JP2016079885A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of restricting an increased volume of an injection passage acting as a dead volume while an increasing flow rate of fluid flowing from an injection passage into a compression chamber is attained.SOLUTION: An injection passage 51 is formed in such a way that a middle pressure refrigerant in the injection passage 51 has a speed component facing toward a revolving direction DRrt of a movable scroll 11 and flows into a compression chamber 15. Accordingly, the middle pressure refrigerant in the injection passage 51 may easily be flown into the central portion of the compression chamber 15 just before closing of the injection passage 51. Accordingly, it is possible to reduce a loss of flowing-in pressure from the injection passage 51 into the compression chamber 15 just before closing of the injection passage 51. As a result, it is possible to increase a flow rate of refrigerant from the injection passage 51 into the compression chamber 15 as seen over an entire processing of the refrigerant at the compression chamber 15.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a compressor that compresses a fluid.

  Conventionally, as this type of compressor, there is one described in Patent Document 1, for example. The compressor described in Patent Document 1 is a scroll compressor that performs intermediate injection. The compressor of Patent Document 1 has an injection port as a joining passage that joins fluid (specifically, refrigerant) sucked from the outside to fluid in a compression process in the compression chamber. The injection port is formed at a position communicating with the compression chamber immediately after the suction closing. In addition, the movable side wrap that constitutes a part of the movable scroll includes a thick part in the part, and the thick part increases in tooth thickness from the winding start side to the winding end side of the movable side wrap. And a tooth thickness reducing portion that reduces the tooth thickness from the tooth thickness expanding portion toward the winding end side of the movable wrap. And the diameter of the injection port is enlarged according to the thick part. Thereby, the increase of the injection flow volume which flows in into a compression chamber from an injection port is aimed at.

JP 2013-79643 A

  The compressor of Patent Document 1 can certainly increase the injection flow rate. However, since the diameter of the injection port is enlarged, the volume of the injection port, that is, the volume of the merging passage is increased. The communication between the merging passage and the compression chamber is blocked by the movable wrap during the compression process, but in this case, the merging passage is not completely blocked by the movable wrap, A gas flows into the injection port. That is, since the merging passage becomes a dead volume in the compression process of the compressor, the volume expansion of the merging passage acts in a direction that substantially lowers the discharge amount of the fluid discharged by the compressor per one rotation. In addition, this causes a reduction in the efficiency of the compressor.

  An object of the present invention is to provide a compressor capable of suppressing an increase in volume of a merging passage as a dead volume while increasing the flow rate of fluid flowing from the merging passage into the compression chamber. To do.

In order to achieve the above object, in the compressor invention according to claim 1, a stationary member (12) as a non-rotating member;
A revolving side member (11) that changes the volume of the compression chamber by forming a compression chamber (15) between the fixed side member and revolving in a predetermined revolving direction (DRrt) with respect to the fixed side member. As well as
A compressor provided with a merging suction port (39) for joining fluid sucked from the outside into a fluid in a compression process in a compression chamber,
A backflow prevention device (50) for preventing the fluid from flowing back from the compression chamber side to the merging inlet side;
The stationary member is formed with a merging passage (51) for merging the fluid sucked from the outside with the fluid in the compression process in the compression chamber from the backflow prevention device,
The merging passage is formed so that the fluid in the merging passage flows into the compression chamber having a velocity component facing the revolution direction of the swivel member.

  According to the above-described invention, the merging passage is formed so that the fluid in the merging passage has a velocity component directed in the revolution direction of the swivel member and flows into the compression chamber. The fluid in the passage is likely to flow toward the central portion of the compression chamber immediately before the joining passage is closed by the swivel member.

  Here, when the fluid in the merging passage starts to flow into the compression chamber, the fluid flow is throttled by the wall surface forming the compression chamber, so that inflow pressure loss occurs, but the merging passage communicates with the compression chamber. Immediately after that, since the pressure in the compression chamber is significantly lower than the pressure in the merging passage, the influence of the inflow pressure loss on the inflow rate into the compression chamber is small. On the other hand, since the pressure difference between the compression chamber and the merging passage is small immediately before the merging passage is closed, the influence of the inflow pressure loss on the inflow flow rate is large.

