JP6087635B2 - Compressor and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to a compressor that sucks gas refrigerant separated from an economizer into a compression process, and a refrigeration cycle apparatus.

  As a conventional centrifugal compressor, a suction nozzle that introduces refrigerant from the outer peripheral side in the radial direction of the rotating shaft to the inner peripheral side, and a substantially donut-shaped space that communicates with the suction nozzle on the outer peripheral side, introduced from the suction nozzle And a chamber for guiding the gas refrigerant to an inlet opening of the impeller that is opened in the axial direction of the rotation shaft and arranged in a substantially annular shape. The chamber has a radial width that rotates from a connection portion that communicates with the suction nozzle. Some are formed so as to gradually become narrower in the circumferential direction of the rotating shaft as it goes toward the axis (for example, see Patent Document 1). By forming such a chamber, the amount of the gas refrigerant flowing into the impeller is made uniform in the circumferential direction, that is, there is no uneven distribution of the gas refrigerant in the circumferential direction, and the compression performance is improved.

  Conventionally, a two-stage compression two-stage expansion cycle has been adopted as a refrigeration cycle from the viewpoint of improving the performance of the refrigeration capacity of the refrigeration cycle. Here, the two-stage compression and two-stage expansion cycle means that the refrigerant that has been radiated by the radiator and expanded and depressurized by the expansion valve to become a gas-liquid two phase is gas-liquid separated by an economizer, and the gas refrigerant is compressed. This is a refrigeration cycle that is sucked into a refrigerant flow path between two stages of compression elements (impellers) of the machine. After gas-liquid separation by the economizer, the liquid refrigerant is further expanded and depressurized by another expansion valve, and becomes a gas refrigerant by the evaporator. This gas refrigerant is sucked into the compressor and merges with the gas refrigerant sucked between the two stages of the compression elements.

  In the above two-stage compression and two-stage expansion cycle, the gas refrigerant separated by the economizer is sucked into the annular refrigerant flow path between the two stages of the compression elements of the compressor. When inhaled, a large amount of refrigerant is present near the suction port, and there is an uneven distribution of the refrigerant in the circumferential direction. However, since the gas refrigerant is sucked from the economizer between the stages of the two-stage compression elements (impellers), the influence on the compression performance is not so great.

JP 2010-203251 A

  However, in recent years, there has been a demand for a single-stage compressor from the viewpoint of cost reduction and downsizing of the compressor. In a single-stage compressor, it is necessary to flow the gas refrigerant circulated from the economizer directly into the impeller blades that are compression elements. In this case, when sucked from one place in the circumferential direction toward the blade of the impeller, there will be a large amount of refrigerant in the vicinity of the suction port, and there will be an uneven distribution in the circumferential direction of the refrigerant. There was a possibility that the compression performance and the refrigerating capacity would be reduced.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor and a refrigeration cycle apparatus that suppress a decrease in compression performance and refrigeration capacity.

  A compressor according to the present invention for solving the above-described problems is provided with an impeller fixed to a rotating shaft, an intermediate suction port through which refrigerant is sucked from an economizer, and an outer peripheral side communicating with the intermediate suction port. An intermediate suction chamber, which is a space formed along the circumferential direction of the shaft, into which the refrigerant sucked from the intermediate suction port flows into the impeller through an inlet formed on the inner peripheral side; A plurality of guide channels disposed in the intermediate suction chamber and guiding the refrigerant sucked from the intermediate suction port to the inflow port, wherein the plurality of guide channels are the intermediate suction port Is divided into a plurality of portions, and the refrigerant is guided toward each portion of the inlet to the impeller, and the area of each portion of the intermediate suction port divided into a plurality is divided from the intermediate suction port to the refrigerant. Corresponding to each guide channel to be inhaled It is characterized in that the serial has a area corresponding to the area of each portion of the inlet to the impeller. Among these, the ratio of the area of each part of the intermediate suction port divided into a plurality of parts is that each part of the inflow port to the impeller corresponding to each guide channel through which the refrigerant is sucked from the intermediate suction port. It is preferable that the area ratio is substantially the same. The guide flow path may be formed by a guide plate disposed in the intermediate suction chamber. The intermediate suction port may be plural.

  As a result, the refrigerant sucked from the intermediate suction chamber is uniformly introduced into the impeller through the inflow port over the entire circumference in the circumferential direction of the inflow port, and the compression performance by centrifugal compression of the impeller Can be improved.

  Further, in the compressor according to the present invention, the cross-sectional shape perpendicular to the axial direction of the rotation shaft of the intermediate suction chamber is approximately the direction substantially perpendicular to the radial direction passing through the intermediate suction port. It is characterized by an elliptical ring shape.

  As a result, it is possible to secure a large guide channel for rectifying the refrigerant sucked from the intermediate suction port along the circumferential direction as compared with a case where the guide channel is formed into a perfect circular ring shape. It is possible to reach the end of the inflow.

  Further, in the compressor according to the present invention, the guide flow path for guiding the refrigerant from the intermediate suction port along the circumferential direction is formed so as to be gradually narrowed and flows from the opposite direction of the circumferential direction. It is characterized by being formed so as not to be mixed with the refrigerant.

  Accordingly, the refrigerant sucked from the intermediate suction port and rectified along the circumferential direction by the guide flow path can be promoted so as to be directed to the portion of the inlet on the terminal side of the guide flow path.

