JP6507557B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor for compressing a fluid.

  Conventionally, as a compressor of this type, for example, there is one described in Patent Document 1. 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 merging passage for merging a fluid (specifically, a refrigerant) sucked from the outside into a fluid in a compression process in a 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 portion in a portion thereof, and the thick portion increases in tooth thickness from the winding start side to the winding end side of the movable side wrap And a tooth thickness reduction part in which the tooth thickness is reduced from the tooth thickness expansion part toward the winding end side of the movable side wrap. And the diameter of the injection port is enlarged according to the thick part. As a result, the injection flow rate flowing from the injection port into the compression chamber is increased.

JP, 2013-79643, A

  The compressor of Patent Document 1 can certainly increase the injection flow rate. However, as the diameter of the injection port is expanded, the volume of the injection port, that is, the volume of the merging passage increases. The communication between the merging passage and the compression chamber is interrupted by the movable wrap in the compression process, but in this case the merging passage is not completely closed by the movable wrap, so the fluid in the process of compression Some gas flows into the injection port. That is, since the merging passage is a dead volume in the compression process of the compressor, the volume expansion of the merging passage acts in a direction to substantially reduce the discharge amount of the fluid discharged by the compressor per rotation. Cause a reduction in the efficiency of the compressor.

  In view of the above-described points, the present invention has an object to provide a compressor capable of suppressing an increase in volume of a merging passage as a dead volume while aiming to increase the flow rate of fluid flowing from the merging passage into the compression chamber. Do.

In order to achieve the above object, in the compressor invention according to claim 1, a stationary side member (12) as a non-rotating member,
A pivoting side member (11) which forms a compression chamber (15) between it and the stationary side member and changes the volume and position of the compression chamber by orbiting the stationary side member in a predetermined revolving direction (DRrt) ) And,
A intermediate pressure fluid sucked from the external scroll compressor confluence inlet for combining the fluid compression process (39) is provided in the compression chamber,
A backflow prevention device (50) for preventing backflow of fluid from the compression chamber side to the merging suction port side is provided in the compression mechanism portion (10) having the fixed side member and the turning side member ,
The fixed side member is formed with a joining passage (51) for joining the fluid sucked from the outside to the fluid in the compression process in the compression chamber from the backflow prevention device,
The merging passage has a passage inlet (51a) connected to the backflow prevention device and a passage outlet (51b) connected to the compression chamber,
Radial direction passing through the center of the virtual scroll base circle defining the side wall surface (12b) of the scroll groove (12a) of the stationary member and the center of the passage exit when viewed from the central axis direction (DR1) of the revolution movement The inclination angle α of the merging passage with respect to the reference straight line (Lst) is set in the range of “0 ° <α <180 °”, and the passage outlet moves the compression chamber by the revolution movement with respect to the passage inlet. It is characterized by being shifted to the

According to the invention described above, the fluid coupling diverted passage is immediately before the confluence passage is cut closed by turning side member, it tends to flow toward the central portion of the compression chamber.

  Here, when the fluid in the merging passage starts to flow into the compression chamber, the fluid flow is restricted by the wall surface forming the compression chamber, so an inflow pressure loss occurs, but the merging passage is communicated with the compression chamber Immediately after the pressure in the compression chamber is much lower than the pressure in the merging passage, the influence of the above-mentioned inflow pressure loss on the inflow rate to the compression chamber is small. On the other hand, immediately before the closing of the merging passage, the pressure difference between the compression chamber and the inside of the merging passage is small, so the influence of the inflow pressure loss on the inflow rate is large.

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

  Further, in the compressor of the above-described invention, the inflow rate is increased according to the direction of the merging path, and the inflow rate is increased by thickening the merging path as in the compressor of Patent Document 1. It is not possible. Therefore, the volume expansion of the merging passage as a dead volume can be suppressed.

  In addition, each code | symbol in the parentheses described in the claim and this column is an example which shows the correspondence with the specific content as described in embodiment mentioned later.