  Therefore, for example, compared with the configuration in which the fluid in the merging passage flows into the compression chamber without having the velocity component in the revolution direction, the pressure loss of the fluid when flowing into the compression chamber immediately before the merging passage is closed. As a result, it is possible to increase the flow rate of the inflow flowing into the compression chamber from the merging passage when viewed over the entire fluid compression process.

  Further, in the compressor of the above-described invention, the inflow rate is increased by the direction of the merging passage, and the increase in the inflow rate is increased by thickening the merging passage as in the compressor of Patent Document 1. It is not intended. Therefore, it is possible to suppress the volume expansion of the merging passage as a dead volume.

  In addition, each code | symbol in the bracket | parenthesis described in a claim and this column is an example which shows a corresponding relationship with the specific content as described in embodiment mentioned later.

It is explanatory drawing which showed the heat pump cycle 100 of embodiment with which this invention was applied. It is sectional drawing of the compressor 1 contained in the heat pump cycle 100 of FIG. FIG. 3 is a sectional view taken along line III-III in FIG. 2. It is the figure which extracted the vicinity of the injection channel | path 51 and the non-return valve 50 in the IV-IV sectional drawing of FIG. FIG. 5 is a diagram in which the vicinity of an injection passage 51 and a check valve 50 is extracted from the VV cross-sectional view of FIG. 3. FIG. 4 is a view showing a state immediately after the injection passage 51 of FIG. 3 communicates with the compression chamber 15, and is a view showing the vicinity of the passage outlet 51 b of the injection passage 51 in the III-III sectional view of FIG. 2. 3 is a view showing a state immediately before the injection passage 51 of FIG. 3 is closed with respect to the compression chamber 15, and is a view showing the vicinity of the passage outlet 51 b of the injection passage 51 in the III-III sectional view of FIG. 2. is there. When the injection passage 51 illustrated on the lower side in FIG. 3 in the pair of injection passages 51 is viewed from the central axis direction DR1 of the revolving motion, the direction components LV1 and LV2 of the direction of the injection passage 51 are schematically illustrated. FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments including other embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
In the present embodiment, the present invention is applied to the compressor 1 included in the heat pump cycle 100 of the hot water supply system. FIG. 1 is an explanatory diagram showing a heat pump cycle 100 of the present embodiment. The heat pump cycle 100 includes a heat exchanger that heats hot water by performing heat exchange between the compressor 1 that sucks and compresses the refrigerant, and hot water and refrigerant discharged from the compressor 1, that is, water refrigerant heat. Exchanger 2, first expansion valve 3 that decompresses the refrigerant that has flowed out of the water-refrigerant heat exchanger 2, gas-liquid separator 4, second expansion valve 5, and heat that absorbs heat from outside air and evaporates the refrigerant An exchanger or evaporator 6 is provided. The fluid compressed by the compressor 1, that is, the refrigerant circulating in the heat pump cycle 100 is specifically carbon dioxide (CO ₂ ).

  The gas-liquid separator 4 is disposed on the downstream side of the refrigerant flow of the first expansion valve 3 and the upstream side of the second expansion valve 5. The gas-liquid separator 4 has an intermediate pressure reduced by the first expansion valve 3. Refrigerant flows in. The gas-liquid separator 4 separates the flowing intermediate-pressure refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant. The gas-liquid separator 4 causes a part of the gas-phase refrigerant to flow to the intermediate pressure inlet 39 of the compressor 1 through the intermediate pressure refrigerant pipe 37. On the other hand, the remaining gas-liquid two-phase refrigerant or gas-phase refrigerant is caused to flow to the second expansion valve 5.

  The first expansion valve 3 and the second expansion valve 5 are both electric expansion valves having a motor. The valve opening degree of the first expansion valve 3 and the valve opening degree of the second expansion valve 5 are respectively adjusted according to a control signal from a control device (not shown).