  Further, the refrigeration cycle apparatus according to the present invention includes any one of the above-described compressors, a radiator that radiates the refrigerant discharged from the compressor, and the refrigerant that has flowed out of the radiator by decompressing the air. A first expansion valve that is a liquid two-phase refrigerant; an economizer that gas-liquid separates the gas-liquid two-phase refrigerant that has flowed out of the first expansion valve; and a second that depressurizes the liquid refrigerant that has been gas-liquid separated by the economizer An expansion valve and an evaporator for evaporating the liquid refrigerant flowing out of the second expansion valve, and the refrigerant flowing out of the evaporator is sucked into the compressor and separated into gas and liquid by the economizer The gas refrigerant is sucked into the intermediate suction chamber from the intermediate suction port of the compressor.

  Thus, since the compressor with improved compression performance is provided, the refrigeration capacity of the entire refrigeration cycle apparatus can be improved.

  According to the compressor of the present invention, the refrigerant sucked from the intermediate suction chamber is uniformly introduced into the impeller through the inlet, over the entire circumference of the inlet. Compression performance can be improved.

FIG. 1 is a configuration diagram of a refrigerant circuit of the refrigeration cycle apparatus according to the first embodiment. FIG. 2 is a cross-sectional view of a main part of the compressor according to the first embodiment. FIG. 3 is an enlarged cross-sectional view of the vicinity of the impeller of the compressor according to the first embodiment. 4 is a cross-sectional view taken along line AA in FIG. FIG. 5 is a Mollier diagram of the refrigeration cycle according to the first embodiment. FIG. 6 is a cross-sectional view in the axial direction of the rotating shaft of the compressor according to the second embodiment.

[Embodiment 1]
(Configuration of refrigerant circuit of refrigeration cycle apparatus 101)
1 is a configuration diagram of a refrigerant circuit of a refrigeration cycle according to Embodiment 1. FIG. The configuration of the refrigerant circuit of the refrigeration cycle apparatus 101 according to Embodiment 1 will be described with reference to FIG. The refrigeration cycle shown in FIG. 1 can be applied to a turbo chiller, an air conditioner, or the like, and these will be collectively referred to as a refrigeration cycle apparatus 101.

  As shown in FIG. 1, the refrigeration cycle apparatus 101 according to the present embodiment includes a compressor 1, a radiator 2, an evaporator 3, a first expansion valve 4, an economizer 5, a second expansion valve 6, and an electric motor 7. ing.

  The compressor 1 is a centrifugal single-stage compressor that centrifugally compresses sucked gas refrigerant and discharges it as a high-temperature and high-pressure refrigerant when an impeller 13 described later rotates. Further, as will be described later, the compressor 1 sucks the gas refrigerant separated by the economizer 5 from the intermediate suction port 15a, mixes it with the gas refrigerant sucked from the suction port 14a, and compresses the gas refrigerant.

  The radiator 2 performs heat exchange by radiating the heat of the high-temperature and high-pressure refrigerant discharged from the compressor 1 to air or water. The refrigerant flowing out of the radiator 2 is sent to the first expansion valve 4.

  The first expansion valve 4 expands and depressurizes the refrigerant flowing from the radiator 2 to form a gas-liquid two-phase refrigerant. The first expansion valve 4 is, for example, an electronic expansion valve having a variable opening.

  The economizer 5 separates the gas-liquid two-phase refrigerant flowing from the first expansion valve 4 into a liquid refrigerant having a low enthalpy and a gas refrigerant having a high enthalpy. The gas / liquid separated liquid refrigerant is directed to the second expansion valve 6, and the gas refrigerant is directed to the intermediate suction port 15 a of the compressor 1.

  The second expansion valve 6 further expands and depressurizes the liquid refrigerant separated from the gas and liquid by the economizer 5 to form a gas-liquid two-phase refrigerant. The second expansion valve 6 is, for example, an electronic expansion valve having a variable opening.

  The evaporator 3 absorbs heat from air or water to the gas-liquid two-phase refrigerant flowing from the second expansion valve 6 to exchange heat, thereby evaporating the refrigerant. The gas refrigerant flowing out from the evaporator 3 is sent to the compressor 1.

  The electric motor 7 is a motor for rotating the rotary shaft 12 of the compressor 1. Specifically, a gear 1a is installed at the end of the rotating shaft 12 extending from the compressor 1, and a gear 7a is installed at the end of the motor shaft of the electric motor 7, and the gear 1a. Is engaged. Therefore, when the electric motor 7 is driven and the motor shaft rotates, the rotational power is transmitted to the gear 7a, the gear 1a, and the rotating shaft 12, and the compressor 1 is compressed.

(Structure of compressor 1)
FIG. 2 is a cross-sectional view of a main part of the compressor according to the first embodiment, and FIG. 3 is an enlarged cross-sectional view in the vicinity of the impeller of the compressor according to the first embodiment. The structure of the compressor 1 will be described with reference to FIGS. 2 and 3.

  As shown in FIG. 2, the compressor 1 according to the present embodiment forms a main body of the compressor 1, a substantially cylindrical casing 11 into which a gas refrigerant to be compressed is introduced, and a casing inside the casing 11. 11, a rotary shaft 12 disposed along a substantially cylindrical shaft center, and a substantially disk-shaped impeller 13 fixed to the outer peripheral surface of the rotary shaft 12. The rotating shaft 12 is supported at both ends by a bearing (not shown) provided on the casing 11 so as to be rotatable in the circumferential direction C.

