JP4529954B2 - Vapor compression refrigeration cycle - Google Patents

Description

  The present invention uses an ejector, which is a decompression means for decompressing a fluid, and a momentum transporting pump that transports fluid by an entrainment action of a working fluid ejected at high speed, as a refrigerant decompression means and a refrigerant circulation means in a refrigeration cycle. The present invention relates to a vapor compression refrigeration cycle.

Conventionally, in the vapor compression refrigeration cycle, as described in Patent Document 1, a vapor compression refrigeration cycle having an ejector as means for reducing the pressure of the condensed refrigerant is known. The ejector includes a nozzle portion that takes in the refrigerant on one side of the refrigerant flow branched from the branch portion downstream from the radiator and ejects the refrigerant at a high speed, and a suction portion that sucks the branched refrigerant on the other side through the evaporator. And.
JP 2005-308384 A

  However, the conventional vapor compression refrigeration cycle has a problem in that the nozzle efficiency is reduced when the refrigerant guided to the inlet of the nozzle of the ejector is a supercooled liquid phase refrigerant. Furthermore, in order to improve this problem, when the refrigerant supplied to the inlet of the nozzle part is a gas-liquid two-phase flow, the refrigerant flow rate supplied to the nozzle part and the refrigerant supplied to the suction part side from the efficiency of the system It is necessary to distribute the flow rate appropriately.

  The present invention has been made in view of the above points, and a vapor compression refrigeration cycle having high efficiency by supplying a gas-liquid two-phase refrigerant appropriately distributed to each of the nozzle portion side and the suction portion side of the ejector. The purpose is to provide.

In order to achieve the above object, the following technical means are adopted. In other words, the first invention relating to the vapor compression refrigeration cycle includes a compressor (1) that sucks refrigerant and compresses it into a high-pressure refrigerant, and heat dissipation that dissipates heat of the high-pressure refrigerant discharged from the compressor (1). , A radiator (2), a first throttle means (3) for decompressing the refrigerant downstream, and a flow path for distributing the flow of refrigerant decompressed by the first throttle means (3) into a plurality of flows The flow rate distributor (10, 20, 30, 40) having a flow rate and the one refrigerant distributed by the flow rate divider (10, 20, 30, 40) are taken in and injected from the nozzle part (5a), and the high speed An ejector (5) that forms a refrigerant flow and sucks the other refrigerant from the suction part (5b) by a high-speed refrigerant flow, and the other of the other distributed by the flow distributor (10, 20, 30, 40) The refrigerant is taken in and evaporated, and the suction part (5b An evaporator (8) that emits toward includes a,
The flow distributor (10, 20, 30, 40) is a distribution channel mechanism (12, 13, 14, 22, 23, 24, 32, 33, 34, 42, 43, and the like) that distributes the refrigerant flowing into a predetermined amount. 44).

  According to the present invention, the refrigerant on the downstream side of the radiator is decompressed by the first throttling means, so that the gas-liquid two-phase refrigerant is supplied to the ejector side, and the refrigerant is distributed by the distribution flow path mechanism of the flow distributor. Thus, the gas-liquid two-phase refrigerant appropriately distributed to the nozzle part side and the suction part side of the ejector can be supplied. Thereby, the efficiency of the vapor compression refrigeration cycle provided with the ejector can be improved.

  Furthermore, the distribution flow path mechanism in the first invention is branched from the first flow path (12, 22, 32, 42) into which the refrigerant depressurized by the first throttle means (3) flows, and the first flow path. A second flow path (13, 23, 33, 43) for flowing out the refrigerant to the evaporator (8) side, and a third flow path for branching from the first flow path and for flowing the refrigerant to the ejector (5) side (14, 24, 34, 44), and the first flow passage, the second flow passage, and the third flow passage are arranged on substantially the same horizontal plane, and the flow of the second flow passage is It is preferable that the path diameter (φd2) is larger than the flow path diameter (φd1) of the first flow path and further larger than the flow path diameter (φd3) of the third flow path.

  According to this invention, the flow path diameter of the second flow path is larger than the flow path diameter of the first flow path, and the flow path diameter of the third flow path is larger than the flow path diameter of the third flow path, thereby flowing into the third flow path. It is possible to increase the efficiency of the vapor compression refrigeration cycle by reducing the refrigerant flow rate to be smaller than the refrigerant flow rate flowing into the second flow passage and reducing the refrigerant flow rate flowing into the nozzle portion of the ejector.

  According to a second invention, the flow distributor according to any one of the above inventions has swirl flow forming means (13, 23, 25, 33, 35, 43, 45, 28) for swirling the flow of the distributed refrigerant. It is preferable.

  According to the present invention, since the swirl flow forming means is provided, the liquid refrigerant can be formed into a swirl flow, so that the relative refrigerant flow rate in the flow path is increased, and the boiling of the liquid refrigerant is promoted to increase the vapor. The efficiency of the compression refrigeration cycle can be increased.