  FIG. 2 is a cross-sectional view of the compressor 1 included in the heat pump cycle 100 of FIG. An arrow DR1 in FIG. 2 indicates the direction of the compressor 1. That is, the double-ended arrow DR1 in FIG. 2 indicates the vertical direction DR1. The compressor 1 shown in FIG. 2 is a scroll-type electric compressor, and is a vertical type in which a compression mechanism unit 10 that compresses refrigerant and an electric motor unit 20 that drives the compression mechanism unit 10 are arranged in the vertical direction (vertical direction). It is a stand type. The compressor 1 includes a compression mechanism unit 10, an electric motor unit 20, a housing 30, an oil separator 40, and the like.

  The housing 30 is an airtight container that forms an outer shell of the compressor 1 and is airtight. The housing 30 roughly has a cylindrical shape with both ends closed, and includes a cylindrical member 31 having the vertical direction DR1 as an axial direction, and a lid member 32 provided on the upper side of the cylindrical member 31. The bottom member 33 is provided below the cylindrical member 31. The housing 30 accommodates the compression mechanism unit 10 and the electric motor unit 20 in the housing 30.

  The electric motor unit 20 includes a stator 21 that forms a stator and a rotor 22 that forms a rotor. The stator 21 has a stator core and a stator coil wound around the stator core.

  Electric power is supplied to the stator coil of the stator 21 through the power supply terminal 23. The power supply terminal 23 is disposed on the lid member 32 of the housing 30, that is, the upper end portion of the housing 30. When electric power is supplied to the stator coil, a rotating magnetic field is applied to the rotor 22 to generate a rotational force in the rotor 22, and the drive shaft 25 rotates integrally with the rotor 22. The drive shaft 25 is formed in a cylindrical shape, and an internal space thereof constitutes an oil supply passage 251 that supplies lubricating oil to a sliding portion (lubrication target portion) of the drive shaft 25. The oil supply passage 251 is opened at the lower end surface of the drive shaft 25, and the upper end surface of the drive shaft 25 is closed by the closing member 26.

  A portion of the drive shaft 25 that protrudes below the rotor 22 is provided with a flange 252 that protrudes in the horizontal direction, which is a direction orthogonal to the axial direction parallel to the vertical direction DR1. Is provided with a balance weight 254. Balance weights 221 and 222 are also provided on both sides of the rotor 22 in the vertical direction. The drive shaft 25 is supported by a bearing member 27 and a bearing portion 291 of the middle housing 29.

  The middle housing 29 has a cylindrical shape whose outer diameter and inner diameter increase stepwise from the upper side toward the lower side, and the outermost peripheral surface thereof is fixed to the cylindrical member 31 of the housing 30. An upper portion of the middle housing 29 constitutes a bearing portion 291. The movable scroll 11 of the compression mechanism unit 10 is accommodated in a lower part of the middle housing 29. A fixed scroll 12 of the compression mechanism unit 10 is disposed below the movable scroll 11. The fixed scroll 12 is a fixed side member as a non-rotating member fixed to the housing 30, and the movable scroll 11 is a turning side member that turns with respect to the fixed scroll 12.

  The movable scroll 11 and the fixed scroll 12 have disk-shaped substrate portions 111 and 121. Both substrate portions 111 and 121 are arranged so as to face each other in the vertical direction DR1. A cylindrical boss portion 113 into which the lower end portion 253 of the drive shaft 25 is inserted is formed at the center portion of the movable scroll substrate portion 111. The lower end portion 253 of the drive shaft 25 is an eccentric portion 253 that is eccentric with respect to the rotation center of the drive shaft 25.

  The movable scroll 11 and the fixed scroll 12 are provided with a rotation prevention mechanism (not shown) that prevents the movable scroll 11 from rotating about the eccentric portion 253. For this reason, when the drive shaft 25 rotates, the movable scroll 11 does not rotate around the eccentric portion 253, but revolves (turns) in a predetermined revolution direction DRrt (see FIG. 3) with the rotation center of the drive shaft 25 as the revolution center. To do. The central axis direction DR1 of the revolution movement, that is, the axial direction of the revolution center is the vertical direction DR1, as shown in FIG.