  The casing 11 is formed with a working chamber 11a in which the impeller 13 is accommodated. The casing 11 is a substantially annular space communicating with the suction pipe 16 for sucking the gas refrigerant from the evaporator 3 on the outer peripheral side, and rotates with respect to the working chamber 11a in which the impeller 13 is accommodated. A chamber 14 communicated from the upstream side L1 in the axial direction L of the shaft 12 is provided. Specifically, the chamber 14 communicates with the suction pipe 16 through a suction port 14 a formed in the outer peripheral surface of the casing 11. The casing 11 is a substantially elliptical ring-shaped space communicating with the intermediate suction pipe 17 for sucking the gas refrigerant separated by the economizer 5 on the outer peripheral side, and the working chamber 11a in which the impeller 13 is accommodated. An intermediate suction chamber 15 is provided which communicates with. Specifically, the intermediate suction chamber 15 communicates with the intermediate suction pipe 17 through an intermediate suction port 15 a formed in the outer peripheral surface of the casing 11. Further, the intermediate suction chamber 15 communicates with the working chamber 11a through an inflow port 15c formed inside the radial direction D.

  The casing 11 passes through the inside of the chamber 14 and sucks in from the upstream side L1 of the impeller 13 (the front edge portion 13b side of the blade 13a of the impeller 13), and the outside of the impeller 13 in the radial direction D (blade of the impeller 13). A discharge passage 11b for guiding the gas refrigerant discharged from the rear edge portion 13c side of 13a to the downstream L2 side is formed. The discharge channel 11b is formed in an annular shape in the circumferential direction C. The gas refrigerant flowing through the discharge flow passage 11b flows toward the downstream side L2, and discharge ports (not shown) drilled on the outer peripheral side of the casing 11 via an annular scroll (not shown). ).

  The impeller 13 is a substantially disk-shaped object fixed to the outer peripheral surface of the rotating shaft 12, and a member in which a plurality of blades 13a are fixed in a spiral shape with a predetermined interval on a curved peripheral surface formed on the upstream side L1 side. It is. The front edge 13b of the blade 13a faces the chamber 14, and the rear edge 13c faces the discharge flow path 11b. That is, the gas refrigerant flowing through the chamber 14 is sucked between the plurality of blades 13a from the front edge 13b side and centrifugally compressed by the impeller 13 rotating in the circumferential direction C, and from the rear edge 13c side. It discharges to the discharge flow path 11b.

  The chamber 14 is curved so as to go from the outer peripheral side in the radial direction D to the inner peripheral side and gradually toward the downstream side L2 in the axial direction L, and communicates with the working chamber 11a in which the impeller 13 is accommodated. It is a ring-shaped space. Also, the guide plate 14b that rectifies the gas refrigerant so that the gas refrigerant sucked from the suction port 14a is uniformly sucked in the circumferential direction C from the front edge portion 13b side to the impeller 13 in the chamber 14. Are arranged. That is, the gas refrigerant that has flowed out of the evaporator 3 is sucked into the chamber 14 via the suction pipe 16 and the suction port 14a, and is directed from the outer peripheral side in the radial direction D to the inner peripheral side by the rectifying action of the guide plate 14b. At the same time, the air flows toward the downstream side L2 in the axial direction L and is sucked into the impeller 13 from the front edge portion 13b side of the blade 13a.

  As shown in FIG. 2, the intermediate suction chamber 15 is a substantially annular space formed on the downstream side L <b> 2 side of the chamber 14, and the working chamber is formed by an inflow port 15 c formed on the inner side in the radial direction D. 11a. Further, in the intermediate suction chamber 15, the gas refrigerant sucked from the intermediate suction port 15a is interposed between the front edge portion 13b and the rear edge portion 13c of the blade 13a with respect to the impeller 13 through the inflow port 15c. A plurality of guide plates (described later) that rectify so as to be sucked uniformly from the portion in the circumferential direction C are arranged. That is, the gas refrigerant separated from the gas and liquid by the economizer 5 is sucked into the intermediate suction chamber 15 through the intermediate suction pipe 17 and the intermediate suction port 15a, and is circulated in the circumferential direction C by the rectifying action of the guide plate (described later). From the outer peripheral side in the radial direction D toward the inner peripheral side so as to be uniform over the entire area. The gas refrigerant is sucked into the impeller 13 through the inflow port 15c from a substantially intermediate portion between the front edge portion 13b and the rear edge portion 13c of the blade 13a.

  As described above, the gas refrigerant sucked through the suction port 14a (suction refrigerant F1) flows through the chamber 14 and is sucked into the impeller 13 from the front edge portion 13b side, and passes through the intermediate suction port 15a. The gas refrigerant (intermediate suction refrigerant F2) sucked through the refrigerant flows through the intermediate suction chamber 15 and is sucked into the impeller 13 from a substantially middle portion between the front edge portion 13b and the rear edge portion 13c. The suction refrigerant F1 and the intermediate suction refrigerant F2 sucked into the impeller 13 are merged between the blades 13a while being centrifugally compressed by the rotation of the impeller 13, and are discharged as the discharge refrigerant F3 from the rear edge portion 13c toward the discharge flow path 11b. The

(Configuration of guide plate in the intermediate suction chamber 15 of the compressor 1)
4 is a cross-sectional view taken along line AA in FIG. The structure of the guide plate in the intermediate suction chamber 15 and the flow of the gas refrigerant rectified by the guide plate will be described with reference to FIG.

  As shown in FIG. 4, the shape of the cross section perpendicular to the axial direction L of the intermediate suction chamber 15 is a substantially elliptical ring shape whose major axis is a direction perpendicular to the radial direction D passing through the center of the intermediate suction port 15a. It has become. In the intermediate suction chamber 15, the intermediate suction refrigerant F2 sucked through the intermediate suction port 15a is rectified and circulated in the intermediate suction chamber 15 to the impeller 13 through the inlet 15c. Guide plates 21 and 22a to 22e to be sucked are disposed in a portion between the front edge portion 13b and the rear edge portion 13c of 13a.

