valve chamber 23 provided in the main valve body 10 is provided on the body portion 25 b provided on the bottom side of the valve body 25. Although it is provided at two places, it is a matter of course that it may be two places or more, preferably three places or more.

  As a biasing member that biases the valve body 25 in the valve closing direction (in the direction of the valve port 21) between the valve body 25 (the end face on the conical portion 25a side in the body portion 25b) and the spring receiving member 27. The compression coil spring 26 of FIG.

  In the differential pressure valves 20 </ b> A and 20 </ b> B having such a configuration, the valve opening pressure is changed according to the set load (biasing force) of the compression coil spring 26. In this example, the set load of the compression coil spring 26 is the depth of the annular mounting grooves 24A and 24B to which the spring receiving member 27 is mounted and fixed by press-fitting or the like, that is, as shown in FIG. The length (total height) La and Lb of the compression coil spring 26 in the state is determined. In this example, the annular mounting groove 24B of the differential pressure valve 20B is deeper than the annular mounting groove 24A of the differential pressure valve 20A by h, so that the length (total height) of the compression coil spring 26 is the differential pressure valve 20B ( Lb) is shorter (by h) than the differential pressure valve 20A (La). Therefore, the set load of the compression coil spring 26 of the differential pressure valve 20B is larger than the set load of the compression coil spring 26 of the differential pressure valve 20A, so that the valve opening pressure is larger in the differential pressure valve 20B than in the differential pressure valve 20A.

  As described above, in the composite valve 1 of the present example, the difference is obtained only by changing the depths of the annular mounting grooves 24A and 24B using common parts (the valve body 25, the compression coil spring 26, and the spring receiving member 27). Since the valve opening pressures of the pressure valves 20A and 20B can be changed, parts costs and assembly costs can be considerably reduced.

  The valve opening pressures of the differential pressure valves 20A and 20B may be adjusted, for example, by changing the spring coefficient of the compression coil springs 26 of the differential pressure valves 20A and 20B, or the shape of the valve body 25 and the spring receiving member 27. You may adjust by changing.

Under such a configuration, the refrigerant flow rate changes as shown in FIG. 3 with respect to the differential pressure before and after the valve. That is,
(i) When the high pressure side pressure is low and the load is low, the differential pressure valves 20A and 20B remain closed (see FIG. 2D), the refrigerant flows only through the fixed throttle hole 17, and the refrigerant flow rate becomes the differential pressure. It increases gradually according.
(ii) When the high-pressure side pressure increases from a low pressure to an intermediate pressure (that is, from a low load state to an intermediate load state), the differential pressure valve 20A having a small valve opening pressure opens, so that the refrigerant is fixed to the fixed throttle hole 17. In addition, the flow path between the valve port 21 on the differential pressure valve 20A side → the part (25a, 25b, 25e) other than the inscribed portion 25c in the valve body 25 and the inner peripheral surface of the valve chamber 23 → the circular opening 25d When the gap between the valve body 25 (the bottom end portion of the body portion 25b) and the spring receiving member 27 (the valve body 25 (the bottom end portion of the body portion 25b) contacts the spring receiving member 27, a circular opening is provided. 25d) → flowed through the outlet 22 of the spring receiving member 27 (see FIG. 2E), and the refrigerant flow rate rapidly increases.
(iii) When the high-pressure side pressure is medium load, the refrigerant flows through the differential pressure valve 20A in addition to the fixed throttle hole 17, so the refrigerant flow rate gradually increases according to the differential pressure.
(iv) When the high-pressure side pressure increases from the medium pressure to the high pressure (that is, from the medium load state to the high load state), the differential pressure valve 20B having a large valve opening pressure is opened in addition to the differential pressure valve 20A. Is supplied to the differential pressure valve 20B in addition to the fixed throttle hole 17 and the differential pressure valve 20A in the same manner as the above-described differential pressure valve 20A, and the refrigerant flow rate rapidly increases.
(v) When the high pressure side pressure is high and the load is high, the refrigerant flows through the differential pressure valve 20B in addition to the fixed throttle hole 17 and the differential pressure valve 20A, so the refrigerant flow rate gradually increases according to the differential pressure.

  Thus, in the composite valve 1 of the present embodiment, the refrigerant flow rate flowing through the passage member 7 (refrigerant passage 105) can be changed in three stages according to the high-pressure side pressure, in other words, according to the outside air temperature. Therefore, energy saving or the like can be achieved in the cooling-only air conditioner 100 in which the composite valve 1 is used.