  The movable scroll 11 has a tooth portion 112 protruding from the substrate portion 111 toward the fixed scroll 12 side. The tooth portion 112 is formed in a spiral shape as shown in FIG. 3 which is a sectional view taken along line III-III in FIG.

  As shown in FIGS. 2 and 3, the fixed scroll 12 has a tooth portion 122 that meshes with the tooth portion 112 of the movable scroll 11 on the upper surface (surface on the movable scroll 11 side) of the fixed scroll substrate portion 121. Yes. The tooth portion 122 is formed in a spiral shape, thereby forming a spiral scroll groove 12a into which the movable scroll 11 is inserted.

  The movable scroll 11 and the fixed scroll 12 form a compression chamber 15 between the scrolls 11 and 12. That is, a part of the scroll groove 12 a of the fixed scroll 12 serves as the compression chamber 15. More specifically, the tooth portions 112 and 122 of the scrolls 11 and 12 mesh with each other and come into contact with each other at a plurality of locations, thereby forming a plurality of compression chambers 15. As shown in FIG. 3, the compression chamber 15 has a crescent shape extending in the revolution direction DRrt and having both ends of the compression chamber 15 pointed when viewed from the central axis direction DR1 of the revolution motion. It is formed. The movable scroll 11 changes the volume of the compression chamber 15 formed in this way by revolving in the revolving direction DRrt relative to the movable scroll 11. Specifically, decrease.

  As shown in FIGS. 2 and 3, the refrigerant is supplied to the compression chamber 15 through a refrigerant supply passage including a refrigerant inlet 36 and a refrigerant supply chamber 128. A refrigerant pipe 38 (see FIG. 1) for guiding the refrigerant flowing out of the evaporator 6 (see FIG. 1) to the compressor 1 is connected to the refrigerant suction port 36, and the refrigerant from the evaporator 6 is indicated by an arrow FLin. Flow into. The refrigerant supply chamber 128 of the fixed scroll substrate 121 has a communication port 128a that communicates with the scroll groove 12a, and communicates with the outermost peripheral portion of the scroll groove 12a via the communication port 128a.

  A main discharge hole 123 through which the refrigerant compressed in the compression chamber 15 is discharged is formed in the central portion of the fixed scroll substrate portion 121. Further, a pair of sub-discharge holes 126 that are narrower than the main discharge holes 123 and are arranged on the outer side in the radial direction with the main discharge holes 123 interposed therebetween are also formed in the central portion. A discharge chamber 124 communicating with the main discharge hole 123 and the sub discharge hole 126 is formed in the fixed scroll substrate portion 121 below the main discharge hole 123 as shown in FIG. The discharge chamber 124 is defined by a recess 125 formed on the lower surface of the fixed scroll 12 and a partition member 18 fixed on the lower surface of the fixed scroll 12. In the discharge chamber 124, a reed valve that forms a check valve that prevents the refrigerant from flowing back to the compression chamber 15 and a stopper 19 that restricts the maximum opening of the reed valve are disposed. The refrigerant in the discharge chamber 124 is discharged to the outside of the housing 30 through a refrigerant discharge passage 54 formed in the fixed scroll substrate 121 and a housing discharge port (not shown) formed in the tubular member 31 of the housing 30. It has become so.

  A housing discharge port of the housing 30 communicating with the refrigerant discharge passage 54 is connected to a refrigerant inlet 47 of the oil separator 40 via a refrigerant pipe 48. The oil separator 40 serves to separate the lubricating oil from the compressed refrigerant discharged from the housing 30 and return the separated lubricating oil into the housing 30 via the pipe connection member 34.