  The guide plate 21 divides the intermediate suction port 15a into three suction ports of suction port portions A1 to A3, and the intermediate suction refrigerant F2 sucked through the intermediate suction port 15a is respectively passed through the suction port portions A1 to A3. Rectify so as to flow in three directions. That is, among the intermediate suction refrigerant F2, the gas refrigerant sucked from the suction port portion A1 by the guide plate 21 goes to the inlet port portion 11 which is a portion of the inlet port 15c facing the intermediate suction port 15a. Further, among the intermediate suction refrigerant F2, the gas refrigerant sucked from the suction port portion A2 by the guide plate 21 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inlet portion 12 which is the portion of the inlet 15c. . Of the intermediate suction refrigerant F2, the gas refrigerant sucked from the suction port portion A3 by the guide plate 21 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inflow port portion l3 that is the portion of the inflow port 15c. .

  The guide plate 22a allows the gas refrigerant sucked from the suction port portion A1 by the guide plate 21 among the intermediate suction refrigerant F2 to be directed toward the impeller 13 from the inlet portion l1 of the inlet port 15c uniformly in the circumferential direction C. And rectify so that it flows.

  The guide plate 22b is supplied to the impeller 13 so that the gas refrigerant sucked from the suction port portion A2 by the guide plate 21 out of the intermediate suction refrigerant F2 is distributed in the circumferential direction C from the inlet portion l2 of the inlet 15c. Rectify to flow in. Further, the guide plate 22d is provided with an intermediate suction on the side opposite to the intermediate suction port 15a with respect to the rotary shaft 12 from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 which is shifted by approximately 90 ° in the circumferential direction C from the center of the intermediate suction port 15a. The flow path of the gas refrigerant is arranged so as to become gradually narrower in the circumferential direction C toward the vicinity of the inner peripheral wall of the working chamber 15. By disposing the guide plate 22d in this manner, the gas refrigerant can be promoted so as to go to the portion of the inflow port portion 12 opposite to the intermediate suction port 15a with respect to the rotation shaft 12. Accordingly, the gas refrigerant sucked from the inlet port portion A2 is rectified by the guide plates 22b and 22d so as to flow uniformly from the inlet port portion l2 of the inlet port 15c toward the impeller 13 in the circumferential direction C. The

  The guide plate 22c is supplied to the impeller 13 so that the gas refrigerant sucked from the suction port portion A3 by the guide plate 21 out of the intermediate suction refrigerant F2 is distributed in the circumferential direction C from the inlet portion l3 of the inlet port 15c. Rectify to flow in. Further, the guide plate 22e is provided with an intermediate suction on the opposite side to the intermediate suction port 15a with respect to the rotary shaft 12 from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 which is shifted by approximately 90 ° in the circumferential direction C from the center of the intermediate suction port 15a. The flow path of the gas refrigerant is arranged so as to become gradually narrower in the circumferential direction C toward the vicinity of the inner peripheral wall of the working chamber 15. Thus, by arrange | positioning the guide plate 22e, a gas refrigerant can be promoted so that it may go to the part on the opposite side to the intermediate | middle suction inlet 15a with respect to the rotating shaft 12 among the inflow port parts l3. Accordingly, the gas refrigerant sucked from the inlet port portion A3 is rectified by the guide plates 22c and 22e so as to flow uniformly from the inlet port portion l3 of the inlet port 15c toward the impeller 13 in the circumferential direction C. The

  The guide plates 22d and 22e partition the flow path of the gas refrigerant at the inner peripheral wall portion of the intermediate suction chamber 15 opposite to the intermediate suction port 15a with respect to the rotating shaft 12. Therefore, depending on the arrangement configuration of the guide plates 22d and 22e, the gas refrigerant sucked from the suction port portion A2 and directed toward the inlet portion l2, and the gas refrigerant sucked from the suction port portion A3 and directed toward the inlet portion l3. Will not mix.

  With the arrangement configuration of the guide plates 21 and 22a to 22e as described above, a guide channel in the intermediate suction chamber 15 of the intermediate suction refrigerant F2 sucked from the intermediate suction port 15a is formed.

  The guide plates 21 and 22a to 22e are arranged and configured so that the ratio of the areas of the suction inlet portions A1 to A3 is substantially the same as the ratio of the areas of the inlet portions 11 to 13. Therefore, the ratio of the amount of the gas refrigerant toward each of the inlet portions l1 to l3 is substantially the same as the ratio of the areas of the inlet portions A1 to A3. That is, the intermediate suction refrigerant F2 flows into the impeller 13 through the inlet 15c uniformly over the entire circumference in the circumferential direction C of the inlets 11 to 13, that is, the inlet 15c. The compression performance by centrifugal compression of the impeller 13 can be improved, whereby the refrigeration capacity of the entire refrigeration cycle apparatus 101 can be improved.

  As described above, the cross-sectional shape perpendicular to the axial direction L of the intermediate suction chamber 15 is a substantially elliptical ring shape whose major axis is a direction perpendicular to the radial direction D passing through the center of the intermediate suction port 15a. It has become. Thus, by making the cross-sectional shape of the intermediate suction chamber 15 into a substantially elliptical ring shape, the guide flow path of the gas refrigerant sucked from the suction port portions A2 and A3 is compared with the case of a perfect circular ring shape. Thus, the gas refrigerant can reach the portion of the inlet 15c opposite to the intermediate suction port 15a (the end of the guide channel) with respect to the rotary shaft 12.

  The guide plate 21 divides the intermediate suction port 15a into three suction ports, suction port portions A1 to A3, and the intermediate suction refrigerant F2 flows in three directions through the suction port portions A1 to A3. However, it is not limited to this. That is, the intermediate suction refrigerant F2 may be branched in two directions or branched in four or more directions by the guide plate 21.