  In the third invention, the swirl flow forming means in the second invention preferably has a flow path (13, 23, 25, 33, 35, 43, 45) having a larger flow path diameter than the upstream flow path. According to the present invention, the swirling flow that contributes to the efficiency improvement can be formed with a simple configuration. Further, by adopting a flow distributor in which the ratio of the flow path diameters before and after expansion is adjusted to a desired value, it is possible to easily adjust the amount of increase in the relative refrigerant flow rate due to the swirling flow.

  Furthermore, the swirling flow forming means (25, 35, 45, 28) in the second or third invention preferably swirls the refrigerant flowing into the nozzle portion (5a) of the ejector (5). According to the present invention, by causing the swirling liquid refrigerant to flow into the nozzle portion of the ejector, the relative refrigerant flow rate is increased, the boiling of the liquid refrigerant is promoted, and the nozzle efficiency can be increased.

  Furthermore, it is preferable that the distribution flow path mechanism in any one of the above inventions has flow paths (34, 35, 44, 45) having different height positions in the gravity direction from other flow paths. According to the present invention, since the flow rate of the refrigerant flowing through the flow passage having a different height position in the gravity direction from that of the other flow passages can be reduced, the distribution of the refrigerant flow rate in the flow distributor can be performed with a simple configuration. .

  Furthermore, in any one of the above inventions, the second throttle means (4) for decompressing and expanding the other refrigerant distributed by the flow distributor (10, 20, 30, 40) before supplying to the evaporator (8). It is preferable to provide. According to the present invention, the flow rate of the refrigerant flowing out from the flow distributor toward the ejector suction side can be strictly adjusted, so that the efficiency of the vapor compression refrigeration cycle can be further controlled. .

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
FIG. 1 shows an example of a vapor compression refrigeration cycle provided with an ejector of the present invention. This vapor compression refrigeration cycle is a compressor 1, a radiator 2 that radiates the heat of the high-pressure refrigerant discharged from the compressor 1, and a first throttle means that decompresses the refrigerant downstream of the radiator 2. A decompressor 3 and a flow distributor 10 having a plurality of flow passages for distributing the refrigerant flow decompressed by the decompressor 3 into a plurality of flows are provided.

  Furthermore, the vapor compression refrigeration cycle takes in one refrigerant distributed by the flow distributor 10 and injects it from the nozzle portion 5a to form a high-speed refrigerant flow, while the other refrigerant is made to flow by the high-speed refrigerant flow. The ejector 5 sucked from the suction unit 5b, the other refrigerant distributed by the flow distributor 10 is evaporated, the second evaporator 8 discharged toward the suction unit 5b, and the refrigerant discharged from the ejector 5 are discharged. A first evaporator 7 that takes in and exchanges heat with external air. The first evaporator 7 and the second evaporator 8 are provided inside the case 11 with the first evaporator 7 as the windward side. Air forcibly blown to both evaporators by a blower (not shown) is cooled by exchanging heat with the refrigerant and sent to the air-conditioning target space.

  Further, the vapor compression refrigeration cycle includes an internal heat exchanger 6 so that the high-pressure refrigerant flowing between the radiator 2 and the decompressor 3 and the low-pressure refrigerant sucked into the compressor 1 exchange heat. . The high-pressure refrigerant flowing between the radiator 2 and the decompressor 3 is cooled by heat exchange between the refrigerants in the internal heat exchanger 6, so that the refrigerant inlet / The enthalpy difference (cooling capacity) of the refrigerant between the outlets can be increased.

  The compressor 1 sucks, compresses and discharges refrigerant, and is driven to rotate by a vehicle travel engine via an electromagnetic clutch and a belt. As the compressor 1, for example, a swash plate type variable displacement compressor capable of continuously variably controlling the discharge capacity by a control signal from the outside is used.

  In the compressor 1 of the present embodiment, the discharge capacity can be continuously changed from 100% to approximately 0% by adjusting the pressure in the swash plate chamber. Therefore, the compressor 1 can be substantially deactivated by reducing the discharge capacity to approximately 0%. Therefore, it is good also as a clutchless structure which always connects the rotating shaft of the compressor 1 via a pulley and the belt V to a vehicle engine.

  The radiator 2 is a heat exchanger that radiates and condenses the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 1 and outside air that is forcibly blown by a blower (not shown). It is.

  The decompressor 3 has a function of decompressing the high-pressure refrigerant that has been heat-exchanged by the radiator 2, and includes, for example, a flow rate adjusting valve that regulates the flow rate of the refrigerant. By controlling the decompressor 3 with a control device (not shown), the high-pressure refrigerant can be made to flow into the flow distributor 10 in a gas-liquid two-phase flow state. The gas-liquid two-phase flow at this time takes the form of a stratified flow, spiral flow, slag flow, etc. depending on the dryness and flow velocity of the refrigerant, and the gas refrigerant is located above and the liquid refrigerant is located below. It takes the form of a separated flow. The decompressor 3 may be an electric flow control valve capable of variably controlling the refrigerant flow rate, or may be a fixed flow control valve.