  The refrigerant gas, which is a compressed refrigerant discharged from the housing 30 and flowing into the refrigerant inlet 47 of the oil separator 40, is introduced into the cylindrical space 40 a in the oil separator 40. The oil separator 40 generates a swirling flow in the refrigerant gas in the cylindrical space 40a, and separates the lubricating oil from the refrigerant gas by the action of centrifugal force generated by the swirling flow. The refrigerant gas from which the lubricating oil is separated by the oil separator 40 flows out from the refrigerant outlet 49 of the oil separator 40 as indicated by the arrow FLout, and is supplied to the heat exchanger 2 (see FIG. 1). On the other hand, the separated lubricating oil is temporarily stored in an oil sump 41 provided below the cylindrical space 40a, and returned from the oil sump 41 into the housing 30 via the pipe connecting member 34. . The refrigerant outlet 49 of the oil separator 40 is also a refrigerant outlet 49 of the compressor 1 having the oil separator 40.

  A fixed-side oil supply passage (not shown) is formed inside the fixed scroll substrate portion 121, and a movable-side oil supply passage (intermittently communicating with the fixed-side oil supply passage (inside the movable scroll substrate portion 111) (Not shown) is formed. Lubricating oil from the oil separator 40 passes through the pipe connecting member 34 and is supplied between the fixed scroll substrate portion 121 and the movable scroll substrate portion 111, and then between the eccentric portion 253 and the boss portion 113 of the movable scroll 11. Supplied and supplied to the bearing members 27 and 291 through the oil supply passage 251. An oil storage chamber 35 in which lubricating oil is accumulated is formed at the bottom of the housing 30.

  Next, an injection device that injects an intermediate-pressure refrigerant supplied from the intermediate-pressure refrigerant pipe 37 (see FIG. 1) to the compressor 1 into the compression chamber 15 during compression will be described. The intermediate pressure means a pressure between the discharge pressure that is the refrigerant pressure at the refrigerant discharge port 49 of the compressor 1 and the suction pressure that is the refrigerant pressure at the refrigerant suction port 36 of the compressor 1.

  As shown in FIG. 2, the compressor 1 has a check valve 50 embedded in the fixed scroll substrate 121 from below, and the fixed scroll substrate 121 has an injection connecting the check valve 50 and the compression chamber 15. A passage 51 is formed. In the present embodiment, the portion of the fixed scroll substrate 121 where the injection passage 51 is formed and the check valve 50 constitute the injection device.

  The injection passage 51 is a fine hole extending from the check valve 50 to the compression chamber 15 as shown in FIGS. 4 is a cross-sectional view taken along line IV-IV in FIG. 3, and FIG. 5 is a cross-sectional view taken along line V-V in FIG. Two pairs of the injection passage 51 and the check valve 50 are provided in pairs. The passage outlet 51b of the injection passage 51 is disposed outside the main discharge hole 123 and the sub discharge hole 126 in the radial direction of the revolution center axis, and is disposed inside the communication port 128a of the refrigerant supply chamber 128. ing.

  The volume of the injection passage 51, which is the space between the compression chamber 15 and the check valve 50, becomes a dead volume in the compression operation of the compressor 1, and the larger the volume, the more likely the deterioration of the efficiency of the compressor 1 becomes. The passage cross-sectional area and the passage length of the passage 51 are determined so as not to cause an inflow pressure loss and to be as small as possible so that the flow rate of the refrigerant flowing into the compression chamber 15 from the injection passage 51 becomes insufficient.

  The injection passage 51 has a passage inlet 51a through which the refrigerant flows and a passage outlet 51b through which the refrigerant flows out. The passage inlet 51 a is connected to the check valve 50, and the passage outlet 51 b is connected to the compression chamber 15.