(Operation of the refrigeration cycle of the refrigeration cycle apparatus 101)
FIG. 5 is a Mollier diagram of the refrigeration cycle according to the first embodiment. The overall operation of the refrigeration cycle of the refrigeration cycle apparatus 101 will be described with reference to FIGS. 1, 2, and 5. P1 to P8 shown in FIG. 5 correspond to P1 to P8 shown in FIG. 1, respectively.

  The gas refrigerant (P6) sucked into the compressor 1 is compressed by the centrifugal compression of the impeller 13 of the compressor 1 (P7), and the compressed refrigerant is mixed with the gas refrigerant circulated from the economizer 5 and the impeller 13. (P8), and further compressed and discharged. The high-temperature and high-pressure refrigerant (P1) discharged from the compressor 1 flows into the radiator 2. The refrigerant flowing into the radiator 2 exchanges heat with air or water to radiate heat and flows out of the radiator 2. The refrigerant (P2) flowing out from the radiator 2 flows into the first expansion valve 4. The refrigerant that has flowed into the first expansion valve 4 is expanded and depressurized by the first expansion valve 4 (P3), becomes a gas-liquid two-phase refrigerant, and flows into the economizer 5. The gas-liquid two-phase refrigerant that has flowed into the economizer 5 is gas-liquid separated by the economizer 5, the liquid refrigerant (P4) having a low enthalpy is directed to the second expansion valve 6, and the gas refrigerant having a higher enthalpy than the liquid refrigerant is compressed. Head to Aircraft 1.

  The liquid refrigerant that has flowed into the second expansion valve 6 from the economizer 5 is expanded and depressurized by the second expansion valve 6 (P5), becomes a gas-liquid two-phase refrigerant, and flows into the evaporator 3. The gas-liquid two-phase refrigerant that has flowed into the evaporator 3 evaporates by exchanging heat with air or water and the like, and becomes a gas refrigerant and flows out of the evaporator 3. The gas refrigerant (P6) flowing out from the evaporator 3 is sucked into the compressor 1 again.

  The gas refrigerant separated by the economizer 5 is sucked into the intermediate suction chamber 15 of the compressor 1 through the intermediate suction pipe 17 and the intermediate suction port 15a. The gas refrigerant sucked into the intermediate suction chamber 15 is uniformly distributed over the entire circumference in the circumferential direction C of the inflow port 15c by the rectifying action of the guide plates 21, 22a to 22e. The air is sucked into the impeller 13. Specifically, the gas refrigerant is sucked into the impeller 13 from a substantially intermediate portion between the front edge portion 13b and the rear edge portion 13c of the blade 13a. The gas refrigerant sucked into the impeller 13 is sucked into the chamber 14 of the compressor 1 from the evaporator 3 and merged with the refrigerant sucked into the impeller 13 from the front edge portion 13b side (P8), and the merged refrigerant is compressed. And discharged (P1).

  By the operations of the refrigeration cycle apparatus 101 and the compressor 1 described above, the entire circumference of the inflow port 15c in the circumferential direction C is uniformly sucked into the impeller 13 through the inflow port 15c. The compression performance by centrifugal compression can be improved. Further, this can improve the refrigeration capacity of the entire refrigeration cycle apparatus 101 (enthalpy difference Δh shown in FIG. 5).

  In addition, as shown in FIG. 4, although the shape of the cross section perpendicular | vertical to the axial direction L of the intermediate | middle suction chamber 15 shall be substantially elliptical ring shape, it is not limited to this. That is, the guide plate arranged in the intermediate suction chamber 15 is sucked into the impeller 13 through the inlet 15c uniformly over the entire circumference in the circumferential direction C of the inlet 15c. As long as the guide channel can be configured, for example, it may have a substantially perfect circular shape.

[Embodiment 2]
The compressor 1 according to the second embodiment will be described focusing on differences from the structure of the compressor 1 according to the first embodiment.

(Structure of the compressor 1 and the structure of the guide plate in the intermediate suction chamber 15)
FIG. 6 is a cross-sectional view in the axial direction of the rotating shaft of the compressor according to the second embodiment. The structure of the compressor 1 and the structure of the guide plate in the intermediate suction chamber 15 will be described with reference to FIG.

  The casing 11 is a substantially elliptical ring-shaped space communicating with two intermediate suction pipes (not shown) for sucking the gas refrigerant separated by the economizer 5 on the outer peripheral side, and the impeller 13 is accommodated therein. An intermediate suction chamber 15 communicating with the working chamber 11a is provided. Specifically, the intermediate suction chamber 15 includes two intermediate suction pipes via intermediate suction ports 15 a and 15 d drilled at the outer peripheral surface of the casing 11 and at positions corresponding to the rotation shaft 12. To communicate with each other. Further, the intermediate suction chamber 15 communicates with the working chamber 11a through an inflow port 15c formed inside in the radial direction.

  The intermediate suction chamber 15 is a substantially elliptical ring-shaped space, and communicates with the working chamber 11a through an inflow port 15c formed inside in the radial direction. Further, in the intermediate suction chamber 15, the gas refrigerant sucked from the intermediate suction ports 15 a and 15 d is interposed between the front edge portion and the rear edge portion of the blade 13 a with respect to the impeller 13 through the inlet port 15 c. A plurality of guide plates (described later) that rectify so as to be sucked in uniformly from the portion in the circumferential direction of the rotating shaft 12 (hereinafter referred to as the circumferential direction) are arranged. That is, the gas refrigerant separated from the gas and liquid by the economizer 5 is sucked into the intermediate suction chamber 15 through the intermediate suction pipes and the intermediate suction ports 15a and 15d, and is circulated in the circumferential direction by the rectifying action of the guide plate (described later). From the outer peripheral side in the radial direction to the inner peripheral side so as to be uniform over the entire area. The gas refrigerant is sucked into the impeller 13 through the inflow port 15c from a substantially intermediate portion between the front edge portion and the rear edge portion of the blade 13a.