  Further, by using the composite valve 1 of the present embodiment in the cooling-only air conditioner 100 instead of the capillary tube, a bypass passage that bypasses the capillary tube is provided and a differential pressure valve is incorporated in the bypass passage as in the prior art. Thus, the piping system can be simply configured, and assembly costs, parts costs, and the like can be effectively suppressed.

  Further, by providing the fixed throttle hole 17 in the main valve body 10, the required number of differential pressure valves can be reduced by one (if the refrigerant flow rate is to be changed in three stages, only two differential pressure valves are required), Since the two differential pressure valves 20A and 20B are provided in the common main valve body 10, the differential pressure valves 20A and 20B do not require a case portion that forms an inlet, an outlet, a valve chamber, or the like. For this reason, the number of parts can be reduced, and assembly costs, parts costs, and the like can be further suppressed.

  In the first embodiment, the main valve body 10 is provided with the fixed throttle hole 17 and the two differential pressure valves 20A and 20B in parallel to change the refrigerant flow rate in three stages. For example, as shown in FIG. 5A, there are three differential pressure valves 20 having different valve opening pressures (in the example shown, three at 120 ° angular intervals on a concentric circle). The refrigerant flow rate is increased and changed in four stages, or, as shown in FIG. 5B, four differential pressure valves 20 having different valve opening pressures (in the example shown, an angle of 90 ° on a concentric circle). It is also possible to increase the refrigerant flow rate to five levels by increasing the number to four).

  As the differential pressure valve, a spherical ball valve body 28 as shown in FIG. 6 may be used instead of the conical valve body at the tip as in the above embodiment. The spring receiving member 27 of the differential pressure valve 20E using the ball valve body 28 is provided with a stopper 27a for the compression coil spring 26 so as to protrude (so as to surround the outer periphery of the compression coil spring 26).

  Further, the fixed throttle hole 17 of the main valve body 10 may be omitted. In this case, the required number of differential pressure valves cannot be reduced by one as in the above embodiment, but the flow rate of refrigerant passing through the composite valve can be reduced in two stages when there are two differential pressure valves, and in three stages when there are three differential pressure valves. Thus, it can be changed stepwise according to the number of differential pressure valves.

[Second Embodiment]
7A and 7B show a second embodiment of the composite valve according to the present invention, in which FIG. 7A is a longitudinal sectional view of the flow from left to right, and FIG. 7B is a longitudinal sectional view of the flow from right to left. In FIG. 7, the main valve bodies 11 and 12 are cross-sectional views taken along the line ZZ in FIG. 8A, and the check valve body 30 is a cross-sectional view taken along the line ZZ ′ in FIG. is there.

  In the composite valve 2 of the second embodiment, portions corresponding to the respective parts of the composite valve 1 of the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  The composite valve 2 of the second embodiment shown in the figure is arranged in a cooling / heating air conditioner 200 as shown in FIG. 9 to be described later, in the refrigerant passage 205 connecting the outdoor heat exchanger 220 and the indoor heat exchanger 230, instead of the expansion valve. A passage member 8 corresponding to the passage member 7 of the first embodiment, and a pair of main valve bodies 11, 12 disposed facing each other so as to hermetically partition the passage member 8. Is provided. Each of the pair of main valve bodies 11 and 12 can be understood by referring to FIG. 8 in addition to FIG. 7, and the fixed throttle hole 17 similar to that of the first embodiment and two different valve opening pressures. The differential pressure valves 20A and 20B are provided in parallel, and a through valve port 15 is provided in parallel to them.

  In this example, the fixed throttle hole 17 and the two differential pressure valves 20A and 20B are provided concentrically at an angular interval of about 120 ° from each other, and the through valve port 15 is formed of the main valve bodies 11 and 12. (Refer to FIG. 8A), the effective passage cross-sectional area of this through valve port 15 provides the maximum required flow rate that should flow through the passage member 8. It is larger than the effective passage area.

  In the passage member 8, between the pair of main valve bodies 11-12 opposed to each other, the through valve ports 15 and 15 in the pair of main valve bodies 11 and 12 are selectively opened and closed (through the main valve body 11). When the valve port 15 is open, the through valve port 15 of the main valve body 12 is closed. Conversely, when the through valve port 15 of the main valve body 11 is closed, the through valve port of the main valve body 12 is closed. 15 is opened), a differential pressure drive type check valve body 30 is slidably disposed in a direction along the center line O.