  The refrigerant to be injected (intermediate pressure gas refrigerant) is introduced into the compressor 1 from the intermediate pressure suction port 39 through the intermediate pressure refrigerant pipe 37 (see FIG. 1). The intermediate pressure inlet 39 communicates with the intermediate pressure introduction passage 9 provided in the partition member 18 in FIG. 2 inside the compressor 1, and the intermediate pressure inlet 39 flows into the intermediate pressure inlet 39 from the intermediate pressure refrigerant pipe 37. The pressurized refrigerant is supplied to the injection passage 51 through the intermediate pressure introduction passage 9 and the check valve 50 in this order. Then, the intermediate pressure refrigerant flows into the compression chamber 15 by opening the injection passage 51 to the compression chamber 15. That is, the injection passage 51 converts the intermediate pressure gas refrigerant sucked into the compressor 1 from the gas-liquid separator 4 provided outside the compressor 1 into the refrigerant in the compression process in the compression chamber 15 (in other words, in the middle of compression). This is a merging passage for merging into the refrigerant. The intermediate pressure suction port 39 is a merging suction port that joins the intermediate pressure gas refrigerant from the gas-liquid separator 4 to the refrigerant in the compression process in the compression chamber 15.

  The check valve 50 disposed between the intermediate pressure introduction passage 9 and the injection passage 51 is a backflow prevention device that prevents the refrigerant from flowing back from the injection passage 51 to the intermediate pressure introduction passage 9. More specifically, the check valve 50 is connected to the compression chamber 15 via the injection passage 51, and the refrigerant in the injection passage 51 moves from the compression chamber 15 side to the intermediate pressure suction port 39 (see FIG. 1) side. Prevent backflow. In other words, the check valve 50 allows the refrigerant flow from the intermediate pressure introduction passage 9 to the injection passage 51, while preventing the refrigerant flow from the injection passage 51 to the intermediate pressure introduction passage 9.

  The check valve 50 is embedded in the fixed scroll substrate 121 near the compression chamber 15. Specifically, as shown in FIGS. 4 and 5, the check valve 50 is a circular shape formed in the fixed scroll substrate 121. It is inserted in the hole 121a. The check valve 50 includes a valve seat 501 and a sheet-like reed valve 502, and refrigerant flow in the check valve 50 is permitted when the reed valve 502 is lifted from the valve seat 501, and the reed valve 502 is moved to the valve seat 501. It is blocked by being pressed. Since the specific structure of the check valve 50 is the same as that of the check valve disclosed in, for example, Japanese Patent Application Laid-Open No. 2013-209954, description thereof is omitted.

  Since the injection passage 51 has the above dead volume, it is usually necessary to form a minimum volume for the purpose of reducing the efficiency reduction of the compressor 1. In order to achieve this, the injection passage 51 is arranged so that the injection passage 51 is parallel to the central axis direction DR1 of the revolving motion in order to connect the compression chamber 15 and the check valve 50 with the shortest distance. It is considered desirable to be.

  Here, immediately after the injection passage 51 communicates with the compression chamber 15, as shown in FIG. 6, the intermediate pressure refrigerant is injected into one tip portion of the crescent-shaped compression chamber 15, and the injection passage 51 is moved to the movable scroll 11. The intermediate pressure refrigerant is injected into the other tip portion of the crescent-shaped compression chamber 15 as shown in FIG. 6 is a view showing a state immediately after the injection passage 51 communicates with the compression chamber 15, and is a view showing the vicinity of the passage outlet 51b of the injection passage 51 in the III-III sectional view of FIG. FIG. 7 is a view showing a state immediately before the injection passage 51 is closed with respect to the compression chamber 15, and shows the vicinity of the passage outlet 51 b of the injection passage 51 in the III-III sectional view of FIG. 2. FIG.

  For example, assuming a comparative example in which the injection passage 51 is arranged in parallel with the central axis direction DR1 of the revolving motion as described above, the refrigerant flow of the injection passage 51 in the comparative example is immediately after the communication or immediately before closing. The passage outlet 51b is throttled to the same extent and inflow pressure loss occurs.

  However, since the pressure in the compression chamber 15 is significantly lower than the pressure in the injection passage 51 immediately after the communication, the influence of the inflow pressure loss on the flow rate of the intermediate pressure refrigerant into the compression chamber 15 is reduced. On the other hand, since the pressure difference between the compression chamber 15 and the injection passage 51 is small immediately before the closing, the influence of the inflow pressure loss on the inflow flow rate is large. Therefore, even if the inflow pressure loss immediately after the communication is somewhat increased, the emphasis on reducing the inflow pressure loss immediately before the closing is more intermediate than that in the comparative example. It is considered that the inflow rate of the pressurized refrigerant can be increased.