  As shown in FIG. 6, the shape of the cross section perpendicular to the axial direction (hereinafter referred to as the axial direction) of the rotary shaft 12 in the intermediate suction chamber 15 is perpendicular to the radial direction passing through the centers of the intermediate suction ports 15a and 15d. It has a substantially elliptical ring shape with the long axis as the major axis. In the intermediate suction chamber 15, the intermediate suction refrigerant F2a sucked through the intermediate suction port 15a is rectified, and the intermediate suction chamber 15 is circulated to the impeller 13 through the inlet 15c. Guide plates 31, 32a to 32e are disposed to be sucked into a portion between the front edge portion and the rear edge portion of 13a. Further, in the intermediate suction chamber 15, the intermediate suction refrigerant F2b sucked through the intermediate suction port 15d is rectified and circulated in the intermediate suction chamber 15 to the impeller 13 through the inlet 15c. The guide plates 41 and 42a to 42e are disposed to be sucked into a portion between the front edge portion and the rear edge portion of the blade 13a.

  The guide plate 31 divides the intermediate suction port 15a into three suction ports of suction port portions A1 to A3, and the intermediate suction refrigerant F2a sucked through the intermediate suction port 15a is respectively passed through the suction port portions A1 to A3. Rectify so as to flow in three directions. That is, in the intermediate suction refrigerant F2, the gas refrigerant sucked from the suction port portion A1 by the guide plate 31 goes to the inlet portion l1, which is the portion of the inlet 15c facing the intermediate suction port 15a. Further, among the intermediate suction refrigerant F2a, the gas refrigerant sucked from the suction port portion A2 by the guide plate 31 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inlet portion 12 corresponding to the inlet 15c. . Of the intermediate suction refrigerant F2a, the gas refrigerant sucked from the suction port portion A3 by the guide plate 31 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inlet portion l3 that is the portion of the inlet 15c. .

  The guide plate 32a allows the gas refrigerant sucked from the suction port portion A1 by the guide plate 31 among the intermediate suction refrigerant F2a to be uniformly directed from the inlet portion l1 of the inlet 15c toward the impeller 13 in the circumferential direction. Rectify to flow in.

  The guide plate 32b is directed toward the impeller 13 so that the gas refrigerant sucked from the suction port portion A2 by the guide plate 31 among the intermediate suction refrigerant F2a is distributed from the inlet portion l2 of the inlet port 15c in the circumferential direction. And rectify so that it flows. Further, the guide plate 32d has an intermediate suction chamber that is shifted 90 ° in the circumferential direction from the center of the intermediate suction port 15a from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 that is shifted by a predetermined angle in the circumferential direction from the center of the intermediate suction port 15a. The flow path of gas refrigerant is arrange | positioned so that it may become narrow gradually in the circumferential direction as it goes to 15 inner peripheral wall vicinity. By arranging the guide plate 32d in this manner, the gas refrigerant can be promoted so as to go to a portion of the inflow port portion 12 that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15a. Therefore, the gas refrigerant sucked from the suction port portion A2 is rectified by the guide plates 32b and 32d so as to flow uniformly from the inlet portion l2 of the inlet port 15c toward the impeller 13 in the circumferential direction. .

  The guide plate 32c is directed toward the impeller 13 so that the gas refrigerant sucked from the suction port portion A3 by the guide plate 31 among the intermediate suction refrigerant F2a is distributed from the inlet portion l3 of the inlet port 15c in the circumferential direction. And rectify so that it flows. Further, the guide plate 32e is formed in the intermediate suction chamber that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15a from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 that is shifted from the center of the intermediate suction port 15a by a predetermined angle in the circumferential direction. The flow path of gas refrigerant is arrange | positioned so that it may become narrow gradually in the circumferential direction as it goes to 15 inner peripheral wall vicinity. By disposing the guide plate 32e in this manner, the gas refrigerant can be promoted so as to go to a portion of the inlet portion l3 that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15a. Therefore, the gas refrigerant sucked from the suction port portion A3 is rectified by the guide plates 32c and 32e so as to flow uniformly from the inlet portion l3 of the inlet port 15c toward the impeller 13 in the circumferential direction. .

  The guide plate 41 divides the intermediate suction port 15d into three suction ports of suction port portions A4 to A6, and the intermediate suction refrigerant F2b sucked through the intermediate suction port 15d is respectively passed through the suction port portions A4 to A6. Rectify so as to flow in three directions. That is, in the intermediate suction refrigerant F2b, the gas refrigerant sucked from the suction port portion A4 by the guide plate 41 goes to the inlet portion l4 that is a portion of the inlet 15c facing the intermediate suction port 15d. Further, among the intermediate suction refrigerant F2b, the gas refrigerant sucked from the suction port portion A5 by the guide plate 41 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inlet portion 15 that is the portion of the inlet 15c. . Of the intermediate suction refrigerant F <b> 2 b, the gas refrigerant sucked from the suction port portion A <b> 6 by the guide plate 41 travels along the inner peripheral wall of the intermediate suction chamber 15 toward the inlet portion 16 that is the portion of the inlet 15 c. .

  In the intermediate suction refrigerant F2b, the guide plate 42a causes the gas refrigerant sucked from the suction port portion A4 by the guide plate 41 toward the impeller 13 from the inlet portion 14 of the inlet 15c uniformly in the circumferential direction. Rectify to flow in.