  As can be understood with reference to FIGS. 8B and 8C, the check valve body 30 is provided between the conical portions 30a provided at both ends (left and right) and the conical portions 30a. In addition, the cylindrical member 30b is formed by a relatively long prismatic body 30b having four arcuate inscribed portions 30c in plan view that are slidably inscribed on the inner peripheral surface of the passage member 8. On the 30b side, a flat surface portion 30d other than the inscribed portion 30c in the body portion 30b and an arcuate flat surface portion 30e flush with each other are formed. Therefore, a flow passage is formed between portions (30a, 30d, 30e) of the check valve body 30 other than the inscribed portion 30c and the inner peripheral surface of the passage member 8.

  In the present example, four inscribed portions 30c having a circular arc in plan view that are slidably inscribed in the passage member 8 are provided in the body portion 30b. Of course, it is sufficient if there are at least three, preferably at least three.

  In the composite valve 2 of this example, the check valve body 30 is pushed rightward by the refrigerant when the left to right flow (cooling operation) as shown in FIG. The through valve port 15 is opened and the through valve port 15 of the main valve body 11 is closed.

  During this flow from left to right, the differential pressure valves 20A and 20B provided on the left main valve body 12 are always closed, and are provided on the right main valve body 11 as in the first embodiment. The fixed throttle hole 17 and the differential pressure valves 20A and 20B allow the refrigerant flow rate (the through valve port 15 and the fixed throttle hole 17 provided in the left main valve main body 12 to be adjusted in the check valve body 30) with respect to the differential pressure before and after the valve. The flow rate of the refrigerant that has flowed through the flow passage between the portions (30a, 30d, 30e) other than the contact portion 30c and the inner peripheral surface of the passage member 8) changes in three stages as shown in FIG. (See also FIG. 8D).

  On the other hand, at the time of right-to-left flow (heating operation) as shown in FIG. 7B, the check valve body 30 is pushed leftward by the refrigerant to open the through valve port 15 of the main valve body 11. At the same time, the through valve port 15 of the main valve body 12 is closed.

  During the flow from right to left, the differential pressure valves 20A and 20B provided in the right main valve body 11 are always closed, and the fixed throttle hole 17 and the differential pressure valves 20A and 20B provided in the left main valve body 12 are closed. Therefore, the flow rate of the refrigerant with respect to the differential pressure before and after the valve (through valve port 15 and fixed throttle hole 17 provided on the right main valve body 11 → the portion other than the inscribed portion 30c in the check valve body 30 (30a, 30d , 30e) and the flow rate of the refrigerant flowing through the flow passage between the inner peripheral surface of the passage member 8) changes in three stages as shown in FIG.

  The composite valve 2 of the present embodiment having the configuration as described above is for both cooling and heating provided with a compressor 210, an outdoor heat exchanger 220, an indoor heat exchanger 230, and a four-way switching valve 240 as shown in FIG. In the air conditioner 200, a refrigerant passage 205 connecting the outdoor heat exchanger 220 and the indoor heat exchanger 230 is interposed instead of the expansion valve.

  In the cooling / heating air conditioner 200 using this composite valve 2, during the cooling operation, as shown in FIG. 9A, the discharge side high-pressure port D of the four-way switching valve 240 becomes the outdoor input / output port C, and the room The inner inlet / outlet ports E are respectively connected to the suction side low pressure port S. As a result, the refrigerant is sucked into the compressor 210, and the high-temperature and high-pressure refrigerant is led from the compressor 210 to the outdoor heat exchanger 220 via the four-way switching valve 240, where it is condensed by exchanging heat with outdoor air. The high-pressure two-phase refrigerant is introduced into the composite valve 2. The high-pressure refrigerant is decompressed by the composite valve 2, and the decompressed low-pressure refrigerant is introduced into the indoor heat exchanger 230, where it heats (cools) and evaporates with the indoor air, and evaporates from the indoor heat exchanger 230. The low-temperature and low-pressure refrigerant is returned to the suction side of the compressor 210 through the four-way switching valve 240.