It is an explanatory view showing heat pump cycle 100 of an embodiment to which the present invention was applied. It is sectional drawing of the compressor 1 contained in the heat pump cycle 100 of FIG. It is the III-III sectional view of FIG. It is the figure which extracted the vicinity of the injection passage 51 and the non-return valve 50 in IV-IV sectional drawing of FIG. It is the figure which extracted the vicinity of the injection passage 51 and the non-return valve 50 in VV sectional drawing of FIG. FIG. 4 is a view showing a state immediately after the injection passage 51 of FIG. 3 is in communication 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. 4 is a view showing a state immediately before the injection passage 51 of FIG. 3 is closed and closed with respect to the compression chamber 15, 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 of the pair of injection passages 51 is viewed from the central axis direction DR1 of the revolution movement, direction components LV1 and LV2 of the direction of the injection passage 51 are schematically shown. FIG.

  Hereinafter, an embodiment of the present invention will be described based on the drawings. In the following embodiments including the other embodiments, parts identical or equivalent to each other are given the same reference numerals in the drawings.

First Embodiment
This embodiment applies this invention to the compressor 1 which the heat pump cycle 100 of a hot-water supply system has. FIG. 1 is an explanatory view showing a heat pump cycle 100 of the present embodiment. The heat pump cycle 100 is a heat exchanger that heats the hot water, that is, heat of the hot water, by performing heat exchange between the hot water and the refrigerant discharged from the compressor 1. Exchanger 2, first expansion valve 3 for decompressing the refrigerant flowing out of the water refrigerant heat exchanger 2, gas-liquid separator 4, second expansion valve 5, and heat from the outside air to evaporate the refrigerant An exchanger or evaporator 6 is provided. The fluid that the compressor 1 compresses, that is, the refrigerant that circulates in the heat pump cycle 100, is specifically carbon dioxide (CO ₂ ).

  The gas-liquid separator 4 is disposed on the refrigerant flow downstream side of the first expansion valve 3 and on the upstream side of the second expansion valve 5, and the gas-liquid separator 4 has an intermediate pressure reduced by the first expansion valve 3. Refrigerant flows into the The gas-liquid separator 4 separates the inflowing intermediate pressure refrigerant into a gas phase refrigerant and a liquid phase refrigerant. Then, the gas-liquid separator 4 causes a part of the gas phase refrigerant to flow to the intermediate pressure suction port 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 allowed to flow to the second expansion valve 5.

  Each of the first expansion valve 3 and the second expansion valve 5 is an electric expansion valve 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-sided 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 arrangement in which a compression mechanism unit 10 for compressing a refrigerant and a motor unit 20 for driving the compression mechanism unit 10 are arranged vertically (vertically). It is a place type. The compressor 1 includes a compression mechanism unit 10, a 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 whose both ends are closed, and a cylindrical member 31 whose axial direction is the vertical direction DR1 and a lid member 32 provided on the upper side of the cylindrical member 31. And a bottom member 33 provided on the lower side of the cylindrical member 31. The housing 30 accommodates the compression mechanism portion 10 and the motor portion 20 in the housing 30.

  The motor unit 20 has a stator 21 forming a stator and a rotor 22 forming a rotor. The stator 21 has a stator core and a stator coil wound around the stator core.

  The supply of power to the stator coils of the stator 21 is performed via the feed terminal 23. The feed terminal 23 is disposed at the lid 32 of the housing 30, that is, at the upper end 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 on 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 its internal space constitutes an oil supply passage 251 for supplying lubricating oil to the sliding portion (portion to be lubricated) of the drive shaft 25. The oil supply passage 251 opens at the lower end surface of the drive shaft 25 and is closed by the closing member 26 at the upper end surface of the drive shaft 25.

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

  The middle housing 29 has a cylindrical shape in which the outer diameter and the inner diameter increase in a stepwise manner from the upper side to the lower side, and the outermost peripheral surface thereof is fixed to the cylindrical member 31 of the housing 30. The upper side portion of the middle housing 29 constitutes a bearing portion 291. The movable scroll 11 of the compression mechanism unit 10 is accommodated in the lower side portion of the middle housing 29. The 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 which turns relative to the fixed scroll 12.

  The movable scroll 11 and the fixed scroll 12 have disk-shaped substrate portions 111 and 121. The two substrate portions 111 and 121 are disposed 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 central portion of the movable scroll base portion 111. The lower end portion 253 of the drive shaft 25 is an eccentric portion 253 which 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 preventing mechanism (not shown) for preventing the movable scroll 11 from rotating around the eccentric portion 253. Therefore, when the drive shaft 25 rotates, the movable scroll 11 does not rotate around the eccentric portion 253, and revolves (turns) in a predetermined revolving direction DRrt (see FIG. 3) with the rotation center of the drive shaft 25 as the revolution center. Do. As shown in FIG. 2, the central axis direction DR1 of the revolution movement, that is, the axial direction of the revolution center is in the vertical direction DR1.