  The guide plate 42b is directed toward the impeller 13 so that the gas refrigerant sucked from the suction port portion A5 by the guide plate 41 in the intermediate suction refrigerant F2b is distributed from the inlet portion 15 of the inlet 15c in the circumferential direction. And rectify so that it flows. Further, the guide plate 42d is formed in an intermediate suction chamber that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15d from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 that is shifted from the center of the intermediate suction port 15d by a predetermined angle in the circumferential direction. The flow path of gas refrigerant is arrange | positioned so that it may become narrow gradually in the circumferential direction as it goes to 15 inner peripheral wall vicinity. By disposing the guide plate 42d in this manner, the gas refrigerant can be promoted so as to go to a portion of the inflow port portion 15 that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15d. Therefore, the gas refrigerant sucked from the inlet port portion A5 is rectified by the guide plates 42b and 42d so as to flow uniformly from the inlet port portion 15 of the inlet port 15c toward the impeller 13 in the circumferential direction. .

  The guide plate 42c is directed toward the impeller 13 so that the gas refrigerant sucked from the suction port portion A6 by the guide plate 41 among the intermediate suction refrigerant F2b is distributed from the inlet portion l6 of the inlet port 15c in the circumferential direction. And rectify so that it flows. Further, the guide plate 42e is formed in an intermediate suction chamber that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15d from the vicinity of the inner peripheral wall of the intermediate suction chamber 15 that is shifted from the center of the intermediate suction port 15d by a predetermined angle in the circumferential direction. The flow path of gas refrigerant is arrange | positioned so that it may become narrow gradually in the circumferential direction as it goes to 15 inner peripheral wall vicinity. By arranging the guide plate 42e in this manner, the gas refrigerant can be promoted so as to be directed to a portion of the inflow port portion 16 that is shifted by 90 ° in the circumferential direction from the center of the intermediate suction port 15d. Therefore, the gas refrigerant sucked from the inlet port portion A6 is rectified by the guide plates 42c and 42e so as to flow uniformly from the inlet port portion l6 of the inlet port 15c toward the impeller 13 in the circumferential direction. .

  Further, the guide plates 32d and 42d are formed on the inner peripheral wall portion (the inlet portion 12 and the inlet portion 12 of the inlet port 15c) of the intermediate suction chamber 15 which is shifted by 90 ° in the circumferential direction from the center of the intermediate inlet port 15a (intermediate inlet port 15d). The flow path of the gas refrigerant is partitioned at the boundary portion with the portion 15). Therefore, depending on the arrangement configuration of the guide plates 32d and 42d, the gas refrigerant sucked from the suction port portion A2 and directed toward the inlet portion l2, and the gas refrigerant sucked from the suction port portion A5 and directed toward the inlet portion l5. Will not mix.

  Further, the guide plates 32e and 42e are formed on the inner peripheral wall portion (the inlet portion l3 and the inlet port of the inlet port 15c) of the intermediate suction chamber 15 which is shifted by 90 ° in the circumferential direction from the center of the intermediate inlet port 15a (intermediate inlet port 15d). The flow path of the gas refrigerant is partitioned by a boundary portion with the portion l6). Therefore, depending on the arrangement configuration of the guide plates 32e and 42e, the gas refrigerant sucked from the inlet port portion A3 and directed toward the inlet port portion 13 and the gas refrigerant sucked from the inlet port portion A6 and directed toward the inlet port portion l6. Will not mix.

  Other structures of the compressor 1 are the same as those of the compressor 1 according to the first embodiment.

  With the arrangement configuration of the guide plates 31 and 32a to 32e as described above, a guide channel in the intermediate suction chamber 15 of the intermediate suction refrigerant F2a sucked from the intermediate suction port 15a is formed. Moreover, the guide flow path in the intermediate | middle suction chamber 15 of the intermediate | middle suction refrigerant | coolant F2b suck | inhaled from 15d of intermediate | middle suction ports is formed by the arrangement structure of the guide plates 41 and 42a-42e.

  Further, the guide plates 31 and 32a to 32e are arranged and configured such that the area ratio of the suction inlet portions A1 to A3 is substantially the same as the area ratio of the inlet portions 11 to l3. Therefore, the ratio of the amount of the gas refrigerant toward each of the inlet portions l1 to l3 is substantially the same as the ratio of the areas of the inlet portions A1 to A3. In other words, the intermediate suction refrigerant F2a flows into the impeller 13 through the inlet 15c uniformly over the inlet portions l1 to l3, that is, the circumferential half of the inlet 15c.

  Further, the guide plates 41, 42a to 42e are arranged and configured such that the area ratio of the suction inlet portions A4 to A6 is substantially the same as the area ratio of the inlet portions l4 to l6. Therefore, the ratio of the amount of gas refrigerant toward each of the inlet portions l4 to l6 is substantially the same as the ratio of the areas of the inlet portions A4 to A6. That is, the intermediate suction refrigerant F2b flows into the impeller 13 through the inlet 15c uniformly over the inlet portions l4 to l6, that is, the half circumference in the circumferential direction of the inlet 15c.

  Further, the intermediate suction refrigerants F2a and F2b sucked from the intermediate suction ports 15a and 15d have the same amount. Thus, the entire intermediate suction refrigerant is uniformly introduced into the impeller 13 through the inlet 15c over the entire circumference in the circumferential direction of the inlet 15c, and the compression performance of the impeller 13 by centrifugal compression is improved. Thus, the refrigeration capacity of the entire refrigeration cycle apparatus 101 can be improved.