  The flow distributor 10 is a cube or a rectangular body in which a plurality of flow passages are formed, and has a distribution channel mechanism that distributes the refrigerant that has been decompressed by the decompressor 3 and flows into a predetermined amount. . As shown in FIG. 2, the flow distributor 10 has a first flow passage 12 into which the refrigerant depressurized by the decompressor 3 flows in, and branches from the first flow passage 12 to flow out the refrigerant to the second evaporator 8 side. And a third flow passage 14 which branches from the first flow passage 12 and flows out of the refrigerant to the nozzle portion 5a side of the ejector 5, and these flow passages are distributed flow path mechanisms. Is configured.

  As shown in FIG. 3, the first flow passage 12, the second flow passage 13, and the third flow passage 14 extend in the horizontal direction, and are disposed on substantially the same horizontal plane. In other words, the first flow path 12 and the third flow path 14 are a flow path center line 15 extending in the flow path axial direction of the first flow path 12 and a flow extending in the flow path axial direction of the third flow path 14. It is provided so that the road center line 16 substantially coincides. Furthermore, the flow path center line extending in the flow path axial direction of the second flow path 13 is also disposed on substantially the same horizontal plane including the flow path center line 15 and the flow path center line 16. That is, all the flow paths formed inside the flow distributor 10 are provided at the same height position with respect to the direction of gravity.

  The first flow path 12, the second flow path 13, and the third flow path 14 are all substantially cylindrical flow paths, and the diameters of the flow paths are φd1, φd2, and φd3. The relationship between φd1, φd2, and φd3 is φd2> φd1 and φd2> φd3. That is, the flow path diameter φd2 of the second flow path is larger than the flow path diameter φd1 of the first flow path, and further larger than the flow path diameter φd3 of the third flow path. In FIG. 2, the second flow path 13 and the third flow path 14 branch from the first flow path 12 is a right-angled branch, but both flow paths branch symmetrically in a divergent shape. The form to do may be sufficient.

  When the flow path diameter φd2 of the second flow path is larger than the flow path diameter φd1 of the first flow path and larger than the flow path diameter φd3 of the third flow path, the flow rate of refrigerant flowing into the third flow path 14 Can be reduced as compared with the case where each channel diameter is equal. In this way, an efficient vapor compression refrigeration cycle having an optimum flow rate ratio can be obtained by configuring the distribution flow path mechanism that satisfies the relationship between the flow path to be reduced and the flow path to be increased. Further, the distribution flow path mechanism configured in this way maximizes the system coefficient of performance in consideration of the ejector nozzle efficiency and the evaporator refrigeration capacity.

  In addition, the flow distributor 10 has the distribution channel mechanism as described above, thereby suppressing the uneven distribution of the gas-phase refrigerant and the liquid-phase refrigerant due to gravity in the second flow path 13 and the third flow path 14, Variations in these biases can be formed symmetrically. And the influence which the flow of a gas-liquid two-phase flow gives can be reduced, and a refrigerant can be distributed in a desired ratio. For example, the uneven distribution state of the gas phase refrigerant and the liquid phase refrigerant is similarly generated in each flow path, and even if the operation state of the cycle is changed, the uneven distribution state is similarly changed in each flow path.

  Further, the flow distributor 10 has swirl flow forming means for swirling the flow of the distributed refrigerant. This swirl flow forming means is configured by having a flow path having a larger flow path diameter than the upstream flow path. The swirl flow forming means in the present embodiment is that the flow path diameter φd2 of the second flow path 13 is formed larger than the flow path diameter φd1 of the first flow path 12 that is the upstream flow path.

  FIG. 6 is a perspective view showing the velocity vector of the swirling flow 26 formed by the swirling flow forming means. When the gas-liquid two-phase refrigerant that has flowed into the first flow path 12 flows into the second flow path 13, as shown in FIG. 6, the centrifugal force acting radially outward of the flow path expands the second flow path 13. It works diagonally forward along the inner wall surface and contributes to the generation of the actual velocity vector V. At this time, the liquid refrigerant mainly turns. This is because the liquid refrigerant is easily affected by inertia.

  Here, the velocity vector V is a resultant force of the velocity vector component V1 in the flow channel axis direction and the velocity vector component V2 in the radial direction of the flow channel. Further, since the flow rate of the refrigerant flowing through the flow path is the same regardless of whether or not the swirl flow is generated, the speed vector component V1 is equal to the speed vector component in the flow path axis direction when the flow does not swirl. That is, the absolute value V of the actual refrigerant speed when the swirl flow is generated is larger than the absolute value of the refrigerant speed penetrating the flow path cross-sectional area in the right angle direction when the swirl flow is not generated.

  Therefore, when the swirl flow is generated, the relative refrigerant flow rate in the flow path is increased, the disturbance from the inner wall surface of the flow path is easily received, and the boiling of the liquid refrigerant is promoted. In addition, when a swirling flow or mixed flow is generated in the gas-liquid two-phase refrigerant in the flow path, the refrigerant droplets are subdivided, reducing the gas-liquid speed difference, and the flow in the flow path is homogeneous. Will approach. This makes it easier for the liquid refrigerant to boil and improves the coefficient of performance of the system.