  From such an idea, in this embodiment, as shown in FIGS. 3 to 5, the injection passage 51 has a direction component LV1 in which the direction of the injection passage 51 from the passage inlet 51a to the passage outlet 51b is the revolution direction DRrt (see FIG. 3). 8).

  Specifically, as shown in FIGS. 4 and 5, the injection passage 51 is inclined inward so that the passage outlet 51 b is displaced from the passage inlet 51 a toward the revolution center side. In addition to this, as shown in FIG. 3, when viewed from the central axis direction DR1 of the revolving motion, the injection passage 51 includes the center of the virtual scroll base circle that defines the side wall surface 12b of the scroll groove 12a and the passage outlet 51b. It is inclined by an angle α with respect to a radial reference line Lst passing through the center. Thereby, the direction of the injection passage 51 is not only the radial inward component LV2 directed to the revolution center of the movable scroll 11 but also the revolution direction DRrt when viewed from the central axis direction DR1 of the revolution movement as shown in FIG. Direction component LV1.

  That is, assuming the refrigerant flow in the injection passage 51, the injection passage 51 has a velocity component in which the refrigerant in the injection passage 51 faces the revolution direction DRrt of the movable scroll 11 (the same direction as the revolution direction component LV1 in FIG. 8). It can be said that it is formed so as to flow into the compression chamber 15. 8 shows the direction components LV1 and LV2 of the direction of the injection passage 51 when the injection passage 51 shown on the lower side in FIG. 3 of the pair of injection passages 51 is viewed from the central axis direction DR1 of the revolving motion. FIG. Strictly speaking, the direction of the injection passage 51 is the direction of the injection passage 51 toward the passage outlet 51b.

  Note that the angle α with respect to the radial reference straight line Lst shown in FIG. 3 is sufficient if the direction of the injection passage 51 has a direction component LV1 (see FIG. 8) in the revolution direction DRrt, for example, “0 ° <α <180. It may be set within the range of “°”.

  As described above, according to the present embodiment, the injection passage 51 has the intermediate pressure refrigerant in the injection passage 51 so as to flow into the compression chamber 15 with a speed component facing the revolution direction DRrt of the movable scroll 11. Is formed. Accordingly, the intermediate pressure refrigerant in the injection passage 51 is likely to flow toward the central portion of the compression chamber 15 as indicated by the arrow FLj immediately before the injection passage 51 shown in FIG. 7 is closed. In other words, the intermediate pressure refrigerant can be injected from the injection passage 51 toward the wide side of the crescent-shaped compression chamber 15.

  As described above, the inflow pressure loss from the injection passage 51 to the compression chamber 15 does not significantly affect the refrigerant inflow rate immediately after the injection passage 51 communicates with the compression chamber 15, but the injection passage 51 is closed. Immediately before, the refrigerant flow rate is greatly affected.

  Therefore, for example, compared with a configuration in which the intermediate pressure refrigerant in the injection passage 51 flows into the compression chamber 15 without having a speed component in the revolution direction DRrt, the injection passage 51 is compressed from the compression chamber 15 immediately before the injection passage 51 is closed. As a result, the flow rate of the refrigerant flowing into the compression chamber 15 from the injection passage 51 can be increased when viewed over the entire compression process of the refrigerant in the compression chamber 15. In short, the total flow rate of the intermediate pressure refrigerant flowing into the compression chamber 15 from the injection passage 51 can be increased.

  In addition, by directing the injection passage 51 in the revolving direction DRrt of the movable scroll 11, there is also an effect of cooling the central portion in the compression chamber 15 that is at high pressure and high temperature, and an increase in internal pressure during compression can be suppressed. It is also possible to obtain the effect of reducing the power consumed by the compression.