  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 cross-sectional view taken along the line III-III in FIG.

  Further, 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 (the surface on the movable scroll 11 side) of the fixed scroll base portion 121. There is. 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 is a compression chamber 15. Specifically, the teeth 112 and 122 of the scrolls 11 and 12 mesh with each other and contact each other at a plurality of points, thereby forming a plurality of compression chambers 15. And, as shown in FIG. 3, the compression chamber 15 extends in the revolving direction DRrt and has a crescent shape in which both ends of the compression chamber 15 are pointed when viewed from the central axis direction DR1 of the revolving 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 with respect 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 the refrigerant suction port 36 and the refrigerant supply chamber 128. A refrigerant pipe 38 (see FIG. 1) for leading 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 as shown by arrow FLin. Flow into The refrigerant supply chamber 128 of the fixed scroll base portion 121 has a communication port 128a communicating with the scroll groove 12a, and is in communication with the outermost portion of the scroll groove 12a through the communication port 128a.

  In the central portion of the fixed scroll base portion 121, a main discharge hole 123 is formed to which the refrigerant compressed in the compression chamber 15 is discharged. Further, a pair of sub-discharge holes 126 which are thinner than the main discharge hole 123 and disposed radially outside the main discharge hole 123 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 on the lower side of the main discharge hole 123 in the fixed scroll substrate portion 121 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 dividing member 18 fixed to the lower surface of the fixed scroll 12. In the discharge chamber 124, a reed valve serving as a check valve for preventing the backflow of the refrigerant to the compression chamber 15 and a stopper 19 for restricting the maximum opening degree of the reed valve are disposed. The refrigerant in the discharge chamber 124 is discharged to the outside of the housing 30 through the refrigerant discharge passage 54 formed in the fixed scroll base portion 121 and the housing discharge port (not shown) formed in the cylindrical member 31 of the housing 30. It has become so.

  The housing discharge port of the housing 30 communicating with the refrigerant discharge passage 54 is connected to the refrigerant inflow port 47 of the oil separator 40 via the refrigerant pipe 48. The oil separator 40 serves to separate the lubricating oil from the compressed refrigerant discharged from the housing 30 and to 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 in the oil separator 40 flows out from the refrigerant outlet 49 of the oil separator 40 as indicated by an 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 the oil reservoir 41 provided below the cylindrical space 40a, and is returned from the oil reservoir 41 into the housing 30 through the pipe connection member 34. . The refrigerant outlet 49 of the oil separator 40 is also the refrigerant outlet 49 of the compressor 1 having the oil separator 40.

  A fixed side oil supply passage (not shown) is formed in the fixed scroll base portion 121, and a movable side oil supply passage (not shown) is intermittently communicated with the fixed side oil supply passage in the movable scroll base portion 111. Not shown) is formed. Lubricating oil from the oil separator 40 passes through the pipe connection member 34 and is supplied between the fixed scroll base portion 121 and the movable scroll base portion 111, and thereafter, between the eccentric portion 253 and the boss portion 113 of the movable scroll 11. It is supplied and supplied to the bearing members 27, 291 and the like via the oil supply passage 251. At the bottom of the housing 30, an oil storage chamber 35 in which the lubricating oil is accumulated is formed.

  Next, an injection device for injecting a refrigerant at an intermediate pressure 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 is a pressure between the discharge pressure which is the refrigerant pressure at the refrigerant discharge port 49 of the compressor 1 and the suction pressure which 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 base portion 121 from below, and the fixed scroll base portion 121 is an injection that connects the check valve 50 and the compression chamber 15. A passage 51 is formed. In the present embodiment, a portion of the fixed scroll base portion 121 where the injection passage 51 is formed and the check valve 50 constitute the above-described injection device.

  The injection passage 51 is a pore 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 of FIG. 3, and FIG. 5 is a cross-sectional view taken along line V-V of FIG. The injection passage 51 and the check valve 50 are provided in pairs as a pair. The passage outlet 51 b 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 central axis, and is disposed inside the communication port 128 a 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 efficiency of the compressor 1 tends to deteriorate as this volume increases. The passage cross sectional area and the passage length of the passage 51 are determined so as not to cause an inflow pressure loss as the flow rate of the refrigerant flowing from the injection passage 51 into the compression chamber 15 runs short and as small as possible.