  In addition, you may comprise a swirl | vortex flow formation means by the helical groove | channel 28 formed in the inner wall face of a flow path, as shown in FIG. When the refrigerant flows in the flow path provided with the spiral groove 28, the refrigerant flows so as to be guided by the spiral groove 28, and a swirl flow as shown in FIG. 6 is formed. Further, the swirling flow forming means may be constituted by a spiral rib that has the same spiral shape and protrudes inward from the inner wall surface instead of the spiral groove 28.

  The flow distributor 10 is made of the same material as the refrigerant pipe (for example, aluminum), and is formed by cutting an aluminum block or forming aluminum in order to obtain a flow path having the desired dimension and shape. It can be manufactured by die casting or forging. The flow distributor 10 may be made of brass or copper. Each of the first flow passage 12, the second flow passage 13, and the third flow passage 14 of the flow distributor 10 is brazed and joined to each refrigerant pipe to be connected.

  Next, the refrigerant pipe connected to the third flow passage 14 is connected to the ejector 5. The ejector 5 is a pressure reducing means for reducing the pressure of the refrigerant, and is also a refrigerant circulating means for transporting the fluid by circulating the refrigerant by a suction action (winding action) of the refrigerant flow ejected at high speed.

  The ejector 5 takes in one refrigerant distributed by the flow distributor 10 and communicates with a nozzle portion 5a for reducing the passage area and reducing and expanding the refrigerant in an isentropic manner, and a refrigerant outlet of the nozzle portion 5a. And a suction part 5b for sucking the gas-phase refrigerant from the second evaporator 8 is provided.

  A mixing unit that mixes the high-speed refrigerant flow from the nozzle unit 5a and the suction refrigerant from the suction unit 5b is provided on the downstream side of the nozzle unit 5a and the suction unit 5b. And the diffuser part which makes a pressure | voltage rise part downstream from the mixing part is arrange | positioned. The diffuser portion is formed in a shape that gradually increases the refrigerant passage area, and has a function of decelerating the refrigerant flow to increase the refrigerant pressure, that is, a function of converting the velocity energy of the refrigerant into pressure energy.

  A first evaporator 7 is connected to the downstream side of the diffuser section in the refrigerant flow direction. The first evaporator 7 is a heat absorber that exchanges heat between the forcedly blown air and the refrigerant, evaporates the refrigerant, and exerts an endothermic effect.

  An accumulator 9 is connected to the downstream side of the first evaporator 7 in the refrigerant flow direction. The accumulator 9 is a gas-liquid separator that separates the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant. The gas phase refrigerant outlet side of the accumulator 9 is connected to the suction side of the compressor 1 via the internal heat exchanger 6.

  Next, in the refrigerant pipe connected to the second flow passage 13, the capillary 4 serving as the second throttling means and the second evaporator 8 are disposed in a downstream portion of the capillary 4. The capillary 4 performs flow rate adjustment and pressure reduction of the refrigerant flowing into the second evaporator 8, and is formed by a thin tube wound spirally. The second throttle means may be configured with a fixed throttle such as an orifice.

  The second evaporator 8 is a heat absorber that evaporates the refrigerant and exerts an endothermic effect. In the present embodiment, the first evaporator 7 and the second evaporator 8 are assembled into an integrated structure. Specifically, each component of the 1st evaporator 7 and the 2nd evaporator 8 is comprised with aluminum, and it joined to the integral structure by brazing.

  A control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. This control device performs various calculations and processes based on a control program stored in the ROM to control the operation of various devices. Further, detection signals from various sensor groups and various operation signals from an operation panel (not shown) are input to the control device. The operation panel is provided with a temperature setting switch for setting the cooling temperature of the space to be cooled, an air conditioning operation switch for outputting an operation command signal for the compressor 1, and the like.

  Next, the operation of the present embodiment will be described with the configuration as described above. When the air conditioning operation switch is turned on, the electromagnetic clutch of the compressor 1 is energized by the control output of the control device, the electromagnetic clutch is connected, and the rotational driving force is transmitted to the compressor 1 from the vehicle travel engine.

  When the control current In is output from the control device to the electromagnetic capacity control valve of the compressor 1 based on the control program, the compressor 1 sucks, compresses and discharges the gas-phase refrigerant.

  The high-temperature and high-pressure gas-phase refrigerant compressed and discharged from the compressor 1 flows into the radiator 2. In the radiator 2, the high-temperature and high-pressure refrigerant is cooled by the outside air and condensed. The high-pressure refrigerant after heat dissipation flowing out of the radiator 2 exchanges heat with the low-pressure gas-phase refrigerant flowing out of the accumulator 9 in the internal heat exchanger 6.