  Further, according to the present embodiment, the injection passage 51 is formed such that the direction of the injection passage 51 from the passage inlet 51a toward the passage outlet 51b has a direction component LV1 (see FIG. 8) in the revolution direction DRrt. . Therefore, it is possible to cause the intermediate pressure refrigerant passing through the injection passage 51 to be injected into the compression chamber 15 with a speed component facing the revolution direction DRrt.

(Other embodiments)
(1) In the above-described embodiment, the present invention is applied to the heat pump cycle 100 of the hot water supply system, but may be applied to anything, for example, may be applied to a heat pump system of a vehicle air conditioner, The present invention may also be applied to heat pump systems for industrial and household air conditioners. Moreover, the present invention may be applied to a compressor used for applications other than heat pumps.

  (2) In the above-described embodiment, the compressor 1 is a scroll compressor. However, the compressor 1 is not necessarily limited to this. For example, a rolling piston type rotary compression as disclosed in JP-A-11-294355 is disclosed. It can be a machine.

  (3) In FIG. 1 of the above-described embodiment, the gas-liquid separator is not provided in the path through which the refrigerant flows from the evaporator 6 to the compressor 1, but the gas-phase refrigerant flows exclusively through the compressor 1. On the other hand, a gas-liquid separator for storing the liquid phase refrigerant may be provided.

  (4) In the above-described embodiment, the compressor 1 is a vertical type, but may be a horizontal type.

  (5) In the above-described embodiment, the injection passage 51 is a linearly extending hole. However, if the direction of the injection passage 51 on the side of the passage outlet 51b has a direction component LV1 in the revolution direction DRrt, a check is made. Even if it is bent in the middle from the valve 50 to the compression chamber 15, it does not matter.

  (6) In the above-described embodiment, the check valve 50 is installed to be inclined with respect to the up-down direction DR1, but may be oriented in any direction.

  (7) In the above-described embodiment, the sub-ejection hole 126 is provided in the fixed scroll substrate portion 121. However, the sub-ejection hole 126 may be omitted.

  In addition, this invention is not limited to above-described embodiment, In the range described in the claim, it can change suitably. Further, in the above-described embodiment, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered to be essential in principle. . Further, in the above embodiment, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is particularly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to a specific number except for cases. Further, in the above embodiment, when referring to the material, shape, positional relationship, etc. of the component, etc., unless otherwise specified and in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship and the like are not limited.

1 Compressor 11 Movable scroll (turning side member)
12 Fixed scroll (fixed side member)
15 Compression chamber 39 Intermediate pressure inlet (Merging inlet)
50 Check valve (backflow prevention device)
51 Injection passage (confluence passage)
DRrt Revolution direction

Claims (4)

A stationary member (12) as a non-rotating member;
A revolving side member (11) that forms a compression chamber (15) between the fixed side member and changes the volume of the compression chamber by revolving in a predetermined revolving direction (DRrt) with respect to the fixed side member. And with
A compressor provided with a merging suction port (39) for joining fluid sucked from the outside to fluid in a compression process in the compression chamber,
A backflow prevention device (50) for preventing fluid from flowing back from the compression chamber side to the merging inlet side;
The stationary member is formed with a merging passage (51) for merging the fluid sucked from the outside from the backflow prevention device to the fluid in the compression process in the compression chamber,
The merging passage is formed so that the fluid in the merging passage has a velocity component directed in the revolution direction of the swivel member and flows into the compression chamber. The merging passage is
A passage inlet (51a) connected to the backflow prevention device and a passage outlet (51b) connected to the compression chamber;
2. The compressor according to claim 1, wherein a direction of the merging passage from the passage inlet toward the passage outlet has a direction component (LV1) in the revolution direction. A scroll compressor,
The compression chamber is formed so as to extend in the revolution direction and have both ends of the compression chamber pointed when viewed from the central axis direction (DR1) of the revolution motion. Item 3. The compressor according to Item 1 or 2.   The compressor according to any one of claims 1 to 3, wherein the fluid compressed in the compression chamber is carbon dioxide.

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