  On the other hand, during heating operation, as shown in FIG. 9B, the discharge side high-pressure port D of the four-way switching valve 240 becomes the indoor side input / output port E, and the outdoor side input / output port C becomes the suction side low pressure port S. The high-temperature and high-pressure refrigerant is communicated from the compressor 210 to the indoor heat exchanger 230, where it heats (heats) and evaporates with the room air, evaporates, and becomes a high-pressure two-phase refrigerant. be introduced. The composite valve 2 decompresses the high-pressure refrigerant, and the decompressed low-pressure refrigerant is introduced into the outdoor heat exchanger 220 where it is condensed by exchanging heat with outdoor air. Is returned to the suction side of the compressor 210 via the four-way switching valve 240.

  As described above, the composite valve 2 of the second embodiment can be interposed in the refrigerant passage corresponding to both flows, that is, the flow direction can be switched. As with the composite valve 1, the refrigerant flow rate can be changed stepwise.

  Therefore, in the cooling / heating air conditioner 200, the composite valve 2 of the second embodiment can be interposed in the refrigerant passage 205 connecting the outdoor heat exchanger 220 and the indoor heat exchanger 230 in place of the conventional expansion valve. it can. In this case, the refrigerant flow rate can be changed stepwise (three steps) according to the outside air temperature during cooling operation, and the refrigerant flow rate can be changed stepwise according to the differential pressure before and after the valve during heating operation. Because it can, you can save energy.

  Even when the composite valves 1 and 2 of the first and second embodiments are used in a refrigeration cycle apparatus other than an air conditioner (for example, a refrigeration, refrigeration, or refrigerated warm-up showcase), effects such as energy saving can be obtained. Of course.

1 Compound valve (first embodiment)
2 Compound valve (second embodiment)
7 passage member (first embodiment)
8 passage member (second embodiment)
10 Main valve body (first embodiment)
11 Main valve body (second embodiment)
12 Main valve body (second embodiment)
15 Through valve port 17 Fixed throttle holes 20A, 20B Differential pressure valve 21 Valve port (inlet)
22 outlet 23 valve chamber 24A, 24B annular mounting groove 25 valve body 26 compression coil spring (biasing member)
27 Spring receiving member 30 Check valve body 100 Air conditioner for exclusive use of cooling (refrigeration cycle apparatus)
200 Cooling and heating air conditioner (refrigeration cycle equipment)

Claims (11)

  A composite valve characterized in that a plurality of differential pressure valves with different valve opening pressures are provided in parallel in a single passage member.   A passage member and a main valve body disposed in the passage member, wherein the main valve body is provided with a fixed throttle hole and a plurality of differential pressure valves having different valve opening pressures in parallel. Characteristic composite valve.   A passage member and a pair of main valve bodies disposed opposite to each other in the passage member, and each of the pair of main valve bodies includes a plurality of differential pressure valves and through valve ports having different valve opening pressures. A differential pressure drive type check valve body is movably disposed between the pair of main valve bodies so as to selectively open and close the through valve ports in the pair of main valve bodies. A composite valve characterized by   The differential pressure valve includes a valve body having a conical or spherical tip and a biasing member that biases the valve body in a valve closing direction, and the valve opening pressure changes according to the biasing force of the biasing member. 4. The composite valve according to claim 1, wherein the composite valve is configured as described above.   On the bottom side of the valve body, there is provided a rectangular tube-shaped body portion provided with two or more arc-shaped inscribed portions that are slidably inscribed in a valve chamber provided in the main valve body, An opening is formed in a portion of the body portion other than the inscribed portion, and a flow passage is formed between the portion other than the inscribed portion and the inner peripheral surface of the valve chamber. The composite valve according to claim 4.   4. The composite valve according to claim 3, wherein an effective passage cross-sectional area of the through-valve port is larger than an effective passage cross-sectional area at which a maximum required flow rate to be flowed through the passage member is obtained.   The composite valve according to claim 3, wherein the through valve port is provided on a center line of the passage member.   The check valve body is provided with conical portions at both end portions, and two or more arc-shaped inscribed portions that are slidably inscribed in the passage member are provided between the conical portions. The composite valve according to claim 3, wherein a flow passage is formed between a portion other than the inscribed portion and an inner peripheral surface of the passage member.   The composite valve according to claim 3, wherein the pair of main valve bodies are provided with fixed throttle holes in parallel with the plurality of differential pressure valves, respectively.   A refrigeration cycle apparatus, wherein the composite valve according to claim 1 or 2 is interposed in a refrigerant passage connecting the outdoor heat exchanger and the indoor heat exchanger.   4. A refrigeration cycle apparatus, wherein the composite valve according to claim 3 is interposed in a refrigerant passage connecting the outdoor heat exchanger and the indoor heat exchanger.

Images