  Then, the refrigerant flowing out from the internal heat exchanger 6 is decompressed and expanded to a desired pressure by the decompressor 3 to form a gas-liquid two-phase flow. The gas-liquid two-phase refrigerant flows into the flow distributor 10, and one is distributed at an appropriate flow rate to the refrigerant flow toward the ejector 5 and the other toward the capillary 4.

  Here, the flow distributor 10 is disposed so that the first flow passage 12, the second flow passage 13, and the third flow passage 14 formed therein are substantially on the same horizontal plane. The liquid phase refrigerant that has flowed into the flow distributor 10 is appropriately diverted without being affected by gravity.

  Accordingly, in the flow distributor 10, the ratio of the liquid phase refrigerant in the refrigerant flowing out to the nozzle portion 5 a side of the ejector 5 and the ratio of the liquid phase refrigerant in the refrigerant flowing out to the second evaporator 8 side are substantially equal. Thus, the refrigerant is distributed. As a result, the liquid phase refrigerant surely flows into the nozzle portion 5a side of the ejector 5.

  Then, the refrigerant flowing into the ejector 5 is decompressed and expanded by the nozzle portion 5a. Since the pressure energy of the refrigerant is converted into velocity energy during the decompression and expansion, the refrigerant is ejected at a high speed from the ejection port of the nozzle portion 5a. Then, the refrigerant after passing through the second evaporator 8 is sucked from the suction portion 5b by the refrigerant suction action of the refrigerant jet flow.

  The refrigerant ejected from the nozzle part 5a and the refrigerant sucked by the suction part 5b are mixed in the mixing part on the downstream side of the nozzle part 5a and flow into the diffuser part. In the diffuser portion, the refrigerant pressure increases because the velocity energy of the refrigerant is converted into pressure energy due to the expansion of the passage area.

  Here, in this embodiment, since the liquid-phase refrigerant is configured to surely flow into the nozzle portion 5a side of the ejector 5, the diffuser portion easily exhibits the boosting capability, and the cycle operating efficiency is deteriorated. Can be suppressed.

  Then, the refrigerant flowing out from the diffuser portion of the ejector 5 flows into the first evaporator 7. In the first evaporator 7, the low-pressure refrigerant absorbs heat from the blown air and evaporates. Then, the refrigerant after passing through the first evaporator 7 flows into the accumulator 9 and is separated into a gas phase refrigerant and a liquid phase refrigerant.

  And the gaseous-phase refrigerant | coolant which flowed out from the accumulator 9 flows in into the internal heat exchanger 6, and performs heat exchange with a high voltage | pressure refrigerant | coolant. And the gaseous-phase refrigerant | coolant which flowed out from the internal heat exchanger 6 is suck | inhaled by the compressor 1, and is compressed again.

  On the other hand, the refrigerant flowing out to the second evaporator 8 side is decompressed by the capillary 4 to become a low-pressure refrigerant, and this low-pressure refrigerant flows into the second evaporator 8. In the second evaporator 8, the low-pressure refrigerant that has flowed in absorbs heat from the blown air cooled by the first evaporator 7 and evaporates. The refrigerant evaporated in the second evaporator 8 is sucked from the suction part 5b of the ejector 5, mixed with the liquid-phase refrigerant that has passed through the nozzle part 5a in the mixing part, and flows into the first evaporator 7. .

  Thus, the flow distributor 10 of the vapor compression refrigeration cycle of the present embodiment has a distribution flow path mechanism that distributes the inflowing refrigerant to a predetermined amount. The distribution channel mechanism includes a first flow passage 12 into which the refrigerant decompressed by the decompressor 3 flows, and a second branch that branches from the first flow passage 12 and flows out to the second evaporator 8 side. The flow path 13 and the 3rd flow path 14 which branches off from the 1st flow path 12, and flows out a refrigerant | coolant to the ejector 5 side are provided. The first flow path 12, the second flow path 13, and the third flow path 14 are arranged on substantially the same horizontal plane, and the flow path diameter φd2 of the second flow path 13 is larger than the flow path diameter φd1 of the first flow path 12. It is larger and further larger than the flow path diameter φd3 of the third flow passage 14.

  According to this configuration, the flow rate of refrigerant flowing into the third flow passage 14 is made smaller than the flow rate of refrigerant flowing into the second flow passage 13 and the flow rate of refrigerant flowing into the nozzle portion 5a of the ejector 5 is reduced. Can be distributed appropriately.

  The flow distributor 10 has swirl flow forming means for swirling the flow of the distributed refrigerant, and the swirl flow forming means is configured by a flow path having a flow path diameter larger than that of the upstream flow path. preferable.

  When this configuration is adopted, the relative refrigerant flow velocity in the flow path increases due to the formation of the swirling flow, and is easily subject to disturbance from the inner wall surface of the flow path, promoting the boiling of the liquid refrigerant and vapor compression refrigeration. Cycle efficiency can be increased. Further, the swirl flow can be formed with a simple configuration. Further, by adjusting the ratio of the flow path diameters before and after expansion to a desired value, it is possible to easily adjust the amount of increase in the relative refrigerant flow rate due to the swirling flow.