  The intermediate suction refrigerants F2a and F2b sucked from the intermediate suction ports 15a and 15d have the same amount, but the present invention is not limited to this. That is, the ratio between the intermediate suction refrigerant F2a and the intermediate suction refrigerant F2b is such that the area of the inlet portions l1 to l3 of the inlet 15c into which the intermediate suction refrigerant F2a flows and the flow rate of the inlet 15c into which the intermediate suction refrigerant F2b flows. If the ratio with the area of the inlet portions l4 to l6 is substantially the same, the intermediate suction refrigerants F2a and F2b need not have the same amount.

  Further, although two intermediate suction ports (intermediate suction ports 15a and 15d) through which the gas refrigerant is sucked into the intermediate suction chamber 15 are formed, the present invention is not limited to this, and three or more intermediate ports are formed. A suction port may be formed.

  Moreover, it cannot be overemphasized that the compressor 1 shown in FIG. 6 is applicable to the refrigerating-cycle apparatus 101 shown in FIG.

  As mentioned above, although Embodiment 1 and 2 were demonstrated, Embodiment 1 and 2 are not limited by the content mentioned above. In addition, the constituent elements of the first and second embodiments described above include those that can be easily conceived by those skilled in the art, those that are substantially the same, and those that are so-called equivalent ranges. Furthermore, various omissions, substitutions, and changes of the components can be made without departing from the spirit of the first and second embodiments.

DESCRIPTION OF SYMBOLS 1 Compressor 1a Gear 2 Radiator 3 Evaporator 4 1st expansion valve 5 Economizer 6 2nd expansion valve 7 Electric motor 7a Gear 11 Casing 11a Working chamber 11b Discharge flow path 12 Rotating shaft 13 Impeller 13a Blade 13b Front edge 13c Rear edge Part 14 Chamber 14a Suction port 14b Guide plate 15 Intermediate suction chamber 15a Intermediate suction port 15c Inlet 15d Intermediate suction port 16 Suction piping 17 Intermediate suction piping 21, 22a-22e Guide plates 31, 32a-32e Guide plates 41, 42a- 42e Guide plate 101 Refrigeration cycle apparatus A1 to A6 Suction port portion C Circumferential direction D Radial direction F1 Suction refrigerant F2, F2a, F2b Intermediate suction refrigerant F3 Discharge refrigerant L Axial direction L1 Upstream L2 Downstream l11-16 Inlet portion Δh Enthalpy difference

Claims (7)

An impeller fixed to the rotating shaft;
An intermediate inlet through which the refrigerant is drawn from the economizer;
The space communicated with the intermediate suction port on the outer peripheral side and formed along the circumferential direction of the rotating shaft, and the refrigerant sucked from the intermediate suction port is passed through the inlet formed on the inner peripheral side. An intermediate suction chamber for flowing into the impeller;
A plurality of guide passages disposed in the intermediate suction chamber for guiding the refrigerant sucked from the intermediate suction port to the inlet;
With
The plurality of guide channels divide the intermediate suction port into a plurality, and guide the refrigerant so as to go to each part of the inlet to the impeller,
The ratio of the area of each part of the intermediate suction port divided into a plurality of areas is the area of each part of the inflow port to the impeller corresponding to each guide channel through which the refrigerant is sucked from the intermediate suction port. A compressor characterized by substantially the same ratio . A cross-sectional shape perpendicular to the axial direction of the rotation shaft of the intermediate suction chamber is a substantially elliptical ring shape whose major axis is a direction substantially perpendicular to a radial direction passing through the intermediate suction port. The compressor according to claim 1 . The guide flow path for guiding the refrigerant from the intermediate suction port along the circumferential direction is formed so as to be gradually narrowed and partitioned so as not to mix with the refrigerant flowing from the opposite direction of the circumferential direction. The compressor according to claim 1 or 2 , wherein the compressor is formed as described above. The compressor according to any one of claims 1 to 3 , wherein the guide flow path is formed by a guide plate disposed in the intermediate suction chamber. The intermediate suction port, the compressor according to any one of claims 1 to 4, wherein a plurality.   An impeller fixed to the rotating shaft;
  An intermediate inlet through which the refrigerant is drawn from the economizer;
  The space communicated with the intermediate suction port on the outer peripheral side and formed along the circumferential direction of the rotating shaft, and the refrigerant sucked from the intermediate suction port is passed through the inlet formed on the inner peripheral side. An intermediate suction chamber for flowing into the impeller;
  A plurality of guide passages disposed in the intermediate suction chamber for guiding the refrigerant sucked from the intermediate suction port to the inlet;
  With
  The plurality of guide channels divide the intermediate suction port into a plurality, and guide the refrigerant so as to go to each part of the inlet to the impeller,
  The area of each part of the intermediate suction port divided into a plurality is in accordance with the area of each part of the inflow port to the impeller corresponding to each guide channel through which the refrigerant is sucked from the intermediate suction port. It is an area
  The compressor having a plurality of the intermediate suction ports. The compressor according to any one of claims 1 to 6,
A radiator that radiates heat from the refrigerant discharged from the compressor;
A first expansion valve that decompresses the refrigerant flowing out of the radiator into a gas-liquid two-phase refrigerant;
The economizer for gas-liquid separation of the gas-liquid two-phase refrigerant flowing out of the first expansion valve;
A second expansion valve for depressurizing the liquid refrigerant gas-liquid separated by the economizer;
An evaporator for evaporating the liquid refrigerant flowing out of the second expansion valve;
With
The refrigerant flowing out of the evaporator is sucked into the compressor,
The refrigeration cycle apparatus, wherein the gas refrigerant separated into gas and liquid by the economizer is sucked into the intermediate suction chamber from the intermediate suction port of the compressor.

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