  Further, the injection passage 51 has a passage inlet 51a into which the refrigerant flows and a passage outlet 51b from 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 (intermediate pressure gas refrigerant) to be injected is introduced into the interior of the compressor 1 from the intermediate pressure suction port 39 through the intermediate pressure refrigerant pipe 37 (see FIG. 1). The intermediate pressure suction port 39 communicates with the intermediate pressure introduction passage 9 provided in the dividing member 18 of FIG. 2 inside the compressor 1 and flows into the intermediate pressure suction port 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 order. Then, the intermediate pressure refrigerant flows into the compression chamber 15 by the injection passage 51 being opened to the compression chamber 15. That is, the injection passage 51 is a refrigerant in the compression process in the compression chamber 15 (in other words, in the middle of compression) of the intermediate pressure gas refrigerant sucked into the compressor 1 from the gas-liquid separator 4 provided outside the compressor 1 It becomes a passage for confluence to be joined to the Further, the intermediate pressure suction port 39 is a suction port for merging the intermediate pressure gas refrigerant from the gas-liquid separator 4 into 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 backward from the injection passage 51 to the intermediate pressure introduction passage 9. 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 is moved from the compression chamber 15 to the intermediate pressure inlet 39 (see FIG. 1). Prevent backflow. In other words, the check valve 50 allows the flow of refrigerant from the intermediate pressure introduction passage 9 to the injection passage 51 while blocking the flow of refrigerant from the injection passage 51 to the intermediate pressure introduction passage 9.

  The check valve 50 is embedded near the compression chamber 15 in the fixed scroll base portion 121. Specifically, as shown in FIGS. 4 and 5, a circle formed on the fixed scroll base portion 121 It is fitted in the hole 121a. The check valve 50 includes a valve seat 501 and a sheet-like reed valve 502. The 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 a valve seat. It is blocked by being pushed. 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, and thus the description thereof is omitted.

  Since the injection passage 51 has the above-mentioned dead volume, it is usually necessary to form the injection passage 51 to have a minimum volume in order to reduce the efficiency drop of the compressor 1. In order to achieve that, the injection passage 51 is disposed such that the injection passage 51 is parallel to the central axis direction DR1 of the revolution movement in order to connect the compression chamber 15 and the check valve 50 with the shortest distance. It is believed to be desirable.

  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 end portion of the crescent-shaped compression chamber 15, and the injection passage 51 becomes the movable scroll 11. As shown in FIG. 7, the medium pressure refrigerant is injected into the other end of the crescent-shaped compression chamber 15 immediately before the closing of the compression chamber 15 by the tooth portion 112. FIG. 6 is a view showing a state immediately after the injection passage 51 is in communication 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. Further, FIG. 7 is a view showing a state immediately before the injection passage 51 is closed and opened with respect to the compression chamber 15, and the vicinity of the passage outlet 51b of the injection passage 51 in the III-III sectional view of FIG. FIG.

  For example, assuming the comparative example in which the injection passage 51 is disposed in parallel with the central axis direction DR1 of the revolution movement as described above, the refrigerant flows in the injection passage 51 immediately after the communication or immediately before the closing in the comparative example. It is throttled to the same degree at the passage outlet 51b to cause inflow pressure loss.

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

  From this point of view, in the present embodiment, as shown in FIGS. 3 to 5, in the injection passage 51, the direction component of the injection passage 51 from the passage inlet 51a to the passage outlet 51b is a direction component LV1 in the revolution direction DRrt (see FIG. 8) is formed.

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

  That is, assuming that the refrigerant flow in the injection passage 51, in the injection passage 51, the velocity component in which the refrigerant in the injection passage 51 is directed in the revolving direction DRrt of the movable scroll 11 (same direction as the revolving direction component LV1 in FIG. 8) And is configured to flow into the compression chamber 15. FIG. 8 shows directional 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 revolution movement. Are schematically illustrated. The direction of the injection passage 51 is, strictly speaking, the direction of the passage outlet 51 b side of the injection passage 51.

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

  As described above, according to the present embodiment, the injection passage 51 causes the intermediate pressure refrigerant in the injection passage 51 to flow into the compression chamber 15 with the velocity component facing the revolution direction DRrt of the movable scroll 11. Is formed. Therefore, 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 medium pressure refrigerant can be injected from the injection passage 51 toward the wide side of the crescent-shaped compression chamber 15.