  The refrigerant distributed by the flow distributor 10 is preferably decompressed and expanded by the capillary 4 before being supplied to the second evaporator 8. In this case, since the flow rate of the refrigerant flowing out from the flow distributor 10 toward the suction part 5b side of the ejector 5 can be adjusted strictly, control is performed to further improve the efficiency of the vapor compression refrigeration cycle. Can do.

(Second Embodiment)
In the second embodiment, the configuration of the flow distributor 20 will be described with reference to FIGS. 4 and 5. FIG. 4 is a plan view showing the internal configuration of the flow distributor in the present embodiment, and FIG. 5 is a view in the direction of the arrow X in FIG. The vapor compression refrigeration cycle to which the flow distributor 20 is applied is the same as the cycle described in the first embodiment.

  The flow distributor 20 is different from the flow distributor 10 in that the refrigerant flow that flows into the nozzle portion 5a side of the ejector 5 has a swirl flow. This embodiment is the same as the first embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 4, the flow distributor 20 has a first flow passage 22 into which the refrigerant decompressed by the decompressor 3 flows, and a branch from the first flow passage 22 and flows the refrigerant to the second evaporator 8 side. A second flow passage 23 that flows, a third flow passage 24 that branches off from the first flow passage 22 and communicates with the nozzle portion 5a side of the ejector 5, and a refrigerant that passes through the third flow passage 24 on the nozzle portion 5a side of the ejector 5 And a fourth flow passage 25 that flows out into the flow path, and these flow passages constitute a distribution flow path mechanism.

  As shown in FIG. 5, the first flow path 22, the second flow path 23, the third flow path 24, and the fourth flow path 25 extend in the horizontal direction, and are disposed on substantially the same horizontal plane. ing. In other words, the first flow path 22 and the third flow path 24 are flow paths that extend in the flow path axis direction of the first flow path 22 and in the flow path axis direction of the third flow path 24. The road center line 16 is provided so as to substantially coincide. Further, the flow path center line extending in the flow path axis direction of the second flow path 23 and the flow path center line extending in the flow path axis direction of the fourth flow path 25 are also the flow path center line 15 and the flow path center line 16. Are disposed on substantially the same horizontal plane. That is, all the flow paths formed inside the flow distributor 20 are provided at the same height position with respect to the direction of gravity.

  The first flow path 22, the second flow path 23, the third flow path 24, and the fourth flow path 25 are all substantially cylindrical flow paths, and the diameters of the flow paths are φd1, φd2, φd3, and φd4, respectively. is there. The relationship between φd1, φd2, and φd3 is φd2> φd1, φd2> φd3, and φd4> φd3. That is, the distribution flow path mechanism of the flow distributor 20 is different from the distribution flow path mechanism of the flow distributor 10 in that the flow path diameter φd4 of the fourth flow path is larger than the flow path diameter φd3 of the third flow path. ing.

  The swirl flow forming means in the present embodiment is such that the flow passage diameter φd2 of the second flow passage 23 is formed larger than the flow passage diameter φd1 of the first flow passage 22 that is the upstream flow passage, and the fourth flow passage. That is, the flow path diameter φd4 of 25 is formed larger than the flow path diameter φd3 of the third flow passage 24 that is the upstream flow path.

  Therefore, in the second flow path 23 that flows out the refrigerant to the second evaporator 8 side and the fourth flow path 25 that flows out the refrigerant to the nozzle portion 5a side of the ejector 5, the refrigerant flow in the flow path becomes a swirl flow. As shown in FIG. 6, the relative refrigerant flow rate in the flow path is increased, the disturbance from the inner wall surface of the flow path is easily received, and the boiling of the liquid refrigerant is promoted.

  Thus, in the flow distributor 20 of the present embodiment, the refrigerant that flows into the nozzle portion 5a of the ejector 5 is swirled. When this configuration is adopted, the swirling liquid refrigerant is caused to flow into the nozzle portion 5a of the ejector 5, whereby the relative refrigerant flow rate is increased, the boiling of the liquid refrigerant is promoted, and the expansion loss energy is increased. The nozzle efficiency can be increased.

(Third embodiment)
In the third embodiment, the configuration of the flow distributor 30 will be described with reference to FIGS. 8 and 9. FIG. 8 is a plan view showing the internal configuration of the flow distributor in the present embodiment, and FIG. 9 is a view in the direction of the arrow X in FIG. The vapor compression refrigeration cycle to which the flow distributor 30 is applied is the same as the cycle described in the first embodiment.

  The flow distributor 30 is provided such that a flow passage for flowing the refrigerant to be introduced into the nozzle portion 5a side of the ejector 5 is provided at a position higher than the other flow passages in the weight direction with respect to the flow distributor 20. Is different. The present embodiment is the same as the first and second embodiments in the other configurations, and has the same functions and effects.

  As shown in FIG. 8, in the same manner as the flow distributor 20, the flow distributor 30 is branched from the first flow path 32 into which the refrigerant depressurized by the pressure reducer 3 flows and the second flow path 32. The second flow passage 33 that flows out the refrigerant to the evaporator 8 side, the third flow passage 34 that branches from the first flow passage 32 and communicates with the nozzle portion 5a side of the ejector 5, and the refrigerant that passes through the third flow passage 34 And a fourth flow passage 35 that flows out toward the nozzle portion 5a side of the ejector 5, and these flow passages constitute a distribution flow path mechanism.

  As shown in FIG. 9, among the first flow passage 32, the second flow passage 33, the third flow passage 34, and the fourth flow passage 35, the third flow passage 34 and the fourth flow passage 35 are other flow passages. It is provided at a position higher than the direction of gravity. That is, when the third flow passage 34 branches from the first flow passage 32, the flow passage inlet is disposed at a position where it has moved upward by a predetermined distance. In other words, the flow path center line 36 extending in the flow path axial direction of the first flow path 32 is positioned below the flow path center line 37 extending in the flow path axial direction of the third flow path 34 by a predetermined distance. Will do.

  In addition, the 1st flow path 32 and the 2nd flow path 33 are arrange | positioned on the substantially the same horizontal surface. The third flow passage 34 and the fourth flow passage 35 are disposed on a horizontal plane located above the horizontal plane on which the first flow passage 32 and the second flow passage 33 are located.

  The distribution flow path mechanism in the present embodiment includes a third flow path 34 and a fourth flow path 35 that are provided at positions higher than the other flow paths in the direction of gravity. By having this distribution flow path mechanism, the refrigerant flow rate flowing into the third flow passage 34 can be made smaller than the refrigerant flow rate flowing into the second flow passage 33, and the refrigerant flow rate flowing into the nozzle portion 5 a of the ejector 5. Can be distributed appropriately.

  As described above, the flow distributor 30 of the present embodiment includes the third flow path 34 and the fourth flow path 35 whose height in the gravitational direction is above the other flow paths. When this configuration is adopted, the flow rate adjustment for reducing the refrigerant flow rates of the third flow passage 34 and the fourth flow passage 35 can be performed with a simple configuration.

(Fourth embodiment)
In the fourth embodiment, the configuration of the flow distributor 40 will be described with reference to FIGS. 10 and 11. FIG. 10 is a plan view showing the internal configuration of the flow distributor in the present embodiment, and FIG. 11 is a view in the direction of the arrow X in FIG. The vapor compression refrigeration cycle to which the flow distributor 40 is applied is the same as the cycle described in the first embodiment.

  The flow distributor 40 is provided such that the flow passage for flowing the refrigerant flowing into the nozzle portion 5a side of the ejector 5 is provided at a position lower than the other flow passages in the weight direction with respect to the flow distributor 30. Is different. The present embodiment is the same as the first and second embodiments in the other configurations, and has the same functions and effects.

  As shown in FIG. 10, in the same manner as the flow distributor 30, the flow distributor 40 is branched from the first flow path 42 into which the refrigerant decompressed by the decompressor 3 flows, and the second flow path 42 is branched from the first flow path 42. A second flow path 43 that flows out the refrigerant to the evaporator 8 side, a third flow path 44 that branches from the first flow path 42 and communicates with the nozzle portion 5a side of the ejector 5, and a refrigerant that passes through the third flow path 44 And a fourth flow path 45 that flows out to the nozzle portion 5a side of the ejector 5, and these flow paths constitute a distribution flow path mechanism.

  As shown in FIG. 11, the third flow path 44 and the fourth flow path 45 are provided at a position lower than the other flow paths in the direction of gravity. That is, when the third flow passage 44 branches from the first flow passage 42, the third flow passage 44 is disposed at a position where the flow path inlet has moved downward by a predetermined distance. In other words, the flow path center line 46 extending in the flow path axial direction of the first flow path 42 is positioned a predetermined distance above the flow path center line 47 extending in the flow path axial direction of the third flow path 44. Will do.

  In addition, the 1st flow path 42 and the 2nd flow path 43 are arrange | positioned on the substantially the same horizontal surface. Further, the third flow path 44 and the fourth flow path 45 are arranged on a horizontal plane located below the horizontal plane where the first flow path 42 and the second flow path 43 are located.

  As described above, the flow distributor 40 of the present embodiment has the third flow path 44 and the fourth flow path 45 whose height position in the gravitational direction is below the other flow paths. When this configuration is adopted, the flow rate adjustment for reducing the coolant flow rates in the third flow passage 44 and the fourth flow passage 45 can be performed with a simple configuration.

(Other embodiments)
The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  The vapor compression refrigeration cycle in the above embodiment can be applied to a vehicle air conditioner, a heat pump cycle for a water heater or an indoor air conditioner. The installation location is a moving body such as a vehicle or a fixed body placed at a fixed position.