  Then, as described above, the inflow pressure loss from the injection passage 51 to the compression chamber 15 has little influence on the flow rate of the refrigerant inflow immediately after the communication of the injection passage 51 to the compression chamber 15, but closing the injection passage 51 Immediately before, it greatly affects the refrigerant inflow rate.

  Therefore, for example, as compared with the configuration in which the intermediate pressure refrigerant in the injection passage 51 flows into the compression chamber 15 without the velocity component in the revolution direction DRrt, the compression chamber 15 to the compression chamber 15 immediately before closing the injection passage 51. The inflow pressure loss can be reduced, and as a result, when viewed over the entire compression process of the refrigerant in the compression chamber 15, the flow rate of the refrigerant flowing from the injection passage 51 into the compression chamber 15 can be increased. In short, the total flow rate of the intermediate pressure refrigerant flowing from the injection passage 51 into the compression chamber 15 can be increased.

  Further, 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 which is high pressure and high temperature, and the internal pressure rise during compression can be suppressed. It is also possible to obtain the effect of reducing the power consumed by 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 to 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 the velocity component facing the revolution direction DRrt.

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

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

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

  (4) In the above-mentioned embodiment, although compressor 1 is vertical installation type, it may be horizontal installation type.

  (5) In the above embodiment, the injection passage 51 is a linearly extending hole, but if the direction of the passage outlet 51b of the injection passage 51 has the direction component LV1 in the revolution direction DRrt, It may be bent on the way from the valve 50 to the compression chamber 15.

  (6) In the above-mentioned embodiment, although the non-return valve 50 is installed inclined with respect to vertical direction DR1, it does not matter even if it faces any direction.

  (7) In the above-mentioned embodiment, although the secondary discharge hole 126 is provided in the fixed scroll base portion 121, the secondary discharge 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 embodiment, it is needless to say that the elements constituting the embodiment are not necessarily essential except in the case where it is clearly indicated that it is particularly essential, and in the case where it is considered to be obviously essential in principle. . Further, in the above embodiment, when numerical values such as the number, numerical value, amount, range and the like of the constituent elements of the embodiment are mentioned, it is clearly indicated that it is particularly essential and clearly limited to a specific number in principle. It is not limited to the specific number except in the case where Further, in the above embodiment, when referring to materials, shapes, positional relationships, etc. of constituent elements, etc., unless otherwise specified or in principle when limited to a specific material, shape, positional relationship, etc. It is not limited to the material, the shape, the positional relationship, etc.

1 Compressor 11 Movable scroll (turning side member)
12 Fixed scroll (fixed side member)
15 Compression chamber 39 Intermediate pressure inlet (Suction inlet for merging)
50 check valve (backflow prevention device)
51 Injection passage (passage for merging)
DRrt revolution direction

Claims (3)

A stationary side member (12) as a non-rotational member;
A swirling side member which forms a compression chamber (15) between the fixed side member and changes the volume and the position of the compression chamber by revolving in a predetermined revolving direction (DRrt) with respect to the fixed side member (11) and,
Confluence inlet for combining the fluid compression process in the intermediate pressure fluid sucked from outside the compression chamber (39) A scroll type compressor provided with,
The compression mechanism (10) having the fixed side member and the turning side member is provided with a backflow prevention device (50) for preventing the fluid from flowing backward from the compression chamber side to the merging suction port side,
The fixed side member is formed with a junction (51) for joining the fluid sucked from the outside to the fluid in the compression process in the compression chamber from the backflow prevention device.
The merging passage has a passage inlet (51a) connected to the backflow prevention device and a passage outlet (51b) connected to the compression chamber,
When viewed from the central axis direction (DR1) of the revolution movement, the center of a virtual scroll base circle defining the side wall surface (12b) of the scroll groove (12a) of the fixed side member and the center of the passage outlet The inclination angle α of the merging passage with respect to the radial reference straight line (Lst) to be passed is set in the range of “0 ° <α <180 °”, and the passage outlet corresponds to the revolution of the passage inlet. A compressor characterized in that the compression chamber is displaced to the moving side by movement . When viewed said centric shaft towards suited et al, the compression chamber, to claim 1, characterized in that both ends of and the compression chamber extends to the revolving direction is formed so as to have a pointed shape Description compressor. The compressor according to claim 1 or 2, characterized in that the fluid is compressed in the compression chamber is carbon dioxide.

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