  Further, in the above embodiment, the type of the refrigerant is not particularly specified, but the refrigerant can be applied to any of a vapor compression supercritical cycle and a subcritical cycle such as a fluorocarbon refrigerant, an HC refrigerant, and a carbon dioxide refrigerant. There may be.

  In addition, the ejector in the above embodiment may be a variable flow type that can vary the refrigerant flow area of the nozzle.

  In addition, the flow distributor in the above embodiment is constituted by a branch pipe having a plurality of flow paths described in the above embodiment, in addition to a form in which a flow path is provided inside a cubic or rectangular block. Also good.

It is the schematic diagram which showed the structure of the vapor | steam compression refrigerating cycle in 1st Embodiment of this invention from 4th Embodiment. It is the top view which showed the internal structure of the flow volume divider | distributor in 1st Embodiment. FIG. 3 is a view as viewed in the X direction in FIG. 2. It is the top view which showed the internal structure of the flow volume divider | distributor in 2nd Embodiment. It is a X direction arrow line view in FIG. It is the perspective view which showed the velocity vector of the swirl flow formed by the swirl flow formation means in the first to fourth embodiments. It is the perspective view which showed the helical groove | channel in the flow path which comprises a rotational flow formation means. It is the top view which showed the internal structure of the flow volume divider | distributor in 3rd Embodiment. It is an X direction arrow directional view in FIG. It is the top view which showed the internal structure of the flow volume divider | distributor in 4th Embodiment. It is a X direction arrow directional view in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor 2 ... Radiator 3 ... Pressure reducer (1st throttle means)
4 ... Capillary (second throttle means)
DESCRIPTION OF SYMBOLS 5 ... Ejector 5a ... Nozzle part 5b ... Suction part 8 ... Evaporator 10, 20, 30, 40 ... Flow volume distributor 12, 22, 32, 42 ... 1st flow path (distribution flow path mechanism)
13, 23, 33, 43 ... second flow passage (distribution flow path mechanism, swirl flow forming means)
14, 24, 34, 44 ... third flow path (distribution flow path mechanism)
25, 35, 45 ... fourth flow passage (swirl flow forming means)
28 ... Spiral groove (swirl flow forming means)

Claims (7)

A compressor (1) for sucking the refrigerant and compressing it into a high-pressure refrigerant;
A radiator (2) for radiating heat of the high-pressure refrigerant discharged from the compressor (1);
A first throttling means (3) for depressurizing the refrigerant on the downstream side of the radiator (2);
A flow distributor (10, 20, 30, 40) having a flow path for distributing the flow of the refrigerant decompressed by the first throttle means (3) into a plurality of flows;
One of the refrigerants distributed by the flow distributors (10, 20, 30, 40) is taken in and injected from the nozzle part (5a) to form a high-speed refrigerant flow, and the other by the high-speed refrigerant flow Ejector (5) for sucking the refrigerant from the suction part (5b),
An evaporator (8) that takes in and evaporates the other refrigerant distributed by the flow distributor (10, 20, 30, 40) and discharges it toward the suction part (5b),
The flow distributor (10, 20, 30, 40) is a distribution channel mechanism (12, 13, 14, 22, 23, 24, 32, 33, 34, 42, 43) that distributes the inflowing refrigerant to a predetermined amount. , 44). A vapor compression refrigeration cycle. The distribution channel mechanism branches from the first flow path (12, 22, 32, 42) into which the refrigerant depressurized by the first throttling means (3) flows, and branches from the first flow path to the evaporator. (8) The second flow passage (13, 23, 33, 43) for flowing out the refrigerant to the side, and the third flow passage (14) branching out from the first flow passage and flowing out the refrigerant to the ejector (5) side. , 24, 34, 44)
The first flow path, the second flow path, and the third flow path are arranged on substantially the same horizontal plane, and the flow path diameter (φd2) of the second flow path is the flow path diameter (φd1) of the first flow path. 2. The vapor compression refrigeration cycle according to claim 1, wherein the vapor compression refrigeration cycle is larger than the flow path diameter (φd3) of the third flow passage.   The flow rate distributor has swirl flow forming means (13, 23, 25, 33, 35, 43, 45, 28) for swirling the flow of the distributed refrigerant. Vapor compression refrigeration cycle.   The said compression flow formation means has a flow path (13, 23, 25, 33, 35, 43, 45) with a larger flow path diameter than an upstream flow path, The vapor compression of Claim 3 characterized by the above-mentioned. Refrigeration cycle.   5. The vapor compression according to claim 3, wherein the swirl flow forming means (25, 35, 45, 28) swirls the refrigerant that flows into the nozzle portion (5 a) of the ejector (5). Refrigeration cycle.   The steam according to any one of claims 1 to 5, wherein the distribution channel mechanism has a channel (34, 35, 44, 45) having a height position different from that of another channel in the direction of gravity. Compression refrigeration cycle.   A second throttle means (4) is provided for decompressing and expanding the other refrigerant distributed by the flow distributor (10, 20, 30, 40) before being supplied to the evaporator (8). The vapor compression refrigeration cycle according to any one of claims 1 to 6.

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